EP1898093A1 - Dispositif de pompe - Google Patents

Dispositif de pompe Download PDF

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Publication number
EP1898093A1
EP1898093A1 EP07016273A EP07016273A EP1898093A1 EP 1898093 A1 EP1898093 A1 EP 1898093A1 EP 07016273 A EP07016273 A EP 07016273A EP 07016273 A EP07016273 A EP 07016273A EP 1898093 A1 EP1898093 A1 EP 1898093A1
Authority
EP
European Patent Office
Prior art keywords
diaphragm
control
pressure
pump head
pump
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
EP07016273A
Other languages
German (de)
English (en)
Other versions
EP1898093B1 (fr
Inventor
Bernd Ferk
Gunnar Gode
Henning Ladiges
Dirk Petersen
Uwe Schade
Wilfried Tille
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.)
BRAN and LUEBBE
SPX Flow Technology Germany GmbH
Original Assignee
BRAN and LUEBBE
Bran und Luebbe 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 BRAN and LUEBBE, Bran und Luebbe GmbH filed Critical BRAN and LUEBBE
Priority to DK09009999.5T priority Critical patent/DK2108838T3/da
Priority to EP09009999A priority patent/EP2108838B1/fr
Publication of EP1898093A1 publication Critical patent/EP1898093A1/fr
Application granted granted Critical
Publication of EP1898093B1 publication Critical patent/EP1898093B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B43/025—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
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • the invention relates to a pump device with a first diaphragm pump head and a second diaphragm pump head hydraulically coupled thereto.
  • piston pumps For the promotion or recirculation of viscous media with high solids content (suspensions) at high pressures of over 200 bar and high temperature of over 300 ° C piston pumps can be used. However, they are suitable for such an application only limited, since the solids fractions in a relatively short time destroy associated seals a piston and cause scoring on a surface of the piston.
  • plastic membranes for example made of PTFE
  • metal membranes is possible in principle, but technical requirements such as multi-layer membrane with fracture signaling and a design as a freely oscillating in the product space membrane with layer control can be realized only with great effort, see EP 0 085 725 A1 ,
  • the high pressure of the fluid to be pumped leads to another problem.
  • the piston rod force of reciprocating displacement pumps resulting from the product of pressure and area may require the use of very large pump drive assemblies which may be uneconomical for the required application in two respects. On the one hand, this entails considerably higher investment costs and, on the other hand, higher life-cycle costs, which can be characterized in particular by energy costs and expenditures for wear and spare parts.
  • the economic consideration of pump systems for recirculation with the boundary conditions mentioned above is of particular importance in processes for energy recovery from biological waste.
  • the pump device comprises a first diaphragm pump head with two or an integer multiple of two fluid delivery chambers and associated membranes, which are hydraulically coupled to a second diaphragm pump head, wherein the second diaphragm pump head has two additional fluid delivery chambers and associated additional membranes that of a double-acting piston can be driven via associated diaphragm control chambers, wherein in each case a refill valve is connected to the diaphragm control chambers and the membrane control chambers are temporarily acted upon by the Nach Glallventile with a membrane pressure which is greater than atmospheric pressure.
  • Such a pumping device is advantageous in that, at a time when the refill valves top up the diaphragm control chambers with a control fluid to compensate for unavoidable leakage of the control fluid, a short-term pressure drop in the diaphragm control chambers, which has hitherto been common in position-controlled diaphragms, up to atmospheric pressure through the diaphragm control chambers superimposed diaphragm control pressure which is greater than the atmospheric pressure can be limited.
  • the pump device is configured such that the diaphragm control pressure corresponds approximately to a fluid pressure at the inlet of a fluid delivery chamber of the first diaphragm pump head.
  • This allows almost complete compensation of the described short-term pressure drop in the diaphragm control chamber of the second diaphragm pump head.
  • the drive unit for the piston only has to be designed for forces which correspond approximately to the pressure difference between the inlet and the outlet of a fluid delivery chamber of the first diaphragm pump head.
  • the membrane control pressure can preferably be adapted to the fluid pressure by means of a control loop with associated sensors and actuators. Especially with an electronic control circuit this allows an optimally coordinated Compensation of the described pressure drop and thus the prevention of pressure surges, which can exert a detrimental effect on the drive unit.
  • the membrane control pressure may be generated by a pump which is coupled to a respective container for a diaphragm control chamber, each container having one of the refill valves and each container is acted upon by the pump with a static back pressure.
  • the pump is permanently in operation.
  • the membrane control pressure can be generated by a controllable pump which feeds a pressure accumulator, which is in each case coupled to a container for a diaphragm control chamber.
  • the container serves as a refill reservoir in this case.
  • the pump is only in operation when a predetermined lower limit pressure in the accumulator is exceeded. The pump then operates until an upper limit pressure is reached again in the accumulator (two-step control).
  • a respective container as a refill reservoir of a control fluid for a diaphragm control chamber of the second diaphragm pump head, wherein each container an adjustable throttle device is connected downstream.
  • the pump can be constantly in operation, so that a continuous circulation of a control fluid is given.
  • the structure of the pumping device and its operation is relatively symmetrical when the piston is designed as a double-acting disc piston with opposing piston rods.
  • the piston surfaces on both sides of the disc piston have an identical size, so that during a suction stroke or pressure stroke in each case the same pressure change and the same volume displacement is generated.
  • the membranes of the first diaphragm pump head are each free-swinging metal membranes, due to the material metal, a fluid can be transported at high temperatures. Since the first diaphragm pump head and the second diaphragm pump head are coupled via lines with a control fluid, these lines can act as cooling sections.
  • the membranes of the second diaphragm pump head may be formed of a plastic, in particular PTFE, so that none There is a risk that these plastic membranes show a significant flow because of too high a temperature.
  • the membranes of the second diaphragm pump head each have a multi-layered design and are provided with a position control and breakage signaling, the safety during conveying of the fluid can be increased.
  • An even higher level of safety is achieved if a conductivity or viscosity sensor is provided within the diaphragm control chambers of the first diaphragm pump head. Should a metal diaphragm break in the first diaphragm pump head, the fluid to be delivered could enter the adjacent diaphragm control chambers, so that a mixing of delivery fluid and control fluid would occur. Such mixing may alter the electrical conductivity or viscosity of the mixture as compared to the values of the control fluid so that the sensor can detect a break in a metal membrane.
  • the hydraulic coupling between the first diaphragm pump head and the second diaphragm pump head may be by means of control fluids comprising water or oil.
  • control fluids comprising water or oil.
  • oil for example, a special heat transfer oil can be used when the pumping device is used to convey a fluid at high temperatures.
  • the bulging of the membrane 3 is effected by the application of a pressure in the first diaphragm control chamber 5. If there is applied by dp higher pressure, there is a pressure p1 + dp at the pressure valve 62, with which the fluid is transported to the discharge line 63.
  • the pressure p1 + dp is provided by a first conduit 13 from a second diaphragm pump head 8.
  • This has a second membrane 9, which separates a second fluid delivery chamber 10 from a second diaphragm control chamber 11.
  • the second fluid delivery chamber 10 is coupled to the first diaphragm control chamber 5 by a first control fluid 12.
  • this first control fluid 12 is passed through the first line 13 to the first diaphragm control chamber 5, so that the first diaphragm 3 bulges.
  • Such a displacement of the first control fluid 12 is achieved by means of a piston 15, which exerts a stroke, which is directed downward in the embodiment shown in Fig. 1.
  • the stroke movement of the disk piston 31 in a direction pointing downwards in the embodiment shown in FIG. 1 is effected by a pump drive unit 51 by means of a first piston rod 33.
  • a second piston rod 35 is arranged opposite to the first piston rod 33.
  • the disk piston 31 is constructed symmetrically, so that on both opposite end faces of the disk piston 31, the same area is present. This has the consequence that in a piston stroke in the lower piston chamber 32, the same amount of pressure and volume change is achieved as in a piston stroke in an opposite upper piston chamber 34th
  • the upper piston chamber 34 is part of a third diaphragm control chamber 17 which is separated from a third fluid delivery chamber 19 by a third diaphragm 18.
  • the transfer medium used is a third control fluid 16 in the third diaphragm control chamber 17.
  • the pressure p1 alternately across the membranes 3 and 24, the control fluids 12 and 21, the membranes 9 and 18 and the control fluids 14 and 16 respectively on the piston chamber 32 and 34 executing the suction stroke transfer.
  • a short-term pressure drop to atmospheric pressure takes place in the respective diaphragm control chamber.
  • a pressure p2 is then superimposed on the pressure present in the diaphragm control chambers 11 and 17, so that the pressure reduction can be compensated.
  • the pressure p2 is provided by a pump 50 via a supply line 36 to the containers 37 and 39. In the case of the refilling process controlled by the membrane position, the pressure p2 is forwarded into the membrane control chambers 11 and 17. Excess control fluid is discharged via a vent valve 42 and 44 into a container 41 and 43, respectively, and conducted by means of a return line 53 into a control fluid reservoir 52.
  • the upper piston space 34 is increased, so that the third diaphragm 18 is compressed.
  • This also increases the volume of the third fluid delivery chamber 19, which is coupled via a fourth control fluid 21 and the second conduit 22 to a fourth diaphragm control chamber 23.
  • the fourth diaphragm control chamber 23 is located in the embodiment shown in FIG. 1 in the first diaphragm control head 2 and is separated by a fourth diaphragm 24 from a fourth fluid conveying chamber 25.
  • This structure is a mirror image of the structure with the first membrane 3, the first fluid conveying chamber 4 and the first diaphragm control chamber 5.
  • the volume of the fourth fluid delivery chamber 25 is increased, so that a suction or a fluid supply via the inlet opening 26 takes place with the suction valve 64. If the disc piston is moved in an upward stroke, the conditions described above are reversed. Then, the fourth fluid delivery chamber 25 conveys a fluid through an outlet port 28 by means of a vent valve 65 into a discharge line 63, while the first fluid delivery chamber 4 is filled.
  • the first membrane 3 and fourth membrane 24 are free-swinging metal membranes. On a multi-layer design and a membrane layer control can be omitted. A check as to whether a breakage of a metal membrane has occurred can be made indirectly by means of a conductivity or viscosity sensor 29 or 30. At a break of e.g. the membrane 3, there is a mixing of the fluids in the first fluid conveying space 4 and the first diaphragm control chamber 5, so that the electrical conductance or the viscosity changes, which can be detected by the sensors 29 or 30.
  • the third diaphragm 18 is compressed in the pump device in the second diaphragm pump head 8 during a suction stroke of the disc piston 31 in such a way that it reaches its rear end, the pressure in the third diaphragm control chamber 17 can drop to below or below the atmospheric pressure, as mentioned above , This is undesirable, since in this case a significant increase in the thrust force of the piston 15 occurs abruptly and the pump drive unit is heavily loaded. In the case of the pump device according to the invention, this can be avoided by the permanent pressurization with p2, which corresponds approximately to p1, via the containers 37 and 39.
  • the second diaphragm pump head 8 for the respective second 9 and third diaphragm 18 has a separate diaphragm position control, as described in US Pat EP 0 085 725 A1 is disclosed.
  • the respective refill valves 38 and 40 are replaced by a spring-mounted control plunger, which has a region with a conical surface screwed into its circumferential surface, and a tumbling rod operatively connected therewith, which in turn releases or blocks a spring-loaded refill valve.
  • a spring-mounted support plate secured against falling out in the direction of the respective diaphragm 18 or 9 and provided with passage openings for the respective control fluid 16 or 14 is arranged, which is in operative connection with the control tappet.
  • Has a loss give the control fluid 16 and 14, so shifts the respective towards the diaphragm control chamber 17 and 11 directed end position of the diaphragm 18 and 9, so that the support plate against the spring force supporting them and against the plunger supporting spring force is moved.
  • the movement of the support plate thus moves the control plunger, so that its conical peripheral region releases the tumbler, which, for example, falls by gravity in the direction of the control plunger longitudinal axis.
  • a spring force the tumbler in the direction of the control plunger is released by the tumbler, so that due to the pressure prevailing in the diaphragm control chamber 17 and 11 negative pressure, the refill is opened against the supporting spring force and the control fluid 16 and 14 can flow into the respective diaphragm control chamber 17 and 11 respectively.
  • the previously shifted end position of the affected membrane moves back 18 or 9 in the correct end position and thus again releases the support plate which releases the control plunger and thus the tumbler bar pushes back into the blocking position, whereby the valve is locked, which is also closed by the pressure balance due to its supporting spring again.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Eye Examination Apparatus (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Polarising Elements (AREA)
  • Fluid-Driven Valves (AREA)
  • Seal Device For Vehicle (AREA)
EP07016273A 2006-09-04 2007-08-20 Dispositif de pompe Active EP1898093B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DK09009999.5T DK2108838T3 (da) 2006-09-04 2007-08-20 Pumpeindretning
EP09009999A EP2108838B1 (fr) 2006-09-04 2007-08-20 Dispositif de pompe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006041420A DE102006041420A1 (de) 2006-09-04 2006-09-04 Pumpenvorrichtung

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP09009999A Division EP2108838B1 (fr) 2006-09-04 2007-08-20 Dispositif de pompe

Publications (2)

Publication Number Publication Date
EP1898093A1 true EP1898093A1 (fr) 2008-03-12
EP1898093B1 EP1898093B1 (fr) 2009-08-05

Family

ID=38691113

Family Applications (2)

Application Number Title Priority Date Filing Date
EP07016273A Active EP1898093B1 (fr) 2006-09-04 2007-08-20 Dispositif de pompe
EP09009999A Active EP2108838B1 (fr) 2006-09-04 2007-08-20 Dispositif de pompe

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP09009999A Active EP2108838B1 (fr) 2006-09-04 2007-08-20 Dispositif de pompe

Country Status (8)

Country Link
US (2) US8360750B2 (fr)
EP (2) EP1898093B1 (fr)
JP (2) JP5221085B2 (fr)
AT (2) ATE547631T1 (fr)
CA (1) CA2599949C (fr)
DE (3) DE102006041420A1 (fr)
DK (2) DK2108838T3 (fr)
ES (1) ES2331030T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2154371A1 (fr) 2008-08-14 2010-02-17 Bran + Lübbe GmbH Dispositif de pompe
DE202008010872U1 (de) 2008-08-14 2010-02-25 Bran+Luebbe Gmbh Pumpenvorrichtung

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US8955491B2 (en) * 2005-03-09 2015-02-17 Merton W. Pekrul Rotary engine vane head method and apparatus
US8197231B2 (en) 2005-07-13 2012-06-12 Purity Solutions Llc Diaphragm pump and related methods
EP2531729B1 (fr) * 2010-02-02 2020-03-04 Dajustco Ip Holdings Inc. Pompe à diaphragme avec système de commande de fluide hydraulique
US9610392B2 (en) 2012-06-08 2017-04-04 Fresenius Medical Care Holdings, Inc. Medical fluid cassettes and related systems and methods
DE102013207193A1 (de) * 2013-04-22 2014-10-23 Robert Bosch Gmbh Mikrohydraulisches System, insbesondere zum Einsatz in planaren Mikrofluidiklaboren
CN103277289A (zh) * 2013-05-10 2013-09-04 北京京城压缩机有限公司 一种具有单缸体双缸盖的隔膜式压缩机集成缸体部件
US9845794B2 (en) 2013-10-08 2017-12-19 Ingersoll-Rand Company Hydraulically actuated diaphragm pumps
EP3115607B1 (fr) * 2015-07-10 2018-02-21 J. Wagner AG Pompe a double membrane
US12004329B1 (en) * 2017-08-28 2024-06-04 Equinix, Inc. Data center refrigeration system
KR102167568B1 (ko) * 2020-03-11 2020-10-20 톈진 나가르 메커니컬 인더스트리 리미티드 컴퍼니 고압 플런저 방식 더블 다이아프램 펌프
WO2021211463A1 (fr) * 2020-04-13 2021-10-21 S.P.M. Flow Control, Inc. Système de pompage ayant des blocs vannes distants
KR20230101838A (ko) * 2020-11-09 2023-07-06 피디씨 머신즈 인크. 유압 구동식 다이어프램 컴프레서 시스템
US11867169B2 (en) 2021-11-08 2024-01-09 Pdc Machines, Inc. High-throughput diaphragm compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3630642A (en) * 1970-02-03 1971-12-28 Du Pont Diaphragm pump
EP0011022A1 (fr) * 1978-10-27 1980-05-14 COMMISSARIAT A L'ENERGIE ATOMIQUE Etablissement de Caractère Scientifique Technique et Industriel Pompe équipée d'un système amortisseur de vibrations
EP0085725A1 (fr) * 1982-02-05 1983-08-17 Bran & Lübbe GmbH Pompe à membrane entraînée par un piston

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2154371A1 (fr) 2008-08-14 2010-02-17 Bran + Lübbe GmbH Dispositif de pompe
DE202008010872U1 (de) 2008-08-14 2010-02-25 Bran+Luebbe Gmbh Pumpenvorrichtung

Also Published As

Publication number Publication date
ES2331030T3 (es) 2009-12-18
US20130017101A1 (en) 2013-01-17
ATE547631T1 (de) 2012-03-15
US20080056916A1 (en) 2008-03-06
CA2599949A1 (fr) 2008-03-04
ATE438801T1 (de) 2009-08-15
EP2108838B1 (fr) 2012-02-29
DK2108838T3 (da) 2012-06-25
JP5629796B2 (ja) 2014-11-26
DK1898093T3 (da) 2009-09-14
EP1898093B1 (fr) 2009-08-05
JP2013137031A (ja) 2013-07-11
JP2008064096A (ja) 2008-03-21
US8360750B2 (en) 2013-01-29
DE102006041420A1 (de) 2008-03-20
JP5221085B2 (ja) 2013-06-26
DE502007001229D1 (de) 2009-09-17
CA2599949C (fr) 2016-03-15
DE202007019423U1 (de) 2012-06-12
EP2108838A1 (fr) 2009-10-14

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