EP2394056B1 - Pump with an elastic membrane and hydraulic control - Google Patents
Pump with an elastic membrane and hydraulic control Download PDFInfo
- Publication number
- EP2394056B1 EP2394056B1 EP10707069.0A EP10707069A EP2394056B1 EP 2394056 B1 EP2394056 B1 EP 2394056B1 EP 10707069 A EP10707069 A EP 10707069A EP 2394056 B1 EP2394056 B1 EP 2394056B1
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- chamber
- pump
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- volume
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- 239000012528 membrane Substances 0.000 title description 16
- 239000012530 fluid Substances 0.000 claims description 18
- 230000000694 effects Effects 0.000 claims description 6
- 238000000638 solvent extraction Methods 0.000 claims description 6
- 238000013022 venting Methods 0.000 claims 1
- 238000005192 partition Methods 0.000 description 15
- 239000007788 liquid Substances 0.000 description 8
- 238000005086 pumping Methods 0.000 description 8
- 239000007789 gas Substances 0.000 description 6
- 238000007872 degassing Methods 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 3
- 230000005484 gravity Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000003745 diagnosis Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000010943 off-gassing Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000010926 purge Methods 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 230000000007 visual effect Effects 0.000 description 1
- 238000012800 visualization Methods 0.000 description 1
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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
- F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
- F04B43/0081—Special features systems, control, safety measures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
- F04B43/0081—Special features systems, control, safety measures
- F04B43/009—Special features systems, control, safety measures leakage control; pump systems with two flexible members; between the actuating element and the pumped fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
- F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
Definitions
- the present invention relates to hydraulically controlled diaphragm pumps and more particularly to the device for maintaining a suitable volume of liquid in the intermediate chamber between the piston and the diaphragm. See GB1300500 A , with the closest state of the art.
- the liquid present in the intermediate chamber decreases in volume for three main reasons: the existence of leaks, the existence of dissolved gases which affect the performance of the pump and the presence of a safety valve which allows a fluid evacuation in case of overpressure.
- the known recharge devices are of two main types: automatic devices and controlled devices.
- the automatic devices are constituted by a single calibrated valve, suction opening from the reservoir to the intermediate chamber from a certain value of depression.
- the controlled devices comprise one or more valves whose opening is triggered mechanically by the displacement of the membrane and which allow the refeeding only when it is in extreme rear position.
- the membrane is deformable without stiffness or significant elasticity, so that the suction height of the pump is a function of the pressure in the intermediate chamber.
- the automatic systems have the disadvantage of greatly reducing the suction capacity of the pump compared to those of a piston pump because it is necessary to tare the valve so that its opening intervenes at the latest before cavitation in the intermediate chamber and when this opening occurs, the suction immediately stops. If the diaphragm has not traveled all of its suction stroke, the displacement of the pump will be affected.
- Some of the known controlled systems comprise a valve cooperating with a fixed seat through which the refeeding duct opens into the intermediate chamber, the valve being biased on its seat by a spring and being actuated at the opening by the membrane when it tends to exceed the end of the suction stroke of the pump.
- the membrane is flexible and practically without stiffness.
- the diaphragm used is an elastically deformable dome-shaped or cone-shaped membrane of great stiffness and which has a memory of its shape at rest corresponding to the end of the suction stroke at which it returns elastically when the pressure in the intermediate chamber ceases.
- the small displacement of these pumps does not allow to simply transpose the known devices that provide this function. It is therefore appropriate to adapt the compensation system to the particular operating conditions of these pumps.
- the invention consists in this adaptation and leads to a miniaturization of the compensation circuit of the working chamber which There are also advantages, in particular reduced space, in pumps with higher flow rates.
- the subject of the invention is a hydraulically controlled diaphragm pump comprising a pumping chamber formed between a head and a pump body, with a mobile wall formed by an elastically deformable membrane from its resting form. which corresponds to its state at the end of the suction stroke of the pump, a constant volume intermediate hydraulic chamber formed in the pump body, adjacent to the pumping chamber at the level of the membrane and comprising a piston driven by a movement alternating inside this intermediate chamber, a leakage compensation volume of the intermediate chamber being connected thereto by a feedback channel through a free unidirectional valve and without calibration whose direction is in the direction of the intermediate chamber, characterized in that the unidirectional valve and at least one reservoir part of the compensation volume are housed in a body attached to the pump body at the highest point of the intermediate hydraulic chamber in the working position of the pump.
- the insert body is in two parts, namely a lower partition element carrying the seat of the free valve and a holding element of the partition element forming a reservoir for the compensation and closure volume of the latter. .
- the volume of the intermediate chamber (or working chamber) is divided between a main volume swept by the end of the piston in its reciprocating movement and a reduced secondary volume formed by the extremely short feed line and functional spaces. existing due to the constitution of the body of the pump in several pieces assembled to delimit the working chamber. This volume is thus limited to the minimum necessary for the operation of the pump, with dead spaces of reduced volume and virtually without seals subjected to high pressure so likely to modify, by their deformation, the volume of the working chamber.
- the channels that belong to the secondary volume of the working chamber can affect weak sections because the fluid used is of high quality without solid particles and without a lot of dissolved gases.
- the invention makes it possible to reduce to a few cubic centimeters the capacity of the compensation volume for the fluid necessary for the replenishment of the intermediate hydraulic chamber.
- the compensation volume is also distributed between the reported body which contains the greater part of this volume by forming a reservoir which is radially implanted in the body of the pump, for example in the part of this body close to the guide bearing surface of the pump. working piston and the various channels and functional clearances which are at atmospheric pressure, in the vicinity of the working piston guiding bearing surface and in communication with this reservoir.
- the free unidirectional valve is, in the sense of the invention a valve completely free of return spring on its seat, which may be the case when this recall is provided by the effect of the force of gravity or a valve assisted to closing by a spring whose role is to compensate for the effect of gravity if the latter for example has the effect of moving the valve from its seat.
- the working chamber is also connected to the reservoir of the compensation volume by a channel discharge and through a calibrated safety valve which closes it when the pressure in the working chamber is below the calibration value.
- the aforesaid body includes this discharge channel bypassing the free valve in the partition element.
- a degassing channel is provided between the discharge channel and the reservoir of the compensation volume bypassing the safety valve.
- the safety valve advantageously comprises a rod whose free end constitutes an overpressure indicator in the working chamber.
- a space belonging to the compensation volume is formed between the piston and its guide sleeve and forms a means for collecting leaks between the piston and the sleeve.
- a hydraulically controlled pump head comprises a pumping head 1 which defines with a membrane 2 a pumping chamber 3.
- the membrane 2 is elastically deformable from its form at rest (the one shown) which corresponds to its state at the end of the suction stroke of the pump.
- the stiffness of this membrane is such that the suction power of the pump is defined by the ability of the membrane to return by itself to its rest position. It is more specifically a low flow pump and medium or high pressure.
- the pumping chamber is connected to the outside by a suction channel 4 and a discharge channel 5, which are equipped with unidirectional valves contained in valve boxes 6 and 7.
- the membrane constitutes the deformable wall of an intermediate hydraulic chamber 8 formed in the body 9 of the pump.
- a piston 10 is mechanically driven by a motor and a transmission known in themselves, a movement back and forth in the intermediate chamber 8.
- the volume of the chamber 8 is theoretically constant and the volume swept into this chamber by the piston 10 corresponds to the variation of volume of the pumping chamber 3.
- the fluid contained in this chamber although incompressible, sees its volume vary due to leaks between the piston and the guide of its reciprocating movement in the body of the pump .
- the working fluid contains dissolved gases that are released during the compression-decompression cycles that it undergoes.
- a safety valve allows the fluid to escape from the intermediate chamber when there is a blockage at the pumping chamber.
- the volume of the chamber 8 is not constant and it is necessary to provide the compensation of the fluid lost by suction of a sufficient amount of the latter during the suction stroke of the piston 10.
- the intermediate chamber 8 is in communication with a compensation tank 11 by two channels 12a and 12b.
- Channel 12a is a feed channel which connects the working chamber to the compensation tank 11.
- This channel 12a comprises a unidirectional valve 13, free, that is to say whose valve freely falls on its seat or is recalled by a very weak support spring. The forward direction is that going from the tank 11 to the intermediate chamber 8.
- the channel 12b is a discharge channel and comprises a calibrated valve 15 which constitutes the safety valve mentioned above for the chamber 8. This valve is passing in the direction from the chamber 8 to the tank 11 if the pressure in the Chamber 8 exceeds an adjustable threshold value by adjusting the calibration of the valve by means, for example, of a screw 16. A purge passage for the gas contained in the chamber 8 may be made bypassing the safety valve 15 as illustrated by FIG. example by channel 14.
- channel 12a that is downstream of valve 13 opposite its direction, participates in the known pumps, the need for compensation of displacement losses of the pump.
- this channel portion is generally made in the form of independent conduits, connected by means of seals and which are source of leaks of the fluid they contain, subject to pressure variations during operation of the pump and of which the volume is large compared to that of the working chamber of a small flow pump.
- the invention is a constructive measure, one of the advantages of which is to make this volume of fluid "dead” minimal and confined under reinforced sealing to reduce the needs for compensation of the working chamber of the pump.
- the piston 10 is slidably mounted in a guide sleeve 17 mounted in the pump body 9 so that the guide 17 defines on the side of the intermediate chamber 8 with the pump body 9 which receives it, an annular space 18 which opens on the intermediate chamber 8 and forms part of the channel 12a or part of the chamber 8.
- the sleeve 17 also delimits with the piston 10 a collection chamber 19 leaks of the working liquid.
- the chamber 8, the annular space 18 and the chamber 19 are connected by channels 20, 21 to a cavity 22 formed in the body 9 of the pump in which a tubular partition element 23 is housed.
- This partitioning element defines in the cavity 22 a chamber 24 in which opens the channel 20 from the chamber 19 for collecting leaks.
- the bottom of the tubular partition element 23 has a central channel 25 which communicates with the chamber 24.
- This channel opens into a housing 26 of the partition element in which is housed the safety valve 15.
- the seat of this valve 15 is constituted by the bottom of this housing 26 above the outlet of the channel 25. Above this seat, the valve 15 defines an annular chamber 27 in the housing 26, in which opens an extension 28 of the channel 21 formed in the partition element 23.
- a chamber 29 formed in the valve 15 communicates with the channel 25 and thus the chamber 24 by a channel 30 which comprises the valve 13, passing in the direction from the chamber 24 to the chamber 29.
- valve 13 is here a ball valve movable relative to a seat carried by the calibrated valve 15 which is the outlet in the chamber 29 of the channel 30.
- the stroke of this valve is limited by a stop 13a housed in the safety valve 15.
- the chamber 29 is above this ball under the abutment 13a.
- the annular chamber 27 communicates continuously with the chamber 29 by a channel 29a through the body of the valve 15.
- the end of the valve 15 facing the bottom of the housing 26 is conical, which allows the pressure in the chamber 29 , therefore in the chamber 8, to reign in a chamber 27a and to be applied to a large effective surface of the valve 15. Above the annular chamber 27, the valve 15 slides in the housing 26.
- the safety valve 15, inside the partition element 23, is returned to its seat by a spring R.
- a tubular element 31 forms the enclosure of the compensation reservoir 34 and cooperates by screwing with a threaded portion 22a of the cavity 22 to firmly secure the partitioning element 23 at the bottom of this cavity. cavity.
- This tubular element carries a perforated transverse partition 32 to support the adjusting screw 16 for setting the return spring of the valve 15.
- the spring R thus extends between this screw 16 and the valve 15 in the internal space of the element 31 which constitutes a reservoir 34 which is the main part of the compensation volume 11.
- a channel 33 formed in the partition element 23 permanently connects the reservoir 34 to the chamber 24.
- a seal 35 is provided at the connection of the channels 21 and 28.
- the assembly is surmounted by a transparent cover 36 removable that closes the compensation volume, allows access to add oil if necessary and allows several checks of the operation of the pump.
- the working oil level that is to say the fluid contained in the intermediate hydraulic chamber and in the compensation volume, is adjusted to be in operation above the perforated partition 32.
- the portion of the feed channel 12a downstream of the valve 13 here comprises the chamber 29 the bore 29a, the channel 28 and the channel 21 and that the upstream portion of the discharge channel 12b further comprises channels and spaces preceding the chamber 27 and the chamber 27a.
- the compensation volume is formed by all parts of the hydraulic circuit which are at atmospheric pressure, namely chambers, channels, volumes and orifices 19, 20, 24, 25, 30, 33 and 34.
- the degassing channel 14 here consists of the cylindrical functional clearance that exists between the stop 13a of the valve 13 and the inner surface of the valve 15 as well as the functional clearance between the valve 15 and the housing 26 of the element 23.
- the elastic return of the membrane to its state of rest is allowed.
- the volume of liquid in the chamber 8 may be less than that of the working chamber, of course increased by the volume of all the channels and adjoining chambers that communicate freely with chamber 8 because of permanent leakage of this fluid and outgassing.
- the last part of the suction stroke of the piston can cause in this case a vacuum in this chamber and the valve 13 opens. Liquid is therefore admitted in addition to the intermediate hydraulic chamber 8 and the displacement of the pump is preserved. As a result, there is a compensation flow supplying the hydraulic chamber.
- the figure 3 illustrates a preferred embodiment of the invention.
- the differences of embodiment are due to the body attached to the pump body 9.
- the partitioning element 23 carries two ball valves 40 and 41 in series. The valves are no longer formed in the body of the safety valve 15.
- the channel 21 extended by the channel 28 is in communication with a section 29b of the chamber 29 around the second valve 41.
- the chamber 29 is located above the element 23, hollowed as a counterbore of the body of the valve 15 of a drawer 42 with an internal channel 43 which comes from the highest point of the chamber 29.
- the spool Under the effect of an overpressure, the spool is raised against the effect of the return spring R, the overpressure being that which can prevail in the working chamber 8, 18 and reaching the chamber 29 through the channels 21 and 28.
- the slide 42 is no longer properly a safety valve through which the fluid under excessive pressure. It constitutes, with the element 31 in which it is slidably guided, a variable volume capacity which constitutes an expansion chamber for limiting the pressure in the channels to that set by the calibration of the spring R.
- the spring R tends to press the drawer 42 on the partitioning element 23, making the volume of the chamber 29 minimal.
- the functional clearance serves as a degassing channel 14 at the outlet of the channel 43.
- the pressure part of the channel 12a comprises the channels 21, 28, the chamber 29 with its section 29b (increased by the volume of the blind channel 43 while the pressure portion of the channel 12b comprises the channels and spaces 28, 29b, 29 and 43, the spaces 29 and 29b being of variable volume.
- the slide 42 is provided with a rod 44 whose end 44a, which can be colored, constitutes an overpressure indicator in the working chamber and therefore an abnormal operation of the pump. Indeed, an operator will easily notice, through the transparent wall 36, the beat of the end 44a of the rod 44 under this wall, sign for example that the discharge circuit of the pump is closed. It is then possible for him to intervene quickly. In order for this indicator to be visible, the screw 16 for setting the safety valve is replaced in this variant by a hollow nut 16a.
- valves 40, 41 open and a replenishment of the working volume occurs.
- the valves 40 and 41 are supported on their seat by the discharge pressure and the working fluid is trapped in the working chamber, leaks near which are weak and compensated during the next suction stroke .
- the cylindrical partition element 23 houses the two valves and is housed in the recess 22 of the pump body which extends perpendicularly to the axis of the piston 10.
- the functions, compensation, safety and degassing, increased by a visualization function, are provided by an assembly which is mounted as a cartridge in the transverse recess 22 of the body 9 of the pump, namely the cylindrical partition element element 23, the two valves 40, 41, the R spring and the tubular element 31 for fixing this partition element in the cavity 22 of the pump body which closes the main reservoir 34 of the compensation volume, which carries the setting means of the safety valve or sliding drawer the expansion chamber and which allows a transparent hood 36 monitoring the operation of the device and in particular to make a visual diagnosis of the pressure at the discharge of the pump.
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Description
La présente invention concerne les pompes à membrane à commande hydraulique et plus spécialement le dispositif destiné à maintenir un volume de liquide convenable dans la chambre intermédiaire comprise entre le piston et la membrane. Voir
Le liquide présent dans la chambre intermédiaire voit son volume diminuer pour trois raisons principales : l'existence de fuites, l'existence de gaz dissous qui affectent la performance de la pompe et la présence d'une soupape de sécurité qui permet une évacuation de fluide en cas de surpression.The liquid present in the intermediate chamber decreases in volume for three main reasons: the existence of leaks, the existence of dissolved gases which affect the performance of the pump and the presence of a safety valve which allows a fluid evacuation in case of overpressure.
Il est donc nécessaire, dans ce type de pompe, de prévoir un système de réalimentation de la chambre en question, généralement à partir d'un réservoir auxiliaire. Ce système, dit système de compensation, doit maintenir dans la chambre intermédiaire un volume de liquide permettant dans toutes les conditions de marche un débattement de la membrane correspondant à la cylindrée balayée par le piston sans risque de détérioration de cette membrane ni de perturbation du débit.It is therefore necessary, in this type of pump, to provide a system for refilling the chamber in question, generally from an auxiliary tank. This system, called the compensation system, must maintain in the intermediate chamber a volume of liquid allowing in all operating conditions a deflection of the diaphragm corresponding to the piston swept volume without risk of deterioration of this membrane or disturbance of the flow rate. .
Les dispositifs de réalimentation connus sont de deux types principaux: les dispositifs automatiques et les dispositifs commandés. Les dispositifs automatiques sont constitués par un simple clapet taré, d'aspiration s'ouvrant du réservoir vers la chambre intermédiaire à partir d'une certaine valeur de dépression. Les dispositifs commandés comportent un ou plusieurs clapets dont l'ouverture est déclenchée mécaniquement par le débattement de la membrane et qui permettent la réalimentation uniquement lorsque celle-ci se trouve en position arrière extrême.The known recharge devices are of two main types: automatic devices and controlled devices. The automatic devices are constituted by a single calibrated valve, suction opening from the reservoir to the intermediate chamber from a certain value of depression. The controlled devices comprise one or more valves whose opening is triggered mechanically by the displacement of the membrane and which allow the refeeding only when it is in extreme rear position.
Dans les deux cas, la membrane est déformable sans raideur ou élasticité significative, si bien que la hauteur d'aspiration de la pompe est une fonction de la pression dans la chambre intermédiaire. Dans ces conditions les systèmes automatiques ont l'inconvénient de diminuer fortement les capacités d'aspiration de la pompe par rapport à celles d'une pompe à piston car il convient de tarer le clapet pour que son ouverture intervienne au plus tard avant la cavitation dans la chambre intermédiaire et au moment ou cette ouverture intervient, l'aspiration cesse immédiatement. Si la membrane n'a pas parcouru la totalité de sa course d'aspiration, la cylindrée de la pompe sera affectée.In both cases, the membrane is deformable without stiffness or significant elasticity, so that the suction height of the pump is a function of the pressure in the intermediate chamber. Under these conditions the automatic systems have the disadvantage of greatly reducing the suction capacity of the pump compared to those of a piston pump because it is necessary to tare the valve so that its opening intervenes at the latest before cavitation in the intermediate chamber and when this opening occurs, the suction immediately stops. If the diaphragm has not traveled all of its suction stroke, the displacement of the pump will be affected.
Certains des systèmes commandés connus comportent un clapet coopérant avec un siège fixe au travers duquel le conduit de réalimentation débouche dans la chambre intermédiaire, le clapet étant rappelé sur son siège par un ressort et étant actionné à l'ouverture par la membrane lorsqu'elle tend à dépasser la fin de la course d'aspiration de la pompe. Dans la plupart des cas la membrane est souple et pratiquement sans rigidité.Some of the known controlled systems comprise a valve cooperating with a fixed seat through which the refeeding duct opens into the intermediate chamber, the valve being biased on its seat by a spring and being actuated at the opening by the membrane when it tends to exceed the end of the suction stroke of the pump. In most cases the membrane is flexible and practically without stiffness.
Dans certaines pompes à petit débit, la membrane mise en oeuvre est une membrane en forme de dôme ou de cône élastiquement déformable, de grande raideur et qui possède une mémoire de sa forme au repos correspondant à la fin de la course d'aspiration à laquelle elle retourne élastiquement quand la pression dans la chambre intermédiaire cesse.In certain small flow pumps, the diaphragm used is an elastically deformable dome-shaped or cone-shaped membrane of great stiffness and which has a memory of its shape at rest corresponding to the end of the suction stroke at which it returns elastically when the pressure in the intermediate chamber ceases.
La faible cylindrée de ces pompes ne permet pas de simplement transposer les dispositifs connus qui assurent cette fonction. Il convient donc d'adapter le système de compensation aux conditions particulières de fonctionnement de ces pompes. L'invention consiste en cette adaptation et conduit à une miniaturisation du circuit de compensation de la chambre de travail qui trouve également des avantages, notamment de diminution d'encombrement, dans des pompes de plus forts débits.The small displacement of these pumps does not allow to simply transpose the known devices that provide this function. It is therefore appropriate to adapt the compensation system to the particular operating conditions of these pumps. The invention consists in this adaptation and leads to a miniaturization of the compensation circuit of the working chamber which There are also advantages, in particular reduced space, in pumps with higher flow rates.
C'est ainsi que l'invention a pour objet une pompe à membrane à commande hydraulique comportant une chambre de pompage ménagée entre une tête et un corps de pompe, avec une paroi mobile formée par une membrane élastiquement déformable à partir de sa forme au repos qui correspond à son état en fin de course d'aspiration de la pompe, une chambre hydraulique intermédiaire à volume constant ménagée dans le corps de pompe, mitoyenne de la chambre de pompage au niveau de la membrane et comportant un piston animé d'un mouvement alternatif à l'intérieur de cette chambre intermédiaire, un volume de compensation des fuites de la chambre intermédiaire étant relié à cette dernière par un canal de réalimentation au travers d'un clapet unidirectionnel libre et sans tarage dont le sens passant est en direction de la chambre intermédiaire, caractérisée en ce que le clapet unidirectionnel et au moins une partie formant réservoir du volume de compensation sont logés dans un corps rapporté sur le corps de pompe au point le plus haut de la chambre hydraulique intermédiaire dans la position de travail de la pompe.Thus, the subject of the invention is a hydraulically controlled diaphragm pump comprising a pumping chamber formed between a head and a pump body, with a mobile wall formed by an elastically deformable membrane from its resting form. which corresponds to its state at the end of the suction stroke of the pump, a constant volume intermediate hydraulic chamber formed in the pump body, adjacent to the pumping chamber at the level of the membrane and comprising a piston driven by a movement alternating inside this intermediate chamber, a leakage compensation volume of the intermediate chamber being connected thereto by a feedback channel through a free unidirectional valve and without calibration whose direction is in the direction of the intermediate chamber, characterized in that the unidirectional valve and at least one reservoir part of the compensation volume are housed in a body attached to the pump body at the highest point of the intermediate hydraulic chamber in the working position of the pump.
Pour des raisons d'assemblage, le corps rapporté est en deux parties, à savoir un élément de cloisonnement inférieur portant le siège du clapet libre et un élément de maintien de cet élément de cloisonnement formant réservoir pour le volume de compensation et fermeture de ce dernier.For assembly reasons, the insert body is in two parts, namely a lower partition element carrying the seat of the free valve and a holding element of the partition element forming a reservoir for the compensation and closure volume of the latter. .
Le volume de la chambre intermédiaire (ou chambre de travail) se répartit entre un volume principal balayé par l'extrémité du piston dans son mouvement alternatif et un volume secondaire réduit formé du conduit de réalimentation extrêmement court et d'espaces fonctionnels existant du fait de la constitution du corps de la pompe en plusieurs pièces assemblées pour délimiter la chambre de travail. Ce volume est ainsi limité au minimum nécessaire au fonctionnement de la pompe, avec des espaces morts de volume réduit et pratiquement sans joints d'étanchéité soumis à la haute pression donc susceptibles de modifier, par leur déformation, le volume de la chambre de travail. Les chenaux qui appartiennent au volume secondaire de la chambre de travail peuvent affecter des sections faibles car le fluide utilisé est de très grande qualité sans particules solides et sans beaucoup de gaz dissous.The volume of the intermediate chamber (or working chamber) is divided between a main volume swept by the end of the piston in its reciprocating movement and a reduced secondary volume formed by the extremely short feed line and functional spaces. existing due to the constitution of the body of the pump in several pieces assembled to delimit the working chamber. This volume is thus limited to the minimum necessary for the operation of the pump, with dead spaces of reduced volume and virtually without seals subjected to high pressure so likely to modify, by their deformation, the volume of the working chamber. The channels that belong to the secondary volume of the working chamber can affect weak sections because the fluid used is of high quality without solid particles and without a lot of dissolved gases.
Ainsi l'invention permet de réduire à quelques centimètres cubes la capacité du volume de compensation pour le fluide nécessaire à la réalimentation de la chambre hydraulique intermédiaire. Le volume de compensation est aussi réparti entre le corps rapporté qui contient la plus grande part de ce volume en formant un réservoir qui est radialement implanté dans le corps de la pompe, par exemple dans la partie de ce corps voisine de la portée de guidage du piston de travail et les différents canaux et jeux fonctionnels qui sont à la pression atmosphérique, au voisinage de la portée de guidage du piston de travail et en communication avec ce réservoir .Thus, the invention makes it possible to reduce to a few cubic centimeters the capacity of the compensation volume for the fluid necessary for the replenishment of the intermediate hydraulic chamber. The compensation volume is also distributed between the reported body which contains the greater part of this volume by forming a reservoir which is radially implanted in the body of the pump, for example in the part of this body close to the guide bearing surface of the pump. working piston and the various channels and functional clearances which are at atmospheric pressure, in the vicinity of the working piston guiding bearing surface and in communication with this reservoir.
Le clapet unidirectionnel libre est, au sens de l'invention un clapet totalement dépourvu de ressort de rappel sur son siège, ce qui peut être le cas lorsque ce rappel est assuré par l'effet de la force de la gravité ou un clapet assisté à la fermeture par un ressort dont le rôle est de compenser l'effet de la gravité si cette dernière a par exemple pour effet d'éloigner le clapet de son siège.The free unidirectional valve is, in the sense of the invention a valve completely free of return spring on its seat, which may be the case when this recall is provided by the effect of the force of gravity or a valve assisted to closing by a spring whose role is to compensate for the effect of gravity if the latter for example has the effect of moving the valve from its seat.
Par ailleurs, la chambre de travail est également reliée au réservoir du volume de compensation par un canal de décharge et au travers d'un clapet de sécurité taré qui l'obture lorsque la pression dans la chambre de travail est en dessous de la valeur de tarage. Le corps rapporté susdit comporte ce canal de décharge en dérivation du clapet libre dans l'élément de cloisonnement.Moreover, the working chamber is also connected to the reservoir of the compensation volume by a channel discharge and through a calibrated safety valve which closes it when the pressure in the working chamber is below the calibration value. The aforesaid body includes this discharge channel bypassing the free valve in the partition element.
De plus, un canal de dégazage est prévu entre le canal de décharge et le réservoir du volume de compensation en dérivation du clapet de sécurité.In addition, a degassing channel is provided between the discharge channel and the reservoir of the compensation volume bypassing the safety valve.
On notera que la paroi de sommet du corps rapporté est transparente.Note that the top wall of the reported body is transparent.
Le clapet de sécurité comporte avantageusement une tige dont l'extrémité libre constitue un témoin de surpression dans la chambre de travail.The safety valve advantageously comprises a rod whose free end constitutes an overpressure indicator in the working chamber.
Enfin, un espace appartenant au volume de compensation est ménagé entre le piston et son manchon de guidage et forme un moyen de collecte des fuites entre le piston et le manchon.Finally, a space belonging to the compensation volume is formed between the piston and its guide sleeve and forms a means for collecting leaks between the piston and the sleeve.
D'autres caractéristiques et avantages de l'invention ressortiront de la description donnée ci-après d'un exemple de réalisation de l'invention.Other features and advantages of the invention will emerge from the description given below of an exemplary embodiment of the invention.
Il sera fait référence aux dessins annexés parmi lesquels :
- la
figure 1 est un schéma fonctionnel de la pompe selon l'invention, - la
figure 2 est un plan de coupe d'une première réalisation de la pompe selon lafigure 1 et lafigure 2A est un agrandissement partiel de cettefigure 2 , - la
figure 3 illustre un agrandissement partiel d'une variante de réalisation préférée de l'invention.
- the
figure 1 is a block diagram of the pump according to the invention, - the
figure 2 is a cutting plane of a first realization of the pump according to thefigure 1 and theFigure 2A is a partial enlargement of thisfigure 2 , - the
figure 3 illustrates a partial enlargement of a preferred embodiment of the invention.
En se reportant à la
La chambre de pompage est reliée à l'extérieur par un canal d'aspiration 4 et un canal de refoulement 5, lesquels sont équipés de clapets unidirectionnels contenus dans des boîtes à clapets 6 et 7.The pumping chamber is connected to the outside by a
La membrane constitue la paroi déformable d'une chambre hydraulique intermédiaire 8 ménagée dans le corps 9 de la pompe. Un piston 10 est animé mécaniquement par un moteur et une transmission connus en eux-mêmes, d'un mouvement de va et vient dans la chambre intermédiaire 8. Le volume de la chambre 8 est théoriquement constant et le volume balayé dans cette chambre par le piston 10 correspond à la variation de volume de la chambre de pompage 3. Le fluide contenu dans cette chambre bien qu'incompressible, voit son volume varier du fait des fuites entre le piston et le guide de son mouvement alternatif dans le corps de la pompe. En outre, le fluide de travail contient des gaz dissous qui se libèrent au cours des cycles de compression-décompression qu'il subit. Enfin, une soupape de sécurité permet un échappement du fluide de la chambre intermédiaire quand survient un blocage au niveau de la chambre de pompage. Le volume de la chambre 8 n'est donc pas constant et il convient de prévoir la compensation du fluide perdu par aspiration d'une quantité suffisante de ce dernier lors de la course d'aspiration du piston 10.The membrane constitutes the deformable wall of an intermediate
A cet effet, la chambre intermédiaire 8 est en communication avec un réservoir de compensation 11 par deux canaux 12a et 12b. Le canal 12a est un canal de réalimentation qui relie la chambre de travail au réservoir de compensation 11. Ce canal 12a comporte un clapet unidirectionnel 13, libre, c'est-à-dire dont le clapet retombe librement sur son siège ou est rappelé par un ressort d'assistance très faible. Le sens passant est celui allant du réservoir 11 vers la chambre intermédiaire 8.For this purpose, the
Le canal 12b est un canal de décharge et comporte un clapet taré 15 qui constitue la soupape de sécurité évoquée ci-dessus pour la chambre 8. Ce clapet est passant dans le sens allant de la chambre 8 vers le réservoir 11 si la pression dans la chambre 8 excède une valeur de seuil réglable par réglage du tarage du clapet au moyen par exemple d'une vis 16. Un passage de purge pour le gaz contenu dans la chambre 8 peut être réalisé en dérivation de la soupape de sécurité 15 comme illustré par exemple par le canal 14.The
On comprend qu'une course vers l'arrière du piston 10 permet le retour élastique de la membrane 3 dans sa position de repos. Si cette position est atteinte avant que le piston ait atteint son point mort arrière, il se produit une dépression dans la chambre 8 qui se traduit par l'aspiration d'un volume de liquide soutiré du réservoir 11 au travers du clapet 13. D'autre part, lors du fonctionnement de la pompe, le gaz contenu dans le liquide de travail de la chambre 8 est, au gré des cycles de compression dépression, purgé en continu par le canal 14. On aura pris la précaution de placer le canal 12a au-dessus de la chambre 8 de manière à profiter de l'accumulation naturelle du gaz au point haut de cette chambre. Enfin, si un blocage se produit dans la chambre de pompage, le fluide de la chambre 8 peut être évacué par le canal 12b au travers de la soupape de sécurité 15 qui débouche dans le réservoir 11.It is understood that a stroke towards the rear of the
La partie du canal 12a qui se trouve en aval du clapet 13 en regard de son sens passant, participe, dans les pompes connues, du besoin en compensation des pertes de cylindrée de la pompe. En effet, cette partie de canal est en général réalisée sous forme de conduits indépendants, raccordés par l'intermédiaire de joints et qui sont source de fuites du fluide qu'ils contiennent, soumis aux variations de pression lors du fonctionnement de la pompe et dont le volume est important par rapport à celui de la chambre de travail d'une pompe à petit débit.The portion of channel 12a that is downstream of
L'invention est une mesure constructive dont l'un des avantages est de rendre ce volume de fluide « mort » minimal et confiné sous étanchéité renforcée pour réduire les besoins en compensation de la chambre de travail de la pompe.The invention is a constructive measure, one of the advantages of which is to make this volume of fluid "dead" minimal and confined under reinforced sealing to reduce the needs for compensation of the working chamber of the pump.
Aux
Dans cette réalisation, le manchon 17 délimite aussi avec le piston 10 une chambre de collecte 19 des fuites du liquide de travail.In this embodiment, the
La chambre 8, l'espace annulaire 18 et la chambre 19 sont reliés par des canaux 20, 21 à une cavité 22 ménagée dans le corps 9 de la pompe dans laquelle un élément de cloisonnement tubulaire 23 est logé. Cet élément de cloisonnement définit dans la cavité 22 une chambre 24 dans laquelle débouche le canal 20 issu de la chambre 19 de collecte des fuites.The
Le fond de l'élément de cloisonnement tubulaire 23 possède un canal 25 central qui communique avec la chambre 24. Ce canal débouche dans un logement 26 de l'élément de cloisonnement dans lequel est logé le clapet de sécurité 15. Le siège de ce clapet 15 est constitué par le fond de ce logement 26 autour du débouché du canal 25. Au dessus de ce siège, le clapet 15 définit une chambre annulaire 27 dans le logement 26, dans laquelle débouche une prolongation 28 du canal 21 ménagée dans l'élément de cloisonnement 23.The bottom of the
Une chambre 29 ménagée dans le clapet 15 communique avec le canal 25 et donc la chambre 24 par un canal 30 qui comporte le clapet 13, passant dans le sens allant de la chambre 24 à la chambre 29.A
On constate que le clapet 13 est ici un clapet à bille mobile par rapport à un siège porté par le clapet taré 15 qui est le débouché dans la chambre 29 du canal 30. La course de ce clapet est limitée par une butée 13a logée dans le clapet de sécurité 15. La chambre 29 est au dessus de cette bille sous la butée 13a.It is found that the
La chambre annulaire 27 communique en permanence avec la chambre 29 par un canal 29a au travers du corps du clapet 15. L'extrémité du clapet 15 en regard du fond du logement 26 est conique, ce qui permet à la pression régnant dans la chambre 29, donc dans la chambre 8, de régner dans une chambre 27a et d'être appliquée sur une surface utile importante du clapet 15. Au dessus de la chambre annulaire 27, le clapet 15 coulisse dans le logement 26.The
Le clapet de sécurité 15, à l'intérieur de l'élément de cloisonnement 23, est rappelé sur son siège par un ressort R.The
Un élément tubulaire 31 forme l'enceinte du réservoir 34 de compensation et coopère par vissage avec une partie taraudée 22a de la cavité 22 pour assujettir fermement l'élément de cloisonnement 23 au fond de cette cavité. Cet élément tubulaire porte une cloison transversale 32 ajourée pour supporter la vis 16 de réglage du tarage ressort de rappel du clapet 15.A
Le ressort R s'étend donc entre cette vis 16 et le clapet 15 dans l'espace interne de l'élément 31 qui constitue un réservoir 34 qui est la partie principale du volume de compensation 11.The spring R thus extends between this
Un canal 33 ménagé dans l'élément de cloisonnement 23 relie de manière permanente le réservoir 34 à la chambre 24. Un joint 35 est prévu au raccordement des canaux 21 et 28.A
L'ensemble est surmonté d'un capot transparent 36 amovible qui ferme le volume de compensation, en permet l'accès pour y ajouter de l'huile le cas échéant et permet plusieurs contrôles du fonctionnement de la pompe. Le niveau d'huile de travail, c'est-à-dire le fluide contenu dans la chambre hydraulique intermédiaire et dans le volume de compensation, est ajusté pour être en fonctionnement au-dessus de la cloison ajourée 32.The assembly is surmounted by a
On notera que la partie du canal 12a de réalimentation en aval du clapet 13 (par référence à la
Le canal de dégazage 14 est ici constitué par le jeu fonctionnel cylindrique qui existe entre la butée 13a du clapet 13 et la surface intérieure du clapet 15 ainsi que par le jeu fonctionnel existant entre le clapet 15 et le logement 26 de l'élément 23.The degassing
En fonctionnement, lorsque le piston 10 se déplace dans la direction A d'aspiration, le retour élastique de la membrane vers son état de repos est autorisé. Généralement il règne une pression supérieure à pression atmosphérique dans la chambre 8. Toutefois, le volume de liquide dans la chambre 8 peut être inférieur à celui de la chambre de travail, augmenté bien entendu du volume de tous les canaux et chambres annexes qui communiquent librement avec la chambre 8 à cause des fuites permanentes de ce fluide et du dégazage. La dernière partie de la course d'aspiration du piston peut provoquer dans ce cas une dépression dans cette chambre et le clapet 13 s'ouvre. Du liquide est donc admis en complément dans la chambre hydraulique intermédiaire 8 et la cylindrée de la pompe est préservée. Il se produit donc en tant que de besoin, un débit de compensation alimentant la chambre hydraulique.In operation, when the
Lors de la course de refoulement (sens C sur les figures) la pression dans la chambre 8 est très élevée ce qui conduit à la fermeture du clapet 13. C'est pendant cette partie de la course que les fuites se produisent. Si la pression est supérieure à une valeur critique correspondant au tarage de la soupape de sécurité 15, le clapet 15 de cette soupape s'ouvre et la surpression est évacuée en direction de l'espace 34 au-dessus de l'élément de cloisonnement 23 par l'intermédiaire des conduits 25, 24 et 33. La turbulence du niveau d'huile qui s'ensuit en surface du réservoir 34, est perçue par l'opérateur comme le signe de ce dysfonctionnement. Le dégazage du fluide de travail est ici réalisé, si nécessaire à chaque coup de pompe le long du canal capillaire 14 qui existe entre la butée 13a du clapet 13 et le corps du clapet de décharge 15.During the discharge stroke (direction C in the figures) the pressure in the
La
Sous l'effet d'une surpression, le tiroir est soulevé contre l'effet du ressort de rappel R, la surpression étant celle pouvant régner dans la chambre de travail 8, 18 et parvenant à la chambre 29 par les canaux 21 et 28. Le tiroir 42 n'est plus à proprement parlé une soupape de sécurité traversée par le fluide sous pression excessive. Il constitue, avec l'élément 31 dans lequel il est guidé à coulissement, une capacité à volume variable qui constitue une chambre d'expansion pour limiter la pression dans les canaux à celle réglée par le tarage du ressort R. Le ressort R tend à plaquer le tiroir 42 sur l'élément de cloisonnement 23 rendant minimal le volume de la chambre 29. Entre le tiroir 42 et l'élément 31, le jeu fonctionnel sert de canal de dégazage 14 à la sortie du canal 43.Under the effect of an overpressure, the spool is raised against the effect of the return spring R, the overpressure being that which can prevail in the working
Pour comparer cette réalisation avec celle de la
Il faut enfin mentionner que le tiroir 42 est pourvu d'une tige 44 dont l'extrémité 44a, qui peut être colorée, constitue un témoin de surpression dans la chambre de travail donc d'un fonctionnement anormal de la pompe. En effet, un opérateur remarquera aisément, au travers de la paroi transparente 36, le battement de l'extrémité 44a de la tige 44 sous cette paroi, signe par exemple que le circuit de refoulement de la pompe est fermé. Il lui est alors possible d'intervenir rapidement. Pour que ce témoin puisse être visible, la vis 16 de tarage du clapet de sécurité est remplacée dans cette variante par un écrou évidé 16aFinally, it should be mentioned that the slide 42 is provided with a
On constate que le volume de fluide qui est soumis à la haute pression et aux variations cycliques est limité par des parois indéformables, c'est-à-dire sans joint - sauf un joint torique 35 à la jonction des canaux 21 et 28. Cette disposition contribue à la stabilité de la cylindrée de la pompe dans le temps.It can be seen that the volume of fluid which is subjected to high pressure and to cyclic variations is limited by walls which are dimensionally stable, that is to say without joints - except for an O-
Le fonctionnement de cette variante de réalisation est le suivant. En cas de manque de fluide dans le volume de travail de la pompe, en fin de course d'aspiration, la pression dans la chambre 29 est inférieure à la pression atmosphérique. Les clapets 40, 41 s'ouvrent et une réalimentation du volume de travail se produit. Pendant la course de refoulement, les clapets 40 et 41 sont appuyés sur leur siège par la pression de refoulement et le fluide de travail est prisonnier de la chambre de travail, aux fuites près qui sont faibles et compensées lors de la course d'aspiration suivante.The operation of this variant embodiment is as follows. In case of lack of fluid in the working volume of the pump, at the end of suction stroke, the pressure in the
L'un des avantages de ces réalisations réside dans la compacité de l'assemblage, la chambre de compensation étant répartie dans différents logements ménagés dans le corps de la pompe et, principalement, dans le corps rapporté qui contient le clapet de compensation et la soupape de sécurité. L'encombrement suivant la direction du piston de travail est ainsi réduite car le volume de compensation, qu'il était usuel de loger dans le carter de la pompe entre le moteur agissant sur le piston et la chambre de travail, est situé pour la plus grande partie de son volume à l'extérieur du carter.One of the advantages of these achievements lies in the compactness of the assembly, the compensation chamber being distributed in different housings formed in the body of the pump and, mainly, in the insert body which contains the compensation valve and the valve of security. Congestion in the direction of the working piston is thus reduced because the compensation volume, which was usual to lodge in the pump casing between the engine acting on the piston and the working chamber, is located for the most part. much of its volume outside the housing.
Par ailleurs, l'élément de cloisonnement 23 cylindrique loge les deux clapets et est logé dans l'évidement 22 du corps de pompe qui s'étend perpendiculairement à l'axe du piston 10. Les fonctions, compensation, sécurité et dégazage, augmentées d'une fonction de visualisation, sont assurées par un ensemble qui se monte comme une cartouche dans l'évidement transversal 22 du corps 9 de la pompe, à savoir l'élément de élément de cloisonnement cylindrique 23, les deux clapets 40, 41, le ressort R et l'élément tubulaire 31 de fixation de cet élément de cloisonnement dans la cavité 22 du corps de la pompe qui referme le réservoir principal 34 du volume de compensation, qui porte les moyens de tarage de la soupape de sécurité ou du tiroir coulissant de la chambre d'expansion et qui permet par un capot transparent 36 la surveillance du fonctionnement du dispositif et notamment de faire un diagnostique visuel de la pression au refoulement de la pompe.Furthermore, the
Claims (10)
- A hydraulically-controlled diaphragm pump comprising a pump chamber (3) formed between a pump head (1) and a pump body (9) with a movable wall formed by a diaphragm (2) that is elastically deformable from its rest shape that corresponds to its state at the end of the suction stroke of the pump, a constant volume intermediate hydraulic chamber (8) formed in the pump body adjacent to the pump chamber (3) level with the diaphragm (2) and including a piston (10) driven with reciprocating motion inside said intermediate chamber (8), a leak compensation volume (11) for compensating leaks from the intermediate chamber (8) being connected thereto by a top-up channel (12a) via a free check valve (13) that is not rated and that passes fluid towards the intermediate chamber (8), the pump being characterized in that the check valve (13) and at least a portion (34) of the compensation volume are housed in a body (23, 31) fitted to the pump body (9) at the high point of the intermediate hydraulic chamber (8) in the working position of the pump.
- A pump according to claim 1, characterized in that the fitted body is in two portions, namely a lower partitioning element (23) carrying the seat of the free check valve (13), and a holder element (31) for holding the partitioning element and forming a tank (34) for the compensation volume and closure thereof.
- A pump according to claim 2, characterized in that the above-mentioned fitted body (23, 31) defines a discharge channel connecting the intermediate chamber to the compensation volume tank (34) in parallel with the free check valve (13) and through a rated safety valve (15) that it closes when the pressure is below the rating value.
- A pump according to any preceding claim, characterized in that a venting channel (14) is provided in parallel with the rated safety valve (15) between the intermediate hydraulic chamber (8) and the tank (34) for the compensation volume (11).
- A pump according to any preceding claim, characterized in that the seat of the free check valve (13) is carried by the body of the safety valve (15).
- A pump according to any preceding claim, characterized in that the valves (13, 15) lie on a common axis that is directed perpendicularly to the axis of the working piston (10).
- A pump according to claim 2, characterized in that the above-mentioned fitted body (23, 31) defines a discharge channel connecting the intermediate chamber (8) to an expansion chamber (29, 29b) in parallel with the free check valve (13) and defined by a slider (42) sliding in the element (31) and subjected to the effect of a spring (R) tending to minimize the volume of said expansion chamber.
- A pump according to any preceding claim, characterized in that the compensation volume tank (34) is closed by a transparent outside wall (36) enabling its content to be inspected visually.
- A pump according to any preceding claim, characterized in that a portion (19) of the compensation volume (11) is implemented between the piston (10) and its guide sleeve (17) so as to constitute a leak-collecting chamber (19) between the piston (10) and the sleeve (17).
- A pump according to any preceding claim, characterized in that the safety valve (42) advantageously includes a rod (44) having its free end (44a) constituting an indicator of the existence of excess pressure in the intermediate chamber (8).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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FR0900440A FR2941749A1 (en) | 2009-02-03 | 2009-02-03 | ELASTIC MEMBRANE PUMP WITH HYDRAULIC CONTROL |
PCT/FR2010/000081 WO2010089476A1 (en) | 2009-02-03 | 2010-02-03 | Pump with an elastic membrane and hydraulic control |
Publications (2)
Publication Number | Publication Date |
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EP2394056A1 EP2394056A1 (en) | 2011-12-14 |
EP2394056B1 true EP2394056B1 (en) | 2018-12-19 |
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Family Applications (1)
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EP10707069.0A Active EP2394056B1 (en) | 2009-02-03 | 2010-02-03 | Pump with an elastic membrane and hydraulic control |
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US (1) | US8888469B2 (en) |
EP (1) | EP2394056B1 (en) |
JP (1) | JP5416226B2 (en) |
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CA (1) | CA2750861C (en) |
FR (2) | FR2941749A1 (en) |
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WO (1) | WO2010089476A1 (en) |
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US20130287600A1 (en) * | 2012-04-27 | 2013-10-31 | Checkpoint Fluidic Systems International, Ltd. | Direct Volume-Controlling Device (DVCD) for Reciprocating Positive-Displacement Pumps |
FR3021713B1 (en) * | 2014-05-27 | 2019-04-05 | Milton Roy Europe | HYDRAULICALLY CONTROLLED MEMBRANE PUMP COMPRISING A DEDICATED DEGASSAGE PATH |
CN107806406A (en) * | 2017-10-20 | 2018-03-16 | 项达章 | A kind of Hydraulic Diaphragm Metering Pump for pressing spacing repairing |
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DE10143978B4 (en) * | 2001-09-07 | 2005-03-03 | Lewa Herbert Ott Gmbh + Co. | Hydraulically driven diaphragm pump with prestressed diaphragm |
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RU31153U1 (en) * | 2003-04-18 | 2003-07-20 | Подрезов Александр Владимирович | Diaphragm hydraulic metering pump |
RU38365U1 (en) * | 2004-01-30 | 2004-06-10 | Подрезов Александр Владимирович | MEMBRANE HYDRAULIC DRIVE DOSING PUMP |
US7425120B2 (en) * | 2005-04-26 | 2008-09-16 | Wanner Engineering, Inc. | Diaphragm position control for hydraulically driven pumps |
RU67195U1 (en) * | 2006-12-21 | 2007-10-10 | ЗАО "Талнах" | MEMBRANE HYDRAULIC DRIVE DOSING PUMP |
CN101245777B (en) * | 2007-02-13 | 2010-09-08 | 米尔顿罗伊欧洲公司 | Hydraulic pressure driven membrane pump with leakage compensation equipment |
-
2009
- 2009-02-03 FR FR0900440A patent/FR2941749A1/en active Pending
-
2010
- 2010-02-03 FR FR1000446A patent/FR2941748B1/en active Active
- 2010-02-03 CN CN201080006408.XA patent/CN102301139B/en not_active Expired - Fee Related
- 2010-02-03 US US13/145,254 patent/US8888469B2/en active Active
- 2010-02-03 EP EP10707069.0A patent/EP2394056B1/en active Active
- 2010-02-03 WO PCT/FR2010/000081 patent/WO2010089476A1/en active Application Filing
- 2010-02-03 JP JP2011546906A patent/JP5416226B2/en not_active Expired - Fee Related
- 2010-02-03 RU RU2011136676/06A patent/RU2505707C2/en active
- 2010-02-03 CA CA2750861A patent/CA2750861C/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
CN102301139B (en) | 2015-05-27 |
JP2012516962A (en) | 2012-07-26 |
EP2394056A1 (en) | 2011-12-14 |
RU2011136676A (en) | 2013-03-10 |
US8888469B2 (en) | 2014-11-18 |
US20110280747A1 (en) | 2011-11-17 |
FR2941749A1 (en) | 2010-08-06 |
CA2750861A1 (en) | 2010-08-12 |
RU2505707C2 (en) | 2014-01-27 |
JP5416226B2 (en) | 2014-02-12 |
CA2750861C (en) | 2013-08-06 |
FR2941748A1 (en) | 2010-08-06 |
CN102301139A (en) | 2011-12-28 |
FR2941748B1 (en) | 2011-08-19 |
WO2010089476A1 (en) | 2010-08-12 |
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