EP1706601B1 - System for converting thermal to motive energy - Google Patents

System for converting thermal to motive energy Download PDF

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EP1706601B1
EP1706601B1 EP05700542A EP05700542A EP1706601B1 EP 1706601 B1 EP1706601 B1 EP 1706601B1 EP 05700542 A EP05700542 A EP 05700542A EP 05700542 A EP05700542 A EP 05700542A EP 1706601 B1 EP1706601 B1 EP 1706601B1
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assembly according
gas
line
pressure
bore
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German (de)
French (fr)
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EP1706601A1 (en
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Gerhard Stock
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    • 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
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/005—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for by means of hydraulic motors
    • 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
    • F01K25/02—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the fluid remaining in the liquid phase

Definitions

  • the invention relates to an arrangement for converting thermal into motor energy with at least one pressure vessel having at least one upper injection opening for a hot and / or cold fluid, and with a coupled with a working cycle liquid piston pump within the pressure vessel.
  • the EP 1 159 512 B1 describes a gas expansion element for a device for converting thermal into motor energy, consisting of a filled with a gas or gas mixture closed pressure vessel, which is operatively connected via a displaceable piston with the arrangement and an upper injection port for hot water and an upper injection port for cold water and a lower drainage hole.
  • the lower water drain opening is arranged at the lower end of a sump which projects downwards over the pressure vessel and has a substantially smaller diameter than the pressure vessel, and the piston is designed as a liquid piston pump which is connected on the inlet side to the water outlet opening of the pressure vessel, which is assigned a water inlet of a working cycle. and On the output side is connected to a water outlet of the working cycle.
  • the DE 102 09 998 A1 a gas expansion element for a device for converting thermal into motor energy, consisting of a filled with a gas mixture closed pressure vessel, which is connected via a liquid piston with the arrangement and each having an upper injection port for hot water and cold water and a lower connected to a working circuit Has water drainage opening.
  • the liquid piston is provided within the pressure vessel and floats on the pressurized surface of the liquid piston acted upon by the gas or gas mixture pressure-resistant separation layer.
  • a gas expansion element is also from the US Pat. No. 3,608,311 A1 known.
  • the liquid piston is in each case via an opening with a flow and a return of a working circuit and with the injection openings for hot and cold water in combination.
  • the object is achieved in that the pressure vessel has a horizontal wall provided with a bore, wherein above the wall, a gas or gas mixture and below the wall, the liquid piston pump is located.
  • the bore forms a kind of sump, which reduces an overflow of the gaseous medium in the region of the liquid piston pump and thus reduces heat transfer between the air and the liquid piston, wherein precipitated condensate passes through the bore in the liquid piston.
  • the local boundary through the wall ensures rapid penetration of the gas with the hot or cold fluid for expansion or contraction of the air.
  • the bore widens conically in the direction of the gas-filled portion of the pressure vessel. Due to the taper of the bore, which extends approximately to the wall of the pressure vessel, the collection and discharge of condensate from the gas-filled portion of the pressure vessel is favored, the bore due to its cylindrical part favorable to the heat transfer between the gas and affects the liquid piston.
  • a float valve with the bore for filling level limitation of the liquid piston pump is inserted into the wall.
  • the float valve releases the bore upon expansion of the gas in the pressure vessel to allow the liquid piston pump to be pressurized and closes the bore upon reaching a maximum level of the liquid piston pump to prevent overflow of the fluid into the gas filled area of the pressure vessel.
  • the float valve comprises a screwed into the wall basket for receiving a plastic ball, wherein the basket has the cylindrical part of the bore.
  • the plastic ball has a lower density than the liquid of the liquid piston pump and is sized to close the bore.
  • the screen In order to protect the plastic ball of the float valve against thermal damage when exposed to gas with the warm fluid, wearing in a design of the basket mounted on a spacer sockets screen which projects into the gas or gas mixture filled area of the pressure vessel.
  • the screen can be made, for example, of a metallic material and prevents the direct impingement of the plastic ball with the fluid. Furthermore, the screen contributes to a distribution of the injected fluid into the pressure vessel, which thus penetrates the gas within the pressure vessel relatively quickly.
  • the pressure vessel at its lower end on a connecting piece for connection to a flow line of the working cycle.
  • the connecting piece is coupled to a return of the working cycle.
  • the liquid piston or the filling level within the liquid piston pump by a relatively simple float circuit to detect or limit by the float valve.
  • the return line of the working circuit in particular with the interposition of a controllable valve, connected to a line leading to the injection port for the cold fluid or to a reservoir for the fluid.
  • the fluid in the return line of the working circuit is at a relatively low temperature level and can be passed as a cold fluid into the pressure vessel to cause a contraction of the gas therein.
  • the feed line leads to a turbine, from which the return line goes off.
  • the flow line is preferably connected via a line to the reservoir.
  • the filling level of the storage tank can be regulated with a float valve.
  • valves may be formed, for example, as a relatively simple check valves to pressurize the gas within the pressure vessel alternately alternately with hot or cold fluid, which of course also the arrangement of a controlled multi-way valve is conceivable.
  • the heating and the cooling device are each coupled with the interposition of a controlled valve with one of the injection ports.
  • the fluid is water or an organic substance containing pentane, toluene or silicone oil.
  • organic substances are used in power plant operation in the so-called Organic Rankine Cycle (ORC) use and have the advantage that they evaporate at ambient pressure even at relatively low temperatures.
  • a short-circuit pipeline with at least one controllable valve for pressure equalization between the pressure vessels after performing the work of the gas is provided according to an advantageous development of the inventive idea between two pressure vessels.
  • a pressure difference which is due to the hot gas of a pressure vessel and the cold gas of the other pressure vessel.
  • the pressure equalization takes place a heat flow, whereby the remaining heat energy in the one Pressure vessel for heating the gas of the other pressure vessel is used to an equilibrium temperature.
  • the amount of gas in the pressure vessel increases with the expanding gas, which is accompanied by an increase in the pressure difference between the two pressure vessels and thus an increase in performance.
  • the arrangement comprises four pressure vessels 1, 2, 3, 4, each having an upper injection port 5 for hot water and an upper injection port 6 for cold water and at its lower ends a connecting piece 7 for connection to a working circuit 8.
  • the injection port 5 for hot water is connected via a line 9 with an inserted heater 10 with an associated formed as a check valve valve 11 in conjunction, which is coupled via a line 14 with a serving as Kochström seer reservoir 15 for the charging circuit.
  • the line 14 is connected via a further designed as a check valve 37 via a valve coupled to a cooling device 13 line 12 with the injection port 6 for cold water.
  • each pressure vessel 1, 2, 3, 4 opens on the one hand with the interposition of a check valve 16 in a flow line 17 and the other in a likewise a check valve 18 having return line 19 of the working circuit 8, wherein the flow line 17 both with a turbine 20 as Also coupled with the interposition of a check valve 24 to the reservoir 15.
  • the pressure vessel 1, 2, 3, 4 connecting return line 19 is connected to the turbine 20 with the interposition of a controllable valve designed as a two-way valve 22.
  • each pressure vessel 1, 2, 3, 4 is a coupled to the working circuit 8 liquid piston pump 25th educated.
  • each pressure vessel 1, 2, 3, 4 has a bore 26 provided with a horizontal wall 27, wherein above the wall 27, the gas and below the wall 27, the liquid piston pump 25 is present.
  • the bore 26 expands within the wall 27 in the direction of the gas-filled portion of the pressure vessel 1, 2, 3, 4 conically up to the inner wall of the pressure vessel 1, 2, 3, 4, to collect accumulating condensate and to direct the liquid piston pump 25 ,
  • a float valve 28 is screwed, which projects into the region of the liquid piston pump 25 to limit their level.
  • the upper end face 30 of the float valve 28 is formed corresponding to the conical shape of the bore 26 and flush with it. Furthermore, the cylindrical part 29 of the bore 26 is located centrally in the float valve 28. In the upper end face 30 of the float valve 28 there are two mutually spaced blind holes 31 for a screw-in. In a basket 32 of the float valve 28, which is closed with a cover 33, a plastic ball 34 is arranged, which serves to close the bore 26 upon reaching a maximum level of the liquid piston pump 25. In order to protect the plastic ball 34 against thermal stress during injection of the warm fluid into the pressure vessel 1, 2, 3, 4, a substantially rectangular screen 35 is screwed on spacer bushes 36 on the upper end face 30 of the float valve 28.
  • the controllable valve 22 in the return line 19 is connected in such a way that it prevents water from entering the pressure vessels 1, 2, 3, 4 as long as pressure equalization exists between each two pressure vessels 1, 2, 3, 4.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Description

Die Erfindung bezieht sich auf eine Anordnung zum Umwandeln von thermischer in motorische Energie mit mindestens einem Druckbehälter, der mindestens eine obere Einspritzöffnung für ein warmes und/oder kaltes Fluid aufweist, und mit einer mit einem Arbeitskreislauf gekoppelten Flüssigkolbenpumpe innerhalb des Druckbehälters.The invention relates to an arrangement for converting thermal into motor energy with at least one pressure vessel having at least one upper injection opening for a hot and / or cold fluid, and with a coupled with a working cycle liquid piston pump within the pressure vessel.

Die EP 1 159 512 B1 beschreibt ein Gasausdehnungselement für eine Anordnung zum Umwandeln von thermischer in motorische Energie, bestehend aus einem mit einem Gas- oder Gasgemisch gefüllten geschlossenen Druckbehälter, der über einen verschiebbaren Kolben mit den Anordnung wirksam verbunden ist und eine obere Einspritzöffnung für Warmwasser sowie eine obere Einspritzöffnung für Kaltwasser und eine untere Wasserablauföffnung hat. Die untere Wasserablauföffnung ist am unteren Ende eines den Druckbehälter nach unten überragenden Sumpfes angeordnet, der einen wesentlich kleineren Durchmesser als der Druckbehälter hat, und der Kolben ist als Flüssigkolbenpumpe ausgebildet, die eingangsseitig mit der Wasserablauföffnung des Druckbehälters, der ein Wasserzulauf eines Arbeitskreislaufes zugeordnet ist, und ausgangsseitig mit einem Wasserablauf des Arbeitskreislaufes verbunden ist.The EP 1 159 512 B1 describes a gas expansion element for a device for converting thermal into motor energy, consisting of a filled with a gas or gas mixture closed pressure vessel, which is operatively connected via a displaceable piston with the arrangement and an upper injection port for hot water and an upper injection port for cold water and a lower drainage hole. The lower water drain opening is arranged at the lower end of a sump which projects downwards over the pressure vessel and has a substantially smaller diameter than the pressure vessel, and the piston is designed as a liquid piston pump which is connected on the inlet side to the water outlet opening of the pressure vessel, which is assigned a water inlet of a working cycle. and On the output side is connected to a water outlet of the working cycle.

Des Weiteren offenbart die DE 102 09 998 A1 ein Gasausdehnungselement für eine Anordnung zum Umwandeln von thermischer in motorische Energie, bestehend aus einem mit einem Gasgemisch gefüllten geschlossenen Druckbehälter, der über einen Flüssigkolben mit der Anordnung wirksam verbunden ist und jeweils eine obere Einspritzöffnung für Warmwasser sowie für Kaltwasser und eine untere mit einem Arbeitskreislauf verbundene Wasserablauföffnung aufweist. Der Flüssigkolben ist innerhalb des Druckbehälters vorgesehen und auf der druckbeaufschlagten Oberfläche des Flüssigkolbens schwimmt eine von dem Gas oder Gasgemisch beaufschlagte druckbeständige Trennschicht. Ein solches Gasausdehnungselement ist auch aus der US 3 608 311 A1 bekannt. Hierbei steht der Flüssigkolben über jeweils eine Öffnung mit einem Vorlauf und einem Rücklauf eines Arbeitskreislaufes sowie mit den Einspritzöffnungen für Warm- und Kaltwasser in Verbindung. Diese Gasausdehnungselemente sind insofern nachteilig, als das bei der Zufuhr von Warmwasser expandierende Gas den Flüssigkolben nur unzureichend beaufschlagt und eine verhältnismäßig große Wärmemenge des gespritzten Warmwassers in den Flüssigkolben eingetragen wird und damit nicht mehr zur Expansion des Gases zur Verfügung steht, weshalb die Anordnung zum Umwandeln von thermischer in motorische Energie einen relativ geringen Wirkungsgrad aufweist.Furthermore, the DE 102 09 998 A1 a gas expansion element for a device for converting thermal into motor energy, consisting of a filled with a gas mixture closed pressure vessel, which is connected via a liquid piston with the arrangement and each having an upper injection port for hot water and cold water and a lower connected to a working circuit Has water drainage opening. The liquid piston is provided within the pressure vessel and floats on the pressurized surface of the liquid piston acted upon by the gas or gas mixture pressure-resistant separation layer. Such a gas expansion element is also from the US Pat. No. 3,608,311 A1 known. Here, the liquid piston is in each case via an opening with a flow and a return of a working circuit and with the injection openings for hot and cold water in combination. These gas expansion elements are disadvantageous in that when the supply of hot water expanding gas to the liquid piston is insufficiently applied and a relatively large amount of heat of the injected hot water is introduced into the liquid piston and thus is no longer available for expansion of the gas, which is why the arrangement for converting from thermal to motor energy has a relatively low efficiency.

Es ist Aufgabe der Erfindung, eine Anordnung zum Umwandeln von thermischer in motorische Energie der eingangs genannten Art zu schaffen, die bei einem einfachen Aufbau einen relativ hohen Wirkungsgrad aufweist.It is an object of the invention to provide an arrangement for converting thermal into motor energy of the aforementioned To create kind, which has a relatively high efficiency with a simple structure.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass der Druckbehälter eine mit einer Bohrung versehene horizontale Wandung aufweist, wobei sich oberhalb der Wandung ein Gas oder Gasgemisch und unterhalb der Wandung die Flüssigkolbenpumpe befindet.According to the invention the object is achieved in that the pressure vessel has a horizontal wall provided with a bore, wherein above the wall, a gas or gas mixture and below the wall, the liquid piston pump is located.

Mit der horizontalen Wandung wird eine thermische Trennung zwischen den abwechselnd mit einem warmen bzw. kalten Fluid beaufschlagten Gas und der Flüssigkolbenpumpe erzielt. Hierbei bildet die Bohrung eine Art Sumpf, der ein Überströmen des gasförmigen Mediums in den Bereich der Flüssigkolbenpumpe reduziert und damit einen Wärmeübergang zwischen der Luft und dem Flüssigkolben vermindert, wobei ausfallendes Kondensat durch die Bohrung in den Flüssigkolben gelangt. Des Weiteren stellt die örtliche Begrenzung durch die Wandung ein schnelles Durchdringen des Gases mit dem warmen bzw. kalten Fluid zur Expansion bzw. Kontraktion der Luft sicher.With the horizontal wall, a thermal separation between the alternately acted upon with a hot or cold fluid gas and the liquid piston pump is achieved. Here, the bore forms a kind of sump, which reduces an overflow of the gaseous medium in the region of the liquid piston pump and thus reduces heat transfer between the air and the liquid piston, wherein precipitated condensate passes through the bore in the liquid piston. Furthermore, the local boundary through the wall ensures rapid penetration of the gas with the hot or cold fluid for expansion or contraction of the air.

Bevorzugt erweitert sich die Bohrung in Richtung des mit Gas gefüllten Abschnittes des Druckbehälters konisch. Durch die Konizität der Bohrung, die sich bis annähernd an die Wand des Druckbehälters erstreckt, ist das Sammeln und Ableiten von Kondensat aus dem mit Gas gefüllten Abschnitt des Druckbehälters begünstigt, wobei sich die Bohrung aufgrund ihres zylindrischen Teils günstig auf den Wärmeübergang zwischen dem Gas und dem Flüssigkolben auswirkt.Preferably, the bore widens conically in the direction of the gas-filled portion of the pressure vessel. Due to the taper of the bore, which extends approximately to the wall of the pressure vessel, the collection and discharge of condensate from the gas-filled portion of the pressure vessel is favored, the bore due to its cylindrical part favorable to the heat transfer between the gas and affects the liquid piston.

Nach einer vorteilhaften Ausgestaltung ist in die Wandung ein Schwimmerventil mit der Bohrung zur Füllstandsbegrenzung der Flüssigkolbenpumpe eingesetzt. Das Schwimmerventil gibt beim Expandieren des Gases im Druckbehälter die Bohrung frei, damit eine Beaufschlagung der Flüssigkolbenpumpe stattfindet, und verschließt die Bohrung beim Erreichen eines Maximalfüllstandes der Flüssigkolbenpumpe, um ein Überströmen der Flüssigkeit in den mit Gas gefüllten Bereich des Druckbehälters zu verhindern.According to an advantageous embodiment, a float valve with the bore for filling level limitation of the liquid piston pump is inserted into the wall. The float valve releases the bore upon expansion of the gas in the pressure vessel to allow the liquid piston pump to be pressurized and closes the bore upon reaching a maximum level of the liquid piston pump to prevent overflow of the fluid into the gas filled area of the pressure vessel.

Vorzugsweise umfasst das Schwimmerventil einen in die Wandung eingeschraubten Korb zur Aufnahme einer Kunststoffkugel, wobei der Korb den zylindrischen Teil der Bohrung aufweist. Die Kunststoffkugel hat eine geringere Dichte als die Flüssigkeit der Flüssigkolbenpumpe und ist derart bemessen, dass sie die Bohrung verschließt.Preferably, the float valve comprises a screwed into the wall basket for receiving a plastic ball, wherein the basket has the cylindrical part of the bore. The plastic ball has a lower density than the liquid of the liquid piston pump and is sized to close the bore.

Um die Kunststoffkugel des Schwimmerventils vor einer thermischen Beschädigung bei einer Gasbeaufschlagung mit dem warmen Fluid zu schützen, trägt in Ausgestaltung der Korb einen über Distanzbuchsen befestigten Schirm, der in den mit Gas oder Gasgemisch gefüllten Bereich des Druckbehälters ragt. Der Schirm kann beispielsweise aus einem metallischen Werkstoff gefertigt sein und verhindert die direkte Beaufschlagung der Kunststoffkugel mit dem Fluid. Des Weiteren trägt der Schirm zu einer Verteilung des in den Druckbehälter eingespritzten Fluids bei, das demnach das Gas innerhalb des Druckbehälters relativ schnell durchdringt.In order to protect the plastic ball of the float valve against thermal damage when exposed to gas with the warm fluid, wearing in a design of the basket mounted on a spacer sockets screen which projects into the gas or gas mixture filled area of the pressure vessel. The screen can be made, for example, of a metallic material and prevents the direct impingement of the plastic ball with the fluid. Furthermore, the screen contributes to a distribution of the injected fluid into the pressure vessel, which thus penetrates the gas within the pressure vessel relatively quickly.

Zweckmäßigerweise weist der Druckbehälter an seinem unteren Ende einen Anschlussstutzen zur Verbindung mit einer Vorlaufleitung des Arbeitskreislaufes auf. Vorteilhafterweise ist der Anschlussstutzen mit einem Rücklauf des Arbeitskreislaufes gekoppelt. In dieser Kombination, in der sowohl die Vorlaufleitung als auch die Rücklaufleitung des Arbeitskreislaufes mit dem Anschlussstutzen verbunden sind, ist der Flüssigkolben bzw. die Füllstandshöhe innerhalb der Flüssigkolbenpumpe durch eine relativ einfache Schwimmerschaltung zu erfassen bzw. durch das Schwimmerventil zu begrenzen. Alternativ dazu ist die Rücklaufleitung des Arbeitskreislaufes, insbesondere unter Zwischenschaltung eines steuerbaren Ventils, mit einer zu der Einspritzöffnung für das kalte Fluid oder zu einem Vorratsbehälter für das Fluid führenden Leitung verbunden. Das Fluid in der Rücklaufleitung des Arbeitskreislaufes befindet sich auf einem relativ niedrigen Temperaturniveau und kann als kaltes Fluid in den Druckbehälter geleitet werden, um ein Kontrahieren des darin befindlichen Gases zu bewirken.Conveniently, the pressure vessel at its lower end on a connecting piece for connection to a flow line of the working cycle. Advantageously, the connecting piece is coupled to a return of the working cycle. In this combination, in which both the supply line and the return line of the working circuit are connected to the connecting piece, the liquid piston or the filling level within the liquid piston pump by a relatively simple float circuit to detect or limit by the float valve. Alternatively, the return line of the working circuit, in particular with the interposition of a controllable valve, connected to a line leading to the injection port for the cold fluid or to a reservoir for the fluid. The fluid in the return line of the working circuit is at a relatively low temperature level and can be passed as a cold fluid into the pressure vessel to cause a contraction of the gas therein.

Um die translatorische Bewegung der Flüssigkolbenpumpe in eine rotatorische Bewegung umzuwandeln, führt die Vorlaufleitung zu einer Turbine, von der die Rücklaufleitung abgeht.In order to convert the translational movement of the liquid piston pump into a rotational movement, the feed line leads to a turbine, from which the return line goes off.

Zum Laden des Speisewasserkreislaufs und zum Druckausgleich innerhalb der Anordnung ist vorzugsweise die Vorlaufleitung über eine Leitung an den Vorratsbehälter angeschlossen. Der Füllstand des Vorratsbehälters ist mit einem eingesetzten Schwimmerventil regulierbar.For loading the feedwater circuit and pressure equalization within the arrangement, the flow line is preferably connected via a line to the reservoir. The filling level of the storage tank can be regulated with a float valve.

Nach einer weiteren Ausgestaltung der Erfindung geht von dem Vorratsbehälter eine Leitung ab, die unter Zwischenschaltung von Ventilen zu einer Heiz- und einer Kühleinrichtung für das Fluid verzweigt. Hierbei können die Ventile beispielsweise als relativ einfache Rückschlagventile ausgebildet sein, um das Gas innerhalb des Druckbehälters druckgesteuert abwechselnd mit warmem oder kaltem Fluid zu beaufschlagen, wobei selbstverständlich auch die Anordnung eines gesteuerten Mehrwege-Ventils denkbar ist. Zweckmäßigerweise sind die Heiz- und die Kühleinrichtung jeweils unter Zwischenschaltung eines gesteuerten Ventils mit einer der Einspritzöffnungen gekoppelt.According to a further embodiment of the invention is from the reservoir from a line which branches with the interposition of valves to a heating and a cooling device for the fluid. In this case, the valves may be formed, for example, as a relatively simple check valves to pressurize the gas within the pressure vessel alternately alternately with hot or cold fluid, which of course also the arrangement of a controlled multi-way valve is conceivable. Conveniently, the heating and the cooling device are each coupled with the interposition of a controlled valve with one of the injection ports.

Vorzugsweise ist das Fluid Wasser oder eine Pentan, Toluol oder Silikonöl enthaltende organische Substanz. Solche organischen Substanzen finden im Kraftwerksbetrieb im so genannten Organic Rankine Cycle (ORC) Verwendung und haben den Vorteil, dass sie bei Umgebungsdruck bereits bei verhältnismäßig geringen Temperaturen verdampfen.Preferably, the fluid is water or an organic substance containing pentane, toluene or silicone oil. Such organic substances are used in power plant operation in the so-called Organic Rankine Cycle (ORC) use and have the advantage that they evaporate at ambient pressure even at relatively low temperatures.

Zur weitergehenden Steigerung der Leistung der Anordnung ist nach einer vorteilhaften Weiterbildung des Erfindungsgedankens zwischen jeweils zwei Druckbehältern eine Kurzschlussrohrleitung mit mindestens einem steuerbaren Ventil zum Druckausgleich zwischen den Druckbehältern nach dem Verrichten der Arbeit des Gases vorgesehen. Am Ende der Arbeitsphase herrscht zwischen den beiden Druckbehältern eine Druckdifferenz, die durch das warme Gas des einen Druckbehälters und das kalte Gas des anderen Druckbehälters bedingt ist. Mit dem Druckausgleich findet eine Wärmeströmung statt, wodurch die noch vorhandene Wärmeenergie in dem einen Druckbehälter zur Erwärmung des Gases des anderen Druckbehälters bis zu einer Ausgleichtemperatur ausgenutzt wird. Gleichzeitig steigt die Gasmenge in dem Druckbehälter mit dem expandierenden Gas, womit eine Steigerung der Druckdifferenz zwischen den beiden Druckbehältern und damit eine Leistungserhöhung einhergeht.To further increase the performance of the arrangement, a short-circuit pipeline with at least one controllable valve for pressure equalization between the pressure vessels after performing the work of the gas is provided according to an advantageous development of the inventive idea between two pressure vessels. At the end of the working phase prevails between the two pressure vessels, a pressure difference, which is due to the hot gas of a pressure vessel and the cold gas of the other pressure vessel. With the pressure equalization takes place a heat flow, whereby the remaining heat energy in the one Pressure vessel for heating the gas of the other pressure vessel is used to an equilibrium temperature. At the same time the amount of gas in the pressure vessel increases with the expanding gas, which is accompanied by an increase in the pressure difference between the two pressure vessels and thus an increase in performance.

Es versteht sich, dass die vorstehend genannten und nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen verwendbar sind. Der Rahmen der vorliegenden Erfindung ist nur durch die Ansprüche definiert.It goes without saying that the features mentioned above and those yet to be explained below can be used not only in the respectively specified combination but also in other combinations. The scope of the present invention is defined only by the claims.

Die Erfindung wird im Folgenden anhand eines Ausführungsbeispieles unter Bezugnahme auf die zugehörigen Zeichnungen näher erläutert. Es zeigt:

Fig. 1
eine schematische Darstellung der erfindungsgemäßen Anordnung zum Umwandeln von thermischer in motorische Energie,
Fig. 2
eine vergrößerte Darstellung der Einzelheit II gemäß Fig. 1 im Teilschnitt,
Fig. 3
eine vergrößerte Schnittdarstellung der Einzelheit III gemäß Fig. 2,
Fig. 4
eine Draufsicht auf die Darstellung nach Fig. 3 und
Fig. 5
eine Prinzipdarstellung eines Druck-Zeit-Diagramms der Anordnung nach Fig. 1.
The invention will be explained in more detail below with reference to an embodiment with reference to the accompanying drawings. It shows:
Fig. 1
a schematic representation of the arrangement according to the invention for converting thermal into motor energy,
Fig. 2
an enlarged view of the detail II according to Fig. 1 in partial section,
Fig. 3
an enlarged sectional view of the detail III according to Fig. 2 .
Fig. 4
a plan view of the illustration after Fig. 3 and
Fig. 5
a schematic representation of a pressure-time diagram of the arrangement according to Fig. 1 ,

Die Anordnung umfasst vier Druckbehälter 1, 2, 3, 4, die jeweils eine obere Einspritzöffnung 5 für warmes Wasser sowie eine obere Einspritzöffnung 6 für kaltes Wasser und an ihren unteren Enden einen Anschlussstutzen 7 zur Verbindung mit einem Arbeitskreislauf 8 aufweisen. Die Einspritzöffnung 5 für warmes Wasser steht über eine Leitung 9 mit einer eingesetzten Heizeinrichtung 10 mit einem zugeordneten als Rückschlagventil ausgebildeten Ventil 11 in Verbindung, das über eine Leitung 14 mit einem als Überströmbehälter dienenden Vorratsbehälter 15 für den Ladekreislauf gekoppelt ist. Im Weiteren ist die Leitung 14 über ein weiteres als Rückschlagventil ausgebildetes Ventil 37 über eine mit einer Kühleinrichtung 13 gekoppelte Leitung 12 mit der Einspritzöffnung 6 für kaltes Wasser verbunden. Der Anschlussstutzen 7 jedes Druckbehälters 1, 2, 3, 4 mündet zum einen unter Zwischenschaltung eines Rückschlagventils 16 in eine Vorlaufleitung 17 und zum anderen in eine ebenfalls ein Rückschlagventil 18 aufweisende Rücklaufleitung 19 des Arbeitskreislaufes 8, wobei die Vorlaufleitung 17 sowohl mit einer Turbine 20 als auch unter Zwischenschaltung eines Rückschlagventils 24 mit dem Vorratsbehälter 15 gekoppelt ist. Die die Druckbehälter 1, 2, 3, 4 verbindende Rücklaufleitung 19 ist unter Zwischenschaltung eines steuerbaren als Zwei-Wege-Ventil ausgestalteten Ventils 22 mit der Turbine 20 verbunden.The arrangement comprises four pressure vessels 1, 2, 3, 4, each having an upper injection port 5 for hot water and an upper injection port 6 for cold water and at its lower ends a connecting piece 7 for connection to a working circuit 8. The injection port 5 for hot water is connected via a line 9 with an inserted heater 10 with an associated formed as a check valve valve 11 in conjunction, which is coupled via a line 14 with a serving as Überströmbehälter reservoir 15 for the charging circuit. Furthermore, the line 14 is connected via a further designed as a check valve 37 via a valve coupled to a cooling device 13 line 12 with the injection port 6 for cold water. The connecting piece 7 of each pressure vessel 1, 2, 3, 4 opens on the one hand with the interposition of a check valve 16 in a flow line 17 and the other in a likewise a check valve 18 having return line 19 of the working circuit 8, wherein the flow line 17 both with a turbine 20 as Also coupled with the interposition of a check valve 24 to the reservoir 15. The pressure vessel 1, 2, 3, 4 connecting return line 19 is connected to the turbine 20 with the interposition of a controllable valve designed as a two-way valve 22.

Innerhalb eines jeden Druckbehälters 1, 2, 3, 4 ist eine mit dem Arbeitskreislauf 8 gekoppelte Flüssigkolbenpumpe 25 ausgebildet. Hierzu weist jeder Druckbehälter 1, 2, 3, 4 eine mit einer Bohrung 26 versehene horizontale Wandung 27 auf, wobei oberhalb der Wandung 27 das Gas und unterhalb der Wandung 27 die Flüssigkolbenpumpe 25 vorhanden ist. Die Bohrung 26 erweitert sich innerhalb der Wandung 27 in Richtung des mit Gas gefüllten Abschnittes des Druckbehälters 1, 2, 3, 4 konisch bis zur Innenwandung des Druckbehälters 1, 2, 3, 4, um anfallendes Kondensat zu sammeln und zur Flüssigkolbenpumpe 25 zu leiten. In die in den Druckbehälter 1, 2, 3, 4 eingeschweißte Wandung 27 ist ein Schwimmerventil 28 eingeschraubt, das in den Bereich der Flüssigkolbenpumpe 25 ragt, um deren Füllstand zu begrenzen. Die obere Stirnseite 30 des Schwimmerventils 28 ist korrespondierend zu dem konischen Verlauf der Bohrung 26 ausgebildet und schließt bündig damit ab. Des Weiteren befindet sich der zylindrische Teil 29 der Bohrung 26 zentrisch in dem Schwimmerventil 28. In der oberen Stirnseite 30 des Schwimmerventils 28 befinden sich zwei zueinander beabstandete Sacklöcher 31 für ein Einschraubwerkzeug. In einem Korb 32 des Schwimmerventils 28, der mit einem Deckel 33 verschlossen ist, ist eine Kunststoffkugel 34 angeordnet, die zum Verschließen der Bohrung 26 beim Erreichen eines maximalen Füllstandes der Flüssigkolbenpumpe 25 dient. Um die Kunststoffkugel 34 vor einer thermischen Belastung beim Einspritzen des warmen Fluids in den Druckbehälter 1, 2, 3, 4 zu schützen, ist auf der oberen Stirnseite 30 des Schwimmerventils 28 ein im Wesentlichen rechteckförmiger Schirm 35 über Distanzbuchsen 36 angeschraubt.Within each pressure vessel 1, 2, 3, 4 is a coupled to the working circuit 8 liquid piston pump 25th educated. For this purpose, each pressure vessel 1, 2, 3, 4 has a bore 26 provided with a horizontal wall 27, wherein above the wall 27, the gas and below the wall 27, the liquid piston pump 25 is present. The bore 26 expands within the wall 27 in the direction of the gas-filled portion of the pressure vessel 1, 2, 3, 4 conically up to the inner wall of the pressure vessel 1, 2, 3, 4, to collect accumulating condensate and to direct the liquid piston pump 25 , In the welded into the pressure vessel 1, 2, 3, 4 wall 27, a float valve 28 is screwed, which projects into the region of the liquid piston pump 25 to limit their level. The upper end face 30 of the float valve 28 is formed corresponding to the conical shape of the bore 26 and flush with it. Furthermore, the cylindrical part 29 of the bore 26 is located centrally in the float valve 28. In the upper end face 30 of the float valve 28 there are two mutually spaced blind holes 31 for a screw-in. In a basket 32 of the float valve 28, which is closed with a cover 33, a plastic ball 34 is arranged, which serves to close the bore 26 upon reaching a maximum level of the liquid piston pump 25. In order to protect the plastic ball 34 against thermal stress during injection of the warm fluid into the pressure vessel 1, 2, 3, 4, a substantially rectangular screen 35 is screwed on spacer bushes 36 on the upper end face 30 of the float valve 28.

Zu Beginn des Betriebs der Anordnung findet zunächst ventilgesteuert ein Druckausgleich zwischen den Druckbehältern 1 und 2 statt, wie es durch Pfeil A in Fig. 5 symbolisiert ist. Der Pfeil B weist auf den Zeitpunkt hin, bei dem warmes Wasser in den Druckbehälter 3 eingespritzt wird, das ein Expandieren des in diesem Druckbehälter 3 vorhandenen Gases bewirkt. Durch das expandierende Gas wird der verschiebbare Kolben der Flüssigkolbenpumpe 25 verlagert, der somit translatorische Arbeit verrichtet, die über die Vorlaufleitung 17 des Arbeitskreislaufes 8 der Turbine 20 zur Umwandlung in rotatorische Arbeit zugeführt wird. Nach dem Druckanstieg und dem nach der Kolbendisplazierung der Flüssigkolbenpumpe 25 des Druckbehälters 3 entsprechenden Druckabfall in diesem Druckbehälter 3 fällt Wasser aus, das über die Bohrung 26 in die Flüssigkolbenpumpe 25 geleitet wird. Gleichzeitig wird, wie durch Pfeil C angegeben, in der Kühleinrichtung 13 aufbereitetes Kaltwasser über die entsprechende Einspritzöffnung 6 in den Druckbehälter 4 gespritzt. Beim Einsprühen des Kaltwassers in diesen Druckbehälter 4 kontraktiert das Gas und verrichtet ebenfalls über den verschiebbaren Kolben der entsprechenden Flüssigkolbenpumpe 25 Arbeit. Während dieser Phase befinden sich die Druckbehälter 1, 2 auf einem Druckniveau, das ihrem Ausgleichsdruck entspricht. Nach der Übertragung der nutzbaren Expansions- bzw. Kontraktionsarbeit des Gases erfolgt ein Druckausgleich zwischen den Druckbehältern 3, 4, wobei gleichzeitig in den Druckbehälter 1 kaltes Wasser und in den Druckbehälter 2 warmes Wasser eingeleitet wird, so dass deren zugeordneten Flüssigkolbenpumpen 25 Kontraktions- bzw. Expansionsarbeit verrichten. Der Zeitpunkt des Einspritzens von kaltem Wasser in den Druckbehälter 1 ist durch den Pfeil D und der des Einspritzens von warmem Wasser in den Druckbehälter 2 durch den Pfeil E dargestellt.At the beginning of the operation of the arrangement is first valve-controlled pressure equalization between the pressure vessels 1 and 2 instead, as indicated by arrow A in Fig. 5 is symbolized. The arrow B indicates the time at which hot water is injected into the pressure vessel 3, which causes an expansion of the present in this pressure vessel 3 gas. The displaceable piston of the liquid piston pump 25 is displaced by the expanding gas, which thus performs translational work, which is supplied via the flow line 17 of the working circuit 8 of the turbine 20 for conversion to rotary work. After the increase in pressure and the pressure drop in this pressure vessel 3 corresponding to the piston piston 25 of the pressure vessel 3 after the piston has been removed, water falls out, which is passed via the bore 26 into the liquid piston pump 25. At the same time, as indicated by arrow C, processed cold water in the cooling device 13 via the corresponding injection port 6 into the pressure vessel 4. When the cold water is sprayed into this pressure vessel 4, the gas contracts and also performs work via the displaceable piston of the corresponding liquid piston pump 25. During this phase, the pressure vessels 1, 2 are at a pressure level corresponding to their balancing pressure. After the transfer of the usable expansion or contraction work of the gas pressure equalization between the pressure vessels 3, 4, wherein at the same time in the pressure vessel 1 cold water and in the pressure vessel 2 warm water is introduced, so that their associated liquid piston pump 25 contraction or Perform expansion work. The timing of the injection of cold water into the pressure vessel 1 is shown by the arrow D and that of the injection of warm water into the pressure vessel 2 by the arrow E.

Das steuerbare Ventil 22 in der Rücklaufleitung 19 ist derart geschaltet, dass es verhindert, dass Wasser in die Druckbehälter 1, 2, 3, 4 gelangt, solange zwischen jeweisl zwei Druckbehältern 1, 2, 3, 4 ein Druckausgleich herrscht.The controllable valve 22 in the return line 19 is connected in such a way that it prevents water from entering the pressure vessels 1, 2, 3, 4 as long as pressure equalization exists between each two pressure vessels 1, 2, 3, 4.

Claims (14)

  1. Assembly for converting thermal energy to motor energy with at least one pressure container (1, 2, 3, 4), which pressure container has at least one upper injection opening (5, 6) for a hot and/or cold fluid, and with a liquid piston pump (25) inside the pressure container (1, 2, 3, 4) which is coupled with a working circuit (8), characterised in that that the pressure container (1, 2, 3, 4) has a horizontal partition (27) provided with a bore (26), with a gas or gas mixture being present above the partition (27) and the liquid piston pump (25) being present underneath the partition (27).
  2. Assembly according to claim 1, characterised in that the bore (26) widens conically in the direction of the gas-filled section of the pressure container (1, 2, 3, 4).
  3. Assembly according to claim 1 or 2, characterised in that a float valve (28) is inserted in the partition (27) with the bore (26) in order to limit the upper level of the liquid piston pump (25).
  4. Assembly according to claim 3, characterised in that the float valve (28) comprises a cage (32) which is screwed into the partition (27) to support a plastic ball (34), with the cage (32) having the cylindrical part (29) of the bore (26).
  5. Assembly according to claim 4, characterised in that the cage (32) supports a shield (35), which is fastened by means of spacer sleeves (36) and extends into the gas-filled or gas mixture-filled area of the pressure container (1, 2, 3, 4).
  6. Assembly according to claim 1, characterised in that the pressure container (1, 2, 3, 4) has a connecting piece (7) at its bottom end for connection with a feed line (17) of the working circuit (8).
  7. Assembly according to claim 6, characterised in that the connecting piece (7) is coupled with a return line (19) of the working circuit (8).
  8. Assembly according to claim 7, characterised in that the return line (19) of the working circuit (8), in particular with the interposition of a controllable valve, is connected with a line that leads to the injection opening (6) for the cold fluid or to a reservoir (15) for the fluid.
  9. Assembly according to one of claims 6 to 8, characterised in that the feed line (17) leads to a turbine (20) from which the return line (19) branches off.
  10. Assembly according to one of claims 6 to 9, characterised in that the feed line (17) is connected to the reservoir (15) via a line.
  11. Assembly according to one of claims 1 to 10, characterised in that a line (14) branches off from the reservoir (15) and branches to a heating device (10) and a cooling device (13) for the fluid with the interposition of valves (11, 37).
  12. Assembly according to claim 11, characterised in that the heating device (10) and cooling device (13) are each coupled with one of the injection openings (5, 6) with the interposition of a controlled valve (5, 6).
  13. Assembly according to one of claims 1 to 12, characterised in that the fluid is water or an organic substance containing pentane, toluene or silicone oil.
  14. Assembly according to one of claims 1 to 13, characterised in that a short-circuit line with at least one controllable valve for equalising the pressure between the pressure containers (1, 2, 3, 4) after the gas has performed its work is provided between each of two pressure containers (1, 2, 3, 4).
EP05700542A 2004-01-24 2005-01-13 System for converting thermal to motive energy Active EP1706601B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004003694A DE102004003694A1 (en) 2004-01-24 2004-01-24 Arrangement for converting thermal into motor energy
PCT/DE2005/000037 WO2005071232A1 (en) 2004-01-24 2005-01-13 System for converting thermal to motive energy

Publications (2)

Publication Number Publication Date
EP1706601A1 EP1706601A1 (en) 2006-10-04
EP1706601B1 true EP1706601B1 (en) 2009-07-15

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Application Number Title Priority Date Filing Date
EP05700542A Active EP1706601B1 (en) 2004-01-24 2005-01-13 System for converting thermal to motive energy

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US (1) US7506509B2 (en)
EP (1) EP1706601B1 (en)
JP (1) JP4625029B2 (en)
CA (1) CA2554204C (en)
DE (2) DE102004003694A1 (en)
NO (1) NO328702B1 (en)
WO (1) WO2005071232A1 (en)

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AT503734B1 (en) * 2006-06-01 2008-11-15 Int Innovations Ltd METHOD FOR CONVERTING THERMAL ENERGY TO MECHANICAL WORK
FR2929381B1 (en) * 2008-04-01 2010-05-14 Centre Nat Rech Scient INSTALLATION FOR THE PRODUCTION OF COLD, HEAT AND / OR WORKING
US20120151924A1 (en) * 2009-08-24 2012-06-21 Ogilvy Renault Llp/S.E.N.C.R.L., S.R.L. Method and system for generating high pressure steam
DE102010005232A1 (en) * 2010-01-21 2011-09-08 Gerhard Stock Arrangement for converting thermal into motor energy
US8800280B2 (en) 2010-04-15 2014-08-12 Gershon Machine Ltd. Generator
AU2011311966A1 (en) * 2010-10-06 2013-02-28 Chevron U.S.A. Inc. Utilization of process heat by-product
US9540963B2 (en) 2011-04-14 2017-01-10 Gershon Machine Ltd. Generator
US10947926B1 (en) * 2019-08-21 2021-03-16 Taiwan Happy Energy Co., Ltd. Devices, systems, and methods for generating power
CN111237021B (en) * 2020-01-13 2022-06-28 北京工业大学 Small-pressure-difference steam direct-driven high-supercharging-ratio working medium pump for organic Rankine cycle
DE102020006494A1 (en) 2020-05-26 2021-12-02 Gerhard Stock Small power plant with external combustion
US11874041B2 (en) * 2020-12-16 2024-01-16 Taiwan Happy Energy Co., Ltd. Pumps, air conditioning systems, and methods for extracting heat

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US3237523A (en) * 1963-10-14 1966-03-01 Globe Hoist Co Low liquid level control valve
US3608311A (en) * 1970-04-17 1971-09-28 John F Roesel Jr Engine
EP0043879A3 (en) 1980-07-16 1982-08-11 Thermal Systems Limited. Reciprocating external-combustion engine and method of operating the same
US5074110A (en) * 1990-10-22 1991-12-24 Satnarine Singh Combustion engine
SE9303680L (en) * 1993-05-25 1994-11-26 Haakan Ingvast Produktutveckli Liquid-cured system with device for degassing the liquid
US5647734A (en) * 1995-06-07 1997-07-15 Milleron; Norman Hydraulic combustion accumulator
DE19909611C1 (en) * 1999-03-05 2000-04-06 Gerhard Stock Gas expander for hot water engine has container with sliding piston and hot and cold water injection nozzle in top
DE10133153C1 (en) * 2001-07-07 2002-07-11 Gerhard Stock Gas expansion units, to convert thermal energy into motor energy as a hot water motor, has closed pressure vessels with injection openings for hot and cold water, and a short circuit pipe between them for pressure compensation

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Publication number Publication date
CA2554204C (en) 2013-10-15
JP4625029B2 (en) 2011-02-02
DE102004003694A1 (en) 2005-11-24
US20080016867A1 (en) 2008-01-24
NO328702B1 (en) 2010-04-26
JP2007518923A (en) 2007-07-12
EP1706601A1 (en) 2006-10-04
US7506509B2 (en) 2009-03-24
DE502005007700D1 (en) 2009-08-27
NO20063317L (en) 2006-08-10
WO2005071232A1 (en) 2005-08-04
CA2554204A1 (en) 2005-08-04

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