EP2898192A2

EP2898192A2 - Energy conversion arrangement, thermodynamical system and method for increasing the efficiency of an integrated orc process

Info

Publication number: EP2898192A2
Application number: EP13770418.5A
Authority: EP
Inventors: Suhel Ahmad; Thomas-Dirk Pohlers
Original assignee: Siemens AG
Current assignee: Siemens AG
Priority date: 2012-11-06
Filing date: 2013-09-17
Publication date: 2015-07-29
Also published as: WO2014072104A2; DE102012220188A1; WO2014072104A3; DE102012220188B4

Abstract

The invention relates to an energy conversion arrangement (100) for converting thermal energy into mechanical work. A working medium in the vaporous state can be supplied to a capacitor (110), wherein the capacitor (110) is configured to transfer the working medium from the vaporous state into a liquid state by means of cooling down said working medium. An evaporator (120) is coupled to the capacitor (110) such that the working medium in the liquid state can be supplied from the capacitor (110) to the evaporator (120). The evaporator (120) can be coupled to a compressor arrangement (160) in such a way that thermal energy can be discharged from a process fluid to be compressed of the compressor arrangement to the working medium in the evaporator (120), wherein the evaporator (120) is configured to transfer the working medium from the liquid state into the vaporous state by means of the thermal energy of the process fluid. A turbine (130) for converting thermal energy into mechanical work is coupled to the evaporator (120) in such a way that the working medium can be supplied from the evaporator (120) to the turbine (130). Furthermore, the turbine (130) is coupled to the capacitor (110), and so the working working medium can be supplied from the turbine (130) to the capacitor (110).

Description

description

Integrated ORC process on intercooled compressors to increase the efficiency and reduce the required drive power by using the waste heat

Technical area

The present invention relates to an energy conversion arrangement for converting thermal energy into mechanical work, a thermodynamic system, and a method for converting thermal energy into mechanical work.

Background of the invention

In many technical areas, there is a high demand for compressed process gases, such as compressed air or other compressed chemical process gases. For example, in power stations for the production of energy compressed process gases are necessary. Also in the chemical industry ^¬ the compressed for many chemical processes process gases put an ^¬.

In order to increase the pressure of a process gas, com- pressors are used, which are driven for example by means of a motor be ^¬. In order to minimize the required drive power of the compressors in a compression process ^¬ as in order to keep the self-adjusting compression temperatures for the individual system components, such as the seals, limited, multi-stage compressors are used with intermediate cooling.

Fig. 2 Fig. 2 shows a conventional compaction process. Here, a conventional first compression stage or a conventional first compressor 210 and a conventional second compression stage or a conventional second compressor 220 is connected in series. A conventional drive ^¬ unit 250 drives, via a conventional drive shaft 240 the first conventional first compression stage 210 and the conventional second compression stage 220 at. The uncompressed process gas of the first conventional compression stage 210 is fed via a Pro ^¬ zesseingang two hundred and first After the manufacturing kömmlich first compression stage 210, the teilkompri ^¬-optimized process gas to a conventional cooler 230 is supplied. In this case, the heat which is generated in the first conventional compression stage 210 in a conventional cooler 230 is largely released unused to the environment. Subsequently, the partially compressed process gas is supplied to the conventional second compressor 220 and discharged via a process output 202 further processing steps.

For example, the process gas can be supplied to the conventional first compressor 210 at a temperature of about -62 ° C and a pressure of about 3.3 bar. After the first conventional compressor 210, the process gas already at about 65 ° C and about 20.6 bar. In the conventional radiator 230, the partially compressed process gas is approximately isobarically cooled to about 40.9 ° C and supplied to the conventional second compressor 220. After the conventional second compressor 220, the process gas, for example, about 157 ° C and about 80 bar have on ^¬ . In the example shown, it is clear that in each of the conventional compressors 210, 220, the process gas is partially heated about 110 ° C to 120 ° C. The ^{herkömmli ¬} che cooler 230 cools the process gas, for example, from about 20 ° C to about 30 ° C, this waste heat is discharged to the conventional compression processes unused to the environment. With the above-mentioned compaction process and exemplary temperatures and pressures, in the example shown in FIG. 2, almost 14.8 megawatts are released unused via the conventional radiator 230 to the environment.

The conventional cooler 230 or intermediate cooling is, however, necessary in order to limit the compression temperatures and to reduce the required technical work in the compression process. In addition, the reduced Efficiency of compression at too high temperatures of the process gas.

Presentation of the invention

It is an object of the present invention to provide an efficient compaction process.

This object is achieved by an energy conversion arrangement for converting thermal energy into mechanical work, by a thermodynamic system and by a method for converting thermal energy into mechanical work according to the independent claims.

According to a first aspect of the present invention, an energy conversion arrangement for converting thermal energy to mechanical work is described. The Energieumwand ^¬ lung assembly includes a condenser, an evaporator and a turbine.

The condenser can be supplied with a working medium in the vapor state, wherein the condenser is set up to transfer or liquefy the working medium into a liquid state by means of cooling the working medium. The evaporator is coupled to the condenser such that the working fluid from the condenser in the liquid state can be supplied to the evaporator.

The evaporator can be coupled to a compressor assembly that thermal energy can be emitted to the working medium in the evaporator of a process fluid of the Ver ^¬ tight arrangement. The evaporator is further configured to convert the working fluid by means of the thermal energy of the process fluid into a vaporous state or to evaporate.

The turbine is designed to convert thermal energy and mechanical work. The turbine is equipped with steamer coupled such that the working fluid from the evaporator in the vapor state of the turbine can be fed. The turbine is further coupled to the condenser in such a way that the working medium from the turbine can preferably be fed to the condenser in the vapor state.

According to a further aspect, a thermodynamic system is described, which has the above-described Energieumwand ^¬ lungsanordnung. Further, the thermodynamic system comprises the compressor assembly, wherein the evaporator is coupled to the compressor assembly such that thermal energy from the process fluid of the compressor assembly to the working fluid in the evaporator is transferable.

In accordance with another aspect of the present invention, a method of converting thermal energy to mechanical work is described. A working medium is supplied to a condenser in the vapor state. The ^working medium is liquefied by cooling of the working medium in the condensate ^¬ sator. The working medium is supplied in the liquid state from the condenser to an evaporator. In the evaporator, thermal energy is released from a process fluid ei ^¬ ner compressor assembly to the working fluid. The evaporator is for this purpose coupled to the compressor assembly. The working medium is evaporated by means of the thermal energy of the process fluid. The working medium is supplied in dampfför ^¬-shaped condition from the evaporator to a turbine. By means of the turbine thermal energy of Arbeitsmedi ^¬ ums is converted into mechanical work. The working medium is supplied in the vapor state from the turbine to the condenser.

The energy conversion arrangement described above for converting thermal energy into mechanical work implements ei ^¬ nen thermodynamic cycle. In particular, a Clausius-Rankine cycle is implemented. As will be explained further below, the working medium may consist of an organic medium, so that the energy conversion arrangement in particular according to an Organic Rankme Cycle (ORC) process.

The Clausius-Rankine cycle and, correspondingly, the ORC cycle have the turbine, condenser and evaporator described above. To drive the cycle and to increase the pressure of the working fluid in flüssi ^¬ gen state, a feed pump is used to ensure a flow of the working fluid between the functional units and to print the working fluid between the condenser and the evaporator. Pipelines connect the condenser with the evaporator, the evaporator with the turbine and the turbine with the condenser. Between the condenser and the evaporator, the feed pump is interposed ^¬ tet.

According to the Rankine Cycle mecha ^¬ African energy is first produced by condensing the working medium in the cycle alternately at low pressure and evaporated at high pressure. The pressure is applied by the feed pump through labor and dissipated in the turbine with delivery of labor.

In the turbine, the working fluid in the vapor state is adiabatically, so that this mechanical work is evidence in particular of the thermal energy of the working medium it ^¬. The working medium is then ^¬ nearly isobaric condensed in the vapor state, so that the working medium then in the liquid state in the condenser. The pressure of the Ar ^¬ beitsmediums is then virtually adiabatically and nearly isotropic increase in the feed pump. After the feed pump, the working medium is supplied in the liquid state to the evaporator, wherein the working medium can be heated to the first evaporation point and then at ^¬ example (almost isothermally) can be evaporated.

In another exemplary embodiment, the vaporous working medium in the evaporator by further Heating overheated. The working fluid is expanded in an overheated condition in the turbine so that the risk of premature condensation of the working fluid in the turbine is reduced.

The condenser is provided as explained above to liquefy the vaporous working fluid after the turbine. The condenser can be designed, for example, as a water-cooled condenser or as an air-cooled condenser, which has a fan, for example. As the water-cooled condenser can be used, in particular a water-cooled surface condenser, for example in the form of a tube bundle heat exchanger or a Plattenwärmetau ^¬.

The turbine is a turbomachine, which converts the internal energy of the vaporous working medium into rotational energy and ultimately into mechanical working energy. The turbine has in particular rotor blades, which are mounted on an output shaft. Due to the flow around the working fluid on the rotor blades, a portion of the internal energy of the working medium, which is composed, for example, of movement, position and pressure energy, ent ^¬ pulled, and transmitted to the rotor blades. This causes the output shaft of the turbines to rotate, generating usable power or mechanical work. For example, a generator or another working machine can be coupled to the output shaft. The evaporator converts the liquid working medium into a vaporous state. For this purpose, the evaporator thermal energy, in particular from the compressor assembly, are supplied. The evaporator is, for example, a heat exchanger in which in a first region of the heat exchanger, the working medium can be fed and discharged and in a second region, the process fluid of the compressor assembly can be fed and discharged. The evaporator is arranged such that between the first region and the second rich thermal energy, for example by convection, between the process fluid and the working medium is interchangeable. The compressor arrangement has, for example, at least one compressor, which can be driven by means of a motor or a drive unit. The compressor compresses the process fluid. After the first compressor, the printed or compressed process fluid is supplied to the evaporator, thus providing a transition of the thermal energy from the process fluid to the working fluid. The process fluid may be present as a process fluid, process steam or pro ^¬ zessgass. In the following, a compressor is understood to be a closed compressor module or a compressor stage, which is arranged in the compressor assembly. For example, a first compressor stage can be understood as the first compressor and a second compressor stage of the compressor module can be understood as the second compressor. The compressor arrangement and the energy conversion arrangement each have a closed system per se, ie the compressor arrangement has a process fluid circuit and the energy conversion arrangement has a working fluid circuit which is separate from the process fluid circuit.

With the coupling of the evaporator to the compressor assembly, the present invention describes an efficient system for converting thermal energy to mechanical work. The thermal energy of the process fluid contributes to the operation of the cycle of the system for converting thermal energy into mechanical work.

In conventional approaches, the thermal energy of the process fluid is simply released to the environment and thus lost ^¬ . The mechanical work generated by the Turbi ^¬ ne of the system, for example, can be used as ^¬ to turn to the compressor of the Verdichteranord- operate. Thus, a highly-efficient compressor assembly ef ^¬ due to the coupling, for example, provided with the energy conversion assembly on the evaporator.

According to a further exemplary embodiment, the evaporator has a further heat exchanger, in particular a thermal oil heat exchanger, which has an intermediate medium. The evaporator can be coupled to the compressor arrangement such that thermal energy of the compressor can be delivered to the intermediate medium in the heat exchanger. The heat exchanger is further configured such that thermal energy of the intermediate medium can be delivered to the working medium. In particular, when the process fluid is a process gas, and thus is present in the gaseous state, the liner Ver ^¬ achieved with the heat exchanger and the intermediate medium, a more efficient transfer of thermal energy between the process gas (process fluid) to the working fluid. This is in particular achieved in that the intermediate medium in particular ^¬ sondere in the liquid state and the intermediate medium has a good heat transfer coefficient. In particular, the intermediate medium can be a thermal oil which comprises, for example, mineral oils, silicone oils or biological oils.

According to a further exemplary embodiment, the working medium comprises an organic medium, such as, for example, a silicone oil, toluene, isopentane and / or isooctane. If the working medium consists of an organic medium, the so-called Organic Rankine Cycle (ORC) process can be carried out by means of the energy conversion arrangement. The organi ^¬ cal working medium has a lower evaporation temperature ^¬ ture than water. Thereby, the ORC process is Zvi ^¬ rule the evaporator and the condenser particularly advantageous in a low temperature gradient of the working medium, since already at a low temperature differential between the evaporator and the condenser, an efficient operation of the ORC process is possible. Thus, with the present exemplary embodiment of the invention, the waste heat generated in the compressor assembly can be efficiently utilized in the integrated ORC process. The compressor assembly generates thermal energy, which according to the present invention, the energy conversion assembly (which, for example, a closed

Circular system represents) supplied. The power conversion assembly is operated with the organic working fluid, which has the property, as compared to water be ^¬ already at a moderate pressure and moderate ambient temperature to condense. In the evaporator, the thermal energy is supplied to the compressor assembly, so that the organic working medium is evaporated.

According to a further exemplary embodiment, the system comprises a generator coupled to the turbine in such a way that the generator means of the turbine is at ^¬ drivable. Thus, power is generated from the waste heat of the compressor arrangement by means of the generator of the energy conversion arrangement.

As explained above, the compressor arrangement can have a first compressor (or a first compressor stage), wherein the evaporator is coupled to the first compressor in such a way that the process fluid can be fed to the evaporator after being compressed by means of the first compressor, thus providing a transition from provide thermal energy to the working medium of the energy conversion assembly.

According to a further exemplary embodiment, the compressor assembly further comprises a second compressor (or a second compressor stage). The second compressor is coupled to the evaporator such that the process fluid can be fed to the second compressor after cooling in the evaporator. The second compressor can thus be operated more effectively due to the cooling ^¬ len of the process fluid. Ei ^¬ nem compressor such as a too hot process fluid supplied (especially in the gaseous state), the efficiency of the corresponding compressor is greatly reduced. The cooler the process fluid, the more effectively a compressor can compress the process fluid.

The compressor assembly may thus have two compressors connected in series or two compressor stages connected in series. In the case of compressor stages connected in series, the entire compression process is carried out within one machine or compressor assembly. The process gas is thus brought into the first compressor stage at a certain partial pressure, then led out of the machine or compressor assembly and cooled by a cooler geeigne ^¬ th (for example, air cooler and the evaporator). After the cooling process, the process gas, in turn, the Maschi ^¬ ne or compressor assembly is fed to be then brought into the second compressor stage to the required final pressure. The compressor arrangement may have a multiplicity of compressors or compressor stages.

According to a further exemplary embodiment, the evaporator is coupled to the second compressor in such a way that the process fluid can be fed to the evaporator after being compressed by means of the second compressor. In other words, the process fluid may be supplied to the evaporator before it enters the second compressor and exits the second compressor. Thus, more effectively, the thermal energy of the process fluid is utilized during compression in the compressor assembly.

According to another exemplary embodiment, the compressor assembly comprises a drive unit (eg, a motor) and a drive shaft. The drive shaft is connected to the drive unit at ^¬ and the first compressor (and / or the second compressor) coupled such that the first compressor and / or the second compressor) driven by means of the drive unit. The drive unit may, for example, a Gas turbine, have an internal combustion engine or an electric motor.

According to a further exemplary embodiment, the turbine is coupled to the drive shaft of the compressor assembly such that the first compressor and / or the second compressor is / are drivable exclusively or in addition to the drive unit described above. By means of the turbine, for example, the mechanical work produced in moderate energy ^¬ conversion arrangement is induced in the Ver ^¬ tight arrangement. Thus, the efficiency of the compressor assembly is increased because, for example, the performance of the drive unit can be reduced.

In summary, with the present invention, the thermal energy of the compressor assembly is used, which is discharged in ei ^¬ nem conventional compressor process to the environment. Thus, the required drive power of the drive unit for driving the compressor assembly can be reduced. Thus, in turn, the overall effect ^¬ This improves degree. In turn leads to a greener densification process. The corresponding functional units, such as, for example, the feed pump, the condenser, the evaporator, the turbine, the generator, the first compressor, the second compressor and / or the drive unit, can be flexibly coupled to each other, so that the described thermal Modynamic system can be offered as a plug-and-play solution.

In particular, the forming of the working medium as organic ^¬ ULTRASONIC working medium, and thus the implementation of the ORC cycle process is advantageous since a lower pressure level, for example, only 10 bar for operating the ORC process is sufficient. It should be noted that the embodiments described herein represent only a limited selection of possible embodiments of the invention. Thus, it is possible to combine the features of individual embodiments with one another in a suitable manner, so that a multiplicity of different embodiments are to be regarded as obviously disclosed to the person skilled in the art with the embodiment variants that are explicit here.

Brief description of the drawings

In the following, for further explanation and for a better understanding of the present invention, embodiments will be described in detail with reference to the accompanying figures.

1 shows a schematic representation of the thermodynamic system according to an exemplary embodiment of the present invention; and

Fig. 2 shows a conventional compressor arrangement.

Detailed Description of Exemplary Embodiments

The same or similar components are provided in the figures with the same reference numerals. The illustrations in the figures are schematic and not to scale.

Fig. 1 shows a thermodynamic system, which has a 100 Ener ^¬ gieumwandlungsanordnung for converting thermal energy into mechanical work, a compressor assembly. The functional elements (capacitor 110, dining pump 105, evaporator 120, turbine 130) of the Energieumwand ^¬ lung arrangement 100 are shown in the dashed area in FIG. 1. The energy conversion arrangement 100 has a capacitor 110, a feed pump 105, an evaporator 120 and a turbine ^¬ 130. In the condenser 110, a vaporous working medium from the turbine 130 is fed. The capacitor 110 is a ^¬ directed to liquefy the working medium by cooling the Arbeitsme ^¬ diums. The waste heat Q can be released to the environment. In another exemplary embodiment, the capacitor by means of a heat exchanger on the evaporator 120 is ge ^¬ coupled, so that the waste heat Q which is released during cooling of the working medium in the condenser 110, the working medium in the evaporator 120 is supplied.

The charge pump 105 receives from the capacitor 110, the Ar ^¬ beitsmedium in liquid state. The feed pump 105 increases the pressure of the liquid working medium and forwards the working medium to the evaporator 120.

The evaporator 120 receives the working fluid in the liquid state 120 from the feed pump 105 or the condenser 110. Furthermore, the evaporator is coupled to a compressor arrangement 160 such that thermal energy can be released from a process fluid of the compressor arrangement 160 to the working medium in the evaporator 160 is. The evaporator 120 is filed in such a way that the working medium is vaporized by means of the thermi ^¬ rule energy of the process fluid.

The turbine 130 receives the working medium in the vapor state from the evaporator 120. The working medium in the vapor state relaxes in the turbine 130, so that the turbine ^¬ 130 generates mechanical work.

The turbine 130 is coupled to the condenser 110 such that the working medium in the vapor state can be fed from the turbine 130 to the condenser 110. The energy conversion arrangement 100 is therefore suitable for carrying out a cycle process, in particular a Clausius-Rankine process, in order to generate mechanical work from thermal energy. In a preferred embodiment, the working fluid is an organic working Medi ^¬ a way, that the power conversion device 100 is particularly suitable for an Organic Rankine Cycle (ORC) process to carry out.

The compressor assembly 160 includes a first compressor 161 which is driven by a drive unit 166. Via a process gas inlet 164, the process fluid, in particular a process gas, is supplied to the first compressor 161. The first compressor 161 compresses the process fluid and forwards it to the evaporator 120. In the evaporator 120, thermal energy is taken from the process fluid and supplied to the working fluid of the energy conversion assembly 100. After the evaporator 120, the process fluid is cooled and can be supplied according to its intended use. Further, as shown in FIG. 1, the process fluid may be supplied to another second compressor 162. In the second compressor 162, the process fluid is further compressed and removed at a process gas outlet 165 for further use. The first compressor 161 and the second compressor 162 may represent functionally separate compressor assemblies or may represent two compressor stages of a machine or a compressor assembly, respectively. The second compressor 162 is coupled to the drive unit 166 by means of a drive shaft 163. Also may be coupled to the on ^¬ drive shaft 163 of the first compressor 161st

The turbine 130 may be coupled to a generator 140 via a first drive shaft 150 to drive the generator 140 to generate power. Alternatively or additionally, the turbine 100 may be coupled to the first compressor 161 and / or the second compressor 162 via a second drive shaft 151. In this embodiment, the turbine 130 supports the compression process of the compressor assembly 160, since the mechanical Ar ^¬ beit, which was generated by the turbine 130, for loading ^¬ drive the corresponding compressor 161, can be used 162nd Thus, the efficiency of the compressor assembly 160 is increased.

In the following, an exemplary mode of operation of the thermodynamic system of Figure 1, which in particular has the energy conversion assembly with the organic working fluid, with examples of parameter values for pressure and temperature of the working medium and the process fluid erläu ^¬ tert.:

The process fluid, which may be in gaseous form and is referred to below as "process gas", has a temperature of about -60 ° C. to about -65 ° C. and a pressure of about 3 bar to 4 bar at the process gas inlet 164 on. In the first compressor 161, the pressure is increased to about 15 bar to about 25 bar and the temperature to about 60 ° C to about 70 ° C. On closing ^¬ the process gas is supplied to the evaporator 120. In the evaporator 120, the process gas is cooled almost isobarically to about 35 ° C to about 45 ° C. Thereafter, the Pro ^¬ zessgas is supplied to the evaporator 120 to the second compressor 162nd The second compressor 162 compresses the process gas ^¬ further so that the process gas has to output 165, the process gas has a pressure of about 70 bar to about 90 bar and a temperature of Tempe ^¬ about 150 ° C to 170 ° C.

At the entrance of the evaporator 120, the working medium, in particular the organic working medium, is in liquid form and has a temperature of about 20 ° C to about 30 ° C and a pressure of about 15 bar to about 25 bar. In the evaporator 120, the working fluid absorbs the thermal energy of the process fluid and is vaporized. After the evaporator 120, the working medium is in a vaporous state and has a temperature of about 60 ° C to 70 ° C at a pressure of about 15 bar to 25 bar. During the evaporation of the working medium in the evaporator 120, the pressure thus remains almost the same (isobaric heating). In the turbine 130, the working fluid expands from initially about 15 bar to about 25 bar to about 5 bar to about 10 bar. At the same time, the working medium cools from approx. 60 ° C to 70 ° C to approx. 30 ° C to 40 ° C. After the turbine 130, the working medium is supplied to the condenser 110 in the vapor state. In the condenser, the working medium is liquefied or condensed, for example by means of air or water ^¬ cooling. The working medium cools in the condenser 110 from, for example, about 30 ° C to 40 ° C to about 15 ° C to 25 ° C from. The pressure of the working medium remains almost constant during the condensation in the condenser 110 (isobaric cooling). After the condenser 110, the liquid working medium of the feed pump 105 is supplied ^¬ . In the feed pump 105, the pressure of Ar ^¬ beitsmediums of about 5 increases bar to about 10 bar to about 15 bar to about 25 bar, the temperature only slightly rises.

After the feed pump 105, the working medium, as mentions ^¬ ing, about 20 ° C to 25 ° C and a pressure of about 20 bar. With these parameter values, the liquid working medium is provided to the evaporator 120.

In summary, about 1 megawatt to about 2 megawatts can be obtained with the ORC process described above and fed to the compressor assembly 160 and the generator 140. Thus, for example, about 7% to about 10% of the previously unused waste heat can be used.

In addition, it should be pointed out that "comprehensive" does not exclude any ^other elements or steps and "one" or "one" does not exclude a large number. Further thereon was hingewie ^¬ sen that features or steps which have been described with reference to one of the above embodiments, also in combination with other characteristics or steps of other exemplary embodiments described above are used Kings ^¬ nen. Reference signs in the claims are not to be considered as limiting.

Claims

claims

An energy conversion assembly (100) for converting thermal energy to mechanical work, comprising the energy conversion assembly (100)

a condenser (110), to which a working medium in the vaporous state can be supplied,

wherein the capacitor (110) is adapted to the working Medi ^¬ order to transfer by means of cooling from the vapor state to a liquid state,

an evaporator (120) connected to the capacitor (110) is coupled, so that the working medium in the flüssi ^¬ gen state from the condenser (110) to the evaporator (120) can be fed,

wherein the evaporator (120) is coupled to a compressor assembly (160) such that thermal energy from a process fluid of the compressor assembly (160) to be compressed is deliverable to the working fluid in the evaporator (120), wherein the evaporator (120) is configured Transfer working fluid by means of the thermal energy of the process fluid from the liquid state to the vapor state, and

a turbine (130) for converting thermal energy into mechanical work,

wherein the turbine (130) to the evaporator (120) so ge ^¬ is coupled, that the working medium from the evaporator (120) of the turbine (130) can be fed,

wherein the turbine (130) is further ge ^¬ coupled with the capacitor (110), so that the working fluid from the turbine (130) to the capacitor (110) can be fed.

2. energy conversion arrangement (100) according to claim 1, wherein the evaporator (120) has a heat exchanger, in particular a thermal oil heat exchanger, with an intermediate medium,

wherein the evaporator (120) can be coupled to the compressor arrangement (160) in such a way that thermal energy of the process flow is ids can be delivered to the intermediate medium in the heat exchanger, and

wherein the heat exchanger is further configured such that thermal energy of the intermediate medium can be delivered to the working medium.

3. energy conversion arrangement (100) according to claim 1 or 2,

wherein the working medium comprises an organic medium, in particular silicone oil, toluene, isopentane and / or iso-octane.

The energy conversion assembly (100) of any one of claims 1 to 3, further comprising

a generator (140) coupled to the turbine (130) such that the generator (140) is drivable by the turbine (130).

5. Thermodynamic system comprising

the energy conversion arrangement (100) according to one of claims 1 to 4, and

the compressor assembly (160),

wherein the evaporator (120) to the compressor assembly (160) is coupled such that thermal energy from the Pro ^¬ zessfluid the compressor assembly (160) to the working medium in the evaporator (120) can be emitted.

6. Thermodynamic system according to claim 5,

wherein the compressor assembly (160) comprises a first compressor

(161),

wherein the evaporator (120) to the first compressor (161) is coupled such that the process fluid according to any one Comp ^¬ rimieren means of the first compressor (161) is fed to the evaporator (120).

7. Thermodynamic system according to claim 6,

wherein the compressor assembly (160) comprises a second compressor

(162), wherein said second compressor (162) to the evaporator (120) is coupled such that the process fluid after a cool down ^¬ len in the evaporator (120) the second compressor (162) can be fed.

8. Thermodynamic system according to claim 7,

wherein the evaporator (120) to the second compressor (162) is coupled such that the process fluid according to any one Comp ^¬ rimieren means of the second compressor (162) is fed to the evaporator (120) or a further evaporator.

9. Thermodynamic system according to one of claims 6 to 8,

the compressor arrangement (160) having a drive unit (166) and a drive shaft (163),

wherein the drive shaft (163) with the drive unit (166) and the first compressor (161) is coupled such that the first compressor (161) by means of the drive unit (166) is drivable.

10. Thermodynamic system according to one of claims 6 to 9,

wherein the turbine (130) is coupled to the drive shaft (163) such that the first compressor (161) is drivable by the turbine (130).

11. A method of converting thermal energy to mechanical work, comprising the method

Supplying a working medium in the vapor state to a condenser (110),

Liquefying the working medium by means of cooling the working medium in the condenser (110),

Supplying the working fluid in the liquid state from the condenser (110) to an evaporator (120),

Dissipating thermal energy from a process fluid of a compressor assembly (160) to the working fluid in the evaporator (120), wherein the evaporator (120) is coupled to the compressor assembly (160),

Vaporizing the working medium into a vapor state by means of the thermal energy of the process fluid, supplying the working medium in the vapor state from the vaporizer (120) to a turbine (130),

Converting thermal energy of the working medium into mechanical work by means of the turbine (130), and

Supplying the working fluid from the turbine (130) to the condenser (110).