US20130209280A1 - Membrane Pump Having an Inertially Controlled Leakage Compensation Valve - Google Patents

Membrane Pump Having an Inertially Controlled Leakage Compensation Valve Download PDF

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Publication number
US20130209280A1
US20130209280A1 US13/818,119 US201113818119A US2013209280A1 US 20130209280 A1 US20130209280 A1 US 20130209280A1 US 201113818119 A US201113818119 A US 201113818119A US 2013209280 A1 US2013209280 A1 US 2013209280A1
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US
United States
Prior art keywords
pressure
hydraulic chamber
closing body
working fluid
leakage compensation
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
US13/818,119
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English (en)
Inventor
Horst Fritsch
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.)
Prominent GmbH
Original Assignee
Prominent Dosiertechnik 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 Prominent Dosiertechnik GmbH filed Critical Prominent Dosiertechnik GmbH
Assigned to PROMINENT DOSIERTECHNIK GMBH reassignment PROMINENT DOSIERTECHNIK GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FRITSCH, HORST
Publication of US20130209280A1 publication Critical patent/US20130209280A1/en
Assigned to PROMINENT GMBH reassignment PROMINENT GMBH CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: PROMINENT DOSIERTECHNIK GMBH
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
    • 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
    • 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
    • F04B43/0009—Special features
    • F04B43/0081—Special features systems, control, safety measures
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • Membrane pumps generally comprise a pumping chamber separated from a hydraulic chamber by a membrane, wherein the pumping chamber is connected to a suction connection and a pressure connection.
  • a pulsating working fluid pressure can be applied to the hydraulic chamber, which can be filled with working fluid.
  • the pulsating working fluid pressure brings about a pulsating movement of the membrane, whereupon the volume of the pumping chamber expands and contracts periodically.
  • pumping medium can be sucked in via the suction connection, which is connected to the pumping chamber via a respective non-return valve, when the volume of the pumping chamber is expanded, and discharged under pressure via the pressure connection, which is also connected to the pumping chamber by means of a respective non-return valve, when the volume of the pumping chamber contracts.
  • the membrane separates the medium to be pumped from the drive, whereupon on the one hand the drive is protected from damage caused by the pumping medium and on the other hand, the pumping medium is also protected from damage, for example contamination, caused by the drive.
  • the pulsating working fluid pressure is usually produced by means of a movable piston which is in contact with the working fluid.
  • the piston is moved to and fro in a cylindrical hollow element, whereby the volume of the hydraulic chamber is expanded and contracted, resulting in increasing and decreasing the pressure in the hydraulic chamber and, as a result, in movement of the membrane.
  • DE 1 034 030 proposed connecting the hydraulic chamber via an interposed valve, a so-called leakage compensation valve, to a reservoir of working fluid.
  • the leakage compensation valve usually comprises a closing body, for example in the form of a closing ball, which can move to and fro between a closed position in which the valve gate is closed and an open position in which the valve gate is open.
  • This closing body is biased into the closed position with the aid of a pressure element, for example a spring.
  • This pressure element is designed such that the closing body only moves in the direction of the open position when the pressure in the hydraulic chamber is lower than a set pressure p L .
  • the set pressure p L must be set such that during the suction stroke no fluid can get into the hydraulic chamber via the leakage compensation valve.
  • the leakage compensation valve should only let in any working fluid that might be missing at the end of the suction stroke when the piston is hardly moving.
  • the set pressure p L In order to prevent the leakage compensation valve from opening during this pressure pulse so that working fluid can flow into the hydraulic chamber, the set pressure p L must be set correspondingly low, which means that the pressure element of the leakage compensation valve must be relatively large in size.
  • the aim of the invention is to provide a membrane pump with a leakage compensation valve which reduces or even overcomes the disadvantages mentioned.
  • the aim of the present invention is to provide a method for dimensioning a leakage compensation valve which reduces or even overcomes the disadvantages mentioned.
  • the closing body moves by no more than 0.1 mm in the direction of the open position when a drop in pressure which lasts no longer than 1 millisecond occurs as a result of a pressure pulse in the hydraulic chamber.
  • the maximum pressure pulse might result in a drop in the pressure in the hydraulic chamber to 0 bar.
  • An example of the calculation of the mass of the closing body is provided below.
  • the pressure in the hydraulic chamber will not drop to 0 bar, but to a minimum pressure p min .
  • This minimum pressure p min is dependent on the process parameters, such as, for example, the static pressure at the pump suction connection, the speed of the piston and the volume of the hydraulic chamber and the pumping chamber.
  • p L is normally less than p min
  • p L is larger than p min .
  • the return spring of the leakage compensation valve can thus be made smaller, which significantly facilitates operation of the pump.
  • the aim defined above is achieved by providing that the mass of the closing body is selected such that the closing body moves by no more than 0.2 mm, preferably by no more than 0.1 mm in the direction of the open position when a drop in pressure which lasts no longer than 1 millisecond occurs as a result of a pressure pulse in the hydraulic chamber.
  • FIG. 1 a partial sectional view of a membrane pump of the prior art
  • FIG. 2 the profile of the pressure in the hydraulic chamber during the suction stroke
  • FIG. 3 a sectional view of a leakage compensation valve in accordance with one embodiment of the invention.
  • FIG. 1 shows the essential parts of a membrane pump in a partial sectional view.
  • the membrane pump comprises a membrane 1 , which separates the hydraulic chamber 8 from the pumping chamber 9 .
  • the pumping chamber 9 is connected to a suction connection and a pressure connection via respective non-return valves.
  • a pulsating working fluid pressure can be applied to the hydraulic chamber 8 with the aid of a piston 3 .
  • the membrane 1 is connected to a spring 10 installed in a mounting 13 , which ensures that the membrane is biased in the direction of the hydraulic chamber.
  • the pulsating pressure of the working fluid moves the membrane to and fro between the walls 4 and 7 , whereupon the volume of the pumping chamber expands and contracts.
  • the pumping fluid in the pumping chamber is discharged via the non-return valve at the pressure outlet.
  • the volume of the pumping chamber expands due to the backwards movement of the membrane 1 , pumping fluid is sucked in via the non-return valve out of the suction connection.
  • the periodic movement of the membrane periodically sucks in pumping fluid from the suction connection and discharges it via the pressure connection at a higher pressure.
  • the membrane is held between the clamping rims 11 , 12 .
  • the presence of the return spring 10 means that the membrane could bulge, as indicated by the dashed line 14 .
  • a leakage compensation valve 6 is provided, via which the hydraulic chamber 8 is connected to a working fluid reservoir 15 .
  • This leakage compensation valve comprises a small ball, which is urged into a valve seat by means of a spring. The spring of the leakage compensation valve 6 establishes the set pressure p L .
  • the ball of the leakage compensation valve lifts from the valve seat and additional working fluid can flow from the working fluid reservoir 15 , which is generally under atmospheric pressure (1 bar), into the hydraulic chamber 8 until the pressure in the hydraulic chamber 8 has risen above the set pressure p L , since then the spring of the leakage compensation valve 6 urges the ball back into the valve seat and thus closes off the valve gate.
  • FIG. 2 diagrammatically shows the pressure in the hydraulic chamber during the suction stroke as a function of time.
  • the pressure in the hydraulic chamber is approximately the same as the pressure with which the pump discharges the pumping medium from the delivery connection. This pressure is substantially higher than the static pressure of the suction line. It should be understood that the pressure in the hydraulic chamber is also determined by the return spring 10 . This pressure difference will not be considered below, however, as it is not relevant to the invention.
  • the set pressure p L of the leakage compensation valve is smaller than P min .
  • the set pressure p L can be selected to be substantially higher than p min , as long as p L is below a mean pressure p m in the hydraulic chamber.
  • the invention is based on the recognition that the pressure pulse occurs over only a very brief time interval ⁇ ts ⁇ 1 millisecond.
  • the mass of the closing body is selected to be sufficiently large such that such a pressure pulse only results in a lift of less than 0.2 mm or, preferably, less than 0.1 mm.
  • FIG. 3 A leakage compensation valve in accordance with the invention is shown in FIG. 3 .
  • This leakage compensation valve comprises a closing body 16 accommodated in a valve body 18 , which comprises a closing element 20 which closes a bore in the valve body 18 in the closed position, so that the line to the working fluid reservoir 19 is separated from the hydraulic chamber 8 .
  • the closing body is biased into the closed position with the aid of a spring element 17 , as shown in FIG. 3 .
  • the pressure of the working fluid in the working fluid reservoir, and thus also the pressure in the line 19 remain essentially constant.
  • the closing body 16 in the position shown in FIG. 3 is moved upwards, so that a connection is opened between the line 19 and the hydraulic chamber 8 .
  • the closing body moves by only 0.2 millimetres, the gap between the valve body 18 and the closing element 20 is not sufficient to discharge a significant quantity of working fluid through the line 19 into the hydraulic chamber.
  • ⁇ t is the duration of the pressure pulse and b is the acceleration of the closing body due to the pressure pulse.
  • the acceleration is calculated as follows:
  • the mass of the closing body has to be at least 17.5 g in order to prevent a movement of the closing body by more than 0.1 mm.
  • the method described may be further improved by considering that the pressure pulse generally does not result in a pressure drop to 0 bar, but only to a minimum pressure p min .
  • the difference p L ⁇ p min between the set pressure p L and the minimum pressure p min due to the pressure pulse can be used, whereupon the mass can be reduced still further.
  • the set pressure p L can be increased, whereupon the spring 17 can be made weaker, simplifying operation of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US13/818,119 2010-08-26 2011-08-15 Membrane Pump Having an Inertially Controlled Leakage Compensation Valve Abandoned US20130209280A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010039829A DE102010039829A1 (de) 2010-08-26 2010-08-26 Membranpumpe mit trägheitsgesteuertem Leckergänzungsventil
DE102010039829.2 2010-08-26
PCT/EP2011/064045 WO2012025423A1 (de) 2010-08-26 2011-08-15 Membranpumpe mit trägheitsgesteuertem leckergänzungsventil

Publications (1)

Publication Number Publication Date
US20130209280A1 true US20130209280A1 (en) 2013-08-15

Family

ID=44630450

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/818,119 Abandoned US20130209280A1 (en) 2010-08-26 2011-08-15 Membrane Pump Having an Inertially Controlled Leakage Compensation Valve

Country Status (10)

Country Link
US (1) US20130209280A1 (zh)
EP (1) EP2609332A1 (zh)
JP (1) JP5862903B2 (zh)
KR (1) KR20130138194A (zh)
CN (1) CN103154517B (zh)
BR (1) BR112013004584A2 (zh)
CA (1) CA2808388C (zh)
DE (1) DE102010039829A1 (zh)
RU (1) RU2573069C2 (zh)
WO (1) WO2012025423A1 (zh)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015031884A1 (en) * 2013-08-30 2015-03-05 Flow Control Llc. High viscosity portion pump
US20150267854A1 (en) * 2012-10-16 2015-09-24 Water Powered Technologies Limited Gas Spring Accumulator
WO2015188185A3 (en) * 2014-06-06 2016-03-10 Flow Control Llc. Single piston foundation bag-in-box (bib) pump
US9964105B2 (en) 2013-05-16 2018-05-08 Prominent Gmbh Diaphragm pump having position control
EP3460243A1 (de) * 2017-09-26 2019-03-27 ProMinent GmbH Membranpumpe mit einer funktionssicheren membranlagensteuerung

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014002720B4 (de) 2013-04-04 2023-10-12 Mann+Hummel Gmbh Pumpe zum Fördern eines Fluids
FR3012538B1 (fr) * 2013-10-30 2018-05-18 Dosatron International Pompe a membrane et dispositif a clapets pour une telle pompe
DE102016225512A1 (de) 2016-12-20 2018-06-21 Volkswagen Aktiengesellschaft Kraftstofftanksystem und Verfahren zur Prüfung der Dichtheit eines solchen Kraftstofftanksystems
CN113614373B (zh) * 2019-01-10 2023-06-09 Psg加利福尼亚公司 泄漏检测和容纳消声器系统
CN115405499B (zh) * 2021-05-27 2024-08-02 上海兴邺材料科技有限公司 隔膜泵或隔膜压缩机及控制方法和控制器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4494727A (en) * 1980-10-23 1985-01-22 Robert Bosch Gmbh Electrically controllable valve
US5655894A (en) * 1994-06-15 1997-08-12 Lewa Herbert Ott Gmbh & Co. Controlled prevention of premature snuffle valve actuation in high pressure membrane pumps

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DE1034030B (de) 1955-09-22 1958-07-10 Reiners Walter Dr Ing Membranpumpe fuer nicht schmierende und chemisch aggressive Fluessigkeiten, insbesondere zur Schaedlingsbekaempfung in der Landwirtschaft
US3680981A (en) * 1970-12-21 1972-08-01 Josef Wagner Pump and method of driving same
ATE10670T1 (de) * 1980-12-29 1984-12-15 Lewa Herbert Ott Gmbh + Co. Membranpumpe mit druckentlastet eingespannter membran.
US4365745A (en) * 1981-02-05 1982-12-28 Louis Beck Diaphragm pump
DE3446952A1 (de) * 1984-12-21 1986-07-10 Lewa Herbert Ott Gmbh + Co, 7250 Leonberg Membranpumpe mit umlaufspuelung
DE3546189A1 (de) * 1985-12-27 1987-07-02 Ott Kg Lewa Verfahren und vorrichtung zur durchflussmessung bei oszillierenden verdraengerpumpen
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DE4141670C2 (de) * 1991-12-17 1994-09-29 Ott Kg Lewa Hydraulisch angetriebene Membranpumpe mit Membranhubbegrenzung
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RU2079715C1 (ru) * 1994-05-06 1997-05-20 Акционерное общество открытого типа Рязанское научно-техническое акционерное предприятие "Нефтехиммашсистемы" Мембранный гидроприводной дозировочный насос
CN100371595C (zh) * 1999-11-12 2008-02-27 日机装株式会社 膜片型往复泵
DE10308421A1 (de) * 2003-02-27 2004-09-09 Leybold Vakuum Gmbh Kolbenpumpe, vorzugsweise Kolbenvakuumpumpe, mit Auslassventil
DE10322221B3 (de) * 2003-05-16 2005-01-27 Lewa Herbert Ott Gmbh + Co Leckageüberwachung im Hydraulikdruckraum einer Membranpumpe
RU38365U1 (ru) * 2004-01-30 2004-06-10 Подрезов Александр Владимирович Мембранный гидроприводной дозировочный насос
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Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4494727A (en) * 1980-10-23 1985-01-22 Robert Bosch Gmbh Electrically controllable valve
US5655894A (en) * 1994-06-15 1997-08-12 Lewa Herbert Ott Gmbh & Co. Controlled prevention of premature snuffle valve actuation in high pressure membrane pumps

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150267854A1 (en) * 2012-10-16 2015-09-24 Water Powered Technologies Limited Gas Spring Accumulator
US9556995B2 (en) * 2012-10-16 2017-01-31 Water Powered Technologies Limited Gas spring accumulator
US9964105B2 (en) 2013-05-16 2018-05-08 Prominent Gmbh Diaphragm pump having position control
WO2015031884A1 (en) * 2013-08-30 2015-03-05 Flow Control Llc. High viscosity portion pump
US10267303B2 (en) 2013-08-30 2019-04-23 Flow Control Llc. High viscosity portion pump
WO2015188185A3 (en) * 2014-06-06 2016-03-10 Flow Control Llc. Single piston foundation bag-in-box (bib) pump
US11592013B2 (en) 2014-06-06 2023-02-28 Flow Control LLC Single piston foundation bag-in-box (BIB) pump
EP3460243A1 (de) * 2017-09-26 2019-03-27 ProMinent GmbH Membranpumpe mit einer funktionssicheren membranlagensteuerung

Also Published As

Publication number Publication date
CA2808388C (en) 2018-02-20
JP2013536364A (ja) 2013-09-19
JP5862903B2 (ja) 2016-02-16
WO2012025423A1 (de) 2012-03-01
RU2013113209A (ru) 2014-10-10
CA2808388A1 (en) 2012-03-01
BR112013004584A2 (pt) 2016-09-06
RU2573069C2 (ru) 2016-01-20
KR20130138194A (ko) 2013-12-18
CN103154517B (zh) 2016-01-20
EP2609332A1 (de) 2013-07-03
DE102010039829A1 (de) 2012-03-01
CN103154517A (zh) 2013-06-12

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