WO1988002087A2

WO1988002087A2 - Continuous steam generator and steam recovery unit

Info

Publication number: WO1988002087A2
Application number: PCT/DE1987/000437
Authority: WO
Inventors: Michael Laumen
Original assignee: Michael Laumen Thermotechnik
Priority date: 1986-09-08
Filing date: 1987-09-07
Publication date: 1988-03-24
Also published as: WO1988002087A3

Abstract

To avoid continually having power and heating peaks required for steam shock effects, for example for steam smoothing irons or automatic ironing machines, use is made of the thermal capacity of a continuous steam generator made from porous sintered metal. 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. In a preferred embodiment, a jet pump is fitted in the steam extraction duct between the steam user and the steam generator, said pump sucking back the unused steam from the environment. On this occasion, 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. In continuous operation, a superheater is installed downstream of the evaporator.

Description

Continuous steam generator and steam recuperator

Steam generators are used in many industrial areas. In addition to the performance-related dimensioning, which varies from 1 kg / h to several t / h, another distinguishing feature for the design of the primary power supply is extremely important. It is the modes of operation that are classified according to continuous or discontinuous steam extraction.

Particularly in the case of discontinuous steam extraction, the construction of a steam generator according to the invention offers considerable advantages over the prior art. In the case of discontinuous operation, the installed power supply of the primary energy supply can be below the value that would be required for the current steam extraction. Conventionally, this is done in such a way that a water supply is overheated in a closed container to such an extent that the Δ t between hot water and the desired steam temperature is so high that sufficient power is provided for the current steam extraction. "However, this has the disadvantage that the hot water container must be designed for the pressure corresponding to the final storage temperature. Such pressure vessels are expensive. According to the invention, this is circumvented by using a heat exchanger in the form of a porous sintered metal.

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. Conventionally, steam is extracted by opening a valve above the steam phase and releasing the hot water, which results in a thermodynamic equilibrium. Here, 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).

According to the invention, steam removal is achieved by metering the water supply via the feed pump in such a way that steam of the desired condition and quantity is made available on the basis of the coordination of the power available and the current power supply. Surprisingly, this results in a pressure that is below the pressure that would occur if the phase change took place at the end temperature of the storage.

Since the water supply only took place when the evaporation valve was open, the water or the working medium passes into the saturated steam area at the appropriate pressure in order to overheat as the sintered metal evaporator continues to flow without any appreciable increase in pressure. During the opening phase, the phase change area moves downstream. It is advantageous here that the storage capacity of the metal can also be used below the evaporation temperature, since the feed water in the parts of the evaporator which are not sufficiently heated for evaporation is sensitively heated. The energy supply through the primary heat exchanger is always switched off when the storage tank end temperature is reached; the connection either when the minimum temperature required for evaporation is reached, in any case when steam is removed. This circuit enables the primary energy exchanger to be designed for the power that would have to be installed for continuous evaporation of the maximum amount of steam demanded per hour.

For the possibility of thermal storage performance, 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 μm, since grain or ball sizes of 250- 500 μm application. In the case of an electrical energy supply in particular, the re-heating can take place at a large Δt, so that fast re-heating times can be achieved.

If the liquid phase of the heat transfer medium remains in the re-heating phase, ie with the steam valve closed, the phase change temperature and the pressure inevitably increase for this portion. This is a systemically desired effect according to the invention since, for example, a spring-loaded overflow valve is installed between the flow-through steam generator and the exhaust steam valve, which leads steam into a filter candle at a preset maximum pressure. This filter candle is also made of porous sintered metal and is used to separate suspended matter and scale from the feed water. The porosity of the filter candle corresponds at most to the pore radius of the evaporator. The filter surface is dimensioned in such a way that the minimum water level ximum amount of water per second can flow. The

The introduction of the steam on the one hand causes backwashing of the filter pores through the steam boost and heating of the candle through condensation of the steam. Heating is important insofar as an increased precipitation of calcium carbonate (scale) can be expected, in particular from a temperature of 62 ° C. The process technology described above has the purpose of reducing deposits in the evaporator, and the chemical treatment of the feed water can at least be reduced.

If there is the possibility of extracting exhaust steam in a targeted manner, 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.

Here, 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

Functional mixing tube remainder whereby the to be added continuously the TTrreeiibbssttrr what to a considerable

Reduced shock losses in the mixing tube.

The sucked steam is carried out on the molds only for increasing the imperature or in the form that the

D

the porous mixing tube is heated to one and only the cooling compressor is

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. For particularly heavy fabric qualities, however, larger amounts of steam, e.g. a maximum of 3 g / s, may be required «

The evaporator block (1) made of highly conductive porous sintered metal is dimensioned so that the evaporation surface and storage capacity are sufficient for the maximum amount of steam with the selected grain size and porosity. If the grain size and pore radius are optimally matched to the working medium to be evaporated, heat transfer coefficients> 70 kW / m2 * K can be used in relation to the outflow surface. The side surfaces of the evaporator (1), which are adjacent to the receptacle (2), are designed in such a way that the amount of heat can be transferred from the radiator (3) which is required to generate the predetermined maximum hourly amount of steam in continuous operation.

In the example these are 2.5 kg corresponding to 0.7 g / s. The required performance is:

sensitive: 4.36 kJ * 2.5 x Δt 115 = 1225 kJ latent: 2.60 kJ * 2.5 = 5400 kJ

6625 kJ

The required power is 1.85 kW. The transfer area can now be determined by specifying a Δ t between the evaporation temperature or the minimum temperature of the sintered metal evaporator and the radiator, or the required storage capacity is first calculated and the required Δ t determined for a given area. An instantaneous output of 3.96 kJ / s is to be achieved for the required feed rate of 1.5 g / s. The storage capacity is 2.11 kJ / h since 1.85 kJ / s can be fed directly. The sintered block of sintered bronze shown by way of example in FIG. 1 has a storage capacity of 0.372 kJ / K, so that a t of 5.67 k must be reduced per second. With a cycle time of 10 s, a storage Δ t of approximately 58 k between the minimum evaporator temperature and the storage end temperature is calculated.

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. For longer cycles or larger amounts of water, the storage Δt 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. For the mass flow of 3.0 g / s specified as the highest limit value, a heat flow of 6.07 kW that can be drawn from the storage must be maintained while maintaining the aforementioned parameters.

For this example, it is worth taking a slightly more differentiated look at the sensitive and latent portion of the performance to be retained. 1.46 kJ / s are required for heating the feed water to the evaporation temperature, and 4.61 kJ / s for the power determining the storage Δt for the evaporation enthalpy. With a fixed memory Δt of 58 K, a memory capacity of 21.6 kJ is calculated, from which a cycle time of 4.68 s is calculated. The charging takes approx. 15.4 s. To achieve larger ones opening times of the steam valve, the storage Δt can be increased, but this further increases the charging time.

In order to achieve the value for 1.5 g / s, a conventional pressurized water tank with a capacity of 0.5 l must be designed for a tank operating pressure of approx. 4 bar for the pressure from 3.0 g / s to 4.7 bar (4.68 s) at a desired 10 s cycle time to approx. 7bar.

In the evaporator (1), which is dimensioned in this way, the water quantity corresponding to the desired amount of steam is passed via a feed line (4) into a distribution chamber (5), and only then when the valve in the evaporation line (6) is open so that the phase change occurs can set low pressure.

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 small design reduces radiation losses to a minimum and significantly reduces losses and heating-up times after decommissioning. The operational readiness for the steam quantity of 0.7 g / s is reached after approx. 30 s, that of the storage tank temperature after approx. 40 s.

The device application described above can of course also be operated with other primary energies. Here, 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. In particular for such continuously operating continuous steam generators, the application variant described below is also advantageous in terms of temperature control and heating-up time in comparison to conventional systems. According to the invention, 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 (receptacle) is preferably made of poorly heat-conducting materials, eg. B. ceramic or carbon, provided no additional external heating is to take place.

Particularly in systems in which high steam temperatures at low pressures are desired, it is appropriate to carry out training in accordance with FIG. 1A.

In this case, a targeted overheating of the steam is aimed at, which offers a thermal separation of the evaporator and superheater. 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). Here, 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.

It is also possible for the evaporator (8) and the

To operate superheater (9) by means of different primary circuits, for example the evaporator by means of an oil burner and / or the condensate circuit and the superheater for the purpose of rapid and precise temperature control by means of electrical heating devices.

It should also be pointed out here that several 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. Especially if you want to do without a water treatment system that is common in conventional technology. Here, 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. In particular in the case of longer interruptions in operation, this blowdown can be preceded by an acid rinse so that calcium carbonate which is already adhering is dissolved. As a result of the chemical reaction, 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.

Regardless of the other arrangement, the evaporator made of porous sintered metal is also suitable for other energy transfer systems for the evaporation of fluids.

In terms of process engineering, 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. Furthermore, 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.

The safety devices prescribed by law in steam boiler construction were not mentioned because the definition of the standards for steam generators of the genus according to the invention are not applicable and these provisions change due to performance, application and region.

Fig. 2 shows the system structure of a continuous steam supply according to the invention without a steam recuperator.

Points 1, 2 and 3 exemplify the discontinuously operating evaporator described above, the receptacle and the heat exchanger for the primary energy supply. (17) identifies a metal casting for better heat dissipation from the heat exchanger (3), which is shown here as an example as an electric heating coil. (18) indicates insulation of the entire heat exchanger- (19) indicates the feed pump! which is connected in parallel with the steam valve (20) via the steam request. (21) characterizes an unpressurized feed water supply can be realized through the water network. (22) identifies a filter cartridge that is preferably made of porous sintered stainless steel. This filter candle has a pore radius which corresponds at most to the pore radius of the evaporator. 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. Depending on the hardness of the untreated feed water, 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.

In larger systems in particular, the filter candle can be additionally heated by means of the condensate return.

Via a temperature sensor (2b), which monitors the temperature of the sintered metal evaporator or alternatively the heating surface temperature, and 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.

Here, 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.

As already mentioned in the calculation example, 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. As a result, a maximum of 23% with steam recovery in open systems. of energy for feed water preparation can be recovered. In the recuperation according to the invention in open systems, 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.

In principle, 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.

In particular, a steam jet compressor according to FIG. 4 is provided as the compressor.

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

Porous sintered metal heat exchanger (37) encased. 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.

However, 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. At constant motive steam conditions, either an increased pressure at the compressor outlet (40) with a reduced mass flow on the suction side or a lowering of the absolute can

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.

In order to achieve a further reduction in the absolute pressure in the outer suction chamber (42), 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. By opening 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.

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).

If 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.

With a recuperation rate of SO%, 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.

In principle, 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.

These are, for example, steam-humidified steam-jet devices for cleaning and disinfection or sterilization, as well as decentralized heating devices on machines for the textile, plastics, paper and food industries. In addition to the precise conditioning of the steam, doing without central steam systems and networks and the resulting increased operational safety are important here.

Furthermore, 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.

INTERNATIONAL APPLICATION PUBLISHED AFTER THE INTERNATIONAL COOPERATION AGREEMENT IN THE PATENT AREA (PCT)

(51) International Patent Classification ⁴ (11) International Publication Number: WO 88/02

F22B 27/14, 1/28, F01K 19/08

A3 F04F 5/46 (43) International

Release DATE: March 24, 1988 (24.0

(21) International file number: PCT / DE87 / 00437 (81) Destination countries: AT (European patent), BE European patent), CH (European patent),

(22) International filing date: (European patent), FR (European patent),

September 7, 1987 (07.09.87) (European patent), IT (European patent), LU (European patent), NL (European patent SE (European patent), US.

(31) Priority reference number: G 8624038.2 U G 86 28 756.7 U Released

With international research report.

(32) Priority dates: September 8, 1986 (September 8, 1986) Before the expiry of the period allowed for changes in claims October 28, 1986 (October 28, 1986). Publication will be repeated if changes occur.

(33) Country of priority: DE

(88) Published date of international research

(71) Applicant (for all destinations except US): As of May 19, 1988 (May 19, 8

CHAEL LAUMEN THERMOTECHNIK [DE / DE]; Krützpoort 16, D-4150 Krefeld (DE).

(72) inventor; and

(75) Inventor / Applicant (for US only): LAUMEN, Michael [DE / DE]; Am Brustert 47, D-4150 Krefeld-Hüls (DE).

(74) Lawyer: KÜHNEN, WACKER &PARTNER;

Schneggstrasse 3-5, P.O.Box 17 29, D-8050 Freising (DE).

(54) Title: CONTINUOUS STEAM GENERATOR AND STEAM RECOVERY UNIT

(54) Designation: CONTINUOUS STEAM GENERATOR AND STEAM RECUPERATOR

(57) Abstract

To avoid continually having power and heating peaks required for steam shock effects, for example for steam smoothing irons or automatic ironing machines, use is made of the thermal capacity of a continuous steam generator made from porous sintered metal. 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. In a preferred embodiment, a jet pump is fϊtted in the steam extraction duct between the steam user and the steam generator, said pump sucking back the un- used steam from the environment. On this occasion, 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. In continuous operation, a superheater is installed downstream of the evaporator.

ONLY FOR THE MFORMAπON

Code used to identify PCT contracting states on the header of the publications that publish international applications under the PCT.

AT Austria FR France MR Mauritania

AU Australia GA Gabon MW Malawi

BB Barbados GB United Kingdom NL Netherlands

BE Belgium HU Hungary NO Norway

BG Bulgaria IT Italy RO Romania

BJ Benin JP Japan SD Sudan

BR Brazil KP Democratic People's Republic of Korea SE Sweden

CF Central African Republic KR Republic of Korea SN Senegal

CG Congo LI Liechtenstein SU Sovϊet Union

CH Switzerland LK Sri Lanka TD Chad

CM Cameroon LU Luxembourg TG Togo

DE Germany, Federal Republic of MC Monaco US United States

DK Denmark MG Madagascar

Fl Finland ML Mali

Claims

1. Continuous-flow steam generator with an evaporator and a heating device characterized in that the evaporator has a block (1; 8) made of porous sintered metal which can be flowed through by the medium to be evaporated.

2. continuous steam generator according to claim 1, characterized gekennzeichnett that the heating device (3; 10) in

Sintered metal is embedded, and that the evaporator (1; 8) from a wall made of a poorly heat-conducting material. B. is coated with carbon.

3. Continuous steam generator according to claim 1 or 2, because by gekennzeichnett that the heating device (3; 10) supplies the evaporator (1; 8) heating energy by means of a magnetic field.

4. continuous steam generator according to claim 1, 2 or 3, characterized in that the heating device (3; 10) has an ultrasonic source so that the evaporator (1; 8) is excited by ultrasound and fluid evaporation can take place below the temperature to the prevailing Heard ambient pressure.

5. Continuous-flow steam generator according to one of the preceding claims, characterized in that the evaporator (8) is followed by a superheater (9) separated by the gas phase, the energy consumption of which supply according to the heating device according to claim 2 and / or claim 3 and / or claim 4 is formed.

6. Continuous steam generator according to one of the preceding claims, characterized in that the volume and thus the heat storage capacity of the block (1; 8) made of porous sintered metal and the maximum heating temperature in the block (1; 8) are selected so that brief bursts of steam can be emitted emitted heat output corresponding to the greater than the continuous heating output of the heating device (3; 10).

7. Continuous steam generator according to one of the preceding claims, characterized in that in the feed water line (4; 13) a blow-down section is provided via which steam and / or flushing water or flushing acid as well as dissolved and / or undissolved evaporation residues can be removed when the steam valve (20) is closed are.

8. Continuous steam generator according to one of the preceding claims, characterized in that an ultrasonic wave source is provided for removing scale deposits «

9. Continuous steam generator according to one of the preceding claims, characterized in that the block (1) is made of porous sintered metal and is used in a sensor (2) made of a good heat-conducting material which is in direct contact with the heating device (3).

10. Steam supply systems characterized in that they consist of several continuous steam generators of claims 1-9

11. Steam supply system for generating brief bursts of steam with a feed water tank (21), a steam generator (1, 2, 3, 4, 5) and a steam outlet valve (20), characterized in that as a steam generator a continuous steam generator according to one of claims 1 to 9 is used.

12. Steam supply system according to claim 11, characterized gekennzeichnett that in the feed water supply line (4) between the feed water tank (21) and steam generator, a filter candle (22) made of porous sintered metal iste which is via a valve (25) lockable steam line (24) on the steam side with the

Steam generator is connected so that the filter candle (22) can be backwashed by means of a steam boost, the filter candle (22) being heated by condensation of the steam.

13. Steam supply system according to claim 11 or 12, characterized in that a jet pump (32) is installed between the steam generator and steam outlet valve (20) which sucks in the steam or condensate.

14. Steam and condensate recuperator in the form of a steam jet pump with a driving nozzle (34), a diffuser (35), a mixing path (36) located between the driving nozzle and diffuser and a suction chamber (42), characterized in that around the mixing section (36) Heat exchanger (37) is arranged.

15. steam and condensate recuperator according to claim 14, characterized gekennzeichnett that the heat exchanger (37) consists at least partially of porous sintered metal.

16. steam and condensate recuperator according to claim 14 or 15, characterized gekennzeichnett that the heat exchanger (37) is tubular and that the driving nozzle (34) and / or the diffuser (35) in the axial direction of the tubular heat exchanger (37) are slidably movable.

17. Steam supply system according to claim 13, characterized gekennzeichnett that the jet pump (32) is a steam and condensate recuperator according to one of claims 14 to 16.

18. The method for operating the steam supply system according to one of claims 11 to 13 or 17, characterized

that the evaporator block (1, 8) made of porous sintered metal is heated to a maximum heating temperature without the medium to be evaporated and

that after reaching the maximum heating temperature, a certain amount of medium to be evaporated is supplied in accordance with the required amount of steam, which evaporates when flowing through the evaporator block (1, 8) and is fed to a steam consumer through the opened steam outlet valve (20).