Cycle process device, thermal management system, vehicle and method

Abstract

The invention relates to a cycle process device (10), in particular a heat pump, comprising: a refrigerant circuit which is designed such that a refrigerant can circulate therein, an evaporator (11) and a condenser (12) which are each arranged in the refrigerant circuit and are designed to exchange thermal energy, at least one expansion valve (13) which is arranged in the refrigerant circuit and is designed to adjust a pressure of the refrigerant, at least one compressor unit (14) which is arranged in the refrigerant circuit and is designed to compress the refrigerant, a drive unit (15) which is arranged in the refrigerant circuit and is designed to drive a compressor unit (14), wherein the drive unit (15) is thermally coupled to the refrigerant circuit in order to transmit thermal energy to the refrigerant, and a control unit which is designed to control the drive unit, wherein the control unit is designed to control the drive unit on the basis of temperature information.

Description

[0001] ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26

[0002] Cycle process device, thermal management system, vehicle and process

[0003] The present invention relates to a cyclic process device, in particular a heat pump, a thermal management system, a vehicle and a method.

[0004] It is well known that thermodynamic cycles are used, for example, in electric or hybrid vehicles. Heat pumps, for instance, can provide the necessary heating and cooling for the entire vehicle at the required temperature levels. This heating and cooling capacity can be transferred to the components to be heated and cooled using a refrigerant, such as water. Thermodynamic cycles in a thermal management system utilize thermal energy supplied by the environment or a reservoir. The lower the ambient temperature, the lower the temperature of the refrigerant must be, and consequently, the lower the low-pressure level at the evaporator, in order to extract sufficient thermal energy from the environment. The lower the low-pressure level, the lower the density of the refrigerant drawn in at the inlet of a compressor unit.The low density results in a low mass flow rate. This low mass flow rate also reduces the thermal output, particularly the heating output. At low ambient temperatures, the heating output generated by the cycle devices may no longer be sufficient to meet the heating demand. In existing thermal management systems with cycle devices, a separate electric heater, such as an electric auxiliary heater or a PTC heater, can be used to provide sufficient heating output.

[0005] It has therefore become apparent that there is a need to provide a circular process device or a heat pump that enables improved heating performance.

[0006] The object of the present invention is to provide a thermodynamic cycle device, particularly with regard to heating performance. It is further an object of the present invention to provide a thermal management system with such a thermodynamic cycle device, a vehicle, and a method.

[0007] The problem is solved by a circular process device with the features of claim 1 and by a thermal management system with the features of claim 8, by a vehicle with the features of claim 9 and by a method with the features of claim 10.

[0008] A first aspect of the present invention relates to a cyclic process device, in particular a heat pump, comprising: a refrigerant circuit configured to allow a refrigerant to circulate in it, an evaporator and a condenser, each arranged in the refrigerant circuit and configured for the exchange of thermal energy, at least one expansion valve arranged in the refrigerant circuit and configured to adjust the pressure of the refrigerant, at least one compressor unit arranged in the refrigerant circuit and configured to compress the refrigerant, a drive unit arranged in the refrigerant circuit and configured to drive a compressor unit, wherein the drive unit is thermally coupled to the refrigerant circuit to transfer thermal energy to the refrigerant, and a control unit configured to control the drive unit.the control unit is designed to control the drive unit based on temperature information.

[0009] Compared to the prior art, the present invention offers the advantage that the power loss of the drive unit can be varied to transfer thermal energy to the refrigerant. The compressor unit is driven by the drive unit. Depending on the operating point, the drive unit operates with varying efficiencies. The power loss must be dissipated in the form of heat energy. This heat energy is preferably dissipated via the refrigerant of the heat pump. Heat is usually also dissipated to the environment, regardless of the cooling method. The power loss of the compressor unit's drive unit is used to generate additional heating power. For this purpose, the drive unit can, for example, be operated with low efficiency, i.e., high power loss, using special current-driven strategies. ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26The power loss from the electric drive motor is transferred to the refrigerant as described. This makes it possible to supply additional heat energy to the refrigerant in the refrigerant circuit as needed. For example, this can compensate for a low temperature in the refrigerant circuit that is insufficient to provide enough heat energy for the evaporator. In this way, it is possible to achieve sufficient heating capacity from the heat pump and meet the heating demand, even with a low temperature in the refrigerant circuit.

[0010] The cycle device can preferably be a heat pump. The cycle device can be designed to allow a refrigerant to circulate in one flow direction. More precisely, the cycle device can be designed to have a refrigerant circuit in which the refrigerant can circulate in one flow direction.

[0011] A thermodynamic cycle can be understood as a sequence of state changes of a fluid, referred to as the working fluid (e.g., a refrigerant), along a closed trajectory within the fluid's state space. The working fluid or refrigerant can be a liquid, vapor, and / or a gas. During the cycle, the working fluid or refrigerant can only pass through states that are in thermodynamic equilibrium. The state changes in the working fluid or refrigerant can be triggered by changes in state variables such as pressure, temperature, or volume. Typically, mechanical and thermal energy are converted into one another during the passage of a thermodynamic cycle.Since the corresponding forms of energy transport, mechanical work and heat, are process variables, the amount of mechanical work performed by or on the working medium and the amount of heat absorbed or released by the working medium depend on the path of the cycle. Thermodynamic cycles are used, for example, to model the operation of heat pumps and refrigeration machines, such as refrigerators. Ideal Carnot cycles, in which a working medium is alternately brought into contact with two given heat reservoirs, define the theoretically possible maximum efficiency under these conditions.

[0012] The expansion valve can, for example, include a valve or be designed as a valve. In particular, the expansion valve can be designed as a direct-acting valve. This makes it possible to actively set or vary the pressure level in the refrigerant circuit.

[0013] The refrigerant circuit comprises a piping system designed to allow the refrigerant to flow through it in the direction of flow. The piping system can include multiple lines. The components of the cycle device are at least indirectly interconnected via this piping system.

[0014] The evaporator and condenser are heat exchangers, in particular plate heat exchangers. The evaporator and condenser are preferably thermally coupled to a refrigerant circuit. The refrigerant circuit is designed to be circulated by a refrigerant. In particular, the evaporator can be thermally coupled to a low-temperature circuit and the condenser to a high-temperature circuit. The evaporator is designed to transfer thermal energy from the refrigerant in the low-temperature circuit to the refrigerant in the refrigerant circuit. The condenser is designed to transfer thermal energy from the refrigerant in the refrigerant circuit to the refrigerant in the high-temperature circuit.

[0015] The compressor unit is designed to compress the refrigerant in the refrigerant circuit. The compressor unit can, for example, be a scroll compressor. The compressor unit is located in the refrigerant circuit downstream of the evaporator in the refrigerant flow direction. The refrigerant compressed by the compressor unit is in a gaseous state.

[0016] The drive unit can be integrated with the compressor unit as a single component. The drive unit is preferably arranged upstream of the compressor unit in the refrigerant flow direction (ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26). The drive unit is designed to drive the compressor unit and is thermally coupled to the refrigerant circuit to transfer thermal energy to the refrigerant. The drive unit is preferably designed as an electric motor. The drive unit is designed to be at least partially permeated by the refrigerant flow. For example, the refrigerant can flow through a stator and / or a rotor of the drive unit. This allows the drive unit to transfer thermal energy to the refrigerant, thus cooling the drive unit.

[0017] The control unit is designed to control the drive unit. The control unit controls the drive unit based on temperature information. This temperature information can be indicative of the temperature of the refrigerant and / or a coolant. In particular, the control unit can be designed to control the power loss of the drive unit. Power loss refers to the power of the drive unit that is transferred as thermal energy to the refrigerant in the coolant circuit. For example, the control unit is designed to control the power electronics of the drive unit. The power electronics can comprise various electronic components. For example, the power electronics can include a power converter, a rectifier, an inverter, a DC-DC converter, and / or a frequency converter.In particular, the drive unit can be designed to compensate for a difference between a target temperature of the refrigerant and the actual temperature of the refrigerant. For example, the control unit can control the drive unit based on temperature information, which may include an actual temperature, resulting in a higher power loss from the drive unit. This higher power loss is transferred to the refrigerant in the refrigerant circuit via thermal coupling between the drive unit and the refrigerant circuit. This allows the actual temperature of the refrigerant to be regulated. The control unit can be connected to the drive unit via signal transmission, in particular wirelessly or via a cable. ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26.

[0018] In one embodiment, a temperature sensor is arranged in the refrigerant circuit and / or the coolant circuit to obtain temperature information, with the control unit being configured to control the drive unit based on the obtained temperature information. The temperature sensor in the coolant circuit, particularly in the low-temperature circuit, can determine whether the coolant circuit temperature is sufficient to transfer enough thermal energy to the refrigerant so that a preferred refrigerant temperature level is not undershot. Furthermore, the temperature sensor can be arranged in a high-temperature coolant circuit or a heating circuit. This allows the system to determine whether a temperature level required for heating is present in the high-temperature circuit or the heating circuit. The temperature sensor in the refrigerant circuit allows the preferred temperature level to be monitored directly.For this purpose, the temperature sensor is preferably located in the area of ​​the evaporator and the compressor unit. The temperature sensor can be, for example, an invasive or a non-invasive temperature sensor.

[0019] In one embodiment, the refrigerant circuit comprises at least one low-pressure line extending downstream of the expansion valve and one high-pressure line extending downstream of the compressor unit. During operation, the refrigerant pressure in the low-pressure line is lower than in the high-pressure line, and the drive unit is thermally coupled to the low-pressure line. This allows for the transfer of additional thermal energy to the refrigerant before it enters the compressor unit. This additional thermal energy is generated by the power losses of the drive unit. This ensures that the refrigerant is completely vaporized before entering the compressor unit. Furthermore, it ensures that a preferred temperature level of the refrigerant is maintained.

[0020] In one embodiment, the cycle device comprises a medium-pressure line extending between the condenser and the compressor unit, wherein, during operation, the refrigerant pressure in the medium-pressure line is higher than the pressure in the low-pressure line and lower than the pressure in the high-pressure line, and the drive unit is thermally coupled to the medium-pressure line. ZF Friedrichshafen AG file 304897, Friedrichshafen, September 26, 2024, indicates that, during operation, the cycle does not use refrigerant flowing towards the drive unit before it enters the compressor unit's intake. Refrigerant flowing through the medium-pressure line, and thus operating at a medium-pressure level, is used to cool the drive unit.

[0021] In one embodiment, the cycle device has a second expansion valve. The second expansion valve is preferably arranged downstream of the condenser in the refrigerant circuit, in the direction of refrigerant flow. The second expansion valve allows the intermediate pressure level in the intermediate pressure line to be adjusted.

[0022] Another possible embodiment includes the following features. The low-pressure line extends between the expansion valve and the compressor unit. The high-pressure line extends between the compressor unit and at least the condenser. Preferably, the high-pressure line extends to the expansion valve or to the second expansion valve. The medium-pressure line extends between the second expansion valve and the compressor unit. The low-pressure line is configured to carry a refrigerant mass flow set at a low-pressure level. The medium-pressure line is configured to carry a refrigerant mass flow set at a medium-pressure level, wherein the medium-pressure level is higher than the low-pressure level.The high-pressure line is designed to carry a refrigerant mass flow set at a high-pressure level, where the high-pressure level is higher than the intermediate-pressure level. The intermediate-pressure line is connected in parallel to the low-pressure line. This parallel connection divides the refrigerant mass flow. The refrigerant mass flow at the intermediate-pressure level can be injected into the compressor unit or a compressor during the compression process. Introducing the power loss from the drive unit in the form of heat at the intermediate-pressure level allows refrigerant to evaporate at this level, and this intermediate-pressure mass flow can then be introduced into the compression process to increase the refrigerant mass flow at the ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26.

[0023] To increase the refrigerant flow rate in the condenser, preferably the low-pressure and medium-pressure lines are supplied with different refrigerant mass flows. The refrigerant mass flow rate at the condenser or in the high-pressure line is the sum of the refrigerant mass flow rate at the evaporator or in the low-pressure line and the refrigerant mass flow rate through the medium-pressure line. The refrigerant mass flow rate through the low-pressure line is preferably higher than the refrigerant mass flow rate through the medium-pressure line. The increased refrigerant mass flow rate in the high-pressure line at the condenser increases the heating capacity of the heat pump.

[0024] The second expansion valve can be installed in parallel with the existing expansion valve. Alternatively, the two expansion valves can be arranged in series, with the second expansion valve positioned upstream of the first in the flow direction and a branch of the refrigerant mass flow occurring between the two expansion valves at the intermediate pressure level. This branch directs part of the refrigerant mass flow to the intermediate pressure line and another part to the low pressure line. In a series arrangement of the valves, the second expansion valve is positioned upstream of the first in the fluid flow direction, so that the refrigerant mass flow is initially set to the intermediate pressure level. Subsequently, downstream of the second expansion valve, the branch splits the refrigerant mass flow set to the intermediate pressure level.Part of the refrigerant mass flow is directed into the medium-pressure line, and another part is directed into the low-pressure line. Following the branch, the first expansion valve in the low-pressure line further reduces the pressure level and adjusts it to the low-pressure level. The refrigerant mass flow at the condenser is the sum of the refrigerant mass flow at the evaporator and the refrigerant mass flow through the medium-pressure line. The refrigerant mass flow through the low-pressure line is preferably greater than the refrigerant mass flow through the medium-pressure line. The increased refrigerant mass flow at the condenser increases the heating capacity of the heat pump. ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26.

[0025] In one embodiment, the temperature sensor is located in both the low-pressure and medium-pressure lines. This allows for the acquisition of actual temperature readings in both the medium-pressure and low-pressure lines. Both temperature values ​​can be part of the temperature information transmitted to the control unit and can therefore be used to control the drive unit.

[0026] In one embodiment, the intermediate-pressure line is coupled to the compressor unit in such a way that the refrigerant from the intermediate-pressure line can be supplied to the compressor unit during a compression process. For example, the refrigerant can be supplied at the intermediate-pressure level by blowing it into the compressor unit. This allows the refrigerant mass flow rate to be increased and the absorbed thermal energy of the refrigerant mass flow rate to be increased by the additional energy from the power loss of the drive unit.

[0027] In one embodiment, a heat exchanger, in particular a precooler, is arranged in the medium-pressure line. The heat exchanger or precooler can be an additional water-refrigerant heat exchanger that essentially performs the same function as the first evaporator. It is circulated by the refrigerant at medium pressure and allows heat to flow from the cooling water to the refrigerant. The cooling water can, for example, be passed first through the precooler or heat exchanger and then through the evaporator in a counterflow configuration. Part of the water's cooling process thus takes place in the precooler or heat exchanger. Only a smaller amount of heat then needs to be extracted from the precooled water in the evaporator. This means that only a smaller refrigerant mass flow rate is required in the low-pressure line at the low-pressure level.The precooler thus offers the advantage that, with constant thermal output from the cycle system or heat pump, a reduction in compression effort is possible. Furthermore, an increase in cooling capacity and heating capacity can be achieved, thereby improving the overall efficiency of the cycle system. ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26.

[0028] Another aspect of the present invention relates to a thermal management system with a cycle process device according to one of the preceding embodiments.

[0029] Another aspect of the present invention relates to a vehicle with a thermal management system according to the preceding claim or a cycle process device according to one of the preceding embodiments.

[0030] Another aspect of the present invention relates to a method for controlling a drive unit of a compressor unit in a cycle process device, in particular according to one of the preceding embodiments, comprising the following steps: obtaining at least one temperature information; controlling the drive unit depending on the temperature information in order to vary the waste heat of the drive unit.

[0031] Individual features or embodiments of the present invention can be combined with other features or embodiments to form new embodiments. Advantages and further developments mentioned for the features or embodiments also apply analogously to the new embodiments. Further developments and advantages mentioned in connection with the device also apply analogously to the system and vice versa.

[0032] Advantageous embodiments of the invention are described in detail below with reference to the accompanying figures:

[0033] Figure 1 is a schematic view of a circular process device according to an embodiment of the present invention;

[0034] Figure 2 is a schematic view of another circular process device according to an embodiment of the present invention;

[0035] Figure 3 is a schematic view of another circular process device according to an embodiment of the present invention; and ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26

[0036] Figure 4 is a schematic view of a process.

[0037] Figure 1 shows a refrigerant circuit of a cycle device 10. The direction of refrigerant flow is indicated by the arrows. The cycle device 10 comprises an evaporator 11, a condenser 12, and an expansion valve.

[0038] 13 and a compressor unit 14. The compressor unit 14 is arranged downstream of the evaporator 11 in the direction of refrigerant flow. The condenser 12 is located downstream of the compressor unit in the direction of refrigerant flow.

[0039] The expansion valve 13 is arranged downstream of the condenser 12 and upstream of the evaporator 11 in the direction of refrigerant flow. A high-pressure line H is arranged downstream between the compressor unit 14 and the expansion valve 13 in the direction of refrigerant flow. A low-pressure line N is arranged downstream between the expansion valve 13 and the compressor unit 14 in the direction of refrigerant flow.

[0040] The evaporator 11 is coupled to a cooling water circuit KK for transferring thermal energy. The evaporator 11 is designed to extract thermal energy from the cooling water circuit KK. The condenser 12 is coupled to a heating water circuit HK for transferring thermal energy. The condenser 12 is designed to supply thermal energy to the heating water circuit HK.

[0041] The expansion valve 13 is designed to adjust the pressure of the refrigerant. In particular, the expansion valve 13 is designed to reduce the pressure of the refrigerant from a high-pressure level to a low-pressure level. The expansion valve 14 can be designed as a directly controllable valve for this purpose.

[0042] The compressor unit 14 is operatively connected to a drive unit 15. In other words, the drive unit 15 drives the compressor unit 14. The drive unit

[0043] The drive unit 15 is coupled to the low-pressure line N for the transfer of thermal energy. This means that the drive unit 15 is cooled, at least partially, by the refrigerant. It is possible that individual components, such as a rotor and / or a stator, of the drive unit 15 are cooled by the refrigerant flowing through them. The drive unit 15 is signal-connected to a control unit (not shown). The control unit serves to control the drive unit 15. For example, the drive unit 15 can be operated with a low efficiency, i.e., high power loss, using a special power supply strategy. For this purpose, the drive unit 15 would have additional or special loads or resistors. The power loss of the drive unit 15 is transferred to the refrigerant. This allows additional thermal energy to be transferred to the refrigerant.The control unit makes it possible to regulate or vary the amount of thermal energy transferred to the refrigerant. This allows the refrigerant in the refrigerant circuit to be maintained at a preferred or efficient temperature level.

[0044] Figure 2 shows another refrigerant circuit of a cycle process device 10. This refrigerant circuit essentially corresponds to the refrigerant circuit shown in Figure 1. In contrast to the refrigerant circuit shown in Figure 1, the drive unit 15 in Figure 2 is not thermally coupled to the low-pressure line N.

[0045] The refrigerant circuit shown in Figure 2 has a medium-pressure line M. The refrigerant in the medium-pressure line is set to a medium pressure level. For this purpose, the refrigerant circuit has an additional second expansion valve 13b. More precisely, the second expansion valve 13b is located in the medium-pressure line M. The second expansion valve sets the medium pressure level in the medium-pressure line M. In Figure 2, the expansion valve 13 and the second expansion valve 13b are connected in parallel. Downstream of the condenser 12, the refrigerant circuit has a branch 16. After the branch 16, the high-pressure line H splits into two lines. The branch 16 divides the refrigerant mass flow into two smaller refrigerant mass flows. The magnitude of the refrigerant mass flows is schematically represented by the thickness of the arrows. Between the compressor unit 14 and the branch 16, i.e., in the high-pressure line H, the refrigerant mass flow is greatest.After branch 16, the refrigerant mass flow splits between the low-pressure line N and the medium-pressure line M, with the refrigerant mass flow in the low-pressure line N being greater than the refrigerant mass flow in the medium-pressure line M. ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26.

[0046] The intermediate pressure level is defined as being higher than the low pressure level at the evaporator 11 and lower than the high pressure level at the condenser 12. The refrigerant mass flow at the intermediate pressure level can be introduced into the compressor unit 14 by injection during the compression process. Introducing the electrical power loss in the form of heat at the intermediate pressure level allows refrigerant to evaporate at this level, and this intermediate pressure mass flow can then be introduced into the compression process to increase the refrigerant mass flow at the condenser 12. The refrigerant mass flow at the condenser 12 is the sum of the refrigerant mass flow at the evaporator 12 (or the low-pressure line N) and the refrigerant mass flow in the intermediate pressure line M.The increased refrigerant mass flow at condenser 12 increases the heating power of the cycle device.

[0047] Figure 3 shows an alternative configuration of the expansion valves. In Figure 3, the two expansion valves are connected in series. Downstream of the condenser 12 in the refrigerant flow direction, the second expansion valve 13b is located, which sets the intermediate pressure level of the refrigerant. Downstream of the second expansion valve 13b, the expansion valve 13 is located in series. The expansion valve 13 sets the low pressure level in the low-pressure line N. A branch 16 to the pressure line is located between the second expansion valve 13b and the expansion valve 13. The intermediate pressure line M is connected in parallel to the low-pressure line N between the branch 16 and the compressor unit. In other words, the refrigerant mass flow is divided between the second expansion valve 13b and the expansion valve 13.

[0048] Figure 4 shows a method for controlling a drive unit 15 of a compressor unit 14 in a cycle device 10, particularly according to one of the preceding embodiments. In a first step S1, a cycle device 10 is provided. In a second step S2, at least one temperature signal is obtained. The temperature signal can be obtained, for example, by means of a temperature sensor. In a third step S3, the drive unit 15 is controlled depending on the obtained temperature signal in order to vary the waste heat of the drive unit 15. The waste heat of the drive unit 15 can be controlled, for example, by controlling the power loss during operation of the drive unit 15.

[0049] Other embodiments of the present invention are possible and can be understood and carried out by persons skilled in the art when applying the claimed subject matter by studying the figures, the disclosure, and the appended claims. In particular, the respective parts / functions of each embodiment described above can also be combined with one another. In the claims, the word "comprising" does not exclude other elements or steps, and the indefinite article "a" or "an" does not exclude a plurality. The mere fact that certain measures are mentioned in interdependent claims does not mean that a combination of these measures cannot be advantageous. Any reference numerals in the claims should not be interpreted as limiting the scope of the claims.

[0050] ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26

[0051] Reference sign

[0052] H High-pressure line

[0053] M Medium pressure line

[0054] N Low-pressure line

[0055] HK heating water circuit

[0056] KK cooling water circuit

[0057] 10 Circular process device

[0058] 11 evaporators

[0059] 12 Capacitor

[0060] 13 Expansion valve

[0061] 13b second expansion valve

[0062] 14 Compressor unit

[0063] 15 Drive unit

[0064] 16 Junction

Claims

ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26 Patent claims 1. Cyclic process device (10), in particular a heat pump, comprising: - a refrigerant circuit designed to allow a refrigerant to circulate within it, - an evaporator (11) and a condenser (12), each arranged in the refrigerant circuit and designed for the exchange of thermal energy, - at least one expansion valve (13) arranged in the refrigerant circuit and designed to adjust the pressure of the refrigerant, - at least one compressor unit (14) arranged in the refrigerant circuit and designed to compress the refrigerant, - a drive unit (15) arranged in the refrigerant circuit and designed to drive a compressor unit (14), wherein the drive unit (15) is thermally coupled to the refrigerant circuit to transfer thermal energy to the refrigerant, - a control unit designed to control the drive unit, - the control unit is designed to control the drive unit based on temperature information.

2. Cycle process device (10) according to claim 1, wherein a temperature sensor is arranged in the refrigerant circuit and / or in the coolant circuit to obtain temperature information, wherein the control unit is designed to control the drive unit (15) on the basis of the obtained temperature information.

3. Circular process device (10) according to claim 1 or 2, wherein the refrigerant circuit has at least one low-pressure line (N) extending downstream of the expansion valve (13) and one high-pressure line (H) extending downstream of the compressor unit (14), wherein during operation the pressure of the refrigerant in the low-pressure line (N) is lower than in the ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26 high pressure line (H) and wherein the drive unit (15) is thermally coupled to the low pressure line (N).

4. Cycle process device (10) according to claim 3, wherein the cycle process device (10) comprises a medium-pressure line (M) extending between the condenser (12) and the compressor unit (14), wherein during operation the pressure of the refrigerant in the medium-pressure line (M) is greater than the pressure in the low-pressure line (N) and less than the pressure in the high-pressure line (H), wherein the drive unit (15) is thermally coupled to the medium-pressure line (M).

5. Cycle process device (10) according to one of the preceding claims, wherein the temperature sensor is arranged in the low-pressure line (N) and in the medium-pressure line (M).

6. Circular process device (10) according to one of the preceding claims, wherein the medium pressure line (M) is coupled to the compressor unit (14) in such a way that the refrigerant from the medium pressure line (M) can be supplied to the compressor unit (14) during a compression process.

7. Cycle process device (10) according to one of the preceding claims, wherein a heat exchanger, in particular a precooler, is arranged in the medium pressure line (M).

8. Thermal management system with a cycle process device (10) according to one of the preceding claims.

9. Vehicle with a thermal management system according to the preceding claim or a cycle process device (10) according to any of the preceding claims. ZF Friedrichshafen AG File 304897 Friedrichshafen 2024-09-26 10. Method for controlling a drive unit of a compressor unit (14) in a thermodynamic device (10), in particular according to one of the preceding claims, comprising the following steps: Obtain at least one temperature information; Controlling a drive unit (15) depending on the temperature information in order to vary the waste heat of the drive unit (15).

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