EP1473464A1 - Centrifugal compressor of the overhung type - Google Patents

Centrifugal compressor of the overhung type Download PDF

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Publication number
EP1473464A1
EP1473464A1 EP04290914A EP04290914A EP1473464A1 EP 1473464 A1 EP1473464 A1 EP 1473464A1 EP 04290914 A EP04290914 A EP 04290914A EP 04290914 A EP04290914 A EP 04290914A EP 1473464 A1 EP1473464 A1 EP 1473464A1
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EP
European Patent Office
Prior art keywords
compressor
impeller
rotor
pipe
compressor according
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Granted
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EP04290914A
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German (de)
French (fr)
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EP1473464B1 (en
Inventor
Jean-Marc Pugnet
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Thermodyn SAS
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Thermodyn SAS
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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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0516—Axial thrust balancing balancing pistons

Definitions

  • the invention relates to a centrifugal compressor unit and, in particular, a centrifugal compressor for compressor group of the cantilever type.
  • the invention relates to the balancing of the axial thrust of a centrifugal compressor when it is put into service, to allow starting even with a machine left behind pressurized when stopped.
  • a compressor unit of the conventional cantilever type conventionally includes a means motor 10, constituted for example by an electric motor or by a turbine arranged inside a casing 12 and driving in rotation a rotor 14, which is held in position by a set of bearings radial, such as 16, and axial bearings, such as 18.
  • the turbocharger includes a compressor 20.
  • the compressor 20 is a single stage compressor.
  • This compressor includes an impeller 22 driven in rotation by the rotor 14 in a stator 24 ensuring, on the one hand, an increase in pressure static of an incident gas, sucked in the direction represented by the arrow F1 from an intake pipe 26 and, on the other hand, a increase in the kinetic energy of this gas.
  • the gas Downstream of the wheel 22, the gas is collected by an outlet volute 28 in order to channel it, then slow it down, thus turning part of the pressure significant of its kinetic energy, then is delivered at the output of the compressor according to arrow F2.
  • the increase in pressure of the gas in the paddle wheel 22 causes an axial reaction force, directed towards the entry of gas into the wheel. This is why the compressor is provided means for balancing the axial thrust thus generated.
  • compressors are generally kept under pressure when they are stopped.
  • this pressure maintenance of the compressor generates, when stationary, forces on the impeller 22 causing the appearance a resultant force on the rotor, which applies to the packing shaft end sealing, on a surface defined by a diameter seal.
  • the axial thrust balancing means are effective in compensating for the forces exerted on the rotor during operation of the turbocharger, they are ineffective for compensate for the axial thrust exerted on the seal at the end of the shaft, when the compressor stops while the compressor is kept under pressure when stopped.
  • the object of the invention is therefore to overcome this drawback and to supply a compressor for centrifugal compressor group of the type overhang capable of balancing the axial thrust generated on the rotor at compressor stop.
  • the invention therefore relates to a centrifugal compressor for cantilever type compressor unit comprising a set at least one compression impeller mounted on a rotor intended to be rotated by a motor means in a body stator and means for compensating the axial thrust which is generated by the force exerted by the gas on the impeller and which is applied to the rotor.
  • the compensation means are adapted to compensate for the thrust axial supported by the rotor when the compressor stops.
  • the compensation means include means for generate a depression on one of the faces capable of compensating for the less in part said axial thrust.
  • the vacuum is formed on the wheel of the first compression stage.
  • the face on which generates the depression is therefore the suction side of a gas handled by the compressor.
  • the stator body comprises a through pipe opening opposite said face of the wheel.
  • the leading edge of the blades of the impeller has a front flange with an axial annular shoulder delimited by two cylindrical portions of increasing diameter of the edge leading to the trailing edge of the wheel, the pipe emerging opposite this annular shoulder.
  • the pipeline leads to the exterior of the compressor and is advantageously equipped with a pressure regulating device suitable for sealing said pipeline during compressor operation and to open said pipe at compressor stop.
  • FIG 2 there is shown a centrifugal compressor of a compressor unit of the cantilever type.
  • the compressor is a single stage compressor.
  • the invention also applies to the production of a compressor multi-storey, for example two storeys.
  • the compressor portion shown in this figure 2 is intended to be part of a group centrifugal compressor cantilever type compressor, i.e. a group compressor which comprises a motor means, for example a motor electric or a turbine driving in rotation a rotor 28, of which only a part has been shown, on which is directly mounted a compressor.
  • a group centrifugal compressor cantilever type compressor i.e. a group compressor which comprises a motor means, for example a motor electric or a turbine driving in rotation a rotor 28, of which only a part has been shown, on which is directly mounted a compressor.
  • the compressor meanwhile, has a number stator elements, such as 30 and 32, jointly delimiting a intake pipe 34 through which the gas to be handled is sucked in, and downstream, considering the direction of gas distribution in the compressor, a diffuser 36, which opens into a volute of repression (not shown).
  • a number stator elements such as 30 and 32, jointly delimiting a intake pipe 34 through which the gas to be handled is sucked in, and downstream, considering the direction of gas distribution in the compressor, a diffuser 36, which opens into a volute of repression (not shown).
  • a paddle wheel 38 is integral with the rotor 28. This paddle wheel has, at its leading edge, a front flange 40 and, at trailing edge level, a rear flange 42.
  • the body stator consisting of the aforementioned elements 30 and 32, is provided a pipe 44 passing through the body and, in particular, the element stator designated by the reference numeral 30, so as to put at atmospheric pressure an axial annular portion 46 of the flange before 40. It can be seen in particular in this FIG. 2 that the pipe 44 opens into a cavity 48 formed between the stator body and the front flange 40, in the vicinity of this annular surface 46.
  • This surface 46 is delimited by a first cylindrical portion 50 of the front flange 40 and by a second cylindrical portion 52 of outer diameter greater than the first portion 50 and arranged coaxially respectively towards the front of the compressor and towards the back of the compressor, considering the gas flow at the inlet compressor.
  • two labyrinth seals 54 and 56 are interposed between the stator body and the first and second cylindrical portions 50 and 52, respectively.
  • the axial annular surface 46 has dimensions corresponding to those of the seal of so that the pressures are validly compensated. The stop of the compressor is relieved, and it can easily start.
  • line 44 is connected to the torches 58 via a pressure regulating device 60.
  • This device comprises a valve 62 controlled at the opening and at the closing by a control device 64.
  • Measuring means 66 of the pressure prevailing in the line 44 provide information as to the pressure prevailing in line 44, and therefore in the cavity 48.
  • the control device 64 is duly programmed to depressurize cavity 48 during start-up of the compressor and to close line 44 by acting on the valve 62 during normal operation of the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The compressor has a radial flow impeller (38) mounted on a rotor (28) rotated by two stator bodies (30, 32). The body (30) has a conduit (44) opening in a cavity (48). The conduit and cavity create a depression on one side (40) of the impeller to compensate an axial push that is created by effort exerted by gas on the impeller and is applied on the rotor, when the compressor stops.

Description

L'invention concerne un groupe compresseur centrifuge et, en particulier, un compresseur centrifuge pour groupe compresseur du type en porte-à-faux.The invention relates to a centrifugal compressor unit and, in particular, a centrifugal compressor for compressor group of the cantilever type.

Plus particulièrement, l'invention concerne l'équilibrage de la poussée axiale d'un compresseur centrifuge lors de sa mise en service, afin de permettre le démarrage même avec une machine restée pressurisée à l'arrêt.More particularly, the invention relates to the balancing of the axial thrust of a centrifugal compressor when it is put into service, to allow starting even with a machine left behind pressurized when stopped.

Comme on le voit sur la figure 1, un groupe compresseur du type en porte-à-faux conventionnel comporte classiquement un moyen moteur 10, constitué par exemple par un moteur électrique ou par une turbine disposée à l'intérieur d'un carter 12 et entraínant en rotation un rotor 14, lequel est maintenu en position par un ensemble de paliers radiaux, tels que 16, et de paliers axiaux, tels que 18.As seen in Figure 1, a compressor unit of the conventional cantilever type conventionally includes a means motor 10, constituted for example by an electric motor or by a turbine arranged inside a casing 12 and driving in rotation a rotor 14, which is held in position by a set of bearings radial, such as 16, and axial bearings, such as 18.

En outre, le turbocompresseur comporte un compresseur 20. Dans l'exemple de réalisation représenté sur la figure 1, le compresseur 20 est un compresseur mono étagé. Ce compresseur comporte une roue à aubes 22 entraínée en rotation par le rotor 14 dans un stator 24 assurant, d'une part, un accroissement de la pression statique d'un gaz incident, aspiré selon la direction représentée par la flèche F1 à partir d'une conduite d'admission 26 et, d'autre part, un accroissement de l'énergie cinétique de ce gaz. En aval de la roue 22, le gaz est recueilli par une volute de sortie 28 en vue de le canaliser, puis de le ralentir, transformant ainsi en pression une partie importante de son énergie cinétique, puis est délivré en sortie du compresseur selon la flèche F2.In addition, the turbocharger includes a compressor 20. In the embodiment shown in Figure 1, the compressor 20 is a single stage compressor. This compressor includes an impeller 22 driven in rotation by the rotor 14 in a stator 24 ensuring, on the one hand, an increase in pressure static of an incident gas, sucked in the direction represented by the arrow F1 from an intake pipe 26 and, on the other hand, a increase in the kinetic energy of this gas. Downstream of the wheel 22, the gas is collected by an outlet volute 28 in order to channel it, then slow it down, thus turning part of the pressure significant of its kinetic energy, then is delivered at the output of the compressor according to arrow F2.

De manière connue en soi, l'élévation de pression du gaz dans la roue aubée 22 provoque une force de réaction axiale, dirigée vers l'entrée du gaz dans la roue. C'est pourquoi le compresseur est pourvu de moyens d'équilibrage de la poussée axiale ainsi engendrée.In a manner known per se, the increase in pressure of the gas in the paddle wheel 22 causes an axial reaction force, directed towards the entry of gas into the wheel. This is why the compressor is provided means for balancing the axial thrust thus generated.

Par ailleurs, afin d'éviter de rejeter dans l'atmosphère ambiante des effluents gazeux qui peuvent être nuisibles pour le personnel ou pour l'environnement ou d'économiser le gaz, ou encore dans le but d'accélérer les procédures de démarrage, pour rendre plus rapide la fourniture de gaz aux unités dans lesquelles les compresseurs sont installés, en supprimant notamment l'inertage préalable par un gaz inerte lorsque le gaz de procédé est inflammable, les compresseurs sont généralement maintenus sous pression lorsqu'ils sont à l'arrêt. Comme on le sait, ce maintien sous pression du compresseur engendre, à l'arrêt, des efforts sur la roue à aubes 22 provoquant l'apparition d'une force résultante sur le rotor, laquelle s'applique sur la garniture d'étanchéité de bout d'arbre, sur une surface définie par un diamètre d'étanchéité de la garniture d'étanchéité.Furthermore, in order to avoid discharging into the ambient atmosphere gaseous effluents which may be harmful to personnel or for the environment or to save gas, or even for the purpose to speed up the start-up procedures, to make the supply of gas to the units in which the compressors are installed, in particular by eliminating prior inerting with a gas inert when process gas is flammable, compressors are generally kept under pressure when they are stopped. As we know, this pressure maintenance of the compressor generates, when stationary, forces on the impeller 22 causing the appearance a resultant force on the rotor, which applies to the packing shaft end sealing, on a surface defined by a diameter seal.

Ainsi, alors que les moyens d'équilibrage de poussée axiale sont efficaces pour compenser les efforts qui s'exercent sur le rotor lors du fonctionnement du turbocompresseur, ils sont inefficaces pour compenser la poussée axiale qui s'exerce sur la garniture d'étanchéité de bout d'arbre, à l'arrêt du compresseur alors que celui-ci est maintenu sous pression à l'arrêt.So while the axial thrust balancing means are effective in compensating for the forces exerted on the rotor during operation of the turbocharger, they are ineffective for compensate for the axial thrust exerted on the seal at the end of the shaft, when the compressor stops while the compressor is kept under pressure when stopped.

Le but de l'invention est donc de pallier cet inconvénient et de fournir un compresseur pour groupe compresseur centrifuge du type en porte-à-faux capable d'équilibrer la poussée axiale engendrée sur le rotor à l'arrêt du compresseur.The object of the invention is therefore to overcome this drawback and to supply a compressor for centrifugal compressor group of the type overhang capable of balancing the axial thrust generated on the rotor at compressor stop.

L'invention a donc pour objet un compresseur centrifuge pour groupe compresseur du type en porte-à-faux comprenant un ensemble d'au moins une roue à aubes de compression montée sur un rotor destiné à être entraíné en rotation par un moyen moteur dans un corps statorique et des moyens de compensation de la poussée axiale qui est engendrée par l'effort exercé par le gaz sur la roue à aubes et qui est appliquée sur le rotor. The invention therefore relates to a centrifugal compressor for cantilever type compressor unit comprising a set at least one compression impeller mounted on a rotor intended to be rotated by a motor means in a body stator and means for compensating the axial thrust which is generated by the force exerted by the gas on the impeller and which is applied to the rotor.

Selon une caractéristique générale de ce compresseur, les moyens de compensation sont adaptés pour compenser la poussée axiale supportée par le rotor à l'arrêt du compresseur.According to a general characteristic of this compressor, the compensation means are adapted to compensate for the thrust axial supported by the rotor when the compressor stops.

Selon une autre caractéristique du compresseur selon l'invention, les moyens de compensation comportent des moyens pour engendrer une dépression sur l'une des faces aptes à compenser au moins en partie ladite poussée axiale.According to another characteristic of the compressor according to the invention, the compensation means include means for generate a depression on one of the faces capable of compensating for the less in part said axial thrust.

Dans le cas où le compresseur est multiétagé, la dépression est formée sur la roue du premier étage de compression. La face sur laquelle est engendrée la dépression est dès lors la face d'aspiration d'un gaz manipulé par le compresseur.If the compressor is multi-stage, the vacuum is formed on the wheel of the first compression stage. The face on which generates the depression is therefore the suction side of a gas handled by the compressor.

Dans un mode de réalisation, le corps statorique comporte une canalisation traversante débouchant en regard de ladite face de la roue.In one embodiment, the stator body comprises a through pipe opening opposite said face of the wheel.

Afin d'exercer un effort apte à compenser la poussée axiale appliquée sur le rotor, le bord d'attaque des aubes de la roue à aubes comporte un flasque avant pourvu d'un épaulement annulaire axial délimité par deux portions cylindriques de diamètre croissant du bord d'attaque vers le bord de fuite de la roue, la canalisation débouchant en regard de cet épaulement annulaire.In order to exert an effort capable of compensating for the axial thrust applied to the rotor, the leading edge of the blades of the impeller has a front flange with an axial annular shoulder delimited by two cylindrical portions of increasing diameter of the edge leading to the trailing edge of the wheel, the pipe emerging opposite this annular shoulder.

En ce qui concerne la canalisation, celle-ci débouche vers l'extérieur du compresseur et est équipée avantageusement d'un dispositif de régulation de pression adapté pour obturer ladite canalisation lors du fonctionnement du compresseur et à ouvrir ladite canalisation à l'arrêt du compresseur.As for the pipeline, it leads to the exterior of the compressor and is advantageously equipped with a pressure regulating device suitable for sealing said pipeline during compressor operation and to open said pipe at compressor stop.

D'autres buts, caractéristiques et avantages de l'invention apparaítront à la lecture de la description suivante, donnée uniquement à titre d'exemple non limitatif, et faite en référence aux dessins annexés sur lesquels :

  • la figure 1, dont il a déjà été fait mention, illustre la structure générale d'un groupe compresseur conventionnel ;
  • la figure 2 illustre une vue en coupe d'une partie d'un compresseur conforme à l'invention ; et
  • la figure 3 illustre un autre mode de réalisation d'un compresseur selon l'invention pourvu d'un dispositif de régulation de pression.
Other objects, characteristics and advantages of the invention will appear on reading the following description, given solely by way of nonlimiting example, and made with reference to the appended drawings in which:
  • Figure 1, which has already been mentioned, illustrates the general structure of a conventional compressor unit;
  • Figure 2 illustrates a sectional view of part of a compressor according to the invention; and
  • FIG. 3 illustrates another embodiment of a compressor according to the invention provided with a pressure regulation device.

Sur la figure 2, on a représenté un compresseur centrifuge d'un groupe compresseur du type en porte-à-faux.In Figure 2, there is shown a centrifugal compressor of a compressor unit of the cantilever type.

Sur cette figure, seule une partie pertinente du compresseur a été représentée, le reste du groupe compresseur étant par ailleurs identique au groupe compresseur décrit précédemment en référence à la figure 1.In this figure, only a relevant part of the compressor has was represented, the rest of the compressor group being also identical to the compressor unit described above with reference to Figure 1.

Sur cette figure 2, on a également considéré que le compresseur est un compresseur à un seul étage. On conçoit cependant que l'invention s'applique également à la réalisation d'un compresseur multiétagé, par exemple à deux étages.In this figure 2, it has also been considered that the compressor is a single stage compressor. However, we can see that the invention also applies to the production of a compressor multi-storey, for example two storeys.

Ainsi, la portion de compresseur représentée sur cette figure 2 est destinée à faire partie d'un compresseur centrifuge d'un groupe compresseur du type en porte-à-faux, c'est-à-dire un groupe compresseur qui comporte un moyen moteur, par exemple un moteur électrique ou une turbine entraínant en rotation un rotor 28, dont seule une partie a été représentée, sur lequel est directement monté un compresseur.Thus, the compressor portion shown in this figure 2 is intended to be part of a group centrifugal compressor cantilever type compressor, i.e. a group compressor which comprises a motor means, for example a motor electric or a turbine driving in rotation a rotor 28, of which only a part has been shown, on which is directly mounted a compressor.

Le compresseur, quant à lui, comporte un certain nombre d'éléments statoriques, tels que 30 et 32, délimitant conjointement une conduite d'admission 34 par laquelle le gaz à manipuler est aspiré et, en aval, en considérant la direction de distribution du gaz dans le compresseur, un diffuseur 36, lequel débouche dans une volute de refoulement (non représentée).The compressor, meanwhile, has a number stator elements, such as 30 and 32, jointly delimiting a intake pipe 34 through which the gas to be handled is sucked in, and downstream, considering the direction of gas distribution in the compressor, a diffuser 36, which opens into a volute of repression (not shown).

Une roue à aube 38 est solidaire du rotor 28. Cette roue à aubes comporte, au niveau de son bord d'attaque, un flasque avant 40 et, au niveau du bord de fuite, un flasque arrière 42.A paddle wheel 38 is integral with the rotor 28. This paddle wheel has, at its leading edge, a front flange 40 and, at trailing edge level, a rear flange 42.

Afin d'équilibrer la pression appliquée sur le rotor à l'arrêt du compresseur, lorsque celui-ci est maintenu sous pression, le corps statorique, constitué par les éléments précités 30 et 32, est pourvu d'une canalisation 44 traversant le corps et, en particulier, l'élément statorique désigné par la référence numérique 30, de manière à mettre à la pression atmosphérique une portion annulaire axiale 46 du flasque avant 40. On voit en particulier sur cette figure 2 que la canalisation 44 débouche dans une cavité 48 ménagée entre le corps statorique et le flasque avant 40, au voisinage de cette surface annulaire 46. Cette surface 46 est délimitée par une première portion cylindrique 50 du flasque avant 40 et par une deuxième portion cylindrique 52 de diamètre extérieur supérieur à la première portion 50 et disposées coaxialement respectivement vers l'avant du compresseur et vers l'arrière du compresseur, en considérant la circulation du gaz à l'entrée du compresseur.In order to balance the pressure applied to the rotor when the compressor, when it is kept under pressure, the body stator, consisting of the aforementioned elements 30 and 32, is provided a pipe 44 passing through the body and, in particular, the element stator designated by the reference numeral 30, so as to put at atmospheric pressure an axial annular portion 46 of the flange before 40. It can be seen in particular in this FIG. 2 that the pipe 44 opens into a cavity 48 formed between the stator body and the front flange 40, in the vicinity of this annular surface 46. This surface 46 is delimited by a first cylindrical portion 50 of the front flange 40 and by a second cylindrical portion 52 of outer diameter greater than the first portion 50 and arranged coaxially respectively towards the front of the compressor and towards the back of the compressor, considering the gas flow at the inlet compressor.

Afin d'assurer une étanchéité au gaz, deux joints à labyrinthe 54 et 56 sont interposés entre le corps statorique et les première et deuxième portions cylindriques 50 et 52, respectivement.To ensure gas tightness, two labyrinth seals 54 and 56 are interposed between the stator body and the first and second cylindrical portions 50 and 52, respectively.

Comme on le conçoit, la mise à la pression atmosphérique de la cavité 48 alors que le reste du compresseur est sous pression provoque l'apparition d'un effort d'aspiration sur le flasque avant 40, localisé à la surface annulaire 48, dirigé selon la flèche F3. La force d'attraction ainsi créée par cette dépression régnant dans la cavité 48 est prévue pour compenser la force développée sur la garniture d'étanchéité de bout d'arbre par la pression interne régnant dans le reste de la machine.As can be seen, putting the atmospheric pressure of the cavity 48 while the rest of the compressor is under pressure causes the appearance of a suction force on the front flange 40, located at the annular surface 48, directed according to arrow F3. The force of attraction thus created by this depression prevailing in the cavity 48 is provided to compensate for the force developed on the seal of end of shaft by internal pressure prevailing in the rest of the machine.

Ainsi, de préférence, la surface annulaire axiale 46 présente des dimensions correspondant à celles de la garniture d'étanchéité de sorte que les pressions soient valablement compensées. La butée du compresseur est soulagée, et celui-ci, peut aisément démarrer.Thus, preferably, the axial annular surface 46 has dimensions corresponding to those of the seal of so that the pressures are validly compensated. The stop of the compressor is relieved, and it can easily start.

On notera que la mise en communication de la cavité 48 avec l'atmosphère ne s'effectue que lors du démarrage du compresseur de manière à faciliter ce dernier. Au cours de cette mise en communication, une fuite de gaz ainsi créée, à partir d'une zone du corps pressurisé délimitée par les deux joints 54 et 56, est envoyée à un réseau de torches afin d'éviter l'apparition d'effluents gazeux au voisinage du compresseur. Comme indiqué précédemment, cette fuite n'est cependant créée que pendant le court instant pendant lequel la vitesse du compresseur est augmentée.It will be noted that the communication of the cavity 48 with the atmosphere only takes place when the compressor starts so as to facilitate the latter. During this implementation communication, a gas leak thus created, from an area of the pressurized body delimited by the two seals 54 and 56, is sent to a network of torches to avoid the appearance of gaseous effluents compressor vicinity. As previously stated, this leak however, is only created during the short time during which the compressor speed is increased.

Comme on le voit sur la figure 3, afin de permettre cette dépression localisée et momentanée dans le compresseur lors du démarrage de la machine, la canalisation 44 est raccordée au réseau de torches 58 par l'intermédiaire d'un dispositif de régulation de pression 60. Ce dispositif comporte une vanne 62 pilotée à l'ouverture et à la fermeture par un dispositif de commande 64. Des moyens de mesure 66 de la pression régnant dans la canalisation 44 fournissent des informations quant à la pression régnant dans la canalisation 44, et donc dans la cavité 48. Le dispositif de commande 64 est dûment programmé de manière à dépressuriser la cavité 48 lors du démarrage du compresseur et à obturer la canalisation 44 par action sur la vanne 62 lors du fonctionnement normal du compresseur.As seen in Figure 3, to allow this localized and momentary depression in the compressor during machine start-up, line 44 is connected to the torches 58 via a pressure regulating device 60. This device comprises a valve 62 controlled at the opening and at the closing by a control device 64. Measuring means 66 of the pressure prevailing in the line 44 provide information as to the pressure prevailing in line 44, and therefore in the cavity 48. The control device 64 is duly programmed to depressurize cavity 48 during start-up of the compressor and to close line 44 by acting on the valve 62 during normal operation of the compressor.

Claims (7)

Compresseur pour groupe compresseur centrifuge du type en porte-à-faux, comprenant un ensemble d'au moins une roue à aubes (38) de compression montée sur un rotor (28) destiné à être entraíné en rotation par un moyen moteur dans un corps statorique (30, 32) et des moyens (44, 48) de compensation de la poussée axiale qui est engendrée par l'effort exercé par le gaz sur la roue à aubes et qui est appliquée sur le rotor, caractérisé en ce que les moyens de compensation sont adaptés pour compenser la poussée axiale supportée par le rotor à l'arrêt du compresseur.Compressor for a centrifugal compressor group of the cantilever type, comprising a set of at least one compression impeller (38) mounted on a rotor (28) intended to be driven in rotation by a motor means in a body stator (30, 32) and means (44, 48) for compensating for the axial thrust which is generated by the force exerted by the gas on the impeller and which is applied to the rotor, characterized in that the means are adapted to compensate the axial thrust supported by the rotor when the compressor stops. Compresseur selon la revendication 1, caractérisé en ce que les moyens de compensation comportent des moyens (44, 48) pour engendrer une dépression sur l'une des faces (40) d'une roue à aubes apte à compenser au moins en partie ladite poussée axiale.Compressor according to claim 1, characterized in that the compensation means comprise means (44, 48) for generating a vacuum on one of the faces (40) of an impeller capable of at least partially compensating for said thrust axial. Compresseur selon la revendication 2, caractérisé en ce que la face sur laquelle est engendrée la dépression est la face (40) d'aspiration d'un gaz manipulé par le compresseur.Compressor according to claim 2, characterized in that the face on which the vacuum is generated is the face (40) of suction of a gas handled by the compressor. Compresseur selon l'une des revendications 2 et 3, caractérisé en ce que la roue à aubes (38) sur laquelle est appliquée la dépression est la roue constitutive d'un premier étage de compression.Compressor according to one of claims 2 and 3, characterized in that the impeller (38) to which the vacuum is applied is the wheel constituting a first compression stage. Compresseur selon l'une quelconque des revendications 2 à 4, caractérisé en ce que le corps statorique comporte une canalisation traversante (44) débouchant en regard de ladite face de la roue.Compressor according to any one of claims 2 to 4, characterized in that the stator body comprises a through pipe (44) opening opposite said face of the wheel. Compresseur selon la revendication 5, caractérisé en ce que le bord d'attaque des aubes de la roue à aubes comporte un flasque avant (40) pourvu d'un épaulement annulaire axial (46) délimité par deux portions cylindriques (50, 52) de diamètre croissant du bord d'attaque vers le bord de fuite de la roue, la canalisation débouchant en regard dudit épaulement annulaire (46).Compressor according to claim 5, characterized in that the leading edge of the blades of the impeller comprises a front flange (40) provided with an axial annular shoulder (46) delimited by two cylindrical portions (50, 52) of increasing diameter from the leading edge to the trailing edge of the wheel, the pipe opening facing said annular shoulder (46). Compresseur selon l'une des revendications 5 et 6, caractérisé en ce que la canalisation (44) débouche vers l'extérieur du compresseur et est équipée d'un dispositif de régulation de pression (60) adapté pour obturer ladite canalisation lors du fonctionnement du compresseur et à ouvrir ladite canalisation à l'arrêt du compresseur.Compressor according to either of Claims 5 and 6, characterized in that the pipe (44) opens out towards the outside of the compressor and is equipped with a pressure regulating device (60) suitable for closing said pipe during operation of the compressor and to open said pipe when the compressor stops.
EP04290914A 2003-04-28 2004-04-06 Centrifugal compressor of the overhung type Expired - Lifetime EP1473464B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0305185 2003-04-28
FR0305185A FR2854208B1 (en) 2003-04-28 2003-04-28 COMPRESSOR FOR CENTRIFUGAL COMPRESSOR GROUP TYPE IN DOOR-A-FALSE

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EP1473464A1 true EP1473464A1 (en) 2004-11-03
EP1473464B1 EP1473464B1 (en) 2010-11-10

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DE (1) DE602004029956D1 (en)
FR (1) FR2854208B1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITCO20100025A1 (en) * 2010-05-11 2011-11-12 Nuovo Pignone Spa CONFIGURATION OF BALANCING DRUM FOR COMPRESSOR ROTORS

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4385768A (en) * 1979-07-19 1983-05-31 Rotoflow Corporation, Inc. Shaft mounting device and method
FR2592688A1 (en) * 1986-01-08 1987-07-10 Alsthom Turbine machine
EP0373817A1 (en) * 1988-12-13 1990-06-20 Nova Corporation Of Alberta Gas compressor having a dry gas seal on an overhung impeller shaft
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4385768A (en) * 1979-07-19 1983-05-31 Rotoflow Corporation, Inc. Shaft mounting device and method
FR2592688A1 (en) * 1986-01-08 1987-07-10 Alsthom Turbine machine
EP0373817A1 (en) * 1988-12-13 1990-06-20 Nova Corporation Of Alberta Gas compressor having a dry gas seal on an overhung impeller shaft
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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITCO20100025A1 (en) * 2010-05-11 2011-11-12 Nuovo Pignone Spa CONFIGURATION OF BALANCING DRUM FOR COMPRESSOR ROTORS
EP2386763A3 (en) * 2010-05-11 2017-11-22 Nuovo Pignone S.p.A. Balancing piston

Also Published As

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DE602004029956D1 (en) 2010-12-23
EP1473464B1 (en) 2010-11-10
FR2854208A1 (en) 2004-10-29
FR2854208B1 (en) 2008-02-15

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