EP3187736B1 - Pompe centrifuge horizontale multi-etagée destinée au transport d'un fluide et son procédé de réparation - Google Patents

Pompe centrifuge horizontale multi-etagée destinée au transport d'un fluide et son procédé de réparation Download PDF

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Publication number
EP3187736B1
EP3187736B1 EP16200174.7A EP16200174A EP3187736B1 EP 3187736 B1 EP3187736 B1 EP 3187736B1 EP 16200174 A EP16200174 A EP 16200174A EP 3187736 B1 EP3187736 B1 EP 3187736B1
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Prior art keywords
pump
shaft
wear
rotor
wear ring
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EP16200174.7A
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German (de)
English (en)
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EP3187736A1 (fr
Inventor
Nicolas Lagas
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Sulzer Management AG
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Sulzer Management AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/007—Details, component parts, or accessories especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/10—Multi-stage pumps with means for changing the flow-path through the stages, e.g. series-parallel, e.g. side loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/08—Multi-stage pumps the stages being situated concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0072—Installation or systems with two or more pumps, wherein the flow path through the stages can be changed, e.g. series-parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/0245—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the pump
    • F04D15/0272—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the pump the condition being wear or a position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/14—Multi-stage pumps with means for changing the flow-path through the stages, e.g. series-parallel, e.g. side-loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • 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
    • F04D29/0473—Bearings hydrostatic; hydrodynamic for radial pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft sealings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/185—Rotors consisting of a plurality of wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/622—Adjusting the clearances between rotary and stationary parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type

Definitions

  • the invention relates to a multistage horizontal centrifugal pump for conveying a fluid, as well as a method for repairing or overhauling a multistage horizontal centrifugal pump according to the preamble of the independent claim of the respective category.
  • Multistage horizontal centrifugal pumps are used in many different technological areas, for example in the oil and gas processing industry or in industrial energy generation. In the latter, such multi-stage pumps are used, for example, as feed pumps or boiler feed pumps in order to feed the water to a steam generator under the necessary pressure.
  • each pump stage comprising a stage housing in each of which an impeller is provided which conveys the fluid, for example water, from the low-pressure side inlet of this pump stage to its high-pressure side outlet, which then connected to the inlet of the next stage.
  • All impellers are rotatably arranged on a common shaft, which consequently extends through all the stage housing and driven by a drive, for. B. an electric motor is driven.
  • the individual pump stages are typically sealed along the common shaft by wear rings which are arranged or mounted in a stationary manner with respect to the stage housing.
  • two wear rings are provided for a pump stage, namely a first wear ring on the low-pressure side, which surrounds the front cover plate of the impeller, and on the high-pressure side a second wear ring, which is fixedly attached to a partition that guides the fluid from the outlet of the stage to the inlet of the next stage and typically includes a stator for the next stage.
  • the wear rings are each designed with a predetermined clearance with respect to the shaft, so that an annular gap is formed between the radially inner, cylinder jacket-shaped boundary surface of the wear ring and the rotating outer jacket surface of the shaft, through which a leakage flow from the high-pressure side to the low-pressure side is made possible.
  • This leakage flow is advantageous on the one hand because it contributes to the hydrodynamic stabilization of the rotor (shaft with impellers), on the other hand it also means a certain loss in terms of the efficiency of the pump.
  • the dimensioning of this clearance therefore plays an important role. The aim is, of course, always to avoid direct physical contact between the stationary wear rings and the rotating shaft during operation of the pump.
  • the wear rings are - as their name suggests - wear parts that have to be replaced during the life of the pump. This is primarily due to the fact that the leakage flow causes erosion on the wear rings. This increases the gap between the respective wear ring and the shaft, which leads to an increase in the leakage flow. Since the increase in leakage flow reduces the efficiency of the pump, the wear rings usually have to be replaced with new ones.
  • a particular problem with multistage horizontal centrifugal pumps which occurs in particular with higher numbers of stages, lies in the length of the shaft and the mass of the impellers arranged on it in a rotationally fixed manner.
  • the rotor thus includes the shaft and the impellers. With long shafts or rotors, there is a not insignificant deflection of the shaft due to its own mass. This deflection is usually largest in the middle area of the shaft.
  • the center line of the shaft which without bending would be a straight line that coincides with the center axis of the pump and the axis of rotation, becomes a curved line through the bending, which is referred to below as the bending line of the shaft or the bending line of the rotor.
  • the deviation of the bending line from the central axis of the pump is greatest approximately in the middle between the radial bearings for the shaft. Due to the force of gravity, the bending line in a horizontal pump is a convex function.
  • the deflection of the shaft is greatest when the pump is at a standstill.
  • stretching of the shaft usually results, i.e. in particular its maximum deflection is reduced. This stretching is based in particular on hydrodynamic effects such as the lomakine effect.
  • the play is usually measured in such a way that the rotor does not come into physical contact with the wear rings in all normal operating conditions.
  • the deflection of the rotor increases, so that when the rotor comes to a standstill at the latest, it comes into physical contact with at least some wear rings and rests on them.
  • Another possibility for solving this problem would be to considerably increase the play between the rotor and the wear rings so that the rotor can rotate freely even when it is at a standstill.
  • this solution is undesirable or even unacceptable, because this increased play inevitably leads to a reduction in the efficiency or the efficiency of the pump, which leads to the pursuit of minimizing energy consumption and environmentally conscious handling Resources.
  • a multistage horizontal centrifugal pump for pumping a fluid with a rotor that comprises a rotatably arranged shaft and several impellers for pumping the fluid, all of the impellers being non-rotatably arranged on the shaft, and with a stator that has several stage housings ( 31), which one behind the other with respect to an axial direction defined by a central axis are arranged, wherein the stator surrounds the rotor, and wherein all stage housings are designed and arranged centrally with respect to the central axis (A), and multiple wear rings are provided between the rotor and the stator, each of which is fixed with respect to the stator, and the Each rotor surrounds with a clearance, and at least one of the wear rings is designed eccentrically.
  • each pump stage having an impeller provided with a front cover disk for conveying the fluid, as well as a stage housing with a stationary impeller opening for receiving the front cover plate of one of the impellers, and a partition wall, which is stationary with respect to the stage housing, for guiding the fluid to the adjacent pump stage, the impellers of all pump stages in a rotationally fixed manner on the shaft are ordered, each stationary impeller opening being delimited radially on the inside by a first wear ring which surrounds the front cover plate of the impeller with a clearance, and each stationary partition wall being delimited radially on the inside by a second wear ring which surrounds the shaft with clearance, and wherein at least one of the first or the second wear rings is designed eccentrically.
  • the term "eccentrically designed" with respect to the wear ring means that the radially outer limiting surface of the wear ring is centered around a first axis and the radially inner limiting surface of the wear ring is centered around a second axis, the first and second axes being parallel but not congruent are.
  • an eccentric wear ring is provided in particular where the deflection of the shaft or rotor is greatest, it can be ensured that the shaft or rotor in the operating state, especially in the area of the greatest deflection, is approximately centered in the eccentric wear ring rotates, ie the rotor is approximately centered with respect to the eccentric wear ring. If you now stop the rotor, which increases its maximum deflection, then the eccentric wear ring still has enough play so that physical contact between the rotor and the wear ring is reliably avoided even when the rotor is at a standstill. The shaft or the rotor is thus free, in particular, even at a standstill, that is to say without contact with the wear ring, and can for example be rotated by hand.
  • a particular advantage of this embodiment according to the invention is that the deflection of the shaft can only be compensated for by a very inexpensive component, namely the wear ring, or several of them.
  • this also enables an extremely cost-effective and less time-consuming adaptation to changes in the rotor setting, because if necessary only one or more wear rings need to be replaced, but in particular no further structural changes to other, significantly more expensive components of the pump, such as one of the stage housings, are required .
  • All stage housings are preferably arranged concentrically to the central axis of the pump. This is particularly advantageous from a structural point of view because the stage housing can then be designed essentially the same for at least almost all pump stages. Since the deflection of the rotor is already compensated for by the eccentric design of the wear ring, it is in particular not necessary to compensate for the deflection of the shaft by structural measures on the stepped housing itself. For example, an eccentric design of one or more stage housings or other components can be dispensed with.
  • the number of wear rings for which an eccentric design is preferred naturally depends on the specific application and in particular on the length of the shaft, the number of impellers and the mass of the rotor. For many applications it is preferred if a plurality of the wear rings are designed eccentrically.
  • the eccentricity of the wear rings is not constant over the length of the shaft. It is particularly advantageous if the wear rings have an eccentricity which increases in the direction of the center of the pump. This means that seen from one end of the pump, the eccentricity of the wear rings initially increases until it reaches its maximum in the area of the center of the pump, i.e. where the shaft is usually the greatest, and then decreases again.
  • the distance between the first axis, around which the radially outer boundary surface of the wear ring is centered, from the second axis, around which the radially inner boundary surface of the wear ring is centered, is taken.
  • the eccentricity of the wear rings is adapted to the bending line of the shaft. This means that the greater the distance between the bending line and the central axis of the pump, the greater the selected eccentricity of the wear ring, so that the eccentricity essentially follows the bending line of the shaft.
  • This measure also has the particular advantage that all stage housings can be arranged parallel and perpendicular to the central axis of the pump. It is thus possible to dispense with an inclined arrangement of the stage housing or other components.
  • the eccentricity of all wear rings is dimensioned such that when the shaft is at a standstill, none of the wear rings touches the shaft or an impeller. Since the deflection of the shaft or the rotor is greatest at standstill, this measure can minimize the radial width of the gap between the wear rings on the one hand and the rotor (shaft or impeller). It is also preferred if the eccentricity of all wear rings is dimensioned such that the bending line of the shaft runs essentially centrally between all wear rings at a nominal speed of the pump. The bent shaft then rotates at least approximately centered with respect to the wear rings, so it has the same in all radial directions Game. Among other things, this is particularly advantageous for thermally induced changes in the rotor. For example, when the temperature changes. B. in the medium to be conveyed, significantly steeper temperature changes, so larger temperature gradients are allowed without additional measures, such as preheating of the rotor are necessary. This is particularly advantageous with regard to applications in industrial power generation.
  • the pump has several pump stages which are arranged one behind the other with respect to the axial direction, each pump stage comprising an impeller provided with a front cover plate for conveying the fluid, as well as one of the stage housings and a partition wall stationary with respect to the stage housing for guiding of the fluid to the adjacent pump stage, the stage housing being designed with a stationary impeller opening for receiving the front cover plate of one of the impellers, each stationary impeller opening being delimited radially on the inside by a first wear ring which surrounds the front cover plate of the impeller with a clearance, and each stationary partition wall being delimited radially on the inside by a second wear ring which surrounds the shaft with play.
  • the eccentricity of all wear rings is dimensioned in such a way that, when the shaft is at a standstill, none of the wear rings touches the shaft or an impeller. This makes it possible to further reduce both the play between the shaft and the second wear rings and the play between the front cover disks of the impellers and the first wear rings compared to known multiphase pumps, which increases the efficiency of the pump according to the invention.
  • each eccentric wear ring has a positioning means in order to position the respective wear ring in a predetermined angular orientation in the respective step housing or the respective partition.
  • This positioning means can be, for example, a visually recognizable marking on the wear ring or a positioning pin which engages in a corresponding bore in the step housing or in the partition.
  • the positioning means is particularly preferably provided where the respective wear ring has its maximum width in the radial direction, because this enables particularly simple assembly of the wear ring.
  • the pump is designed as a barrel casing pump, in which all stage casings are arranged in a casing. Since all stage housings can be arranged parallel to one another and perpendicular to the central axis of the pump, the inlet connector can be manufactured in a conventional manner, that is, the problematic inclination of the inlet connector described at the beginning can be dispensed with. In addition, it is possible to provide reliable seals between the stepped housings and the outer casing. In this way, different pressure spaces can be provided in the interior of the jacket housing, in which the fluid is present at different pressures.
  • the pump according to the invention can be designed with an inlet and an outlet and an intermediate outlet for the fluid to be conveyed, the intermediate outlet being designed and arranged in such a way that at least part of the fluid can be removed through the intermediate outlet under an intermediate pressure is which intermediate pressure is greater than the pressure of the fluid at the inlet of the pump and less than the pressure of the fluid at the outlet of the pump.
  • This possibility of intermediate withdrawal of the fluid with a different pressure than that at the outlet is a great advantage for many applications.
  • the invention also proposes a method for repairing or overhauling a multistage horizontal centrifugal pump for pumping a fluid with a rotor which comprises a rotatably arranged shaft and several impellers for delivering the fluid, with all impellers being arranged on the shaft in a rotationally fixed manner, and with a stator comprising a plurality of stage housings which are arranged one behind the other with respect to an axial direction defined by a central axis, wherein the stator surrounds the rotor, and wherein all stage housings are designed and arranged centrally with respect to the central axis, and several between the rotor and the stator Wear rings are provided, each of which is fixed with respect to the stator, and each surrounds the rotor with a clearance, in which method one or more of the wear rings are replaced, one or more of the wear rings each being replaced by an eccentrically configured wear ring ssring is replaced.
  • the method is also suitable for repairing or overhauling a multistage horizontal centrifugal pump for pumping a fluid with a rotatably arranged shaft and with several pump stages which are arranged one behind the other with respect to an axial direction defined by a central axis, each pump stage having a front cover plate provided impeller for conveying the fluid, as well as a stage housing with a stationary impeller opening for receiving the front cover plate of one of the impellers, and a partition wall, which is stationary with respect to the stage housing, for guiding the fluid to the adjacent pump stage, the impellers of all pump stages being arranged in a rotationally fixed manner on the shaft are, wherein each stationary impeller opening is delimited radially inwardly by a first wear ring which surrounds the front cover plate of the impeller with a clearance, and each stationary partition wall radially inwardly by a two th wear ring is limited, which surrounds the shaft with a game.
  • a first wear ring which surrounds the front cover plate of the impeller with
  • Fig. 1 shows in a schematic side view an embodiment of a multistage horizontal centrifugal pump according to the invention, which is designated as a whole with the reference number 1.
  • Fig. 1 some parts of the pump 1 are shown in breakout.
  • Fig. 2 shows some parts of the pump 1 in an enlarged sectional view.
  • Such multi-stage pumps are used, for example, in industrial energy generation, e.g. B. as feed or boiler feed pumps, in which the fluid to be pumped is water, which is conveyed by the pump 1 to a steam generator.
  • Such pumps are also used in the oil and gas industry, both for pumping water, for example as injection pumps, or for pumping petroleum or other hydrocarbons.
  • the pump 1 is designed with an outer casing 2 (barrel casing), which has an inlet 4, an outlet 5, and optionally an intermediate outlet 51 for the fluid to be conveyed.
  • outer casing 2 barrel casing
  • the pump 1 has a rotatable shaft 6 which extends in the center through the pump 1 and which can be set in rotation by a drive (not shown), for example an electric motor.
  • the pump 1 has a central axis A, which extends through the center of the space provided for the shaft 6 in the interior of the pump 1, and which represents the target axis of rotation about which the shaft 6 is to rotate. If the shaft 6 mounted in the pump 1 were not bent, the central axis A would be congruent with the longitudinal axis of the shaft.
  • the direction of the central axis A of the pump 1 is always meant.
  • the radial direction then means a direction perpendicular to the axial direction.
  • a plurality of - here for example eight - pump stages 3 are provided in a manner known per se, which are arranged one behind the other with respect to the axial direction.
  • the pump 1 is shown in its normal position of use, ie in a horizontal arrangement, in which the central axis A runs horizontally or parallel to the ground.
  • FIG. 2 Shows for a better understanding Fig. 2 in an enlarged illustration, a perspective sectional view of one of the pump stages 3 (see also Fig. 3 ).
  • Each pump stage 3 comprises, in a manner known per se, an impeller 32, a stage housing 31 and, on the high-pressure side, a partition 33 which delimits the pump stage 3 from the next pump stage 3.
  • Each impeller 32 is designed as a closed impeller 32, that is to say it comprises a front cover disk 34, a rear cover disk 35 and a plurality of blades 36 arranged between the cover disks 34, 35 for conveying the fluid.
  • Each stage housing 31 comprises a stationary impeller opening 37 for receiving the front cover plate 34 of one of the impellers 32.
  • the partition 33 is also stationary with respect to the stage housing 31 and serves to convey the fluid conveyed by the impeller 32 to the inlet, ie to the impeller 32 of the next pump stage 3 lead.
  • the partition 33 comprises a stationary guide wheel, which is not shown in more detail in the drawing figures.
  • the impellers 32 of all pump stages 3 are non-rotatably connected to the shaft 6, so that the impellers 32 rotate together with the shaft 6.
  • the term “rotor” means the entirety of all components of the pump 1 that rotate in the operating state of the pump 1.
  • the rotor of the pump 1 thus comprises both the shaft 6 and all of the impellers 32 arranged thereon, as well as possibly other components of the pump 1, which rotate together with the shaft 6 or are connected to the shaft 6 in a rotationally fixed manner.
  • the term “stator” of the pump means the entirety of the stationary, that is to say non-rotating, components of the pump.
  • the stator thus includes, in particular, all step housings 31 and all partition walls 32.
  • Fig. 1 shows, all pump stages 3 and all stage casings 31 are arranged parallel to one another in such a way that the surfaces enclosed by the impeller openings 37 are perpendicular to the central axis A.
  • a first wear ring 7 is fitted into the impeller opening 37 of the stage housing 31 so that the stationary impeller opening is delimited radially on the inside by the first wear ring 7, which is firmly connected to the stage housing 3 and is therefore stationary.
  • the first wear ring 7 thus surrounds the front cover disk 34 of one of the running wheels 32.
  • a The second wear ring 8 is provided radially on the inside on the stationary partition 33 and surrounds the shaft 6, i.e. the stationary partition 33 is delimited on the radially inside by the second wear ring 8, which is arranged between the partition 33 and the shaft 6 with respect to the radial direction.
  • the second wear ring 8 is firmly connected to the partition 33 and is therefore also stationary.
  • each of the wear rings 7, 8 serves to seal the pump stages 3 along the shaft 6.
  • each of the wear rings 7, 8 surrounds the rotor with play, so that there is a gap between the radially outer boundary surface of the rotor and the radially inner boundary surface of the wear ring 7, 8 forms an annular gap through which a leakage flow flows counter to the general conveying direction of the fluid.
  • This leakage flow is desirable on the one hand, in particular in order to stabilize the rotor hydrodynamically, but on the other hand it should not be too large because the leakage flow reduces the efficiency of the pump.
  • direct physical contact between the rotor (shaft 6 or impeller 32) and one of the wear rings 7, 8 should be avoided.
  • FIG. 3 an enlarged sectional view to illustrate the play of a first and a second wear ring 7 and 8, respectively.
  • a deflection of the shaft 6 or of the rotor due to the mass of the rotor is in Fig. 6 shown very schematically on the basis of a bending line B.
  • the bending line B of the shaft 6 means the center line of the shaft 6 when the shaft 6, including the impellers 32 and other components connected to it in a rotationally fixed manner, i.e. the rotor, is mounted in the pump 1, i.e. when the shaft 6 is in its bearings and in particular the radial bearings are arranged, which are here on the outside in the region of the two ends of the shaft 6, but are not shown in more detail.
  • the deflection D of the shaft 6 is understood to mean the distance between the bending line B and the central axis A. Due to the direction of the gravitational force, the bending line B in a horizontal pump 1 is always a convex curve. The maximum of the deflection D is approximately in the middle of the pump 1, as shown in FIG Fig. 6 is shown. Depending on the length of the shaft 6 and the mass of the running wheels 32, the maximum deflection D can be a few tenths of a millimeter, for example 0.2-0.5 mm or more.
  • At least one of the first or the second wear rings 7 or 8 be designed eccentrically.
  • Fig. 4 an embodiment of such an eccentrically designed wear ring 7 or 8 is shown in a perspective view.
  • Fig. 5 shows a section through the wear ring 7, 8 from Fig. 4 , the cut being made in the axial direction, i.e. in the same way as in Fig. 3 . Additionally illustrated Fig. 5 the concept of eccentric design or eccentricity.
  • the eccentric configuration means that the radially outer limiting surface of the wear ring 7, 8 is surrounded by a different one Axis is centered than its radially inner boundary surface.
  • This is in Fig. 5 for the simple embodiment of the wear ring 7 or 8, in which the cross-sectional area of the wear ring 7 or 8 is rectangular.
  • both the radially outer and the radially inner limiting surface of the wear ring 7 and 8 are each a cylinder jacket surface.
  • the radially outer boundary surface has a radius R1 and the radially inner boundary surface has a radius R2, whereby of course R2 is smaller than R1.
  • the radially outer limiting surface is centered around a first axis A1, ie A1 is here identical to the cylinder axis of the radially outer limiting surface.
  • the radially inner limiting surface is centered around a second axis A2, ie A2 is here identical to the cylinder axis of the radially inner limiting surface.
  • the axes A1 and A2 run parallel to one another but are not congruent. This configuration of the non-congruent axes A1 and A2 is referred to as eccentric.
  • the eccentricity E which is given by the distance between the two axes A1 and A2, is established as a measure of the strength of the eccentric configuration.
  • the eccentricity E can be in the range of up to a few tenths of a millimeter. With modern machining methods customary today, it is not a problem to produce such eccentricities E with sufficient accuracy in a wear ring 7 or 8.
  • the radial width F of the wear ring 7 or 8 varies along its circumference, that is, there is a maximum radial width F and a minimum radial width F, the radial width F being the radial extent of the wear ring 7 or 8 Direction is.
  • the wear ring 7 or 8 Due to the variation in the radial width F, the wear ring 7 or 8 must be fastened to the stepped housing 31 or to the partition 33 in the correct angular orientation. Since the deflection D of the shaft 6 always takes place downwards with respect to the normal position of use, the wear ring 7 or 8 is used in such an orientation that the The area of its maximum radial width F is perpendicular above the central axis A, or the area of its minimum radial width F is perpendicular below the central axis A.
  • each eccentric wear ring 7 or 8 has a positioning means 9.
  • This positioning means 9 can be, for example, a pin 9 which protrudes in the axial direction from the ring and engages in a corresponding bore (not shown) in the respective step housing 31 or in the respective partition 33 during assembly.
  • other positioning means 9 are also possible, e.g. B. a projection or a recess on the wear ring 7 or 8, which interacts positively with a recess or a projection in the step housing 31 or in the partition 33, or optically recognizable markings such as notches, lines or arrows.
  • the positioning means 9 - as in FIG Fig. 4 is provided where the respective wear ring 7 or 8 has its maximum radial width F.
  • the illustrated rectangular cross-sectional area of the wear ring 7 or 8 is only to be understood as an example.
  • the wear rings 7 and 8 can also have other and more complex cross-sectional areas, in particular those known from the prior art for wear rings in centrifugal pumps.
  • the cross-sectional area of the wear ring 7 or 8 can, for example, also be L-shaped or trapezoidal; it can have boundary lines running at an oblique or acute angle to one another.
  • roundings or bevels can be provided. A sufficient number of possibilities for the design of this cross-sectional area are known to those skilled in the art.
  • the first wear ring 7 generally has a different geometrical configuration than the second wear ring 8, even if the geometrical configurations can in principle be the same.
  • each wear ring 7 or 8 is usually a cylinder jacket surface with a radius R2 (see Fig. 5 ).
  • This radius R2 is typically different for the first wear rings 7 and the second wear rings 8.
  • the radius R2 for the second wear rings 8 is smaller than for the first wear rings 7.
  • the at least one wear ring 7 or 8, which is designed eccentrically according to the invention, is provided where the deflection D of the shaft 6 is greatest.
  • the eccentricity E of this wear ring is preferably dimensioned in such a way that the rotating shaft 6 or the rotating cover disk 34 of the impeller 32 is at least approximately centered with respect to the radially inner boundary surface of the eccentric wear ring 7 or 8, i.e. the eccentricity E is selected in this way that it is at least approximately the deflection D of the rotating shaft 6 at the location of this wear ring 7 or 8. This then results in the rotating shaft 6 or the rotating cover disk 34 in this eccentrically configured wear ring 7 or 8 with respect to the second axis A2 (see FIG Fig. 5 ) is at least approximately centered.
  • This eccentrically designed wear ring 7 or 8 is now attached to the stepped housing 31 or to the partition 33, preferably using the positioning means 9, in such a way that its area in which the radial width F is at a maximum is arranged vertically above the central axis A.
  • the rotor now rotates, it is essentially centered in this wear ring 7 or 8, that is to say the rotor is - as described above - at least approximately centered with respect to the axis A2.
  • This means that the game S1 or S2 (see Fig. 3 ) is at least approximately constant within this wear ring 7 or 8, viewed in the circumferential direction of the rotor, so the rotor can rotate without contact with respect to the wear ring 7 or 8.
  • this freedom from contact is also advantageous for starting and stopping the pump 1 because there is no dragging between the rotor and the wear ring 7 or 8.
  • a coating of the wear ring 7 or 8 can be dispensed with and, on the other hand, the service life of the rotor is increased because its components are not subjected to any mechanical grinding on the wear ring 7 or 8.
  • both the first and the second wear rings 7 and 8 are designed to be eccentric.
  • the eccentricity E of an individual wear ring 7 or 8 is adapted to the deflection D of the shaft 6 at its individual location.
  • the eccentricity E of the first and second wear rings over the entire length of the wear rings 7, 8 is particularly preferred
  • the enclosed part of the rotor is adapted to the bending line B of the shaft 6, as follows with reference to FIG Fig. 6 and 7th is explained.
  • the bending line B of the shaft arranged in a pump 1 can be determined, for example, on the basis of empirical or historical data. It is of course also possible to determine the bending line B by measurement or to determine it by means of calculations, for example simulations.
  • the bending line B for a specific pump 1 is known at least approximately, it can also be decided in which areas of the rotor the deflection D of the shaft 6 is so great that there eccentrically configured wear rings 7 and 8 are advantageous.
  • the eccentricity E of the wear ring 7 or 8 is dimensioned such that when the shaft 6 is at a standstill, none of the wear rings 7 or 8 touches the shaft 6, so that the shaft 6 does not lie on any of the wear rings 7 or 8 at a standstill is thus freely rotatable, especially by hand.
  • the second criterion is to dimension the eccentricity for each individual wear ring 7 or 8 so that the bending line B of the shaft 6 at a typical speed at which the pump 1 is operated, for example the nominal speed, is essentially or at least approximately in the middle runs between all wear rings 7 and 8, respectively.
  • the aim is that for each individual wear ring 7 or 8, the shaft 6 is at least approximately centered with respect to the axis A2 of the radially inner boundary surface of this wear ring 7 or 8 .
  • the Fig. 6 and 7th show in a schematic representation this adaptation of the eccentricity E to the bending line B of the shaft 6. Because it is better for understanding, the rotor is in the Fig. 6 and 7th each represented only by the bending line B of the shaft 6, ie in Fig. 6 and Fig. 7 does not take into account that the rotor has a finite extent in the radial direction. The radial expansion of the rotor is not shown, but the Bending line B is to be understood as symbolic for a representation of the rotor or the shaft 6 with the impellers 32.
  • Fig. 6 shows for the exemplary embodiment Fig. 1 the situation for the state when the shaft 6 rotates at a typical speed, for example the nominal speed of the pump 1.
  • the eccentricity E of both the first and the second wear rings 7 and 8 increases from the left end according to the illustration to approximately the middle of the pump 1 and then decreases again in the direction of the right end of the pump according to the illustration.
  • the bending line B is at least approximately centered with respect to the radially inner boundary surface of all wear rings 7 and 8, respectively.
  • the play S1 or S2 (see Fig. 5 ) for each of the wear rings 7 and 8, viewed in the circumferential direction, at least approximately constant.
  • Fig. 7 shows for the exemplary embodiment Fig. 1 the situation for the state when the shaft 6 is stationary. It can be seen that the deflection D of the shaft 6 and in particular the maximum of the deflection D has increased, but that the rotor or the shaft 6 - represented by the bending line B - at no point is in direct physical contact with the wear rings 7 or 8 comes, so is freely rotatable with respect to the wear rings.
  • the above-described adaptation of the eccentricity E of the wear rings 7 and 8 to the bending line B is particularly advantageous with regard to temperature changes, especially rapid or temporary temperature changes. Since the rotor or the shaft 6 is always in an optimal position with respect to the stage housing 31 or the partition walls 32, or more generally expressed with respect to the stator of the pump 1, steeper temperature changes, ie larger temperature gradients, are possible without the There is a risk that the rotor will come into direct physical contact with the wear rings 7 or 8, and without it being necessary to take other measures, such as preheating the pump 1, for example.
  • Another advantage that results from the adjustment of the eccentricity E of the wear rings 7 or 8 to the bending line B of the shaft 6 is that the clearance S1 or S2 ( please refer Fig. 3 ) can be reduced, so that the efficiency of the pump 1 or its efficiency can be increased.
  • a particular advantage of the design according to the invention is the possibility of adapting the stator of the pump 1, i.e. in particular the step housing 31, the partition walls 32 and the wear rings 7, 8, to the bending line B of the shaft 6 only with the help of the wear rings 7 and 8 realize that can be manufactured particularly inexpensively as wear parts. No further modifications or structural measures are required for this adaptation.
  • All components with the exception of the wear rings 7, 8, i.e. especially the step housing 31, can be centered or concentric to the central axis A of the pump 1 are designed and arranged. This is a very significant advantage for structural and manufacturing reasons.
  • the inlet 4 of the pump 1 does not have to be inclined with respect to the central axis A, but can be configured and arranged, as is generally customary, so that the axis C of the Inlet 4 (see Fig. 1 ) is perpendicular to the central axis A.
  • the intermediate outlet 51 can be provided on the casing 2, through which the fluid can be withdrawn from the pump at an intermediate pressure which is lower than the delivery pressure at the outlet 5 of the pump 1 and higher than the suction pressure at the inlet 4 of the pump 1.
  • the water can be made available as the medium to be conveyed at different pressures.
  • the invention is particularly suitable as a method for maintaining, repairing and overhauling pumps that have already been commissioned especially for those pumps in which no or insufficient adjustment to the bending line B of the shaft 6 has been made.
  • At least one of the first and / or the second wear rings is replaced by an eccentrically configured wear ring 7 or 8, respectively.
  • the eccentricity E of the wear rings 7 and 8 is adapted to the bending line B of the shaft.
  • the invention is not based on the embodiment according to Fig. 1
  • the type of pump described is limited, but is particularly suitable for all multistage horizontal centrifugal pumps.
  • the pump 1 can also be configured as a section pump (ring section pumps), in which the entirety of the stage housing 31 forms the outer pump housing, where no additional casing housing 2 is provided.
  • the invention is also particularly suitable for pumps in which the impellers 32 are arranged in a so-called back-to-back arrangement.
  • the multistage pump has two groups of impellers, namely a first group of impellers, which are aligned with their inlet (their suction side) in the direction of one end of the pump, and a second group of impellers, which are aligned with their inlet (their suction side) are each aligned in the direction of the other end of the pump. These two groups are therefore arranged back to back to one another. It goes without saying that in the case of a two-stage pump each of the two groups comprises only one impeller. These two impellers are then arranged in such a way that their suction sides face away from each other.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (15)

  1. Une pompe centrifuge horizontale à plusieurs étages pour pomper un fluide, ayant un rotor (6, 32) qui comprend un arbre (6) disposé de manière rotative et une pluralité de roues (32) pour pomper le fluide, toutes les roues (32) étant disposées de manière non rotative sur l'arbre (6), et ayant un stator (31, 33) qui comprend une pluralité de boîtiers d'étage (31) disposés les uns derrière les autres par rapport à une direction axiale définie par un axe central (A), dans laquelle le stator (31, 33) entoure le rotor (6, 32), et dans laquelle tous les boîtiers d'étage (31) sont conçus et disposés de manière centrale par rapport à l'axe central (A), et dans laquelle une pluralité de bagues d'usure (7, 8) est prévue entre le rotor (6, 32) et le stator (31, 33), chacun d'entre eux étant fixé par rapport au stator (31, 33) et entourant le rotor (6, 32) avec un jeu respectif (S1, S2), caractérisé en ce qu'au moins une des bagues d'usure (7, 8) est conçue de manière excentrique, dans laquelle la conception excentrique de la bague d'usure signifie que la surface limite radialement extérieure de la bague d'usure est centrée sur un premier axe et la surface limite radialement intérieure de la bague d'usure est centrée sur un deuxième axe, les premier et deuxième axes étant parallèles mais non coïncidents.
  2. Une pompe selon la revendication 1, dans laquelle une pluralité de bagues d'usure (7, 8) sont conçues de manière excentrique.
  3. Une pompe selon l'une des revendications précédentes, dans laquelle les bagues d'usure (7, 8) ont une excentricité (E) qui augmente vers le centre de la pompe.
  4. Une pompe selon la revendication 3, dans laquelle l'excentricité (E) des bagues d'usure (7, 8) est adaptée à la ligne de flexion (B) de l'arbre (6).
  5. Une pompe selon la revendication 3 ou 4, dans laquelle l'excentricité (E) de toutes les bagues d'usure (7, 8) est dimensionnée de telle sorte que, lorsque l'arbre (6) est à l'arrêt, aucune des bagues d'usure (7, 8) ne touche l'arbre (6) ou une roue (32).
  6. Une pompe selon l'une des revendications 3 à 5, dans laquelle l'excentricité (E) de toutes les bagues d'usure (7, 8) est dimensionnée de telle sorte que la ligne de flexion (B) de l'arbre (6) est sensiblement centrale entre toutes les bagues d'usure (7, 8) à une vitesse nominale de la pompe.
  7. Une pompe selon l'une des revendications précédentes avec une pluralité d'étages de pompe (3) disposés les uns derrière les autres par rapport à la direction axiale, dans laquelle chaque étage de pompe (3) comprend une roue (32) munie d'une plaque de couverture avant (34) pour pomper le fluide, et un des boîtiers d'étage (31), et une paroi de séparation (33) stationnaire par rapport au boîtier d'étage (31) pour guider le fluide vers l'étage de pompe (3) adjacent, dans laquelle le boîtier d'étage (31) est conçu avec une ouverture de roue (37) stationnaire pour recevoir la plaque de couverture avant (34) de l'une des roues (32), dans laquelle chaque ouverture de roue (37) stationnaire est limitée radialement vers l'intérieur par une première bague d'usure (7) qui entoure la plaque de couverture avant (34) de la roue (32) avec un jeu (S1), et dans laquelle chaque paroi de séparation (33) stationnaire est délimitée radialement vers l'intérieur par une deuxième bague d'usure (8) qui entoure l'arbre (6) avec un jeu (S2).
  8. Une pompe selon l'une des revendications précédentes, dans laquelle chaque bague d'usure excentrique (7, 8) présente un moyen de positionnement (9) pour positionner la bague d'usure (7, 8) respective dans une orientation angulaire prédéterminée dans le boîtier d'étage (31) respectif ou la paroi de séparation (33) respective.
  9. Une pompe selon la revendication 8, dans laquelle le moyen de positionnement (9) est prévu à l'endroit où la bague d'usure (7, 8) respective présente sa largeur maximale (F) dans la direction radiale.
  10. Une pompe selon l'une des revendications précédentes, dans laquelle tous les boîtiers d'étage (31) sont disposés dans un boîtier d'enveloppe (2).
  11. Une pompe selon l'une des revendications précédentes avec une entrée (4) et une sortie (5) et une sortie intermédiaire (51) pour le fluide à pomper, dans laquelle la sortie intermédiaire (51) est conçue et disposée de telle sorte qu'au moins une partie du fluide peut être amenée sous une pression intermédiaire par la sortie intermédiaire (51), laquelle pression intermédiaire est supérieure à la pression du fluide à l'entrée (4) de la pompe et inférieure à la pression du fluide à la sortie (5) de la pompe.
  12. Une méthode de réparation ou de révision d'une pompe centrifuge (1) horizontale à plusieurs étages pour pomper un fluide, ayant un rotor (6, 32) qui comprend un arbre (6) disposé de manière rotative et une pluralité de roues (32) pour pomper le fluide, toutes les roues (32) étant disposées de manière non rotative sur l'arbre (6), et ayant un stator (31, 33) qui comprend une pluralité de boîtiers d'étage (31) disposés les uns derrière les autres par rapport à une direction axiale définie par un axe central (A), dans laquelle le stator (31, 33) entoure le rotor (6, 32), et dans lequel tous les boîtiers d'étage (31) sont conçus et disposés de manière centrale par rapport à l'axe central (A), et dans laquelle une pluralité de bagues d'usure (7, 8) est prévue entre le rotor (6, 32) et le stator (31, 33), chacun d'entre eux étant fixé par rapport au stator (31, 33) et entourant le rotor (6, 32) avec un jeu respectif (S1, S2), dans laquelle méthode une ou plusieurs des bagues d'usure (7, 8) sont remplacées, caractérisée en ce qu'une ou plusieurs des bagues d'usure (7, 8) sont chacune remplacées par une bague d'usure (7, 8) conçue de manière excentrique, dans laquelle la conception excentrique de la bague d'usure signifie que la surface limite radialement extérieure de la bague d'usure est centrée sur un premier axe et la surface limite radialement intérieure de la bague d'usure est centrée sur un deuxième axe, les premier et deuxième axes étant parallèles mais non coïncidents.
  13. Une méthode selon la revendication 12, dans laquelle l'excentricité (E) des bagues d'usure (7, 8) est adaptée à une ligne de flexion (B) de l'arbre (6).
  14. Une méthode selon la revendication 12 ou 13, dans laquelle l'excentricité (E) des bagues d'usure (7, 8) est dimensionnée dans chaque cas de telle sorte que, lorsque l'arbre (6) est à l'arrêt, aucune des bagues d'usure (7, 8) ne touche l'arbre (6).
  15. Une méthode selon l'une des revendications 12 à 14, dans laquelle l'excentricité (E) des bagues d'usure (7, 8) est dimensionnée dans chaque cas de telle sorte que la ligne de flexion (B) de l'arbre est sensiblement centrale entre toutes les bagues d'usure (7, 8) à une vitesse nominale de la pompe.
EP16200174.7A 2015-12-30 2016-11-23 Pompe centrifuge horizontale multi-etagée destinée au transport d'un fluide et son procédé de réparation Active EP3187736B1 (fr)

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RU2732086C2 (ru) 2020-09-11
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AU2016269429A1 (en) 2017-07-20
CN106930968A (zh) 2017-07-07
SG10201610286XA (en) 2017-07-28
EP3187736A1 (fr) 2017-07-05
ES2866155T3 (es) 2021-10-19
CA2951644A1 (fr) 2017-06-30
CA2951644C (fr) 2024-04-16
US20170191480A1 (en) 2017-07-06
US10724526B2 (en) 2020-07-28
CN106930968B (zh) 2023-03-21
AU2016269429B2 (en) 2022-01-06
RU2016149552A (ru) 2018-06-20
RU2016149552A3 (fr) 2020-03-20

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