US20150308446A1 - Impeller for a centrifugal pump, a centrifugal pump and a use thereof - Google Patents

Impeller for a centrifugal pump, a centrifugal pump and a use thereof Download PDF

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Publication number
US20150308446A1
US20150308446A1 US14/680,212 US201514680212A US2015308446A1 US 20150308446 A1 US20150308446 A1 US 20150308446A1 US 201514680212 A US201514680212 A US 201514680212A US 2015308446 A1 US2015308446 A1 US 2015308446A1
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United States
Prior art keywords
pump
impeller
vanes
shroud
face
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Abandoned
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US14/680,212
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English (en)
Inventor
Matti Koivikko
Kalle TIITINEN
Sami Virtanen
Jussi Ahlroth
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Sulzer Management AG
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Sulzer Management AG
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Assigned to SULZER MANAGEMENT AG reassignment SULZER MANAGEMENT AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AHLROTH, JUSSI, KOIVIKKO, MATTI, Tiitinen, Kalle, VIRTANEN, SAMI
Publication of US20150308446A1 publication Critical patent/US20150308446A1/en
Abandoned legal-status Critical Current

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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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F04D7/045—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous with means for comminuting, mixing stirring or otherwise treating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D31/00—Pumping liquids and elastic fluids at the same time

Definitions

  • the present invention relates to an impeller for a centrifugal pump, a centrifugal pump and a use thereof.
  • the present invention relates especially to a novel closed impeller structure for a centrifugal pump.
  • the centrifugal pump utilizing the impeller of the present invention is suitable for pumping both clean liquids and solids-containing liquids like for instance fibrous suspensions of pulp and paper or board industry.
  • FIG. 1 illustrates schematically two efficiency curves in relation to the specific speed
  • FIG. 2 the specific speed and its relation to basic pump construction. What FIG. 2 in practice teaches is that the specific speed is the higher the larger is the capacity of the pump. In other words, small sized pumps have a low specific speed.
  • Specific speed means a dimensional value characterizing the shape of the pump impeller by head (H), flow (Q) and speed (n). Specific speed is calculated by using the following equation:
  • n s n*Q BEP 1/2 /H BEP 3/4 [min ⁇ 1],
  • hydraulic pump efficiency or mere efficiency ( ⁇ ) which is the ratio between the mechanical power transferred to the liquid during its passage through the pump and the mechanical input power transmitted to the pump at its shaft.
  • the solid curve A shows the efficiency required by the EU
  • the dashed curve B the efficiency of a series of today's pumps having a semi-open impeller.
  • a series of pumps is meant pumps having the same basic construction but a differing capacity/flow designed to cover, more or less, all the pumping needs (in view of flow) of the customers.
  • the semi-open impellers have an efficiency well above that required by the EU.
  • the efficiency curve B drops below the EU-curve A.
  • centrifugal pumps having closed impellers, shrouds with smooth faces opposite to the working vanes and wear rings.
  • specific speed of a centrifugal pump correlates to efficiency, it has been understood now when studying the pumps having a low specific speed that they have low efficiency due to two impeller-related factors having a relatively high impact to efficiency.
  • the first factor being high leakage flow, in relation to the total flow, via the wear rings.
  • the second factor is the energy wasted on the smooth faces of the shrouds in relation to the total power used by the pump.
  • the leakage flows appear in the case of open impellers at the opposite side edges of the impeller vanes, as there has to be a certain running clearance between the side edges of the vanes and the walls of the volute casing, whereby a part of the fluid to be pumped is able to pass via such a clearance from a preceding vane cavity to a succeeding vane cavity.
  • the closing of the side edges of the working vanes in closed impellers not only creates a leakage flow round the radially outer circumferential edge/s of the shroud/s but also subjects the face/s of the shroud/s opposite to the working vanes to the pressure of the pumped fluid.
  • the pressure distribution at the rear side of the shroud is parabolic, i.e. at its highest at the outer circumference of the impeller from where it reduces gradually when moving towards the shaft of the impeller.
  • the pressure results, both with semi-open and closed impellers, in an axial thrust pushing the impeller towards the pump inlet, as the full area of the rear shroud is subjected to the fluid pressure.
  • the axial thrust is clearly greater in semi-open impellers than in closed impellers, as, in semi-open impellers there is no front shroud to the front side of which the pressure could act like in closed impellers. Yet, in both impeller types the impeller needs to be balanced such that the bearings of the shaft of the pump are not subjected to a too high axial load. Also, without any measures the pressure affects the shaft sealing, and has to be limited for preventing the sealing from deteriorating.
  • the axial force is balanced by arranging to the rear face of the shroud pump-out vanes the purpose of which is to increase the speed of the fluid entering the rear side of the shroud such that its pressure is reduced. Thus, the rear pump-out vanes act somewhat like the impeller working vanes.
  • the situation is different. There is no need to fight the pressure, which is one of the major tasks of the rear pump-out vanes, as there is no reason to try to lower the pressure due to the fact that the area of the front shroud face opposite to the working vanes is much smaller than the area of the rear shroud face opposite the working vanes.
  • the front face of the shroud has to be provided with means to minimize the leakage flow round the impeller circumference to the front side of the front shroud. At its worst there is a significant recirculating leakage flow from the pressure side of the impeller back to the suction side of the impeller through the gap between the front shroud of the impeller and the volute casing.
  • Such a leakage flow takes a substantial amount of energy used for pumping, whereby the efficiency of the impeller is decreased remarkably.
  • the leakage flow may be controlled, i.e. either by arranging a sealing, most often called as a wear ring, between the impeller and the volute casing, or by arranging front pump-out vanes on the front face of the front shroud, i.e. on the face opposite to the working vanes.
  • Wear rings which function basically as a slide ring sealing, restrict efficiently the amount of discharge fluid that tries to circulate back to the suction side of the impeller. Wear rings provide an adequate solution for applications that handle clear water or occasionally handle light solids. However, as the wear ring has a certain operating clearance, the wear ring must be replaced, when the clearance becomes excessive. The flow restriction created by the tight clearance between the stationary and rotating wear ring faces causes very high local velocities and hence a high wear rate. If the fluid to be pumped contains abrasive particles, wear rings, because they are subject to a very high flow velocity, will have an unacceptably short life span, even when made of hard materials or when their surfaces have been specifically treated in view of wear. Thus the use of a wear ring is not desirable when pumping liquids containing solids.
  • Pump-out vanes offer a better alternative for handling abrasive solids.
  • the use of such pump-out vanes is known from slurry pumps like, for instance, those discussed in US-A1-20090226317.
  • Pump-out vanes control the leakage through a pumping action creating a head to prevent or at least counter any leakage or recirculation from an outer high pressure peripheral outlet of the impeller radially inwardly in-between the impeller and the volute casing.
  • the pump-out vanes are typically almost radial, or arranged at an angle of 10-30 degrees from the radial direction.
  • a further known disadvantage of closed impellers is that the smooth front and back shrouds (not having pump-out vanes), rotating in close proximity to the casing walls, generate disc friction that lowers the efficiency of the pump relative to that found in open impeller designs.
  • an object of the present invention is to find a way to improve the construction of the centrifugal pumps at least at the lower end of the specific speed range of a series of pumps such that the efficiency for the entire range of pumps is above the EU efficiency curve.
  • Another object of the present invention is to change the construction of the impeller such that the efficiency of an impeller may be raised.
  • Yet another object of the present invention is to design the impeller such that its pump-out vanes both prevent the leakage flow and function in an energy efficient manner, i.e. the pump-out vanes are to be designed such that they prevent the leakage flow in an optimal way in view of the total efficiency of the impeller.
  • a still further object of the present invention is to design a novel impeller that is able to prevent the recirculating leakage flow of liquids containing solids without the use of wear ring/s.
  • an impeller for a centrifugal pump having a front shroud, a rear shroud, and one or more working vanes therebetween, the front shroud having a front (first) face opposite to the (second) face having the working vanes, the rear shroud having a rear (first) face opposite to the (second) face having the working vanes, the front shroud having an outer circumference and a plurality of front pump-out vanes attached to the front face of the shroud, the rear shroud having a plurality of rear pump-out vanes attached to the rear face of the shroud, wherein the front pump-out vanes are dimensioned in accordance with an equation:
  • the centrifugal pump impeller of the present invention brings about several advantages in comparison to prior art centrifugal pumps. At least the following advantages may be found
  • FIG. 1 illustrates schematically a comparison between the efficiency curves based on EU-regulations and on a present series of centrifugal pumps
  • FIG. 2 explains schematically the correlation between the impeller type and the specific speed
  • FIG. 3 illustrates schematically a partial axial cross sectional view of a prior art centrifugal pump
  • FIG. 4 illustrates schematically a partial axial cross sectional view of another prior art centrifugal pump
  • FIG. 5 illustrates schematically the basic functional differences between the pump-out vanes of the impeller of the present invention by comparing such in the total head vs. flow rate coordinates with both the working vanes and the pump-out vanes of the front shroud of a prior art impeller,
  • FIG. 6 illustrates the impeller in accordance with a preferred embodiment of the present invention
  • FIG. 7 illustrates schematically a comparison between the efficiency curves based on EU-regulations and on centrifugal pumps utilizing the impeller of the present invention.
  • FIG. 3 is a schematical cross sectional illustration of a prior art centrifugal pump having a closed impeller.
  • the pump of FIG. 3 comprises a volute casing 2 , a rear wall 4 , a shaft 6 and an impeller 8 attached to the end of the shaft 6 .
  • the volute casing 2 comprises an inlet or suction duct 10 , and an outlet or discharge duct 12 .
  • the rear wall 4 which is fastened to the volute casing 2 comprises some kind of sealing means or device 14 for axially sealing the shaft 6 .
  • a stuffing box type sealing is shown.
  • the impeller 8 is, as mentioned already above, a closed one, which means that the working vanes 16 of the impeller 8 are at their both sides covered by a shroud, a rear shroud 18 and a front shroud 20 .
  • To the sides of the shrouds 18 , 20 opposite to the working vanes 16 so called pump-out vanes 22 , 24 , respectively, have been arranged.
  • the vanes 22 , 24 are usually radial though also somewhat (of the order of 10-30 degrees from radial direction) inclined pump-out vanes have been used.
  • the impeller may also be provided with a series of balance holes (not shown) arranged to run through the rear shroud 18 close to the shaft 6 .
  • the impeller 8 is arranged to run in the volute casing 2 at a small clearance, i.e. such that the clearance between the rear pump-out vanes 22 and the rear wall 4 is as small as practically possible, i.e. of the order of 0.4-1.0 mm.
  • the front side of the impeller 8 is sealed by means of a so called wear ring 26 in relation to the volute casing 2 .
  • the wear ring 26 is a cylindrical sleeve arranged at the end of the inlet duct 12 facing the impeller 8 .
  • the impeller 8 is provided with a cylindrical extension 28 fitting within the wear ring 26 with a small clearance.
  • the cylindrical extension 28 may also be provided with a specifically treated surface or a specific ring facing the wear ring 26 of the volute casing.
  • FIG. 4 is a schematical cross sectional illustration of a prior art centrifugal pump having a closed impeller.
  • the centrifugal pump of FIG. 4 is identical to the pump of FIG. 3 except for the front end of the impeller.
  • the impeller of FIG. 3 included the lengthy cylindrical extension 28 cooperating with the wear ring arranged to the casing surface
  • the casing surface of the pump of FIG. 4 is not provided with any wear ring, but the shorter cylindrical extension of the impeller is arranged at a distance 30 from the counter surface of the volute casing such that liquid to be pumped may flow relatively freely to or from the volume between the front shroud and the volute casing.
  • the treatment of the leakage flow has to be thought over once again.
  • a centrifugal pump cannot be designed merely for pumping pure water, liquid or suspensions containing more or less solids has to be taken into account, too.
  • the use of the wear ring remains a secondary means for fighting the leakage flow, as the wear ring is susceptible to considerable wear and difficult maintenance operation if the liquid to be pumped contains solids.
  • the design of pump-out vanes in a novel way.
  • the aim of the invention is to design pump-out vanes such that they prevent the leakage flow in an optimal way in view of the total efficiency of the impeller.
  • the main task of the front pump-out vanes is to prevent the leakage flow, it has to be accepted that they consume power, but their power consumption has to be minimized.
  • the front pump-out vanes in the volume between the front shroud and the volute casing are designed to improve the efficiency by means of following three mechanisms:
  • the velocity field thereof is dimensioned such that the friction subjected to the shroud surface is as low as possible, preferably lower than when using a smooth-faced shroud.
  • the pressure the pump-out vanes create is dimensioned such that the pump does not leak at its BEP (best efficiency point) from its outer circumference to the suction duct.
  • the hydraulic energy transferred via the front volume is kept at such a low level that only a minimal flow is allowed via the front volume. Thereby, even if the efficiency of the front pump-out vanes themselves is weak, its effect on the total efficiency of the impeller is negligible. Thus, substantially all of the hydraulic energy is produced by the working vanes operating in high-efficiency closed liquid passages.
  • the impeller When the impeller is constructed in accordance with the above guidelines, the impeller has a front and a rear shroud and liquid passages formed between the shrouds and each successive pairs of working vanes. Both the front and the rear shrouds are provided with front and rear pump-out vanes, respectively. The pump-out vanes create a field of pressure. When pumping liquid with the pump a small or negligible flow compared to the flow via the liquid passages is allowed to be guided to the effective area of the front pump-out vanes.
  • the impeller should be designed to work without the wear ring in case the liquid to be pumped contains solids.
  • the present invention introduces a manner by which the total efficiency of the impeller may be raised in impellers having a low specific speed.
  • the power needed for running the front pump-out vanes is negligible compared to traditional pump-out vanes.
  • the pump-out vanes of the present invention are still able to maintain rotation in the liquid between the front shroud and the volute casing and prevent the leakage flow with minimal power consumption.
  • FIG. 5 is a schematic representation of the behavior of the front pump-out vanes of the invention (curve C) compared to the working vanes (curve D) and the pump-out vanes of conventional slurry pumps (curve E) in total head vs. flow rate coordinates.
  • FIG. 5 illustrates clearly that the pump-out vanes of the present invention lose their ability to create head when the flow rate increases.
  • the mass flow or flow rate is kept small so that the mixing of liquids having different energies (meaning different speed and different direction of speed) is minimized. Additionally, the aim is that when the mass flows of the working vanes and the pump-out vanes meet they would have as closely matching dynamic and static energies as possible so that there is no need to convert static energy to dynamic or vice versa in the energy interface area. If there is a difference the equalizing of the energies means loss.
  • the circumferential velocity component of the mass flow is kept in about a half of that of the impeller, as has already been discussed earlier in this specification. And when it is a question of an impeller provided with a wear ring, the liquid has to be accelerated to a circumferential velocity higher than a half of the impeller circumferential velocity.
  • FIG. 6 An exemplary impeller 40 of the present invention is shown in FIG. 6 .
  • the impeller has a rear shroud 42 , a front shroud 44 and working vanes 46 therebetween.
  • the rear shroud 42 has pump-out vanes 48
  • the front shroud 44 has pump-out vanes 50 , too.
  • the front pump-out vanes 50 have a height h of at most 2%, preferably between 0.5-1.5% of the diameter D of the front shroud of the impeller.
  • the front pump-out vanes may be of equal length, but they may also be of variable length. An option is to have a certain number of full-length vanes and an equal number of shorter vanes, or shorter vanes twice the number of full-length vanes.
  • the number of front pump-out vanes 50 may be higher, the same or lower than that of the working vanes 46 .
  • the number of pump-out vanes 50 is twice that of the working vanes 46 .
  • the front pump-out vanes 50 of the present invention are designed in accordance with the following guidelines:
  • the number of pump-out vanes 50 may be defined by using the equation
  • the front pump-out vanes 50 When testing the front pump-out vanes 50 it has been learned that such a vane may not extend radially outside the outer circumference of the front shroud 44 , as, if it does, the vanes 50 start acting like those of a side channel pump, which is known to have a very low efficiency.
  • the front pump-out vanes 50 should, preferably but not necessarily, irrespective of their length, extend radially to the outer circumference of the front shroud 44 , i.e. to the same outer diameter as the working vanes.
  • FIG. 7 shows the efficiency curve F of the impellers in accordance with the present invention.
  • the impellers of the pumps having a low specific speed in the series of pumps have been manufactured in the manner described above, and the result is that the entire series of pumps has an efficiency higher than what the EU ecodesign requires.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US14/680,212 2014-04-23 2015-04-07 Impeller for a centrifugal pump, a centrifugal pump and a use thereof Abandoned US20150308446A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14165689 2014-04-23
EP14165689.2 2014-04-23

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US (1) US20150308446A1 (fr)
EP (1) EP2940307B1 (fr)
CN (1) CN105003458B (fr)
BR (1) BR102015007960A2 (fr)
RU (1) RU2688066C2 (fr)

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EP3686436A1 (fr) * 2019-07-31 2020-07-29 Sulzer Management AG Pompe à plusieurs étages et agencement de pompage sous-marin
US10851801B2 (en) 2018-03-02 2020-12-01 Ingersoll-Rand Industrial U.S., Inc. Centrifugal compressor system and diffuser
US11300134B2 (en) 2019-03-22 2022-04-12 Shinano Kenshi Kabushiki Kaisha Blower
US20230059460A1 (en) * 2020-01-31 2023-02-23 Lg Electronics Inc. Pump
US11680578B1 (en) 2022-04-21 2023-06-20 Mxq, Llc Impeller for disc pump
US11713768B1 (en) * 2022-06-22 2023-08-01 Robert Bosch Gmbh Impeller for a centrifugal pump
CN117989136A (zh) * 2024-04-07 2024-05-07 成都理工大学 一种圆盘齿型复合离心泵

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CN106438458A (zh) * 2016-12-27 2017-02-22 安特洛(福安市)电机有限公司 一种离心泵闭式半开式混合叶轮结构
CN108227027B (zh) 2017-12-29 2020-12-01 同方威视技术股份有限公司 车载背散射检查系统
CN108980099A (zh) * 2018-07-03 2018-12-11 浙江融乐环境科技有限公司 一种半封闭式水泵叶轮
DE102018216048A1 (de) * 2018-09-20 2020-03-26 KSB SE & Co. KGaA Pumpenanordnung
DE202020105664U1 (de) 2020-10-02 2021-09-20 Renner Gmbh Tauchkreiselpumpe und Laufrad für eine solche
CN114607613A (zh) * 2022-02-11 2022-06-10 江苏大学 一种减少磨损的多级半开式离心泵

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US10851801B2 (en) 2018-03-02 2020-12-01 Ingersoll-Rand Industrial U.S., Inc. Centrifugal compressor system and diffuser
US11300134B2 (en) 2019-03-22 2022-04-12 Shinano Kenshi Kabushiki Kaisha Blower
EP3686436A1 (fr) * 2019-07-31 2020-07-29 Sulzer Management AG Pompe à plusieurs étages et agencement de pompage sous-marin
US11988213B2 (en) 2019-07-31 2024-05-21 Sulzer Management Ag Multistage pump and subsea pumping arrangement
US20230059460A1 (en) * 2020-01-31 2023-02-23 Lg Electronics Inc. Pump
US11913458B2 (en) * 2020-01-31 2024-02-27 Lg Electronics Inc. Pump
US11680578B1 (en) 2022-04-21 2023-06-20 Mxq, Llc Impeller for disc pump
US11713768B1 (en) * 2022-06-22 2023-08-01 Robert Bosch Gmbh Impeller for a centrifugal pump
CN117989136A (zh) * 2024-04-07 2024-05-07 成都理工大学 一种圆盘齿型复合离心泵

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RU2015112285A (ru) 2016-10-20
CN105003458B (zh) 2018-07-13
EP2940307B1 (fr) 2017-02-08
RU2015112285A3 (fr) 2018-10-29
RU2688066C2 (ru) 2019-05-17
EP2940307A1 (fr) 2015-11-04
CN105003458A (zh) 2015-10-28
BR102015007960A2 (pt) 2016-04-26

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