EP3167191A1 - Diaphragm pump with reduced leak extension in the event of overload - Google Patents
Diaphragm pump with reduced leak extension in the event of overloadInfo
- Publication number
- EP3167191A1 EP3167191A1 EP15738312.6A EP15738312A EP3167191A1 EP 3167191 A1 EP3167191 A1 EP 3167191A1 EP 15738312 A EP15738312 A EP 15738312A EP 3167191 A1 EP3167191 A1 EP 3167191A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- pressure
- working fluid
- hydraulic
- relief valve
- 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
Links
- 239000012530 fluid Substances 0.000 claims abstract description 103
- 239000010720 hydraulic oil Substances 0.000 claims description 12
- 239000012528 membrane Substances 0.000 description 19
- 238000010438 heat treatment Methods 0.000 description 10
- 238000005086 pumping Methods 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
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
- F04B43/06—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
- F04B43/0009—Special features
- F04B43/0081—Special features systems, control, safety measures
- F04B43/009—Special features systems, control, safety measures leakage control; pump systems with two flexible members; between the actuating element and the pumped fluid
-
- 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
-
- 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
- F04B2203/00—Motor parameters
- F04B2203/09—Motor parameters of linear hydraulic motors
- F04B2203/0902—Liquid pressure in a working chamber
Definitions
- the present invention relates to a diaphragm pump with a leak-relief valve.
- Diaphragm pumps generally have a delivery chamber which is separated from a hydraulic chamber by a membrane, wherein the delivery chamber is connected both to a suction connection and to a pressure connection.
- the filled with working fluid hydraulic chamber can then be acted upon with a pulsating working fluid pressure. Due to the pulsating working fluid pressure, a pulsating movement of the diaphragm between a pressure position, in which the volume of the delivery chamber is smaller, and a suction position, in which the volume of the delivery chamber is greater, reciprocated.
- the medium to be pumped is separated from the drive, whereby on the one hand the drive is shielded from harmful influences of the pumped medium and on the other hand, the fluid from harmful influences of the drive, for example impurities, is shielded.
- the pulsating working fluid pressure is often provided by means of a movable piston in contact with the working fluid.
- the piston is reciprocated, for example, in a hollow cylindrical element, whereby the volume of the hydraulic space is reduced and increased, which leads to an increase and decrease of the pressure in the hydraulic chamber and in consequence to a movement of the membrane.
- a vent valve is often connected to the hydraulic chamber, via which a certain amount of gas and possibly a small amount of working fluid is discharged during the pressure stroke. This also gradually reduces the amount of working fluid in the hydraulic chamber.
- DE 1 034 030 has already been proposed to connect the hydraulic chamber with the interposition of a valve, a so-called leak-relief valve, with a working fluid reservoir.
- working fluid can be added to the hydraulic chamber through this leak-relief valve.
- the leak relief valve In normal operation, the leak relief valve is designed so that exactly the amount of working fluid that has been lost during the pressure stroke, at the end of the suction stroke, i. essentially in the suction position, is refilled.
- the metering pump described is typically used in a corresponding process plant, i. It is connected to a corresponding suction line and a pressure line. Although not generally desired, it can happen that the pressure line is accidentally closed in the process plant, so that the metering pump pumps against a closed volume, which can lead to an unacceptably high pressure development, resulting in damage to the membrane or drive parts the pump can lead.
- the hydraulic chamber is equipped with an outlet channel which is closed by a pressure relief valve, which is designed such that when the pressure in the hydraulic chamber above a predetermined maximum value p ma x increases, the pressure relief valve opens, so that working fluid on the Outlet channel can leave the hydraulic chamber and is generally fed back into the working fluid reservoir. As a result, a further increase in pressure can be prevented.
- the temperature of the pump can increase significantly, as with each pressure stroke again hydraulic fluid must be discharged through the pressure relief valve and is fed back through the leak-relief valve.
- Another way to comply with the ATEX guidelines is to use an appropriate temperature sensor that senses the temperature of the pump, preferably near the pressure relief valve, and outputs a signal when the limit temperature is exceeded, which then shuts down the pump. By this measure, however, a temperature sensor must be maintained. In addition, the signal emitted by the temperature sensor must be prepared and processed accordingly.
- Another solution is to use a flow switch in the outlet channel, which detects the hydraulic oil flow via the pressure relief valve in case of overpressure and ensures that the pump is switched off.
- this object is achieved in that the working fluid reservoir is arranged in a first and in a second chamber, wherein the two chambers are connected to each other via a first connecting channel.
- connection channel is either closable or the flow through the connection channel throttled or at least throttled, so that in the overpressure case, i.
- the hydraulic oil has left the hydraulic space via the pressure limiting valve, more hydraulic oil from the first chamber is fed into the hydraulic chamber than can flow in from the second chamber into the first chamber during a stroke.
- the outlet channel is connected to the working fluid reservoir, this should then be connected to the second chamber of the working fluid reservoir.
- the working fluid flowing past the piston can be returned to one of the two chambers.
- the overpressure causes the pressure in the first chamber and / or the filling level in the first chamber to drop, since less working fluid can flow from the second chamber into the first chamber than via the leak-relief valve from the first chamber into the first chamber Hydraulic room is discharged.
- the measure according to the invention therefore ensures that, in the overpressure case, gas penetrates into the hydraulic chamber and thereby prevents further heating of the pump.
- the connecting channel can be closed by means of a valve.
- the valve is usually closed.
- the amount of working fluid that is released via the piston or the venting valve has escaped, refilled. However, this amount is very low, so that the level of fluid flow in the first chamber drops only very slowly.
- the first chamber can be sized so that the pump can be operated in this state for several days or even weeks, without the level or the working fluid pressure drops so far that gas penetrates through the leak-relief valve in the hydraulic chamber.
- the valve of the connecting channel In order to put the pump back into operation, the valve of the connecting channel must be opened, so that the first chamber is filled again with sufficient working fluid. Since a certain gas volume is conveyed out of the hydraulic chamber with each pressure stroke, when gas is in the hydraulic chamber, and now no more gas is supplied via the leak-relief valve, the pump can work normally again.
- the valve of the connection channel can be regularly opened for a short time, either manually - e.g. in the event of an error or during regular checks - or automatically, e.g. Timed every 24 hours to increase the working fluid level in the first chamber.
- a second connection channel between the first and second chamber is provided.
- the second connecting channel can be arranged above the first connecting channel and preferably above the leak-relief valve, wherein the second connecting channel is particularly preferably arranged above the working-fluid level in the second chamber.
- the second communication passage When the second communication passage is located above the working fluid levels in the two chambers, it provides pressure equalization between the first and second chambers.
- the second communication passage may have a large cross section, so that the pressure in the first and second chambers is always the same.
- the first connection channel is so di- that in the overpressure case, as already described above, more working fluid can be discharged from the first chamber into the hydraulic chamber than can flow from the second chamber via the first connecting channel into the first chamber.
- the first chamber is designed such that working fluid can only reach the first chamber via the first connecting channel. In this case, therefore, no pressure compensation via a second connection channel is possible. In overpressure, this means that more working fluid is transferred via the leak-relief valve from the first chamber into the hydraulic chamber as working fluid from the second chamber can flow into the first chamber, that the pressure of the working fluid in the first chamber is significantly reduced.
- the hydraulic oil cavitates and thus introduces gas into the hydraulic chamber. As a result, the hydraulic displacement process of the pump is disturbed so much that the power consumption of the drive drops sharply and consequently there is no excessive heating of the hydraulic system.
- a second connection channel may be helpful if it is closed by a check valve, wherein the flow direction of the check valve is arranged in the direction of the second chamber.
- the check valve ensures that the second connection channel remains closed in all the previously described functional states of the pump.
- a safety valve or a specially designed leak-relief valve returns at least a portion of the working fluid back to the first chamber to protect the membrane. This is the case, for example, in the case of a blockage of the suction line, if the membrane does not move back into the suction position and therefore too much Working fluid flows into the hydraulic chamber. During the pressure stroke, the membrane then moves beyond the pressure position, which can lead to damage to the membrane. Therefore, a safety valve or a specially designed leak-relief valve can be provided, which opens in the event that the membrane moves beyond the pressure position.
- the safety valve or the leak-relief valve are designed such that the escaping working fluid is returned to the first chamber, the use of the check valve in the second connecting channel is advantageous, which then possibly give overpressure occurring in the first chamber via the check valve in the second chamber can be.
- the leak-relief valve is advantageously designed such that it has a between a closed position, in which the valve passage is closed, and an open position in which the valve passage is open, a reciprocating closing body, which held by means of a pressure element in the closed position is, wherein the pressure element is designed such that when the pressure in the hydraulic chamber is less than a set pressure pmin, the closing body moves in the direction of the open position.
- the first connection channel is arranged lower than the leak-relief valve.
- the second chamber can be dimensioned to be relatively compact, since it is only necessary for the connecting channel to always be below the working fluid inlet in the second chamber.
- the device according to the invention has the advantage that no external power supply is necessary. In addition, no signal processing and evaluation is required, which makes the inventive measure maintenance and wear. There are no additional components needed.
- FIG. 1 shows a partial sectional view of a first embodiment according to the invention
- FIG. 2 shows a schematic representation of the mode of operation of the embodiment of FIG. 1 in normal operation
- FIG. 3 shows a schematic representation of the mode of operation of the embodiment of FIG. 1 in overpressure operation
- FIG. 4 is a partial sectional view of a second embodiment of the invention and FIG. 5 shows a schematic representation of the mode of operation of the second embodiment according to FIG. 4.
- FIG. 1 shows a partial sectional view of a first embodiment of the invention.
- the membrane (not shown) is located on the left outside the representation of Figure 1 and is connected to the leak-relief valve 5, which is resiliently biased within the hydraulic chamber 6 and closes the connection between the hydraulic chamber 6 and the first chamber 1 of the working fluid Vorrats.
- the working fluid is arranged in the first chamber 1 and in the second chamber 2.
- the first chamber 1 and the second chamber 2 are connected to each other via a first connecting channel 4, which is designed here as a nozzle.
- the nozzle cross-section is dimensioned such that in the overpressure case, more working fluid will be discharged via the leak-relief valve 5 into the hydraulic chamber 6 than can be tracked via the nozzle 4. Furthermore, an opening 3, which functions as a second connection channel, is arranged between the first chamber 1 and the second chamber 2.
- the leak-relief valve 5 is designed such that, in particular when at the end of the suction stroke, i. is in the suction position too little working fluid in the hydraulic chamber 6, the leak-relief valve 5 opens so that working fluid from the first chamber can flow into the hydraulic chamber 6. In normal operation, the amount of working fluid that needs to be replaced by the leak-relief valve is very low. In the overpressure case, i.
- the pressure in the hydraulic chamber 6 increases rapidly, so for safety reasons working fluid via a pressure relief valve (not shown) discharged from the hydraulic chamber 6 and discharged, for example, in the second chamber 2 of the working fluid reservoir.
- a pressure relief valve (not shown) discharged from the hydraulic chamber 6 and discharged, for example, in the second chamber 2 of the working fluid reservoir.
- the leak-relief valve 5 In the case of overpressure, the leak-relief valve 5 must track a significantly larger amount of working fluid out of the first chamber.
- FIG. 2 shows the state in normal operation.
- the working fluid reservoir which consists of the first chamber 1 and the second chamber 2, which is connected to each other by a below the liquid level nozzle 4, which acts as a first connecting channel.
- the second connection channel is realized through the opening 3, which is above the working fluid level.
- the loss of working fluid in the hydraulic chamber is so small that during a complete stroke the tracked working fluid can easily be tracked through the first connecting channel 4 from the second chamber to the first chamber.
- the pressure relief valve will no longer open and therefore no larger amount of hydraulic oil will leave the hydraulic chamber.
- more working fluid will again flow from the second chamber into the first chamber via the nozzle 4 as working fluid from the first chamber 1 is fed into the hydraulic chamber via the leak-relief valve 5, so that the working fluid level in the first chamber 1 will increase again.
- gas is no longer in the hydraulic system. supplied and the dosing capacity increases again.
- the gas contained in the hydraulic chamber can be discharged via a vent valve.
- FIG. 4 shows a partial sectional view of a second embodiment according to the invention. This differs essentially from the first embodiment in that there is no pressure equalization, the second connecting channel is present and the connection of the first and second chamber is closed by a check valve 9, a liquid working fluid from the second chamber 2 into the first chamber 1 prevents and has a bypass 10, which has a small cross-section, so that working fluid can flow from the second chamber 2 into the first chamber 1 to a lesser extent.
- Fig. 4a the check valve 9 is shown enlarged with a bypass 10. It can be seen that the bypass line 10 provides a direct connection between the first chamber 1 and second chamber 2.
- Fig. 5 is a diagram illustrating the operation of the embodiment of Fig. 4;
- the loss of working fluid in the hydraulic chamber is so small that during a complete stroke, the amount of working fluid supplied via the leak-relief valve 5 can be easily tracked through the bypass 10 from the second chamber into the first chamber.
- the pressure relief valve will not open and therefore no larger amount of hydraulic oil leave the hydraulic chamber.
- more working fluid will again flow from the second chamber into the first chamber via the bypass 10 as working fluid from the first chamber 1 is fed into the hydraulic chamber via the leak-relief valve 5, so that the pressure in the first chamber 1 will increase again.
- the gas contained in the hydraulic chamber can be discharged via a vent valve.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014109801.3A DE102014109801A1 (en) | 2014-07-11 | 2014-07-11 | Diaphragm pump with reduced leakage supplement in case of overload |
PCT/EP2015/065907 WO2016005596A1 (en) | 2014-07-11 | 2015-07-10 | Diaphragm pump with reduced leak extension in the event of overload |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3167191A1 true EP3167191A1 (en) | 2017-05-17 |
EP3167191B1 EP3167191B1 (en) | 2019-10-30 |
Family
ID=53610874
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15738312.6A Active EP3167191B1 (en) | 2014-07-11 | 2015-07-10 | Diaphragm pump with reduced leak extension in the event of overload |
Country Status (6)
Country | Link |
---|---|
US (1) | US10378530B2 (en) |
EP (1) | EP3167191B1 (en) |
CN (1) | CN106460823B (en) |
CA (1) | CA2946093A1 (en) |
DE (1) | DE102014109801A1 (en) |
WO (1) | WO2016005596A1 (en) |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB597106A (en) * | 1945-08-09 | 1948-01-19 | Norman Emile Mcclelland | Improvements in or relating to diaphragm pumps |
DE7420466U (en) * | 1975-01-16 | Lewa H Kg | Diaphragm pump | |
DE1034030B (en) | 1955-09-22 | 1958-07-10 | Reiners Walter Dr Ing | Diaphragm pump for non-lubricating and chemically aggressive fluids, especially for pest control in agriculture |
US3254845A (en) * | 1964-12-11 | 1966-06-07 | Panther Pumps & Equipment Comp | Fluid power transfer apparatus |
DE1528474B1 (en) * | 1966-03-01 | 1970-07-23 | Lewa Herbert Ott Fa | Hydraulic control device on a diaphragm pump |
US3612727A (en) * | 1969-10-17 | 1971-10-12 | Crane Co | Metering pump |
USRE29055E (en) * | 1970-12-21 | 1976-11-30 | Pump and method of driving same | |
DE7303301U (en) * | 1973-01-30 | 1974-04-04 | Feluwa Schlesiger & Co Kg | Diaphragm piston pump |
US4019837A (en) * | 1975-05-30 | 1977-04-26 | Graco Inc. | Pressure unloading apparatus for a diaphragm pump |
JPS5685583A (en) * | 1979-12-14 | 1981-07-11 | Diesel Kiki Co Ltd | Controlling device for variable delivery rotary pump |
DE2923284A1 (en) * | 1979-06-08 | 1980-12-11 | Wagner Gmbh J | METHOD AND DEVICE FOR CONTROLLING THE PERFORMANCE OF DIAPHRAGM PUMPS |
EP0055467B1 (en) * | 1980-12-29 | 1984-12-05 | LEWA Herbert Ott GmbH + Co. | Diaphragm pump with a pressure relieved diaphragm |
DE3708868A1 (en) * | 1987-03-18 | 1988-10-06 | Ott Kg Lewa | METHOD AND DEVICE FOR STARTING A HYDRAULIC DIAPHRAGM PUMP AGAINST LOAD |
US4934906A (en) * | 1988-01-29 | 1990-06-19 | Williams James F | High pressure diaphragm pump |
DE4018464A1 (en) * | 1990-06-08 | 1991-12-12 | Ott Kg Lewa | DIAPHRAGM FOR A HYDRAULICALLY DRIVED DIAPHRAGM PUMP |
DE4141670C2 (en) * | 1991-12-17 | 1994-09-29 | Ott Kg Lewa | Hydraulically driven diaphragm pump with diaphragm stroke limitation |
DE4327969C2 (en) | 1993-08-19 | 1997-07-03 | Ott Kg Lewa | Hydraulically driven diaphragm pump |
DE4420863C2 (en) * | 1994-06-15 | 1998-05-14 | Ott Kg Lewa | Controlled sniffing hindrance for high pressure diaphragm pumps |
US5647733A (en) * | 1995-12-01 | 1997-07-15 | Pulsafeeder Inc. | Diaphragm metering pump having modular construction |
FR2895036B1 (en) * | 2005-12-20 | 2008-02-22 | Milton Roy Europ Sa | HYDRAULICALLY ACTUATED MEMBRANE PUMP WITH LEAK COMPENSATION DEVICE |
CN101245777B (en) * | 2007-02-13 | 2010-09-08 | 米尔顿罗伊欧洲公司 | Hydraulic pressure driven membrane pump with leakage compensation equipment |
DE102010039831B4 (en) * | 2010-08-26 | 2022-02-03 | Prominent Gmbh | Diaphragm pump and method for adjusting such |
-
2014
- 2014-07-11 DE DE102014109801.3A patent/DE102014109801A1/en not_active Withdrawn
-
2015
- 2015-07-10 CN CN201580023902.XA patent/CN106460823B/en active Active
- 2015-07-10 WO PCT/EP2015/065907 patent/WO2016005596A1/en active Application Filing
- 2015-07-10 US US15/304,257 patent/US10378530B2/en active Active
- 2015-07-10 EP EP15738312.6A patent/EP3167191B1/en active Active
- 2015-07-10 CA CA2946093A patent/CA2946093A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
US20170037840A1 (en) | 2017-02-09 |
EP3167191B1 (en) | 2019-10-30 |
WO2016005596A1 (en) | 2016-01-14 |
CA2946093A1 (en) | 2016-01-14 |
CN106460823B (en) | 2020-04-17 |
DE102014109801A1 (en) | 2016-01-14 |
US10378530B2 (en) | 2019-08-13 |
CN106460823A (en) | 2017-02-22 |
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