Use of different heat sources in ORC systems

Abstract

The invention relates to a system comprising the following: an organic Rankine cycle device, ORC device, having at least one ORC heat exchanger which comprises a preheating region for preheating and an evaporation region for evaporating a working medium of the ORC device; a heat-transfer-medium circuit for supplying heat from a low-temperature fluid at a first temperature to the evaporation region and / or to the preheating region; a first heat exchanger for supplying heat from a high-temperature fluid at a second temperature to the heat transfer medium; wherein a first temperature range of the low-temperature fluid is at least partially lower than a second temperature range of the high-temperature fluid, and wherein the first temperature lies in the first temperature range and the second temperature lies in the second temperature range; and a controller for controlling the supply of heat to the evaporation region and / or the supply of heat to the preheating region.

Description

[0001] USE OF DIFFERENT HEAT SOURCES IN ORC SYSTEMS

[0002] Field of the invention

[0003] The invention relates to a system with an ORC device and a ship with such a system.

[0004] State of the art

[0005] Devices are known that use the Organic Rankine Cycle (ORC) to generate energy, particularly electrical energy, from waste heat.

[0006] In the case of maritime use of such ORC systems on a ship, waste heat is present in various forms and at different temperature ranges. Until now, only such a heat source has been used to evaporate the working fluid of an ORC system.

[0007] This is disadvantageous in that other existing sources of waste heat remain unused.

[0008] The problem is to operate an ORC device with both high-temperature heat (e.g. exhaust gas, steam, thermal oil, charge air cooling) and low-temperature heat (e.g. engine cooling water) for evaporation (previously engine cooling water was used for preheating and high-temperature heat for evaporation).

[0009] Description of the invention

[0010] The object of the invention is to avoid or at least mitigate the aforementioned disadvantages. In particular, two or more heat sources are to be used to generate electrical energy in an ORC device. The inventive solution is defined by a system having the features according to claim 1.

[0011] The invention thus discloses a system comprising: an Organic Rankine Cycle (ORC) device, with at least one ORC heat exchanger comprising a preheating region for preheating and an evaporation region for evaporating working medium of the ORC device; a heat transfer medium circuit for supplying heat from a low-temperature fluid having a first temperature to the evaporation region and / or to the preheating region; a first heat exchanger for supplying heat from a high-temperature fluid having a second temperature to the heat transfer medium; wherein a first temperature range of the low-temperature fluid is at least partially lower than a second temperature range of the high-temperature fluid, and wherein the first temperature lies in the first temperature range and the second temperature lies in the second temperature range;and a controller for controlling the heat supply to the evaporation region and / or the heat supply to the preheating region;

[0012] In this way, heat from two different heat sources with different temperature ranges can be used in the ORC device to generate electrical energy. Heat from the low-temperature fluid can be supplied to the ORC device via the heat transfer medium circuit. Heat from the high-temperature fluid can be coupled into the heat transfer medium circuit via the first heat exchanger and supplied to the ORC device. In addition to evaporation, the evaporation zone can optionally also be used to superheat the working medium of the ORC device. This option also applies to each of the further developments and embodiments described below.

[0013] A further development of the system according to the invention is that the preheating region can comprise a preheater heat exchanger for preheating the working medium, and the evaporation region can comprise an evaporator heat exchanger for evaporating the preheated working medium, wherein the preheater heat exchanger and the evaporator heat exchanger are provided separately; or wherein the at least one ORC heat exchanger comprises a preheating section for preheating the working medium and an evaporation section for evaporating the preheated working medium.

[0014] The ORC heat exchanger can therefore be designed as two separate heat exchangers (a preheater and an evaporator), or alternatively, the ORC heat exchanger has a section for preheating the working medium and a subsequent section for evaporating the working medium.

[0015] Another development is that an upper end range of the first temperature range can overlap with a lower end range of the second temperature range.

[0016] Heat from a continuous temperature range consisting of the first and second temperature ranges can be utilized in the ORC device. However, the first temperature of the low-temperature fluid can be lower than the second temperature of the high-temperature fluid.

[0017] According to another embodiment, the heat transfer medium and the low-temperature fluid can be identical and the heat transfer medium circuit can be a low-temperature fluid circuit.

[0018] The low-temperature fluid is also used as a heat transfer medium for the circuit to supply heat to the ORC device (to the evaporation area and / or to the preheating area).

[0019] Another development is that a second heat exchanger can be provided in the heat transfer medium circuit for supplying heat from the low-temperature fluid to the heat transfer medium.

[0020] In this development, the heat from the low-temperature fluid is coupled into the heat transfer medium circuit via the second heat exchanger. According to another development, the controller can be configured to control a mass flow of the heat transfer medium through the second heat exchanger via a bypass with a first valve.

[0021] In this way, the transfer of heat between the low-temperature fluid and the heat transfer medium can be controlled.

[0022] Another development is that the system can comprise a hydraulic connection which is designed to guide a return flow of the low-temperature fluid from the second heat exchanger completely or partially to the preheating area.

[0023] If the return flow of the low-temperature fluid from the second heat exchanger is directed completely or partially to the preheating zone of the ORC heat exchanger, heat from the low-temperature fluid can first be directed to the heat transfer medium and thus to the evaporation zone for evaporating the working medium of the ORC device. Furthermore, heat from the already cooled return flow of the low-temperature fluid can be directed directly to the preheating zone for preheating the working medium of the ORC device. If the return flow is only partially directed to the preheating zone, the control system can be used to adjust the volume or mass flow flowing to the preheating zone to influence the amount of heat transferred in the preheating zone.

[0024] According to another development, the controller can be designed to control a mass flow of the low-temperature fluid through the second heat exchanger via a second valve.

[0025] This allows the heat exchange between the low-temperature fluid and the heat transfer medium to be controlled.

[0026] Another refinement is that the controller can be configured to control a mass flow of the high-temperature fluid through the first heat exchanger via a third valve. This allows the heat exchange between the high-temperature fluid and the heat transfer medium to be regulated.

[0027] According to another development, the heat transfer medium and the high-temperature fluid can be identical, the heat transfer medium can be present as a liquid, the high-temperature fluid supplied to the first heat exchanger in an inlet can be present as steam and the high-temperature fluid discharged from the first heat exchanger in a return can be present as condensate.

[0028] The heat transfer medium can be, for example, liquid water, and the heat transfer medium circuit can be a hot water circuit. The steam can be, in particular, water vapor, and the condensate can be condensed water vapor.

[0029] Another refinement consists in that a first connection with a first pressure control valve can be provided between the high-temperature fluid inlet and the heat transfer medium circuit, and / or a second connection with a second pressure control valve can be provided between the high-temperature fluid return and the heat transfer medium circuit. The controller can be configured to regulate pressurization with the first pressure control valve and / or to regulate pressure reduction with the second pressure control valve.

[0030] This provides a connection, for example, between a steam circuit (high-temperature fluid) and a hot water circuit (heat transfer medium). Pressure control can be achieved in the inlet of the ORC device.

[0031] As an alternative to the previous embodiment, the high-temperature fluid inlet can comprise a third pressure control valve to the first heat exchanger, a direct connection of the return from the first heat exchanger to a return of the heat transfer medium circuit from the ORC device can be provided, a return of condensate to a steam generator can be provided via a fourth pressure control valve, and the controller can be configured to regulate pressurization with the third pressure control valve and / or to regulate pressure reduction with the fourth pressure control valve. In this way, condensate heat can be utilized and pressure control in the heat transfer medium circuit can be simplified.

[0032] The invention also relates to a vehicle, in particular a ship, which comprises a system according to the invention or one of the above-mentioned developments of the system according to the invention.

[0033] Particularly in maritime applications on a ship, there are various heat sources with different temperature ranges that are provided for various applications, but are sometimes not (fully) used.

[0034] In a further development, the low-temperature heat source can comprise cooling water of a drive engine of the vehicle and / or cooling water of a charge air cooler of the drive engine of the vehicle.

[0035] In another development, the high-temperature heat source can comprise cooling water of a charge air cooler of a / the drive engine of the vehicle and / or steam heated by means of exhaust gas from the drive engine and / or thermal oil heated by means of exhaust gas from the drive engine and / or hot water heated by means of exhaust gas from the drive engine and / or and / or warm water heated by means of exhaust gas from the drive engine.

[0036] The training courses mentioned can be used individually or combined as required.

[0037] Further features and exemplary embodiments, as well as advantages of the present invention, are explained in more detail below with reference to the drawings. It is understood that the embodiments do not exhaust the scope of the present invention. It is further understood that some or all of the features described below can also be combined in other ways. Drawings

[0038] Fig. 1 shows variants of the ORC device.

[0039] Fig. 2 shows a first embodiment of the system according to the invention.

[0040] Fig. 3 shows a second embodiment of the system according to the invention.

[0041] Fig. 4 shows a third embodiment of the system according to the invention.

[0042] Fig. 5 shows a fourth embodiment of the system according to the invention.

[0043] Fig. 6 shows a fifth embodiment of the system according to the invention.

[0044] Fig. 7 shows a sixth embodiment of the inventive

[0045] System.

[0046] Fig. 8 shows a seventh embodiment of the inventive

[0047] System.

[0048] Fig. 9 shows an eighth embodiment of the system according to the invention.

[0049] Fig. 10 shows a ninth embodiment of the system according to the invention.

[0050] The same reference symbols in the drawings refer to identical or corresponding components.

[0051] Embodiments

[0052] There are operating points, particularly on ships, where high-temperature exhaust heat in the form of steam, thermal oil, etc. is not available, or not sufficient, to enable the operation of an ORC system. This is particularly the case with modern 2-stroke engines, where very little heat is contained in the exhaust gas. In addition, exhaust gas temperatures are very low (cf. modern diesel engines in cars). For this reason, the usable high-temperature heat in modern 2-stroke engines is very low at cold outside temperatures, meaning that an ORC system designed only to operate with high-temperature heat can in many cases only achieve a short number of operating hours. The amount of heat decreases with decreasing outside temperatures, as the engine's efficiency increases; at high outside temperatures, however, the amount of heat increases. This is in contrast to the demand for heat; here more heat is required in cold temperatures and less in warm outside temperatures.In this context, the cooling water temperatures (e.g. sea water temperature) should also be mentioned, which influence the charging via the intercooler.

[0053] One challenge here is operating the ORC system with both high-temperature (HT) heat (exhaust gas / steam / thermal oil / or charge air cooling) and low-temperature (LT) heat (engine cooling water, MKW). This problem forms the basis of the present invention.

[0054] Fig. 1 shows an ORC device 10 with variants regarding the design of the preheating zone 1, 1a and the evaporation zone 2, 2a for the working medium of the ORC device. The ORC device 10 further comprises - as known from the prior art - an expansion device 3 with an electric generator 4, a condenser 5 and a pump 6.

[0055] In the left version, preheater 1 and evaporator 2 are provided separately and the heat is supplied from two different heat sources.

[0056] In the middle version, preheater 1 and evaporator 2 are also provided separately, with the heat being supplied from a heat source in each case by passing a return flow from the evaporator 2 via the preheater 1.

[0057] In the right-hand version, preheater 1a and evaporator 2a are provided as a structural unit, whereby heat from a heat source is used in the evaporation area 2a for evaporation and in the preheating area 1a for preheating the working medium.

[0058] Fig. 2 shows a first embodiment 100 of the system according to the invention.

[0059] In this embodiment, the system 100 according to the invention comprises an Organic Rankine Cycle device 10 with an ORC heat exchanger, which comprises a preheating region 1, 1a for preheating and an evaporation region 2, 2a for evaporating working medium of the ORC device 10; a heat transfer medium circuit 20 for supplying heat from a low-temperature fluid at a first temperature to the evaporation region 2, 2a and / or to the preheating region 1, 1a; a first heat exchanger 31 for supplying heat from a high-temperature fluid at a second temperature to the heat transfer medium; wherein a first temperature range of the low-temperature fluid is at least partially lower than a second temperature range of the high-temperature fluid, and wherein the first temperature lies in the first temperature range and the second temperature lies in the second temperature range;and a controller 90 for controlling the heat supply to the evaporation region 2, 2a and / or the heat supply to the preheating region 1, 1a.;

[0060] The heat transfer medium and the low-temperature fluid are identical in this embodiment, namely water or a mixture of water and glycol and / or other additives. The low-temperature fluid here is engine cooling water (MKW) of an internal combustion engine 40, in particular a propulsion engine of a ship.

[0061] A pump 50 is provided to pump the heat transfer medium in the heat transfer medium circuit 20 and to conduct it through the ORC device 10. A valve 21 (three-way valve) serves to regulate a portion of the MKW that circulates in the heat transfer medium circuit 20 through the ORC device 10. The control system can allow engine cooling water to flow into the heat transfer medium circuit 20 via the valve 21 if the temperature of the MKW is greater than the temperature of the return flow of the heat transfer medium (the water) from the ORC device 10. Alternatively to the illustrated position, the three-way valve 21 can be installed in the return flow to the combustion engine 40 (generally to the heat source), in particular as a distribution valve downstream of the pump 50.

[0062] Excess steam present on a ship, for example, can be coupled as a high-temperature fluid via the first heat exchanger 31 in order to transfer heat from it to the heat transfer medium. When heat from excess steam is coupled into the engine cooling water as a heat transfer medium, no separate pressure maintenance is necessary. However, additional safety devices (not shown here) are generally provided to prevent specified parameters of the engine cooling water circuit 20 from being exceeded. The condenser 5 of the ORC device 10 can be cooled directly using seawater. The direct use of seawater for recooling leads to a reduction of the condensation temperature to the lowest possible level; however, indirect recooling via a cooling water circuit can alternatively be achieved.

[0063] Fig. 3 shows a second embodiment 200 of the system according to the invention.

[0064] In this embodiment, the heat from the low-temperature fluid (e.g., MKW) is coupled into the heat transfer medium of the heat transfer medium circuit 20 via a second heat exchanger 32. The heat transfer medium circuit 20 here is an intermediate circuit between the low-temperature fluid and the ORC device. In particular, the heat transfer medium can be water, so that the heat transfer medium circuit 20 is then a hot water intermediate circuit. However, in addition to water, the heat transfer medium can also contain glycol and / or additives (antifreeze, corrosion prevention).

[0065] Fig. 4 shows a third embodiment 300 of the system according to the invention.

[0066] Compared to the second embodiment 200, a first valve 61 (three-way valve) is provided in the heat transfer medium circuit 20, with which the second heat exchanger 32 can be partially or completely bypassed. The controller 90 is designed to control a mass flow of the heat transfer medium through the second heat exchanger 32 via the bypass with the first valve 61.

[0067] Fig. 5 shows a fourth embodiment 400 of the system according to the invention.

[0068] In this embodiment, low-temperature fluid (e.g., MKW) is fed directly to the preheating zone 1, 1a of the ORC device. Thus, high-temperature heat (exhaust gas, steam, etc.) is transferred via the first heat exchanger 31 to the heat transfer medium circuit 20, which is designed as an intermediate circuit between the high-temperature fluid and the ORC device 10. The intermediate circuit can be designed, for example, as a hot water circuit. A third valve 63 can be used to regulate the mass flow of the high-temperature fluid through the first heat exchanger 31.

[0069] Low-temperature heat (e.g. from MKW) is absorbed directly via a connection, e.g. to preheater 1 in ORC module 10.

[0070] Fig. 6 shows a fifth embodiment 500 of the system according to the invention.

[0071] Compared to the fourth embodiment 400 shown in Fig. 5 and described above, in the fifth embodiment 500 (as already described in the fourth embodiment 400), a second heat exchanger 32 is provided in the heat transfer medium circuit 20 for coupling heat from the low-temperature fluid. Just as in the fourth embodiment 400, the first valve 61 is provided for the bypass in the heat transfer medium circuit 20.

[0072] With a second valve 62, the mass flow of the low-temperature fluid through the second heat exchanger 32 can be controlled by means of the controller 90.

[0073] High-temperature heat (exhaust gas, steam, etc.) is transferred to the intermediate circuit 20 via the first heat exchanger 31. An additional, optional transfer of low-temperature heat takes place via the second heat exchanger 32 in the intermediate circuit 20. This heat can only be transferred if the temperature in the intermediate circuit 20 is lower than the temperature of the low-temperature heat. In particular, the temperature of the fluid in the intermediate circuit 20 at the inlet to the heat exchanger 31 must be lower than the temperature of the high-temperature fluid. Care must also be taken to ensure that no heat is transferred back into the low-temperature fluid, as the low-temperature fluid is usually engine cooling water and must not be influenced or exposed to additional heat to avoid compromising engine cooling.

[0074] Low-temperature heat (e.g., from MKW) is absorbed via a connection directly to the preheating zone 1, 1a in the ORC module. A disadvantage here is that, when MKW is used exclusively as the low-temperature fluid and no heat from the high-temperature fluid, the intermediate circuit 20 has a lower temperature than the low-temperature fluid in the preheating zone, since a temperature difference is necessary for heat transfer in the second heat exchanger 32. Thus, the preheating zone 1, 1a is supplied with a higher temperature than the evaporation zone 2, 2a. This can lead to (partial) evaporation already in the preheating zone, which can be problematic during operation (inconsistent fluid distribution, start-up problems, etc.). This can be prevented by appropriately regulating the mass flows through the controller 90 using the valves.

[0075] Fig. 7 shows a sixth embodiment 600 of the system according to the invention.

[0076] Compared to the fifth embodiment shown in Fig. 6 and described above, in the sixth embodiment 600 a hydraulic connection 65 is provided which is designed to guide a return flow of the low-temperature fluid from the second heat exchanger 32 completely to the preheating region 1, 1a.

[0077] Thus, a connection of the return flow from the second heat exchanger 32 to the preheating zone 1, 1a is provided. This is particularly advantageous because it eliminates problems with evaporation in the preheating zone, since the temperature of the low-temperature fluid is lower than the temperature of the heat transfer medium in the intermediate circuit 20, or at least less significantly above the temperature in the intermediate circuit 20 than in the circuit according to the fifth embodiment.

[0078] In this configuration according to the sixth embodiment 600, the entire return flow from the second heat exchanger 32 is used for preheating, which, however, entails the disadvantage of increased pressure losses. A lower volume flow would be sufficient for preheating. This enables the configuration according to the seventh embodiment 700 described below.

[0079] Fig. 8 shows a seventh embodiment 700 of the system according to the invention.

[0080] Compared to the sixth embodiment 600, the hydraulic connection 65 is designed such that a return of the low-temperature fluid from the second heat exchanger 32 is partially (not completely) guided to the preheating region 1, 1a.

[0081] The mass or volume flows can be adjusted by installing a throttle valve (not shown) in the return flow of the low-temperature fluid from the second heat exchanger 32 for the intermediate circuit 20. Only a portion of the return flow of the low-temperature fluid is used for preheating in the ORC device 10. Alternatively, a controllable valve (three-way valve) could be used.

[0082] The mass flows are adjusted according to the required amount of heat in the evaporation and preheating area (1, 1a; 2, 2a).

[0083] Description of the operation for the sixth and seventh embodiments 600, 700:

[0084] Operation A: Heat transfer of low-temperature heat via the second heat exchanger 32 to the intermediate circuit 20 and heat input into the ORC system in the evaporation zone 2, 2a through the intermediate circuit 20. Preheating via the hydraulic connection 65 through the return flow (total volume flow or partial volume flow) of the second heat exchanger 32 at a lower temperature level than the intermediate circuit 20.

[0085] Operation B: The first valve 61 is switched so that the second heat exchanger 32 is bypassed to the intermediate circuit 20. The temperature level of the low-temperature fluid is thus also present in the preheating area 1, 1a. Operation C: The inlet to the second heat exchanger 32 is shut off, and no heat is introduced into the preheating area. Heat is introduced only via the high-temperature fluid or the intermediate circuit 20 via the first heat exchanger 31.

[0086] Advantages of the sixth and seventh embodiments 600, 700:

[0087] Due to the wiring, in operation A (low-temperature heat only), the temperature at the entry into the evaporation area (supply intermediate circuit 20) will always be above the temperature at which the low-temperature heat is integrated into the preheating area.

[0088] In the fifth embodiment 500, the temperature of the low-temperature fluid would be higher than the temperature of the intermediate circuit 20. The reason for this is that, thanks to the second heat exchanger 32, the temperature level in the intermediate circuit 20 is always below the low-temperature heat. As a result, evaporation (or part of the evaporation) already occurs in the preheating area. This is not suitable from a process engineering perspective (two-phase flow in the preheater, pressure losses, process control, instabilities, uneven distribution). Due to the interconnection in the sixth and seventh embodiments 600, 700, in operation A, the temperature between the evaporation area (heat integration via the intermediate circuit 20) and the preheating area (heat integration via the low-temperature fluid) is automatically adjusted so that the process-engineered and advantageous properties of the evaporator and preheater can be utilized.The preheater is not technically designed or suitable for evaporation. Furthermore, process-related problems can arise from the entry of partially evaporated medium into the evaporator (after the preheater). Due to the automatic temperature grading, this cannot occur in the 600 and 700 versions, or only to a limited extent.

[0089] The sixth and seventh configurations (600, 700) require only one connection to the low-temperature heat source instead of two. This saves on equipment costs.

[0090] Fig. 9 shows an eighth embodiment 800 of the system according to the invention. According to the eighth embodiment 800, the heat transfer medium and the high-temperature fluid are identical; the heat transfer medium is present as a liquid, the high-temperature fluid supplied to the first heat exchanger 31 via an inlet is present as steam, and the high-temperature fluid discharged from the first heat exchanger 31 via a return line is present as condensate. The heat transfer medium can be, for example, liquid water, and the heat transfer medium circuit 20 can be a hot water circuit. The steam can be, in particular, water vapor, and the condensate can be condensed water vapor.

[0091] A first connection with a first pressure control valve 66 is provided between the high-temperature fluid inlet and the heat transfer medium circuit 20, and a second connection with a second pressure control valve 67 is provided between the high-temperature fluid return and the heat transfer medium circuit 20. The controller 90 is configured to control pressurization with the first pressure control valve 66 and / or to control pressure reduction with the second pressure control valve 67. The connection between the heat transfer medium circuit 20 and the second pressure control valve 67 can be established at any point in the heat transfer medium circuit 20.

[0092] This provides a connection, for example, between a steam circuit (high-temperature fluid) and a hot water circuit (heat transfer medium). Pressure control can be achieved in the inlet of the ORC device.

[0093] The steam network on a ship is usually in the range of 6 to 8 bar pressure and is always in operation, but excess steam is not always available. Here, the steam and / or condensate line is connected to hot water circuit 20. Since hot water circuit 20 is full, no condensation occurs.

[0094] As in the seventh embodiment 700, a bypass of the second heat exchanger 32 can be provided via a bypass with the first valve 61 in the heat transfer medium circuit 20, with which the second heat exchanger 32 can be partially or completely bypassed. Fig. 10 shows a ninth embodiment 900 of the system according to the invention.

[0095] According to the ninth embodiment 900, the inlet of the high-temperature fluid comprises a third pressure control valve 68 to the first heat exchanger 31 and a direct connection of the return from the first heat exchanger 31 into a return of the heat transfer medium circuit 20 from the ORC device 10, wherein a return of condensate to a steam generator is provided via a fourth pressure control valve 69, and the controller is designed to regulate a pressurization with the third pressure control valve 68 and / or to regulate a pressure reduction with the fourth pressure control valve 69.

[0096] In this way, condensate heat can be utilized and pressure control in the heat transfer medium circuit 20 can be simplified.

[0097] When excess steam is used for heat injection, the condensate cannot be cooled below the temperature of the return flow of the heat transfer medium circuit 20 from the ORC device 10; approximately 10 K of usable potential still remains. This design allows for a 2 to 3% increase in heat input while simplifying pressure maintenance. For this purpose, a direct connection of the condensate return from the first heat exchanger 31 (here also a steam condenser) to the return flow of the ORC device 10 is provided. Condensate from the hot water circuit 20 is returned to the steam boiler from the hot water circuit 20 directly downstream of the ORC device 10.

[0098] As in the seventh embodiment 700, a bypass of the second heat exchanger 32 can be provided via a bypass with the first valve 61 in the heat transfer medium circuit 20, with which the second heat exchanger 32 can be partially or completely bypassed.

[0099] The illustrated embodiments are merely exemplary and the full scope of the present invention is defined by the claims.

Claims

Patent claims 1. A system (100-900) comprising: an Organic Rankine Cycle device (10), ORC device, with at least one ORC heat exchanger (1, 2; 1a, 2a) comprising a preheating region (1) for preheating and an evaporation region (2) for evaporating working medium of the ORC device; a heat transfer medium circuit (20) for supplying heat from a low-temperature fluid having a first temperature to the evaporation region (2, 2a) and / or to the preheating region (1, 1a); a first heat exchanger (31) for supplying heat from a high-temperature fluid having a second temperature to the heat transfer medium; wherein a first temperature range of the low-temperature fluid is at least partially lower than a second temperature range of the high-temperature fluid, and wherein the first temperature lies in the first temperature range and the second temperature lies in the second temperature range;and a controller (90) for controlling the heat supply to the evaporation region (2, 2a) and / or the heat supply to the preheating region (1, 1a).; 2. System according to claim 1, wherein the preheating region comprises a preheater heat exchanger (1) for preheating the working medium and the evaporation region comprises an evaporator heat exchanger (2) for evaporating the preheated working medium, wherein the preheater heat exchanger (1) and the evaporator heat exchanger (2) are provided separately; or wherein the at least one ORC heat exchanger comprises a preheating section (1a) for preheating the working medium and a Evaporation section (2a) for evaporating the preheated working medium.

3. The system of claim 1 or 2, wherein an upper end region of the first temperature range overlaps with a lower end region of the second temperature range.

4. System according to one of claims 1 to 3, wherein the heat transfer medium and the low-temperature fluid are identical and the heat transfer medium circuit (20) is a low-temperature fluid circuit.

5. System according to one of claims 1 to 3, wherein a second heat exchanger (32) is provided in the heat transfer medium circuit (20) for supplying heat from the low-temperature fluid to the heat transfer medium.

6. System according to claim 5, wherein the controller (90) is designed to control a mass flow of the heat transfer medium through the second heat exchanger (32) via a bypass with a first valve (61).

7. System according to claim 5 or 6, comprising a hydraulic connection (65) which is designed to guide a return of the low-temperature fluid from the second heat exchanger (32) completely or partially to the preheating region.

8. System according to one of claims 5 to 7, wherein the controller is designed to control a mass flow of the low-temperature fluid through the second heat exchanger (32) via a second valve (62).

9. System according to one of claims 1 to 8, wherein the controller is designed to control a mass flow of the high-temperature fluid through the first heat exchanger (31) via a third valve (63).

10. System according to one of claims 5 to 9, wherein the heat transfer medium and the high-temperature fluid are identical, the heat transfer medium is present as a liquid, the high-temperature fluid supplied to the first heat exchanger (31) in an inlet (31a) is present as steam and the high-temperature fluid discharged from the first heat exchanger (31) in a return (31b) is present as condensate.

11. The system according to claim 10, wherein a first connection to a first pressure control valve (66) is provided between the inlet (31a) of the high-temperature fluid and the heat transfer medium circuit (20), and / or wherein a second connection to a second pressure control valve (67) is provided between the return (31b) of the high-temperature fluid and the heat transfer medium circuit (20); and wherein the controller (90) is designed to regulate pressurization with the first pressure control valve (66) and / or to regulate pressure reduction with the second pressure control valve (67).

12. System according to claim 10, wherein the inlet (31a) of the high-temperature fluid comprises a third pressure control valve (68) to the first heat exchanger (31), a direct connection of the return line (31 b) from the first heat exchanger (31) into a return line (20 b) of the heat transfer medium circuit (20) from the ORC device (10) is provided, a return of condensate from the return line (20 b) of the heat transfer medium circuit (20) to a steam generator via a fourth pressure control valve (69) is provided, and wherein the controller (90) is designed to regulate a pressurization with the third pressure control valve (68) and / or to regulate a pressure reduction with the fourth pressure control valve (69).

13. Vehicle, in particular a ship, comprising: System according to one of claims 1 to 12.

14. Vehicle according to claim 13, wherein the low-temperature heat source comprises cooling water of a drive engine (40) of the vehicle and / or cooling water of a charge air cooler of the drive engine (40).

15. Vehicle according to claim 13 or 14, wherein the high-temperature heat source comprises cooling water of a charge air cooler of / the drive engine (40) of the vehicle and / or steam heated by means of exhaust gas from the drive engine (40) and / or thermal oil heated by means of exhaust gas from the drive engine (40) and / or hot water heated by means of exhaust gas from the drive engine (40) and / or and / or warm water heated by means of exhaust gas from the drive engine (40).

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