EP0002157B1 - Pumpe - Google Patents
Pumpe Download PDFInfo
- Publication number
- EP0002157B1 EP0002157B1 EP78400182A EP78400182A EP0002157B1 EP 0002157 B1 EP0002157 B1 EP 0002157B1 EP 78400182 A EP78400182 A EP 78400182A EP 78400182 A EP78400182 A EP 78400182A EP 0002157 B1 EP0002157 B1 EP 0002157B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- disk
- helical grooves
- shaft
- wheel
- pump
- 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.)
- Expired
Links
- 238000007789 sealing Methods 0.000 claims description 19
- 230000010355 oscillation Effects 0.000 claims 3
- 239000007788 liquid Substances 0.000 description 14
- 230000000694 effects Effects 0.000 description 11
- 238000005086 pumping Methods 0.000 description 6
- 210000003027 ear inner Anatomy 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007792 gaseous phase Substances 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 230000008646 thermal stress Effects 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
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 on the other hand radially in a wheel runout with radial extension running opposite a tangential discharge duct.
- French patent 1,505,487 has already proposed a pump having a motor shaft mounted in a pump housing, with, on the shaft outlet side, sealing means with pair of disks facing coaxial and at the lowest axial distance from each other, one fixed and integral with the casing and the other movable in rotation and mounted with axial movement on said shaft, one of said discs having spiral grooves, the other being smooth .
- Such a rotary junction sealing means has a definite advantage because the liquid layer which is interposed between the discs not only seals but also durably reduces the wear of the moving parts relative to one another. 'other.
- An object of the invention is to provide seals for a particular pump which are particularly effective in that they certainly avoid undesirable leaks, which improves the yield, and which moreover have almost zero wear by friction. , 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 being of the paddle wheel type mounted at the end of said shaft, each blade forming a conduit extending on one side in an axial wheel body and opening out opposite '' a suction duct and on the other side radially in a wheel runout with radial extension running past a tangential delivery duct, the movable disc in rotation of said first rotation means is integral with the wheel runout and in that the axial clearance is due to mounting with limited axial clearance of the wheel on the shaft and in that said pump is equipped, at its suction side, with a second sealing means with double coaxial discs and facing each other, one with spiral grooves, the other smooth, one of which is mounted at the end of said axial wheel body and the other at the end of a medium-blast fixed to the casing around the suction duct.
- the start-up of a cryogenic pump is made easier and faster thanks to the hydrodynamic junctions described.
- the shafts of the motor and of the pump may not be aligned as rigorously as in conventional motor-pump units and it is even possible, if desired, to remove the support of the pump by the engine block, which reduces thermal 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, an impeller 5 forming a plurality of vanes constituted by identical conduits 6 arranged around the shaft 1 and having an axial suction part 7 in a wheel body 5 ′ located in the vicinity of the shaft 1 and a radial delivery part 8 in a wheel run 5 "with radial extension.
- the suction parts 7 open out view of a casing opening 9 on which is fixed, by flange 10, a suction duct 11 ..
- the discharge parts 8 open into the pump casing 4 while scrolling 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 towards the outside (according to arrow f a ), the other sealing means, generally designated by 18, is located “suction side" 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 disc 24 secured to the impeller 5 since the disc 24 secured to the impeller 5 is not only movable in rotation, but also undergoes axial displacements equal and consistent with those of the disc 22, that is to say in a direction which is opposite to that desired for the disc 24 opposite of the disc 25, the latter disc is provided with a fairly large clearance thanks to the presence of the bellows 28. It is specified that it is only when the pump is stopped, when the impeller 5 stops rotating that the discs 22 and 23 on the one hand, 24 and 25 on the other hand must approach each other until they come to bear face to face.
- the rotating disc 22 (or 24) has a face opposite the other disc, which is completely smooth, while in the face of the 'another disc 23 or 25 respectively which is fixed in rotation has been made a plurality of grooves in the form of spirals 40 (see Figure 2) of depth equal to a few hundredths of a millimeter, releasing between them, an equal number of projecting spans in spirals 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 since the internal periphery (where this pressure is equal to the suction pressure) towards 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 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 sealing, because the spiral grooves then constitute 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 sufficient liquid intake at start-up.
- 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 external source of gas.
- a paddle wheel 49 is here fitted, on the shaft outlet side 43, with a smooth rotary 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 smooth disc 44, while facing the remaining radially inner part 44 'of smooth disc 44 is formed, on the casing wall 45, a bearing smooth 47 ensuring a good seal when the pump is stopped, the parts 46 and 47 being separated by a groove 48. This gives a better seal when the pump stops by pressing face against face of the radially inner part 44 'of the disc 44 and the bearing 47.
- this bearing 47 may be arranged radially outside the disc with spiral grooves 46 as indicated at 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)
Claims (8)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
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 |
FR7735036 | 1977-11-22 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0002157A1 EP0002157A1 (de) | 1979-05-30 |
EP0002157B1 true 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 (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3939156A1 (de) * | 1989-11-27 | 1991-05-29 | Grundfos Int | Zusammengesetztes laufrad fuer eine kreiselpumpe |
Families Citing this family (67)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5827887A (ja) * | 1981-08-11 | 1983-02-18 | Sugino Mach:Kk | 水中水圧モ−タ |
US4806080A (en) * | 1983-07-06 | 1989-02-21 | Ebara Corporation | Pump with shaftless impeller |
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 |
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 |
US4944653A (en) * | 1988-03-24 | 1990-07-31 | Jacuzzi, Inc. | Plastic centrifugal pump |
US4913619A (en) * | 1988-08-08 | 1990-04-03 | Barrett Haentjens & Co. | Centrifugal pump having resistant components |
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 |
US6034465A (en) * | 1997-08-06 | 2000-03-07 | Shurfle Pump Manufacturing Co. | Pump driven by brushless motor |
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 |
ITMI981112A1 (it) * | 1998-05-20 | 1999-11-20 | Termomeccanica S P A | Pompa centrifuga a tenuta radiale |
US6074166A (en) * | 1998-10-01 | 2000-06-13 | Moddemeijer; Pieter J. H. | Pump |
ITMI990626U1 (it) * | 1999-10-15 | 2001-04-15 | Termomeccanica S P A | Pompa bilanciata con aspirazione e mandata sullo stesso asse |
US6290467B1 (en) * | 1999-12-03 | 2001-09-18 | American Standard International Inc. | Centrifugal impeller assembly |
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 |
US20050013715A1 (en) | 2003-07-14 | 2005-01-20 | Cooper Paul V. | System for releasing gas into molten metal |
US7470392B2 (en) | 2003-07-14 | 2008-12-30 | Cooper Paul V | Molten metal pump components |
US7402276B2 (en) | 2003-07-14 | 2008-07-22 | Cooper Paul V | Pump with rotating inlet |
US20070253807A1 (en) | 2006-04-28 | 2007-11-01 | Cooper Paul V | Gas-transfer foot |
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 |
CA2742183A1 (en) | 2004-06-08 | 2005-12-29 | Phil Durango, Llc | Tourniquet and method of use |
US7631497B2 (en) * | 2005-04-21 | 2009-12-15 | Borgwarner Inc. | Turbine heat shield with ribs |
US9409232B2 (en) | 2007-06-21 | 2016-08-09 | Molten Metal Equipment Innovations, Llc | Molten metal transfer vessel and method of construction |
US8366993B2 (en) | 2007-06-21 | 2013-02-05 | Cooper Paul V | System and method for degassing molten metal |
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 |
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 |
US9205490B2 (en) | 2007-06-21 | 2015-12-08 | Molten Metal Equipment Innovations, Llc | Transfer well system and method for making same |
US9643247B2 (en) | 2007-06-21 | 2017-05-09 | Molten Metal Equipment Innovations, Llc | Molten metal transfer and degassing system |
EP2218998B1 (de) * | 2009-02-03 | 2012-12-19 | Ipsen, Inc. | Dichtungsmechanismus für einen Vakuumwärmebehandlungsofen |
US8535603B2 (en) * | 2009-08-07 | 2013-09-17 | Paul V. Cooper | Rotary degasser and rotor therefor |
US8524146B2 (en) | 2009-08-07 | 2013-09-03 | Paul V. Cooper | Rotary degassers and components therefor |
US8449814B2 (en) | 2009-08-07 | 2013-05-28 | Paul V. Cooper | Systems and methods for melting scrap metal |
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 |
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 |
BR112013001314A2 (pt) * | 2010-07-21 | 2016-05-17 | Itt Mfg Entpr Llc | dispositivo de redução de desgaste para equipamentos rotativos de manuseio de sólidos |
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 |
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 |
WO2014011467A1 (en) * | 2012-07-10 | 2014-01-16 | Borgwarner Inc. | Exhaust-gas turbocharger |
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 |
JP7124422B2 (ja) * | 2018-04-27 | 2022-08-24 | 株式会社アイシン | ポンプ |
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 |
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 |
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 |
US11931802B2 (en) | 2019-05-17 | 2024-03-19 | Molten Metal Equipment Innovations, Llc | Molten metal controlled flow launder |
US11873845B2 (en) | 2021-05-28 | 2024-01-16 | Molten Metal Equipment Innovations, Llc | Molten metal transfer device |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE370787A (de) * | ||||
DE708593C (de) * | 1939-06-29 | 1941-07-24 | Amag Hilpert Pegnitzhuette Akt | Kreiselpumpe mit entlasteter Stopfbuechse |
US3137237A (en) * | 1961-08-22 | 1964-06-16 | Wilfley & Sons Inc A | Pump sealing apparatus |
FR1505487A (fr) * | 1966-10-28 | 1967-12-15 | Guinard Pompes | Perfectionnement aux joints tournants à régulation de fuite |
NL6617168A (de) * | 1966-12-07 | 1968-06-10 | ||
US3578874A (en) * | 1968-09-26 | 1971-05-18 | Dominion Eng Works Ltd | Removable runner seal |
US3535051A (en) * | 1968-12-03 | 1970-10-20 | Ellicott Machine Corp | Recessed expeller vanes |
AU8739075A (en) * | 1974-12-24 | 1977-06-16 | Warman Int Ltd | Self centring festrictor bush |
-
1977
- 1977-11-22 FR FR7735036A patent/FR2409406A1/fr not_active Withdrawn
-
1978
- 1978-11-13 IT IT29714/78A patent/IT1100276B/it active
- 1978-11-15 US US05/962,032 patent/US4242039A/en not_active Expired - Lifetime
- 1978-11-15 DE DE7878400182T patent/DE2860265D1/de not_active Expired
- 1978-11-15 EP EP78400182A patent/EP0002157B1/de not_active Expired
- 1978-11-17 JP JP14124378A patent/JPS5478509A/ja active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3939156A1 (de) * | 1989-11-27 | 1991-05-29 | Grundfos Int | Zusammengesetztes laufrad fuer eine kreiselpumpe |
Also Published As
Publication number | Publication date |
---|---|
EP0002157A1 (de) | 1979-05-30 |
IT1100276B (it) | 1985-09-28 |
DE2860265D1 (en) | 1981-01-29 |
US4242039A (en) | 1980-12-30 |
FR2409406A1 (fr) | 1979-06-15 |
IT7829714A0 (it) | 1978-11-13 |
JPS5478509A (en) | 1979-06-22 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Designated state(s): BE CH DE FR GB LU NL SE |
|
17P | Request for examination filed | ||
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Designated state(s): BE CH DE FR GB LU NL SE |
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