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US20130101445A1 - Double diaphragm pump - Google Patents

Double diaphragm pump Download PDF

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Publication number
US20130101445A1
US20130101445A1 US13/637,374 US201113637374A US2013101445A1 US 20130101445 A1 US20130101445 A1 US 20130101445A1 US 201113637374 A US201113637374 A US 201113637374A US 2013101445 A1 US2013101445 A1 US 2013101445A1
Authority
US
United States
Prior art keywords
piston
diaphragm pump
hydraulic
pump according
space
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.)
Abandoned
Application number
US13/637,374
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English (en)
Inventor
Thomas Schütze
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.)
Promera GmbH and Co KG
Original Assignee
Promera GmbH and Co KG
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
Application filed by Promera GmbH and Co KG filed Critical Promera GmbH and Co KG
Assigned to PROMERA GMBH & CO. KG reassignment PROMERA GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHUTZE, THOMAS
Publication of US20130101445A1 publication Critical patent/US20130101445A1/en
Abandoned 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
    • 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
    • F04B43/025—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel
    • F04B43/026—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel each plate-like pumping flexible member working in its own pumping chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve

Definitions

  • the present invention relates to a diaphragm pump having at least one diaphragm.
  • the diaphragm delimits a conveying space in which a supply line and a discharge line open.
  • non-return valves are arranged in the supply and discharge lines in such a manner that, by the diaphragm being moved back and forth, the conveying medium can first be drawn via the supply line into the conveying space and can subsequently be pressed out of the conveying space via the discharge line.
  • the spaces which are separated from the conveying space by the diaphragms are connected to the environment by means of channels so that, in the event of a leakage, the conveying medium can be discharged from the pump and does not impede the movement of the diaphragms.
  • the disadvantage of this pump is that the diaphragms, owing to the high pressure in the conveying space and the ambient pressure behind the diaphragm, are subjected to a high differential pressure load, which leads to rapid wear in the diaphragms.
  • a further developed pneumatically driven dual-diaphragm pump is known from WO 2009/024619.
  • the compressed air which drives the piston is directed at the same time into the space behind the diaphragm.
  • the diaphragm is supported by means of a plate but the plate completely abuts the diaphragm in a supporting manner only at a dead centre point.
  • the disadvantage of this pump is that, in the event of a defect of the diaphragm, the conveying medium reaches the pneumatic system and disables the valves and consequently the entire pump. The pump can subsequently be restarted, if at all, only with great complexity.
  • a dual-chamber diaphragm pump without a driven piston is known from DE 32 06 242.
  • the disadvantage of this pump involves the large spaces which must be filled with compressed air after the dead centre point has been reached so that the diaphragms can be moved in the other direction. A very large amount of compressed air is thereby required, which increases the maintenance costs of the pump.
  • a similarly constructed pump with the same disadvantages is known from CA 1172904, WO97/10902 and U.S. Pat. No. 5,368,452. With the pump known from WO2009/024619, a disproportionately large amount of compressed air is required for the operation of the pump. These pumps are also not pressure-boosted so that the conveying pressure is always below the feed pressure.
  • An object of the present invention is to provide a diaphragm pump in which the diaphragms have a long service-life and are subjected to low differential pressures and which has a good level of efficiency.
  • a diaphragm pump wherein a fluid moves at least a first piston of a first piston/cylinder system back and forth, the first piston being mechanically connected to at least one other hydraulic piston and the hydraulic piston driving at least one diaphragm (M 1 , M 2 ) by means of a hydraulic medium
  • the diaphragm pump is a dual-diaphragm pump having at least two diaphragms (M 1 , M 2 ), a hydraulic medium moving or driving the diaphragms (M 1 , M 2 ), at least one hydraulic piston moving the hydraulic medium, and in that two diaphragms (M 1 , M 2 ) are mechanically connected to each other by means of a connection element, in particular a rod or a pipe, respectively.
  • the diaphragm pump has a first piston/cylinder system whose piston drives at least one hydraulic cylinder.
  • the piston can be driven in this instance by means of a fluid, for example, compressed air or a fluid medium, that is to say, moved back and forth.
  • the at least one hydraulic piston is also thereby moved back and forth.
  • the hydraulic piston is itself arranged in a cylinder and divides it into two operating spaces, a first and a second operating space. At least the first operating space is filled in this instance with a hydraulic medium which acts on the diaphragm of the diaphragm pump.
  • the diaphragm pump is constructed as a dual-diaphragm pump so that each of the two diaphragms conveys alternately.
  • the first operating space is delimited at the end face by the hydraulic piston and the diaphragm, respectively.
  • the operating space it is also possible for the operating space to be connected via a connection line to the space separated from the conveying space by the diaphragm and for the hydraulic medium moved by the hydraulic piston thus to act on the diaphragm and adjust it.
  • the first piston of the first piston/cylinder system is in this instance advantageously driven by means of compressed air so that the diaphragm pump can also be used in explosion-protected spaces.
  • any pressure boost between the driving pneumatic pressure and the conveying pressure of the pump can be adjusted.
  • the diaphragms are subjected to a maximum differential pressure load (maximum suction power) of one bar, whereby a long service life of the diaphragms is advantageously obtained.
  • An inert fluid for the conveyed medium is advantageously selected as a hydraulic medium so that, in the event of a defect of the diaphragm, the conveying medium does not become contaminated. Should conveying medium enter the first operating space in the event of a malfunction, this does not influence the pump.
  • the second operating spaces of the hydraulically acting piston/cylinder systems are connected to each other so that they act as damping members by the medium which is located in these operating spaces and which is advantageously the same inert hydraulic medium as in the first operating spaces being pumped back and forth.
  • the diaphragms are advantageously connected to each other by means of a connection element which synchronises the movement of the diaphragms.
  • This connection element does not serve to drive the diaphragms.
  • the connection element has at each of the ends thereof a thread by means of which it is screwed into the diaphragms. The screwing can be carried out directly into the material, in particular rubber, or into a threaded socket which is enclosed in the diaphragm. Since the connection element does not transmit any great forces, it is possible in most cases to dispense with a threaded socket.
  • a small structural form is advantageously achieved when the driving first piston/cylinder system is arranged between the hydraulically acting piston/cylinder systems.
  • the first piston is rigidly connected to the two hydraulic pistons by means of piston rods, whereby they are synchronously adjusted therewith.
  • the connection element of the diaphragms may advantageously extend through the tubular piston rods and is displaceably supported therein. That is to say, the connection element extends through the hydraulic pistons, correspondingly arranged seals preventing hydraulic medium from one operating space reaching the other through the piston rods.
  • the diaphragm pump has at least one device for monitoring the quantity of the hydraulic medium in one and/or more operating space(s) of the hydraulically acting piston/cylinder systems and/or in the connection line thereof. If hydraulic medium escapes and is drawn from a storage container, this is recognised by the device and the pump is stopped and/or an error signal is transmitted to a superordinate control system.
  • the fluid which moves the first piston of the first piston/cylinder system back and forth, in particular compressed air, is directed by a main valve, which is controlled in particular by the movement of the first piston, alternately into the first and second operating space of the first piston/cylinder system.
  • switching valves in particular 3/2 way valves, which are mechanically actuated by the first piston before or when the respective dead centre point or switching point is reached.
  • the switching valves control the compressed air which switches the main valve.
  • uncontrolled compressed air is used in this instance, that is to say, compressed air which is provided by an external compressed air source.
  • This pressure is generally higher than the pressure with which the diaphragm pumps according to the prior art are operated. It is thereby ensured that the diaphragm pump according to the invention switches in a reliable manner. This is often not the case with diaphragm pumps according to the prior art in which the main valve has only one inlet for controlled air, since the controlled pressure at the first piston/cylinder system is often very low.
  • the first piston actuates the valve adjustment members of the switching valves mechanically, the switching valves being constructed in particular as cartridge valves, that is to say, so as to be able to be inserted, in particular screwed, from the outer side into the wall of the first piston/cylinder system that delimits at the end face in each case.
  • the switching valves being constructed in particular as cartridge valves, that is to say, so as to be able to be inserted, in particular screwed, from the outer side into the wall of the first piston/cylinder system that delimits at the end face in each case.
  • a particularly favourable construction is thereby achieved since the valves can be replaced without opening the conveying spaces.
  • the main valve is also advantageously arranged on the housing of the diaphragm pump at the outer side so that the main valve can also be readily cleaned, repaired or replaced.
  • the main valve is advantageously constructed as a 4/2 way valve or as a 5/2 way valve. That is to say, the valve control element of the main valve moves alternately back and forth between two end positions. It consequently has only two defined positions in the form of the end positions.
  • the two operating spaces of the first piston/cylinder system are connected to each other by means of the valve control element of the main valve and the receiving operating space is consequently prefilled with the compressed air from the transferring operating space.
  • the operating space which has been prefilled is further filled with controlled air.
  • the other operating space is connected to the valve outlet so that the remaining operating air from the operating space can expand via silencers.
  • the main valve has an inlet for uncontrolled compressed air from an external compressed air source, the main valve itself being able to have a pressure control device for producing controlled compressed air of a specific pressure.
  • a valve control element which is displaceably arranged in the housing of the main valve and which is adjusted by the compressed air which is controlled by the switching valves, in particular the uncontrolled compressed air, the controlled compressed air is directed alternately into the operating spaces of the first piston/cylinder system.
  • the axial cylinder walls of the cylinder of the first piston/cylinder system may advantageously be adapted to the shape of the axial walls of the first piston.
  • a planar construction of the walls is preferred in this instance.
  • the switching valves may advantageously have throttles so that the air which is pressed out of the respective operating space is braked by the throttle and a slowed movement of the valve control element of the main valve from the centre region is thereby achieved, whereby the phase of the pressure compensation between the pretensioned operating space and the operating space which is to be emptied next and the operating space which is to be filled next is as long as possible.
  • the throttle does not yet act so strongly at the beginning of the movement of the pneumatic piston so that the valve control element of the main valve is adjusted with high speed from the end position thereof in the direction of the central region, in which the operating spaces of the pneumatic cylinder are bypassed.
  • Each conveying space may advantageously be connected by means of a supply channel to a common supply line, respectively, and/or by means of an outlet channel to a common pressure line, respectively, the supply line and/or the pressure line being supported in a floating manner on at least one connection region of the pump housing. It is thereby advantageously possible that no alternately occurring loads occur at the connection locations (appearances of mechanical fatigue). Valves, in particular non-return valves, are arranged in the supply channels and in the outlet channels, respectively.
  • diaphragm pump which is constructed as a dual-diaphragm pump is explained in greater detail below with reference to drawings.
  • FIG. 1 is a perspective view of the diaphragm pump according to the invention in the form of a dual-diaphragm pump;
  • FIG. 2 is a sectioned illustration of the diaphragm pump according to FIG. 1 ;
  • FIG. 3 is a sectioned illustration through the dual-diaphragm pump according to FIGS. 1 and 2 ;
  • FIG. 4 is a partial cutout from FIG. 3 ;
  • FIG. 5 is a pneumatic diagram for a diaphragm pump according to the invention having a 5/2 way valve as a main valve;
  • FIG. 6 is a pneumatic diagram for a diaphragm pump according to the invention having a 4/2 way valve as a main valve.
  • FIGS. 1 and 2 are perspective views of the diaphragm pump according to the invention in the form of a dual-diaphragm pump.
  • the dual-diaphragm pump has a housing cover 19 and a housing portion 11 which receives the cylinder 10 of the hydraulically acting piston/cylinder system 9 , 10 .
  • the housing portion 11 as illustrated in FIG. 2 , is secured by means of coaxial screws 11 a to the axial cylinder wall 3 of the first piston/cylinder system.
  • the diaphragm M is clamped at 22 by the housing cover 19 and the housing portion 11 (see FIGS. 3 and 4 ).
  • the housing cover 19 and housing portion 11 are connected to each other by means of the screws 19 a and fix the diaphragm M in position.
  • the housing cover 19 forms at the top and bottom a receiving member for a non-return valve 24 , respectively.
  • the non-return valves 23 , 24 are inserted before the housing flanges 25 , 27 are screwed to the housing cover 19 into the corresponding recesses of the housing cover 19 . Additional seals prevent conveying medium from being able to be introduced around the housing of the non-return valves 23 , 24 .
  • the axial walls 3 of the first piston/cylinder system are retained with spacing by means of spacer sleeves 7 and connected to each other by means of the screws 6 .
  • the cylindrical wall sleeve 2 which forms the cylinder is further arranged between the walls 3 in a pressure-tight manner, additional seals ensuring the tightness.
  • the screws 6 have a screw head 6 a and at the end thereof a thread 6 b with which they are screwed to the first axial wall 3 .
  • the first piston 1 which is formed by two discs 1 a , 1 b and which separates the operating spaces A and B from each other.
  • the discs 1 a , 1 b are screwed together by means of the screws 4 .
  • the cylindrical wall 2 has, at the outer side thereof, ribs for absorbing heat from the ambient air in order to prevent ice forming on the diaphragm pump.
  • the axial walls 3 also have recesses 3 b which also serve to better conduct heat and to provide rigidity and save material.
  • the piston 1 has a continuous seal 1 c which abuts the inner wall of the cylinder 2 in a sealing manner.
  • the piston rods 8 a, 8 b are pushed beforehand through the holes 1 d until the collars 8 c rest in the corresponding recesses 1 e of the piston discs 1 a , 1 b . Owing to the assembly of the piston discs 1 a , 1 b , the piston rods 8 a, 8 b are secured to the piston 1 in a positive-locking manner.
  • the piston rods 8 a, 8 b extend through the holes 3 a of the axial walls 3 , seals 56 ensuring that no compressed air from the operating spaces A, B reaches the hydraulic spaces H 2 . With the ends 8 d thereof, the piston rods 8 a, 8 b are connected to the hydraulic pistons in a sealing manner by means of screws 60 .
  • the piston rods 8 a, 8 b are constructed as pipes in which the connection element 5 rests in a displaceable manner in the form of a rod.
  • the connection element 5 is screwed with the ends 5 a thereof having the outer thread into the diaphragm plate 20 .
  • the diaphragm plate 20 is formed in the diaphragm M 1 in the centre 21 thereof.
  • the hydraulic pistons 9 each have a continuous seal 12 which abuts the inner wall of the cylinder wall 10 in a sealing manner and separates the two operating spaces H 1 , H 2 from each other.
  • the two hydraulic spaces H 2 of the two hydraulic piston/cylinder systems are connected to each other by means of the connection channels 16 , 17 and 18 .
  • Differential pressure valves 13 are arranged in each case in the hydraulic pistons 9 . If the differential pressure between the operating spaces H 1 and H 2 exceeds a specific value when the pump is operated, the differential pressure valve 13 opens and the differential pressure can be reduced to a predetermined value.
  • the connection channel 16 , 17 , 18 can be connected by means of an additional connection line (not illustrated) to a storage container and/or a sensor.
  • an influx or discharge of hydraulic medium now occurs at the storage container or the connection line, this may signify a breakage of the diaphragm, whereupon an error signal can be sent to a superordinate control system and/or the diaphragm pump is automatically stopped. This can be carried out, for example, by the forced closing of the line which supplies the pump with compressed air.
  • the supply channels 28 are connected to each other by means of the supply line 36 , the supply line 36 forming with the one end 41 thereof the conveying medium inlet of the pump.
  • the other end of the supply line 36 which is constructed as a pipe is closed by means of a screwed-in plug 34 .
  • the supply line 36 rests with the regions 36 a thereof in a floating manner in the housing flanges 27 , seals 39 ensuring the necessary sealing.
  • the housing flanges 27 have an annular space 40 which surrounds the regions 36 a and which is formed by a continuous groove.
  • the supply line 36 has window-like openings 38 through which the conveying medium is introduced from the inner space 37 of the supply line 36 into the annular space 40 and from there into the supply channel 28 .
  • the outlet channels 26 are connected to each other by means of the pressure line 29 , the pressure line 29 forming the conveying medium outlet of the pump with the one end 33 thereof.
  • the other end of the pressure line 29 which is constructed as a pipe is closed by means of a screwed-in plug 34 .
  • the pressure line 29 rests with the regions 29 a thereof in a floating manner in the housing flanges 25 , seals 39 ensuring the necessary fluid-tightness.
  • the housing flanges 25 have an annular space 32 which surrounds the regions 29 a and which is formed by a continuous groove. In the regions 29 a, the pressure line 29 has window-like openings 31 , through which the conveying medium can be introduced from the annular space 32 into the inner space 30 of the pressure line 29 .
  • switching valves 14 which extend with an extension 15 of the valve control members thereof into the operating spaces A, B. If the piston 1 reaches its dead centre point, the respective switching valve is actuated, whereby compressed air is directed to the main valve 50 by means of channels which are not illustrated, and the main valve is in turn switched off.
  • the main valve 50 is arranged at the outer side on the pump housing so that good heat exchange with the ambient air can take place, whereby the risk of formation of ice is reduced.
  • the conveying medium which is located in the conveying space F 1 is conveyed by the non-return valve 24 into the outlet channel 26 .
  • the non-return valve 23 is closed during this. If enlargement subsequently occurs in the conveying space F 1 by the diaphragm M 1 being moved back, conveying medium is drawn from the supply line 36 into the conveying space F 1 via the non-return valve 23 which is open. During the suction phase, the non-return valve 24 is closed.
  • FIG. 5 shows a pneumatic diagram of the diaphragm pump according to FIGS. 1 to 4 .
  • the diaphragm pump which is operated with compressed air has a compressed air inlet 43 which is advantageously arranged on the main valve 50 .
  • the pressure control device 45 which is connected to the inlet 43 by means of the input line 44 .
  • the pressure control device 45 may be a proportional valve which may have an adjustment mechanism, for example, in the form of an adjustment screw, by means of which a spring can be pretensioned for pressure adjustment. If, by means of the external compressed air source (not illustrated), uncontrolled pressure of 7 bar is provided, controlled compressed air of, for example, 5.5 bar can be supplied to the main valve 50 by means of the pressure control device 45 via the connection line.
  • the inlet 43 is connected to the switching valves 14 by means of connection lines 48 , 49 .
  • the switching valves are constructed as 3/2 way valves and are switched by means of the extensions 15 of their valve control members extending into the operating spaces A, B.
  • a spring presses the valve control members into the illustrated position, in which the control lines 52 , 53 are not connected to the valve inlet or the connection line 48 , 49 .
  • the switching valve 14 is switched and the uncontrolled compressed air of the external pressure source switches the main valve 50 .
  • the main valve 50 is constructed as a 5/2 way valve.
  • the controlled compressed air reaches the operating space A via the connection line 57 .
  • the piston 1 is consequently moved to the right together with the hydraulic pistons 9 .
  • the non-illustrated right-hand diaphragm is moved to the right, whereby the conveying space which is associated therewith is reduced.
  • the right-hand diaphragm consequently conveys.
  • the left-hand diaphragm which is also not illustrated in FIG. 5 draws conveying medium from the supply line into the conveying space thereof.
  • the right-hand switching valve 14 is switched via the extension 15 so that the main valve 50 is also switched.
  • the connection of the operating space A to the connection line 47 is first interrupted. Afterwards, the two operating spaces are bypassed with respect to each other so that the pretensioned compressed air located in the operating space B can expand into the operating space A. A specific time period is available for this until the main valve 50 has ultimately completely switched through and compressed air which is controlled via the connection line 47 is directed into the operating space B, whereby the piston 1 is moved to the left.
  • the remaining compressed air which has not yet been expanded in the pressure space B subsequently expands via the valve outlets 51 via the silencers 35 into the environment.
  • FIG. 6 illustrates an alternative embodiment in which the main valve 50 is constructed as a 4/2 way valve.
  • the main valve 50 differs from the main valve illustrated in FIG. 5 simply in that only one outlet 51 is provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US13/637,374 2010-03-26 2011-03-18 Double diaphragm pump Abandoned US20130101445A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010013108.3 2010-03-26
DE102010013108A DE102010013108A1 (de) 2010-03-26 2010-03-26 Doppelmembranpumpe
PCT/EP2011/001360 WO2011116911A2 (de) 2010-03-26 2011-03-18 Doppelmembranpumpe

Publications (1)

Publication Number Publication Date
US20130101445A1 true US20130101445A1 (en) 2013-04-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
US13/637,374 Abandoned US20130101445A1 (en) 2010-03-26 2011-03-18 Double diaphragm pump

Country Status (5)

Country Link
US (1) US20130101445A1 (de)
EP (1) EP2553269B1 (de)
CN (1) CN102947593B (de)
DE (1) DE102010013108A1 (de)
WO (1) WO2011116911A2 (de)

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US20220145874A1 (en) * 2020-11-09 2022-05-12 Pdc Machines Inc. Active oil injection system for a diaphragm compressor
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USD1014562S1 (en) * 2022-02-11 2024-02-13 Graco Minnesota Inc. Displacement pump
US20240093682A1 (en) * 2022-09-20 2024-03-21 Protec Co., Ltd. Diaphragm Pump
US11986850B2 (en) 2018-04-10 2024-05-21 Graco Minnesota Inc. Handheld airless sprayer for paints and other coatings
US12366233B2 (en) 2020-03-31 2025-07-22 Graco Minnesota Inc. Electrically operated pump for a plural component spray system

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DE102010013108A1 (de) 2011-09-29
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WO2011116911A2 (de) 2011-09-29

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