EP3299626B1 - Zentrifugalpumpe zum fördern eines fluids - Google Patents

Zentrifugalpumpe zum fördern eines fluids Download PDF

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Publication number
EP3299626B1
EP3299626B1 EP17190755.3A EP17190755A EP3299626B1 EP 3299626 B1 EP3299626 B1 EP 3299626B1 EP 17190755 A EP17190755 A EP 17190755A EP 3299626 B1 EP3299626 B1 EP 3299626B1
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EP
European Patent Office
Prior art keywords
housing
impeller
diffuser
centrifugal pump
guide device
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.)
Active
Application number
EP17190755.3A
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German (de)
English (en)
French (fr)
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EP3299626A1 (de
Inventor
Thomas Welschinger
Torsten Johne
Mike Singer
Nitin Ugale
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Sulzer Management AG
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Sulzer Management AG
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Publication of EP3299626A1 publication Critical patent/EP3299626A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/007—Details, component parts, or accessories especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/466—Fluid-guiding means, e.g. diffusers adjustable especially adapted for liquid fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/60—Assembly methods
    • F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
    • F05D2230/642—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins using maintaining alignment while permitting differential dilatation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/38—Retaining components in desired mutual position by a spring, i.e. spring loaded or biased towards a certain position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/502—Thermal properties
    • F05D2300/5021—Expansivity
    • F05D2300/50212—Expansivity dissimilar

Definitions

  • the invention relates to a centrifugal pump for conveying a fluid according to the preamble of the independent patent claim.
  • Centrifugal pumps are used for many different applications, for example in the oil and gas industry, in power generation, in the water industry or in the pulp and paper industry, to name just a few examples. There are also applications in which the fluid to be conveyed by the pump has extremely high or very low temperatures.
  • LNG liquid natural gas
  • LNG liquefied natural gas
  • High temperature applications can be found, for example, in the generation of energy in thermal power plants.
  • So-called boiler circulation pumps are used here to transfer heat transfer media, e.g. B. water) to circulate in the primary circuit of the power plant.
  • the heat transfer medium can definitely have temperatures of 400 ° C. or more.
  • Another area of application with very high fluid temperatures is energy generation using solar energy, especially using CSP (concentrated solar power) technology.
  • CSP concentrated solar power
  • Such systems use mirrors or lenses to focus the sunlight, which is collected over a large area, onto a small area, for example on the top of a central tower, where the concentrated sunlight heats a heat transfer fluid (HTF: heat transfer fluid), which is then used to generate steam, which drives turbines to generate energy.
  • HTF heat transfer fluid
  • a molten salt is used as the heat transfer medium, which already has a temperature of 350 ° C., for example, on the low-temperature side.
  • the heat transfer medium can have temperatures of up to 600 ° C. or even more.
  • centrifugal pumps are used to circulate this very hot heat transfer medium.
  • pumps used for fluidized bed or ebullated bed processes in the hydrocarbon processing industry are used, for example, to remove heavy hydrocarbons, e.g. B. heavy oil, or refinery residues to clean or break up into more usable more volatile hydrocarbons. This is often done by applying hydrogen to the heavy hydrocarbons, the mixed components being swirled in a reactor and the heavy hydrocarbons being broken up there with the help of catalysts.
  • process fluid which usually consists mainly of heavy hydrocarbons
  • special pumps are used, for which the term ebullating pump has become common.
  • ebullator pumps are usually provided as circulation pumps for the process fluid directly on the reactor and, depending on the process, are designed in such a way that the pump is arranged above the drive with respect to the vertical. Ebullator pumps have to work as reliably as possible and over a long period of time in continuous operation under extremely challenging conditions. Because the process fluid is typically under a very high pressure of, for example, 200 bar or more, and has a very high temperature of more than 400 ° C., e.g. B. 460 ° C.
  • Such temperature gradients or temperature transients can cause enormous thermal stresses in the pump, which are due to the different thermal expansion of various components. It is not even necessary for the various components of the pump to have very different coefficients of thermal expansion, because the geometry or the different masses of the components or strong temperature gradients can result in different thermal expansions in the components, which can lead to considerable stresses. This problem can of course be even more pronounced if the components of the pump are made of different materials that have significantly different coefficients of thermal expansion, for example if the diffuser is made of a different material than the housing.
  • This surrounding area of the diffuser (diffuser) or housing viewed in the radial direction, provides a very narrow gap.
  • This gap or this play is deliberately kept very small, in particular in order to avoid an excessive backflow of the fluid from the high pressure side to the inlet of the pump. Because of this small gap or play, it is very important that the impeller is centered as precisely as possible.
  • a centrifugal pump for conveying a fluid with a housing which has an inlet and an outlet for the fluid, with an impeller arranged in the housing for rotation about an axial direction with which the fluid moves from the inlet to the outlet is conveyable, with a shaft for driving the impeller, which extends in the axial direction, and with a stationary nozzle for guiding the fluid from the impeller to the outlet, which nozzle is connected to the housing, wherein between the housing and the nozzle a resilient compensating element is provided, which is arranged around the shaft, and with which the diffuser can be retained in a centered position relative to the impeller during a radial movement relative to the housing.
  • the impeller is usually centered with respect to the housing by the bearings and in particular by the radial bearings with which the shaft carrying the impeller is mounted and which are fixed with respect to the housing.
  • the diffuser is attached to the housing and is arranged in such a way that it is centered with respect to the impeller via the housing.
  • the compensating element is configured in an annular manner.
  • the compensating element is then a ring, which can be arranged in a simple manner between the diffuser and the housing around the shaft during assembly.
  • the compensating element comprises a first and a second contact surface, the first contact surface resting on the diffuser and the second contact surface resting on the housing, and the first contact surface and the second contact surface being offset from one another with respect to the axial direction.
  • the compensating element makes contact with the diffuser only with the first contact surface and the housing only with the second contact surface with respect to the radial direction. This measure enables the compensation function to be implemented in a particularly simple manner, because the two contact surfaces thus converge with respect to the radial direction or move away from each other so as to compensate for radial relative movements between the diffuser and the housing.
  • the compensating element comprises a first transverse limb for contacting the diffuser and a second transverse limb for contacting the housing, the first transverse limb and the second transverse limb being connected by a longitudinal limb which extends in the axial direction .
  • the main function of the compensating element is to ensure that the centered position of the diffuser relative to the impeller is maintained in the event of thermally induced radial relative movements between the diffuser and the housing, for example when the housing is displaced relative to the diffuser in the radial direction.
  • This relative displacement can be absorbed by deformation of the connecting elements via which the diffuser is connected to the housing.
  • These fasteners typically include screws or bolts. Relatively strong mechanical stresses, for example due to shear stresses or bending stresses, can occur in the connecting elements.
  • the invention proposes providing a plurality of connecting elements which fix the diffuser on the housing with respect to the axial direction, each connecting element being designed such that there is a radial relative movement between the housing and allows the diffuser.
  • the diffuser is mounted so as to be floating in the radial direction with respect to the housing, so it can be moved or displaced in the radial direction relative to the housing.
  • each connecting element comprises for this purpose a sleeve which is arranged in an axial bore in the housing or in the diffuser, as well as a fixing means for fixing the diffuser, the fixing means extending through the sleeve, and the sleeve having an outside diameter, which is smaller than the inner diameter of the axial bore, so that an annular gap is formed between the sleeve and the wall delimiting the axial bore.
  • the fixing means is preferably a screw, in particular an expansion screw or a threaded bolt.
  • each sleeve has a length in the axial direction that is greater than the length of the axial bore in which the sleeve is arranged, and each sleeve has a flange at one of its axial ends which has an outside diameter which is larger than the inner diameter of the respective axial bore in which the sleeve is arranged.
  • each fixing means so for example each screw or each threaded bolt that connects the housing to the diffuser, can be tightened by a nut or other securing means, this nut being supported on the respective flange in order to secure and reliable fixation of the Ensure diffuser in the axial direction.
  • each sleeve is designed such that an axial gap is formed with respect to the axial direction between the flange and the housing or the diffuser in which the respective axial bore is provided so that the flange does not rest on the housing or on the diffuser becomes. Because the flange does not rest on the housing (or on the diffuser, depending on which of the two parts the axial bore is provided in) due to the axial gap, no adhesive or sliding friction forces are required between the flange when the housing is displaced relative to the diffuser and the housing (or the diffuser) to be overcome, which is particularly advantageous in terms of mechanical stress.
  • the impeller and / or the diffuser are made of a different material than the housing. Because it the solution according to the invention makes it possible to compensate for different thermal expansions, in particular of the housing and the diffuser, the diffuser and / or the impeller can also be made of a different material than the housing. In particular, two materials with very different specific thermal expansion coefficients can also be used. Depending on the application, for technical reasons it is sometimes desirable to manufacture the impeller and / or the diffuser from a different material than the housing. For example, this is advantageous for applications in which chemically aggressive or highly abrasive fluids are conveyed. For the impeller and / or the diffuser, a material can then be selected that is optimized in terms of its resistance to the fluid to be pumped, while another, z. B. a cheaper material can be chosen.
  • a configuration of the centrifugal pump is preferred in which a drive unit is provided for driving the impeller, which drive unit is connected to the shaft, the drive unit being arranged in the housing.
  • a drive unit is provided for driving the impeller, which drive unit is connected to the shaft, the drive unit being arranged in the housing.
  • Such configurations are particularly advantageous for applications in which the pump is completely or completely immersed in a liquid, e.g. B. water, or when the pump is operated in hard to reach places or under difficult conditions or environmental conditions.
  • shaft seals such. B. mechanical seals, for sealing the shaft passage from the housing to an externally arranged drive unit cannot be used or cannot be used effectively.
  • the housing is designed as a pressure housing, preferably for an operating pressure of at least 200 bar.
  • the centrifugal pump is designed for a fluid that has a temperature of more than 400 ° C.
  • the configuration according to the invention is also particularly suitable for pumps in which a drive unit is provided which is arranged below the impeller with respect to the vertical. In relation to the normal position of use of the pump, this means that the pump is arranged above the drive unit.
  • the drive unit is preferably arranged in the housing of the centrifugal pump.
  • impeller is designed as a radial impeller.
  • centrifugal pump is designed as a boiler circuit pump or as an ebullator pump for the circulation of a process fluid.
  • Fig. 1 shows, in a partially schematic sectional illustration, an exemplary embodiment of a centrifugal pump according to the invention for conveying a fluid, which is designated as a whole with the reference number 1.
  • the centrifugal pump 1 has a housing 2, which has an inlet 3 and an outlet 4 for the fluid, an impeller 5 arranged in the housing 2 for rotation about an axial direction A, which is defined by the target axis of rotation of the centrifugal pump 1, a shaft 6 for Driving the impeller 5, which extends in the axial direction A, as well as a stationary diffuser 7, which is connected to the housing 2 and which guides the fluid conveyed by the impeller 5 to the outlet 4.
  • the designation "diffuser" is also common for the diffuser 7.
  • Fig. 1 shows the embodiment in a section along the axial direction A.
  • a direction perpendicular to the axial direction A is referred to as a radial direction.
  • the housing 2 comprises an upper housing part 21 and a lower housing part 22, which are connected to one another in a sealing manner by screw connections (not shown) or a flange connection.
  • the centrifugal pump 1 also includes a drive unit 8 for driving the impeller 5, which is connected to the shaft 6 on which the impeller 5 is arranged, the drive unit 8 being arranged in the housing 2 of the centrifugal pump 1.
  • the invention is not limited to such configurations in which the drive unit 8 is in the housing 2 of the pump 1 is integrated. Rather, it is of course also possible for the drive unit 8 to be arranged as a separate device outside the housing 2 of the centrifugal pump 1.
  • ebullator pumps are pumps that are used for fluidized bed or ebullated bed processes in the hydrocarbon processing industry. These processes are used to purify heavy hydrocarbons that remain in the bottom of the separation columns, for example in the oil refinery, for example to desulfurize them and / or break them down into lighter hydrocarbons, which can then be used more economically as distillates.
  • An example of heavy hydrocarbons is heavy oil that remains in the refinery of petroleum.
  • the starting substance ie the heavy hydrocarbons such as. B.
  • ebullated bed reactor fluidized bed or boiling bed reactor
  • the process fluid is then cleaned or broken up in the reactor with the aid of catalysts which are kept in suspension in the reactor in order to ensure the closest possible contact with the process fluid.
  • An ebullator pump which is typically mounted directly on the reactor, is used to supply the reactor with the process fluid or for the circulation of the process fluid.
  • the ebullator pump Since the process fluid is under a very high pressure of, for example, at least 200 bar and under a very high temperature of, for example, over 400 ° C., the ebullator pump must also be designed for such pressures and temperatures.
  • the housing 2 of the centrifugal pump 1, which encloses the impeller 5 and the drive unit 8, is designed as a pressure housing that can reliably withstand these high operating pressures of, for example, 200 bar or more.
  • the ebullator pump 1 is also designed in such a way that it contains a hot process fluid which has a temperature of more than 400.degree has, can convey safely.
  • the ebullator pump 1 is usually arranged in such a way that the shaft 6 extends in the vertical direction, with the impeller 5 being arranged on top. This usual position of use is also in Fig. 1 shown.
  • centrifugal pump 1 can also be designed for other applications, for example as a submersible pump which, during operation, is completely or partially immersed in a liquid, e.g. B. water, is immersed.
  • the centrifugal pump 1 can also be designed as a horizontal pump, in which the shaft 6 extends in the horizontal direction.
  • the invention is particularly suitable for such centrifugal pumps with which very hot fluids of, for example, more than 400 ° C.
  • centrifugal pumps 1 are conveyed, as well as for centrifugal pumps 1, with which very cold fluids of, for example, -160 ° C. or even lower temperatures are conveyed.
  • boiler circuit pumps with which the heat transfer medium, especially the heat transfer medium in the primary circuit, is circulated in thermal power plants to generate energy, or pumps, which are used in the field of energy generation by means of CSP (concentrated solar power) technology to convey the heat transfer medium (HTF: heat transfer fluid), usually a molten salt, can be used, or pumps in the cryo industry or cryotechnology, with which, for example, liquid natural gas (LNG: liquefied natural gas) is conveyed in the temperature range of -160 ° C, for example.
  • LNG liquid natural gas
  • the in Fig. 1 The illustrated embodiment of the inventive centrifugal pump 1 designed as an ebullator pump is the impeller 5 with respect to the normal position of use shown in FIG Fig. 1 is shown, arranged above the drive unit 8.
  • the impeller 5 comprises a plurality of blades or vanes 51 with which the fluid is conveyed from the inlet 3, which is arranged here above the impeller 5, to the outlet 4, which is arranged here on the side of the housing 2.
  • the impeller 5 is designed here in a manner known per se as a closed impeller 5, with a hub 53 and a cover disk 52 facing the inlet 3 (see FIG Fig. 2 ), between them the wings 51 are arranged.
  • the cover disk 52 covers the wings 51 so that essentially closed channels for the fluid are formed between them.
  • the impeller 5 is surrounded in a manner known per se by the stationary diffuser 7, also called a diffuser, which is arranged around the impeller 5 on the outside with respect to the radial direction.
  • the diffuser 7 comprises a plurality of stationary guide vanes 71 (see FIG Fig. 2 ), with which the fluid conveyed by the impeller 5 is guided to the outlet 4 of the pump 1.
  • the stationary diffuser 7 is mounted on the housing 2 via a plurality of connecting elements 9 and is connected here in particular to the lower housing part 22 of the housing 2.
  • Each connecting element 9 preferably comprises a fixing means 91 provided with a thread (see FIG Fig. 2 ), by means of which the diffuser 7 is attached to the housing 2.
  • the fixing means 91 is in particular a screw connection, for example a screw or a (threaded) bolt.
  • the drive unit 8 is provided, which is designed here in a manner known per se as an electric canned motor.
  • the drive unit 8 comprises an inner rotor 81 and an outer stator 82 surrounding the rotor 81.
  • a can 83 is provided between the rotor 81 and the stator 82, which hermetically seals the stator 82 from the rotor 81 in a known manner.
  • the rotor 81 is non-rotatably connected to the shaft 6, which extends in the axial direction A and which, on the other hand, is non-rotatably connected to the impeller 5, so that the impeller 5 can be driven by the drive unit 8.
  • a radial bearing 12 is provided for the radial bearing of the shaft 6.
  • the impeller 5 is centered with respect to the housing 2 by the radial bearings 12.
  • An axial bearing 16 for the shaft 6 is provided below the lower radial bearing 12 as shown.
  • the fluid to be conveyed has a very high temperature in the ebullator pump 1, which is in the range of 450 ° C., for example.
  • This enormously high temperature causes very high thermal loads in the pump 1.
  • These thermal loads are based, for example, on the high temperature gradients in the pump 1, because on the one hand parts of the pump 1, such as the impeller 5 or the diffuser 7, are in direct physical contact with the hot fluid that flows through it, and on the other hand parts of the pump, such as at least parts of the housing 2, are in direct physical contact and thus in thermal contact with the surroundings of the pump 1, the ambient temperature typically being drastically lower - or, in the case of low-temperature applications, drastically higher - is.
  • Such temperature gradients or temperature transients can cause enormous thermal stresses in the pump 1, which are due, among other things, to the different thermal expansion of various components, especially the different thermal expansion of the housing 2 on the one hand and the diffuser 7 connected to the housing 2 on the other. It is not even necessary for these different components such as housing 2 and diffuser 7 to have very different coefficients of thermal expansion, because the geometry or the different masses of the components or strong temperature gradients alone can result in different thermal expansions in these components that are too considerable Tension. This problem can of course be even more pronounced if the housing 2 of the pump 1 and the diffuser 7 are made of different materials which have significantly different coefficients of thermal expansion.
  • a resilient compensating element 10 is provided between the housing 2 and the diffuser 7, which is arranged around the shaft 6 and with which the diffuser 7 in a radial relative movement, i.e. in particular in a relative displacement between the housing 2 and the diffuser 7 can be retained in a centered position with respect to the impeller 5.
  • FIG. 2 an enlarged sectional view of the connection between the housing 2 and the diffuser 7 with the spring-elastic compensating element 10 arranged between them.
  • the section is made in the axial direction A.
  • FIG Fig. 3 a sectional view of the compensating element 10 in a section along the axial direction A.
  • FIG Fig. 3 the diffuser 7 indicated, while the housing 2 is not shown.
  • the resilient compensating element 10 is deformed , whereby the relative displacement of the housing 2 in the radial direction relative to the diffuser 7 is compensated in this area, so that the diffuser 7 remains in its centered position with respect to the impeller 5.
  • the compensating element 10 thus acts as a spring with which the relative movements in the radial direction between the housing 2 and the diffuser 7 are compensated so that the diffuser 7 remains centered with respect to the impeller 5.
  • the resilient compensating element 10 is designed in the form of a ring, specifically as a spring ring which is axially symmetrical with respect to the axial direction A.
  • spring steel is characterized in particular by a significantly higher elastic limit.
  • the compensating element 10 is preferably designed with regard to its material properties and its geometry in such a way that it is elastically deformed in the operating state of the pump 1 when stresses occur, i.e. returns to its original shape after the stresses have ceased. A plastic deformation of the compensating element 10, that is to say an exceeding of its elasticity limit, is preferably avoided.
  • the annular compensating element 10 is arranged symmetrically around the shaft 6 between the housing 2 and the diffuser 7 so that the diffuser 7 is in contact with the housing 2 via the compensating element 10 in relation to the radial direction.
  • the diffuser 7 comprises a mounting foot 72 (see Fig. 2 ), by means of which the diffuser 7 is connected to the housing 2.
  • the assembly foot 72 comprises a radially inner, concentric to the shaft 6 and thus with respect to the axial direction A axially symmetrical annular surface 73 on which the compensating element 10 is supported.
  • the housing 2 here the lower housing part 22, has an annular support surface 23 which is concentric to the shaft 6 and thus axially symmetrical with respect to the axial direction A and on which the compensating element 10 is supported.
  • the support surface 23 is arranged radially on the inside with respect to the annular surface 73, the support surface 23 and the annular surface 73 running coaxially.
  • the compensating element 10 has a first and a second contact surface 101 and 102, the first contact surface 101 resting against the diffuser 7, namely on the annular surface 73 of the diffuser 7, and the second contact surface 102 resting against the housing 2, namely on the support surface 23.
  • the first and the second contact surface 101 and 102 are arranged offset from one another with respect to the axial direction A.
  • the compensating element 10 is designed in such a way that in the radial direction it contacts the diffuser 7 only with the first contact surface 101 and the housing 22 only with the second contact surface 102.
  • the compensating element 10 has an essentially S-shaped cross-sectional area, that is to say the compensating element 10 has a first transverse limb 103 for contacting the diffuser 7, and a second transverse limb 104 for contacting the housing 2, the first transverse limb 103 and the second transverse limb 104 are connected by a longitudinal leg 105 which extends in the axial direction A.
  • the first and second transverse legs 103 and 104 each extend in the radial direction.
  • the first transverse limb 103 comprises the first contact surface 101 and the second transverse limb 104 comprises the second contact surface 102.
  • the annular compensating element 10 is preferably dimensioned with regard to its outer diameter DA such that it can be inserted into the diffuser 7 with an interference fit, so that the first contact surface 101 is pretensioned against the annular surface 73.
  • the inner diameter DI of the ring-shaped compensating element 10 is dimensioned such that the compensating element 10 can still be mounted after it has been inserted into the diffuser 7, i.e. in the pretensioned state, i.e. can be arranged around the support surface 23 of the housing 2.
  • the outer diameter DA of the first transverse leg 103 in the unstressed state is somewhat larger than the diameter of the space bounded by the annular surface 73.
  • the inner diameter DI of the second transverse leg 104 is dimensioned so that after the insertion of the compensating element 10 into the diffuser 7, i.e. in the pretensioned state of the compensating element 10, it is at least as large as the diameter of the part of the housing 2 which is covered by the support surface 23 is limited.
  • the two contact surfaces 101 and 102 of the compensating element 10 are shifted relative to one another in the radial direction, whereby the radial relative movement between the housing 2 and the diffuser 7 is balanced so that the diffuser 7 remains in its centered position with respect to the impeller 5.
  • the main function of the compensating element 10 is therefore to ensure that the centered position of the diffuser 7 relative to the impeller 5 is maintained in the event of thermally induced radial relative movements between the diffuser 7 and the housing 2.
  • the relative displacement between the housing 2 and the diffuser 7 can be absorbed by deformation of the connecting elements 9 via which the diffuser 7 is connected to the housing 2.
  • relatively strong mechanical stresses, z. B. occur through shear stresses or bending stresses.
  • each connecting element 9 being designed in such a way that there is a radial relative movement between the Housing 2 and the diffuser 7 allows.
  • the diffuser 7 is mounted so as to be floating in the radial direction with respect to the housing 2, so it can be moved or displaced in the radial direction relative to the housing 2.
  • FIG. 4 shows Fig. 4 a sectional view of the connecting element 9 in a section along the axial direction A, wherein in Fig. 4 the fixing means 91 is not shown for reasons of clarity.
  • Each connecting element 9 comprises a sleeve 92 which is arranged in an axial bore 13 in the diffuser 7, more precisely in the mounting foot 72 of the diffuser 7. Deviating from the representation in the Fig. 2 and 4th It is of course also possible in a similar manner that the axial bore 13, which receives the sleeve 92, is provided in the housing 2.
  • the connecting element 9 further comprises the fixing means 91 for fixing the diffuser 7 on the housing 2, the fixing means 91 extending in the axial direction A through the sleeve 92 into the housing 2.
  • the fixing means 91 preferably implements a screw connection and particularly preferably an expansion screw connection.
  • the fixing means 91 is preferably a screw or a threaded or screw bolt, especially preferably an expansion screw or an expansion screw bolt, as shown in FIG Fig. 2 is shown.
  • the expansion screw 91 engages with its lower end as shown ( Fig. 2 ) into a threaded bore 24 in the housing 2, which is aligned with the axial bore 13, but has a smaller inner diameter than the axial bore 13.
  • the thread provided in the area of the lower end of the expansion screw 91 engages the thread of the threaded bore 24, so that the expansion screw 91 is firmly connected to the housing 2.
  • the sleeve 92 has an outer diameter D92 which is smaller than the inner diameter D13 of the axial bore 13, so that an annular wall is formed between the sleeve 92 and the wall delimiting the axial bore 13 Gap 14 is formed which extends in the axial direction A over the entire length L of the axial bore 13.
  • the sleeve 92 has a length H in the axial direction A which is greater than the length L of the axial bore 13. At its illustrated ( Fig. 4 ) At the upper axial end, the sleeve 92 has a flange 93, which has an outer diameter D93 which is greater than the inner diameter D13 of the axial bore 13. With its ( Fig. 4 ) the lower axial end, the sleeve 92 is supported on the housing 2.
  • the length H of the sleeve 92 is dimensioned such that an annular axial gap 15 is formed with respect to the axial direction A between the flange 93 and the diffuser 7 in which the axial bore 13 is provided, so that the flange rests 93 on the diffuser 7 is avoided.
  • the expansion screw 91 reaching through the sleeve 92 is screwed into the threaded bore 24 in the housing 2.
  • the upper end which is also provided with a thread, protrudes in the axial direction A beyond the flange 93.
  • a nut 94 which is ultimately supported on the flange 93, is screwed onto this end.
  • the expansion bolt 91 is preferably tensioned in this case.
  • the diffuser 7 is connected to the housing 2, the diffuser 7 being fixed in relation to the axial direction A.
  • This is done here by the preferably tensioned expansion screw bolts 91 in cooperation with the sleeve 92, which is supported on the one hand on the housing 2 and which, on the other hand, with its flange 93 forms the support surface for the nut 94 with which the expansion screw 91 can be tensioned.
  • the diffuser 7 is fixed in the axial direction with an axial play.
  • the diffuser 7 is mounted floating relative to the housing 2 with respect to the radial direction. Despite the fixation in the axial direction A, the diffuser 7 can namely be moved in the radial direction relative to the housing 2. If, during operation of the pump 1, the housing 2 on the one hand and the diffuser 7 on the other hand expand differently, the connecting elements 9 allow a relative displacement between the housing 2 and the diffuser 7 due to the annular gap 14.
  • the axial gap 15, which is provided between the flange 93 and the assembly foot 72 of the diffuser 7, is also particularly advantageous. Because the flange 93 has no direct physical contact with the assembly foot 72, i.e. does not rest on it, no static or sliding friction forces need to be overcome in the event of a relative displacement, which would occur when the flange 93 rests on or with the assembly foot 72 would work.
  • the connecting elements 9, which fix the diffuser 7 on the housing 2 with respect to the axial direction A are designed in such a way that they enable a radial relative movement between the housing 2 and the diffuser 7 without axial tension.
  • the solution according to the invention is also particularly suitable for configurations in which the impeller 5 and / or the diffuser 7 are made of a different material than the housing 2. It can be advantageous for technical reasons to use a different material for the impeller 5 and / or the diffuser 7 than for the housing 2.
  • the housing 2 usually consists of a steel or of a cast material such as cast iron.
  • the impeller 5 is made of a different material.
  • the Ebullator Pump 1 an in the Usually chemically very aggressive fluid is conveyed, which can also have abrasive properties. It can therefore be desirable to manufacture the impeller 5 and the diffuser 7, through which the fluid flows, from a different material with higher wear resistance, which is better able to withstand the collective loads caused by the fluid, and thus a longer service life or longer maintenance intervals enables.
  • This can be, for example, a material with very good corrosion or hot corrosion resistance.
  • Particularly suitable for the impeller 5 and the guide device 7 of an ebullator pump, but also for other high-temperature applications, are the nickel-based alloys, which are known under the trade name Inconel.
  • Inconel is also advantageous because it can be treated particularly well by surface hardening processes such as boronizing.
  • the diffusion processes during boriding extend significantly deeper into the material than with other materials, for example austenitic steel, so that particularly wear-resistant surfaces can be generated by boriding Inconel.
  • a first variant for the compensating element 10 is shown, in which the compensating element 10 is again designed in a ring shape.
  • the configuration shown in Fig. 5 The first variant shown has a cross-sectional area which essentially has the shape of a parallelogram, which is supported with the first contact surface 101 on the diffuser 7, and with the second contact surface on the housing 2. It can be advantageous to enlarge the contact surfaces 101 or 102 to flatten the corresponding corners of the parallelogram.
  • Fig. 6 shows a second variant for the compensating element 10 in a section perpendicular to the axial direction A, wherein the cutting plane lies in the compensation element 10.
  • the compensating element 10 comprises a plurality, here four, separate segments 10a, 10b, 10c, 10d, each of which is arranged between the housing 2 and the diffuser 7, the segments 10a, 10b, 10c, 10d preferably being symmetrical are arranged around the shaft 6.
  • Each individual segment 10a, 10b, 10c, 10d can be designed, for example, with a cross-sectional area which corresponds to that in FIG Fig. 3 or in Fig. 5 shown corresponds. Of course, other configurations with regard to the cross-sectional area are also possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP17190755.3A 2016-09-23 2017-09-13 Zentrifugalpumpe zum fördern eines fluids Active EP3299626B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16190413 2016-09-23

Publications (2)

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EP3299626A1 EP3299626A1 (de) 2018-03-28
EP3299626B1 true EP3299626B1 (de) 2020-08-19

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US (1) US11353043B2 (ko)
EP (1) EP3299626B1 (ko)
KR (1) KR102423441B1 (ko)
CN (1) CN107869477B (ko)
AU (1) AU2017232183B2 (ko)
BR (1) BR102017020099A2 (ko)
CA (1) CA2978979A1 (ko)
MX (1) MX2017011755A (ko)
RU (1) RU2737931C2 (ko)
SG (1) SG10201707225UA (ko)

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CN109826802B (zh) * 2019-03-25 2023-09-08 扬州大学 一种具有隐藏后导叶结构的双向轴流泵装置
CN110552895A (zh) * 2019-10-12 2019-12-10 北京慨尔康科技发展有限公司 一种离心泵
WO2022022792A1 (en) * 2020-07-31 2022-02-03 Copenhagen Atomics Aps A canned rotodynamic flow machine for a molten salt nuclear reactor and an active magnetic bearing for use in a flow machine for a molten salt nuclear reactor
CN112283164A (zh) * 2020-11-09 2021-01-29 大福泵业有限公司 一种新型水力模型
CN216111302U (zh) * 2021-08-16 2022-03-22 博西华电器（江苏）有限公司 可输送经加热的流体的泵
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AU2017232183A1 (en) 2018-04-12
RU2017133096A3 (ko) 2020-10-16
RU2017133096A (ru) 2019-03-22
EP3299626A1 (de) 2018-03-28
AU2017232183B2 (en) 2022-10-13
BR102017020099A2 (pt) 2018-05-02
US20180087532A1 (en) 2018-03-29
CN107869477B (zh) 2021-08-06
MX2017011755A (es) 2018-09-25
US11353043B2 (en) 2022-06-07
CA2978979A1 (en) 2018-03-23
KR20180033099A (ko) 2018-04-02
CN107869477A (zh) 2018-04-03
KR102423441B1 (ko) 2022-07-20
RU2737931C2 (ru) 2020-12-07
SG10201707225UA (en) 2018-04-27

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