EP0002157A1 - Pumpe - Google Patents

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Publication number
EP0002157A1
EP0002157A1 EP78400182A EP78400182A EP0002157A1 EP 0002157 A1 EP0002157 A1 EP 0002157A1 EP 78400182 A EP78400182 A EP 78400182A EP 78400182 A EP78400182 A EP 78400182A EP 0002157 A1 EP0002157 A1 EP 0002157A1
Authority
EP
European Patent Office
Prior art keywords
disc
pump
spiral
shaft
wheel
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
EP78400182A
Other languages
English (en)
French (fr)
Other versions
EP0002157B1 (de
Inventor
Jean-Claude Villard
Gilbert Berthereau
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.)
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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
Application filed by Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Publication of EP0002157A1 publication Critical patent/EP0002157A1/de
Application granted granted Critical
Publication of EP0002157B1 publication Critical patent/EP0002157B1/de
Expired 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
    • F04D29/08—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
    • 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

  • the present invention relates to a pump of the paddle wheel type mounted at the end of a driving shaft and placed in a casing, each blade forming a conduit extending on one side in an axial wheel body and emerging opposite. a suction duct and another radially c8té in a wheel extension with radial extension running opposite a tangential delivery duct.
  • An object of the invention is to provide pump seals, which are particularly effective in that they undoubtedly avoid undesirable leaks, which improves the yield, and which moreover have almost zero wear by friction, this which gives the pump thus equipped a very long service life and, at the same time, leads to particularly reduced maintenance; a pump according to the invention has very high safety in use.
  • the pump according to the invention is characterized in that the pump wheel is mounted with slight axial clearance and in that the disc of the suction sealing device is mounted at the end of an axially elastic and sealed hub, such that 'a bellows, fixed to the housing around a suction passage of said housing.
  • the invention therefore represents a transposition and a particular adaptation to pumps of the technique of spiral groove bearings which has been proposed until now essentially to serve as an axial stop for a shaft subjected to a strong axial thrust, which is the case. usually from most pumps and turbines, or from shaft support.
  • this technique is described in some publications, in particular in an article entitled “New forms of bearings: gas bearings and spiral grooves” by EA HUIJD £ RHAN published in “Revue Technique PHILIPS", tome 25, 1963/64 n ° 9 - page 245 to 266. Briefly summarized, this technique consists in “pumping" a fluid, which is generally a gas, radially towards the center of the two discs, which causes a separation of the discs, so that the support of the part mobile in rotation is effected by the medium in question.
  • a merit of the present invention is to have discerned the advantage of this technique for ensuring the tightness of a pump through the use, as sealing fluid, of the liquid to be pumped itself, and to provide the particular adaptations to this application which notably consist in causing a centrifugal increase in the pressure of the sealing fluid, which determines a particular direction of rotation of the smooth disc relative to the disc with spiral grooves, (while the centrifugal or centripetal direction , the pumping effect is indifferent in the previously proposed applications of axial stop and shaft support) and to measure this increase in pressure by constructive methods resulting from relatively complex calculations and experiments, so that 'It corresponds substantially to the increase in pressure due to the pumping effect.
  • the back pressure thus developed at the junctions makes it possible, during rotation of the wheel, to completely block the leaks without any wear of the parts rotating relative to each other, which are separated by a thin liquid film projecting from spiral grooves to interpose between the sail spans lantes between grooves of the spiral grooved disc and the smooth face of the other facing disc, while a certain friction of parts takes place exclusively at the times of starting and stopping the pump and that leaks along grooves can intervene when stopped, if certain technical measures detailed below, which are also in accordance with the invention, are not implemented.
  • This process is particularly indicated in the field of cryogenic pumps by avoiding solid friction junctions undergoing significant thermal stresses.
  • the start-up of a cryogenic pump is made easier and faster thanks to the hydrodynamic junctions described.
  • the shafts of the motor and the pump may not be aligned as rigorously as in conventional motor-pump groups and it is even possible, if desired, to remove the support of the pump by the motor block, which reduces heat losses by conduction along this support. It is also understood that the technique for producing the pumps is considerably simplified at the same time as their weight is reduced.
  • a cryogenic pump comprises a shaft 1 of a motor 2 extending through a support 3 towards a pump casing 4, where the shaft 1 receives, at the end, a wheel with blades 5 forming a plurality of blades made up of identical conduits 6 arranged around the shaft 1 and having an axial suction part 7 in a wheel body 5 'situated in the vicinity of the shaft 1 and a delivery part radial 8 in a 5 "wheel flap with radial extension.
  • the suction parts 7 open out opposite a casing opening 9 on which is fixed, by flange 10, a supply duct 11.
  • the discharge parts 8 open into the pump casing 4 while passing opposite a tangential discharge duct 12.
  • the impeller 5 is associated with two main sealing means, one of these means generally designated by 13 is located on the "shaft outlet” side and aims to prevent leaks of liquid flowing between a front wall 14 of the impeller 5 and a transverse wall 15 of the pump housing 4 (according to arrow f 1 ) on the one hand, between the shaft 1 and a hub 16 of the impeller 5 towards the suction (according to arrow f 2 ) and incidentally along the shaft 1 outwards (according to arrow f 3 ), the other sealing means, generally designated by 18, is located “suction suction" of the pump and aims to avoid liquid recirculation leaks, which may occur between one end 19 of the impeller 5 and another wall 20, incorporating the suction opening 9, of the pump housing 4.
  • the two sealing means 13 and 18 both consist of two opposite radial annular discs 22 and 23 for the sealing means 13 and 24, 25 for the sealing means 18.
  • the discs 22 and 24 are secured with the impeller 5, while the discs 23 and 25 are fixed in rotation, the disc 23 being fixed on the casing wall 15, while the disc 25 is fixed in leaktight manner, preferably by its inner periphery 26, to one end of a bellows 28, of which another end 29 is fixed to the casing wall 20 at the periphery of the suction opening 9.
  • each pair of discs 22 and 23 on the one hand and 24, 25 on the other hand must be able to come into contact face against face and deviate somewhat from each other and this simultaneously and in the same direction for the two pairs of discs 22 and 23, 24 and 25.
  • the disc 23 is not only immobilized in axial rotation, but also in axial translation, since it is secured to the casing wall 15, the impeller 5 is mounted with a slight axial movement on the shaft 1 by means of grooves 30, however preventing any rotation movement, this axial movement being moreover limited by a stop 31 more or less screwed at the end of the shaft 1.
  • the rotating disc 22 (or 24) has a face opposite the- tre disc, which is quite smooth, while in the face of the other disc 23 or 25 respectively which is fixed in rotation was made a plurality of grooves in the form of spirals 40 (see Figure 2) of depth equal to a few hundredths of a millimeter, freeing between them, an equal number of projecting spiral bearing surfaces 41 which, advantageously, have the same transverse surface as the grooves 40.
  • a rotation in the direction of arrow F of the rotating mobile disc (22 or 24) relative to the fixed rotating disc (23 or 25 respectively) causes a significant pumping effect on the liquid according to arrows a and a significant increase in pressure from the internal periphery (where this pressure is equal to the suction pressure) to the external periphery (where the prevailing pressure is the discharge pressure ).
  • this pressure increase depends on different parameters, including in particular the nature and in particular the viscosity of the liquid, the number and the shape of the grooves (which however always have a logarithmic shape) and the speed of rotation (which is imposed here by the engine working substantially at constant speed).
  • the impeller tends to stop in a position which applies the disc 22 against the disc 23 and the disc 25 against the disc 24 thus ensuring a satisfactory although partial seal, because the spiral grooves constitute alois as many leakage conduits, however, having a high pressure drop due both to their elongation thanks to the spiral shape and their very shallow depth.
  • one or more channels 42 can be provided ensuring a sufficient liquid supply. when the engine starts.
  • the shaft sealing means described also serves to receive the axial thrust exerted on the impeller, thus eliminating any other provision for this purpose.
  • FIG. 3 which is an improved version of FIG. 1, a paddle wheel 30, mounted on a shaft 32 is equipped, on the side of the shaft outlet, with a pair of discs 33 and 34; the disc 33 is smooth and extends over a fairly large radial extension of the wheel 30 from the periphery of the shaft 32.
  • the spiral disc has a lesser radial extension and is located opposite a outer peripheral part of the disc 33.
  • an annular groove 36 coaxial with the shaft 32 into which opens a conduit 37 connected to a source gas outside.
  • a paddle wheel 42 is here fitted, on the shaft outlet side 43, with a smooth rotating disc 44 with large radial extension, while a casing wall 45 is here fitted of a grooved disc 46 extending radially over a radially outer part of the disk 44, while facing the remaining radially inner part 44 'of smooth disc 44 is formed, on the casing wall 45, a smooth surface 47 ensuring a good seal when the pump stops, the parts 46 and 47 being separated by a groove 48.
  • this bearing 47 can be mena radially outside the spiral grooved disc 46 as shown in 47 '.
  • the invention applies to all impeller pumps, or turbopumps for conveying liquids, and more particularly cryogenic liquids.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP78400182A 1977-11-22 1978-11-15 Pumpe Expired EP0002157B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7735036 1977-11-22
FR7735036A FR2409406A1 (fr) 1977-11-22 1977-11-22 Procede de realisation des etancheites interne et de sortie d'arbre d'une pompe et pompe mettant en oeuvre ce procede

Publications (2)

Publication Number Publication Date
EP0002157A1 true EP0002157A1 (de) 1979-05-30
EP0002157B1 EP0002157B1 (de) 1980-10-29

Family

ID=9197885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78400182A Expired EP0002157B1 (de) 1977-11-22 1978-11-15 Pumpe

Country Status (6)

Country Link
US (1) US4242039A (de)
EP (1) EP0002157B1 (de)
JP (1) JPS5478509A (de)
DE (1) DE2860265D1 (de)
FR (1) FR2409406A1 (de)
IT (1) IT1100276B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102588304A (zh) * 2012-02-10 2012-07-18 宁波大叶园林设备有限公司 旋涡喷嘴发动机直联有高速函数叶轮及偶旋迷宫的离心泵
CN110410357A (zh) * 2018-04-27 2019-11-05 爱信精机株式会社 泵

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JPS5827887A (ja) * 1981-08-11 1983-02-18 Sugino Mach:Kk 水中水圧モ−タ
JPS6014615A (ja) 1983-07-06 1985-01-25 Ebara Corp スラスト軸受およびその製造方法
US4806080A (en) * 1983-07-06 1989-02-21 Ebara Corporation Pump with shaftless impeller
JPS60158316A (ja) * 1984-01-30 1985-08-19 Osaka Gas Co Ltd タ−ビン式流量計
US4613281A (en) * 1984-03-08 1986-09-23 Goulds Pumps, Incorporated Hydrodynamic seal
DE3600126A1 (de) * 1986-01-04 1987-07-16 Fortuna Werke Maschf Ag Geblaese zum umwaelzen grosser gasmengen, insbesondere fuer hochleistungs-laser
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US5209652A (en) * 1991-12-06 1993-05-11 Allied-Signal, Inc. Compact cryogenic turbopump
US5312224A (en) * 1993-03-12 1994-05-17 International Business Machines Corporation Conical logarithmic spiral viscosity pump
JPH08232892A (ja) * 1995-02-27 1996-09-10 Unisia Jecs Corp クローズド型ポンプ
US5947703A (en) * 1996-01-31 1999-09-07 Ntn Corporation Centrifugal blood pump assembly
US6132186A (en) * 1997-08-06 2000-10-17 Shurflo Pump Manufacturing Co. Impeller pump driven by a dynamo electric machine having a stator comprised of a mass of metal particles
US6034465A (en) * 1997-08-06 2000-03-07 Shurfle Pump Manufacturing Co. Pump driven by brushless motor
ITMI981112A1 (it) * 1998-05-20 1999-11-20 Termomeccanica S P A Pompa centrifuga a tenuta radiale
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ITMI990626U1 (it) * 1999-10-15 2001-04-15 Termomeccanica S P A Pompa bilanciata con aspirazione e mandata sullo stesso asse
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DE20013350U1 (de) * 2000-08-03 2000-12-28 Assoma Inc Pumpe
ITMI20010593A1 (it) * 2001-03-21 2002-09-21 Umberto Cambiaghi Pompa centrifuga verticale orizzontale a spinta assiale autoequilibrata
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US7470392B2 (en) 2003-07-14 2008-12-30 Cooper Paul V Molten metal pump components
US20050013715A1 (en) 2003-07-14 2005-01-20 Cooper Paul V. System for releasing gas into molten metal
US7402276B2 (en) 2003-07-14 2008-07-22 Cooper Paul V Pump with rotating inlet
US7906068B2 (en) 2003-07-14 2011-03-15 Cooper Paul V Support post system for molten metal pump
WO2005024230A2 (en) * 2003-09-04 2005-03-17 University Of Utah Research Foundation Rotary centrifugal and viscous pumps
EP1753344B1 (de) 2004-06-08 2011-12-28 Phil Durango Llc Tourniquet manschette
US7631497B2 (en) * 2005-04-21 2009-12-15 Borgwarner Inc. Turbine heat shield with ribs
US8613884B2 (en) 2007-06-21 2013-12-24 Paul V. Cooper Launder transfer insert and system
US8337746B2 (en) 2007-06-21 2012-12-25 Cooper Paul V Transferring molten metal from one structure to another
US9643247B2 (en) 2007-06-21 2017-05-09 Molten Metal Equipment Innovations, Llc Molten metal transfer and degassing system
US9156087B2 (en) 2007-06-21 2015-10-13 Molten Metal Equipment Innovations, Llc Molten metal transfer system and rotor
US9410744B2 (en) 2010-05-12 2016-08-09 Molten Metal Equipment Innovations, Llc Vessel transfer insert and system
US8366993B2 (en) 2007-06-21 2013-02-05 Cooper Paul V System and method for degassing molten metal
US9205490B2 (en) 2007-06-21 2015-12-08 Molten Metal Equipment Innovations, Llc Transfer well system and method for making same
US9409232B2 (en) 2007-06-21 2016-08-09 Molten Metal Equipment Innovations, Llc Molten metal transfer vessel and method of construction
EP2218998B1 (de) * 2009-02-03 2012-12-19 Ipsen, Inc. Dichtungsmechanismus für einen Vakuumwärmebehandlungsofen
US8449814B2 (en) 2009-08-07 2013-05-28 Paul V. Cooper Systems and methods for melting scrap metal
US8524146B2 (en) 2009-08-07 2013-09-03 Paul V. Cooper Rotary degassers and components therefor
US10428821B2 (en) 2009-08-07 2019-10-01 Molten Metal Equipment Innovations, Llc Quick submergence molten metal pump
US8444911B2 (en) 2009-08-07 2013-05-21 Paul V. Cooper Shaft and post tensioning device
US8535603B2 (en) 2009-08-07 2013-09-17 Paul V. Cooper Rotary degasser and rotor therefor
US8714914B2 (en) 2009-09-08 2014-05-06 Paul V. Cooper Molten metal pump filter
US9108244B2 (en) 2009-09-09 2015-08-18 Paul V. Cooper Immersion heater for molten metal
CN109185163A (zh) * 2010-07-21 2019-01-11 Itt制造企业有限责任公司 用于旋转固体处理装备的磨损减少装置
FR2964425B1 (fr) * 2010-09-03 2014-02-14 Snecma Turbopompe, en particulier pour l'alimentation de moteurs de fusee
US8834028B2 (en) * 2011-12-22 2014-09-16 Energy Recovery, Inc. Debris resistant thrust bearing assembly for high speed hydraulic centrifugal turbines and pumps
JP6153609B2 (ja) * 2012-07-10 2017-06-28 ボーグワーナー インコーポレーテッド 排気ガスターボチャージャ
US9903383B2 (en) 2013-03-13 2018-02-27 Molten Metal Equipment Innovations, Llc Molten metal rotor with hardened top
US9011761B2 (en) 2013-03-14 2015-04-21 Paul V. Cooper Ladle with transfer conduit
US10052688B2 (en) 2013-03-15 2018-08-21 Molten Metal Equipment Innovations, Llc Transfer pump launder system
CN103603823B (zh) * 2013-11-15 2016-01-13 广东技术师范学院 一种渣浆泵叶轮的支撑传动装置
DE102014000765A1 (de) * 2014-01-24 2015-07-30 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Elektromotorische Wasserpumpe
US10138892B2 (en) 2014-07-02 2018-11-27 Molten Metal Equipment Innovations, Llc Rotor and rotor shaft for molten metal
DE102014110078A1 (de) * 2014-07-17 2016-01-21 Pfeiffer Vacuum Gmbh Vakuumsystem
US10947980B2 (en) 2015-02-02 2021-03-16 Molten Metal Equipment Innovations, Llc Molten metal rotor with hardened blade tips
RU2623596C2 (ru) * 2015-12-02 2017-06-28 Открытое акционерное общество "Красногорский завод "Электродвигатель" Электроцентробежный насос
US10267314B2 (en) 2016-01-13 2019-04-23 Molten Metal Equipment Innovations, Llc Tensioned support shaft and other molten metal devices
RU2665740C1 (ru) * 2017-02-13 2018-09-04 Акционерное общество "Красногорский завод "Электродвигатель" Электроцентробежный насос
US11149747B2 (en) 2017-11-17 2021-10-19 Molten Metal Equipment Innovations, Llc Tensioned support post and other molten metal devices
CN108825549B (zh) * 2018-05-02 2020-03-31 江苏大学 一种具有机翼型导流叶片的离心泵径向密封环
CN108757546B (zh) * 2018-05-02 2020-05-01 江苏大学 一种具有平板型导流叶片的离心泵径向密封环
CN108869384B (zh) * 2018-05-02 2020-05-05 江苏大学 一种具有圆柱型导流叶片的离心泵径向密封环
US20200360990A1 (en) 2019-05-17 2020-11-19 Molten Metal Equipment Innovations, Llc Molten Metal Transfer System and Method
US11873845B2 (en) 2021-05-28 2024-01-16 Molten Metal Equipment Innovations, Llc Molten metal transfer device

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FR2296124A1 (fr) * 1974-12-24 1976-07-23 Warman Int Ltd Agencement de coussinet restricteur a centrage automatique

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FR2296124A1 (fr) * 1974-12-24 1976-07-23 Warman Int Ltd Agencement de coussinet restricteur a centrage automatique

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102588304A (zh) * 2012-02-10 2012-07-18 宁波大叶园林设备有限公司 旋涡喷嘴发动机直联有高速函数叶轮及偶旋迷宫的离心泵
CN102588304B (zh) * 2012-02-10 2014-04-16 宁波大叶园林设备有限公司 旋涡喷嘴发动机直联有高速函数叶轮及偶旋迷宫的离心泵
CN110410357A (zh) * 2018-04-27 2019-11-05 爱信精机株式会社 泵

Also Published As

Publication number Publication date
US4242039A (en) 1980-12-30
FR2409406A1 (fr) 1979-06-15
DE2860265D1 (en) 1981-01-29
IT1100276B (it) 1985-09-28
EP0002157B1 (de) 1980-10-29
JPS5478509A (en) 1979-06-22
IT7829714A0 (it) 1978-11-13

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