EP2386767A2 - Pompe hélico-axiale, rotor pour une pompe hélico-axiale, palier hydrodynamique d'un rotor d'une pompe hélico-axiale et pompe hybride dotée d'un rotor pour une pompe hélico-axiale - Google Patents

Pompe hélico-axiale, rotor pour une pompe hélico-axiale, palier hydrodynamique d'un rotor d'une pompe hélico-axiale et pompe hybride dotée d'un rotor pour une pompe hélico-axiale Download PDF

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Publication number
EP2386767A2
EP2386767A2 EP11161758A EP11161758A EP2386767A2 EP 2386767 A2 EP2386767 A2 EP 2386767A2 EP 11161758 A EP11161758 A EP 11161758A EP 11161758 A EP11161758 A EP 11161758A EP 2386767 A2 EP2386767 A2 EP 2386767A2
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EP
European Patent Office
Prior art keywords
stabilizing
rotor
helico
gap
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11161758A
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German (de)
English (en)
Other versions
EP2386767B1 (fr
EP2386767A3 (fr
Inventor
Paul Meuter
Thomas Welschinger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer Management AG
Original Assignee
Sulzer Pumpen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sulzer Pumpen AG filed Critical Sulzer Pumpen AG
Priority to EP11161758.5A priority Critical patent/EP2386767B1/fr
Publication of EP2386767A2 publication Critical patent/EP2386767A2/fr
Publication of EP2386767A3 publication Critical patent/EP2386767A3/fr
Application granted granted Critical
Publication of EP2386767B1 publication Critical patent/EP2386767B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • 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
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing 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
    • F04D31/00—Pumping liquids and elastic fluids at the same time

Definitions

  • the invention relates to a helico-axial pump for conveying multiphase mixtures, a rotor for a helico-axial pump, a hybrid pump with a helico-axial pump and a method for mounting a rotor in a helico-axial pump according to the preamble of the independent claims 1 , 10, 13 and 14.
  • Such pumping or compression device for multi-phase mixtures with increased gas content for example, already from the GB-A-1 561 454 , of the EP 0 486 877 or the US 5,961,282 known.
  • the hybrid pump is according to US 5,961,282 a system for compressing a multiphase mixture, which may comprise, in addition to a liquid phase in particular a significant proportion of gas.
  • the pump in this case comprises a multi-stage axial flow pump for reducing the relative gas content, ie the axial flow pump serves to increase the density of the multiphase mixture, so that it can finally be pumped from a lower level to a higher level by another conventional centrifugal pump, for example from the bottom of the Marine on an oil platform, a ship or a land-based facility.
  • the helico-axial pump acting as a compressor comprises a rotor having a plurality of compression stages, in practice for example up to sixteen or more stages, such that the multiphase mixture progressively increases from a relatively low density with a high relative volume fraction of gas is compressible to a highly compressed multiphase mixture having such a high density that the highly compressed mixture can be further conveyed by a usual feed pump.
  • a known compression stage K 'of a rotor 2' of a helico-axial pump 1 ' is shown schematically in FIG Fig. 1a and Fig. 1b shown for clarity in Fig. 1b a section II of a section according to Fig. 1a is shown parallel to the longitudinal axis A '.
  • Each compression stage K ' comprises a rotating impeller 3' with screw 31 ', the rotating impeller 3' resembling a short Archimedean screw, and a stator 4 'adjoining it, which consists of a plurality of static, ie non-rotating blades 41' , Impeller 3 'and stator 4' are in such a way with respect to a common pump shaft 5 ', mounted that the impeller 3' is set in the operating state of the pump shaft 5 'in rotation, while the stator 4' from the rotational movement of the pump shaft 5 ' is decoupled and therefore not rotated with respect to the impeller 3 '.
  • the pump shaft 5 ' extends along a longitudinal axis A'.
  • the plurality of compression stages K ' are arranged in series in a substantially tubular pump housing 6' in series.
  • the rotating screw 31 ' conveys the multi-phase mixture M' in the direction of the arrow, for example, from a in Fig. 1a and Fig. 1b not shown preceding compression stage K 'in the stator 4', whereby in the stator 4 'kinetic energy is converted into pressure energy, which leads to the compression of the multiphase mixture M'.
  • the efficiency of the pump 1 ' can be reduced and in the worst case, even damage to the pump 1' are to be feared when the rotor 2 ', for example, begins to vibrate so strong and uncontrolled that parts of the rotor 2', such as the wheels 3 'come into contact with the pump housing, for example, by the oscillatory motion.
  • the type and intensity of the vibrations of the rotor 2 ' depends not only on the specific geometry but also on the operating state of the pump 1', the multiphase mixture M 'to be pumped, the rotational speed of the pump 1' and other known parameters, some of which are not exactly known so that it is hardly possible to get to grips with the problems with the harmful vibrations of the rotor 2 'solely by adapting the geometrical relationships of known pumps 1' or by using new materials.
  • the object of the invention is therefore to propose a helico-axial pump for promoting multi-phase mixtures, in which the harmful vibrations of the rotor are largely avoided and the vibrations of the rotor are reduced or damped to a predeterminable degree, so that on the one hand an improved run of Rotor can be achieved in the operating state and the pump on the other hand can be operated at speeds or in order to a rotating field in which the from the state
  • the art known Helico-axial pumps can not be operated due to the above-described harmful vibrations of the rotor.
  • the new pump should be able to be equipped alternatively or simultaneously with more compression levels than is possible with the previously known in the prior art pumps, in which limits the length of the pump and thus the maximum number of compression stages by the vibrations of the rotor in the operating state is.
  • the invention thus relates to a helico-axial pump for conveying a multiphase mixture, which helico-axial pump comprises a rotor rotatably mounted in a pump housing about a longitudinal axis with a first part rotor and a second part rotor, wherein the first part rotor and the second part rotor for compression of Multiphase mixture comprises a compression stage with a helico-axial impeller and a stator.
  • a hydrodynamic stabilizing bushing with a stabilizing surface is provided between the first part rotor and the second part rotor and configured such that a stabilizing gap is formed in front of the stabilizing surface, so that a hydrodynamic stabilizing layer of a stabilizing medium can be formed in the stabilizing gap in the operating state.
  • a hydrodynamic stabilizing bush is provided with a stabilizing surface in the pump housing, so that a stabilizing gap is formed in front of the stabilizing surface, in which stabilizing gap a hydrodynamic stabilizing layer is formed in the operating state of the pump.
  • the present invention thus decisively improves the rotor dynamics because the damping and stiffness of the oscillatory rotor system is decisively increased by the stabilization layer.
  • the harmful vibrations of the rotor are largely avoided by the formation of the stabilizing layer in the stabilizing gap in front of the stabilizing surface of the stabilizing bushing and are reduced or damped at least to a predeterminable tolerable measure, so that the pump can be operated even at a speed or in a certain revolution field where this is no longer possible without the use of the stabilizing layer according to the invention.
  • possibly even a higher efficiency of the pump and a smoother improved running of the rotor can be achieved in the operating state. This ultimately leads, of course, not only to save energy for the operation of the pump, but also the maintenance intervals can be extended, whereby the associated costs can be drastically reduced and at the same time the life of the pump is significantly increased.
  • Another particular advantage is that the invention makes it possible for the first time to design pumps with a much higher number of compression stages than was previously possible. So far, the possible number of compression stages alone was limited by the massively increasing with increasing number of compression stages oscillations of the rotor. By means of the invention, the rotor can be reliably stabilized practically on any length.
  • the stabilizing layer in the stabilizing gap in front of the stabilizing surface of the hydrodynamic stabilizing bushing is quasi-automatic, so that in a simple embodiment, which is of particular importance in practice, except for a suitable adjustment of the size or form the stabilizing gap or the stabilizing bushing and / or their stabilizing surface no further structural measures must be made.
  • a pressure difference between the multiphase mixture, which is located in the first part rotor and that which is in the second part rotor develops in the operating state above the stabilizing gap such that a predeterminable flow of multiphase mixture from the second sub-rotor on the stabilizing gap back to the first sub rotor automatically adjusts, which automatically forms a stabilizing layer for stabilizing or damping the harmful vibrations of the rotor.
  • the degree ie the strength of the damping depending on technical requirements or specifications in a novel helico-axial pump in a simple manner adaptable.
  • This can be done, for example, by a suitable choice of geometry, for example the geometric shape or width of the stabilizing gap.
  • An inventive helico-axial pump is particularly preferably designed in the form of a so-called back-to-back arrangement.
  • the expert understands an arrangement of two pump rotors in series, which forms such a pump with two pressure levels.
  • the medium to be pumped is fed via a suction opening of the pump of the first pressure stage, wherein the medium passes through the first pressure stage in a first axial direction, wherein the pressure of the medium to be pumped is increased to a first intermediate pressure.
  • the medium is then supplied via a channel system of the second pressure stage such that the medium passes through the second pressure stage in a second axial direction, which is opposite to the first axial direction of the first pressure stage.
  • the second pressure level is the Medium then brought to the desired final pressure and removed via a pressure port for further use of the pump.
  • the back-to-back arrangement of the pumps known from the prior art which are not all helico-axial pumps, is that the flow direction of the medium in the first pressure stage is opposite to the direction of flow in the second pressure stage.
  • the back-to-back arrangement serves exclusively to compensate for the enormous thrust forces acting in the axial direction on the bearings of the pump shaft, at least partially, and thus to relieve the bearings.
  • the enormous axial thrust forces are due to the fact that in these known from the prior art pumps very high pressures are generated with very large components in the axial direction.
  • an additional mechanical bearing for example Ball bearing is provided, which additionally stores the pump rotor in the middle mechanically.
  • the essential realization of the invention is therefore that the back-to-back arrangement can be used successfully in the case of helico-axial pumps, if between the first part rotor and the second part rotor a stabilizing bush according to the invention is provided, so that due to the pressure gradient between the first part rotor and the second part rotor in the stabilizing gap can form a stabilizing layer of the stabilizing medium, which is particularly preferably the multiphase mixture itself to be pumped, so that damped by the stabilizing layer, the vibrations of the rotor to a specifiable, innocuous measure.
  • the first part rotor and the second part rotor are thus provided in a back-to-back arrangement in the pump housing such that the multiphase mixture can be fed via a suction opening to a first input compression stage of the first part rotor and via a first output compression stage from the first part rotor in a first cross-channel is discharged again.
  • the multiphase mixture can then be fed to a second input compression stage of the second sub-rotor and can be discharged again via a second output compression stage from the second sub-rotor via a second cross-channel and a pressure opening from the helico-axial pump.
  • the first output compression stage and the second output compression stage are each arranged adjacent to the stabilization bushing.
  • the stabilizing bush is configured and arranged on the rotor such that the stabilizing gap is formed between the stabilizing bushing and the pump housing.
  • the stabilizing bushing can be designed and arranged on the rotor such that the stabilizing gap is formed between the stabilizing bushing and the rotor.
  • a hydrodynamic stabilizing element having a stabilizing surface is additionally provided and configured in such a way that in front of the stabilizing surface of the stabilizing surface Stabilizing gap is formed so that in operation a hydrodynamic stabilizing layer of the stabilizing medium in the stabilizing gap can be formed
  • the additional stabilizing element is preferably a cover ring which surrounds the helico-axial impeller in the circumferential direction, so that the stabilizing gap between the cover ring and the pump housing is formed
  • a cover ring may be provided on all helico-axial impellers of a rotor, or only on selected individual impellers, whereby the production of the rotor, of course, becomes much less expensive and cost-effective.
  • the additional stabilizing element is provided in the form of a stabilizing sleeve between two adjacent compression stages on the rotor.
  • a stabilizing sleeve can be provided between all adjacent compression stages of a rotor, whereby a particularly good damping of the vibrations of the rotor can be achieved, especially at very high loads, or only between individual selected pairs of compression stages, whereby the production of the rotor, of course, significantly less consuming and cost-effective.
  • the stabilizing sleeve can be designed and arranged on the rotor such that the stabilizing gap is formed between the stabilizing sleeve and the pump housing, and / or the stabilizing sleeve can also be designed and arranged on the rotor such that the stabilizing gap is formed between the stabilizing sleeve and the rotor ,
  • both variants can be realized on one and the same rotor, whereby in certain cases a particularly high smoothness and particularly good damping of the rotor vibrations can be achieved.
  • a pressure difference between the multiphase mixture which is at a higher pressure level and that which is at a lower pressure level is formed in the operating state above the stabilizing gap is such that a predeterminable flow of multiphase mixture automatically adjusts itself via the stabilizing gap from the higher pressure level back to the lower pressure level, whereby a stabilizing layer for additional stabilization or damping of the damaging vibrations of the rotor automatically forms.
  • an already more highly compressed multiphase mixture taken from a compression stage in which the multiphase mixture is already more compressed than it is compressed in the stage in which it is used for the formation of the stabilization layer is particularly preferable to use an already more highly compressed multiphase mixture taken from a compression stage in which the multiphase mixture is already more compressed than it is compressed in the stage in which it is used for the formation of the stabilization layer.
  • a multiphase mixture compressed in the same compression stage may be used to form the hydrodynamic stabilization layer, which is still the case for example with reference to FIG Fig. 4 will be explained in detail.
  • the stabilizing medium for forming the stabilizing layer in special cases can also be provided by other external sources, for example by a pressure accumulator or by a pump, the medium for forming the stabilizing layer under a predetermined, in particular a controllable and / or controllable pressure for introduction into the stabilizing gap provides.
  • the stabilizing medium need not necessarily be the multiphase mixture to be pumped to form the stabilizing layer, but may also be another stabilizing medium, e.g. an oil, water or other liquid or gaseous stabilizing medium or fluid.
  • the pressure of the multiphase mixture introduced into the stabilizing gap is controlled and / or regulated by means of a valve known per se. It is also possible, for example, to supply the multiphase mixture simultaneously or alternatively from different compression stages to the stabilizing gap, whereby likewise the pressure in the stabilizing gap and thus the degree of damping or stiffness of the oscillating rotor can be set in a very simple manner and very flexibly to different requirements and changing operating conditions is customizable.
  • the stabilizing gap on the additional stabilizing element and of course on the stabilizing sleeve, for example between the stabilizing surface and the pump housing are formed and / or between the stabilizing surface and the rotor can be provided ,
  • a feed channel may be provided which is designed and arranged such that a multiphase mixture which is under a prescribable pressure and hence a prescribable amount of multiphase mixture through the feed channel to the stabilizing gap for forming the hydrodynamic stabilizing layer in the stabilizing gap can be fed, wherein the feed channel is preferably provided in a split ring.
  • the stabilizing element may for example be designed as a stator with a feed channel, wherein the feed channel is formed and arranged on the stator, that for the formation of the hydrodynamic stabilizing layer in the stabilizing gap under a predeterminable pressure a predetermined amount of a stabilizing medium, in particular to multi-phase mixture through the feed channel Stabilizing gap can be fed.
  • the feed channel can be arranged and formed on the pump housing in such a way that a predeterminable amount of stabilizing medium, in particular a multiphase mixture, can be fed to the stabilizing gap through the feed channel to form the hydrodynamic stabilizing layer in the stabilizing gap.
  • a feed channel is arranged and formed on the rotor such that a predeterminable amount of stabilizing medium, in particular a multiphase mixture, can be supplied to the stabilizing gap through the feed channel for forming the hydrodynamic stabilizing layer in the stabilizing gap.
  • the stabilization medium in particular the multiphase mixture
  • the stabilization medium can be particularly preferably fed to the feed channel from a compression stage be fed, at which a higher pressure level prevails, than at the compression stages, where it is supplied as a stabilizing medium.
  • a multiphase mixture compressed in the same compression stage can also be used to form the hydrodynamic stabilization layer.
  • the invention further relates to a rotor for arrangement in a pump housing of a helico-axial pump for conveying a multiphase mixture.
  • the rotor rotatably mounted about a longitudinal axis comprises a first part rotor and a second part rotor, and the first part rotor and the second part rotor for compression of the multiphase mixture comprises a compression stage with a helico-axial impeller and a stator.
  • a hydrodynamic stabilizing bushing with a stabilizing surface is provided between the first part rotor and the second part rotor and configured so that a stabilizing gap can be formed in front of the stabilizing surface, so that a hydrodynamic stabilizing layer can be formed from a stabilizing medium in the stabilizing gap in the operating state.
  • an additional hydrodynamic stabilizing element may be provided with a stabilizing surface in the form of a cover ring, which surrounds the helico-axial impeller in the circumferential direction, so that the stabilizing gap between the cover ring and a pump housing of the helico-axial pump can be formed.
  • the hydrodynamic stabilizing element can also be a stabilizing sleeve, which is provided, for example, between two adjacent compression stages, so that the stabilizing gap is formed between the stabilizing sleeve and the pump housing.
  • a feed channel may be provided which is designed and arranged such that a predeterminable amount of stabilizing medium, in particular a multiphase mixture, can be fed to the stabilizing gap through the feed channel to form the hydrodynamic stabilizing layer in the stabilizing gap.
  • the invention further relates to a hybrid pump with a rotor according to the invention for a helico-axial pump he present invention for the promotion of a multi-phase mixture.
  • the invention also relates to a method for hydrodynamic mounting of a rotor according to the invention in a helico-axial pump or in a hybrid pump according to the present invention, wherein in a pump housing, the rotor is rotatably supported about a longitudinal axis, and the rotor for compression of the multiphase mixture, a compression stage comprising a helico-axial impeller and a stator.
  • a hydrodynamic stabilizing bushing with a stabilizing surface is provided and configured in the pump housing in such a way that a stabilizing gap is formed in front of the stabilizing surface, so that in operation a hydrodynamic stabilizing layer is formed from a stabilizing medium in the stabilizing gap for the hydrodynamic bearing of the rotor.
  • the helico-axial pump 1 for conveying a multi-phase mixture M comprises a rotatably mounted in a pump housing 6 about a longitudinal axis A rotor 2 with a first part rotor 21 and a second part rotor 22.
  • the rotor 2 is driven by a drive 1000, which is for example an electric motor 1000.
  • the first sub-rotor 21 and the second sub-rotor 22 for compression of the multiphase M each comprise a plurality of compression stages K with a helico-axial impeller 3 and a stator 4.
  • a hydrodynamic stabilizing bushing 70 having a stabilizing surface 700 between the first sub rotor 21 and the second part rotor 22, a stabilizing gap 8 is formed in front of the stabilizing surface 700, so that a hydrodynamic stabilizing layer S can be formed from a stabilizing medium in the stabilizing gap 8 in the operating state of the pump 1.
  • the Fig. 3 shows a detailed representation of the back-to-back arrangement according to Fig. 2 in the operating state of the helico-axial pump 1.
  • the first part rotor 21 and the second part rotor 22 are arranged in a back-to-back arrangement on a common pump shaft 5 in the pump housing 6.
  • the first part rotor 21 and the second part rotor 22 are separated from each other by the stabilizing bushing 70.
  • the multiphase mixture M is fed via a suction opening 101, a first annular space R1 and a second annular space R2 of a first input compression stage K1 E of the first part rotor 21 and a first output compression stage K1 A from the first part rotor 21 in a first cross channel KR1 from the first part rotor 21 again dissipated.
  • the multiphase mixture M then becomes a second annular space R3 of a second annular space R3 of a second
  • Input compression stage K2E of the second sub-rotor 22 is supplied and discharged via a second output compression stage K2A from the second sub-rotor 22 via a second cross channel KR2, a fourth annular space R4 and a pressure port 102 from the helico-axial pump for further use again.
  • the first output compression stage K1A and the second output compression stage K2A are each arranged adjacent to the stabilizing bushing 70.
  • the stabilizing bushing 70 is designed and arranged on the rotor 2 such that the stabilizing gap 8 is formed between the stabilizing bushing 70 and the pump housing 6.
  • the stabilizing sleeve 70 may alternatively or even simultaneously configured and arranged on the rotor 2, that the Stabilizing gap 8 between the stabilizing sleeve 70 and the rotor 2 is formed.
  • FIG. 4a which shows a section with two adjacent compression stages K of a rotor 2 according to the invention in a schematic representation, an embodiment with an additional hydrodynamic stabilizing element in the form of a cover ring will be briefly discussed.
  • the rotor 2 of the helico-axial pump 1 is rotatably mounted in the pump housing 6 about a longitudinal axis A.
  • the rotor 2 comprises the compression stages K with a helico-axial impeller 3 and a stator 4 for compressing the multiphase mixture M in a manner known per se.
  • a hydrodynamic stabilizing element 7, 71 provided with a stabilizing surface 700 in the pump housing 6 and configured such that a stabilizing gap 8 is formed in front of the stabilizing surface 700, so that in the operating state here a hydrodynamic stabilizing layer S from the multiphase M in the Stabilizing gap 8 is formed.
  • Fig. 4 is the additional stabilizing element 7, a cover ring 71 which surrounds the helico-axial impeller 3 in the circumferential direction, so that the stabilizing gap 8 between the cover ring 71 and the pump housing 6 can be formed.
  • a helico-axial pump 1 according to the invention comprises only a single compression stage K
  • a helico-axial pump 1 according to the invention ie the first part rotor 21 and the second part rotor 22 in practice a plurality of compression stages K.
  • the stabilizing layer S from the stabilizing medium M in the stabilizing gap 8, characterized in that the multiphase mixture M, as shown symbolically by the double arrow M, according to presentation from the left of the representation according left compression stage K is fed and compressed by this in a conventional manner, which of course with a corresponding pressure increase is accompanied, which also establishes itself as a pressure difference .DELTA.P on the helico-axial impeller 3 compression stage K.
  • multiphase mixture M is pressed into the stabilizing gap 8 from the illustration to the right on the right, whereby the hydrodynamic stabilizing layer S between the stabilizing surface 700 of the cover ring 7 and the pump housing 6 is formed automatically the wings of the rotor 2 and the sub-rotors 21, 22 are damped and the run of the rotor 2 is stabilized.
  • the cover ring 71 may be formed either on all helico-axial wheels 3 of the rotor, or only on certain selected helico-axial wheels 3. Otherwise, depending on the application or ever according to the special requirements of the cover ring 71 completely cover a helico-axial impeller 3 or a certain predetermined range of the circumference of the helico-axial impeller third
  • Fig. 5a Based on Fig. 5a is a second embodiment according to Fig. 4 shown schematically, which differs from that of the Fig. 4 differs in that an injection of the stabilizing medium M is provided on the cover ring 71 of the helico-axial impeller 3. Here additionally stabilizing medium M is introduced through the feed channel 400, 402 in the stabilizing gap 8 to form the stabilizing layer S.
  • stabilizing medium M is introduced through the feed channel 400, 402 in the stabilizing gap 8 to form the stabilizing layer S.
  • a pressure difference .DELTA.P over the helico-axial impeller 3 in the operating state, whereby the stabilizing layer S is already partially formed.
  • an additional injection of stabilizing medium can also take place in the stabilizing gap S of the stabilizing bushing 70.
  • Fig. 5b differs from that of the Fig. 5a only in that the injection of the stabilizing medium M on the cover ring 71 of the helico-axial impeller 3 is carried out under a significantly higher pressure than in the example of Fig. 5a , This can be clearly seen from the fact that the stabilizing medium M at Fig. 5b according to the representation both to the left, ie in the direction of a compression stage K with a lower pressure level as well as to the right, ie also in the direction of a compression stage with a higher pressure level from the stabilizing gap 8 is pressed out.
  • the stabilizing medium M can be provided by an external pressure accumulator or an external pump as already described; however, is preferably provided by another compression stage K having a higher pressure level.
  • a feed channel 400, 401 in the form of a bore is provided on the stator 4, for example on a blade of the stator 4, or else a separate feed channel 400, 401 may be provided which, as in FIG Fig. 6a represented by the pump housing 6 extends to the stabilizing gap 8, so that between the rotor 2 and the stabilizing surface 700 of the stator 4 designed as a stabilizing element 73, a stabilizing layer S according to the invention from stabilizing medium M, which in the specific example of Fig. 6a Multi-phase mixture M from another compression stage is, can be formed.
  • Fig. 6b is another embodiment according to Fig. 6a represented, which differs from that of Fig. 6a only differs in that the helico-axial impeller 3 no cover ring 71 is provided.
  • Such a simplified construction can be used successfully, for example, whenever the stabilization of the rotor 2 by the stabilization layer S on the stator 4 is already sufficient.
  • Fig. 6c shows a further variant of the embodiment according to Fig. 6b ,
  • the supply of the stabilizing medium M does not take place via a feed channel 400, 401 through the pump housing 6, but the injection of the stabilizing medium M takes place through a feed channel 400, 403, which is formed in the rotor 2.
  • the rotor 2 may, for example, have a hollow rotor shaft or suitable channels or lines may be formed in the rotor shaft through which the stabilizing medium M, for example multi-phase mixture M, can be supplied from a compression stage K with a higher pressure level.
  • the Fig. 7a shows a fourth, different embodiment according to Fig. 4 in which between two adjacent compression stages K, an additional stabilizing sleeve 72 is provided, wherein injection of the stabilizing medium M in the stabilizing gap 8 by a guided through the pump housing 6 feed channel 400, 402 takes place.
  • the injection into the stabilizing gap 8 can in principle also be analogous to Fig. 6c take place through the rotor shaft of the rotor 2.
  • Fig. 7b shown of course also possible that can be dispensed with all or different helico-axial wheels 3 on the bezel.
  • a stabilizing sleeve 72 may be provided within a compression stage K between the helico-axial impeller 3 and the stator 4.
  • a stabilizing sleeve 72 must be provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP11161758.5A 2010-05-11 2011-04-08 Pompe hélico-axiale et procédé pour supporter un rotor dans une pompe hélico-axiale Active EP2386767B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11161758.5A EP2386767B1 (fr) 2010-05-11 2011-04-08 Pompe hélico-axiale et procédé pour supporter un rotor dans une pompe hélico-axiale

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP10162520 2010-05-11
EP11161758.5A EP2386767B1 (fr) 2010-05-11 2011-04-08 Pompe hélico-axiale et procédé pour supporter un rotor dans une pompe hélico-axiale

Publications (3)

Publication Number Publication Date
EP2386767A2 true EP2386767A2 (fr) 2011-11-16
EP2386767A3 EP2386767A3 (fr) 2017-11-01
EP2386767B1 EP2386767B1 (fr) 2021-01-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11161758.5A Active EP2386767B1 (fr) 2010-05-11 2011-04-08 Pompe hélico-axiale et procédé pour supporter un rotor dans une pompe hélico-axiale

Country Status (3)

Country Link
US (1) US9234529B2 (fr)
EP (1) EP2386767B1 (fr)
BR (1) BRPI1102495B1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3657024A1 (fr) 2018-11-21 2020-05-27 Sulzer Management AG Pompe à phases multiples
EP3536975B1 (fr) 2018-03-07 2021-04-28 OneSubsea IP UK Limited Système et méthodologie pour faciliter le pompage de fluide

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150167652A1 (en) * 2013-12-18 2015-06-18 General Electric Company Submersible pumping system and method
CA3133286C (fr) * 2014-02-24 2023-11-07 Baker Hughes Esp, Inc. Processeur a compresseur de gaz humide de fond de trou
US10844701B2 (en) 2019-02-05 2020-11-24 Saudi Arabian Oil Company Balancing axial thrust in submersible well pumps
US11326607B2 (en) 2019-02-05 2022-05-10 Saudi Arabian Oil Company Balancing axial thrust in submersible well pumps
EP3812595A1 (fr) * 2019-10-25 2021-04-28 Sulzer Management AG Pompe multiphase avec amortisseur de palier à film de fluide comprimé
EP3913226A1 (fr) 2020-05-18 2021-11-24 Sulzer Management AG Pompe à phases multiples
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
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US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1561454A (en) 1976-12-20 1980-02-20 Inst Francais Du Petrole Devices for pumping a fluid comprising at least a liquid
EP0486877A1 (fr) 1990-11-20 1992-05-27 Chiron-Werke GmbH & Co. KG Machine outil et méthode pour ouvrir et fermer une griffe
US5961282A (en) 1996-05-07 1999-10-05 Institut Francais Du Petrole Axial-flow and centrifugal pumping system

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4606700A (en) * 1979-10-15 1986-08-19 Vsesojuzny Naucho-Issledovatelsky Institut Burovoi Tekhniki Turbodrill multistage turbine
FR2670539B1 (fr) * 1990-12-14 1994-09-02 Technicatome Pompe multi-etagee destinee particulierement au pompage d'un fluide multiphasique.
US5445494A (en) * 1993-11-08 1995-08-29 Bw/Ip International, Inc. Multi-stage centrifugal pump with canned magnetic bearing
GB2312929B (en) * 1996-05-07 2000-08-23 Inst Francais Du Petrole Axial-flow and centrifugal pump system
US5961301A (en) * 1997-07-31 1999-10-05 Ansimag Incorporated Magnetic-drive assembly for a multistage centrifugal pump
FR2771024B1 (fr) * 1997-11-19 1999-12-31 Inst Francais Du Petrole Dispositif et procede de compression diphasique d'un gaz soluble dans un solvant
GB9724899D0 (en) * 1997-11-26 1998-01-28 Triangle Engineering Consultan Downhole pump/motor assembly
CA2299606C (fr) * 2000-02-25 2007-08-21 Cn & Lt Consulting Ltd. Ensemble support pour forage de puits
US6547514B2 (en) * 2001-06-08 2003-04-15 Schlumberger Technology Corporation Technique for producing a high gas-to-liquid ratio fluid
EP1452688A1 (fr) * 2003-02-05 2004-09-01 Siemens Aktiengesellschaft Rotor pour une turbine à vapeur, procédé et utilisation de refroidissement d'un tel rotor
US20040258518A1 (en) * 2003-06-18 2004-12-23 Steven Buchanan Self-lubricating ceramic downhole bearings

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1561454A (en) 1976-12-20 1980-02-20 Inst Francais Du Petrole Devices for pumping a fluid comprising at least a liquid
EP0486877A1 (fr) 1990-11-20 1992-05-27 Chiron-Werke GmbH & Co. KG Machine outil et méthode pour ouvrir et fermer une griffe
US5961282A (en) 1996-05-07 1999-10-05 Institut Francais Du Petrole Axial-flow and centrifugal pumping system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3536975B1 (fr) 2018-03-07 2021-04-28 OneSubsea IP UK Limited Système et méthodologie pour faciliter le pompage de fluide
EP3657024A1 (fr) 2018-11-21 2020-05-27 Sulzer Management AG Pompe à phases multiples
EP4063665A1 (fr) 2018-11-21 2022-09-28 Sulzer Management AG Pompe à phases multiples

Also Published As

Publication number Publication date
EP2386767B1 (fr) 2021-01-06
EP2386767A3 (fr) 2017-11-01
US9234529B2 (en) 2016-01-12
BRPI1102495B1 (pt) 2021-07-20
BRPI1102495A2 (pt) 2012-11-06
US20110280741A1 (en) 2011-11-17

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