EP0724113B1 - Appareil pour refroidir de la vapeur - Google Patents

Appareil pour refroidir de la vapeur Download PDF

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Publication number
EP0724113B1
EP0724113B1 EP95118402A EP95118402A EP0724113B1 EP 0724113 B1 EP0724113 B1 EP 0724113B1 EP 95118402 A EP95118402 A EP 95118402A EP 95118402 A EP95118402 A EP 95118402A EP 0724113 B1 EP0724113 B1 EP 0724113B1
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EP
European Patent Office
Prior art keywords
nozzle
steam
jet
duct
jet pump
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
EP95118402A
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German (de)
English (en)
Other versions
EP0724113A1 (fr
Inventor
Helmut Bälz
G. Dr.-Ing. Ehrhardt
Hans Dipl.-Ing. Hesselbacher
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.)
Helmut Baelz GmbH
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Helmut Baelz GmbH
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.)
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Publication date
Application filed by Helmut Baelz GmbH filed Critical Helmut Baelz GmbH
Publication of EP0724113A1 publication Critical patent/EP0724113A1/fr
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Publication of EP0724113B1 publication Critical patent/EP0724113B1/fr
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Classifications

    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/002—Steam conversion

Definitions

  • Both in heating and in process engineering gases or vapors must be cooled frequently.
  • tense that is, is under a higher pressure as well as having a high temperature that is over 500 degrees Celsius can be.
  • On the side of the heat consumer but often much lower temperatures are desired, so that it is necessary the steam temperature at the heat consumer belittling. This can be done, for example happen that the tense and superheated steam mixed with condensate, with colder steam or with cold water becomes.
  • the superheated steam supply wet steam using a jet pump.
  • the jet pump is with its blowing agent connection to the superheated steam connected and there is a too at their suction connection a conduit leading duct provided.
  • the Jet pump sucks the steam in the steam trap Condensate resulting wet steam, whereby the wet steam in the jet pump with the superheated steam jet mixes.
  • the resulting steam has a reduced temperature, but usually overheats a bit, So it is neither full nor wet.
  • the maximum admixable Amount of wet steam and thus the achievable temperature reduction are due to the amount of condensate and condensate temperature which limits the Determine the evaporation of the condensate.
  • a superheated steam cooler which has a central, with a venturi provided through opening.
  • the Venturi nozzle is a constriction of the otherwise cylindrical one Through opening. From a cylindrical Starting from the section, the free flow cross-section narrows seen abruptly in flow cross-section, then gradually expands and then goes with one Step into a cylindrical area. Sideways that means radial to that defined by the Venturi nozzle Flow direction, a channel leads into the widening Section of the Venturi nozzle and opens at an in Longitudinal section oval or elliptical, on the nozzle wall held injector.
  • a jet pump with axial adjustable regulating cone known, which additionally an Contains water supply channel.
  • the jet pump contains one Driving nozzle with a constriction in which an annular Channel for cooling water opens.
  • the annular channel mouth is fixed on the drive nozzle, while the valve stem is axially adjustable and thus the Air jet cross section more or less releases.
  • Corresponding the pressure conditions also change at the mouth the annular water injection opening.
  • FR-A-829648 From FR-A-829648 is a mixing vessel for steam and Known water carried by or in the steam has been injected.
  • the mixing vessel contains one larger interior, in which one of a steam jet through which the Venturi nozzle is arranged. In the interior there may be a backflow from the venturi outlet train to their entrance.
  • the device serves the Swirling of steam and intense Mixing. A statement about an optimal location of the Water supply is not taken.
  • the hot medium in question in a jet pump is colder Medium, preferably of the same type, added.
  • the jet pump Jet of liquid medium water added in steam systems. In one embodiment, this is in the form in front of the driving nozzle, sprayed jet traversing the capture nozzle. This makes a compared to the known method and devices significantly improved part-load behavior reached. For example, if the heat consumption is on the heat consumer connected to the outlet opening is low, this can be done with a correspondingly small amount, through the propellant nozzle amounts of superheated steam flowing into the devices are covered become.
  • the cooler gas or vaporous medium is from the inflowing superheated steam taken and to the traversing the trap nozzle Beam accelerates.
  • Another major advantage is that with the use as a jet pump mixing device the residual heat contained in the condensate is possible. This evaporates afterwards, giving relatively cool steam and thus a large part of its residual heat.
  • the one setting of heat transfer to the Control range of the device enabling heat consumers is very far. Even if, for example, in one The amount of steam accumulated is insufficient is sufficient to cool a stream of superheated steam can be achieved by increasing the admixture of liquid Temperature can be set.
  • a first option the liquid injection results when the liquid across to the catch nozzle and the mixing channel crossing jet is injected into this. The liquid medium injected transversely to the direction of movement is captured by the gaseous or vaporous jet and accelerated, being atomized.
  • the one with the opening direction arranged transversely to the catch nozzle Injection nozzle preferably has a mouth opening surrounding, inclined to the central axis of the Ring surface on the nozzle. This creates behind the Injector a swirl area that is used to atomize the injected liquid contributes.
  • An improved way of liquid injection is the liquid axially to the propellant nozzle through this into the emerging motive steam jet to inject.
  • the atomization effect becomes immediate here before the mouth of the driving nozzle through the expanding here and accelerating propellant steam or gas jet brought about.
  • For the vaporization of the atomized Liquid is available for the entire length of the mixing channel Available, which makes this embodiment special well suited for extreme part-load operation.
  • the central and axial injection with respect to the driving nozzle of liquid in the motive steam jet can be realized very effectively in a simple way, if a corresponding water supply channel in a Regulation of the steam jet emerging from the motive steam nozzle already existing regulating needle is arranged.
  • the liquid channel can preferably be at its tip flow out so that the liquid is highest at one point Gas or steam velocity emerges.
  • this arrangement of water leakage even when almost closed Propellant steam nozzle completely open so that the water inflow regardless of the axial position of the regulating needle is separately adjustable.
  • One especially for the Partial load advantageous jet pump has a Cross-section preferably ring-shaped channel for returning mixture present at the outlet opening in those limited by the propulsion nozzle and the catch nozzle Aisle gap.
  • the heat consumer station 1 shows a heat consumer station 1, which has a heat consumer 2.
  • the heat consumer station 1 is fed via a steam line 01 and supplied with superheated steam and via a condensate manifold 02 drained.
  • the heat consumer station 1 is a computer-based Control unit 3 is provided, the central PC 4th with a controller 5 based on a microprocessor is connected, the pressure values in the heat consumer station p and temperature values ⁇ recorded, whereupon later The position is dealt with in detail.
  • the PC 4 is with a keyboard 4 T, a monitor 4 M, a printer 4D and an alarm generator 4A and an interface 45 for coupling connected to controller 5.
  • a branch line 6 which has a pressure and temperature sensor 7, to a blowing agent connection 8 one in detail Steam cooling device 10 shown in Figure 2, which as Jet pump is designed.
  • the steam cooling device 10 also has a suction port 12 and an outlet port 14 for chilled steam.
  • the output connector 14 is via a pressure and temperature sensor 15
  • Flow line 16 connected to the heat consumer 2, of those pre-cooled in the steam cooling device 10
  • Also on the condensate line 18 is connected to the regulator 5 Pressure and temperature sensor 19 provided.
  • the lead pipe 16 is connected to the Suction port 12 of the steam cooling device 10 connected.
  • On the shunt line 20 is a measured value to the controller delivering pressure and temperature sensor 21 arranged.
  • the steam cooling device 10 is with a water connection 22 provided via a corresponding line 24 is loaded with water.
  • line 24 is a Temperature sensor 25 arranged, which is connected to the controller 5 is.
  • the steam cooling device is 10 ⁇ m enable adaptation to different load conditions, with an actuator 26 shown in FIG. 2, such as providing a nozzle needle that is connected to the Controller 5 connected electric motor 28 is actuated.
  • the heat consumer station 1 described so far can be adapted to different load cases.
  • the actuator 26 can be operated in such a way that if necessary more or less from the steam line 01 Coming steam reaches the heat consumer 2.
  • the Superheated steam flows through the branch line 6 into the Steam cooling device 10, being from the shunt line 20 sucking in and taking away coming, cooler steam, mixes with this and via the output connection 14 flows out and so via the flow line 16 to the heat consumer 2 arrives.
  • Part of the in the flow line 16 flowing, pre-cooled steam over the Branch line 20 branches, so that over the Suction port 12 and the outlet port 14 of the steam cooler 10, as well as a section of the flow line 16 and the shunt line with a circuit opposite the inflowing amount of superheated steam forms an increased mass flow. This is greater than the mass flow in the branch line 6 and it is also greater than the mass flow in the flow line 16 immediately before the heat consumer 2nd
  • the steam cooling device 10 is shown in detail in FIG. 2 shown. It has a housing 30 which one with the propellant port 8 related steam room 32 encloses.
  • a driving nozzle is located above the steam chamber 32 34 charged with steam, which is a conical, has central nozzle opening 36. The nozzle opening 36 tapers away from the steam chamber 32 Muzzle.
  • the housing 30 is also spaced apart from one another arranged slide guides 38, 40 one than that Control element 26 serving nozzle needle 42 held and axially slidably mounted.
  • the nozzle needle 42 is coaxial arranged to the nozzle opening 36 and towards or adjustable away from this. This movement is from that Electric motor 28 controlled.
  • the nozzle needle 42 Bears on its side facing the nozzle opening 36 the nozzle needle 42 a regulating cone, the dimensions of which and position are dimensioned so that by a corresponding Linear movement of the nozzle needle 42, the nozzle opening 36 fully released, throttled or, if necessary, completely closed can be.
  • the slide guides 38, 40 are aligned with one another arranged on a corresponding housing section 46 and keep the nozzle needle 42 sealed and axially displaceable.
  • the housing section 46 encloses an annular, water supply chamber connected to the water connection 22 48, the outside and against the steam room 32 is sealed. From the water supply chamber 48 lead bores 50 in a provided in the nozzle needle 42 Channel 52 which at the end of the drive nozzle side Nozzle needle 42 in one provided on the regulating cone 44 Spray nozzle opening 54 opens.
  • Both the nozzle needle 42 and the coaxial to it arranged driving nozzle 34 define a longitudinal central axis 56, to which a catch nozzle 58 is arranged coaxially.
  • an elongated hollow cylindrical Mixing channel 62 is provided, which in one frustoconically widening diffuser 64 merges. At the end of the diffuser 64 remote from the driving nozzle 34 the output terminal 14 is provided.
  • the length of the Mixing channel 62 is dimensioned such that the maximum to be injected Amount of water with minimal steam flow and minimum steam temperature on the way through the mixing channel 62 evaporated safely.
  • suction gap 60 opens into one with the suction connection 12 related and otherwise according to externally sealed, annular suction space 66.
  • Hot steam flowing in via the blowing agent connection 8 enters the steam chamber 32 and acts on the propellant nozzle 34.
  • the actuator 36 in a release position stands, as shown in Figure 2, is the Nozzle opening 36 open, so that the standing in the vapor space 32 Steam as a jet at high speed from the Nozzle opening 36 emerges and into the catch nozzle 58 with the flowing mixing channel 62 and diffuser 64.
  • This causes a in the area of the suction gap 60 Vacuum generated, the suction port 12 for suction of colder steam.
  • the water supply chamber 48 and the holes 50 is the in the nozzle needle 42nd provided channel 52 water supplied at the Spray nozzle opening 54 axially to the nozzle opening 36 of the Driving nozzle 34 emerges.
  • the one from the spray nozzle opening 54 escaping water jet is of that at high speed superheated steam flowing through the nozzle opening 36 surrounded, which tears open the water jet and droplets atomized.
  • the hot steam jet settles in its outer area like a coat around the atomized Water jet so that a touch of the relatively cold Water droplets with the heated parts of the catch nozzle 58, the mixing channel 62, the diffuser 64 or other parts the steam cooling device 10 is prevented.
  • To the Output port 14 is double cooled steam, which through water injection until just above its condensation temperature may have cooled down.
  • FIG. 3 Another steam cooling device 10a is shown in FIG. 3 shown, with identical or functionally identical parts without further reference to those related to the steam cooler 10 provided reference numerals already used are supplemented with an "a" for identification purposes are.
  • Deviating from the steam cooling device already described 10 is the steam cooling device 10a Nozzle needle 42a full, that is, formed without an inner channel 52.
  • the regulating cone 44a is also full, that is to say formed and has no outlet openings a cone tip 70. Accordingly, the in Figure 3 shown steam cooling device 10a the water chamber 48.
  • the water connection 22a leads to a spray nozzle 72, the one cylindrical, radial to the longitudinal central axis 56a arranged spray nozzle opening.
  • the spray nozzle opening 74 is approximately midway between the longitudinal central axis 56a and the wall defining the mixing channel 62a arranged so that injected water along the Longitudinal central axis 56a is taken.
  • the spray nozzle 72 is arranged at the end of the mixing channel 62a on the catch nozzle side, so that almost its entire length for formation of the water-steam mixture and for evaporating the water is available.
  • An annular, against the longitudinal central axis 56a inclined plane surface 76 surrounds the Spray nozzle opening 74.
  • the mode of operation of the steam cooling device described so far 10a, for example in a heat consumer station 1 is provided according to Figure 1 corresponds largely the mode of operation described above the steam cooler 10.
  • water across the through the trap nozzle 58a, the mixing channel 62 and the diffuser 64 passing beam injected which consists of pre-mixed steam.
  • This mixture flows through at such a high speed the mixing channel 62a that the injected water easily is atomized even when the driving nozzle 34a is almost is closed and only little high-tension steam emerges from the nozzle opening 36a.
  • the ring surface 76 becomes an additional swirl brought about.
  • a modified heat consumer station 1b is in Figure 4, which, like those related heat consumer station 1 described with FIG. 1, both with a steam cooling device 10, as shown in FIG 2, as well as with a steam cooling device 10a, as shown in Figure 3 is shown, can be equipped. Furthermore for regulation or control is the already explained Control unit 3, not shown, is provided. in the Difference to the heat consumer station already described 1, however, the flow line is not tapped, but as a feed line 16b from the output port 14 the steam cooling device 10 without branching to the heat consumer 2b led.
  • the condensate line 18b leads to a steam trap 80, which via a further condensate line 18b drained into the condensate manifold 02.
  • the steam trap 80 becomes there by post-evaporation steam generated via the shunt line 20b to the suction port 12 of the steam cooling device 10 guided.
  • the via the suction port 12 on the steam trap 80 drastic low pressure and that in the Condensate contained in the steam trap Residual heat leads to re-evaporation of the condensate, so that relatively cool and wet steam to the suction port 12 arrives in the steam cooling device 10 with that of the steam line 01 via the branch line 6b introduced superheated steam mixes.
  • For further cooling water is supplied to this via the water connection 22.
  • This heat consumer station 1 is also in the Partial load operation of a superheated steam jet with a relatively low Mass or volume flow one via the flow line 16b, the heat consumer 2b, the condensate line 18b, the steam trap 80 and the shunt line 20b circulating circuit driven with higher mass throughput.
  • upstream mixing channel 62 is therefore a sufficient for atomizing the injected water Steam flow available.
  • that is enough Speed especially in the extreme partial load range of, for example, only 10% of the maximum inflowing Amount of superheated steam for water evaporation.
  • FIG. 5 is a further heat consumer station 1c shown that an internal steam cooling device 10c Has repatriation.
  • the heat consumer station is 1c regulated by means of the control unit 3, not shown.
  • the steam cooling device 10c has a propellant connection 8c and an output terminal 14c. However a suction connection has been omitted.
  • the propellant connection 8c is directly on via branch line 6c the steam line 01 connected and the output connection 14c lies directly on the heat consumer via the flow line 16c 2c, the direct via the condensate line 18c is connected to the condensate manifold 02 and in this drains.
  • the steam cooling device 10c has a drainage connection 82 on, possibly from within the steam cooler 10 resulting condensate in a steam trap 84 and from this into the condensate manifold 02 can flow off. All of FIGS. 1, 4 and 5 shown heat consumer stations 1, 1b, 1c common Steam cycle is at the heat consumer station 1c located within the steam cooler 10c.
  • the steam cooling device 10c is separate and schematic shown in Figure 6, so far with the steam cooling device There are 10 matching parts, these with those already introduced, recognizable by a c made reference numerals are provided without this are explained again.
  • the steam cooler 10c is one of the output port 14c channel 90 leading to the suction space 66c provided that the diffuser 64c and the mixing channel 62c surrounds.
  • the trap nozzle 58c, the mixing channel 62c and the diffuser 64c are formed by a piece of pipe which is from the Surrounded in cross section circular channel 90 and by means of a bore 92, 94 having intermediate wall in the Housing 30c is held.
  • the channel 90 thus provides one Shunt is the one at the heat consumer station 1 provided (Fig. 1) shunt line 20 replaced.
  • the Catch nozzle 58c and the mixing channel 62c overmix the hot steam flowing in through the nozzle opening 36c Channel 90 recirculated, pre-cooled steam and from the Spray nozzle opening 54c injected into the hot steam jet Water.
  • the suction space 66c is at the condensate outlet connection 82 out over which is located in the suction space 66c or condensate can flow off.
  • the steam cooling devices 10, 10a, 10c have in common that the steam velocity at the points of water injection very large and largely independent of primary steam flow rate. This results in a good control behavior from full load to light load. Furthermore is the steam quality of the cooled steam compared to known steam cooling devices emitted steam significantly improved. As a result of the intensive mixing of Steam and water within the mixing channel 62, 62a, 62b, 62c, the cooled steam is very homogeneous. It will possible to produce saturated or nearly saturated steam, that carries little or no water droplets.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)

Claims (12)

  1. Pompe à jet (10) pour le transport et le refroidissement de fluide gazeux ou sous forme de vapeur, comprenant
    une tuyère motrice (34) susceptible d'être alimentée en fluide sous pression et présentant une ouverture de tuyère (36) pour la production d'un jet de fluide sous forme de vapeur, sortant à vitesse élevée,
    un pointeau de tuyère (42) qui est disposé coaxialement à l'ouverture de tuyère (36) et est réglable dans le sens d'un rapprochement ou d'un éloignement de cette dernière, en vue du réglage de la pompe à jet (10),
    un canal (52) qui est prévu dans le pointeau de tuyère (42), qui débouche à l'extrémité du pointeau (42), côté tuyère motrice, dans une ouverture de tuyère d'injection (54), qui peut être alimenté en fluide liquide se trouvant à une température inférieure à celle du fluide sous forme de vapeur, et qui débouche dans l'espace intérieur,
    une tuyère de reprise (58) disposée en face de la tuyère motrice (34), un canal mélangeur (62) se raccordant à cette tuyère de reprise ainsi qu'un diffuseur (64) pour la reprise et l'écoulement du jet entrant dans la tuyère de reprise (58),
    le canal mélangeur (62) délimitant en direction radiale et la tuyère motrice délimitant en direction axiale un espace intérieur qui peut être parcouru axialement et qui débouche dans une ouverture de sortie (14), et
    un canal d'aspiration (12) qui débouche dans l'espace intérieur dans la zone située entre la tuyère motrice (34) et la tuyère de reprise (58) et par lequel le fluide gazeux ou sous forme de vapeur peut être amené au jet.
  2. Pompe à jet suivant la revendication 1, caractérisée par le fait que le canal mélangeur (62) s'étend, à la suite de la tuyère de reprise (58), sous forme rectiligne sur une longueur et que sa longueur est un multiple du diamètre intérieur de la tuyère de reprise (58).
  3. Pompe à jet suivant la revendication 1, caractérisée par le fait que le canal mélangeur (62) est de conformation cylindrique.
  4. Pompe à jet suivant la revendication 1, caractérisée par le fait que le canal (52) débouche dans l'ouverture de tuyère (36).
  5. Pompe à jet suivant la revendication 1, caractérisée par le fait que le canal (52) débouche en avant de l'ouverture de tuyère (36).
  6. Pompe à jet suivant la revendication 1, caractérisée par le fait que le pointeau de tuyère (42) traverse une chambre d'amenée d'eau (48) susceptible d'être alimentée en eau, dans laquelle il est guidé de façon mobile en translation de façon étanche et à coulissement.
  7. Pompe à jet suivant la revendication 1, caractérisée par le fait qu'elle présente un canal (90) reliant l'ouverture de sortie (14) au canal d'aspiration (12).
  8. Pompe à jet suivant la revendication 7, caractérisée par le fait que le canal (90) présente une section de couronne circulaire et est disposé concentriquement par rapport au canal mélangeur (62) et au diffuseur (64).
  9. Pompe à jet suivant la revendication 1, caractérisée par le fait que le pointeau de tuyère (42) porte un cône de réglage par lequel l'ouverture de tuyère (36) peut être dégagée, partiellement fermée ou en cas de besoin entièrement fermée.
  10. Pompe à jet suivant la revendication 1, caractérisée par le fait que le pointeau de tuyère (42) est réglable à l'aide d'un moteur électrique.
  11. Pompe à jet suivant la revendication 10, caractérisée par le fait que le moteur électrique est commandé par un régulateur (5).
  12. Pompe à jet (10) pour le transport et le refroidissement de fluide gazeux ou sous forme de vapeur, comprenant
    une tuyère motrice (34) susceptible d'être alimentée en fluide sous pression, pour la production d'un jet de fluide sous forme de vapeur, sortant à vitesse élevée,
    une tuyère de reprise (58) disposée en face de la tuyère motrice (34), un canal mélangeur (62) se raccordant à cette tuyère de reprise ainsi qu'un diffuseur (64) pour la reprise et l'écoulement du jet entrant dans la tuyère de reprise (58),
    le canal mélangeur délimitant en direction radiale et la tuyère motrice délimitant en direction axiale un espace annulaire susceptible d'être parcouru axialement et débouchant dans une ouverture de sortie (14),
    un canal d'aspiration (12) qui débouche dans l'espace intérieur dans la zone comprise entre la tuyère motrice (34) et la tuyère de reprise (58) et par lequel le fluide gazeux ou sous forme de vapeur peut être amené au jet, et
    un canal (72) disposé dans un tube (72) qui traverse le canal mélangeur (62), qui est disposé radialement par rapport à la direction de mouvement du jet traversant la tuyère de reprise (58) et qui présente un orifice (74) de section réduite à son extrémité disposée dans l'espace intérieur, le canal (72) pouvant être alimenté en fluide liquide se trouvant à une température inférieure à celle du fluide sous forme de vapeur.
EP95118402A 1995-01-27 1995-11-23 Appareil pour refroidir de la vapeur Expired - Lifetime EP0724113B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19502538A DE19502538C2 (de) 1995-01-27 1995-01-27 Vorrichtung zur Dampfkühlung
DE19502538 1995-01-27

Publications (2)

Publication Number Publication Date
EP0724113A1 EP0724113A1 (fr) 1996-07-31
EP0724113B1 true EP0724113B1 (fr) 1999-01-13

Family

ID=7752455

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95118402A Expired - Lifetime EP0724113B1 (fr) 1995-01-27 1995-11-23 Appareil pour refroidir de la vapeur

Country Status (3)

Country Link
EP (1) EP0724113B1 (fr)
AT (1) ATE175762T1 (fr)
DE (2) DE19502538C2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19882242B4 (de) * 1998-01-23 2010-12-23 Mitsubishi Heavy Industries, Ltd. Gas- und Dampfturbinen-Kraftwerk
DE19830244C2 (de) * 1998-07-07 2000-05-18 Holter Gmbh & Co Einspritzkühler zur Temperaturregelung von überhitztem Dampf
EP1191285A1 (fr) 2000-09-22 2002-03-27 Siemens Aktiengesellschaft Bouclier thérmique , chambre de combustion avec garnissage interne et turbine à gaz

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE421475C (de) * 1924-11-16 1925-11-12 Ernst Koenemann Dr Ing Regelungsvorrichtung fuer Dampfanlagen mit Druckumformung
FR829648A (fr) * 1937-02-27 1938-07-01 Soc Fr Regulateurs Arca Dispositif destiné à assurer le brassage d'un mélange de fluides divers, en particulier de vapeur et d'eau pulvérisée, à l'intérieur d'une capacité telle que le corps d'un surchauffeur à vapeur
US2550683A (en) * 1946-08-17 1951-05-01 Babcock & Wilcox Co Attemperator
DE1833236U (de) * 1958-08-23 1961-06-22 Siemens Ag Dampfumformventil zur reduzierung und kuehlung von hochgespanntem dampf in waermekraftanlagen.
US3134827A (en) * 1959-12-23 1964-05-26 Siemens Ag Steam conversion valve
DE1137037B (de) * 1960-07-05 1962-09-27 C Herbert Zikesch Dipl Ing Vorrichtung zur Drosselung und Kuehlung von Heissdampf
US3981946A (en) * 1974-02-12 1976-09-21 Tokico Ltd. Perforated plate of steam reforming valve

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Publication number Publication date
DE59504810D1 (de) 1999-02-25
DE19502538C2 (de) 1999-04-01
EP0724113A1 (fr) 1996-07-31
DE19502538A1 (de) 1996-08-08
ATE175762T1 (de) 1999-01-15

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