CH669641A5 - - Google Patents
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- Publication number
- CH669641A5 CH669641A5 CH4982/86A CH498286A CH669641A5 CH 669641 A5 CH669641 A5 CH 669641A5 CH 4982/86 A CH4982/86 A CH 4982/86A CH 498286 A CH498286 A CH 498286A CH 669641 A5 CH669641 A5 CH 669641A5
- Authority
- CH
- Switzerland
- Prior art keywords
- stator
- high pressure
- capacity
- piston
- orifice
- Prior art date
Links
- 238000002955 isolation Methods 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 5
- 230000001105 regulatory effect Effects 0.000 claims 1
- 230000000694 effects Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/044—Active magnetic bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
-
- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
- F04D29/0516—Axial thrust balancing balancing pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C39/00—Relieving load on bearings
- F16C39/04—Relieving load on bearings using hydraulic or pneumatic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/50—Bearings
- F05D2240/51—Magnetic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/50—Bearings
- F05D2240/52—Axial thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/42—Pumps with cylinders or pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/44—Centrifugal pumps
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
DESCRIPTION DESCRIPTION
La présente invention concerne une turbomachine du type comprenant un rotor comportant un arbre muni d'au moins une roue et un stator entourant le rotor et comportant une extrémité basse pression munie d'un orifice et une extrémité haute pression munie d'un orifice, ledit arbre ayant une première extrémité située dans le stator et soumise à l'une des deux dites pressions et une seconde extrémité sortant du stator à travers un joint d'étanchéité, turbomachine comprenant un piston d'équilibrage axial situé sur l'arbre à l'intérieur du stator et dont deux faces opposées sont soumises à des pressions différentes. The present invention relates to a turbomachine of the type comprising a rotor comprising a shaft provided with at least one wheel and a stator surrounding the rotor and comprising a low pressure end provided with an orifice and a high pressure end provided with an orifice, said shaft having a first end located in the stator and subjected to one of said two pressures and a second end leaving the stator through a seal, turbomachine comprising an axial balancing piston located on the shaft at inside the stator and two opposite faces of which are subjected to different pressures.
On sait que, dans ce genre de machine, il existe un «effet de fond» qui est un effort axial supporté par une butée. Dans le cas particulier d'un compresseur centrifuge à une roue et dont l'arbre comporte une première extrémité dans le stator du côté de la basse pression et dont l'autre extrémité, extérieure au stator, est soumise à la pression atmosphérique, cet effort axial F est alors schématique-ment donné par la relation: We know that, in this kind of machine, there is a "bottom effect" which is an axial force supported by a stop. In the particular case of a centrifugal compressor with one wheel and whose shaft has a first end in the stator on the low pressure side and whose other end, outside the stator, is subjected to atmospheric pressure, this effort axial F is then schematically given by the relation:
F = (Po - Pa) Si — (pf — p„) S2 relation dans laquelle p0 représente la basse pression, pf la haute pression, pa la pression atmosphérique, Si la section de l'arbre au niveau de l'étanchéité de sortie d'arbre et S2 la section différentielle entre la section correspondant à l'entrée dans la roue, côté basse pression, et la section du piston d'équilibrage. F = (Po - Pa) Si - (pf - p „) S2 relation in which p0 represents the low pressure, pf the high pressure, pa the atmospheric pressure, If the section of the shaft at the outlet seal shaft and S2 the differential section between the section corresponding to the entry in the wheel, low pressure side, and the section of the balancing piston.
En choisissant correctement le diamètre du piston d'équilibrage, on peut ainsi faire en sorte que cet effet de fond supporté par la butée soit acceptable. Cependant, à l'arrêt de la machine, le piston d'équilibrage n'a plus d'effet car, très rapidement, pf et p0 s'équilibrent pour s'établir à une pression de circuit pc, et l'on a alors By correctly choosing the diameter of the balancing piston, it is thus possible to ensure that this background effect supported by the stop is acceptable. However, when the machine stops, the balancing piston no longer has any effect because, very quickly, pf and p0 equilibrate to establish themselves at a circuit pressure pc, and we then have
F = (pc — pa) Sl5 effort qui peut être très important si la pression du circuit pc est très élevée. F = (pc - pa) Sl5 effort which can be very important if the pressure of the pc circuit is very high.
Cela conduit à prévoir un dimensionnement de butée non pas calculé pour le fonctionnement de la machine à son régime nominal, mais au contraire lors de ses mises en marche ou arrêts; cela peut conduire aussi à une impossibilité d'utilisation de butées à gaz ou magnétiques qui n'acceptent que des charges modérées, ainsi qu'à une limitation de l'emploi des machines en porte à faux ou à paliers intégrés. This leads to providing a stop dimensioning not calculated for the operation of the machine at its nominal speed, but on the contrary when it is started or stopped; this can also lead to the impossibility of using gas or magnetic stops which accept only moderate loads, as well as to a limitation of the use of machines with cantilever or integrated bearings.
La présente invention a pour but de pallier cet inconvénient et a pour objet une turbomachine du type défini ci-dessus, caractérisée en ce que ledit piston d'équilibrage est étagé sur deux diamètres distincts, un dispositif d'étanchéité rotatif étant disposé au niveau de chaque diamètre du piston entre le piston et le stator, une cavité intermédiaire interne au stator étant aménagée entre les deux dispositifs d'étanchéité, en ce qu'une conduite relie ladite cavité intermédiaire à une capacité liée à ladite haute pression et en ce qu'une vanne d'isolement permet d'obturer la communication entre ladite capacité et l'orifice de l'extrémité correspondante du stator. The present invention aims to overcome this drawback and relates to a turbomachine of the type defined above, characterized in that said balancing piston is stepped on two distinct diameters, a rotary sealing device being arranged at each diameter of the piston between the piston and the stator, an intermediate cavity internal to the stator being provided between the two sealing devices, in that a pipe connects said intermediate cavity to a capacity linked to said high pressure and in that an isolation valve makes it possible to close the communication between said capacity and the orifice of the corresponding end of the stator.
On va maintenant donner la description d'un exemple particulier de mise en œuvre de l'invention en se référant au dessin annexé dans lequel: We will now give the description of a particular example of implementation of the invention with reference to the appended drawing in which:
la figure unique montre un compresseur centrifuge selon l'invention. the single figure shows a centrifugal compressor according to the invention.
Le compresseur représenté sur la figure comprend un ensemble mobile ou rotor 1 comportant un arbre 2 munit de quatre roues centrifuges 3,4, 5 et 6. Cet ensemble mobile est situé à l'intérieur d'un stator 7 et est supporté dans ce stator par deux paliers magnétiques 8 et 9, et sa position axiale est fixée par une butée magnétique double 10. Il est muni en outre de deux paliers auxiliaires à billes 11 et 12. The compressor shown in the figure comprises a mobile assembly or rotor 1 comprising a shaft 2 provided with four centrifugal wheels 3, 4, 5 and 6. This mobile assembly is located inside a stator 7 and is supported in this stator by two magnetic bearings 8 and 9, and its axial position is fixed by a double magnetic stop 10. It is also provided with two auxiliary ball bearings 11 and 12.
Le stator 7 comporte une extrémité basse pression constituant, dans l'exemple particulier décrit, l'entrée ou l'aspiration, munie d'un orifice d'aspiration 13, et une extrémité haute pression, ou refoulement, munie d'un orifice de refoulement 14. The stator 7 has a low pressure end constituting, in the particular example described, the inlet or suction, provided with a suction port 13, and a high pressure end, or discharge, provided with a port return 14.
Comme on le voit sur la figure, l'extrémité de l'arbre située à droite, c'est-à-dire du côté aspiration, est située à l'intérieur du stator 7 et est soumise à la pression d'aspiration, tandis que l'extrémité de l'arbre située à gauche, du côté de la haute pression, traverse le stator à travers un joint d'étanchéité 15 et est soumise à la pression extérieure. As can be seen in the figure, the end of the shaft situated on the right, that is to say on the suction side, is located inside the stator 7 and is subjected to the suction pressure, while that the end of the shaft located on the left, on the high pressure side, crosses the stator through a seal 15 and is subjected to external pressure.
Du côté de l'extrémité haute pression, au-delà de la dernière roue 6, l'arbre 2 porte un piston d'équilibrage 16 dont la face 17 la plus éloignée de l'extrémité basse pression 13 est soumise à cette basse pression par une canalisation 18 reliant l'extrémité basse pression à une capacité 19 communiquant avec cette face 17. On the side of the high pressure end, beyond the last wheel 6, the shaft 2 carries a balancing piston 16, the face 17 furthest from the low pressure end 13 is subjected to this low pressure by a pipe 18 connecting the low pressure end to a capacity 19 communicating with this face 17.
Le piston d'équilibrage 16 est étagé sur deux diamètres distincts 0A et 0B dont le plus grand, 0B, est situé du côté du piston le plus proche de l'extrémité basse pression. The balancing piston 16 is stepped on two separate diameters 0A and 0B, the largest of which, 0B, is located on the side of the piston closest to the low pressure end.
Un dispositif d'étanchéité, respectivement 20 et 21, est situé au droit de chacun de ces deux diamètres 0A et 0B du piston 16, entre le piston et le stator. Une cavité intermédiaire 22 du stator est située entre ces deux étanchéités. Cette cavité est reliée par une conduite 23 à une capacité à haute pression 24 constituée, par exemple, par le circuit haute pression auquel est relié l'orifice de refoulement 14. Ainsi, l'épaulement 25 reliant les deux diamètres du piston est soumis à la pression de ce circuit haute pression 24. A sealing device, respectively 20 and 21, is located to the right of each of these two diameters 0A and 0B of the piston 16, between the piston and the stator. An intermediate cavity 22 of the stator is located between these two seals. This cavity is connected by a pipe 23 to a high pressure capacity 24 constituted, for example, by the high pressure circuit to which the discharge port 14 is connected. Thus, the shoulder 25 connecting the two diameters of the piston is subjected to the pressure of this high pressure circuit 24.
La sortie haute pression 14 est munie d'une vanne d'isolement 26 permettant d'obturer l'extrémité haute pression. The high pressure outlet 14 is provided with an isolation valve 26 for closing the high pressure end.
L'orifice d'aspiration 13 est relié à un circuit basse pression 27 dans lequel aspire le compresseur. The suction port 13 is connected to a low pressure circuit 27 in which the compressor is aspirated.
En fonctionnement, la vanne 26 est ouverte, la basse pression à l'aspiration est par exemple de 30 bar et la haute pression au refoulement de 60 bar. Tout se passe comme si l'on avait un piston d'équilibrage 16 de diamètre 0A soumis à la basse pression de 30 bar. Le labyrinthe 21 est soumis des deux côtés à la même pression — haute pression de 60 bar — et ne joue donc aucun rôle en fonctionnement normal de la machine. In operation, the valve 26 is open, the low suction pressure is for example 30 bar and the high discharge pressure 60 bar. Everything happens as if we had a balancing piston 16 of diameter 0A subjected to the low pressure of 30 bar. The labyrinth 21 is subjected on both sides to the same pressure - high pressure of 60 bar - and therefore plays no role in normal operation of the machine.
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Lors de la commande d'arrêt du compresseur, la vanne 26 est fermée et très rapidement la pression de refoulement en amont de la vanne décroît pour arriver à la valeur de la pression de l'aspiration voisine de 30 bar à l'arrêt. When the compressor stop command is given, the valve 26 is closed and very quickly the discharge pressure upstream of the valve decreases to arrive at the value of the suction pressure close to 30 bar when stopped.
Cependant, grâce au labyrinthe 21, la cavité intermédiaire 22 se 5 maintient à la haute pression voisine de 60 bar pendant toute la durée du ralentissement jusqu'à l'arrêt. However, thanks to the labyrinth 21, the intermediate cavity 22 is maintained at the high pressure close to 60 bar for the entire duration of the deceleration until stopping.
On bénéficie donc ainsi d'un gain de pression proche de 60 — 30 bar = 30 bar, qui s'exerce sur la surface de l'épaulement 25, générant une force s'opposant à l'effet de fond. 10 There is thus a pressure gain close to 60 - 30 bar = 30 bar, which is exerted on the surface of the shoulder 25, generating a force opposing the bottom effect. 10
Compte tenu du diamètre de l'arbre, il suffit de calculer convenablement la surface de cet épaulement 25, donc les diamètres 0A et 0B, pour que l'effort axial sur la butée 10 soit raisonnable. Given the diameter of the shaft, it suffices to calculate the surface of this shoulder 25 properly, therefore the diameters 0A and 0B, so that the axial force on the stop 10 is reasonable.
Si on calcule l'effort axial F en prenant, comme dans le cas de l'art antérieur cité, l'hypothèse d'un compresseur centrifuge à une 15 seule roue, on obtient la relation: If the axial force F is calculated by taking, as in the case of the cited prior art, the hypothesis of a centrifugal compressor with a single wheel, the relationship is obtained:
F = S! (p„-pa) - SBA (Pf-Po) - S3 (pf-p„) F = S! (p „-pa) - SBA (Pf-Po) - S3 (pf-p„)
relation dans laquelle p„ est la pression d'aspiration, pf la pression de refoulement et pa la pression atmosphérique, Sj la section de l'arbre 20 au niveau de l'étanchéité, SBA la section différentielle entre la section du piston de diamètre 0A et la section du piston de diamètre 0B, et relation in which p „is the suction pressure, pf the discharge pressure and pa the atmospheric pressure, Sj the section of the shaft 20 at the seal, SBA the differential section between the section of the piston of diameter 0A and the cross section of the piston of diameter 0B, and
S3 la section différentielle entre la section d'aspiration et la section du piston de diamètre 0B. S3 the differential section between the suction section and the piston section of diameter 0B.
D'après cette relation, on voit qu'à l'arrêt le terme S3 (pr—p0) s'annule rapidement à cause de la décroissance rapide de pf, tandis que le terme SBA (pr—p0) reste sensiblement constant, car la face 25 du piston est toujours soumise à une pression voisine de pf (haute pression). According to this relation, we see that at standstill the term S3 (pr — p0) vanishes quickly because of the rapid decrease in pf, while the term SBA (pr — p0) remains substantially constant, because the face 25 of the piston is always subjected to a pressure close to pf (high pressure).
Le dispositif s'applique également pour soulager la butée au démarrage à condition de disposer d'un circuit haute pression 24. Si le circuit sur lequel est installé le compresseur n'est pas naturellement en pression, il suffit de disposer d'une capacité auxiliaire à haute pression contenant le volume nécessaire de fluide sous pression pour assurer le démarrage. The device also applies to relieve the starting stop on the condition of having a high pressure circuit 24. If the circuit on which the compressor is installed is not naturally under pressure, it suffices to have an auxiliary capacity at high pressure containing the necessary volume of pressurized fluid to ensure start-up.
La conduite 23 peut être munie d'une vanne 28 de régulation de pression commandée en fonction de la mesure de la poussée axiale, permettant ainsi de moduler la pression dans la cavité intermédiaire 22. Line 23 can be provided with a pressure regulation valve 28 controlled as a function of the measurement of the axial thrust, thus making it possible to modulate the pressure in the intermediate cavity 22.
De même, on peut avoir un circuit de by-pass 29 muni d'une vanne ou d'un clapet pilote 30 reliant l'aspiration au refoulement en 31 avant la vanne d'isolement 26 et permettant d'éviter le pompage dans la séquence transitoire de démarrage ou d'arrêt. Likewise, there may be a bypass circuit 29 provided with a pilot valve 30 connecting the suction to the discharge at 31 before the isolation valve 26 and making it possible to avoid pumping in the sequence transient start or stop.
R R
1 feuille dessin 1 drawing sheet
Claims (4)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR8600180A FR2592688B1 (en) | 1986-01-08 | 1986-01-08 | TURBOMACHINE. |
Publications (1)
Publication Number | Publication Date |
---|---|
CH669641A5 true CH669641A5 (en) | 1989-03-31 |
Family
ID=9330908
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CH4982/86A CH669641A5 (en) | 1986-01-08 | 1986-12-15 |
Country Status (5)
Country | Link |
---|---|
JP (1) | JPS62189394A (en) |
CH (1) | CH669641A5 (en) |
DE (1) | DE3700153A1 (en) |
FR (1) | FR2592688B1 (en) |
IT (1) | IT1214379B (en) |
Families Citing this family (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU1900888A (en) * | 1987-12-03 | 1989-06-08 | Rockwell International Corporation | Pump hydrostatic bearing assembly |
JPH0676798B2 (en) * | 1988-08-22 | 1994-09-28 | 株式会社荏原製作所 | Centrifugal pump with magnetic bearing |
US5141389A (en) * | 1990-03-20 | 1992-08-25 | Nova Corporation Of Alberta | Control system for regulating the axial loading of a rotor of a fluid machine |
CH684495A5 (en) * | 1991-09-04 | 1994-09-30 | Escher Wyss Ag | Turbomachinery. |
JP3143986B2 (en) * | 1991-10-14 | 2001-03-07 | 株式会社日立製作所 | Single shaft multi-stage centrifugal compressor |
DE4227280C1 (en) * | 1992-08-18 | 1993-08-05 | Siemens Ag, 8000 Muenchen, De | |
US5445494A (en) * | 1993-11-08 | 1995-08-29 | Bw/Ip International, Inc. | Multi-stage centrifugal pump with canned magnetic bearing |
DE4419379A1 (en) * | 1994-05-27 | 1995-12-07 | Mannesmann Ag | Turbocompressor system for gases |
JPH08312582A (en) * | 1995-05-23 | 1996-11-26 | Daikin Ind Ltd | Reversal preventing device for compressor |
US6367241B1 (en) * | 1999-08-27 | 2002-04-09 | Allison Advanced Development Company | Pressure-assisted electromagnetic thrust bearing |
NL1018212C2 (en) † | 2001-06-05 | 2002-12-10 | Siemens Demag Delaval Turbomac | Compressor unit comprising a centrifugal compressor and an electric motor. |
ITMI20011348A1 (en) * | 2001-06-27 | 2002-12-27 | Nuovo Pignone Spa | BALANCING PISTON FOR CENTRIFUGAL COMPRESSORS WITH DIVERGENT CELLETTE SEAL |
ITMI20022337A1 (en) * | 2002-11-05 | 2004-05-06 | Nuovo Pignone Spa | AXIAL THRUST BALANCING ASSEMBLY FOR ONE |
FR2854208B1 (en) * | 2003-04-28 | 2008-02-15 | Thermodyn | COMPRESSOR FOR CENTRIFUGAL COMPRESSOR GROUP TYPE IN DOOR-A-FALSE |
BRPI0504326A (en) * | 2005-10-11 | 2007-06-26 | Brasil Compressores Sa | aerostatic bearing fluid compressor, aerostatic bearing compressor control system and aerostatic bearing compressor control method |
IT1397707B1 (en) * | 2009-12-22 | 2013-01-24 | Nuovo Pignone Spa | DYNAMIC BALANCE OF PUSHING FOR CENTRIFUGAL COMPRESSORS. |
US8878372B2 (en) * | 2010-01-15 | 2014-11-04 | Dresser-Rand Company | Integral compressor-expander |
JP5364684B2 (en) | 2010-12-03 | 2013-12-11 | 三菱重工業株式会社 | Power plant |
JP2013087622A (en) * | 2011-10-13 | 2013-05-13 | Hitachi Plant Technologies Ltd | Pump |
ITCO20120066A1 (en) * | 2012-12-20 | 2014-06-21 | Nuovo Pignone Srl | METHOD TO BALANCE THE PUSH, TURBINE AND ENGINE IN TURBINE |
EP3121450B1 (en) * | 2015-07-23 | 2020-09-02 | Sulzer Management AG | Pump for conveying a fluid with varying viscosity |
IT201600120314A1 (en) | 2016-11-28 | 2018-05-28 | Nuovo Pignone Tecnologie Srl | TURBO-COMPRESSOR AND OPERATING METHOD OF A TURBO-COMPRESSOR |
FR3088684B1 (en) * | 2018-11-21 | 2023-07-28 | Thermodyn | BALANCING AND SEALING PISTON, COOLING CIRCUIT AND ASSOCIATED METHOD |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE289341C (en) * | ||||
GB190916373A (en) * | 1909-07-13 | 1910-07-07 | Emil Schauffelberger | Improvements in and relating to Means for Balancing the End-thrust on the Rotor in Rotary Pumps, Blowers, Compressors and the like. |
US3071076A (en) * | 1959-04-28 | 1963-01-01 | Tiraspolsky Wladimir | Axial pumps |
US3105632A (en) * | 1960-03-14 | 1963-10-01 | Dresser Ind | High pressure centrifugal compressor |
DE2728400A1 (en) * | 1977-06-24 | 1979-01-11 | Bbc Brown Boveri & Cie | GAS TURBINE |
US4170435A (en) * | 1977-10-14 | 1979-10-09 | Swearingen Judson S | Thrust controlled rotary apparatus |
US4413946A (en) * | 1981-08-20 | 1983-11-08 | Dresser Industries, Inc. | Vented compressor inlet guide |
-
1986
- 1986-01-08 FR FR8600180A patent/FR2592688B1/en not_active Expired
- 1986-12-15 CH CH4982/86A patent/CH669641A5/fr not_active IP Right Cessation
-
1987
- 1987-01-05 DE DE19873700153 patent/DE3700153A1/en active Granted
- 1987-01-06 JP JP62000974A patent/JPS62189394A/en active Pending
- 1987-01-07 IT IT8767004A patent/IT1214379B/en active
Also Published As
Publication number | Publication date |
---|---|
JPS62189394A (en) | 1987-08-19 |
IT1214379B (en) | 1990-01-18 |
IT8767004A0 (en) | 1987-01-07 |
FR2592688A1 (en) | 1987-07-10 |
FR2592688B1 (en) | 1988-03-18 |
DE3700153A1 (en) | 1987-07-09 |
DE3700153C2 (en) | 1989-03-09 |
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