WO2010017997A2 - Pumpenvorrichtung - Google Patents
Pumpenvorrichtung Download PDFInfo
- Publication number
- WO2010017997A2 WO2010017997A2 PCT/EP2009/005928 EP2009005928W WO2010017997A2 WO 2010017997 A2 WO2010017997 A2 WO 2010017997A2 EP 2009005928 W EP2009005928 W EP 2009005928W WO 2010017997 A2 WO2010017997 A2 WO 2010017997A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pulsator
- working space
- line
- pressure
- pump head
- Prior art date
Links
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
- 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
- F04B53/06—Venting
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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
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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
- 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
- F04B53/08—Cooling; Heating; Preventing freezing
Definitions
- the invention relates to a pump device with a pulsator as a drive element for a main pump head, which is located in a feed line and whose working space is provided with a suction-side check valve and a pressure-side check valve, according to the preamble of claim 1.
- a membrane pulsator is understood to mean a
- Piston diaphragm pump corresponds, which does not necessarily have suction and pressure side check valves, but otherwise usually has all the features of a piston diaphragm pump.
- a person skilled in the art understands a piston diaphragm pump to mean a piston pump coupled to a diaphragm, the deflection of the piston being transmitted to the diaphragm via a hydraulic coupling.
- Membrane pulsators, in particular as well as piston diaphragm pumps can have a preferably diaphragm-controlled refilling and / or venting device for the hydraulic fluid, as is known, for example, from EP 0 085 725 A1.
- the invention relates to a pump device with a pulsator, in particular a membrane pulsator, as a drive element for a main pump head, which is located in a feed line and the working space is provided with a suction-side check valve and a pressure-side check valve.
- the working space of the pulsator is connected directly to the working space of the main pump head via a suspension line filled with pumping medium, in such a way that the pulsator oscillates in the conveying medium from the delivery line sucks into the working space of the main pump head or pushes out of the work space.
- the pump device according to the invention is particularly well suited for conveying suspensions, such as mixtures of biomass and supercritical water, and in particular for high pressures and temperatures.
- Pumps of this type are known from EP 0919724 Bl and EP 1898093 Al.
- a lying in the feed line main pump head is driven by a further pump head, which is referred to as a pulsator.
- a pump device is also referred to as a "remote head” pump.
- Such pumping devices are typically used to pump high solids, high temperature liquids.
- the known pumps can not be used readily in particularly aggressive media, such as supercritical aqueous solutions, especially when processes are present with very high throughput at high temperatures and high pressures.
- the invention has for its object to provide a pump device of the type mentioned, which can be used for pumping aggressive fluids at high temperature, and yet operates at low cost with high reliability, which is why in particular an entry of solid particles are avoided in the pulsator should.
- a pump device with a pulsator as a drive element for a main pump head which is located in a feed line and the working space is provided with a suction-side check valve and a pressure-side check valve, indicated, wherein the working space of the pulsator via a filled with conveying medium shuttle with the working space of the main pump head is connected in such a way that the pulsator draws in an oscillating medium from the delivery line into the working space of the main pump head or pushes out of the working space, a vent valve is provided for venting the working space of the pulsator, wherein the vent valve is a timed valve and / or a pressure-controlled double seat valve and / or a device for introducing a liquid into the working space of the pulsator and / or the pendulum line is provided.
- a timed valve and / or a pressure-controlled double-seat valve has the advantage that the time in which the valve is open for venting, can be kept very short, which can avoid undesirable side streams, the increased entry of solid particles in the pulsator could result.
- the introduction of liquid into the working space of the pulsator or the replenishment of fluid into the working space to compensate for losses, for example by venting the working space has the advantage that a liquid balance does not have to be done by the driven main pump head and thus no solid particles from the main pump head transported to the pulsator.
- the liquid may be water and / or conveying medium and / or another suitable liquid.
- the time- and / or pressure-controlled venting valve may be a single-seated valve and / or a double-seated valve.
- the device for introducing a liquid into the working chamber of the pulsator and / or the commutation line may comprise a time- and / or pressure-controlled refill valve and / or a refilling reservoir.
- the time- and / or pressure-controlled refill valve or venting valve can be controlled in time and / or pressure so that after a start-up phase of the process, the refill valve or vent valve is closed and / or the upper limit to close the time- and / or pressure-controlled Refill valve or
- Venting valve is increased after a start-up phase of the process and / or after a start-up phase of the process, the lower limit for closing the time- and / or pressure-controlled refill valve or vent valve is lowered.
- the pressure applied to the refill reservoir substantially corresponds to the pressure in the working space of the pulsator.
- the refill valve between the working space and the refill reservoir may be a time and / or pressure controlled valve.
- the working space of the pulsator can be connected via the and / or another venting valve to the suction side of the delivery line.
- the suction side of the conveying line for automatic venting can advantageously be arranged above the venting valve.
- the working space of the pulsator can be connected to the pressure side of the delivery line via the and / or a further venting valve.
- the vent valve in conjunction with a return pump positively controlled, in particular timed be.
- the working space of the pulsator can be connected via the and / or a further venting valve to a replenishment reservoir for compensating for leakage in the workspace of the pulsator and / or the pendulum line.
- the working chamber of the pulsator can be connected via the and / or a further venting valve to a collecting container for collecting and for possibly later recycling of conveying medium exiting during the venting.
- the valve may be time and / or pressure controlled so that it is closed at least above a certain pressure.
- the pulsator generates in the working space a continuously alternating pressure with a pressure phase and a suction phase.
- no venting should happen at least above a certain pressure in the working space to prevent a, albeit possibly small, pressure drop in the working space and thus a reduction of the flow from the pendulum ,
- the valve may be time and / or pressure controlled so that it is closed at least below a certain pressure.
- a vent should be avoided below a certain pressure in the working space of the pulsator, because by the, although low pressure drop, a greater suction and thus a stronger flow would occur in the pendulum, which could suck more solid particles in the pendulum. Therefore, the valve should be closed at least below a certain pressure in the working space.
- the venting takes place only in the temporal regions between the suction and the pressure phase, where a substantially low or no flow of the conveying fluid takes place in the transfer line.
- a substantially low or no flow of the conveying fluid takes place in the transfer line.
- a pump device is provided with a pulsator as a drive element for a main pump head, which is located in a feed line and the Working space is provided with a suction-side check valve and a pressure-side check valve, wherein the working space of the pulsator is connected via a pumping medium filled with the transfer line working space of the main pump head in such a way that the pulsator sucks oscillating fluid from the delivery line into the working space of the main pump head or pushes out of the working space, wherein the pump device has a refill reservoir for replenishing fluid, which is acted upon by a pressure which substantially corresponds to the system pressure.
- the pendulum line can be provided with a cooling in all embodiments of the invention.
- the pulsator can be arranged above the main pump head in all embodiments of the invention. Additionally or alternatively, according to the invention, the pendulum line can be aligned in a downward direction from the pulsator to the main pump head. Such embodiments of the invention have the advantage that the gravitational force additionally counteracts an entry of solid particles through the pendulum line in the pulsator.
- the pendulum line can be provided with a sink as a receiving space for solid particles in the pumped medium.
- the working space of the pulsator can at least temporarily be acted upon by a compensating medium for compensating for leakage loss.
- a pump device with a Pulsator specified as a drive element for a main pump head which is located in a feed line and the working space is provided with a suction-side check valve and a pressure-side check valve, the working space of the pulsator is connected via a conveyor medium filled with the transfer line working space of the main pump head in a manner in that the pulsator draws in an oscillating conveying medium from the delivery line into the working space of the main pump head or pushes it out of the working space, wherein the pendulum line is divided into at least two parallel sections at least in one section.
- the pendulum can also be divided over its entire course, i. that, for example, two or more parallel pendulum lines can be provided.
- inventions of the invention have the advantage that by providing a corresponding control, for example in the suction phase, the at least two subsections are opened and in the pressure phases at least one subsection (at two subsections preferably alternately one and the other subsection) at least partially and preferably completely at least during a part of the pressure phase is closed in order to prevent deposits of particulate matter in the subsections by the thus resulting in the other subsections and the higher outflow velocity.
- the volume of the parallel sections of the pendulum line and the volume of the parallel pendulum lines can each be at least as large as or preferably greater than the stroke volume of the pulsator.
- control valves can be provided for at least partially opening and closing the sections of the pendulum line or the parallel pendulum lines.
- a sensor system can be provided in order to synchronize the timing of the control valves with the respective phase position of the pulsator diaphragm.
- a sensor and / or switch can be provided which switches the control valve in at least one end position of the membrane of the pulsator.
- a sensor and / or switch for the other membrane layer can be provided to switch the control valve.
- the control valves could also be displaced into a closed position or partial closed position only during part of the pressure phase. It would also be conceivable to at least partially close different control valves during a pressure phase.
- the pendulum line can preferably be divided in the region upstream of the main pump head into a plurality of lines connected in parallel, preferably two lines connected in parallel, which are at least partially and preferably completely closed by a time-controlled and / or pressure-controlled valve.
- the time and / or pressure control should be set so that all lines are open as long as possible during the suction phase, so that the flow to the various Distributed parallel lines, while in the pressure phases alternately a sub-line with the full pressure and thus a much higher flow rate is applied. This should be an entry of solid particles in the pendulum line safely avoided.
- a pump device is provided with a pulsator as a drive element for a main pump head, which lies in a delivery line and whose working space with a suction-side check valve and a pressure-side Non-return valve is provided, wherein the working space of the pulsator is connected via a medium filled with transfer line with the working space of the main pump head in such a way that the pulsator sucks oscillating fluid from the delivery line into the working space of the main pump head or pushes out of the working space, the main pump head has at least two parallel suction side check valves (16, 161).
- This embodiment of the invention has the advantage that during the pressure phase in the line section between the exits of the two suction-side check valves, a higher flow velocity is generated, so that the risk of the entry of solid particles in the shuttle from the downstream with respect to the flow direction during the pressure phase suction side Check valve is reduced.
- the cross-section of the line receiving the downstream of the suction-side check valve with respect to the flow direction during the pressure phase can be greater than that Cross section of the other suction-side check valve receiving line.
- the cross sections of the two lines could be the same size or more than two lines and a corresponding number of suction-side check valves are provided.
- a larger cross-section of the relation to the flow direction during the pressure phase upstream suction-side check valve receiving line conceivable, which still offers a albeit lower advantage over the versions with only one suction-side check valve.
- a pump device is provided with a pulsator as a drive element for a main pump head, which lies in a delivery line and whose working space with a suction-side check valve and a pressure-side Non-return valve is provided, wherein the working space of the pulsator is connected via a pumped medium filled with the working space of the main pump head in such a way that the pulsator sucks oscillating fluid from the delivery line into the working space of the main pump head or pushes out of the working space, in the Pendelön a separating piston is arranged.
- the aforementioned embodiments of the pump device according to the invention may be formed with a double-acting pulsator and two pump circuits driven in opposite directions.
- a pump device is provided with a pulsator as a drive element for a main pump head, which lies in a delivery line and whose working space with a suction-side check valve and a pressure-side Check valve is provided, wherein the working space of the pulsator is connected via a pumped medium filled with the working space of the main pump head pump in such a way that the pulsator sucks oscillating fluid from the delivery line into the working space of the main pump head or pushes out of the working space, the pulsator is designed as a double-acting pulsator, one side of which is designed as a drive element for the main pump head, and the other side is acted upon by a pressure which substantially corresponds to the system pressure.
- Such embodiments of the invention with a double-acting pulsator for driving two mutually driven pump circuits are preferred, because a uniform promotion can be achieved.
- the pulsator can be driven at high suction pressures of for example 250 bar with a drive designed for much lower pressures, for example when a double-acting Piston is used, which only has to overcome the differential pressure between the pressure during the pressure phase in one Pulsatorhclient and the pressure during the suction phase in the other Pulsatorhphp.
- This advantage also applies to double-acting pulsators for driving only one pump circuit when the other side of the pulsator, which does not drive the pump circuit, is pressurized.
- the refill reservoir is pressurized to approximately the system pressure, so that the drive also takes place valve-controlled during the refilling process when the diaphragm is at its rear mechanical attachment reached, is not exposed to a higher pressure than the differential pressure between suction and pressure phase and thus does not have to be dimensioned larger, and the membrane is not destroyed at the inflow channels of their rear mechanical system.
- Hydraulic fluid can be provided, as it is known for example from EP 0 085 725 Al.
- compensation medium for compensating for leakage loss may be present in the diaphragm control chamber in a refill reservoir which is connected via a valve to the diaphragm control chamber, wherein the refill reservoir is pressurized to a pressure which is higher than the atmospheric pressure.
- This embodiment of the invention has the advantage that the pulsator with a drive (eg hydraulically, mechanically and / or pneumatically, eg a piston drive) are driven can, whose performance only the pressure difference between the suction and the pressure side must overcome.
- a shock on the drive, for example, the piston can be prevented by pressurizing the Nach Stirllreservoirs for leakage fading compensation in the diaphragm control chamber.
- this pressure in the refill reservoir can correspond approximately to the system pressure.
- a control system adapted to the system pressure pressure regulation can be provided in the refill reservoir, as described for example in EP 1 898 093 Al.
- the pulsator can be designed in membrane or tubular membrane construction.
- the pulsator can be designed in piston or plunger construction.
- a basic idea of the invention thus also lies in the fact that the pulsator acts on a main pump head which, in principle, is designed like a piston pump head, without, however, requiring a piston.
- a pump head suitable for high temperatures and pressures standard component can be used, which represents an overall cost-effective alternative to the known solutions by combining with a standard membrane pulsator, the principle of a "remote head" pump is maintained.
- the wear is further reduced by the fact that any particles present in the pumped medium do not come into contact with the workspace of the pulsator, since the liquid is moved in the pendulum line only in the scope of the pump stroke back and forth, and mixes only slightly with freshly sucked liquid.
- the pulsator can be designed in membrane or tubular membrane design as well as in piston or Plungerbauweise be executed. If the pulsator is a membrane pulsator, particles will not get to the membrane. Since high temperatures in the pumped medium decrease in the course of the transfer line, membrane pulsators can be used with inexpensive plastic membranes, such as PTFE, even at high pressures and high temperatures in the delivery line. Therefore, pumping devices according to the invention are particularly well suited for the conveyance of biomass in the production of biofuel.
- the inlet into the suction-side delivery line is preferably located above the ventilation valve, so that the gases escape from the working space automatically.
- a forced ventilation for example with a time and / or pressure-controlled valve may be present.
- a preferred embodiment of the invention is that the pendulum line is provided with a cooling.
- the commutation line is oriented downwards from the membrane pulsator to the main pump head. The particles thus remain in the region of the main pump head and are returned to the delivery line.
- the pendulum line is provided with a sink as a receiving space for solid particles in the pumped medium.
- an area is provided in the pendulum line, which is below the working space of the Membrane pulsator is located so that the particles accumulate there due to gravity and not get into the working space of the pulsator.
- the working chamber of the pulsator is acted upon by a compensating medium to compensate for leakage fade, so that a flow through the pendulum line and a migration of solid particles to the pulsator can be prevented.
- a further advantageous embodiment of the invention is to arrange a separating piston in the pendulum line.
- a low drive power is achieved in that a double-acting pulsator and two oppositely driven pump circuits are present, which is particularly advantageous when used in recirculation processes with high suction pressures.
- FIG. 1 shows a vertical section through a first embodiment of a pump device.
- FIG. 1A shows a vertical section corresponding to FIG. 1 through a further pump device according to the invention with a double-acting pulsator and two pump circuits driven in opposite directions.
- Fig. 2 is a circuit diagram of a composite of two pumping devices of Figure 1 pump configuration according to the invention.
- Fig. 3 features further embodiments of a pump device according to the invention.
- FIG. 4 is a circuit diagram corresponding to FIG. 2 of an alternative pump configuration according to the invention.
- FIG. 5 is a circuit diagram corresponding to FIG. 2 of a further alternative pump configuration according to the invention.
- FIG. 6 is a circuit diagram corresponding to FIG. 2 of a further alternative pump configuration according to the invention.
- FIG. 7 is a circuit diagram corresponding to FIG. 2 of a further alternative pump configuration according to the invention.
- Fig. 8 features further embodiments of a pump device according to the invention.
- Fig. 9 features further embodiments of a pump device according to the invention.
- Fig. 10 is a circuit diagram of a composite of two pumping devices of Figure 1 pump configuration according to the invention.
- Fig. 11 is a pV diagram of the time profile of the pressure of the pump over the stroke volume with an indication of a possible refilling during the printing phase.
- Fig. 12 is a pV diagram of the time course of the pressure of the pump over the stroke volume with an indication of a possible refill during the suction phase.
- a pump device 1 has a membrane pulsator 10 serving as a pulsator, a main pump head 11 and a transfer line 12.
- the main pump head 11 has an inlet 13 and an outlet 14 for installation in a delivery line whose pressure side is denoted by 5 and the suction side by 15.
- On the inlet side (suction side) is a suction-side check valve 16 and the output side (pressure side), a pressure-side check valve 17 is present.
- the conveying direction is marked with arrow 6.
- the main pump head 11 corresponds constructively to a pump head of a piston pump. However, he has no piston. His working space 18 is rather directly connected via the pendulum line 12 with a working space 20 of the Membranpulsators 10.
- the membrane pulsator 10 is provided with a connection 7 for the shuttle 12. Furthermore, there is a connection 8 for venting with a venting valve 9 (FIG. 2) and a connection 4 for a replenishment reservoir 30 (FIG. 2).
- a venting valve 9 FIG. 2
- a replenishment reservoir 30 FIG. 2
- the pendulum line 12 is filled with delivery fluid 21. It leads via a control input 22 of the main pump head 11 to the working space 20 of the membrane pulsator 10.
- the pendulum line 12 is provided with a cooling, which is formed by a cooling liquid applied to the cooling jacket 23. In this way, a temperature reduction of, for example, about 360 ° C. at the main pump head 11, as typically has the biomass to be pumped in the bio-fuel production, to about 100 0 C on the Membranpulsator 10 are made.
- the transfer line 12 contains the delivery liquid 21, which may also have solid particles 24, there is a portion 25 in the transfer line 12, which drops from the membrane pulsator 10 to the main pump head 11, and which opens directly into the working space 18 of the main pump head 11. At its lowest point, the transfer line 12 thus lies at the level of the working space 18 of the main pump head 11. The solids particles 24 thus remain in the working space 18 of the main pump head 11 due to gravity and do not reach the working space 20 of the membrane pulsator 10 pressure-side conveying line 5 is supplied.
- the membrane pulsator 10 has a membrane 26, which is hydraulically controlled via a diaphragm control chamber 27.
- the membrane material is preferably PTFE. Alternatively, elastomers, metallic materials or composite materials can be used.
- the membrane control chamber 27 is acted upon by a piston 28, which is driven mechanically, for example by a motor 29 (FIG. 2), and / or hydraulically and / or pneumatically, for example by alternately pressurizing the chambers adjacent to the disc 281.
- a refilling reservoir 30 filled with a compensating medium, which emits compensation medium into the working space 20 of the membrane pulsator 10 via a controlled valve 31 (FIG. 2).
- the feed is designated 4 in FIG.
- FIG. 2 comprises a double-acting pulsator with two pump devices as illustrated in FIG.
- the pump devices are connected in parallel in two counteracted branches A, B.
- a pumping operation will be described with reference to a branch.
- the pendulum line 12 and the working space 18 of the main pump head 11 are completely filled with conveying fluid.
- the suction-side check valve 16 and the pressure-side check valve 17 are closed.
- each main pump head 11 with a single-acting pulsator equal or opposite directions can be controlled.
- FIG. 3 is a detail of a second embodiment, a portion of a pendulum line 12 'is illustrated.
- a longitudinally slidably mounted according to double arrow 35 separating piston 32 in the pendulum line 12' is arranged. Any existing solid particles 24 thereby remain in a region 33 on the side of the main pump head 11 and can not reach a region 34 on the side of the membrane pulsator.
- Fig. IA shows an embodiment with a double-acting pulsator.
- FIG. 1A essentially corresponds to the embodiment shown in FIG. 1, wherein the pump device of FIG. 1 basically exists twice and is driven by a common piston 28.
- the double-acting pulsator is shown in Fig.
- the double-acting piston 28 describes an end position (on the right, the diaphragm 26 is bulged, ie the pressure stroke or the pressure phase is completed, on the left the diaphragm 26 is flattened, ie the suction stroke or the suction phase is complete).
- Fig. 2 shows an embodiment with ventilation in the suction line 15.
- the refilling takes place from a pressure accumulator 30 (with gas cushion) time or pressure controlled during the pressure stroke of the pulsator.
- the used switching symbol for the valve 31 describes a controlled non-return valve, in which the closing is prevented during activation.
- the pressure in the refill reservoir 30 must be greater than the system pressure.
- the refilling volume flow must be greater than or equal to the leakage flow of the venting process.
- a follow-up regulation of the accumulator pressure as a function of the changing system pressure is recommended. If necessary, manual control is also possible.
- Fig. 4 shows an embodiment with ventilation in the pressure line 5.
- the refilling takes place from a pressure accumulator 30 (with gas cushion) time or pressure controlled during the suction stroke of the pulsator.
- the switching symbol used for the valve 31 describes a controlled non-return valve, in which the opening is prevented when actuated.
- the pressure in the refill reservoir 30 must be greater than the suction pressure.
- the refilling volume flow must be greater than or equal to the leakage flow of the venting process. A follow-up of the accumulator pressure as a function of the changing suction pressure is recommended. If necessary, manual control is also possible.
- Fig. 5 shows an embodiment with a vent in the Nach Glallreservoir 30.
- the refilling takes place from a pressure accumulator 30 (with gas cushion) timed.
- the symbol for the refill valve 31 shows no specific function.
- Fig. 6 shows an embodiment with ventilation in any storage or collecting container 36.
- the refilling takes place from a pressure accumulator 30 (with gas cushion) timed.
- the symbol for the refill valve 31 shows no specific function.
- Fig. 7 shows an embodiment of the invention of a pump device with a single-acting pulsator.
- the venting or refilling can be carried out according to the abovementioned embodiments of the invention, for example according to FIG. 2, FIG. 4, FIG. 5 or FIG. 6.
- Exemplary is the Venting shown in the pressure line 5 as one of the possible variants.
- the unused page is subjected to a pressure which corresponds approximately to the system pressure, for example by means of a pressure accumulator.
- a pressure accumulator for example by means of a pressure accumulator.
- FIG. 8 shows a possible embodiment of the main pump head 11 of pump devices according to the invention.
- two suction-side check valves 16, 161 are provided, which may also have a different size.
- This embodiment has the advantage that during the pressure stroke of the pulsator in the line section between the two suction-side check valves, a higher flow velocity is generated.
- the pendulum line 12 has a slope towards the suction-side check valves 161, 16. When sucking the suction flow is distributed according to the
- the pendulum line is at least in a section divided into at least two sections 121, 122, which are used with the help of controlled shut-off valves 123, 124 in the suction phases simultaneously for suction and can be alternately opened and closed in the pressure phases, respectively, by the thus generated higher Outflow velocity in the sections 121, 122 to prevent deposits of solid particles.
- each subsection 121, 122 should preferably be at least as great as and preferably greater than the stroke volume of the pulsator. This prevents solid particles from getting behind the controlling valves by alternately closing in the pressure phase.
- each section In a first suction so each section would initially filled up to half of its volume with particles. The subsequently sealed section would possibly retain this condition. When re-suction, the subsection would then at most complete with Be filled with particles before a full rinse in the printing phase would take place.
- time-controlled shut-off valves 123, 124 are provided which should be synchronized exactly with the respective phase position of the pulsator diaphragm with the aid of sensor technology.
- Fig. 10 shows another embodiment of the invention. Identical parts are provided with the same reference numerals. Reference is made to the description of the above statements.
- the pulsator is shown in somewhat greater detail, wherein the drive for the double-acting piston 28 is not shown. In particular, the course of the hydraulic channels of the double-acting pulsator is shown in more detail.
- the pump device of FIG. 10 has two refill valves 37 of the diaphragm control chamber, which are preferably subjected to a pressure which corresponds approximately to the system pressure.
- the pressure is provided by a hydraulic pump 38.
- two vent valves 39 are provided for venting the diaphragm control chambers.
- Figures 11 and 12 show schematic PV diagrams showing the time course of the pump pressure over the stroke volume. Beginning at the point on the left-hand side below, you can clearly see the steep slope of the pressure increase during the compression phase, the pressure oscillations due to the valve kinematics, the displacement of the stroke volume (maximum pressure at maximum piston speed), as well as the steep decompression phase and the intake phase. (Note: In the present case, the circular process was shown clockwise in both figures for illustrative purposes.) The dashed line in Fig. 11 shows the required pressure level and a possible time window for a controlled Leckagelach Stahl during the print stroke. The adjusting, mean working pressure of the pulsator in the pressure stroke (pD) is slightly greater than the system pressure.
- the dashed line in Fig. 12 shows the required pressure level and a possible time window for a controlled Leckagelach Stahlgang during the suction stroke. When refilling during the suction stroke, it is sufficient if the pressure level is slightly above the suction pressure.
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Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ES09777900T ES2773043T3 (es) | 2008-08-14 | 2009-08-14 | Dispositivo de bomba |
EP09777900.3A EP2329147B1 (de) | 2008-08-14 | 2009-08-14 | Pumpenvorrichtung |
PL09777900T PL2329147T3 (pl) | 2008-08-14 | 2009-08-14 | Układ pompy |
CN200980131732.1A CN102124226B (zh) | 2008-08-14 | 2009-08-14 | 泵装置 |
US13/058,904 US20110135514A1 (en) | 2008-08-14 | 2009-08-14 | Pump Device |
BRPI0917663A BRPI0917663A2 (pt) | 2008-08-14 | 2009-08-14 | dispositivo de bomba |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP08014528.7 | 2008-08-14 | ||
EP08014528.7A EP2154371B1 (de) | 2008-08-14 | 2008-08-14 | Pumpenvorrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2010017997A2 true WO2010017997A2 (de) | 2010-02-18 |
WO2010017997A3 WO2010017997A3 (de) | 2010-04-08 |
Family
ID=39883770
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/005928 WO2010017997A2 (de) | 2008-08-14 | 2009-08-14 | Pumpenvorrichtung |
Country Status (8)
Country | Link |
---|---|
US (1) | US20110135514A1 (de) |
EP (2) | EP2154371B1 (de) |
CN (1) | CN102124226B (de) |
BR (1) | BRPI0917663A2 (de) |
DK (1) | DK200800165U3 (de) |
ES (1) | ES2773043T3 (de) |
PL (1) | PL2329147T3 (de) |
WO (1) | WO2010017997A2 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
IN2014CN03132A (de) | 2011-09-30 | 2015-07-03 | Aker Wirth Gmbh | |
DE102012102088A1 (de) | 2012-03-13 | 2013-09-19 | Prominent Dosiertechnik Gmbh | Verdrängerpumpe mit Zwangsentlüftung |
KR101374048B1 (ko) * | 2012-06-14 | 2014-03-13 | 한국과학기술연구원 | 유체 펌핑 장치, 이를 이용하는 연료전지 장치 및 연료 가스 재순환 방법 |
DE102013114320A1 (de) * | 2013-12-18 | 2015-06-18 | Mhwirth Gmbh | Heißschlammpumpe |
WO2016004958A1 (en) * | 2014-07-11 | 2016-01-14 | Aarhus Universitet | A method and apparatus for producing biofuel in an oscillating flow production line under supercritical fluid conditions |
DE102016015110A1 (de) * | 2016-12-20 | 2018-06-21 | Fresenius Medical Care Deutschland Gmbh | Verdrängerpumpe für medizinische Flüssigkeiten und Blutbehandlungsvorrichtung mit einer Verdrängerpumpe für medizinische Flüssigkeiten sowie Verfahren zur Steuerung einer Verdrängerpumpe für mediizinische Flüssigkeiten |
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US3216360A (en) * | 1963-06-10 | 1965-11-09 | Lapp Insulator Company Inc | Fluid transport device |
DE2553794A1 (de) * | 1975-11-29 | 1977-06-02 | Bayer Ag | Verfahren und vorrichtung zum kontinuierlichen foerdern heisser aggressiver fluessigkeiten |
US4378183A (en) * | 1980-09-18 | 1983-03-29 | The Pittsburgh & Midway Coal Mining Co. | Apparatus and method for pumping hot, erosive slurry of coal solids in coal derived, water immiscible liquid |
DE19903061A1 (de) * | 1999-01-26 | 2000-08-03 | Emmerich Josef Pumpenfab | Verdrängerpumpe |
US20040062662A1 (en) * | 2002-09-27 | 2004-04-01 | Claude Cordell E. | Effervescent gas bleeder apparatus |
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US2444586A (en) * | 1944-03-20 | 1948-07-06 | Wuensch Charles Erb | Pump |
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GB1108424A (en) * | 1964-01-08 | 1968-04-03 | Panther Pumps & Equipment Comp | Diaphragm fluid pumping systems |
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US4247266A (en) * | 1979-02-16 | 1981-01-27 | Vapor Corporation | Fluid pump drive system |
DE3012028A1 (de) * | 1980-03-28 | 1981-10-08 | Josef Emmerich Pumpenfabrik GmbH, 5481 Hönningen | Vorrichtung zum foerdern von fliessfaehigen medien |
DE3021851C2 (de) * | 1980-06-11 | 1984-04-12 | Pumpenfabrik Urach, 7432 Urach | Hochdruckkolbenpumpe |
US4386888A (en) * | 1980-09-29 | 1983-06-07 | Mccann's Engineering And Manufacturing Company | Double diaphragm operated reversing valve pump |
DE3040478C2 (de) * | 1980-10-28 | 1986-07-10 | Uraca Pumpenfabrik GmbH & Co KG, 7432 Bad Urach | Pumpe od.dgl. hydraulische Arbeitsmaschine |
EP0055467B1 (de) * | 1980-12-29 | 1984-12-05 | LEWA Herbert Ott GmbH + Co. | Membranpumpe mit druckentlastet eingespannter Membran |
EP0085725B1 (de) * | 1982-02-05 | 1984-11-28 | Bran & Lübbe GmbH | Kolbenmembranpumpe |
US5310321A (en) * | 1990-07-24 | 1994-05-10 | Baker Hughes Incorporated | Pump system |
US5249932A (en) * | 1991-10-07 | 1993-10-05 | Erik Van Bork | Apparatus for controlling diaphragm extension in a diaphragm metering pump |
NL1004890C2 (nl) * | 1996-12-24 | 1998-06-25 | Envirotech Pumpsystems Netherl | Pompsysteem in het bijzonder geschikt voor het verpompen van hete media. |
IT1297087B1 (it) | 1997-11-28 | 1999-08-03 | Enea Ente Nuove Tec | Dispositivo per il pompaggio di liquidi o aeriformi, con moto alternativo a doppio effetto ottenuto per via idraulica. |
DE102006041420A1 (de) * | 2006-09-04 | 2008-03-20 | Bran + Luebbe Gmbh | Pumpenvorrichtung |
-
2008
- 2008-08-14 EP EP08014528.7A patent/EP2154371B1/de active Active
- 2008-08-27 DK DK200800165U patent/DK200800165U3/da not_active IP Right Cessation
-
2009
- 2009-08-14 ES ES09777900T patent/ES2773043T3/es active Active
- 2009-08-14 BR BRPI0917663A patent/BRPI0917663A2/pt not_active Application Discontinuation
- 2009-08-14 WO PCT/EP2009/005928 patent/WO2010017997A2/de active Application Filing
- 2009-08-14 US US13/058,904 patent/US20110135514A1/en not_active Abandoned
- 2009-08-14 EP EP09777900.3A patent/EP2329147B1/de active Active
- 2009-08-14 CN CN200980131732.1A patent/CN102124226B/zh active Active
- 2009-08-14 PL PL09777900T patent/PL2329147T3/pl unknown
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US3216360A (en) * | 1963-06-10 | 1965-11-09 | Lapp Insulator Company Inc | Fluid transport device |
DE2553794A1 (de) * | 1975-11-29 | 1977-06-02 | Bayer Ag | Verfahren und vorrichtung zum kontinuierlichen foerdern heisser aggressiver fluessigkeiten |
US4378183A (en) * | 1980-09-18 | 1983-03-29 | The Pittsburgh & Midway Coal Mining Co. | Apparatus and method for pumping hot, erosive slurry of coal solids in coal derived, water immiscible liquid |
DE19903061A1 (de) * | 1999-01-26 | 2000-08-03 | Emmerich Josef Pumpenfab | Verdrängerpumpe |
US20040062662A1 (en) * | 2002-09-27 | 2004-04-01 | Claude Cordell E. | Effervescent gas bleeder apparatus |
Also Published As
Publication number | Publication date |
---|---|
EP2329147B1 (de) | 2019-12-18 |
EP2154371A1 (de) | 2010-02-17 |
US20110135514A1 (en) | 2011-06-09 |
ES2773043T3 (es) | 2020-07-09 |
BRPI0917663A2 (pt) | 2015-12-01 |
DK200800165U3 (da) | 2009-12-11 |
PL2329147T3 (pl) | 2020-06-29 |
WO2010017997A3 (de) | 2010-04-08 |
EP2154371B1 (de) | 2018-09-19 |
CN102124226B (zh) | 2014-09-17 |
CN102124226A (zh) | 2011-07-13 |
EP2329147A2 (de) | 2011-06-08 |
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