EP0002157A1 - Pump - Google Patents

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Publication number
EP0002157A1
EP0002157A1 EP78400182A EP78400182A EP0002157A1 EP 0002157 A1 EP0002157 A1 EP 0002157A1 EP 78400182 A EP78400182 A EP 78400182A EP 78400182 A EP78400182 A EP 78400182A EP 0002157 A1 EP0002157 A1 EP 0002157A1
Authority
EP
European Patent Office
Prior art keywords
disc
pump
spiral
shaft
wheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP78400182A
Other languages
German (de)
French (fr)
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EP0002157B1 (en
Inventor
Jean-Claude Villard
Gilbert Berthereau
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Application filed by Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Publication of EP0002157A1 publication Critical patent/EP0002157A1/en
Application granted granted Critical
Publication of EP0002157B1 publication Critical patent/EP0002157B1/en
Expired legal-status Critical Current

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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
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance

Definitions

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

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

Abstract

La présente invention concerne la réalisation des étanchéités interne et de sortie d'arbre d'une pompe. De part et d'autre d'une roue à aubes 5 est ménagé un couple de disques coaxiaux (22-23) et (24-25), la face d'un disque étant lisse et la face de l'autre disque présentant des rainures spirales, l'un des disques de chaque couple étant solidaire en rotation de la roue 5, le tout de façon que le liquide entre deux disques subisse un accroissement de pression radialement vers l'extérieur compensant au moins l'accroîssement de pression dû au pompage par la roue 5. Application notamment aux pompes pour liquides cryogéniques.The present invention relates to the production of internal seals and shaft outlet of a pump. On either side of an impeller 5 is formed a pair of coaxial discs (22-23) and (24-25), the face of a disc being smooth and the face of the other disc having spiral grooves, one of the discs of each pair being integral in rotation with the wheel 5, the whole so that the liquid between two discs undergoes an increase in pressure radially outward compensating at least the increase in pressure due to the pumping by the wheel 5. Application in particular to pumps for cryogenic liquids.

Description

La présente invention concerne une pompe du genre à roue à aubes montée en bout d'un arbre menant et placée dans un carter, chaque aube formant un conduit s'étendant d'un côté dans un corps axial de roue et débouchant en regard d'un conduit d'aspiration et d'un autre c8té radialement dans un voile de roue à extension radiale défilant en regard d'un conduit de refoulement tangentiel.The present invention relates to a pump of the paddle wheel type mounted at the end of a driving shaft and placed in a casing, each blade forming a conduit extending on one side in an axial wheel body and emerging opposite. a suction duct and another radially c8té in a wheel extension with radial extension running opposite a tangential delivery duct.

Les pompes actuellement connues sont rendues étanches au niveau de leur conduit d'aspiration, entre roue et carter (étanchéité dite interne) et au niveau de la sortie d'arbre au travers du carter, par une configuration en labyrinthe de l'une des parties (fixe ou rotative) par rapport à l'autre, généralement associée à des joints d'étanchéité en matériau résistant à l'usure par frottement. Malgré ces dispositions, on est obligé de procéder à d'assez fréquents changements de joints et cela d'autant plus fréquemment que le liquide pompé est à une température très différente de la température ambiante, qu'elle soit très chaude ou très froide. En outre, les défauts d'étanchéité, notamment de l'étanchéité interne, conduisent à des fuites qui généralement sont "recirculées" à l'aspiration de la pompe, ce qui contrecarre l'obtention d'un bon rendement de pompage.Currently known pumps are sealed at their suction duct, between impeller and housing (so-called internal sealing) and at the level of the shaft outlet through the housing, by a labyrinth configuration of one of the parts (fixed or rotary) with respect to the other, generally associated with seals made of material resistant to wear by friction. Despite these provisions, it is necessary to make fairly frequent changes of seals and all the more frequently that the pumped liquid is at a temperature very different from the ambient temperature, whether it is very hot or very cold. In addition, leaks, particularly of the internal seal, lead to leaks which are generally "recirculated" when the pump is sucked, which counteracts obtaining good pumping performance.

Un objet de l'invention vise à réaliser des étanchéités de pompe, qui soient particulièrement efficaces en ce qu'elles évitent à coup sûr les fuites indésirables, ce qui améliore le rendement, et qui de surcroît présentent une usure par frottement quasiment nulle, ce qui confère à la pompe ainsi équipée une très longue durée de vie et, en même temps, conduit à une maintenance particulièrement réduite; une pompe selon l'invention présente une très grande sécurité d'utilisation.An object of the invention is to provide pump seals, which are particularly effective in that they undoubtedly avoid undesirable leaks, which improves the yield, and which moreover have almost zero wear by friction, this which gives the pump thus equipped a very long service life and, at the same time, leads to particularly reduced maintenance; a pump according to the invention has very high safety in use.

La pompe selon l'invention est caractérisée en ce que la roue de pompe est montée à léger débattement axial et en ce que le disque du dispositif d'étanchéité d'aspiration est monté en bout d'un moyeu axialement élastique et étanche, tel qu'un soufflet,fixé au carter autour d'un passage d'aspiration dudit carter. L'invention représente donc une transposition et une adaptation particulière aux pompes de la technique des paliers à rainures spirales qui a été proposée jusqu'à maintenant essentiellement pour servir de butée axiale à un arbre soumis à une forte poussée axiale, ce qui est le cas généralement de la plupart des pompes et turbines, ou de support d'arbre. Cette technique est décrite dans quelques publications, notamment dans un article intitulé "Nouvelles formes de paliers : les paliers à gaz et à rainure spirale " par E.A. HUIJD£RHAN paru dans la " Revue Technique PHILIPS", tome 25, 1963/64 n° 9 - page 245 à 266. Brièvement résumée, cette technique consiste à "pomper" un fluide, qui est généralement un gaz, radialement vers le centre des deux disques, ce qui provoque un écartement des disques, en sorte que le supportage de la partie mobile en rotation s'effectue par l'intermédiaire du fluide en question. Un mérite de la présente invention est d'avoir discerné l'intérêt de cette technique pour assurer les étanchéités d'une pompe grâce à l'utilisation, à titre de fluide d'étanchéité, du liquide à pomper lui-même, et de prévoir les adaptations particulières à cette application qui consistent notamment à provoquer un accroissement centrifuge de la pression du fluide d'étanchéité, ce qui détermine un sens particulier de rotation du disque lisse par rapport au disque à rainures spirales, (alors que le sens centrifuge ou centripète, de l'effet de pompage est indifférent dans les applications proposées précédemment de butée axiale et de supportage d'arbre) et à doser cet accroissement de pression par des modalités constructives résultant de calculs et d'expérimentations relativement complexes, de façon à ce qu'il corresponde substantiellement à l'accroissement de pression dû à l'effet de pompage. De la sorte, la contre-pression ainsi développée à l'endroit des jonctions permet d'obtenir, lors de la rotation de la roue, un blocage complet des fuites sans aucune usure des pièces tournant l'une par rapport à l'autre, qui sont séparées par un mince film liquide débordant des rainures spirales pour s'interposer entre les portées saillantes entre rainures du disque à rainures à spirales et la face lisse de l'autre disque en regard, alors qu'un certain frottement de pièces a lieu exclusivement aux moments du démarrage et de l'arrêt de la pompe et que des fuites le long des rainures peuvent intervenir à l'arrêt, si l'on ne met pas en oeuvre certaines mesures techniques détaillées plus loin, également conformes à l'invention. Ce procédé est particulièrement indiqué dans le domaine des pompes cryogéniques en évitant les jonctions à frottement solides subissant d'importantes contraintes thermiques. En outre, la mise en route d'une pompe cryogénique est rendue plus aisée et plus rapide gràce aux jonctions hydrodynamiques décrites. De plus, les arbres du moteur et de la pompe peuvent ne pas être alignés de façon aussi rigoureuse que dans les groupes moto-pompes classiques et l'on peut même, si on le désire, supprimer le supportage de pompe par le bloc moteur, ce qui réduit les pertes thermiques par conduction le long de ce supportage. On comprend également qu'on simplifie considérablement la technique de réalisation des pompes en même temps qu'on allège leur poids.The pump according to the invention is characterized in that the pump wheel is mounted with slight axial clearance and in that the disc of the suction sealing device is mounted at the end of an axially elastic and sealed hub, such that 'a bellows, fixed to the housing around a suction passage of said housing. The invention therefore represents a transposition and a particular adaptation to pumps of the technique of spiral groove bearings which has been proposed until now essentially to serve as an axial stop for a shaft subjected to a strong axial thrust, which is the case. usually from most pumps and turbines, or from shaft support. This technique is described in some publications, in particular in an article entitled "New forms of bearings: gas bearings and spiral grooves" by EA HUIJD £ RHAN published in "Revue Technique PHILIPS", tome 25, 1963/64 n ° 9 - page 245 to 266. Briefly summarized, this technique consists in "pumping" a fluid, which is generally a gas, radially towards the center of the two discs, which causes a separation of the discs, so that the support of the part mobile in rotation is effected by the medium in question. A merit of the present invention is to have discerned the advantage of this technique for ensuring the tightness of a pump through the use, as sealing fluid, of the liquid to be pumped itself, and to provide the particular adaptations to this application which notably consist in causing a centrifugal increase in the pressure of the sealing fluid, which determines a particular direction of rotation of the smooth disc relative to the disc with spiral grooves, (while the centrifugal or centripetal direction , the pumping effect is indifferent in the previously proposed applications of axial stop and shaft support) and to measure this increase in pressure by constructive methods resulting from relatively complex calculations and experiments, so that 'It corresponds substantially to the increase in pressure due to the pumping effect. In this way, the back pressure thus developed at the junctions makes it possible, during rotation of the wheel, to completely block the leaks without any wear of the parts rotating relative to each other, which are separated by a thin liquid film projecting from spiral grooves to interpose between the sail spans lantes between grooves of the spiral grooved disc and the smooth face of the other facing disc, while a certain friction of parts takes place exclusively at the times of starting and stopping the pump and that leaks along grooves can intervene when stopped, if certain technical measures detailed below, which are also in accordance with the invention, are not implemented. This process is particularly indicated in the field of cryogenic pumps by avoiding solid friction junctions undergoing significant thermal stresses. In addition, the start-up of a cryogenic pump is made easier and faster thanks to the hydrodynamic junctions described. In addition, the shafts of the motor and the pump may not be aligned as rigorously as in conventional motor-pump groups and it is even possible, if desired, to remove the support of the pump by the motor block, which reduces heat losses by conduction along this support. It is also understood that the technique for producing the pumps is considerably simplified at the same time as their weight is reduced.

Les caractéristiques et avantages de l'invention ressortiront d'ailleurs de la description qui suit, à titre d'exemple, en référence aux dessins annexés dans lesquels :

  • - la figure 1 est une vue en coupe axiale d'une pompe selon l'invention ;
  • - la figure 2 est une vue à échelle agrandie selon la ligne II-II de la figure 1 ;
  • - la figure 3 est une vue en coupe axiale d'une variante de réalisation ;
  • - la figure 4 est une vue schématique en coupe axiale d'une autre variante de réalisation.
The characteristics and advantages of the invention will become apparent from the following description, by way of example, with reference to the accompanying drawings in which:
  • - Figure 1 is an axial sectional view of a pump according to the invention;
  • - Figure 2 is an enlarged view along the line II-II of Figure 1;
  • - Figure 3 is an axial sectional view of an alternative embodiment;
  • - Figure 4 is a schematic view in axial section of another alternative embodiment.

En se référant aux figures 1 et 2, une pompe cryogénique comporte un arbre 1 d'un moteur 2 s'étendant au travers d'un support 3 vers un carter de pompe 4, où l'arbre 1 reçoit, en bout, une roue à aubes 5 formant une pluralité d'aubes constituées de conduits identiques 6 disposés autour de l'arbre 1 et présentant une partie d'aspiration axiale 7 dans un corps de roue 5' situé au voisinage de l'arbre 1 et une partie de refoulement radiale 8 dans un voile de roue 5" à extension radiale. Les parties d'aspiration 7 débouchent en regard d'une ouverture de carter 9 sur laquelle est fixée, par bride 10, un conduit d'alimentation 11. Les parties de refoulement 8 débouchent dans le carter de pompe 4 en défilant en regard d'un conduit de refoulement tangentiel 12.Referring to Figures 1 and 2, a cryogenic pump comprises a shaft 1 of a motor 2 extending through a support 3 towards a pump casing 4, where the shaft 1 receives, at the end, a wheel with blades 5 forming a plurality of blades made up of identical conduits 6 arranged around the shaft 1 and having an axial suction part 7 in a wheel body 5 'situated in the vicinity of the shaft 1 and a delivery part radial 8 in a 5 "wheel flap with radial extension. The suction parts 7 open out opposite a casing opening 9 on which is fixed, by flange 10, a supply duct 11. The discharge parts 8 open into the pump casing 4 while passing opposite a tangential discharge duct 12.

La roue à aubes 5 est associée à deux moyens principaux d'étanchéité, l'un de ces moyens désigné globalement par 13 se situe côté "sortie d'arbre" et vise à empêcher les fuites de liquide s'écoulant entre une paroi frontale 14 de la roue à aubes 5 et une paroi transversale 15 du carter de pompe 4 (selon la flèche f1) d'une part, entre l'arbre 1 et un moyeu 16 de la roue à aubes 5 vers l'aspiration (selon flèche f2) et accessoirement le long de l'arbre 1 vers l'extérieur (selon flèche f3), l'autre moyen d'étanchéité, désigné globalement par 18, se situe "c8té aspiration" de la pompe et vise à éviter les fuites de recirculation de liquide, qui risquent de se produire entre une extrémité 19 de la roue à aubes 5 et une autre paroi 20, incorporant l'ouverture d'aspiration 9, du carter de pompe 4.The impeller 5 is associated with two main sealing means, one of these means generally designated by 13 is located on the "shaft outlet" side and aims to prevent leaks of liquid flowing between a front wall 14 of the impeller 5 and a transverse wall 15 of the pump housing 4 (according to arrow f 1 ) on the one hand, between the shaft 1 and a hub 16 of the impeller 5 towards the suction (according to arrow f 2 ) and incidentally along the shaft 1 outwards (according to arrow f 3 ), the other sealing means, generally designated by 18, is located "suction suction" of the pump and aims to avoid liquid recirculation leaks, which may occur between one end 19 of the impeller 5 and another wall 20, incorporating the suction opening 9, of the pump housing 4.

Les deux moyens d'étanchéité 13 et 18 sont tous deux constitués de deux disques annulaires radiaux en regard 22 et 23 pour le moyen d'étanchéité 13 et 24, 25 pour le moyen d'étanchéité 18. Les disques 22 et 24 sont solidarisés avec la roue à aubes 5, tandis que les disques 23 et 25 sont fixes en rotation, le disque 23 étant fixé sur la paroi de carter 15, tandis que le disque 25 est fixé de façon étanche, de préférence par sa périphérie intérieure 26, à une extrémité d'un soufflet 28, dont une autre extrémité 29 est fixée à la paroi de carter 20 à la périphérie de l'ouverture d'aspiration 9.The two sealing means 13 and 18 both consist of two opposite radial annular discs 22 and 23 for the sealing means 13 and 24, 25 for the sealing means 18. The discs 22 and 24 are secured with the impeller 5, while the discs 23 and 25 are fixed in rotation, the disc 23 being fixed on the casing wall 15, while the disc 25 is fixed in leaktight manner, preferably by its inner periphery 26, to one end of a bellows 28, of which another end 29 is fixed to the casing wall 20 at the periphery of the suction opening 9.

Chaque couple de disques 22 et 23 d'une part et 24, 25 d'autre part doit pouvoir venir en contact face contre face et s'écarter quelque peu l'un de l'autre et cela simultanément et dans le même sens pour les deux couples de disques 22 et 23, 24 et 25. A cet effet, puisque le disque 23 est non seulement immobilisé en rotation axiale, mais également en translation axiale, puisque solidarisé avec la paroi de carter 15, la roue à aubes 5 est montée avec un léger débattement axial sur l'arbre 1 grâce à des cannelures 30, interdisant cependant tout débattement en rotation, ce débattement axial étant d'ailleurs limité par une butée 31 plus ou moins vissées en bout d'arbre 1. Pour ce qui concerne le couple de disques 24, 25, puisque le disque 24 solidarisé avec la roue à aubes 5 est non seulement mobile en rotation, mais également subit des déplacements axiaux égaux et concomittents à ceux du disque 22, c'est-à-dire dans un sens qui est contraire à celui souhaité pour le disque 24 en regard du disque 25, on assure à ce dernier disque un assez fort débattement grâce à la présence du soufflet 28. On précise que c'est seulement à l'arrêt de la pompe, lorsque la roue à aubes 5 cesse de tourner que les disques 22 et 23 d'une part, 24 et 25 d'autre part doivent se rapprocher l'un de l'autre jusqu'à venir en appui face contre face. Ce rapprochement est assuré pour le disque 22 normalement par l'effet de poussée exercée sur la roue à aubes 5 en direction du moteur 2 due, au repos, à l'effet de pression -même résiduelle - sur la partie d'aspiration axiale 7 et pour le disque 25 par l'effet de pression exercée en fin de marche par la pression de refoulement, même résiduelle, dans le carter de pompe 4. On précise dès maintenant que cet effet de pression s'exerce sur les disques 22 (en direction du disque 23) et 25 (en direction du disque 24) non seulement à la fin d'une opération de pompage, mais également et d'ailleurs de façon accentuée pendant l'opération de pompage, car d'une part s'ajoute, dans la roue à aubes 5, à l'effet de pression statique sur la partie d'aspiration axiale 7, l'effet dynamique de circulation du liquide dans les conduits 6 s'exerçant dans le même sens et que d'autre part la pression de refoulement s'exerce dans toute sa plénitude sur toute la face du disque 25 grâce à la fixation du soufflet 28 le long de sa périphérie interne (alors qu'un soufflet de plus fort diamètre aurait diminué cet effet, car il aurait fait intervenir sur une partie radialement intérieure du disque 25 la seule pression d'aspiration plusieurs fois inférieure à la pression de refoulement). Mais cet effet accentué de pression tendant à rapprocher l'un vers l'autre les disques 22 et 23 d'une part, 24 et 25 d'autre part est combattu par un autre effet qu'on va maintenant expliciter, en sorte que c'est précisément pendant la rotation de la roue à aubes 5 que le disque 22 s'écarte du disque 23 et le disque 25 du disque 24.Each pair of discs 22 and 23 on the one hand and 24, 25 on the other hand must be able to come into contact face against face and deviate somewhat from each other and this simultaneously and in the same direction for the two pairs of discs 22 and 23, 24 and 25. For this purpose, since the disc 23 is not only immobilized in axial rotation, but also in axial translation, since it is secured to the casing wall 15, the impeller 5 is mounted with a slight axial movement on the shaft 1 by means of grooves 30, however preventing any rotation movement, this axial movement being moreover limited by a stop 31 more or less screwed at the end of the shaft 1. As regards the pair of discs 24, 25, since the disc 24 secured to the impeller 5 is not only mobile in rotation, but also undergoes axial displacements equal and concomitant with those of the disc 22, that is to say in a direction which is opposite to that desired for the disc 24 opposite the disc 25, this latter disc is provided with a fairly large clearance thanks to the presence of the bellows 28. It is specified that it is only when the pump is stopped, when the impeller 5 stops spinning that the discs 22 and 23 on the one hand, 24 and 25 on the other hand must approach each other until 'to come face to face. This approximation is ensured for the disc 22 normally by the pushing effect exerted on the impeller 5 towards the motor 2 due, at rest, to the pressure effect - even residual - on the axial suction part 7 and for the disc 25 by the pressure effect exerted at the end of the operation by the discharge pressure, even residual, in the pump casing 4. It is specified now that this pressure effect is exerted on the discs 22 (in direction of the disc 23) and 25 (towards the disc 24) not only at the end of a pumping operation, but also and moreover in an accentuated manner during the pumping operation, because on the one hand is added , in the impeller 5, to the effect of static pressure on the axial suction part 7, the dynamic effect of circulation of the liquid in the conduits 6 being exerted in the same direction and that on the other hand the discharge pressure is exerted in all its fullness on the entire face of the disc 25 thanks to the fixing of the bellows 28 along its internal periphery (whereas a bellows of larger diameter would have reduced this effect, because it would have involved on a radially inner part of the disc 25 the single suction pressure several times lower than the discharge pressure) . But this accentuated effect of pressure tending to bring discs 22 and 23 towards one another on the one hand, 24 and 25 on the other hand is combated by another effect which will now be explained, so that c It is precisely during the rotation of the impeller 5 that the disc 22 moves away from the disc 23 and the disc 25 from the disc 24.

En effet, pour chaque couple de disques 22, 23 et 24, 25, le disque en rotation 22 (ou 24) présente une face en regard de lau- tre disque, qui est tout à fait lisse, tandis que dans la face de l'autre disque 23 ou 25 respectivement qui est fixe en rotation a été pratiquée une pluralité de rainures en forme de spirales 40 (voir figure 2) de profondeur égale à quelques centièmes de millimètre, dégageant entre elles, un nombre égal de portées saillantes en spirales 41 qui, avantageusement, ont la même surface transversale que les gorges 40.Indeed, for each pair of discs 22, 23 and 24, 25, the rotating disc 22 (or 24) has a face opposite the- tre disc, which is quite smooth, while in the face of the other disc 23 or 25 respectively which is fixed in rotation was made a plurality of grooves in the form of spirals 40 (see Figure 2) of depth equal to a few hundredths of a millimeter, freeing between them, an equal number of projecting spiral bearing surfaces 41 which, advantageously, have the same transverse surface as the grooves 40.

De façon connue en soi, ainsi qu'il a été expliqué plus haut, une rotation dans le sens de la flèche F du disque mobile en rotation (22 ou 24) par rapport au disque fixe en rotation (23 ou 25 respectivement) provoque un important effet de pompage sur le liquide selon les flèches a et un accroissement notable de la pression depuis la périphérie interne (où cette pression est égale à la pression d'aspiration) vers la périphérie externe (où la pression qui règne est la pression de refoulement). On sait que cet accroissement de pression dépend de différents paramètres, dont notamment la nature et en particulier la viscosité du liquide, le nombre et la forme des rainures (qui ont toutefois toujours une allure logarithmique) et la vitesse de rotation (qui est ici imposée par le moteur travaillant sensiblement à vitesse constante). On peut ainsi déterminer, par le calcul et par des essais, un accroissement de pression tel qu'il est au moins égal et en tout cas peu supérieur à l'accroissement réel de pression dû à la roue à aubes 5 depuis la pression d'aspiration jusqu'à la pression de refoulement. Dans un tel cas, pendant le fonctionnement de la pompe, aucune fuite ne peut plus se produire entre le côté haute pression de refoulement et le côté basse pression d'aspiration par les deux voies possibles qui ont été équipées des moyens d'étanchéité décrits précédemment. A l'arrêt, l'effet dynamique sur le liquide entre les disques cesse, mais comme indiqué précédemment, la roue à aubes a tendance à s'arrêter dans une position qui applique le disque 22 contre le disque 23 et le disque 25 contre le disque 24 assurant ainsi une étanchéité satisfaisante bien que partielle, car les rainures spirales constituent alois autant de conduits de fuites présentant cependant une forte perte de charge du fait à la fois de leur allongement grâce à la forme en spirale et de leur très faible profondeur. On notera qu'on peut prévoir un ou plusieurs canaux 42 assurant un apport liquide suffisant au démarrage. Bien entendu, le moyen d'étanchéité d'arbre décrit sert également à recevoir la poussée axiale exercée sur la roue à aubes, supprimant ainsi toute autre disposition à cet effet.In a manner known per se, as explained above, a rotation in the direction of arrow F of the rotating mobile disc (22 or 24) relative to the fixed rotating disc (23 or 25 respectively) causes a significant pumping effect on the liquid according to arrows a and a significant increase in pressure from the internal periphery (where this pressure is equal to the suction pressure) to the external periphery (where the prevailing pressure is the discharge pressure ). We know that this pressure increase depends on different parameters, including in particular the nature and in particular the viscosity of the liquid, the number and the shape of the grooves (which however always have a logarithmic shape) and the speed of rotation (which is imposed here by the engine working substantially at constant speed). It is thus possible to determine, by calculation and by tests, an increase in pressure such that it is at least equal and in any case little greater than the real increase in pressure due to the impeller 5 from the pressure of suction up to discharge pressure. In such a case, during operation of the pump, no more leakage can occur between the high discharge pressure side and the low suction pressure side by the two possible channels which have been fitted with the sealing means described above. . When stopped, the dynamic effect on the liquid between the discs ceases, but as indicated above, the impeller tends to stop in a position which applies the disc 22 against the disc 23 and the disc 25 against the disc 24 thus ensuring a satisfactory although partial seal, because the spiral grooves constitute alois as many leakage conduits, however, having a high pressure drop due both to their elongation thanks to the spiral shape and their very shallow depth. It will be noted that one or more channels 42 can be provided ensuring a sufficient liquid supply. when the engine starts. Of course, the shaft sealing means described also serves to receive the axial thrust exerted on the impeller, thus eliminating any other provision for this purpose.

A la figure 3, qui est une version améliorée de la figure 1, une roue 30 à aubes 31, montée sur un arbre 32 est équipée,du côté de la sortie d'arbre, d'une paire de disques 33 et 34; le disque 33 est lisse et s'étend sur une assez grande extension radiale de la roue 30 à partir de la périphérie de l'arbre 32. Au contraire, le disque à spirales a une extension radiale moindre et se situe en regard d'une partie périphérique extérieure du disque 33. Le long d'un bord radialement intérieur du disque 34 est ménagéedans une paroi 35 d'un carter de pompe, une gorge annulaire 36 coaxiale à l'arbre 32 dans laquelle débouche un conduit 37 relié à une source extérieure de gaz. Au-delà de la gorge 36, en direction de l'arbre 32, est pratiquée dans la paroi de carter 35 une succession de rainures étagées en labyrinthes 38. De la sorte, on peut interdire en tout cas toute entrée d'air vers les disques 33 - 34, ce qui serait préjudiciable en cas de pompage de liquide cryogénique (risque de blocage par condensation solide de vapeur d'eau, ou entraînement d'impuretés dangereuses en cas de pompage d'oxygène liquide, par exemple en formant par insufflation de gaz "chaud" (qui parviendrait d'une phase gazeuse du liquide pompé par exemple) un bouchon contre toute entrée d'air susceptible d'être aspirée de l'atmosphère extérieure via la sortie d'arbre. On notera que pendant le fonctionnement de la pompe, la jonction à labyrinthe 38 permet d'éviter une trop grande fuite de gaz vers l'extérieur.In FIG. 3, which is an improved version of FIG. 1, a paddle wheel 30, mounted on a shaft 32 is equipped, on the side of the shaft outlet, with a pair of discs 33 and 34; the disc 33 is smooth and extends over a fairly large radial extension of the wheel 30 from the periphery of the shaft 32. On the contrary, the spiral disc has a lesser radial extension and is located opposite a outer peripheral part of the disc 33. Along an radially inner edge of the disc 34 is formed in a wall 35 of a pump housing, an annular groove 36 coaxial with the shaft 32 into which opens a conduit 37 connected to a source gas outside. Beyond the groove 36, in the direction of the shaft 32, there is formed in the casing wall 35 a succession of grooves stepped in labyrinths 38. In this way, any entry of air to the discs 33 - 34, which would be harmful in the event of pumping of cryogenic liquid (risk of blockage by solid condensation of water vapor, or entrainment of dangerous impurities in the event of pumping of liquid oxygen, for example by forming by insufflation of "hot" gas (which would come from a gaseous phase of the pumped liquid for example) a plug against any air intake likely to be sucked from the outside atmosphere via the shaft outlet. Note that during operation of the pump, the labyrinth junction 38 makes it possible to avoid too great a gas leak towards the outside.

Selon la variante de réalisation représentée à la figure 4, une roue à aubes 42 est ici équipée, côté sortie d'arbre 43,d'un disque rotatif lisse 44 à large extension radiale, tandis qu'une paroi de carter 45 est ici équipée d'un disque à rainures 46 s'étendant radialement sur une partie radialement extérieure du disquelie- se 44, tandis qu'en regard de la partie restante radialement intérieure 44' de disque lisse 44 est formée, sur la paroi de carter 45, une portée lisse 47 assurant une bonne étanchéité à l'arrêt de la pompe, les parties 46 et 47 étant séparées par une gorge 48. On obtient ainsi une meilleure étanchéité à l'arrêt de la pompe par appu face contre face de la partie radialement intérieure 44' du disque 44 et de la portée 47. En variante, cette portée 47 peut être ménagée radialement à l'extérieur du disque à rainures spirales 46 comme indiqué en 47'.According to the variant embodiment shown in FIG. 4, a paddle wheel 42 is here fitted, on the shaft outlet side 43, with a smooth rotating disc 44 with large radial extension, while a casing wall 45 is here fitted of a grooved disc 46 extending radially over a radially outer part of the disk 44, while facing the remaining radially inner part 44 'of smooth disc 44 is formed, on the casing wall 45, a smooth surface 47 ensuring a good seal when the pump stops, the parts 46 and 47 being separated by a groove 48. This gives a better seal when the pump stops by pressing against the face of the radially inner part 44 'of the disc 44 and the bearing 47. As a variant, this bearing 47 can be mena radially outside the spiral grooved disc 46 as shown in 47 '.

L'invention s'applique à toutes les pompes à roues, ou turbopompes pour le véhiculage de liquides, et plus particulièrement de liquides cryogéniques.The invention applies to all impeller pumps, or turbopumps for conveying liquids, and more particularly cryogenic liquids.

Claims (8)

1. Pompe, du genre à roue à aubes montée en bout d'un arbre menant et placée dans un carter, chaque aube formant un conduit s'étendant d'un côté dans un corps axial de roue et débouchant en regard d'un conduit d'aspiration et d'un autre côté radialement dans un voile de roue à extension radiale défilant en regard d'un conduit de refoulement tangentiel, ladite pompe étant équipée, à son côté sortie d'arbre d'une part, et à son côté d'aspiration d'autre part, d'une paire de disques en regard dont un est à rainures spirales, coaxiaux audit arbre, dont l'un est solidaire en rotation du carter de pompe et dont l'autre est solidaire en rotation de ladite roue de pompe, caractérisée en ce que la roue de pompe est montée à léger débattement axial et en ce que le disque du dispositif d'étanchéité d'aspiration est monté en bout d'un moyeu axialement élastique et étanche, tel qu'un soufflet, fixé au carter autour d'un passage d'aspiration dudit carter.1. Pump, of the paddle wheel type mounted at the end of a driving shaft and placed in a casing, each blade forming a duct extending on one side in an axial wheel body and opening opposite a duct suction and on the other side radially in a wheel runout with radial extension running opposite a tangential delivery duct, said pump being equipped, on its side with shaft output on the one hand, and on its side on the other hand, a pair of facing discs, one of which has spiral grooves, coaxial with said shaft, one of which is integral in rotation with the pump housing and the other of which is integral in rotation with said pump wheel, characterized in that the pump wheel is mounted with slight axial clearance and in that the disc of the suction sealing device is mounted at the end of an axially elastic and sealed hub, such as a bellows , fixed to the housing around a suction passage of said housing. 2. Pompe selon la revendication 1, caractérisée en ce que le disque du dispositif d'étanchéité d'aspiration est fixé au soufflet par sa périphérie radialement intérieure.2. Pump according to claim 1, characterized in that the disk of the suction sealing device is fixed to the bellows by its radially inner periphery. 3. Pompe selon l'une quelconque des revendications 1 et 2, caractérisée en ce que le disque à rainures spirales présente en outre une partie radiale lisse adaptée à venir en contact avec une partie en regard du disque lisse.3. Pump according to any one of claims 1 and 2, characterized in that the disc with spiral grooves further has a smooth radial part adapted to come into contact with a part facing the smooth disc. 4. Pompe selon la revendication 3, caractérisée en ce que la partie lisse du disque à spirales est située plus près de l'arbre que la partie à spirales du disque.4. Pump according to claim 3, characterized in that the smooth part of the spiral disc is located closer to the shaft than the spiral part of the disc. 5. Pompe selon la revendication 3, caractérisée en ce que la partie lisse du disque à spirales est située à une distance radiale de l'arbre plus éloignée que la partie à spirales du disque.5. Pump according to claim 3, characterized in that the smooth part of the spiral disc is located at a radial distance from the shaft more distant than the spiral part of the disc. 6. Pompe selon l'une quelconque des revendications 3 à 5, caractérisée en ce que le disque lisse est solidaire en rotation de de la roue, tandis qu'un disque à spirales est solidaire en rotation du carter.6. Pump according to any one of claims 3 to 5, characterized in that the smooth disc is integral in rotation with of the wheel, while a spiral disc is integral in rotation with the casing. 7. Pompe selon la revendication 1, caractérisée en ce que l'un des disques d'une paire de disques présente une gorge annulaire radialement intérieure à la partie à spirales du disque à spirales, ladite gorge étant raccordée par canalisation à une source de gaz, tandis qu'une partie radialement intérieure à ladite gorge forme un labyrinthe d'étanchéité.7. Pump according to claim 1, characterized in that one of the discs of a pair of discs has an annular groove radially internal to the spiral part of the spiral disc, said groove being connected by pipeline to a gas source , while a portion radially inside said groove forms a sealing labyrinth. 8. Pompe selon la revendication 1, caractérisée par une perforation dans le voile du corps de roue débouchant dans une zone radialement intérieure au dispositif d'étanchéité de sortie d'arbre.8. Pump according to claim 1, characterized by a perforation in the web of the wheel body opening into a zone radially internal to the shaft outlet sealing device.
EP78400182A 1977-11-22 1978-11-15 Pump Expired EP0002157B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7735036A FR2409406A1 (en) 1977-11-22 1977-11-22 PROCESS FOR REALIZING THE INTERNAL SEALS AND SHAFT OUTLET OF A PUMP AND PUMP IMPLEMENTING THIS PROCESS
FR7735036 1977-11-22

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EP0002157A1 true EP0002157A1 (en) 1979-05-30
EP0002157B1 EP0002157B1 (en) 1980-10-29

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DE (1) DE2860265D1 (en)
FR (1) FR2409406A1 (en)
IT (1) IT1100276B (en)

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Publication number Priority date Publication date Assignee Title
CN102588304A (en) * 2012-02-10 2012-07-18 宁波大叶园林设备有限公司 Centrifugal pump with swirl sprayer engine directly connected with high-speed function vane wheel and even-spinning labyrinth
CN102588304B (en) * 2012-02-10 2014-04-16 宁波大叶园林设备有限公司 Centrifugal pump with swirl sprayer engine directly connected with high-speed function vane wheel and even-spinning labyrinth
CN110410357A (en) * 2018-04-27 2019-11-05 爱信精机株式会社 Pump

Also Published As

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

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