EP3447256A1 - Orc device for cooling a process fluid - Google Patents

Abstract

The invention relates to a system for cooling a process fluid of a heat-generating device, comprising: an output of the heat-generating device (10), the output (11) being provided for discharging process fluid to be cooled from the heat-generating device; an input (12) of the heat generating means, the input being for supplying cooled process fluid to the heat generating means; and a thermodynamic cycle apparatus, in particular an ORC apparatus, the thermodynamic cycle apparatus comprising: an evaporator (20) having an inlet for supplying the process fluid to be cooled from the outlet of the heat generating means and having an outlet for discharging the cooled process fluid to the entrance of the heat generating means wherein the evaporator is adapted to evaporate a working medium of the thermodynamic cycle device by means of heat from the process fluid; an expansion machine (30) for expanding the vaporized working medium and for generating mechanical and / or electrical energy; a condenser (50) for liquefying the expanded working medium, in particular an air-cooled condenser; and a pump (60) for pumping the liquefied working fluid to the evaporator.

Description

Field of the invention

The invention relates to a system for cooling a process fluid of a heat-generating device.

State of the art

Currently, there are numerous applications in industry (e.g., refrigeration of air compressors, food industry, chemical industry), power generation (e.g., cooling of engine cooling water in stationary engines, transformers), or in transportation (internal combustion engines, e.g., trucks) in which e.g. electrical (or mechanical) energy is used to drive a cooler, such as an air cooler. In this case, we the medium to be cooled i.d.R. passed into a heat exchanger, which is flowed through by ambient air. The air flow is hereby e.g. generated by electrically or mechanically driven fans. The medium to be cooled (hereinafter referred to as process fluid) releases the energy into the ambient air and returns to the process in a cooled state. The disadvantage here is that electrical or mechanical energy is expended to remove the process thermal energy.

Description of the invention

The object of the invention is to avoid the disadvantages mentioned or at least mitigate.

The invention describes the solution of the abovementioned problem by partially converting the heat taken from the medium into mechanical and / or electrical energy by means of a thermodynamic cycle device.

The solution according to the invention is defined by a device having the features according to claim 1.

The invention thus discloses a system for cooling a process fluid of a heat-generating device, comprising: an output of the heat-generating device, the output being provided for discharging process fluid to be cooled from the heat-generating device; an input of the heat generating means, the input for supplying cooled process fluid to the heat generating means is provided; and a thermodynamic cycle apparatus, in particular an ORC apparatus, the thermodynamic cycle apparatus comprising: an evaporator having an inlet for supplying the process fluid to be cooled from the outlet of the heat generating means and having an outlet for discharging the cooled process fluid to the entrance of the heat generating means; Evaporator for vaporizing a working medium of the thermodynamic cycle device is formed by means of heat from the process fluid; an expansion machine for expanding the vaporized working medium and for generating mechanical and / or electrical energy; a condenser for liquefying the expanded working medium, in particular an air-cooled condenser; and a pump for pumping the liquefied working fluid to the evaporator. The recovered mechanical and / or electrical energy can be used for operating the capacitor, in particular for driving a fan of an air-cooled condenser.

A development of the system according to the invention consists in that a cooler, in particular an air cooler, can be provided for cooling at least part of the process fluid to be cooled. In this way, a Notlauffähigkeit can be ensured in case of failure of the thermodynamic cycle device.

Another development is that a branch, which is provided with respect to a flow direction of the process fluid downstream of the output of the heat generating device and upstream of the input of the heat generating means for dividing the process fluid to be cooled in a first and a second partial flow of the process fluid the Branch optionally includes a valve; and a junction provided with respect to a flow direction of the process fluid downstream of the branch and upstream of the entrance of the heat generating means for merging the first and second substreams of the process fluid.

According to this development, the stream of process fluid can be divided into two sub-streams, for example, with one sub-stream being passed through the evaporator and the other sub-stream passing through the cooler. However, it is also possible not to conduct the flow of the process fluid at all or only partially through the evaporator and / or cooler, for example if otherwise a cooling of the process fluid that is too strong for the heat-generating device would take place. For this purpose, the branch or a further branch and the combination or a further combination can be connected via a connecting line, that the exiting from the output of the heat generating device process fluid is at least partially directly fed back to the entrance, the mass flow through the Connecting line can be adjusted via the or another valve.

This may be developed in that the branch is provided with respect to a flow direction of the process fluid downstream of the exit and upstream of the inlet for dividing the process fluid to be cooled into the first and the second substream of the process fluid, the branch optionally comprising a valve. This makes it possible to direct the process fluid to be cooled in front of the evaporator wholly or partly directly to the radiator.

The merging may be provided with respect to a flow direction of the process fluid downstream of the outlet and upstream of the inlet for merging the cooled by the cooler second partial flow of the process fluid and the cooled by the evaporator first partial flow of the process fluid; wherein the branch for supplying the first partial flow to the evaporator and for supplying the second partial flow to the radiator is formed. Thus, with respect to the flow of the process fluid is a parallel Interconnection of the components (evaporator, cooler), which extract heat from the process fluid, realized.

In another embodiment, the radiator may be located downstream of the outlet with respect to a flow direction of the process fluid and upstream of the inlet for further cooling the process fluid cooled by the evaporator. This represents a series connection of the components (evaporator, cooler) that extract heat from the process fluid.

According to another embodiment, the cooler may form a structural unit with the capacitor or be provided separately from the capacitor. If the radiator is formed in a structural unit with the condenser, e.g. be provided a common fan for air cooling. In contrast, if the radiator is formed separately from the condenser, the cooling capacity of these components can be controlled independently of each other.

Another development is that the system may further comprise a control device for controlling the heat input into the radiator, whereby in particular a desired temperature of the input of the heat-generating device recycled process fluid can be achieved.

According to another development may be provided for thermal connection of the condenser and the condenser, an intermediate circuit with a heat transfer fluid, wherein the condenser is provided for transferring heat from the expanded working fluid to the heat transfer fluid and wherein the radiator is provided for cooling the heat transfer fluid.

This can be developed to the effect that useful heat can be dissipated from a branch of the heat transfer fluid flowing from the condenser to the condenser to a useful heat device.

In this case, a (chemical) composition of the heat transfer fluid can be identical to a composition of the process fluid.

The system according to the invention or one of its developments can furthermore comprise a further heat exchanger, which is provided with respect to a flow direction of the process fluid downstream of the evaporator for transferring heat from the process fluid cooled by the evaporator to a heat transfer fluid.

This can be further developed in that the system further comprises a valve for controlling the mass flow of the heat transfer fluid through the further heat exchanger. Thus, pre-cooled process fluid is supplied to a further heat exchanger in the evaporator and can be cooled therein to a target temperature. Furthermore, a temperature measuring device for measuring the temperature of the process fluid can be provided downstream of the further heat exchanger, wherein the regulation of the valve can then take place as a function of the measured temperature.

The system according to the invention or one of its developments may further comprise: a further evaporator between the outlet and the inlet for further evaporation of working medium by means of heat from the process fluid; a throttle valve for lowering the pressure of the working medium; and a liquid jet pump and / or a steam jet pump between the further evaporator and the condenser for lowering the pressure in the further evaporator, wherein in particular a part of the liquefied working medium or a part of the evaporated working medium serves as a propulsion jet. This realizes a 3-stage cooling of the process fluid described in more detail in the embodiments.

The developments with a cooler can be configured such that the outlet of the evaporator is connected to an input of the cooler, an output of the cooler to an input of the capacitor and an output of the capacitor to the input of the heat-generating device, so that in operation the process fluid from Evaporator is passed through the condenser for further cooling, then passed therethrough as a heat-absorbing medium through the condenser and is then passed thereafter to the entrance of the heat-generating device. The cooler therefore becomes independent of the thermodynamic cycle operated and provides a possibility for a Notlauffähigkeit of the system (in terms of emergency cooling of the process fluid).

The cited developments can be used individually or combined as claimed suitable.

Further features and exemplary embodiments and advantages of the present invention will be explained in more detail 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 may be combined with each other in other ways.

drawings

Fig. 1

shows a first embodiment (variant 1) of the device according to the invention.

Fig. 2

shows a second embodiment (variant 2A) of the device according to the invention.

Fig. 3

shows a third embodiment (variant 2B) of the device according to the invention.

Fig. 4

shows a temperature-heat flow diagram (T-Q diagram)

Fig. 5

shows a fourth embodiment (variant 2C) of the device according to the invention.

Fig. 6

shows a fifth embodiment (variant 3A) of the device according to the invention.

Fig. 7

shows a sixth embodiment (variant 3B) of the device according to the invention.

Fig. 8

shows a seventh embodiment (variant 4) of the device according to the invention.

Fig. 9

shows an eighth embodiment (variant 5) of the device according to the invention.

Figure 10

shows a ninth embodiment (variant 6) of the device according to the invention.

Fig. 11

shows a tenth embodiment (variant 7) of the device according to the invention.

Like reference numerals in the drawings refer to identical or corresponding components.

embodiments

In many applications of air coolers (see section: State of the art), a medium with temperatures> 50 ° C is cooled. This temperature level is sufficient to operate a thermodynamic cycle, e.g. an Organic Rankine Cycle Process (ORC process). It can therefore be provided in addition to the cooling function still usable mechanical and / or electrical energy. This energy can, for example, drive an air cooler or be used for other purposes (operation of consumers close to the process, pumps, energy storage ...).

The thermodynamic cycle thus replaces the air cooler originally used in the respective application, which is why in the case of an Organic Rankine cycle process, for example, an ORC cooler can be used for the application.

Specific preferred requirements for the ORC cooler:

• The cooling capacity should be guaranteed even if the ORC circuit fails.
• In the case of applications, no surplus electricity is to be generated, because the technical and legal complexity may increase disproportionately due to a direct grid feed-in. Therefore, in such a case, no connection to the mains is required.
• It should be as maintenance-free as possible or there should be no increase in maintenance costs compared to conventional coolers.
• If necessary, a temperature level of the main process / process to be cooled should be maintained, e.g. If a temperature of the recirculated process fluid should be achieved or undershot. By adding at least one further heat exchanger, there is a further temperature difference between the working fluid and the cooling fluid of a cooler (for example ambient air or cooling water), so that the target temperature of the process to be cooled can not be maintained. The interconnections below solve the problem of additional temperature difference.
• Modularity of the system is preferred in order to provide higher cooling capacities when needed.
• There should be no influence on the existing control system of the main process.

In general, the ORC cooler can be used for all processes where the fluid to be cooled can be returned to the process at a sufficiently large temperature distance from the ambient temperature (e.g., above 40 ° C).

Example applications for processes to be cooled (not complete):

• Engines (train, truck, construction machinery, crane, navy)
• Air compressors
• Industrial processes (automotive, chemicals, printing, electrical and electronics, glass, rubber, plastics, lasers, food, pharmaceutical, textile, environment, packaging, ...)
• Transformer stations
• Data Center (server cooling)

Detailed description in connection with the drawings Variant 1 - basic connection

Fig. 1 shows a first embodiment 100 of the thermodynamic cycle device according to the invention.

The system 100 for cooling a process fluid (e.g., water) of a heat generating device 10 includes: an output 11 of the heat generating device, the output 11 for discharging process fluid to be cooled from the heat generating device 10; an input 12 of the heat generating device 10, the input 12 for supplying cooled process fluid to the heat generating device 10 being provided; and a thermodynamic cycle device, in particular an ORC device, wherein the thermodynamic cycle device comprises: an evaporator 20 having an inlet 21 for supplying the process fluid to be cooled from the outlet 11 of the heat generating device 10 and having an outlet 22 for discharging the cooled process fluid to the inlet 12 the heat generating device 10, wherein the evaporator 20 is formed for evaporating a working medium of the thermodynamic cycle device by means of heat from the process fluid; an expansion machine 30 for expanding the vaporized working medium and for generating mechanical and / or electrical energy, for example by means of electrical generator 40; a condenser 50 for liquefying the expanded working medium, in particular an air-cooled condenser 50; and a pump 60 for pumping the liquefied working fluid to the evaporator.

The implementation of the invention in its simplest embodiment according to Fig. 1 as follows. In the evaporator 20, the hot process _fluid with the process temperature T _{proz, from} to the target temperature T _{proz, a} cooled, while the heat absorbed to evaporate the working medium in the ORC circuit is used. The live steam produced in this way is released under work delivery in the expansion machine 30, as a result of which, for example, a generator 40 can be driven. The exhaust steam is liquefied in the condenser 50 and then is liquid on the pump 60 at. The pump 60 then brings the working fluid back to the desired pressure. Through the device in Fig. 1 the previously used conventional air cooler of the process 10 is replaced and additionally generates useful power. However, as stated above, due to the additional circulation of the working fluid, the target temperature T _{Proz may} not be as low as without the ORC loop. Furthermore, in this first embodiment, a Runnability of the system not given. That is, in case of failure of the ORC system, the temperature T _{Proz, from} can not be lowered, it can not be cooled.

Variant 2A - Parallel connection

Fig. 2A shows a second embodiment 200 of the device according to the invention.

In this second embodiment 200 of the system according to the invention, cooler 70 (here an air cooler 70) is additionally provided for cooling at least part of the process fluid to be cooled. The system 200 includes a branch 71, which is provided by way of example with respect to a flow direction of the process fluid downstream of the outlet 11 and upstream of the inlet 21 for dividing the process fluid to be cooled into a first and a second partial flow of the process fluid, wherein the branch 71 in this Example, a valve V includes. The system 200 further includes a merging 72 provided with respect to a flow direction of the process fluid downstream of the outlet 22 and upstream of the inlet 12 for merging the second partial stream of the process fluid cooled by the cooler 70 and the first partial stream of the process fluid cooled by the evaporator 20 is; wherein the branch 71 is designed to supply the first partial flow to the evaporator 20 and to supply the second partial flow to the cooler 70. Thus, in relation to the flow of the process fluid, a parallel connection of the components (evaporator 20, cooler 70), which withdraw heat from the process fluid, is realized. The cooler 70 is here formed in a structural unit with the condenser 50, and a common fan for air cooling may be provided.

The interconnection according to Fig. 2A thus solves the problem of emergency running property. The bypass option (via valve V) of the ORC circuit ensures cooling in the event of an ORC circuit failure. The target temperature T _{proz, a} can be achieved by a partial _flow bypasses the ORC cycle, directly in the air cooler (eg: V-cooler, table cooler) is cooled and then the part stream from the ORC evaporator 20 is mixed. The current generated in the ORC cycle by the generator 40 can directly for the supply of the air cooler 70 (or the Combination of evaporator 50 and air cooler 70) can be used, whereby its electricity costs are significantly reduced, which in turn leads to increase the efficiency of the cooler 70 (evaporator 50). In addition, with this interconnection it is always possible to reach the target temperature T _{Proz, one} .

Fig. 2B represents a modification of the embodiment according to Fig. 2A by not allowing the flow of ambient air as in Fig. 2A passes in parallel through the condenser 50 and the radiator 70, but successively first through the radiator 70 and then through the condenser 50. This has the advantage of a compact design with the lowest air temperature at the radiator 70, thereby providing a low temperature of the process fluid can be achieved while the cooling of the working medium in the condenser 50 is less effective.

Fig. 2C represents an alternative to the modification according to Fig. 2B In this case, with respect to the air flow, the sequence of cooler 70 and evaporator 50 is reversed, so that the ambient air flows first through the evaporator 50 and then through the cooler 70. As a result, the lowest air temperature is present at the condenser 50, so that a higher power generation via the generator 40 is possible with the ORC circuit.

In the modifications according to Figs. 2B and 2C stays in relation to Fig. 2A described runflat ability received.

Variant 2B - Serial connection

Fig. 3 shows a third embodiment 300 of the device according to the invention.

In the third embodiment, the radiator 70 is disposed downstream of the outlet 22 of the evaporator 20 with respect to a flow direction of the process fluid and upstream of the inlet 12 of the heat generating device 10 for further cooling the process fluid cooled by the evaporator. This realizes a series connection of the components (evaporator 20, cooler 70), which extract heat from the process fluid. In a modified version, (similar to Embodiment according to Fig. 2 a valve may be provided which only supplies a portion of the process fluid via the radiator 70.

The process fluid / water return from the ORC evaporator 20 is sent through the air cooler 70 to allow further cooling. In a further development, the heat input to the air cooler 70 can be regulated by an intelligent regulation (eg with the aid of the named valve) so as not to cool further than necessary. The goal is to achieve the required T _{perc, one} without consuming electricity. This is in the temperature-heat flow diagram according to Fig. 4 shown (TQ diagram).

If the cooling T ₁ achievable by the ORC cycle is above a required limit, a lower temperature T _percent, can be achieved via additional cooling by means of water or air in the downstream cooler.

Variant 2C - Independent interconnection

Fig. 5 shows a fourth embodiment 400 of the device according to the invention.

The fourth embodiment substantially corresponds to the second embodiment according to FIG Fig. 2 , The difference is that the radiator 70 is provided separately from the condenser 50.

The advantage of this variant is that the ORC cooler (with the components 20, 30, 40, 50, 60) and the air cooler (emergency cooler) 70 can be operated completely independently of each other and emergency cooling for the process even if the ORC cooler fails is guaranteed. In addition, the systemic separation of the ORC cooler and air cooler facilitates easy integration into existing cooling systems. The existing cooler functions as an emergency cooler after integration and the ORC cooler as an additional module ("backpack module") for retrofits or extensions.

Variant 3A - Parallel connection in the water circuit

Fig. 6 shows a fifth embodiment 500 of the device according to the invention.

The fifth embodiment is based essentially on the second embodiment according to FIG Fig. 2 ,

However, according to the fifth embodiment, the thermal connection system 500 of the condenser 50 and the radiator 70a, 70b further includes an intermediate circuit including a heat transfer fluid (here, water), the condenser 50 being for transferring heat from the expanded working fluid to the heat transfer fluid, and wherein the radiator 70a, 70b is provided for cooling the heat transfer fluid. From a branch of the heat transfer fluid flowing from the condenser 50 to the cooler 70a, 70b, for example, useful heat can be dissipated to a useful heat device 80.

Variant 3B - Serial connection in the water circuit

Fig. 7 shows a sixth embodiment 600 of the device according to the invention.

The sixth embodiment is based on the third embodiment according to FIG Fig. 3 and was modified analogously to the fifth embodiment. The (chemical) composition of the heat transfer fluid is identical to the composition of the process fluid.

Often it is difficult to integrate air coolers (eg table coolers) due to their large footprint in existing systems. The Verschaltungsvarianten 3A and 3B reduce this problem by between ORC condenser 50 and the radiator 70, a further heat exchanger 75 and a DC link with a heat transfer fluid (eg water) are inserted. Thus, the installation sites of the heat source and the radiator are decoupled from each other and achieved a great flexibility in setting up the ORC process. Furthermore, the water intermediate circuit feed additional heat consumers. The variants 3A and 3B may also be permuted with respect to the heat source and the heat sink.

Variant 4 - combination radiator - preheater - ORC

Fig. 8 shows a seventh embodiment 700 of the device according to the invention.

According to the seventh embodiment 700 of the system according to the invention, a further heat exchanger 25 is provided which is provided (with respect to a flow direction of the process fluid downstream of the evaporator 20) for transferring heat from the process fluid cooled by the evaporator 20 to a heat transfer fluid.

The system comprises a valve 26 for controlling the mass flow of the heat transfer fluid through the further heat exchanger 25. Furthermore, a temperature measuring device 27 for measuring the temperature of the process fluid downstream of the further heat exchanger 25 is provided by way of example here, wherein the control of the valve 26 as a function of the measured Temperature takes place.

In this embodiment, it is possible to achieve a lowering of the temperature T _{Proz, one} to the same temperature level as without ORC, by additionally using a partial flow of a cold process medium (heat transfer fluid, here water) to be heated for cooling. The heat loss then happens in a first step through the ORC circuit. The pre-cooled heat transfer process fluid then flows through the further heat exchanger 25 in which it is cooled down to the target temperature.

In this case, another partial flow of the cold, to be heated process medium can be added to the process fluid in the flow direction after the other heat exchanger 25 for setting the target temperature.

Variant 5 - 3-stage cooling of the heat-supplying medium

Fig. 9 shows an eighth embodiment 800 of the device according to the invention.

According to the eighth embodiment, another evaporator 90 is provided between the outlet 22 and the inlet 12 for further evaporation of working fluid by means of heat from the process fluid. In addition, a throttle valve 91 for lowering the pressure of the working medium in the further evaporator 90 and a liquid jet pump 92 and / or a steam jet pump 93 between the further evaporator 90 and the condenser 50 for lowering the pressure in the further evaporator 90 is arranged, wherein in particular a part the liquefied working medium or a part of the vaporized working medium serves as a propulsion jet. This realizes a 3-stage cooling of the process fluid, as described below. In the drawing, both the embodiment with the liquid jet pump 92 and with the steam jet pump 93 is shown. As a rule, only one of the two pumps is provided. With the liquid jet pump 92, the lower line after the pump 60 to the liquid jet pump 92 is required, while in the case of the steam jet pump 93, the upper line for the vaporized in the evaporator 20 working fluid is required.

1st stage: normal operation

Heat-supplying medium is returned to the heat to be cooled in the evaporator after heat dissipation.

2nd stage: Cooling operation

A partial flow of the working medium is supplied via the throttle valve (throttle) 91 to the evaporator 90. The throttle 91 is adjusted so that the pressure approximately corresponds to the pressure in the condenser 50. As a result of the pressure reduction, the working medium in evaporator 90 only evaporates minimally above the condensation pressure and the condensation temperature of condenser 50, thus allowing cooling of the medium to be cooled to a temperature which is similarly low as the minimum achievable temperature in a direct heat exchanger to be cooled medium in air. That way you can even when retrofitting the cooling system with an ORC system ensure that the required temperatures of the medium to be cooled are maintained.

3rd stage: throttling to a pressure below the condenser pressure

A liquid jet pump 92 or a steam jet pump 93 causes a pressure drop in the evaporator 90 to a pressure below the condensation pressure in the condenser 50. It can thus even a lower boiling pressure than the condensation pressure in the condenser 50 can be achieved. As a result, the working fluid is promoted with very little expenditure of energy and raised again to the condensation pressure. The advantage here is that the working fluid must be promoted only in low mass flows and low pressure increase. Here, either a part of the live steam or a part of the feed fluid serves as a propulsion jet.

Variant 6 - Extension by an ORC module for existing coolers / without direct condensation

Fig. 10 shows a ninth embodiment 900 of the device according to the invention.

According to the tenth embodiments, the outlet 22 of the evaporator 20 is connected to an inlet 71 of the radiator 70, an outlet 72 of the radiator 70 to an inlet 51 of the condenser 50 and an outlet 52 of the condenser 50 to the inlet 12 of the heat-generating device 10. In operation, the process fluid from the evaporator 20 is passed through the cooler 70 for further cooling, then passed through the condenser 50 as a heat-accepting medium, and then routed thereafter to the input 12 of the heat-generating device 10.

This interconnection solves the problem of emergency running, because the radiator 70 is operated independently of the ORC cycle. Depending on the desired target temperature takes the ORC cycle heat, the necessary cooling capacity is reduced and the downstream fan is relieved, resulting in a reduction of its maintenance intervals. This variant is characterized by its compactness (few Components) and synergy effects of the common components. It can be used well to integrate existing cooling systems. In addition to the evaporation, the condensation takes place in the ORC circuit against the fluid to be cooled (in the other variants, the condensation takes place against the ambient air).

Variant 7 - Extension by an ORC module for existing coolers / with direct condensation

Fig. 11 shows a tenth embodiment 1000 of the device according to the invention.

This embodiment is similar to the ninth embodiment 900 of FIG Fig. 10 with the difference being found in the condenser 50 of the ORC circuit. In the variant 7 shown here there is a direct condensation between ambient air and ORC working medium. Due to structural adaptations of the heat exchanger surfaces, the expansion of standard models in the industry is associated with little effort. Depending on the cooler model, the measure differs.

All variants can be combined with each other.

Advantages / disadvantages of the system according to the invention:

As advantages can be mentioned: Increased operational safety (2 independent cooling systems, ORC + cooler); Use of as many synergy components as possible from Kühler and ORC; low maintenance; very good economy (saving of electrical energy); Reduction of CO ₂ emission; Increase in efficiency (efficiency of the cooling process is increased, synergy between components). Furthermore, an existing radiator can be used to cool the ORC capacitor and, with little design effort, a process that requires energy becomes an energy neutral or energy producing process.

The disadvantage is that adding additional components increases the complexity of the overall system (for example: coordination of the regulations, additional costs, additional interfaces, ...).

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

Claims (15)

A system for cooling a process fluid of a heat generating device, comprising: an output of the heat generating means, the output for discharging process fluid to be cooled from the heat generating means being provided; an input of the heat generating means, the input for supplying cooled process fluid to the heat generating means is provided; and a thermodynamic cycle device, in particular an ORC device, wherein the thermodynamic cycle device comprises: an evaporator having an inlet for supplying the process fluid to be cooled from the outlet of the heat-generating device and having an outlet for discharging the cooled process fluid to the input of the heat-generating device, wherein the evaporator is formed by heat from the process fluid for evaporating a working fluid of the thermodynamic cycle device; an expansion machine for expanding the vaporized working medium and for generating mechanical and / or electrical energy; a condenser for liquefying the expanded working medium, in particular an air-cooled condenser; and a pump for pumping the liquefied working fluid to the evaporator. The system of claim 1, further comprising: a cooler, in particular an air cooler, for cooling at least a portion of the process fluid to be cooled. The system of claim 1 or 2, further comprising: a branch provided with respect to a flow direction of the process fluid downstream of the output of the heat generating device and upstream of the input of the heat generating device for dividing the process fluid to be cooled into a first and a second substream of the process fluid, the junction optionally including a valve; and a merger provided with respect to a flow direction of the process fluid downstream of the branch and upstream of the entrance of the heat generating means for merging the first and second sub-streams of the process fluid. The system of claim 3, wherein the branch is configured to supply the first substream to the evaporator and supply the second substream to the chiller, and wherein the merging is to merge the cooled by the cooler second substream of the process fluid and cooled by the evaporator first part flow of the process fluid is trained. The system of claim 3, wherein the merging is configured to merge the first partial flow of the process fluid cooled by the evaporator and the second partial flow of the process fluid; and where the Merging is designed for supplying the merged partial streams of the process fluid to the radiator. The system of claim 2, wherein the radiator is disposed downstream of the outlet of the evaporator with respect to a flow direction of the process fluid and upstream of the entrance of the heat generating means for further cooling the process fluid cooled by the evaporator. System according to one of claims 2 to 6, wherein the cooler forms a structural unit with the capacitor or is provided separately from the capacitor. System according to one of claims 2 to 7, further comprising a control device for controlling the heat input into the radiator, whereby in particular a target temperature of the process fluid returned to the input of the heat generating device can be achieved. System according to one of claims 2 to 8, wherein for the thermal connection of the condenser and the radiator, an intermediate circuit is provided with a heat transfer fluid, wherein the condenser is provided for transferring heat from the expanded working fluid to the heat transfer fluid and wherein the radiator for cooling the heat transfer fluid is provided. The system of claim 9, wherein from a flowing from the condenser to the radiator branch of the heat transfer fluid useful heat is dissipated to a Nutzwärmeeinrichtung. The system of claim 9 or 10, wherein a composition of the heat transfer fluid is identical to a composition of the process fluid. The system of any one of claims 1 to 11, further comprising: another heat exchanger, which is provided with respect to a flow direction of the process fluid downstream of the evaporator for transferring heat from the cooled by the evaporator process fluid to a heat transfer fluid. The system of claim 12, further comprising: a valve for controlling the mass flow of the heat transfer fluid through the further heat exchanger; wherein preferably a temperature measuring device is provided for measuring the temperature of the process fluid downstream of the further heat exchanger, wherein the regulation of the valve takes place as a function of the measured temperature. The system of any one of claims 1 to 11, further comprising: a further evaporator between the outlet of the evaporator and the input of the heat generating means for further evaporation of working medium by means of heat from the process fluid; a throttle valve for adjusting the size of a partial flow of the working fluid through the further evaporator; and a liquid jet pump or a steam jet pump between the further evaporator and the condenser for lowering the pressure in the further evaporator, wherein in particular a part of the liquefied working medium or a part of the evaporated working medium serves as a propulsion jet. The system of claim 2, wherein the outlet of the evaporator is connected to an input of the radiator, an output of the radiator to an input of the capacitor, and an output of the capacitor to the input of the heat generating means, so that in operation, the process fluid from the evaporator for further cooling the cooler is then passed therethrough as heat-absorbing medium through the condenser and in turn is subsequently passed to the entrance of the heat-generating device.

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