EP0724113A1 - Procédé et appareil pour refroidir de la vapeur - Google Patents

Procédé et appareil pour refroidir de la vapeur Download PDF

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Publication number
EP0724113A1
EP0724113A1 EP95118402A EP95118402A EP0724113A1 EP 0724113 A1 EP0724113 A1 EP 0724113A1 EP 95118402 A EP95118402 A EP 95118402A EP 95118402 A EP95118402 A EP 95118402A EP 0724113 A1 EP0724113 A1 EP 0724113A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
jet
steam
channel
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.)
Granted
Application number
EP95118402A
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German (de)
English (en)
Other versions
EP0724113B1 (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
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Publication of EP0724113A1 publication Critical patent/EP0724113A1/fr
Application granted granted Critical
Publication of EP0724113B1 publication Critical patent/EP0724113B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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

  • Gases or vapors often have to be cooled in both heat and process engineering. This is the case, for example, when steam is supplied for heating purposes, which is excited to achieve a high energy density, that is to say is under a higher pressure and has a high temperature which can be above 500 degrees Celsius. On the heat consumer side, however, much lower temperatures are often desired, so that it is necessary to lower the steam temperature at the heat consumer. This can be done, for example, by mixing the strained and superheated steam with condensate, with colder steam or with cold water.
  • the resulting steam has a reduced temperature, although it is usually still a little overheated, so it is neither saturated nor wet.
  • the maximum admixable amount of wet steam and thus the achievable lowering of temperature at the jet pump are limited by the amount of condensate and the condensate temperature that determine the post-evaporation of the condensate.
  • a superheated steam cooler which has a central through opening provided with a Venturi nozzle.
  • the Venturi nozzle represents a constriction of the otherwise cylindrical passage opening.
  • the free flow cross section narrows abruptly in flow cross section, then gradually widens and then changes with a step into a cylindrical area.
  • a channel leads into the widening section of the Venturi nozzle and opens out at an injection nozzle which is oval or elliptical in longitudinal section and held on the nozzle wall.
  • the water emerging from the injection nozzle is finely distributed due to the high flow rate of the steam, whereby it evaporates and cools the steam.
  • the steam speed is noticeably lower and the atomization is restricted. Therefore thermal shocks can occur.
  • the hot medium in question is mixed with colder medium, preferably of the same type, in a jet pump.
  • liquid medium is added to the jet forming in the jet pump, water in steam systems. This is injected into the jet that forms in front of the driving nozzle and traverses the catching nozzle.
  • This method and the mixing device enabling this method have a significantly improved part-load behavior compared to the known methods and devices. If, for example, the heat consumption of a heat consumer connected to the outlet opening is low, this can be covered with correspondingly small amounts of hot steam flowing into the devices through the propellant nozzle.
  • the cooler gaseous or vaporous medium flowing in via the suction channel is carried along by the inflowing superheated steam and accelerated to the jet passing through the collecting nozzle.
  • a sufficient atomization effect is only achieved when the superheated steam flow itself has exceeded a certain lower limit of approximately 50% of the maximum value, the gas or steam flow causing the atomization is so strong even in the extreme part-load range of approximately 10% full load, that the injected liquid is completely atomized, evaporates and cools the gas or vapor stream.
  • Another important advantage is that the mixing device designed as a jet pump makes it possible to use the residual heat contained in the condensate. This evaporates, giving off relatively cool steam and thus a large part of its residual heat.
  • the colder gaseous or vaporous medium to be supplied to the device via the suction channel can be removed from the downstream system at different points. If the steam throughput in the heat consumer in the partial load range is not restricted, the suction channel of the device can be connected to a return line coming from the consumer or to a condensate collection vessel connected to it. However, if the mass flow through the heat consumer is also to be reduced, the suction channel is connected to the flow line leading to the heat consumer and connecting it to the outlet opening. This can be done both by an external pipe connection and within the device itself. In all three cases mentioned, a circular flow of gaseous or vaporous medium at a reduced temperature results from the steam jet, which is reduced in mass flow during part-load operation. The flow leads from the trap nozzle and the mixing duct directly or via the connected heat consumer to the suction duct. The mass flow in this circular flow is significantly higher than that of the motive steam jet emerging from the motive nozzle.
  • the control range of the device that enables the heat transfer to be adjusted to the heat consumer is very wide. Even if the amount of steam generated in a condensate collection vessel, for example, is not sufficient to cool a hot steam stream sufficiently, the desired temperature can be set by an increased admixture of liquid.
  • a first possibility of liquid injection arises when the liquid is injected into the jet at right angles to the jet passing through the collecting nozzle and the mixing channel. The liquid medium injected transversely to the direction of movement is caught and accelerated by the gaseous or vaporous jet, whereby it is atomized.
  • the injection nozzle which is arranged with the opening direction transverse to the catch nozzle, preferably has an annular surface surrounding its mouth opening and inclined to the central axis of the catch nozzle. This creates a swirl area behind the injection nozzle, which contributes to the atomization of the injected liquid.
  • An improved possibility of liquid injection is to inject the liquid axially to the driving nozzle through the latter into the emerging driving steam jet.
  • the atomizing effect is brought about here directly before the mouth of the driving nozzle by the expanding and accelerating driving steam or gas jet.
  • the entire length of the mixing channel is available for the evaporation of the atomized liquid, which makes this embodiment particularly well suited for extreme part-load operation.
  • the central and axial injection of liquid into the motive steam jet with respect to the motive nozzle can be realized very effectively in a simple manner if a corresponding water supply channel is arranged in a regulating needle which is present anyway for regulating the steam jet emerging from the motive steam nozzle.
  • the liquid channel can preferably open at its tip, so that the liquid emerges at a point of the highest gas or vapor velocity.
  • the water outlet is completely open even when the motive steam nozzle is almost closed, so that the water inflow can be adjusted independently of the axial position of the regulating needle.
  • a jet pump which is particularly advantageous for part-load operation, has a preferably cross-sectionally shaped channel for returning mixture present at the outlet opening into the passage gap delimited by the driving nozzle and the catching nozzle.
  • FIG. 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 dewatered via a condensate collecting line 02.
  • a computer-aided control unit 3 is provided, the central PC 4 of which is connected to a controller 5 based on a microprocessor, which detects pressure values p and temperature values ⁇ in the heat consumer station, which will be discussed in more detail later.
  • the PC 4 is connected to a keyboard 4 T, a monitor 4 M, a printer 4D and an alarm device 4A and an interface 45 for coupling to the controller 5.
  • the steam cooling device 10 also has a suction connection 12 and an outlet connection 14 for cooled steam.
  • the output connection 14 is connected via a flow line 16 having a pressure and temperature sensor 15 to the heat consumer 2, which condenses the steam pre-cooled in the steam cooling device 10 and releases it via a condensate line 18 into the condensate manifold as condensate.
  • a pressure and temperature sensor 19 connected to the controller 5 is also provided on the condensate line 18.
  • the flow line 16 is connected to the suction connection 12 of the steam cooling device 10 via a shunt line 20.
  • a pressure and temperature sensor 21 delivering measured values to the controller is arranged on the shunt line 20.
  • the steam cooling device 10 is provided with a water connection 22 which is supplied with water via a corresponding line 24.
  • a Temperature sensor 25 is arranged, which is connected to the controller 5.
  • the steam cooling device 10 is provided with an actuator 26 which can be seen in FIG. 2, such as a nozzle needle, which is actuated by an electric motor 28 connected to the controller 5.
  • the heat consumer station 1 described so far can be adapted to different load cases.
  • the actuator 26 can be actuated via the electric motor 28 in such a way that, if necessary, more or less steam coming from the steam line 01 reaches the heat consumer 2.
  • the superheated steam flows through the branch line 6 into the steam cooling device 10, whereby it draws cooler steam coming from the shunt line 20 and takes it with it, mixes with it and flows out via the outlet connection 14 and thus reaches the heat consumer 2 via the feed line 16.
  • a part of the pre-cooled steam flowing in the feed line 16 is branched off via the bypass line 20, so that a circuit with the inflowing amount of superheated steam flows through the suction connection 12 and the outlet connection 14 of the steam cooling device 10, as well as a section of the feed line 16 and the bypass line 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 2.
  • water is injected via line 24 and water connection 22, which is atomized and thereby evaporates. It absorbs heat, cooling the steam flow, so that steam at a lower temperature is present at the outlet connection 14.
  • the steam can be cooled to the boiling point, so it can be saturated or wet if necessary.
  • the computer unit 3 detects the pressures and temperatures in the heat consumer station 1 with the sensors 7, 15, 19, 21, 25 and regulates the steam cooling device 10 to minimum steam consumption for a given heat requirement at the heat consumer 2.
  • the characteristics of the jet pump are stored in formula or table form in the PC 4, so that according to the measured pressure and temperature values both via the electric motor 28 the inflowing amount of superheated steam as well as regulating elements (not shown in further detail), the amount of water flowing in via line 24 is adjusted.
  • a valve controlled by the regulator 5 can be provided in the shunt line 20, by means of which the recirculated steam quantity can be set.
  • the steam cooling device 10 is shown in detail in FIG. 2. It has a housing 30 which encloses a steam space 32 which is connected to the propellant connection 8. A drive nozzle 34 is acted upon by steam via the steam chamber 32 and has a conical central nozzle opening 36. The nozzle opening 36 tapers to its mouth remote from the vapor space 32.
  • a nozzle needle 42 serving as the regulating member 26 is also held and spaced axially displaceably by means of spaced-apart sliding guides 38, 40.
  • the nozzle needle 42 is arranged coaxially with the nozzle opening 36 and is adjustable towards and away from it. This movement is controlled by the electric motor 28.
  • the nozzle needle 42 On its side facing the nozzle opening 36, the nozzle needle 42 carries a regulating cone, the dimensions and position of which are dimensioned such that the nozzle opening 36 can be completely released, throttled or, if necessary, closed completely by a corresponding linear movement of the nozzle needle 42.
  • the slide guides 38, 40 are arranged in alignment with one another 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 48 which is connected to the water connection 22 and is sealed to the outside and to the steam space 32. Bores 50 lead from the water supply chamber 48 into a channel 52 provided in the nozzle needle 42, which opens at the end of the nozzle needle 42 on the driving nozzle side into a spray nozzle opening 54 provided on the regulating cone 44.
  • Both the nozzle needle 42 and the driving nozzle 34 arranged coaxially thereto define a longitudinal central axis 56 to which a catching nozzle 58 is arranged coaxially.
  • the catching nozzle 58 narrowing like a funnel delimits with the driving nozzle 34 an annular suction gap 60 which is open radially.
  • an elongated hollow cylindrical mixing channel 62 is provided which merges into a diffuser 64 which widens in the shape of a truncated cone.
  • the output connection 14 is provided at the end of the diffuser 64 remote from the driving nozzle 34.
  • the length of the mixing channel 62 is dimensioned such that the maximum amount of water to be injected evaporates safely through the mixing channel 62 with a minimum steam throughput and a minimum steam temperature.
  • the suction gap 60 defined between the driving nozzle 34 and the catching nozzle 58 opens into an annular suction space 66 which is connected to the suction connection 12 and is otherwise sealed off from the outside.
  • the steam cooling device 10 described so far operates in the heat consumer station 1 shown in FIG. 1 as follows: Hot steam flowing in via the blowing agent connection 8 enters the steam chamber 32 and acts on the blowing agent nozzle 34.
  • the actuator 36 When the actuator 36 is in a release position, as shown in FIG. 2, the nozzle opening 36 is open, so that the steam standing in the steam chamber 32 as The jet exits the nozzle opening 36 at high speed and flows into the catching nozzle 58 with the subsequent mixing channel 62 and diffuser 64.
  • a negative pressure is generated in the area of the suction gap 60, which leads to the suction of colder steam via the suction connection 12.
  • the superheated steam emerging from the nozzle opening 36 and the colder steam sucked in via the suction gap 60 mix in the cylindrical mixing channel 62, as a result of which the steam temperature is reduced.
  • water is supplied to the channel 52 provided in the nozzle needle 42, which emerges axially from the spray nozzle opening 54 to the nozzle opening 36 of the driving nozzle 34.
  • the water jet emerging from the spray nozzle opening 54 is surrounded by the superheated steam flowing through the nozzle opening 36 at high speed, which tears open the water jet and atomizes it into droplets.
  • the superheated steam jet wraps around the atomized water jet in its outer area, so that contact 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 of the steam cooling device 10 is prevented.
  • At the outlet connection 14 there is double-cooled steam which can be cooled down to just above its condensation temperature by the water injection.
  • FIG. 3 A further steam cooling device 10a is shown in FIG. 3, parts which are identical in construction or function are provided without further reference with the reference numerals already used in connection with the steam cooling device 10, which are supplemented with an "a" for identification purposes.
  • the nozzle needle 42a in the steam cooling device 10a is full, that is to say it is designed without an inner channel 52.
  • the regulating cone 44a is also full, that is to say is formed without any outlet openings, and has a cone tip 70. Accordingly, the water chamber 48 is omitted in the steam cooling device 10a shown in FIG. 3.
  • the water connection 22a leads to a spray nozzle 72 which has a cylindrical spray nozzle opening arranged radially to the longitudinal central axis 56a.
  • the spray nozzle opening 74 is approximately in the middle between the longitudinal central axis 56a and the wall defining the mixing channel 62a arranged so that injected water is taken along the longitudinal central axis 56a.
  • 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 is available for forming the water-steam mixture and for evaporating the water.
  • An annular flat surface 76 which is arranged at an angle to the longitudinal central axis 56a, surrounds the spray nozzle opening 74.
  • the mode of operation of the steam cooling device 10a described so far which is provided, for example, in a heat consumer station 1 according to FIG. 1, largely corresponds to the mode of operation of the steam cooling device 10 described above the diffuser 64 injected jet, which consists of pre-mixed steam.
  • This mixture flows through the mixing channel 62a at such a high speed that the injected water is easily atomized, even if the driving nozzle 34a is almost closed and only a little high-pressure steam emerges from the nozzle opening 36a. Additional swirling is brought about by the inclination of the annular surface 76.
  • FIG. 4 A modified heat consumer station 1b is shown in FIG. 4, which, like the heat consumer station 1 already described in connection with FIG. 1, has both a steam cooling device 10, as shown in FIG. 2, and a steam cooling device 10a, as shown in FIG. 3 is equipped.
  • the control unit 3 which has already been explained and is not shown, is provided for regulation or control.
  • the feed line is not tapped, but is led as a feed line 16b from the outlet connection 14 of the steam cooling device 10 to the heat consumer 2b without branching.
  • the condensate line 18b leads to a condensate drain 80 which drains into the condensate manifold 02 via a further condensate line 18b.
  • a circuit with a higher mass flow rate is driven by a superheated steam jet with a relatively low mass or volume flow via the supply line 16b, the heat consumer 2b, the condensate line 18b, the condensate drain 80 and the bypass line 20b.
  • a sufficient steam flow for the atomization of the injected water is therefore present in the mixing channel 62 upstream of the outlet connection 14 of the steam cooling device 10.
  • the speed is sufficient for water evaporation, especially in the extreme partial load range of, for example, only 10% of the maximum inflowing superheated steam quantity.
  • FIG. 5 shows a further heat consumer station 1c, which has a steam cooling device 10c with internal recirculation.
  • the heat consumer station 1c is regulated by means of the control unit 3, not shown.
  • the steam cooling device 10c has a propellant connection 8c and an output connection 14c.
  • a suction connection has been dispensed with.
  • the propellant connection 8c is directly connected to the branch line 6c the steam line 01 is connected and the output connection 14c is connected via the flow line 16c directly to the heat consumer 2c, which is connected directly to the condensate collection line 02 via the condensate line 18c and dewatered into the latter.
  • the steam cooling device 10c has a drainage connection 82, from which any condensate that may form inside the steam cooling device 10 can flow into a condensate drain 84 and from there into the condensate collecting line 02.
  • the steam circuit common to all of the heat consumer stations 1, 1b, 1c shown in FIGS. 1, 4b and 5c is located at the heat consumer station 1c within the steam cooling device 10c.
  • the steam cooling device 10c is shown separately and schematically in FIG. 6, parts which correspond to the steam cooling device 10 being provided with the reference symbols already introduced, identified by a c, without these being explained again.
  • a channel 90 is provided which leads from the outlet connection 14c to the suction space 66c and surrounds the diffuser 64c and the mixing channel 62c.
  • the catching nozzle 58c, the mixing channel 62c and the diffuser 64c are formed by a tube piece which is surrounded by the channel 90 which is circular in cross section and is held in the housing 30c by means of an intermediate wall having bores 92, 94.
  • the channel 90 thus represents a shunt which replaces the shunt line 20 provided in the heat consumer station 1 (FIG. 1).
  • the superheated steam flowing in via the nozzle opening 36c mixes with pre-cooled steam recirculated via the channel 90 and water injected into the superheated steam jet from the spray nozzle opening 54c.
  • the suction chamber 66c is led to the condensate outlet connection 82, via which condensate located or formed in the suction chamber 66c can flow off.
  • the steam cooling devices 10, 10a, 10c have in common that the steam speed at the points of water injection is very high and largely independent of the primary steam throughput. This results in good control behavior from full load to low load.
  • the steam quality of the cooled steam is significantly improved compared to steam emitted by known steam cooling devices.
  • the cooled steam is very homogeneous. This makes it possible to generate saturated or nearly saturated steam that carries little or no water drops.

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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)
  • Motor Or Generator Cooling System (AREA)
  • Jet Pumps And Other Pumps (AREA)
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 true EP0724113A1 (fr) 1996-07-31
EP0724113B1 EP0724113B1 (fr) 1999-01-13

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ID=7752455

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

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002025173A1 (fr) 2000-09-22 2002-03-28 Siemens Aktiengesellschaft Brique de protection thermique, chambre de combustion a garniture interieure et turbine a gaz

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2284487C (fr) * 1998-01-23 2004-10-19 Mitsubishi Heavy Industries, Ltd. Centrale electrique a cycle mixte
DE19830244C2 (de) * 1998-07-07 2000-05-18 Holter Gmbh & Co Einspritzkühler zur Temperaturregelung von überhitztem Dampf

Citations (3)

* 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
US3134827A (en) * 1959-12-23 1964-05-26 Siemens Ag Steam conversion valve

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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.
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

Patent Citations (3)

* 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
US3134827A (en) * 1959-12-23 1964-05-26 Siemens Ag Steam conversion valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002025173A1 (fr) 2000-09-22 2002-03-28 Siemens Aktiengesellschaft Brique de protection thermique, chambre de combustion a garniture interieure et turbine a gaz

Also Published As

Publication number Publication date
DE59504810D1 (de) 1999-02-25
ATE175762T1 (de) 1999-01-15
DE19502538C2 (de) 1999-04-01
EP0724113B1 (fr) 1999-01-13
DE19502538A1 (de) 1996-08-08

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