EP2491304B1 - Séparateur cyclonique pour la séparation de phases d'un courant fluidique à plusieurs phases, installation turbine à vapeur dotée d'un séparateur cyclonique et procédé de fonctionnement associé - Google Patents

Séparateur cyclonique pour la séparation de phases d'un courant fluidique à plusieurs phases, installation turbine à vapeur dotée d'un séparateur cyclonique et procédé de fonctionnement associé Download PDF

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Publication number
EP2491304B1
EP2491304B1 EP20100776937 EP10776937A EP2491304B1 EP 2491304 B1 EP2491304 B1 EP 2491304B1 EP 20100776937 EP20100776937 EP 20100776937 EP 10776937 A EP10776937 A EP 10776937A EP 2491304 B1 EP2491304 B1 EP 2491304B1
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EP
European Patent Office
Prior art keywords
condensate
cyclone separator
housing
steam
pressure turbine
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.)
Not-in-force
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EP20100776937
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German (de)
English (en)
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EP2491304A2 (fr
Inventor
Barnaby Bruce
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Areva GmbH
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Areva GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/26—Steam-separating arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C3/00—Apparatus in which the axial direction of the vortex flow following a screw-thread type line remains unchanged ; Devices in which one of the two discharge ducts returns centrally through the vortex chamber, a reverse-flow vortex being prevented by bulkheads in the central discharge duct
    • B04C3/04—Multiple arrangement thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C3/00—Apparatus in which the axial direction of the vortex flow following a screw-thread type line remains unchanged ; Devices in which one of the two discharge ducts returns centrally through the vortex chamber, a reverse-flow vortex being prevented by bulkheads in the central discharge duct
    • B04C3/06—Construction of inlets or outlets to the vortex chamber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C5/00—Apparatus in which the axial direction of the vortex is reversed
    • B04C5/02—Construction of inlets by which the vortex flow is generated, e.g. tangential admission, the fluid flow being forced to follow a downward path by spirally wound bulkheads, or with slightly downwardly-directed tangential admission
    • B04C5/04—Tangential inlets
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C5/00—Apparatus in which the axial direction of the vortex is reversed
    • B04C5/14—Construction of the underflow ducting; Apex constructions; Discharge arrangements ; discharge through sidewall provided with a few slits or perforations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C5/00—Apparatus in which the axial direction of the vortex is reversed
    • B04C5/20—Apparatus in which the axial direction of the vortex is reversed with heating or cooling, e.g. quenching, means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/26—Steam-separating arrangements
    • F22B37/32—Steam-separating arrangements using centrifugal force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/26—Steam-separating arrangements
    • F22B37/32—Steam-separating arrangements using centrifugal force
    • F22B37/327—Steam-separating arrangements using centrifugal force specially adapted for steam generators of nuclear power plants

Definitions

  • the invention relates to a cyclone separator for phase separation of a multiphase fluid flow having a substantially rotationally symmetrical about a central axis designed, enclosing a cavity housing, with at least one supply line for the fluid flow, which is designed for a substantially tangential to the housing interior inflow of the fluid stream, and with at least one discharge line for the separated gaseous portion of the fluid stream.
  • the invention further relates to a steam turbine plant with a high-pressure turbine and a low-pressure turbine and with such a cyclone separator. It also relates to a method for operating such a steam turbine plant.
  • water separators connected in series and reheaters are usually used which can be structurally combined in the manner of a secondary or a series installation (combined water separator / reheater, WaZü for short).
  • the water content of the steam is usually reduced in a first component of the water separator / reheater before the now substantially gaseous portion is passed into a second component in which it is superheated.
  • the thus superheated steam is now introduced into the low-pressure turbine, where it is relaxed and thereby performs work.
  • Various devices can be used to separate the water content. These include, for example, sheets on which the steam flow is passed along.
  • a so-called cyclone separator or cyclone in the essentially rotationally symmetrical housing of which the vapor stream is introduced tangentially to the inner side of the housing.
  • the lighter, substantially gaseous portion flows due to the forming in the cyclone flow conditions in the interior of the housing surrounded cavity and collects there.
  • the gaseous portion of the vapor is now passed into a downstream and structurally / spatially separated second component of the WaZü, in which it is superheated. This is usually achieved by the heating of the steam pipes, which heat the steam by heat transfer accordingly or overheat.
  • US 4263025 discloses a cyclone separator of the prior art.
  • a uniform and homogeneous flow distribution of the steam to be heated when entering the heating phase should be ensured.
  • a method for operating such a steam turbine plant is to be specified.
  • the cavity starting from the center axis in the radial direction having a discharge space with a substantially circular cross-section and then in the order mentioned a heating space, a space, a dryer space and a Inlet space, each having a substantially circular cross-section, wherein the inflow space is bounded to the outside by the housing, wherein the heating chamber for heating the gaseous portion comprises designed heating elements, wherein at least one fine separator and at least one associated condensate catcher are arranged in the dryer space, and wherein the at least one condensate catch pan is connected to at least one condensate drain pipe arranged in the intermediate space through which the condensate forming in the operating state in the at least one fine separator emerges from the condensate drain pipe Cavity is dissipated.
  • the invention is based on the consideration that the comparatively large space requirement of conventional water separators / reheaters inter alia It is based on the fact that the separation of water from the steam originally leaving the high-pressure turbine and the subsequent overheating of the separated gaseous fraction take place one after the other in two spatially separated spatial regions or device components which are arranged one behind the other in the manner of a flow-side series connection. As a result, specific requirements are placed on the structural design of the water separator / reheater, the system requires a relatively large installation space.
  • these two spatial areas do not necessarily have to be arranged structurally in succession in separate rooms. Assuming suitable flow conditions, these spatial regions can also be arranged nested in one single housing, wherein the liquid separation and the superheating of the gaseous fluid fraction for a given volume element of the fluid take place substantially simultaneously or shortly one after the other.
  • Such suitable flow conditions are provided by a cyclone-type water separator. Due to the tangential influx of the inside of the housing of the cyclone takes place by acting on the current centrifugal force, the deposition of the heavy component, such as water, in the outer region of the housing surrounded by the cavity on the inside of the housing.
  • the lighter, gaseous fraction of the original fluid stream for example water vapor, flows into the interior of the cavity. If heating elements for heating or overheating of the gaseous fraction are now arranged in an inner or middle region of the cavity, in particular in a heating chamber, so that the passage of the lighter phase into the inner region is still possible, the gaseous fractions become directly during their passage heated or overheated in the interior.
  • Such a construction is not limited to the treatment of water vapor. It can always be used when one or more phases of heavy particles or constituents are to be separated off from a multicomponent fluid flow, and the light fraction or portions of the original fluid stream are to be heated.
  • a plurality of arranged in the dryer space condensate trap walls are provided, which together form at least approximately a condensate catcher ring, each of the condensate catch pans with an associated, each arranged in the intermediate space condensate drain pipe connected is.
  • each condensate catch basin can be assigned to one or more of the fine separators or dryers. It is also alternatively conceivable to use exactly one annular condensate catch basin in each level or in some of the levels.
  • the preferred number of annularly distributed condensate catch pans and the associated condensate drain pipes and their dimensions may depend on several factors, such as the dimensioning of the housing, the throughput of condensate in the operating state of the cyclone through the condensate drain pipes , as well as the desired Pressure loss that should occur during the flow through the fluid flow through the arrangement of the condensate drain pipes.
  • a first level is provided with a first condensate catcher ring and at least a second level with a second condensate catcher ring, the first condensate catcher ring having a first group of condensate drainpipes and the second condensate Cradle ring is associated with a second group of condensate drainpipes.
  • condensate which forms in the dryers at different locations along the central axis of the housing, flow into the next in the flow direction of the condensate next condensate catcher.
  • the condensate catch pans of the first and second levels can each be arranged in pairs one above the other. Depending on the length of the housing and condensate throughput in the operating state of the cyclone, three or more levels may be provided.
  • the condensate drain pipes are preferably each connected only to a condensate catch pan to ensure a high throughput. In an alternative embodiment, at least some of the condensate drain pipes are connected to more than one condensate catch basin.
  • a longitudinal section of the intermediate space in which both condensate drainage pipes of the first group and condensate drainage pipes of the second group run, these are arranged alternately as viewed in the circumferential direction of the cyclone separator.
  • This longitudinal section of the intermediate space preferably extends over the entire length of the intermediate space, with all condensate drainage pipes being guided over the full length of the housing.
  • the inflow conditions for the gaseous phase of the fluid flow for example the steam to be heated, are the same everywhere along the central axis.
  • some of the condensate drain pipes in certain longitudinal sections serve exclusively the flow guide, while in other longitudinal sections additionally act as a drain for the condensate formed in the fine separators.
  • This type of arrangement can also be generalized to more than two levels, in which case in the circumferential direction, for example, a cyclic arrangement of belonging to the respective groups condensate drain pipes can be done.
  • the condensate drain pipes are advantageously aligned parallel to the central axis, whereby the steam in its flow substantially undergoes a reduction in velocity perpendicular to the central axis of the housing.
  • the respective condensate catch basin is advantageously connected by a supply line with the respective condensate drain pipe.
  • the supply line connects in the manner of an intermediate piece on the flow side, the condensate catch pan with the respective condensate drain pipe, in the operating state, the condensate from the corresponding condensate catcher can flow through the supply line in the condensate drain pipe.
  • the supply line can be connected, for example via a welded connection with the condensate catch basin and / or the condensate drain pipe. It may also be formed as an integral part of the condensate catch basin or the condensate drain pipe.
  • the heating chamber is designed with the heating elements for a flow through the gaseous portion of the fluid stream.
  • it separates the cavity into the areas lying between the inside of the housing and the heating chamber intermediate space, dryer space and inflow space and lying within the boiler room outflow space.
  • a clear separation of the two spatial areas allows optimized separation of the two successive processes. It is particularly advantageous if the portion of the fluid flow flowing into the inflow space has the smallest possible proportion of the heavy component in order to save energy for its heating.
  • the cyclone has exactly two discharge lines, wherein the two discharge lines are connected to the outflow in the direction of the central axis opposite ends of the housing with the outflow.
  • the housing can taper toward one direction, in particular in the direction of the discharge line (flow outlet), in its cross section.
  • a separation of water from a steam / water stream is preferably carried out in a substantially hollow cylindrical housing.
  • the central axis of the housing preferably has a substantially vertical orientation.
  • the heavy component of the fluid flow then moves (flows) down the inside of the housing and can be collected or removed there.
  • a vertical installation of the cyclone separator is advantageous since in this case the force of gravity does not cause any imbalance in the turbulent flow.
  • the steam taken from the high-pressure turbine should be supplied to the low-pressure turbine in the overheated state.
  • the heating elements should be designed with regard to their heating power to overheat the gaseous portion of the fluid stream, in particular water vapor.
  • the most effective use of the device is achieved when the multiphase fluid flow is supplied through multiple supply lines.
  • the supply lines - at least in the region of its housing connection - in a to the center axis of the Housing substantially vertical plane they are advantageously designed such that the velocity vector of the fluid stream flowing into the cavity has a component which points out of this plane.
  • an averaged velocity vector is meant, which is averaged over the individual components of the fluid flow.
  • the fluid flow flows at an angle between 10 ° and 30 °, in particular of about 15 °, to a plane perpendicular to the central axis. That is, the vortex flow which arises as a result of the wall geometry is preferably superimposed on a velocity component in the direction of the central axis, so that overall a helical flow is formed.
  • the velocity component directed in the direction of the center axis advantageously points downwards.
  • the inflowing fluid flow can advantageously be divided in this way into four equal areas of the inside of the housing, without the individual streams meeting and interfering with each other.
  • the flow conditions forming in the housing of the device ensure that the gaseous portion of the fluid flow flows into the interior of the cavity surrounded by the housing. There it flows to the heating elements and is heated or overheated.
  • the direction in which the heating elements are flown can optionally be optimized by guide plates or guide vanes arranged in the inflow space. For example, can be achieved in this way that the heating pipes are flowed substantially frontal, or the tangential component can be reduced.
  • these vanes reduce the inflow space, it should be decided, depending on the application, whether and with what dimensions they are used.
  • the cyclone separator is suitable for both single-stage and multi-stage (intermediate) overheating.
  • two or more groups of heating elements can be arranged one behind the other in the heating chamber perpendicular to the central axis.
  • the heating elements belonging to the individual groups can be designed for different heating outputs or heating temperatures.
  • the heating elements are designed tubular.
  • the heating elements can be flowed through by a fluid heating medium, in particular water vapor.
  • a multi-stage heating can be used, for example, in different groups of heating elements steam with different pressure and / or different temperature.
  • rectilinear pipes are used as heating elements, which are aligned parallel to the central axis of the building.
  • a plurality of tubes can be arranged in the boiler room, which can be designed differently depending on the application.
  • smooth tubes or finned tubes, or favorable combinations of these tube types can be used.
  • the individual tubes are spaced apart from each other such that the unhindered passage of the gaseous phase separated from the fluid flow from the outer inflow space into the inner outflow space can take place through the remaining interspaces.
  • a certain "density" of pipes is required to achieve the desired heating effect.
  • the heating tubes are advantageously combined into tube bundles.
  • so-called ring bundles can be used, in which the tubes are arranged more or less evenly distributed in the boiler room.
  • so-called single bundles can be used.
  • a plurality of mutually adjacent heating elements are combined to form a bundle.
  • the individual bundles can be pre-assembled and can be handled as a whole. in the If necessary, they are easier to assemble, disassemble or exchange than single tubes.
  • the above-mentioned object is achieved according to the invention by connecting the supply line or all supply lines of the above-described separation device to the steam outlet of the high-pressure turbine, and the discharge line or all discharge lines are connected to the steam inlet of the low-pressure turbine.
  • the steam from the high-pressure turbine is introduced into the separation device, in which on the one hand, the water content is separated from the steam and on the other hand, the gaseous portion is overheated.
  • the superheated steam is then introduced into the low-pressure turbine, where it is used for further energy production.
  • the above-mentioned object is achieved according to the invention by passing the vapor emerging from the steam outlet of the high-pressure turbine into a cavity which is surrounded by a housing substantially rotationally symmetrical about a central axis, whereby the steam is set in rotation and its gaseous portion of separated liquid portion and is collected in an inner region of the housing, and wherein the substantially gaseous portion is passed in its passage into the inner region through a fine separator, wherein its liquid portion is further reduced, and then by a ring-shaped arrangement of condensate Exhaust pipes, then heated by heating elements and then fed to the steam inlet of the low-pressure turbine.
  • At least some of the heating elements are tubular, thus forming heating pipes.
  • the live steam generated by a steam generator is directed into at least some of the heating tubes, whereby the gaseous portion of the fluid flow introduced into the separation device is heated or superheated in contact with the outer sides of the heating tubes.
  • the high-pressure turbine bleed steam can be removed, which is then passed into at least some of the heating elements. In this way In particular, a two- or multi-stage overheating of the gaseous portion of the fluid stream can be achieved.
  • the advantages achieved by the invention are in particular that by a clever arrangement of heating elements within a cyclone separator, a separation of a heavy component or a liquid phase of a multi-phase fluid flow with simultaneous heating or overheating of the gaseous portion of the fluid flow in extremely space-saving and material and construction costs can be realized gentle way.
  • the device is particularly suitable for use in systems that must be built in a small space.
  • the installation of fine separators allows a further reduction of the heavy component.
  • the arrangement of the condensate drain pipes in an annular space between the fine separators and the heating elements is achieved by a targeted pressure loss optimized flow distribution. This leads to a further saving of material, since due to the dual function of the condensate drain pipes on pinhole or similar components (as far as possible) can be dispensed with.
  • a steam turbine plant in which such a separation device is connected between a high-pressure turbine and low-pressure turbine, can be realized in a particularly compact and material-saving design.
  • the device can be mounted substantially in a vertically positioned housing directly under the high-pressure turbine, so that the gas from the steam outlet of the high-pressure turbine at the upper end of the housing can flow into the device. Through discharge lines at the bottom and / or top of the housing then the superheated steam of the low-pressure turbine can be supplied.
  • the in Fig. 1 shown cyclone separator 1 for phase separation of a multi-phase fluid flow comprises a substantially around a central axis M rotationally symmetrical and hollow cylindrical designed housing 2, which encloses a cavity 3 and in the four supply lines 6 are embedded.
  • the left and right correspond respectively the right half of the Fig. 1 a possible embodiment of the cyclone, wherein in reality both halves are realized in one of the two ways shown here.
  • the housing 2 with a substantially vertically aligned central axis M in a preferred embodiment has a diameter of about 6 meters.
  • the multiphase fluid flow (not shown) flows in the inflow direction 10 substantially tangentially to the housing inner side 11 in the cavity 3 surrounded by the housing 2.
  • the fluid flow may be, for example, steam which is conducted from the steam outlet of a high-pressure turbine installed in a steam turbine plant through the supply lines 6 into the housing 2 of the cyclone separator 1.
  • the housing 2 is preferably made of steel or stainless steel, and depending on the field of application, other materials may be advantageous.
  • the fluid flow is thereby set in rotation, wherein the force acting on the fluid flow centrifugal force pulls the heavy component of the fluid flow, in this case water, to the outside of the housing inner side 11.
  • the gaseous portion of the fluid flow moves due to the forming in the cavity 3 flow conditions of an inflow 12 through a dryer room 13 and a gap 15 in a heating chamber 14.
  • the annular cross-shaped heating chamber 14 includes a lying inside the housing 2 cylindrical outflow space 16 spatially one.
  • FIG Fig. 2 The spatial arrangement (going radially outward from the central axis M) of the outflow space 16, the heating space 14, the intermediate space 15, the dryer space 13 and the inflow space 12 is in FIG Fig. 2 illustrated schematically. While the outflow chamber 16 is cylindrically shaped, the spaces lying farther out in the housing 2 to a certain extent form shells, each with an annular cross-section. Their imaginary inner and outer cross-sectional boundaries form concentric circles whose common center lies on the central axis M.
  • heating elements which in terms of their heating power to overheat the gaseous Portion of the fluid flow are arranged.
  • individual heating pipes 18 can be used, which in a sense form ring bundles in their entirety.
  • a length of the tubes used in the ring bundle of about 11.5 m and a housing diameter of 6 m are at an outer diameter of the bundle of about 3.6 m and a finned tube core diameter of about 22.4 mm with a total number of approx 7900 pipes approx 22,000 m 2 heating surface available.
  • individual bundles 20 can be used.
  • the heating tubes 18 or individual bundles 20 are flown in the flow direction 22 of the gaseous portion of the fluid stream.
  • the gaseous fraction is overheated in the heating chamber 14, whereupon it continues to flow into the outflow chamber 16. From there it is through discharge lines 24 (in Fig. 1 not shown) in the low-pressure turbine forwarded.
  • fine separator 28 are mounted in the dryer room.
  • a fine separator 28 for example, differently configured sheets can be used. It is also possible to use what are known as lamella droppers, which consist of packets of corrugated metal sheets. Usually these separation elements are fastened or anchored in a frame.
  • the fine separators 28 are condensate collecting trays 32 (in Fig. 1 not shown), into which the condensate which forms in the fine separator 28 during operation is drained off.
  • the condensate catch trays 32 are preferably arranged in the dryer room 13.
  • the condensate catch trays 32 are connected on the flow side with condensate drain pipes 34 arranged in the intermediate space 15, by means of which the condensate is discharged from the cavity 3.
  • the condensate drain pipes 34 extend substantially in a straight line parallel to the central axis M and extend over the entire length of the housing 2. They are anchored at the two ends of the housing 2 in each case with the aid of a plate 90. Between the bottom of the housing arranged plate 90 and the housing inner side 11, a gap 94 or annular gap is provided, through which the water collecting on the inside of the housing 11 can flow down.
  • the condensate drain pipes 34 perform a dual function. On the one hand, the condensate forming in the fine separators 28 is directed downwards out of the cavity 3 through it. On the other hand, their spatial arrangement between the fine separators 28 and the heating tubes 18 leads to an advantageous pressure loss of the fluid flow flowing from the inflow space 12 to the outflow space 16, whereby the vertical flow distribution in the heating space 14 improves. In particular, a back pressure in the lower region of the cavity 3 is avoided or greatly reduced. Furthermore, by the arrangement of the condensate drain pipes 34 and the direction of flow of the heating pipes 18 can be influenced. The turbulence generated thereby improves the heat transfer of the fluid flow to the first rows of tubes of the bundle.
  • the water content can be reduced to ⁇ 0.5% to 1%.
  • the fine separator 28 are arranged in the dryer room 13 on a lying around the central axis M outer circle with about 4m diameter and provide a flow area of about 70 m 2 ready.
  • baffles, perforated plates or vanes may be arranged in the inflow 12 or in the more interior spaces. By this deflection, however, the inflow space 12 is reduced in size. Baffles, perforated plates and vanes can be used in Zyklonabscheider 1 each alone or in different combinations with each other.
  • heating elements tube bundles can be used as they u.a. used in heat exchangers. In order to provide the largest possible heating surface, it is possible to use finned tubes or slotted finned tubes. It can also be used - optionally in combination with these - smooth tubes.
  • the tubes are flowed through, for example, by live steam at about 70 bar and / or - in multi-stage heating - by tapping the high-pressure turbine at about 30 bar.
  • the heating tubes 18 preferably have on the outside of a round cross-sectional profile in order to oppose the flow of fluid to be heated as little as possible flow resistance.
  • the cyclone 1 from Fig. 1 is in Fig. 3 in a left and right-hand longitudinal section each shown in a possible embodiment.
  • the housing 2 of the cyclone separator 1 is set up substantially vertically.
  • the housing 2 is designed substantially hollow cylindrical and rotationally symmetrical about the central axis M.
  • There are four supply lines 6 are provided in each case, which are distributed uniformly over the circumference of the housing 2 and preferably have a diameter of 1400 mm.
  • the steam emerging from the high-pressure turbine flows into the cavity 3 with a downwardly directed velocity component going beyond the force of gravity, with a gradient of about 15 °, thereby assisting the desired, essentially helical or helical flow guidance.
  • a discharge line 24 of approximately 1800 mm diameter is provided, which is in each case connected to the outflow chamber 16 on the flow side.
  • the steam can thus flow out of the housing 2 after its heating, both upwards and downwards, and subsequently passed through the discharge lines 24 to the low-pressure turbine (not shown).
  • the cyclone separator 1 is expediently arranged spatially in relation to the low-pressure turbine in such a way that the discharge line 24 connected at the top to the discharge space 16 on the discharge side can be connected essentially directly to the inlet opening of the low-pressure turbine.
  • the discharge line 24, which opens out at the lower end of the outflow chamber 16, is diverted upward to the inlet opening of the low-pressure turbine.
  • the embodiment of the cyclone separator 1 shown in the left-hand side section is designed for a two-stage heating or overheating of the steam.
  • heating tubes 18 are mounted in the form of a ring bundle.
  • the steam flows (indicated by the flow direction 22) first through the fine separator 28 and then through the arrangement of the condensate drain pipes 34, which, so to speak, oppose a resistance to the steam and thus lead to a pressure loss.
  • the heating tubes 18 may not be used in their full length for heating.
  • the steam then flows through a in the heating chamber 14 concentrically about the central axis M lying first stage 36 and first group of heating tubes 18. Subsequently, it flows on its way to the discharge chamber 16 through a second stage 37 and second group of heating tubes 18, concentric is disposed within the first stage 36.
  • the outer first stage 36 is supplied by a bleed steam feed line 40 with bleed steam at about 30 bar from the high pressure turbine.
  • the inner second stage 37 of heating tubes 18 is supplied by a live steam supply line 38 with live steam from a steam generator 66 (not shown) at about 70 bar.
  • separating plates 82 may be provided for the separation of the respective vapors. This also applies to the exit collector. Instead of arranging two tube bundles into one another, it is also possible to use a ring bundle with a separate tubesheet.
  • the thus heated in two stages of steam flows into the discharge chamber 16 and from there through the discharge lines 24 to the low-pressure turbine.
  • the gaseous fraction is thus heated successively on its way into the interior of the discharge space 16.
  • This type of two-stage heating can be generalized to multi-stage heating with the aid of additional steam feeds and tube groups in an obvious manner.
  • FIG. 3 In the right-hand side of the picture Fig. 3 an embodiment is shown with one-stage heating.
  • the heating pipes 18 are all supplied via the live steam supply line 38 with live steam.
  • the fine separator 28 are connected to condensate collecting trays 32, from which condensate drain pipes 34, the condensate is passed through condensate drains 46 from the housing 2.
  • condensate drain 43 The flowing down on the inside of the housing 11 condensate, here water, runs in the condensate drain 43 and leaves the housing 2 through a condensate drainage 46.
  • a second condensate drain 42 is provided in the recessed bottom region of the housing 2, through which the lower partial space is collected Condensate can drain through a condensate drain 46.
  • Fig. 3 illustrated embodiments of the cyclone 1 can with the in Fig. 1 Embodiments shown combined with ring bundles or individual bundles 20.
  • the drier or fine separator 28 is connected to a condensate collecting trough 32 into which the condensate forming in the operating state of the cyclone separator 1 in the drier or fine separator 28 runs. It runs through one or more supply lines 41 through each connected to the supply line 41 condensate drain pipes 34 down.
  • the condensate catch pans 32 can be configured differently depending on requirements.
  • each fine separator 28 is assigned a condensate catch basin 32. It is also possible a single one use annular condensate catcher 32 into which the condensate from all fine separators 28 can flow.
  • condensate traps 32 are mounted at different heights in the housing 2.
  • the condensate traps 32 are mounted in the housing 2 at two different levels.
  • Fig. 5 shows a condensate catch basin 32 of the upper level in plan view of the in Fig. 3 shown cyclone separator 1.
  • two supply lines 41 connected thereto on the flow side and condensate drain pipes 34 connected thereto are shown.
  • two further pairs of supply lines 41 and condensate drain pipes 34 can be seen, these pairs not being connected on the flow side to the condensate catch basin 32 shown. Rather, they are connected to the condensate catching basin which lies below, here concealed by the upper condensate catching basin 32.
  • the condensate drain pipes 34 which belong to the two condensate catching basins 32 lying at different heights are mounted alternately along the circumference in which they are mounted. The circular curvature is in the most schematic and not to scale Fig. 5 not visible.
  • each condensate discharge pipe 34 is connected to exactly one condensate catch basin 32, has the advantage that a high throughput of condensate in the operating state is ensured.
  • a plurality of condensate catch pans 32 may be connected to the same condensate discharge pipe 34 on the flow side.
  • FIG. 6 An advantageous embodiment of a steam turbine plant 62 is in Fig. 6 shown. It comprises a steam generator 66, a high-pressure turbine 70, and a low-pressure turbine 74.
  • the cyclone separator 1 is connected on the flow side between the high-pressure turbine 70 and the low-pressure turbine 74.
  • the live steam generated in the steam generator 66 is directed to perform work in the high pressure turbine 70. By doing work, the steam in the high pressure turbine 70 relaxes, increasing its water content. So that the steam in the low-pressure turbine 74 can be used as efficiently as possible for energy production, it must be prepared in a suitable manner. This must be its water content be reduced before it is then transferred to a superheated state.
  • the steam exiting from the steam outlet of the high-pressure turbine 70 is conducted via a distributor through supply lines 6 into the housing 2 of the cyclone separator 1.
  • the steam flows tangentially to the housing inner side 11 and is thereby set in rotation.
  • the gaseous portion of the steam flows into the housing interior, where it is put into a superheated state by heating elements, in particular heating pipes.
  • the superheated steam is passed through discharge lines 24 into the steam inlet of the low pressure turbine 74.
  • the heating tubes (not shown here) of the cyclone separator 1 are supplied in this embodiment by the heating supply line 78 with live steam from the steam generator 66.
  • the high pressure turbine 70 could be removed for this purpose bleed steam.
  • the cyclone separator 1 is not limited to use in steam turbine plants. It can essentially always be used where the heavier component or phase is to be separated from a multiphase fluid flow and the gaseous fraction is to be heated or superheated.
  • the heavy component of the fluid stream can be water as explained above. However, applications are also conceivable in which the heavy component consists of solid particles. This could be, for example, soot or dirt particles.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Cyclones (AREA)

Claims (15)

  1. Séparateur à cyclone (1) pour la séparation des phases d'un courant de fluid multiphase, avec un boîtier (2) essentiellement configuré à symétrie de révolution autour d'un axe central (M) et enfermant une cavité (3), avec au moins un conduit d'alimentation (6) pour le courant de fluid, configuré pour une affluence du courant de fluid qui est essentiellement tangentielle à la paroi intérieure (11) du boîtier, et avec au moins un conduit d'évacuation (24) pour la fraction gazeuse séparatée du courant de fluid, dite cavité (3) incluant, vu en direction radiale à partir de l'axe central (M), une chambre d'échappement (16) de section essentiellement circulaire suivie, dans l'ordre indiqué, par une chambre de chauffage (14), une chambre intermédiaire (15), une chambre de séchage (13) et une chambre d'affluence (12), chacune d'elles ayant une section essentiellement annulaire, la chambre d'affluence (12) étant délimitée vers l'extérieur par le boîtier (2), la chambre de chauffage (14) contenant des éléments de chauffage conçus pour chauffer la fraction gazeuse, au moins un séparateur fin (28) et au moins une cuve collectrice de condensat (32) y affectés étant disposés dans la chambre de séchage (13), et la, au moins une, cuve collectrice de condensat (32) étant reliée avec au moins un tuyau d'évacuation de condensat (34) disposé dans la chambre intermédiaire (15), à travers lequel le condensat se formant en état d'opération dans le au moins un séparateur fin (28) est évacué de la cavité (3).
  2. Séparateur à cyclone (1) selon la revendication 1, dans lequel une pluralité de cuves collectrices de condensat (32) disposée dans la chambre de séchage (13) est prévue dans au moins un plan (E) s'étendant perpendiculairement à l'axe central (M), dite pluralité de cuves formant ensemble au moins approximativement un anneau de cuves collectrices de condensat, chacune des dites cuves collectrices de condensat (32) étant reliée avec un tuyau d'évacuation de condensat y affecté, disposé à chaque fois dans la chambre intermédiaire (15).
  3. Séparateur à cyclone (1) selon la revendication 2, dans lequel un premier plan (E) avec un premier anneau de cuves collectrices de condensat est prévu et au moins un deuxième plan (E) avec un deuxième anneau de cuves collectrices de condensat est prévu, dans lequel un premier groupe de tuyaux d'évacuation de condensat (34) est affecté au premier anneau de cuves collectrices de condensat et un deuxième groupe de tuyaux d'évacuation de condensat (34) est affecté au deuxième anneau de cuves collectrices de condensat.
  4. Séparateur à cyclone (1) selon la revendication 3, dans lequel, dans une partie longitudinale de la chambre intermédiaire (15), dans laquelle s'étendent et des tuyaux d'évacuation de condensat (34) du premier groupe et des tuyaux d'évacuation de condensat (34) du deuxième groupe, dits tuyaux d'évacuation de condensat (34) sont disposés alternativement, vu en direction circonférentielle du séparateur à cyclone (1).
  5. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 4, dans lequel chaque tuyau d'évacuation de condensat (34) est aligné parallèlement à l'axe central (M).
  6. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 5, dans lequel les points de percée de tous les tuyaux d'évacuation de condensat (34) dans un plan de la section qui s'étend perpendiculairement à l'axe central (M) se trouvent essentiellement sur un cercle.
  7. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 6, dans lequel la cuve collectrice de condensat (32) respective est reliée avec le tuyau d'évacuation de condensat (34) respectif au moyen d'ue conduit d'alimentation (41).
  8. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 7, ayant exactement deux conduits d'évacuation (24), dans lequel les deux conduits d'évacuation (24) sont reliés du côté de courant, aux bouts opposés du boîtier (2), vu en direction de l'axe central (M), avec la chambre d'échappement (16).
  9. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 8, dans lequel le boîtier (2) est essentiellement réalisé comme un cylindre creux.
  10. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 9, dans lequel l'axe central (M) est essentiellement aligné en direction verticale.
  11. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 10, dans lequel le ou chaque conduit d'alimentation (6) est configuré de façon que le vecteur de vélocité du courant de fluid affluant dans la cavité (3) a une composante en direction de l'axe central (M) du boîtier (2).
  12. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 11, ayant quatre conduits d'alimentation (6) régulièrement répartis sur la circonférence du boîtier (2).
  13. Séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 12, dans lequel les éléments de chauffage ont une forme tubulaire et sont configurés pour être traversés par un milieu de chauffage fluide, en particulier par de la vapeur d'eau.
  14. Installation de turbine à vapeur (62), comprenant une turbine haute pression (70) et une turbine basse pression (74) et un séparateur à cyclone (1) selon l'une quelconque des revendications 1 à 13, dans lequel le au moins un conduit d'alimentation (6) est relié avec la sortie de vapeur de la turbine haute pression (70), et dans lequel le au moins un conduit d'évacuation (24) est relié avec l'entrée de vapeur de la turbine basse pression (74).
  15. Procédé pour faire fonctionner une installation de turbine à vapeur (62) comprenant une turbine haute pression (70) et une turbine basse pression (74), dans lequel la vapeur échappant de la sortie de vapeur de la turbine haute pression (70) est dirigée vers une cavité (3) du séparateur à cyclone (1), qui est enfermée par un boîtier (2) essentiellement configuré à symétrie de révolution autour d'un axe central (M), ce par quoi la vapeur est mise en rotation et sa fraction gazeuse est séparée de sa fraction liquide et accumulée dans une zone intérieure du boîtier (2), et dans lequel la fraction essentiellement gazeuse est dirigée à travers des séparateurs fins (28) lors de son passage à la zone intérieure, ce qui réduit encore plus sa fraction liquide, et est alors conduite à travers une disposition distribuée annulairement de tuyaux d'évacuation de condensat (34), est ensuite chauffée par des éléments de chauffage et est alors alimentée à l'entrée de vapeur de la turbine basse pression (74).
EP20100776937 2009-10-20 2010-10-20 Séparateur cyclonique pour la séparation de phases d'un courant fluidique à plusieurs phases, installation turbine à vapeur dotée d'un séparateur cyclonique et procédé de fonctionnement associé Not-in-force EP2491304B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910050087 DE102009050087B4 (de) 2009-10-20 2009-10-20 Zyklonabscheider zur Phasenseparation eines Mehrphasen-Fluidstroms, Dampfturbinenanlage mit einem Zyklonabscheider und zugehöriges Betriebsverfahren
PCT/EP2010/006407 WO2011047849A2 (fr) 2009-10-20 2010-10-20 Séparateur cyclonique pour la séparation de phases d'un courant fluidique à plusieurs phases, installation turbine à vapeur dotée d'un séparateur cyclonique et procédé de fonctionnement associé

Publications (2)

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EP2491304A2 EP2491304A2 (fr) 2012-08-29
EP2491304B1 true EP2491304B1 (fr) 2013-08-14

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EP20100776937 Not-in-force EP2491304B1 (fr) 2009-10-20 2010-10-20 Séparateur cyclonique pour la séparation de phases d'un courant fluidique à plusieurs phases, installation turbine à vapeur dotée d'un séparateur cyclonique et procédé de fonctionnement associé

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US (1) US9127834B2 (fr)
EP (1) EP2491304B1 (fr)
JP (1) JP5591340B2 (fr)
CN (1) CN102575841B (fr)
DE (1) DE102009050087B4 (fr)
WO (1) WO2011047849A2 (fr)

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AT511613B1 (de) * 2012-01-24 2013-01-15 Inteco Special Melting Technologies Gmbh Verfahren und anlage zur abgasreinigung bei vakuum-stahlbehandlungsprozessen
DE102013210917A1 (de) * 2013-06-12 2014-12-18 Robert Bosch Gmbh Vorrichtung und Verfahren zur Abtrennung von Schmutzpartikeln aus dem Arbeitsmedium einer Turbine
CN103438440B (zh) * 2013-09-10 2015-09-09 章礼道 超临界二次再热循环流化床锅炉
EP2881660B1 (fr) * 2013-12-09 2019-11-13 Gorenje d.d. Séparateur centrifuge de fluide et de vapeur d'un appareil ménager
CN106368670B (zh) * 2016-08-30 2019-08-09 泰州富士达制冷设备有限公司 油气分离压力法
CN108591995A (zh) * 2018-05-29 2018-09-28 德清县德沃工业设备安装有限公司 一种快速产生蒸汽的蒸汽发生装置
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WO2011047849A2 (fr) 2011-04-28
JP5591340B2 (ja) 2014-09-17
EP2491304A2 (fr) 2012-08-29
CN102575841B (zh) 2014-06-18
CN102575841A (zh) 2012-07-11
DE102009050087B4 (de) 2011-12-22
US9127834B2 (en) 2015-09-08
DE102009050087A1 (de) 2011-07-07
WO2011047849A3 (fr) 2011-12-15
US20120227405A1 (en) 2012-09-13
JP2013508133A (ja) 2013-03-07

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