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WO2009083179A1 - Dispositif fluidique pour la manipulation contrôlée de liquides et système fluidique équipé d'un dispositif fluidique - Google Patents

Dispositif fluidique pour la manipulation contrôlée de liquides et système fluidique équipé d'un dispositif fluidique Download PDF

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Publication number
WO2009083179A1
WO2009083179A1 PCT/EP2008/010901 EP2008010901W WO2009083179A1 WO 2009083179 A1 WO2009083179 A1 WO 2009083179A1 EP 2008010901 W EP2008010901 W EP 2008010901W WO 2009083179 A1 WO2009083179 A1 WO 2009083179A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluidic
valve
flow
fluidic device
fluidic element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2008/010901
Other languages
German (de)
English (en)
Inventor
Heinz Kueck
Daniel Benz
Frank Wolter
Volker Mayer
Karl-Peter Fritz
Hans-Otto Maier
Rolf Heitmeier
Dominik Niedenzu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
B Braun Melsungen AG
Hann-Schickard-Gesellschaft fuer Angewandte Forschung eV
Original Assignee
B Braun Melsungen AG
Hann-Schickard-Gesellschaft fuer Angewandte Forschung eV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by B Braun Melsungen AG, Hann-Schickard-Gesellschaft fuer Angewandte Forschung eV filed Critical B Braun Melsungen AG
Publication of WO2009083179A1 publication Critical patent/WO2009083179A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
    • 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
    • F04B53/1077—Flow resistance valves, e.g. without moving parts
    • 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
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons

Definitions

  • the present invention relates to a fluidic device and a fluidic system, by means of which a fluid can be conveyed and additionally or alternatively a quantity of fluid flowing through a fluidic device can be determined.
  • the prior art discloses a multiplicity of pumps or fluidic systems which can be used for conveying fluids.
  • the sizes of the pumps vary from micromachined pumps of the lowest flow rate to very large pumps with high pump capacities, which are used, for example, in power plants.
  • the pumps belonging to the state of the art are predominantly complex constructions which contain the structure which causes the liquid transport, a drive and optionally a control or regulating device. Disadvantages of the high complexity of the known pumps are the high production costs, which virtually preclude the use of such pumps for single-use applications. In addition, reliability is reduced when many complex mechanical and electronic components need to work together.
  • auxiliaries such as lubricating oils or greases for their drive or the maintenance of the drive.
  • auxiliaries can either come into contact with the fluid to be delivered during normal operation or in the presence of a slight disturbance, and this thus contaminate.
  • the known in the art pumps are predominantly driven mechanically, such as in a push rod of a conventional piston pump.
  • the mechanical drive is also usually lubricated so that if a seal fails between the mechanical drive and the fluid, the fluid being pumped can be easily contaminated.
  • a fluidic device is used to deliver a liquid which serves to convey fluid along a fluid path from a fluidic device inlet to a fluidic device outlet.
  • the delivery of the liquid is achieved by means of a fluidic element which is movable along the fluid path between a first and a second position.
  • the fluid path is enclosed by a fluidic device housing, which fluidly encloses the fluidic element so that fluid can be delivered when the fluidic element is moved from the first position to the second position.
  • the fluidic element is arranged to be freely movable in the fluid path.
  • the fluidic element is not mechanically connected to the fluidic device housing. Consequently, there is no direct mechanical connection with the fluidic device housing, by which movement of the fluidic element is restricted. In other words, the fluidic element is not mechanically connected to the fluidic device housing in a direction perpendicular to the flow direction.
  • the fluidic element is used to measure or determine a flow rate or volume of a fluid flowing through the fluidic device.
  • the fluidic element can be equipped with a valve which has an opening force
  • valve (For example, because a gasket is mechanically biased) requires greater than a force on the valve caused by the liquid flowing through the fluidic device.
  • the valve thus remains closed when the fluidic element moves in the flow direction from the first position to the second position. If the fluid ment detected at the second position, it is moved from the second position back to the first position.
  • the bias of the valve is selected such that a dynamic pressure caused by the fluid exerts a force on the valve which is greater than the force required to open the valve, so that the fluid element moves relative to the fluid to the first position can. If such movement cycles are performed multiple times, the number of strokes or the movements from the second to the first position is directly a measure of what volume of liquid has flowed through the fluidic device.
  • the fluidic element is at least partially made of a magnetizable material so that the fluidic element can be moved from the first position to the second position or from the second position to the first position by applying an electromagnetically induced force to the fluidic element along the fluid path ,
  • liquid can be delivered without the driving force (the source of the electromagnetic fields) actually causing the driving force coming into direct contact with the fluid or fluid to be delivered.
  • the fluidic element has a bore or fluid passage through which the fluid to be delivered can flow.
  • the liquid channel is secured by a seal which is designed so that liquid through the liquid channel only in a predetermined direction can flow. This is the flow direction, so that when the piston or the fluid element is moved in the flow direction, ie relative to the fluidic device housing located in the fluid against the flow direction, the seal closes and the liquid located in front of the piston is displaced from the fluidic.
  • the valve opens and allows liquid to be newly delivered through the liquid channel to flow into the volume located in front of the fluidic element, so that upon subsequent movement of the fluidic element from the first to the second position, this liquid can be displaced or promoted.
  • the fluidic element only the movement of the fluidic element in the direction opposite to the direction of flow (from the 2nd to the 1st position) is achieved by electromagnetic force. If the relevant electromagnetic force is no longer applied, for example by a magnetic field being switched off, the fluidic element is moved by mechanical components, for example by a prestressed spring, along the fluid path from the first position to the second position.
  • the flow rate ie the amount of liquid delivered per unit time
  • the flow rate ie the amount of liquid delivered per unit time
  • the mechanical force for example the spring force
  • a check valve disposed in the fluid path within the fluidic device or the valve located on the fluidic element is already biased, ie, the force used to open the Valve is required, is increased by appropriate measures, so that liquid can be conveyed reliably even if the pressure of the fluid at Fluidikvor- direction input is greater than the pressure of the fluid at Fluidikvor therapiessausgang.
  • Some embodiments include a fluidic device and a drive device that is configured to be reversibly coupled to the fluidic device, wherein the drive device is configured separately from the fluidic device.
  • the drive device includes means for generating an electromagnetic force or electromagnetic field by which the fluidic element is moved from the second to the first position. Since the drive device, which has the comparatively expensive electromagnetic field generating and electromagnetic field monitoring electronics, is reversibly couplable to the fluidic device, a plurality of fluidic devices can be operated by only one drive device. In this case, the individual fluidic devices can be designed as low-cost, simple components.
  • the drive device or component of the drive device which causes the drive force, is physically separated from the fluid path and thus from the fluid to be delivered.
  • the fluidic device or drive device further comprises a detection device configured to determine the position of the fluidic element within the fluidic device.
  • the delivery rate per unit time can be determined at any time, or it can be detected whether the fluidic device runs within its specification and works without problems.
  • the detection device determines, for example, the per stroke promoted Volume and counting counts the number of strokes.
  • deviation from the normal operation state can be prevented by properly controlling the drive device based on the results of the detection order.
  • Fig. Ia an embodiment of a fluidic device
  • FIG. 1b shows a further embodiment of a fluidic device
  • Fig. Ic is a sectional view of the fluidic device of Fig. Ib;
  • FIG. 2 embodiments of fluidic elements
  • FIG. 3 shows embodiments of valves attached to the fluidic element
  • FIG. 4 shows a further exemplary embodiment of a valve attached to the fluidic element
  • FIG. 6 shows a further exemplary embodiment of a valve attached to the fluidic element
  • Fig. 7a embodiments for in the Fluidikvorrich- and 7b direction attached check valves
  • FIG. 8a further exemplary embodiments for check valves mounted in the fluidic and 8b devices;
  • FIG. 9 shows an example of the dimensioning of flow resistances for achieving a predetermined delivery stroke;
  • FIG. 10 shows an exemplary embodiment of a fluidic system comprising a fluidic device and a drive device
  • FIG. 11 shows an alternative embodiment of a fluidic system
  • Fig. 13 shows another embodiment of a fluidic system.
  • FIG. 1 a shows a sectional view of an embodiment of a fluidic device for conveying a fluid from a fluidic device inlet 2 to a fluidic device outlet 4.
  • the fluidic device is shown on the one hand in a hatched representation for ease of understanding and on the other hand in a representation, in which only the contours of the individual elements are visible.
  • the fluidic device serves to convey fluid from the fluidic device inlet 2 to the fluidic device outlet 4, wherein the fluid within the fluidic device is conveyed in a flow direction 6 along a fluid path.
  • the fluid path consists, as explained in more detail in the following sections, of a series of different fluid path sections with varying cross sections. In the case of the fluidic device shown in FIG.
  • the fluidic device shown in Fig. Ia has a fluidic device housing 8, which is formed in several pieces in the example shown, if this is necessary for reasons of the geometry of the housing for assembly. In alternative embodiments, however, the fluidic device housing can also be made in one piece.
  • the fluid path formed by the fluidic device housing 8 is logically subdividable into a plurality of fluid path segments 10a-f. Due to the rotationally symmetric geometry of the fluidic device, the individual fluid path segments 10a to 10f are each formed of concentric cylindrical volumes which adjoin one another along the fluid path.
  • rotationally symmetric geometries are discussed in the example shown in FIG. 1 and with reference to the exemplary embodiments described below, rotational symmetry is not a mandatory prerequisite. Rather, it is also conceivable, for example, to use a fluid path or fluid path segments which have a square or rectangular cross section.
  • the fluid first flows through the fluid path segment 10a, which is adjoined in the flow direction by the fluid path segment 10b, which has a narrowed cross section.
  • the narrowing of the cross-section can be used to suitably dimension the dynamic properties, that is to say the pumping properties of the fluidic device, as will be explained in more detail below.
  • the fluid path segment 10c, which adjoins the fluid path segment 10b in the flow direction, is separated therefrom by a check valve 12, which ensures that fluid can only move in the flow direction 6 through the fluidic device.
  • Fluid path segment 10c has an expanded cross-section and serves to house a spring 14 used as a restoring device, which has a stop on the input side, and which rests on the opposite side of the input side of the fluid element to exert on this acting in the flow direction restoring force.
  • the spring 14 is installed in a prestressed state or is tensioned by movement of the fluidic element 16 counter to the flow direction 6.
  • the fluidic element is at least partially made of magnetizable material. That is, although it is indicated in Fig. 1 that the fluidic element is made in one piece, it is possible in further embodiments that the fluidic element 16 consists of several different lent material components. For example, it is conceivable that the fluidic element 16 is partially formed of magnetizable material and partly of dielectric material.
  • the fluidic element 16 further has a central bore designed as a liquid passage 18 which extends in the flow direction 6 through the entire fluidic 16, so that liquid can flow through the fluidic 16.
  • the fluidic element 16 itself is located in the fluid path segment 10 d, which has a diameter which is dimensioned such that the fluidic device housing 8 terminates fluidically with the outer diameter of the fluidic element 16. In other words, no liquid can flow past at the edges of the fluidic element 16.
  • the fluidic element 16 further has a seal 20, which has the function of a check valve, which allows fluid to flow only in the flow direction 6 through the fluidic 16.
  • the fluidic element 16 is thus freely movable within the fluid path segment 10 d, for example from a first position 22 defined by an input-side stop to a second position 24 defined by a first position output-side stop is defined, can be moved.
  • the fluidic element within the fluid path segment 10d is free to move. This means that it is not necessary to mechanically fix the fluidic element in a direction perpendicular to the fluid path with respect to the fluidic device housing. This considerably simplifies the construction of the fluidic device housing, so that this can be produced inexpensively in large numbers. Further, it thereby becomes possible to adjust the pumping characteristics substantially by the flow resistances along the fluid path within the fluidic device, without having to take into account any mechanical damping that might be generated by a fixation of the fluidic element with respect to the fluidic device housing.
  • Fluid path segment 10e has a restricted cross-section with fluid path segment 10d and, similar to fluid path segment 10b, may be used to adjust the dynamic pumping characteristics.
  • the fluidic device outlet 4 is formed by fluid path segment 10f.
  • the two flow-directionally-permeable valves 12 and 20 cooperate such that fluid can not escape on the inlet side, the fluid passing through the fluid channel 18 of the fluidic element through the fluid particles ment flows.
  • liquid is in a volume of the fluid path segment 10d located in the exit direction in front of the fluidic element 16 when the fluidic element 16 has completed its return movement, ie is at the first position 22. This state defines the beginning of a delivery stroke during which liquid is conveyed through the outlet 4.
  • the conveying speed that is, the liquid volume displaced by the fluidic element 16 per unit of time, is determined by the spring force and the flow resistance of the fluid path segment having the greatest flow resistance. In the case shown in Fig. Ia, this is fluid path segment 10b which has the smallest diameter. Since the spring force of the spring 14 is approximately constant over the entire path, the conveying speed, ie the speed with which the fluidic element 16 is moved, can be easily determined by the dimensioning of the components used, that is to say in particular the spring and set the maximum flow resistance (the smallest used diameter along the fluid path). This can be achieved by a simple geometric dimensioning of the components used, without, for example, a complicated electronic control for a drive motor would be required.
  • the fluidic element 16 is moved from the second position 24 to the first position 22 at the beginning of a delivery stroke. This can be achieved when the fluidic element 16 is at least partially made of a magnetizable material, for example by generating a magnetic field in the fluid path segment 10c and 10d, through which the fluidic element 16 is pulled to the first position 22 while simultaneously biasing the spring 14.
  • the magnitude of the electromagnetic force exerted on the fluidic element is decisive.
  • the flow resistance of the liquid channel 18, through which the displaced liquid must flow counteracts. Consequently, by suitable dimensioning of the flow resistance of the fluid channel 18, the speed of the return movement of the fluidic element 16 can be adjusted. If the flow resistance of the liquid channel 18 is low, an almost continuous operation of the fluidic device can be achieved, because then the return movement of the fluidic 16 is hardly hindered or attenuated so that it takes place extremely fast compared to the forward movement.
  • a conveying action during a delivery stroke can be achieved in an alternative embodiment of the invention even if the fluidic element has no valve 20. This is possible if the flow resistance of the throughflow opening is greater during a movement of the fluid element from the first 22 to the second 24 position than the flow resistance between the fluidic element and the fluidic device output 4. Such a configuration may in alternative embodiments of the invention itself without valve 20 a net pumping action can be achieved.
  • the check valve can be dispensed with if the flow resistance of the throughflow opening is smaller during a movement of the fluidic element from the second (24) to the first (22) position than the flow resistance between the fluidic element and the fluidic device input (4), so that liquid flows through the flow-through opening during the return movement.
  • a magnetic field generating device may be used as a driving device serving to apply the force required for retrieving the fluidic element 16 to the fluidic element 16.
  • These may be, for example, coils which are arranged outside the fluidic device and generate a magnetic field running parallel to the flow direction.
  • the drive device does not come into physical contact with the liquid to be delivered.
  • the drive device may be physically separate from the fluidic device so that a plurality of fluidic devices, possibly only once used, may be operated by only a single drive device. This has the advantage that the existing in the drive device Electronics, which is a costly component of a pumping system or a fluidic system, only needs to be generated once.
  • FIG. 1b shows a further exemplary embodiment of a fluidic device, which is based on the principle already discussed in detail with reference to FIG. 1a.
  • the fluidic element 16 is separated in FIG. 1 b into two functionally different regions (a drive region 16 a and a sealing region 16 b).
  • the two areas can both be formed in multiple pieces, that is, assembled from discrete individual components, as well as manufactured in one piece.
  • the drive region 16a facing the fluidic device inlet 2 serves to drive the fluidic element 16, ie it has all the devices and means which make it possible to drive the fluidic element 16 without contact.
  • the fluidic device outlet 4 facing the sealing region 16b of the fluidic element 16 serves to ensure the fluidic seal upon movement of the fluidic element from the first position 22 to the second position 24.
  • the geometric dimensioning of the sealing region 16 or of the fluid path segment 10g, within which the sealing region 16b of the fluidic element 16 is moved makes it possible to adapt the dynamic properties of the fluidic device to the most varied flow rates, by the Cross section of the sealing portion 16b is selected accordingly.
  • the appropriate dimensioning of the different cross sections along the fluid path reference is here made to the statements made in FIG. 1a.
  • the flow resistance which is initially determined by the flow resistance of the flow opening 18, which serves as a central bore through the drive region 16a and Sealing area 16b is executed.
  • additional channels 50a and 50b are provided in the drive region 16a in the exemplary embodiment shown in FIG. 1b, as can be seen from the sectional view AA 'shown in FIG.
  • the fluidic element 16 has channels or flow-through openings 50a and 50b which extend over the entire length, ie the axial extent, of the cylindrical sealing region 16b.
  • the geometric shape of the throughflow openings or of the channels 50a and 50b shown in FIG. 1c is to be understood merely as an example. These can also have any other geometric shape, for example, rectangular, if they are introduced by means of a milling cutter.
  • FIG. 1b Also shown in FIG. 1b is an active check valve as an alternative to the use of a passive valve.
  • the active valve comprises several functional components. These are on the one hand, the passive valve 12 and a support 80 a, which is arranged along the flow direction after the valve 12 and coupled with this mechanical.
  • the carrier 80a is made of magnetizable material and can be acted upon by an electromagnetic field with a force acting counter to the flow direction 6 force. By adjusting this force, the valve 12 can be biased, the force of the bias being adjustable within wide limits over the magnitude of the electric field.
  • the force on the carrier 80a may be generated from the same field that also serves to move the fluidic element 16.
  • a magnetizable guide member 80b is provided for this purpose, which directs the magnetic flux in the form of a yoke.
  • the support 80a can be pressed against the valve 12 with a predetermined, adjustable force so that it opens only when an adjustable force is reached. This makes it possible to adapt the dynamic properties of the fluidic device even more precisely to the conditions.
  • a fluidic device may also be used as a fluidic sensor.
  • the fluidic element may for example have a smaller diameter than the inner diameter of the housing.
  • FIG. 2 shows two ways in which the fluidic element 16 can be attached or arranged in a fluid-tight manner within the fluid path segment 10d.
  • the fluidic element is made with a diameter corresponding to the diameter of the fluid path segment 10d with minimal tolerance so that no gap is formed between the cylindrical diameter of the fluidic element 16 and the wall of the fluid path segment or fluidic device housing 8.
  • the diameter of the fluidic element 16 is smaller than the diameter of the fluidic device housing 8.
  • a groove 28 is milled into the fluidic element 16 into which an O-ring 30 is inserted, which ensures the seal between the fluidic 16 and the wall of the Fluidikvoriquessgephaseuses 8.
  • piston rings may also be used.
  • the seal can be done by a very precise storage of the piston, in which the remaining, annular gap, between the piston and the housing wall is not greater than, for example, about 10 microns.
  • one or more O-rings may be used, as outlined in FIG. 2 below.
  • O-rings instead of O-rings also piston rings can be used.
  • FIG. 3 shows some embodiments of a seal 20 or of valves 20 that can be used to seal the fluid element 16 during the delivery stroke.
  • the fluidic element 16 is partially shown in a 3-dimensional perspective view and in a sectional view.
  • Fig. 3 above shows the possibility of using a flap cap seal 40 attached to a base of the cylindrical fluidic element 16.
  • The, for example made of rubber, flap cover seal 40 has a central cover portion 42 which is connected via two webs 44a and 44b with an edge region of the flap cover seal 40.
  • the flap lid 42 with the exception of the two webs 44a and 44b from the rest of the flap cover gasket 40 completely separated by a circumferential groove.
  • the flap lid 42 can lift under a force in the direction of flow 6, so that the liquid can flow in the flow direction 6 through the liquid channel 18 of the fluidic.
  • the flexibility of the webs 44a and 44b may be selected, for example, such that only the pressure of the liquid acting on the flap lid 42 by the return movement of the fluidic element 16 is sufficient to open the flap cover gasket 40.
  • the flap cover gasket 40 closes automatically when a pressure against the flow direction 46 acts on the flap cover gasket 40.
  • the contact surface of the flap cover 42 on the fluidic element 16 can be minimized so that a greater contact force is achieved with the same pressure.
  • the cross-diaphragm 50 shown in Fig. 3 bottom left has the same operation as the flap cover seal 40. The only difference is that the central opening membrane part 50 of the cross-membrane of four webs 52a to 52d, which are arranged in a cross shape, with the rest of the cross-membrane 50 is connected.
  • the flap lid seal attached to the end face of the piston forms a valve with the piston, so that the medium can only flow in one direction.
  • This mode of operation is comparable to that of a check valve, so that the medium can only flow in the direction of flow through the liquid channel 18 of the fluidic element 16.
  • the seal is also airtight to ensure good self-priming of the fluidic system when used as a pump.
  • the piston on the front side on small annular grooves, which serve to increase the surface pressure of the sealing part of the flap cover seal and the cross-diaphragm seal.
  • the opening and closing times of the valve can be set in a simple manner via the material thickness, the web width or the Shore hardness of the material used to produce the seal.
  • the seal operated with the function of a check valve serves to increase the flow resistance against the direction of flow when the fluid element moves from the first position 22 into the second position 24 to approximately infinity. hen. When the return movement of the fluidic element, however, this remains small, since the seal used then opens automatically.
  • a cylindrical fluid channel 18 is not a prerequisite for the successful application of the inventive concept. Rather, a liquid channel 18 with a different cross section can also be used.
  • a general advantage of axial bores is that they have a low flow resistance.
  • Fig. 4 shows an alternative embodiment of a fluidic element 16 with integrated valve, which has a check valve corresponding action.
  • the valve is formed by an arrangement of a spring 60 and a ball 62, wherein the ball is loaded by the spring and is pressed against a matched to the diameter of the ball 62 ball seat 64.
  • the spring 60 and the ball 62 are arranged, for example, within a stepped bore 66 in the fluidic element.
  • the spring 60 is supported, for example, by a stop 68 introduced into the fluidic element 16.
  • the valve formed by the ball 62 and the ball seat 64 opens and allows fluid to flow in the direction of flow 6 the fluidic element 16 flows.
  • the force exerted by the spring 60 on the ball 62 force is additionally reinforced by the fluid pressure, so that the sealing effect of the valve shown in Fig. 4 is still improved.
  • the piston shown in FIG. 4 or the fluidic element shown in FIG. 4 has an axial stepped bore, one step serving as a sealing seat or stop for a further movable element located in the bore.
  • the movable element is z. B.
  • the movable sealing element can be significantly smaller in diameter than the bore, in order to achieve the smallest possible flow resistance.
  • the inertia of the movable sealing element reinforces the sealing effect in addition to the spring force when the piston or the fluidic element 16 moves along the flow direction 6.
  • Figures 5a to 5d show further embodiments of seals associated with the fluidic element 16 wherein the seals are biased so that the pressure applied to the seal needed to open the seal is opposite that shown in Figs 4 discussed embodiments is increased.
  • 5 a to c show examples of fluidic elements 16 in a sectional view, while FIG. 5 d shows a possibility of implementation by means of a special sealing element.
  • the seal or the check valve is mechanically biased, so that the opening pressure required for opening the valve or the seal is increased.
  • This can be used to adjust the dynamic properties of the system so as to cause, for example, an extension of the return movement of the fluidic element 16.
  • the fluidic system when used as a pump, can still provide controlled delivery even when the fluid reservoir located at the fluidic device inlet has a higher static pressure than the outlet of the fluidic device.
  • the seal 20 of the fluidic device and / or the check valve 12 of the fluidic device withstand the overpressure at the inlet to ; prevent the valves from opening and the fluid from flowing through the fluidic device regardless of the delivery strokes made by the fluidic element.
  • the diaphragm 50 of the cross-diaphragm seal described in FIG. 3 is prestressed by forming pins 70 projecting from the fluidic element 16 out of the material of the fluidic element 16 which blocks the cross-diaphragm against the restoring action of the cross-diaphragm webs 52 a to 52 d ahead steer.
  • Fig. 5b shows an example of how the opening force for a flap cover gasket can be increased by deflecting the flap cover gasket or flap cover 42 of the flap cover gasket against the restoring force of the webs 44a and 44b. This is achieved by attaching asymmetrically shaped pegs 72a and 72b to the fluidic element 16 which provide for pilot deflection of the flap cap seal.
  • a flap lid seal it must be noted that the elements causing the deflection must be shaped in such a way that the flap lid seal closes tightly with the fluidic element 16 in the pre-steered state. Contrary to the case shown in FIG. 5a, these elements can therefore not be symmetrical.
  • Fig. 5d shows an embodiment of a seal in which the bias is achieved by the shape of the gasket itself by having in the central region a protruding structure 74 which is comparable to a nose and that leads to a forward deflection of the seal when the nose is placed on a solid abutment.
  • the seals presented by way of example in FIG. 3 can thus be biased in different words by various measures. This can be achieved, for example, by means of a pin protruding at the end face of the piston or fluid element 16, which biases the flap cover of the flap cover gasket or the cross-membrane.
  • the preload force can be varied by the pin height, the material thickness, the material hardness and the web widths of the seals.
  • the biasing force of the spring can be selected accordingly, which can be done on the one hand on the variation of the spring stiffness and on the other via the variation of the forward steering.
  • a gasket may be made having a protruding nose from the gasket surface so that the bias is directly generated by the gasket in question itself.
  • FIG. 6 shows, in a cutaway view of the fluidic device shown in FIG. 1, a further possibility of achieving a prestressing of the seal 20 of the fluidic element 16.
  • the bias voltage is achieved in that an additional biasing spring 80 which is mounted on an abutment 82, against the flow direction 6 presses on the sealing element 20 of the fluidic 16.
  • a variation of the bias voltage can, as just discussed with reference to FIG. 5 case, be achieved via a change in the spring hardness or the bias of the spring.
  • an additional mechanical spring which is supported on a stop on the fluidic device outlet, presses against the sealing membrane 20 of the piston valve (for example flap cover or cross-diaphragm).
  • the sealing membrane 20 of the piston valve for example flap cover or cross-diaphragm.
  • the minimum preload force results from the required dynamic boost pressure. Due to the boost pressure, a safe closing of the check valve at the fluidic device inlet is to be achieved during the return movement of the piston, even at negative delivery heights.
  • negative delivery heights mean that the fluid level of the medium flowing through is higher at the inlet of the fluidic device than at the outlet of the fluidic device. For example, up to 0.2 bar pre-pressure can be compensated.
  • the mechanical preloading of the valve 20, as illustrated with reference to FIGS. 5a to 5c and 6, makes it possible, in particular, to use embodiments of fluidic devices for measuring or determining the flow of a fluid through the fluidic device.
  • This can be dispensed with a drive device.
  • the fluidic element 16, or the force required to open the valve 20 of the fluidic element 16 is dimensioned such that when the fluid is flowing through the fluidic device, the seal remains closed and the fluidic element 16 is thus driven by the fluid flow moved first position 22 to the second position 24. If it is detected by an external detector that the fluidic element 16 has arrived at the second position 24, this information can be used to move the fluidic element back from the second position to the first position. If the valve is suitably biased, the additional back pressure of the fluid generates a force high enough to open the valve 20, so that the number of fluid cycles per unit of time, ie, the stroke frequency, is used to calculate the amount of fluid flowing through the fluidic device can.
  • FIGS. 7a and 7b show an enlarged detail of a fluidic device already discussed with reference to FIG. direction and, in particular, the fluidic device inlet 2 with the two first fluid path segments 10a and 10b and the check valve 12 adjoining the fluid path segment 10b.
  • FIGS. 7a and 7b merely show sectional enlargements of the two previously discussed implementations with flap lid gasket 12a (FIG. 7a) and cross-diaphragm seal 12b (FIG. 7b), reference should be made to the explanations of the preceding figures with respect to the operation of the components shown in FIGS. 7a and 7b.
  • the check valve 12 which may be made of rubber, for example, can be inserted, glued or fixed in a recess in the housing.
  • the seal placed over the bore (fluid path segment 10b) in the housing acts like a check valve.
  • This check valve 12 seals in some embodiments, even at very low pressure difference airtight.
  • the opening and closing times of the valve can be adjusted via the material thickness and the web widths of the hinged lid or the cross-diaphragm.
  • the opening and closing pressure can be influenced by the material thickness, the web width of the webs of the seals and the Shore hardness of a possibly used sealing rubber.
  • FIGS. 8a and 8b show in a sectional view the detail enlargements already discussed with reference to FIGS. 7a and 7b in a sectional view, the possibility additionally being illustrated in FIGS. 8a and 8b also of the check valves 12a and 12b at the inlet of the fluidic bias device by means of suitable material tabs 14a and 14b, so that the pressure required to open the valve is increased.
  • suitable material tabs 14a and 14b so that the pressure required to open the valve is increased.
  • the flap-end diskless 12b and the cross-diaphragm 12a are slightly biased by means of a protruding pin 14a and 14b on the fluidic device housing 8, respectively.
  • the pin surface 14b should be inclined in accordance with the setting angle in order to ensure complete seating of the flap lid 12b.
  • the biasing force on the pin height, the material thickness, the material hardness and the web widths of the seals vary.
  • a secure closing of the check valve at the fluidic device inlet can also be achieved at negative delivery heights.
  • the duty cycle is defined as the difference between the duration of a forward movement 80 and a return movement 82 in relation to the sum of the times required for both movements.
  • a duration 80 of the forward movement can be adjusted via the flow resistance of the fluid path segment with maximum flow resistance used (ie via the diameter and the length of the flow channel), assuming that the spring tension remains constant , Due to the approximately constant restoring force of the spring or the approximately constant flow velocity fluidity prevails in the fluidic device during a forward motion, a continuous, nearly constant fluid flow.
  • the fluidic system can be operated in a clocked manner so that a quasi-continuous fluid flow can be realized.
  • a delivery stroke or forward movement of the fluidic element it is often necessary for a delivery stroke or forward movement of the fluidic element to occur at least every ten seconds.
  • the return movement of the fluidic element is very short compared to the delivery stroke due to the low flow resistance of the fluidic element with the fluid channel.
  • FIG. 10 shows an exemplary embodiment of a fluidic system that includes a non-contact driveable fluidic device 100 and a drive device 110.
  • the fluidic device 100 is, for example, the fluidic device described with reference to FIG. 1.
  • the fluidic system further includes the drive device 110, which is configured to move the fluidic element 16 from the second position 24 to the first position 22.
  • the fluidic element 16 is located at the first position 22, ie immediately at the beginning of a delivery stroke.
  • the fluidic device shown in FIG. 10 merely serves to illustrate the interaction between the fluidic device and the drive device 110, so that a further discussion of the fluidic device 100 shown only schematically at this point in favor of a thorough discussion of the drive device 110 is dispensed with.
  • the drive device 110 and the fluidic device 100 are, as can be seen in FIG. 10, configured in such a way that both are constructed separately from each other and reversibly coupled to one another.
  • the drive device 110 consists, for example, of two collapsible halves 112a and 112b which, when folded together, form an internal volume which corresponds to the volume of the fluidic device 110, so that this can also be completely introduced into the drive device 110.
  • the drive device is designed to move the fluidic element 16 from the second position 24 to the first position 22. This is achieved in the embodiment shown in FIG.
  • the fluidic device 100 and the drive device 110 can be coupled to each other in any reversible manner.
  • the more expensive drive device only needs to be manufactured or purchased once.
  • By means of a drive device an arbitrary number of fluidic devices can be successively operated. Complete sterility using sterilized fluidic devices can be readily ensured by the fluidic system as illustrated in FIG. 10.
  • the coil 114 shown schematically in FIG. 10 for generating a magnetic field as a drive or as a cause for the restoring force acting on the fluidic element 16 is only one example of a very wide variety of implementations. Any other restoring force applying drive devices may be used. This may be, for example, an electrostatic force exerted on the fluidic element 16 by electrodes disposed at the position of the coil 114. Further, with sufficient mass of the fluidic element 16, a restoring force or force causing the fluidic element 16 to move from the second position 24 to the first position 22 may also be the inertial force. To achieve this, it is possible to move the drive device with high acceleration in the flow direction 6, so that by the inertia of the fluidic 16 this in the first position 22 is moved, from which a renewed movement in the flow direction can take place.
  • FIG. 10 makes it possible in a simple manner to integrate a detection device into the drive device, which makes it possible to detect the deflection or movement of the fluidic element 16.
  • FIGS. 11 to 13 schematically describe various possibilities for carrying out such a detection.
  • a detection device 116 is formed by an additional coil 118 and an evaluation device 120 connected to the coil, which surrounds the path covered by the fluid element 16 along the fluid path.
  • the at least partially made of a magnetizable or electrically conductive material fluid element 16 induces a voltage in the coil 118 during its movement or changes the inductance of the coil 118.
  • the inductance or voltage change is determined by the evaluation device 120, which also due to a theoretical model or a pre-performed calibration, the position or movement speed of the fluidic element 16, based on the measured quantities, can determine.
  • an additional coil 118 is not necessarily required. Rather, the inductance Change or voltage change to the coil 114, which generates the restoring force are read out directly, so as to be able to dispense with the use of an additional coil 118 if necessary.
  • FIG. 12 shows a further example of how a detection device 116 can be configured which determines a position of the fluidic element 16.
  • the detection device 116 consists of an electrode arrangement consisting of the electrodes 122a and 122b, which form a capacitance, which in turn is detected by a capacitance measuring device located within an evaluation device 120.
  • the capacitance measured between the electrodes changes.
  • This effect can additionally be influenced by the fact that the fluidic element 16 at least partially consists of a dielectric with a high dielectric constant. From the measured capacitance between the electrodes 122a and 122b, a suitable evaluation device can close the position of the fluidic element 16, so that the operation of the fluidic device can be monitored in this way.
  • FIG. 13 shows a further exemplary embodiment of a detection device 116, which comprises one or more light sources 130 and a spatially resolving light sensor arrangement 132.
  • the light sensor arrangement 132 is connected to the evaluation device 120 so that a change in intensity that results on the light sensor arrangement 132 when the fluid element 16 is moved into the sensitive area of the light sensor arrangement 132 can be used by the evaluation unit 120 to determine the current one Position of the fluidic element 16 and the piston 16 to determine.
  • further measures are conceivable which serve to determine the position of the piston.
  • a small magnetic field can be generated within the yoke via a small coil additionally mounted on the yoke.
  • the changing magnetic field induces a voltage.
  • This voltage Ui n d is dependent inter alia on the magnetic resistance of the magnetic circuit.
  • This magnetic resistance in turn, depends on, among other things, the position of the piston. In this way, could also monitor whether the piston has driven the entire hub and whether he z. B. got stuck.
  • An electronic evaluation unit can be used to calculate the piston speed at any time and to count the number of movements in the flow direction. From this it is possible to calculate directly the amount of fluid that has flowed through the fluidic device.
  • the piston or the material of the piston can be suitably changed in order to simplify the optical detection of the surface of the piston.
  • markings with strong light-dark contrasts can be attached to the outer diameter of the fluidic element 16.
  • the degree of reflection or the degree of absorption of the fluidic element can be influenced by suitable choice of the material.
  • the fluidic device according to the invention or the fluidic system according to the invention can be used in many other technical fields.
  • they are suitable for chemically corrosive or dangerous (explosive, toxic) liquids because the actual drive device is physically separate from the fluidic device. This minimizes the possibility of leaks and ensures maximum safety.
  • the materials used for the fluidic element can be freely adapted to the required conditions within wide limits. If, for example, a magnetic drive is to be used, the fluidic element is at least partially made of magnetizable material, for example of ferromagnetic or paramagnetic material. For an electrostatic drive electrically conductive materials could be used. In addition, the fluidic element may be partially formed of dielectric materials if required to detect the position of the fluidic element 16 along the fluidic path or increase detection accuracy.
  • the restoring force that is, the force that moves the fluidic element 16 during the delivery stroke
  • this type of force generation is not the only one possible.
  • the force which moves the fluidic element 16 can also be generated in the delivery stroke, that is to say during the movement from the first position 22 to the second position 24.
  • the fluidic device housing 8 may be made of a variety of materials. For example, come thermally moldable plastics or chemically resistant materials into consideration. If necessary, it should be ensured that the electrostatic forces or the electromagnetic fields which may be required to drive the fluidic element 16 can penetrate into the fluidic device housing so that they can act on their force acting on the fluidic element 16.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Check Valves (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif fluidique servant à acheminer un liquide s'écoulant entre une entrée (2) du dispositif fluidique et une sortie (4) du dispositif fluidique le long d'une voie de fluide s'étendant dans un sens d'écoulement (6), ou à déterminer la quantité de ce liquide. Ce dispositif fluidique présente un élément fluidique (16) qui peut être déplacé à l'intérieur de la voie de fluide entre une première position et une seconde position située en aval de la première position dans le sens d'écoulement (6), ainsi qu'un boîtier (8) entourant la voie de fluide. L'élément fluidique (16) présente une ouverture de passage (18) qui possède une première résistance à l'écoulement en cas de déplacement de l'élément fluidique (16) de la première (22) à la seconde (24) position et une seconde résistance à l'écoulement en cas de déplacement de l'élément fluidique (16) de la seconde (24) à la première (22) position, la seconde résistance à l'écoulement étant différente de la première résistance à l'écoulement. L'élément fluidique (16) et le boîtier (8) du dispositif fluidique sont conçus de sorte que l'élément fluidique puisse être déplacé de la seconde (24) à la première (22) position par l'intermédiaire d'un système d'entraînement sans contact.
PCT/EP2008/010901 2008-01-02 2008-12-19 Dispositif fluidique pour la manipulation contrôlée de liquides et système fluidique équipé d'un dispositif fluidique Ceased WO2009083179A1 (fr)

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DE102008003020.1 2008-01-02
DE200810003020 DE102008003020B4 (de) 2008-01-02 2008-01-02 Fluidikvorrichtung für kontrolliertes Handhaben von Flüssigkeiten und Fluidiksystem mit einer Fluidikvorrichtung

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012062628A1 (fr) * 2010-11-12 2012-05-18 BSH Bosch und Siemens Hausgeräte GmbH Équipement de préparation de boissons comportant une détection du débit
DE102011004743A1 (de) 2011-02-25 2012-08-30 Hahn-Schickard-Gesellschaft für angewandte Forschung e.V. Flusssensor und Verfahren zum Erfassen eines Flusses
EP2650539A1 (fr) * 2012-04-11 2013-10-16 TI Automotive Fuel Systems SAS Pompe à piston de solénoïde pour l'injection d'un additif, avec mode d'écoulement inverse intégré et capable de créer et de réguler une pression élevée
EP3848578A1 (fr) * 2020-01-08 2021-07-14 Bilfinger EMS GmbH Pompe et système d'odorisation doté d'une telle pompe
US20220244747A1 (en) * 2021-01-29 2022-08-04 Donaldson Company, Inc. Cyclic flow apparatus

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2925814A (en) * 1956-10-30 1960-02-23 Foster L Vibber Transfusion apparatus
DE2410072A1 (de) * 1974-03-02 1975-09-11 Bosch Gmbh Robert Elektromagnetische pumpe
WO1991019903A1 (fr) * 1990-06-16 1991-12-26 Pwm Drives Limited Pompes de fluides
US6942470B1 (en) * 1998-05-15 2005-09-13 Rolland Versini Motor pump system with axial through flow utilizing an incorporated flowmeter and pressure controller

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1101960B (de) * 1960-01-26 1961-03-09 Otto Muehlschlegel Dipl Ing Elektromagnetisch angetriebene Freischwingerpumpe
DE2757594A1 (de) * 1977-12-23 1979-06-28 Siegfried Dr Ing Kofink Elektromagnetische kolbenpumpe fuer fluessige und gasfoermige medien
DE4035835C2 (de) * 1990-11-10 1994-09-01 Webasto Ag Fahrzeugtechnik Elektromagnetisch betätigte Kolbenpumpe
JP2002130117A (ja) * 2000-10-18 2002-05-09 Mikuni Corp 電磁駆動型プランジャポンプ
DE10147172C2 (de) * 2001-09-25 2003-11-27 Siemens Ag Reduktionsmittelpumpe für eine Abgasnachbehandlungsanlage einer Brennkraftmaschine
DE102005035835A1 (de) * 2005-07-30 2007-02-08 Ksb Aktiengesellschaft Schwingankerpumpe mit elektromagnetischem Antrieb

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2925814A (en) * 1956-10-30 1960-02-23 Foster L Vibber Transfusion apparatus
DE2410072A1 (de) * 1974-03-02 1975-09-11 Bosch Gmbh Robert Elektromagnetische pumpe
WO1991019903A1 (fr) * 1990-06-16 1991-12-26 Pwm Drives Limited Pompes de fluides
US6942470B1 (en) * 1998-05-15 2005-09-13 Rolland Versini Motor pump system with axial through flow utilizing an incorporated flowmeter and pressure controller

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012062628A1 (fr) * 2010-11-12 2012-05-18 BSH Bosch und Siemens Hausgeräte GmbH Équipement de préparation de boissons comportant une détection du débit
CN103188973A (zh) * 2010-11-12 2013-07-03 Bsh博世和西门子家用电器有限公司 带流量检测的饮料制备机构
CN103188973B (zh) * 2010-11-12 2016-09-07 Bsh家用电器有限公司 带流量检测的饮料制备机构
DE102011004743A1 (de) 2011-02-25 2012-08-30 Hahn-Schickard-Gesellschaft für angewandte Forschung e.V. Flusssensor und Verfahren zum Erfassen eines Flusses
WO2012113882A2 (fr) 2011-02-25 2012-08-30 Hahn-Schickard-Gesellschaft für angewandte Forschung e.V. Capteur de flux et procédé pour détecter un flux
EP2650539A1 (fr) * 2012-04-11 2013-10-16 TI Automotive Fuel Systems SAS Pompe à piston de solénoïde pour l'injection d'un additif, avec mode d'écoulement inverse intégré et capable de créer et de réguler une pression élevée
EP3848578A1 (fr) * 2020-01-08 2021-07-14 Bilfinger EMS GmbH Pompe et système d'odorisation doté d'une telle pompe
US20220244747A1 (en) * 2021-01-29 2022-08-04 Donaldson Company, Inc. Cyclic flow apparatus

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