EP0547404B1 - Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane - Google Patents
Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane Download PDFInfo
- Publication number
- EP0547404B1 EP0547404B1 EP92119928A EP92119928A EP0547404B1 EP 0547404 B1 EP0547404 B1 EP 0547404B1 EP 92119928 A EP92119928 A EP 92119928A EP 92119928 A EP92119928 A EP 92119928A EP 0547404 B1 EP0547404 B1 EP 0547404B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- diaphragm
- valve
- membrane
- control slide
- stroke
- 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.)
- Expired - Lifetime
Links
- 239000012528 membrane Substances 0.000 title description 73
- 239000012530 fluid Substances 0.000 claims description 23
- 238000006073 displacement reaction Methods 0.000 claims description 11
- 210000004379 membrane Anatomy 0.000 description 79
- 239000013589 supplement Substances 0.000 description 12
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 230000009471 action Effects 0.000 description 5
- 230000008901 benefit Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000009469 supplementation Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 230000007257 malfunction Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000004033 plastic Substances 0.000 description 2
- 230000009172 bursting Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007667 floating Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000004810 polytetrafluoroethylene Substances 0.000 description 1
- 229920001343 polytetrafluoroethylene Polymers 0.000 description 1
- 239000000047 product Substances 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Images
Classifications
-
- 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 a hydraulically driven diaphragm pump according to the preamble of claim 1.
- a diaphragm system-controlled leakage supplement device is provided.
- the leakage supplement device provided in the known diaphragm pump, that of the diaphragm system-controlled type has prevailed.
- the diaphragm itself takes over the actuation of a control valve, a control slide controlled by the diaphragm, which is displaceably guided in the area of the connecting channel between diaphragm working space and piston working space, in the suction stroke end position of the diaphragm opening a connection from the storage space to the piston working space.
- the leak can only be supplemented when the membrane has reached a predetermined limit position at the end of the suction stroke.
- leakage supplement devices of diaphragm pumps are described in DE-PS 28 43 054 and in FR-PS 24 92 473.
- the control of the leakage supplementation by the membrane system offers a number of other advantages compared to the pressure-controlled leakage addition with a snifting valve.
- large suction heights can be overcome, the suction height being limited solely by the vapor pressure of the delivery fluid and hydraulic fluid.
- overloading of the hydraulic space is excluded. Such pronounced vacuum peaks preferably occur in the case of large high-pressure diaphragm pumps at the beginning of the suction phase when the liquid column in the suction line is accelerated suddenly when the suction valve is opened.
- the membrane system-controlled leak supplement enables sniffing of hydraulic fluid at a low differential pressure of, for example less than 0.3 bar, ie the absolute pressure remains at around 0.7 bar.
- the pressure-controlled leakage supplement requires a relatively high setting of the differential pressure at the snifting valve of, for example, 0.6 bar in order to ensure safe operation.
- the resulting pressure drop in the hydraulic chamber during the sniffing process to, for example, 0.4 bar absolute pressure leads to increased gas formation. This results in a reduced delivery rate and delivery accuracy.
- the manual positioning of the membrane before starting the pump is relatively complex. It is usually carried out in such a way that a connection between the hydraulic space and the storage space is created, which is done, for example, by removing the pressure relief valve.
- the diaphragm is then pressed in the direction of its drive by applying overpressure on the suction side of the pump, which accordingly also acts on the diaphragm surface on the delivery chamber side. Then when the membrane is in the direction of its drive moved, hydraulic fluid is simultaneously displaced from the hydraulic space into the storage space.
- the described complex yet necessary start-up of the diaphragm pump has a particularly disadvantageous effect in modern triple diaphragm pumps, in which the initial diaphragm positioning has to be carried out on three pump heads.
- This membrane positioning can be simplified with solenoid valves that are installed between the hydraulic space and the storage space.
- the design and control engineering effort remains considerable in any case. It is also not always easy to provide the necessary overpressure on the suction side of the pump to push the membrane in the direction of its drive.
- the invention has for its object to design the diaphragm pump of the generic type in such a way that the diaphragm stroke is functionally limited in both directions with simple means and that the pump is started up without manual preparatory work to influence the diaphragm system can be.
- the invention is based on the idea of providing the devices for limiting the diaphragm stroke in both directions on the control slide of the leak-supplementing device which is already present. This results in an incredibly simple, yet functionally reliable design. At the same time, it is ensured that the pump can be put into operation without manual preparatory work having to be carried out to influence the membrane system.
- the diaphragm pump designed according to the invention uses a double or combined principle with regard to the limitation of the diaphragm travel provided in both stroke directions.
- This consists in that on the one hand the diaphragm stroke limitation in the suction stroke end position takes place in a purely mechanical way, namely by means of the almost gap-free support surface formed by the support plate and assigned pump body surface and adapted to the natural diaphragm geometry, while on the other hand the diaphragm stroke limitation in the pressure stroke limit position is effected purely hydraulically by the valve member provided on the piston-side end of the control slide interrupts the hydraulic connection from the piston working chamber to the membrane working chamber. In the latter case, excess hydraulic oil is then displaced into the hydraulic reservoir via the pressure relief valve provided.
- the invention thus realizes the principle that on the basis of the membrane system-controlled leak supplementation which takes place by means of the control slide valve, a membrane system-controlled leak Path or stroke limitation of the membrane is effected both in the direction of the pressure stroke and in the direction of the suction stroke.
- a membrane system-controlled leak Path or stroke limitation of the membrane is effected both in the direction of the pressure stroke and in the direction of the suction stroke.
- the mechanical support surface is designed without holes, which has proven to be particularly advantageous when the invention is used for high-pressure diaphragm pumps.
- the second control valve by means of which the hydraulic limitation of the diaphragm stroke takes place in the pressure stroke end or limit position, is expediently designed as a plate valve, the valve plate of which, be it in the form of a plate washer, a plate shell or the like, in the pressure stroke end position, the connection channel or channels closes.
- control slide of the leakage supplement device which has the support plate fixedly connected to it at its membrane-side end, can be designed such that the valve member of the second control valve provided on the piston-side end is also firmly connected to it.
- valve member of the second control valve is fastened to one end of a valve tappet, which in turn is slidably guided in the control slide of the first control valve, coaxially to the latter and rests with the other end under spring force of the diaphragm, so that it scans the membrane over the entire membrane stroke.
- control slide of the first control valve is biased in the direction of the diaphragm by a spring which is stronger than the spring which prestresses the valve tappet of the second control valve. It is within the scope of the invention that the spring biasing the valve tappet of the second control valve is supported on the control slide itself.
- the control slide has a stop at its piston-side end, which limits the displacement of the control slide in the direction of the diaphragm pressure stroke .
- the control slide follows the diaphragm only in a certain range, which is preferably 30-40% of the total diaphragm stroke, when the diaphragm moves from its suction stroke end position in the direction of the pressure stroke. This means that the control slide, when the diaphragm returns from its pressure stroke end position to the suction stroke end position, is only actuated by the diaphragm to the last 30 - 40% of the suction stroke or pushed back against spring force.
- the valve tappet of the valve plate scans the membrane over the entire membrane stroke.
- the second control valve works completely independently of the first control valve, ie it still scans the membrane when the function of the first control valve is disturbed, for example by the effect of dirt.
- the valve tappet runs along with it as it were.
- the valve disk closes the connection channel or channels between the piston working room and the membrane working room. The hydraulic connection is thus interrupted so that the membrane cannot be deformed any further in the direction of the delivery chamber. Accordingly, the membrane is secured against overstretching. The excess hydraulic fluid in the piston working chamber is pushed back into the hydraulic reservoir via the pressure relief valve.
- the invention thus not only results in a desirable protection of the diaphragm when the pump is started up, but also an additional improvement in the operational reliability of the pump is achieved due to the completely independent functioning of the two control valves. This is essential if the function of the first control valve is disturbed, for example by the action of dirt, and remains in an open position continuously, so that an uncontrolled sniffing of hydraulic fluid would be possible. In this case, however, the second control valve reliably prevents membrane damage by preventing a pressure stroke of the membrane beyond the normal end position in the manner described. The excess hydraulic fluid is then discharged back into the storage space. The pump only works with reduced power and the pressure relief valve responds.
- Another advantage according to the invention results from the design of the control slide and the valve tappet which is displaceably guided therein.
- the end faces of these two control elements together with the associated pump body surface form an almost gap-free mechanical support surface which is adapted to the natural membrane shape.
- the diaphragm In its suction stroke end position, the diaphragm is mechanically supported by this contact surface and can be pressed on with the full delivery pressure without suffering any damage.
- the invention therefore provides significant advantages, inter alia, achieved in that the commissioning of the pump can be carried out without manual preparatory work and that the diaphragm deflection is automatically limited by simple means both in the pressure stroke and in the suction stroke. This reliably prevents the membrane from overstretching or even bursting. For this reason, the diaphragm pump is also much easier to integrate into automated process sequences, which among other things. is based on the fact that there is no need for time-consuming manual preparatory work to influence the membrane system. Furthermore, the risk of membrane damage due to incorrect operation is eliminated. Costly downtimes can be avoided.
- the diaphragm pump has a conventional diaphragm 1, in particular made of plastic. This is at its edge between a pump body 2 and a pump cover that is detachably attached to the end thereof 3 clamped and separates a delivery chamber 4 from a pressure chamber 5 filled with hydraulic fluid, which represents the piston working chamber.
- the diaphragm pump has a hydraulic diaphragm drive in the form of an oscillating displacement piston 6, which, sealed in the pump body 2, can be displaced between the piston working space 5 and a storage space 7 for the hydraulic fluid.
- the piston working chamber 5 is connected via at least one axial bore 8 arranged in the pump body 2 to a diaphragm-side pressure chamber 9, which represents the diaphragm working chamber and together with the piston working chamber 5 forms the hydraulic chamber as a whole.
- the diaphragm working space 9 is delimited on the one hand by the diaphragm 1 and on the other hand by a rear (piston-side) calotte 10.
- This rear limitation cap 10 is formed by the appropriately designed end face of the pump body 2 and represents part of that - still to be described - mechanical support surface on which the membrane 1 bears at the end of the suction stroke (see FIG. 5).
- a front limitation cap 11 formed by the end face of the pump cover 3 is formed in the delivery chamber 4.
- the pump cover 3 is provided in the usual way with a spring-loaded inlet valve 12 (suction valve) and a spring-loaded outlet valve 13 (pressure valve). These two valves 12, 13 are connected via an inlet duct 14 and an outlet duct 15 to the delivery chamber 4 in such a way that the delivery medium during the suction stroke of the displacer 6 and thus the diaphragm 1 to the right according to FIG. 1 and thus the diaphragm 1 in the direction of the arrow via the suction valve 12 and the inlet channel 14 is sucked into the delivery chamber 4.
- the conveyed medium is then metered in via the outlet channel 15 and the pressure valve 13 in the direction of the arrow discharged from the funding room 4.
- a leakage supplementation device In order to prevent the occurrence of cavitation at the end of the membrane suction stroke and to ensure the leakage supplementation required due to the leakage losses, a leakage supplementation device is provided.
- This has a conventional spring-loaded sniffer valve 16, which is connected via a channel 17 to the storage space 7 and via a channel 18 and the connecting channel 8 on the one hand to the piston working space 5 and on the other hand to the diaphragm working space 9.
- the leakage supplement is controlled by a first control valve which has a control slide 19.
- This is axially displaceable with the displacement piston 6 in the area of the connecting channel 8 between the diaphragm working space 9 and the piston working space 5 in a corresponding bore of the pump body 2 and is under the action of a compression spring 23 (see FIG. 2).
- the compression spring 23 is supported on the one hand in the pump body 2 and on the other hand on the diaphragm-side end of the control slide 19, so that the control slide 19 is biased in the direction of the diaphragm 1 and follows the movement of the diaphragm 1 from the suction stroke end position in the pressure stroke direction.
- control slide 19 has a stop 28 at its piston-side end, for example in the form of a circlip, which has a corresponding one in the piston working chamber 5 provided collar 29 cooperates and limits the displacement of the spool 19 in the direction of the membrane pressure stroke.
- a circumferential groove 30 is provided which, in the suction stroke end position of the membrane 1 (FIG. 5), the connection between the snifting valve 16 of the leakage supplement device and the hydraulic chamber 5, 9 - via the channels 18, 8 - produces.
- a second control valve 20 is provided at the piston-side end of the control slide 19.
- this is designed as a poppet valve and has a shell-like valve disk 21, a valve tappet 22 connected to it, and a compression spring 24, which is supported in the manner shown on the control slide 19 and the second control valve 20 in Biased towards membrane 1.
- the valve tappet 22 is displaceable in the control slide 19, coaxially with the latter, and its membrane-side end is always in contact with the membrane 1 due to the action of its compression spring 24, so that it scans the membrane 1 over the entire membrane stroke.
- the valve plate 21 is designed such that it closes the connection channel (s) 8 in the limit position of the membrane pressure stroke end position (see FIG. 4).
- the diaphragm-side end of the control slide 19 is designed as a support plate 31. This is shaped so that its end face 10 'together with the associated end face 10 of the pump body 2 and the end face 10' 'of the diaphragm-side end of the valve lifter 22 forms an almost gap-free mechanical support surface for the diaphragm 1 in its suction stroke end position.
- This support surface 10, 10 ', 10' ' is adapted to the natural membrane geometry, it being particularly important that it is designed to be completely bore-free.
- the support plate 31 In the compressed position of the control slide 19, the support plate 31 is received in a corresponding bore 32 of the pump housing 2, but it is not necessary that the support plate 31 lies tightly against the seat formed by the bore 32. It is only necessary to ensure that the mechanical support surface described is provided by all of the end faces 10, 10 ′, 10 ′′ mentioned is formed for the membrane 1 in the suction stroke end position.
- a pressure limiting valve 27 is finally provided in the pump body 2, which is connected on the one hand via a channel 33 to the piston working chamber 5 and on the other hand via a channel 34 to the hydraulic reservoir 7.
- the displacement piston 6 is moved to the right in order to carry out the suction stroke.
- the mechanical support surface 10, 10 ′, 10 ′′ which is formed by the end faces of the pump body 2, the support plate 31 and the membrane-side end of the valve lifter 22, lies in the suction stroke end position, as can be seen from FIG. 5 .
- the control slide 19 with its diaphragm-side support plate 31 and the valve tappet 22 are in the compressed position, in which the abovementioned end faces 10, 10 ', 10''are the described support surface adapted to the diaphragm shape form.
- the membrane 1 is thus fully mechanically supported in its suction stroke end position and can be pressed on at the full delivery pressure without suffering any damage.
- the circumferential groove 30 of the control slide 19 also establishes the connection, which serves to supplement the leak, between the hydraulic reservoir 7 and the hydraulic chamber 5, 9, specifically via the channel 17, the snifting valve 16, the channel 18 and the connection channel or channels 8.
- the diaphragm 1 also carries out the pressure stroke due to the hydraulic medium acting on it in the hydraulic chamber 5, 9, namely up to the pressure stroke end position according to FIG. 3 corresponding to the normal position
- the control slide 19 of the diaphragm 1 which is under the action of the compression spring 23, follows only over a distance which corresponds to approximately 30-40% of the total diaphragm pressure stroke, since the stop 28 of the control slide 19 strikes the collar 29 on the housing side and thus the displacement path of the Control spool 19 limited.
- valve tappet 22 which is under the pretension of the compression spring 24, scans the membrane 1 over its entire pressure stroke.
- the valve lifter 22 runs as it were, as long as the diaphragm 1 operates in its predetermined stroke range. This means that in the normal pressure stroke end position of the diaphragm 1, the valve tappet 22 has such a position that the valve disk 21 does not close the connecting channels 8 between the piston working space 5 and the diaphragm working space 9.
- the process described in the introduction is then repeated by means of the displacement movement of the displacer 6 to the right until the membrane 1 abuts the support surface 10, 10 ′, 10 ′′ in the end of the suction stroke position and is supported there mechanically.
- control slide 19 has become stuck in its guide bore, for example due to the effect of dirt, in such a way that it remains permanently in an open position.
- an uncontrolled sniffing of hydraulic fluid into the hydraulic chamber 5, 9 is possible, membrane damage is reliably prevented due to the described configuration.
- the valve plate 21 closes the connecting channels 8 during the next pressure stroke of the diaphragm 1 in its pressure stroke limit position, so that it is thereby the hydraulic diaphragm travel limitation in the pressure stroke limit position results.
- the excess hydraulic fluid is then discharged from the piston working chamber 5 into the storage chamber 7 via the pressure limiting valve 27.
- the malfunction described can be recognized easily and in good time due to the increased response of the pressure limiting valve 27 and due to the reduced pump output, so that the malfunction can be remedied immediately.
- a vent hole 25 is provided in the pump housing 2, which runs from the geodetically highest point of the diaphragm working space 9 to the combined pressure limiting and gas discharge valve 27.
- the vent hole 25 has a check valve 26. This is prestressed or arranged in such a way that it enables the desired ventilation of the membrane working space 9, i.e. a control from the membrane work space 9 to the gas discharge valve 27 permits.
- the check valve 26 prevents a bypass flow from the piston working space 5 to the diaphragm working space 9 when the second control valve 20 is closed.
- the further modified embodiment according to FIG. 8 represents a simplified design compared to the previously described construction, to the extent that the second control valve 20 consists only of the disk-shaped valve plate 21, that is to say, no separately guided in the control slide 19 under the action of a compression spring has standing valve lifter.
- the valve disk 21 is fixedly connected to the piston-side end of the control slide 19 and is arranged or dimensioned such that it also closes the connecting channels 8 between the piston working chamber 5 and the membrane working chamber 9 in the end position of the diaphragm 1 corresponding to a limit stroke.
- the respective membrane system is only affected by the pressure spring 23 Control slide 19 or scanned by its support plate 31, otherwise the same advantageous effects result as in the previously described embodiments.
- the leakage in the hydraulic chamber 5, 9 is effected via an axial bore 35 provided in the control slide 19, which on the one hand opens out into the piston working chamber 5 through the valve plate 21 and on the other hand via a radially extending bore section 36 with the channel 18 or the sniffer valve 16 is connected.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Claims (7)
- Pompe à membrane entraînée par voie hydraulique, comportant une membrane serrée du côté bordure entre un corps de pompe et un couvercle de pompe, laquelle sépare une chambre de refoulement d'une chambre hydraulique, la chambre hydraulique étant subdivisée en une chambre de travail de membrane et en une chambre de travail de piston reliée à celle-ci via au moins un canal de liaison, et comportant un entraînement de membrane hydraulique sous forme d'un piston de refoulement oscillant qui est mobile dans le corps de pompe entre un réservoir pour le liquide hydraulique et la chambre de travail de piston, et comportant un dispositif de compensation de fuites commandé par la position de la membrane, qui présente une soupape de commande avec un poussoir de commande guidé en déplacement dans la région du canal de liaison entre la chambre de travail de membrane et la chambre de travail de piston, ledit poussoir de commande ouvrant une liaison depuis le réservoir jusqu'à la chambre de travail de piston dans ou au-delà de la position de fin de course d'aspiration de la membrane, caractérisée en ce que le poussoir de commande (19) du dispositif de compensation de fuites est pourvue à ses deux extrémités de dispositifs (31 ; 20) pour limiter la course de la membrane serrée et en oscillation libre (1), de telle sorte que le poussoir de commande (19) présente à son extrémité côté membrane une rondelle d'appui (31) qui est réalisée de telle sorte qu'elle forme pour la membrane, conjointement avec la surface de corps de pompe (10) de la chambre de travail de membrane (9), une surface d'appui mécanique (10, 10', 10") pratiquement exempte de fente et adaptée à la forme géométrique naturelle de la membrane dans sa position de fin de course d'aspiration, et en ce que le poussoir de commande (19) présente à son extrémité côté piston une seconde soupape de commande (20) avec un organe de soupape (21) qui interrompt la liaison hydraulique depuis la chambre de travail de piston (5) jusqu'à la chambre de travail de membrane (9) dans ou au-delà de la position de fin de course de compression de la membrane (1).
- Pompe à membrane selon la revendication 1, caractérisée en ce que la surface d'appui mécanique (10, 10', 10") pour la membrane (1) est réalisée sans perçage dans sa position de fin de course d'aspiration.
- Pompe à membrane selon la revendication 1, caractérisée en ce que la seconde soupape de commande (20) est une soupape à rondelle dont l'organe de soupape réalisé sous forme de rondelle de soupape (21) referme le ou les canaux de liaison (8) dans la position limite de course de compression de la membrane (1).
- Pompe à membrane selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'organe de soupape (21) de la seconde soupape de commande (20) est fixé à une extrémité d'un poinçon de soupape (22) qui est guidé en déplacement dans le poussoir de commande (19) de la première soupape de commande coaxialement à celui-ci et qui s'appuie par son autre extrémité sous la force de ressort de la membrane (1) de telle sorte qu'il palpe la membrane (1) sur toute sa course.
- Pompe à membrane selon la revendication 4, caractérisée en ce que le poussoir de commande (19) de la première soupape de commande est mis sous précontrainte en direction de la membrane (1) par un ressort (23) qui est plus fort que le ressort (24) mettant sous précontrainte le poinçon de soupape (22) de la seconde soupape de commande (20).
- Pompe à membrane selon la revendication 5, caractérisée en ce que le ressort (24) mettant sous précontrainte le poinçon de soupape (22) de la seconde soupape de commande (20) est appuyé contre le poussoir de commande (19).
- Pompe à membrane selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le poussoir de commande (19) présente à son extrémité côté piston une butée (29) qui limite la course de déplacement du poussoir de commande (19) en direction de la course de compression de la membrane.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4141670A DE4141670C2 (de) | 1991-12-17 | 1991-12-17 | Hydraulisch angetriebene Membranpumpe mit Membranhubbegrenzung |
DE4141670 | 1991-12-17 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0547404A1 EP0547404A1 (fr) | 1993-06-23 |
EP0547404B1 true EP0547404B1 (fr) | 1997-02-05 |
Family
ID=6447287
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92119928A Expired - Lifetime EP0547404B1 (fr) | 1991-12-17 | 1992-11-23 | Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane |
Country Status (4)
Country | Link |
---|---|
US (1) | US5246351A (fr) |
EP (1) | EP0547404B1 (fr) |
JP (1) | JPH05240162A (fr) |
DE (2) | DE4141670C2 (fr) |
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DE4327970C2 (de) * | 1993-08-19 | 1997-07-03 | Ott Kg Lewa | Hydraulisch angetriebene Membranpumpe mit mechanischer Membranhubbegrenzung |
DE4327969C2 (de) * | 1993-08-19 | 1997-07-03 | Ott Kg Lewa | Hydraulisch angetriebene Membranpumpe |
US5547351A (en) * | 1994-03-01 | 1996-08-20 | The United States Of America As Represented By The Secretary Of The Department Of Health And Human Services | Low pressure low volume liquid pump |
DE4420863C2 (de) * | 1994-06-15 | 1998-05-14 | Ott Kg Lewa | Gesteuerte Schnüffelbehinderung für Hochdruck-Membranpumpen |
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CN1407644A (zh) * | 2001-08-23 | 2003-04-02 | 亚太燃料电池科技股份有限公司 | 燃料电池的膜片泵及使用此膜片泵的阳极气体循环系统 |
US6582204B2 (en) * | 2001-09-06 | 2003-06-24 | The United States Of America As Represented By The Administrator Of The U.S. Enviromental Protection Agency | Fully-controlled, free-piston engine |
JP4330323B2 (ja) * | 2001-10-24 | 2009-09-16 | 株式会社タクミナ | 往復動ポンプ |
KR100743691B1 (ko) * | 2002-10-09 | 2007-07-30 | 가부시끼가이샤 타쿠미나 | 왕복 운동 펌프 및 역류 방지판 |
BRPI0318302B1 (pt) * | 2003-05-16 | 2017-03-28 | Wanner Eng Incorporated | bomba de diafragma |
US7425120B2 (en) * | 2005-04-26 | 2008-09-16 | Wanner Engineering, Inc. | Diaphragm position control for hydraulically driven pumps |
US7686595B1 (en) * | 2005-12-12 | 2010-03-30 | Stephen Graham | Diaphragm pump |
FR2895036B1 (fr) * | 2005-12-20 | 2008-02-22 | Milton Roy Europ Sa | Pompe a membrane a actionnement hydraulique avec dispositif de compensation des fuites |
CN101245777B (zh) * | 2007-02-13 | 2010-09-08 | 米尔顿罗伊欧洲公司 | 具有泄漏补偿设备的液压致动隔膜泵 |
CN101037992B (zh) * | 2007-03-29 | 2010-10-06 | 合肥华升泵阀有限责任公司 | 高真空隔膜泵 |
US7665974B2 (en) * | 2007-05-02 | 2010-02-23 | Wanner Engineering, Inc. | Diaphragm pump position control with offset valve axis |
WO2012015929A1 (fr) * | 2010-07-27 | 2012-02-02 | Delaware Capital Formation, Inc. | Pompe doseuse à cylindrée variable à grand rendement énergétique |
DE102010039829A1 (de) * | 2010-08-26 | 2012-03-01 | Prominent Dosiertechnik Gmbh | Membranpumpe mit trägheitsgesteuertem Leckergänzungsventil |
CN102352831B (zh) * | 2011-10-24 | 2014-11-05 | 重庆水泵厂有限责任公司 | 隔膜泵自动补排油装置 |
DE102013105072A1 (de) | 2013-05-16 | 2014-11-20 | Prominent Gmbh | Membranpumpe mit Lagensteuerung |
CN103629088A (zh) * | 2013-11-22 | 2014-03-12 | 德帕姆(杭州)泵业科技有限公司 | 一种新型均压限位补油的液压隔膜计量泵 |
CN104088777B (zh) * | 2014-05-27 | 2016-09-28 | 德帕姆(杭州)泵业科技有限公司 | 一种隔膜定量压缩的计量泵 |
DE102014109801A1 (de) * | 2014-07-11 | 2016-01-14 | Prominent Gmbh | Membranpumpe mit reduzierter Leckageergänzung im Überlastfall |
WO2016077751A1 (fr) * | 2014-11-14 | 2016-05-19 | Checkpoint Fluidic Systems International, Ltd. | Mécanisme de pompe à diaphragme sandwich métallique |
CN105003424B (zh) * | 2015-07-27 | 2017-03-01 | 杭州大泉泵业科技有限公司 | 一种高温液压式隔膜计量泵 |
GB201601194D0 (en) * | 2016-01-22 | 2016-03-09 | Carlisle Fluid Tech Inc | Active surge chamber |
DE102017122270B4 (de) * | 2017-09-26 | 2020-09-10 | Prominent Gmbh | Membranpumpe mit einer funktionssicheren Membranlagensteuerung |
JP7346445B2 (ja) * | 2018-04-18 | 2023-09-19 | ワナー・エンジニアリング・インコーポレーテッド | ダイヤフラムポンプを圧力差から保護するためのデバイス |
IT201800004722A1 (it) * | 2018-04-19 | 2019-10-19 | Pompa volumetrica a membrana | |
CN110425120A (zh) * | 2019-08-13 | 2019-11-08 | 王建设 | 一种自动调压隔膜泵 |
DE102019125998B4 (de) | 2019-09-26 | 2022-01-05 | Audi Ag | Membrandosierer |
CN112049772B (zh) * | 2020-09-10 | 2024-04-26 | 北京通嘉宏瑞科技有限公司 | 一种集成管路以及减震效果好的真空泵 |
FI4124755T3 (fi) * | 2021-07-26 | 2023-06-13 | Gea Mech Equipment Italia S P A | Kalvopohjainen mäntäpumppu ja homogenointilaite käsittäen kalvopohjaisen mäntäpumpun |
DE202021106223U1 (de) * | 2021-11-15 | 2021-11-19 | Feluwa Pumpen Gmbh | Membrankolbenpumpe |
CN114320847B (zh) * | 2021-11-26 | 2023-11-14 | 嘉善边锋机械股份有限公司 | 一种实现自动憋压的气动计量泵 |
CN115263708A (zh) * | 2022-07-13 | 2022-11-01 | 德帕姆(杭州)泵业科技有限公司 | 一种高性能微量输送的计量泵 |
CN115182872B (zh) * | 2022-08-05 | 2024-01-26 | 德帕姆(杭州)泵业科技有限公司 | 一种容积式活塞泵 |
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Publication number | Priority date | Publication date | Assignee | Title |
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US4068982A (en) * | 1976-12-20 | 1978-01-17 | Graco Inc. | Charge control valve and piston assembly for diaphragm pump |
AU515126B2 (en) * | 1977-05-02 | 1981-03-19 | Yamada Yuki Seizo Co. Ltd. | Diaphragm pump |
US4184809A (en) * | 1977-05-11 | 1980-01-22 | Louis Beck | Diaphragm pump construction having pulsator piston and mechanically actuated means to supply pulsator fluid |
FR2492473B1 (fr) * | 1980-10-17 | 1985-06-28 | Milton Roy Dosapro | Pompe a membrane a compensation dans la chambre hydraulique de commande |
US4365745A (en) * | 1981-02-05 | 1982-12-28 | Louis Beck | Diaphragm pump |
US4467605A (en) * | 1982-09-27 | 1984-08-28 | Wabco Ltd. | Hydro-pneumatic actuator with automatic slack adjuster |
FR2557928B1 (fr) * | 1984-01-11 | 1988-04-22 | Milton Roy Dosapro | Perfectionnement aux pompes a membrane a debit variable. |
DE3430721A1 (de) * | 1984-08-21 | 1986-03-06 | Alldos Eichler Kg, 7507 Pfinztal | Membranpumpe, insbesondere zum dosieren von fluessigkeiten |
DE3446914A1 (de) * | 1984-12-21 | 1986-07-03 | Ott Kg Lewa | Membranpumpe mit hydaulisch angetriebener rollmembran |
US5163820A (en) * | 1987-11-16 | 1992-11-17 | Karldom Corporation | Airless sprayer with adjustable pressure unloading valve |
-
1991
- 1991-12-17 DE DE4141670A patent/DE4141670C2/de not_active Expired - Fee Related
-
1992
- 1992-11-23 EP EP92119928A patent/EP0547404B1/fr not_active Expired - Lifetime
- 1992-11-23 DE DE59208018T patent/DE59208018D1/de not_active Expired - Fee Related
- 1992-11-30 US US07/982,831 patent/US5246351A/en not_active Expired - Fee Related
- 1992-12-17 JP JP4336959A patent/JPH05240162A/ja active Pending
Also Published As
Publication number | Publication date |
---|---|
DE4141670C2 (de) | 1994-09-29 |
DE59208018D1 (de) | 1997-03-20 |
JPH05240162A (ja) | 1993-09-17 |
EP0547404A1 (fr) | 1993-06-23 |
US5246351A (en) | 1993-09-21 |
DE4141670A1 (de) | 1993-07-01 |
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