Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
  • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours

Definitions

• the present invention relates to systems for producing electrical or mechanical energy.
• thermodynamic cycle of Rankine It finds for advantageous application the systems of production of energy of small power, calling on a thermodynamic cycle of Rankine. It will apply, for example, to the production of energy from thermal discharges produced by factories, by vehicle engines or from heat from systems recovering solar energy or from biomass.
• Rankine cycles are all based on transformations successively comprising: the pumping of a working fluid in liquid form, the creation of steam and its possible overheating, the relaxation of the steam to generate a movement and condensation of steam.
• the working fluid may be selected from water, carbon dioxide or an organic fluid. In the latter case, we speak of organic Rankine cycle.
• the majority of thermal power generation systems are based on the use of such cycles.
• a machine based on a Rankine cycle is, in known manner, consisting of four main organs, namely:
• thermodynamic cycle it is on this type of thermodynamic cycle that the majority of nuclear power plants, coal-fired power plants, or heavy-fuel thermal power plants are based in order to produce high power.
• the hot springs have a very high power and temperature.
• thermal discharges that is to say thermal discharges whose temperature is most often less than 200 ° C or less than 150 ° C.
• Systems based on a Rankine cycle would theoretically produce electrical or mechanical energy from these heat discharges.
• the powers that could be produced would then be relatively low, typically of the order of a few kilowatts to a hundred kilowatts for thermal discharges below one megawatt, because of the low thermodynamic efficiency.
• FIG. 1 illustrates the system according to this prior art. This is a subcritical cycle.
• This circuit comprises a pump 150, a heat exchanger 1 10, an expander 120 and a cold exchanger 130 arranged to perform a Rankine cycle as indicated above.
• the circuit comprises an injector 100 and an additional pump 152.
• the output of the injector 100 is connected to the inlet of the cold exchanger 130 (condenser).
• the two inputs of the injector 100 are connected on the one hand to the output of the expander 120 and on the other hand to the output of the additional pump 152 whose input is connected to the output of the cold exchanger 130 .
• this second pump 152 at the injector inlet 100 complicates the installation and reduces the overall efficiency.
• the present invention relates to a system for producing electrical or mechanical energy comprising a fluid circuit in which an organic working fluid circulates and comprising a plurality of members traversed by the working fluid and among which: at least one first heat exchanger configured to be thermally coupled to at least a first heat source, an expander having an inlet fluidly connected to an outlet of the first heat exchanger, a second heat exchanger configured to be thermally coupled to a second heat source colder than the first heat source and a pump, the circuit being configured so that the working fluid set in motion by the pump passes successively through at least the pump, the first heat exchanger, the expander and the second exchanger, and then again the pump.
• the system comprises an injector comprising: a first input fluidically connected to an output of the second heat exchanger; heat, a second input fluidically connected to the output of the first exchanger and an output fluidically connected to an input of said pump.
• the system is configured so that the second inlet of the injector is fluidly connected downstream of the first exchanger and strictly upstream of the expander.
• the upstream and the downstream at a given point are taken with reference to the direction of circulation of the fluid in the circuit.
• the second inlet of the injector is fluidly connected between the outlet of the first exchanger and the inlet of the expander.
• circuit proposed by the invention increases the cavitation margin at the pump, making the system more reliable and reducing the wear of the pump.
• the invention thus provides an effective solution for valuing thermal discharges with relatively low temperatures.
• the second inlet of the injector is fluidly connected downstream of the first exchanger and strictly upstream of the expander.
• the second inlet of the injector is not connected downstream of the expander or the expander itself, for example an intermediate stage of the latter.
• the system is configured so that at the outlet of the first exchanger the working fluid is brought into a supercritical state.
• the system is configured such that the pressure and temperature of the working fluid at the outlet of the first exchanger is greater than the critical pressures and temperatures of the working fluid.
• the fluid is thus brought beyond its critical point.
• the system then operates according to a supercritical Rankine cycle.
• the temperature difference between the working fluid and the hot source is then less, thereby resulting in a lower energy dissipation.
• the overall efficiency of the system is then improved while maintaining high reliability and limited complexity.
• the working fluid is an organic fluid.
• organic fluid is meant a fluid composed of molecules or a mixture of molecules consisting of carbon atoms, hydrogen and possibly other atoms such as, for example, oxygen, fluorine, nitrogen, chlorine, bromine.
• the working fluid is not an organic fluid.
• the expression "A fluidically connected to B" does not necessarily mean that there is no organ between A and B.
• the present invention also relates to a method for producing electrical or mechanical energy from the system according to any one of the preceding claims comprising at least the following steps:
• a mixing step in the injector of the working fluid issuing from the outlet of the second heat exchanger and of said second portion of the working fluid coming from the first heat exchanger, so as to deliver a fluid at the outlet of the injector; mixed having a pressure greater than that of the working fluid from the outlet of the second exchanger.
• the method may have any of the optional features and steps set forth below that can be taken separately or in combination:
• the method comprises a step of cooling a cooling fluid thermally coupled to the working fluid by a third heat exchanger, the working fluid circulating in the third heat exchanger being taken at the outlet of the injector and reinjected at the the expander's output.
• the coolant cools an alternator coupled to the expander.
• the invention makes it possible to make the use of heat rejects at low temperature profitable, while requiring little energetic means.
• the present invention provides a simplified system, inexpensive, low energy consumption, while having improved energy efficiency without overloading the pump or increase the cost and complexity of the system.
• FIG. 1 illustrates a system made from a Rankine cycle according to the prior art.
• FIG. 2a illustrates an exemplary system according to the present invention, the system comprising an injector of which one of the two inputs is fluidically connected to the output of a first heat exchanger.
• FIGURE 2b illustrates an embodiment for which the system comprises an additional exchanger.
• FIG. 2c illustrates another embodiment for which the first exchanger comprises two separate exchangers.
• FIGURE 2d illustrates another embodiment for which the separate exchangers have different temperatures and flow rates.
• FIGURE 3 illustrates a system according to the present invention comprising an additional cooling circuit.
• FIG. 4 represents a sectional view illustrating the principle of cooling the stator of an energy conversion system such as an alternator.
• FIGURE 5 is a sectional view of an example of an injector that can be used in the context of the various embodiments of the invention.
• the system comprises a cooling circuit connected in parallel with the injector and the second heat exchanger, the cooling circuit being fluidly connected on the one hand to the outlet of the injector and on the other hand leaves the expander.
• the cooling circuit is fed by a portion of the working fluid which is taken out of the injector. Its pressure is increased.
• the system comprises an energy conversion device configured to convert a mechanical movement produced by the expander into electricity or another mechanical movement.
• the cooling circuit comprises a third heat exchanger thermally coupled with a third heat source exchanging heat with the energy converting device, the system being configured such that the outlet pressure of the third heat exchanger is greater than the pressure at the outlet of the expander.
• the energy conversion device comprises an alternator configured to convert the mechanical movement produced by the expander into electricity and the third heat source comprises a circuit thermally coupled with the alternator.
• the third source of heat absorbs the calories produced by the alternator. Part of the calories absorbed by the third heat source is then absorbed by the working fluid circulating in the third heat exchanger.
• the alternator comprises a stator and the third heat source comprises a fluid circuit in contact with the stator and enclosing a heat transfer fluid.
• the first heat exchanger comprises at least one primary heat exchanger and a secondary heat exchanger.
• the inlet of the primary heat exchanger (corresponding to the inlet of the first heat exchanger) is preferably fluidly connected to the outlet of the pump.
• the output of the primary heat exchanger is preferably fluidly connected to the inlet of the secondary heat exchanger.
• the output of the secondary heat exchanger (corresponding to the output of the first heat exchanger) is fluidly connected to the inlet of the expander.
• the primary heat exchanger and the secondary heat exchanger are configured to be each thermally coupled to the same heat source.
• the primary heat exchanger is configured to be thermally coupled to a primary heat source and the secondary heat exchanger is configured to be thermally coupled to a secondary heat source separate from the primary heat source.
• the first heat exchanger is configured to bring the working fluid to its outlet at a temperature below 200 ° C. and preferably below 150 ° C.
• the circuit is configured so that the temperature of the working fluid at the outlet of the first exchanger is between room temperature and 200 ° C and preferably between room temperature and 150 ° C.
• the system comprises the hot source.
• the hot source and the first exchanger are configured to provide at the outlet of the first exchanger a temperature for the working fluid of less than 200 ° C and preferably less than 150 ° C.
• the second heat exchanger is configured to bring the working fluid to its outlet at a temperature between room temperature and 150 ° C., the temperature of the working fluid leaving the second heat exchanger being lower than the temperature of the heat exchanger. working fluid at the outlet of the first exchanger.
• the system is configured so that the pressure and the temperature of the working fluid at the outlet of the first exchanger are greater than the critical pressure and temperature of the working fluid.
• the working fluid is refrigerant and selected from R410a, R134a, R227ea, or R245fa. These fluids make it possible to reach a supercritical regime with hot springs at temperatures below 200 ° C. They are therefore particularly advantageous for producing energy from thermal discharges from factories or thermal engines.
• the system is configured so that the first inlet of the injector receives the working fluid at least partially in the liquid state and preferably in the liquid state only and in such a way that the second inlet of the injector receives the working fluid at least partially in the gaseous state and preferably in the gaseous state only.
• the system comprises the first heat source, the first heat source being thermally coupled with a heat rejection circuit of a plant or engine.
• the first heat exchanger is configured to heat the working fluid; the expander is configured to increase the pressure of the working fluid and the second heat exchanger is configured to cool the working fluid.
• the injector is configured to increase the pressure of the working fluid.
• the pump is configured to increase the pressure of the working fluid.
• the system comprises an additional heat exchanger configured to transfer heat from the expander outlet working fluid to the working fluid located between the pump outlet and the inlet of the first exchange.
• the additional exchanger acts as economizer. It makes it possible to use a portion of the energy remaining in the working fluid at the outlet of the expander to preheat the liquid at the outlet of the pump. This increases the efficiency of the installation.
• the first heat exchanger comprises at least two heat exchangers each coupled to a heat source having a different temperature, one being configured to bring the working fluid into a sub-critical state (liquid) and the other, disposed downstream, being configured to bring the working fluid into a supercritical state.
• An interest is to allow a better match between the working fluid and the first exchanger and thus to increase the efficiency of the exchanger, reducing the temperature nip between the heat source and the working fluid.
• Pinch means the minimum temperature difference between the working fluid and the hot source.
• a second interest is then to be able to possibly use two or more different hot springs that would have different temperatures and different flow rates.
• the system is configured so that the fluid has a difference ( ⁇ ) between the temperature of the heat source and the critical temperature of the working fluid; said gap ( ⁇ ) being between 20 ° C and 70 ° C. This range makes it possible to have a particularly high yield.
• the system comprises an energy conversion device configured to convert a mechanical movement produced by the expander into electrical or mechanical energy and configured so that the power provided by the conversion device energy is less than 100 kW.
• the expander is a turbine, preferably kinetic.
• the expander is a volumetric machine.
• the expander is a volumetric machine, of the following type: a volumetric compressor operating as an expander.
• the expander is a hermetic machine; said machine comprising the expander, a shaft and the alternator; the expander being connected to the shaft and the shaft being connected to the alternator.
• Figure 2a illustrates an exemplary system according to the present invention. This system is particularly advantageous for a small power production (for example from a few kilowatts to a hundred kilowatts). It is configured to implement a Rankine thermodynamic cycle. It includes commonly used components:
• This working fluid is advantageously refrigerant.
• the working fluid is preferably organic which allows to reach a supercritical regime (also called supercritical) while maintaining relatively low pressure and temperature levels.
• the working fluid is preferably selected from R410a, R134a, R227a, R245fa.
• supercritical fluid is meant a fluid having reached a supercritical regime.
• This first heat exchanger 1 10 is thermally coupled to a hot source 170, for example heated by heat discharges. Preferably it allows the fluid to reach a supercritical regime.
• the first exchanger can thus be described as a supercritical exchanger. It allows the working fluid to exceed the critical temperature.
• the critical temperature of the working fluid is, for example of the order of 70 ° C, for a working fluid of the refrigerant gas type R410a.
• R410a is one of the most common refrigerants used to operate a heat pump.
• R410a has the advantage of not being harmful to the ozone layer, while being energy efficient. In particular, it has a higher compression capacity and cooling capacity than many other refrigerants.
• the critical temperature is, for example, of the order of: 101 ° C for the fluid R134a, 103 ° C for the fluid R227a and 154 ° C for the fluid R245fa.
• volumetric compressor operating as an expander (volumetric) 120.
• This expander 120 makes it possible to relax the fluid and to produce mechanical energy from this expansion. In one embodiment, this energy is recovered on a rotating shaft 190. This mechanical energy can then be recovered in electrical form at an alternator located on said rotating shaft 190.
• the expander 120 is advantageously derived from a conventional volumetric compressor of the refrigeration industry.
• a second heat exchanger 130 thermally coupled to a source colder than the hot source 170 and for cooling the working fluid. During this cooling, the saturation temperature is reached. The cooling is then accompanied by the phenomenon of condensation.
• an injector 140 making it possible to define an intermediate level of pressure.
• the injector comprises: at least two inputs, one for a first fluid and the other for a second fluid, usually gaseous, having a higher energy than the first fluid; at least one mixing chamber of the two fluids disposed downstream of the two inputs; at least one neck and then a divergent portion serving as a diffuser, disposed downstream of the mixing chamber and configured to allow the diffusion of the mixed fluid at the outlet of the mixing chamber.
• the injector 140 thus makes it possible to increase the pressure of the first fluid and to supply a fluid at an intermediate pressure, that is to say at a pressure between those of the first and second fluids.
• the operation of the injector 140 resides on a simple and passive principle: the second fluid (gaseous and coming from the output 1 10b of the first exchanger 1 10) at high energy drives a low-energy fluid (liquid and coming from the output 130b the second heat exchanger 130) and allows to raise the pressure of the latter without requiring a motor member such as a pump.
• the intermediate pressure delivered by the injector 140 is for example of the order of a few bars above the level of the low pressure; said bass pressure around the ten bars.
• the injector 140 also makes it possible to supply pressure having said intermediate level of pressure at the inlet 150a of the pump 150. The pump is thus relieved, which brings numerous advantages as will be detailed hereinafter.
• the fluid at the outlet of the first exchanger 1 10 is in gaseous form and the inlet 140c of the injector 140 receives fluid in gaseous form only.
• a pump 150 Preferably it allows the working fluid to relax the fluid and thus exceed the critical pressure.
• the power of the pump 150 can be reduced through the use of the injector 140. It is thus in ranges of standard design, less restrictive. By reducing the total driving height required for the pump 150 from 400 meters to about 350 meters, the pump 150 is less complex and expensive. In addition, since the inlet pressure is higher, the risk of cavitation is reduced, which is less restrictive for the design of the pump 150.
• the injector 140 is positioned so as to allow simplification of realization while optimizing the energy efficiency.
• the output 140b of the injector 140 is connected to the inlet of the pump 150.
• the second inlet 140c of the injector 140 is connected to the outlet 1 10b of the first exchanger 1 10.
• the connection socket at the outlet 1 10b of the first exchanger 1 10 thus allows to introduce into the injector fluid having a high energy, especially a high pressure.
• this configuration makes it possible to simplify the realization of the circuit.
• the temperature of the hot source 170 is less than 200 ° C. and preferably less than 150 ° C. and the temperature of the cold source 180 is less than 50 ° C. and preferably of the order of 30 ° C.
• the temperature of the cold source 180 is greater than the ambient temperature and more generally of the order of the ambient temperature.
• the maximum temperature is that of the outlet of the expander 120, that is to say a little less than 150 ° C.
• the minimum temperature is that of the output of the pump 150, that is to say a little higher than the ambient temperature.
• the maximum temperature is that of the outlet of the turbine or other expander (120), that is to say intermediate, between the temperatures of the hot (150 ° C) and cold (30 ° C) sources.
• the minimum temperature of the second exchanger 130 is that of the temperature of the cold source 180, that is to say, generally the ambient temperature.
• the present invention makes it possible to reduce the power consumed by the pump 150. Indeed, in some organic Rankine cycles, the power consumed by the pump 150 is large enough to seek to reduce it drastically and thus increase the efficiency.
• the injector 140 is also used to reduce the driving height to be provided by the pump 150.
• Another advantage of the present invention is also to have a lower investment cost for the pump 150 which generally represents a significant part of the overall cost of the installation. This cost is directly related to the power of said pump 150. It is not generally strictly proportional to the power, but remains increasing with it.
• a further advantage of the invention is also to reduce the risk of cavitation in the pump.
• the inlet pressure in the pump 150 is higher in the case of the invention 150.
• the margin for cavitation for a given installation is expressed by the difference between the inlet pressure minus the pressure of saturation vapor and a characteristic value of the pump 150 (NPSH: net positive suction head).
• NPSH net positive suction head
• the inlet pressure will be higher and the saturation vapor pressure will be only marginally affected.
• the integration of the Clapeyron relationship leads to the estimation of an order of magnitude of the increase in saturated vapor pressure due to a temperature difference:
• the system comprises an additional exchanger 230.
• the additional exchanger 230 comprises a first inlet 231 fluidically connected to the outlet 120b of the expander 120 and a first outlet 231b fluidically connected to the the input 130a of the second heat exchanger 130.
• the additional exchanger 230 comprises a second input 232a fluidly connected to the output 150b of the pump 150 and a second output 232b fluidly connected to the input 1 10a of the first heat exchanger 1 10.
• This additional heat exchanger 230 makes it possible to use a portion of the energy remaining in the fluid after passing through the expander 120 to preheat the liquid at the outlet of the pump 150.
• This additional heat exchanger 230 thus serves as an economizer.
• the interest is a gain on the efficiency of the installation. It is an internal exchanger cycle: the working fluid exchange with itself.
• the first exchanger 1 10, preferably of the hot exchanger type may be made of at least two distinct parts, for example using two exchangers 1 10 ', 1 10 ". 1 10 ', 1 10 ", designated primary exchanger 1 10' and secondary exchanger 1 10", are preferably connected in series, the inlet 1 10 'a of the primary exchanger 1 10' (corresponding to the inlet 1 10a of the first exchanger 1 10) is preferably fluidly connected to the outlet 150b of the pump 150.
• the outlet 1 10'b of the primary exchanger 1 10 ' is preferably fluidly connected to the inlet 1 10 "a of the secondary heat exchanger 1 10 "
• the output 1 10" b of the secondary heat exchanger 1 10 "(corresponding to the outlet 1 10b of the first heat exchanger 1 10) is fluidly connected to the inlet 120a of the expander 120.
• the heat exchangers primary 1 10 'and secondary 1 10 "forming the first exchanger 1 10 are coupled thermally each to the same heat source 170.
• one of the exchangers 1 10 ' is used to heat the fluid under subcritical conditions, while the other 1 10' is used to make the complement.
• the first interest is to allow a better match between the working fluid and the first exchanger 1 10 and thus increase the efficiency of the exchanger, reducing the temperature nip between the heat source 170 and the working fluid.
• the second interest is then to possibly be able to use two different exchangers 1 10 ', 1 10 ", as illustrated in FIG. 2d, which would have different temperatures thanks to different heat sources 170, 270 and different flow rates.
• FIG. 2d two different exchangers 1 10 ', 1 10 "
• the inlet 1 10 'a of the primary exchanger 1 10' (corresponding to the inlet 1 10a of the first exchanger 1 10) is preferably fluidly connected to the outlet 150b of the pump 150.
• Outlet 1 10 'b of the primary exchanger 1 10' is preferably fluidly connected to the inlet 1 10 "a of the secondary exchanger 1 10"
• the outlet 1 10 "b of the secondary exchanger 1 10" ( corresponding to the output 1 10b of the first exchanger 1 10) is fluidly connected to the inlet 120a of the expander 120.
• the primary exchanger 1 10 'and secondary 1 10 "forming the first exchanger 1 10 does not are thermally coupled to the same The heat exchanger 170.
• the primary heat exchanger 110 ' is thermally coupled to a primary heat source 270 and the secondary heat exchanger 110' is thermally coupled to a secondary heat source 170.
• the temperature of the hot source being given the working fluid will be chosen optimally to best match the characteristics of the first exchanger 1 10 and in particular the temperature of the hot fluid of the first exchanger 1 10.
• the critical temperature of the working fluid chosen is slightly lower than the temperature of the hot fluid of this first exchanger 1 10.
• the fluid has a difference ( ⁇ ) between the temperature of the heat source 170 of the first exchanger 1 10 and the critical temperature of the working fluid; said gap ( ⁇ ) being between 20 ° C and 70 ° C. This range makes it possible to have a particularly high yield.
• FIG. 3 illustrates a particular embodiment in which the system comprises a hermetic expander 300 composed of the expander 120, the shaft 190 and the alternator 200 and a cooling circuit of the hermetic assembly.
• the cooling circuit is connected on the one hand to the output 140b of the injector 140 and on the other hand to the outlet 120b of the expander 120.
• It comprises a third heat exchanger 160 whose input 160a is connected to the output 140b of the injector 140 and whose output 160b is connected to the output 120b of the expander 120.
• the system is configured so that the outlet pressure 160b of the third exchanger 160 is greater than the outlet pressure of the expander 120, thus ensuring that the fluid flows well through the third exchanger 160 from its outlet 160a to its inlet 160b .
• the injector 140 there is thus a cold fluid having an increased pressure without introducing an additional pump. A portion of this cold fluid is thus recovered at the outlet 140b of the injector 140 and can be used to cool an auxiliary member such as for example a motor or an energy conversion device coupled to the expander 120.
• the The system is equipped with an alternator 200 serving as an energy conversion device to convert the mechanical movement of the expander 120 into electricity, most often in the form of a volumetric expander.
• the third heat exchanger 160 is configured to cool the hermetic expander 300 to an acceptable temperature level. For example, it is traversed by a heat transfer fluid that keeps the temperature of the hermetic expander to an acceptable level.
• the invention thus provides an effective solution to increase the overall efficiency of the system without decreasing its reliability and stability.
• the cooling circuit makes it particularly advantageous to cool, for example, an alternator 200 or a motor operating in reverse mode (in the case of a compressor operating as an expander) comprising a stator. 210.
• the third heat exchanger 160 allows cooling, thanks to to the working fluid taken at the outlet 140b of the injector 140, a fluid circulated around the stator 210.
• One of the advantages of the invention is thus to have an intermediate pressure level for the auxiliary members such as an alternator or a motor. Indeed, if we had only the high level to supply a cooling circuit, we would consume work done in the pump 150. With the injector 140, cold fluid is available without significantly impacting the pump 150.
• the power of the first exchanger 1 10 is 150kW; the working fluid is preferably R134a (one of the main constituents of this fluid is, for example, 1, 1, 1, 2-tetrafluoroethane); the maximum pressure is 50 bar; the maximum temperature is 130 ° C; the minimum pressure is 10.17 bars; the minimum temperature is 30 ° C; the gross power of 16.9 kW; the power to be evacuated by the 2kW cooling system; the cooling temperature 76.3 ° C; the ratio of the drive flow rate is 20. This ratio corresponds to the ratio between the steam flow rate and the liquid flow rate. It is measured, for example, using two flow meters.
• R134a one of the main constituents of this fluid is, for example, 1, 1, 1, 2-tetrafluoroethane
• the maximum pressure is 50 bar
• the maximum temperature is 130 ° C
• the minimum pressure is 10.17 bars
• the minimum temperature is 30 ° C
• the gross power of 16.9 kW the power to be evacuated by the 2kW cooling system
• the efficiency of the injector 140 is 34.73%.
• This report can be evaluated from a thermal balance of the installation. It will be recalled that exergy in thermodynamics is defined as being a quantity for measuring the quality of an energy.
• the injector 140 comprises:
• At least two inputs 141, 142 each forming a nozzle, one for a first fluid and the other for a second fluid having a higher pressure than the first fluid;
• At least one mixing chamber 143 the section of which is preferably convergent
• This ratio corresponds to the ratio between the steam flow rate and the liquid flow rate. It is measured, for example, using two flow meters.
• This yield corresponds to the exergy yield, that is to say to the ratio between the exergy at the outlet of the injector and the exergy upstream of it. It can be evaluated from a thermal balance of the installation.
• the first heat exchanger 110 that is, the hot heat exchanger, allows the working fluid to absorb the calories of a heat rejection fluid.
• the hot fluid is the thermal discharge fluid and the cold fluid is the working fluid.
• the second heat exchanger 130 that is to say the cold exchanger, allows the working fluid to evacuate its calories.
• the hot fluid is therefore the working fluid.
• the cold fluid can be water.
• the expander 120 is preferably of the volumetric expander type.
• the expander 120 is preferably a hermetic scroll compressor. Numerical values relating to the expander 120 are shown in Table 4, by way of non-limiting example of the invention.
• the expander 120 is associated with a power conversion device such as an alternator 200.
• the pump 150 is preferably a positive displacement pump. Numerical values relating to the pump 150 are shown in Table 5, by way of non-limiting example of the invention.
• the present invention Due to the use and in particular the positioning of the injector 140 in the circuit, the present invention has better performance than known solutions while having a high reliability and complexity that remains limited.
• use may be made of such methods for generating electrical energy in the processing industry (metallurgy, chemistry, paper mill) with low-temperature heat rejection, transport with a heat engine ( automobile, boat), solar concentrating, or biomass.
• the pump output is directly connected to the inlet of the first exchanger.
• the output of the first exchanger is directly connected to the second input of the injector.
• the injector outlet is directly connected to the pump inlet.
• a directly connected to B means that the connection is direct and that there is no other intermediate member (pump, exchanger, valve, injector, expander etc.) between A and B

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• 2014
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• 2015
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