WO2019214905A1 - Pulsationsdämpfungssystem - Google Patents
Pulsationsdämpfungssystem Download PDFInfo
- Publication number
- WO2019214905A1 WO2019214905A1 PCT/EP2019/059600 EP2019059600W WO2019214905A1 WO 2019214905 A1 WO2019214905 A1 WO 2019214905A1 EP 2019059600 W EP2019059600 W EP 2019059600W WO 2019214905 A1 WO2019214905 A1 WO 2019214905A1
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- WIPO (PCT)
- Prior art keywords
- pump
- pressure
- chamber
- fluid
- storage container
- Prior art date
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- 238000013016 damping Methods 0.000 title claims abstract description 89
- 230000010349 pulsation Effects 0.000 title claims abstract description 86
- 239000012530 fluid Substances 0.000 claims abstract description 187
- 230000010355 oscillation Effects 0.000 claims abstract description 12
- 238000003860 storage Methods 0.000 claims description 153
- 238000006073 displacement reaction Methods 0.000 claims description 33
- 230000008859 change Effects 0.000 claims description 22
- 239000012528 membrane Substances 0.000 claims description 17
- 230000001105 regulatory effect Effects 0.000 claims description 10
- 238000011144 upstream manufacturing Methods 0.000 claims description 9
- 238000000926 separation method Methods 0.000 claims description 5
- 230000001276 controlling effect Effects 0.000 claims description 4
- 239000007787 solid Substances 0.000 description 15
- 230000009467 reduction Effects 0.000 description 9
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 7
- 239000002245 particle Substances 0.000 description 7
- 241000124008 Mammalia Species 0.000 description 6
- 230000001133 acceleration Effects 0.000 description 6
- 238000005086 pumping Methods 0.000 description 5
- 230000033228 biological regulation Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 3
- 238000012432 intermediate storage Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 239000002609 medium Substances 0.000 description 1
- 238000007639 printing Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 239000010802 sludge Substances 0.000 description 1
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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
- F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
-
- 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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
-
- 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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
- F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
Definitions
- the invention relates to a pulsation damping system for reducing pressure oscillations in inlet and / or outlet pipelines, in particular in the intake and / or high pressure region, of piston pumps, in particular for conveying fluids with solids fractions, such as sludge feed pumps, with at least one a pump chamber having a piston pump, wherein the pump chamber for conveying a fluid or fluid via a first fluid port with a pump inlet channel, or suction port, and fluidly connected via a second fluid port with a pump outlet.
- the invention relates to a pulsation damping system for reducing pressure oscillations in inlet and / or outlet pipes, in particular in the intake and / or high pressure region of piston pumps, with at least one for conveying a fluid or conveying fluid with a pump chamber of a piston pump fluidly connectable Pumpeneinlasskanal and Pumpenauslasska- channel, wherein in the pump inlet channel and / or in the pump outlet channel, a first storage container is arranged, in which in a first region, or pressure chamber called, a fluid to be delivered cacheable and in a second area, also also called pressure chamber, a gas volume, in particular a compressible gas volume, is arranged.
- Such pulsation damping systems are known in numerous variants and are usually used in piping systems in which - for example, by the operation of a pump, an actuator or due to other flow influences caused - pressure oscillations or pressure surges can come.
- an actuator or due to other flow influences caused - pressure oscillations or pressure surges can come.
- uneven flow rates occur both in the intake tract and at the outlet of the pump.
- These non-uniform volume flows can lead to pressure pulsations that have a negative effect on the functioning of the pump and can lead to unwanted vibrations in the adjacent piping system.
- these pulsations can cause cavitation, which on the one hand can lead to a reduction in the efficiency of the pump and, on the other hand, to damage to the pump.
- pulsation dampers are usually arranged in the inlet and / or outlet piping of the pump and usually comprise a filled with a compressible gas volume equalization or storage chamber, which is in fluid communication with the pulsating fluid to be delivered. These dampers act in such a way that an increase in pressure is compensated by a compression of the gas volume in the storage chamber. Since the gas, due to its high compressibility in comparison to the fluid while only a small pressure changes, thus pressure pulsations due to the impressed volume flow pulsations can be reduced.
- an inlet-side pipe means a pump inlet channel or a suction line and the outlet-side pipe is a pump outlet channel or a high-pressure line, wherein the pump inlet channel is usually connected to a fluid source for sucking the delivery fluid and the pump inlet channel Pump outlet channel a further transport of the fluid to be pumped.
- a check valve is usually arranged in each case between the above-mentioned storage chamber and the pump chamber for conveying the fluid by means of the piston pump.
- the pump can be embodied in particular as a conventional piston pump with, for example, a single pump chamber or as a piston diaphragm pump with a pump chamber comprising a pump working chamber and a pump conveying chamber.
- it is customary to use a plurality of pistons or piston pumps which suck in the fluid to be delivered from a common intake line with a central storage container and convey this into a common high-pressure line on the high-pressure side.
- the invention achieves the stated object by a pulsation damping system with the features of the main claim and by a Pulsationsdämpfungs- system with the features of claim 11.
- Advantageous embodiments and further developments of the invention are disclosed in the dependent claims, the description and the figures.
- the pump chamber of a pulsation damping system has at least one further fluid connection, also called damping fluid connection, with which the pump chamber, in particular the fluid contained therein, is fluidically connected to a damping device for damping pressure oscillations.
- the damping can take place, in particular, by a time-controlled and / or quantity-controlled supply or discharge of a fluid in the pump chamber in the direction of or away from the damper device.
- a pump chamber and / or the adjoining one can be provided.
- the acceleration effects caused by the oscillating movement of the piston and exerted on the fluid medium, which occur in the pump chamber and in the pump chamber, can be intercepted by means of the damping device the adjacent inlet-side and / or outlet-side pipes to can lead to relatively high acceleration forces and consequently to pressure pulsations, thus reducing pressure surges in a particularly simple manner.
- the fluid flowing between the pump chamber and the damping device can advantageously be embodied as an incompressible barrier fluid, such as, for example, a hydraulic oil, in particular a pump working medium, or alternatively be the fluid medium to be delivered. Due to this configuration, in particular by a preferred damping fluid acting on the pump chamber independently of the fluid to be delivered, the present pulsation damping system is particularly suitable for use in piping systems for conveying fluids with solids fractions.
- At least one throttle valve is arranged in a pipe arranged between the pump chamber and the damping device.
- the throttle valve may in particular be arranged between the pump chamber and a pressure chamber fluidically connected to the pump chamber, for example a volume change device or a reservoir.
- a pressure pulse of a fluid for example, which is at least partially in the pump chamber and flows due to a very high or very low pressure through the Dämpfungsflu- idan gleich toward or away from the damping device, when flowing through the throttle valve is converted into heat be, so that in particular pressure pulsations can be reduced.
- the throttle valve can consequently also be regarded as part of the damping device.
- the throttle may in principle also be arranged in a secondary or downstream piping system which, although not directly fluidly connected to the pump chamber, is operatively connected to the pump in relation to the pressure prevailing in the pump chamber, for example by means for transmitting pressure from the fluid in the pumping chamber to a separate second fluid.
- the damping device preferably has a volume change device, also called volume compensation device, for changing the volume. at least one fluidically connected to the pump chamber pressure chamber.
- a fluid located in the pump chamber, which is exposed to increased pressure for example, can be controllably conducted or conveyed through the damping fluid port in the direction of or away from the damping device.
- This control of the fluid flow can be achieved, for example, by increasing a pressure space downstream of the damping fluid port to release an inflow of the fluid from the pump chamber into the pressure chamber or by reducing the pressure space for the fluid to flow back and forth from the pressure chamber the pump chamber done.
- controllable means, in particular, that a flow through the throttle and a pressure reduction caused thereby can be defined in terms of time and quantity, preferably predictably, particularly preferably automatically.
- the volume change device has a displacement body for changing the volume of the at least one pressure chamber, which is formed in particular as a displaceable wall, displaceable piston or displaceable membrane.
- the displacement body can be subjected to a counterpressure with respect to the fluid pressure applied on the pressure chamber side, for example via a spring-elastic element.
- the displacement body as a piston, in particular separating piston, or as a membrane of a self-closed system, such as a piston-cylinder unit is formed.
- the counterpressure acting on the piston or the diaphragm can be effected, for example, by a correspondingly arranged and pressurized second pressure chamber.
- the displacement of the displacement body can be controlled in a particularly advantageous manner, in particular actively.
- the volume changing device has a first pressure chamber, which is fluidically connected to the pump chamber, and a first pressure chamber connected to the pump chamber. From this body fluidly separated and with this operatively connected second pressure chamber.
- the second pressure chamber is advantageously filled with a gas volume.
- the second pressure chamber volume can be reduced when the first pressure chamber volume is increased and the second pressure chamber volume can be increased when the first pressure chamber volume is reduced ,
- a flow of the fluid located in the pump chamber through the damping fluid connection in the direction of or away from the damping device can be controlled particularly advantageously, and a particularly efficient damping, in particular in the region of the throttle point, can be effected.
- the second pressure chamber can be fluidly connected directly and / or indirectly via a control valve to a separate gas source.
- a control valve to a separate gas source.
- the regulation of the gas pressure prevailing in the second pressure chamber can be effected, for example, by means of the abovementioned separate or external pressure or gas source and the regulating valve serving for the control, the control of the control valve being arranged via at least one in the pump inlet channel and / or the pump outlet channel - Neten pressure sensor and a suitable PID control (proportional-integral-differential control) for controlling the control valves can be done.
- the control valve of a volume change device arranged on the pump inlet side can, for example, be actuated as a function of a pressure prevailing in the pump inlet channel and / or the control valve of a volume change device arranged on the pump outlet side as a function of a pressure prevailing in the pump outlet channel.
- the respective control valve can also be actuated as a function of a pressure prevailing in the pump chamber, for which purpose the pressure sensor is advantageously arranged in the region of the pump chamber.
- the second pressure chamber is preferably directly or indirectly in operative connection with the pressure prevailing in the pump inlet channel and / or in the pump outlet channel.
- the second pressure chamber can be fluidically connected to a reservoir, which is fluidically connected to the pump inlet channel or to the pump outlet channel, such as a pressurized wind tank.
- the pressure prevailing in the pump inlet channel and / or in the pump outlet channel can serve as pressure source or pressure gauge for the fluid of the second pressure chamber, wherein the fluid of the second pressure chamber preferably, for example by means of a membrane, of which in the pump inlet channel or the pump discharge passage located conveying fluid is fluidly separated.
- the damping device has a reservoir arranged in the pump inlet channel and / or in the pump outlet channel, in particular on a fluid side of a non-return valve arranged in the respective channel, having a delivery fluid inlet and a delivery fluid outlet, wherein in each case in the reservoir Area the conveying fluid and in an upper region of a pressurized, that is, a pressurized gas volume is arranged.
- the storage container can be designed, in particular to form or take up a volume in the storage container, particularly preferably as a volume and / or pressure storage container, in which the delivery fluid can advantageously be intermediately stored for delivery.
- the reservoir is designed as a pressure vessel.
- the gas volume can, for example, be directly or indirectly in operative connection with the fluid in the second pressure chamber.
- the reservoir can be fluidly connected at least temporarily and / or indirectly via a control valve to a separate gas source.
- the gas volume of the reservoir is preferably fluidically connected to the second pressure chamber of the volume change device via a pressure line.
- the pressure prevailing in the gas volume of the reservoir pressure can act directly on the displacement body.
- Such an embodiment is particularly advantageous for conveying fluids with solid particles and in particular enables a safe and automatic displacement of the displacement body, and thereby ultimately a reduction of pulsation pressures.
- a pressure of the medium to be delivered, in particular of a fluid mixed with solids, on the pump inlet side or pump outlet side can be transferred to a fluid, in particular a gaseous fluid, fluidically connected to the second pressure chamber, in a particularly simple and reliable manner.
- the piston pump is designed as a diaphragm piston pump with a pump working chamber and a fluidically separated from this and in operative connection with this pump delivery chamber, wherein at the pump delivery chamber, the first and second delivery fluid port and the pump working chamber, the at least one damping fluid port is arranged.
- a pressure medium may be provided in the pump working chamber, which is fluidically connected via the damping fluid connection with the first pressure chamber of the volume changing device.
- the pump working chamber is arranged on the piston side, in particular with respect to the diaphragm of the pump, and the pump delivery chamber is arranged on the side of the diaphragm facing away from the piston.
- a second storage tank which is preferably separately formed, or else equalization tank, pressurized wind tank or volume change device, is additionally mentioned.
- the present Pulsationsdämpfungssystem is particularly suitable for use in piping systems of piston pumps, where particularly large amplitudes and / or high frequencies of pressure fluctuations and pressure pulses occur.
- the damping can in particular by a time- and / or volume-regulated inlet or discharge of a lasskanal in the pump inlet, in particular in the immediately upstream of the pump chamber inlet port arranged pipe section of the pump inlet channel and / or in the pump outlet channel, in particular in the immediately downstream of the Pumpenschlass - Completely arranged pipe section of the pump outlet channel, located conveying fluid in the direction towards or away from the respective second storage tank done.
- This control of the fluid flow can be effected, for example, by releasing an inflow of the fluid from the pump inlet channel or pump outlet channel into the second storage container or an outflow of the fluid from the second storage container into the pump inlet channel or pump outlet channel.
- a pump inlet channel means a pump inlet-side pipe or a suction pipe and a pump outlet channel a pump outlet-side pipe or a high-pressure pipe
- the pump inlet channel is usually connected to a fluid source for sucking the conveying fluid and the Pump outlet channel a further transport of the fluid to be delivered is used.
- the pump can be embodied in particular as a conventional piston pump with, for example, a single pump chamber or as a piston diaphragm pump with a pump chamber comprising a pump working chamber and a pump delivery chamber.
- several pistons or piston pumps are usually used which suck the fluid to be conveyed from a common intake line with a central storage container and convey it into a common high-pressure line on the high-pressure side.
- the second storage container is filled in a first region with the conveying fluid to be conveyed and in a second region with a compressible gas volume.
- the delivery fluid is arranged in a lower region, and in an upper region, a pressurized, that is to say a pressurized, gas volume is arranged.
- the second storage container may be particularly preferably designed as a volume and / or pressure storage container in which the delivery fluid for delivery is advantageously temporarily storable, in particular with the formation of a volume in the second storage container.
- the second storage tank is designed as a pressure vessel.
- the gas volume located in the second region which is preferably arranged at the top, can be in operative connection, for example, directly or indirectly with the fluid located in the preferably lower region.
- the storage tank can be provided directly and / or indirectly via a control valve at least temporarily with a separate gas source be fluidly connected.
- no additional component such as a partition
- a fluid level can be formed.
- the respective volume of the first and second regions can be changed relative to one another, in particular the second region can be reduced when the first region is enlarged and the second region can be increased when the first region is reduced.
- a particularly efficient damping can be effected. This flow is preferably controllable, for example by releasing an inflow or outflow of the fluid from the pump inlet channel or pump outlet channel into or out of the second storage container.
- the second storage tank in particular the first area of the second storage tank, is preferably connected to the pipe section of the pump inlet channel or the pump outlet channel via a branch pipe, and a throttle valve is arranged in the branch pipe.
- a throttle valve is arranged in the branch pipe.
- the inlet-side second storage tank, or the first area of this second storage tank, via a first branch pipe with the pipe section of the pump inlet channel and the outlet side second storage tank, or the first portion of this second storage tank, via a second branch pipe with the Pipe section of the pump outlet channel be connected, wherein in the branch pipes in each case a throttle valve is arranged.
- controllable means, in particular, that a flow through the throttle and a reduction in pressure caused thereby can be carried out with a defined amount of time and quantity, preferably predictable, particularly preferably automatically.
- the first storage container arranged in the pump inlet channel is preferably provided with the second storage container via a fluid inlet with a delivery fluid source and via a fluid outlet with the second storage container and / or the first storage container arranged in the pump outlet channel via a fluid inlet with the second storage container and via a fluid outlet a derivative directly or indirectly fluidly connected.
- the second storage tank may be disposed in the pump inlet channel downstream of the first storage tank and in the pump outlet channel upstream of the first storage tank.
- the gas volume of the second storage container and / or the gas volume of the first storage container can be connected directly and / or indirectly via a control valve to a separate gas source.
- a control valve to a separate gas source.
- the control can be effected, for example, by means of a control valve, the control of the control valve being arranged, for example, via at least one pressure sensor arranged in the pump inlet channel and / or the pump outlet channel and a PID control (proportional integral differential control) suitable for this purpose. can be done to control the control valves.
- control valve of a storage tank arranged on the pump inlet side can be actuated in dependence on a pressure prevailing in the pump inlet channel and / or the control valve of a storage tank arranged on the pump outlet side as a function of a pressure prevailing in the pump outlet channel.
- the respective control valve can also be actuated as a function of a pressure prevailing in the pump chamber, for which purpose the pressure sensor is advantageously arranged in the region of the pump chamber.
- the gas volume of the second storage tank is fluidly connected to the gas volume of the first storage tank, in particular via a separate secondary pipe, such as a gas pressure line.
- a separate secondary pipe such as a gas pressure line.
- a check valve and the second storage tank, or the branch of the branch pipe leading into the second storage tank are arranged in the pipe section arranged between the pump chamber and the first storage tank. This allows the pump to work very efficiently.
- the pump inlet-side second storage container is in the flow direction downstream of the pump inlet-side first storage container and upstream of the pump chamber, in particular upstream of a check valve, and / or the pump outlet side second storage container with the pump outlet channel downstream of the pump chamber, in particular downstream of a check valve. and fluidly connected upstream of the pump outlet side first storage tank.
- the second storage container is arranged on a fluid side, facing away from the piston pump, of the check valve arranged in the respective pump channel. This allows a particularly effective pressure pulsation damping.
- a fluidic separation of the first region and the second region can take place by means of the different densities of the fluid in the first region and of the gas in the second region.
- no release agent is thus provided between the first region and the second region.
- the regulation of the fill level in the respective storage container can take place via a regulation of the gas pressure.
- a displacement body is arranged, in particular as a sliding wall, displaceable Piston or displaceable membrane is formed.
- the pressure prevailing in the storage container can act directly on the displacement body, in particular as a counterforce to a force applied by the fluid.
- the displacement body is designed as a flexible membrane.
- the storage container can thus in particular each have a first pressure space filled with the fluid and a second pressure space which is fluidically separated from the latter by means of the displacement body and is operatively connected thereto and preferably filled with the gas.
- Such an embodiment is particularly advantageous for conveying fluids with solid particles and, in particular for such fluids, enables safe and low-maintenance pulsation damping.
- a pressure of the medium to be delivered, in particular of a fluid mixed with solids, on the pump inlet side or pump outlet side can be transmitted to the second region of the storage container, in particular to a gaseous fluid, in a particularly simple and secure manner.
- the displacement body can preferably shift in the direction of the first or the second region.
- the respective volume of the first and second regions can be changed relative to one another in a relatively simple manner.
- the second region or the second pressure chamber volume can be reduced and increased when the first region or pressure chamber volume is increased Reduction of the first area of the second area can be increased.
- a flow of the fluid located in the pump inlet channel or pump outlet channel into or out of the second storage container can be controlled particularly advantageously, and a particularly efficient damping can be effected.
- the displacement body can be acted upon by a counter-pressure, for example via a spring-elastic element, with respect to the pressure present on the conveying fluid side.
- the displacement body is preferably designed as a piston, in particular a separating piston, of a closed system, such as a piston-cylinder unit.
- the counterpressure acting on the piston or the membrane can be effected, for example, by a medium located in the correspondingly arranged and pressurized second pressure chamber.
- the piston pump is designed as a piston diaphragm pump with a pump working chamber and a fluid pumping chamber separated from and fluidly connected thereto.
- the pump working chamber is arranged on the piston side, in particular with respect to the diaphragm of the pump, and the pump delivery chamber is arranged on the side of the diaphragm facing away from the piston.
- the pump working chamber and the pump delivery chamber form a common pump chamber.
- FIG. 1 - a piston diaphragm pump known from the prior art
- FIG. 2a shows a first embodiment of a pulsation damping system according to the invention on a piston diaphragm pump
- FIG. 2b shows an expanded variant of the pulsation damping system from FIG. 2a;
- FIG. 3 shows a third embodiment of a pulsation damping system according to the invention on a classic piston pump
- FIG. 4a shows a fourth embodiment of a pulsation damping system according to the invention on a classic piston pump
- FIG. 4b shows an expanded variant of the pulsation damping system
- FIG. 5 a piston diaphragm pump known from the prior art
- FIG. 6 shows a first embodiment of a pulsation damping system according to the invention on a piston diaphragm pump
- FIG. 7 shows a second embodiment of a pulsation damping system according to the invention on a piston diaphragm pump
- FIG. 1 shows the basic structure of a piston diaphragm pump 101 known from the prior art with those pipelines 6, 13 connected thereto and the intermediate storage container 8, 15, or reservoir, which are advantageous for promoting a delivery requirement.
- the oscillating movement of the piston 1 is thereby transferred to a pressure medium 2a located in a first pressure chamber 2 designed as a pump working chamber.
- This pressure medium 2a is operatively connected via a flexible membrane 3 to the second pressure chamber 4, which in the present case is designed as a pump feed chamber, with respect to a pressure transmission.
- Both pressure chambers 2, 4 are surrounded by a pressure-resistant housing 5.
- the medium 9 to be conveyed is located in the pump delivery chamber 4, which medium can enter the pump delivery chamber 4 via a fluid inlet 6a and exit the pump delivery chamber 4 through a fluid outlet 13a.
- the medium 9 to be conveyed can be sucked into the pump delivery chamber 4 through the fluid inlet 6a from an intake line 6 in which a mammalian valve 7 designed as a check valve is located.
- a reservoir 8 also called a pressure vessel, which is partly filled with the fluid 9 to be delivered, and in the upper part thereof pressurized gas 10, such as compressed air, is located.
- the storage container 8 is in this case connected to a source 11, which has an increased geodetic height in relation to the pump 101, in order thus to be able to provide the required suction pressure.
- the reservoir can also be acted upon by so-called feed pumps, not shown here, which then generate the necessary suction pressure in the suction line 6.
- the fill level in the reservoir 8 is controlled by the pressure of the gas 10.
- the gas pressure 10 can be varied in particular via a control valve 12 so that a predetermined fill level in the reservoir 8 is adjusted as accurately as possible.
- the reservoir 8 is connected via a arranged in the gas volume 10 pneumatic line and via the control valve 12 to a gas source.
- the pump delivery chamber 4 of the pump 101 is connected to a further storage container 15 via an outlet line 13, in which a pressure valve 14 designed as a check valve is located.
- a pressure valve 14 designed as a check valve is located.
- the medium 9 to be pumped is likewise located in the lower region of the outlet-side storage container 15, while a gas or air volume 17 under pressure is located above it.
- the level of the reservoir 15 can be controlled via a fluidically connected to the air volume 17 control valve 18 and an adjoining, not shown gas source. Via a discharge line 19, the volume flow generated by the pump 101 can then be supplied to the intended application.
- the pulsation damper system 100 Due to the oscillating movement of the piston 1, an acceleration effect is exerted on the fluid medium 9 to be conveyed, which can lead to pulsations in the pressure chambers 2 and 4, the adjacent suction tube 6 and the discharge tube 13.
- the pulsation damper system 100 is presented below, by means of which, above all, the pulsations which propagate when the medium 9 is sucked can be reduced.
- FIG. 2a shows a first embodiment of the pulsation damping system 100 according to the invention.
- This embodiment additionally provides, for example, a damping device 103 on the typical structure of a piston diaphragm pump system shown in FIG.
- the damping device 103 comprises in particular a volume change device 105 designed as a piston-cylinder unit, or also called a volume displacement unit.
- the volume change device 105 has a cylinder 21 with a first pressure chamber 22 arranged therein, connected to the pump working chamber 2 via a damping fluid connection 20a and a hydraulic connecting line 20, and a second pressure chamber 24 fluidically separated from the first pressure chamber 22 by means of a separating piston 23 ,
- a part of the pressure medium contained in the pump working chamber 2 in particular a hydraulic oil, can flow into or out of the first pressure chamber 22 of the cylinder 21.
- the second pressure chamber 24 is connected via a pressure line 25 to the gas volume 10 of the pressure vessel 8 arranged on the inlet side, so that in the second pressure chamber 24 an average pressure is established which corresponds to the mean pressure in the reservoir 8.
- a throttle point 26 is introduced into the hydraulic connection line 20. If there is an increase in pressure due to pulsations in the pump chamber 2, this results in a volume flow from the pump working chamber 2 into the first pressure chamber 22 if the separating piston 23 is not in its right end position 28. As it flows through the throttle point 26, a part of the pulsation energy is converted into heat and thus reduces the magnitude of the pressure pulsations.
- the system can permanently convert pulsation energy into heat during the suction phase, as long as the movement of the separating piston 23 is not prevented by reaching one or one of the end stops or cylinder stops 27 or 28.
- the pulsation damping system 100 according to FIG. 2 a is additionally expanded by a damping device 104 on the discharge side of the pump 101.
- a damping device 104 Analogous to the damping of the pulsations during the suction phase, such a damper 103 can also be used for the discharge side of the pump 101.
- the pump working chamber 2 is fluidly connected via a pressure line 29 with an additional volume changing means 106.
- the volume changing means 106 is basically the same as the volume changing means 105.
- the volume changing device 106 in turn has a cylinder 30 with a first pressure chamber 32 arranged therein, connected via a damping fluid port 29a and a hydraulic connecting line 29 to the pump working chamber 2, and a second pressure chamber 33 fluidically separated from the first pressure chamber 32 by means of a separating piston 31 on.
- the first pressure chamber 32 is filled with the pressure medium 2a, the second pressure chamber with gas or air.
- this gas or the second pressure chamber 33 is connected via a pressure line 34 with the gas volume 17 of the reservoir 15 on the discharge side of the pump 101.
- the suction phase of the pump 101 prevail in the pump chamber 2, 4 so low pressures that the pressure in the gas volume 17 moves the separating piston 31 to a first stop 35 and this persists there until the onset of the compression phase.
- the opening pressure of pressure valve 14 is exceeded, it is opened and at the same time in the first pressure chamber 32 generates an increase in pressure, whereby a movement of the piston 31 to, in FIG. 2b, on the right in the direction of the second stop 37 is effected.
- FIG. 3 shows a further application of the pulsation damping system 100 to a conventional or classical piston pump 102, whereby the arrangement shown in the preceding figures with the pipelines 6, 13, in particular supply line 6 and discharge line 13 adjoining the pump 102, is also shown for the fluid medium 2a to be conveyed, as well as the intermediate storage containers 8 and 15, which are each advantageously advantageously arranged therein to promote a delivery requirement.
- the pump 102 is configured differently in FIG. In this context, it should again be noted that the type of piston pump for the present invention is of minor importance.
- the fluid medium 2a to be delivered is used directly as the medium for damping the pressure pulsations occurring in the pump chamber 4 and the pipelines 6 and 13.
- the fluid medium 2a can be conveyed not only through the pipelines 6, 13 into or out of the pump chamber 4, but also via the pressure lines 20 and 29 additionally connected to the pump chamber 4 via a respective damping fluid port 20a, 29a is - otherwise the same function as in the arrangement of Figure 2b - now in the pump chamber 4 located fluid medium 2a for damping in addition - depending on the operation of the piston 1, in particular suction or printing - towards or away from the respective inlet side and outlet side Damping device 103, 104 passed, in particular by the arranged in the respective pipe 6, 13 throttle body 26, 36 for damping the pressure pulsations, in particular by converting the pressure energy into heat.
- FIGS. 4a and 4b each show a further possible application of the pulsation damping system 100.
- the active principle of the pulsation damping system 100 according to the invention can also be used in such a pump arrangement.
- the second pressure space 24 provided on the inlet-side volume change device 105 and, as shown in FIG. 4 b, also the second pressure space 33 provided on the outlet-side volume change device 106 are each connected via a pressure line.
- pressure line 34 - connected via a control valve 37, 38 with an external compressed air supply, not shown.
- the gas pressure present in the respective second pressure chamber 24, 33 can consequently be adjusted and regulated via the respective control valve 37, 38, in particular by the respective pneumatic pressure in the second pressure chamber 24, 33 to the mean pressures of the suction line 6 or Adjust pressure line 13.
- the respective control valve 37, 38 in particular by the respective pneumatic pressure in the second pressure chamber 24, 33 to the mean pressures of the suction line 6 or Adjust pressure line 13.
- the pressure in the respective line 6, 13 or, as shown in FIG. 4a via corresponding pressure sensors 39 and 40 can be determined directly via at least one pressure sensor 43 on the pump chamber 4 and via regulating devices 41 and 42 are automatically adjusted in the second pressure chambers 24 and 33.
- mechanical control valves are also conceivable which convert the hydraulic pressure into a corresponding pneumatic pressure.
- the scope of the present invention is not limited to the described embodiments.
- the structure of the piston pump and of the adjoining main pipelines for conveying a fluid medium can - without changing the essence of the invention - be thoroughly modified.
- the design of the volume change devices 105, 106 can be designed differently, for example, instead of the separating piston 23, 31 a membrane can be provided.
- FIG. 5 shows the basic structure of a piston diaphragm pump 2101 known from the prior art with adjoining pipelines 206, 213 as well as first storage containers 208, 215 or also respectively arranged therein for conveying a pumped medium in an advantageous manner - Schen or reservoir called, shown.
- the oscillating movement of the piston 201 is transferred to a pressure medium located in a first pressure chamber 202 designed as a pump working chamber.
- This pressure medium is operatively connected via a flexible membrane 203 with the second pressure chamber 204 designed here as a pump delivery chamber with respect to a pressure transmission.
- Both pressure chambers 202, 204 are surrounded by a pressure-resistant housing 205.
- the fluid medium 209 to be delivered is located in the pump delivery chamber 204, which can enter the pump delivery chamber 204 via a fluid inlet from a pump inlet passage 206 and exit through a fluid outlet from the pump delivery chamber 204 into a pump outlet passage 213.
- the fluid 209 to be delivered can be sucked into the pump delivery chamber 4 from the pump inlet channel 206, which is also referred to as the suction line, in which a mammal valve 207 designed as a check valve is located.
- the inlet-side first storage tank 208 which is additionally arranged in the suction line 206 of the pump 2101 in the here presented arrangement as a storage tank, is in a lower partial area 208a with the fluid 209 to be delivered and in an upper partial area 208b with a pressurized gas 210, such as compressed air, filled.
- the lower region 208a of the first storage container 208 is fluidically connected to the pump inlet channel 206, in particular via a conveying fluid inlet 206a facing a conveying fluid source 211, which is not illustrated in greater detail, and via a pipe section 206c of the pump inlet channel 206 connecting to the first storage container 208 with the pump chamber 204 Delivery fluid outlet 206b.
- the source 211 is typically a tank having an increased geodetic height with respect to the pump 2101 to provide the necessary suction pressure.
- the lower portion 208a and the upper portion 208b of the The first storage container 208 may in principle be fluidly separated from one another by a displacement body formed, for example, as a membrane.
- the lower part region 208a and the upper part region 208b are separated due to the different arrangement and densities of the fluid 209 and the gas 210, which form a filling level 232 at the separating surface, the respective filling level 232 in the first storage container 208 being above the pressure of the gas 210 is regulated.
- the gas pressure 210 can be varied in particular via a control valve 212 so that a predetermined fill level 232 in the first storage tank 208 is adjusted as accurately as possible.
- the inlet-side first storage container 208 is connected via a pneumatic or pressure line arranged in the region of the gas volume 210 and via the control valve 212 to a gas source (not shown).
- this intake-side first storage tank 208 can also be acted upon by so-called feed pumps (not shown), which then generate the necessary suction pressure in the intake line 6.
- the outlet-side first storage tank 215, in particular a lower area 215a of the first storage tank 215, is fluidically connected to the pump outlet channel 213, in particular via a pump inlet 213c of the pump outlet channel 213 connected to a pumping chamber 204 with the outlet side first storage tank 215 connected conveyor fluid inlet 213a, and via a conveyor fluid outlet 213b, which is connected to a delivery fluid discharge line 219, not shown in more detail.
- the fluid 209 to be pumped is also located in the lower region 215a of the outlet-side first storage container 215, while in the upper region 215b there is a gas under pressure - or air volume 217 is located.
- the lower portion 215a and the upper portion 215b are in this case also not by a separate release agent, such as a displacement body, fluidly separated from each other, but due to the different arrangement and densities of the fluid 209 and the gas 217 separiert, which form a level height 216 at the interface.
- the level 216 of the outlet-side first storage container 215 can be regulated via a control valve 218, which can be fluidically connected to the gas volume 217, and to a gas source, which is connected thereto in detail. Via a discharge line 219, the volume flow of the delivery fluid 209 generated by the pump 2101 can be supplied to a non-illustrated intended application.
- the mammary valve 207 automatically opens and the fluid 209 to be delivered flows from the inlet-side first storage tank 208 into the first storage tank 208 Pump delivery chamber 204.
- the piston 201 As soon as the piston 201 has reached the extremely left-hand position shown in FIG. 5, it then moves again to the right. This results in a compression of the two pressure chambers 202 and 204. This increase in pressure causes the mammary valve 207 closes and no further fluid 209 is sucked more. If the piston 201 moves further and further to the right, the pressure in the two pressure chambers 202, 204 continues to increase until the pressure prevailing in the outlet line 213 and in the first storage tank 215 is exceeded. As a result, the pressure valve 214 opens and the pump 2101 delivers the fluid 209 from the pump delivery chamber 204 into the reservoir 215 until the piston 201 has again reached the extreme right position and the process repeats itself.
- the pulsation damper system 2100 Due to the oscillating movement of the piston 201, acceleration effect is exerted on the fluid medium 209 to be conveyed, which can lead to pulsations in the pressure chambers 202 and 204, the adjacent suction tube 206 and the discharge tube 213.
- the pulsation damper system 2100 is presented below, by means of which, in particular, the pulsations which propagate when the fluid 209 is aspirated can be reduced.
- FIG. 6 shows a first embodiment of the pulsation damping system 2100 according to the invention.
- this refinement additionally provides, on the typical structure of a piston diaphragm pump system shown in FIG. 5, a second storage container 220 arranged on the pump inlet side.
- the second storage container 220 is likewise designed in the manner of a storage container or pressure vessel and has a first region or pressure chamber 220a and a second pressure chamber 220b.
- the present lower area 220a of the inlet-side second storage tank 220 is fluidically connected to the pump inlet channel 206 via a branch pipe 221 and filled with the delivery fluid 209.
- connection of the branch pipe 221 to the pump inlet channel 206 is in particular as close as possible to the pump chamber 204, but always in the flow direction before, ie upstream of the check valve or inlet valve 207, in particular in the pipeline section 206c.
- a part of the delivery fluid 209 contained in the pump inlet channel 206 can flow into or out of the first pressure chamber 220a.
- a gas volume 225 is formed in the upper area or pressure space 220b, as is the case with the first storage tank 208 as well.
- the second pressure chamber 220b is connected via a pressure line 223 to the gas volume 210 of the first storage container 208 arranged on the inlet side, so that an average pressure which corresponds to the mean pressure in the first storage container 208 is established in the second pressure chamber 220b.
- pressure pulsations in the suction line 6 of the pump 2101 occur, they lead to a volume flow of the fluid 209 to be pumped from the pump inlet channel 206 through the branch pipe 221 into the first pressure chamber 220a of the pump 211 during an increase in pressure second storage tank 220.
- a restriction 224 is introduced into the branch pipe 221.
- the pressure in the gas-filled pressure chamber 220b leads to an increased counterpressure and consequently to a displacement, in particular lowering of the level 222 and a volume flow of the fluid 209 the first pressure chamber 220a in the pump inlet passage 206, wherein at the throttle point 224 again pressure energy is converted into heat, and thus the pulsation is further reduced.
- the mammary valve 207 again closes and the fluid 209 to be pumped is conveyed via the line 213 into the outlet-side first storage container 215.
- a short-term pressure reduction can occur in the suction tube 206, as a result of which a portion of the fluid 209 can again flow out of the second storage container 220 back into the suction line 206, where hydraulic energy is converted into heat again when the throttle 224 flows through, and the pulsations is further reduced.
- the system can permanently convert pulsation energy into heat, especially during the suction phase.
- the tanks 208, 220 Since slight differences in average pressures in the containers 208 and 220 may occur due to friction losses and flow effects in the intake manifold 206, the tanks 208, 220 generally form different average geodetic filling levels 222, 232. In order to prevent the container 220 from running empty or becoming overfilled, which would considerably impair the function of the damper, the regulation of the fill level 232 is in the container 208 and the installation height and the size of the container 220 matched to each other.
- the damper shown in FIG. 6 thus reduces the pulsations that prevail in the suction region of the pump 2101. Since, however, comparable pulsations can also occur on the discharge side of the pump 2101, a second embodiment of the pulsation damping system 2100 is shown in FIG. 7, in which a pulsation damper for the pressure line is provided in addition to the suction damper.
- the pulsation damping system 2100 according to FIG. 6 is additionally widened by a second storage tank 226 arranged on the discharge side of the pump 2101 and by a throttle point 230 in the supply line to this second storage tank 226.
- the pressure pulsation energy is also converted into heat during the flow through the fluid 209 through the throttle 230 in the arrangement on the discharge side.
- Similar assumptions and requirements apply to the intake-side damper.
- the construction and operation of the outlet-side second storage tank 226 and its integration into the outlet-side piping system therefore essentially corresponds to the arrangement of the second storage tank 220 on the pump inlet side.
- a region or pressure chamber 226a filled with the fluid 209 is formed in a lower part, and an area or pressure chamber 226b filled with a gas volume 231 is formed in an upper part.
- the lower region 226a is fluidically connected to the pump outlet channel 213 via a branch pipe 227.
- the connection of the branch pipe 227 to the pump outlet channel 213 is as close as possible to the pump chamber 204, but always in the flow direction after, that is arranged downstream of the check or outlet valve 214, in particular in the region of the pipe section 213c.
- a gas volume 231 is formed in the upper pressure chamber 226b, as is the case with the inlet-side first storage container 208 as well.
- the second pressure chamber 220b is connected via a pressure line 229 to the gas volume 217 of the first storage container 215 arranged on the outlet side, so that an average pressure which corresponds to the mean pressure in the first storage container 215 adjusts in the second pressure chamber 226b.
- this pressure increase causes the fluid 209 to be pumped from the pressure line 213 into the second storage container 226 the pulsation energy is converted into heat and thereby pressure pulsations are reduced.
- the pressure in the pump outlet channel 213 is subsequently reduced, the pressure in the gas-filled pressure chamber 226b leads to an increased back pressure and consequently to a displacement, in particular lowering of the level 228 and a volume flow of the fluid 209 from the first pressure space 226a in the pump outlet 213, wherein at the throttle point 230 again pressure energy is converted into heat, and thus the pulsations are further reduced.
- this system can not only permanently convert pulsation energy into heat during the suction phase but also during the pressure phase.
- the construction of the piston pump and the adjoining main pipelines for conveying a fluid medium can - without changing the essence of the invention - be thoroughly modified.
- the first storage container it is not absolutely necessary for the first storage container to be fluidically connected to the second storage container.
- the configuration of the first and second storage container may be formed differently, for example, instead of the membrane disposed therein, a partition wall or a separating piston may be formed.
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19718326.2A EP3791068B1 (de) | 2018-05-07 | 2019-04-15 | Pulsationsdämpfungssystem |
US17/053,073 US20210231113A1 (en) | 2018-05-07 | 2019-04-15 | Pulsation damping system |
PE2020001795A PE20210092A1 (es) | 2018-05-07 | 2019-04-15 | Sistema de amortiguacion de pulsaciones |
CN201980031194.2A CN112469898A (zh) | 2018-05-07 | 2019-04-15 | 脉动阻尼系统 |
AU2019266890A AU2019266890B2 (en) | 2018-05-07 | 2019-04-15 | Pulsation damping system |
BR112020022574-6A BR112020022574A2 (pt) | 2018-05-07 | 2019-04-15 | sistema de amortecimento de pulsação |
AU2023204415A AU2023204415B2 (en) | 2018-05-07 | 2023-07-07 | Pulsation Damping System |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102018110848.6 | 2018-05-07 | ||
DE102018110847.8 | 2018-05-07 | ||
DE102018110848.6A DE102018110848A1 (de) | 2018-05-07 | 2018-05-07 | Pulsationsdämpfungssystem |
DE102018110847.8A DE102018110847A1 (de) | 2018-05-07 | 2018-05-07 | Pulsationsdämpfungssystem |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2019214905A1 true WO2019214905A1 (de) | 2019-11-14 |
Family
ID=66223720
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2019/059600 WO2019214905A1 (de) | 2018-05-07 | 2019-04-15 | Pulsationsdämpfungssystem |
Country Status (7)
Country | Link |
---|---|
US (1) | US20210231113A1 (de) |
EP (1) | EP3791068B1 (de) |
CN (1) | CN112469898A (de) |
AU (2) | AU2019266890B2 (de) |
BR (1) | BR112020022574A2 (de) |
PE (1) | PE20210092A1 (de) |
WO (1) | WO2019214905A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2607592A (en) * | 2021-06-07 | 2022-12-14 | Mhwirth Gmbh | Pump pulsation damping |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113018577B (zh) * | 2021-03-29 | 2022-07-08 | 四川大学华西医院 | 一种静脉导管冲洗装置 |
CN114876915B (zh) * | 2022-04-08 | 2023-03-17 | 北京航空航天大学 | 一种自调压的气液耦合式流体脉动消振装置 |
Citations (7)
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DE8111221U1 (de) * | 1981-04-14 | 1981-08-27 | Loewe Pumpenfabrik GmbH, 2120 Lüneburg | Dosiervorrichtung |
US4477237A (en) * | 1982-05-10 | 1984-10-16 | Grable William A | Fabricated reciprocating piston pump |
US5165869A (en) * | 1991-01-16 | 1992-11-24 | Warren Rupp, Inc. | Diaphragm pump |
EP0679832A1 (de) | 1994-04-26 | 1995-11-02 | Lüthin, Heinz | Vorrichtung zum Reduzieren von Druckpulsationen in Hydraulikleitungen |
WO1998049040A1 (fr) * | 1997-04-25 | 1998-11-05 | Unisia Jecs Corporation | Dispositif de freinage |
US20100115932A1 (en) * | 2008-01-22 | 2010-05-13 | Armin Kassel | Metering system |
DE102010024813A1 (de) * | 2010-06-23 | 2011-12-29 | Bis E.M.S. Gmbh | Odoriervorrichtung und Odorierverfahren |
Family Cites Families (6)
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US1627257A (en) * | 1924-10-24 | 1927-05-03 | Stevens Blamey | Hydraulically-operated diaphragm pump |
US2934025A (en) * | 1955-11-08 | 1960-04-26 | Wilson John Hart | Suction flow equalizer for mud pumps |
BE662393A (de) * | 1964-04-24 | |||
US3692433A (en) * | 1971-03-01 | 1972-09-19 | Sioux Steam Cleaner Corp | Damping and auxiliary pumping apparatus |
US6068448A (en) * | 1996-12-09 | 2000-05-30 | Sugino Machine Limited | Pressure hydraulic pump having first and second synchronously driven reciprocating pistons with a pressure control structure |
DE19706114C9 (de) * | 1997-02-17 | 2014-02-06 | Linde Hydraulics Gmbh & Co. Kg | Vorrichtung zur Pulsationsverminderung an einer hydrostatischen Verdrängereinheit |
-
2019
- 2019-04-15 WO PCT/EP2019/059600 patent/WO2019214905A1/de unknown
- 2019-04-15 AU AU2019266890A patent/AU2019266890B2/en active Active
- 2019-04-15 PE PE2020001795A patent/PE20210092A1/es unknown
- 2019-04-15 CN CN201980031194.2A patent/CN112469898A/zh active Pending
- 2019-04-15 EP EP19718326.2A patent/EP3791068B1/de active Active
- 2019-04-15 BR BR112020022574-6A patent/BR112020022574A2/pt unknown
- 2019-04-15 US US17/053,073 patent/US20210231113A1/en active Pending
-
2023
- 2023-07-07 AU AU2023204415A patent/AU2023204415B2/en active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE8111221U1 (de) * | 1981-04-14 | 1981-08-27 | Loewe Pumpenfabrik GmbH, 2120 Lüneburg | Dosiervorrichtung |
US4477237A (en) * | 1982-05-10 | 1984-10-16 | Grable William A | Fabricated reciprocating piston pump |
US5165869A (en) * | 1991-01-16 | 1992-11-24 | Warren Rupp, Inc. | Diaphragm pump |
EP0679832A1 (de) | 1994-04-26 | 1995-11-02 | Lüthin, Heinz | Vorrichtung zum Reduzieren von Druckpulsationen in Hydraulikleitungen |
WO1998049040A1 (fr) * | 1997-04-25 | 1998-11-05 | Unisia Jecs Corporation | Dispositif de freinage |
US20100115932A1 (en) * | 2008-01-22 | 2010-05-13 | Armin Kassel | Metering system |
DE102010024813A1 (de) * | 2010-06-23 | 2011-12-29 | Bis E.M.S. Gmbh | Odoriervorrichtung und Odorierverfahren |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2607592A (en) * | 2021-06-07 | 2022-12-14 | Mhwirth Gmbh | Pump pulsation damping |
GB2607592B (en) * | 2021-06-07 | 2023-07-05 | Mhwirth Gmbh | Pump pulsation damping |
Also Published As
Publication number | Publication date |
---|---|
AU2019266890A1 (en) | 2020-11-19 |
AU2019266890B2 (en) | 2023-04-13 |
PE20210092A1 (es) | 2021-01-11 |
AU2023204415A1 (en) | 2023-08-03 |
EP3791068A1 (de) | 2021-03-17 |
EP3791068B1 (de) | 2022-02-23 |
CN112469898A (zh) | 2021-03-09 |
BR112020022574A2 (pt) | 2021-02-02 |
AU2023204415B2 (en) | 2024-03-07 |
US20210231113A1 (en) | 2021-07-29 |
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