EP0075506A1 - Turbine pump with adjustable stator blades - Google Patents

Turbine pump with adjustable stator blades Download PDF

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Publication number
EP0075506A1
EP0075506A1 EP82401648A EP82401648A EP0075506A1 EP 0075506 A1 EP0075506 A1 EP 0075506A1 EP 82401648 A EP82401648 A EP 82401648A EP 82401648 A EP82401648 A EP 82401648A EP 0075506 A1 EP0075506 A1 EP 0075506A1
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European Patent Office
Prior art keywords
fins
inlet
rotation
outlet
control
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German (de)
French (fr)
Inventor
Pierre Patin
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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2200/00—Mathematical features
    • F05B2200/20—Special functions
    • F05B2200/26—Special functions trigonometric
    • F05B2200/264—Cotangent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • the present invention relates to an improvement to turbopumps intended to provide them with a maximum efficiency practically independent of their flow rate and their rotational speed.
  • Turbopumps have undergone multiple improvements with a view to increasing their efficiency, in particular the layout and fineness of the rotor fins, as well as by the presence of fin guides placed upstream or downstream of the rotor, or both .
  • the optimum inclination of the steering fins depends on the speed of rotation of the rotor and the flow rate, hence the need to define a nominal speed and a nominal flow rate for which the output will be maximum and to accept a lower yield for the other possible values of speed and flow (or discharge pressure which is linked to the flow at a given speed, by the characteristic of the pump).
  • the present invention proposes an automatic orientation of the fins of the inlet director, so that the efficiency is maximum whatever the speed of rotation.
  • the turbopump according to the invention comprises an inlet director whose fins are orientable, an outlet director whose fins also pivoting are oriented under the action of the fluid, and means for controlling the angle of rotation inlet fins at the angle of rotation of the outlet fins.
  • the outlet fins are connected by connecting rod-crank assemblies to a first ring, the inlet fins to a second ring and a servo control the rotation of said second ring as a function of the rotation of said first crown.
  • said slave is designed so that the cotangent of the angle of rotation of the inlet fins is a linear function of the cotangent of the angle of rotation of the outlet fins.
  • This control can be achieved by a shaft fitted with two pinions which respectively mesh with said first and second crowns, or by a cam connecting said first and second crowns and whose profile is specially adapted, or by a motor which drives said second crown and who is enslaved in position by a logic circuit connected at input to an angular position sensor linked to said first ring.
  • FIGS. 1 and 2 make it possible to find the conventional elements of a turbopump: the rotor 1 with its fins 2, the inlet pipe 3 and the outlet volute 4.
  • the entry director (or before-director) is composed of fins 5, seven in number in the drawing, which, unlike the known embodiments, are orientable and not fixed. For this, they each have an axis 6 placed substantially in their median plane so that the pressures exerted by the fluid are substantially balanced on either side of the fin.
  • a core 7 is placed at the center of the inlet pipe 3; its external profile and that of the pipe 3 follow the path of the edges of the movable fins 5.
  • the optimal angle ⁇ 1 depends on the speed of rotation ⁇ and on the flow rate Q.
  • the efficiency of the turbopump is maximum for a given value of the speed of rotation ⁇ , only for a certain flow rate Q.
  • the turbopump according to the invention comprises, in addition to the inlet director with orientable fins 5, an outlet director (or rear director) whose fins 8 are pivotally mounted around one. axis 9 placed near the edge of the fin closest to the rotor 1.
  • This outlet director receives the fluid as soon as it leaves the fins 2 of the rotor 1 and until it arrives in the outlet volute 4. Its fins 8 are therefore subjected to the fluid outlet pressure which therefore tends to cause them to take an instantaneous inclination equal to the aforementioned angle ⁇ 2 corresponding to the instantaneous values of the flow rate Q and of the speed Q.
  • the angle a 2 varies in accordance with equation (2).
  • the goal being to obtain the correct inclination ⁇ 1 of the inlet fins 5, a servo connecting the axes 9 and 6 respectively of the outlet fins 8 and inlet 5, imposes on the latter a rotation controlled by the rotation of the first .
  • the parameters determining this enslavement are such that the constant relationship between the cotangents of the angles ⁇ 1 and ⁇ 2 is verified.
  • each outlet fin 8 is provided with a crank 10, which is connected to a crown 11 by a link 12.
  • the cranks 10 on the one hand and the links 12 on the other hand having equal lengths respectively, to any rotation of the outlet fins 8 corresponds a rotation of the crown 11.
  • cranks 13 integral with the axes 6 and connecting rods 15 which connect the latter to a ring 14.
  • Figure 4 shows schematically a servo by means of a cam.
  • the aforementioned pinion 16 drives a cam 20 against which a roller 21 is applied which is integral with the aforementioned crown 14.
  • the profile of the cam 20 is determined point by point so as to achieve the relationship (3) between the angles a 1 and ⁇ 2 taking into account the dimensions of the cranks 10 and 13, the links 12 and 15 and the rings 11 and 14.
  • FIG. 5 Another embodiment of this control is shown schematically in Figure 5; it consists in connecting the aforementioned pinions 16 and 17 respectively to an angular position sensor 22 and to an electric motor 23, which is controlled in position by means of an electronic circuit 24 of any known type capable of controlling the rotation of the motor 23 according to that of the sensor 22 according to a law determined by the relation (3) on the one hand and all the cranks, rods and crowns on the other hand.
  • the senor 22 and the electric motor 23 could be replaced by a hydraulic or pneumatic assembly giving the same results.
  • the shaft 25 connecting the pinions 16 and 17 ( Figure 1) or the pinion 16 and the cam 20 ( Figure 4) may be in two parts separated by any servo-control system allowing to multiply the effort provided by the fins 8 to better act on the fins 5.
  • the present invention is applicable to any type of turbopump when good efficiency is desired for various operating regimes. This is the case in particular in hydraulic transmissions, and more particularly those equipping a vehicle because variations in load, gradient and others lead to values of flow and pressure varying in large proportions.

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

Abstract

The invention relates to a turbine pump of the type comprising a rotor 1 with blades 2 and vanes with inlet 5 and outlet 8 blades. These inlet 5 and outlet 8 blades are, moreover, mounted pivotably about axles 6 and 9 and control means 10 to 25 determine the angle of rotation of the inlet blades 5 as a function of that of the outlet blades 8. Such a turbine pump is especially advantageous when the operating conditions (speed, flow, pressure) vary within wide proportions, as in hydraulic transmissions for vehicles. <IMAGE>

Description

La présente invention concerne un perfectionnement aux turbopompes destiné à leur assurer un rendement maximal pratiquement indépendant de leur débit et de leur vitesse de rotation.The present invention relates to an improvement to turbopumps intended to provide them with a maximum efficiency practically independent of their flow rate and their rotational speed.

Les turbopompes ont connu de multiples améliorations en vue d'augmenter leur rendement, notamment le tracé et la finesse des ailettes du rotor, ainsi que par la présence de directrices à ailettes placées en amont ou en aval du rotor, ou les deux à la fois.Turbopumps have undergone multiple improvements with a view to increasing their efficiency, in particular the layout and fineness of the rotor fins, as well as by the presence of fin guides placed upstream or downstream of the rotor, or both .

Cependant l'inclinaison optimale des ailettes de directrices dépend de la vitesse de rotation du rotor et du débit, d'où la nécessité de définir une vitesse nominale et un débit nominal pour lesquels le rendement sera maximal et d'accepter un moindre rendement pour les autres valeurs possibles de la vitesse et du débit (ou de la pression de refoulement qui est liée au débit à vitesse donnée, par la caractéristique de la pompe).However, the optimum inclination of the steering fins depends on the speed of rotation of the rotor and the flow rate, hence the need to define a nominal speed and a nominal flow rate for which the output will be maximum and to accept a lower yield for the other possible values of speed and flow (or discharge pressure which is linked to the flow at a given speed, by the characteristic of the pump).

Pour pallier cet inconvénient, la présente invention propose une orientation automatique des ailettes de la directrice d'entrée, afin que le rendement soit maximal quelle que soit la vitesse de rotation.To overcome this drawback, the present invention proposes an automatic orientation of the fins of the inlet director, so that the efficiency is maximum whatever the speed of rotation.

Pour cela, la turbopompe selon l'invention comporte une directrice d'entrée dont les ailettes sont orientables, une directrice de sortie dont les ailettes également pivotantes s'orientent sous l'action du fluide, et des moyens pour asservir l'angle de rotation des ailettes d'entrée à l'angle de rotation des ailettes de sortie.For this, the turbopump according to the invention comprises an inlet director whose fins are orientable, an outlet director whose fins also pivoting are oriented under the action of the fluid, and means for controlling the angle of rotation inlet fins at the angle of rotation of the outlet fins.

Dans un mode avantageux de réalisation, les ailettes de sortie sont reliées par des ensembles bielle-manivelle à une première couronne, les ailettes d'entrée à une seconde couronne et un asservissement commande la rotation de ladite seconde couronne en fonction de la rotation de ladite première couronne. Avantageusement, ledit asservis- serrent est conçu pour que la cotangente de l'angle de rotation des ailettes d'entrée soit une fonction linéaire de la cotangente de l'angle de rotation des ailettes de sortie. Cet asservissement peut être réalisé par un arbre équipé de deux pignons qui engrènent respectivement avec lesdites première et seconde couronnes, ou par une came reliant lesdites première et seconde couronnes et dont le profil est spécialement adapté, ou par un moteur qui entraîne ladite seconde couronne et qui est asservi en position par un circuit logique connecté en entrée à un capteur de position angulaire lié à ladite première couronne.In an advantageous embodiment, the outlet fins are connected by connecting rod-crank assemblies to a first ring, the inlet fins to a second ring and a servo control the rotation of said second ring as a function of the rotation of said first crown. Advantageously, said slave is designed so that the cotangent of the angle of rotation of the inlet fins is a linear function of the cotangent of the angle of rotation of the outlet fins. This control can be achieved by a shaft fitted with two pinions which respectively mesh with said first and second crowns, or by a cam connecting said first and second crowns and whose profile is specially adapted, or by a motor which drives said second crown and who is enslaved in position by a logic circuit connected at input to an angular position sensor linked to said first ring.

D'autres caractéristiques de la présente invention apparai- tront à l'étude de l'exemple de réalisation donné ci-après à titre illustratif et nullement limitatif, en regard du dessin annexé dans lequel :

  • - la figure 1 est une coupe longitudinale de la turbopompe, suivant la ligne I-I de la figure 2,
  • - la figure 2 est une coupe transversale suivant la ligne II-II de la figure 1,
  • - la figure 3 est une vue extérieure montrant, avec la figure 1, l'asservissement de la rotation des ailettes,
  • - là figure 4 représente schématiquement une autre réalisation mécanique de cet asservissement,
  • - la figure 5 représente schématiquement une réalisation électrique de cet asservissement.
Other characteristics of the present invention will appear on studying the example of embodiment given below by way of illustration and in no way limitative, with reference to the appended drawing in which:
  • FIG. 1 is a longitudinal section of the turbopump, along line II of FIG. 2,
  • FIG. 2 is a cross section along line II-II of FIG. 1,
  • FIG. 3 is an external view showing, with FIG. 1, the control of the rotation of the fins,
  • FIG. 4 schematically represents another mechanical embodiment of this control,
  • - Figure 5 shows schematically an electrical embodiment of this control.

Les figures 1 et 2 permettent de retrouver les éléments classiques d'une turbopompe : le rotor 1 avec ses ailettes 2, la conduite d'arrivée 3 et la volute de sortie 4.FIGS. 1 and 2 make it possible to find the conventional elements of a turbopump: the rotor 1 with its fins 2, the inlet pipe 3 and the outlet volute 4.

La directrice d'entrée (ou avant-directrice) est composée d'ailettes 5, au nombre de sept sur le dessin, qui, contrairement aux réalisations connues, sont orientables et non fixes. Pour cela, elles comportent chacune un axe 6 placé sensiblement dans leur plan médian de façon telle que les pressions exercées par le fluide s'équilibrent sensiblement de part et d'autre de l'ailette. Pour assurer la continuité de la veine fluide, un noyau 7 est placé au centre de la conduite d'arrivée 3 ; son profil extérieur et celui de la conduite 3 épousent la trajectoire des bords des ailettes mobiles 5.The entry director (or before-director) is composed of fins 5, seven in number in the drawing, which, unlike the known embodiments, are orientable and not fixed. For this, they each have an axis 6 placed substantially in their median plane so that the pressures exerted by the fluid are substantially balanced on either side of the fin. To ensure the continuity of the fluid stream, a core 7 is placed at the center of the inlet pipe 3; its external profile and that of the pipe 3 follow the path of the edges of the movable fins 5.

On sait, par l'analyse du triangle des vitesses d'entrée, qu'une turbopompe aura un rendement maximal si le fluide arrive sur les ailettes 2 du rotor 1 avec un angle α1 qui dépend de l'angle β1 d'inclinaison des ailettes 2 du rotor 1, de la vitesse de rotation Ω -du rotor, du débit Q, du rayon r1 et de la largeur e de la surface cylindrique à l'entrée du rotor, suivant la relation

Figure imgb0001
We know, by the analysis of the triangle of input speeds, that a turbopump will have a maximum efficiency if the fluid arrives on the fins 2 of the rotor 1 with an angle α 1 which depends on the angle β 1 of inclination of the fins 2 of the rotor 1, of the speed of rotation Ω -of the rotor, of the flow rate Q, of the radius r 1 and of the width e of the cylindrical surface at the inlet of the rotor, according to the relation
Figure imgb0001

On voit ainsi que, pour des caractéristiques dimensionnelles r1, e1 et β1 données, l'angle α1 optimal dépend de la vitesse de rotation Ω et du débit Q .It can thus be seen that, for given dimensional characteristics r 1 , e 1 and β 1 , the optimal angle α 1 depends on the speed of rotation Ω and on the flow rate Q.

En conséquence, dans les réalisations connues où l'angle α1 est constant, le rendement de la turbopompe n'est maximal pour une valeur donnée de la vitesse de rotation Ω, que pour un certain débit Q.Consequently, in known embodiments where the angle α 1 is constant, the efficiency of the turbopump is maximum for a given value of the speed of rotation Ω, only for a certain flow rate Q.

Pour toute autre valeur ce rendement décroît, ce qui conduit les constructeurs à établir des réseaux de courbes caractéristiques, donnant l'évolution du rendement en fonction de la vitesse, du débit et/ou de la pression de refoulement ("collines" de rendement).For any other value, this efficiency decreases, which leads manufacturers to establish networks of characteristic curves, giving the evolution of the efficiency as a function of the speed, the flow and / or the discharge pressure ("hills" of efficiency). .

Ce phénomène, peu sensible quand la hauteur de refoulement est constante, est beaucoup plus gênant quand elle est fortement variable, ce qui est le cas, par exemple dans les transmissions hydrauliques pour véhicules.This phenomenon, not very sensitive when the delivery head is constant, is much more troublesome when it is highly variable, which is the case, for example in hydraulic transmissions for vehicles.

Pour que ce rendement reste maximal quels que soient la vitesse Ω et le débit Q, il suffit de donner à l'angle α1 sa bonne valeur c'est-à-dire celle résultant de la formule (1) susmentionnée.For this efficiency to remain maximum whatever the speed Ω and the flow rate Q, it suffices to give the angle α 1 its good value, that is to say that resulting from the above formula (1).

Ceci serait certes possible par la mesure du débit Q et de la vitesse Q , mais ce n'est pas simple ; aussi la turbopompe selon la présente invention est basée sur un autre principe.This would certainly be possible by measuring the flow rate Q and the speed Q, but it is not simple; also the turbopump according to the present invention is based on another principle.

En effet, une loi identique à celle (1) précitée pour l'angle α1, existe entre les valeurs des mêmes paramètres pris cette fois au niveau de la surface cylindrique à la sortie du rotor et affectés de l'indice 2 ; d'où la relation :

Figure imgb0002
Indeed, a law identical to that (1) mentioned above for the angle α 1 , exists between the values of the same parameters taken this time at the level of the cylindrical surface at the outlet of the rotor and assigned to the index 2; hence the relationship:
Figure imgb0002

Il en résulte, en combinant les deux relations (1) et (2), une relation entre l'angle α1 que doit prendre la directrice d'entrée pour offrir un rendement maximal et l'angle α 2 que prennent les filets fluides à leur sortie du rotor. Cette relation peut s'écrire :

Figure imgb0003
avec
Figure imgb0004
et K' = K cotg β2 - cotg β1 ce qui montre bien que les angles α 1 et α 2 évoluent suivant une loi linéaire de leurs cotangentes dont les termes sont définis par les caractéristiques géométriques de la turbopompe : r i, r 2, e1, e2, β et β2, et quelles que soient les valeurs du débit Q et de la vitesse Q.The result is, by combining the two relations (1) and (2), a relation between the angle α 1 which the entry director must take to offer maximum efficiency and the angle α 2 which the fluid threads take their exit from the rotor. This relation can be written:
Figure imgb0003
 with
Figure imgb0004
 and K '= K cotg β 2 - cotg β 1 which clearly shows that the angles α 1 and α 2 evolve according to a linear law of their cotangents, the terms of which are defined by the geometric characteristics of the turbopump: r i , r 2 , e 1 , e 2 , β and β 2 , and whatever the values of flow rate Q and speed Q.

Ainsi, la turbopompe selon l'invention comporte, en plus de la directrice d'entrée à ailettes 5 orientables, une directrice de sortie (ou arrière-directrice) dont les ailettes 8 sont montées pivotantes autour d'un. axe 9 placé près du bord de l'ailette le plus proche du rotor 1. Cette directrice de sortie reçoit le fluide dès sa sortie des ailettes 2 du rotor 1 et jusqu'à son arrivée dans la volute de sortie 4. Ses ailettes 8 sont donc soumises à la pression de sortie du fluide qui tend donc à leur faire prendre une inclinaison instantanée égale à l'angle α2 précité correspondant aux valeurs instantanées du débit Q et de la vitesse Q . Lorsque l'une au moins de ces valeurs varie, l'angle a 2 varie conformément à la relation (2).Thus, the turbopump according to the invention comprises, in addition to the inlet director with orientable fins 5, an outlet director (or rear director) whose fins 8 are pivotally mounted around one. axis 9 placed near the edge of the fin closest to the rotor 1. This outlet director receives the fluid as soon as it leaves the fins 2 of the rotor 1 and until it arrives in the outlet volute 4. Its fins 8 are therefore subjected to the fluid outlet pressure which therefore tends to cause them to take an instantaneous inclination equal to the aforementioned angle α 2 corresponding to the instantaneous values of the flow rate Q and of the speed Q. When at least one of these values varies, the angle a 2 varies in accordance with equation (2).

Le but étant d'obtenir la bonne inclinaison α 1 des ailettes d'entrée 5, un asservissement reliant les axes 9 et 6 respectivement des ailettes de sortie 8 et d'entrée 5, impose à ces dernières une rotation commandée par la rotation des premières. Les paramètres déterminant cet asservissement sont tels que la relation constante entre les cotangentes des angles α 1 et α2 soit vérifiée.The goal being to obtain the correct inclination α 1 of the inlet fins 5, a servo connecting the axes 9 and 6 respectively of the outlet fins 8 and inlet 5, imposes on the latter a rotation controlled by the rotation of the first . The parameters determining this enslavement are such that the constant relationship between the cotangents of the angles α 1 and α 2 is verified.

Cet asservissement peut être réalisé de diverses manières et notamment comme représenté à la figure 3. L'axe 9 de chaque ailette de sortie 8 est muni d'une manivelle 10, laquelle est reliée à une couronne 11 par une biellette 12. Les manivelles 10 d'une part et les biellettes 12 d'autre part ayant respectivement des longueurs égales, à toute rotation des ailettes de sortie 8 correspond une rotation de la couronne 11.This control can be achieved in various ways and in particular as shown in Figure 3. The axis 9 of each outlet fin 8 is provided with a crank 10, which is connected to a crown 11 by a link 12. The cranks 10 on the one hand and the links 12 on the other hand having equal lengths respectively, to any rotation of the outlet fins 8 corresponds a rotation of the crown 11.

Un ensemble analogue est associé aux ailettes d'entrée 5, il comporte des manivelles 13 solidaires des axes 6 et des biellettes 15 qui relient celles-ci à une couronne 14.A similar assembly is associated with the inlet fins 5, it comprises cranks 13 integral with the axes 6 and connecting rods 15 which connect the latter to a ring 14.

Lorsque la plage de variation de la vitesse et/ou du débit est suffisamment faible, une liaison des deux couronnes 11 et 14 par un arbre 25 équipé de deux pignons 16 et 17 qui engrènent avec des dentures 18 et 19 solidaires des couronnes 11 et 14, permet de réaliser avec une approximation satisfaisante la relation (3) entre les angles α1 et a 2 des ailettes.When the range of variation of the speed and / or the flow is sufficiently small, a connection of the two crowns 11 and 14 by a shaft 25 equipped with two pinions 16 and 17 which mesh with teeth 18 and 19 integral with the crowns 11 and 14 , allows to realize with a satisfactory approximation the relation (3) between the angles α 1 and a 2 of the fins.

Dans les autres cas, une meilleure approche de la relation (3) sera possible par tout moyen d'asservissement angulaire.In the other cases, a better approach to relation (3) will be possible by any means of angular servo-control.

La figure 4 représente schématiquement un asservissement au moyen d'une came. Le pignon 16 précité entraîne une came 20 contre laquelle s'applique un galet 21 solidaire de la couronne 14 précitée. Le profil de la came 20 est déterminé point par point de manière à réaliser la relation (3) entre les angles a 1 et α 2 compte tenu des dimensions des manivelles 10 et 13, des biellettes 12 et 15 et des couronnes 11 et 14.Figure 4 shows schematically a servo by means of a cam. The aforementioned pinion 16 drives a cam 20 against which a roller 21 is applied which is integral with the aforementioned crown 14. The profile of the cam 20 is determined point by point so as to achieve the relationship (3) between the angles a 1 and α 2 taking into account the dimensions of the cranks 10 and 13, the links 12 and 15 and the rings 11 and 14.

Un autre exemple de réalisation de cet asservissement est représenté schématiquement par la figure 5 ; il consiste à relier les pignons 16 et 17 précités respectivement à un capteur de position angulaire 22 et à un moteur électrique 23, lequel est asservi en position au moyen d'un circuit électronique 24 de tout type connu capable de piloter la rotation du moteur 23 en fonction de celle du capteur 22 selon une loi déterminée par la relation (3) d'une part et l'ensemble des manivelles, biellettes et couronnes d'autre part.Another embodiment of this control is shown schematically in Figure 5; it consists in connecting the aforementioned pinions 16 and 17 respectively to an angular position sensor 22 and to an electric motor 23, which is controlled in position by means of an electronic circuit 24 of any known type capable of controlling the rotation of the motor 23 according to that of the sensor 22 according to a law determined by the relation (3) on the one hand and all the cranks, rods and crowns on the other hand.

D'autres modes de réalisation de cet asservissement peuvent, sans sortir du cadre de la présente invention, être imaginés. Par exemple, on pourrait remplacer le capteur 22 et le moteur électrique 23 par un ensemble hydraulique ou pneumatique donnant les mêmes résultats. De même, l'arbre 25 reliant les pignons 16 et 17 (figure 1) ou le pignon 16 et la came 20 (figure 4) pourra être en deux parties séparées par tout système de servo-conmande permettant de multiplier l'effort fourni par les ailettes 8 pour mieux agir sur les ailettes 5.Other embodiments of this control can, without departing from the scope of the present invention, be imagined. For example, the sensor 22 and the electric motor 23 could be replaced by a hydraulic or pneumatic assembly giving the same results. Similarly, the shaft 25 connecting the pinions 16 and 17 (Figure 1) or the pinion 16 and the cam 20 (Figure 4) may be in two parts separated by any servo-control system allowing to multiply the effort provided by the fins 8 to better act on the fins 5.

La présente invention est applicable à tout type de turbopompe lorsqu'un bon rendement est souhaité pour divers régimes de fonctionnement. C'est le cas notamment dans les transmissions hydrauliques, et plus particulièrement celles équipant un véhicule car les variations de charge, de déclivité et autres conduisent à des valeurs de débit et pression variant dans de larges proportions.The present invention is applicable to any type of turbopump when good efficiency is desired for various operating regimes. This is the case in particular in hydraulic transmissions, and more particularly those equipping a vehicle because variations in load, gradient and others lead to values of flow and pressure varying in large proportions.

Claims (8)

1. Turbopompe comportant un rotor 1 à ailettes 2 et des directrices à ailettes d'entrée 5 et de sortie 8 placées respectivement entre la conduite d'arrivée 3 et le rotor 1 et entre celui-ci et la volute de sortie 4,lesdites ailettes de directrices 5 et 8 étant pivotantes, caractérisée par le fait que des moyens d'asservissement pilotés par la rotation des ailettes de sortie 8, commandent la rotation des ailettes d'entrée 5.1. Turbopump comprising a rotor 1 with fins 2 and directors with inlet fins 5 and outlet 8 placed respectively between the inlet pipe 3 and the rotor 1 and between the latter and the outlet volute 4, said fins guidelines 5 and 8 being pivoting, characterized in that servo means controlled by the rotation of the outlet fins 8, control the rotation of the inlet fins 5. 2. Turbopompe selon la revendication 1, caractérisée par le fait que lesdits moyens d'asservissement sont conçus pour que la cotangente de l'angle de rotation cll des ailettes d'entrée 5 soit une fonction linéaire de la cotangente de l'angle de rotationt α2 des ailettes de sortie 8.2. Turbopump according to claim 1, characterized in that said control means are designed so that the cotangent of the angle of rotation cl l of the inlet fins 5 is a linear function of the cotangent of the angle of rotationt α 2 of the outlet fins 8. 3. Turbopompe selon l'une des revendications 1 et 2, caractérisée par le fait que les ailettes de sortie 8 sont reliées par des ensembles bielle-manivelle 12-10 à une première couronne 11, les ailettes d'entrée 5 à une seconde couronne 14 et un asservissement commande la rotation de ladite seconde couronne 14 à partir de la rotation de ladite première couronne 11.3. Turbopump according to one of claims 1 and 2, characterized in that the outlet fins 8 are connected by connecting rod-crank assemblies 12-10 to a first ring 11, the inlet fins 5 to a second ring 14 and a servo control the rotation of said second ring 14 from the rotation of said first ring 11. 4. Turbopompe selon la revendication 3, caractérisée par le fait que ledit asservissement est réalisé par un arbre 25 équipé de deux pignons 16 et 17 qui engrènent respectivement avec lesdites première 11 et seconde 14 couronnes.4. Turbopump according to claim 3, characterized in that said control is produced by a shaft 25 equipped with two pinions 16 and 17 which mesh respectively with said first 11 and second 14 crowns. 5.. Turbopompe selon la revendication 3, caractérisée par le fait que ledit asservissement est réalisé par une came 20 reliant lesdites première 11 et seconde 14 couronnes et dont le profil est spécialement adapté.5 .. Turbopump according to claim 3, characterized in that said control is produced by a cam 20 connecting said first 11 and second 14 rings and whose profile is specially adapted. 6. Turbopompe selon la revendication 3, caractérisée par le fait que ledit asservissement est réalisé par un moteur 23 qui entraîne ladite seconde couronne 14 et qui est asservi en position par un circuit logique 24 connecté en entrée à un capteur de position angulaire 22 lié à ladite première couronne 11.6. Turbopump according to claim 3, characterized in that said control is produced by a motor 23 which drives said second ring 14 and which is controlled in position by a logic circuit 24 connected at input to an angular position sensor 22 linked to said first crown 11. 7. Turbopompe selon l'une des revendications 1 à 6, caractérisée par le fait que chaque ailette d'entrée 5 est pivotante autour d'un axe 6 parallèle à l'axe de rotation du rotor 1 et placé sensiblement dans son plan médian de façon telle que les pressions exercées par le fluide s'équilibrent sensiblement de part et d'autre de cet axe 6.7. Turbopump according to one of claims 1 to 6, characterized in that each inlet fin 5 is pivotable about an axis 6 parallel to the axis of rotation of the rotor 1 and placed substantially in its median plane of in such a way that the pressures exerted by the fluid are substantially balanced on either side of this axis 6. 8. Turbopompe selon la revendication 7, caractérisée par le fait que la conduite d'arrivée 3 comporte en outre un noyau central 7 et que son profil intérieur épouse la trajectoire des bords des ailettes d'entrée 5.8. Turbopump according to claim 7, characterized in that the inlet pipe 3 further comprises a central core 7 and that its inner profile follows the path of the edges of the inlet fins 5.
EP82401648A 1981-09-18 1982-09-10 Turbine pump with adjustable stator blades Withdrawn EP0075506A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8117663A FR2513325B1 (en) 1981-09-18 1981-09-18 TURBOPUMP WITH ADJUSTABLE STEERING VANES
FR8117663 1981-09-18

Publications (1)

Publication Number Publication Date
EP0075506A1 true EP0075506A1 (en) 1983-03-30

Family

ID=9262276

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82401648A Withdrawn EP0075506A1 (en) 1981-09-18 1982-09-10 Turbine pump with adjustable stator blades

Country Status (5)

Country Link
EP (1) EP0075506A1 (en)
JP (1) JPS58107899A (en)
CA (1) CA1199224A (en)
FR (1) FR2513325B1 (en)
SU (1) SU1144624A3 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8231341B2 (en) 2009-03-16 2012-07-31 Pratt & Whitney Canada Corp. Hybrid compressor
WO2012104366A1 (en) * 2011-02-02 2012-08-09 Siemens Aktiengesellschaft Coupled outlet vane device/angular adjustment
CN113944656A (en) * 2021-11-26 2022-01-18 中国北方发动机研究所(天津) Variable cross-section end wall pre-rotation guide vane pipeline structure

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2022094019A (en) * 2020-12-14 2022-06-24 三菱重工コンプレッサ株式会社 Rotary machine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2350839A (en) * 1940-04-08 1944-06-06 Szydlowski Josef Machine for compressing gases by centrifugal effect
GB1058898A (en) * 1964-05-14 1967-02-15 Hispano Suiza Sa Improvements in compressors of the centrifugal type or mixed flow type
US3639075A (en) * 1969-12-12 1972-02-01 Gen Electric Turbomachinery vane adjustment mechanism
US3992128A (en) * 1975-06-09 1976-11-16 General Motors Corporation Variable diffuser

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2350839A (en) * 1940-04-08 1944-06-06 Szydlowski Josef Machine for compressing gases by centrifugal effect
GB1058898A (en) * 1964-05-14 1967-02-15 Hispano Suiza Sa Improvements in compressors of the centrifugal type or mixed flow type
US3639075A (en) * 1969-12-12 1972-02-01 Gen Electric Turbomachinery vane adjustment mechanism
US3992128A (en) * 1975-06-09 1976-11-16 General Motors Corporation Variable diffuser

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8231341B2 (en) 2009-03-16 2012-07-31 Pratt & Whitney Canada Corp. Hybrid compressor
WO2012104366A1 (en) * 2011-02-02 2012-08-09 Siemens Aktiengesellschaft Coupled outlet vane device/angular adjustment
CN113944656A (en) * 2021-11-26 2022-01-18 中国北方发动机研究所(天津) Variable cross-section end wall pre-rotation guide vane pipeline structure
CN113944656B (en) * 2021-11-26 2024-04-30 中国北方发动机研究所(天津) Variable cross-section end wall pre-rotation guide vane pipeline structure

Also Published As

Publication number Publication date
FR2513325A1 (en) 1983-03-25
JPS58107899A (en) 1983-06-27
FR2513325B1 (en) 1986-08-22
CA1199224A (en) 1986-01-14
SU1144624A3 (en) 1985-03-07

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