EP0014630A1 - Thermodynamische Maschine und ihre Verwendung als Motor oder als Kälteerzeugungsmaschine - Google Patents

Thermodynamische Maschine und ihre Verwendung als Motor oder als Kälteerzeugungsmaschine Download PDF

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Publication number
EP0014630A1
EP0014630A1 EP80400127A EP80400127A EP0014630A1 EP 0014630 A1 EP0014630 A1 EP 0014630A1 EP 80400127 A EP80400127 A EP 80400127A EP 80400127 A EP80400127 A EP 80400127A EP 0014630 A1 EP0014630 A1 EP 0014630A1
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EP
European Patent Office
Prior art keywords
circuit
fluid
exchanger
working
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP80400127A
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English (en)
French (fr)
Inventor
Philippe Clavier
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Individual
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Individual
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Publication date
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Publication of EP0014630A1 publication Critical patent/EP0014630A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F01K25/10—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 the vapours being cold, e.g. ammonia, carbon dioxide, ether

Definitions

  • the invention relates to a thermodynamic machine with a fluid working circuit working in the liquid-vapor phase between a hot source which may be only the atmosphere and a cold source created, according to a new design, using the machine itself, of purely thermal operating principle based on the borrowing of calories from the atmosphere which can be, if necessary, increased by exploiting solar energy or by external combustion of additional supply, which leads to eliminate or reduce the consumption of chemical energy as well as the usual resulting pollution in applications of engine or refrigeration machines in particular.
  • thermodynamic machine comprising a fluid working circuit working in the liquid-vapor phase between a hot source and a cold source, comprising a motor for using the gaseous expansion of the fluid interposed between the hot source and the cold source each comprising an exchanger, and means for forced circulation of the fluid in the working circuit driven from said operating motor, is characterized in that it is associated with said working circuit a refrigerating circuit with refrigerant working in liquid-vapor phase to create a cold source cooperating with the cold source exchanger of the working circuit, while the hot source exchanger of the working circuit, cooperating with a medium possibly being only the atmosphere or of a higher temperature than the latter, said refrigeration circuit comprising means for forced circulation of the refrigerant also driven from said operating motor.
  • the invention also extends to a particular embodiment of the refrigeration circuit, while the choice of fluids in the two circuits also conditions its optimization as will be seen below.
  • the working circuit of the machine object of figure 1 comprises an exchanger 1 constituting the cold source of this circuit and in which the working fluid is intended to be liquefied.
  • This exchanger 1 is disposed in an enclosure 2 constituting the cold source of a refrigeration circuit which will be described later.
  • the working circuit includes another exchanger 3 forming an evaporator and cooperating with the atmosphere.
  • a valve 4 followed by a pump 5 intended to pump the liquefied fluid in order to inject it under a certain pressure into the exchanger 3.
  • a storage tank 6 of pressurized gaseous fluid Between the exchanger 3 and the exchanger 1 are successively disposed a storage tank 6 of pressurized gaseous fluid, a valve 7, a turbine 8 constituting the operating motor and a pressure regulator 9 opening directly into the exchanger 1.
  • the turbine 8 is used in particular to drive the pump 5. Initially the valves 4 and 7 are closed and the circuit is loaded with gaseous ethylene under pressure in its part including the pump 5, the exchanger 3 and the storage tank 6.
  • the cold source being considered as established, the operation of the machine, for which the valves 4 and 7 are put in the open position, takes place in the working circuit according to the cycle object of the temperature-pressure diagram of FIG. 2, the temperature T y being expressed in degrees Kelvin and the pressure P in bars.
  • This cycle is established by way of example for ethylene (C 2 H 4 ) chosen as working fluid among other possible, and for a maximum pressure of 30 bars in the flask, from which the possible excess can be derived.
  • this pipe 11 may include a non-return valve preventing any discharge to the turbine when the valve 7 is closed.
  • a to B is shown the expansion phase considered adiabatic of ethylene admitted into the turbine 8 from the storage tank 6 until it passes through the regulator 9, at the outlet of which it relaxes along the portion BC of its liquefaction curve L, entering the cold source exchanger 1, where it will be entirely liquefied according to CD and brought to D at a temperature lower than that of its liquefaction temperature under the prevailing residual pressure, which is the temperature corresponding to point C.
  • This temperature in D depends of course on the temperature reached in the enclosure 2 of cold source and the. diagram of figure 2 is established here for a cold source obtained by using Xenon under 1 bar, which corresponds to a temperature of 165 ⁇ k.
  • the ethylene thus liquefied is then discharged by the pump 5 under a certain pressure in the exchanger 1, this rise in pressure corresponding to the phase DE of the diagram.
  • the liquefied ethylene is then heated by the calories captured from the atmosphere by the exchanger, and its temperature in liquid phase rises according to the illustrated phase from E to F, while from this last point F placed on the liquefaction curve L, the ethylene is vaporized in the exchanger 1 and here considered to be heated to constant volume according to the illustrated phase from F to A, where we find our at the initial point A of the cycle corresponding to the state of the ethylene gas in the storage tank 6 (a constant pressure heating diagram would pass through D, E1, A, the practical diagram being established between the two).
  • valve 7 is closed first and the liquid ethylene present in the exchanger 1 is exhausted using the pump 5, towards the exchanger 3 and ball 6, where the ethy lene remains stored in the gas phase, after closing the valve 4.
  • This reconditioning of the circuit is provided with the use of external energy to drive the pump 5 due to the shutdown of the turbine 8, the time required for simple volumetric pumping of the quantity of liquid ethylene present in the exchanger 1, so that after a predetermined timed actuation of the pump 5 the valve 4 can be closed and the working circuit returned to the initial starting condition.
  • This external energy can be taken outside the machine or taken from storage means associated with the latter and charged by taking from the work of the turbine (such as accumulator batteries supplying an electric motor for driving the pump). An energy balance of such a cycle will be explained later on after the description of the refrigeration circuit creating the cold source.
  • the refrigeration circuit of the machine object of FIG. 3, with refrigerant working in liquid-vapor phase comprises a storage tank 12 of gaseous fluid under pressure which is connected by a conduit 13 provided with a valve 14 to a regulator 15 opening in enclosure 2 of cold source.
  • the vapor phase of the latter is sucked in via a pipe 16 and a compressor 17, which recompresses it to pass it through a valve 18 and a pipe 19 through a heat exchanger 20 disposed in the enclosure 2 and the outlet duct 21 of which opens into the latter via a pressure reducer 22.
  • a conduit 23 connecting the valve 18 to the storage tank 12 are also arranged a compressor 24 followed by an exchanger 25 immersed in the atmosphere.
  • this refrigeration circuit is described below using the temperature-pressure diagram in FIG. 4, corresponding to the use of Xenon as a refrigerant, assuming that initially the valve 14 is closed, the valve 18 is in position I, and that the Xenon in the gaseous state is stored under a pressure of approximately 10 bars, at atmospheric temperature of approximately 290 ⁇ K, in the balloon 12, in fact in the part of circuit between the valves 18 and 14 including the exchanger 25 and the tank 12.
  • the gaseous Xenon of the balloon 12 reaches the regulator 15 where it relaxes along the portion of adiabatic A, Bx followed by the portion BxCx of its liquefaction curve L, which here corresponds roughly to a liquefaction at 50% (ratio of A1 Cx on the ordinate of A1) the residual gas phase being pumped into enclosure 2 by the compressor 17 which recompresses it according to CxDx, by sending it to the exchanger 20 where it is here considered to be cooled to constant volume along the portion of curve DxBx in the diagram, before being expanded again in the expander 22 along the portion BxCx of the liquefaction curve L, where it is then still liquefied to about 50% (cooling at constant pressure would pass the diagram through DxB1, BxCx, the practical diagram being established between the two).
  • the valve 18 is passed to position II for connection of the compressor 17 on the additional compressor 24 which compresses the gaseous phase of the Xenon up to 'upon exhaustion of its liquid phase in the enclosure 2, by heating it along the portion of adiabatic CxDxE of Figure 4, while it is then cooled in the exchanger 25 to accumulate in the tank 12 to the ambient temperature according to the portion of curve EA returning to the starting point of the cycle, the valve 18 being brought back to position 1 at the end of this phase to maintain the portion of circuit including the tank 12 and between valves 18 and 14 in gas phase under pressure.
  • This reconditioning of the refrigeration circuit is also provided with the use of external energy to drive the compressors 17 and 24 due to the shutdown of the turbine 8, until, for example, the pressure in the source enclosure 2 cold has fallen to a value corresponding to the absence of liquid Xenon. This energy can be taken as indicated during the presentation of reconditioning of the working circuit.
  • the useful work from A to B is given by the formula: with Y adiabatic exponent equal to (ratio of mass heat at constant pressure and volume), T o the temperature corresponding to P o at A and p the pressure at B. Since ⁇ . can vary between 1.1 and 1.7, it is preferable to choose a fluid with small ⁇ .
  • Ethylene for example, has an ⁇ of 1.255 in the region of the pressures and temperatures involved, corresponding to a C v of 8.5 cal / mole.
  • the useful work is done with a residual pressure of 4 bars, and if the ambient temperature is 290 ⁇ K, the useful work will be of the order of 700 (calories / mole).
  • the work necessary to compress ethylene is given by: with at in bars from D to E the molecular mass in grams the density in grams / cm 3 .
  • ethylene is half liquefied and its heat of vaporization is 3,250 (cal / mole), it will be necessary to give, to liquefy the ethylene completely, 1,625 (cal / mole d 'ethylene) at the cold source.
  • the flow rate in moles of the cold source should therefore be approximately 1.4 moles of Xenon per mole of C 2 H 4 .
  • the work of the compressor 17 of the cold source will therefore be 448 cal / mole of C 2 H 4 .
  • valves of the two circuits being in the off position, to fill each circuit with corresponding gas under pressure by means of the valves 26 and 27 respectively provided on balloon 6 and balloon 12, then put the valves in the machine operating position.
  • the machine can be restarted after stop reconditioning according to the procedures already set out.
  • thermodynamic machine it is therefore possible with a thermodynamic machine according to the invention to create a refrigerating machine, or a motor, or a combination of the two, without using energy other than that taken from the atmosphere and while having working pressures which can be easily between 20 and 40 bars in particular.
  • the cold source part of the two circuits will of course be carefully insulated to avoid losses in its place.
  • the cold source enclosure 2 In use as a refrigerating machine, the cold source enclosure 2 will constitute at least part of itself the role of the usual evaporator in a refrigerating machine.
  • the engine of use is not necessarily a turbine but can also be a piston engine with distribution by usual valves, mono or polycylindrical for example, with intake manifold receiving the fluid under pressure from balloon 6 and manifold exhaust connected to the regulator 9 of the working circuit.
  • the ⁇ vary by 1.1 (C p 20 cal / mole) to 1.7 (Cp 5 cal / mole).
  • Xenon is all the better as its heat of vaporization is 3,000 cal / mole.
  • the vaporization temperature of the fluid in the working circuit must be higher than that of the fluid in the cold source circuit, this being to be taken into account given that the smallest pressure in the two circuits has not need to be the same. So that one can relatively increase the vaporization temperature of the working fluid by keeping it under a certain pressure above the atmosphere. We lose part of it liquefaction, so that the cold source must be able to recover more heat.
  • FIG. 6 An example has been given in FIG. 6 of an entropy diagram for the two fluid circuits, with ethylene in the working circuit and with Xenon in the refrigeration circuit, this diagram making it possible to assess the efficiency which can be expected from a such machine.
  • the band "Ambient temperature" Ta shows when the possible auxiliary hot source must intervene which will heat the gas from this ambient temperature to the temperature corresponding to A.
  • the segment (Cx-Cx) corresponds to the evaporation of Xenon in the cold source
  • the segment (Cx-Dx) corresponds to the compression of the gaseous Xenon
  • the segment (Dx-Bx) corresponds to cooling
  • the segment (Bx-Cx) corresponds to the expansion along the liquefaction curve.
  • Useful work is represented by the area (A, B, C, D, E, F, F, A) minus the work required by the refrigerant circuit, i.e. the hatched area (Dx, Bx, Cx, Cx, Dx) , while Carnot's performance would be the theoretical efficiency of the engine is only: 16.3%.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
EP80400127A 1979-01-29 1980-01-25 Thermodynamische Maschine und ihre Verwendung als Motor oder als Kälteerzeugungsmaschine Withdrawn EP0014630A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7902218A FR2485085A1 (fr) 1979-01-29 1979-01-29 Machine thermodynamique
FR7902218 1979-01-29

Publications (1)

Publication Number Publication Date
EP0014630A1 true EP0014630A1 (de) 1980-08-20

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EP80400127A Withdrawn EP0014630A1 (de) 1979-01-29 1980-01-25 Thermodynamische Maschine und ihre Verwendung als Motor oder als Kälteerzeugungsmaschine

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EP (1) EP0014630A1 (de)
JP (1) JPS55104509A (de)
FR (1) FR2485085A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3943161A1 (de) * 1989-12-28 1991-07-04 Walter Diel Fluessiggasdampfmotoren/-turbinen mit luftwaerme, erdwaerme, wasserwaerme als energietraeger zur krafterzeugung
WO1996001362A1 (de) * 1994-07-04 1996-01-18 Georg Rauscher Niedertemperatur-wärmekraftmaschine, niedertemperaturmotor ntm bzw. tieftemperaturmotor
FR2938003A1 (fr) * 2008-11-05 2010-05-07 Claude Antoine Blaizat Procede et dispositif de production d'electricite en utilisant de l'energie thermique a partir d'une source chaude,d'une source froide et d'un gaz moteur.

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE114604C (de) *
FR1138415A (fr) * 1955-10-31 1957-06-13 Procédé et appareillage de production de puissance
FR2122078A5 (de) * 1971-01-13 1972-08-25 Corenwinder Pierre
DE2654097A1 (de) * 1976-11-29 1978-06-01 Kurt Leczkowski Verfahren und anlagen zur gewinnung von nutzarbeit und/oder nutzkaelte aus waerme
EP0001382A2 (de) * 1977-10-11 1979-04-18 Kurt Leczkowski Verfahren und Anlagen zur Gewinnung von Nutzarbeit und/oder Nutzkälte aus Wärme

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE114604C (de) *
FR1138415A (fr) * 1955-10-31 1957-06-13 Procédé et appareillage de production de puissance
FR2122078A5 (de) * 1971-01-13 1972-08-25 Corenwinder Pierre
DE2654097A1 (de) * 1976-11-29 1978-06-01 Kurt Leczkowski Verfahren und anlagen zur gewinnung von nutzarbeit und/oder nutzkaelte aus waerme
EP0001382A2 (de) * 1977-10-11 1979-04-18 Kurt Leczkowski Verfahren und Anlagen zur Gewinnung von Nutzarbeit und/oder Nutzkälte aus Wärme

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3943161A1 (de) * 1989-12-28 1991-07-04 Walter Diel Fluessiggasdampfmotoren/-turbinen mit luftwaerme, erdwaerme, wasserwaerme als energietraeger zur krafterzeugung
WO1996001362A1 (de) * 1994-07-04 1996-01-18 Georg Rauscher Niedertemperatur-wärmekraftmaschine, niedertemperaturmotor ntm bzw. tieftemperaturmotor
WO1996001363A1 (de) * 1994-07-04 1996-01-18 Georg Rauscher Niedertemperaturmotor (ntm), tieftemperaturmotor (ttm) bzw. kältekraftmaschine (kkm)
FR2938003A1 (fr) * 2008-11-05 2010-05-07 Claude Antoine Blaizat Procede et dispositif de production d'electricite en utilisant de l'energie thermique a partir d'une source chaude,d'une source froide et d'un gaz moteur.

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Publication number Publication date
FR2485085A1 (fr) 1981-12-24
JPS55104509A (en) 1980-08-11

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