EP0148691A2 - Membrane pump with controlled rate of flow - Google Patents
Membrane pump with controlled rate of flow Download PDFInfo
- Publication number
- EP0148691A2 EP0148691A2 EP84402657A EP84402657A EP0148691A2 EP 0148691 A2 EP0148691 A2 EP 0148691A2 EP 84402657 A EP84402657 A EP 84402657A EP 84402657 A EP84402657 A EP 84402657A EP 0148691 A2 EP0148691 A2 EP 0148691A2
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- EP
- European Patent Office
- Prior art keywords
- piston
- axis
- eccentric
- stroke
- fixed shaft
- 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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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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
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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
Definitions
- the invention relates to an improvement to variable-flow diaphragm pumps, more particularly to means for driving and guiding the piston with a fixed stroke for hydraulic actuation of the diaphragm.
- various systems of diaphragm pumps with variable flow rate are known, in which the membrane limiting the pumping chamber is hydraulically actuated by a liquid contained in a second chamber called the displacement chamber in which a piston moving with movement moves. fixed stroke alternative.
- the variation in flow is then obtained by a device making it possible to discharge part of the liquid contained in the displacement chamber during a variable part of the stroke.
- this device can be constituted by a hollow piston provided in the vicinity of the rear bottom with radial orifices obscured by an outer ring during part of the stroke and opening into a reserve chamber at atmospheric pressure during another part of this stroke.
- An adjustment of the axial position of the outer ring makes it possible to vary the portion of the stroke called "active stroke" during which the orifices are concealed and thereby the flow rate of the pump.
- this pump system Compared to hydraulically operated diaphragm pumps with variable stroke or rate of the piston, this pump system has a notable simplification of construction and cost price. However, it has a main drawback.
- the invention relates to an improvement to diaphragm pumps with variable flow rate, the diaphragm limiting a pumping chamber being actuated hydraulically by a liquid contained in a displacement chamber in which a piston moving with a reciprocating movement moves. fixed, said piston being hollow and having, in the vicinity of the rear bottom, radial orifices obscured by an outer ring during part of the stroke and opening into a reserve chamber at atmospheric pressure during another part of the stroke, said piston being driven in an alternating movement by a circular eccentric cooperating with two opposite surfaces integral with the piston and perpendicular to its axis.
- said eccentric is integral with the wheel of a wheel and screw reducing couple, the eccentric wheel assembly being mounted so as to turn idly on a fixed shaft whose axis is perpendicular to the axis of the piston and passes through this axis, said piston ending in a U-shaped tail whose wings perpendicular to the axis of the piston and spaced a length slightly greater than the diameter of said eccentric carry said opposite surfaces, and the base of which is perpendicular to said fixed shaft and is provided with a longitudinal groove parallel to the axis of the piston which is crossed by said fixed shaft, the width of said groove being very slightly greater than the diameter of the fixed shaft.
- FIG. 1 From left to right from the front face, there are successively: The pumping chamber 1 provided with the suction valve 2 and the discharge valve 3, the membrane 4, the displacement chamber 5 housing the hollow piston 6, and the piston drive system 7.
- the membrane 4 shown is a composite membrane formed from a central core of flexible elastomer plated with two thin layers of teflon 4a and 4b. It is provided with a rupture detector not described in detail, indicated diagrammatically at 8.
- the membrane 4 is circular and it is held at its periphery by pinching between two rigid stops 9 and 10 disposed respectively in the chambers 1 and 5.
- Each stop 9,10 is in the form of a ring coaxial with the membrane 4, and whose face 11,12 facing the membrane 4 has a generally conical profile flaring towards the membrane 4.
- the face 11 of the stop 9 has a conical profile portion 13 extending radially inwards from the nip zone of the membrane 4, which continues with a bowl profile portion 14 up to the central orifice 15 of the stop 9 in the shape of a ring.
- the orifice 15 preferably has a diameter of between a third and a half of the outside diameter of the stop 9.
- the face 12 of the stop 10 only has a symmetrical profile of the profile of the aforementioned portion 13, with respect to the plane of pinching of the membrane.
- the face 12 extends radially as far as the central orifice 16 of the stop 10, this orifice therefore having a diameter greater than the orifice 15.
- the orifice 16 is crossed honrizontal by a beam 23 resting on the walls of the orifice and the face 24 of which faces the membrane 4 is slightly set back relative to the corresponding inlet of the orifice 16.
- the beam 23 is provided with an axial through hole 25.
- each deflector 17,18 has a flat face 19,20 in contact with the membrane 4.
- the deflector 17 of the pumping chamber 1 has a conical profile 21 complementary to the bowl profile 14 of the stop 9.
- the deflector 17 ends at center by a cylindrical nose 22 slightly engaging in the orifice 15.
- the deflector 18 of the displacement chamber consists of a simple flat washer of diameter slightly smaller than that of the orifice 16 of the stop 10 and equal to outer diameter of the deflector 17.
- the thickness of the deflector 18 corresponds to the axial offset between the face 24 of the beam 23 looking at the membrane 4 and the corresponding inlet of the orifice 16 of the stop 10.
- the deflectors 17 and 18 are assembled on the membrane 4 by means of a screw 26 which rests on the deflector 18, passes through the latter, the membrane 4 and is fixed in the deflector 17.
- the size of the hole 25 of the beam 23 is sufficient to accommodate the head of the screw 26.
- the displacement chamber 5 is provided as is conventional, with a safety valve 27 and its evacuation takes place through the passage 28 in the reserve chamber 29 which is in principle at atmospheric pressure.
- the hollow piston 6 is provided at its rear part with a plurality of holes 30 which can be closed or open out in the chamber 29 depending on the relative position of the piston and of the adjustment sleeve 31 mounted floating on the piston with very little play. longitudinal position of this sleeve 31 can be adjusted by means of a rack 32 driven by the pinion 33, itself controlled by the graduated adjustment button 34.
- the adjustment system is set so that in the extreme front position shown from the sleeve 31, the holes 30 are uncovered during the entire stroke of the piston shown here in the extreme forward position. This corresponds to the zero flow of the pump.
- a reducing gear wheel 35 and screw 36 is fixed in the casing 37 of the reserve chamber 29.
- the screw 36 has an axial recess opening 38 at its upper end intended to cooperate with the shaft of a drive motor fixed on the casing 37.
- the screw 36 rests at its lower end on a thrust bearing 39.
- the wheel 35 is in one piece with a circular eccentric 40. This assembly is mounted so as to turn idly on a fixed shaft 41 whose axis is perpendicular to the axis of the piston 6 and passes through this axis.
- the piston 6 has at its rear end a U-shaped tail 42 whose wings 43,44 are permendicular to the axis of the piston 6 and spaced a length very slightly greater than the diameter of the eccentric 40, that -ci being equipped with a rotating ring 45 mounted on its running surface.
- the base 46 of the U-shaped tail 42 is perpendicular to the fixed shaft 41 and it is provided with a longitudinal groove 47 parallel to the axis of the piston 6, which is crossed by the fixed shaft 41, the width of the groove 47 being very slightly greater than the diameter of the fixed shaft 41, and its length being sufficient not to hinder the movement of the piston.
- the operation of the pump as a whole is conventional.
- the movement of the piston results in a displacement of the membrane producing in the pumping chamber a sweep equivalent to the useful displacement, that is to say that swept by the piston during the part of the stroke where the holes 30 are closed.
- the displacement chamber 5 is in communication with the reserve chamber 29.
- the membrane 4 is at the end of the rear stroke and it is applied against the stop 10 and, by means of the deflector 18, against the beam 23.
- the face 12 of the stop 10 and the face 20 of the deflector 18 constitute a substantially continuous bearing surface for said membrane.
- the other stop 9 defines, in cooperation with the other deflector 17, a large annular passage promoting the flow of the fluid.
- the invention finds its application in the manufacture of diaphragm pumps with adjustable flow rate.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Separation Using Semi-Permeable Membranes (AREA)
Abstract
Description
L'invention est relative à un perfectionnement aux pompes à membrane à débit variable concernant plus particulièrement des moyens d'entraînement et de guidage du piston à course fixe d'actionnement hydraulique de la membrane. Il est connu dans leur principe divers systèmes de pompes à membrane à débit variable dans lesquelles la membrane limitant la chambre de pompage est actionnée hydrauliquement par un liquide contenu dans une deuxième chambre dite chambre de déplacement dans laquelle se déplace un piston animé d'un mouvement alternatif à course fixe. La variation de débit est alors obtenue par un dispositif permettant de décharger une partie du liquide contenu dans la chambre de déplacement pendant une partievariable de la course. Plus particulièrement ce dispositif peut être constitué par un piston creux muni au voisinage du fond arrière d'orifices radiaux occultés par une bague extérieure pendant une partie de la course et débouchant dans une chambre de réserve à pression atmosphérique pendant une autre partie de cette course. Un réglage de la position axiale de la bague extérieure permet de faire varier la portion de la course dite "course active" pendant laquelle les orifices sont occultés et par là, le débit de la pompe.The invention relates to an improvement to variable-flow diaphragm pumps, more particularly to means for driving and guiding the piston with a fixed stroke for hydraulic actuation of the diaphragm. In principle, various systems of diaphragm pumps with variable flow rate are known, in which the membrane limiting the pumping chamber is hydraulically actuated by a liquid contained in a second chamber called the displacement chamber in which a piston moving with movement moves. fixed stroke alternative. The variation in flow is then obtained by a device making it possible to discharge part of the liquid contained in the displacement chamber during a variable part of the stroke. More particularly, this device can be constituted by a hollow piston provided in the vicinity of the rear bottom with radial orifices obscured by an outer ring during part of the stroke and opening into a reserve chamber at atmospheric pressure during another part of this stroke. An adjustment of the axial position of the outer ring makes it possible to vary the portion of the stroke called "active stroke" during which the orifices are concealed and thereby the flow rate of the pump.
Par rapport aux pompes à membrane à commande hydraulique à course ou à cadence variables du piston, ce système de pompe comporte une notable simplification de construction et de prix de revient. Néanmoins il présente un inconvénient principal.Compared to hydraulically operated diaphragm pumps with variable stroke or rate of the piston, this pump system has a notable simplification of construction and cost price. However, it has a main drawback.
Du fait de la présence, à l'arrière du piston,du mécanisme réglable d'occultation des trous, l'encombrement longitudinal est augmenté, ainsi que le porte -à-faux dans le cas des systèmes d'entraînement classiques du type bielle- manivelle ou came et rappel par ressort, limité pour des raisons bien connues aux petites puissances. Cette augmentation du porte à faux entraîne soit un risque d'usure prématurée du piston, soit un allongement important du guidage avant du piston,qui entraîne une augmentation du prix, du poids et de l'encombrement de la pompe.Due to the presence, at the rear of the piston, of the adjustable hole concealment mechanism, the longitudinal dimensions are increased, as well as the overhang in the case of conventional drive systems of the connecting rod type. crank or cam and spring return, limited for reasons well known to small powers. This increase in the overhang causes either a risk of premature wear of the piston, or a significant elongation of the front guide of the piston, which leads to an increase in the price, the weight and the size of the pump.
Grâce à l'invention , cet inconvénient est évité par l'utilisation d'un système d'entraînement du piston qui assure un guidage longitudinal simple de celui-ci au niveau de sa partie arrière, contrairement au dispositif antérieur connu par le brevet AT 314 851 qui révèle un guidage par glissières extérieures très encombrant.Thanks to the invention, this drawback is avoided by the use of a piston drive system which ensures simple longitudinal guidance of the latter at its rear part, unlike the prior device known by the patent AT 314 851 which reveals guiding by very bulky external slides.
L'invention concerne à cet effet un perfectionnement aux pompes à membrane à débit variable dont la membrane limitant une chambre de pompage est actionnée hydrauliquement par un liquide contenu dans une chambre de déplacement dans laquelle se déplace un piston animé d'un mouvement alternatif à course fixe, ledit piston étant creux et présentant au voisinage du fond arrière des orifices radiaux occultés par une bague extérieure pendant une partie de la course et débouchant dans une chambre de réserve à pression atmosphérique pendant une autre partie de la course, ledit piston étant entraîné dans un mouvement alternatif par un excentrique circulaire coopérant avec deux surfaces opposées solidaires du piston et perpendiculaires à son axe.To this end, the invention relates to an improvement to diaphragm pumps with variable flow rate, the diaphragm limiting a pumping chamber being actuated hydraulically by a liquid contained in a displacement chamber in which a piston moving with a reciprocating movement moves. fixed, said piston being hollow and having, in the vicinity of the rear bottom, radial orifices obscured by an outer ring during part of the stroke and opening into a reserve chamber at atmospheric pressure during another part of the stroke, said piston being driven in an alternating movement by a circular eccentric cooperating with two opposite surfaces integral with the piston and perpendicular to its axis.
Selon l'une des caractéristiques principales de l'invention ledit excentrique est solidaire de la roue d'un couple réducteur roue et vis, l'ensemble excentrique roue étant monté de façon à tourner fou sur un arbre fixe dont l'axe est perpendiculaire à l'axe du piston et passe par cet axe, ledit piston se terminant par une queue en forme de U dont les ailes perpendiculaires à l'axe du piston et écartées d'une longueur légèrement supérieure au diamètre dudit excentrique portent lesdites surfaces opposées, et dont la base est perpendiculaire audit arbre fixe et est pourvue d'une rainure longitudinale parallèle à l'axe du piston qui est traversée par ledit arbre fixe, la largeur de ladite rainure étant très légèrement supérieure au diamètre de l'arbre fixe.According to one of the main characteristics of the invention, said eccentric is integral with the wheel of a wheel and screw reducing couple, the eccentric wheel assembly being mounted so as to turn idly on a fixed shaft whose axis is perpendicular to the axis of the piston and passes through this axis, said piston ending in a U-shaped tail whose wings perpendicular to the axis of the piston and spaced a length slightly greater than the diameter of said eccentric carry said opposite surfaces, and the base of which is perpendicular to said fixed shaft and is provided with a longitudinal groove parallel to the axis of the piston which is crossed by said fixed shaft, the width of said groove being very slightly greater than the diameter of the fixed shaft.
D'autres détails et avantages de l'invention apparaîtront au cours de la description qui suit d'un mode de réalisation donné à titre d'exemple non limitatif, en regard des figures annexées dans lesquelles :
- La figure 1 représente une pompe munie du perfectionnement selon l'invention, en coupe longitudinale.
- La figure 2 est une vue de dessus de la pompe, en coupe partielle suivant la ligne II-II de la figure 1.
- Figure 1 shows a pump provided with the improvement according to the invention, in longitudinal section.
- FIG. 2 is a top view of the pump, in partial section along the line II-II of FIG. 1.
Le principe, la construction et le fonctionnement d'une pompe à membrane à débit variable du type représenté sont connus. Les éléments classiques seront seulement décrits schématiquement, les éléments du perfectionnement selon l'invention étant seuls décrits en détail. Sur la figure 1, de gauche à droite à partir de la face avant, on trouve successivement : La chambre de pompage 1 munie du clapet d'aspiration 2 et du clapet de refoulement 3, la membrane 4, la chambre de déplacement 5 logeant le piston creux 6, et le système d'entraînement 7 du piston.The principle, construction and operation of a variable flow diaphragm pump of the type shown are known. The conventional elements will only be described schematically, the elements of the improvement according to the invention being alone described in detail. In FIG. 1, from left to right from the front face, there are successively: The pumping chamber 1 provided with the suction valve 2 and the discharge valve 3, the
La membrane 4 représentée est une membrane composite formée d'une âme centrale en élastomère souple plaquée de deux minces couches de téflon 4a et 4b. Elle est munie d'un détecteur de rupture non décrit en détail repéré schématiquement en 8. La membrane 4 est circulaire et elle est maintenue à sa périphérie par pincement entre deux butées rigides 9 et 10 disposées respectivement dans les chambres 1 et 5. Chaque butée 9,10 est en forme d'anneau coaxial à la membrane 4, et dont la face 11,12 tournée vers la membrane 4 présente un profil de forme générale conique s'évasant vers la membrane 4. La. face 11 de la butée 9 présente une portion de profil conique 13 s'étendant radialement vers l'intérieur à partir de la zone de pincement de la membrane 4, qui se poursuit par une portion de profil en cuvette 14 jusqu'à l'orifice central 15 de la butée 9 en forme d'anneau. L'orifice 15 a de préférence un diamètre compris entre le tiers et la moitié du diamètre extérieur de la butée 9 . La face 12 de la butée 10 présente uniquement un profil symétrique du profil de la portion 13 susdite, par rapport au plan de pincement de la membrane. La face 12 s'étend radialement jusqu'à l'orifice central 16 de la butée 10, cet orifice ayant donc un diamètre supérieur à l'orifice 15. L'orifice 16 est traversé honrizontalement par une poutre 23 s'appuyant sur les parois de l'orifice et dont la face 24 dirigée vers la membrane 4 est en léger retrait par rapport à l'entrée correspondante de l'orifice 16. La poutre 23 est pourvue d'un trou axial traversant 25.The
De part et d'autre de la membrane 4, et sur celle-ci sont fixés deux déflecteurs rigides circulaire 17,18 coaxiaux aux butées 9,10. Chaque déflecteur 17,18 présente une face plane 19,20 en contact avec la membrane 4. Le déflecteur 17 de la chambre de pompage 1 présente un profil conique 21 complémentaire du profil en cuvette 14 de la butée 9. Le déflecteur 17 se termine au centre par un nez cylindrique 22 s'engageant légèrement dans l'orifice 15. Le déflecteur 18 de la chambre de déplacement est constitué d'une simple rondelle plate de diamètre légèrement inférieur à celui de l'orifice 16 de la butée 10 et égal au diamètre extérieur du déflecteur 17. L'épaisseur du déflecteur 18 correspond au décalage axial entre la face 24 de la poutre 23 regardant la membrane 4 et l'entrée correspondante de l'orifice 16 de la butée 10.On either side of the
Les déflecteurs 17 et 18 sont assemblés sur la membrane 4 au moyen d'une vis 26 qui s'appuie sur le déflecteur 18, traverse ce dernier, la membrane 4 et se fixe dans le déflecteur 17. La taille du trou 25 de la poutre 23 est suffisante pour pouvoir y loger la tête de la vis 26.The
La chambre de déplacement 5 est munie comme il est classique, d'une soupape de sûreté 27 et son évacuation se fait à travers le passage 28 dans la chambre de réserve 29 laquelle se trouve en principe à la pression atmosphérique. Le piston creux 6 est muni à sa partie arrière d'une pluralité de trous 30 pouvant être obturés ou débouchant dans la chambre 29 suivant la position relative du piston et de la douille de réglage 31 montée flottante sur le piston avec très faible jeu. La position longitudinale de cette douille 31 peut être réglée au moyen d'une crémaillère 32 entraînée par le pignon 33 , lui même commandé par le bouton de réglage gradué 34. Le système de réglage est calé de manière qu'à la position extrême avant représentée de la douille 31, les trous 30 soient découverts pendant toute la course du piston représenté ici en position avant extrême. Ceci correspond au débit nul de la pompe. Lorsque la douille est déplacée vers la droite, les trous 30 sont recouverts pendant une partie de la course, ce qui permet de faire varier le débit proportionnellement au déplacement de la douille 31. La position extrême qui correspond à environ les 5/6 de la course du piston doit laisser les trous découverts pendant 1/6 de cette course pour permettre le remplissage de la chambre de déplacement.The
La commande du piston et son guidage sont maintenant décrits en regard des figures 1 et 2. Un couple réducteur roue 35 et vis 36 est fixé dans le carter 37 de la chambre de réserve 29. La vis 36 possède un évidement axial débouchant 38 à son extrémité supérieure destiné à coopérer avec l'arbre d'un moteur d'entraînement fixé sur le carter 37. La vis 36 repose par son extrémité inférieure sur un roulement de butée 39. La roue 35 est d'une seule pièce avec un excentique circulaire 40. Cet ensemble est monté de façon à tourner fou sur un arbre fixe 41 dont l'axe est perpendiculaire à l'axe du piston 6 et passe par cet axe.The piston control and its guidance are now described with reference to FIGS. 1 and 2. A reducing
Le piston 6 présente à son extrémité arrière une queue 42 en forme de U dont les ailes 43,44 sont permendicu- laires à l'axe du piston 6 et écartées d'une longueur très légèrement supérieure au diamètre de l'excentique 40, celui-ci étant équipé d'une bague tournante 45 montée sur sa surface de roulement. La base 46 de la queue 42 en forme de U est perpendiculaire à l'arbre fixe 41 et elle est pourvue d'une rainure longitudinale 47 parallèle à l'axe du piston 6, qui est traversée par l'arbre fixe 41, la largeur de la rainure 47 étant très légèrement supérieure au diamètre de l'arbre fixe 41, et sa longueur étant suffisante pour ne pas entraver le mouvement du piston.The
En fonctionnement, lorsqu'un moteur est engagé par son axe dans l'évidement 38 de la vis 36 du couple réducteur, la roue 35 et donc l'excentrique 40 tournent autour de l'arbre fixe 41. L'excentrique 40 effectue un mouvement à composantes verticale et horizontale mais, grâce à la queue 42 en forme de U, il n'entraîne le piston 6 que suivant la composante horizontale. Le piston 6 bénéficie constamment d'un guidage précis puisque sa rainure de queue 47 est maintenue horizontale par l'arbre fixe 41. La combinaison, dans une seule pièce solidaire du piston, de la rainure de guidage et de l'entraînement à excentrique à rappel positif permet, à rigidité égale, une réduction de longueur du guidage avant du piston, et par là du prix et du poids de la pompe par rapport aux systèmes connus.In operation, when a motor is engaged by its axis in the
Le fonctionnement de la pompe dans son ensemble est classique. Le mouvement du piston se traduit par un déplacement de la membrane produisant dans la chambre de pompage un balayage équivalent à la cylindrée utile, c'est à dire à celle balayée par le piston pendant la partie de la course où les trous 30 sont obturés. Pendant la période ou les trous 30 sont découverts, la chambre de déplacement 5 est en communication avec la chambre de réserve 29.The operation of the pump as a whole is conventional. The movement of the piston results in a displacement of the membrane producing in the pumping chamber a sweep equivalent to the useful displacement, that is to say that swept by the piston during the part of the stroke where the
Telle que représentée en figure 1, la membrane 4 est en fin de course arrière et elle vient s'appliquer contre la butée 10 et, par l'intermédiaire du déflecteur 18, contre la poutre 23. La face 12 de la butée 10 et la face 20 du déflecteur 18 constituent une surface d'appui sensiblement continue pour ladite membrane. Dans la position dessinée, l'autre butée 9 définit, en coopération avec l'autre déflecteur 17, un large passage annulaire favorisant l'écoulement du fluide.As shown in FIG. 1, the
Lorsque la membrane 4 est en fin de course avant, elle vient s'appliquer contre la butée 9 directement et par l'intermédiaire du déflecteur 17 qui vient se loger dans la cuvette 14. La face de butée 13 et la face de déflecteur 19 constituent une surface d'appui quasi-continue pour la membrane.When the
L'invention trouve son application dans la fabrication de pompes à membrane à débit réglable.The invention finds its application in the manufacture of diaphragm pumps with adjustable flow rate.
Claims (2)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT84402657T ATE27849T1 (en) | 1984-01-11 | 1984-12-19 | DIAPHRAGM PUMP WITH ADJUSTABLE FLOW. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR8400343A FR2557928B1 (en) | 1984-01-11 | 1984-01-11 | IMPROVEMENT ON VARIABLE FLOW MEMBRANE PUMPS. |
FR8400343 | 1984-01-11 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0148691A2 true EP0148691A2 (en) | 1985-07-17 |
EP0148691A3 EP0148691A3 (en) | 1985-09-11 |
EP0148691B1 EP0148691B1 (en) | 1987-06-16 |
Family
ID=9300002
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP84402657A Expired EP0148691B1 (en) | 1984-01-11 | 1984-12-19 | Membrane pump with controlled rate of flow |
Country Status (6)
Country | Link |
---|---|
US (1) | US4883412A (en) |
EP (1) | EP0148691B1 (en) |
AT (1) | ATE27849T1 (en) |
CA (1) | CA1248411A (en) |
DE (1) | DE3464276D1 (en) |
FR (1) | FR2557928B1 (en) |
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US5059099A (en) * | 1989-07-28 | 1991-10-22 | Wagner Spray Tech Corporation | Integral pump housing |
GB2282419A (en) * | 1993-10-02 | 1995-04-05 | Munster Simms Engineering Limi | Diaphragm pump |
WO1997013069A1 (en) * | 1995-10-04 | 1997-04-10 | Wanner Engineering, Inc. | Diaphragm pump |
FR2741945A1 (en) * | 1995-12-01 | 1997-06-06 | Pulsafeeder Inc | DIAPHRAGM MEASURING PUMP HAVING MODULAR CONSTRUCTION |
WO2017016635A1 (en) * | 2015-07-30 | 2017-02-02 | Linde Aktiengesellschaft | Device for increasing the pressure of a fluid, in particular in the form of a pressurized-gas bottle valve |
WO2017016642A1 (en) * | 2015-07-30 | 2017-02-02 | Linde Aktiengesellschaft | Device for increasing the pressure of a fluid, having a pressure-limiting valve |
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DE3829566A1 (en) * | 1988-08-31 | 1990-03-08 | Fritz Mueller | PISTON DRIVE |
US5106274A (en) * | 1990-07-23 | 1992-04-21 | Mark Holtzapple | Hermetic compressor |
FR2670537B1 (en) * | 1990-12-18 | 1994-10-28 | Milton Roy Dosapro | HYDRAULICALLY CONTROLLED MEMBRANE PUMP FOR HIGH PRESSURES. |
DE4141670C2 (en) * | 1991-12-17 | 1994-09-29 | Ott Kg Lewa | Hydraulically driven diaphragm pump with diaphragm stroke limitation |
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US2450912A (en) * | 1944-05-05 | 1948-10-12 | Putnam James Boyd | Internal-combustion motor with pistons symmetrically arranged about cams on the drive shaft |
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US3312171A (en) * | 1965-10-12 | 1967-04-04 | New York Air Brake Co | Pumps |
US3910727A (en) * | 1972-09-13 | 1975-10-07 | Valve Syst Int Inc | Metering pump |
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1984
- 1984-01-11 FR FR8400343A patent/FR2557928B1/en not_active Expired
- 1984-12-19 EP EP84402657A patent/EP0148691B1/en not_active Expired
- 1984-12-19 DE DE8484402657T patent/DE3464276D1/en not_active Expired
- 1984-12-19 AT AT84402657T patent/ATE27849T1/en not_active IP Right Cessation
-
1985
- 1985-01-10 CA CA000471858A patent/CA1248411A/en not_active Expired
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1987
- 1987-07-27 US US07/077,983 patent/US4883412A/en not_active Expired - Fee Related
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FR732745A (en) * | 1932-03-07 | 1932-09-24 | Improvements to thermal engines | |
AT314851B (en) * | 1969-10-06 | 1974-04-25 | Vni K I T I Gidromashinostroen | Device for setting the delivery rate of metering pumps |
US3612727A (en) * | 1969-10-17 | 1971-10-12 | Crane Co | Metering pump |
FR2161608A5 (en) * | 1971-11-16 | 1973-07-06 | Ransburg Corp |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0375848A1 (en) * | 1988-12-30 | 1990-07-04 | Alltech Dosieranlagen Gmbh | Dosing pump |
US5059099A (en) * | 1989-07-28 | 1991-10-22 | Wagner Spray Tech Corporation | Integral pump housing |
GB2282419A (en) * | 1993-10-02 | 1995-04-05 | Munster Simms Engineering Limi | Diaphragm pump |
GB2282419B (en) * | 1993-10-02 | 1997-07-09 | Munster Simms Engineering Limi | Diaphragm pump |
WO1997013069A1 (en) * | 1995-10-04 | 1997-04-10 | Wanner Engineering, Inc. | Diaphragm pump |
US5707219A (en) * | 1995-10-04 | 1998-01-13 | Wanner Engineering | Diaphragm pump |
FR2741945A1 (en) * | 1995-12-01 | 1997-06-06 | Pulsafeeder Inc | DIAPHRAGM MEASURING PUMP HAVING MODULAR CONSTRUCTION |
WO2017016635A1 (en) * | 2015-07-30 | 2017-02-02 | Linde Aktiengesellschaft | Device for increasing the pressure of a fluid, in particular in the form of a pressurized-gas bottle valve |
WO2017016642A1 (en) * | 2015-07-30 | 2017-02-02 | Linde Aktiengesellschaft | Device for increasing the pressure of a fluid, having a pressure-limiting valve |
WO2021029877A1 (en) * | 2019-08-13 | 2021-02-18 | Hewlett-Packard Development Company, L.P. | Fluid ejection apparatus for discreet packet transfer of fluid |
Also Published As
Publication number | Publication date |
---|---|
DE3464276D1 (en) | 1987-07-23 |
FR2557928B1 (en) | 1988-04-22 |
US4883412A (en) | 1989-11-28 |
FR2557928A1 (en) | 1985-07-12 |
ATE27849T1 (en) | 1987-07-15 |
CA1248411A (en) | 1989-01-10 |
EP0148691A3 (en) | 1985-09-11 |
EP0148691B1 (en) | 1987-06-16 |
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