EP2108838B1 - Pumpenvorrichtung - Google Patents

Pumpenvorrichtung Download PDF

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Publication number
EP2108838B1
EP2108838B1 EP09009999A EP09009999A EP2108838B1 EP 2108838 B1 EP2108838 B1 EP 2108838B1 EP 09009999 A EP09009999 A EP 09009999A EP 09009999 A EP09009999 A EP 09009999A EP 2108838 B1 EP2108838 B1 EP 2108838B1
Authority
EP
European Patent Office
Prior art keywords
diaphragm
pressure
pump
pump head
diaphragm control
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.)
Active
Application number
EP09009999A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2108838A1 (de
Inventor
Bernd Ferk
Gunnar Gode
Hennig 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.)
SPX Flow Technology Germany GmbH
Original Assignee
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 und Luebbe GmbH filed Critical Bran und Luebbe GmbH
Publication of EP2108838A1 publication Critical patent/EP2108838A1/de
Application granted granted Critical
Publication of EP2108838B1 publication Critical patent/EP2108838B1/de
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 diaphragm pump head and a hydraulically coupled downstream pump head.
  • piston pumps For pumping or recirculation of viscous media with high solids content (suspensions) at high pressures of over 200 bar and high temperatures 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 position control can be realized only with great effort, see EP 0 085 725 A1 , the next state of the art.
  • a diaphragm pump operates as an upstream pulsator, which operates via a pipeline serving as a cooling line, the working valves in the downstream remote valve head of the pump by means of the fluid to be delivered.
  • This ensures that the diaphragm pump can operate in the uncritical low-temperature range up to approx. 150 ° C.
  • the disadvantage is that possible solids content of the fluid to be pumped can clog the pipe between the upstream pulsator and the remote valve head and thus the conveying effect is impaired.
  • the pump device comprises a diaphragm pump head and a downstream pump head with two or an integer multiple of two fluid delivery chambers, which are hydraulically coupled to the diaphragm pump head for driving the downstream pump head, the diaphragm pump head having two fluid delivery chambers and two associated membranes that from 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 diaphragm control chambers are temporarily acted upon by the Nach Glallventile with a diaphragm control pressure which is greater than atmospheric pressure.
  • Such a pumping device is advantageous in that, at a time when the refill valves are replenishing the diaphragm control chambers with a control fluid to compensate for unavoidable leakage of the control fluid, a more common approach has heretofore been with position controlled diaphragms short-term pressure drop in the diaphragm control chambers can be limited up to atmospheric pressure by the superimposed diaphragm control pressure, which is greater than the atmospheric pressure.
  • the pump device By using the pump device according to the invention it is achieved that a movement of the piston is possible at any time with a lower force than in solutions in the prior art, so that a delivery pressure alternately in the respective diaphragm control chambers of the diaphragm pump head and from there to the downstream pump head (remote Valve-Head) can be passed to transport fluid through the downstream pump head.
  • a delivery pressure alternately in the respective diaphragm control chambers of the diaphragm pump head and from there to the downstream pump head (remote Valve-Head) can be passed to transport fluid through the downstream pump head.
  • the total pressure in the downstream pump head for conveying the fluid may be relatively high, it is possible to pump with a relatively small force exerted on the piston and thus generated pressure difference. This creates a situation as if the piston would exert the pressure increase directly in the downstream pump head.
  • the piston can be driven by a drive unit, which can be designed for much lower forces than in previously known solutions, so that
  • the pump device is designed such that the diaphragm control pressure corresponds approximately to a fluid pressure at the inlet of a fluid delivery chamber of the downstream pump head.
  • This allows almost complete compensation of the described short-term pressure drop in the diaphragm control chamber of the diaphragm pump head.
  • the drive unit for the piston only needs to be designed for forces which approximately the pressure difference between the inlet and the outlet of a fluid delivery chamber of the downstream pump head correspond.
  • the membrane control pressure can preferably be adapted to the fluid pressure by means of a control loop with associated sensors and actuators. Particularly in the case of an electronic control circuit, this enables 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).
  • each container is an adjustable throttle device is 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 downstream pump head is a second diaphragm pump head
  • the membranes of the second diaphragm pump head are each free-swinging metal membranes
  • a fluid can be transported at high temperatures.
  • the second diaphragm pump head and the first diaphragm pump head are coupled via lines with a control fluid, these lines can act as cooling sections.
  • the membranes of the first diaphragm pump head may be formed from a plastic, in particular PTFE, so that there is no danger that these plastic membranes will show significant flow because of too high a temperature.
  • the membranes of the first diaphragm pump head each have a multi-layered design and are provided with a position control and a break signal, 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 second diaphragm pump head. Should a metal diaphragm break in the second diaphragm pump head, the fluid to be pumped could the adjacent diaphragm control chambers pass, so that a mixing of conveying 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 downstream pump head and the diaphragm pump head can be done 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.
  • a pump device 1 with a downstream pump head 2 and a diaphragm pump head 8 is shown.
  • the downstream pump head 2 has a first diaphragm 3, which separates a first fluid conveying chamber 4 from a first diaphragm control chamber 5.
  • a fluid to be conveyed through the first fluid conveying space 4 is supplied to an inlet port 6 with a suction valve 61 through a supply line 60 in which a fluid pressure p1 prevails (see arrow 7).
  • the fluid can be transported at a bulge of the first membrane 3 through the first fluid conveying space 4 to a pressure valve 62 at one end of the fluid conveying space 4.
  • the bulging of the membrane 3 is carried out by applying a pressure in the first diaphragm control chamber 5. If there is applied to dp higher pressure, is Pressure valve 62, a pressure p1 + dp before, with the fluid to the discharge line 63 is transported.
  • 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 at the in Fig. 1 illustrated embodiment is directed downwards.
  • a second control fluid 14 present in the second diaphragm control chamber 11 serves as the transmission medium for the volume change in an associated lower piston chamber 32.
  • the second diaphragm control chamber 11 extends as far as a disk piston 31 of the piston 15, so that the lower piston chamber 32 forms part of the second diaphragm control chamber 11.
  • the lifting movement of the disc piston 31 in a direction that in the in Fig. 1 shown embodiment 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 via the membranes 3 and 24, the control fluids 12 and 21, the membranes 9 and 18 and the control fluids 14 and 16 each transmitted to the suction stroke exporting piston chamber 32 and 34 respectively.
  • 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 at in Fig. 1 illustrated embodiment in the downstream pump head 2 and is separated by a fourth diaphragm 24 from a fourth fluid conveying space 25.
  • This construction is a mirror image of the structure with the first membrane 3, the first fluid delivery chamber 4 and the first diaphragm control chamber 5.
  • 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 pressure in the third diaphragm control space 17 may drop to or below the atmospheric pressure. 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 diaphragm pump head 8 for the respective second 9 and third diaphragm 18, a separate membrane layer control, as shown in the 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 plunger. If there has been a loss of the control fluid 16 or 14, then the respective end position of the membrane 18 or 9 directed in the direction of the diaphragm control chamber 17 or 11 shifts so that the support plate counteracts the spring force supporting it and against the plunger 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 spring force supporting them 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 rod again pushes back into the blocking position, whereby the valve is locked, which also by the pressure balance due to its supporting spring again is closed.
  • the double-acting piston 15 outside the diaphragm pump head 8.
  • the piston 15 is arranged with the disc piston 31 and the piston rods 33 and 35 in a separate from the diaphragm pump head 8 control fluid-tight housing, which includes the piston 15 receiving piston chambers 32 and 34 and flexible or installed lines for the control fluid 16 and 14. These lines connect the respective piston chambers 32 and 34 with the diaphragm control chambers 16 and 11th

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  • 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)
EP09009999A 2006-09-04 2007-08-20 Pumpenvorrichtung Active EP2108838B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006041420A DE102006041420A1 (de) 2006-09-04 2006-09-04 Pumpenvorrichtung
EP07016273A EP1898093B1 (de) 2006-09-04 2007-08-20 Pumpenvorrichtung

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP07016273.0 Division 2007-08-20
EP07016273A Division EP1898093B1 (de) 2006-09-04 2007-08-20 Pumpenvorrichtung

Publications (2)

Publication Number Publication Date
EP2108838A1 EP2108838A1 (de) 2009-10-14
EP2108838B1 true EP2108838B1 (de) 2012-02-29

Family

ID=38691113

Family Applications (2)

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

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP07016273A Active EP1898093B1 (de) 2006-09-04 2007-08-20 Pumpenvorrichtung

Country Status (8)

Country Link
US (2) US8360750B2 (da)
EP (2) EP2108838B1 (da)
JP (2) JP5221085B2 (da)
AT (2) ATE547631T1 (da)
CA (1) CA2599949C (da)
DE (3) DE102006041420A1 (da)
DK (2) DK2108838T3 (da)
ES (1) ES2331030T3 (da)

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Also Published As

Publication number Publication date
CA2599949A1 (en) 2008-03-04
ATE438801T1 (de) 2009-08-15
DE102006041420A1 (de) 2008-03-20
DE202007019423U1 (de) 2012-06-12
JP5629796B2 (ja) 2014-11-26
EP2108838A1 (de) 2009-10-14
CA2599949C (en) 2016-03-15
JP5221085B2 (ja) 2013-06-26
JP2013137031A (ja) 2013-07-11
ES2331030T3 (es) 2009-12-18
ATE547631T1 (de) 2012-03-15
DK1898093T3 (da) 2009-09-14
JP2008064096A (ja) 2008-03-21
US20130017101A1 (en) 2013-01-17
EP1898093A1 (de) 2008-03-12
EP1898093B1 (de) 2009-08-05
US8360750B2 (en) 2013-01-29
DE502007001229D1 (de) 2009-09-17
US20080056916A1 (en) 2008-03-06
DK2108838T3 (da) 2012-06-25

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