WO2012025289A1 - Centrifugal pump - Google Patents
Centrifugal pump Download PDFInfo
- Publication number
- WO2012025289A1 WO2012025289A1 PCT/EP2011/061741 EP2011061741W WO2012025289A1 WO 2012025289 A1 WO2012025289 A1 WO 2012025289A1 EP 2011061741 W EP2011061741 W EP 2011061741W WO 2012025289 A1 WO2012025289 A1 WO 2012025289A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- curve
- pump
- flow
- blades
- Prior art date
Links
- 230000003247 decreasing effect Effects 0.000 claims description 13
- 230000001360 synchronised effect Effects 0.000 claims description 13
- 238000005265 energy consumption Methods 0.000 abstract description 9
- 238000001595 flow curve Methods 0.000 description 12
- 238000004804 winding Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000004907 flux Effects 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- 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
- 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
- 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. It is known to reduce the energy consumption rate of a pump by regulating the speed of the pump. This may by way of example be done by using a frequency converter in a pump. This solution is however relative technical demanding and expensive. Therefore, it is desirable to have a cheaper alternative to this solution.
- 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 Href corresponding to the highest hydraulic power and Href 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 Href is greater than Ho. If the impeller blades are forward swept, by way of example, Href 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 Href) .
- 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.
- Href is greater than Ho
- I ⁇ is also possible ⁇ o have pump where the entire Q-H curve is an increasing function of the 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 re- stricts 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 im- peller 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 start wind- ing in the rotor has to be used. During the start, currents are induced in the rotor winding. These currents interact with the stator flux field ⁇ o produce an asynchronous torque that accelerates fhe rotor.
- the impeller blades are arced and distributed symmetrically along fhe periphery of fhe impeller plafe.
- Href fhe head corresponding ⁇ o fhe highest hydraulic power andHo is the head af zero flow.
- the impeller comprises a first set of impeller blades and a second sef of blades, wherein fhe first set of impeller blades fhe impeller blades are longer than the second sef of impeller blades and where fhe first set of impeller blades and fhe second sef of impeller blades are distributed alternately along the periphery of fhe impeller plafe.
- a Q-H curve having fhe desired properties can be achieved.
- (2/3) Href > Ho A pump having a Q-H curve with these properties will be significantly less energy consuming than the prior art centrifugal pumps.
- a pump with such Q-H curve would also be significantly less energy consuming than fhe prior art centrifugal pumps.
- FIG. 3a shows the power-flow curve for a pump having fhe Q-H curve illustrated in Fig. 3a;
- FIG. 4a shows the power-flow curve for a pump having fhe Q-H curve illustrated in Fig. 4a;
- FIG. 8 - illustrates an impeller according to one embodiment of the invention.
- 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
- p is the density of the fluid
- Q is the flow.
- 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 ac- cording to the actual demand.
- Speed regulation requires a regulation of the motor.
- a frequency converter is used to regulate the speed of the motor, however; such solution is expensive and technical demanding.
- 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 Href 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 Href 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 gener- ally 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
- Href 30 is greater than Ho 28 (where Href is the head corresponding to the highest hydraulic power and Ho is the head at zero flow).
- Ho 28 where Href 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 Href 30 (where Href is the head corresponding to the highest hydraulic power andHo 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 Qi oo% 22, the flow Q25% 1 6 corresponding to 25% of the maximal flow Qi oo% 22, the flow Qso% 18 corresponding to 50% of the maximal flow Qi oo% 22 and the flow Q75% 20 corresponding to 75% of the maximal flow Qi oo% 22 are lying relative high (the indicated power values 16, 18, 20 and 22) on the power-flow curve 12.
- 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 Q25% 16 corresponding to 25% of the maximal flow Qi oo% 22
- the flow Qso% 18 corresponding to 50% of the maximal flow Qi oo% 22
- the flow Qzs% 20 corresponding to 75% of the maximal flow Qi oo% 22 are associated with lower power values 1 6, 18, 20 than in the prior art pump curve 4 illustrated in Fig. 3 b.
- Fig. 5 shows a comparison of the power-flow curves illustrated in Fig. 3a and Fig. 4a. It can bee seen from Fig. 5 that the maximal flow Qi oo% 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 Q25% 16" corresponding to 25% of the maximal flow Qi oo% is significantly lower than the prior art power value at the flow Q25% 16'.
- the power value at the flow Qso% 18' ' corresponding to 50% of the maximal flow Qi oo% is sig- nificantly lower than the prior art power value at the flow Qso% 1 8' .
- the power value at the flow Q7s% 20" corresponding to 75% of the maximal flow Qioo% is significantly lower than the prior art power value at the flow Qzs% 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 1 0 of the Q-H curve 4 has a negative slope and therefore, the last part 1 0 of the Q-H curve 4 is decreasing.
- Href 30 is greater than Ho 28 (where Href is the head corresponding to the highest hydraulic power andHo 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) re f 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 im peller 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 im peller 32 and the outer side of the im peller 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 im peller 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 im peller 32 comprises first set of im peller blades 34 and a second set of blades 35, where the first set of impeller blades 34 are longer than the second set of im peller blades 35 and where the first set of im- peller blades 34 and the second set of im peller blades 35 are distributed alternately along the periphery of the impeller plate 48.
- the where the first set of im peller blades 34 comprises ten blades and where the second set of im peller blades 35 comprise also ten blades.
- Fig. 9 illustrates a typical impeller 32 having a num ber of back wards swept im peller blades 34, i.e. the im peller blades are swept or curved against the rotational direction 36. It is indicated that the rotational di- rection 36 is counter clockwise - the rotational speed is denoted ⁇ and the radius r of the im peller 32 is also indicated.
- the absolute velocity C of the fluid is given by the sum of the tangential velocity U of the impeller 32 and the relative velocity W relative to the im peller 32. Theses ve- locities C, U and W are indicated with arrows.
- the magnitude of the tangential velocity U of the im peller 32 is given by the product of the radius r and the rotational speed ⁇ :
- the blade angle ⁇ is less than 90 degrees.
- Fig. 1 0 illustrates an im peller 32 with a forward swept im peller blade 34, i.e. the blades are swept in rotational direction 36. It is indicated that the rotational direction 36 is counter clockwise like in Fig. 9. The projection Cu of C in the tangential plane is indicated and it can be seen that this forward swept im peller has the following characteristic:
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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)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201180040484.7A CN103069171B (en) | 2010-08-21 | 2011-07-11 | centrifugal circulating pump |
US13/818,166 US20130216407A1 (en) | 2010-08-21 | 2011-07-11 | Centrifugal pump |
RU2013112610/06A RU2556153C2 (en) | 2010-08-21 | 2011-07-11 | Rotary circulation pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10008738.6 | 2010-08-21 | ||
EP10008738.6A EP2420678B2 (en) | 2010-08-21 | 2010-08-21 | Centrifugal pump |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012025289A1 true WO2012025289A1 (en) | 2012-03-01 |
Family
ID=43385615
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2011/061741 WO2012025289A1 (en) | 2010-08-21 | 2011-07-11 | Centrifugal pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US20130216407A1 (en) |
EP (1) | EP2420678B2 (en) |
CN (1) | CN103069171B (en) |
RU (1) | RU2556153C2 (en) |
WO (1) | WO2012025289A1 (en) |
Families Citing this family (4)
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 |
EP2778432B1 (en) * | 2013-03-15 | 2015-10-14 | ebm-papst Mulfingen GmbH & Co. KG | Ventilator assembly with flow rectifier |
EP2910788B1 (en) * | 2014-02-25 | 2018-04-04 | TACO ITALIA S.r.l. | Method for controlling a pumping station within a fluid circulation system, related circulation system and pumping station for realizing said method |
EP3382888B1 (en) * | 2017-03-31 | 2020-06-17 | Grundfos Holding A/S | Pump assembly and controlling method |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2005768A (en) * | 1977-10-08 | 1979-04-25 | Plessey Co Ltd | A centrifugal pump |
SU1581865A1 (en) * | 1988-06-08 | 1990-07-30 | Всесоюзный Научно-Исследовательский Институт Горной Механики Им.М.М.Федорова | Centrifugal pump impeller |
EP0551550A1 (en) * | 1992-01-17 | 1993-07-21 | Siemens Aktiengesellschaft | Pump with a wet rotor |
CN1210705A (en) * | 1997-07-18 | 1999-03-17 | 松下电器产业株式会社 | Cleaning and drying machine for tableware |
US20070132330A1 (en) * | 2005-12-12 | 2007-06-14 | Fei Renyan W | Fan assemblies employing LSPM motors and LSPM motors having improved synchronization |
CN200952491Y (en) * | 2006-07-15 | 2007-09-26 | 河南省西峡汽车水泵股份有限公司 | Vehicle water pump vane with staggered vanes |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4070A (en) * | 1845-06-07 | Ihstettment for | ||
SU1064047A2 (en) * | 1982-02-18 | 1983-12-30 | Предприятие П/Я М-5841 | Centrifugal pump |
US5127800A (en) * | 1984-03-20 | 1992-07-07 | Baker Hughes Incorporated | Flow-stabilizing volute pump and liner |
JPH08275600A (en) | 1992-01-09 | 1996-10-18 | Tomiko Kikukawa | Ac communication information system (ac is an abbreviation for alive computer and refers to the force of a computer which is alive,glows and evolves.this force contributes to the implementation of a computer system which is fully automatic,has mind and life,is alive,thinks and moves in theworld of soft media.ac communication system is the system constructed by means of the force.) |
DE4201100A1 (en) † | 1992-01-17 | 1993-07-22 | Klein Schanzlin & Becker Ag | DEVICE FOR CONTROLLING THE FLOW RATE OF A CENTRIFUGAL PUMP IN A CLOSED PIPE NETWORK |
DE102009042214A1 (en) | 2008-10-22 | 2010-04-29 | Ksb Aktiengesellschaft | Rotor of a self-starting electric motor |
-
2010
- 2010-08-21 EP EP10008738.6A patent/EP2420678B2/en not_active Not-in-force
-
2011
- 2011-07-11 WO PCT/EP2011/061741 patent/WO2012025289A1/en active Application Filing
- 2011-07-11 US US13/818,166 patent/US20130216407A1/en not_active Abandoned
- 2011-07-11 CN CN201180040484.7A patent/CN103069171B/en not_active Expired - Fee Related
- 2011-07-11 RU RU2013112610/06A patent/RU2556153C2/en active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2005768A (en) * | 1977-10-08 | 1979-04-25 | Plessey Co Ltd | A centrifugal pump |
SU1581865A1 (en) * | 1988-06-08 | 1990-07-30 | Всесоюзный Научно-Исследовательский Институт Горной Механики Им.М.М.Федорова | Centrifugal pump impeller |
EP0551550A1 (en) * | 1992-01-17 | 1993-07-21 | Siemens Aktiengesellschaft | Pump with a wet rotor |
CN1210705A (en) * | 1997-07-18 | 1999-03-17 | 松下电器产业株式会社 | Cleaning and drying machine for tableware |
US20070132330A1 (en) * | 2005-12-12 | 2007-06-14 | Fei Renyan W | Fan assemblies employing LSPM motors and LSPM motors having improved synchronization |
CN200952491Y (en) * | 2006-07-15 | 2007-09-26 | 河南省西峡汽车水泵股份有限公司 | Vehicle water pump vane with staggered vanes |
Non-Patent Citations (1)
Title |
---|
TROSKOLANSKI A: "Les Turbopompes Théorie, tracé et construction", 1 January 1977, LES TURBOPOMPES THÉORIE, TRACÉ ET CONSTRUCTION,, PAGE(S) 250 - 253, XP007916630 * |
Also Published As
Publication number | Publication date |
---|---|
EP2420678B2 (en) | 2018-08-15 |
US20130216407A1 (en) | 2013-08-22 |
RU2013112610A (en) | 2014-09-27 |
CN103069171A (en) | 2013-04-24 |
RU2556153C2 (en) | 2015-07-10 |
EP2420678A1 (en) | 2012-02-22 |
EP2420678B1 (en) | 2015-02-25 |
CN103069171B (en) | 2016-08-03 |
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