EP2386767A2 - Helico-axial pump, rotor for same, method for hydrodynamic bearing of a rotor of a helicon-axial pump and a hybrid pump with a rotor for a helico-axial pump - Google Patents
Helico-axial pump, rotor for same, method for hydrodynamic bearing of a rotor of a helicon-axial pump and a hybrid pump with a rotor for a helico-axial pump Download PDFInfo
- 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
- Authority
- 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
Links
- 238000000034 method Methods 0.000 title claims abstract description 5
- 230000006835 compression Effects 0.000 claims abstract description 84
- 238000007906 compression Methods 0.000 claims abstract description 84
- 239000000203 mixture Substances 0.000 claims abstract description 67
- 230000006641 stabilisation Effects 0.000 claims abstract description 20
- 238000011105 stabilization Methods 0.000 claims abstract description 20
- 230000000087 stabilizing effect Effects 0.000 claims description 260
- 230000015572 biosynthetic process Effects 0.000 claims description 5
- 239000003381 stabilizer Substances 0.000 claims 1
- 238000002347 injection Methods 0.000 description 13
- 239000007924 injection Substances 0.000 description 13
- 239000007789 gas Substances 0.000 description 10
- 239000012071 phase Substances 0.000 description 10
- 238000013016 damping Methods 0.000 description 9
- 239000007788 liquid Substances 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 230000001419 dependent effect Effects 0.000 description 2
- 239000007792 gaseous phase Substances 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000003534 oscillatory effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 239000010779 crude oil Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
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.
Landscapes
- 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)
Abstract
Description
Die Erfindung betrifft eine helico-axiale Pumpe zur Förderung von Mehrphasengemischen, einen Rotor für eine helico-axiale Pumpe, eine Hybridpumpe mit einer helico-axialen Pumpe sowie ein Verfahren zur Lagerung eines Rotors in einer helico-axialen Pumpe gemäss dem Oberbegriff der unabhängigen Ansprüche 1, 10, 13 und 14.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.
Bei der Förderung von Mehrphasengemischen, wie beispielsweise Rohöl, das neben Erdöl auch Erdgas und häufig auch Wasser und Feststoffanteile wie z.B. Sand enthält, stellt sich das Problem, dass mit steigendem Gasanteil im Mehrphasengemisch der Wirkungsgrad der verwendeten Pumpvorrichtungen abnimmt. Beispielsweise ist bei niedrigen Gasdichten der Einsatz von Pumpvorrichtungen mit radialen Laufrädern bereits ab einem volumetrischen Gas/Flüssigkeitsverhältnis von grösser als 0.04 bis 0.06 nicht mehr möglich bzw. nicht mehr wirtschaftlich. In herkömmlichen Förderanlagen wird deshalb bei einem höheren Gasanteil die gasförmige Phase der Mehrphasengemische von der flüssigen zunächst abgetrennt und die beiden Phasen dann getrennt unter jeweils unterschiedlichen Förderbedingungen gefördert. Eine derartige Trennung der flüssigen und gasförmigen Phase der Mehrphasengemische ist abhängig von den speziellen Einsatzbedingungen am Ort der Förderung und nicht immer möglich oder wirtschaftlich. Es wurden deshalb spezielle Pump- oder Kompressionsvorrichtungen entwickelt, um das volumetrische Gas/Flüssigkeitsverhältnis der zu fördernden Mehrphasengemische soweit zu verringern, dass anschliessend eine herkömmliche Pumpvorrichtung für die weitere Förderung eingesetzt werden kann, beispielsweise eine Verdrängerpumpe, eine Rotationspumpe oder eine Strahlpumpe.In the promotion of multiphase mixtures, such as crude oil, which in addition to petroleum also contains natural gas and often also water and solid fractions such as sand, there is the problem that with increasing proportion of gas in the multiphase mixture, the efficiency of the pumping devices used decreases. For example, at low gas densities, the use of pumping devices with radial impellers is already no longer possible or no longer economical even at a volumetric gas / liquid ratio of greater than 0.04 to 0.06. In conventional conveyor systems, therefore, the gaseous phase of the multiphase mixtures is first separated from the liquid at a higher gas content and the two phases are then conveyed separately under different delivery conditions. Such a separation of the liquid and gaseous phase of the multiphase mixtures is dependent on the specific conditions of use at the site of promotion and not always possible or economical. Special pump or compression devices have therefore been developed in order to reduce the volumetric gas / liquid ratio of the multiphase mixtures to be delivered to such an extent that subsequently a conventional pumping device can be used for further delivery, for example a positive displacement pump, a rotary pump or a jet pump.
Derartige Pump- oder Kompressionsvorrichtung für Mehrphasengemische mit erhöhtem Gasanteil sind beispielsweise bereits aus der
Beispielsweise ist die Hybridpumpe gemäss
Wie bereits erwähnt, umfasst die als Verdichter wirkende helico-axiale Pumpe einen Rotor mit mehreren Kompressionsstufen, in der Praxis zum Beispiel mit bis zu sechzehn oder mehr Stufen, so dass das Mehrphasengemisch schrittweise von einer relativ niedrigen Dichte mit einem hohen relativen Volumenanteil an Gas bis zu einem hoch verdichteten Mehrphasengemisch mit einer so hohen Dichte komprimierbar ist, dass das hoch komprimierte Gemisch mit einer gewöhnlichen Förderpumpe weitergefördert werden kann.As already mentioned, 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.
Eine an sich bekannte Kompressionsstufe K' eines Rotors 2' einer helico-axialen Pumpe 1' ist schematisch in
Jede Kompressionsstufe K' umfasst dabei ein rotierendes Laufrad 3' mit Schraube 31', wobei das rotierende Laufrad 3' einer kurzen archimedischen Schraube ähnelt, und einen daran anschliessenden Stator 4', der aus einer Mehrzahl von statischen, also nicht rotierenden Schaufeln 41' besteht. Laufrad 3' und Stator 4' sind dabei derart in Bezug auf eine gemeinsame Pumpenwelle 5', montiert, dass das Laufrad 3' im Betriebszustand von der Pumpenwelle 5' in Rotation versetzt wird, während der Stator 4' von der Drehbewegung der Pumpenwelle 5' entkoppelt ist und daher in Bezug auf das Laufrad 3' nicht rotiert. Die Pumpenwelle 5' erstreckt sich dabei entlang einer Längsangsachse A'. Die Mehrzahl der Kompressionsstufen K' sind dabei in einem im wesentlichen rohrartigen Pumpengehäuse 6' in Serie hintereinander angeordnet.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.
Die rotierende Schraube 31' fördert das Mehrphasengemisch M' in Pfeilrichtung z.B. aus einer in
Um eine ausreichend hohe Kompression des Mehrphasengemischs M' zu erhalten, müssen in der Praxis, wie bereits erwähnt, eine grössere Anzahl von zum Beispiel bis zu sechzehn oder noch mehr Kompressionsstufen K', jeweils bestehend aus einem Laufrad 3' und einem Stator 4' in Serie vorgesehen werden, was zwangläufig zu einer beträchtlichen Baulänge der helico-axialen Pumpe 1' führt.In order to obtain a sufficiently high compression of the multiphase mixture M ', in practice, as already mentioned, a larger number of, for example, up to sixteen or more compression stages K', each consisting of an impeller 3 'and a stator 4' in Series are provided, which inevitably leads to a considerable length of the helico-axial pump 1 '.
Der entscheidende Nachteil solch langer Rotoren 2' gebildet aus einer Vielzahl von Kompressionsstufen K' ist daher, dass sie schwingungsmässig nur sehr schwer zu beherrschen sind. Diese langen Rotoren 2' bilden im Inneren des rohrförmigen Pumpengehäuses 6' nämlich ein schwingungsfähiges System, das insbesondere verschiedene transversale Schwingungsmoden ausbilden kann, die so intensiv sein können, dass die Pumpe bei einer vorgegebenen Umdrehungszahl bzw. in einem bestimmten Umdrehungsfeld nicht mehr betrieben werden kann. Darüber hinaus kann auch der Wirkungsgrad der Pumpen 1' reduziert sein und im schlimmsten Fall sogar Beschädigungen der Pumpe 1' zu befürchten sind, wenn der Rotor 2' zum Beispiel so stark und unkontrolliert zu schwingen beginnt, dass Teile des Rotors 2', wie etwa die Laufräder 3' durch die Schwingungsbewegung beispielsweise mit dem Pumpengehäuse in Kontakt kommen. Dabei hängt die Art und Intensität der Schwingungen des Rotors 2' nicht nur von der speziellen Geometrie sondern auch vom Betriebszustand der Pumpe 1', des zu pumpenden Mehrphasengemischs M', der Drehzahl der Pumpe 1' und weiteren bekannten und zum Teil nicht genau bekannten Parametern ab, so dass es kaum möglich ist, allein durch eine Anpassung der geometrischen Verhältnisse bekannter Pumpen 1' oder durch Verwendung neuer Materialien die Probleme mit den schädlichen Schwingungen des Rotors 2' in den Griff zu bekommen.The decisive disadvantage of such long rotors 2 'formed from a plurality of compression stages K' is that they are very difficult to control in terms of vibration. These long rotors 2 'form in the interior of the tubular pump housing 6' namely a vibratory system, which in particular can form different transverse vibration modes that can be so intense that the Pump can not be operated at a given number of revolutions or in a certain revolution field. In addition, 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.
Dabei besteht der deutliche Wunsch nach Pumpen mit einer immer höheren Anzahl von Kompressionsstufen, damit Mehrphasengemische mit immer höherem Gasanteil immer besser, das heisst zu immer höheren Drücken komprimiert werden können, so dass das so komprimierte Mehrphasengemisch zuverlässiger und über immer noch grössere Druck- bzw. Höhendifferenzen weiter gepumpt werden kann.There is a clear desire for pumps with an ever higher number of compression stages, so that multi-phase mixtures with ever higher gas content always better, that can be compressed to ever higher pressures, so that the thus compressed multiphase more reliable and still greater pressure or Height differences can be pumped further.
Aufgabe der Erfindung ist es daher, eine helico-axiale Pumpe zur Förderung von Mehrphasengemischen vorzuschlagen, bei welcher die schädlichen Schwingungen des Rotors weitgehend vermieden werden und die Schwingungen des Rotors auf ein vorgebbares Mass reduziert bzw. gedämpft sind, so dass einerseits ein verbesserter Lauf des Rotors im Betriebszustand erreicht werden kann und die Pumpe andererseits bei Drehzahlen bzw. in einem Um drehungsfeld betrieben werden kann, in dem die aus dem Stand der Technik bekannten Helico-axialen Pumpen aufgrund der oben beschriebenen schädlichen Schwingungen des Rotors nicht betrieben werden können. Daneben soll die neue Pumpe alternativ oder gleichzeitig mit mehr Kompressionsstufen ausgestattet werden können, als das bei den bisher im Stand der Technik bekannten Pumpen möglich ist, bei welchen die Länge der Pumpe und damit die maximale Zahl der Kompressionsstufen durch die Schwingungen des Rotors im Betriebszustand begrenzt ist.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. In addition, 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.
Die diese Aufgabe lösenden Gegenstände der Erfindung sind durch die Merkmale der unabhängigen Ansprüche der jeweiligen Kategorie gekennzeichnet.The objects of the invention which solve this object are characterized by the features of the independent claims of the respective category.
Die abhängigen Ansprüche beziehen sich auf besonders vorteilhafte Ausführungsformen der Erfindung.The dependent claims relate to particularly advantageous embodiments of the invention.
Die Erfindung betrifft somit eine helico-axiale Pumpe zur Förderung eines Mehrphasengemischs, welche helico-axiale Pumpe einen in einem Pumpengehäuse um eine Längsachse drehbar gelagerten Rotor mit einem ersten Teilrotor und einen zweiten Teilrotor umfasst, wobei der erste Teilrotor und der zweite Teilrotor zur Kompression des Mehrphasengemischs eine Kompressionsstufe mit einem helico-axialen Laufrad und einem Stator umfasst. Erfindungsgemäss ist eine hydrodynamische Stabilisierungsbuchse mit einer Stabilisierungsfläche derart zwischen dem ersten Teilrotor und dem zweiten Teilrotor vorgesehen und ausgestaltet, dass vor der Stabilisierungsfläche ein Stabilisierungsspalt ausgebildet ist, so dass im Betriebszustand eine hydrodynamische Stabilisierungsschicht aus einem Stabilisierungsmedium im Stabilisierungsspalt bildbar ist.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. According to the invention, 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.
Wesentlich für die Erfindung ist es somit, dass ein hydrodynamische Stabilisierungsbuchse mit einer Stabilisierungsfläche im Pumpengehäuse vorgesehen ist, so dass vor der Stabilisierungsfläche ein Stabilisierungsspalt ausgebildet ist, in welchem Stabilisierungsspalt im Betriebszustand der Pumpe eine hydrodynamische Stabilisierungsschicht gebildet wird.It is therefore essential for the invention that 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.
Durch die vorliegende Erfindung wird somit die Rotordynamik entscheidend verbessert, weil durch die Stabilisierungsschicht die Dämpfung und Steifigkeit des schwingungsfähigen Rotorsystems entscheidend erhöht wird.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.
Die schädlichen Schwingungen des Rotors werden durch die Ausbildung der Stabilisierungsschicht im Stabilisierungsspalt vor der Stabilisierungsfläche der Stabilisierungsbuchse weitgehend vermieden und werden zumindest auf ein vorgebbares tolerierbares Mass reduziert bzw. gedämpft, so dass die Pumpe auch bei einer Umdrehungszahl bzw. in einem bestimmten Umdrehungsfeld betrieben werden kann, wo das ohne Verwendung der erfindungsgemässen Stabilisierungsschicht bisher nicht mehr möglich ist. Darüber hinaus kann eventuell sogar ein höherer Wirkungsgrad der Pumpe und ein ruhigerer verbesserter Lauf des Rotors im Betriebszustand erreicht werden. Was letztlich natürlich dazu führt, dass nicht nur Energie für den Betrieb der Pumpe eingespart werden kann, sondern auch die Wartungsintervalle verlängert werden können, wodurch die damit verbundenen Kosten drastisch gesenkt werden können und gleichzeitig auch die Lebensdauer der Pumpe wesentlich erhöht wird.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. In addition, 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.
Ein weiterer besonderer Vorteil besteht darin, dass es durch die Erfindung erstmals möglich ist, Pumpen mit einer viel höheren Anzahl von Kompressionsstufen zu konstruieren, als das bisher möglich war. Bisher war die mögliche Anzahl der Kompressionsstufen allein schon durch die mit steigender Zahl der Kompressionsstufen massiv ansteigenden Schwingungen des Rotors eingeschränkt. Durch die Erfindung ist der Rotor praktisch auf einer beliebigen Länge sicher stabilisierbar.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.
Dabei bildet sich bei einer erfindungsgemässen helico-axialen Pumpe die Stabilisierungsschicht im Stabilisierungsspalt vor der Stabilisierungsfläche der hydrodynamischen Stabilisierungsbuchse quasi automatisch aus, so dass in einem einfachen Ausführungsbeispiel, das jedoch in der Praxis von besonderer Bedeutung ist, ausser einer geeigneten Einstellung der Grösse oder Form des Stabilisierungsspaltes bzw. der Stabilisierungsbuchse und / oder deren Stabilisierungsfläche keine weiteren baulichen Massnahmen vorgenommen werden müssen.In the case of a helico-axial pump according to the invention, 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.
Ist die Geometrie des Stabilisierungsspalt bei einer erfindungsgemässen helico-axialen Pumpe entsprechend den Anforderungen eingestellt, bildet sich im Betriebszustand über dem Stabilisierungsspalt eine Druckdifferenz zwischen dem Mehrphasengemisch, das sich im ersten Teilrotor befindet und demjenigen, das sich im zweiten Teilrotor befindet, derart aus, dass sich ein vorgebbarer Fluss von Mehrphasengemisch vom zweiten Teilrotor über den Stabilisierungsspalt zurück zum ersten Teilrotor automatisch einstellt, wodurch sich automatisch eine Stabilisierungsschicht zur Stabilisierung bzw. Dämpfung der schädlichen Schwingungen des Rotor ausbildet.If the geometry of the stabilizing gap in a helico-axial pump according to the invention is set according to the requirements, 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.
Dabei ist der Grad, also die Stärke der Dämpfung je nach technischen Anforderungen oder Spezifikationen bei einer erfindungsgemässen helico-axialen Pumpe auf einfache Weise anpassbar. Dies kann zum Beispiel durch geeignete Wahl der Geometrie, beispielsweise der geometrische Form oder Breite des Stabilisierungsspalts geschehen.In this case, 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.
Eine erfindungsgemässe helico-axiale Pumpe ist dabei besonders bevorzugt in Form einer sogenannten Back-to-Back Anordnung ausgestaltet. Unter einer Back-to-Back Anordnung versteht der Fachmann eine Anordnung von zwei Pumpenrotoren in Serie, die so eine Pumpe mit zwei Druckstufen ausbildet. Das zu pumpende Medium wird dabei über eine Saugöffnung der Pumpe der ersten Druckstufe zugeführt, wobei das Medium die erste Druckstufe in einer ersten axialen Richtung durchläuft, wobei dabei der Druck des zu pumpenden Mediums auf einen ersten Zwischendruck erhöht wird. Aus der ersten Druckstufe wird das Medium dann über ein Kanalsystem der zweiten Druckstufe derart zugeführt, dass das Medium die zweite Druckstufe in einer zweiten axialen Richtung durchläuft, die der ersten axialen Richtung der ersten Druckstufe entgegen gesetzt ist. In der zweiten Druckstufe wird das Medium dann auf den gewünschten Enddruck gebracht und über eine Drucköffnung zur weiteren Verwendung aus der Pumpe abgeführt.An inventive helico-axial pump is particularly preferably designed in the form of a so-called back-to-back arrangement. Under a 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. From the first pressure stage, 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. In 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.
Wesentlich für die Back-to-Back Anordnung der aus dem Stand der Technik bekannten Pumpen, die sämtlich keine helico-axialen Pumpen sind, ist dabei, dass die Flussrichtung des Medium in der ersten Druckstufe entgegengesetzt zur Flussrichtung in der zweiten Druckstufe ist. Bei den bekannten Pumpen dient die Back-to-Back Anordnung nämlich ausschliesslich dazu, die enormen Schubkräfte, die in axialer Richtung auf die Lager der Pumpenwelle wirken, zumindest teilweise zu kompensieren und damit die Lager zu entlasten. Die enormen axialen Schubkräfte sind dabei darauf zurückzuführen, dass in diesen aus dem Stand der Technik bekannten Pumpen sehr hohe Drücke mit sehr grossen Komponenten in axialer Richtung erzeugt werden. Schwingungen des Pumpenrotors spielen hier eine sehr untergeordnete Rolle, weil die Rotoren selbst in der Regel keine grosse axiale Ausdehnung haben und / oder nur aus je einer Kompressionsstufe bestehen und / oder zwischen der ersten Druckstufe und der zweiten Druckstufe ein zusätzliches mechanisches Lager, zum Beispiel ein Kugellager vorgesehen ist, das den Pumpenrotor in der Mitte zusätzlich mechanisch lagert.Essential for 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. In the known pumps, 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. Vibration of the pump rotor play a very minor role here, because the rotors themselves usually have no large axial extent and / or consist of only one compression stage and / or between the first pressure stage and the second pressure stage an additional mechanical bearing, for example Ball bearing is provided, which additionally stores the pump rotor in the middle mechanically.
Da bei helico-axialen Pumpen die axialen Druckkomponenten im Vergleich zu anderen konventionellen Pumpen eher klein sind, spielen hier die Schubkräfte, die in axialer Richtung auf die Lager der helico-axialen Pumpe wirken, keine entscheidende Rolle. Daher wurde eine Back-to-Back Anordnung für helico-axiale Pumpen bisher auch nie in Betracht gezogen, weil bei helico-axialen Pumpen der bekannte Vorteil der Back-to-Back Anordnung eigentlich nicht ausgenutzt werden kann.Since in helico-axial pumps, the axial pressure components are rather small compared to other conventional pumps, the thrust forces which act in the axial direction on the bearings of the helico-axial pump play no decisive role here. Therefore, a back-to-back arrangement for helico-axial pump has never been considered, because in helico-axial pumps, the known advantage of the back-to-back arrangement can not actually be exploited.
Die wesentliche Erkenntnis der Erfindung ist es daher, dass die Back-to-Back Anordnung im Falle von helico-axialen Pumpen dann erfolgreich eingesetzt werden kann, wenn zwischen dem ersten Teilrotor und dem zweiten Teilrotor eine erfindungsgemässe Stabilisierungsbuchse vorgesehen wird, so dass sich aufgrund des Druckgefälles zwischen dem ersten Teilrotor und dem zweiten Teilrotor im Stabilisierungsspalt eine Stabilisierungsschicht aus dem Stabilisierungsmedium ausbilden kann, das besonders bevorzugt das zu pumpende Mehrphasengemisch selbst ist, so dass durch die Stabilisierungsschicht die Schwingungen des Rotors auf ein vorgebbares, unschädliches Mass gedämpft werden.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.
In einem besonders bevorzugten Ausführungsbeispiel ist somit der erste Teilrotor und der zweite Teilrotor derart in einer Back-to-Back Anordnung im Pumpengehäuse vorgesehen, dass das Mehrphasengemisch über eine Saugöffnung einer ersten Eingangskompressionsstufe des ersten Teilrotors zuführbar ist und über eine erste Ausgangskompressionsstufe aus dem ersten Teilrotor in einen ersten Kreuzkanal wieder abführbar ist. Aus dem ersten Kreuzkanal ist das Mehrphasengemisch dann einer zweiten Eingangskompressionsstufe des zweiten Teilrotors zuführbar und über eine zweite Ausgangskompressionsstufe aus dem zweiten Teilrotor über einen zweiten Kreuzkanal und eine Drucköffnung aus der helico-axialen Pumpe wieder abführbar. Dabei sind die erste Ausgangskompressionsstufe und die zweite Ausgangskompressionsstufe jeweils benachbart zur Stabilisierungsbuchse angeordnet.In a particularly preferred embodiment, 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. From the first cross-channel, 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. In this case, the first output compression stage and the second output compression stage are each arranged adjacent to the stabilization bushing.
Wie in den Zeichnungen später noch genauer erläutert werden wird, ist die Stabilisierungsbuchse dabei derart ausgestaltet und am Rotor angeordnet, dass der Stabilisierungsspalt zwischen der Stabilisierungsbuchse und dem Pumpengehäuse ausgebildet ist. Gleichzeitig oder alternativ kann die Stabilisierungsbuchse jedoch derart ausgestaltet und am Rotor angeordnet sein, dass der Stabilisierungsspalt zwischen der Stabilisierungsbuchse und dem Rotor ausgebildet ist.As will be explained in more detail later in the drawings, 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. At the same time or alternatively, however, 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.
Bei einem für die Praxis ebenfalls wichtigen Ausführungsbeispiel ist zusätzlich ein hydrodynamisches Stabilisierungselement mit einer Stabilisierungsfläche derart vorgesehen und ausgestaltet, dass vor der Stabilisierungsfläche der Stabilisierungsspalt ausgebildet ist, so dass im Betriebszustand eine hydrodynamische Stabilisierungsschicht aus dem Stabilisierungsmedium im Stabilisierungsspalt bildbar ist, wobei das zusätzliche Stabilisierungselement bevorzugt ein Deckring ist, der das helico-axiale Laufrad in Umfangsrichtung umschliesst, so dass der Stabilisierungsspalt zwischen dem Deckring und dem Pumpengehäuse ausgebildet ist. Dabei kann ein solcher Deckring an allen helico-axialen Laufrädern eines Rotors vorgesehen sein, oder nur an ausgewählten einzelnen Laufrädern, wodurch die Herstellung des Rotors natürlich deutlich weniger aufwändig und kostengünstiger wird.In an embodiment which is likewise important for practice, 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, wherein 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 , In this case, such 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.
Bei einem anderen wichtigen Ausführungsbeispiel der vorliegenden Erfindung ist das zusätzliche Stabilisierungselement in Form einer Stabilisierungshülse zwischen zwei benachbarten Kompressionsstufen am Rotor vorgesehen. Wobei eine Stabilisierungshülse zwischen allen benachbarten Kompressionsstufen eines Rotors vorgesehen sein kann, wodurch vor allem bei sehr hohen Belastungen eine besonders gute Dämpfung der Schwingungen des Rotors erreichbar ist, oder aber auch nur zwischen einzelnen ausgewählten Paaren von Kompressionsstufen, wodurch die Herstellung des Rotors natürlich deutlich weniger aufwändig und kostengünstiger wird.In another important embodiment of the present invention, the additional stabilizing element is provided in the form of a stabilizing sleeve between two adjacent compression stages on the rotor. Whereby 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.
Die Stabilisierungshülse kann dabei derart ausgestaltet und am Rotor angeordnet sein, dass der Stabilisierungsspalt zwischen der Stabilisierungshülse und dem Pumpengehäuse ausgebildet ist, und / oder die Stabilisierungshülse kann auch derart ausgestaltet und am Rotor angeordnet sein, dass der Stabilisierungsspalt zwischen der Stabilisierungshülse und dem Rotor ausgebildet ist. Im Speziellen können an ein und demselben Rotor beide Varianten verwirklicht sein, wodurch sich in bestimmten Fällen eine besondere hohe Laufruhe und besonders gute Dämpfung der Rotorschwingungen erreichen lässt.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 , In particular, 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.
Ist die Geometrie des Stabilisierungsspalts des zusätzlichen hydrodynamischen Stabilisierungselements bei einer erfindungsgemässen helico-axialen Pumpe entsprechend den Anforderungen eingestellt, bildet sich im Betriebszustand über dem Stabilisierungsspalt eine Druckdifferenz zwischen dem Mehrphasengemisch, das sich auf einem höheren Druckniveau befindet und demjenigen, das sich auf einem niedrigeren Druckniveau befindet, derart aus, dass sich ein vorgebbarer Fluss von Mehrphasengemisch über den Stabilisierungsspalt vom höheren Druckniveau zurück zum niedrigeren Druckniveau automatisch einstellt, wodurch sich automatisch eine Stabilisierungsschicht zur zusätzlichen Stabilisierung bzw. Dämpfung der schädlichen Schwingungen des Rotor ausbildet.If the geometry of the stabilizing gap of the additional hydrodynamic stabilizing element in a helico-axial pump according to the invention is set according to the requirements, 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.
Zur Ausbildung der hydrodynamischen Stabilisierungsschicht können jedoch auch zusätzliche Massnahmen ergriffen werden, insbesondere wenn die auftretenden Schwingungen sehr stark sind bzw. wenn die Dämpfung in Abhängigkeit von bestimmten Betriebsparametern, wie zum Beispiel der Last, unter der die Pumpe betrieben wird, oder in Abhängigkeit von der Umdrehungszahl eingestellt werden soll.However, additional measures can be taken to form the hydrodynamic stabilizing layer, in particular if the oscillations occurring are very strong or if the damping depends on certain operating parameters, such as the load under which the pump is operated, or depending on the RPM should be set.
So kann besonders bevorzugt ein bereits höher komprimiertes Mehrphasengemisch benutzt werden, das einer Kompressionsstufe entnommen wird, in der das Mehrphasengemisch bereits stärker komprimiert ist, als es in der Stufe komprimiert wird, in der es für die Bildung der Stabilisierungsschicht benutzt wird. Alternativ oder gleichzeitig kann jedoch zur Ausbildung der hydrodynamischen Stabilisierungsschicht ein in derselben Kompressionsstufe komprimiertes Mehrphasengemisch verwendet werden, was zum Beispiel noch anhand der
Es versteht sich dabei, dass das Stabilisierungsmedium zur Bildung der Stabilisierungsschicht in speziellen Fällen auch von anderen externen Quellen zur Verfügung gestellt werden kann, zum Beispiel von einem Druckspeicher oder von einer Pumpe, die das Medium zur Bildung der Stabilisierungsschicht unter einem vorgebbaren, im Speziellen unter einem steuer- und / oder regelbaren Druck zur Einleitung in den Stabilisierungsspalt zur Verfügung stellt. Auch muss das Stabilisierungsmedium zur Bildung der Stabilisierungsschicht nicht zwingend das zu pumpende Mehrphasengemisch sein, sondern kann auch ein anderes Stabilisierungsmedium, z.B. ein Öl, Wasser oder ein anderes flüssiges oder gasförmiges Stabilisierungsmedium bzw. Fluid sein.It is understood that 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. Also, 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.
Weiter ist es zum Beispiel möglich, dass mittels eines an sich bekannten Ventils der Druck des in den Stabilisierungsspalt eingeleiteten Mehrphasengemischs gesteuert und / oder geregelt wird. Auch ist es beispielsweise möglich, das Mehrphasengemisch gleichzeitig oder alternativ aus verschiedenen Kompressionsstufen dem Stabilisierungsspalt zuzuführen, wodurch ebenfalls der Druck im Stabilisierungsspalt und damit der Grad der Dämpfung bzw. der Steifigkeit des schwingungsfähigen Rotors auf sehr einfach Weise eingestellt werden kann und sehr flexibel auf unterschiedliche Anforderungen und wechselnde Betriebsbedingungen anpassbar ist.Furthermore, it is possible, for example, for the pressure of the multiphase mixture introduced into the stabilizing gap to be 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.
Wie später noch anhand der Zeichnungen exemplarisch an besonders bevorzugten Ausführungsbeispielen erläutert werden wird, kann der Stabilisierungsspalt am zusätzlichen Stabilisierungselement und selbstverständlich auch an der Stabilisierungsbuchse, zum Beispiel zwischen der Stabilisierungsfläche und dem Pumpengehäuse ausgebildet sind und / oder auch zwischen der Stabilisierungsfläche und dem Rotor vorgesehen werden.As will be explained later by way of example with reference to the drawings of particularly preferred embodiments, 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 ,
Dabei kann in einer besonders bevorzugten Ausführungsvariante der vorliegenden Erfindung ein Zuführkanal vorgesehen sein, der so ausgebildet und angeordnet ist, dass zur Ausbildung der hydrodynamischen Stabilisierungsschicht im Stabilisierungsspalt ein unter einem vorgebbaren Druck stehendes Mehrphasengemisch und daraus resultierend eine vorgebbare Menge an Mehrphasengemisch durch den Zuführkanal dem Stabilisierungsspalt zuführbar ist, wobei der Zuführkanal bevorzugt in einem Spaltring vorgesehen ist.In this case, in a particularly preferred embodiment of the present invention, 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.
So kann das Stabilisierungselement zum Beispiel als Stator mit einem Zuführkanal ausgestaltet sein, wobei der Zuführkanal so am Stator ausgebildet und angeordnet ist, dass zur Ausbildung der hydrodynamischen Stabilisierungsschicht im Stabilisierungsspalt unter einem vorgebbaren Druck eine vorgebbare Menge eines Stabilisierungsmediums, insbesondere an Mehrphasengemisch durch den Zuführkanal dem Stabilisierungsspalt zuführbar ist.Thus, 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.
In einer weiteren Ausführungsvariante kann der Zuführkanal derart am Pumpengehäuse angeordnet und ausgebildet sein, dass zur Ausbildung der hydrodynamischen Stabilisierungsschicht im Stabilisierungsspalt eine vorgebbare Menge an Stabilisierungsmedium, insbesondere Mehrphasengemisch durch den Zuführkanal dem Stabilisierungsspalt zuführbar ist.In a further embodiment variant, 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.
Oder aber ein Zuführkanal ist derart am Rotor angeordnet und ausgebildet, dass zur Ausbildung der hydrodynamischen Stabilisierungsschicht im Stabilisierungsspalt eine vorgebbare Menge an Stabilisierungsmedium, insbesondere Mehrphasengemisch durch den Zuführkanal dem Stabilisierungsspalt zuführbar ist.Or else 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.
Wie bereits erwähnt, kann bei einer erfindungsgemässen helico-axialen Pumpe das Stabilisierungsmedium, insbesondere das Mehrphasengemisch dem Zuführkanal besonders bevorzugt von einer Kompressionsstufe zugeführt werden, an der ein höheres Druckniveau herrscht, als an derjenigen Kompressionsstufen, der es als Stabilisierungsmedium zugeführt wird. Alternativ oder gleichzeitig kann jedoch zur Ausbildung der hydrodynamischen Stabilisierungsschicht auch ein in derselben Kompressionsstufe komprimiertes Mehrphasengemisch verwendet werden.As already mentioned, in the case of a helico-axial pump according to the invention, the stabilization medium, in particular the multiphase mixture, 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. Alternatively or simultaneously, however, a multiphase mixture compressed in the same compression stage can also be used to form the hydrodynamic stabilization layer.
Die Erfindung betrifft weiterhin einen Rotor zur Anordnung in einem Pumpengehäuse einer helico-axialen Pumpe zur Förderung eines Mehrphasengemischs. Dabei umfasst der um eine Längsachse drehbar lagerbare Rotor einen ersten Teilrotor und einen zweiten Teilrotor, und der erste Teilrotor und der zweite Teilrotor umfasst zur Kompression des Mehrphasengemischs eine Kompressionsstufe mit einem helico-axialen Laufrad und einem Stator. Erfindungsgemäss ist eine hydrodynamische Stabilisierungsbuchse mit einer Stabilisierungsfläche derart zwischen dem ersten Teilrotor und dem zweiten Teilrotor vorgesehen und ausgestaltet, dass vor der Stabilisierungsfläche ein Stabilisierungsspalt ausbildbar ist, so dass im Betriebszustand eine hydrodynamische Stabilisierungsschicht aus einem Stabilisierungsmedium im Stabilisierungsspalt bildbar ist.The invention further relates to a rotor for arrangement in a pump housing of a helico-axial pump for conveying a multiphase mixture. In this case, 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. According to the invention, 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.
Bei einem speziellen Ausführungsbeispiel kann ein zusätzliches hydrodynamisches Stabilisierungselement mit einer Stabilisierungsfläche in Form eines Deckrings vorgesehen sein, der das helico-axiale Laufrad in Umfangsrichtung umschliesst , so dass der Stabilisierungsspalt zwischen dem Deckring und einem Pumpengehäuse der helico-axialen Pumpe ausbildbar ist. Alternativ oder gleichzeitig kann das hydrodynamische Stabilisierungselement aber auch eine Stabilisierungshülse sein, die zum Beispiel zwischen zwei benachbarten Kompressionsstufen vorgesehen ist, so dass der Stabilisierungsspalt zwischen der Stabilisierungshülse und dem Pumpengehäuse ausgebildet ist.In a specific embodiment, 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. Alternatively or simultaneously, however, 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.
Im Speziellen kann ein Zuführkanal vorgesehen sein, der so ausgebildet und angeordnet ist, dass zur Ausbildung der hydrodynamischen Stabilisierungsschicht im Stabilisierungsspalt eine vorgebbare Menge an Stabilisierungsmedium, insbesondere Mehrphasengemisch durch den Zuführkanal dem Stabilisierungsspalt zuführbar ist.In particular, 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.
Die Erfindung betrifft weiter eine Hybridpumpe mit einem erfindungsgemässen Rotor für eine helico-axiale Pumpe er vorliegenden Erfindung zur Förderung eines Mehrphasengemischs.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.
Schliesslich betrifft die Erfindung auch ein Verfahren zur hydrodynamischen Lagerung eines erfindungsgemässen Rotors in einer helico-axialen Pumpe oder in einer Hybridpumpe gemäss der vorliegenden Erfindung, wobei in einem Pumpengehäuse der Rotor drehbar um eine Längsachse gelagert wird, und der Rotor zur Kompression des Mehrphasengemischs eine Kompressionsstufe mit einem helico-axialen Laufrad und einem Stator umfasst. Erfindungsgemäss wird eine hydrodynamische Stabilisierungsbuchse mit einer Stabilisierungsfläche derart im Pumpengehäuse vorgesehen und ausgestaltet, dass vor der Stabilisierungsfläche ein Stabilisierungsspalt ausgebildet wird, so dass im Betriebszustand eine hydrodynamische Stabilisierungsschicht aus einem Stabilisierungsmedium im Stabilisierungsspalt zur hydrodynamischen Lagerung des Rotors gebildet wird.Finally, 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. According to the invention, 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.
Im Folgenden wird die Erfindung an Hand der Zeichnung näher erläutert. Es zeigen in schematischer Darstellung:
- Fig. 1 a
- eine Kompressionsstufe einer aus dem Stand der Technik bekannten helico-axialen Pumpe;
- Fig. 1 b
- eine Pumpe gemäss
Fig. 1a teilweise im Schnitt; - Fig. 2
- ein Ausführungsbeispiel einer erfindungsgemässen helicoaxialen Pumpe in Back-to-Back Anordnung;
- Fig. 3
- eine Detaildarstellung der Back-to-Back Anordnung gemäss
Fig. 2 im Betriebszustand; - Fig. 4
- ein Ausführungsbeispiel mit einem zusätzlichen hydrodynamischen Stabilisierungselement in Form eines Deckrings;
- Fig. 5a
- ein Ausführungsbeispiel der
Fig. 4 mit zusätzlicher Einspritzung am Deckring; - Fig. 5b
- das Ausführungsbeispiel der
Fig. 5a mit Einspritzung unter höherem Druck; - Fig. 6a
- ein drittes Ausführungsbeispiel gemäss
Fig. 4 mit Einspritzung am Stator; - Fig. 6b
- ein anderes Ausführungsbeispiel gemäss
Fig. 6a ohne Deckring am helico-axialen Laufrad; - Fig. 6c
- ein weiteres Ausführungsbeispiel gemäss
Fig. 6b mit Einspritzung aus dem Rotor; - Fig. 7a
- ein viertes Ausführungsbeispiel gemäss
Fig. 4 mit Stabilisierungshülse und Einspritzung; - Fig. 7b
- ein anderes Ausführungsbeispiel gemäss
Fig. 7a ohne Deckring am helico-axialen Laufrad.
- Fig. 1 a
- a compression stage of a known from the prior art helico-axial pump;
- Fig. 1 b
- a pump according to
Fig. 1a partly in section; - Fig. 2
- An embodiment of an inventive helicoaxial pump in back-to-back arrangement;
- Fig. 3
- a detailed representation of the back-to-back arrangement according to
Fig. 2 in the operating condition; - Fig. 4
- an embodiment with an additional hydrodynamic stabilizing element in the form of a cover ring;
- Fig. 5a
- an embodiment of the
Fig. 4 with additional injection on the cover ring; - Fig. 5b
- the embodiment of
Fig. 5a with injection under higher pressure; - Fig. 6a
- a third embodiment according to
Fig. 4 with injection at the stator; - Fig. 6b
- another embodiment according to
Fig. 6a without cover ring on helico-axial impeller; - Fig. 6c
- a further embodiment according to
Fig. 6b with injection from the rotor; - Fig. 7a
- a fourth embodiment according to
Fig. 4 with stabilization sleeve and injection; - Fig. 7b
- another embodiment according to
Fig. 7a without cover ring on the helico-axial impeller.
Der anhand der
An dieser Stelle sei im Übrigen darauf hingewiesen, dass zur besseren Unterscheidung der Erfindung vom Stand der Technik in den Zeichnungen diejenigen Bezugszeichen, die sich auf Merkmale bzw. Ausführungsformen aus dem Stand der Technik beziehen, mit einem Hochkomma versehen sind, während Bezugszeichen zu Merkmalen erfindungsgemässer Ausführungsbeispiele kein Hochkomma tragen.It should be noted that to better distinguish the invention from the prior art in the drawings, those reference numerals relating to features or embodiments of the prior art are provided with a single quote, while reference numerals to features according to the invention Embodiments do not wear an apostrophe.
Anhand der
Die helico-axiale Pumpe 1 zur Förderung eines Mehrphasengemischs M gemäss
Die
Eingangskompressionsstufe K2E des zweiten Teilrotors 22 zugeführt und über eine zweite Ausgangskompressionsstufe K2A aus dem zweiten Teilrotor 22 über einen zweiten Kreuzkanal KR2, einen vierten Ringraum R4 und eine Drucköffnung 102 aus der helico-axialen Pumpe zur weiteren Verwendung wieder abgeführt wird. Um eine maximale Druckdifferenz ΔP über der Stabilisierungsbuchse 70 zu erhalten und damit die Ausbildung einer optimalen Stabilisierungsschicht S im Stabilisierungsspalt 8 zu gewährleisten, sind die erste Ausgangskompressionsstufe K1 A und die zweite Ausgangskompressionsstufe K2A jeweils benachbart zur Stabilisierungsbuchse 70 angeordnet.Input compression stage K2E of the
Beim Beispiel der
Anhand der
Der Rotor 2 der helico-axiale Pumpe 1 ist im Pumpengehäuse 6 um eine Längsachse A drehbar gelagert. Der Rotor 2 umfasst dabei zur Kompression des Mehrphasengemischs M in an sich bekannter Weise die Kompressionsstufen K mit einem helico-axialen Laufrad 3 und einem Stator 4.The
Gemäss der vorliegenden Erfindung ist dabei zusätzlich zu der in
Im vorliegenden Beispiel der
Aus Gründen der Übersichtlichkeit sind dabei in allen folgenden Figuren jeweils nur eine oder zwei Kompressionsstufen K dargestellt. Auch wenn es im Prinzip möglich ist, dass eine erfindungsgemässe helico-axiale Pumpe 1 nur eine einzige Kompressionsstufe K umfasst, wird eine erfindungsgemässe helico-axiale Pumpe 1, d.h. der erste Teilrotor 21 und der zweite Teilrotor 22 in der Praxis eine Vielzahl von Kompressionsstufen K umfassen, zum Beispiel bis zu sechzehn Kompressionsstufen K oder sogar noch deutlich mehr Kompressionsstufen K, die bevorzugt hintereinander in Serie entlang der Längsachse A angeordnet sind, so dass in an sich bekannter Weise eine ausreichende Gesamtkompression des Mehrphasengemischs M erzeugt werden kann und das so komprimierte Mehrphasengemisch M dann zum Beispiel mit einer nach geschalteten Druckpumpe auf ein höheres Niveau und / oder über weite Strecken zur Weiterverarbeitung gefördert werden kann.For reasons of clarity, only one or two compression stages K are shown in each of the following figures. Although it is possible in principle that 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
Beim Ausführungsbeispiel gemäss
Aufgrund der Druckdifferenz ΔP wird, wie durch die kleinen gebogenen Pfeile M angedeutet, vom darstellungsgemäss rechts gelegen höheren Druckniveau Mehrphasengemisch M in den Stabilisierungsspalt 8 gepresst, wodurch sich automatisch die hydrodynamische Stabilisierungsschicht S zwischen der Stabilisierungsfläche 700 des Deckrings 7 und dem Pumpengehäuse 6 ausbildet, wodurch die Schwingen des Rotors 2 bzw. der Teilrotoren 21, 22 gedämpft werden und der Lauf des Rotors 2 stabilisiert wird.Due to the pressure difference .DELTA.P, as indicated by the small curved arrows M, multiphase mixture M is pressed into the stabilizing
Es versteht sich dabei, dass bei einem Rotor 2 der vorliegenden Erfindung der Deckring 71 entweder an allen helico-axialen Laufrädern 3 des Rotors ausgebildet sein kann, oder nur an bestimmten ausgewählten Helico-axialen Laufrädern 3. Im übrigen kann je nach Anwendung bzw. je nach den speziellen Erfordernissen der Deckring 71 ein helico-axiales Laufrad 3 vollständig abdecken oder einen eine bestimmten vorgebbaren Bereich des Umfangs des helico-axialen Laufrads 3.It is understood that in a
Anhand der
Im Prinzip kann eine zusätzliche Einspritzung von Stabilisierungsmedium auch in den Stabilisierungsspalt S der Stabilisierungsbuchse 70 erfolgen.In principle, an additional injection of stabilizing medium can also take place in the stabilizing gap S of the stabilizing
Das Ausführungsbeispiel der
Dagegen ist beim Beispiel der
Das Stabilisierungsmedium M kann dabei wie bereits beschrieben von einem externen Druckspeicher oder einer externen Pumpe zur Verfügung gestellt werden; wird jedoch bevorzugt von einer anderen Kompressionsstufe K, die ein höheres Druckniveau hat, zur Verfügung gestellt.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.
Anhand der schematischen
In
Die
Dabei ist es in speziellen Fällen selbstverständlich auch möglich, dass alternativ oder zusätzlich zu der Stabilisierungshülse 72 zwischen jeweils zwei benachbarten Kompressionsstufen K, eine Stabilisierungshülse 72 auch innerhalb einer Kompressionsstufe K zwischen dem helico-axialen Laufrad 3 und dem Stator 4 vorgesehen sein kann. Dabei versteht der Fachmann sofort, dass nicht an jeder bzw. nicht zwischen jedem Paar von Kompressionsstufen K eine Stabilisierungshülse 72 vorgesehen sein muss.It is of course also possible in special cases that alternatively or in addition to the stabilizing sleeve 72 between each two adjacent compression stages K, a stabilizing sleeve 72 may be provided within a compression stage K between the helico-
Es versteht sich, dass alle oben beschriebenen Ausführungsbeispiele der Erfindung nur beispielhaft bzw. exemplarisch zu verstehen sind und die Erfindung insbesondere, aber nicht nur, alle geeigneten Kombinationen der beschriebenen Ausführungsbeispiele umfasst.It is understood that all embodiments of the invention described above are to be understood as exemplary only or by way of example, and the invention particularly, but not exclusively, includes all suitable combinations of the described embodiments.
Claims (15)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11161758.5A EP2386767B1 (en) | 2010-05-11 | 2011-04-08 | Helico-axial pump and method for bearing a rotor in a helico-axial pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10162520 | 2010-05-11 | ||
EP11161758.5A EP2386767B1 (en) | 2010-05-11 | 2011-04-08 | Helico-axial pump and method for bearing a rotor in a helico-axial pump |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2386767A2 true EP2386767A2 (en) | 2011-11-16 |
EP2386767A3 EP2386767A3 (en) | 2017-11-01 |
EP2386767B1 EP2386767B1 (en) | 2021-01-06 |
Family
ID=42830261
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11161758.5A Active EP2386767B1 (en) | 2010-05-11 | 2011-04-08 | Helico-axial pump and method for bearing a rotor in a helico-axial pump |
Country Status (3)
Country | Link |
---|---|
US (1) | US9234529B2 (en) |
EP (1) | EP2386767B1 (en) |
BR (1) | BRPI1102495B1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3657024A1 (en) | 2018-11-21 | 2020-05-27 | Sulzer Management AG | Multiphase pump |
EP3536975B1 (en) | 2018-03-07 | 2021-04-28 | OneSubsea IP UK Limited | System and methodology to facilitate pumping of fluid |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150167652A1 (en) * | 2013-12-18 | 2015-06-18 | General Electric Company | Submersible pumping system and method |
RU2674479C2 (en) * | 2014-02-24 | 2018-12-11 | ДжиИ ОЙЛ ЭНД ГЭС ЭСП, ИНК. | Downhole wet gas compressor processor |
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 (en) * | 2019-10-25 | 2021-04-28 | Sulzer Management AG | Multiphase pump with bearing squeeze film damper |
EP3913226A1 (en) | 2020-05-18 | 2021-11-24 | Sulzer Management AG | Multiphase pump |
US11371326B2 (en) | 2020-06-01 | 2022-06-28 | Saudi Arabian Oil Company | Downhole pump with switched reluctance motor |
US11499563B2 (en) | 2020-08-24 | 2022-11-15 | Saudi Arabian Oil Company | Self-balancing thrust disk |
US11920469B2 (en) | 2020-09-08 | 2024-03-05 | Saudi Arabian Oil Company | Determining fluid parameters |
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 |
US11994016B2 (en) | 2021-12-09 | 2024-05-28 | Saudi Arabian Oil Company | Downhole phase separation in deviated wells |
US12012550B2 (en) | 2021-12-13 | 2024-06-18 | Saudi Arabian Oil Company | Attenuated acid formulations for acid stimulation |
US20240175339A1 (en) * | 2022-11-30 | 2024-05-30 | Halliburton Energy Services, Inc. | High volume axial flow electric submersible pump (esp) pump stage |
Citations (3)
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 (en) | 1990-11-20 | 1992-05-27 | Chiron-Werke GmbH & Co. KG | Machine tool and method for opening and closing a gripper |
US5961282A (en) | 1996-05-07 | 1999-10-05 | Institut Francais Du Petrole | Axial-flow and centrifugal pumping system |
Family Cites Families (11)
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 (en) * | 1990-12-14 | 1994-09-02 | Technicatome | MULTI-STAGE PUMP PARTICULARLY FOR PUMPING A MULTIPHASIC FLUID. |
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 (en) * | 1997-11-19 | 1999-12-31 | Inst Francais Du Petrole | DEVICE AND METHOD FOR DIPHASIC COMPRESSION OF A SOLUBLE GAS IN A SOLVENT |
GB9724899D0 (en) * | 1997-11-26 | 1998-01-28 | Triangle Engineering Consultan | Downhole pump/motor assembly |
CA2299606C (en) * | 2000-02-25 | 2007-08-21 | Cn & Lt Consulting Ltd. | Bearing assembly for wellbore drilling |
US6547514B2 (en) * | 2001-06-08 | 2003-04-15 | Schlumberger Technology Corporation | Technique for producing a high gas-to-liquid ratio fluid |
EP1452688A1 (en) * | 2003-02-05 | 2004-09-01 | Siemens Aktiengesellschaft | Steam turbine rotor, method and use of actively cooling such a rotor |
US20040258518A1 (en) * | 2003-06-18 | 2004-12-23 | Steven Buchanan | Self-lubricating ceramic downhole bearings |
-
2011
- 2011-04-08 EP EP11161758.5A patent/EP2386767B1/en active Active
- 2011-04-20 US US13/090,704 patent/US9234529B2/en active Active
- 2011-05-06 BR BRPI1102495-0A patent/BRPI1102495B1/en active IP Right Grant
Patent Citations (3)
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 (en) | 1990-11-20 | 1992-05-27 | Chiron-Werke GmbH & Co. KG | Machine tool and method for opening and closing a gripper |
US5961282A (en) | 1996-05-07 | 1999-10-05 | Institut Francais Du Petrole | Axial-flow and centrifugal pumping system |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3536975B1 (en) | 2018-03-07 | 2021-04-28 | OneSubsea IP UK Limited | System and methodology to facilitate pumping of fluid |
EP3657024A1 (en) | 2018-11-21 | 2020-05-27 | Sulzer Management AG | Multiphase pump |
EP4063665A1 (en) | 2018-11-21 | 2022-09-28 | Sulzer Management AG | Multiphase pump |
US12006949B2 (en) | 2018-11-21 | 2024-06-11 | Sulzer Management Ag | Multiphase pump |
Also Published As
Publication number | Publication date |
---|---|
US9234529B2 (en) | 2016-01-12 |
EP2386767A3 (en) | 2017-11-01 |
BRPI1102495B1 (en) | 2021-07-20 |
US20110280741A1 (en) | 2011-11-17 |
EP2386767B1 (en) | 2021-01-06 |
BRPI1102495A2 (en) | 2012-11-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2386767B1 (en) | Helico-axial pump and method for bearing a rotor in a helico-axial pump | |
EP2386766B1 (en) | Helico-axial pump, rotor for same, method for hydrodynamic bearing of a rotor of a helicon-axial pump and a hybrid pump with a rotor for a helico-axial pump | |
DE2514723C3 (en) | Hydrodynamic bearing | |
DE102010052892A1 (en) | Bearing arrangement for a shaft of a turbine wheel | |
EP2626563B1 (en) | Pump, recirculating device for a pump and rotor shaft for a pump | |
DE102006036243A1 (en) | Feed screw for eccentric screw pump | |
DE2653630A1 (en) | DEVICE FOR PUMPING FLUIDS | |
DE69807930T2 (en) | HIGH PRESSURE GAS PRODUCTION | |
EP0363503A1 (en) | Pump stage for a high vacuum pump | |
DE19962554A1 (en) | Adjustable rotating lubrication pump for an internal combustion engine has an eccentric hub operating inside the casing with fitted to a guide ring | |
DE102013113710B4 (en) | Bearing device for an exhaust gas turbocharger and exhaust gas turbocharger | |
DE102012112618B3 (en) | Multiple pump | |
EP3175112B1 (en) | Process pump with a crank mechanism | |
DE102010001538A1 (en) | Gas laser with radial and axial gas bearings | |
EP2667034B1 (en) | Multistage pump | |
DE102011112689B4 (en) | vacuum pump | |
EP2148094A2 (en) | Vacuum pump | |
EP1454055A1 (en) | Radial piston pump having force-feed lubrication | |
DE10208574A1 (en) | Radial piston pump | |
EP2071123B1 (en) | Turning head vacuum pump with modified shaft bearing | |
DE10149366A1 (en) | Axial friction vacuum pump has two concentric rotor components with drives, rotating in opposite directions to improve relative speed of pumping structures | |
DE102005048971A1 (en) | Cylinder roller bearing for radial and axial suspension of shafts, has cylindrical roller bodies arranged between outer and inner rings and including respective eccentric borehole that extends parallel to longitudinal axis of roller bodies | |
DE102021208481A1 (en) | Feed pump and motor vehicle with such a feed pump | |
WO2014044416A1 (en) | Multi-stage hydraulic engine | |
DE2901638C3 (en) |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SULZER MANAGEMENT AG |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04D 31/00 20060101ALI20170925BHEP Ipc: F04D 29/66 20060101AFI20170925BHEP Ipc: F04D 29/047 20060101ALI20170925BHEP Ipc: F04D 29/057 20060101ALI20170925BHEP |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20180502 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20190624 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20201015 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1352673 Country of ref document: AT Kind code of ref document: T Effective date: 20210115 Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502011017031 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20210106 |
|
REG | Reference to a national code |
Ref country code: NO Ref legal event code: T2 Effective date: 20210106 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210407 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210406 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210506 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210506 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502011017031 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 |
|
26N | No opposition filed |
Effective date: 20211007 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210408 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20210430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210430 Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210408 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210506 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 1352673 Country of ref document: AT Kind code of ref document: T Effective date: 20210408 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210408 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20110408 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230412 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210106 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20240419 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240418 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NO Payment date: 20240422 Year of fee payment: 14 Ref country code: FR Payment date: 20240426 Year of fee payment: 14 |