EP0314994A1 - Dispositif de pompage avec double pompe - Google Patents

Dispositif de pompage avec double pompe Download PDF

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Publication number
EP0314994A1
EP0314994A1 EP88117547A EP88117547A EP0314994A1 EP 0314994 A1 EP0314994 A1 EP 0314994A1 EP 88117547 A EP88117547 A EP 88117547A EP 88117547 A EP88117547 A EP 88117547A EP 0314994 A1 EP0314994 A1 EP 0314994A1
Authority
EP
European Patent Office
Prior art keywords
pump
displacement
piston
pumps
piston rod
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.)
Granted
Application number
EP88117547A
Other languages
German (de)
English (en)
Other versions
EP0314994B1 (fr
Inventor
Wilfried Schlinkheider
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.)
Graco Verfahrenstechnik GmbH
Original Assignee
Kopperschmidt-Muller GmbH and Co KG
Boellhoff Verbindungstechnik 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
Application filed by Kopperschmidt-Muller GmbH and Co KG, Boellhoff Verbindungstechnik GmbH filed Critical Kopperschmidt-Muller GmbH and Co KG
Priority to AT88117547T priority Critical patent/ATE65296T1/de
Publication of EP0314994A1 publication Critical patent/EP0314994A1/fr
Application granted granted Critical
Publication of EP0314994B1 publication Critical patent/EP0314994B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
    • F04B9/135—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting elastic-fluid motors, each acting in one direction
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members

Definitions

  • the invention relates to a pump arrangement with a double pump which has two alternatingly delivering individual pumps, in which a single-directional, in particular pneumatic, axial piston motor which drives a reversing valve drives the individual pumps by means of its reciprocating piston rod, two fixedly arranged limit switch elements can each be actuated at the end of the engine stroke and an adjustment device for changing the pump stroke volume is provided.
  • piston is used here in its general meaning. It includes all forms of engine elements that axially drive the piston rod when pressurized. This includes not only rigid pistons that can be slid in the cylinder, but also pistons designed as a membrane or combined with them.
  • a pneumatic axial piston motor is arranged between the two individual pumps.
  • the end position valves are attached to the end walls of the engine cylinder arranges and are actuated by the piston shortly before it lies against the end wall.
  • the two limit switch elements designed as valves in turn control the reversing valve.
  • the pneumatic axial piston motor therefore has a constant stroke.
  • the piston rod carries along a displacement piston which is guided in a cylinder and which, during each pressure stroke, conveys pressure fluid from its displacement into a working space delimited by an axially movable pump element, namely a membrane.
  • a liquid container is provided, which is connected to the displacement at least at the end of the suction stroke by means of a valve.
  • the valve is formed in that the end face of the displacer covers a control opening in the cylinder wall.
  • a pneumatic axial piston motor with a constant stroke actuates two double pumps, the actuating rods of which can be taken from the motor piston rod via a coupling piece.
  • the actuating rod of a double pump consists of two sections which are connected to one another via a clamping device, so that the axial distance between the two rod sections is changed symmetrically to one another by turning the clamping sleeve.
  • the dead travel that each displacement piston has to travel through until the control opening in the housing-fixed cylinder is overridden, which leads to an equally large change in the stroke volume in both individual pumps leads. If the stroke volume is adjusted to lower values, the drive power is periodically fluctuating unevenly distributed among the pumps working in parallel.
  • the invention is based on the object of specifying a pump arrangement of the type described at the outset which is suitable in particular for the conveyance of two or more components and with stepless stroke adjustment, in which no dead paths promoting the pulsation have to be traversed.
  • the piston rod is divided into two sections each associated with a single pump, the axial distance can be changed by means of the adjusting device, that each section is connected to an actuating element which is each assigned to one of the two limit switch elements and this each on The end of the engine stroke corresponding to the suction stroke of the associated single pump is actuated, and that the axial piston engine has two pistons, each connected to a piston rod section, which are located in the region of an end face area of the engine displacement when the associated limit switch element is actuated.
  • the respective stroke volume of the two individual pumps is determined by the stroke of the axial piston motor. While the pistons of the motor and the pump elements of the individual pumps assume reversing positions at the end of the pressure stroke, which are dependent on the stroke setting, they reach the same end position with each stroke setting at the end of the suction stroke. Therefore, the volume of the engine displacement to be filled with pressure medium, in particular compressed air, up to the beginning of the pressure stroke of the respective individual pump is constant regardless of the stroke setting and can be achieved by appropriate design of the dead space be kept to a minimum. This results in a favorable efficiency. Since the individual pumps do not have to travel through dead paths, their pressure strokes can be connected directly to one another, so that a pressure drop caused by an idle stroke is avoided. The pump arrangement is therefore particularly suitable for the continuous supply of spray devices.
  • axial adjustment There are various options for axial adjustment.
  • a symmetrical adjustment is preferred. This is achieved in a simple manner in that the adjusting device has a coupling piece which engages with opposing threads on the two piston rod sections and is provided with a torque engagement surface.
  • the pistons are supported in their end position on the end face of the engine displacement.
  • the dead space in the engine displacement can be kept particularly small.
  • the limit switch element is protected against overload.
  • the two pistons of the axial piston motor each delimit an engine displacement with their sides facing one another and each with a space under ambient pressure with their sides facing away from one another.
  • the two pistons of the axial piston motor each limit an engine displacement with their sides facing one another and a pump chamber of an individual pump with their sides facing away from each other.
  • the piston rod carries a displacement piston in a cylinder for each individual pump, which conveys pressure fluid from its displacement to a working space delimited by an axially movable pump element for each pressure stroke, and a fluid container is provided which is connected to the displacement by means of a valve at least at the end of the suction stroke is connected, one can arrange the cylinders for both displacement pistons fixed to the housing due to the end position of the displacement pistons, which is independent of the stroke setting.
  • the displacer guided in the cylinder bore is axially displaceable relative to the piston rod by a limited amount, that the drive of the displacer during the pressure stroke by contacting an end face of the piston rod on the end face of the displacer facing away from the displacement and the drive during the suction stroke by means of two oppositely directed driving surfaces on the piston rod and displacement piston, and that the valve is formed between the end faces of the piston rod and displacement piston lying against one another during the pressure stroke and is connected to the displacement space via at least one longitudinal channel running through the displacement piston.
  • a particularly useful application of the invention is the promotion of two or more components. This is done by at least one second, two alternately delivering single pumps having double pump, the axial piston motor passes through a stroke determined by stationary limit switch elements, and by a reversing valve circuit that operates the double pumps in the same or push-pull mode. In this way, with mix two or more components with high accuracy.
  • a preferred application is the supply of two-component paints to a spraying device.
  • the second double pump can have a fixed stroke or also an adjustable stroke. Any mixing ratio can be set in a wide range.
  • the synchronous reversal ensures that each stroke of one double pump corresponds to one stroke of the other double pump.
  • a common start of stroke can be achieved in a very simple manner in that two series connections, each with a limit switch element of each double pump, are provided for reversing the double pumps.
  • the reversal of the double pumps only takes place when both or all double pumps have reached their end position.
  • a common reversing valve can be provided for at least two double pumps. This simplifies the structure.
  • Three or more double pumps can also be provided and their limit switch elements connected in series.
  • the double pump 1 illustrated in FIG. 1 comprises two single pumps 2 and 3.
  • the single pump 2 has a pump chamber 4 which is delimited on the one hand by an end wall 5 and on the other hand by a piston 6 designed as a membrane.
  • the pump chamber 4 is connected to a suction line via a suction valve 7 and to a pressure line via a pressure valve 8.
  • the individual pump 3 has a pump chamber 9 which is delimited by an end wall 10 and a piston 11 designed as a membrane.
  • the pump chamber 9 is also connected to a suction valve 12 and a pressure valve 13.
  • the two individual pumps 2 and 3 are driven with the aid of an axial piston motor 14, which has two engine displacements 15 and 16, which are limited on the one hand by a housing wall 17 and 18 and on the other hand by the pistons 6 and 11, which act here as engine pistons .
  • the two pistons 6 and 11 are connected via a piston rod 19 which has a first section 20 which is connected to the piston 6 and a second section 21 which is connected to the piston 11.
  • the two sections are connected to one another by an adjusting device 22 in the form of a coupling piece which engages with two opposing threads 23 and 24 in the two piston sections 20 and 21 and with a torque engagement surface 25 is provided. After loosening two lock nuts 26 and 27, the axial distance between the two sections 20 and 2i can be changed.
  • a reversing valve 28 designed as a 5/2-way valve has a flat slide 29 which connects a compressed air inlet 30 optionally via a duct 31 to the engine displacement 15 or via a duct 32 to the engine displacement 16.
  • the respective other engine displacement is connected to the ambient air via the interior of this reversing valve 28 and an outlet 33.
  • the flat slide 29 is displaced by an actuating slide 34 when one of the two control pressure spaces 35 and 36 on the front side is supplied with compressed air.
  • Two fixed end position valves 37 and 38 are provided as end position switching elements.
  • An actuating element 39 for the end position valve 37 is firmly connected to the piston rod section 21
  • an actuating element 40 for the end position switching valve 38 is firmly connected to the piston rod section 20.
  • the position of the actuating elements 39 and 40 is such that, shortly after actuation of the end position valves, the associated piston 11 on an end face 41 or the piston 6 on an end face 42 of the respective engine displacement 15 or 16 for abutment or somewhat in front of it to hold can come.
  • the double pump 1 with the two single pumps 2 and 3 and the two-part motor 14 is illustrated schematically.
  • the two end position valves 37 and 38 are connected via control lines L1 and L2 to the control pressure chambers 35 and 36 of the reversing valve 28.
  • the inlet 44 feeds the two end position valves 37 and 38 with compressed air.
  • the axial piston motor 14 goes back and forth continuously, each pump 2 and 3 alternately delivering the same stroke volume.
  • the distance between the two pistons 6 and 11 can be changed.
  • the distance between the actuating elements 39 and 40 is changed at the same time. This leads to a variation in the engine and pump stroke, but the position of the pistons remains unchanged at the end of the suction stroke.
  • the first difference is that the axial piston motor has two rigid pistons 106 and 111. They limit the engine displacement 115 and 116 on the sides facing each other. The spaces 146 and 147 delimited by the opposite piston sides are connected to the atmosphere via channels 148 and 148 '.
  • the single pump 102 has a pump chamber which is delimited by a pump element 149 in the form of a membrane. This rests under the influence of a return spring 150 against a support plate 152 provided with holes 151.
  • a displacer piston 153 When a displacer piston 153 is pushed to the left by the piston rod 119 in the cylinder 154 fixed to the housing, pressure fluid is displaced from the displacement 155 into a working space 156 between the support plate 152 and the pump element 149.
  • the pump element 149 returns under the influence of the return spring 150 back to the illustrated resting position.
  • the displacer piston 153 has a circumferential seal 163 and an inner channel 157. In the rest position, it will have a seal with its spring 158 the end face 159 pressed against an end face 160 of the piston rod 119. There are stops 161 outside the piston rod. Therefore, when the piston rod 119 is pulled back further, a valve opens, which is formed between the end face 159 and the end face 160. Liquid can then flow from a liquid container 162 into the displacement 155 if this is necessary.
  • the piston rod 119 takes the displacer piston along by abutting the end faces 159 and 160.
  • the spring 158 is sufficient between two opposing driving surfaces in order to return the displacement piston 153. Further details can be found in DE-OS 35 42 926. Also in this context, it is of interest that the piston rod always assumes the same end position regardless of any stroke volume adjustment in which the valve between the end faces 159 and 160 is just slightly open is.
  • the double pump 101 is constructed symmetrically.
  • the parts of the second individual pump correspond to those of the first individual pump 102.
  • the double pump 101 has the single pumps 102 and 103, which are of the two-part axial piston benmotor 144 are driven.
  • the double pump 101a has the single pumps 102a and 103a, which are driven by the two-part axial piston motor 114a.
  • a reversing valve 128 is common to both double pumps.
  • the channel 131 therefore leads to one engine cubic capacity each and the channel 132 likewise leads to one engine cubic capacity each of the two double pumps 101 and 101a.
  • the end position valve 137 supplied with compressed air at the inlet 144 is connected in series with the end position valve 137a and only this series connection acts on the one control pressure chamber of the reversing valve 128.
  • the end position valves 138 and 138a in series with one another are with the other control pressure chamber of the reversing valve 128 connected. The consequence of this is that the switchover of both double pumps only takes place when the slower of the two single pumps working in parallel or the single pump covering the larger stroke has reached its end position. Then the changeover takes place, so that a common stroke of both double pumps then takes place again.
  • the series circuits therefore form a reversing valve circuit S in conjunction with the reversing valve 128 designed as a 5/2-way valve, which operates both double pumps in the same or push-pull mode.
  • the series connections each contain an end position valve of all double pumps. If each double pump is equipped with its own reversing valve, the series connection of FIG. 5 can still be used, in which case a series connection in each case acts on the similar control pressure spaces of both reversing valves.
  • electrical end positions can also be used as end position switching elements position switches are used, for example, when the reversing valves are actuated electromagnetically.
  • the series connection can then also be constructed electrically.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP88117547A 1987-11-04 1988-10-21 Dispositif de pompage avec double pompe Expired - Lifetime EP0314994B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88117547T ATE65296T1 (de) 1987-11-04 1988-10-21 Pumpanordnung mit doppelpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873737350 DE3737350A1 (de) 1987-11-04 1987-11-04 Pumpenanordnung mit doppelpumpe
DE3737350 1987-11-04

Publications (2)

Publication Number Publication Date
EP0314994A1 true EP0314994A1 (fr) 1989-05-10
EP0314994B1 EP0314994B1 (fr) 1991-07-17

Family

ID=6339719

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88117547A Expired - Lifetime EP0314994B1 (fr) 1987-11-04 1988-10-21 Dispositif de pompage avec double pompe

Country Status (3)

Country Link
EP (1) EP0314994B1 (fr)
AT (1) ATE65296T1 (fr)
DE (1) DE3737350A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2708050A1 (fr) * 1993-07-20 1995-01-27 Graco Inc Appareil de pompage à double membrane ayant un actionneur à ventouse à deux étapes.
GB2296534A (en) * 1993-07-20 1996-07-03 Graco Inc Air valve assembly for a double-diaphragm pump
WO1997046819A1 (fr) * 1996-06-03 1997-12-11 Ivan Rupert Soupape de commande d'air de travail
EP0903496A2 (fr) * 1997-09-18 1999-03-24 Yamada T.S. Co., Ltd. Commande de pression pour une pompe à membrane double
WO2006029898A1 (fr) * 2004-09-17 2006-03-23 Almatec Maschinenbau Gmbh Pompe a membrane destinee au transport de liquides
US7807118B2 (en) 2004-09-07 2010-10-05 Tristel Plc Decontamination system
US8642054B2 (en) 2004-09-07 2014-02-04 Tristel Plc Sterilant system
WO2019077207A1 (fr) * 2017-10-20 2019-04-25 Pimatic Oy Agencement de cylindre oscillant
US11286923B2 (en) 2018-04-02 2022-03-29 Graco Minnesota Inc. Reduced pressurization shift within diaphragm pump cavity

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010013108A1 (de) * 2010-03-26 2011-09-29 Promera Gmbh & Co. Kg Doppelmembranpumpe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1350149A (fr) * 1962-12-15 1964-01-24 Pompage de fluides
FR2161614A5 (fr) * 1971-11-16 1973-07-06 Warren Rupp Cy
DE2408006A1 (de) * 1974-02-20 1975-08-21 Wilhelm Schoeps Membranpumpe, insbesondere fuer laborzwecke
US4381180A (en) * 1981-07-13 1983-04-26 Sell John R Double diaphragm pump with controlling slide valve and adjustable stroke
GB2140097A (en) * 1983-05-19 1984-11-21 Kenneth Ian Fitzsimmonds Valve system
DE3542926A1 (de) * 1985-12-04 1987-06-11 Kopperschmidt Mueller & Co Pumpe
EP0226070A2 (fr) * 1985-12-13 1987-06-24 Böllhoff Verfahrenstechnik GmbH & Co. KG Dispositif de pompage pour débiter des quantités prédéterminées d'au moins deux composants

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1267093B (de) * 1956-05-29 1968-04-25 Weyburn Engineering Company Lt Membranmesspumpenaggregat
GB2059516B (en) * 1979-09-19 1983-09-07 Seeger Corp Two-component metering pumps
IL68647A (en) * 1983-05-10 1988-03-31 Tmb Fertilizer Pumps Diaphragm double pump installation

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1350149A (fr) * 1962-12-15 1964-01-24 Pompage de fluides
FR2161614A5 (fr) * 1971-11-16 1973-07-06 Warren Rupp Cy
DE2408006A1 (de) * 1974-02-20 1975-08-21 Wilhelm Schoeps Membranpumpe, insbesondere fuer laborzwecke
US4381180A (en) * 1981-07-13 1983-04-26 Sell John R Double diaphragm pump with controlling slide valve and adjustable stroke
GB2140097A (en) * 1983-05-19 1984-11-21 Kenneth Ian Fitzsimmonds Valve system
DE3542926A1 (de) * 1985-12-04 1987-06-11 Kopperschmidt Mueller & Co Pumpe
EP0226070A2 (fr) * 1985-12-13 1987-06-24 Böllhoff Verfahrenstechnik GmbH & Co. KG Dispositif de pompage pour débiter des quantités prédéterminées d'au moins deux composants

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2708050A1 (fr) * 1993-07-20 1995-01-27 Graco Inc Appareil de pompage à double membrane ayant un actionneur à ventouse à deux étapes.
GB2280479A (en) * 1993-07-20 1995-02-01 Graco Inc Pilot and main valve controlled double-diaphragm pump
GB2296534A (en) * 1993-07-20 1996-07-03 Graco Inc Air valve assembly for a double-diaphragm pump
GB2296534B (en) * 1993-07-20 1996-12-04 Graco Inc A two-stage air valve actuator for a double-diaphragm pump
GB2280479B (en) * 1993-07-20 1996-12-04 Graco Inc A two-stage air valve actuator for a double-diaphragm pump
WO1997046819A1 (fr) * 1996-06-03 1997-12-11 Ivan Rupert Soupape de commande d'air de travail
EP0903496A2 (fr) * 1997-09-18 1999-03-24 Yamada T.S. Co., Ltd. Commande de pression pour une pompe à membrane double
EP0903496A3 (fr) * 1997-09-18 1999-10-20 Yamada T.S. Co., Ltd. Commande de pression pour une pompe à membrane double
US7807118B2 (en) 2004-09-07 2010-10-05 Tristel Plc Decontamination system
US8080216B2 (en) 2004-09-07 2011-12-20 Tristel Plc Decontamination system
US8642054B2 (en) 2004-09-07 2014-02-04 Tristel Plc Sterilant system
WO2006029898A1 (fr) * 2004-09-17 2006-03-23 Almatec Maschinenbau Gmbh Pompe a membrane destinee au transport de liquides
WO2019077207A1 (fr) * 2017-10-20 2019-04-25 Pimatic Oy Agencement de cylindre oscillant
US11168714B2 (en) 2017-10-20 2021-11-09 Pimatic Oy Oscillation cylinder arrangement
US11286923B2 (en) 2018-04-02 2022-03-29 Graco Minnesota Inc. Reduced pressurization shift within diaphragm pump cavity

Also Published As

Publication number Publication date
DE3737350A1 (de) 1989-05-24
ATE65296T1 (de) 1991-08-15
DE3737350C2 (fr) 1990-03-29
EP0314994B1 (fr) 1991-07-17

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