EP0061706A1 - Pompe à membrane double, actionnée par l'air sous pression - Google Patents

Pompe à membrane double, actionnée par l'air sous pression Download PDF

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Publication number
EP0061706A1
EP0061706A1 EP82102428A EP82102428A EP0061706A1 EP 0061706 A1 EP0061706 A1 EP 0061706A1 EP 82102428 A EP82102428 A EP 82102428A EP 82102428 A EP82102428 A EP 82102428A EP 0061706 A1 EP0061706 A1 EP 0061706A1
Authority
EP
European Patent Office
Prior art keywords
air
piston
valve control
diaphragm pump
control piston
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.)
Withdrawn
Application number
EP82102428A
Other languages
German (de)
English (en)
Inventor
Dirk Budde
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
DEPA GmbH
Original Assignee
DEPA GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE19813112434 external-priority patent/DE3112434A1/de
Priority claimed from DE19813150976 external-priority patent/DE3150976A1/de
Application filed by DEPA GmbH filed Critical DEPA GmbH
Publication of EP0061706A1 publication Critical patent/EP0061706A1/fr
Withdrawn legal-status Critical Current

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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
    • F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • F04B43/0736—Pumps having fluid drive the actuating fluid being controlled by at least one valve with two or more pumping chambers in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/063—Arrangements with main and auxiliary valves, at least one of them being fluid-driven the auxiliary valve being actuated by the working motor-piston or piston-rod

Definitions

  • valve control piston is driven by a mechanically operating drive system with a mechanical energy store, the mechanical energy store in turn being actuated by the movement of the membrane devices.
  • This pressure equalization results, on the one hand, in a further improvement in the efficiency, namely in that the inevitable dead space in the air chambers is not acted upon by the working air itself, but rather by the relief air from the other air chamber, before the air chamber is supplied with the working air by the main valve control piston is associated. Furthermore, the pressure compensation also reduces the noise development, which is particularly evident at the outlet.
  • the new construction also makes it possible to use plastic-metal sealing surfaces instead of metal-metal sealing surfaces, so that lubrication with oil mist is unnecessary.
  • the risk of icing at the air outlet is also reduced in the pump with a pilot valve, so that work can be carried out with increased performance without the risk of icing.
  • the pilot valve pump tends to operate in extreme operating conditions, e.g. B. with very slow operation, to get stuck in the end positions. This mode of operation can result if the pump works against pressure, e.g. B. against a normally closed filling valve, with which the material to be conveyed should only be removed for a short time if necessary. In the This danger does not exist for pumps with mechanical energy storage devices that can be suddenly discharged. Depending on the application, one or the other embodiment will therefore be preferred.
  • FIG. 1 shows a somewhat schematic sectional view of a conventional compressed air-driven double membrane pump 10, consisting of a pump housing 12 with two housing chambers 14 arranged at a distance from one another, each of which has a membrane 16 and is divided into a pump chamber 18 and an air chamber 20 , wherein, as can be readily seen, the two air chambers 20 are aligned with one another and a compressed air reversing device 22 between them have the air from above supplied pressurized A rbeits-, see arrow 24, the two air chambers 20 feeds (arrow 26).
  • the pump chambers are connected via ball valve devices 30 to a common suction port 32, which in turn is connected to a storage container supplying the medium to be conveyed, and via further valve devices 28 to a common pressure port 34, which is connected to the device, which is connected to this promotional good is to be delivered.
  • the membrane devices 16 each comprise annular membrane support plates 36, which are each screwed onto the end of a membrane piston 38 and hold an annular membrane 40 made of resilient material on their inner border between them in a pressure-tight manner, while the outer border of the annular membrane part 40 between the edges of correspondingly shaped parts of the pump housing 12, see e.g. B. the housing part 21 is kept pressure-tight.
  • FIG. 2 shows in greater detail the compressed air reversing device 22 used in the double diaphragm pump according to FIG. 1, which consists of an air control valve housing 42 which can be screwed to the pump housing 12 and which has an inlet 44 for working air and an outlet 46 for exhaust air.
  • the outlet 46 opens into a silencer 48 which is intended to dampen at least part of the flow noise of the escaping compressed air.
  • the lower side of the piston 52 is not vented, so that the working air supplied leads to a build-up of pressure and finally moves the piston 52 away from the position shown in FIG. 2 and upwards, as a result of which the connection 58 present in the piston 52 now Openings 68 and 56 bridged and thus connects the right air chamber with the outlet space 64.
  • the corresponding connection of the left air chamber to the discharge space 64 is interrupted, as a result of which pressure can now build up in the left air chamber due to the working air, so that the working cycle is repeated in the opposite direction.
  • the known air control valve thus supplies both air chambers with working air under all operating conditions and in any position of the membranes.
  • the membrane movement takes place by venting the air chamber.
  • FIG. 3 it is the leftmost position in which the valve spool 52 is shifted to the left, as shown.
  • FIG. 3 essentially represents a schematic view, while the further FIGS. 4 to 17 represent a practical exemplary embodiment, FIG. 4 representing a side view of the air outlet side of the housing 42 of the reversing device 22, while FIG. 5 shows a view of the piston axis vertical sectional view along the arrows VV, again through the housing 42 of the reversing device 22, without inserted individual parts.
  • the air pressure control device 22 comprises a G e- h äuse 42 having an inlet 44 for supply air and an outlet 46 for exhaust air.
  • a muffler not shown here, can be screwed into the exhaust air opening 46 in order to dampen the flow noise of the compressed air even more.
  • An oil container is not shown here since the piston 52 is mounted in its cylinder 54 and in guides 232, see FIG. 3, in such a way that no metal-to-metal friction occurs, as will be explained in more detail later.
  • the piston 52 is parallel to the membrane piston 38 and can therefore be actuated very easily. Mechanically by the movement of, for example, the membrane support plate or the membrane plate, as has already been briefly explained in connection with FIG. 3.
  • valve control part 53 of the piston 52 in an axial section (Fig. 10) and the associated K olbenzylinder 54 in a cross-sectional view (Fig. 8) and also an axial cross-sectional (Fig. 9) in reproduced on a scale that corresponds to that of FIG. 3, while the parts in FIGS. 4, 5, 6 and 7 are shown only about half as large.
  • annular space 204 in the position of the piston 52 within the cylinder 54 shown in FIG. 3 is connected to the opening 208, which in turn opens via an annular space 212 - formed by the cylinder 54 - in a channel 210, which in turn is in the cast housing 42 5, 6 and 7.
  • This channel 210 is in turn connected to a bore 213, see FIG. 16, which in turn is connected to the air chamber 20 in a manner not shown, see the bore 23 in the housing part 21 in FIG. 1.
  • annular space 204 is also connected to bores 218, which can be seen in FIG. 9 and establish a connection with an annular space 220 formed by the cylinder 54, see also FIG. 3.
  • This annular space 220 formed by the piston cylinder 54 protrudes a relatively narrow duct connection 222 in connection with the outlet space 64, from which exhaust air reaches the outlet 46, see FIGS. 4 and 5.
  • the drive plate 240 is shown in FIG. 14 in a sectional view and a top view, its particular shape being explained in more detail later.
  • the drive plate 240 is designed so that it can slide on the threaded rod 236 in the axial direction, as well as within a bore 244 formed inside the part 53, which is closed at the two ends of the part 53 by inwardly pointing ring-like projections or ring shoulders 246 and which is interrupted in the middle by a further ring projection 248, see FIG. 3.
  • the ring projection 248 as well as the ring projections 246 have such an inner diameter that the compression spring 238 pushed onto the threaded rod 236 can be pushed through it unhindered, but that the drive plate 240 can bear against the ring shoulders 250 and 252 formed by the ring projections 246 and 248, respectively.
  • the driving disk 240 shown in FIG. 14 can be introduced through the circular openings formed by the ring projections 246, it has the flattening 254 which can be seen in FIG. 14.
  • sealing rings 132 can be of a conventional type, for example they could be commercially available jacket rings which comprise an inner O-ring made of a rubber material and an outer race made of PTFE (Teflon). Compared to purely rubber-elastic sealing rings, jacket rings have lower running friction and lower breakaway forces even after long downtimes, and they also have high wear resistance even when completely dry.
  • the PTFE is usually filled with powdered bronze, so that the z. B. also from bronze alloys existing metal parts of the valve piston 54 give favorable dry-running properties.
  • piston-cylinder device 54 shown in FIG. 9 it should be added that it has ring projections 276, which form a plurality of receiving grooves 278 for sealing rings 280, the latter being recognizable in FIG. 3 and used to serve the various annular spaces formed by the cylinder 54, e.g. B. 212 to separate from each other pressure-tight.
  • the cylinder 54 is inserted into a corresponding bore 282 of the valve housing 42 and then held in place on both sides by the cap-like guides 232.
  • the cap-like guide 232 is in turn festge by means of a holding plate 284 3, where a sealing washer 286 can also be seen.
  • the holding plate 284 is in turn suitably secured to the side surfaces 288 of housing 42, see F ig. 4, for example screwed together with the housing plate 21 of the pump chamber 18 resting on the reversing device, for example with the aid of screw bolts passed through bores 290 (FIG. 5).
  • the reversing device according to the invention can be designed for different operating pressure ranges, it only being necessary to ensure that appropriately dimensioned spring devices are provided.
  • the friction between the piston 52 and the cylinder wall of the cylinder 54 caused by the sealing devices 132 is higher, so that the spring 238 accordingly also receives a greater spring force in order to carry out the switching of the valve safely and quickly in the event of a trigger.
  • the ring spring 274, which is shown in one embodiment in FIG. 18, must then be dimensioned to be larger, so that the piston 52 is held securely until the drive plate 240 reaches the shoulder 252 for the purpose of triggering the changeover.
  • the compressed air reversing device can also be maintained relatively easily, since the individual parts, in particular also the piston cylinder, can be easily replaced, the same applies to the valve piston and the various sealing rings, which may be subject to wear.
  • the membrane piston can also be mounted in exchangeable guide rings. Alternatively, storage can also take place in a bearing bush 37 with sealing sets, one of which (reference number 35) is shown in more detail in FIG. 18, which FIG. 18 shows the overall structure of the compressed air reversing device.
  • Such interchangeable seal sets can be constructed similarly to the sealing rings used for the piston 52, i. H. e.g. B. from a bronze-loaded PTFE sealing ring and an O-ring made of z. B. synthetic rubber exist as an extrusion ring.
  • the overall construction of the compressed air reversing device 22 according to this and the embodiment of the present invention to be described later is designed so that it can be used for diaphragm pump units of different sizes.
  • the reversing device for any travel of the diaphragm, because the reversal always takes place in the last part of the respective stroke, ie that the valve travel of the pilot valve is independent of the travel of the membrane and in particular can be kept much smaller than the travel of the membrane. This not only increases the versatility of the reversing device, it also reduces wear.
  • This compressed air control device 22 also includes an air control valve housing 42 with an inlet 44 for supply air and an outlet 46 for exhaust air.
  • a silencer can also be provided here, but it is not absolutely necessary because of the significantly lower flow noise of the compressed air according to the invention.
  • An oil container is also missing here, since the piston 52 is mounted in its cylinder 54 in such a way that metal-metal friction no longer occurs, as will be explained.
  • the pilot valve control piston 70 is shaped such that in this position it connects a central opening 78 in the pilot piston cylinder 80 with an opening 82 to the right of it according to FIG. 24, which can also be seen in FIG. 25, which figure is perpendicular to the sectional view of FIG 24 is a section through the pilot valve axis, see also arrows XXV-XXV of FIG. 19.
  • the opening 78 can also be seen in FIG. 19, which is a longitudinal section through the main valve 52 and thus a section along the line IXX- IXX of FIG. 25.
  • working air supplied to the inlet 44 thus flows, for example, via a dust filter 84 into the supply air space 86 and from there into the duct 88, from where the air passes through the opening 78 into the annular space 90 formed by the pilot valve 70. From there, the air then passes, see FIG. 25, according to the position of the pilot valve 70 shown in FIG. 25, through the opening 82 into a duct 92 which opens into a duct 94, which in FIG. 20 only contains the air control valve housing 42 19, can be seen in a sectional view similar to that in FIG. 19 and ends in an opening 96 at the right end of the cylinder 54.
  • the main valve 52 Similar to the pilot valve, the main valve 52, together with its cylinder, forms 54 annular spaces, 98, 100 and 102, which are used to bridge different channels, which in turn end in openings which are partially recognizable in FIG. 19. overall, however, can be seen from the various radial sectional views in FIG. 22.
  • the main valve 52 In addition to these three fairly wide annular spaces 98, 100 and 102, the main valve 52 also forms two narrow annular spaces 1 0 4 and 106, which pass through a bore 108 running inside the valve piston 52 and through a radial bore 110 and 112, respectively, emanating from this axial bore 108 communicate with each other.
  • the channel 88 and thus the pressurized supply air is connected via openings 114 to the annular space 98, which in turn is connected via an opening in the cylinder 54 above the drawing plane in FIG. can be seen in section D of FIG. 21/22 and provided with the reference number 116) and a further channel extending from this opening is connected to the left air chamber according to FIG. 24.
  • the data associated with the connection to the right air chamber openings in the cylinder 54 are opposed strength in the F. 19 recognizable, see reference number 118.
  • These openings 118 open, see FIG. 20, in the channel 120, which can also be seen in FIG. 25, which is connected to the right air chamber.
  • annular space 100 is connected to the exhaust air space 124 via an opening 122 in FIG. 19 above the plane of the drawing, see section G of FIG. 21/22, this results in a desired ventilation of the right air chamber.
  • the corresponding openings 126 for the other air chamber are in Fig. 19, in turn, can be seen as well as the conces- örige h, leading to the exhaust chamber 124.
  • a switchover takes place in such a way that the supply air entering through duct 78 no longer reaches the right duct 94 and thus the right end of the main valve 52, but instead via the left one, with the Reference number 194 provided channel to the opening 196 and thus to the left side of the main valve 52.
  • This pressure equalization is achieved by an intermediate position which is maintained for a sufficiently long time due to the slow changeover movement of the main valve 52 and which is shown under 2 in FIG. 30.
  • the central bore 108 connects the openings 116 and 118 with their annular spaces 104 and 106, while the openings 132 connected to the exhaust air chamber and the openings 114 connected to the supply air chamber in annular spaces 100, 102 and 98 are blind end and are closed, as indicated by the crosses. This leaves only a connection between the left air chamber and the right air chamber, so that the desired pressure equalization between the two air chambers takes place via the openings 116 and 118 together with the associated connecting channels and the axial bore 108 of the main valve 52.
  • the energy gained through pressure equalization depends on the size of the dead volume of the air chamber in the end position of the diaphragm pump.
  • this dead space which is initially at atmospheric pressure, is raised to a pressure by the right air chamber under working pressure, which depending on the volume ratio between the dead space and the maximally large other air chamber is either only slightly below the working pressure (with a very small dead space), or it drops a little more if the dead space is larger Takes up part of the usable space.
  • pressure equalization saves filling the dead space with valuable working air under pressure, so working air is only required to carry out the actual working stroke.
  • efficiency improvements of between 10 and 30% can be achieved with the usual double diaphragm pumps.
  • Another advantage is that there is no direct connection path between the connection for working air and the outlet at any position of the membrane piston, as in the prior art, so that if the membrane piston rod stops at any point due to, for example, a blocked material flow, no working air is consumed. In the prior art, it could happen that this position was available at certain positions of the diaphragm piston rod, so that the result was a constant discharge of working air with correspondingly high operating costs.
  • cylinder insert bushes which are inserted into a housing 42, allows the production of the housing 42 - from die-cast metal and thus results in a very simple and cost-saving manufacturing process without complex metalworking steps.
  • a lubrication is not required, eliminating the associated maintenance of an oil reservoir, and in particular also be dispensed with impurities of the conveying medium and the outside of the pump through the exhaust air-oil mist.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP82102428A 1981-03-28 1982-03-24 Pompe à membrane double, actionnée par l'air sous pression Withdrawn EP0061706A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19813112434 DE3112434A1 (de) 1981-03-28 1981-03-28 Druckluftgetriebene doppelmembran-pumpe
DE3112434 1981-03-28
DE19813150976 DE3150976A1 (de) 1981-12-23 1981-12-23 Druckluftgetriebene doppelmembranpumpe
DE3150976 1981-12-23

Publications (1)

Publication Number Publication Date
EP0061706A1 true EP0061706A1 (fr) 1982-10-06

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Application Number Title Priority Date Filing Date
EP82102428A Withdrawn EP0061706A1 (fr) 1981-03-28 1982-03-24 Pompe à membrane double, actionnée par l'air sous pression

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EP (1) EP0061706A1 (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0102311A2 (fr) * 1982-07-30 1984-03-07 Bellofram Corporation Moteur à fluide
DE3310131A1 (de) * 1983-03-21 1984-09-27 DEPA Gesellschaft für Verfahrenstechnik mbH, 4000 Düsseldorf Umsteuerventileinsatz fuer eine druckluftgetriebene doppelmembranpumpe
GB2162591A (en) * 1984-08-02 1986-02-05 Shoketsu Kinzoku Kogyo Kk Fluid pressure booster
EP0172780A2 (fr) * 1984-06-12 1986-02-26 Bellofram Corporation Pompe à commande liquide
EP0180170A2 (fr) * 1984-11-02 1986-05-07 Nordson Corporation Agencement d'un moteur à pistons commandé par la pression de fluide
DE3913351A1 (de) * 1989-04-22 1990-10-25 Teves Gmbh Alfred Vorrichtung zur hilfsdruckerzeugung
EP0498565A1 (fr) * 1991-02-05 1992-08-12 Harrison Group Limited Pompes
FR2708050A1 (fr) * 1993-07-20 1995-01-27 Graco Inc Appareil de pompage à double membrane ayant un actionneur à ventouse à deux étapes.
EP0727580A1 (fr) * 1995-02-14 1996-08-21 Itt Manufacturing Enterprises, Inc. Vanne à va et vient commandée pneumatiquement pour actionner une pompe réciprocante
EP0708244A3 (fr) * 1994-10-17 1996-10-23 Aro Corp Clapet d'air anti-givrage
US6382934B2 (en) 1997-09-04 2002-05-07 Almatec Maschinenbau Gmbh Reversing valve for a compressed air membrane pump
EP1398504A1 (fr) * 2002-09-12 2004-03-17 Ingersoll-Rand Company Pompe à membrane double
CN101936282A (zh) * 2010-09-30 2011-01-05 潘万桑 气动式双隔膜泵
CN113864169A (zh) * 2021-09-27 2021-12-31 陶渊政 一种可快速更换隔膜的空气泵

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH224724A (de) * 1941-11-19 1942-12-15 Sulzer Ag Pumpanlage zur Förderung von Flüssigkeiten auf hohen Druck.
US2307566A (en) * 1940-07-31 1943-01-05 Wright Aeronautical Corp Pneumatic drive fuel pump
GB805540A (en) * 1953-02-17 1958-12-10 Sperry Gyroscope Co Ltd An improved liquid pump
US3207080A (en) * 1962-11-05 1965-09-21 Panther Pumps & Equipment Co Balanced pressure pump
DE1285322B (de) * 1963-10-31 1968-12-12 Detrez Georges Gerard Hochdruckpumpe
DE1813712A1 (de) * 1968-12-10 1970-07-09 Georg Wagner Doppelmembranpumpe
DE2255414A1 (de) * 1971-11-16 1973-05-24 Rupp Co Warren Rueckschlagventil fuer pumpen
US3838946A (en) * 1971-07-12 1974-10-01 Dorr Oliver Inc Air pressure-actuated double-acting diaphragm pump
DE2444844B2 (de) * 1973-09-24 1977-08-04 The Oilgear Co Milwaukee, Wis (VStA) Hochdruckpumpe mit hydrostatisch betriebenem doppelwirkendem einzylindermotor
DE2726674B1 (de) * 1977-06-14 1978-05-18 Draegerwerk Ag Druckgasbetaetigte Doppelmembranpumpe

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2307566A (en) * 1940-07-31 1943-01-05 Wright Aeronautical Corp Pneumatic drive fuel pump
CH224724A (de) * 1941-11-19 1942-12-15 Sulzer Ag Pumpanlage zur Förderung von Flüssigkeiten auf hohen Druck.
GB805540A (en) * 1953-02-17 1958-12-10 Sperry Gyroscope Co Ltd An improved liquid pump
US3207080A (en) * 1962-11-05 1965-09-21 Panther Pumps & Equipment Co Balanced pressure pump
DE1285322B (de) * 1963-10-31 1968-12-12 Detrez Georges Gerard Hochdruckpumpe
DE1813712A1 (de) * 1968-12-10 1970-07-09 Georg Wagner Doppelmembranpumpe
US3838946A (en) * 1971-07-12 1974-10-01 Dorr Oliver Inc Air pressure-actuated double-acting diaphragm pump
DE2255414A1 (de) * 1971-11-16 1973-05-24 Rupp Co Warren Rueckschlagventil fuer pumpen
DE2444844B2 (de) * 1973-09-24 1977-08-04 The Oilgear Co Milwaukee, Wis (VStA) Hochdruckpumpe mit hydrostatisch betriebenem doppelwirkendem einzylindermotor
DE2726674B1 (de) * 1977-06-14 1978-05-18 Draegerwerk Ag Druckgasbetaetigte Doppelmembranpumpe

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0102311A2 (fr) * 1982-07-30 1984-03-07 Bellofram Corporation Moteur à fluide
EP0102311B1 (fr) * 1982-07-30 1987-05-20 Bellofram Corporation Moteur à fluide
US4705458A (en) * 1982-07-30 1987-11-10 Bellofram Corporation Fluid operated pump
DE3310131A1 (de) * 1983-03-21 1984-09-27 DEPA Gesellschaft für Verfahrenstechnik mbH, 4000 Düsseldorf Umsteuerventileinsatz fuer eine druckluftgetriebene doppelmembranpumpe
EP0172780A2 (fr) * 1984-06-12 1986-02-26 Bellofram Corporation Pompe à commande liquide
EP0172780A3 (fr) * 1984-06-12 1986-06-25 Bellofram Corporation Pompe à commande liquide
GB2162591A (en) * 1984-08-02 1986-02-05 Shoketsu Kinzoku Kogyo Kk Fluid pressure booster
EP0180170A2 (fr) * 1984-11-02 1986-05-07 Nordson Corporation Agencement d'un moteur à pistons commandé par la pression de fluide
EP0180170A3 (en) * 1984-11-02 1987-04-08 Nordson Corporation Fluid pressure operated piston engine assembly
FR2646211A1 (fr) * 1989-04-22 1990-10-26 Teves Gmbh Alfred Dispositif generateur de pression auxiliaire, notamment pour vehicule automobile
DE3913351A1 (de) * 1989-04-22 1990-10-25 Teves Gmbh Alfred Vorrichtung zur hilfsdruckerzeugung
US5137436A (en) * 1989-04-22 1992-08-11 Alfred Teves Gmbh Device for the generation of auxiliary pressure
EP0498565A1 (fr) * 1991-02-05 1992-08-12 Harrison Group Limited Pompes
FR2708050A1 (fr) * 1993-07-20 1995-01-27 Graco Inc Appareil de pompage à double membrane ayant un actionneur à ventouse à deux étapes.
EP0708244A3 (fr) * 1994-10-17 1996-10-23 Aro Corp Clapet d'air anti-givrage
EP0727580A1 (fr) * 1995-02-14 1996-08-21 Itt Manufacturing Enterprises, Inc. Vanne à va et vient commandée pneumatiquement pour actionner une pompe réciprocante
US6382934B2 (en) 1997-09-04 2002-05-07 Almatec Maschinenbau Gmbh Reversing valve for a compressed air membrane pump
DE19738779C2 (de) * 1997-09-04 2003-06-12 Almatec Maschb Gmbh Umsteuersystem für eine druckgetriebene Membranpumpe
EP1398504A1 (fr) * 2002-09-12 2004-03-17 Ingersoll-Rand Company Pompe à membrane double
CN101936282A (zh) * 2010-09-30 2011-01-05 潘万桑 气动式双隔膜泵
CN101936282B (zh) * 2010-09-30 2013-02-27 台州市昌宇气动设备有限公司 气动式双隔膜泵
CN113864169A (zh) * 2021-09-27 2021-12-31 陶渊政 一种可快速更换隔膜的空气泵
CN113864169B (zh) * 2021-09-27 2022-08-23 陶渊政 一种可快速更换隔膜的空气泵

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