Classifications

• • 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
  • F22B37/266—Separator reheaters
• • 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
• • 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 an apparatus for phase separation of a multiphase senfluidstroms having a substantially around a central axis rotationally symmetrical 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 device. It also relates to a method for operating such a steam turbine Anläge.
• water separators connected in series and reheaters which can be structurally combined in the manner of a secondary or a series installation (combined water separator).
• 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 conducted 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 steam is now passed into a downstream and structurally / spatially separated second component of the WaZu, 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.
• the invention is therefore based on the object to provide a device for Phasensepara- tion of a multi-phase fluid flow, which is suitable for heating the gaseous portion of the fluid stream, eg steam, and low demands on material and space requirements. Furthermore, a steam turbine plant with a high-pressure turbine and a low-pressure turbine, in which such a device can be used particularly advantageous, indicated contact. Furthermore, a method for operating such a steam turbine plant is to be specified.
• heating elements designed in the cavity for heating the gaseous fraction are arranged in an annular space concentric with the central axis.
• the invention is based on the consideration that the comparatively large space requirement of conventional water separators / reheaters is based inter alia on the fact that the separation of water from the steam initially leaving the high-pressure turbine and the subsequent overheating of the separated gaseous fraction take place chronologically one after another in two separate room areas or device components takes place, which are arranged one behind the other in the manner of a flow-side series connection.
• specific requirements are placed on the structural design of the water separator / reheater, the system requires a relatively large installation space.
• these two space regions do not necessarily have to be arranged structurally in succession in separate housings. Assuming suitable flow conditions, these spatial regions can also be arranged nested in one single housing, wherein the liquid separation and the overheating of the gaseous fluid fraction for a given volume element of the fluid take place substantially simultaneously or shortly after one another in terms of time.
• 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 Proportion of the original fluid stream for example water vapor, flows into the interior of the cavity. If, in an inner or middle region of the cavity, in particular in an annular space, heating elements for heating or overheating the gaseous portion are arranged in such a way that the passage of the lighter phase into the inner area is still possible, the gaseous portions become directly during their passage heated or overheated in the interior.
• an inner space area which essentially contains the superheated steam, arises in the interior of the outer space area designed for water separation.
• the superheated, gaseous portion can then be led out of the inner space area and used as needed.
• 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 stream, and the light fraction or portions of the original fluid stream are to be heated.
• the annular space is designed with the heating elements for a flow through the gaseous portion of the fluid stream. In doing so, it separates the cavity into an inlet space lying between the inside of the housing and the annular space and a discharge space located inside the annular 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. When used in a steam turbine plant thereby efficiency and lifetime or maintenance intervals of the turbine can be increased.
• different embodiments of the rotationally symmetrical housing are advantageous.
• 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 center 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 for overheating 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 a plurality of supply lines.
• the supply lines-at least in the region of their housing connection-lie in a plane substantially perpendicular to the central axis of the housing they are advantageously designed such that the velocity vector of the fluid flow flowing into the cavity has a component pointing 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 result of the Wandgeometrie adjusting vortex flow is preferably superimposed on a velocity component in the direction of the central axis, so that overall forms a helical flow.
• the velocity component directed in the direction of the central axis advantageously points downwards.
• four supply lines are used for the inflow of the fluid flow, which are arranged distributed uniformly and symmetrically over the circumference of the housing.
• the inflowing fluid flow advantageous to four equal areas of
• Housing inside be divided without the individual streams meet and interfere 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 be optimized by guide vanes 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 inflow space further separation fine separator can be arranged.
• the condensate forming in the fine separator can be removed from the cavity by condensate drainage.
• the device 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 annular space in the direction of the central axis.
• the heating elements belonging to the individual groups can be designed in each case 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 annular space, 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 annular space.
• 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. If necessary, they are easier to assemble, dismantle or exchange than single tubes.
• an annular, aligned perpendicular to the central axis partition plate is inserted into the housing, which divides the cavity into two subspaces, and whose inner circle substantially coincides with the inner circle of the annular space, and whose outer circle radius is slightly less than the radius of Housing inside is.
• the two subspaces are fluidly connected to each other only by a lying in the inner circle of the partition plate and thus in the interior of the annulus passage.
• the supply lines and the discharge lines are each in different subspaces.
• the gaseous portion of the fluid flow can be performed in this way particularly favorable through the housing, being ensured that it flows through the annulus twice, namely once from outside to inside, and once from the inside to the outside. Since the partition plate in the radial direction does not extend to the inside of the housing, the condensate can flow away unhindered there.
• 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 connecting the discharge line or all discharge lines 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 liquid portion is separated and collected in an inner region of the cavity surrounded by the housing, and wherein the gaseous portion is heated by its passage in the inner region by heating elements and then supplied to the steam inlet of the low-pressure turbine.
• the heating elements are tubular, thus forming heating pipes.
• the live steam generated by a steam generator is conducted 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 with the outside 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 deposition 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 a very 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 additional fine separators allows a further reduction of the heavy component.
• the flow of the heating elements, which are designed for heating or overheating of the light phase of the fluid flow can be further improved by the use of baffles, vanes or pinhole.
• 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 essentially be mounted in a vertically positioned housing directly under the high-pressure turbine, so that the gas can flow from the steam outlet of the high-pressure turbine at the upper end of the housing into the device. Through discharge lines at the bottom of the housing then the superheated steam of the low-pressure turbine can be supplied.
• FIG. 1 shows four different contiguous quarter-circle-shaped partial cross sections of four different possible embodiments of a device for phase separation of a multi-phase fluid flow with a substantially rotationally symmetrical about a central axis designed housing, wherein the respective cross-sectional plane is selected perpendicular to the central axis,
• Fig. 2 is a longitudinal section through the left-side half of an embodiment of
• FIG. 3 shows a further embodiment of the device according to FIG. 1 in the right-hand longitudinal section
• FIGS. 1 to 3 shows a plurality of heating elements of the device according to FIGS. 1 to 3 and guide vanes associated with the heating elements, here shown in cross section with a viewing direction in the direction of the central axis,
• FIG. 5 shows a longitudinal section through the left half of a further preferred embodiment of the device according to FIG. 1, and
• Fig. 6 is a schematic block diagram of a steam turbine plant with a
• High-pressure turbine a low-pressure turbine, a fresh steam generator and with a device for phase separation of a multi-phase fluid flow according to an embodiment of FIG. 1 to FIG. 5.
• the apparatus 1 shown in FIG. 1 for the phase separation of a multiphase fluid flow comprises a housing 2, which is configured substantially symmetrically about a center axis M and has a hollow cylindrical shape and encloses a cavity 3 and into which four supply lines 6 are embedded.
• each quadrant of FIG. 1 corresponds to a possible embodiment of the device, wherein in reality all four quadrants are realized in one of the four ways shown here.
• the housing 2 has a diameter of about 6 meters in a preferred embodiment.
• 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 stream may be 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 device 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 flow conditions forming in the cavity 3 from the inflow space 12 into the annular space 14.
• the annular annular space 14 encloses the cylindrical outflow space 16 located inside the housing 2 spatially.
• heating elements which are designed in terms of their heating power for overheating of the gaseous portion of the fluid stream 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 13 m and a housing diameter of 6 m are at an outer diameter of the bundle of about 3.5 m and a tube diameter of about 2.3 cm with a total number of about 5000 Pipes approximately 16,000 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 annular space 14, whereupon it continues to flow into the outflow space 16. From there he will through discharge lines 24 (not shown in Fig. 1) forwarded to the low-pressure turbine.
• a separation efficiency of the water of up to about 80% can be achieved on the basis of previous experience.
• 12 fine separator 28 may be mounted in the inflow space.
• differently configured plates can be used as a fine separator 28.
• fin separators can be used as a fine separator 28.
• Another alternative consists of packets of corrugated sheets. Usually these separation elements are fastened or anchored in a frame. With the aid of the fine separator 28, the water content can be reduced to about 0.5% to 1%.
• the fine separator 28 are arranged on a lying around the central axis M outer circle with about 4m diameter and provide a Anströmungs- surface of about 70 m 2 ready.
• the additional used heat caused by the increased water content of about 2.6% (without fine separator 28) compared to 0.5 to 1% (with fine separators 28) at the entrance of the tube bundle would probably be negligible by eliminating the pressure drop caused by the fine separators 28.
• the energy balance results as follows: In order to achieve the same outlet pressure and the same outlet temperature of the vapor at the discharge line 24 with a water content of 2.6% as with a water content of 0.5 to 1%, approx. more live steam is tapped from the main steam line or from the high-pressure turbine and introduced into the heating tubes. However, if the tube-side mass flow through the heating tube remains the same, the outlet temperature drops by approx. 20 K due to the approx.
• perforated plates 34 and vanes 36 may be arranged in the inflow 12. By this deflection, however, the inflow space 12 is reduced in size. Baffles 32, perforated plates 34 and vanes 36 may be used in the device 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 - from tapping steam of the high-pressure turbine at about 30 bar.
• the heating tubes 18 preferably have a round cross-sectional profile on the outside in order to counteract as little flow resistance as possible to the fluid flow to be heated.
• the device 1 is shown in Fig. 2 in a left-side longitudinal section in a possible embodiment.
• the housing 2 of the device 1 is set up substantially vertically.
• the housing 2 is designed substantially hollow cylindrical and rotationally symmetrical about the central axis M.
• heating tubes 18 are mounted in the form of a ring bundle.
• live steam is supplied through the live steam supply line 38.
• the cavity 3 is divided by a horizontally oriented annular partition plate 37 into an upper and a lower subspace.
• the partition plate 37 extends in the radial direction from the inner diameter of the annular space 14 or annular bundle almost to the inside of the housing 11.
• the upper and the lower subspace are in this way fluidly only via the lying within the partition plate 37 gleichsab- section of the outflow space 16 connected.
• This embodiment can be combined (at least in the upper subspace) with all four variants shown in FIG.
• the heating tubes 18 may be performed by the partition plate 37 and extend over both subspaces.
• two groups of heating tubes 18, namely a group in the upper compartment and a group in the lower compartment, can be used.
• the heating tubes 18 of the two groups can be designed for different heating outputs.
• the steam emerging from the high-pressure turbine is conducted through the supply lines 6 into the housing 2 in the upper subspace and flows in the housing inner side 11 in the tangential direction.
• the water content of the vapor is deposited on the inside of the housing 11. Due to the forming in the cyclone flow conditions and optionally with the help of baffles 32, vanes 36 and perforated plates 34, the gaseous portion of the vapor flows into the discharge chamber 16 and passes through the located in the interior of the partition plate 37 transition to the lower subspace. The gaseous portion changes its direction after passing through the transition and is again directed outward through the annular space 14 in the direction of the inside of the housing 11, whereby a renewed heating takes place through the heating pipes 18 arranged in the annular space 14. Subsequently, the heated, gaseous fraction flows into the discharge lines 24, which are attached laterally to the housing 2, and further into the low-pressure turbine.
• a second condensate drain 43 is provided in the recessed bottom region of the housing 2, via which the condensate collecting in the lower subspace can drain through a condensate drain 46.
• FIG. 1 A further embodiment of the device 1, which can be combined with the embodiments shown so far, can be seen in FIG. Again, the central axis M of the housing 2 is oriented substantially vertically.
• the supply lines 6 in the housing 2 in such a way that the fluid flow with a gradient of about 15 °, the inside of the housing 2 flows.
• the vortex flow in the interior of the cavity is superimposed on a downwardly directed velocity component, which goes beyond the gravitational effect, whereby the desired, essentially spiral or helical, flow guidance is supported.
• FIG. 4 A possible embodiment of the optionally provided guide vanes 36 is shown in Fig. 4 in a cross section.
• the selected cross-sectional plane is perpendicular to the central axis M of the device 1.
• the guide vanes 36 are mounted between an imaginary inner border 54 and an outer border 58.
• the borders 54 and 58 are in reality circular, but this is not apparent in the completely schematic and not to scale Fig. 4.
• the guide vanes 36 have a curved profile tapering in the direction of the heating tubes 18 (only the outer heating tubes 18 of the ring bundle surrounded by the guide vanes 36 are shown).
• the vanes 36 affect the flow direction 22 of the fluid flow.
• suitable shape and positioning of the guide vanes 36 can be achieved that the heating tubes 18 are flowed substantially frontally. A tangential or oblique inflow of the heating tubes 18 can thereby be greatly reduced or avoided.
• the embodiment of the device 1 shown in FIG. 5 with a substantially vertical alignment of the center axis M is designed for a two-stage heating or overheating of the fluid flow.
• a group of heating tubes 18 located in the outer region of the annular space 14 is supplied with a bleed steam taken from a high-pressure turbine, for example, at about 30 bar via a bleed steam feed line 40.
• An internal group of heating tubes 18 is fed via the live steam supply 38 live steam at about 70 bar.
• the forming in the annular space 14 condensate can be derived from the device 1 via the condensate drains 46. Between the inlet headers for the supplied with different steam groups of heating tubes 18 separating plates 82 may be provided for the separation of the respective vapors. This also applies to the exit collector.
• the proportion of water is deposited on the inside of the housing 11 and possibly additionally on fine separators 28 arranged in the inflow space 12, while the gaseous portion flows into the annular space 14.
• the gaseous fraction flows around the outer group of heating tubes 18 supplied with bleed steam and then, on its way into the interior of the outflow space 16, around the inner group of heating tubes 18.
• 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 obviously be generalized to multi-stage heating with the aid of additional steam feeders and tube groups.
• this form of two-stage or multi-stage heating with the variant in which viewed in the direction of the central axis M of the housing 2 a plurality, designed for different heating power groups of heating tubes 18 behind or are arranged one above the other, combined.
• the discharge line 24 leads downwards out of the outflow space 16 in the vertical direction.
• This embodiment of the discharge line 24 and the associated, vertically downward discharge of the heated steam can also be combined with a single-stage heating.
• FIG. It An advantageous embodiment of a steam turbine plant 62 is shown in FIG. It comprises a main steam generator 66, a high-pressure turbine 70, and a low-pressure turbine 74.
• the device 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 fresh steam generator 66 is conducted to perform work in the high pressure turbine 70.
• the steam in the high pressure turbine 70 relaxes, increasing its water content.
• 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. For this purpose, its water content must be reduced, before it is subsequently transferred to a superheated state.
• the steam exiting the steam outlet of the high-pressure turbine 70 is conducted via a distributor through supply lines 6 into the housing 2 of the device 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 pipes (not shown here) of the device 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 device 1 is of course 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 stream 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)
• Engine Equipment That Uses Special Cycles (AREA)
• Cyclones (AREA)
• Separating Particles In Gases By Inertia (AREA)
• Centrifugal Separators (AREA)

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• 2009
  • 2009-04-01 DE DE102009015260A patent/DE102009015260B4/de not_active Expired - Fee Related
• 2010
  • 2010-03-08 US US13/262,713 patent/US20120023944A1/en not_active Abandoned
  • 2010-03-08 WO PCT/EP2010/001436 patent/WO2010112123A2/de not_active Ceased
  • 2010-03-08 EP EP10713120.3A patent/EP2414730B1/de not_active Not-in-force
  • 2010-03-08 JP JP2012502480A patent/JP5584281B2/ja not_active Expired - Fee Related
  • 2010-03-08 CN CN2010800149872A patent/CN102378877B/zh not_active Expired - Fee Related

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