EP1988292B1 - Rotating machine comprising a passive axial balancing system - Google Patents

Rotating machine comprising a passive axial balancing system Download PDF

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Publication number
EP1988292B1
EP1988292B1 EP08155267A EP08155267A EP1988292B1 EP 1988292 B1 EP1988292 B1 EP 1988292B1 EP 08155267 A EP08155267 A EP 08155267A EP 08155267 A EP08155267 A EP 08155267A EP 1988292 B1 EP1988292 B1 EP 1988292B1
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EP
European Patent Office
Prior art keywords
axial
rotary machine
shaft
balancing system
machine according
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EP08155267A
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German (de)
French (fr)
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EP1988292A1 (en
Inventor
Fabien Wahl
Laurent Fabbri
François Danguy
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Safran Aircraft Engines SAS
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SNECMA SAS
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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
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the present invention relates to the field of rotating machines intended to be traversed by a main flow of liquid, such as for example suction pumps or turbines for generating an electric power. If the rotating machine is a pump, then the main flow of liquid is the aspirated liquid, whereas if the rotating machine is a turbine, the main flow of liquid is the liquid injected into the turbine.
  • a main flow of liquid such as for example suction pumps or turbines for generating an electric power.
  • the rotating machine generally comprises an electrical member consisting of a rotor and a stator, said member being an electric motor when the machine operates as a pump, and said member being an electric generator when the machine operates in a turbine.
  • Such a rotating machine is often intended to be arranged vertically, that is to say that its axis of rotation extends generally vertically, so that one can define the "bottom” and the “top” of the pump with reference to such a vertical axis.
  • This additional force is added to the force of gravity so that the rotation shaft undergoes significant forces directed axially down the machine.
  • such rotating machines generally comprise an active axial balancing system, such as that described in the document US 4,538,960 or in the document GB 17268 which describes the preamble of claim 1, to compensate all or part of these efforts, exerting a force of axial recovery on the shaft in a direction opposite to that of the force of gravity.
  • the intensity of the forces to be compensated can fluctuate, for example due to a fluctuation of the flow rate of the main flow of liquid, so that the intensity of the axial recovery force can suddenly become greater than the intensity of the forces. forces to compensate, thus causing the shaft to move towards the top of the machine.
  • the intensity of the axial return force depends on the displacement of the rotation shaft relative to the housing. This makes it possible to regulate the intensity of the axial recovery force.
  • the intensity of the axial return force decreases if the intensity of the axial return force becomes greater than the intensity of the forces to be compensated and, conversely, the axial recovery force increases if the intensity of the axial return force increases. the axial recovery force becomes less than the intensity of the forces to be compensated. In other words, the intensity of the axial recovery force is slaved to the displacement of the rotation shaft.
  • An object of the present invention is to provide a rotating machine having improved axial recovery capability.
  • the rotating machine according to the present invention further comprises a circuit for a secondary flow of liquid taken from the main flow of liquid, and a passive axial balancing system capable of exerting a second force. of axial recovery on the shaft, said passive axial balancing system being fed by the circuit of the secondary flow of liquid.
  • the passive axial balancing system differs from the active axial balancing system in that the intensity of the second force is not slaved to the displacement of the shaft relative to the housing.
  • the intensity of the second force is constant regardless of the displacement of the rotation shaft relative to the housing.
  • the second axial return force has a direction opposite to that of the gravitational force, when the machine is arranged vertically.
  • the second axial recovery force has a direction opposite to that of the tensile force mentioned above.
  • the passive axial balancing system distinct from the active axial balancing system, therefore provides an additional axial return force, namely the second axial return force, as a result of which, the intensity of the overall axial recovery force exerting itself on the rotation shaft is advantageously increased.
  • the flow rate of the secondary liquid flow is substantially lower than that of the main flow of liquid.
  • the flow of secondary liquid flowing in the circuit during operation of the machine advantageously feeds the passive axial balancing system, that is to say that the secondary flow of liquid provides the energy necessary for the operation of the passive axial balancing system.
  • the passive axial balancing system comprises an annular passage between the shaft and the housing, through which the secondary liquid flow is intended to flow, said passage axially defining an upstream fluid chamber of a downstream fluidic chamber. such that the pressure in the upstream fluid chamber is greater than the pressure in the downstream fluid chamber.
  • upstream and downstream are here considered with reference to the direction of flow of the secondary flow of liquid.
  • the pressure difference between the two chambers is due to the fact that the annular passage constitutes a flow restriction for the secondary flow of liquid.
  • the annular passage is defined between a disk attached to the shaft and the housing.
  • the annular passage is defined radially between the outer periphery of the disc and an inner surface of the housing.
  • the disc preferably extends radially from the axis of the rotation shaft, so that it defines axially the upstream chamber of the downstream chamber.
  • the second axial recovery force resulting from the pressure difference between the upstream and downstream chambers, is exerted on the rotation shaft via the disc.
  • the disk comprises at its periphery an annular labyrinth seal.
  • the annular passage is thus defined radially between the labyrinth seal and the inner surface of the housing.
  • the passive axial balancing system further comprises means for calibrating the flow rate of the secondary liquid flow.
  • the flow rate of the secondary liquid flow is calibrated so that a sufficient second axial recovery force is obtained without greatly reducing the efficiency of the rotating machine.
  • the means for calibrating the flow rate of the secondary liquid flow comprise said annular passage.
  • the annular passage participates both in the generation of the second axial recovery force, and in the calibration of the flow rate of the secondary liquid flow.
  • the annular passage has a predetermined radial extension in order to calibrate the flow rate of the secondary flow of liquid.
  • the radial extension corresponds to the radial clearance existing between the disk and the casing.
  • the secondary flow of liquid is also used to cool a rotating element of the machine.
  • the secondary stream of liquid is a flow of coolant.
  • this flow of coolant is advantageously calibrated so that the cooling of the rotating element is sufficient.
  • a rotating element is an element of which at least one component is rotated by the shaft.
  • the rotating element is a bearing, a motor and / or an electric generator.
  • the machine according to the invention may comprise a plurality of rotating elements chosen from the abovementioned elements.
  • the same flow of liquid is used to cool the rotating element and to feed the passive axial balancing system. It is therefore not necessary to provide separate circuits, which allows to advantageously simplify the structure of the machine.
  • the rotating machine is a pump.
  • the rotating machine is a turbine.
  • the figure 1 represents an example of a rotary machine 10 according to the present invention, this rotating machine 10 being intended preferentially but not exclusively to pumping fluid such as liquefied gas. It can advantageously be used to empty the tanks of a LNG carrier.
  • the rotating machine according to the invention may also be a turbine in which circulates a liquid driving a generator that provides an electric power.
  • the machine 10 successively comprises a suction stage 12, a centrifugal wheel 14 and an annular duct 16 for discharging the aspirated liquid.
  • the suction stage 12 comprises a rotary inductor 18 driven in rotation by a rotation shaft 20 of the machine 10, the rotation shaft 20 being driven by a rotating element consisting of an electric motor 22.
  • the electric motor 22 comprises a rotor 24 fixed to the shaft 20 and a stator 26 fixed to a housing 28 of the machine 10.
  • the rotation shaft 20 is rotatably mounted on the housing 28 via a low bearing 30 located between the centrifugal wheel and 14 and the motor 22, and a high bearing 32 located between the motor 22 and a discharge sleeve 34.
  • the rotation shaft 20 comprises a shoulder 36 coming into axial abutment against an inner ring 38 of the low bearing 30.
  • the machine 10 being arranged vertically, it is understood that the low bearing 30 supports the weight of the rotation shaft, the centrifugal wheel 14, the rotor 24 and the inductor 18, weight plus the tensile force undergone by the inductor 18 during the suction of the liquid.
  • the machine 10 further comprises an active axial balancing system 40, well known elsewhere, capable of exerting on the shaft 20 a first axial recovery force R1 .
  • the active axial balancing system 40 further allows the regulation of the intensity of the first axial recovery force R1. More precisely, the regulation depends on the axial displacement of the shaft 20 relative to the casing 28.
  • the active axial balancing system 40 operates a regulation by decreasing the intensity of the first axial recovery force. R1.
  • the active axial balancing system 40 is not sufficiently efficient when the flow rate of the main fluid flow F1 pumped is low. More specifically, it has been found that the regulation means do not work correctly for low flow rates.
  • the rotating machine 10 also comprises, in a particularly advantageous manner, a passive axial balancing system 42, better visible on the figure 2 Which is capable of exerting on the shaft 20 a second axial take-up force R2.
  • This axial balancing system 42 is passive, that is to say that, unlike the active axial balancing system, the second axial recovery force R2 is independent of the axial displacement of the shaft 20 relative to the housing 28. .
  • the passive axial balancing system 42 comprises a disk 44 fixed to the upper end of the shaft 20.
  • This disk 44 is able to slide in a bore 47 made in the casing 28.
  • the high bearing 32 is mounted between the disk 44 and a shoulder 45 of the shaft 20.
  • the disc 44 has at its periphery an annular labyrinth seal 46.
  • annular labyrinth seal 46 may be provided.
  • other types of joints may be provided.
  • the passive axial balancing system 42 is fed by a circuit of a secondary flow of liquid F2 which is taken from the main flow of liquid F1, in this case thanks to a radial passage 49 formed in an inner surface 51 of the annular pipe 16.
  • this secondary flow F2 passes through the gap 48 of the motor 22, whereby the motor is advantageously cooled.
  • the secondary flow of liquid F2 then flows through an annular passage 52 defined radially between the outer periphery of the disc 44 and the casing 28, then flows in a downstream fluidic chamber 54 arranged axially downstream of the disc 44.
  • This downstream fluidic chamber is preferably connected to a discharge orifice 56 to allow the discharge of the secondary liquid flow F2 towards the outside of the rotating machine 10.
  • upstream and downstream are considered here in relation to in the direction of flow of the secondary flow of liquid F2.
  • annular passage 52 defines axially the upstream fluid chamber 50 of the downstream fluidic chamber 54.
  • the annular passage 52 forms a flow restriction for the secondary flow of liquid F 2, so that the pressure in the upstream fluid chamber 50 is greater than the pressure in the downstream fluidic chamber 54.
  • this second axial recovery force R2 depends on the radial clearance between the disk 44 and the casing 28 and not on the displacement of the shaft 20 with respect to the casing 28.
  • the "axial" balancing system 42 is termed "passive". Consequently, the overall axial recovery force R acting on the shaft 20 is the sum of the first and second axial recovery forces R1, R2 .
  • the passive axial balancing system 42 further comprises calibration means for calibrating the flow rate of the secondary liquid flow F2.
  • these calibration means comprise the annular passage 52.
  • the annular passage 52 has a radial extension e predetermined to calibrate the flow of the secondary liquid flow F2.
  • This radial extension e is defined between the outer periphery of the disk 44 and the casing 28.
  • the secondary flow of liquid F 2 is also advantageously used for cooling rotary elements of the machine 10, in this case the motor 22 and the bearing 32.
  • the flow rate of the engine cooling flow is calibrated in a constant manner, whatever the axial position of the rotor 24.
  • the rotating machine according to the invention can also be a turbine.
  • the main flow of liquid has a direction of flow opposite to that of the main flow of liquid F1 of the machine operating as a pump.
  • the secondary flow of liquid in the turbine has the same direction of flow as that of the secondary flow of liquid F2 circulating in the pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Description

La présente invention porte sur le domaine des machines tournantes destinées à être traversées par un flux de principal de liquide, telles par exemple les pompes d'aspiration ou les turbines pour générer une puissance électrique. Si la machine tournante est une pompe, alors le flux principal de liquide est le liquide aspiré, tandis que si la machine tournante est une turbine, le flux principal de liquide est le liquide injecté dans la turbine.The present invention relates to the field of rotating machines intended to be traversed by a main flow of liquid, such as for example suction pumps or turbines for generating an electric power. If the rotating machine is a pump, then the main flow of liquid is the aspirated liquid, whereas if the rotating machine is a turbine, the main flow of liquid is the liquid injected into the turbine.

La machine tournante comprend généralement un organe électrique constitué d'un rotor et d'un stator, ledit organe étant un moteur électrique lorsque la machine fonctionne comme une pompe, et ledit organe étant un générateur électrique lorsque la machine fonctionne en turbine.The rotating machine generally comprises an electrical member consisting of a rotor and a stator, said member being an electric motor when the machine operates as a pump, and said member being an electric generator when the machine operates in a turbine.

Une telle machine tournante est souvent destinée à être disposée verticalement, c'est-à-dire que son axe de rotation s'étend généralement verticalement, de sorte que l'on peut définir le « bas » et le « haut » de la pompe en référence à un tel axe vertical.Such a rotating machine is often intended to be arranged vertically, that is to say that its axis of rotation extends generally vertically, so that one can define the "bottom" and the "top" of the pump with reference to such a vertical axis.

On définit également les termes « axial », « radial » et « tangentiel » en référence à l'axe de la machine.The terms "axial", "radial" and "tangential" are also defined with reference to the axis of the machine.

Du fait de la masse importante de certains des éléments tournants de cette machine tournante, notamment celle de l'organe électrique et de l'arbre de rotation fixé au rotor de l'organe électrique, on comprend que la force de pesanteur qui tend à déplacer ces éléments vers le bas est importante.Due to the large mass of some of the rotating elements of this rotating machine, in particular that of the electrical member and the rotation shaft attached to the rotor of the electric member, it is understood that the gravitational force which tends to move these elements down is important.

En outre, lorsque la machine fonctionne comme une pompe, la contre réaction due au pompage induit une force de traction qui tire vers le bas l'arbre de rotation de la machine et les éléments qui y sont fixés.In addition, when the machine is operating as a pump, the counter-reaction due to pumping induces a pulling force which pulls down the machine rotation shaft and the elements attached thereto.

Cette force supplémentaire s'ajoute à la force de pesanteur si bien que l'arbre de rotation subit des efforts importants dirigés axialement vers le bas de la machine.This additional force is added to the force of gravity so that the rotation shaft undergoes significant forces directed axially down the machine.

Il en résulte que les paliers prévus pour guider en rotation l'arbre de rotation sont fortement sollicités axialement par ces efforts, ce qui nuit à leur durée de vie.As a result, the bearings provided to guide the rotational shaft in rotation are highly stressed axially by these forces, which affects their service life.

Pour pallier à cet inconvénient, de telles machines tournantes comprennent généralement un système d'équilibrage axial actif, tel que celui décrit dans le document US 4 538 960 ou dans le document GB 17268 qui décrit le préambule de la revendication 1, permettant de compenser tout ou partie de ces efforts, en exerçant une force de reprise axiale sur l'arbre dans un sens opposé à celui de la force de pesanteur.To overcome this drawback, such rotating machines generally comprise an active axial balancing system, such as that described in the document US 4,538,960 or in the document GB 17268 which describes the preamble of claim 1, to compensate all or part of these efforts, exerting a force of axial recovery on the shaft in a direction opposite to that of the force of gravity.

On comprend que l'on cherche à obtenir une force de reprise axiale dont l'intensité est sensiblement égale à l'intensité des forces à compenser, ces dernières étant constitués par la force de pesanteur et la force de traction.It is understood that it seeks to obtain an axial recovery force whose intensity is substantially equal to the intensity of the forces to be compensated, the latter being constituted by the force of gravity and the tensile force.

En pratique, l'intensité des forces à compenser peut fluctuer, par exemple en raison d'une fluctuation du débit du flux principal de liquide, si bien que l'intensité de la force de reprise axiale peut devenir soudainement supérieure à l'intensité des forces à compenser, entraînant ainsi le déplacement de l'arbre vers le haut de la machine.In practice, the intensity of the forces to be compensated can fluctuate, for example due to a fluctuation of the flow rate of the main flow of liquid, so that the intensity of the axial recovery force can suddenly become greater than the intensity of the forces. forces to compensate, thus causing the shaft to move towards the top of the machine.

En l'absence d'un système d'équilibrage axial actif, une telle poussée axiale sur l'arbre conduirait à fatiguer les paliers, ce qui nuirait à leur durée de vie.In the absence of an active axial balancing system, such axial thrust on the shaft would lead to fatigue the bearings, which would adversely affect their service life.

Dans un système d'équilibrage axial actif, l'intensité de la force de reprise axiale dépend du déplacement de l'arbre de rotation par rapport au carter. Cela permet de réguler l'intensité de la force de reprise axiale.In an active axial balancing system, the intensity of the axial return force depends on the displacement of the rotation shaft relative to the housing. This makes it possible to regulate the intensity of the axial recovery force.

Ainsi, l'intensité de la force de reprise axiale diminue si l'intensité de la force de reprise axiale devient supérieure à l'intensité des forces à compenser et, à l'inverse, la force de reprise axiale augmente si l'intensité de la force de reprise axiale devient inférieure à l'intensité des forces à compenser. En d'autres termes, l'intensité de la force de reprise axiale est asservie au déplacement de l'arbre de rotation.Thus, the intensity of the axial return force decreases if the intensity of the axial return force becomes greater than the intensity of the forces to be compensated and, conversely, the axial recovery force increases if the intensity of the axial return force increases. the axial recovery force becomes less than the intensity of the forces to be compensated. In other words, the intensity of the axial recovery force is slaved to the displacement of the rotation shaft.

On comprend donc que grâce au système d'équilibrage axial actif, l'intensité de la force de reprise axiale est activement régulée.It is therefore understood that thanks to the active axial balancing system, the intensity of the axial return force is actively regulated.

La présente invention concerne donc une telle machine tournante selon la revendication 1 destinée à être traversée par un flux principal de liquide, comprenant :

  • un arbre monté rotatif par rapport à un carter de la machine tournante,
  • un système d'équilibrage axial actif apte à exercer une première force de reprise axiale sur l'arbre.
The present invention thus relates to such a rotating machine according to claim 1 intended to be traversed by a main stream of liquid, comprising:
  • a shaft rotatably mounted relative to a housing of the rotating machine,
  • an active axial balancing system capable of exerting a first axial return force on the shaft.

Néanmoins, il a été constaté que dans certaines situations, l'intensité de la force de reprise axiale exercée par le système de reprise axial actif n'est pas suffisamment importante.Nevertheless, it has been found that in certain situations, the intensity of the axial recovery force exerted by the active axial recovery system is not sufficiently large.

Un but de la présente invention est de fournir une machine tournante ayant une capacité de reprise axiale améliorée.An object of the present invention is to provide a rotating machine having improved axial recovery capability.

L'invention atteint son but par le fait que la machine tournante selon la présente invention comporte en outre un circuit pour un flux secondaire de liquide prélevé sur le flux principal de liquide, et un système d'équilibrage axial passif apte à exercer une deuxième force de reprise axiale sur l'arbre, ledit système d'équilibrage axial passif étant alimenté par le circuit du flux secondaire de liquide.The invention achieves its object by the fact that the rotating machine according to the present invention further comprises a circuit for a secondary flow of liquid taken from the main flow of liquid, and a passive axial balancing system capable of exerting a second force. of axial recovery on the shaft, said passive axial balancing system being fed by the circuit of the secondary flow of liquid.

Au sens de l'invention, le système d'équilibrage axial passif diffère du système d'équilibrage axial actif en ce que l'intensité de la deuxième force n'est pas asservie au déplacement de l'arbre par rapport au carter.Within the meaning of the invention, the passive axial balancing system differs from the active axial balancing system in that the intensity of the second force is not slaved to the displacement of the shaft relative to the housing.

En d'autres termes, l'intensité de la deuxième force est constante quel que soit le déplacement de l'arbre de rotation par rapport au carter.In other words, the intensity of the second force is constant regardless of the displacement of the rotation shaft relative to the housing.

Par ailleurs, tout comme la première force de reprise axiale, la deuxième force de reprise axiale présente un sens opposé à celui de la force de pesanteur, lorsque la machine est disposée verticalement.Moreover, like the first axial return force, the second axial return force has a direction opposite to that of the gravitational force, when the machine is arranged vertically.

Lorsque la machine tournante selon l'invention est une pompe, la deuxième force de reprise axiale présente un sens opposé à celui de la force de traction mentionnée ci-dessus.When the rotating machine according to the invention is a pump, the second axial recovery force has a direction opposite to that of the tensile force mentioned above.

Le système d'équilibrage axial passif, distinct du système d'équilibrage axial actif, fournit donc une force de reprise axiale supplémentaire, à savoir la deuxième force de reprise axiale, en conséquence de quoi, l'intensité de la force globale de reprise axiale s'exerçant sur l'arbre de rotation est avantageusement augmentée.The passive axial balancing system, distinct from the active axial balancing system, therefore provides an additional axial return force, namely the second axial return force, as a result of which, the intensity of the overall axial recovery force exerting itself on the rotation shaft is advantageously increased.

Selon l'invention, le débit du flux secondaire de liquide est sensiblement inférieur à celui du flux principal de liquide.According to the invention, the flow rate of the secondary liquid flow is substantially lower than that of the main flow of liquid.

Aussi, selon l'invention, le flux de liquide secondaire circulant dans le circuit lors du fonctionnement de la machine, alimente avantageusement le système d'équilibrage axial passif, c'est-à-dire que le flux secondaire de liquide fournit l'énergie nécessaire au fonctionnement du système d'équilibrage axial passif.Also, according to the invention, the flow of secondary liquid flowing in the circuit during operation of the machine, advantageously feeds the passive axial balancing system, that is to say that the secondary flow of liquid provides the energy necessary for the operation of the passive axial balancing system.

Avantageusement, le système d'équilibrage axial passif comprend un passage annulaire entre l'arbre et le carter, au travers duquel le flux secondaire de liquide est destiné à s'écouler, ledit passage délimitant axialement une chambre fluidique amont d'une chambre fluidique aval, de telle sorte que la pression dans la chambre fluidique amont est supérieure à la pression dans la chambre fluidique aval.Advantageously, the passive axial balancing system comprises an annular passage between the shaft and the housing, through which the secondary liquid flow is intended to flow, said passage axially defining an upstream fluid chamber of a downstream fluidic chamber. such that the pressure in the upstream fluid chamber is greater than the pressure in the downstream fluid chamber.

Les termes « amont » et « aval sont ici considérés en référence au sens d'écoulement du flux secondaire de liquide.The terms "upstream" and "downstream" are here considered with reference to the direction of flow of the secondary flow of liquid.

La différence de pression entre les deux chambres est due au fait que le passage annulaire constitue une restriction d'écoulement pour le flux secondaire de liquide.The pressure difference between the two chambers is due to the fact that the annular passage constitutes a flow restriction for the secondary flow of liquid.

De manière avantageuse, le passage annulaire est défini entre un disque fixé à l'arbre et le carter.Advantageously, the annular passage is defined between a disk attached to the shaft and the housing.

De préférence, le passage annulaire est défini radialement entre la périphérie extérieure du disque et une surface interne du carter.Preferably, the annular passage is defined radially between the outer periphery of the disc and an inner surface of the housing.

Aussi, le disque s'étend de préférence radialement depuis l'axe de l'arbre de rotation, de telle sorte qu'il délimite axialement la chambre amont de la chambre aval. La deuxième force de reprise axiale, résultant de la différence de pression entre les chambres amont et aval, s'exerce donc sur l'arbre de rotation par l'intermédiaire du disque.Also, the disc preferably extends radially from the axis of the rotation shaft, so that it defines axially the upstream chamber of the downstream chamber. The second axial recovery force, resulting from the pressure difference between the upstream and downstream chambers, is exerted on the rotation shaft via the disc.

Avantageusement, le disque comporte à sa périphérie un joint labyrinthe annulaire.Advantageously, the disk comprises at its periphery an annular labyrinth seal.

Le passage annulaire est donc défini radialement entre le joint labyrinthe et la surface intérieure du carter.The annular passage is thus defined radially between the labyrinth seal and the inner surface of the housing.

De manière particulière avantageuse, le système d'équilibrage axial passif comporte en outre des moyens pour calibrer le débit du flux secondaire de liquide.Particularly advantageously, the passive axial balancing system further comprises means for calibrating the flow rate of the secondary liquid flow.

En effet, le débit du flux secondaire de liquide ne doit pas être trop élevé car sinon cela diminuerait le rendement de la machine.Indeed, the flow of the secondary flow of liquid must not be too high because otherwise it would reduce the efficiency of the machine.

Grâce à la présente invention, le débit du flux secondaire de liquide est calibré de telle sorte que l'on obtient une deuxième force de reprise axiale suffisante sans trop diminuer le rendement de la machine tournante.Thanks to the present invention, the flow rate of the secondary liquid flow is calibrated so that a sufficient second axial recovery force is obtained without greatly reducing the efficiency of the rotating machine.

Avantageusement, les moyens pour calibrer le débit du flux secondaire de liquide comprennent ledit passage annulaire.Advantageously, the means for calibrating the flow rate of the secondary liquid flow comprise said annular passage.

En d'autres termes, le passage annulaire participe à la fois à la génération de la deuxième force de reprise axiale, et au calibrage du débit du flux secondaire de liquide.In other words, the annular passage participates both in the generation of the second axial recovery force, and in the calibration of the flow rate of the secondary liquid flow.

Avantageusement, le passage annulaire présente une extension radiale prédéterminée afin de calibrer le débit du flux secondaire de liquide.Advantageously, the annular passage has a predetermined radial extension in order to calibrate the flow rate of the secondary flow of liquid.

De préférence, l'extension radiale correspond au jeu radial existant entre le disque et le carter.Preferably, the radial extension corresponds to the radial clearance existing between the disk and the casing.

Avantageusement, le flux secondaire de liquide est également utilisé pour refroidir un élément tournant de la machine.Advantageously, the secondary flow of liquid is also used to cool a rotating element of the machine.

Ainsi, le flux secondaire de liquide constitue un flux de liquide de refroidissement. En ce cas, ce flux de liquide de refroidissement est avantageusement calibré de telle sorte que le refroidissement de l'élément tournant est suffisant.Thus, the secondary stream of liquid is a flow of coolant. In this case, this flow of coolant is advantageously calibrated so that the cooling of the rotating element is sufficient.

Au sens de l'invention, un élément tournant est un élément dont au moins une pièce constitutive est entraînée en rotation par l'arbre.Within the meaning of the invention, a rotating element is an element of which at least one component is rotated by the shaft.

De préférence, l'élément tournant est un palier, un moteur et/ou un générateur électrique. La machine selon l'invention peut comporter plusieurs éléments tournants choisis parmi les éléments précités.Preferably, the rotating element is a bearing, a motor and / or an electric generator. The machine according to the invention may comprise a plurality of rotating elements chosen from the abovementioned elements.

Comme l'élément tournant s'échauffe lors du fonctionnement de la machine, il est nécessaire de le refroidir.As the rotating element heats up during operation of the machine, it is necessary to cool it.

Grâce à l'invention, on utilise le même flux de liquide pour refroidir l'élément tournant et pour alimenter le système d'équilibrage axial passif. Il n'est donc pas nécessaire de prévoir des circuits distincts, ce qui permet de simplifier avantageusement la structure de la machine.Thanks to the invention, the same flow of liquid is used to cool the rotating element and to feed the passive axial balancing system. It is therefore not necessary to provide separate circuits, which allows to advantageously simplify the structure of the machine.

Selon une première variante, la machine tournante est une pompe.According to a first variant, the rotating machine is a pump.

Selon une deuxième variante, la machine tournante est une turbine.According to a second variant, the rotating machine is a turbine.

L'invention sera mieux comprise et ses avantages apparaîtront mieux à la lecture de la description détaillée qui suit, d'un mode de réalisation indiqué à titre d'exemple non limitatif. La description se réfère aux dessins annexés sur lesquels :

  • la figure 1 est une vue en coupe d'une machine tournante selon la présente invention, cette dernière étant une pompe ;
  • la figure 2 est une vue de détail de la machine tournante de la figure 1 , représentant le système d'équilibrage axial passif selon l'invention.
The invention will be better understood and its advantages will appear better on reading the detailed description which follows, of an embodiment indicated by way of non-limiting example. The description refers to the accompanying drawings in which:
  • the figure 1 is a sectional view of a rotating machine according to the present invention, the latter being a pump;
  • the figure 2 is a detail view of the rotating machine of the figure 1 , representing the passive axial balancing system according to the invention.

La figure 1 représente un exemple d'une machine tournante 10 conforme à la présente invention, cette machine tournante 10 étant destinée préférentiellement mais non exclusivement au pompage de fluide tel du gaz liquéfié. Elle peut avantageusement être utilisée pour vider les cuves d'un méthanier.The figure 1 represents an example of a rotary machine 10 according to the present invention, this rotating machine 10 being intended preferentially but not exclusively to pumping fluid such as liquefied gas. It can advantageously be used to empty the tanks of a LNG carrier.

L'exemple représenté sur la figure 1 n'est pas limitatif, la machine tournante selon l'invention pouvant également être une turbine dans laquelle circule un liquide entraînant un générateur qui fournit une puissance électrique.The example shown on the figure 1 is not limiting, the rotating machine according to the invention may also be a turbine in which circulates a liquid driving a generator that provides an electric power.

Dans la description qui suit, les adjectifs « axial » , « tangentiel » et « radial » sont définis par rapport à l'axe de rotation A de la machine 10. In the description which follows, the adjectives "axial", "tangential" and "radial" are defined with respect to the axis of rotation A of the machine 10.

La machine tournante 10 étant généralement destinée à être disposée verticalement, on définit les adjectifs « bas » et « haut » en référence à la direction verticale.Since the rotating machine 10 is generally intended to be arranged vertically, the adjectives "low" and "high" are defined with reference to the vertical direction.

Considérée selon la direction d'aspiration du flux principal de liquide schématisé ici par les flèches référencées F1, la machine 10 comprend successivement un étage d'aspiration 12, une roue centrifuge 14 et une conduite annulaire 16 permettant le refoulement du liquide aspiré.Considered according to the suction direction of the main flow of liquid shown schematically by the arrows referenced F1, the machine 10 successively comprises a suction stage 12, a centrifugal wheel 14 and an annular duct 16 for discharging the aspirated liquid.

L'étage d'aspiration 12 comporte un inducteur 18 rotatif entraîné en rotation par un arbre de rotation 20 de la machine 10, l'arbre de rotation 20 étant quant à lui entraîné par un élément tournant constitué par un moteur électrique 22. The suction stage 12 comprises a rotary inductor 18 driven in rotation by a rotation shaft 20 of the machine 10, the rotation shaft 20 being driven by a rotating element consisting of an electric motor 22.

Le moteur électrique 22 comporte un rotor 24 fixé à l'arbre 20 et un stator 26 fixé à un carter 28 de la machine 10. The electric motor 22 comprises a rotor 24 fixed to the shaft 20 and a stator 26 fixed to a housing 28 of the machine 10.

Comme on le constate sur la figure 1 , l'arbre de rotation 20 est monté rotatif sur le carter 28 par l'intermédiaire d'un palier bas 30 situé entre la roue centrifuge et 14 et le moteur 22, et d'un palier haut 32 situé entre le moteur 22 et un manchon de refoulement 34. As we see on the figure 1 , the rotation shaft 20 is rotatably mounted on the housing 28 via a low bearing 30 located between the centrifugal wheel and 14 and the motor 22, and a high bearing 32 located between the motor 22 and a discharge sleeve 34.

L'arbre de rotation 20 comporte un épaulement 36 venant en butée axiale contre une bague intérieure 38 du palier bas 30. The rotation shaft 20 comprises a shoulder 36 coming into axial abutment against an inner ring 38 of the low bearing 30.

La machine 10 étant disposée verticalement, on comprend que le palier bas 30 supporte le poids de l'arbre de rotation, de la roue centrifuge 14, du rotor 24 et de l'inducteur 18, poids auquel s'ajoute la force de traction subie par l'inducteur 18 lors de l'aspiration du liquide.The machine 10 being arranged vertically, it is understood that the low bearing 30 supports the weight of the rotation shaft, the centrifugal wheel 14, the rotor 24 and the inductor 18, weight plus the tensile force undergone by the inductor 18 during the suction of the liquid.

Pour reprendre au moins en partie la résultante des efforts mentionnés ci-dessus, la machine 10 comporte en outre un système d'équilibrage axial actif 40, bien connu par ailleurs, apte à exercer sur l'arbre 20 une première force de reprise axiale R1. To take back at least partly the resultant of the efforts mentioned above, the machine 10 further comprises an active axial balancing system 40, well known elsewhere, capable of exerting on the shaft 20 a first axial recovery force R1 .

Cette reprise d'effort est réalisée grâce à la première force de reprise axial R1 opposée à la résultante des efforts mentionnés ci-dessus.This recovery effort is achieved through the first axial resumption force R1 opposite to the resultant efforts mentioned above.

De manière connue, le système d'équilibrage axial actif 40 permet en outre la régulation de l'intensité de la première force de reprise axiale R1. Plus précisément, la régulation dépend du déplacement axial de l'arbre 20 par rapport au carter 28. In known manner, the active axial balancing system 40 further allows the regulation of the intensity of the first axial recovery force R1. More precisely, the regulation depends on the axial displacement of the shaft 20 relative to the casing 28.

En pratique, si l'intensité de la première force de reprise axiale R1 est supérieure à celle de la résultante des efforts à reprendre, le système d'équilibrage axial actif 40 opère une régulation en diminuant l'intensité de la première force de reprise axiale R1. In practice, if the intensity of the first axial take-up force R1 is greater than that of the resultant of the forces to be resumed, the active axial balancing system 40 operates a regulation by decreasing the intensity of the first axial recovery force. R1.

Il a été constaté que le système d'équilibrage axial actif 40 n'est pas suffisamment performant lorsque le débit du flux principal de liquide F1 pompé est faible. Plus précisément, il a été constaté que les moyens de régulation ne fonctionnent pas correctement pour des faibles débits.It has been found that the active axial balancing system 40 is not sufficiently efficient when the flow rate of the main fluid flow F1 pumped is low. More specifically, it has been found that the regulation means do not work correctly for low flow rates.

Pour remédier à cet inconvénient, la machine tournante 10 comporte en outre, de manière particulièrement avantageuse, un système d'équilibrage axial passif 42, mieux visible sur la figure 2 , qui est apte à exercer sur l'arbre 20 une deuxième force de reprise axiale R2. To remedy this drawback, the rotating machine 10 also comprises, in a particularly advantageous manner, a passive axial balancing system 42, better visible on the figure 2 Which is capable of exerting on the shaft 20 a second axial take-up force R2.

Ce système d'équilibrage axial 42 est passif, c'est-à-dire que, contrairement au système d'équilibrage axial actif, la deuxième force de reprise axiale R2 est indépendante du déplacement axial de l'arbre 20 par rapport au carter 28. This axial balancing system 42 is passive, that is to say that, unlike the active axial balancing system, the second axial recovery force R2 is independent of the axial displacement of the shaft 20 relative to the housing 28. .

A l'aide de la figure 2, on voit que le système d'équilibrage axial passif 42 comporte un disque 44 fixé à l'extrémité supérieure de l'arbre 20.Using the figure 2 it can be seen that the passive axial balancing system 42 comprises a disk 44 fixed to the upper end of the shaft 20.

Ce disque 44 est apte à coulisser dans un alésage 47 réalisé dans le carter 28.This disk 44 is able to slide in a bore 47 made in the casing 28.

De préférence, le palier haut 32 est monté entre le disque 44 et un épaulement 45 de l'arbre 20.Preferably, the high bearing 32 is mounted between the disk 44 and a shoulder 45 of the shaft 20.

De préférence, le disque 44 comporte à sa périphérie un joint labyrinthe annulaire 46. On peut toutefois prévoir d'autres types de joints.Preferably, the disc 44 has at its periphery an annular labyrinth seal 46. However, other types of joints may be provided.

Conformément à l'invention, le système d'équilibrage axial passif 42 est alimenté par un circuit d'un flux secondaire de liquide F2 qui est prélevé sur le flux principal de liquide F1, en l'espèce grâce à un passage radial 49 ménagé dans une surface intérieure 51 de la conduite annulaire 16.According to the invention, the passive axial balancing system 42 is fed by a circuit of a secondary flow of liquid F2 which is taken from the main flow of liquid F1, in this case thanks to a radial passage 49 formed in an inner surface 51 of the annular pipe 16.

Comme on le voit sur la figure 1, ce flux secondaire F2 traverse l'entrefer 48 du moteur 22, grâce à quoi le moteur est avantageusement refroidi.As we see on the figure 1 this secondary flow F2 passes through the gap 48 of the motor 22, whereby the motor is advantageously cooled.

A l'aide de la figure 2, on constate que le flux secondaire de liquide F2 traverse ensuite le palier haut 32, permettant ainsi de manière avantageuse le refroidissement dudit palier haut, avant de pénétrer dans une chambre fluidique amont 50 disposée axialement en amont du disque 44.Using the figure 2 it can be seen that the secondary flow of liquid F2 then passes through the high bearing 32, thus advantageously allowing cooling of said high bearing, before entering an upstream fluid chamber 50 arranged axially upstream of the disk 44.

Le flux secondaire de liquide F2 s'écoule ensuite au travers d'un passage annulaire 52 défini radialement entre la périphérie extérieure du disque 44 et le carter 28, puis s'écoule dans une chambre fluidique aval 54 disposée axialement en aval du disque 44. Cette chambre fluidique aval est de préférence reliée à un orifice d'évacuation 56 pour permettre l'évacuation du flux secondaire de liquide F2 vers l'extérieur de la machine tournante 10. Les termes « amont » et « aval » sont considérés ici par rapport au sens d'écoulement du flux secondaire de liquide F2.The secondary flow of liquid F2 then flows through an annular passage 52 defined radially between the outer periphery of the disc 44 and the casing 28, then flows in a downstream fluidic chamber 54 arranged axially downstream of the disc 44. This downstream fluidic chamber is preferably connected to a discharge orifice 56 to allow the discharge of the secondary liquid flow F2 towards the outside of the rotating machine 10. The terms "upstream" and "downstream" are considered here in relation to in the direction of flow of the secondary flow of liquid F2.

Comme on l'a représenté sur la figure 2, le passage annulaire 52 délimite axialement la chambre fluidique amont 50 de la chambre de fluidique aval 54.As shown on the figure 2 the annular passage 52 defines axially the upstream fluid chamber 50 of the downstream fluidic chamber 54.

Comme on l'a déjà mentionné, le passage annulaire 52 forme une restriction d'écoulement pour le flux secondaire de liquide F2, si bien que la pression dans la chambre fluidique amont 50 est supérieure à la pression dans la chambre fluidique aval 54.As already mentioned, the annular passage 52 forms a flow restriction for the secondary flow of liquid F 2, so that the pressure in the upstream fluid chamber 50 is greater than the pressure in the downstream fluidic chamber 54.

Il s'ensuit qu'il s'exerce sur une face latérale amont 58 du disque 44 une pression supérieure à celle qui s'exerce sur une face latérale aval 60 du disque 44. Cette différence de pression génère donc la deuxième force de reprise axiale R2 qui s'exerce sur l'arbre 20 via le disque 44.It follows that it exerts on an upstream side face 58 of the disk 44 a pressure greater than that which is exerted on a downstream side face 60 of the disk 44. This pressure difference thus generates the second axial recovery force R2 which is exerted on the shaft 20 via the disk 44.

On comprend en outre que l'intensité de cette deuxième force de reprise axiale R2 dépend du jeu radial entre le disque 44 et le carter 28 et non pas du déplacement de l'arbre 20 par rapport au carter 28. It is furthermore understood that the intensity of this second axial recovery force R2 depends on the radial clearance between the disk 44 and the casing 28 and not on the displacement of the shaft 20 with respect to the casing 28.

Pour cette raison, on qualifie de "passif" le système d'équilibrage axial 42. Par conséquent, la force de reprise axiale globale R s'exerçant sur l'arbre 20 est la somme des première et deuxième forces de reprise axiale R1, R2. For this reason, the "axial" balancing system 42 is termed "passive". Consequently, the overall axial recovery force R acting on the shaft 20 is the sum of the first and second axial recovery forces R1, R2 .

De manière particulièrement avantageuse, le système d'équilibrage axial passif 42 comporte en outre des moyens de calibrage pour calibrer le débit du flux secondaire de liquide F2. En l'espèce, ces moyens de calibrage comprennent le passage annulaire 52. Particularly advantageously, the passive axial balancing system 42 further comprises calibration means for calibrating the flow rate of the secondary liquid flow F2. In this case, these calibration means comprise the annular passage 52.

En l'espèce, le passage annulaire 52 présente une extension radiale e prédéterminée afin de calibrer le débit du flux secondaire de liquide F2. In this case, the annular passage 52 has a radial extension e predetermined to calibrate the flow of the secondary liquid flow F2.

Cette extension radiale e est définie entre la périphérie extérieure du disque 44 et le carter 28. This radial extension e is defined between the outer periphery of the disk 44 and the casing 28.

Comme on l'a vu ci-dessus, le flux secondaire de liquide F2 est également utilisé, de manière avantageuse, pour refroidir des éléments tournants de la machine 10, en l'espèce le moteur 22 et le palier 32. As has been seen above, the secondary flow of liquid F 2 is also advantageously used for cooling rotary elements of the machine 10, in this case the motor 22 and the bearing 32.

II est avantageux de calibrer le débit de ce flux de liquide de refroidissement car un débit trop faible ne refroidirait pas suffisamment les éléments tournants, tandis qu'un débit trop important diminuerait le rendement de la machine, lequel rendement est fonction du débit du flux principal de liquide F1. On comprend en effet que si l'on prélève un flux secondaire de liquide F2 trop important, le flux principal F1 est diminué d'autant.It is advantageous to calibrate the flow rate of this coolant flow because too low a flow rate would not sufficiently cool the rotating elements, while a too high flow rate would reduce the efficiency of the machine, which output is a function of the flow of the main flow of F1 liquid . It is understood that if we take a secondary flow of liquid F2 too large, the main flow F1 is reduced accordingly.

En d'autres termes, grâce à l'invention, le débit du flux de refroidissement moteur est calibré de manière constante, quelle que soit la position axiale du rotor 24. In other words, thanks to the invention, the flow rate of the engine cooling flow is calibrated in a constant manner, whatever the axial position of the rotor 24.

Comme on l'a déjà mentionné ci-dessus, la machine tournante selon l'invention peut également être une turbine. En ce cas, le flux principal de liquide présente un sens d'écoulement opposé à celui du flux principal de liquide F1 de la machine fonctionnant en pompe. En revanche, le flux secondaire de liquide dans la turbine présente le même sens d'écoulement que celui du flux secondaire de liquide F2 circulant dans la pompe.As already mentioned above, the rotating machine according to the invention can also be a turbine. In this case, the main flow of liquid has a direction of flow opposite to that of the main flow of liquid F1 of the machine operating as a pump. On the other hand, the secondary flow of liquid in the turbine has the same direction of flow as that of the secondary flow of liquid F2 circulating in the pump.

Claims (13)

  1. A rotary machine (10) for passing a main liquid stream (F1), the machine comprising:
    - a shaft (20) mounted to rotate relative to a casing (28) of the rotary machine;
    - an active axial balancing system (40) suitable for exerting a first axial take-up force (R1) on the shaft, the intensity of the first axial take-up force depending on the displacement of the shaft relative to the casing; and
    - a centrifugal impeller (14) mounted on the shaft:
    said machine being characterized in that it further comprises a circuit for a secondary liquid stream (F2) taken from the main liquid stream (F1), and a passive axial balancing system (42) that is distinct from the active axial balancing system and from the centrifugal impeller, and that is suitable for exerting a second axial take-up force (R2) on the shaft (20), said passive axial balancing system (42) being fed by the circuit for the secondary liquid stream (F2), and the second axial take-up force not being servo-controlled to the displacement of the shaft relative to the casing.
  2. A rotary machine according to claim 1, characterized in that the passive axial balancing system has an annular passage (52) between the shaft (20) and the casing (28) through which the secondary liquid stream (F2) is to flow, said passage axially separating an upstream fluidic chamber (50) from a downstream fluidic chamber (54) in such a manner that the pressure in the upstream fluidic chamber is greater than the pressure in the downstream fluidic chamber.
  3. A rotary machine according to claim 2, characterized in that the downstream fluidic chamber (54) is connected to a discharge orifice (56).
  4. A rotary machine according to claim 2 or claim 3, characterized in that the annular passage (52) is defined between the casing (28) and a disk (44) secured to the shaft (20).
  5. A rotary machine according to claim 4, characterized in that the disk (44) is secured to one end of the shaft (20).
  6. A rotary machine according to claim 4 or claim 5, characterized in that the disk (44) includes at its periphery an annular labyrinth seal (46).
  7. A rotary machine according to any one of claims 1 to 6, characterized in that the passive axial balancing system (42) further comprises means (52) for calibrating the flow rate of the secondary liquid stream (F2).
  8. A rotary machine according to claims 2 and 7, characterized in that the means for calibrating the flow rate of the secondary liquid stream comprise said annular passage (52).
  9. A rotary machine according to claim 8, characterized in that the annular passage presents a predetermined radial extent (e) for the purpose of calibrating the flow rate of the secondary liquid stream (F2).
  10. A rotary machine according to any one of claims 1 to 9, characterized in that the secondary liquid stream (F2) is also used for cooling a rotary element (22, 32) of the machine.
  11. A rotary machine according to claim 10, characterized in that the rotary element is a bearing (32), a motor (22), and/or an electricity generator.
  12. A rotary machine (10) according to any one of claims 1 to 11, characterized in that it is a pump.
  13. A rotary machine (10) according to any one of claims 1 to 11, characterized in that it is a turbine.
EP08155267A 2007-04-30 2008-04-28 Rotating machine comprising a passive axial balancing system Active EP1988292B1 (en)

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FR0754787A FR2915535B1 (en) 2007-04-30 2007-04-30 ROTATING MACHINE COMPRISING A PASSIVE AXIAL BALANCING SYSTEM

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EP1988292B1 true EP1988292B1 (en) 2010-12-29

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EP (1) EP1988292B1 (en)
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FR2915535B1 (en) 2009-07-24
FR2915535A1 (en) 2008-10-31
KR101550748B1 (en) 2015-09-07
EP1988292A1 (en) 2008-11-05
US20080267763A1 (en) 2008-10-30
JP2008278743A (en) 2008-11-13
JP5650372B2 (en) 2015-01-07
KR20080097111A (en) 2008-11-04

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