EP3187736A1 - 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
EP3187736A1
EP3187736A1 EP16200174.7A EP16200174A EP3187736A1 EP 3187736 A1 EP3187736 A1 EP 3187736A1 EP 16200174 A EP16200174 A EP 16200174A EP 3187736 A1 EP3187736 A1 EP 3187736A1
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EP
European Patent Office
Prior art keywords
pump
shaft
rotor
wear
stage
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Granted
Application number
EP16200174.7A
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German (de)
English (en)
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EP3187736B1 (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
    • 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
    • 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
    • F04D1/08—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 multi-stage horizontal centrifugal pump for conveying a fluid, and a method for repairing or overhauling a multi-stage horizontal centrifugal pump according to the preamble of the independent claim of the respective category.
  • Multi-stage horizontal centrifugal pumps are used in many different technological fields, for example in the oil and gas processing industry or in industrial energy production. In the latter, such multi-stage pumps are used, for example, as feed pumps or boiler feed pumps to supply the water under the necessary pressure to a steam generator.
  • each pump stage comprises a stage housing, in each of which an impeller is provided, which promotes the fluid, so for example water, from the low-pressure side inlet of this pump stage to its high pressure side outlet, then connected to the inlet of the next stage.
  • All wheels are rotatably mounted on a common shaft, which consequently extends through all stage housing and 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 stationary with respect to the stage housing, ie, arranged or mounted stationary.
  • two wear rings are provided for one pump stage, namely a first wear ring on the low pressure side, which encloses the front cover disk of the rotor, and a second wear ring on the high pressure side, which is fixedly attached to a dividing wall which 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 Verschleissringe are each configured with a predetermined clearance with respect to the shaft, so that between the radially inner, cylinder jacket-shaped boundary surface of the wear ring and the rotating outer surface of the shaft, an annular gap is formed, 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 design of this game therefore plays an important role. Of course, it is always desirable that during operation of the pump direct physical contact between the stationary wear rings and the rotating shaft is avoided.
  • the wear rings are - as their name implies - wearing parts, which must be replaced during the life of the pump. This is primarily due to the fact that the leakage flow causes erosion phenomena on the wear rings. As a result, the gap between the respective wear ring and the shaft increases, which leads to an increase in the leakage flow. Since the increase in the leakage flow reduces the efficiency of the pump, then the wear ring must be replaced by new ones in the rule.
  • the rotor thus includes the shaft and the wheels. With long shafts or rotors there is a considerable deflection of the shaft due to its own mass. This deflection is usually the largest in the middle area of the shaft.
  • the center line of the shaft which without deflection would be a straight line which coincides with the center axis of the pump and with the axis of rotation, becomes a curved line through the deflection, which is referred to hereinafter as the bending line of the shaft or bending line of the rotor.
  • the bending line Approximately in the middle between the radial bearings for the shaft, the deviation of the bending line from the central axis of the pump is greatest. Due to the gravitational force, the bending line is a convex function in a horizontal pump.
  • the deflection of the shaft is greatest when the pump is at a standstill. As the shaft rotates, it usually results in stretching the shaft, i. in particular, their maximum deflection is reduced. This stretching is based in particular on hydrodynamic effects, such as the Lomakin bin.
  • Another way to solve this problem would be to significantly increase the clearance between the rotor and the wear rings so that the rotor is free to rotate even at standstill.
  • this solution is not desirable or even unacceptable because this increased clearance inevitably leads to a reduction in pump efficiency and efficiency, in the pursuit of minimizing energy consumption and environmentally friendly handling Resources.
  • a multi-stage horizontal centrifugal pump for conveying a fluid comprising a rotor, which comprises a rotatably arranged shaft and a plurality of impellers for conveying the fluid, all impellers being rotationally fixed on the shaft, and a stator having a plurality of stage housings.
  • radially configured with respect to the wear ring is meant that the radially outer boundary surface of the wear ring is centered about a first axis and the radially inner boundary surface of the wear ring about a second axis, wherein the first and the second axis parallel but not congruent are.
  • an eccentric wear ring is provided, then it can be ensured that the shaft or the rotor in the operating state, especially in the region of the strongest deflection approximately in the middle 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, so is in the eccentric wear ring still sufficient clearance, so that even when the rotor is a physical contact between the rotor and the wear ring is reliably avoided. Thus, the shaft or the rotor is free in particular even at a standstill, ie without contact with the wear ring, and can be rotated for example by hand.
  • a particular advantage of this embodiment according to the invention lies in the fact that the deflection of the shaft can be compensated only by a very cost-effective component, namely the wear ring, or several thereof.
  • a very cost-effective component namely the wear ring, or several thereof.
  • This in particular also allows a very cost-effective and less time-consuming adaptation to changes in the rotor setting, because it may be necessary to replace only one or more wear rings, but in particular requires no further structural change to other, much more expensive components of the pump, such as on one of the stage housing ,
  • all stage housings are arranged concentrically to the central axis of the pump. This is structurally particularly advantageous, because then the stage housing for at least almost all pump stages can be configured substantially the same. Since the deflection of the rotor is already compensated by the eccentric design of the wear ring, it is in particular not necessary to compensate for the deflection of the shaft by constructive measures on the stage housings themselves. For example, can be dispensed with an eccentric design of one or more stage housing or other components.
  • the number of wear rings for which an eccentric configuration is preferred depends on the particular application, and in particular on the length of the shaft, the number of wheels and the mass of the rotor. For many applications, it is preferable if a plurality of the wear rings is designed eccentrically.
  • the eccentricity of the wear rings over the length of the shaft is not constant.
  • the wear rings have an eccentricity that increases in the direction of the center of the pump. That is, as seen from one end of the pump, the eccentricity of the wear rings initially increases until it reaches its maximum in the region of the center of the pump, that is, where usually the deflection of the shaft is greatest, and then decreases again.
  • the eccentricity of the wear rings is adapted to the bending line of the shaft. That is, the greater the distance of the bending line from the center axis of the pump, the greater the eccentricity of the wear ring is selected, so that the eccentricity substantially follows the bending line of the shaft.
  • This measure has in particular the advantage that all stage housing can be arranged parallel and perpendicular to the central axis of the pump. It can thus be dispensed with an oblique arrangement of the stage housing or other components.
  • the eccentricity of all wear rings is dimensioned so that when the shaft is stopped, none of the wear rings touches the shaft or an impeller. Since the deflection of the shaft or of the rotor is greatest at standstill, the radial width of the gap between the wear rings on the one hand and the rotor (shaft or impeller) can be minimized by this measure. It is also preferred if the eccentricity of all wear rings is dimensioned such that the bending line of the shaft extends at a nominal rotational speed of the pump essentially centrally between all wear rings. The bent shaft then rotates at least approximately centered with respect to wear rings, so it has the same in all radial directions Game. Among other things, this is especially advantageous for thermally induced changes in the rotor.
  • the pump has a plurality of pump stages, which are arranged one behind the other with respect to the axial direction, wherein each pump stage comprises a front cover provided with a wheel for conveying the fluid, and one of the stage housing, and with respect to the stage housing stationary partition wall for guiding the fluid housing to the adjacent pump stage, wherein the stage housing is configured with a stationary impeller opening for receiving the front cover plate of one of the wheels, wherein each stationary impeller opening is bounded radially inwardly by a first wear ring, which surrounds the front cover of the impeller with a game, and wherein each stationary partition is bounded radially inwardly by a second wear ring which surrounds the shaft with a clearance.
  • the eccentricity of all wear rings is such that at standstill of the shaft just none of the wear rings touches the shaft or an impeller. This makes it possible to further reduce both the clearance between the shaft and the second wear rings and the clearance between the front shrouds of the wheels and the first wear rings in comparison to known multiphase pumps, whereby the efficiency of the pump according to the invention can be increased still further.
  • each eccentric wear ring has a positioning means to position the respective wear ring in a predetermined angular orientation in the respective stage housing or the respective partition wall.
  • This positioning means may for example be an optically recognizable marking on the wear ring or a positioning pin which engages in a corresponding bore in the step housing or in the partition wall.
  • the positioning means is provided where the respective wear ring has its maximum width in the radial direction, because this allows a particularly simple mounting of the wear ring.
  • the pump is designed as a shell casing pump (barrel casing pump), in which all stage casings are arranged in a shell casing. Since all stage housing can be arranged parallel to each other and perpendicular to the central axis of the pump, the inlet nozzle can be manufactured in a conventional manner, that is, on the above-described problematic tilting of the inlet nozzle can be dispensed with. In addition, it is possible to provide reliable seals between the stage housings and the outer shell casing. Thus, different pressure chambers can be provided in the interior of the shell, in which the fluid is present under different pressures.
  • the pump according to the invention makes it possible in particular for the pump according to the invention to be designed with an inlet and an outlet and an intermediate outlet for the fluid to be delivered, wherein the intermediate outlet is designed and arranged such that at least a portion of the fluid can be removed under an intermediate pressure through the intermediate outlet 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 at a pressure other than that at the outlet is a great advantage for many applications.
  • the invention further proposes a method for repairing or overhauling a multi-stage horizontal centrifugal pump for conveying a fluid having a rotor comprising a rotatably arranged shaft and a plurality of impellers for conveying the fluid, all impellers are rotatably mounted on the shaft, and with a stator comprising a plurality of stage housings arranged one behind another with respect to an axial direction defined by a central axis, the stator surrounding the rotor, and wherein all the stage housings are configured and arranged centrically with respect to the central axis, and wherein there are more between the rotor and the stator Wear rings are provided, each of which is fixed relative to the stator, and surrounds the rotor each with a game, in which method one or more of the wear rings are replaced, wherein one or more of the wear rings each by an eccentrically designed Wear ring is replaced.
  • the method is also suitable for repairing or overhauling a multistage horizontal centrifugal pump for delivering a fluid having a rotatably arranged shaft and having a plurality of pump stages arranged one behind the other with respect to an axial direction defined by a central axis, each pump stage having a front cover plate and a step housing with a stationary impeller opening for receiving the front cover of one of the wheels, and a stationary relative to the stage housing partition for guiding the fluid to the adjacent pump stage, the impellers of all pump stages rotatably mounted on the shaft wherein each stationary impeller opening is bounded radially inwardly by a first wear ring which circumferentially surrounds the front cover disk of the impeller, and wherein each stationary partition wall is radially inward is limited by a second wear ring, which surrounds the shaft with a game.
  • one or more of the first and / or second wear rings is replaced, wherein one or more of the first and / or the second wear rings is replaced
  • this method it is both possible to maintain a pump designed according to the invention, or to adapt it to a different rotor setting, as well as to overhaul or retrofit a conventional pump without eccentric wear rings in such a way that it is subsequently designed according to the invention. Consequently, this method is also particularly suitable for retrofitting existing pumps so that the deflection of the rotor is compensated or better compensated by one or more eccentrically configured wear rings. It is particularly advantageous that this conversion is usually feasible only by replacing the cost wear rings, without modifying other components of the pump.
  • Fig. 1 shows a schematic side view of an embodiment of an inventive multi-stage horizontal centrifugal pump, which is designated overall by the reference numeral 1.
  • Fig. 1 some parts of the pump 1 are shown in the outbreak.
  • 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, z.
  • feed or boiler feed pumps in which the fluid to be pumped is water, which is funded by the pump 1 to a steam generator.
  • such pumps are used both for the promotion of water, for example as injection pumps, or for the extraction of oil or other hydrocarbons.
  • the pump 1 is configured with an outer shell casing 2 (barrel casing) having an inlet 4, an outlet 5, and optionally an intermediate outlet 51 for the fluid to be delivered.
  • outer shell 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 rotated by a drive, not shown, for example, an electric motor in rotation.
  • 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 desired axis of rotation about which the shaft 6 is intended to rotate.
  • the central axis A would be congruent with the longitudinal axis of the shaft.
  • the direction of the center axis A of the pump 1 is always meant.
  • the radial direction is meant a direction perpendicular to the axial direction.
  • a plurality of - in this case for example eight - pump stages 3 are provided in a conventional manner, which are arranged one behind the other with respect to the axial direction.
  • Fig. 1 is the pump 1 in its normal position of use, ie in a horizontal arrangement, shown, in which the central axis A is horizontal or parallel to the ground.
  • FIG. 2 shows 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 step housing 31 and, on the high pressure side, a partition wall 33 which delimits the pump stage 3 with respect to the next pump stage 3.
  • Each impeller 32 is designed as a closed impeller 32, that is, it comprises a front cover plate 34, a rear cover plate 35 and a plurality of arranged between the cover plates 34,35 blades 36 for conveying the fluid.
  • Each stage housing 31 includes a stationary impeller opening 37 for receiving the front shroud 34 of one of the impellers 32.
  • the dividing wall 33 is also stationary with respect to the stage housing 31 and serves to deliver the fluid conveyed by the impeller 32 to the inlet, ie impeller 32 of the next pump stage 3 to lead.
  • the partition 33 comprises a stationary stator, which is not shown in detail in the drawing figures.
  • the wheels 32 of all pump stages 3 are rotatably connected to the shaft 6, so that the wheels 32 rotate together with the shaft 6.
  • the term “rotor” means the entirety of all components of the pump 1, which rotate in the operating state of the pump 1.
  • the rotor of the pump 1 thus comprises both the shaft 6 and all impellers 32 arranged thereon, as well as possibly further components of the pump 1, which rotate together with the shaft 6 or are connected in a rotationally fixed manner to the shaft 6.
  • the term “stator” of the pump means the entirety of the stationary, ie non-rotating, components of the pump.
  • the stator thus comprises in particular all stage housings 31 and all partition walls 32.
  • the fluid to be pumped ie z.
  • This process continues through all pump stages 3 to the last - this is in Fig. 1 the representation according to the leftmost - from the output of the fluid is then passed to the outlet 5 of the pump 1.
  • a first wear ring 7 is fitted in the impeller opening 37 of the stage housing 31, so that the stationary impeller opening is bounded radially inwardly by the first wear ring 7, which is firmly connected to the stage housing 3 and thus stationary.
  • the first wear ring 7 thus surrounds the front cover plate 34 of the wheels 32.
  • a second wear ring 8 is provided radially inwardly of the stationary partition wall 33 and surrounds the shaft 6, that is, the stationary partition 33 is radially inwardly bounded by the second wear ring 8, which is arranged with respect to the radial direction between the partition 33 and the shaft 6.
  • the second wear ring 8 is firmly connected to the partition 33 and thus 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 a clearance, so that in each case 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 flows a leakage flow against the general conveying direction of the fluid.
  • this leakage flow is desirable, in particular in order to hydrodynamically stabilize the rotor, but on the other hand should not be too large because the leakage flow reduces the efficiency of the pump.
  • it should be avoided during the normal operating states of the pump 1 that there is a direct physical contact between the rotor (shaft 6 or impeller 32) and one of the wear ring 7, 8.
  • Fig. 3 an enlarged sectional view illustrating the game of a first and a second wear ring 7 and 8 respectively.
  • Fig. 3 exists between the radially inner boundary surface of the first wear ring 7 and the radially outer boundary surface of the front cover plate 34 of the impeller 32 a game S1 through which an annular gap between the first wear ring 7 and the front cover plate 34 is formed.
  • a game S2 through which an annular gap between the second wear ring 8 and the shaft 6 is formed.
  • the game S1 can, but does not have to be the same size as the game S2.
  • a bend is in Fig. 6 very schematically illustrated by a bending line B.
  • the center line of the shaft 6 is meant when the shaft 6 including the non-rotatably connected wheels 32 and other components, so the rotor, is mounted in the pump 1, when the shaft 6 so in their camps and in particular the radial bearings is arranged, which are located outwardly in the region of the two ends of the shaft 6, but not shown in detail.
  • the deflection D of the shaft 6 is understood to be the distance of the bending line B from 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 in Fig. 6 is shown. Depending on the length of the shaft 6 and mass of the wheels 32, the maximum deflection D may be a few tenths of a millimeter, for example 0.2 - 0.5 mm or more.
  • At least one of the first or second wear rings 7 and 8 is designed eccentrically.
  • Fig. 4 an embodiment of such eccentrically designed wear ring 7 and 8 is shown in a perspective view.
  • Fig. 5 shows a section through the wear ring 7, 8 from Fig. 4 , wherein the cut takes place in the axial direction, ie in the same way as in Fig. 3 , Additionally illustrated Fig. 5 the term eccentric design or eccentricity.
  • both the radially outer and the radially inner boundary 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, of course, R2 is smaller than R1.
  • the radially outer boundary surface is centered about a first axis A1, ie A1 is identical to the cylinder axis of the radially outer boundary surface.
  • the radially inner boundary surface is centered about a second axis A2, ie A2 is identical to the cylinder axis of the radially inner boundary surface here.
  • the axes A1 and A2 are parallel to each other but not congruent. This embodiment of the non-congruent axes A1 and A2 is referred to as eccentric.
  • the eccentricity E is determined, which is given by the distance between the two axes A1 and A2.
  • the eccentricity E can be in the range of up to a few tenths of a millimeter. With today's modern machining methods, it is no problem to manufacture 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, wherein the radial width F, the expansion of the wear ring 7 and 8 in the radial 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 in the correct angular orientation to the step housing 31 or to the dividing wall 33. Since the deflection D of the shaft 6 always takes place with respect to the normal position of use downward, the wear ring 7 or 8 is used in such an orientation that the Area of its maximum radial width F is perpendicular above the central axis A, or the region of its minimum radial width F perpendicular below the central axis A.
  • each eccentric wear ring 7 or 8 has a positioning means 9.
  • This positioning means 9 may be, for example, a pin 9 which protrudes in the axial direction of the ring and during assembly into a corresponding bore (not shown) engages in the respective stage housing 31 and in the respective partition wall 33.
  • other positioning means 9 are possible, for. B. a projection or a recess on the wear ring 7 and 8, which cooperates positively with a recess or a projection in the step housing 31 and in the partition wall 33, or optically recognizable markings, such as notches, dashes or arrows.
  • Fig. 5 shown rectangular cross-sectional area of the wear ring 7 and 8 is to be understood only as an example.
  • the wear rings 7 and 8 may 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 may for example also be designed in an L-shaped or trapezoidal shape, it may have obliquely or at an acute angle to each other extending boundary lines.
  • rounding or bevels may be provided. The person skilled in a sufficient number of ways for the design of this cross-sectional area are known.
  • first wear ring 7 has a different geometric configuration than the second wear ring 8, even if the geometric configurations can be basically 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 and 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 such that the rotating shaft 6 or the rotating cover disk 34 of the impeller 32 is at least approximately centered relative to the radially inner boundary surface of the eccentric wear ring 7 or 8, that is, the eccentricity E is chosen in that it is at least approximately the deflection D of the rotating shaft 6 at the location of this wear ring 7 or 8. It then follows that the rotating shaft 6 or the rotating cover disk 34 in this eccentrically designed wear ring 7 and 8 with respect to the second axis A2 (see Fig. 5 ) is at least approximately centered.
  • This eccentrically designed wear ring 7 or 8 is now attached to the step housing 31 and to the partition wall 33, preferably using the positioning means 9, that its area in which the radial width F is maximum, is arranged vertically above the central axis A. If now the rotor rotates, it is essentially centered in this wear ring 7 or 8, ie the rotor is - as described above - at least approximately centered with respect to the axis A2. This means the game S1 or S2 (see Fig. 3 ) is at least approximately constant within this wear ring 7 or 8 in the circumferential direction of the rotor, so that 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 grinding between the rotor and the wear ring 7 or 8.
  • this freedom from contact is also advantageous for starting and stopping the pump 1, because there is no grinding between the rotor and the wear ring 7 or 8.
  • on the one hand can be dispensed with a coating of the wear ring 7 and 8, and on the other hand increases the life of the rotor, because its components are not exposed to mechanical grinding on the wear ring 7 and 8 respectively.
  • both the first and the second wear rings 7 and 8 is designed eccentrically.
  • the eccentricity E of an individual wear ring 7 or 8 is adapted to the deflection D of the shaft 6 at its individual place.
  • a bending line B as for example in Fig. 6 is shown, therefore, takes the eccentricity E of Verschleissringe 7 and 8, preferably from both ends of the shaft 6 seen from in the direction of the center of the pump 1 to.
  • 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. Of course it is also possible to determine the bending line B metrologically or to determine by calculations, such as simulations.
  • the bending line B is at least approximately known for a specific pump 1, it can also be decided in which regions of the rotor the deflection D of the shaft 6 is so great that wear rings 7 and 8 configured eccentrically there are advantageous.
  • the eccentricity E of the wear ring 7 and 8 is so dimensioned that at standstill of the shaft 6 just none of the wear rings 7 and 8, the shaft 6 touches, so that the shaft 6 at standstill just rests on none of the wear rings 7 and 8 and thus is freely rotatable, especially by hand.
  • the second criterion is to dimension the eccentricity for each individual wear ring 7 or 8 so that the bend line B of the shaft 6 at a typical speed at which the pump 1 is operated, for example the rated speed, substantially, or at least approximately midway between all wear rings 7 and 8 runs.
  • the Fig. 6 and 7 show in a schematic representation of this adjustment of the eccentricity E to the bending line B of the shaft 6. Because it is better for understanding, the rotor in the Fig. 6 and 7 each represented only by the bending line B of the shaft 6, ie in Fig. 6 and Fig. 7 is not considered that the rotor has a finite extent in the radial direction. The radial extent of the rotor is therefore not shown, but the Bend line B is to be understood symbolically for a representation of the rotor or the shaft 6 with the wheels 32.
  • Fig. 6 shows for the embodiment Fig. 1 the situation for the state when the shaft 6 rotates at a typical speed, for example, the rated speed of the pump 1.
  • the eccentricity E of both the first and the second wear rings 7 and 8 initially increases from the illustration according to the left end to approximately the middle of the pump 1 and then decreases again in the direction of the illustration of the right end of the pump.
  • the bending line B is at least approximately centered with respect to the radially inner boundary surface of all wear rings 7 and 8.
  • the game S1 or S2 For each of the wear rings 7 and 8 respectively in the circumferential direction, at least approximately constant.
  • Fig. 7 shows for the 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 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 in terms of temperature changes, especially rapid or temporary temperature changes. Since the rotor or the shaft 6 in operation always in an optimal position with respect to the stage housing 31 and the partition walls 32, or more generally expressed with respect to the stator of the pump 1, steeper temperature changes, ie larger temporal temperature gradients are possible without that There is a risk that the rotor comes into direct physical contact with the wear rings 7 or 8, and without it being necessary to provide other measures such as preheating the pump 1.
  • Another advantage resulting from the adaptation of the eccentricity E of the wear rings 7 or 8 to the bending line B of the shaft 6, is that the optimized positioning of the rotor with respect to the stator in many applications, the game S1 or S2 ( please refer Fig. 3 ), which can increase the efficiency of the pump 1 and its efficiency.
  • a particular advantage of the inventive design is the possibility of adapting the stator of the pump 1, so in particular the stage housing 31, the dividing 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 produced as wear parts particularly cost. There is no need for further modifications or structural measures for this adaptation. Neither does it require an inclination of one or more of the stage housing 31, nor does it require an eccentric design of other components such as the stage housing 31 or the partitions 32. All components except the wear rings 7, 8 so in particular the step housing 31 may be centered or concentric configured and arranged to the central axis A of the pump 1. This is a very significant advantage under design and manufacturing reasons.
  • the inlet 4 of the pump 1 with respect to the central axis A does not have to be inclined, but as generally custom can be configured and arranged so that the axis C of Inlet 4 (see Fig. 1 ) is perpendicular to the central axis A.
  • the advantage results that reliable seals between the outer sides of the step housing 31 and the jacket housing 2 can be provided by the parallel alignment of all pump stages 3 ,r all stage housing 31 in pumps 1 with jacket housing 2 as in the embodiment described here.
  • the intermediate housing 51 can be provided on the jacket housing 2, through which the fluid can be removed from the pump at an intermediate pressure which is smaller than the delivery pressure at the outlet 5 of the pump 1 and greater than the suction pressure at the inlet 4
  • the water can be provided as a medium to be delivered at various pressures.
  • the invention is particularly suitable as a method for the maintenance, repair and overhaul of already put into operation pumps and especially for such pumps in which no or no sufficient adjustment to the bending line B of the shaft 6 has been made so far.
  • At least one of the first and / or the second wear rings is replaced in each case by an eccentrically designed wear ring 7 or 8 in a similar manner as described above.
  • the eccentricity E of the wear rings 7 and 8 is adapted to the bending line B of the shaft.
  • the invention is not according to the embodiment according to Fig. 1 described pump type is limited, but is suitable for all multi-stage horizontal centrifugal pumps.
  • the pump 1 can also be configured as a chain pump (ring section pumps), in which the entirety of the step housings 31 form the outer pump housing, ie where no additional jacket housing 2 is provided.
  • the invention is also suitable for such pumps, in which the wheels 32 are arranged in a so-called back-to-back arrangement.
  • the multi-stage pump has two groups of impellers, namely a first group of impellers aligned with their inlet (their suction side) respectively toward one end of the pump and a second group of impellers provided with their inlet (their suction side) are each aligned in the direction of the other end of the pump. These two groups are thus arranged back to back to each other. It is understood that in the case of a two-stage pump, each of the two groups comprises only one impeller. These two wheels are then arranged so that their suction sides are facing 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)
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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US (1) US10724526B2 (fr)
EP (1) EP3187736B1 (fr)
KR (1) KR20170080478A (fr)
CN (1) CN106930968B (fr)
AU (1) AU2016269429B2 (fr)
CA (1) CA2951644C (fr)
ES (1) ES2866155T3 (fr)
MX (1) MX2016016581A (fr)
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CN108194403A (zh) * 2018-01-23 2018-06-22 江苏沃特加汽车科技有限公司 一种水泵前轴承座
CN108194421A (zh) * 2018-01-23 2018-06-22 江苏沃特加汽车科技有限公司 一种水泵壳体
CN108412777A (zh) * 2018-04-13 2018-08-17 沈阳格瑞德泵业有限公司 一种定子部件挠性弯曲的多级离心泵
JP2020020338A (ja) * 2018-07-18 2020-02-06 サンデン・オートモーティブクライメイトシステム株式会社 送風機
US12006949B2 (en) * 2018-11-21 2024-06-11 Sulzer Management Ag Multiphase pump
EP3667099A1 (fr) * 2018-12-13 2020-06-17 Grundfos Holding A/S Ensemble de pompe
EP3686436A1 (fr) * 2019-07-31 2020-07-29 Sulzer Management AG Pompe à plusieurs étages et agencement de pompage sous-marin
CN110863991A (zh) * 2019-11-26 2020-03-06 福斯流体控制（苏州）有限公司 具有高稳定性的氢进料泵
IT201900023160A1 (it) * 2019-12-06 2021-06-06 Eurotecnica Melamine Ag Pompa centrifuga per processare urea fusa e relativo impianto
DE102021105624A1 (de) * 2021-03-09 2022-09-15 KSB SE & Co. KGaA Herstellung eines Leitrades auf hybride Weise
KR102630188B1 (ko) 2021-10-25 2024-01-29 주식회사 우리원테크 다단 원심 펌프
CN114320996B (zh) * 2021-11-25 2024-05-24 中船双瑞(洛阳)特种装备股份有限公司 一种节能型异形口环及离心泵间隙密封结构
CN114233686A (zh) * 2022-02-10 2022-03-25 浙江水泵总厂有限公司 水泵冷却结构及具有其的冷却系统

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US10724526B2 (en) 2020-07-28
MX2016016581A (es) 2018-06-13
RU2016149552A (ru) 2018-06-20
RU2732086C2 (ru) 2020-09-11
AU2016269429A1 (en) 2017-07-20
AU2016269429B2 (en) 2022-01-06
CN106930968B (zh) 2023-03-21
CA2951644A1 (fr) 2017-06-30
RU2016149552A3 (fr) 2020-03-20
CA2951644C (fr) 2024-04-16
EP3187736B1 (fr) 2021-04-14
US20170191480A1 (en) 2017-07-06
SG10201610286XA (en) 2017-07-28
CN106930968A (zh) 2017-07-07
ES2866155T3 (es) 2021-10-19
KR20170080478A (ko) 2017-07-10

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