EP2420678B2 - Kreiselpumpe - Google Patents

Kreiselpumpe Download PDF

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Publication number
EP2420678B2
EP2420678B2 EP10008738.6A EP10008738A EP2420678B2 EP 2420678 B2 EP2420678 B2 EP 2420678B2 EP 10008738 A EP10008738 A EP 10008738A EP 2420678 B2 EP2420678 B2 EP 2420678B2
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EP
European Patent Office
Prior art keywords
impeller
curve
flow
pump
blades
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10008738.6A
Other languages
English (en)
French (fr)
Other versions
EP2420678B1 (de
EP2420678A1 (de
Inventor
Svend Rasmussen
Troels Jepsen
Pia Stenholt Laursen
Finn Jensen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Management AS
Original Assignee
Grundfos Management AS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Grundfos Management AS filed Critical Grundfos Management AS
Priority to EP10008738.6A priority Critical patent/EP2420678B2/de
Priority to US13/818,166 priority patent/US20130216407A1/en
Priority to PCT/EP2011/061741 priority patent/WO2012025289A1/en
Priority to CN201180040484.7A priority patent/CN103069171B/zh
Priority to RU2013112610/06A priority patent/RU2556153C2/ru
Publication of EP2420678A1 publication Critical patent/EP2420678A1/de
Publication of EP2420678B1 publication Critical patent/EP2420678B1/de
Application granted granted Critical
Publication of EP2420678B2 publication Critical patent/EP2420678B2/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0033—By-passing by increasing clearance between impeller and its casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • 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
    • F04D29/242—Geometry, shape
    • F04D29/245—Geometry, shape for special effects

Definitions

  • the present invention generally relates to a single speed circulator pump.
  • the invention more particularly relates to a circulator pump having a low energy consumption rate in the typical mode of operation.
  • CN 200952491Y and CN 1210705A disclose examples of centrifugal pumps having forward swept blades.
  • GB 2005768A discloses a centrifugal pump having a Q-H curve with decreasing characteristic.
  • the centrifugal pump according to the invention comprises at least one impeller, a pump housing and an electrical motor.
  • the pump has a Q-H pump curve with a head Ho at zero flow and a head H ref corresponding to the highest hydraulic power and H ref is greater than Ho. Therefore, the pump has low energy consumption rate, especially at low flow corresponding to the conditions in which the pump is operated most of the time.
  • the pump according to the invention is less energy consuming than the prior art centrifugal pumps.
  • the at least one impeller comprises impeller blades that are shaped in a manner so that that H ref is greater than Ho. If the impeller blades are forward swept, by way of example, H ref would be greater than Ho in the Q-H pump curve (where the head at zero flow is denoted Ho and where the head corresponding to the highest hydraulic power is denoted H ref ).
  • the forward swept blades are swept or curved from the radial inner side to the radial outer side in rotational direction.
  • the pump the first part of the Q-H curve is an increasing function of the flow.
  • H ref is greater than Ho and more specific a pump having a low energy consumption rate at low flow.
  • the last part of the Q-H curve is a decreasing function of the flow.
  • a pump has a decreasing power consumption rate that so that overload of the motor can be avoided.
  • the last part of the Q-H curve is a decreasing. This may by way of example be achieved by choosing a pump housing geometry that restricts the flow rate at high head.
  • the pump housing may be designed in such way that the cross sectional area of the volute is reduced or can be reduced as a function of the head. This will cause a restricted flow at high head.
  • the special design of the impeller to achieve a restricted flow at high head.
  • the impeller may be configured so that the distance between the front plate and the back plate can be altered as a function of the head.
  • the pump housing and/or the impeller is configured to introduce flow restriction causing that the end part of the Q-H curve as function of the flow is decreasing.
  • flow restriction means that restrict the flow.
  • Flow restriction means may by way of example be an impeller or a pump housing having a specific geometry.
  • the impeller has forward swept blades.
  • Forward swept impeller blades may contribute to an increasing Q-H curve.
  • the size of the impeller may be minimised because an impeller with forward swept impeller blades is capable of creating a higher flow than an impeller with backward swept impeller blades given the same conditions.
  • the impeller may be constructed in a various ways even though the impeller has forward swept impeller blades.
  • the pump has a synchronous motor. This may be an advantage due to the relative high efficiency of synchronous motors especially at low flow.
  • the synchronous motor operates synchronously with line frequency.
  • the rotational speed is determined by the number of pairs of poles and the line frequency.
  • a synchronous motor is highly efficient and thus by using a synchronous motor it is possible to achieve a pump with a low energy consumption rate.
  • the motor is working with constant speed during operation. This can be achieved by using a synchronous motor.
  • the pump is a circulator pump.
  • the circulator pump may be a glandless (wet-runner) pump. This pump may be used heating, domestic hot water and air-conditioning applications by way of example.
  • the motor is a line start permanent magnet motor.
  • a line star permanent magnet motor is basically a combination of an asynchronous motor and a synchronous motor with fixed magnetisation. In a line start permanent magnet motor there is no field winding, instead permanent magnets are used in order to provide the necessary excitation flux.
  • a synchronous motor without a rotor winding has no net torque at the speeds different from the synchronous.
  • some kind of starting in the rotor has to be used.
  • currents are induced in the rotor winding. These currents interact with the stator flux field to produce an asynchronous torque that accelerates the rotor.
  • the rotor speed is sufficiently close to synchronous speed, and on condition that load torque and inertia are not too high, the rotor will be pulled into synchronism.
  • the asynchronous torque vanishes and the motor acts as a synchronous motor except that the rotor magnetisation is supplied by permanent magnets and not by a DC-current in a field winding.
  • the impeller blades are arced and distributed symmetrically along the periphery of the impeller plate.
  • the impeller comprises a first set of impeller blades and a second set of blades, wherein the first set of impeller blades the impeller blades are longer than the second set of impeller blades and where the first set of impeller blades and the second set of impeller blades are distributed alternately along the periphery of the impeller plate.
  • a Q-H curve having the desired properties can be achieved.
  • the pumping performance of a centrifugal pump is frequently expressed in the form of a Q-H curve, depicting the head H (normally measured in m) as function of the flow Q (for instance measured in m 3 /h) of the pump.
  • the slope of the Q-H curve is determined by the pump construction and particularly by the design of the impeller.
  • H is the head
  • g gravity
  • ⁇ is the density of the fluid
  • Q is the flow.
  • ⁇ t ⁇ control ⁇ ⁇ motor ⁇ ⁇ h
  • ⁇ control is the efficiency of the control
  • ⁇ motor is the efficiency of the motor
  • the flow where the pump has the highest efficiency is referred to as the best point.
  • Speed regulated pumps are used to adjust the generated pressure according to the actual demand. Speed regulation requires a regulation of the motor. In many pumps a frequency converter is used to regulate the speed of the motor, however; such solution is expensive and technical demanding. On the other hand, many unregulated motors have a low efficiency. A high efficiency, especially at low loads, can be achieved by using a line start permanent magnet motor.
  • a line start permanent magnet motor has typically a significant position dependent difference in the inductance (difference in the D- and Q-axis inductance). This difference gives a reluctance torque, so that the total torque production from the motor is given by the combination of the alignment torque and the reluctance torque.
  • the reluctance torque can be used to increase the efficiency of the motor at lower load (at a slightly reduced efficiency at maximum load). Hereby the energy consumption can be lowered.
  • Combining a line start motor and a pump having a Q-H pump curve where H ref is greater than Ho may eliminate the use of a frequency converter.
  • a pump with a high efficiency may be achieved by combining a line start motor and a pump having a Q-H pump curve where H ref is greater than Ho. Therefore, the present invention may make it possible to make a high efficiency that is cheaper than the prior art high efficiency pump.
  • unregulated pumps are equipped with manual speed change-over means e.g. a rotary knob that may be set in three different speeds.
  • manual speed change-over means e.g. a rotary knob that may be set in three different speeds.
  • Most pump manufacturers have focused on producing pumps having different regulation curves.
  • Line start motors are generally used for applications in which an exact and constant speed is required.
  • One example of such application is a conveyor belt.
  • a pump is provided with a line start motor there is no speed regulation option. Therefore, pump manufactures use other types of motors for their pumps.
  • the present invention however, the pump is equipped with a line start motor. Hereby it is achieved that the efficiency is increased compared with traditional asynchronous motors especially at the lower loads. Therefore, the line start motor makes it possible to save energy.
  • a Q-H curve 4 according to a preferred embodiment of the present invention is illustrated in Fig. 1 .
  • the Q-H curve 4 illustrates the hydraulic head (H) 2 (hereinafter referred to as "head") as function of the flow (Q) 6.
  • head hydraulic head
  • Q flow
  • H ref 30 is greater than Ho 28 (where H ref is the head corresponding to the highest hydraulic power and Ho is the head at zero flow).
  • Ho 28 where H ref is the head corresponding to the highest hydraulic power and Ho is the head at zero flow.
  • the global maximum 24 of the Q-H curve 4 is indicated and it can be seen that (QH) ref is offset slightly to the right side of the global maximum 24 of the Q-H curve 4.
  • Fig. 2 shows a prior art Q-H curve 4 (the head 2 as function of the flow 6). It can be seen that the head (H) 2 is a decreasing function of the flow (Q) 6.
  • This Q-H curve 4 corresponds to the Q-H curve of a typical centrifugal type circulator pump. It can be seen that Ho 28 is greater than H ref 30 (where H ref is the head corresponding to the highest hydraulic power and H 0 is the head at zero flow).
  • Fig. 3a illustrates the Q-H curve 4 shown in Fig. 2
  • Fig. 3b illustrates the corresponding power-flow curve 12 (the power (P) 14 as function of the flow (Q) 6) for a prior art pump having the Q-H curve 4 illustrated in Fig. 3a .
  • the maximal flow Q 100% 22 the flow Q 25% 16 corresponding to 25% of the maximal flow Q 100% 22
  • Fig. 4a illustrates the Q-H curve 4 shown in Fig. 1
  • Fig. 4b illustrates the power-flow curve 12 (the power (P) 14 as function of the flow (Q) 6) for a pump having the Q-H curve 4 illustrated in Fig. 4a
  • the flow Q 25% 16 corresponding to 25% of the maximal flow Q 100% 22 the flow Q 50% 18 corresponding to 50% of the maximal flow Q 100% 22 and the flow Q 75% 20 corresponding to 75% of the maximal flow Q 100% 22 are associated with lower power values 16, 18, 20 than in the prior art pump curve 4 illustrated in Fig. 3b .
  • Fig. 5 shows a comparison of the power-flow curves illustrated in Fig. 3b and Fig. 4b . It can bee seen from Fig. 5 that the maximal flow Q 100% 22', 22" of both the prior art power-flow curve 38 and for the power-flow curve 40 corresponding to a pump having the Q-H curve 4 according to the invention (illustrated in Fig. 4a ) are almost coinciding. If we look at the power-flow curve 40 corresponding to the invention is can be seen that the power value at the flow Q 25% 16" corresponding to 25% of the maximal flow Q 100% is significantly lower than the prior art power value at the flow Q 25% 16'.
  • the power value at the flow Q 50% 18" corresponding to 50% of the maximal flow Q 100% is significantly lower than the prior art power value at the flow Q 50% 18'.
  • the power value at the flow Q 75% 20" corresponding to 75% of the maximal flow Q 100% is significantly lower than the prior art power value at the flow Q 75% 20'. Accordingly, the pump according to the present invention will have a low energy consumption rate.
  • Fig. 6a illustrates the Q-H curve 4 according to an embodiment of the invention.
  • the head (H) 2 is plotted against the flow (Q) 6.
  • the last third 10 of the Q-H curve 4 has a negative slope and therefore, the last part 10 of the Q-H curve 4 is decreasing.
  • H ref 30 is greater than Ho 28 (where H ref is the head corresponding to the highest hydraulic power and H 0 is the head at zero flow).
  • the global maximum 24 of the Q-H curve 4 is and (QH) ref 26 are almost coinciding.
  • Fig. 6b illustrates a Q-H curve 4 according to another embodiment of the invention.
  • This Q-H curve 4 is almost similar to the Q-H curve 4 shown in Fig. 6a , however; the global maximum 24 of the Q-H curve 4 is and (QH) ref 26 are displaced relative to one another. (QH) ref 26 is located to the right for the global maximum 24 of the Q-H curve 4.
  • Fig. 7a illustrates a schematically view of theoretical Q-H curves 42, 44, 46 for different impeller blade angels.
  • the blade angle ⁇ is indicated in Fig. 7b and represents the angle between the outer periphery of the impeller and the outer side of the impeller blade.
  • Fig. 7a shows that backward swept impellers have a decreasing theoretical Q-H curve 46.
  • Fig. 7a also shows that forward swept impellers have an increasing theoretical Q-H curve 46.
  • the theoretical Q-H curve 44 of a neutral impeller construction where the blade angle ⁇ between the outer periphery of the impeller and the outer side of the impeller blade is 90 degrees is flat (horizontal).
  • forward swept blades By the term forward swept blades is meant that the angle ⁇ is greater than 90°, where ⁇ is defined as the angle between the outer periphery of the impeller 32 and the outer side of the impeller blade 34.
  • backwards swept blades By the term backwards swept blades is meant that the angle ⁇ is less than 90°.
  • neutral swept blades 34 By the term neutral swept blades 34 is meant that the angle ⁇ is equal to 90°.
  • Fig. 7b illustrates a schematically view of three different impeller 32 types where the blade angle ⁇ is under 90 degrees, equal to 90 degrees and more than 90 degrees respectively.
  • the blades 34 as well as the rotational direction of the impeller 36 are indicated in the figure.
  • Fig. 8 shows an impeller 32 according to one embodiment of the invention.
  • the impeller 32 comprises first set of impeller blades 34 and a second set of blades 35, where the first set of impeller blades 34 are longer than the second set of impeller blades 35 and where the first set of impeller blades 34 and the second set of impeller blades 35 are distributed alternately along the periphery of the impeller plate 48.
  • the first set of impeller blades 34 comprises ten blades and the second set of impeller blades 35 comprise also ten blades.
  • both the first set of impeller blades 34 and the second set of blades are forward swept because the angle between the outer periphery of the impeller 32 and the outer side of the impeller blades 34, 35 is greater than 90°.
  • the absolute velocity C of the fluid is given by the sum of the tangential velocity U of the impeller and the relative velocity W relative to the impeller.
  • the magnitude of the tangential velocity U of the impeller is given by the product of the radius r and the rotational speed ⁇ :
  • r ⁇ ⁇
  • the blade angle ⁇ is less than 90 degrees.

Claims (9)

  1. Zentrifugalumwälzpumpe mit mindestens einem Laufrad (32), einem Pumpengehäuse und einem Elektromotor, dadurch gekennzeichnet, dass der Elektromotor ein Line-Start-Dauermagnetmotor ohne Drehzahlregelungsoption ist, wobei das Laufrad nach vorn gepfeilte Flügel hat, und dass die Pumpe eine Q-H-Pumpenkurve (4) mit einer Höhe H0 (28) bei null Strom und einer Höhe Href (30) aufweist, die der höchsten Hydraulikkraft entspricht, wobei Href (30) größer als H0 (28) ist und der letzte Teil (10) der Q-H-Kurve (4) eine abnehmende Funktion des Stroms (6) ist.
  2. Zentrifugalpumpe nach Anspruch 1, dadurch gekennzeichnet, dass das mindestens eine Laufrad (32) Laufradflügel (34) umfasst, die derart geformt sind, dass Href (30) größer ist als H0 (28) ist.
  3. Zentrifugalpumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass der erste Teil (8) der Q-H-Kurve (4) eine zunehmende Funktion des Stroms (6) ist.
  4. Zentrifugalpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Pumpengehäuse und/oder das Laufrad (32) zum Einleiten von Strombegrenzung konfiguriert ist, die bewirkt, dass der Endteil (10) der Q-H-Kurve (4) als Funktion des Stroms (6) abnimmt.
  5. Zentrifugalpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Motor ein Synchronmotor ist.
  6. Zentrifugalpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Zentrifugalpumpe eine Nassläuferpumpe ist.
  7. Zentrifugalpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Laufradflügel (34) gewölbt und symmetrisch entlang des Umfangs der Laufradplatte (48) verteilt sind.
  8. Zentrifugalpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Laufrad (32) einen ersten Satz Laufradflügel (34) und einen zweiten Satz Flügel (35) umfasst, wobei der erste Satz Laufradflügel (34) länger als der zweite Satz Laufradflügel (35) ist, und wobei der erste Satz Laufradflügel (34) und der zweite Satz Laufradflügel (35) abwechselnd entlang des Umfangs der Laufradplatte (48) verteilt sind.
  9. Zentrifugalpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass (2/3)Href ≥ H0, bevorzugt (3/5)Href ≥ H0 ist.
EP10008738.6A 2010-08-21 2010-08-21 Kreiselpumpe Not-in-force EP2420678B2 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP10008738.6A EP2420678B2 (de) 2010-08-21 2010-08-21 Kreiselpumpe
RU2013112610/06A RU2556153C2 (ru) 2010-08-21 2011-07-11 Циркуляционный насос центробежного типа
PCT/EP2011/061741 WO2012025289A1 (en) 2010-08-21 2011-07-11 Centrifugal pump
CN201180040484.7A CN103069171B (zh) 2010-08-21 2011-07-11 离心式循环泵
US13/818,166 US20130216407A1 (en) 2010-08-21 2011-07-11 Centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10008738.6A EP2420678B2 (de) 2010-08-21 2010-08-21 Kreiselpumpe

Publications (3)

Publication Number Publication Date
EP2420678A1 EP2420678A1 (de) 2012-02-22
EP2420678B1 EP2420678B1 (de) 2015-02-25
EP2420678B2 true EP2420678B2 (de) 2018-08-15

Family

ID=43385615

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10008738.6A Not-in-force EP2420678B2 (de) 2010-08-21 2010-08-21 Kreiselpumpe

Country Status (5)

Country Link
US (1) US20130216407A1 (de)
EP (1) EP2420678B2 (de)
CN (1) CN103069171B (de)
RU (1) RU2556153C2 (de)
WO (1) WO2012025289A1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130204546A1 (en) * 2012-02-02 2013-08-08 Ghd Pty Ltd. On-line pump efficiency determining system and related method for determining pump efficiency
PT2778432E (pt) * 2013-03-15 2016-01-29 Ebm Papst Mulfingen Gmbh & Co Dispositivo de ventilação com retificador de fluxo
EP2910788B1 (de) * 2014-02-25 2018-04-04 TACO ITALIA S.r.l. Verfahren zur Steuerung einer Pumpstation in einem Fluidzirkulationssystem, zugehöriges Zirkulationssystem und Pumpstation zur Durchführung dieses Verfahrens
EP3382888B1 (de) * 2017-03-31 2020-06-17 Grundfos Holding A/S Pumpenanordnung und steuerungsverfahren

Citations (1)

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Publication number Priority date Publication date Assignee Title
US5551837A (en) † 1992-01-17 1996-09-03 Ksb Aktiengesellschaft Apparatus for regulating the transport flow of a liquid that is circulated by a centrifugal pump in a closed pipe system

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US4070A (en) * 1845-06-07 Ihstettment for
GB2005768B (en) * 1977-10-08 1982-04-07 Plessey Co Ltd Centrifugal pump
SU1064047A2 (ru) * 1982-02-18 1983-12-30 Предприятие П/Я М-5841 Центробежный насос
US5127800A (en) * 1984-03-20 1992-07-07 Baker Hughes Incorporated Flow-stabilizing volute pump and liner
SU1581865A1 (ru) * 1988-06-08 1990-07-30 Всесоюзный Научно-Исследовательский Институт Горной Механики Им.М.М.Федорова Рабочее колесо центробежного насоса
JPH08275600A (ja) 1992-01-09 1996-10-18 Tomiko Kikukawa ＡＣ、ＡＣコミュニケーション情報システム ＡＣとは、Ａｌｉｖｅ Ｃｏｍｐｕｔｅｒを意味し、生きている、成長する、進化するコンピュータの力である。この力によって、ソフトメディアの世界における完全自動の、心と生命をもって、生きている、考える、運動するコンピュータシステムが実現できる。この力によるシステムを、ＡＣコミュニケーション情報システムという。
EP0551550B1 (de) * 1992-01-17 1995-12-27 Siemens Aktiengesellschaft Nassläuferpumpe
TW385242B (en) * 1997-07-18 2000-03-21 Matsushita Electric Ind Co Ltd Dinner set washing dryer
US20070132330A1 (en) * 2005-12-12 2007-06-14 Fei Renyan W Fan assemblies employing LSPM motors and LSPM motors having improved synchronization
CN200952491Y (zh) * 2006-07-15 2007-09-26 河南省西峡汽车水泵股份有限公司 叶片交错的汽车水泵叶轮
DE102009042214A1 (de) 2008-10-22 2010-04-29 Ksb Aktiengesellschaft Rotor eines selbstanlaufenden Elektromotors

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Publication number Priority date Publication date Assignee Title
US5551837A (en) † 1992-01-17 1996-09-03 Ksb Aktiengesellschaft Apparatus for regulating the transport flow of a liquid that is circulated by a centrifugal pump in a closed pipe system

Non-Patent Citations (3)

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C. Pfleiderer: "Die Kreiselpumpen", edited by Julius Springer Verlag 1932, pages 175-191. †
Taco Inc., "Water Circulation pumps & Circulators, KV Vertical Inline Pumps", Printed in USA. †
Technisches Handbuch, "Pumpen", VEB Kombinat Pumpen und Verdichter, Halle, 4. Auflage, Redaktionsschluss 30.06.1972. †

Also Published As

Publication number Publication date
RU2556153C2 (ru) 2015-07-10
EP2420678B1 (de) 2015-02-25
RU2013112610A (ru) 2014-09-27
WO2012025289A1 (en) 2012-03-01
EP2420678A1 (de) 2012-02-22
CN103069171A (zh) 2013-04-24
CN103069171B (zh) 2016-08-03
US20130216407A1 (en) 2013-08-22

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