EP1559913A1 - Pompe à cavités progressives - Google Patents
Pompe à cavités progressives Download PDFInfo
- Publication number
- EP1559913A1 EP1559913A1 EP05290100A EP05290100A EP1559913A1 EP 1559913 A1 EP1559913 A1 EP 1559913A1 EP 05290100 A EP05290100 A EP 05290100A EP 05290100 A EP05290100 A EP 05290100A EP 1559913 A1 EP1559913 A1 EP 1559913A1
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- EP
- European Patent Office
- Prior art keywords
- pump
- rotor
- cavities
- stator
- hydraulic control
- 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.)
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
- F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
- F04C2/1075—Construction of the stationary member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/007—Venting; Gas and vapour separation during pumping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
- F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/24—Fluid mixed, e.g. two-phase fluid
Definitions
- the present invention relates to improvements brought to volumetric pumps of the type to progressive cavities, also say Sparrow pump, and more specifically it relates to a volumetric pump of type with progressive cavities, perfected, allowing pump single-phase mixtures or effluents or polyphasic, having any viscosity, in particular mixtures or multiphase effluents compressible and viscous to very viscous fluids.
- the pump according to the present invention allows a fortiori to pump a single phase or a liquid phase charged with particles solids, with varying viscosities.
- the progressive cavity pump - designated also hereinafter by the abbreviation PCP - was invented by René Moineau in 1930 and the operation in liquid industrial pumps currently used corresponds basic principles.
- Figure 1 of the attached drawing gives, in (A), a schematic representation partially in longitudinal section axis of a conventional PCP pump, also with (B) a representation of the distribution of pressures on along the pump in the case of pumping a liquid (curve L) and in the case of pumping a mixture polyphasic liquid-gas (curve P).
- the architecture of the PCP 1 pump is made up a helical metal rotor 2 rotating inside a compressible stator 3, generally of elastomer, of helical inner shape.
- the contact between the rotor 2 and the stator 3 is by compression, more or less strong, of the stator 3.
- the rotor 2 has a diameter D (FIG. 2 (B)) greater than the stator channel 3 ( Figure 2 (C)), which generates a compression contact of the stator 3 by the rotor 2 (contact clamping), ensuring a certain seal (Figure 2 (A)).
- the geometry of the rotor 2 and the stator 3 of the PCP pump 1 leads to a set of isolated cavities 4, defined between the rotor 2 and the stator 3, also called cells , of constant volume, that the rotor 2 moves from the suction or inlet 5 (low suction pressure p A ) to the discharge or outlet 6 (high discharge pressure p R ).
- the PCP pump is a positive displacement pump.
- the cavity 4 moves from the low pressure of the suction 5 towards the high delivery pressure 6 and the presence of the gas in the pumped effluent leads to a process of compression of the gas with development of temperature, because the cavity is of constant volume.
- the thermodynamic law of gas shows that if the volume in which the gas is compressed remains constant, the temperature rises considerably.
- the leakage rate through the annular contact rotor 2 / stator 3 fulfills two functions: it partially compensates the volume of compressed gas and it realizes the differential pressure between the cavities 4.
- the annular leakage rate between the rotor 2 and the stator 3 of the pump PCP 1 is adapted to the operation in liquid (incompressible fluid), for the purpose of lubrication with low flow rates; it is not sufficient to compensate for gas compression. Since the leakage rate is low, the last cavities 4 are only partially compensated and the compression occurs on the last stages of the pump, as can be seen in FIG. 1 (B), where p A designates, as already indicated. , the suction pressure and p R designating the discharge pressure. This compression is accompanied by a high temperature. The concentration of the pressures at the outlet of the pump and the strong increase in temperature leads to the risk of mechanical damage: stator degradation, mechanical expansion and vibrations.
- the PCP pump achieves a pressure of 4 MPa (40 bar) on the four top floors, with a strong pressure gradient that develops high temperatures; on thirteen floors he there are only four that compress the mixture.
- US 5,722,820 proposes a variable rotor / stator contact decreasing backflow to suction.
- the leakage flow between the rotor and the stator carry the flow necessary for the compensation in pressure and volume of cavities lying downstream of the pump. It is a global leakage rate; he first compensate the last cavity, to move to the next and so on.
- the pump In viscous fluid, the pump can not avoid the appearance of cavitation.
- this solution can not have limited use and uses a complex architecture without ensuring good reliability.
- the present invention aims to propose an improved pump so as to spread the aforementioned drawbacks of the previous state of the technical.
- a pump with progressive cavities having a helical rotor rotating inside a helical stator, said stator and said rotor being arranged so that the cavities formed between said rotor and said stator move from the suction towards the repression, is characterized, being arranged according to the invention, by the fact that means of hydraulic regulation are provided to ensure a internal recirculation of the fluid pumped between at least two said cavities under conditions capable of providing the least one function among the pressure distribution searched along the pump, the stabilization of temperatures, control of leak rates, and the compensation of compressed gas volumes.
- Internal recirculation means the recirculation between two cavities of a mixing volume pumped as opposed to an external recirculation cavities that is done by the annular contact between the rotor and the stator and that generates a leakage flow.
- the pressure distribution is obtained by a rebalancing of local pressures due to the flow of recirculation of hydraulic regulators.
- the leakage rates between the stator and the rotor are a function of the pressure gradient.
- the control of pressures leads to control of leak rates.
- the role of the hydraulic control means is therefore to control the behavior of the pump, according to production characteristics.
- Pressure control and compensation volume of compressed gas stabilizes temperatures, multiphase pumping (liquid, gas, solid particles).
- the internal regulation of the pressure by the hydraulic control system of the present invention leads to the stabilization of the thermal regime and hydraulic along the pump, and can improve thus the mechanical behavior and the reliability overall.
- the mastery of the contact between rotor and stator means that one can have a superficial contact without a strong compression between stator and rotor, while keeping low leakage rate. This is a way of new operation compared to the PCP pump Traditional.
- the hydraulic control means are advantageously arranged to ensure recirculation internal fluid pumped between at least two cavities adjacent.
- these means can advantageously be arranged to ensure internal recirculation pumped fluid between at least two cavities located in the region of the pump close to the discharge.
- These means can also be arranged to ensure internal recirculation of the fluid pumped between all cavities of the pump.
- the hydraulic control means can be received at least in part by the rotor and / or at least partly by the stator.
- the density of the regulators hydraulics ensures the continuity of the process of regulation along the pump; this density is performance of the pump (flow, distribution pressures).
- the dimensioning of regulators hydraulic is the recirculation flow needed for the cavity for volume compensation compressed and rebalancing pressures.
- the hydraulic control means ensuring internal recirculation of the pumped fluid between two cavities, have at least one channel practiced in the rotor connecting these two cavities, the regulation hydraulically being carried out mechanically using a regulator arranged inside said channel and / or by loss of charge.
- the hydraulic control means ensuring internal recirculation of the pumped fluid between two cavities, have at least one peripheral channel hosted by the rotor and arranged to provide the link between these two cavities with regulation by loss of charge.
- the hydraulic control means ensuring internal recirculation of the pumped fluid between two cavities, have at least one hydraulic channel interior welcomed by the stator and arranged to ensure the connection between these two cavities with regulation by loss of charge.
- the three particular embodiments can be used simultaneously on the same pump.
- the contact between the rotor and the stator can be loosened compared to a pump at progressive cavities not including the means of hydraulic control as defined above. In these conditions, we can increase the rotation speed and the pumped flow without damaging the stator.
- the present invention also relates to the application of the pump as defined above to the pumping compressible multiphase mixtures and pumping viscous fluids.
- FIGS 3 and 4 illustrate the operation of the hydraulic control device (RH) of the invention installed inside the pump.
- the total flow rate Q accesses the cavity 1 and the volume of gas is compressed at the pressure p 1 . Because of the pressure difference (p m - p 1 ), the flow rate q m of the hydraulic control system compensates the compressed volume in the cavity 1 and rebalances the pressures p m and p 1 .
- the process is repeated for each cavity, towards the discharge.
- control system hydraulic system of the invention is the opposite of the systems currently used by the industry: this is a controlled internal regulation, in contrast with the external regulation without control of current systems.
- the mastery of the performances is done by the architecture of the hydraulic control system: dimensions, transfer function, layouts the pump.
- control systems are installed inside the pump by adapting the rotor and / or the stator, without changing completely the initial architecture of the whole of the PCP pump and its manufacture. Maintaining the configuration the original PCP pump means that no modifications not the overall architecture (the rotor and the stator), the transport of the mixture by the displacement of the cavities, the motorization.
- Figures 5 to 12 show achievements particular of the pump according to the invention.
- control system hydraulic RH 7 is constituted by a hydraulic channel 8 which is practiced inside the rotor 2 between two cavities 4 and in which is installed a device for regulation 9 of the recirculation flow.
- FIG. 6 A practical embodiment of the device 9 is shown schematically in Figure 6, where one can see that this device is based on a valve gradually opening to a differential pressure given, which leads to the regulation of the flow of recirculation q ( Figure 4 (A)).
- the regulation system RH 7 consists of a hydraulic channel 8 practiced inside the rotor 2 between two cavities 4.
- the system of RH 7 hydraulic control consists of two channels 10, one being practiced between the cavities 1 and m, and the other inside the cavity 1.
- These two tandem channels, arranged in an offset fashion, represent the simplest structure. The fact that we realize several channels decreases their diameter and the offset ensures better circulation, especially when the opening of the channel in contact with the stator.
- FIGS. 9A-9C show a variant in which a flow control device 9, such as the one shown in Figure 6, is installed in each channels 10 of the tandem, and FIGS. 9A-9C a variant according to which, in each channel 10 of the tandem, the hydraulic regulation is carried out by the pressure drop, as shown in Figs. 7A, 7B.
- the system of hydraulic control RH 7 is realized by a channel peripheral hydraulic rotor 2, between two cavities 4.
- a channel peripheral hydraulic rotor 2 between two cavities 4.
- FIGS. 11A-11C show a variant having a single-channel hydraulic circuit 11, and FIGS. 11A-11C a variant comprising two circuits 12 in tandem shifted.
- the regulation system hydraulic RH 7 has a hydraulic channel 13 internal device to the stator 3, practiced between two cavities 4.
- This test concerns a PCP pump prototype traditional carrying a multiphase mixture (water and air).
- PCP pump with thirteen stages (cavities) transports a polyphasic mixture whose flow rates are 50% water and 50% air, with a suction pressure of 0.1 MPa (1 bar) and a pressure in the conduit of pressure of 4 MPa (40 bar), which is equivalent to gas compression of 40/1. Due to the high rate of compression and the fact that the leakage flow (between rotor and stator) is unable to compensate for the volume of compressed gas, the discharge pressure is carried out on the last four floors (cavities), which amounts to a high pressure gain of 1 MPa (10 bar) / stage. All the work of the pump is carried out by the last four floors, the remaining nine floors of the pump does not not contributing to the compression of the mixture. This strong localized compression on the last floors is accompanied by a strong rise in temperature: inlet temperature is doubled.
- the high temperature and the concentration of pressure at the outlet of the pump are damaging to the mechanical strength of the assembly, in particular the elastomer of the stator and the rotor.
- the pump according to the present invention has a quite different behavior; thanks to regulators Hydraulic RH installed in the rotor, the distribution pressures are standardized and the temperature stabilized. On the last four floors, the density of hydraulic regulators RH is two regulators hydraulics per floor and therefore the gain of pressure is very low (about 0.1 MPa / stage). On the nine remaining floors of the pump, the regulators hydraulics RH are distributed as a regulator RH per floor. In these circumstances, the distribution of pressure is standardized, which amounts to a gain of pressure of about 0.3 MPa (3 bar) / stage.
- the density variation of the regulators hydraulics RH contributes to hydro-thermo-mechanical rebalancing the pump; all floors contribute to the compression of the mixture.
- the same PCP pump carries water with a low pressure at the inlet (0.1 MPa (1 bar)) and a pressure of about 0.5 MPa in the discharge pipe. Because of the dynamic behavior of the contact between rotor and the stator, the pump develops very high pressures weak on floors 7-11 with risk of cavitation.
- the pump according to the present invention controls the distribution of pressures and therefore the pressures are positive and uniformly distributed, without risk of cavitation.
- pressures vary evenly up to the suction pressure 0.1 Mpa (1 bar), without ever reaching locally low cavitation pressures.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
- le pas (PS) du stator 3 est le double du pas (Pr) du rotor 2 ; et
- la longueur L d'une cavité 4 est égale au pas (Ps) du stator 3, et par conséquent, elle est le double du pas (Pr) du rotor 2.
- Il a ainsi été proposé de réaliser un couple rotor/stator dont le volume des cavités diminue de l'aspiration vers le refoulement. C'est ainsi que le document US 2 765 114 propose un système rotor/stator tronconique, avec les diamètres décroissants.Dans le même sens, on peut imaginer un rotor à pas variable dont le volume des cavités est décroissant vers le refoulement.Ces solutions ne sont efficaces que pour un taux de gaz fixe et elles pénalisent le fonctionnement en liquide. Par ailleurs, cette solution ne peut pas éviter l'apparition de la cavitation.Aussi, la modification de l'architecture de la pompe conduit à un processus de fabrication complexe sans en assurer une bonne fiabilité.
- Il a aussi été proposé de réaliser un contact entre rotor et stator qui est variable au long de la pompe.
- la fiabilité du système est améliorée ;
- on peut utiliser des matériaux plus rigides (plus résistants) pour le stator afin d'augmenter la vitesse de rotation et le débit de la pompe.
- la pompe PCP avec un contact rotor/stator tronconique utilisée actuellement est un système global de régulation externe, dont le débit de fuite limité ne compense que les cavités situées près du refoulement de la pompe ;
- la pompe selon la présente invention comporte des moyens de régulation hydraulique interne assurant un écoulement local de recirculation, entre deux cavités, pour compenser la pression différentielle locale, le débit de fuite et la compression du gaz contenu dans la cavité ;
- le débit de recirculation est auto-régulé par le taux de gaz et la pression différentielle.
- la figure 1 représente une pompe PCP traditionnelle, comme cela a été décrit ci-dessus, avec une représentation des distributions des pressions en pompage du liquide et du mélange polyphasique liquide-gaz ;
- la figure 2 représente la composition d'une pompe PCP avec un rotor à simple hélice et un stator à double hélice ;
- la figure 3 est une vue analogue à la figure 1, donnant en (A) une représentation d'une pompe à cavités progressives selon la présente invention, avec représentation schématique des régulateurs hydrauliques (RH), et donnant en (B) une représentation de la distribution des pressions en pompage polyphasique uniforme le long de la pompe ;
- la figure 4 est, à plus grande échelle, une vue analogue à la figure 3, donnant en (A) une représentation d'une section de la pompe de l'invention, permettant de décrire le mécanisme de recirculation locale pour la compensation des volumes comprimés et le rééquilibrage des pressions locales, dans trois cavités successives de la pompe respectivement 1, m et n, et donnant en (B) une représentation de la distribution des pressions le long de la pompe ;
- la figure 5A est, encore à plus grande échelle, une vue analogue à la figure 4, d'une section de pompe de l'invention, montrant le régulateur hydraulique (RH) comportant un canal pratiqué dans le rotor pour assurer la recirculation du fluide pompé entre deux cavités adjacentes 1, m, avec régulation mécanique ;
- la figure 5B est une coupe selon la ligne A-A de la figure 5A ;
- la figure 6 montre, encore à plus grande échelle, le régulateur mécanique de la figure 5 ;
- la figure 7A est une vue analogue à la figure 5, mais avec régulation hydraulique par perte de charge ;
- la figure 7B est une coupe selon la ligne A-A de la figure 7A ;
- la figure 8A est une vue d'une section de pompe de l'invention, montrant le régulateur hydraulique (RH) comportant deux canaux parallèles pratiqués dans le rotor pour assurer la recirculation du fluide pompé entre deux cavités adjacentes, 1, m, avec régulation mécanique ;
- les figures 8B et 8C sont des vues en coupe respectivement selon les lignes A-A et B-B de la figure 8A ;
- la figure 9A est une vue analogue à la figure 8, mais avec régulation par perte de charge ;
- les figures 9B et 9C sont des vues en coupe respectivement selon les lignes A-A et B-B de la figure 9A ;
- la figure 10A est la vue d'une section de pompe de l'invention, montrant le régulateur hydraulique (RH) comportant un canal hydraulique périphérique au rotor pour assurer la recirculation du fluide pompé entre deux cavités adjacentes, 1, m ;
- la figure 10B est une vue en coupe selon la ligne A-A de la figure 10A ;
- la figure 11A est une vue d'une section de pompe de l'invention, montrant le régulateur hydraulique (RH) comportant deux canaux périphériques au rotor, décalés de 180° et d'un 1/2 de pas du rotor, pour assurer la recirculation du fluide pompé entre deux cavités adjacentes, 1, m ;
- les figures 11B et 11C sont des vues en coupe respectivement selon les lignes A-A et B-B de la figure 11A ;
- la figure 12A est la vue d'une section de pompe de l'invention montrant le régulateur hydraulique (RH) comportant un canal hydraulique périphérique à l'intérieur du stator, permettant d'assurer la recirculation du fluide pompé entre les deux cavités adjacentes, 1, m ; et
- la figure 12B est une vue en coupe selon la ligne A-A de la figure 12A.
- Q = QL + QG :
- le débit total du mélange de liquide (L) et de gaz (G) ;
- Q :
- débit de recirculation entre les cavités ; par exemple, qm est le débit du dispositif de régulation hydraulique de la cavité m vers la cavité 1 ;
- P :
- pression locale, dans les cavités (1, m, n) ;
- ζ :
- coefficient de perte de charge du dispositif de régulation hydraulique ;
- S :
- section d'écoulement du dispositif de régulation hydraulique ;
- γ :
- coefficient de transformation adiabatique.
- le débit de recirculation qm revient dans le circuit de régulation hydraulique vers la cavité 1 ;
- le débit Q avance dans la cavité m, poussé par le rotor ;
- à cause de la pression pm, supérieure à la pression précédente p1, le volume de gaz est comprimé ;
- la différence de pression (pn - pm) génère un débit qn dans le système de régulation hydraulique, de la cavité n vers la cavité m, pour compenser le volume comprimé dans la cavité m et rééquilibrer les pressions pn et pm ;
- le débit total (Q + qn) avance dans la cavité n ; le débit de recirculation qn revient dans la régulation hydraulique (RH) vers la cavité m ;
- le débit Q de la pompe est comprimé, le système de régulation hydraulique débite pour compenser la compression et rééquilibrer les pressions.
- rééquilibre localement les pressions entre deux cavités, ce qui conduit à la régularisation de la distribution des pressions au long de la pompe ;
- compense les volumes comprimés, ce qui évite la remontée de la température ;
- le débit pompé Q se conserve ; la recirculation selon l'invention se fait sans perte de débit ;
- par le rééquilibrage des pressions on maítrise les débits de fuite et le contact entre rotor et stator.
- éviter l'apparition de la cavitation, avec les dommages qu'elle engendre sur le stator et le rotor ;
- contrôler le contact entre rotor et stator : débit de fuite, lubrification du contact rotor/stator ;
- obtenir une meilleure fiabilité et augmentation du rendement hydraulique : débit, pression de refoulement, durée de vie, maintenance.
Claims (11)
- Pompe à cavités progressives comportant un rotor hélicoïdal (2) tournant à l'intérieur d'un stator hélicoïdal (3), ledit stator (3) et ledit rotor (2) étant disposés de telle sorte que les cavités (4) formées entre ledit rotor (2) et ledit stator (3) se déplacent de l'aspiration (5) vers le refoulement (6), caractérisée par le fait que des moyens de régulation hydraulique (RH) sont prévus pour assurer une recirculation interne du fluide pompé entre au moins deux desdites cavités (4) dans des conditions capables d'assurer au moins une fonction parmi la distribution des pressions recherchée le long de la pompe, la stabilisation des températures, le contrôle des débits de fuite, et la compensation des volumes de gaz comprimé.
- Pompe selon la revendication 1, caractérisée par le fait que les moyens de régulation hydraulique (RH) sont agencés pour assurer une recirculation interne du fluide pompé entre au moins deux cavités (4) adjacentes.
- Pompe selon la revendication 1 ou 2, caractérisée par le fait que les moyens de régulation hydraulique (RH) sont agencés pour assurer une recirculation interne du fluide pompé entre au moins deux cavités (4) situées dans la région de la pompe (1) voisine du refoulement (6).
- Pompe selon la revendication 1 ou 2, caractérisée par le fait que les moyens de régulation hydraulique (RH) sont agencés pour assurer une recirculation interne du fluide pompé entre toutes les cavités (4) de la pompe(1).
- Pompe selon l'une quelconque des revendications 1 à 4, caractérisée par le fait que les moyens de régulation hydraulique (RH) sont au moins en partie accueillis par le rotor (2).
- Pompe selon la revendication 5, caractérisée par le fait que les moyens de régulation hydraulique (RH), assurant la recirculation interne du fluide pompé entre deux cavités (4), comportent au moins un canal (8) pratiqué dans le rotor (2) reliant ces deux cavités (4), la régulation hydraulique étant effectuée mécaniquement à l'aide d'un régulateur (9) disposé à l'intérieur dudit canal (8) et/ou par perte de charge.
- Pompe selon la revendication 5, caractérisée par le fait que les moyens de régulation hydraulique (RH), assurant la recirculation interne du fluide pompé entre deux cavités (4), comportent au moins un canal périphérique (11) accueilli par le rotor (2) et agencé pour assurer la liaison entre ces deux cavités (4) avec régulation par perte de charge.
- Pompe selon l'une quelconque des revendications 1 à 7, caractérisée par le fait que les moyens de régulation hydraulique (RH) sont au moins en partie accueillis par le stator (3).
- Pompe selon la revendication 8, caractérisée par le fait que les moyens de régulation hydraulique (RH), assurant la recirculation interne du fluide pompé entre deux cavités (4), comportent au moins un canal hydraulique intérieur (13) accueilli par le stator (3) et agencé pour assurer la liaison entre ces deux cavités (4) avec régulation par perte de charge.
- Pompe selon l'une quelconque des revendications 1 à 9, caractérisée par le fait que le contact entre le rotor (2) et le stator (3) est desserré par rapport à une pompe à cavités progressives ne comportant pas les moyens de régulation hydraulique tels que définis à l'une des revendications 1 à 8.
- Application de la pompe telle que définie à l'une quelconque des revendications 1 à 10, au pompage de mélanges polyphasiques compressibles et au pompage de fluides visqueux.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0400927 | 2004-01-30 | ||
FR0400927A FR2865781B1 (fr) | 2004-01-30 | 2004-01-30 | Pompe a cavites progressives |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1559913A1 true EP1559913A1 (fr) | 2005-08-03 |
EP1559913B1 EP1559913B1 (fr) | 2013-11-06 |
Family
ID=34639817
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05290100.6A Active EP1559913B1 (fr) | 2004-01-30 | 2005-01-17 | Pompe à cavités progressives |
Country Status (6)
Country | Link |
---|---|
US (1) | US7413416B2 (fr) |
EP (1) | EP1559913B1 (fr) |
CN (1) | CN1654823B (fr) |
BR (1) | BRPI0500316B1 (fr) |
CA (1) | CA2494444C (fr) |
FR (1) | FR2865781B1 (fr) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2009035337A1 (fr) * | 2007-09-11 | 2009-03-19 | Agr Subsea As | Pompe à cavité progressive conçue pour pomper des fluides compressibles |
US8388327B2 (en) | 2007-09-20 | 2013-03-05 | Agr Subsea As | Progressing cavity pump with several pump sections |
US8496456B2 (en) | 2008-08-21 | 2013-07-30 | Agr Subsea As | Progressive cavity pump including inner and outer rotors and a wheel gear maintaining an interrelated speed ratio |
CN101960145B (zh) * | 2007-12-31 | 2013-09-11 | 普拉德研究及开发股份有限公司 | 高温螺杆马达或泵部件以及制造方法 |
US8613608B2 (en) | 2008-08-21 | 2013-12-24 | Agr Subsea As | Progressive cavity pump having an inner rotor, an outer rotor, and transition end piece |
DE102014012887A1 (de) | 2013-08-30 | 2015-03-05 | Pcm | Schraubenförmiger Rotor, Exzenterschneckenpumpe und Pumpenvorrichtung |
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US7793683B2 (en) | 2006-10-11 | 2010-09-14 | Weatherford/Lamb, Inc. | Active intake pressure control of downhole pump assemblies |
JP2008175199A (ja) * | 2006-12-20 | 2008-07-31 | Heishin Engineering & Equipment Co Ltd | 一軸偏心ねじポンプ |
US7797142B2 (en) * | 2006-12-21 | 2010-09-14 | Caterpillar Inc | Simulating cavitation damage |
US9051780B2 (en) * | 2007-01-09 | 2015-06-09 | Schlumberger Technology Corporation | Progressive cavity hydraulic machine |
US8523545B2 (en) * | 2009-12-21 | 2013-09-03 | Baker Hughes Incorporated | Stator to housing lock in a progressing cavity pump |
US8083508B2 (en) * | 2010-01-15 | 2011-12-27 | Blue Helix, Llc | Progressive cavity compressor having check valves on the discharge endplate |
US8974205B2 (en) * | 2011-05-06 | 2015-03-10 | NETZSCH-Mohopumpen GmbH | Progressing cavity gas pump and progressing cavity gas pumping method |
US9404493B2 (en) | 2012-06-04 | 2016-08-02 | Indian Institute Of Technology Madras | Progressive cavity pump including a bearing between the rotor and stator |
CA2891162C (fr) | 2012-11-20 | 2016-07-12 | Halliburton Energy Services, Inc. | Appareil, systemes et procedes d'amelioration d'un signal acoustique |
AU2012394944B2 (en) | 2012-11-20 | 2016-05-12 | Halliburton Energy Services, Inc. | Dynamic agitation control apparatus, systems, and methods |
CN103883522B (zh) * | 2014-03-17 | 2016-03-02 | 北京工业大学 | 一种锥螺杆-衬套副的曲面成形方法 |
JP5802914B1 (ja) | 2014-11-14 | 2015-11-04 | 兵神装備株式会社 | 流動体搬送装置 |
CN106996764B (zh) * | 2016-01-25 | 2019-05-14 | 中联重科股份有限公司 | 螺杆泵的定子与转子尺寸的确定方法、装置和系统 |
CN109737070B (zh) * | 2019-02-21 | 2021-02-19 | 安徽佳先功能助剂股份有限公司 | 一种硬脂酰苯甲酰甲烷生产用的多腔体输送泵 |
WO2020257033A1 (fr) * | 2019-06-17 | 2020-12-24 | Nov Process & Flow Technologies Us, Inc. | Pompe à cavité progressive ou rotor de moteur |
US11268385B2 (en) | 2019-10-07 | 2022-03-08 | Nov Canada Ulc | Hybrid core progressive cavity pump |
US11813580B2 (en) | 2020-09-02 | 2023-11-14 | Nov Canada Ulc | Static mixer suitable for additive manufacturing |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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FR695539A (fr) * | 1930-05-13 | 1930-12-17 | Pompe | |
FR1361840A (fr) * | 1963-07-10 | 1964-05-22 | Pompe à vis sans fin excentrée | |
JPH03149377A (ja) * | 1989-11-02 | 1991-06-25 | Kyocera Corp | 一軸偏心ねじポンプ |
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US2765114A (en) | 1953-06-15 | 1956-10-02 | Robbins & Myers | Cone type compressor |
US4424013A (en) * | 1981-01-19 | 1984-01-03 | Bauman Richard H | Energized-fluid machine |
RU1772423C (ru) * | 1990-11-29 | 1992-10-30 | Институт проблем надежности и долговечности машин АН БССР | Одновинтовой насос |
FR2743113B1 (fr) * | 1995-12-28 | 1998-01-23 | Inst Francais Du Petrole | Dispositif de pompage ou de compression d'un fluide polyphasique a aubage en tandem |
US5722820A (en) * | 1996-05-28 | 1998-03-03 | Robbins & Myers, Inc. | Progressing cavity pump having less compressive fit near the discharge |
FR2775028B1 (fr) * | 1998-02-18 | 2000-04-21 | Christian Bratu | Cellule de pompage d'un effluent polyphasique et pompe comportant au moins une de ces cellules |
US6241494B1 (en) * | 1998-09-18 | 2001-06-05 | Schlumberger Technology Company | Non-elastomeric stator and downhole drilling motors incorporating same |
US6457958B1 (en) * | 2001-03-27 | 2002-10-01 | Weatherford/Lamb, Inc. | Self compensating adjustable fit progressing cavity pump for oil-well applications with varying temperatures |
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2004
- 2004-01-30 FR FR0400927A patent/FR2865781B1/fr not_active Expired - Fee Related
-
2005
- 2005-01-17 EP EP05290100.6A patent/EP1559913B1/fr active Active
- 2005-01-19 CA CA2494444A patent/CA2494444C/fr active Active
- 2005-01-28 US US11/044,257 patent/US7413416B2/en active Active
- 2005-01-28 BR BRPI0500316-4A patent/BRPI0500316B1/pt active IP Right Grant
- 2005-01-31 CN CN2005100050533A patent/CN1654823B/zh active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR695539A (fr) * | 1930-05-13 | 1930-12-17 | Pompe | |
FR1361840A (fr) * | 1963-07-10 | 1964-05-22 | Pompe à vis sans fin excentrée | |
JPH03149377A (ja) * | 1989-11-02 | 1991-06-25 | Kyocera Corp | 一軸偏心ねじポンプ |
Non-Patent Citations (2)
Title |
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DATABASE WPI Section PQ Week 199345, Derwent World Patents Index; Class Q56, AN 1993-358797, XP002295333 * |
PATENT ABSTRACTS OF JAPAN vol. 015, no. 374 (M - 1160) 20 September 1991 (1991-09-20) * |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009035337A1 (fr) * | 2007-09-11 | 2009-03-19 | Agr Subsea As | Pompe à cavité progressive conçue pour pomper des fluides compressibles |
US8556603B2 (en) | 2007-09-11 | 2013-10-15 | Agr Subsea As | Progressing cavity pump adapted for pumping of compressible fluids |
US8388327B2 (en) | 2007-09-20 | 2013-03-05 | Agr Subsea As | Progressing cavity pump with several pump sections |
CN101960145B (zh) * | 2007-12-31 | 2013-09-11 | 普拉德研究及开发股份有限公司 | 高温螺杆马达或泵部件以及制造方法 |
US8496456B2 (en) | 2008-08-21 | 2013-07-30 | Agr Subsea As | Progressive cavity pump including inner and outer rotors and a wheel gear maintaining an interrelated speed ratio |
US8613608B2 (en) | 2008-08-21 | 2013-12-24 | Agr Subsea As | Progressive cavity pump having an inner rotor, an outer rotor, and transition end piece |
DE102014012887A1 (de) | 2013-08-30 | 2015-03-05 | Pcm | Schraubenförmiger Rotor, Exzenterschneckenpumpe und Pumpenvorrichtung |
FR3010153A1 (fr) * | 2013-08-30 | 2015-03-06 | Pcm | Rotor helicoidal, pompe a cavites progressives et dispositif de pompage |
US9631619B2 (en) | 2013-08-30 | 2017-04-25 | Pcm Technologies | Helical rotor of a progressing cavity pump |
Also Published As
Publication number | Publication date |
---|---|
US20050169779A1 (en) | 2005-08-04 |
FR2865781B1 (fr) | 2006-06-09 |
FR2865781A1 (fr) | 2005-08-05 |
BRPI0500316B1 (pt) | 2018-03-06 |
BRPI0500316A (pt) | 2005-09-20 |
CN1654823A (zh) | 2005-08-17 |
US7413416B2 (en) | 2008-08-19 |
CN1654823B (zh) | 2011-08-17 |
CA2494444C (fr) | 2012-02-21 |
CA2494444A1 (fr) | 2005-07-30 |
EP1559913B1 (fr) | 2013-11-06 |
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