WO1988002087A2 - Generateur de vapeur en continu et recuperateur de vapeur - Google Patents

Generateur de vapeur en continu et recuperateur de vapeur Download PDF

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Publication number
WO1988002087A2
WO1988002087A2 PCT/DE1987/000437 DE8700437W WO8802087A2 WO 1988002087 A2 WO1988002087 A2 WO 1988002087A2 DE 8700437 W DE8700437 W DE 8700437W WO 8802087 A2 WO8802087 A2 WO 8802087A2
Authority
WO
WIPO (PCT)
Prior art keywords
steam
steam generator
continuous
evaporator
sintered metal
Prior art date
Application number
PCT/DE1987/000437
Other languages
German (de)
English (en)
Other versions
WO1988002087A3 (fr
Inventor
Michael Laumen
Original Assignee
Michael Laumen Thermotechnik
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 Michael Laumen Thermotechnik filed Critical Michael Laumen Thermotechnik
Publication of WO1988002087A2 publication Critical patent/WO1988002087A2/fr
Publication of WO1988002087A3 publication Critical patent/WO1988002087A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F04F5/462—Arrangements of nozzles with provisions for cooling the fluid
    • 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
    • F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
    • F01K19/02—Regenerating by compression
    • F01K19/08—Regenerating by compression compression done by injection apparatus, jet blower, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/28—Methods of steam generation characterised by form of heating method in boilers heated electrically
    • F22B1/281—Methods of steam generation characterised by form of heating method in boilers heated electrically other than by electrical resistances or electrodes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/28—Methods of steam generation characterised by form of heating method in boilers heated electrically
    • F22B1/288—Instantaneous electrical steam generators built-up from heat-exchange elements arranged within a confined chamber having heat-retaining walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/18—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes sintered

Definitions

  • This sintered metal body is dimensioned so that an equivalent power reserve is realized based on the specific heat capacity.
  • This is done in the form that the evaporator is heated up sensitively without the liquid phase of the water or heat transfer medium being present in any significant amount.
  • the heating ends at the temperature which corresponds to the amount of energy required for the Evaporation of the amount of water leads that can not be covered by direct heat.
  • the overheating of the vapor phase remaining in the evaporator chamber does not lead to any appreciable pressure rise, since the pressure depends on the temperature at which the phase change takes place.
  • steam is extracted by opening a valve above the steam phase and releasing the hot water, which results in a thermodynamic equilibrium.
  • part of the hot water evaporates so that a larger amount of steam can currently be made available than would be possible by supplying heat to the installed heat exchanger (gradient store).
  • the thermal conductivity of the porous sintered material only plays a subordinate role because the discharge to the steam is only the distance from the center of the ball to the surface of the ball, this distance is systemically only 125-250 ⁇ m, since grain or ball sizes of 250- 500 ⁇ m application.
  • the re-heating can take place at a large ⁇ t, so that fast re-heating times can be achieved.
  • the system can be expanded to include a steam recuperator, which means that very large amounts of energy can be recovered in the form of the enthalpy of vaporization and feed water.
  • the working ability of the steam is used in such a way that by means of at least one jet nozzle and a diffuser, negative pressure is built up in a chamber, the boundary surfaces of which are made of porous sintered metal
  • the sucked steam is carried out on the molds only for increasing the imperature or in the form that the
  • Ereaizbfatt 1 shows an example of a once-through steam generator with electrical heating on a scale of 1: 1 for a steam quantity of 2.5 kg / h saturated steam 135 "C., 3 bar, corresponding to 0.7 g / s.
  • the use as a steam generator for is required for an iron 1.5 g / s for a cycle time of at least 10 s.
  • larger amounts of steam e.g. a maximum of 3 g / s, may be required «
  • the charge time after complete emptying is 4.97 K / s or 11.7 S at the available power of 1.86 kJ / s in order to drive a full load cycle again.
  • the storage ⁇ t can be increased, this is what really matters. whether the exergetic potential of the primary energy source is sufficient and whether other technical limit values e.g. B. maximum temperatures of electric heating elements allow a further temperature increase.
  • a heat flow of 6.07 kW that can be drawn from the storage must be maintained while maintaining the aforementioned parameters.
  • the preferred conical shape of the evaporator particularly when using materials with different coefficients of linear expansion for the evaporator (1) and receptacle (2), ensures good contacting of the interfaces in all temperature ranges.
  • the device application described above can of course also be operated with other primary energies.
  • the heating coil is replaced by a pipe carrying a heating medium and / or the outer wall is used to absorb radiant heat from a burner.
  • the system is particularly suitable for steam generators with continuous operation, where provision of power in the form of stored heat makes no sense, in order to save space and material. Contrary to the previous explanations, such systems should have as little mass as possible in order to reduce standstill losses of such a steam generator to a minimum.
  • the application variant described below is also advantageous in terms of temperature control and heating-up time in comparison to conventional systems.
  • the electrical tube coil or tube carrying the heating medium is also sintered into the evaporator body, so that the heat conduction path to the evaporator surface is shortened.
  • the housing is preferably made of poorly heat-conducting materials, eg. B. ceramic or carbon, provided no additional external heating is to take place.
  • FIG. 1A shows the steam generator (8) made of porous sintered metal, the reheater (9) made of porous sintered metal, the heating device (10) of the steam generator and the heating device (11) of the superheater. Both are surrounded by a water vapor diffusion-tight receptacle (12) and the feed water supply (13) and the steam line (14).
  • the heating devices can be connected via a short-circuit path (15) so that the overheating takes place with the highest temperature of the external circuit.
  • the Satt The steam section (16) can be equipped with droplet separators and can also be designed in the form of a pipeline between the steam generator and the superheater.
  • a modular structure of the boiler is particularly suitable for larger outputs, so that, for example, a superheater (9) could be coupled to a plurality of evaporators (8) to form a supply system.
  • a very inexpensive variant of this design with small amounts of steam consists in that an electric heating cartridge is inserted into a receiving opening provided in the sintered metal body.
  • evaporator bodies can be connected in series to distillation or rectification columns, with a partial stream leaving line (16) in gaseous form and another partial stream in the liquid phase being fed to the next evaporation element.
  • a very simple method of removing calcium carbonates or other solids remaining during evaporation is suitable for the continuously operating steam generators as well as for the discontinuously operating steam generators described above.
  • a backflow preventer is installed in the feed water supply.
  • a valve is installed between this backflow preventer and the inlet into the evaporator. Depending on the time or cycle or due to other indications, this valve is opened with the steam valve closed and the evaporator heated.
  • the vapor phase above the evaporator body now flows through the evaporator body in the opposite direction and sweeps liquid feed water with it. It was experimentally found that such a large amount of scale and other solids can be removed.
  • this blowdown can be preceded by an acid rinse so that calcium carbonate which is already adhering is dissolved.
  • the rinsing liquid takes on a neutral pH value ant so that it can be fed to the drain via the drain valve after the reaction.
  • the evaporator made of porous sintered metal is also suitable for other energy transfer systems for the evaporation of fluids.
  • the first method consists in placing the evaporator and / or the superheater in a magnetic field so that each atom of the sintered spheres is activated as uniformly as possible and the entire heat-exchanging surface has a uniform temperature (electrical eddy current evaporator).
  • This is particularly advantageous for distillation column rectification devices or for disinfection devices with the smallest possible desired temperature gradient or the smallest possible desired control deviation.
  • Another procedural possibility is to excite the evaporator body by ultrasound, so that the vibrations atomize the water, which is already finely distributed in the capillary system.
  • the enthalpy of vaporization can be generated by an energy source below the temperature otherwise required at ambient pressure. This can take place below the ambient temperature, for example, so that a cooling effect also occurs here.
  • the ultrasound excitation can also be used exclusively for eliminating the scale deposition or used to optimize one of the energy transmission systems described above.
  • Fig. 2 shows the system structure of a continuous steam supply according to the invention without a steam recuperator.
  • the filter area is dimensioned so that at the static p of the minimum water level, the amount of water that can be supplied to the evaporator in the same time unit can flow.
  • (23) indicates an increase in price via which the filtered feed water is fed to the pump and exhaust steam is conducted via a line (24) from a pressure relief valve (25) into the interior of the filter candle (22).
  • the valve (25) is set in such a way that it responds briefly after each steam extraction, in order to backwash the filter candle (22) by the burst of steam.
  • the condensing steam simultaneously heats the filter candle.
  • a temperature of> 60 ° C is desirable in order to achieve precipitation, especially of calcium, primarily on the filter candle.
  • the degree of chemical water treatment can be based on the quality of the water, which can be determined on the downstream side of the filter cartridge.
  • (20) indicates a steam passage valve which is opened when steam is requested and essentially serves to ensure that no residual steam flows out during the heating phase and the excess pressure required for filter backwashing can build up.
  • the filter candle can be additionally heated by means of the condensate return.
  • a temperature sensor (2b) which monitors the temperature of the sintered metal evaporator or alternatively the heating surface temperature
  • a controller (27) is used e.g. B. cut off the power supply when the storage tank end temperature is reached switched on when the minimum heating surface temperature is reached.
  • a connection is always made in parallel to the operation of the pump (19) or the valve (20) (steam request) - (28) indicates an analog display for pressure and / or temperature prescribed in the TRD.
  • (21) identifies the power supply for low voltage, (30) a lamp which indicates that it is ready for operation when the minimum heating surface temperature is reached.
  • (31) identifies a manually or motor-operated throttle device for setting the desired amount of water or steam, which can be installed in a bypass line in particular with larger amounts of steam and continuous operation.
  • FIG. 3 shows a plant according to FIG. 2 expanded by a steam recuperator.
  • the steam is conditioned in such a way that sufficient mass flows and pressure ratios are available for the operation of a jet compressor for the given mass flows on the suction side.
  • the ratio of sensitive heat for heating the feed water to the evaporation temperature and the amount of energy necessary for the evaporation is approximately 1: 4.4.
  • a maximum of 23% with steam recovery in open systems. of energy for feed water preparation can be recovered.
  • the maximum recovery rate is approximately 75%, since the steam is not condensed, but can usually be recovered in the state of 1 bar saturated steam or in the wet steam range of 1 bar.
  • the Recuperation takes place in such a way that a steam jet compressor (32) is placed between the evaporator (1) and the exhaust steam valve (20), the suction side of which is connected to a point which ensures the highest possible concentration of steam emitted to the environment.
  • the extracted steam is compressed in the compressor, so that the driving and suction jets are brought to a condition suitable for the consumer on the pressure side.
  • the suction steam can be overheated before entering the suction chamber, so that the suction steam only has to be brought to a desired final pressure in the compressor.
  • a steam jet compressor according to FIG. 4 is provided as the compressor.
  • a line (33) connected to an evaporator Via a line (33) connected to an evaporator, high-tension steam is conducted into a propellant nozzle (34).
  • a diffuser (35) is installed opposite the motive nozzle which receives the mixed jet of motive and suction steam.
  • the usual mixing tube is dispensed with, instead the mixing section (3b) is replaced by one
  • This has the advantage that the sucked-in steam is continuously mixed in over the distance of the driving jet from the nozzle outlet (34) to the diffuser inlet (35).
  • Such a mixing section jacket also has the advantage that the sucked-in steam or the medium can be treated via a heat exchanger (38).
  • 3 means that the steam to be recuperated or the air-steam mixture can be brought to a desired final temperature so that only the work in the compressor The pressure of the superheated suction steam must be increased. This leads to very stable operating conditions in the compressor section, since mixing superheated steam flows is less problematic! than, for example, the suction of wet steam.
  • the arrangement according to the invention offers even more options! which can be used particularly advantageously in the case of larger mass flows and in the discontinuous operation of steam supply and steam recuperation or suction.
  • the negative pressure (suction pressure) building up outside the suction chamber can be influenced in this way! that the distance between the driving nozzle (34) and the diffuser (35) is changed.
  • the horizontal displacement, for example, of the diffuser in the direction of the driving nozzle reduces the volume of the suction surface for the suction steam and the inner suction or mixing chamber in such a way that the diffuser has a piston shape (39) which has the inner surface of the mixing tube heat exchanger (37). made of porous sintered metal.
  • Suction pressure can be achieved at constant pressure at the compressor outlet. This is particularly important in the case of a construction according to the invention according to FIG. 3 if the steam supply and suction are to be decoupled in time for operational requirements. This is done in such a way that a valve (41) is connected upstream of the outer suction chamber (42). This valve (41) is closed and the jet compressor is put into operation in a position of the diffuser according to FIG. 4, so that a large suction-side mass flow can be managed at the starting point! because the large volume the suction chamber or the driving jet section allows the admixture of high suction-side volume flows at a low pressure difference.
  • the volume of the inner suction chamber (3b) or the driving jet path is reduced by retracting the piston (31) in the direction of the driving nozzle (34). This causes a change in the pulse exchange.
  • the process can then be completed! that the diffuser (35) closes the motive steam nozzle outlet (34) and thus the final pressure achieved in the suction chamber (42) can be maintained until the valve (41) opens.
  • the valve (41) due to the pressure difference between the ambient pressure and the suction chamber pressure, the volume of the suction chamber can be extracted up to the pressure equalization regardless of whether the jet compressor is in operation or not.
  • the diffuser In the next cycle of the steam supply, the diffuser is brought back to the starting position and the air-steam mixture in the suction chamber (42) is sucked off and mixed with the supply current after heating in the heat exchanger (37).
  • the condition required here is, for example, 1 kg of saturated steam at 3 bar corresponding to 135 ° C, the energy consumption is 2650 kJ.
  • the energy requirement for the propellant jet is approx. 320 kJ sensitive heat and 1024 kJ latent the amount of heat for the treatment of the recuperated steam 37 kJ, a total of 1351 kJ corresponding to an energy saving of 48% and a fresh water saving of 50%.
  • the connection of the described evaporator according to FIG. 1 with a steam recuperator according to FIG. 4 in a system system according to FIG. 3 has about 50% in open systems. lower investment and space requirements. In discontinuous operation, the connected load can be designed for the maximum hourly output (amount of steam) and has about 50% lower operating costs.
  • the system can also be used for a continuous mode of operation in closed systems, since condensate which can be evaporated again in the heat exchanger of this compressor can just as well be sucked off with the compressor according to FIG. 4.
  • the use of the steam generator in continuously operating steam systems can be seen in the compact design and the very good setting of the desired steam condition, in particular the overheating in low pressure ranges.
  • the small design of the device or the system, which results from the high heat transfer coefficient of the porous sintered metal, can also be used advantageously in other areas of application.
  • the components can be very compact Distillation or rectification device are constructed with the particular advantage that the compressor-evaporator is heated by the heat of condensation of the distillate, which means that after starting up the system there is only an energy requirement for the conditioning of the propellant jet.
  • the sintered metal block (1) is, for example, heated electrically to a maximum predetermined heating temperature and if steam is required, water is fed (4) into the steam generator, said water evaporating on the hot sintered metal pellets and being fed to the user by means of a steam extraction duct (6). No high pressures form in the block (1), since the steam generator is open on the outlet side when the water to be vaporized is inserted. The evaporation of the water inserted therefore takes place at ambient pressure.
  • a jet pump is f ⁇ tted in the steam extraction duct between the steam user and the steam generator, said pump sucking back the un- used steam from the environment.
  • the mixture of steam and air which has been drawn in is treated in a heat exchanger made of porous sintered metal which surrounds the mixing section, depending on the thermal parameters desired for the steam which is to be produced.
  • a superheater is installed downstream of the evaporator.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Energy (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Thermotherapy And Cooling Therapy Devices (AREA)

Abstract

Pour éviter d'avoir en continu les pointes de puissance de chauffage nécessaires aux pointes de vapeur, par ex. pour les fers à repasser à vapeur ou les machines automatiques à repasser, on fait appel à la capacité thermique d'un générateur de vapeur en continu en métal fritté poreux. Le bloc en métal fritté (1) est, par exemple, chauffé électriquement à une température d'échauffement maximale déterminée, et si l'on a besoin de vapeur, on introduit (4) dans le générateur de vapeur de l'eau qui s'évapore sur les grains brûlants du métal fritté et est acheminée au consommateur par l'intermédiaire d'un conduit d'extraction de vapeur (6). Il ne se forme pas de pressions élevées dans le bloc (1), le générateur de vapeur en continu étant ouvert côté sortie lors de l'introduction de l'eau à vaporiser. L'évaporation de l'eau introduite se fait donc à la pression ambiante. Dans une forme d'exécution préférée, une pompe à jet est montée dans le conduit d'extraction de vapeur entre le consommateur de vapeur et le générateur de vapeur, laquelle pompe ré-aspire la vapeur non consommée contenue dans l'environnement. A cette occasion, le mélange vapeur-air ré-aspiré est traité dans un échangeur de chaleur en métal fritté poreux entourant la section de mélange, en fonction des paramètres thermiques souhaités pour la vapeur à produire. En service continu, un surchauffeur est monté en aval de l'évaporateur.
PCT/DE1987/000437 1986-09-08 1987-09-07 Generateur de vapeur en continu et recuperateur de vapeur WO1988002087A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DEG8624038.2U 1986-09-08
DE8624038 1986-09-08
DE8628756 1986-10-28
DEG8628756.7U 1986-10-28

Publications (2)

Publication Number Publication Date
WO1988002087A2 true WO1988002087A2 (fr) 1988-03-24
WO1988002087A3 WO1988002087A3 (fr) 1988-05-19

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Application Number Title Priority Date Filing Date
PCT/DE1987/000437 WO1988002087A2 (fr) 1986-09-08 1987-09-07 Generateur de vapeur en continu et recuperateur de vapeur

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997048947A1 (fr) * 1996-06-18 1997-12-24 Tsp Medical Ab Generateur de vapeur
FR2785975A1 (fr) * 1998-11-17 2000-05-19 Seb Sa Generateur de vapeur a purge rapide
WO2006094324A2 (fr) * 2005-03-11 2006-09-14 Delunamagma Industries Gmbh Moteur a combustion interne comportant une pompe a jet de vapeur servant d'etage de compression
US9631807B2 (en) 2014-09-22 2017-04-25 University Research Glassware Corporation Continuous ultrapure steam generator

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR330901A (fr) * 1903-04-04 1903-08-27 Robert Lucien D Espujols Générateur à vaporisation rapide
FR509135A (fr) * 1920-01-27 1920-11-02 Jean Armand Francois Blanchard Injecteur-récupérateur de vapeur d'échappement
FR558497A (fr) * 1922-11-10 1923-08-28 Chaudière à vapeur à chauffe électrique par courant de haute tension
DE575404C (de) * 1931-06-19 1933-04-27 Siemens Schuckertwerke Akt Ges Dampfkraftanlage
US3048982A (en) * 1960-10-31 1962-08-14 John H Geiger Closed cycle gaseous medium system and method
DE1146602B (de) * 1960-09-26 1963-04-04 Klaus Fischer Periodisch betriebener, mit einer Waerme-speichereinrichtung versehener, elektrisch beheizter Wasserdampferzeuger
US3688083A (en) * 1970-07-31 1972-08-29 Atomic Energy Authority Uk Electric fluid heater
FR2123983A5 (fr) * 1971-02-04 1972-09-15 Castany Ferre Jose
FR2161288A5 (fr) * 1971-11-19 1973-07-06 Snecma
US3781518A (en) * 1972-06-29 1973-12-25 British Oxygen Co Ltd Vacuum pumps
DE2448732A1 (de) * 1974-10-12 1976-06-16 Rinn Manfred Josef Geraet zur herstellung von dampf durch elektrizitaet

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR330901A (fr) * 1903-04-04 1903-08-27 Robert Lucien D Espujols Générateur à vaporisation rapide
FR509135A (fr) * 1920-01-27 1920-11-02 Jean Armand Francois Blanchard Injecteur-récupérateur de vapeur d'échappement
FR558497A (fr) * 1922-11-10 1923-08-28 Chaudière à vapeur à chauffe électrique par courant de haute tension
DE575404C (de) * 1931-06-19 1933-04-27 Siemens Schuckertwerke Akt Ges Dampfkraftanlage
DE1146602B (de) * 1960-09-26 1963-04-04 Klaus Fischer Periodisch betriebener, mit einer Waerme-speichereinrichtung versehener, elektrisch beheizter Wasserdampferzeuger
US3048982A (en) * 1960-10-31 1962-08-14 John H Geiger Closed cycle gaseous medium system and method
US3688083A (en) * 1970-07-31 1972-08-29 Atomic Energy Authority Uk Electric fluid heater
FR2123983A5 (fr) * 1971-02-04 1972-09-15 Castany Ferre Jose
FR2161288A5 (fr) * 1971-11-19 1973-07-06 Snecma
US3781518A (en) * 1972-06-29 1973-12-25 British Oxygen Co Ltd Vacuum pumps
DE2448732A1 (de) * 1974-10-12 1976-06-16 Rinn Manfred Josef Geraet zur herstellung von dampf durch elektrizitaet

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997048947A1 (fr) * 1996-06-18 1997-12-24 Tsp Medical Ab Generateur de vapeur
FR2785975A1 (fr) * 1998-11-17 2000-05-19 Seb Sa Generateur de vapeur a purge rapide
WO2000029787A1 (fr) * 1998-11-17 2000-05-25 Rowenta Werke Gmbh Generateur de vapeur a purge rapide
WO2006094324A2 (fr) * 2005-03-11 2006-09-14 Delunamagma Industries Gmbh Moteur a combustion interne comportant une pompe a jet de vapeur servant d'etage de compression
WO2006094324A3 (fr) * 2005-03-11 2007-02-01 Siegfried Nagel Moteur a combustion interne comportant une pompe a jet de vapeur servant d'etage de compression
US9631807B2 (en) 2014-09-22 2017-04-25 University Research Glassware Corporation Continuous ultrapure steam generator

Also Published As

Publication number Publication date
WO1988002087A3 (fr) 1988-05-19

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