Device and method for heat transfer

Abstract

Device (100) for heat transfer, comprising: - a working medium for absorbing heat from at least one source medium, - at least one evaporator (11) for evaporating the working medium, - at least one compressor (12) for compressing the evaporated working medium, - at least one heat exchanger (13) for transferring heat from the compressed working medium to at least one secondary medium, - at least one throttle (14) for relaxing the working medium before it re-enters the evaporator (11), wherein at least one high-temperature recuperator (15) is arranged in at least one high-temperature section (A1) between the at least one compressor (12) and the at least one heat exchanger (13), wherein the at least one high-temperature recuperator (15) is designed for internal heat recuperation to the working medium in at least one section (A2) between the at least one throttle (14) and the at least one evaporator (11), wherein a mass flow of the working medium through the at least one high-temperature section (A1) can be adjusted via at least one bypass (B1) and a mass flow of the working medium through the at least one section (A2) can be adjusted via at least one further bypass (B2), and / or at least one low-temperature recuperator (16) is arranged in at least one low-temperature section (A3) between the at least one heat exchanger (13) and the at least one throttle (14), wherein the at least one low-temperature recuperator (16) is designed for internal heat recuperation to the working medium in at least one further section (A4) between the at least one throttle (14) and the at least one evaporator (11), wherein a mass flow of the working medium through the at least one low-temperature section (A3) can be adjusted via at least one further bypass (B3) and a mass flow of the working medium through the at least one further section (A4) can be adjusted via at least one further bypass (B4).

Description

[0001] The invention relates to a device for heat transfer and a corresponding method.

[0002] The thermodynamic use of waste heat or ambient heat, e.g. in industrial plants, offers great potential for making processes such as energy-intensive production processes or the heating of buildings more efficient. The operating principle of the heat pump in particular offers the possibility of transporting waste heat or ambient heat from a heat source with a lower temperature level to a heat sink with a higher temperature level. The thermal energy is transferred by a flowing working medium, also called a refrigerant. Typically, the working medium is heated from the heat source by means of a source medium and evaporated for transport to the heat sink in order to, for example, keep energy transport losses to a minimum. Evaporation typically takes place in an evaporator, whereby at least part of the working medium evaporates.

[0003] In practice, however, it is problematic that the heat flow from the heat source used to evaporate the working medium fluctuates, for example with regard to temperature. This can lead, for example, to the available heat flow from the heat source being insufficient to evaporate the liquid working medium, which can adversely affect the heat transfer process and its efficiency. Under certain circumstances, a change in the heat flow from the heat source can even cause the heat transfer process to cease completely or the compressor to suck in liquid working medium and become damaged as a result. Another disadvantage can be that - e.g. in the case of a compressor designed as a turbo compressor - a change in the heat flow leads to what is known as compressor surge, and a resulting reduction in the compressor speed results in a deterioration in the COP value.

[0004] From DE 10 2005 061 480 B3 a heat pump system is known which has a compressor, a throttle element, several heat exchangers and a 4-2 way valve for switching between a first (heating) and a second operating mode (cooling).

[0005] DE 10 2020 134 599 A1 relates to a heat exchanger, a heat exchanger network and a heat exchange process.

[0006] DE 10 2020 115 275 A1 relates to a method for operating a compression refrigeration system and an associated compression refrigeration system with a refrigerant, an evaporator, a compressor, a condenser, a throttle device and a control unit.

[0007] DE 10 2019 001 639 A1 relates to a refrigeration circuit, a method for operating a refrigeration circuit, a heat pump comprising such a refrigeration circuit, and a method for heat transfer through such a refrigeration circuit or through such a heat pump.

[0008] US 8 656 720 B1 concerns heat recovery for the purpose of electrical or mechanical energy generation.

[0009] The technical problem is to create a device and a method for heat transfer which have increased resistance to changes in the heat flow of the heat source.

[0010] The solution to the technical problem is achieved by the subject matter having the features of the independent claims. Further advantageous embodiments of the invention are set forth in the subclaims.

[0011] A heat transfer device is therefore proposed, comprising: - a working medium for absorbing heat from at least one source medium, - at least one evaporator for evaporating the working medium, - at least one compressor for compressing the evaporated working medium, - at least one heat exchanger for transferring heat from the compressed working medium to at least one secondary medium, - at least one throttle to relax the working medium before it re-enters the evaporator.

[0012] Furthermore, at least one high-temperature recuperator is arranged in at least one high-temperature section between the at least one compressor and the at least one heat exchanger, wherein the at least one high-temperature recuperator is designed for internal heat recuperation to the working medium in at least one section between the at least one throttle and the at least one evaporator, wherein a mass flow of the working medium through the at least one high-temperature section can be adjusted via at least one bypass and a mass flow of the working medium through the at least one section can be adjusted via at least one further bypass, and / or at least one low-temperature recuperator is arranged in at least one low-temperature section between the at least one heat exchanger and the at least one throttle, wherein the at least one low-temperature recuperator is designed for internal heat recuperation to the working medium in at least one further section between the at least one throttle and the at least one evaporator, wherein a mass flow of the working medium through the at least one low-temperature section can be adjusted via at least one further bypass and a mass flow of the working medium through the at least one further section can be adjusted via at least one further bypass.

[0013] The device ensures that the working fluid can be heated with recovered thermal energy before entering the evaporator, depending on the mass flow rate. This makes it possible to compensate for, for example, the effects of a change in the heat flow from the heat source, particularly a reduction in the temperature of the source medium. In particular, it can be ensured that the working fluid pressure required for evaporation is maintained in the evaporator. As a result, the heat transfer process is more resistant to changes in the heat flow from the heat source. Furthermore, the efficiency of heat transfer is increased because internal thermal energy is used to stabilize the heat transfer process.

[0014] The working medium is a fluid that, through changes in state, is suitable for transporting thermal energy and thus for heat transfer. The working medium can thus be described by state variables such as pressure, temperature, or a mass flow. In particular, the working medium can assume various states of aggregation and exist at least in liquid, gaseous, or two-phase form. The change in a state variable or state of aggregation can be brought about by one or more of the process steps listed below. Water, ammonia, carbon dioxide, or hydrocarbons are particularly suitable as working media. The same applies to the source medium and / or the secondary medium.

[0015] The evaporator can be designed, for example, as a dry evaporator or a flooded evaporator. The compressor can be designed, for example, as a piston, screw, axial, or radial compressor. The compressor can be electrically driven, for example. The heat exchanger can be designed, for example, as a condenser. The heat exchanger can also be referred to as a heat exchanger. The throttle can be designed, for example, as a throttle valve or perforated disc. The high-temperature recuperator and / or the low-temperature recuperator can be designed, for example, as a shell-and-tube heat exchanger.

[0016] The use of a high-temperature recuperator has the advantage that the working fluid flows through the compressor immediately beforehand, resulting in a particularly high temperature level in the high-temperature section. This high temperature level can be used to heat the working fluid in the section between the throttle and the evaporator particularly quickly, thus enabling a particularly short-term response to fluctuations in the heat flow of the source medium. In particular, this method can prevent or minimize changes in the compressor speed due to short-term fluctuations in the heat flow, which in turn has a positive effect on the COP value of the device.

[0017] The use of a low-temperature recuperator has the advantage that the working fluid flows through the heat exchanger immediately beforehand, and the heat energy remaining in the working fluid in the low-temperature section is therefore unused residual energy that is available for heating the working fluid in the further section between the throttle and the evaporator. In particular, due to the flow through the heat exchanger, the working fluid is almost completely liquefied in the low-temperature section. The liquid state of the working fluid in the low-temperature section can be used to heat the working fluid in the further section between the throttle and the evaporator with a high heat transfer coefficient.

[0018] The advantage of cumulative use of the high-temperature recuperator and the low-temperature recuperator is that the aforementioned effects of each recuperator can be used as needed.

[0019] For the high-temperature recuperator, the mass flow can be adjusted, for example, such that the mass flow of the working medium through the at least one high-temperature section and / or the mass flow of the working medium through the at least one section between the at least one throttle and the at least one evaporator is adjusted manually or by means of a controller. For example, the bypasses can each be at least partially closed or opened by means of at least one valve. For example, the bypass of the high-temperature section and the bypass of the section between the throttle and evaporator can each be completely or partially closed by means of a valve, so that no or only partial bypassing of the high-temperature recuperator is possible when recuperation occurs.In this way, the high-temperature mass flow through the high-temperature section and / or the mass flow to be heated through the section between the throttle and the evaporator can be specifically adjusted.

[0020] For the low-temperature recuperator, the mass flow can be adjusted, for example, such that the mass flow of the working medium through the at least one low-temperature section and / or the mass flow of the working medium through the at least one further section between the at least one throttle and the at least one evaporator is adjusted manually or by means of a controller. For example, the bypasses can each be at least partially closed or opened by means of at least one valve. For example, the bypass of the low-temperature section and the bypass of the further section between the throttle and evaporator can each be completely or partially closed by means of a valve, so that no or only partial bypassing of the low-temperature recuperator is possible when recuperation occurs.In this way, the low-temperature mass flow through the low-temperature section and / or the mass flow to be heated through the further section between the throttle and the evaporator can be specifically adjusted.

[0021] In particular, the high-temperature recuperator and / or low-temperature recuperator, including the described sections and bypasses, can be connected to the device as separate units. This facilitates subsequent integration into existing heat transfer systems.

[0022] In particular, a further compressor can be arranged between the at least one compressor and the at least one heat exchanger. In this way, the working medium can be raised to a particularly high pressure and temperature level. The further compressor can be designed, for example, as an axial or radial compressor. The further compressor can be driven electrically, for example. An intercooler can be arranged between the at least one compressor and the at least one further compressor, which cools the working medium to a suitable operating point before it enters the further compressor. The previously explained high-temperature recuperator can, for example, function as the intercooler and in this way combine the aforementioned positive effects of the high-temperature recuperator with the function of the intercooler.

[0023] If the high-temperature recuperator is arranged downstream of the additional compressor in the direction of flow, it is possible for a so-called medium-temperature recuperator to be arranged between the at least one compressor and the at least one additional compressor. The medium-temperature recuperator can, for example, be designed as a tube-bundle heat exchanger and function as an intercooler. The section between the at least one compressor and the at least one additional compressor can be referred to as the medium-temperature section in order to distinguish it from the downstream high-temperature section. In this case, the high-temperature section can therefore refer to a section between the at least one additional compressor and the at least one heat exchanger.The at least one medium-temperature recuperator is designed, in particular, for internal heat recuperation to the working medium in at least one section between the at least one throttle and the at least one evaporator, wherein a mass flow of the working medium through the at least one medium-temperature section can be adjusted via at least one bypass and / or a mass flow of the working medium through the at least one section can be adjusted via at least one further bypass. The use of such a medium-temperature recuperator thus further improves the responsiveness of the device to fluctuations in the heat flow of the source medium and simultaneously fulfills the purpose of an intercooler between the at least one compressor and the at least one further compressor.The cumulative use of the medium-temperature recuperator and the high-temperature recuperator is particularly advantageous because the respective technical effects can be combined.

[0024] In particular, the temperature lift achievable by the device can have a value in a range of 150°C to 250°C. Such a temperature lift is particularly advantageous for high-temperature applications, such as those found in industrial processes. The device can thus provide a stable heat transfer process for high-temperature applications. For example, the source medium can have a temperature of 100°C upon entering the evaporator, and the secondary medium can be heated to a temperature of 350°C by the device. This corresponds to a temperature lift of 250°C. The value of the temperature lift can be achieved, for example, by using an additional compressor.

[0025] In one embodiment, the device comprises a control device configured to control the mass flow of the working medium through at least one of the previously explained sections as a function of the evaporation pressure of the working medium. In this way, the evaporation pressure in the evaporator can be kept constant, for example. In particular, this ensures that the pressure of the working medium upon entering the evaporator is such that the thermal energy supplied by the source medium is sufficient to evaporate the working medium.

[0026] Controlling the mass flow by means of the control device may include adjusting the mass flow. The previously explained sections include, in particular, the high-temperature section and / or the medium-temperature section and / or the low-temperature section and / or at least one of the aforementioned sections between the throttle and the evaporator.

[0027] The control device can, for example, be designed as a microcontroller or comprise one. The control device can, for example, generate at least one control command to adjust or control the mass flow in at least one of the previously explained sections, which at least partially closes or opens at least one of the previously explained bypasses. For example, a valve position of a valve can be adjusted depending on the at least one control command.

[0028] To control the mass flow as a function of the evaporation pressure, one or more actual values ​​of the working medium, e.g., an actual value of a sensor-determined state variable, can be adjusted to a target value or approximated to this. For example, there may be a known relationship between an actual value or target value and the evaporation pressure of the working medium, which is stored in the control device.

[0029] For example, the mass flow can be controlled in such a way that an actual value is changed by heating the working fluid in the high-temperature recuperator and / or by heating the working fluid in the low-temperature recuperator such that the actual value corresponds to a predetermined target value or is approximated to it, for example, within a tolerance value. However, other types of mass flow control are also possible.

[0030] In one embodiment, at least one actual pressure of the working medium can be determined using a pressure sensor. In this way, the actual pressure can be specifically adjusted to a target pressure, e.g., to an evaporation pressure intended for the working medium. The pressure sensor can be designed, for example, as a semiconductor sensor and can determine, for example, an actual pressure of the working medium upon entering the evaporator. The pressure sensor can be arranged, for example, at an inlet opening of the evaporator.

[0031] In one embodiment, at least one actual temperature of the working medium can be determined by means of a temperature sensor, wherein an actual pressure of the working medium can be determined as a function of the determined actual temperature. The actual pressure can be determined, for example, with the aid of a previously known association between the actual temperature and the actual pressure of the working medium. In this way, the mass flow can be controlled as a function of the evaporation pressure in a particularly cost-effective manner, since a temperature sensor is generally less expensive than, for example, a pressure sensor. The temperature sensor can be designed as a thermocouple, for example. The temperature sensor can be arranged, for example, at an inlet opening of the evaporator.

[0032] In one embodiment, the device has a control device which is designed to control the mass flow of the working medium through at least one of the previously explained sections as a function of at least one actual value of the source medium. In this way, for example, a short-term change in the actual value of the source medium can be immediately taken into account when adjusting the mass flow of the working medium, without, for example, having to wait for a change in a state variable of the working medium. The latency when adjusting the mass flow is consequently reduced. The actual value of the source medium can be an actual value of a state variable of the source medium. The actual value of the source medium can, for example, be determined by sensory means. The actual value of the source medium can, in particular, be an actual temperature of the source medium.For example, there may be a known relationship between the at least one actual value of the source medium and the evaporation pressure of the working medium in the evaporator, which relationship is stored in the control device. The described type of control can be carried out by the previously explained control device or by another control device.

[0033] In one embodiment, the device has a control device which is designed to control the mass flow of the working medium through at least one of the previously explained sections as a function of at least one actual value of the secondary medium. This allows a change in the actual value of the secondary medium to be taken into account when controlling the mass flow. The actual value of the secondary medium can be an actual value of a state variable of the secondary medium. The actual value of the secondary medium can be determined, for example, by sensors. The actual value of the secondary medium can, in particular, be an actual temperature of the secondary medium. For example, there can be a previously known relationship between the at least one actual value of the secondary medium and the evaporation pressure of the working medium in the evaporator, which relationship is stored in the control device.The described type of control can be carried out by the previously explained control device or by another control device.

[0034] In particular, the actual pressure of the working medium and / or the actual temperature of the working medium, as well as the actual value of the source medium and the actual value of the secondary medium, can be determined jointly and taken into account when controlling the mass flow of the working medium. This increases the accuracy, responsiveness, and reliability of the device, especially the control system.

[0035] In one embodiment, at least one vortex tube is arranged in at least one section for supplying the source medium to the at least one evaporator, wherein the at least one vortex tube is designed to separate the source medium into a hot portion and a cold portion. The vortex tube can be designed, for example, as a vortex bundle. The vortex tube allows the hot portion of the source medium to be used to evaporate the working medium in the evaporator.

[0036] The temperature of the source medium can thus be increased by several degrees using the vortex tube without the need for additional energy. This phenomenon is known as the Ranque-Hilsch effect. This enables a particularly high temperature increase. For example, the warm portion of the source medium is passed through the vortex tube to an inlet opening of the evaporator via the feed section. The cold portion can be passed through the vortex tube, for example, into the environment. Another advantage is that the cold portion can be used, for example, to cool components of the device and / or to cool oil-fired units.

[0037] In one embodiment, a mass flow of the source medium through the at least one section for supplying the source medium can be adjusted via at least one bypass. In this way, the effect of the vortex tube can be adjusted as required. The adjustment of the mass flow of the source medium through the supply section can, for example, be designed such that the mass flow of the source medium through the supply section is adjusted manually or by means of a control. For example, the bypass of the supply section can be at least partially closed or opened by means of at least one further valve. Furthermore, for example, the bypass of the supply section can be completely closed by means of the at least one further valve if the source medium is to flow completely through the vortex tube.

[0038] In one embodiment, the device comprises a control device designed to control a mass flow of the source medium through the at least one section as a function of an actual value of the working medium and / or an actual value of the source medium and / or an actual value of the secondary medium. In this way, the effect of the vortex tube can be controlled as required. For example, the mass flow of the source medium can be controlled such that the mass flow through the supply section increases if the actual value (of the working medium, source medium and / or secondary medium) exceeds a previously known target value by more than a previously known tolerance value. Furthermore, for example, the mass flow through the supply section can be reduced if the actual value (of the working medium, source medium and / or secondary medium) falls below a previously known target value by more than a previously known tolerance value.The described type of control can be carried out by the previously explained control device or by another control device.

[0039] Further proposed is a method for heat transfer, comprising the steps: - Evaporation of a working medium in at least one evaporator using heat from a source medium, - Compressing the working medium in at least one compressor, - Transferring heat from the working medium to at least one secondary medium in at least one heat exchanger, - Relaxing the working medium in at least one throttle, wherein at least one high-temperature recuperator is arranged in at least one high-temperature section between the at least one compressor and the at least one heat exchanger, wherein a mass flow of the working medium through the at least one high-temperature section is set via at least one bypass and a mass flow of the working medium through at least one section between the at least one throttle and the at least one evaporator is set via at least one further bypass, wherein heat is recuperated in the at least one high-temperature recuperator when at least a portion of the working medium flows through the at least one high-temperature section and the at least one section between the at least one throttle and the at least one evaporator, and / or wherein at least one low-temperature recuperator is arranged in at least one low-temperature section between the at least one heat exchanger and the at least one throttle, wherein a mass flow of the working medium through the at least one low-temperature section is set via at least one further bypass and a mass flow of the working medium through at least one further section is set via at least one further bypass, wherein heat is recuperated in the at least one low-temperature recuperator when at least a part of the working medium flows through the at least one low-temperature section and the at least one further section between the at least one throttle and the at least one evaporator.

[0040] The proposed method can be carried out, in particular, using a device according to an embodiment described in this disclosure. At least one of the embodiments of the device described in this disclosure can also be configured to carry out one, several, or all steps of the described method. The method thus yields the technical effects and advantages previously explained for the device.

[0041] The invention is explained in more detail using exemplary embodiments. The figures show: Fig. 1 a schematic representation of an embodiment of a device, Fig. 2 a schematic representation of another embodiment of a device, and Fig. 3 a schematic flow diagram of an embodiment of a method.

[0042] In the following, the same reference symbols refer to elements with the same technical features.

[0043] Fig. Figure 1 shows a schematic representation of an embodiment of a device 100 for heat transfer. The device 100 comprises several components that are fluidically connected to one another via, for example, pipelines. A working medium, such as water, can flow through the pipelines from one component to the next component of the device 100, wherein the respective flow direction of the working medium between the components can be Fig. 1 is shown by arrows.

[0044] The components of the device 100 include an evaporator 11 for evaporating the working medium, a compressor 12 designed as a radial compressor for compressing the evaporated working medium, a heat exchanger 13 designed as a condenser for transferring heat from the working medium to at least one secondary medium, and a throttle 14 designed as a throttle valve for expanding the working medium. Between the compressor 12 and the heat exchanger 13, an intercooler 18 designed as a tube-bundle heat exchanger and a further compressor 19 designed as a radial compressor are arranged.

[0045] The intercooler 18 arranged between the compressor 12 and the additional compressor 19 can be designed or referred to in particular as a medium-temperature recuperator as described in this disclosure. The medium-temperature recuperator can therefore be arranged in a so-called medium-temperature section between the compressor 12 and the additional compressor 19.

[0046] For the sake of clarity, the valves and bypasses required for the use of the intercooler 18 as a medium-temperature recuperator are shown in Fig. 1 is not shown. However, a suitable arrangement of the valves and bypasses for the medium-temperature recuperator is derived from the following explanations for a high-temperature recuperator 15, mutatis mutandis.

[0047] The high-temperature recuperator 15 is designed, for example, as a tube bundle heat exchanger. The high-temperature recuperator 15 is arranged in a high-temperature section A1 between the further compressor 19 and the heat exchanger 13. The high-temperature section A1 is in Fig. 1 is limited by a valve 21 designed as a three-way valve and a valve 23 designed as a three-way valve.

[0048] The high-temperature recuperator 15 is designed to transfer thermal energy from the working medium in the high-temperature section A1 to the working medium in the section A2. For the recuperation of thermal energy, the working medium in the section A2 flows through the high-temperature recuperator 15. The section A2 is in Fig. 1 is limited by a valve 22 designed as a three-way valve and a valve 24 designed as a three-way valve.

[0049] A bypass B1 is used to adjust the mass flow of the working fluid through the high-temperature section A1. Bypass B1 thus serves as a bypass of the high-temperature section A1 and runs from valve 21 to valve 23.

[0050] Alternatively or cumulatively, a mass flow of the working medium through at least one section A2 can be adjusted via a further bypass B2. The bypass B2 thus serves as a bypass of the section A2 and therefore runs from the valve 22 to the valve 24. In particular, the cumulative use of the bypasses B1, B2 can ensure that, for example, when the bypasses B1, B2 are fully opened, no more mass flow flows through the high-temperature recuperator 15 or when the bypasses B1, B2 are fully closed, the mass flow flows completely through the sections A1, A2. The recuperation is thus interrupted or started immediately. This improves the latency of the recuperation.

[0051] Furthermore, the device 100 comprises a control device 20 configured as a microcontroller, which is configured, for example, to control the mass flow of the working medium through the sections A1, A2 as a function of an evaporation pressure of the working medium. In particular, the control device 20 can generate a control command by which a valve position of the valve 21 is adjusted. For example, the valve position can be adjusted such that at least a portion of the working medium flows through the high-temperature section A1 and the section A2 when recuperation occurs. For the sake of clarity, Fig. 1 for the valves 21, 22, 23, 24 only a dashed line from the control device 20 to the valve 21 is shown. Of course, if required, by means of the control device 20, each of the Fig. The valves 21, 22, 23, 24 shown in Figure 1 can be controlled individually.

[0052] By adjusting or controlling the mass flow, the working medium can be heated as needed before entering the evaporator 11, so that, for example, fluctuations in the heat flow of the source medium can be compensated. This stabilizes the heat transfer process. For example, an actual pressure of the working medium in the evaporator 11 can be determined using a pressure sensor (not shown). Furthermore, for example, the mass flow can be controlled by means of the control device such that the actual pressure of the working medium in the evaporator 11 is changed by heating the working medium in section A2 such that the actual pressure corresponds to a predetermined target value of the evaporation pressure or is approximated thereto, for example, within a tolerance value.

[0053] Furthermore, a vortex tube 17 is arranged in a section A5 for supplying the source medium to the evaporator 11. The vortex tube 17 is designed to separate the source medium into a hot portion and a cold portion. The hot portion is supplied to the evaporator 11, while the cold portion is discharged, for example, into the environment or for cooling components of the device, such as for cooling the control device 20. The section A5 is in Fig. 1 is limited by a supply line of the source medium between a valve 25 designed as a three-way valve and a valve 26 designed as a three-way valve.

[0054] A further bypass B5 can be used to adjust the mass flow of the source medium through section A5. Bypass B5 thus serves as a bypass of section A5 and runs from valve 25 to valve 26.

[0055] In particular, a mass flow of the source medium through section A5 can be controlled depending on an actual temperature of the source medium. The actual temperature can be determined, for example, by means of a further temperature sensor (not shown). For example, a valve position of the valve 25 can be adjusted depending on the determined actual temperature. For example, an actual temperature of the source medium before entering the evaporator 11 can be determined by means of a temperature sensor (not shown). Furthermore, for example, the mass flow of the source medium through section A5 can be controlled by means of the control device such that the actual temperature corresponds to a predetermined target value of the temperature of the source medium or is approximated thereto, for example within a tolerance value. The temperature of the source medium can thus be adjusted as required by the vortex tube 17. This additionally stabilizes the heat transfer process.For the sake of clarity, in . Fig. 1 for the valves 25, 26 only a dashed line from the control device 20 to the valve 25 is shown. Of course, if required, by means of the control device 20, each of the Fig. The valves 25, 26 shown in Figure 1 can be controlled individually.

[0056] Fig. 2. shows a schematic representation of another embodiment of a device 100 for heat transfer. In addition to the Fig. The embodiment of the device 100 shown in Figure 1 is shown in Fig. 2, a low-temperature recuperator 16 designed as a tube bundle heat exchanger is arranged in a low-temperature section A3 between the heat exchanger 13 and the throttle 14. The section A3 is in Fig. 2 is limited by a valve 33 designed as a three-way valve and a valve 35 designed as a three-way valve.

[0057] The low-temperature recuperator 16 is designed to transfer thermal energy from the working medium in the low-temperature section A3 to the working medium in a further section A4 between the throttle 14 and the evaporator 11. For the recuperation of the thermal energy, the working medium in the further section A4 flows through the low-temperature recuperator 16. The further section A4 is in Fig. 2 is limited by a valve 34 designed as a three-way valve and a valve 36 designed as a three-way valve.

[0058] A bypass B3 is used to adjust the mass flow of the working fluid through the low-temperature section A3. Bypass B3 serves as a bypass for the low-temperature section A3 and therefore runs from valve 33 to valve 35.

[0059] Alternatively or cumulatively, a mass flow of the working medium through the further section A4 can be adjusted via an additional bypass B4. The bypass B4 serves as a bypass of the further section A4 between the throttle 14 and the evaporator 11 and therefore runs from the valve 34 to the valve 36. In particular, the cumulative use of the bypasses B3, B4 can ensure that, for example, when the bypasses B3, B4 are fully opened, no more mass flow flows through the low-temperature recuperator 16, or when the bypasses B3, B4 are fully closed, the mass flow flows completely through sections A3, A4. The recuperation is thus interrupted or started immediately. This improves the latency of the recuperation.

[0060] Furthermore, there is a Fig. 2 is designed to control the mass flow of the working medium through the sections A1, A2 and through the sections A3, A4 as a function of an evaporation pressure of the working medium. In particular, the control device 20 can generate one or more control commands by which at least one valve position of the valves 21, 33 is adjusted. For example, the valve position can be adjusted such that at least a portion of the working medium flows through the low-temperature section A3 and the further section A4 when recuperation occurs. For the sake of clarity, Fig. 2 for the valves 21, 22, 23, 24 and the valves 33, 34, 35, 36, only a dashed line is shown from the control device 20 to the valve 21 or to the valve 33. Of course, if required, each of the valves shown in Fig. 2, the valves 21, 22, 23, 24, 33, 34, 35, 36 shown can be controlled individually.

[0061] By adjusting the mass flow in sections A1, A2 and sections A3, A4, the working medium can be heated as required before entering the evaporator 11 by means of the high-temperature recuperator 15 and / or by means of the low-temperature recuperator 16, so that fluctuations in the heat flow of the source medium can be compensated.

[0062] Of course, the low-temperature recuperator 16 can also be used independently of the high-temperature recuperator 15 and vice versa, for example if the available installation space for the device 100 is limited.

[0063] Fig. Figure 3 shows a schematic flow diagram of an embodiment of a method. The method comprises the following steps: In a step S1, a working medium is evaporated in an evaporator 11 with the aid of heat from a source medium (cf. Fig. 1 and Fig. 2). In a step S2, the working medium is compressed in a compressor 12 (cf. Fig. 1 and Fig. 2) and thereby raised to a higher temperature and pressure level. In a step S3, the heat transported by the working medium is transferred to a secondary medium in a heat exchanger 13 (see Fig. 1 and Fig. 2). In a step S4, the working medium is expanded in a throttle 14 so that the working medium in the evaporator 11 can again absorb heat from the source medium.

[0064] In a step S5, a mass flow is set through at least one of the previously explained sections A1, A2, A3, A4 (cf. Fig. 1 or Fig. 2). This has the advantages and effects explained above. List of reference symbols 11 evaporators 12 compressors 13 heat exchangers 14 Throttle 15 High-temperature recuperator 16 Low-temperature recuperator 17 Vortex tube 18 intercoolers 19 additional compressors 20 Control device 21 ... 24 valves associated with the high-temperature recuperator 25 ... 26 Valves associated with the vortex tube 33 ... 36 valves associated with the low-temperature recuperator 100 device A1 High-temperature section A2 Section between throttle and evaporator A3 Low-temperature section A4 further section between throttle and evaporator A5 Source medium supply section B1 Bypass for the high-temperature section B2 Bypass for the section between throttle and evaporator B3 Bypass for the low-temperature section B4 Bypass for the further section between throttle and evaporator B5 Bypass for the source medium supply section S1 Evaporation step S2 compaction step S3 Heat transfer step S4 Step of relaxation S5 Step of setting the mass flow

Claims

[1] A heat transfer device (100) comprising: - a working medium for absorbing heat from at least one source medium, - at least one evaporator (11) for evaporating the working medium, - at least one compressor (12) for compressing the evaporated working medium, - at least one heat exchanger (13) for transferring heat from the compressed working medium to at least one secondary medium, - at least one throttle (14) for relaxing the working medium before it re-enters the evaporator (11), wherein at least one high-temperature recuperator (15) is arranged in at least one high-temperature section (A1) between the at least one compressor (12) and the at least one heat exchanger (13), wherein the at least one high-temperature recuperator (15) is designed for internal heat recuperation to the working medium in at least one section (A2) between the at least one throttle (14) and the at least one evaporator (11), wherein a mass flow of the working medium through the at least one high-temperature section (A1) can be adjusted via at least one bypass (B1) and a mass flow of the working medium through the at least one section (A2) can be adjusted via at least one further bypass (B2), and / or at least one low-temperature recuperator (16) is arranged in at least one low-temperature section (A3) between the at least one heat exchanger (13) and the at least one throttle (14), wherein the at least one low-temperature recuperator (16) is designed for internal heat recuperation to the working medium in at least one further section (A4) between the at least one throttle (14) and the at least one evaporator (11), wherein a mass flow of the working medium through the at least one low-temperature section (A3) can be adjusted via at least one further bypass (B3) and a mass flow of the working medium through the at least one further section (A4) can be adjusted via at least one further bypass (B4). [2] Device (100) for heat transfer according to claim 1, characterized bythat the device (100) has a control device (20) which is designed to control the mass flow of the working medium through at least one section (A1, A2, A3, A4) as a function of an evaporation pressure of the working medium. [3] Device (100) for heat transfer according to claim 2, characterized by that at least one actual pressure of the working medium can be determined by means of a pressure sensor. [4] Device (100) for heat transfer according to claim 2 or 3, characterized by that at least one actual temperature of the working medium can be determined by means of a temperature sensor, wherein an actual pressure of the working medium can be determined as a function of the determined actual temperature. [5] Device (100) for heat transfer according to one of the preceding claims, characterized bythat the device (100) has a control device (20) which is designed to control the mass flow of the working medium through at least one section (A1, A2, A3, A4) as a function of at least one actual value of the source medium. [6] Device (100) for heat transfer according to one of the preceding claims, characterized by that the device (100) has a control device (20) which is designed to control the mass flow of the working medium through at least one section (A1, A2, A3, A4) as a function of at least one actual value of the secondary medium. [7] Device (100) for heat transfer according to one of the preceding claims, characterized bythat at least one vortex tube (17) is arranged in at least one section (A5) for supplying the source medium to the at least one evaporator (11), wherein the at least one vortex tube (17) is designed to separate the source medium into a hot portion and a cold portion. [8] Device (100) for heat transfer according to claim 7, characterized by that a mass flow of the source medium through the at least one section (A5) can be adjusted via at least one bypass (B5). [9] Device (100) for heat transfer according to claim 7 or 8, characterized by that the device (100) has a control device (20) which is designed to control a mass flow of the source medium through the at least one section (A5) as a function of at least one actual value of the working medium and / or at least one actual value of the source medium and / or at least one actual value of the secondary medium. [10] A method for heat transfer comprising the steps of: - evaporation (S1) of a working medium in at least one evaporator (11) with the aid of heat from a source medium, - compressing (S2) the working medium in at least one compressor (12), - transferring heat (S3) from the working medium to at least one secondary medium in at least one heat exchanger (13), - Relaxing (S4) the working medium in at least one throttle (14), wherein at least one high-temperature recuperator (15) is arranged in at least one high-temperature section (A1) between the at least one compressor (12) and the at least one heat exchanger (13), wherein a mass flow of the working medium through the at least one high-temperature section (A1) is set via at least one bypass (B1) and a mass flow of the working medium through at least one section (A2) between the at least one throttle (14) and the at least one evaporator (11) is set via at least one further bypass (B2), wherein heat is recuperated in the at least one high-temperature recuperator (15) when at least a portion of the working medium flows through the at least one high-temperature section (A1) and the at least one section (A2) between the at least one throttle (14) and the at least one evaporator (11), and / or at least one low-temperature recuperator (16) is arranged in at least one low-temperature section (A3) between the at least one heat exchanger (13) and the at least one throttle (14), wherein a mass flow of the working medium through the at least one low-temperature section (A3) is set via at least one further bypass (B3) and a mass flow of the working medium through at least one further section (A4) is set via at least one further bypass (B4), wherein heat is recuperated in the at least one low-temperature recuperator (16) when at least a portion of the working medium flows through the at least one low-temperature section (A3) and the at least one further section (A4) between the at least one throttle (14) and the at least one evaporator (11).

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