US20130017101A1 - Pump device - Google Patents
Pump device Download PDFInfo
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- US20130017101A1 US20130017101A1 US13/624,388 US201213624388A US2013017101A1 US 20130017101 A1 US20130017101 A1 US 20130017101A1 US 201213624388 A US201213624388 A US 201213624388A US 2013017101 A1 US2013017101 A1 US 2013017101A1
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- United States
- Prior art keywords
- diaphragm
- piston
- pump device
- pump
- pressure
- 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.)
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Classifications
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- 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
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- 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 present invention relates to a pump device having a first diaphragm pump head and a second diaphragm pump head hydraulically coupled thereto.
- Piston pumps may be used to deliver and/or recirculate viscous media having a high proportion of solids (suspensions) at high pressures of greater than 200 bar and high temperatures of greater than 300° C.
- solids suspensions
- they are only suitable in a limited way for an application of this type, because the solid components destroy associated seals of a piston in a relatively short time and cause scoring on a surface of the piston.
- diaphragm pumps A possibility for avoiding these difficulties is to use diaphragm pumps.
- diaphragm pumps To implement delivery at the above-mentioned pressures, only designs having hydraulically driven diaphragms may be used. In turn, these may only be conceived for secure and interference-free operation in the cited temperature range with significant design and material technology outlay.
- plastic diaphragms made of PTFE for example, is not possible, because plastic begins to flow significantly at the cited high pressure and high temperature.
- metal diaphragms is possible in principle, but technical demands such as multilayered diaphragms having fracture signaling and an embodiment as a diaphragm oscillating freely in the product space having position control may only be implemented with great effort, see EP 0 085 725 A1.
- a diaphragm pump operates as an upstream pulsator, which actuates the operating valve in the downstream remote valve head of the pump with the aid of the fluid to be delivered via a pipeline acting as a cooling line.
- the diaphragm pump may operate in the noncritical low temperature range up to approximately 150° C.
- it is disadvantageous that possible solid components of the fluid to be delivered may clog the pipeline between the upstream pulsator and the remote valve head and thus impair the delivery effect.
- the high pressure of the fluid to be delivered results in a further problem.
- the piston rod force of oscillating displacement pumps which results from the product of pressure and area, requires the use of very large pump drive assemblies in certain circumstances, which may be uneconomical in two regards for the required application. Firstly, significantly higher investment costs and secondly higher life cycle costs are connected thereto, which may be particularly distinguished by energy costs and outlay for wearing and replacement parts.
- the economic consideration of pump systems for recirculation having the boundary conditions cited above is especially of very great significance in methods for energy reclamation from biological wastes.
- a first diaphragm pump head having two or an integral multiple of two fluid delivery chambers and diaphragms associated therewith, which are hydraulically coupled to a second pump head for driving the first diaphragm pump head
- the second pump head is a diaphragm pump head which has two additional fluid delivery chambers and two associated additional diaphragms, which are drivable by a double-acting piston, situated in the second diaphragm pump head, via associated diaphragm control chambers, and a refilling valve being connected to each of the diaphragm control chambers, and, using the refilling valves, the diaphragm control chambers being impinged temporarily, during the refilling procedure, which is controlled by the diaphragm position, by a diaphragm control pressure, which is greater than atmospheric pressure and less than the system pressure.
- the pump device comprises a first diaphragm pump head having two or an integral multiple of two fluid delivery chambers and diaphragms associated therewith, which are hydraulically coupled to a second diaphragm pump head, the second diaphragm pump head having two additional fluid delivery chambers and additional diaphragms associated therewith, which are drivable by a double-acting piston via associated diaphragm control chambers, a refilling valve being attached to each of the diaphragm control chambers and the diaphragm control chambers being temporarily impinged by a diaphragm pressure, which is greater than atmospheric pressure, using the refilling valves.
- Such a pump device is advantageous because at a time at which the refilling valve refills the diaphragm control chambers with a control fluid to compensate for unavoidable leakage of the control fluid, a brief pressure drop in the diaphragm control chambers down to atmospheric pressure, which has been typical up to this point in position-controlled diaphragms, for example, may be limited by the superimposed diaphragm control pressure, which is greater than the atmospheric pressure.
- a movement of the piston is possible at any time using a smaller force than in achievements of the object in the prior art, so that a delivery pressure may alternately be conducted into the particular diaphragm control chambers of the second diaphragm pump head and therefrom to the first diaphragm pump head to transport fluid through the first diaphragm pump head.
- the overall pressure in the first diaphragm pump head may be relatively high to deliver the fluid, it is possible to operate a pumping procedure using a relatively small force exerted on the piston and pressure differential thus generated. A situation thus arises as if the piston would exert the pressure increase directly in the first diaphragm pump head.
- the piston may be driven by a drive assembly which may be designed for much smaller forces than in achievements of the object known up to this point, so that a significantly more cost-effective delivery at high temperatures and pressures in the first diaphragm pump head is achieved.
- the pump device is preferably designed in such a way that the diaphragm control pressure approximately corresponds to a fluid pressure at the inlet of a fluid delivery chamber of the first diaphragm pump head. Therefore, the described brief pressure drop in the diaphragm control chamber of the second diaphragm pump head is nearly completely compensated for. In combination with a double-acting embodiment of the piston of the second diaphragm pump head, this has the result that the drive assembly for the piston only has to be designed for forces which approximately correspond to the pressure differential between the inlet and the outlet of a fluid delivery chamber of the first diaphragm pump head.
- the diaphragm control pressure may preferably be adapted to the fluid pressure by a control circuit having associated sensors and actuators.
- a control circuit having associated sensors and actuators.
- this allows an optimally tailored compensation of the described pressure drop and thus the prevention of pressure surges, which may exert a harmful reaction on the drive assemblies.
- the diaphragm control pressure may be generated by a pump which is coupled in each case to a container for a diaphragm control chamber, each container having one of the refilling valves and each container being impinged by a static stagnation pressure by the pump.
- the pump is permanently in operation.
- the diaphragm control pressure may be generated by a controllable pump which feeds a pressure accumulator which is coupled in each case to a container for a diaphragm control chamber.
- the container is used in this case as a refilling reservoir.
- the pump is only in operation when the pressure accumulator falls below a predefined lower limiting pressure. The pump then operates until an upper limit pressure is again reached in the pressure accumulator (two-point regulation).
- a container in each case as a refilling reservoir of a control fluid for a diaphragm control chamber of the second diaphragm pump head, an adjustable throttle device being connected downstream from each container.
- the pump may be continuously in operation, so that continuous circulation of a control fluid is provided.
- the construction of the pump device and its mode of operation are relatively symmetrical if the piston is implemented as a double-acting disk piston having diametrically opposite piston rods.
- the piston faces on both sides of the disk piston having identical sizes, so that during an intake stroke or pressure stroke, the same pressure change and the same volume displacement is generated in each case.
- the diaphragms of the first diaphragm pump head are each freely oscillating metal diaphragms, a fluid may be transported at high temperatures because of the metal material. Because the first diaphragm pump head and the second diaphragm pump head are coupled to a control fluid via lines, these lines may act as cooling lines. Therefore, in a preferred embodiment, the diaphragms of the second diaphragm pump head may be made of a plastic, in particular PTFE, so that there is no danger that these plastic diaphragms will display significant flowing because of too high temperatures.
- the security during delivery of the fluid may be increased. Still greater security is achieved if a conductivity or viscosity sensor is provided inside the diaphragm control chambers of the first diaphragm pump head. If a metal diaphragm in the first diaphragm pump head breaks, the fluid to be delivered may reach the neighboring diaphragm control chambers, so that mixing of delivery fluid and control fluid would occur. Mixing of this type may change the electrical conductivity or the viscosity of the mixture in comparison to the values of the control fluid, so that a fracture of a metal membrane may be detected using the sensor.
- the hydraulic coupling between the first diaphragm pump head and the second diaphragm pump head may occur using control fluids, which have water or oil.
- control fluids which have water or oil.
- special heat transfer oil may be used as the oil, if the pump device is used for delivering a fluid at high temperatures.
- FIG. 1 shows a schematic illustration of an embodiment of the pump device according to the present invention.
- FIG. 1 illustrates a pump device 1 having a first diaphragm pump head 2 and a second diaphragm pump head 8 .
- the first diaphragm pump head 2 has a first diaphragm 3 , which separates a first fluid delivery chamber 4 from a first diaphragm control chamber 5 .
- a fluid to be delivered by the first fluid delivery chamber 4 is fed by a supply line 60 , in which a fluid pressure p 1 exists (see arrow 7 ), to an inlet opening 6 having an intake valve 61 .
- the fluid may be transported by the first fluid delivery chamber 4 to a pressure valve 62 at one end of the fluid delivery chamber 4 .
- the membrane 3 bulges out due to the application of a pressure in the first diaphragm control chamber 5 . If a pressure which is higher by dp is applied there, a pressure p 1 +dp exists at the pressure valve 62 , using which the fluid is transported to the drain line 63 .
- the pressure p 1 +dp is provided through a first line 13 by a second diaphragm pump head 8 .
- This has a second diaphragm 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 conducted through the first line 13 to the first diaphragm control chamber 5 , so that the first diaphragm 3 bulges out.
- a displacement of the first control fluid 12 of this type is achieved using a piston 15 , which exerts a stroke, which is directed downward in the embodiment shown in FIG. 1 .
- a second control fluid 14 provided in the second diaphragm control chamber 11 is used as the transmission medium of the volume change in an associated lower piston chamber 32 .
- the second diaphragm control chamber 11 extends up to a disk piston 31 of the piston 15 , so that the lower piston chamber 32 is a part of the second diaphragm control chamber 11 .
- the stroke movement of the disk piston 31 in a direction which points downward in the embodiment shown in FIG. 1 is caused by a pump drive assembly 51 using a first piston rod 33 .
- a second piston rod 35 is situated diametrically opposite to the first piston rod 33 on the disk piston 31 . Therefore, the disk piston 31 is constructed symmetrically, so that the same area is provided on both diametrically opposite front faces of the disk piston 31 . This has the result that during a piston stroke into the lower piston chamber 32 , the same absolute value of a pressure and volume change is achieved as during a piston stroke up into a diametrically opposite upper piston chamber 34 .
- 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 volume of the upper piston chamber 34 enlarges, so that the third diaphragm 18 is contracted or compressed.
- a third control fluid 16 in the third diaphragm control chamber 17 is used as the transmission medium.
- a transport of a fluid conducted at a pressure p 1 into the first fluid delivery chamber 4 is achieved if a pressure p 1 +dp is transmitted into the first diaphragm control chamber 5 via the line 13 . Therefore, this pressure p 1 +dp must also exist in the second fluid delivery chamber 10 . This is only possible if such a pressure is built up in the second diaphragm control chamber 11 . In achievements of the object according to the prior art, it is typical for a drive assembly to exert this entire pressure p 1 +dp on one or two single-acting plunger pistons. In contrast, in the embodiment according to the present invention, this is no longer necessary. For this purpose, as is obvious from FIG.
- the pressure p 1 is alternately transmitted via the diaphragms 3 and 24 , the control fluids 12 and 21 , the diaphragms 9 and 18 , and the control fluids 14 and 16 to the particular piston chamber 32 or 34 executing the intake stroke. If the unavoidable leakage of the control fluids 14 and 16 is compensated for by the refilling valves 38 and 40 , which are actuated by the diaphragm position controller, a brief pressure reduction down to atmospheric pressure, which is required in principle, occurs in the particular diaphragm control chamber. In the pump device according to the present invention, a pressure p 2 is then superimposed on the pressure existing in the diaphragm control chambers 11 and 17 , so that the pressure reduction may be compensated for.
- the piston of the second diaphragm pump head is implemented as a double-acting piston and the pressure p 2 is approximately equal to p 1 , only enough force has to be exerted on the piston rod 33 using the pump drive assembly 51 so that the piston 15 generates a differential pressure dp.
- the pressure p 2 is provided by a pump 50 via a feed line 36 to the containers 37 and 39 .
- the pressure p 2 is relayed into the diaphragm control chambers 11 and 17 .
- Excess control fluid is drained via a ventilation valve 42 or 44 into a container 41 or 43 , respectively, and conducted using a return line 53 into a control fluid reservoir 52 .
- the upper piston chamber 34 is enlarged, so that the third membrane 18 is compressed. Therefore, the volume of the third fluid delivery chamber 19 also increases, which is coupled via a fourth control fluid 21 and the second line 22 to a fourth diaphragm control chamber 23 .
- the fourth diaphragm control chamber 23 is located in the first diaphragm control head 2 in the embodiment shown in FIG. 1 and is separated using a fourth diaphragm 24 from a fourth fluid delivery chamber 25 .
- This construction is mirror symmetric to the construction having first diaphragm 3 , first fluid delivery chamber 4 , and first diaphragm control chamber 5 .
- the volume of the fourth fluid delivery chamber 25 is also enlarged, so that suction and/or a fluid feed occurs via the image opening 26 having the intake valve 64 . If the disk piston is moved in a downwardly directed stroke, the conditions described above are reversed.
- the fourth fluid delivery chamber 25 delivers a fluid through an outlet opening 28 using a ventilation valve 65 into a drain line 63 , while the first fluid delivery chamber 4 is filled.
- the first diaphragm 3 and fourth diaphragm 24 are freely oscillating metal diaphragms.
- a multilayered embodiment and a diaphragm position controller may be dispensed with.
- a cheek as to whether a fracture of a metal diaphragm has occurred may be performed indirectly by a conductivity or viscosity sensor 29 or 30 .
- mixing of the fluids occurs in the first fluid delivery chamber 4 and first diaphragm control chamber 5 , so that the electrical conductivity or the viscosity changes, which may be detected by the sensors 29 or 30 .
- the pressure in the third diaphragm control chamber may drop to and/or below atmospheric pressure. This is undesirable because in this case a significant shear force increase of the piston 15 occurs suddenly and the pump drive assembly is strongly loaded. This may be avoided in the pump device according to the present invention by the permanent pressure impingement using p 2 , which approximately corresponds to p 1 , via the containers 37 and 39 .
- the second diaphragm pump head 8 has a separate diaphragm position controller in each case for the second diaphragm 9 and the third diaphragm 18 , as disclosed in EP 0 085 725 A1.
- the particular refilling valves 38 and 40 are replaced by a spring-loaded control plunger, which has an area having a conical face turned into its peripheral face, and a retention rod operationally linked thereto, which in turn releases or blocks a spring-loaded refilling valve.
- a spring-loaded support plate which is operationally linked to the control plunger, and which is secured against falling out in the direction of the particular diaphragm 18 or 9 and is provided with through openings for the particular control fluid 16 or 14 , is situated in the area of the diaphragm control chamber 17 or 11 , respectively. If a loss of the control fluid 16 or 14 has occurred, the final position of the diaphragm 18 or 9 directed in the direction toward the diaphragm control chamber 17 or 11 is displaced, so that the support plate is moved against the spring force which supports it and against the spring for supporting the plunger.
- control plate thus moves the control plunger, so that its conical peripheral area releases the retention rod, this rod falling in the direction of the control plunger longitudinal axis because of gravity, for example.
- a spring may also force the retention rod in the direction of the control plunger.
- the refilling valve is released by the retention rod, so that because of the partial vacuum existing in the particular diaphragm control chamber 17 or 11 , the refilling valve is opened against the spring force which supports it and the control fluid 16 or 14 may flow into the diaphragm control chamber 17 or 11 , respectively.
- the double-acting piston 15 is situated outside the second diaphragm pump head 8 .
- the piston 15 is situated with the disk piston 31 and the piston rods 33 and 35 in a control-fluid-tight housing separate from the diaphragm pump head 8 , which comprises the piston chambers 32 and 34 accommodating the piston 15 as well as flexible or installed lines for the control fluids 16 and 14 . These lines connect the particular piston chambers 32 and 34 to the diaphragm control chambers 16 and 11 .
Abstract
Description
- This application is a Continuation application of U.S. patent application Ser. No. 11/896,524 filed Sep. 4, 2007, which claims priority to German Patent Application No. 102006041420.9, filed Sep. 4, 2006, the disclosures of which are hereby incorporated by reference in their entirety.
- The present invention relates to a pump device having a first diaphragm pump head and a second diaphragm pump head hydraulically coupled thereto.
- Piston pumps may be used to deliver and/or recirculate viscous media having a high proportion of solids (suspensions) at high pressures of greater than 200 bar and high temperatures of greater than 300° C. However, they are only suitable in a limited way for an application of this type, because the solid components destroy associated seals of a piston in a relatively short time and cause scoring on a surface of the piston.
- A possibility for avoiding these difficulties is to use diaphragm pumps. To implement delivery at the above-mentioned pressures, only designs having hydraulically driven diaphragms may be used. In turn, these may only be conceived for secure and interference-free operation in the cited temperature range with significant design and material technology outlay.
- The use of plastic diaphragms made of PTFE, for example, is not possible, because plastic begins to flow significantly at the cited high pressure and high temperature. The use of metal diaphragms is possible in principle, but technical demands such as multilayered diaphragms having fracture signaling and an embodiment as a diaphragm oscillating freely in the product space having position control may only be implemented with great effort, see EP 0 085 725 A1.
- Up to this point, pumps having a so-called remote valve head have been used as a measure against the high temperature strain. In such a design, a diaphragm pump operates as an upstream pulsator, which actuates the operating valve in the downstream remote valve head of the pump with the aid of the fluid to be delivered via a pipeline acting as a cooling line. In this way, the diaphragm pump may operate in the noncritical low temperature range up to approximately 150° C. However, it is disadvantageous that possible solid components of the fluid to be delivered may clog the pipeline between the upstream pulsator and the remote valve head and thus impair the delivery effect.
- The high pressure of the fluid to be delivered results in a further problem. The piston rod force of oscillating displacement pumps, which results from the product of pressure and area, requires the use of very large pump drive assemblies in certain circumstances, which may be uneconomical in two regards for the required application. Firstly, significantly higher investment costs and secondly higher life cycle costs are connected thereto, which may be particularly distinguished by energy costs and outlay for wearing and replacement parts. The economic consideration of pump systems for recirculation having the boundary conditions cited above is especially of very great significance in methods for energy reclamation from biological wastes.
- It is therefore an object of the present invention to provide a pump device which may reliably and cost-effectively deliver viscose media having a high solid component at high pressures of greater than 200 bar and high temperatures of greater than 300° C.
- The object is achieved by a first diaphragm pump head having two or an integral multiple of two fluid delivery chambers and diaphragms associated therewith, which are hydraulically coupled to a second pump head for driving the first diaphragm pump head, wherein the second pump head is a diaphragm pump head which has two additional fluid delivery chambers and two associated additional diaphragms, which are drivable by a double-acting piston, situated in the second diaphragm pump head, via associated diaphragm control chambers, and a refilling valve being connected to each of the diaphragm control chambers, and, using the refilling valves, the diaphragm control chambers being impinged temporarily, during the refilling procedure, which is controlled by the diaphragm position, by a diaphragm control pressure, which is greater than atmospheric pressure and less than the system pressure.
- Advantageous embodiments of the present invention are described in the subclaims.
- The pump device according to the present invention comprises a first diaphragm pump head having two or an integral multiple of two fluid delivery chambers and diaphragms associated therewith, which are hydraulically coupled to a second diaphragm pump head, the second diaphragm pump head having two additional fluid delivery chambers and additional diaphragms associated therewith, which are drivable by a double-acting piston via associated diaphragm control chambers, a refilling valve being attached to each of the diaphragm control chambers and the diaphragm control chambers being temporarily impinged by a diaphragm pressure, which is greater than atmospheric pressure, using the refilling valves.
- Such a pump device is advantageous because at a time at which the refilling valve refills the diaphragm control chambers with a control fluid to compensate for unavoidable leakage of the control fluid, a brief pressure drop in the diaphragm control chambers down to atmospheric pressure, which has been typical up to this point in position-controlled diaphragms, for example, may be limited by the superimposed diaphragm control pressure, which is greater than the atmospheric pressure.
- By using the pump device according to the present invention, a movement of the piston is possible at any time using a smaller force than in achievements of the object in the prior art, so that a delivery pressure may alternately be conducted into the particular diaphragm control chambers of the second diaphragm pump head and therefrom to the first diaphragm pump head to transport fluid through the first diaphragm pump head. Although the overall pressure in the first diaphragm pump head may be relatively high to deliver the fluid, it is possible to operate a pumping procedure using a relatively small force exerted on the piston and pressure differential thus generated. A situation thus arises as if the piston would exert the pressure increase directly in the first diaphragm pump head. It is possible due to the pump device according to the present invention that the piston may be driven by a drive assembly which may be designed for much smaller forces than in achievements of the object known up to this point, so that a significantly more cost-effective delivery at high temperatures and pressures in the first diaphragm pump head is achieved.
- The pump device is preferably designed in such a way that the diaphragm control pressure approximately corresponds to a fluid pressure at the inlet of a fluid delivery chamber of the first diaphragm pump head. Therefore, the described brief pressure drop in the diaphragm control chamber of the second diaphragm pump head is nearly completely compensated for. In combination with a double-acting embodiment of the piston of the second diaphragm pump head, this has the result that the drive assembly for the piston only has to be designed for forces which approximately correspond to the pressure differential between the inlet and the outlet of a fluid delivery chamber of the first diaphragm pump head.
- In the pump device according to the present invention, the diaphragm control pressure may preferably be adapted to the fluid pressure by a control circuit having associated sensors and actuators. In particular with an electronic control circuit, this allows an optimally tailored compensation of the described pressure drop and thus the prevention of pressure surges, which may exert a harmful reaction on the drive assemblies.
- The diaphragm control pressure may be generated by a pump which is coupled in each case to a container for a diaphragm control chamber, each container having one of the refilling valves and each container being impinged by a static stagnation pressure by the pump. In such an embodiment, the pump is permanently in operation.
- According to an alternative embodiment, the diaphragm control pressure may be generated by a controllable pump which feeds a pressure accumulator which is coupled in each case to a container for a diaphragm control chamber. The container is used in this case as a refilling reservoir. In this embodiment, it is possible that the pump is only in operation when the pressure accumulator falls below a predefined lower limiting pressure. The pump then operates until an upper limit pressure is again reached in the pressure accumulator (two-point regulation).
- Furthermore, it is possible to provide a container in each case as a refilling reservoir of a control fluid for a diaphragm control chamber of the second diaphragm pump head, an adjustable throttle device being connected downstream from each container. In this case, the pump may be continuously in operation, so that continuous circulation of a control fluid is provided.
- The construction of the pump device and its mode of operation are relatively symmetrical if the piston is implemented as a double-acting disk piston having diametrically opposite piston rods. In this case, the piston faces on both sides of the disk piston having identical sizes, so that during an intake stroke or pressure stroke, the same pressure change and the same volume displacement is generated in each case.
- If the diaphragms of the first diaphragm pump head are each freely oscillating metal diaphragms, a fluid may be transported at high temperatures because of the metal material. Because the first diaphragm pump head and the second diaphragm pump head are coupled to a control fluid via lines, these lines may act as cooling lines. Therefore, in a preferred embodiment, the diaphragms of the second diaphragm pump head may be made of a plastic, in particular PTFE, so that there is no danger that these plastic diaphragms will display significant flowing because of too high temperatures.
- If the diaphragms of the second diaphragm pump head are each implemented as multilayered and are provided with a position controller and fracture signaling, the security during delivery of the fluid may be increased. Still greater security is achieved if a conductivity or viscosity sensor is provided inside the diaphragm control chambers of the first diaphragm pump head. If a metal diaphragm in the first diaphragm pump head breaks, the fluid to be delivered may reach the neighboring diaphragm control chambers, so that mixing of delivery fluid and control fluid would occur. Mixing of this type may change the electrical conductivity or the viscosity of the mixture in comparison to the values of the control fluid, so that a fracture of a metal membrane may be detected using the sensor.
- The hydraulic coupling between the first diaphragm pump head and the second diaphragm pump head may occur using control fluids, which have water or oil. For example, special heat transfer oil may be used as the oil, if the pump device is used for delivering a fluid at high temperatures.
- In the following, the present invention is described further on the basis of an exemplary embodiment illustrated in the drawing.
-
FIG. 1 shows a schematic illustration of an embodiment of the pump device according to the present invention. -
FIG. 1 illustrates a pump device 1 having a firstdiaphragm pump head 2 and a seconddiaphragm pump head 8. The firstdiaphragm pump head 2 has afirst diaphragm 3, which separates a firstfluid delivery chamber 4 from a firstdiaphragm control chamber 5. A fluid to be delivered by the firstfluid delivery chamber 4 is fed by asupply line 60, in which a fluid pressure p1 exists (see arrow 7), to an inlet opening 6 having anintake valve 61. When thefirst diaphragm 3 bulges out, the fluid may be transported by the firstfluid delivery chamber 4 to apressure valve 62 at one end of thefluid delivery chamber 4. Themembrane 3 bulges out due to the application of a pressure in the firstdiaphragm control chamber 5. If a pressure which is higher by dp is applied there, a pressure p1+dp exists at thepressure valve 62, using which the fluid is transported to thedrain line 63. - The pressure p1+dp is provided through a
first line 13 by a seconddiaphragm pump head 8. This has asecond diaphragm 9, which separates a secondfluid delivery chamber 10 from a seconddiaphragm control chamber 11. The secondfluid delivery chamber 10 is coupled to the firstdiaphragm control chamber 5 by afirst control fluid 12. When thesecond diaphragm 9 bulges out, thisfirst control fluid 12 is conducted through thefirst line 13 to the firstdiaphragm control chamber 5, so that thefirst diaphragm 3 bulges out. A displacement of thefirst control fluid 12 of this type is achieved using apiston 15, which exerts a stroke, which is directed downward in the embodiment shown inFIG. 1 . A second control fluid 14 provided in the seconddiaphragm control chamber 11 is used as the transmission medium of the volume change in an associatedlower piston chamber 32. The seconddiaphragm control chamber 11 extends up to adisk piston 31 of thepiston 15, so that thelower piston chamber 32 is a part of the seconddiaphragm control chamber 11. - The stroke movement of the
disk piston 31 in a direction which points downward in the embodiment shown inFIG. 1 is caused by apump drive assembly 51 using afirst piston rod 33. A second piston rod 35 is situated diametrically opposite to thefirst piston rod 33 on thedisk piston 31. Therefore, thedisk piston 31 is constructed symmetrically, so that the same area is provided on both diametrically opposite front faces of thedisk piston 31. This has the result that during a piston stroke into thelower piston chamber 32, the same absolute value of a pressure and volume change is achieved as during a piston stroke up into a diametrically opposite upper piston chamber 34. - The upper piston chamber 34 is part of a third
diaphragm control chamber 17, which is separated from a thirdfluid delivery chamber 19 by athird diaphragm 18. During a downwardly directed stroke movement of thedisk piston 31, the volume of the upper piston chamber 34 enlarges, so that thethird diaphragm 18 is contracted or compressed. Athird control fluid 16 in the thirddiaphragm control chamber 17 is used as the transmission medium. - A transport of a fluid conducted at a pressure p1 into the first
fluid delivery chamber 4 is achieved if a pressure p1+dp is transmitted into the firstdiaphragm control chamber 5 via theline 13. Therefore, this pressure p1+dp must also exist in the secondfluid delivery chamber 10. This is only possible if such a pressure is built up in the seconddiaphragm control chamber 11. In achievements of the object according to the prior art, it is typical for a drive assembly to exert this entire pressure p1+dp on one or two single-acting plunger pistons. In contrast, in the embodiment according to the present invention, this is no longer necessary. For this purpose, as is obvious fromFIG. 1 , the pressure p1 is alternately transmitted via thediaphragms control fluids diaphragms control fluids 14 and 16 to theparticular piston chamber 32 or 34 executing the intake stroke. If the unavoidable leakage of thecontrol fluids 14 and 16 is compensated for by the refillingvalves diaphragm control chambers - If the piston of the second diaphragm pump head is implemented as a double-acting piston and the pressure p2 is approximately equal to p1, only enough force has to be exerted on the
piston rod 33 using thepump drive assembly 51 so that thepiston 15 generates a differential pressure dp. For example, if p1=250 bar, a transport of the fluid through the firstfluid delivery chamber 4 may be achieved using a differential pressure of dp=20 bar. Thepump drive assembly 51 therefore no longer has to be designed for p1+dp=270 bar, but rather only for 20 bar. This allows fluid transport which is significantly more favorable economically. - The pressure p2 is provided by a
pump 50 via afeed line 36 to thecontainers diaphragm control chambers ventilation valve 42 or 44 into acontainer 41 or 43, respectively, and conducted using areturn line 53 into acontrol fluid reservoir 52. - During a downwardly directed stroke of the
disk piston 31, the upper piston chamber 34 is enlarged, so that thethird membrane 18 is compressed. Therefore, the volume of the thirdfluid delivery chamber 19 also increases, which is coupled via afourth control fluid 21 and thesecond line 22 to a fourthdiaphragm control chamber 23. The fourthdiaphragm control chamber 23 is located in the firstdiaphragm control head 2 in the embodiment shown inFIG. 1 and is separated using afourth diaphragm 24 from a fourthfluid delivery chamber 25. This construction is mirror symmetric to the construction havingfirst diaphragm 3, firstfluid delivery chamber 4, and firstdiaphragm control chamber 5. Upon an enlargement of the thirdfluid delivery chamber 19, the volume of the fourthfluid delivery chamber 25 is also enlarged, so that suction and/or a fluid feed occurs via theimage opening 26 having the intake valve 64. If the disk piston is moved in a downwardly directed stroke, the conditions described above are reversed. The fourthfluid delivery chamber 25 delivers a fluid through anoutlet opening 28 using aventilation valve 65 into adrain line 63, while the firstfluid delivery chamber 4 is filled. - The
first diaphragm 3 andfourth diaphragm 24 are freely oscillating metal diaphragms. A multilayered embodiment and a diaphragm position controller may be dispensed with. A cheek as to whether a fracture of a metal diaphragm has occurred may be performed indirectly by a conductivity orviscosity sensor diaphragm 3, for example, mixing of the fluids occurs in the firstfluid delivery chamber 4 and firstdiaphragm control chamber 5, so that the electrical conductivity or the viscosity changes, which may be detected by thesensors - For example, in the pump device in the second
diaphragm pump head 8, if thethird membrane 18 is compressed during an intake stroke of thedisk piston 31 in such a way that it reaches its rear position, as noted above, the pressure in the third diaphragm control chamber may drop to and/or below atmospheric pressure. This is undesirable because in this case a significant shear force increase of thepiston 15 occurs suddenly and the pump drive assembly is strongly loaded. This may be avoided in the pump device according to the present invention by the permanent pressure impingement using p2, which approximately corresponds to p1, via thecontainers - In a further advantageous embodiment (not shown in
FIG. 1 ) the seconddiaphragm pump head 8 has a separate diaphragm position controller in each case for thesecond diaphragm 9 and thethird diaphragm 18, as disclosed in EP 0 085 725 A1. Theparticular refilling valves particular diaphragm particular control fluid 16 or 14, is situated in the area of thediaphragm control chamber control fluid 16 or 14 has occurred, the final position of thediaphragm diaphragm control chamber diaphragm control chamber control fluid 16 or 14 may flow into thediaphragm control chamber diaphragm control chamber diaphragm - In addition, it is also possible in another embodiment of the present invention to situate the double-acting
piston 15 outside the seconddiaphragm pump head 8. Thepiston 15 is situated with thedisk piston 31 and thepiston rods 33 and 35 in a control-fluid-tight housing separate from thediaphragm pump head 8, which comprises thepiston chambers 32 and 34 accommodating thepiston 15 as well as flexible or installed lines for thecontrol fluids 16 and 14. These lines connect theparticular piston chambers 32 and 34 to thediaphragm control chambers - There has thus been outlined, rather broadly, certain embodiments of the invention in order that the detailed description thereof herein may be better understood, and in order that the present contribution to the art may be better appreciated. There are, of course, additional embodiments of the invention that will be described below and which will form the subject matter of the claims appended hereto.
- In this respect, before explaining at least one embodiment of the invention in detail, it is to be understood that the invention is not limited in its application to the details of construction and to the arrangements of the components set forth in the following description or illustrated in the drawings. The inventions capable of embodiments in addition to those described and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein, as well as the abstract, are for the purpose of description and should not be regarded as limiting.
- As such, those skilled in the art will appreciate that the conception upon which this disclosure is based may readily be utilized as a basis for the designing of other structures, methods and systems for carrying out the several purposes of the present invention. It is important, therefore, that the claims be regarded as including such equivalent constructions insofar as they do not depart from the spirit and scope of the present invention.
Claims (21)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/624,388 US20130017101A1 (en) | 2006-09-04 | 2012-09-21 | Pump device |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006041420.9 | 2006-09-04 | ||
DE102006041420A DE102006041420A1 (en) | 2006-09-04 | 2006-09-04 | pump device |
US11/896,524 US8360750B2 (en) | 2006-09-04 | 2007-09-04 | Pump device |
US13/624,388 US20130017101A1 (en) | 2006-09-04 | 2012-09-21 | Pump device |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/896,524 Continuation US8360750B2 (en) | 2006-09-04 | 2007-09-04 | Pump device |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130017101A1 true US20130017101A1 (en) | 2013-01-17 |
Family
ID=38691113
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/896,524 Active US8360750B2 (en) | 2006-09-04 | 2007-09-04 | Pump device |
US13/624,388 Abandoned US20130017101A1 (en) | 2006-09-04 | 2012-09-21 | Pump device |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/896,524 Active US8360750B2 (en) | 2006-09-04 | 2007-09-04 | Pump device |
Country Status (8)
Country | Link |
---|---|
US (2) | US8360750B2 (en) |
EP (2) | EP2108838B1 (en) |
JP (2) | JP5221085B2 (en) |
AT (2) | ATE438801T1 (en) |
CA (1) | CA2599949C (en) |
DE (3) | DE102006041420A1 (en) |
DK (2) | DK2108838T3 (en) |
ES (1) | ES2331030T3 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103277289A (en) * | 2013-05-10 | 2013-09-04 | 北京京城压缩机有限公司 | Diaphragm-type compressor integrated cylinder body part with single cylinder body and double cylinder covers |
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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 |
EP2154371B1 (en) | 2008-08-14 | 2018-09-19 | Bran + Lübbe GmbH | Pumping device |
DE202008010872U1 (en) | 2008-08-14 | 2010-02-25 | Bran+Luebbe Gmbh | pump device |
EP2531729B1 (en) * | 2010-02-02 | 2020-03-04 | Dajustco Ip Holdings Inc. | Diaphragm pump with hydraulic fluid control system |
US9610392B2 (en) | 2012-06-08 | 2017-04-04 | Fresenius Medical Care Holdings, Inc. | Medical fluid cassettes and related systems and methods |
DE102013207193A1 (en) * | 2013-04-22 | 2014-10-23 | Robert Bosch Gmbh | Microhydraulic system, especially for use in planar microfluidic laboratories |
US9845794B2 (en) | 2013-10-08 | 2017-12-19 | Ingersoll-Rand Company | Hydraulically actuated diaphragm pumps |
EP3115607B1 (en) * | 2015-07-10 | 2018-02-21 | J. Wagner AG | Double membrane pump |
KR102167568B1 (en) * | 2020-03-11 | 2020-10-20 | 톈진 나가르 메커니컬 인더스트리 리미티드 컴퍼니 | High-pressure Plunger Type Double Diaphragm Pump |
US20240117802A9 (en) * | 2020-11-09 | 2024-04-11 | Pdc Machines Inc. | Hydraulic drive for diaphragm compressor |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103277289A (en) * | 2013-05-10 | 2013-09-04 | 北京京城压缩机有限公司 | Diaphragm-type compressor integrated cylinder body part with single cylinder body and double cylinder covers |
Also Published As
Publication number | Publication date |
---|---|
EP2108838A1 (en) | 2009-10-14 |
JP2008064096A (en) | 2008-03-21 |
ATE438801T1 (en) | 2009-08-15 |
US20080056916A1 (en) | 2008-03-06 |
DK2108838T3 (en) | 2012-06-25 |
ES2331030T3 (en) | 2009-12-18 |
JP5221085B2 (en) | 2013-06-26 |
EP2108838B1 (en) | 2012-02-29 |
JP5629796B2 (en) | 2014-11-26 |
DK1898093T3 (en) | 2009-09-14 |
DE102006041420A1 (en) | 2008-03-20 |
EP1898093A1 (en) | 2008-03-12 |
CA2599949C (en) | 2016-03-15 |
US8360750B2 (en) | 2013-01-29 |
CA2599949A1 (en) | 2008-03-04 |
EP1898093B1 (en) | 2009-08-05 |
ATE547631T1 (en) | 2012-03-15 |
DE202007019423U1 (en) | 2012-06-12 |
DE502007001229D1 (en) | 2009-09-17 |
JP2013137031A (en) | 2013-07-11 |
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