EP2430314B1 - Pompe centrifuge a double echappement - Google Patents

Pompe centrifuge a double echappement Download PDF

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Publication number
EP2430314B1
EP2430314B1 EP10727469.8A EP10727469A EP2430314B1 EP 2430314 B1 EP2430314 B1 EP 2430314B1 EP 10727469 A EP10727469 A EP 10727469A EP 2430314 B1 EP2430314 B1 EP 2430314B1
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EP
European Patent Office
Prior art keywords
passage
outlet
fluid
pump
impeller
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.)
Active
Application number
EP10727469.8A
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German (de)
English (en)
French (fr)
Other versions
EP2430314A1 (fr
Inventor
François Danguy
Emmanuel Edeline
Laurent Fabbri
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.)
ArianeGroup SAS
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ArianeGroup SAS
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Publication of EP2430314A1 publication Critical patent/EP2430314A1/fr
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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
    • F04D29/40—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
    • 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
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons
    • 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
    • F04D29/2211—More than one set of flow passages
    • 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

Definitions

  • the present invention relates to a centrifugal pump.
  • upstream and downstream are defined with respect to the normal flow direction of the fluid in the pump and the centrifugal wheel.
  • Certain space applications for example rocket engine turbopumps
  • industrial applications for example motor-turbopumps in an LNG gasification cycle
  • having a first flow of fluid at a certain pressure and another flow of fluid. lower than the first flow, at a higher pressure.
  • JPS59158398 presents an example of a pump according to the preamble of claim 1.
  • the figure 4 represents a known turbopump comprising two pumps arranged in series, and its operation is recalled below.
  • a turbopump 100 comprises a rotary shaft 180 adapted to pivot about an axis of rotation A, and a casing 150 surrounding the rotary shaft 180.
  • the casing 150 is fixed in rotation and the rotary shaft 180 is mounted on bearings bearing support on the casing 150.
  • On this axis of rotation A is mounted a primary pump 110, which comprises a primary centrifugal wheel 112 integral in rotation with the rotary shaft 180, and a primary exhaust volute 115.
  • the primary exhaust volute 115 is integrated in the housing 150 and is fixed.
  • the fluid enters the turbopump from the front thereof by an annular passage 102 where an inductor 104 circulates the fluid in a direction parallel to the axis A (in the rest of the description, the terms "before” and “back” are used to define the position of the pump parts relative to each other in a direction parallel to the axis A).
  • This primary centrifugal wheel 112 comprises bent primary passages 114 which radially move the fluid away from the rotary shaft 180 so that the Fluid then flows in a radial direction relative to the axis A. The fluid is thus driven into the diffuser 117 located upstream of the primary exhaust volute 115 and downstream of the primary elbow passages. 114. The fluid entering the primary volute 115 has been compressed by its passage in the primary centrifugal wheel 112.
  • a portion of the fluid flowing in the primary volute 115 is removed and injected into a secondary pump 120 which is located behind the primary pump 110 along the rotary shaft 180.
  • the secondary pump 120 comprises a secondary centrifugal wheel 122 integral in rotation with the rotary shaft 180, and a secondary exhaust volute 125.
  • the secondary exhaust volute 125 is integrated in the housing 150 and is fixed.
  • the fluid from the primary volute 115 flows through bent secondary passages 124 of the secondary pump 120 which radially moves the fluid away from the rotary shaft 180 so that the fluid then flows in a radial direction with respect to the axis A
  • the fluid is thus entrained in the diffuser 127 situated upstream of the secondary exhaust volute 125 and downstream of the bent secondary passages 124.
  • the section of these bent secondary passages 124 is smaller than the section of the bent primary passages 114.
  • the secondary pump 120 provides a lower flow rate and a higher pressure level than the fluid supplied by the primary pump 110.
  • the primary centrifugal wheel 112 comprises an axial balancing system which serves to compensate for the axial forces (along the axis A) generated by the fluid on the rotor.
  • This axial balancing system consists of a chamber 190 located behind the primary centrifugal wheel 112, between the latter and the casing 150. In this chamber 190 flows radially fluid taken from the outlet of the elbow 114 and emerging from this chamber at the portion of the primary centrifugal wheel 112 located closest to the rotary shaft 180. This circulation of fluid in the chamber 190 acts as a cushion resistant to the axial forces exerted by the fluid on the rotor.
  • the operation of this axial balancing system requires that the rotor is able to move axially relative to the housing 150.
  • the primary centrifugal wheel 112 providing a moderate pressure
  • the pressure in the chamber 190 is moderate.
  • the recovery capacity of the system depends on the dimensions of the chamber 190 which is a function of the the speed of rotation of the primary centrifugal wheel 112. This speed must not be too high, otherwise the axial forces exerted by the fluid on the rotor would be too great to be counterbalanced by the axial balancing system, and this would result in a damage to the turbopump.
  • the present invention aims to remedy these disadvantages.
  • the invention aims to provide a pump whose size, weight, and cost are reduced, and whose performance is improved.
  • a pump as defined by claim 1, which comprises a centrifugal wheel and a casing surrounding this centrifugal wheel, this centrifugal wheel having a main passage which divides into a first passage and a second passage with an inlet.
  • this common supply inlet being the inlet of the main passage, the first passage having a first radially oriented outlet, opening to a first diameter with respect to the axis of rotation, and adapted to supply fluid at a first pressure, and the second passage having a second radially oriented outlet and located behind the first outlet, opening to a second diameter greater than the first diameter, the second outlet being able to provide the fluid at a second pressure higher than the first pressure, the centrifugal wheel forming with the casing an axial balancing system co comprising a chamber formed between the rear face of the centrifugal wheel and the portion of the casing facing this rear face, the chamber inlet being at the level of the second outlet.
  • the turbopump has a smaller footprint and mass, since the primary pump and the secondary pump are replaced in a single double-exhaust pump. It is therefore no longer necessary to draw fluid at the outlet of a primary pump to supply a secondary pump.
  • the architecture of the turbopump is simplified, and manufacturing costs are reduced.
  • the diameter of the centrifugal wheel being greater, the performance of the axial balancing system associated with this double exhaust pump is improved, as explained below.
  • the first passage and the second passage are separated by a flange of which at least a portion extends between the first outlet and the second outlet.
  • the figure 1 shows a turbopump 1 which comprises a rotary shaft 80 adapted to pivot about an axis of rotation A, and a pump 10 mounted on this rotary shaft 80.
  • the pump 10 comprises a centrifugal wheel 20 integral in rotation with the rotary shaft 80 , and a housing 50 fixed in rotation, surrounding the rotary shaft 80.
  • the rotary shaft 80 is mounted on bearings bearing on the housing 50.
  • the fluid enters the turbopump 1 from the front thereof by an annular duct 2 opening into an inductor 4 followed by a rectifier 6, downstream of which is located the centrifugal wheel 20.
  • the inductor 4 and the rectifier 6 are part of the pump 10.
  • This centrifugal wheel 20 comprises a main passage 24 with a feed inlet 22 into which the fluid coming from the inductor 4 enters.
  • the feed inlet 22 is oriented along the axis A. Downstream of this inlet of 22, the main passage 24 forms a bend away from the axis of rotation A, where it divides into a first passage 241 and a second passage 242.
  • the first passage 241 opens by a first outlet 243 which is therefore oriented substantially perpendicular to the axis of rotation A.
  • the separation between the first passage 241 and the second passage 242 is performed by a flange 40.
  • the flange 40 is located behind the first passage 241 (that is to say that the first passage is closer to the front of the turbopump), and thus forms the rear wall of the first passage 241 to the first exit 243.
  • the flange 40 is in front of the second passage 242, and thus forms the front wall of the second passage 242.
  • the second passage 242 extends radially beyond the level of the first outlet 243, ending with a second outlet 244 which is more distant from the axis A than the first output 243.
  • the outer portion 48 of the flange 40 is the portion of the flange 40 which extends between the first outlet 243 and the second outlet 244.
  • the flange 40 includes an inner portion which extends the outer portion 48 upstream over most of the bent region of the passage 24.
  • the first passage 241 and the second passage 242 are bent, and cross section (perpendicularly to the flow in the passage) slightly convergent between the upstream end 45 and respectively the first outlet 243 and the second outlet 244.
  • the upstream end 45 of this inner portion of the flange 40 is located downstream of the feed inlet 22.
  • this upstream end 45 is located closer to the feed inlet 22 than to the first outlet 243. .
  • the thickness of the flange 40 is as small as possible so as to optimize the separation of the fluid in the passage 24.
  • the flange 40 may not extend towards the axis A beyond its outer portion 48.
  • the upstream end 45 of the flange 40 is at the same distance from the axis A as the first output 243.
  • the flange 40 may also extend upstream in the main passage 24 for an intermediate distance between the configuration shown in FIG. figure 2 (the flange extends almost to the entrance 22 of the main passage 24) and that represented on the figure 3 (The flange does not extend upstream beyond the first outlet 243).
  • the housing 50 comprises a double exhaust volute which includes a first exhaust volute 51.
  • the first outlet 243 is located opposite a first orifice 513 of the first volute exhaust 51, so that the fluid is driven by the centrifugal wheel 20 to the first exhaust volute 51 through the first port 513.
  • the casing 50 also comprises a second exhaust volute 52.
  • the second outlet 244 is located opposite a second orifice 524 of the second exhaust volute 52, so that the fluid is driven by the centrifugal wheel 20 towards the second exhaust volute 52 through the second port 524.
  • the second passage 242 has a smaller cross section than the first passage 241.
  • first passage 241 provides a large flow at moderate pressure
  • second passage 242 provides a lower flow (because its cross section is smaller) at a higher pressure (because the second outlet 244 is radially further from the axis A as the first output 243).
  • the section of the first exhaust volute 51 may be smaller than the section of the exhaust volute 115.
  • the second exhaust volute 52 is contiguous to the first exhaust volute 51, aft and farther from the axis of rotation A than the latter. This configuration makes it possible to minimize the volume occupied by the casing 50.
  • the outer portion 48 of the flange 40 of the centrifugal wheel 20 is oriented towards the front of the pump. Opposite this external part 48, there is an intermediate wall 58 which forms part of the casing 50 and which separates the diffuser 511 from the first exhaust volute 51 and the diffuser 522 from the second exhaust volute 52.
  • the intermediate wall 58 being a part of the housing 50, is fixed.
  • the outer portion 48 of the flange 40 When the pump operates, the outer portion 48 of the flange 40 is rotated about the axis A, and therefore moves relative to the intermediate wall 58. There is therefore an undesirable leakage of fluid to the fluid. interface between this outer portion 48 and this intermediate wall 58 due to the pressure difference between the first outlet 243 and the second outlet 244 of the centrifugal wheel.
  • this seal is a labyrinth seal.
  • the front wall 29 of the main passage 24 comprises, at the inlet 22 of this passage 24, a dynamic seal at the interface of this front wall with the housing 50.
  • This seal is intended to limit leakage, and therefore the recirculated flow rate between the first outlet 243 of the first passage 241 and the inlet 22 which it will be necessary to recompress.
  • this seal is a labyrinth seal.
  • the front wall 29 of the passage 241 and / or the flange 40 and its outer portion 48 may be omitted.
  • a single axial balancing system which serves to compensate for the axial forces (along the axis A) generated by the fluid on the rotor when the pump is running.
  • the rear wall of the second passage 242 is formed by the centrifugal wheel 20, and the rear face 27 of the centrifugal wheel 20 is opposite, over its entire surface, with a portion 57 of the housing 50.
  • the space between this rear face 27 and this portion 57 forms a chamber 90.
  • Fluid is withdrawn from the second passage 242 at the second outlet 244 and enters this chamber 90 through an annular passage 93 with variable axial play, and exits at an outlet port 96 located at the portion of the centrifugal wheel 20 located closest to the rotary shaft 80.
  • the assembly of the annular passage 93 and the chamber 90 constitutes the axial balancing system.
  • the fluid enters through the annular passage 93 in the chamber 90.
  • the chamber 90 fills, the pressure difference between the annular passage 93 and the outlet orifice 96 ensuring the flow of fluid in the chamber 90.
  • This fluid exerts forward pressure which tends to move the centrifugal wheel 20 forward.
  • the geometry of the passage Ring 93 is such that this forward movement of the centrifugal wheel tends to close it.
  • the pressure in the chamber 90 then decreases, displacing the centrifugal wheel 20 backwards.
  • the axial balancing system keeps the centrifugal wheel 20 in its axial position around a point of equilibrium.
  • the axial balancing system therefore has a function of regulating the axial position of the centrifugal wheel 20 (and therefore of the rotary shaft 80).
  • This system therefore has the advantage of being an active system, as opposed to a passive system in which the compensation force on the centrifugal wheel is independent of the axial position of the rotor / rotary shaft.
  • annular passage 93 comprises a step, according to a known embodiment.
  • the axial balancing system keeps the centrifugal wheel 20 in its axial position around a point of equilibrium.
  • the surface of the chamber 90 on which the pressure is exerted is greater.
  • the pressure difference between the annular passage 93 and the outlet port 96 is larger.
  • the pressure in the chamber 90 can therefore vary more significantly, and the axial balancing system can therefore accommodate greater axial forces. This large increase in capacity of the axial balancing system makes it possible to increase the speed of rotation of the turbopump while retaining a sufficient recovery capacity.
  • the centrifugal wheel 20 it is not necessary for the centrifugal wheel 20 to be coupled with the rotary shaft 80 (as in the prior art) in order to accommodate the operation of the axial balancing system.
  • the pump 10 comprises a single centrifugal wheel, it forms a single block with the rotary shaft 80 (as shown in FIG. figure 1 ) and it is this rotary shaft 80 and the centrifugal wheel 20 that move axially together to accommodate the operation of the axial balancing system.
  • the manufacture of the pump according to the invention is therefore simplified, since it comprises fewer parts.
  • the cross section of the second passage 242 is shown smaller than the section of the first passage 241.
  • the opposite is also possible, provided that the pressure at the outlet of the second passage 242 remains greater than the pressure at the outlet of the first passage 241.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP10727469.8A 2009-05-11 2010-05-07 Pompe centrifuge a double echappement Active EP2430314B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0953096A FR2945330B1 (fr) 2009-05-11 2009-05-11 Pompe centrifuge a double echappement.
PCT/FR2010/050876 WO2010130923A1 (fr) 2009-05-11 2010-05-07 Pompe centrifuge a double echappement

Publications (2)

Publication Number Publication Date
EP2430314A1 EP2430314A1 (fr) 2012-03-21
EP2430314B1 true EP2430314B1 (fr) 2019-07-24

Family

ID=41319475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10727469.8A Active EP2430314B1 (fr) 2009-05-11 2010-05-07 Pompe centrifuge a double echappement

Country Status (6)

Country Link
US (1) US20120051885A1 (ru)
EP (1) EP2430314B1 (ru)
JP (1) JP2012526944A (ru)
FR (1) FR2945330B1 (ru)
RU (1) RU2011146920A (ru)
WO (1) WO2010130923A1 (ru)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170082070A1 (en) * 2012-04-17 2017-03-23 Timothy J. Miller Turbopump with a single piece housing and a smooth enamel glass surface
FR2998920B1 (fr) * 2012-12-04 2018-07-27 Thy Engineering Machine tournante telle qu'une turbine ou un compresseur.
DE102015001271A1 (de) * 2015-02-04 2016-08-04 Airbus Ds Gmbh Turbopumpe für ein Raketentriebwerk mit einer Radialstufe
CN105464711A (zh) * 2015-12-14 2016-04-06 中国北方发动机研究所(天津) 一种适合脉冲增压的新型轴流涡轮机
US10651709B2 (en) * 2017-05-09 2020-05-12 Gentherm Incorporated Fan arbor grounding
US10513928B2 (en) * 2017-08-31 2019-12-24 Flowserve Management Company Axial thrust balancing device
US11536287B2 (en) * 2017-12-04 2022-12-27 Hanwha Power Systems Co., Ltd Dual impeller

Citations (2)

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JPS59158398A (ja) * 1983-02-28 1984-09-07 Mitsubishi Heavy Ind Ltd うず巻ポンプ
US5105616A (en) * 1989-12-07 1992-04-21 Sundstrand Corporation Gas turbine with split flow radial compressor

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US5105616A (en) * 1989-12-07 1992-04-21 Sundstrand Corporation Gas turbine with split flow radial compressor

Also Published As

Publication number Publication date
WO2010130923A1 (fr) 2010-11-18
EP2430314A1 (fr) 2012-03-21
RU2011146920A (ru) 2013-06-20
JP2012526944A (ja) 2012-11-01
US20120051885A1 (en) 2012-03-01
FR2945330B1 (fr) 2011-07-15
FR2945330A1 (fr) 2010-11-12

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