Device and method for heat transfer

Abstract

The invention relates to a device (100) for heat transfer, wherein at least one high-temperature recuperator (15) is arranged in at least one high-temperature section (A1) between at least one compressor (12) and at least one heat exchanger (13), 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 / or a mass flow of the working medium through 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 at least one throttle (14), 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 / or a mass flow of the working medium through at least one further section (A4) can be adjusted via at least one further bypass (B4), and a method for heat transfer.

Description

The invention relates to a device for heat transfer and a corresponding method.The thermodynamic use of waste heat or ambient heat, for example in industrial plants, offers great potential for making processes, such as energy-intensive production processes or the heating of buildings, more efficient. In particular, the operating principle of the heat pump offers the possibility of transporting waste heat or ambient heat which arises from a heat source of lower temperature levels to a heat sink of higher temperature levels. The thermal energy is transferred by a flowing working medium, also called refrigerant. The working medium is usually heated from the heat source by means of a source medium and evaporated for transport to the heat sink, in order to keep energetic transport losses low, for example. The evaporation typically takes place in an evaporator, wherein at least a part of the working medium evaporates.In practice, however, it is problematic that the heat flow of the heat source used for evaporating the working medium fluctuates, for example, with respect to the temperature. This can lead, for example, to the available heat flow of the heat source not being sufficient to evaporate the liquid working medium, as a result of which the heat transfer process and its efficiency can be adversely affected. Under certain circumstances, a change in the heat flow of the heat source can even cause the heat transfer process to be completely stopped or the compressor to suck in liquid working medium and thereby be damaged. It may also be disadvantageous that-for example in the case of a compressor designed as a turbocompressor-a so-called compressor surge occurs due to a change in the heat flow and a concomitant reduction in the rotational speed of the compressor results in a deterioration in the COP value.The technical problem arises to provide a device and a method for heat transfer which have an increased resistance to changes in the heat flow of the heat source.The solution of the technical problem is achieved by the subject matters having the features of the independent claims. Further advantageous embodiments of the invention are evident from the dependent claims.A device for heat transfer 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 for expanding the working medium before renewed entry into the evaporator.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 can be adjusted by the at least one high-temperature section via at least one bypass and / or a mass flow of the working medium can be adjusted by the at least one section 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 can be adjusted by the at least one low-temperature section via at least one further bypass and / or a mass flow of the working medium can be adjusted by the at least one further section via at least one further bypass.The device achieves the effect that the working medium can be heated with re-pumped thermal energy according to an adjustment of the mass flow before entering the evaporator. In this way, for example, the effect of a change in the heat flow of the heat source, in particular a reduction in the temperature of the source medium, can be compensated. In particular, it can be ensured that a pressure of the working medium required for evaporation is provided in the evaporator. As a result, the heat transfer process is thus more resistant to changes in the heat flow of the heat source. In addition, the efficiency of heat transfer is increased because internal heat energy is used to stabilize the heat transfer process.The working medium is a fluid which is suitable for transporting thermal energy and thus for transferring heat by changes in state. The working medium can thus be described by state variables such as, for example, pressure, temperature or a mass flow. In particular, the working medium can assume different aggregate states and be present at least in liquid, gaseous or two-phase form. The change of a state variable or of an aggregate state can be brought about by one or more of the method steps mentioned below. Suitable working media are, in particular, water, ammonia, carbon dioxide or hydrocarbons. The same applies analogously to the source medium and / or the secondary medium.The evaporator can be designed, for example, as a dry evaporator or 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 disk. The high-temperature recuperator and / or the low-temperature recuperator can / can be designed, for example, as tube bundle heat exchangers.Using the high-temperature recuperator has the advantage that the working medium flows through the compressor immediately before and the working medium therefore has a particularly high temperature level in the high-temperature section. This high temperature level can be used to heat the working medium particularly quickly in the section between the throttle and the evaporator and in this way to be able to react particularly quickly to fluctuations in the heat flow of the source medium. In particular, a change in the rotational speed of the compressor as a result of short-term fluctuations in the heat flow can be avoided or kept low in this way, which in turn has a positive effect on the COP value of the device.The use of the low-temperature recuperator has the advantage that the working medium flows through the heat exchanger immediately before and the heat energy remaining in the working medium in the low-temperature section is therefore unused residual energy, which is available for heating the working medium in the further section between the throttle and the evaporator. In particular, the working medium is almost completely liquefied in the low-temperature section due to the flow through the heat exchanger. The liquid aggregate state of the working medium in the low-temperature section can be used to heat the working medium in the further section between the throttle and the evaporator with a high heat transfer coefficient.A cumulative use of the high-temperature recuperator and the low-temperature recuperator has the advantage that the aforementioned effects of the respective recuperator can be used as required.For the high-temperature recuperator, the setting of the mass flow can be designed, for example, in such a way 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 set manually or by means of a controller. For example, the bypasses can be at least partially closed or opened in each case by means of at least one valve. For example, the bypass of the high-temperature section and the bypass of the section between 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 takes place. 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 throttle and evaporator can be adjusted in a targeted manner.For the low-temperature recuperator, the setting of the mass flow can be designed, for example, in such a way 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 set manually or by means of a controller. For example, the bypasses can be at least partially closed or opened in each case by means of at least one valve. For example, the bypass of the low-temperature section and the bypass of the further section between 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 takes place. 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 throttle and evaporator can be adjusted in a targeted manner.In particular, the high-temperature recuperator and / or low-temperature recuperator can / can be connected to the device as a separate unit(s), in each case together with the sections and bypasses explained. This facilitates subsequent integration into existing heat transfer systems.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 compressor 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, said intercooler cooling the working medium to a suitable operating point before entering the further compressor. The above-explained high-temperature recuperator can act, for example, as the intercooler and in this way combine the above-mentioned positive effects of the high-temperature recuperator with the function of the intercooler.In the case where the high-temperature recuperator is arranged downstream of the further compressor in the flow direction, it is possible that a so-called medium-temperature recuperator is arranged between the at least one compressor and the at least one further compressor. The medium-temperature recuperator can be designed, for example, as a tube bundle heat exchanger and function as an intercooler. The section between the at least one compressor and the at least one further compressor can be referred to as a medium-temperature section in order to make it possible to distinguish from the downstream high-temperature section. In this case, the high-temperature section can therefore denote a section between the at least one further 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 can be adjusted by the at least one medium-temperature section via at least one bypass and / or a mass flow of the working medium can be adjusted by the at least one section via at least one further bypass. The use of such a medium-temperature recuperator thus additionally improves the reactivity of the device to fluctuations in the heat flow of the swelling medium and at the same time 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, since the respective technical effects mentioned can be combined.In particular, the temperature swing achievable by means of the device can have a value in a range from 150° C. to 250° C. Such a temperature swing is advantageous in particular for high-temperature applications, as occur, for example, in industrial processes. The device can thus provide a stable heat transfer process for high-temperature applications. For example, the swelling medium can have a temperature of 100° C. on entry into the evaporator and the secondary medium can be heated to a temperature of 350° C. by means of the apparatus. This corresponds to a temperature stroke of 250° C. The value of the temperature stroke can be achieved, for example, by using a further compressor.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 sections explained above as a function of an evaporation pressure of the working medium. In this way, the evaporation pressure in the evaporator can be kept constant, for example. In particular, it is achieved that the pressure of the working medium on entry into the evaporator is such that the thermal energy supplied by means of the source medium is sufficient to evaporate the working medium.Controlling the mass flow by means of the control device can comprise adjusting the mass flow. The sections explained above comprise 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.The control device can be designed as a microcontroller, for example, or can comprise such a microcontroller. The control device can generate, for example, for setting or controlling the mass flow in at least one of the sections explained above, at least one control command which at least partially closes or opens at least one of the bypasses explained above. For example, a valve position of a valve can be set as a function of the at least one control command.To control the mass flow as a function of the evaporation pressure, it is / can be possible in particular to set one or more actual values of the working medium, for example an actual value of a state variable determined by sensors, to a setpoint value or to approximate it. Between an actual value or desired value and the evaporation pressure of the working medium, for example, a previously known relationship can exist, which is stored in the control device.For example, the mass flow can be controlled in such a way that an actual value is changed by heating the working medium in the high-temperature recuperator and / or by heating the working medium in the low-temperature recuperator in such a way that the actual value corresponds to a predefined setpoint value or is approximated to this, e.g., within the scope of a tolerance value. However, other types of control of the mass flow are also possible.In one embodiment, at least one actual pressure of the working medium can be determined by means of a pressure sensor. In this way, the actual pressure can be adjusted specifically to a setpoint pressure, for example to an evaporation pressure provided for the working medium. The pressure sensor can be designed, for example, as a semiconductor sensor and, for example, determine an actual pressure of the working medium upon entry into the evaporator. The pressure sensor can be arranged, for example, at an inlet opening of the evaporator.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 determination of the actual pressure is possible, for example, with the aid of a previously known assignment between the actual temperature and the actual pressure of the working medium. In this way, the mass flow can be controlled in a particularly cost-effective manner as a function of the evaporation pressure, since a temperature sensor is generally more cost-effective than, for example, a pressure sensor. The temperature sensor can be designed, for example, as a thermocouple. The temperature sensor can be arranged, for example, at an inlet opening of the evaporator.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 sections explained above 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 taken into account directly when setting the mass flow of the working medium, without having to wait for a change in a state variable of the working medium, for example. Consequently, latency in adjusting mass flow is 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 be determined, for example, by sensor. The actual value of the source medium can be, in particular, an actual temperature of the source medium. For example, a previously known relationship can exist 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 control device explained above or by a further control device.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 sections explained above as a function of at least one actual value of the secondary medium. As a result, a change in the actual value of the secondary medium can be taken into account in the control of 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 sensor. The actual value of the secondary medium can be, in particular, an actual temperature of the secondary medium. For example, a previously known relationship can exist 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 control device explained above or by a further control device.In particular, the actual pressure of the working medium and / or the actual temperature of the working medium and the actual value of the source medium and the actual value of the secondary medium can be determined jointly and taken into account jointly in the control of the mass flow of the working medium. This increases the accuracy, responsiveness and reliability of the device, particularly the controller.In one embodiment, at least one swirl tube is arranged in at least one section for supplying the source medium to the at least one evaporator, wherein the at least one swirl tube is designed to separate the source medium into a hot portion and a cold portion. The swirl tube can be designed, for example, as a swirl bundle. The swirl tube allows the hot portion of the source medium to be used for evaporating the working medium in the evaporator. The temperature of the source medium can thus be increased by several degrees by means of the swirl tube, without additional energy having to be used for this purpose. This phenomenon is referred to in particular as the Ranque-Hilsch effect. This enables a particularly high temperature swing. Via the section for feeding, for example, the warm portion of the swelling medium is conducted through the swirl tube to an inlet opening of the evaporator. The cold portion can be conducted through the swirl tube, for example, into the environment. In addition, the advantage results that the cold portion can be used, for example, for cooling components of the device and / or, for example, for cooling oil aggregates.In an embodiment company, 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 setting of the mass flow of the source medium by the section for supplying can be configured, for example, in such a way that the mass flow of the source medium by the section for supplying is set manually or by means of a controller. For example, the bypass of the section for feeding can be at least partially closed or opened by means of at least one further valve. Further for example, the bypass of the section for feeding can be completely closed by means of the at least one further valve if the source medium is intended to flow completely through the swirl tube.In one embodiment, the device has a control device which is 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 in such a way that the mass flow through the section for supplying increases if the actual value (of the working medium, source medium and / or secondary medium) exceeds a previously known setpoint value by more than a previously known tolerance value. Furthermore, for example, the mass flow through the section for feeding can be reduced if the actual value (of the working medium, source medium and / or secondary medium) falls below a previously known setpoint value by more than a previously known tolerance value. The described type of control can be carried out by the control device explained above or by a further control device.A method for heat transfer is further proposed, comprising the steps of:evaporating a working medium in at least one evaporator with the aid of 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 is adjusted by the at least one high-temperature section via at least one bypass and / or a mass flow of the working medium is adjusted by at least one section between the at least one throttle and the at least one evaporator via at least one further bypass, wherein heat is recovered in the at least one high-temperature recuperator when at least a part 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 is adjusted by the at least one low-temperature section via at least one further bypass and / or a mass flow of the working medium is adjusted by at least one further section 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.The proposed method can be carried out in particular by means of 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 designed to carry out one, a plurality or all steps of the described method. The technical effects and advantages explained above for the device thus result for the method.The invention is explained in more detail on the basis of exemplary embodiments. The figures show: FIG. 1 shows a schematic illustration of an embodiment of a device, FIG. 2 shows a schematic illustration of a further embodiment of a device, and FIG. 3 is a schematic flow diagram of an embodiment of a method.In the following, the same reference numerals denote elements having the same technical features.FIG. 1 shows a schematic illustration of an embodiment of a device 100 for heat transfer. The device 100 comprises a plurality of components which are connected to one another fluidically via, for example, pipelines. A working medium, e.g. 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 is illustrated by arrows in FIG. 1.The components of the device 100 comprise 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 there is arranged an intercooler 18 designed as a shell-and-tube heat exchanger and a further compressor 19 designed as a radial compressor.The intercooler 18 arranged between the compressor 12 and the further compressor 19 can be designed or referred to in particular as a medium-temperature recuperator described in this disclosure. The medium-temperature recuperator can accordingly be arranged in a so-called medium-temperature section between the compressor 12 and the further compressor 19. The valves and bypasses necessary for using the intercooler 18 as a medium-temperature recuperator are not shown in FIG. 1 for the sake of clarity. A suitable arrangement of the valves and bypasses for the medium-temperature recuperator is obtained, however, by the explanations given below regarding a high-temperature recuperator 15, mutatismutanismutand.The high-temperature recuperator 15 is designed, for example, as a shell-and-tube heat exchanger. The high-temperature recuperator 15 is arranged in a high-temperature section A 1 between the further compressor 19 and the heat exchanger 13. The high-temperature section A 1 is bounded in FIG. 1 by a valve 21 embodied as a three-way valve and a valve 23 embodied as a three-way valve.The high-temperature recuperator 15 is designed to transfer thermal energy from the working medium in the high-temperature section A 1 to the working medium in the section A 2. For the recuperation of the thermal energy, the working medium in the section A 2 flows through the high-temperature recuperator 15. the section A 2 is bounded in FIG. 1 by a valve 22 designed as a three-way valve and a valve 24 designed as a three-way valve.A mass flow of the working medium through the high-temperature section A 1 can be adjusted via a bypass B 1. The bypass B 1 thus serves as a bypass of the high temperature portion A 1 and therefore extends from the valve 21 to the valve 23.Alternatively or cumulatively, a mass flow of the working medium through the at least one section A 2 can be adjusted via a further bypass B 2. The bypass B 2 thus serves as a bypass of the section A 2 and therefore runs from the valve 22 to the valve 24. in particular, the cumulative use of the bypasses B 1, B 2 makes it possible to ensure that, for example, when the bypasses B 1, B 2 are fully opened, no mass flow any longer flows through the high-temperature recuperator 15 or, when the bypasses B 1, B 2 are fully closed, the mass flow flows fully through the sections A 1, A 2. Recuperation is thus immediately interrupted or started. This improves the latency of recuperation.Furthermore, the device 100 has a control device 20 designed as a microcontroller, which is designed, for example, to control the mass flow of the working medium through the sections A 1, A 2 as a function of an evaporation pressure of the working medium. In particular, the control device 20 can generate a control command, by means of 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 A 1 and the section A 2 when recuperation takes place. For the sake of clarity, only a dashed line from the control device 20 to the valve 21 is shown in FIG. 1 for the valves 21, 22, 23, 24. Of course, each of the valves 21, 22, 23, 24 shown in FIG. 1 can be controlled individually if necessary by means of the control device 20.By adjusting or controlling the mass flow, the working medium can be heated as required 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 by means of a pressure sensor (not shown). Furthermore, for example, the mass flow can be controlled by means of the control device in such a way that the actual pressure of the working medium in the evaporator 11 is changed by heating the working medium in the section A 2 in such a way that the actual pressure corresponds to a predefined setpoint value of the evaporation pressure or is approximated thereto, for example, within the scope of a tolerance value.Further, in a portion A5 for supplying the source medium to the evaporator 11, a swirl pipe 17 is disposed. The swirl tube 17 is designed to separate the swelling medium into a hot portion and a cold portion. The hot fraction is supplied to the evaporator 11, while the cold fraction is discharged, for example, into the environment or for cooling components of the apparatus, such as for cooling the control device 20.Furthermore, a mass flow of the source medium through the section A 5 can be adjusted via a further bypass B 5. The bypass B 5 thus serves as a bypass of the section A 5 and therefore runs from the valve 25 to the valve 26.In particular, a mass flow of the source medium through the section A 5 can be controlled as a function of 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 as a function of the determined actual temperature. For example, an actual temperature of the source medium can be determined by means of a temperature sensor (not shown) before entry into the evaporator 11. Furthermore, for example, the mass flow of the source medium can be controlled by the section A 5 by means of the control device in such a way that the actual temperature corresponds to a predefined setpoint value of the temperature of the source medium or is approximated thereto, for example, within the scope of a tolerance value. The temperature of the source medium can thus be adjusted as required by the swirl tube 17. This additionally stabilizes the heat transfer process. For the sake of clarity, only a dashed line from the control device 20 to the valve 25 is shown in FIG. 1 for the valves 25, 26. Of course, each of the valves 25, 26 shown in FIG. 1 can be controlled individually if necessary by means of the control device 20.FIG. 2 shows a schematic illustration of a further embodiment of a device 100 for heat transfer. In addition to the embodiment of the device 100 shown in FIG. 1, a low-temperature recuperator 16 designed as a shell-and-tube heat exchanger is additionally arranged in FIG. 2 in a low-temperature section A 3 between the heat exchanger 13 and the throttle 14. The section A 3 is bounded in FIG. 2 by a valve 33 embodied as a three-way valve and a valve 35 embodied as a three-way valve.The low-temperature recuperator 16 is designed to transfer thermal energy from the working medium in the low-temperature section A 3 to the working medium in a further section A 4 between the throttle 14 and the evaporator 11. For the recuperation of the thermal energy, the working medium flows in the further section A 4 through the low-temperature recuperator 16; the further section A 4 is bounded in FIG. 2 by a valve 34 designed as a three-way valve and a valve 36 designed as a three-way valve.A mass flow of the working medium through the low-temperature section A 3 can be adjusted via a bypass B 3. The bypass B 3 serves as a bypass of the low-temperature portion A 3 and therefore extends from the valve 33 to the valve 35.Alternatively or cumulatively, a mass flow of the working medium through the further section A 4 can be adjusted via a further bypass B 4. The bypass B 4 serves as a bypass of the further section A 4 between throttle 14 and evaporator 11 and therefore runs from the valve 34 to the valve 36. Recuperation is thus immediately interrupted or started. This improves the latency of recuperation.Furthermore, a control device 20 shown in FIG. 2 is designed to control the mass flow of the working medium through the sections A 1, A 2 and through the sections A 3, A 4 as a function of an evaporation pressure of the working medium. In particular, the control device 20 can generate one or more control command(s), by means of which at least one valve position of the valves 21, 33 is adjusted. For example, the valve position can be adjusted in such a way that at least a portion of the working medium flows through the low-temperature section A 3 and the further section A 4 when recuperation takes place. For the sake of clarity, only one dashed line from the control device 20 to the valve 21 or to the valve 33 is shown in FIG. 2 for the valves 21, 22, 23, 24 and the valves 33, 34, 35, 36. Of course, each of the valves 21, 22, 23, 24, 33, 34, 35, 36 shown in FIG. 2 can be controlled individually if necessary by means of the control device 20.By adjusting the mass flow in the sections A 1, A 2 and the sections A 3, A 4, the working medium can be heated as required by means of the high-temperature recuperator 15 and / or by means of the low-temperature recuperator 16 before entering the evaporator 11, so that fluctuations in the heat flow of the source medium can be compensated.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.FIG. 3 shows a schematic flow diagram of an embodiment of a method. The method comprises the following steps:In a step S 1, a working medium is evaporated from a source medium in an evaporator 11 with the aid of heat (cf. FIGS. 1 and 2 ). In a step S 2, the working medium is compressed in a compressor 12 (cf. FIGS. 1 and 2 ) and is thereby raised to a higher temperature and pressure level. In a step S 3, the heat transported by means of the working medium is transferred to a secondary medium in a heat exchanger 13 (cf. FIGS. 1 and 2 ). In a step S 4, the working medium is expanded in a throttle 14, so that the working medium can again absorb heat from the source medium in the evaporator 11.In a step S 5, a mass flow is set by at least one of the sections A 1, A 2, A 3, A 4 explained above (cf. FIG. 1 or FIG. 2 ). This has the advantages and effects explained above.List of reference characters11 Evaporator 12 Compressor 13 Heat exchanger 14 Throttle 15 High-temperature recuperator 16 Low-temperature recuperator 17 Vortex tube 18 Intercooler 19 Further compressor 20 Control device 21... 24 valves in connection with the high temperature recuperator 25... 26 valves in connection with the swirl tube 33... 36 valves in connection 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 section for supplying the source medium 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 section for supplying the source medium S1 step of evaporation S2 step of compression S3 step of heat transfer S4 step of expansion S5 step of adjusting the mass flow

Claims

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 expanding the working medium before re-entry into 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 can be adjusted by the at least one high-temperature section (A1) via at least one bypass (B1) and / or a mass flow of the working medium can be adjusted by the at least one section (A2) 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 can be adjusted by the at least one low-temperature section (A3) via at least one further bypass (B3) and / or a mass flow of the working medium can be adjusted by the at least one further section (A4) via at least one further bypass (B4).Device (100) for heat transfer according to Claim 1, characterized in 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 an evaporation pressure of the working medium.Device (100) for heat transfer according to Claim 2, characterized in that at least one actual pressure of the working medium can be determined by means of a pressure sensor.Device (100) for heat transfer according to Claim 2 or 3, characterized in 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.Device (100) for heat transfer according to one of the preceding claims, characterized in 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 source medium.Device (100) for heat transfer according to one of the preceding claims, characterized in 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.Device (100) for heat transfer according to one of the preceding claims, characterized in that at least one swirl 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 swirl tube (17) is designed to separate the source medium into a hot portion and a cold portion.Device (100) for heat transfer according to Claim 7, characterized in that a mass flow of the source medium through the at least one section (A5) can be adjusted via at least one bypass (B5).Device (100) for heat transfer according to Claim 7 or 8, characterized in 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.Method for heat transfer, comprising the steps of: - evaporating (S1) 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), - expanding (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 is adjusted by the at least one high-temperature section (A1) via at least one bypass (B1) and / or a mass flow of the working medium is adjusted by at least one section (A2) between the at least one throttle (14) and the at least one evaporator (11) via at least one further bypass (B2), wherein heat is recuperated in the at least one high-temperature recuperator (15) when at least a part 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 is adjusted by the at least one low-temperature section (A3) via at least one further bypass (B3) and / or a mass flow of the working medium is adjusted by at least one further section (A4) via at least one further bypass (B4), wherein heat is recuperated in the at least one low-temperature recuperator (16) when at least a part 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).

Images