US3874812A - Axial pressure balancing arrangement for a multistage centrifugal pump - Google Patents

Axial pressure balancing arrangement for a multistage centrifugal pump Download PDF

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Publication number
US3874812A
US3874812A US281546A US28154672A US3874812A US 3874812 A US3874812 A US 3874812A US 281546 A US281546 A US 281546A US 28154672 A US28154672 A US 28154672A US 3874812 A US3874812 A US 3874812A
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Prior art keywords
rotors
stator
rotor
gap
inlet
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Expired - Lifetime
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US281546A
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English (en)
Inventor
Wolfgang Hanagarth
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Klein Schanzlin and Becker AG
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Klein Schanzlin and Becker AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • 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
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance

Definitions

  • Multistage centrifugal pumps as are used, for example, as feeding pumps for boilers having a very great pressure head, develop a pronounced axial force which is generally hydraulically balanced by an additional device.
  • additional balancing device may include relief pistons which require an additional thrust bearing for the remaining axial forces, or relief discs which automatically balance the axial force acting on the rotors of the pump. Combinations of such constructions also require an additional axial thrust bearing to control certain axial forces.
  • the relief devices according to the prior art perform the desired function to a certain degree, but have the disadvantage of a complicated structure which increases the cost and the axial length. Also a substantial loss in efficiency occurs due to the flow losses in the relief device caused by a friction at the endfaces of the relief device. The wear upon the relief device is quite pronounced due to the high pressure differential, and also the mechanical reliability, when pump distortion or rotor bending occurs, is unsatisfactory.
  • the conventional relief devices have the disadvantage that the limit of automatic regulation is located at a value not much greater than Q/Q I :3 to 1:4 which when the pump is operated under an overload, as may occur upon a pipe break or another disturbance, frequently results in jamming of the relief device and destruction of the pump.
  • Another object of the invention is to provide a simple and inexpensive axial pressure balancing arrangement using a duct through each rotor, and a throttle controlling the branch flow through the gap between a rotor and the adjacent stator portion.
  • a multistage centrifugal pump with a plurality of rotors and stator portions between the rotors is provided with gaps between the rotors and stator portions whose width varies depending on the rotor position, and which is arranged in series with one or several relief openings or ducts at each rotor.
  • the arrangement requires only normal tolerances for the several rotors, because the total axial pressure equalization occurs even if the widths of the several gaps differ.
  • the multistage centrifugal pump according to the invention has substantial advantages, for example the elimination of a separate relief device, and thereby the possibility to obtain a short, compact, reliable and inexpensive pump, as well as an increase in efficiency as compared with pump provided with known relief devices.
  • Such improvement of the pump is due to the elimination of friction at the endfaces of the relief devices, and also to the reduction of the endface friction of the several rotors which, according to the invention, are used as relief device.
  • the endface friction is reduced due to the fact that the relief flow flows inwards in radial directions through the gap, while in the prior art the flow takes place outward in the space adjacent the rotor endface, which causes an increased friction on the endfaces.
  • Another advantage of the invention is the increase of the Lomakin forces in the clearances between the rotor shaft and the stator bores of the respective stator portion which results in a better centering of the rotors, and eliminates the necessity for a radial bearing in the middle of a multistage centrifugal pump.
  • Such an additional bearing in accordance with the prior art requires space corresponding to an additional rotor and pump stage.
  • the danger of wear is reduced in the arrangement of the invention since not the entire end pressure is used for balancing the axial force produced by one stage.
  • the increase of the width of the control gaps, as compared with construction of the prior art using relief discs, is another object of the invention.
  • FIG. 1 is a fragmentary axial sectional view illustrating an embodiment of the invention
  • FIG. 2 is a fragmentary sectional view illustrating on an enlarged scale, a modification of the embodiment of FIG. 1;
  • FIG. 3 is a fragmentary axial sectional view illustrating another modification
  • FIG. 4 is a fragmentary axial sectional view illustrating another modification
  • FIG. 5 is a fragmentary axial sectional view illustrating another modification.
  • FIG. 6 is a fragmentary axial sectional view illustrating another embodiment of the invention.
  • FIG. 1 illustrates an embodiment of the invention in which a multistage centrifugal pump has stator means 20 consisting of several parts held together by bolts 21A and supporting a shaft 22 for rotation.
  • Two rotors I have inner hubs 30 surrounding shaft 22.
  • a first stator portion 21 is disposed between the two rotors 1 and has a sleeve 31 surrounding shaft 22.
  • Stator 20 has an inlet 23 and an outlet 24, and a fluid flows into the inlet la of the first rotor 1 and from the outlet lb in outward direction and is then guided by the first stator portion 21 into the inlet 1a of the next following rotor l, and discharging the fluid from the outlet 1b of the second rotor into a second stator portion 21.
  • each rotor 1 is formed with at least one but preferably a plurality of axially extending ducts 2 each of which connects the inlet la of one rotor 1 with the radially inner part of a gap 5 formed between the front face of rotor 1 and the rear face of the next following stator portion 21.
  • the front face of each rotor l is provided with a circular recess 3 confronting a circular projection 4 on the rear face of the respective stator portion 21.
  • Axially extending stator ducts 7 connect the inner part of each gap with the inlet of the next following rotor 1.
  • each duct 7 is located in the respective stator portion 21 adjacent the stator sleeve 31.
  • the circular projection 4 enters the circular recess 3, acting as a throttle. Therefore, parts 3 and 4 may be considered as throttling portions of each rotor and .corresponding stator portion 21.
  • each rotor 1 is relieved and its own pressure head acts in the throttling portions 3 and 4.
  • each control gap 5 is increased so that water flows from the outlet lb of each rotor into the outer part of the respective gap 5 and radially inward through gap 5, past the throttling portions 3 and 4, and through the relief ducts 2 into the respective inlets 1a of the rotors 1.
  • the relieved water flowing through the gaps 5 excites the vortices in the gaps 5 to such an extent that the relative speed between the front faces of the rotors 1 and such vortices becomes smaller, resulting in a substantial reduction of the friction losses on the front faces of the rotors, as compared with the arrangements of the prior art in which the branch stream flowing through gap 5 moves outward in gap 5, braking the vortex at the front face of the rotor, which results in a greater relative speed between the front face of the rotor and the vortex adjacent thereto in gap 5, bringing about greater friction losses, irrespective of the increased axial force due to the slower rotation of the vortex.
  • the relie-fducts 2 are located radially inward of the recesses 3, the modification of FIG. 2 positions the relief duct 2 at the same radial distance as the circular throttling recess 3 so that the duct 2 opens into the recess 3.
  • the branch stream flowing through the stator duct 7 is also regulated by the throttle 3, 4 if it is not required for obtaining greater radial forces, as in the embodiment of FIG. 1.
  • FIG. 3 illustrates another modification in which the relief duct or ducts 2 directly open into the circular recess 3 which has a rectangular cross section, as in the embodiments of FIGS. 1 and 2.
  • the circular projection 4 is differently constructed, and has a radial inner face 4a sliding on a complementary face in the recess 3, and at a greater radius a regulating edge 4b. which is spaced from the corresponding face and edge in recess 3.
  • the regulating edge 4b effects an automatic.
  • the relief duct or ducts 2 also open into the circular recess 3 which cooperates with a circular projection 4 to form a throttle.
  • bores 8 are provided at the inner end of the rotor 1 to connect the inner part of gap 5 with the inlet 1a of rotor 1 and cooperating with the stator duct 7 so I that fluid can flow through stator duct 7 and bores 8, as indicated by arrows.
  • the communication between stator ducts 7 and rotor bores 8 is continuous in the arrangement of FIG. 4.
  • the branch stream through gap 5 is substantially independent of the regulation of the axial forces.
  • the rotor 1 may also be provided with an open bore or duct 8, as shown in FIG. 4, so that the branch stream is practically independent of the balancing of axial forces, and can be regulated in accordance with the diameters of bores 8.
  • FIG. 5 illustrates an embodiment of the invention in.
  • FIG. 5 is a more rigid regulation than in the arrangement of FIGS. 1 to 4, but requires precise tolerances for the throttling face portions 9a and 10a, which is difficult to obtain for high rotary speeds so that the modification of FIG. 5 should mainly be used for pumps having a small number of rotors.
  • FIG. 5 further shows a rotor duct 7, and also two circular grooves 11 having semicircular cross sections and confronting each other to form a circular conduit.
  • each rotor is connected by a conduit 25 of respective stator portion 21 with the inlet 1a of the next following rotor.
  • Only the first rotor 1 is provided with a relief duct 2 as described with reference to FIG. 1.
  • Rotors 40 and 41 have hub portions formed with axial channels 6a com,- municatin g with the inner parts of gaps 5.
  • the channels 6a are aligned with channels 6 in the inner surfaces of I sleeve portions 31 within the stator portions 21.
  • ducts 2' are formed adjacent the outer surface of shaft 22, and may be angularly staggered about the periphery of shaft 22.
  • the channels or ducts 2' take the place of the relief ducts 2, but the first rotor 1 may be constructed as described with reference to FIG. 1.
  • FIG. 6 is advantageous if additional weight acts in axial direction, for example if the pump has a vertical axis and the rotor weight is effective in axial direction.
  • the arrangement of FIG. 6 is also advantageous for extending the limits of relief for high speed rotors.
  • a combination comprising a hollow stator; a shaft rotatably mounted in said stator; a pair of axially movable coaxial rotors mounted in said stator adjacent to each other and being driven by said shaft, each of said rotors having a fluidadmitting inlet nearer to and a fluid-discharging outlet more distant from said shaft and the inlet of one of said rotors being in communication with the outlet of the other of said rotors, each of said rotors defining with said stator a gap extending radially inwardly from and communicating with the respective outlet; and channel means extending from the gap between said stator and said one rotor to the inlet of said other rotor to convey fluid from said last-mentioned gap into said lastmentioned inlet, each of said rotors defining with said stator discrete throttling means for restricting the flow of fluid in the respective gap to an extent which varies in response to changes in the shaft
  • each of said throttling means comprises a circular groove in the respective rotor and a circular projection provided on said stator and registering with the respective groove.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US281546A 1971-08-21 1972-08-17 Axial pressure balancing arrangement for a multistage centrifugal pump Expired - Lifetime US3874812A (en)

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DE2141966 1971-08-21

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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4207023A (en) * 1978-06-08 1980-06-10 Tokyo Shibaura Electric Co., Ltd. Multistage hydraulic machine
US5358378A (en) * 1992-11-17 1994-10-25 Holscher Donald J Multistage centrifugal compressor without seals and with axial thrust balance
GB2278889A (en) * 1993-06-07 1994-12-14 Ford Motor Co Multi-stage automotive fuel pump
US6193462B1 (en) * 1998-04-08 2001-02-27 Nikkiso Co., Ltd. Thrust balance device
US20080056879A1 (en) * 2006-08-30 2008-03-06 Schlumberger Technology Corporation System and Method for Reducing Thrust Acting On Submersible Pumping Components
US20080080965A1 (en) * 2006-09-28 2008-04-03 Snecma Pump comprising an axial balancing system
US7775758B2 (en) 2007-02-14 2010-08-17 Pratt & Whitney Canada Corp. Impeller rear cavity thrust adjustor
US20110058928A1 (en) * 2009-09-09 2011-03-10 Baker Hughes Incorporated Centrifugal pump with thrust balance holes in diffuser
CN102734231A (zh) * 2012-07-03 2012-10-17 芜湖市湖净环保机械有限公司 一种多级泵的平衡环
US20130058777A1 (en) * 2009-12-30 2013-03-07 Schlumberger Technology Corporation Submersible pump stage
US20140370412A1 (en) * 2011-12-01 2014-12-18 Daimler Ag Charging Device for a Fuel Cell, in Particular of a Motor Vehicle
US8925317B2 (en) 2012-07-16 2015-01-06 General Electric Company Engine with improved EGR system
US20160241111A1 (en) * 2013-10-14 2016-08-18 Siemens Aktiengesellschaft Device for deflecting at least a portion of a cooling fluid lowing axially in an intermediate space which is arranged between a rotor and a stator of a rotating electrical machine
EP3739215A1 (fr) * 2020-04-20 2020-11-18 Sulzer Management AG Pompe lubrifiée dans un fluide de traitement
US10890189B2 (en) 2016-06-01 2021-01-12 Schlumberger Technology Corporation Submersible pumping system having thrust pad flow bypass
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
US11499563B2 (en) 2020-08-24 2022-11-15 Saudi Arabian Oil Company Self-balancing thrust disk
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump
US11920469B2 (en) 2020-09-08 2024-03-05 Saudi Arabian Oil Company Determining fluid parameters
US11994016B2 (en) 2021-12-09 2024-05-28 Saudi Arabian Oil Company Downhole phase separation in deviated wells
US20240191723A1 (en) * 2022-12-13 2024-06-13 Sulzer Management Ag Pump for conveying wastewater and impeller for such a pump
US12085687B2 (en) 2022-01-10 2024-09-10 Saudi Arabian Oil Company Model-constrained multi-phase virtual flow metering and forecasting with machine learning

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS527002A (en) * 1975-07-07 1977-01-19 Mitsubishi Heavy Ind Ltd Method of removing thrust of impeller in high pressure multistage pump
JPS5247671U (fr) * 1975-10-02 1977-04-05
JPS5743109Y2 (fr) * 1976-12-24 1982-09-22
JPS5730464Y2 (fr) * 1978-03-17 1982-07-03
JPS56105144A (en) * 1980-01-19 1981-08-21 Kokusai Gijutsu Kaihatsu Kk Rectilinear-feeding mechanism

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US958612A (en) * 1907-08-12 1910-05-17 Wilhelm Heinrich Eyermann Means for balancing turbines and pumps.
US981763A (en) * 1909-03-29 1911-01-17 Heinrich Adolf Huelsenberg Means for regulating the compensation of the axial thrust in centrifugal pumps or blasts.
US996859A (en) * 1907-11-27 1911-07-04 Gen Electric Centrifugal blower, pump, compressor, &c.
US1105808A (en) * 1912-08-02 1914-08-04 Fairbanks Morse & Co Centrifugal pump.
US1151965A (en) * 1913-08-12 1915-08-31 Laval Steam Turbine Co Balancing of centrifugal pumps.
US1151964A (en) * 1913-08-12 1915-08-31 Laval Steam Turbine Co Balancing of centrifugal pumps.
US1609306A (en) * 1924-11-22 1926-12-07 Laval Steam Turbine Co Deep-well pump
US1642914A (en) * 1926-07-03 1927-09-20 Layne & Bowler Corp Sandproof bearing
US2857850A (en) * 1956-02-17 1958-10-28 Tokhem Corp In-line motor pump
US3204562A (en) * 1963-09-30 1965-09-07 Berkeley Pump Company Anti gas-lock construction for turbine pump
US3438330A (en) * 1965-10-20 1969-04-15 Waterous Co Noise suppression means

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US958612A (en) * 1907-08-12 1910-05-17 Wilhelm Heinrich Eyermann Means for balancing turbines and pumps.
US996859A (en) * 1907-11-27 1911-07-04 Gen Electric Centrifugal blower, pump, compressor, &c.
US981763A (en) * 1909-03-29 1911-01-17 Heinrich Adolf Huelsenberg Means for regulating the compensation of the axial thrust in centrifugal pumps or blasts.
US1105808A (en) * 1912-08-02 1914-08-04 Fairbanks Morse & Co Centrifugal pump.
US1151965A (en) * 1913-08-12 1915-08-31 Laval Steam Turbine Co Balancing of centrifugal pumps.
US1151964A (en) * 1913-08-12 1915-08-31 Laval Steam Turbine Co Balancing of centrifugal pumps.
US1609306A (en) * 1924-11-22 1926-12-07 Laval Steam Turbine Co Deep-well pump
US1642914A (en) * 1926-07-03 1927-09-20 Layne & Bowler Corp Sandproof bearing
US2857850A (en) * 1956-02-17 1958-10-28 Tokhem Corp In-line motor pump
US3204562A (en) * 1963-09-30 1965-09-07 Berkeley Pump Company Anti gas-lock construction for turbine pump
US3438330A (en) * 1965-10-20 1969-04-15 Waterous Co Noise suppression means

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4207023A (en) * 1978-06-08 1980-06-10 Tokyo Shibaura Electric Co., Ltd. Multistage hydraulic machine
US5358378A (en) * 1992-11-17 1994-10-25 Holscher Donald J Multistage centrifugal compressor without seals and with axial thrust balance
GB2278889A (en) * 1993-06-07 1994-12-14 Ford Motor Co Multi-stage automotive fuel pump
US5401143A (en) * 1993-06-07 1995-03-28 Ford Motor Company Multi-stage automotive fuel pump having angeled fuel transfer passage
GB2278889B (en) * 1993-06-07 1996-02-07 Ford Motor Co Multi-stage automotive fuel pump
US6193462B1 (en) * 1998-04-08 2001-02-27 Nikkiso Co., Ltd. Thrust balance device
US20080056879A1 (en) * 2006-08-30 2008-03-06 Schlumberger Technology Corporation System and Method for Reducing Thrust Acting On Submersible Pumping Components
US20100040492A1 (en) * 2006-08-30 2010-02-18 Schlumberger Technology Corporation System and method for reducing thrust acting on submersible pumping components
US8337142B2 (en) * 2006-08-30 2012-12-25 Schlumberger Technology Corporation System and method for reducing thrust acting on submersible pumping components
US20080080965A1 (en) * 2006-09-28 2008-04-03 Snecma Pump comprising an axial balancing system
US7686572B2 (en) * 2006-09-28 2010-03-30 Snecma Pump comprising an axial balancing system
US7775758B2 (en) 2007-02-14 2010-08-17 Pratt & Whitney Canada Corp. Impeller rear cavity thrust adjustor
US20110058928A1 (en) * 2009-09-09 2011-03-10 Baker Hughes Incorporated Centrifugal pump with thrust balance holes in diffuser
US8801360B2 (en) * 2009-09-09 2014-08-12 Baker Hughes Incorporated Centrifugal pump with thrust balance holes in diffuser
US20130058777A1 (en) * 2009-12-30 2013-03-07 Schlumberger Technology Corporation Submersible pump stage
US20140370412A1 (en) * 2011-12-01 2014-12-18 Daimler Ag Charging Device for a Fuel Cell, in Particular of a Motor Vehicle
CN102734231A (zh) * 2012-07-03 2012-10-17 芜湖市湖净环保机械有限公司 一种多级泵的平衡环
US8925317B2 (en) 2012-07-16 2015-01-06 General Electric Company Engine with improved EGR system
US20160241111A1 (en) * 2013-10-14 2016-08-18 Siemens Aktiengesellschaft Device for deflecting at least a portion of a cooling fluid lowing axially in an intermediate space which is arranged between a rotor and a stator of a rotating electrical machine
US10199903B2 (en) * 2013-10-14 2019-02-05 Siemens Aktiengesellschaft Device for deflecting at least a portion of a cooling fluid lowing axially in an intermediate space which is arranged between a rotor and a stator of a rotating electrical machine
US10890189B2 (en) 2016-06-01 2021-01-12 Schlumberger Technology Corporation Submersible pumping system having thrust pad flow bypass
US11846297B2 (en) 2020-04-20 2023-12-19 Sulzer Management Ag Process fluid lubricated pump
EP3739215A1 (fr) * 2020-04-20 2020-11-18 Sulzer Management AG Pompe lubrifiée dans un fluide de traitement
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
US11499563B2 (en) 2020-08-24 2022-11-15 Saudi Arabian Oil Company Self-balancing thrust disk
US11920469B2 (en) 2020-09-08 2024-03-05 Saudi Arabian Oil Company Determining fluid parameters
US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump
US11994016B2 (en) 2021-12-09 2024-05-28 Saudi Arabian Oil Company Downhole phase separation in deviated wells
US12085687B2 (en) 2022-01-10 2024-09-10 Saudi Arabian Oil Company Model-constrained multi-phase virtual flow metering and forecasting with machine learning
US20240191723A1 (en) * 2022-12-13 2024-06-13 Sulzer Management Ag Pump for conveying wastewater and impeller for such a pump

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Publication number Publication date
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