EP0688955A1 - Dispositif pour l'équilibrage de la poussée axiale dans les pompes centrifuges - Google Patents

Dispositif pour l'équilibrage de la poussée axiale dans les pompes centrifuges Download PDF

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Publication number
EP0688955A1
EP0688955A1 EP95108418A EP95108418A EP0688955A1 EP 0688955 A1 EP0688955 A1 EP 0688955A1 EP 95108418 A EP95108418 A EP 95108418A EP 95108418 A EP95108418 A EP 95108418A EP 0688955 A1 EP0688955 A1 EP 0688955A1
Authority
EP
European Patent Office
Prior art keywords
impeller
housing
housing wall
gap
ribs
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.)
Granted
Application number
EP95108418A
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German (de)
English (en)
Other versions
EP0688955B1 (fr
Inventor
Wolfgang Metzinger
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.)
KSB AG
Original Assignee
KSB AG
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Filing date
Publication date
Application filed by KSB AG filed Critical KSB AG
Publication of EP0688955A1 publication Critical patent/EP0688955A1/fr
Application granted granted Critical
Publication of EP0688955B1 publication Critical patent/EP0688955B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel

Definitions

  • a device for complete compensation of the axial thrust in centrifugal pumps which, in addition to hydraulic axial thrust compensation, which operates in a conventional manner, has a second, likewise hydraulically acting compensation system.
  • This second system is based on means that a pressure increase in the pressure side space of the impeller at one under cause the predetermined value to drop. Since it is not dependent on the pump head as an effective parameter, it can independently compensate for the axial forces even with small heads.
  • the present invention also aims at a complete hydraulic compensation of the axial thrust. However, it takes a different path than the facility described above.
  • variable sealing gap which has control behavior, is formed by an axial gap between the suction-side end face of the impeller and the housing wall.
  • An alternative embodiment provides a variable sealing gap in the form of a diagonal gap.
  • the housing ribs and the paragraphs closest to them on the housing wall are designed to be directly adjacent to one another.
  • the individual features of the invention are known in principle. However, they have so far been used in combinations other than those according to the invention, in each case still requiring an axial bearing, at least as an emergency bearing.
  • the invention makes an axial bearing dispensable because the rotor, i.e. the unit formed from the impeller, the shaft and the rotor of the driving electric motor, is fixed in an axially contact-free manner and, when deflected from this equilibrium position, is returned to its original position without axial force by high restoring forces becomes.
  • an angular sealing gap which is formed from a variable axial gap 3 between the end face 4 of the impeller 2 and the housing wall 5 opposite it and a radial gap 6 of constant width between the impeller neck 7 and the housing wall 5 surrounding it.
  • Radial sealing gaps 8 and 9 which are formed between a circular and concentric to the axis of the impeller 2 paragraph 10 on the pressure side cover plate 11 of the impeller 2 and paragraphs 12 and 13 on the opposite housing wall 5; a plurality of radially extending housing ribs 14 which are evenly distributed over the circumference and which are delimited radially by the shoulder 13 arranged on a larger diameter and a shoulder 15 provided on a smaller diameter; a variable axial gap 16, which is formed between the shoulder 15 and the pressure-side cover plate 11.
  • relief bores 17 are provided, which are arranged in the vicinity of the hub of the impeller 2.
  • FIG. 2 essentially corresponds to the embodiment of FIG. 1, the only difference is the suction-side sealing gap, which is designed as a diagonal gap 18 in the device in FIG. 2.
  • the advantage of the diagonal gap 18 over the angular gap consisting of the axial gap 3 and the radial gap 6 lies in its better control behavior, as can also be seen from the diagrams in FIGS. 3 and 4.
  • the disadvantage is the more complex manufacture of a diagonal gap.
  • Figures 3 and 4 already mentioned show the variable forces assigned to the axial movement path s of the impeller 2, the force F2 acting on the pressure side and the force F1 acting on the suction side of the impeller 2.
  • the maximum movement path s max should be between 0.8 and 1.2 mm.
  • a stable equilibrium position of the rotor is established by coordinating the elements of the axial thrust compensation with one another, i.e. the position and play of the sealing gaps 3, 6, 8, 9, 16, 18 and the position and size of the housing ribs 14 and the relief bores 17 . This fixes the rotor axially without contact during rotation. When deflected from the equilibrium position, relatively high restoring forces ensure that the rotor returns to its original position, which is free of axial force.
  • the diagonal gap 18 on the suction side is superior to the combination of the axial gap 3 and the radial gap 6 in its control behavior acting on the axial thrust compensation.
  • the device according to the invention can also be realized with a combination of radial (8, 9) and diagonal (22, 23) sealing gaps. Likewise, more than two such sealing gaps (8, 9; 22, 23) can be provided on the pressure side of the impeller (2).
  • the housing ribs 14 of the exemplary embodiments were created by milling out the free spaces between the ribs. As a result, the free space areas of paragraphs 13 and 15 were created. It should be mentioned that milling out with a finger cutter results in an arcuate transition of the housing ribs 14 to the walls of the shoulders 13, 15. In a borderline case applicable to short housing ribs, the outer contour of a rib can be semicircular concave on both sides. This has no negative influence on the control behavior of the housing ribs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
EP95108418A 1994-06-23 1995-06-01 Dispositif pour l'équilibrage de la poussée axiale dans les pompes centrifuges Expired - Lifetime EP0688955B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4421888 1994-06-23
DE4421888A DE4421888A1 (de) 1994-06-23 1994-06-23 Einrichtung zum Axialschubausgleich bei Kreiselpumpen

Publications (2)

Publication Number Publication Date
EP0688955A1 true EP0688955A1 (fr) 1995-12-27
EP0688955B1 EP0688955B1 (fr) 1999-12-29

Family

ID=6521263

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95108418A Expired - Lifetime EP0688955B1 (fr) 1994-06-23 1995-06-01 Dispositif pour l'équilibrage de la poussée axiale dans les pompes centrifuges

Country Status (2)

Country Link
EP (1) EP0688955B1 (fr)
DE (2) DE4421888A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19804768A1 (de) * 1998-02-06 1999-08-12 Pfeiffer Vacuum Gmbh Rotorlagerung für eine Gasreibungspumpe
EP0952352A3 (fr) * 1998-04-20 2001-05-30 Nikkiso Co., Ltd. Equilibrage de poussée axiale
EP1296062A1 (fr) * 2001-09-20 2003-03-26 Grundfos a/s Pompe centrifugale
EP1306557A3 (fr) * 2001-07-13 2004-01-07 Abs Pump Production Ab Pompe centrifugale
GB2442320A (en) * 2006-09-28 2008-04-02 Snecma Pump with axial balancing
WO2012061011A3 (fr) * 2010-10-25 2012-06-28 Dresser-Rand Company Système et appareil permettant de réduire les forces de poussée qui agissent sur un rotor de compresseur
CN103850947A (zh) * 2012-11-29 2014-06-11 上海凯士比泵有限公司 一种抗汽蚀叶片泵
KR101700332B1 (ko) * 2015-07-29 2017-02-14 한국해양대학교 산학협력단 반경류 터빈의 추력감소 장치
CN115306759A (zh) * 2022-08-27 2022-11-08 浙江理工大学 一种高速离心泵轴向力平衡结构及其预测方法

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016220976B3 (de) 2016-10-25 2018-03-29 Engineering Center Steyr Gmbh & Co. Kg Modul für ein Kühlsystem eines Kraftfahrzeugs
DE102017211940A1 (de) * 2017-07-12 2019-01-17 Bayerische Motoren Werke Aktiengesellschaft Brennstoffzellensystem für ein Kraftfahrzeug sowie Strömungsmaschine für ein Brennstoffzellensystem
LU500893B1 (de) * 2021-11-24 2023-05-24 Wilo Se Axiallagerlose Nassläuferpumpe
DE102024204730A1 (de) * 2024-05-23 2025-11-27 Robert Bosch Gesellschaft mit beschränkter Haftung Bauraumoptimierte Integration eines Impellers in eine Doppel-Axialkolbenmaschine in Back-to-back Ausführung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR413135A (fr) * 1910-02-07 1910-08-01 Farcot Freres Et Cie Soc Dispositif d'équilibrage des pompes centrifuges
FR500808A (fr) * 1919-06-18 1920-03-25 Eugene Beaudrey Système pour la réalisation de l'équilibre axial des roues de turbines hydrauliques ou pompes centrifuges
FR518914A (fr) * 1914-07-06 1921-06-02 Jean Guerin équilibrage automatique de la poussée axiale
DE4026905A1 (de) 1990-08-25 1992-02-27 Klein Schanzlin & Becker Ag Axialschubausgleich fuer kreiselpumpen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE390366C (de) * 1924-02-18 Paul Joseph Charles Marechal Entlastungsvorrichtung an Turbomaschinen
DE325196C (de) * 1920-09-14 Aeg Achsialdruckausgleichvorrichtung fuer Zentrifugalpumpen
JPS4938641B1 (fr) * 1970-08-06 1974-10-19
DE2640990A1 (de) * 1976-09-11 1978-03-16 Klein Schanzlin & Becker Ag Kreiselpumpe mit selbsttaetiger axialschubregelung an einem der laufraeder
DE2733631A1 (de) * 1977-07-26 1979-02-08 Hermetic Pumpen Gmbh Kreiselpumpe
SE509487C2 (sv) * 1991-03-22 1999-02-01 Warman Int Ltd Centrifugalpump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR413135A (fr) * 1910-02-07 1910-08-01 Farcot Freres Et Cie Soc Dispositif d'équilibrage des pompes centrifuges
FR518914A (fr) * 1914-07-06 1921-06-02 Jean Guerin équilibrage automatique de la poussée axiale
FR500808A (fr) * 1919-06-18 1920-03-25 Eugene Beaudrey Système pour la réalisation de l'équilibre axial des roues de turbines hydrauliques ou pompes centrifuges
DE4026905A1 (de) 1990-08-25 1992-02-27 Klein Schanzlin & Becker Ag Axialschubausgleich fuer kreiselpumpen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"centrifugal pump lexicon", KLEIN,SCHANZLIN & BECKER *

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19804768A1 (de) * 1998-02-06 1999-08-12 Pfeiffer Vacuum Gmbh Rotorlagerung für eine Gasreibungspumpe
DE19804768B4 (de) * 1998-02-06 2006-08-24 Pfeiffer Vacuum Gmbh Rotorlagerung für eine Gasreibungspumpe
EP0952352A3 (fr) * 1998-04-20 2001-05-30 Nikkiso Co., Ltd. Equilibrage de poussée axiale
EP1306557A3 (fr) * 2001-07-13 2004-01-07 Abs Pump Production Ab Pompe centrifugale
EP1296062A1 (fr) * 2001-09-20 2003-03-26 Grundfos a/s Pompe centrifugale
FR2906578A1 (fr) * 2006-09-28 2008-04-04 Snecma Sa Pompe comprenant un systeme d'equilibrage axial
GB2442320A (en) * 2006-09-28 2008-04-02 Snecma Pump with axial balancing
US7686572B2 (en) 2006-09-28 2010-03-30 Snecma Pump comprising an axial balancing system
GB2442320B (en) * 2006-09-28 2011-09-07 Snecma Pump comprising an axial balancing system
WO2012061011A3 (fr) * 2010-10-25 2012-06-28 Dresser-Rand Company Système et appareil permettant de réduire les forces de poussée qui agissent sur un rotor de compresseur
CN103850947A (zh) * 2012-11-29 2014-06-11 上海凯士比泵有限公司 一种抗汽蚀叶片泵
CN103850947B (zh) * 2012-11-29 2017-03-08 上海凯士比泵有限公司 一种抗汽蚀叶片泵
KR101700332B1 (ko) * 2015-07-29 2017-02-14 한국해양대학교 산학협력단 반경류 터빈의 추력감소 장치
CN115306759A (zh) * 2022-08-27 2022-11-08 浙江理工大学 一种高速离心泵轴向力平衡结构及其预测方法

Also Published As

Publication number Publication date
DE59507508D1 (de) 2000-02-03
DE4421888A1 (de) 1996-01-04
EP0688955B1 (fr) 1999-12-29

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