EP1159512B1 - Gas expansion element provided for a device used to convert thermal energy into motor energy, especially for a hot-water motor - Google Patents

Gas expansion element provided for a device used to convert thermal energy into motor energy, especially for a hot-water motor Download PDF

Info

Publication number
EP1159512B1
EP1159512B1 EP00920368A EP00920368A EP1159512B1 EP 1159512 B1 EP1159512 B1 EP 1159512B1 EP 00920368 A EP00920368 A EP 00920368A EP 00920368 A EP00920368 A EP 00920368A EP 1159512 B1 EP1159512 B1 EP 1159512B1
Authority
EP
European Patent Office
Prior art keywords
water
pressure container
gas expansion
expansion apparatus
hot
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.)
Expired - Lifetime
Application number
EP00920368A
Other languages
German (de)
French (fr)
Other versions
EP1159512A1 (en
Inventor
Gerhard Stock
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1159512A1 publication Critical patent/EP1159512A1/en
Application granted granted Critical
Publication of EP1159512B1 publication Critical patent/EP1159512B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • 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

Definitions

  • the invention relates to a gas expansion element for an arrangement for converting from thermal to motor Energy, especially for a hot water engine from a closed one filled with a gas or a gas mixture Pressure vessel that has a sliding piston is effectively connected to the arrangement and an upper Injection opening for hot water and a lower water drain opening Has.
  • From US-A-4 283 915 is an arrangement for converting thermal known in motor energy, each one Feed for hot water and one for cold water, where a certain temperature difference between the warm and the cold water prevails.
  • the hot and cold water are alternately passed through pipes of a heat exchanger, to expand and contract a working fluid.
  • the working cycle is above a boiling point of the working fluid.
  • Using check valves becomes a relatively high pressure to operate the assembly ensured.
  • the use turns out to be of the heat exchanger as a disadvantage, since such a tube heat exchanger with a large technical effort only has a very limited efficiency and is dependent of the nature of those flowing through and around it Media is relatively susceptible to interference.
  • DE 197 19 190 C2 discloses an arrangement for converting thermal energy into electrical energy a working circuit with a working fluid to drive one Fluid machine and a variety of alternating heat exchangers flowed through by a cold and warm medium consists. There is one in each of the heat exchangers Depending on the temperature of the medium expanding and contracting expansion element arranged, the temperature-related Expansions and contractions over one Buffer memory can be fed to the working cycle. to Every heat exchanger stores a force as a spring trained buffer memory associated with each spring is connected to the piston of a pressure cylinder, the working space each via controllable valves via suction and Pressure lines is connected to a working oil circuit, that drives a turbine with a generator.
  • This arrangement has a relatively complex structure, in particular the buffer storage designed as springs on and includes the disadvantages of a heat exchanger explained above.
  • EP 0 043 879 A1 describes a cylinder Gas expansion element to convert from thermal to known motor energy.
  • a piston slidably mounted.
  • the cylinder points an upper injection opening for hot water and a controllable one lower water drain opening.
  • the hot and cold water each have an injection opening with a spray dog pointing inside the pressure vessel Atomizer nozzle provided.
  • the spray and atomizer nozzle causes a fine distribution of the sprayed warm or Cold water in the pressure vessel and thus a quick penetration of the gas.
  • the separate Ensures injection openings with the assigned atomizing nozzles, that there are no residues when spraying cold water the hot water into the interior of the pressure vessel and Conversely, no residues of the cold water when injecting be introduced by hot water.
  • At least the inner wall of the pressure vessel from a not Heat absorbing material or is with an insulation material coated.
  • the liquid piston pump is expediently each with a Level sensor for an upper and a lower level the water inside the liquid piston pump. To when the upper level is reached, this is done under computer control Injecting the hot water into the pressure vessel, whereupon the gaseous medium in the pressure vessel expands and the level of the water inside the liquid piston pump sinks until the lower level is reached and the assigned level sensor spraying the cold water to contract the gaseous Medium signaled by computer.
  • a check valve is used.
  • the pressure vessel is advantageously funnel-shaped formed the swamp or in the direction of the water drain. This shape favors rapid drainage of the hot or cold water sprayed down.
  • An essentially cylindrical to spherical pressure vessel 1 according to FIG. 1 has an injection opening on its upper side 2, one directed into the interior of the pressure vessel Has spray and atomizer nozzle 3. Via assigned valves 4 can alternately hot water or in the pressure vessel 1 Cold water can be sprayed.
  • the pressure vessel filled with a gas or a gas mixture 1 is in its wall with a displaceable piston 5 connected, the connection to an arrangement 9 for converting thermal energy, especially a hot water engine, manufactures.
  • the pressure vessel 1 is funnel-shaped at its lower section 6 formed in a pressure vessel 1 after below swamp 7 merges with its lower one End has a controllable lower water drain opening 8.
  • the pressure vessel 1 In order to heat the air or other gases of the pressure container 1, becomes hot water directly via the assigned valve 4 and the injection opening 2 via the spray nozzle 3 into the pressure vessel sprayed where there is gas to expand immediately largely permeated.
  • the pressure vessel 1 is at least inside, otherwise insulated so that there is no heat in the material.
  • the inner wall is water-repellent, around the water introduced after cooling quickly to derive down.
  • the air warms up with the spraying of warm water, expands and performs on the sliding piston 5 work, which is a working cycle not shown 20 of the arrangement 9 for converting the thermal energy is fed.
  • the warm water is sprayed so that the heat or cold brought in the water can spread directly in the container. This ensures a high clock frequency (approx. one cycle in one up to three seconds).
  • the amount of water required for heating is very small. It is enough to heat 100 liters of air from 0 ° C to 100 ° C 9.1 kJ in 22 g of water. This is a useful work from 3.6 kJ available (approx. 40% efficiency when using Air).
  • Valves 4 assigned, the one valve 4 via a connecting line 10 with a cooling device 11 for generation of the cold water and the other valve 4 also via one Connection line 10 with a heating device 12 for generation of the hot water is coupled. Both the warm and the cold water enter a separate injection opening 2 each with associated spray and atomizing nozzle 3.
  • the cooling device 11 and the heating device 12 are via a corresponding branching line 13 from one Pump 14 fed, the line 13 with an expansion tank 15 is connected.
  • line 13 is immediate before the cooling device 11 and the heating device 12 a check valve 27, 26 is used, the check valves 27, 26 an outflow of the appropriately tempered Water from the cooling device 11 or the heating device 12 prevent.
  • a check valve 25 between the pump 14 and an inlet 32 of the expansion tank 15 provided to the line 13.
  • the expansion tank 15 protrudes an inlet valve 30 with a corresponding water supply in connection.
  • the expansion tank 15 is a Pressure sensor 31 coupled to the pump 14.
  • the pressure vessel 1 On the underside of the pressure vessel 1 according to FIG. 2 is one arranged with water 16 filled liquid piston pump 17, the on the input side with a water inlet 23 of the working circuit 20 coupled water outlet opening 8 of the pressure vessel 1 and on the output side with a water outlet 33 of the Working circuit 20 is connected.
  • the water 16 in the Liquid piston pump 17 pressurized accordingly and the Level 18 reaches a lower end position by a level sensor 29 is monitored, the end of the spraying phase controls the hot water.
  • the condensate or waste water accumulating in the pressure vessel reaches the working circuit via the liquid piston pump 17 20, which is coupled to the pump 14, which in turn by a corresponding control by the pressure sensor 31 of the Expansion tank 15, the waste water of the cooling device 11, the Heater 12 and the expansion tank 15 supplies.
  • the valves 4, the level sensors, can be used to control the processes 28, 29 of the liquid piston pump 17, the pressure sensor 31 of the expansion tank 17 and / or the pump 14 with a computer, not shown, which is responsible for the injection processes, the level 18 and the pressure monitored and controls the previously listed components accordingly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Nozzles (AREA)
  • Compositions Of Oxide Ceramics (AREA)
  • Motor Or Generator Frames (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Control Of Electric Motors In General (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Glass Compositions (AREA)
  • Carbon And Carbon Compounds (AREA)

Abstract

The invention relates to a gas expansion apparatus which is part of a system for the conversion of thermal energy into motor energy, especially for a hot-water motor.

Description

Die Erfindung bezieht sich auf ein Gasausdehnungselement für eine Anordnung zum Umwandeln von thermischer in motorische Energie, insbesondere für einen Warmwassermotor, bestehend aus einem mit einem Gas oder einem Gasgemisch gefüllten geschlossenen Druckbehälter, der über einen verschiebbaren Kolben mit der Anordnung wirksam verbunden ist und eine obere Einspritzöffnung für Warmwasser sowie eine untere Wasserablauföffnung hat.The invention relates to a gas expansion element for an arrangement for converting from thermal to motor Energy, especially for a hot water engine from a closed one filled with a gas or a gas mixture Pressure vessel that has a sliding piston is effectively connected to the arrangement and an upper Injection opening for hot water and a lower water drain opening Has.

Gase wandeln relativ viel Wärme bei Erhitzung und Ausdehnung in Arbeit um, wobei in schnellen Prozessen, wie etwa dem Stirlingprozess große Einbußen durch Dissipation, ungünstige Kolbensteuerung, Wärme- und Pendelverluste, Totraumeffekte, großen Regeneratorwiderstand und hohe Geschwindigkeiten entstehen.Gases convert relatively much heat when heated and expanded in work around, in quick processes like that Stirling process great losses due to dissipation, unfavorable Piston control, heat and pendulum losses, dead space effects, large regenerator resistance and high speeds arise.

Aus der US-A-4 283 915 ist eine Anordnung zum Umwandeln von thermischer in motorische Energie bekannt, die jeweils eine Einspeisung für Warmwasser und eine für Kaltwasser umfasst, wobei eine bestimmte Temperaturdifferenz zwischen dem Warmund dem Kaltwasser herrscht. Das Warm- und das Kaltwasser werden alternierend durch Rohre eines Wärmetauschers geleitet, um eine Arbeitsflüssigkeit zu expandieren und zu kontraktieren. Der Arbeitszyklus wird oberhalb eines Siedepunktes der Arbeitsflüssigkeit durchgeführt. Mittels Rückschlagventilen wird ein relativ hoher Druck zur Betätigung der Anordnung sichergestellt. Hierbei erweist sich die Verwendung des Wärmetauschers als nachteilig, da ein solcher Rohr-Wärmetauscher bei einem großen technischen Aufwand lediglich einen stark begrenzten Wirkungsgrad aufweist und in Abhängigkeit von der Beschaffenheit der ihn durch- und umströmenden Medien relativ störanfällig ist.From US-A-4 283 915 is an arrangement for converting thermal known in motor energy, each one Feed for hot water and one for cold water, where a certain temperature difference between the warm and the cold water prevails. The hot and cold water are alternately passed through pipes of a heat exchanger, to expand and contract a working fluid. The working cycle is above a boiling point of the working fluid. Using check valves becomes a relatively high pressure to operate the assembly ensured. Here the use turns out to be of the heat exchanger as a disadvantage, since such a tube heat exchanger with a large technical effort only has a very limited efficiency and is dependent of the nature of those flowing through and around it Media is relatively susceptible to interference.

Darüber hinaus offenbart die DE 197 19 190 C2 eine Anordnung zum Umwandeln von thermischer in elektrische Energie, die aus einem Arbeitskreislauf mit einem Arbeitsfluid zum Antrieb einer Strömungsmaschine und aus einer Vielzahl von abwechselnd von einem kalten und warmen Medium durchströmten Wärmetauschern besteht. In den Wärmetauschern ist jeweils ein sich in Abhängigkeit von der Temperatur des Mediums ausdehnendes und zusammenziehendes Ausdehnungselement angeordnet, dessen temperaturbedingten Ausdehnungen und Kontraktionen über einen Puffer-Speicher dem Arbeits-Kreislauf zugeführt werden. Zur Speicherung einer Kraft ist jedem Wärmetauscher ein als Feder ausgebildeter Puffer-Speicher zugeordnet, wobei jede Feder mit dem Kolben eines Druckzylinders verbunden ist, dessen Arbeitsraum jeweils über steuerbare Ventile über Saug- und Druckleitungen mit einem Arbeits-Ölkreislauf verbunden ist, der eine Turbine mit einem Generator antreibt. Diese Anordnung weist einen relativ komplexen Aufbau, insbesondere durch die als Federn ausgeführten Puffer-Speicher auf und umfasst die zuvor erläuterten Nachteile eines Wärmetauschers. In addition, DE 197 19 190 C2 discloses an arrangement for converting thermal energy into electrical energy a working circuit with a working fluid to drive one Fluid machine and a variety of alternating heat exchangers flowed through by a cold and warm medium consists. There is one in each of the heat exchangers Depending on the temperature of the medium expanding and contracting expansion element arranged, the temperature-related Expansions and contractions over one Buffer memory can be fed to the working cycle. to Every heat exchanger stores a force as a spring trained buffer memory associated with each spring is connected to the piston of a pressure cylinder, the working space each via controllable valves via suction and Pressure lines is connected to a working oil circuit, that drives a turbine with a generator. This arrangement has a relatively complex structure, in particular the buffer storage designed as springs on and includes the disadvantages of a heat exchanger explained above.

Ferner ist aus der EP 0 043 879 A1 ein als Zylinder ausgebildetes Gasausdehnungselement zum Umwandeln von thermischer in motorische Energie bekannt. Zur wirksamen Verbindung des Zylinders mit der Anordnung ist in dem mit Luft gefüllten Zylinder ein Kolben verschiebbar gelagert. Der Zylinder weist eine obere Einspritzöffnung für Warmwasser sowie eine steuerbare untere Wasserablauföffnung auf. Furthermore, EP 0 043 879 A1 describes a cylinder Gas expansion element to convert from thermal to known motor energy. For the effective connection of the cylinder with the arrangement is in the air-filled cylinder a piston slidably mounted. The cylinder points an upper injection opening for hot water and a controllable one lower water drain opening.

Es ist Aufgabe der Erfindung, ein Gasausdehnungselement der eingangs genannten Art zu schaffen, mit dem sich bei geringem technischen Aufwand eine relativ große Leistung erzielen lässt.It is an object of the invention to provide a gas expansion element to create the type mentioned, with which at low technical effort to achieve a relatively large performance leaves.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass

  • die untere Wasserablauföffnung am unteren Ende eines den Druckbehälter nach unten überragenden Sumpfes angeordnet ist, der einen wesentlich kleineren Durchmesser als der Druckbehälter hat und
  • der Kolben als Flüssigkolbenpumpe ausgebildet ist, die eingangsseitig mit der Wasserablauföffnung des Druckbehälters, der ein Wasserzulauf eines Arbeitskreislaufes zugeordnet ist, und ausgangsseitig mit einem Wasserablauf des Arbeitskreislaufes verbunden ist.
According to the invention the object is achieved in that
  • the lower water drain opening is arranged at the lower end of a sump projecting downward from the pressure vessel, which has a substantially smaller diameter than the pressure vessel and
  • the piston is designed as a liquid piston pump, which is connected on the input side to the water outlet opening of the pressure vessel, to which a water inlet of a working circuit is assigned, and on the output side is connected to a water outlet of the working circuit.

Durch diese Maßnahmen ist sichergestellt, dass die Ausdehnung und Kontraktion desselben Mediums (Gases) in ein und derselben Kammer des Gasausdehnungselements stattfindet, wodurch das Gasausdehnungselement mit einem geringen technischen Aufwand realisiert ist. Somit beaufschlagt das bei der Zufuhr von Kaltwasser kontraktierende und bei der Zufuhr von Warmwasser expandierende Medium den als Flüssigkolbenpumpe ausgebildeten Kolben, ohne dass Verluste eines Wärmetauschers oder dergleichen auftreten. Hierbei wird zur Erwärmung der Luft bzw. eines anderen Gases im Druckbehälter heißes Wasser direkt in den Druckbehälter gesprüht, wo es das auszudehnende Gas sofort weitestgehend durchdringt. In dem Sumpf, der ein Ausströmen des gasförmigen Mediums aus dem Inneren des Druckbehälters verhindert, wird das Kondensat gesammelt. Durch den relativ geringen Durchmesser des Sumpfes wird bei gleichzeitig relativ großer Länge desselben der Wärmeübergang zwischen dem Inneren des Druckbehälters und einem Ablauf für das Kondensat bzw. dem abfließenden Kondensat selbst vermindert. Darüberhinaus unterliegt die Flüssigkolbenpumpe keinen Reibungsverlusten, wodurch der Wirkungsgrad gegenüber der Verwendung eines in einem Zylinder geführten Kolbens erhöht ist.These measures ensure that the expansion and contraction of the same medium (gas) in one and the same Chamber of the gas expansion element takes place, whereby the gas expansion element with little technical effort is realized. So this affects the supply of cold water contracting and when supplying hot water expanding medium designed as a liquid piston pump Piston without loss of heat exchanger or the like occur. This is used to heat the air or another gas in the pressure vessel hot water directly sprayed into the pressure vessel where it is the most expandable Immediately penetrates the gas as far as possible. In the swamp, the one Outflow of the gaseous medium from the inside of the pressure vessel prevents the condensate from being collected. By the relatively small diameter of the sump is at the same time relatively large length of the same the heat transfer between the inside of the pressure vessel and a drain for the condensate or the draining condensate itself reduced. Furthermore the liquid piston pump is not subject to friction losses, making the efficiency versus use of a piston guided in a cylinder is raised.

Nach einer vorteilhaften Ausgestaltung der Erfindung ist für das Warm- und das Kaltwasser jeweils eine Einspritzöffnung mit einer ins Innere des Druckbehälters gerichteten Sprühund Zerstäuberdüse vorgesehen. Die Sprüh- und Zerstäuberdüse bewirkt eine Feinverteilung des eingesprühten Warm- bzw. Kaltwassers im Druckbehälter und somit eine schnelle Durchdringung des Gases. Darüberhinaus ist durch die separaten Einspritzöffnungen mit den zugeordneten Zerstäuberdüsen sichergestellt, dass beim Einsprühen von Kaltwasser keine Reste des Warmwassers in das Innere des Druckbehälters gelangen und umgekehrt auch keine Reste des Kaltwassers beim Einspritzen von Warmwasser eingeleitet werden.According to an advantageous embodiment of the invention is for the hot and cold water each have an injection opening with a spray dog pointing inside the pressure vessel Atomizer nozzle provided. The spray and atomizer nozzle causes a fine distribution of the sprayed warm or Cold water in the pressure vessel and thus a quick penetration of the gas. In addition, the separate Ensures injection openings with the assigned atomizing nozzles, that there are no residues when spraying cold water the hot water into the interior of the pressure vessel and Conversely, no residues of the cold water when injecting be introduced by hot water.

Um Wärmeverluste weitgehend zu verhindern, besteht bevorzugt mindestens die Innenwand des Druckbehälters aus einem nicht Wärme aufnehmenden Werkstoff oder ist mit einem Isolationsmaterial beschichtet.In order to largely prevent heat loss, there is preference at least the inner wall of the pressure vessel from a not Heat absorbing material or is with an insulation material coated.

Zur relativ schnellen Ableitung des in den Druckbehälter eingesprühten Warm- bzw. Kaltwassers nach unten besteht zweckmäßigerweise die Innenwand des Druckbehälters aus einem wasserabweisenden Werkstoff oder ist mit einem solchen beschichtet. For the relatively quick derivation of the sprayed into the pressure vessel Warm or cold water expediently exists the inner wall of the pressure vessel made of a water-repellent Material or is coated with such.

Zur Steuerung der Einspritzzeit des Warm- oder Kaltwassers, ist zweckmäßigerweise die Flüssigkolbenpumpe jeweils mit einem Niveau-Sensor für einen oberen und einen unteren Pegel des Wassers innerhalb der Flüssigkolbenpumpe versehen. Nach dem Erreichen des oberen Pegels erfolgt rechnergesteuert das Einspritzen des Warmwassers in den Druckbehälter, worauf das gasförmige Medium im Druckbehälter expandiert und der Pegel des Wassers innerhalb der Flüssigkolbenpumpe sinkt, bis der unteren Pegel erreicht ist und der zugeordnete Niveau-Sensor das Einsprühen des Kaltwassers zur Kontraktion des gasförmigen Mediums rechnergesteuert signalisiert.To control the injection time of hot or cold water, the liquid piston pump is expediently each with a Level sensor for an upper and a lower level the water inside the liquid piston pump. To when the upper level is reached, this is done under computer control Injecting the hot water into the pressure vessel, whereupon the gaseous medium in the pressure vessel expands and the level of the water inside the liquid piston pump sinks until the lower level is reached and the assigned level sensor spraying the cold water to contract the gaseous Medium signaled by computer.

Zur Verhinderung eines unerwünschten Druckabfalls sowie zur Vorgabe der Strömungsrichtung in dem Arbeitskreislauf, ist vorzugsweise in den Wasserablauf und den Wasserzulauf jeweils ein Rückschlagventil eingesetzt.To prevent an undesirable pressure drop as well as Specification of the direction of flow in the working circuit is preferably in the water drain and water inlet respectively a check valve is used.

Vorteilhafterweise ist der Druckbehälter trichterförmig in den Sumpf bzw. in Richtung des Wasserablaufs übergehend ausgebildet. Diese Formgebung begünstigt ein schnelles Ableiten des eingesprühten Warm- bzw. Kaltwassers nach unten.The pressure vessel is advantageously funnel-shaped formed the swamp or in the direction of the water drain. This shape favors rapid drainage of the hot or cold water sprayed down.

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, ohne den Rahmen der vorliegenden Erfindung zu verlassen. It is understood that the above and below Features to be explained not only in each case specified combination, but also in other combinations are usable without the scope of the present invention to leave.

Die Erfindung wird im folgenden anhand zweier Ausführungsbeispiele unter Bezugnahme auf die zugehörigen Zeichnungen näher erläutert. Es zeigen:

Fig.1
einen Schnitt durch ein erfindungsgemäßes Gasausdehnungselement mit zugehörigen Komponenten, und
Fig.2
eine alternative Ausführung des Gasausdehnungselementes nach Fig. 1.
The invention is explained in more detail below using two exemplary embodiments with reference to the accompanying drawings. Show it:
Fig.1
a section through an inventive gas expansion element with associated components, and
Fig.2
an alternative embodiment of the gas expansion element of FIG. 1st

Ein im wesentlichen zylinder- bis kugelförmiger Druckbehälter 1 gemäß Fig. 1 hat an seiner Oberseite eine Einspritzöffnung 2, die eine in das Innere des Druckbehälters gerichtete Sprüh- und Zerstäuberdüse 3 aufweist. Über zugeordnete Ventile 4 kann in den Druckbehälter 1 abwechselnd Warmwasser oder Kaltwasser eingesprüht werden.An essentially cylindrical to spherical pressure vessel 1 according to FIG. 1 has an injection opening on its upper side 2, one directed into the interior of the pressure vessel Has spray and atomizer nozzle 3. Via assigned valves 4 can alternately hot water or in the pressure vessel 1 Cold water can be sprayed.

Der mit einem Gas oder einem Gasgemisch gefüllte Druckbehälter 1 ist in seiner Wandung mit einem verschiebbaren Kolben 5 verbunden, der die Verbindung zu einer Anordnung 9 zum Umwandeln der thermischen Energie, insbesondere einem Warmwassermotor, herstellt.The pressure vessel filled with a gas or a gas mixture 1 is in its wall with a displaceable piston 5 connected, the connection to an arrangement 9 for converting thermal energy, especially a hot water engine, manufactures.

Der Druckbehälter 1 ist an seinem unteren Abschnitt 6 trichterförmig ausgebildet, der in einen den Druckbehälter 1 nach unten überragenden Sumpf 7 übergeht, der an seinem unteren Ende eine steuerbare untere Wasserablauföffnung 8 hat.The pressure vessel 1 is funnel-shaped at its lower section 6 formed in a pressure vessel 1 after below swamp 7 merges with its lower one End has a controllable lower water drain opening 8.

Um die Luft bzw. andere Gase des Druckbehälters 1 zu erwärmen, wird heißes Wasser direkt über das zugeordnete Ventil 4 und die Einspritzöffnung 2 über die Sprühdüse 3 in den Druckbehälter eingesprüht, wo es das auszudehnende Gas sofort weitgehend durchdringt. Der Druckbehälter 1 ist mindestens innen, ansonsten ganzwandig so isoliert, dass er keine Wärme im Material aufnimmt. Zudem ist die Innenwand wasserabweisend, um das eingebrachte Wasser nach dem Abkühlen schnell nach unten abzuleiten.In order to heat the air or other gases of the pressure container 1, becomes hot water directly via the assigned valve 4 and the injection opening 2 via the spray nozzle 3 into the pressure vessel sprayed where there is gas to expand immediately largely permeated. The pressure vessel 1 is at least inside, otherwise insulated so that there is no heat in the material. In addition, the inner wall is water-repellent, around the water introduced after cooling quickly to derive down.

Die Luft erwärmt sich mit dem Einsprühen des warmen Wassers, dehnt sich aus und verrichtet über den verschiebbaren Kolben 5 Arbeit, die einem nicht weiter dargestellten Arbeitskreislauf 20 der Anordnung 9 zur Umwandlung der thermischen Energie zugeführt wird. Das Sprühen des warmen Wassers geschieht dabei so, dass die im Wasser mitgebrachte Wärme bzw. Kälte sich unmittelbar im Behälter ausbreiten kann. Dies gewährleistet eine hohe Taktfrequenz (ca. ein Kreisprozess in ein bis drei Sekunden).The air warms up with the spraying of warm water, expands and performs on the sliding piston 5 work, which is a working cycle not shown 20 of the arrangement 9 for converting the thermal energy is fed. The warm water is sprayed so that the heat or cold brought in the water can spread directly in the container. This ensures a high clock frequency (approx. one cycle in one up to three seconds).

Nach dem Druckanstieg und dem nach Kolbendisplazierung entsprechenden Druckabfall im Druckbehälter und nach entsprechender Abkühlung fällt das Wasser aus und setzt sich nach unten im Sumpf 7 ab. Dort lässt die steuerbare untere Wasserablauföffnung 8 rechnergesteuert nur soviel Wasser ab, dass ein Trockenwerden des Sumpfes 7 und damit ein Ausströmen von Gas/Luft vermieden wird. Der Sumpf 7 ist lang und schmal gehalten, damit kein Wärmeübergang in das Abwasser stattfinden kann.After the pressure has risen and after the piston has been deployed Pressure drop in the pressure vessel and after corresponding When the water cools down, it settles down in the swamp 7. The controllable lower water drain opening leaves there 8 computer controlled only so much water that a drying out of the sump 7 and thus an outflow of Gas / air is avoided. The swamp 7 is long and narrow held so that no heat transfer into the waste water takes place can.

Die Menge des zum Aufheizen benötigten Wassers ist sehr gering. So genügen um 100 Liter Luft von 0°C auf 100°C zu erwärmen 9,1 kJ in 22 g Wasser. Dabei wird eine Nutzarbeit von 3,6 kJ verfügbar (ca. 40% Wirkungsgrad bei Verwendung von Luft).The amount of water required for heating is very small. It is enough to heat 100 liters of air from 0 ° C to 100 ° C 9.1 kJ in 22 g of water. This is a useful work from 3.6 kJ available (approx. 40% efficiency when using Air).

Für die Abkühlung und nachfolgende Kontraktion der Luft (Gases) im Druckbehälter 1 wird kaltes Wasser eingesprüht. Es entsteht Unterdruck, so dass der verschiebbare Kolben 5 wieder in die Ausgangsposition zurückgeht. Durch spezielle Gase bzw. Gasgemische kann der Wirkungsgrad gesteigert werden.For cooling and subsequent contraction of the air (gases) cold water is sprayed into pressure vessel 1. It negative pressure is created, so that the displaceable piston 5 again goes back to the starting position. Through special gases or gas mixtures, the efficiency can be increased.

Dem Druckbehälter 1 nach Fig. 2 sind an seiner Oberseite die Ventile 4 zugeordnet, wobei das eine Ventil 4 über eine Verbindungsleitung 10 mit einer Kühleinrichtung 11 zur Erzeugung des Kaltwassers und das andere Ventil 4 ebenfalls über eine Verbindungsleitung 10 mit einer Heizeinrichtung 12 zur Erzeugung des Warmwassers gekoppelt ist. Sowohl das Warm- als auch das Kaltwasser gelangen in eine separate Einspritzöffnung 2 mit jeweils zugeordneter Sprüh- und Zerstäuberdüse 3.2 are on its top Valves 4 assigned, the one valve 4 via a connecting line 10 with a cooling device 11 for generation of the cold water and the other valve 4 also via one Connection line 10 with a heating device 12 for generation of the hot water is coupled. Both the warm and the cold water enter a separate injection opening 2 each with associated spray and atomizing nozzle 3.

Die Kühleinrichtung 11 sowie die Heizeinrichtung 12 werden über eine sich entsprechend verzweigende Leitung 13 von einer Pumpe 14 gespeist, wobei die Leitung 13 mit einem Ausgleichsgefäß 15 verbunden ist. In die Leitung 13 ist jeweils unmittelbar vor der Kühleinrichtung 11 sowie der Heizeinrichtung 12 ein Rückschlagventil 27, 26 eingesetzt, wobei die Rückschlagventile 27, 26 ein Ausströmen des entsprechend temperierten Wassers aus der Kühleinrichtung 11 bzw. der Heizeinrichtung 12 verhindern. Im weiteren ist ein Rückschlagventil 25 zwischen der Pumpe 14 und einem Zulauf 32 des Ausgleichsgefäßes 15 zu der Leitung 13 vorgesehen. Um das gesamte System mit Wasser zu befüllen, steht das Ausgleichsgefäß 15 über ein Zulaufventil 30 mit einer entsprechenden Wasserversorgung in Verbindung. Ferner ist das Ausgleichsgefäß 15 über einen Drucksensor 31 mit der Pumpe 14 gekoppelt.The cooling device 11 and the heating device 12 are via a corresponding branching line 13 from one Pump 14 fed, the line 13 with an expansion tank 15 is connected. In line 13 is immediate before the cooling device 11 and the heating device 12 a check valve 27, 26 is used, the check valves 27, 26 an outflow of the appropriately tempered Water from the cooling device 11 or the heating device 12 prevent. Furthermore there is a check valve 25 between the pump 14 and an inlet 32 of the expansion tank 15 provided to the line 13. To the entire system fill with water, the expansion tank 15 protrudes an inlet valve 30 with a corresponding water supply in connection. Furthermore, the expansion tank 15 is a Pressure sensor 31 coupled to the pump 14.

An der Unterseite des Druckbehälters 1 nach Fig. 2 ist eine mit Wasser 16 gefüllte Flüssigkolbenpumpe 17 angeordnet, die eingangsseitig mit der mit einem Wasserzulauf 23 des Arbeitskreislaufes 20 gekoppelten Wasserablauföffnung 8 des Druckbehälters 1 und ausgangsseitig mit einem Wasserablauf 33 des Arbeitskreislaufes 20 in Verbindung steht. Beim Expandieren des gasförmigen Mediums im Inneren des Druckbehälters 1, also beim Einsprühen von Warmwasser, wird das Wasser 16 in der Flüssigkolbenpumpe 17 entsprechend druckbeaufschlagt und der Pegel 18 gelangt in eine untere Endlage, die von einem Niveau-Sensor 29 überwacht wird, der das Ende der Einsprühphase des Warmwassers steuert. Hierbei wird ein der Wasserablauföffnung 8 zugeordnetes Rückschlagventil 19 geöffnet und der erzeugte Druck pflanzt sich in dem Arbeitskreislauf 20 entsprechend der Richtung des Pfeils 21 fort. Während des Druckaufbaus in dem Arbeitskreislauf 20 ist ein Rückschlagventil 22 in einem zwischen dem Druckbehälter 1 und der Flüssigkolbenpumpe 17 angeordneten Wasserzulauf 23 geschlossen, das zu einem späteren Zeitpunkt, nämlich beim Kontrahieren des gasförmigen Mediums im Inneren des Druckbehälters 1, zur Zuleitung des Mediums 16 in die Flüssigkolbenpumpe 17 und zur Bildung des Arbeitskreislaufes 20 geöffnet wird.On the underside of the pressure vessel 1 according to FIG. 2 is one arranged with water 16 filled liquid piston pump 17, the on the input side with a water inlet 23 of the working circuit 20 coupled water outlet opening 8 of the pressure vessel 1 and on the output side with a water outlet 33 of the Working circuit 20 is connected. When expanding of the gaseous medium inside the pressure vessel 1, that is when spraying hot water, the water 16 in the Liquid piston pump 17 pressurized accordingly and the Level 18 reaches a lower end position by a level sensor 29 is monitored, the end of the spraying phase controls the hot water. This is one of the water drainage opening 8 assigned check valve 19 opened and the generated pressure plants accordingly in the working circuit 20 the direction of arrow 21 continues. During the build-up of pressure In the working circuit 20 is a check valve 22 in a between the pressure vessel 1 and the liquid piston pump 17 arranged water inlet 23 closed that too a later point in time, namely when contracting the gaseous Medium in the interior of the pressure vessel 1, for the supply line of the medium 16 in the liquid piston pump 17 and for formation of the working circuit 20 is opened.

Beim Kontrahieren des gasförmigen Mediums im Inneren des Druckbehälters 1 durch das Einsprühen des Kaltwassers ist das der Wasserablauföffnung 8 zugeordnete Rückschlagventil 19 geschlossen und der Pegel 18 des Mediums 16 der Flüssigkolbenpumpe 17 gelangt in eine obere Endlage, die ebenfalls von einem Niveau-Sensor 28 überwacht wird. Nach einer entsprechenden Signalgebung durch den Niveau-Sensor 28 wird die Einspritzphase des Kaltwassers beendet.When contracting the gaseous medium inside the Pressure vessel 1 by spraying the cold water is that the check valve 19 associated with the water drain opening 8 is closed and the level 18 of the medium 16 of the liquid piston pump 17 reaches an upper end position, which is also from a Level sensor 28 is monitored. After a corresponding Signaling by the level sensor 28 becomes the injection phase of cold water ended.

Während des Durchströmens des Arbeitskreislaufes 20 treibt das Wasser 16 die in den Arbeitskreislauf 20 geschaltete Anordnung 9 zur Umwandlung der thermischen Energie an. Selbstverständlich sind zum Betreiben des Arbeitskreislaufes 20 auch andere flüssige Medien als Wasser 16 einsetzbar.Drives while flowing through the working circuit 20 the water 16 the arrangement in the working circuit 20 9 to convert the thermal energy. Of course are for operating the working cycle 20 liquid media other than water 16 can also be used.

Das in dem Druckbehälter anfallende Kondensat bzw. Abwasser erreicht über die Flüssigkolbenpumpe 17 den Arbeitskreislauf 20, der mit der Pumpe 14 gekoppelt ist, die wiederum durch eine entsprechende Steuerung durch den Drucksensor 31 des Ausgleichsgefäßes 15 das Abwasser der Kühleinrichtung 11, der Heizeinrichtung 12 sowie dem Ausgleichsgefäß 15 zuführt.The condensate or waste water accumulating in the pressure vessel reaches the working circuit via the liquid piston pump 17 20, which is coupled to the pump 14, which in turn by a corresponding control by the pressure sensor 31 of the Expansion tank 15, the waste water of the cooling device 11, the Heater 12 and the expansion tank 15 supplies.

Zur Steuerung der Abläufe können die Ventile 4, die Niveau-Sensoren 28, 29 der Flüssigkolbenpumpe 17, der Drucksensor 31 des Ausgleichsgefäßes 17 und/oder die Pumpe 14 mit einem nicht dargestellten Rechner gekoppelt sein, der die Einspritzvorgänge, den Pegel 18 sowie den Druck überwacht und die zuvor aufgezählten Bauteile entsprechend ansteuert.The valves 4, the level sensors, can be used to control the processes 28, 29 of the liquid piston pump 17, the pressure sensor 31 of the expansion tank 17 and / or the pump 14 with a computer, not shown, which is responsible for the injection processes, the level 18 and the pressure monitored and controls the previously listed components accordingly.

Claims (7)

  1. Gas expansion apparatus for an arrangement (9) for converting thermal energy into motive energy, more especially for a hot-water motor, said apparatus comprising a closed pressure container (1), which is filled with a gas or gas mixture, is operatively connected to the arrangement via a displaceable piston (5) and has an upper injection aperture (2) for hot water and a lower water discharge aperture (8), and the pressure container (1) has an upper injection aperture (2) for cold water, characterised in that
    the lower water discharge aperture (8) is disposed at the lower end of a sump (7), which protrudes downwardly beyond the pressure container (1) and has a substantially smaller diameter than the pressure container (1), and
    the piston (5) is in the form of liquid piston pump (17), which is connected at the inlet end to the water discharge aperture (8) of the pressure container (1), which has a water inflow pipe (23) of a working circuit (20) associated therewith, and is connected at the outlet end to a water outflow pipe (33) of the working circuit (20).
  2. Gas expansion apparatus according to claim 1, characterised in that a respective injection aperture (2), with a spray and atomiser nozzle (3) directed into the interior of the pressure container (1), is provided for the hot and cold water.
  3. Gas expansion apparatus according to claim 1 or 2, characterised in that at least the internal wall of the pressure container (1) is formed from a non-heat-absorbing material or is coated with an insulating material.
  4. Gas expansion apparatus according to one of claims 1 to 3, characterised in that the internal wall of the pressure container (1) is formed from a water-repellent material or is coated with such a material.
  5. Gas expansion apparatus according to claim 1, characterised in that the liquid piston pump (17) is respectively provided with a level sensor (28, 29) for an upper and a lower level (18) of the water inside the liquid piston pump (17).
  6. Gas expansion apparatus according to claim 1, characterised in that a respective non-return valve (19, 22) is inserted into the water outflow pipe (33) and into the water inflow pipe (23).
  7. Gas expansion apparatus according to one of claims 1 to 6, characterised in that the pressure container (1) is funnel-shaped when extending into the sump (7) or respectively in the direction of the water inflow pipe (23).
EP00920368A 1999-03-05 2000-03-04 Gas expansion element provided for a device used to convert thermal energy into motor energy, especially for a hot-water motor Expired - Lifetime EP1159512B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19909611A DE19909611C1 (en) 1999-03-05 1999-03-05 Gas expander for hot water engine has container with sliding piston and hot and cold water injection nozzle in top
DE19909611 1999-03-05
PCT/DE2000/000642 WO2000053898A1 (en) 1999-03-05 2000-03-04 Gas expansion element provided for a device used to convert thermal energy into motor energy, especially for a hot-water motor

Publications (2)

Publication Number Publication Date
EP1159512A1 EP1159512A1 (en) 2001-12-05
EP1159512B1 true EP1159512B1 (en) 2003-10-08

Family

ID=7899758

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00920368A Expired - Lifetime EP1159512B1 (en) 1999-03-05 2000-03-04 Gas expansion element provided for a device used to convert thermal energy into motor energy, especially for a hot-water motor

Country Status (10)

Country Link
US (1) US6564551B1 (en)
EP (1) EP1159512B1 (en)
JP (1) JP2002539351A (en)
AT (1) ATE251713T1 (en)
AU (1) AU4098800A (en)
DE (3) DE19909611C1 (en)
DK (1) DK1159512T3 (en)
ES (1) ES2208307T3 (en)
PT (1) PT1159512E (en)
WO (1) WO2000053898A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005071232A1 (en) * 2004-01-24 2005-08-04 Gerhard Stock System for converting thermal to motive energy

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2376507A (en) * 2001-05-03 2002-12-18 S & C Thermofluids Ltd An engine where the working gases in the cylinder are heated by injection of hot liquid
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
DE10209998B4 (en) * 2002-03-07 2004-04-08 Gerhard Stock Gas expansion element for an arrangement for converting thermal into motor energy
DE10236749A1 (en) * 2002-08-10 2004-02-19 Arnold Berdel Thermodynamically closed-circuit energy conversion process involves temperature of working gas being controlled by mechanical counterpressure acting on this gas
GB0725200D0 (en) * 2007-12-24 2008-01-30 Heptron Ltd Power conversion apparatus
WO2010074616A1 (en) * 2008-12-22 2010-07-01 Exencotech Ab An energy cell
US8096118B2 (en) * 2009-01-30 2012-01-17 Williams Jonathan H Engine for utilizing thermal energy to generate electricity
US8196395B2 (en) 2009-06-29 2012-06-12 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8247915B2 (en) * 2010-03-24 2012-08-21 Lightsail Energy, Inc. Energy storage system utilizing compressed gas
US8436489B2 (en) * 2009-06-29 2013-05-07 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8146354B2 (en) * 2009-06-29 2012-04-03 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
DE102010005232A1 (en) 2010-01-21 2011-09-08 Gerhard Stock Arrangement for converting thermal into motor energy
DE102010022088A1 (en) * 2010-05-31 2011-12-01 Peter Wolf Base load energy storage power plant with process water treatment
KR20130095421A (en) * 2012-02-20 2013-08-28 삼성전자주식회사 Precursor evaporator and method of forming a film using the same
PL240516B1 (en) * 2018-01-09 2022-04-19 Dobrianski Jurij Steam engine
US11125183B1 (en) * 2020-08-04 2021-09-21 Navita Energy, Inc. Effective low temperature differential powered engines, systems, and methods

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3932995A (en) * 1971-04-17 1976-01-20 Milan Pecar System for producing work using a small temperature differential
FR2233871A5 (en) * 1973-06-14 1975-01-10 Mengin Ets Pierre
US4107928A (en) * 1975-08-12 1978-08-22 American Solar King Corporation Thermal energy method and machine
US4283915A (en) 1976-04-14 1981-08-18 David P. McConnell Hydraulic fluid generator
US4545207A (en) * 1978-04-10 1985-10-08 Neary Michael P Solar energy system
EP0043879A3 (en) 1980-07-16 1982-08-11 Thermal Systems Limited. Reciprocating external-combustion engine and method of operating the same
US4748813A (en) * 1985-06-23 1988-06-07 The Board Of Trustees Of The Leland Stanford Junior University Method of operating a thermal engine powered by a chemical reaction
US5074110A (en) * 1990-10-22 1991-12-24 Satnarine Singh Combustion engine
DE19719190C2 (en) 1997-05-08 1999-02-25 Gerhard Stock Hot water motor for converting thermal into electrical energy

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005071232A1 (en) * 2004-01-24 2005-08-04 Gerhard Stock System for converting thermal to motive energy

Also Published As

Publication number Publication date
DE19909611C1 (en) 2000-04-06
JP2002539351A (en) 2002-11-19
PT1159512E (en) 2004-02-27
US6564551B1 (en) 2003-05-20
DK1159512T3 (en) 2004-02-09
DE10080564D2 (en) 2002-02-14
ES2208307T3 (en) 2004-06-16
WO2000053898A1 (en) 2000-09-14
AU4098800A (en) 2000-09-28
ATE251713T1 (en) 2003-10-15
DE50003997D1 (en) 2003-11-13
EP1159512A1 (en) 2001-12-05

Similar Documents

Publication Publication Date Title
EP1159512B1 (en) Gas expansion element provided for a device used to convert thermal energy into motor energy, especially for a hot-water motor
DE102008001308B3 (en) Storage tank for use in e.g. paper factory, has control device guiding fluid flow with higher temperature through outlets or inlets on higher height level and fluid flow with lower temperature through outlets or inlets on lower height level
DE102010005232A1 (en) Arrangement for converting thermal into motor energy
WO2005071232A1 (en) System for converting thermal to motive energy
AT503167B1 (en) Device for converting thermal energy in flowing force and further into motion or electrical energy, has two containers, in which both containers are partly filled with fluid
DE1426698A1 (en) Device for starting up a circulation steam generator
WO2006024182A2 (en) Method and system for controlling a carnot-cycle process
DE10133153C1 (en) 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
EP0152931B1 (en) Method of running a generator-absorption heat pump heating installation for room heating, hot water heating and the like and a generator-absorption heat pump heating installation
WO2012152602A1 (en) Line circuit and method for operating a line circuit for waste-heat utilization of an internal combustion engine
DE9201493U1 (en) Energy-saving combined heat and power
DE2402557A1 (en) Heat-engine operation with low-boiling liquid - which evaporates in working cycle expands in piston engine and is returned to cycle
DE10209998B4 (en) Gas expansion element for an arrangement for converting thermal into motor energy
DE3744487A1 (en) METHOD AND DEVICE FOR CONVEYING BOILABLE LIQUIDS
DE102013013104B4 (en) Heat engine
EP1647768A1 (en) Closed system for feeding back condensate and closed method for feeding back condensate
EP2129975B1 (en) Thermal power plant
EP1146291A1 (en) Method and device for heating sanitary and/or heating water
EP2375027B1 (en) Compensation container for coolant circuits
DE4203438A1 (en) Energy-saving thermal generation plant - has electricity generated by steam engine-generator and IC engine-generator with heat exchange between water and freon cycles
DE10132464B4 (en) Process for the recovery of heat energy from a gaseous medium by means of a heat exchanger
DE29621539U1 (en) Plant for the recovery of heat from the exhaust gases of combustion plants or engines
WO2002009837A1 (en) Device for distilling a medium
DE2512876A1 (en) DEVICE FOR PRODUCING INERT GAS
DE19810978A1 (en) Procedure for multistage heat pumping with heat pumps and heat-carrying fluid emitters in twin chamber cyclones

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20010920

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 50003997

Country of ref document: DE

Date of ref document: 20031113

Kind code of ref document: P

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PA ALDO ROEMPLER

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20040126

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CY

Payment date: 20040220

Year of fee payment: 5

REG Reference to a national code

Ref country code: GR

Ref legal event code: EP

Ref document number: 20040400053

Country of ref document: GR

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20031008

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2208307

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20040709

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IE

Payment date: 20050216

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20050218

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20050221

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20050228

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050304

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050304

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PT

Payment date: 20050304

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20050308

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FI

Payment date: 20050311

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20050314

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20050316

Year of fee payment: 6

Ref country code: LU

Payment date: 20050316

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: MC

Payment date: 20050317

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20050322

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20050331

Year of fee payment: 6

Ref country code: GR

Payment date: 20050331

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20050524

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20050622

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060304

Ref country code: FI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060304

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060304

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060305

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060306

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060306

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060904

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20061001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20061003

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

REG Reference to a national code

Ref country code: PT

Ref legal event code: MM4A

Effective date: 20060904

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20060304

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20061001

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20061130

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20060306

BERE Be: lapsed

Owner name: *STOCK GERHARD

Effective date: 20060331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20061002