EP2438301B1 - Pompe a disques - Google Patents

Pompe a disques Download PDF

Info

Publication number
EP2438301B1
EP2438301B1 EP09785226.3A EP09785226A EP2438301B1 EP 2438301 B1 EP2438301 B1 EP 2438301B1 EP 09785226 A EP09785226 A EP 09785226A EP 2438301 B1 EP2438301 B1 EP 2438301B1
Authority
EP
European Patent Office
Prior art keywords
pump
cavity
end wall
actuator
flexible membrane
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.)
Active
Application number
EP09785226.3A
Other languages
German (de)
English (en)
Other versions
EP2438301A1 (fr
Inventor
Richard Janse Van Rensburg
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.)
Technology Partnership PLC
Original Assignee
Technology Partnership PLC
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 Technology Partnership PLC filed Critical Technology Partnership PLC
Publication of EP2438301A1 publication Critical patent/EP2438301A1/fr
Application granted granted Critical
Publication of EP2438301B1 publication Critical patent/EP2438301B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/04—Pumps having electric drive

Definitions

  • the illustrative embodiments of the invention relate generally to a pump for fluid and, more specifically, to a pump in which the pumping cavity is substantially a disc-shaped, cylindrical cavity having substantially circular end walls and a side wall.
  • thermo-acoustics The generation of high amplitude pressure oscillations in closed cavities has received significant attention in the fields of thermo-acoustics and pump type compressors. Recent developments in non-linear acoustics have allowed the generation of pressure waves with higher amplitudes than previously thought possible.
  • acoustic resonance it is known to use acoustic resonance to achieve fluid pumping from defined inlets and outlets. This can be achieved using a cylindrical cavity with an acoustic driver at one end, which drives an acoustic standing wave. In such a cylindrical cavity, the acoustic pressure wave has limited amplitude. Varying cross-section cavities, such as cone, horn-cone, bulb have been used to achieve high amplitude pressure oscillations thereby significantly increasing the pumping effect. In such high amplitude waves the non-linear mechanisms with energy dissipation have been suppressed. However, high amplitude acoustic resonance has not been employed within disc-shaped cavities in which radial pressure oscillations are excited until recently. International Patent Application No.
  • PCT/GB2006/001487 published as WO 2006/111775 (the '487 Application), discloses a pump having a substantially disc-shaped cavity with a high aspect ratio, i.e., the ratio of the radius of the cavity to the height of the cavity.
  • Such a pump has a substantially cylindrical cavity comprising a side wall closed at each end by end walls.
  • the pump also comprises an actuator that drives either one of the end walls to oscillate in a direction substantially perpendicular to the surface of the driven end wall.
  • the spatial profile of the motion of the driven end wall is described as being matched to the spatial profile of the fluid pressure oscillations within the cavity, a state described herein as mode-matching.
  • work done by the actuator on the fluid in the cavity adds constructively across the driven end wall surface, thereby enhancing the amplitude of the pressure oscillation in the cavity and delivering high pump efficiency.
  • WO2006/111775 which represents the closest prior art, discloses a pump comprising: a pump body having a substantially cylindrical shape defining a cavity for containing a fluid, the cavity being formed by a side wall closed at both ends by end walls, at least one of the end walls being a driven end wall having a central portion and a peripheral portion extending radially outwardly from the central portion of the driven end wall; an actuator operatively associated with the central portion of the driven end wall to cause an oscillatory motion of the driven end wall, thereby generating displacement oscillations of the driven end wall in a direction substantially perpendicular thereto with an annular node between the centre of the driven end wall and the side wall when in use; a first aperture disposed at any location in the cavity other than at the location of the annular node and extending through the pump body; a second aperture disposed at any location in the pump body other than the location of said first aperture and extending through the pump body; and, a valve disposed in at least one of said first aperture and second aperture
  • such a pump is characterised by a ring or disc shaped isolator operatively associated with the peripheral portion of the driven end wall to reduce dampening of the displacement oscillations.
  • FIG. 1A is a schematic cross-section view of a pump 10 according to an illustrative embodiment of the invention.
  • pump 10 comprises a pump body having a substantially cylindrical shape including a cylindrical wall 19 closed at one end by a base 18 and closed at the other end by an end plate 17 and a ring-shaped isolator 30 disposed between the end plate 17 and the other end of the cylindrical wall 19 of the pump body.
  • the cylindrical wall 19 and base 18 may be a single component comprising the pump body and may be mounted to other components or systems.
  • the internal surfaces of the cylindrical wall 19, the base 18, the end plate 17, and the isolator 30 form a cavity 11 within the pump 10 wherein the cavity 11 comprises a side wall 14 closed at both ends by end walls 12 and 13.
  • the end wall 13 is the internal surface of the base 18 and the side wall 14 is the inside surface of the cylindrical wall 19.
  • the end wall 12 comprises a central portion corresponding to the inside surface of the end plate 17 and a peripheral portion corresponding to the inside surface of the isolator 30.
  • the cavity 11 is substantially circular in shape, the cavity 11 may also be elliptical or other shape.
  • the base 18 and cylindrical wall 19 of the pump body may be formed from any suitable rigid material including, without limitation, metal, ceramic, glass, or plastic.
  • the pump 10 also comprises a piezoelectric disc 20 operatively connected to the end plate 17 to form an actuator 40 that is operatively associated with the central portion of the end wall 12 via the end plate 17.
  • the piezoelectric disc 20 is not required to be formed of a piezoelectric material, but may be formed of any electrically active material such as, for example, an electrostrictive or magnetostrictive material.
  • the end plate 17 preferably possesses a bending stiffness similar to the piezoelectric disc 20 and may be formed of an electrically inactive material such as a metal or ceramic.
  • the piezoelectric disc 20 When the piezoelectric disc 20 is excited by an oscillating electrical current, the piezoelectric disc 20 attempts to expand and contract in a radial direction relative to the longitudinal axis of the cavity 11 causing the end plate 17 to bend, thereby inducing an axial deflection of the end wall 12 in a direction substantially perpendicular to the end wall 12.
  • the end plate 17 alternatively may also be formed from an electrically active material such as, for example, a piezoelectric, magnetostrictive, or electrostrictive material.
  • the piezoelectric disc 20 may be replaced by a device in a force-transmitting relation with the end wall 12 such as, for example, a mechanical, magnetic or electrostatic device, wherein the end wall 12 may be formed as an electrically inactive or passive layer of material driven into oscillation by such device (not shown) in the same manner as described above.
  • a device in a force-transmitting relation with the end wall 12 such as, for example, a mechanical, magnetic or electrostatic device, wherein the end wall 12 may be formed as an electrically inactive or passive layer of material driven into oscillation by such device (not shown) in the same manner as described above.
  • the pump 10 further comprises at least two apertures extending from the cavity 11 to the outside of the pump 10, wherein at least a first one of the apertures may contain a valve to control the flow of fluid through the aperture.
  • the aperture containing a valve may be located at any position in the cavity 11 where the actuator 40 generates a pressure differential as described below in more detail
  • one preferred embodiment of the pump 10 comprises an aperture with a valve located at approximately the centre of either of the end walls 12,13.
  • the pump 10 shown in Figures 1A and 1B comprises a primary aperture 16 extending from the cavity 11 through the base 18 of the pump body at about the centre of the end wall 13 and containing a valve 46.
  • the valve 46 is mounted within the primary aperture 16 and permits the flow of fluid in one direction as indicated by the arrow so that it functions as an outlet for the pump 10.
  • the second aperture 15 may be located at any position within the cavity 11 other than the location of the aperture 16 with the valve 46. In one preferred embodiment of the pump 10, the second aperture is disposed between the centre of either one of the end walls 12,13 and the side wall 14.
  • the embodiment of the pump 10 shown in Figures 1A and 1B comprises two secondary apertures 15 extending from the cavity 11 through the actuator 40 that are disposed between the centre of the end wall 12 and the side wall 14. Although the secondary apertures 15 are not valved in this embodiment of the pump 10, they may also be valved to improve performance if necessary.
  • the primary aperture 16 is valved so that the fluid is drawn into the cavity 11 of the pump 10 through the secondary apertures 15 and pumped out of the cavity 11 through the primary aperture 16 as indicated by the arrows to provide a positive pressure at the primary aperture 16.
  • the pump 10 of Figure 1 is shown with an alternative configuration of the primary aperture 16. More specifically, the valve 46' in the primary aperture 16' is reversed so that the fluid is drawn into the cavity 11 through the primary aperture 16' and expelled out of the cavity 11 through the secondary apertures 15 as indicated by the arrows, thereby providing suction or a source of reduced pressure at the primary aperture 16'.
  • reduced pressure generally refers to a pressure less than the ambient pressure where the pump 10 is located.
  • vacuum and negative pressure may be used to describe the reduced pressure, the actual pressure reduction may be significantly less than the pressure reduction normally associated with a complete vacuum.
  • the pressure is "negative" in the sense that it is a gauge pressure, i.e., the pressure is reduced below ambient atmospheric pressure. Unless otherwise indicated, values of pressure stated herein are gauge pressures. References to increases in reduced pressure typically refer to a decrease in absolute pressure, while decreases in reduced pressure typically refer to an increase in absolute pressure.
  • the valves 46 and 46' allow fluid to flow through in substantially one direction as described above.
  • the valves 46 and 46' may be a ball valve, a diaphragm valve, a swing valve, a duck-bill valve, a clapper valve, a lift valve, or any other type of check valve or any other valve that allows fluid to flow substantially in only one direction.
  • Some valve types may regulate fluid flow by switching between an open and closed position.
  • the valves 46 and 46' must have an extremely fast response time such that they are able to open and close on a timescale significantly shorter than the timescale of the pressure variation.
  • One embodiment of the valves 46 and 46' achieve this by employing an extremely light flap valve which has low inertia and consequently is able to move rapidly in response to changes in relative pressure across the valve structure.
  • FIG. 2A a schematic cross-section view of one embodiment of a flap valve 50 is shown mounted within the aperture 16 (or 16').
  • the flap valve 50 comprises a flap 51 disposed between a retention plate 52 and a sealing plate 53 and biased against the sealing plate 53 in a "closed" position which seals the flap valve 50 when not in use, i.e., the flap valve 50 is normally closed.
  • the valve 50 is mounted within the aperture 16 so that the upper surface of the retention plate 52 is preferably flush with the end wall 13 to maintain the resonant quality of the cavity 11.
  • the retention plate 52 and the sealing plate 53 both have vent holes 54 and 55 respectively that extend from one side of the plate to the other as represented by the dashed and solid circles, respectively, in Figure 2B which is a top view of the flap valve 50 of Figure 2A .
  • the flap 51 also has vent holes 56 which are generally aligned with the vent holes 54 of the retention plate 52 to provide a passage through which fluid may flow as indicated by the dashed arrows in Figure 2A (1).
  • the vent holes 54 of the retention plate 52 and the vent holes 56 of the flap 51 are not in alignment with the vent holes 55 of the sealing plate 53 which are blocked by the flap 51 when in the "closed" position as shown so that fluid cannot flow through the flap valve 50.
  • the operation of the flap valve 50 is a function of the change in direction of the differential pressure ( ⁇ P) of the fluid across the flap valve 50.
  • the differential pressure has been assigned a negative value (- ⁇ P) as indicated by the downward pointing arrow.
  • This negative differential pressure (- ⁇ P) drives the flap 51 into the fully closed position as described above wherein the flap 51 is sealed against the sealing plate 53 to block the vent holes 55 and prevent the flow of fluid through the flap valve 50.
  • the differential pressure across the flap valve 50 reverses to become a positive differential pressure (+ ⁇ P) as indicated by the upward pointing arrow in Figure 2A (1), the biased flap 51 is motivated away from the sealing plate 53 against the retention plate 52 into an "open" position.
  • a pump 70 according to another illustrative embodiment of the invention is shown.
  • the pump 70 is substantially similar to the pump 10 of Figure 1 except that the pump body has a base 18' having an upper surface forming the end wall 13' which is frusto-conical in shape. Consequently, the height of the cavity 11 varies from the height at the side wall 14 to a smaller height between the end walls 12,13' at the centre of the end walls 12,13'.
  • the frusto-conical shape of the end wall 13' intensifies the pressure at the centre of the cavity 11 where the height of the cavity 11 is smaller relative to the pressure at the side wall 14 of the cavity 11 where the height of the cavity 11 is larger.
  • the frusto-conical cavity 11 will generally have a smaller pressure amplitude at positions away from the centre of the cavity 11: the increasing height of the cavity 11 acts to reduce the amplitude of the pressure wave.
  • the efficiency of the pump 70 it is advantageous to the efficiency of the pump 70 to reduce the amplitude of the pressure oscillations away from the centre of the cavity 11 by employing a frusto-conical cavity 11 design.
  • the height of the cavity 11 at the side wall 14 is approximately 1.0 mm tapering to a height at the centre of the end wall 13' of approximately 0.3 mm.
  • Either one of the end walls 12,13 or both of the end walls 12,13 may have a frusto-conical shape.
  • the pump 60 is substantially similar to the pump 10 of Figure 1 except that it includes a second actuator 62 that replaces the base 18 of the pump body.
  • the actuator 62 comprises a second disc 64 and a ring-shaped isolator 66 disposed between the disc 64 and the side wall 14.
  • the pump 60 also comprises a second piezoelectric disc 68 operatively connected to the disc 64 to form the actuator 62.
  • the actuator 62 is operatively associated with the end wall 13 which comprises the inside surfaces of the disc 64 and the isolator 66.
  • the second actuator 62 also generates an oscillatory motion of the end wall 13 in a direction substantially perpendicular to the end wall 13 in a manner similar to the actuator 40 with respect to the end wall 12 as described above.
  • control circuitry (not shown) is provided to coordinate the axial displacement oscillations of the actuators. It is preferable that the actuators are driven at the same frequency and approximately out-of-phase, i.e. such that the centres of the end walls 12, 13 move first towards each other and then apart.
  • the dimensions of the pumps described herein should preferably satisfy certain inequalities with respect to the relationship between the height (h) of the cavity 11 and the radius (r) of the cavity which is the distance from the longitudinal axis of the cavity 11 to the side wall 14. These equations are as follows: r / h > 1.2 ; and h 2 / r > 4 ⁇ x ⁇ 10 - 10 meters .
  • the ratio of the cavity radius to the cavity height is between about 10 and about 50 when the fluid within the cavity 11 is a gas.
  • the volume of the cavity 11 may be less than about 10 ml.
  • the ratio of h 2 /r is preferably within a range between about 10 -3 and about 10 -6 meters where the working fluid is a gas as opposed to a liquid.
  • the secondary apertures 15 are located where the amplitude of the pressure oscillations within the cavity 11 is close to zero, i.e., the "nodal" points of the pressure oscillations.
  • the radial dependence of the pressure oscillation may be approximated by a Bessel function of the first kind and the radial node of the lowest-order pressure oscillation within the cavity occurs at a distance of approximately 0.63r ⁇ 0.2r from the centre of the end wall 12 or the longitudinal axis of the cavity 11.
  • the secondary apertures 15 are preferably located at a radial distance (a) from the centre of the end walls 12,13, where (a) ⁇ 0.63r ⁇ 0.2r, i.e., close to the nodal points of the pressure oscillations.
  • the pumps disclosed herein should preferably satisfy the following inequality relating the cavity radius (r) and operating frequency (f) which is the frequency at which the actuator 40 vibrates to generate the axial displacement of the end wall 12.
  • the frequency of the oscillatory motion of the actuator 40 is preferably about equal to the lowest resonant frequency of radial pressure oscillations in the cavity 11, but may be within 20% therefrom.
  • the lowest resonant frequency of radial pressure oscillations in the cavity 11 is preferably greater than 500Hz.
  • the piezoelectric disc 20 is excited to expand and contract in a radial direction against the end plate 17 which causes the actuator 40 to bend, thereby inducing an axial displacement of the driven end wall 12 in a direction substantially perpendicular to the driven end wall 12.
  • the actuator 40 is operatively associated with the central portion of the end wall 12 as described above so that the axial displacement oscillations of the actuator 40 cause axial displacement oscillations along the surface of the end wall 12 with maximum amplitudes of oscillations, i.e., anti-node displacement oscillations, at about the centre of the end wall 12.
  • Figure 1A shows one possible displacement profile illustrating the axial oscillation of the driven end wall 12 of the cavity 11.
  • the solid curved line and arrows represent the displacement of the driven end wall 12 at one point in time, and the dashed curved line represents the displacement of the driven end wall 12 one half-cycle later.
  • the displacement as shown in this figure and the other figures is exaggerated.
  • the actuator 40 is not rigidly mounted at its perimeter, but rather suspended by the isolator 30, the actuator 40 is free to oscillate about its centre of mass in its fundamental mode. In this fundamental mode, the amplitude of the displacement oscillations of the actuator 40 is substantially zero at an annular displacement node 22 located between the centre of the end wall 12 and the side wall 14.
  • the amplitudes of the displacement oscillations at other points on the end wall 12 have amplitudes greater than zero as represented by the vertical arrows.
  • a central displacement anti-node 21 exists near the centre of the actuator 40 and peripheral displacement anti-node 21' exists near the perimeter of the actuator 40.
  • Figure 1 A(2) shows one possible pressure oscillation profile illustrating the pressure oscillation within the cavity 11 resulting from the axial displacement oscillations shown in Figure 1A (1).
  • the solid curved line and arrows represent the pressure at one point in time, and the dashed curved line represents the pressure one half-cycle later.
  • the amplitude of the pressure oscillations has a central pressure anti-node 23 near the centre of the cavity 11 and a peripheral pressure anti-node 24 near the side wall 14 of the cavity 11.
  • the amplitude of the pressure oscillations is substantially zero at the annular pressure node 25 between the pressure anti-nodes 23 and 24.
  • radial dependence of the amplitude of the pressure oscillations in the cavity 11 may be approximated by a Bessel function of the first kind.
  • the pressure oscillations described above result from the radial movement of the fluid in the cavity 11, and so will be referred to as "radial pressure oscillations" of the fluid within the cavity 11 as distinguished from the axial displacement oscillations of the actuator 40.
  • the operation of the flap valve 50 as described above within the pump 10 causes fluid to flow in the direction indicated by the dashed arrows in Figure 2A (1) creating a negative pressure outside the primary aperture 16' of the pump 10.
  • the flap valve 50 is disposed within the primary aperture 16' so that the fluid is drawn into the cavity 11 through the primary aperture 16' and expelled from the cavity 11 through the secondary apertures 15 as indicated by the solid arrows, thereby providing a source of reduced pressure at the primary aperture 16'.
  • the fluid flow through the primary aperture 16' as indicated by the solid arrow pointing upwards corresponds to the fluid flow through the vent holes 54 and 55 of the flap valve 50 as indicated by the dashed arrows in Figure 2A (1) that also point upwards.
  • the operation of the flap valve 50 is a function of the change in direction of the differential pressure ( ⁇ P) of the fluid across the flap valve 50.
  • the differential pressure ( ⁇ P) is assumed to be substantially uniform across the entire surface of the retention plate 52 because its position corresponds to the centre pressure anti-node 23 as shown in Figure 1 A(2), which is generally aligned with the primary aperture 16' in the base 18 of the pump 10 and, therefore, a good approximation that there is no spatial variation in the pressure across the valve 50.
  • the radial dependence of the amplitude of the axial displacement oscillations of the actuator 40 should approximate a Bessel function of the first kind so as to match more closely the radial dependence of the amplitude of the desired pressure oscillations in the cavity 11 (the “mode-shape” of the pressure oscillation).
  • the mode-shape of the displacement oscillations substantially matches the mode-shape of the pressure oscillations in the cavity 11, thus achieving mode-shape matching or, more simply, mode-matching.
  • the axial displacement oscillations of the actuator 40 and the corresponding pressure oscillations in the cavity 11 have substantially the same relative phase across the full surface of the actuator 40 wherein the radial position of the annular pressure node 25 of the pressure oscillations in the cavity 11 and the radial position of the annular displacement node 22 of the axial displacement oscillations of actuator 40 are substantially coincident.
  • the radius of the actuator (r act ) should preferably be greater than the radius of the annular pressure node 25 to optimize mode-matching. Assuming again that the pressure oscillation in the cavity 11 11 approximates a Bessel function of the first kind, the radius of the annular pressure node 25 would be approximately 0.63 of the radius from the centre of the end wall 13 to the side wall 14, i.e., the radius of the cavity 11 (r) as shown in Figure 1 . Therefore, the radius of the actuator 40 (r act ) should preferably satisfy the following inequality: r act ⁇ 0.63 r .
  • the isolator 30 is a flexible membrane 31 which enables the edge of the actuator 40 to move more freely as described above by bending and stretching in response to the vibration of the actuator 40 as shown by the displacement of the peripheral displacement oscillations 21' in Figure 6(a) .
  • the flexible membrane 31 overcomes the potential dampening effects of the side wall 14 on the actuator 40 by providing a low mechanical impedance support between the actuator 40 and the cylindrical wall 19 of the pump 10 thereby reducing the dampening of the axial oscillations of the peripheral displacement oscillations 21' of the actuator 40.
  • flexible membrane 31 minimizes the energy being transferred from the actuator 40 to the side wall 14, which remains substantially stationary.
  • the annular displacement node 22 will remain substantially aligned with the annular pressure node 25 so as to maintain the mode-matching condition of the pump 10.
  • the axial displacement oscillations of the driven end wall 12 continue to efficiently generate oscillations of the pressure within the cavity 11 from the centre pressure anti-node 23 ( Figure 1 A) to the peripheral pressure anti-node 24 at the side wall 14.
  • F bend E a ⁇ u ⁇ ⁇ a 3 2 ⁇ R 3
  • the actuator 40 has an effective Young's modulus ( E a ), thickness ( ⁇ a ), and radius (R).
  • E a Young's modulus
  • ⁇ a thickness
  • R radius
  • the simple flexible membrane 31 should preferably have a thickness ( ⁇ m ) characterized by the following inequality: ⁇ m ⁇ ⁇ E a ⁇ g 2 ⁇ ⁇ a 3 E s ⁇ u ⁇ R 3 .
  • this inequality requires that the thickness of a flexible membrane 31 composed of Kapton is preferably ⁇ m ⁇ 1,000 microns, and the thickness of a flexible membrane 31 composed of steel is preferably ⁇ m ⁇ 100 microns.
  • the diameter of the actuator 40 may be 1-2 mm less than the diameter of the cavity 11 such that the flexible membrane 31 spans the peripheral portion of the end wall 12.
  • the peripheral portion may be an annular gap of 0.5-1.0 mm between the edge of the actuator 40 and the side wall 14 of the cavity 11.
  • the annular width of the flexible membrane 31 should be relatively small compared to the cavity radius (r) such that the actuator diameter is close to the cavity diameter so that the diameter of the annular displacement node 22 is approximately equal to the diameter of the annular pressure node 25, while being large enough to facilitate and not restrict the vibrations of the actuator 40.
  • the flexible membrane 31 may be made from a polymer sheet material of uniform thickness such as, for example, PET or Kapton.
  • the flexible membrane 31 may be made from Kapton sheeting having a thickness of less than about 200 microns.
  • the flexible membrane 31 may also be made from a thin metal sheet of uniform thickness such as, for example, steel or brass, or any other suitable flexible material.
  • the flexible membrane 31 may be made from steel sheeting having a thickness of less than about 20 microns.
  • the flexible membrane 31 may be made of any other flexible material suitable to facilitate vibration of the actuator 40 as described above.
  • the flexible membrane 31 may be glued, welded, clamped, soldered, or otherwise attached to the actuator 40 depending on the material used, and either the same process or a different process may be used to attach the flexible membrane 31 to the side wall 14.
  • the edge of the actuator 40 While the primary component of motion of the edge of the actuator 40 is substantially perpendicular to the driven end wall 12 or substantially parallel to the longitudinal axis of the cavity 11 (the "axial motion"), the edge of the actuator 40 also has a smaller component of "radial motion” occurring in the plane perpendicular to the longitudinal axis of the cavity 11.
  • the flexible membrane 31 should also be designed to stretch in a radial direction. Such radial stretching may be achieved by forming the actuator 40 from a thin elastic material as described above or by incorporating structural features into the flexible membrane 31 to enhance the radial flexibility of the flexible member 31 to stretch and compress, i.e., the stretch-ability of the flexible membrane 31, with the radial movement of the actuator 40 to further facilitate the vibration of the actuator 40.
  • FIG. 7A a first embodiment of a structurally modified flexible membrane 32 is shown that includes an annular concertina portion 33 extending between the actuator 40 and the side wall 14.
  • the concertina portion 33 comprises annular bends in the flexible membrane 32 appearing as waves in Figure 7A that expand and contract with the motion of the actuator 40 like an accordion.
  • the concertina portion 33 of the flexible membrane 32 effectively reduces the radial stiffness of the flexible membrane 32 thereby enhancing the stretch-ability of the flexible membrane 32 and enabling the actuator 40 to expand and contract more easily in a radial direction.
  • a second embodiment of a structurally modified flexible membrane 34 is shown that includes annular, semi-circular grooves 35 staggered on each side of the flexible membrane 34 between the actuator 40 and the side wall 14.
  • the annular grooves 35 of the flexible membrane 34 may be formed by chemical etching, grinding, or any similar processes, or may be formed by laminations.
  • the annular grooves 35 of the flexible membrane 34 effectively reduce the radial stiffness of the flexible membrane 34 thereby enhancing the stretch-ability of the flexible membrane 34 to facilitate the expansion and contraction of the actuator 40 in the radial direction.
  • the structures shown in Figures 7A and 7B and similar structures may also beneficially reduce the force required to bend the isolators 32, 34 in the axial direction.
  • the isolator 30 and flexible membranes 31, 32 and 34 shown in the previous figures are ring-shaped components extending between the side wall 14 and the actuator 40, the isolator 30 may also have different shapes and be supported by the cylindrical wall 19 in different ways without extending fully to the side wall 14 of the cavity 11.
  • alternative embodiments of the flexible membrane 31 are shown including flexible membranes 36 and 37, respectively, that function in a fashion similar to the other flexible membranes 31, 32 and 34.
  • the flexible membrane 36 is formed in the shape of a disc, the inside surface of which forms the end wall 12, rather than the end plate 17. The end plate 17 which remains operatively connected to the upper surface of the flexible membrane 36 as shown.
  • the end wall 12 still comprises the central portion operatively connected to the actuator 40, and the peripheral portion functioning as the isolator 30 between the side wall 14 and the actuator 40.
  • the flexible member 36 operates in a fashion similar to that of the other flexible membranes 31, 32 and 34.
  • the cylindrical wall 19 of the pump body includes a lip portion 19a extending radially inward from the side wall 14 of the pump body.
  • the inside surface of the lip portion 19a facing the cavity 11 forms an outer portion of the peripheral portion of the end wall 12 that is disposed adjacent the side wall 14.
  • the flexible membrane 37 may be ring-shaped or disc-shaped as shown and attached to the inside surface of the lip 19a of the cylindrical wall 19 to form the remaining portion of the end wall 12 as described above. Regardless of the shape of the flexible membrane 37, the end wall 12 still comprises the central portion operatively connected to the actuator 40, and a peripheral portion functioning as the isolator 30 between the actuator 40 and the lip 19a of the cylindrical wall 19.
  • the flexible member 37 operates in a fashion similar to that of the other flexible membranes 31, 32 and 34. It should be apparent that the structure, suspension and shape of the isolator 30 is not limited to these embodiments, but is susceptible to various changes and modifications without departing from the spirit of the inventions described herein.
  • the side wall 14 extends continuously between the end walls 12,13 of the cavity 11, and the radius of the actuator 40 (r act ) is less than the radius of the cavity 11 (r).
  • the side wall 14 defines an uninterrupted surface from which the radial acoustic standing wave formed in the cavity 11 is reflected during operation.
  • the radius of the actuator (r act ) it may be desirable for the radius of the actuator (r act ) to extend all the way to the side wall 14 making it about equal to the radius of the cavity (r) to ensure that the annular displacement node 22 of the displacement oscillations is more closely aligned with the annular pressure node 25 of the pressure oscillations so as to maintain more closely the mode-matching condition described above.
  • the cylindrical wall 19 of the pump body comprises an annular step 19b in the upper, inside surface of the cylindrical wall 19 extending radially outward from the side wall 14 to an annular edge 19c.
  • the annular step 19b is cut sufficiently deep into the upper surface of the cylindrical wall 19 so as not to interfere with the bending of the flexible membrane 38 to enable the actuator 40 to vibrate freely.
  • the step 19b should be sufficiently deep to accommodate the bending of the flexible membrane 38, but not so deep as to significantly diminish the resonant quality of the cavity 11 referred to above.
  • the driven end wall 12 comprises the lower surface of the end plate 17 and the flexible membrane 38, and has a radius (r end ) that is greater than the radius of the cavity 11, i.e., r end > r.
  • the peripheral portion of the end wall 12 extends beyond the side wall 14 of the cavity 11.
  • the radial position of the annular pressure node 25 of the pressure oscillation in the cavity 11 and the radial position of the annular displacement node 22 of the axial oscillation of the actuator 40 may be more coincident to further enhance mode-matching.
  • the depth of the step 19b is preferably minimized as described above.
  • the depth of the step 19b may be sized to maintain so far as possible the resonant qualities of the pump cavity 11.
  • the depth of the step 19b may be less than or equal to 10% of the height of the cavity 11.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (21)

  1. Une pompe (10) comprenant :
    un corps de pompe de forme substantiellement cylindrique définissant une cavité (11) pour contenir un fluide, la cavité étant formée par une paroi latérale (14) fermée aux deux bouts par des parois d'extrémité (12, 13), au moins une des parois d'extrémité étant une paroi d'extrémité entraînée (12), comprenant une partie centrale et une partie périphérique s'étendant radialement et vers l'extérieur depuis la partie centrale de la paroi d'extrémité entraînée ;
    un servomoteur (40) associé fonctionnellement avec la partie centrale de la paroi d'extrémité entraînée, de façon à causer un mouvement oscillatoire de la paroi d'extrémité entraînée, en produisant ainsi des oscillations de déplacement de la paroi d'extrémité entraînée dans une direction substantiellement perpendiculaire à celle-ci, avec un noeud annulaire entre le centre de la paroi d'extrémité entraînée et la paroi latérale, en cours d'usage ;
    une première ouverture (16) disposée en un point quelconque de la cavité, excepté l'emplacement du noeud annulaire, et s'étendant à travers le corps de la pompe ;
    une deuxième ouverture (15) disposée en un point quelconque du corps de la pompe excepté l'emplacement de ladite première ouverture, et s'étendant à travers le corps de la pompe ; et
    un clapet (46) disposé dans au moins une des suivantes : la première ouverture ou la deuxième ouverture ;
    les oscillations de déplacement produisant des oscillations correspondantes de pression radiale du fluide au sein de la cavité dudit corps de pompe, en donnant lieu à un écoulement de fluide à travers lesdites première et deuxième ouvertures en cours d'usage ; caractérisée par
    un séparateur flexible de forme annulaire ou de disque (30) associé fonctionnellement avec la partie périphérique de la paroi d'extrémité entraînée (12), de façon à réduire l'amortissement des oscillations de déplacement.
  2. La pompe (10) selon la revendication 1, le ratio du rayon (r) de la cavité (11), s'étendant de l'axe longitudinal de la cavité à la paroi latérale, sur la hauteur (h) de la paroi de la cavité, étant supérieur à environ 1,2.
  3. La pompe (10) selon la revendication 2, la hauteur (h) de la cavité (11) et le rayon (r) de la cavité étant également liés par l'équation suivante : h2/r > 4 x 10-10 mètres.
  4. La pompe (10) selon la revendication 2, la deuxième ouverture (15) étant disposée dans une des parois d'extrémité (12, 13) à une distance égale à environ 0,63(r) ± 0,2(r) du centre de la paroi d'extrémité.
  5. La pompe (10) selon la revendication 2, dans laquelle ledit servomoteur (40) entraîne la paroi d'extrémité connexe, en causant le mouvement oscillatoire à une fréquence (f).
  6. La pompe (10) selon la revendication 2, dans laquelle ledit servomoteur (40) entraîne la paroi d'extrémité connexe, en causant le mouvement oscillatoire à une fréquence (f), le rayon (r) se rapportant à la fréquence (f) avec l'équation suivante : k 0 ⁢ c s 2 π f ≤ r ≤ k 0 ⁢ c f 2 π f
    Figure imgb0009
    dans laquelle Cs ≈ 115 m/s
    cr ≈ 1970 m/s, et
    k0 ≈ 3,83
  7. La pompe (10) selon la revendication 1, dans laquelle la fréquence résonante la plus basse de la pression radiale est supérieure à environ 500 Hz.
  8. La pompe (10) selon la revendication 1, dans laquelle les oscillations de déplacement de la paroi d'extrémité entraînée (12) sont assorties en mode propre aux oscillations de pression radiale.
  9. La pompe (10) selon la revendication 1, dans laquelle ledit clapet (46) permet au fluide de s'écouler dans la cavité substantiellement dans une direction.
  10. La pompe (10) selon la revendication 1, dans laquelle ledit séparateur (30) étant une membrane flexible.
  11. La pompe (10) selon la revendication 10, dans laquelle la membrane flexible est réalisée en matière plastique.
  12. La pompe (10) selon la revendication 11, dans laquelle la largeur annulaire de la membrane flexible est comprise entre 0,5 et 1,0 mm, et l'épaisseur de la membrane flexible est inférieure à environ 200 microns.
  13. La pompe (10) selon la revendication 10, dans laquelle la membrane flexible est réalisée en métal.
  14. La pompe (10) selon la revendication 13, dans laquelle la largeur annulaire de la membrane flexible mesure entre 0,5 et 1,0 mm, l'épaisseur de la membrane flexible est inférieure à environ 20 microns.
  15. La pompe (10) selon la revendication 1, dans laquelle la paroi latérale (12, 13) de la pompe (10) comprend un évidement s'étendant radialement vers l'extérieur, dans une position adjacente à au moins une des parois d'extrémité au sein de la cavité (11).
  16. La pompe (10) selon la revendication 2, dans laquelle le ratio r/h est environ 10, et environ 50 lorsque le fluide utilisé à l'intérieur de la cavité est un gaz.
  17. La pompe (10) selon la revendication 2, dans laquelle le ratio h2/r est environ 10-3 mètres, et environ 10-6 mètres lorsque le fluide utilisé à l'intérieur de la cavité est un gaz.
  18. La pompe (10) selon la revendication 1, comprenant également :
    Un deuxième servomoteur (62) opérationnellement associé avec la partie centrale de l'autre paroi d'extrémité, en donnant lieu à un mouvement oscillatoire de ladite paroi d'extrémité dans une direction substantiellement perpendiculaire à celle-ci ; et
    Un deuxième séparateur (66) opérationnellement associé avec la partie périphérique de cette paroi d'extrémité, pour réduire l'amortissement du mouvement oscillatoire de ladite paroi d'extrémité par la paroi latérale au sein de la cavité.
  19. La pompe (10) selon la revendication 2, dans laquelle le rayon dudit servomoteur (40) est supérieur ou égal à 0,63(r).
  20. La pompe (10) selon la revendication 2, dans laquelle le rayon dudit servomoteur (40) est inférieur ou égal au rayon de la cavité (r).
  21. La pompe (10) selon la revendication 1, dans laquelle ledit servomoteur (40) comprend un composant piézoélectrique ou magnéto-restrictif pour causer le mouvement oscillatoire.
EP09785226.3A 2009-06-03 2009-06-03 Pompe a disques Active EP2438301B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/GB2009/050613 WO2010139916A1 (fr) 2009-06-03 2009-06-03 Pompe à disque pour fluides

Publications (2)

Publication Number Publication Date
EP2438301A1 EP2438301A1 (fr) 2012-04-11
EP2438301B1 true EP2438301B1 (fr) 2015-10-28

Family

ID=41557597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09785226.3A Active EP2438301B1 (fr) 2009-06-03 2009-06-03 Pompe a disques

Country Status (9)

Country Link
EP (1) EP2438301B1 (fr)
JP (1) JP2012528980A (fr)
CN (1) CN102459900A (fr)
AU (1) AU2009347420B2 (fr)
CA (1) CA2764332C (fr)
MX (1) MX2011012975A (fr)
RU (1) RU2011154213A (fr)
SG (1) SG176226A1 (fr)
WO (1) WO2010139916A1 (fr)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10660994B2 (en) 2012-03-12 2020-05-26 Smith & Nephew Plc Reduced pressure apparatus and methods
USD898925S1 (en) 2018-09-13 2020-10-13 Smith & Nephew Plc Medical dressing
US10898388B2 (en) 2015-04-27 2021-01-26 Smith & Nephew Plc Reduced pressure apparatuses and methods
US11096831B2 (en) 2016-05-03 2021-08-24 Smith & Nephew Plc Negative pressure wound therapy device activation and control
US11116669B2 (en) 2016-08-25 2021-09-14 Smith & Nephew Plc Absorbent negative pressure wound therapy dressing
US11123471B2 (en) 2017-03-08 2021-09-21 Smith & Nephew Plc Negative pressure wound therapy device control in presence of fault condition
US11160915B2 (en) 2017-05-09 2021-11-02 Smith & Nephew Plc Redundant controls for negative pressure wound therapy systems
US11173240B2 (en) 2016-05-03 2021-11-16 Smith & Nephew Plc Optimizing power transfer to negative pressure sources in negative pressure therapy systems
US11285047B2 (en) 2016-04-26 2022-03-29 Smith & Nephew Plc Wound dressings and methods of use with integrated negative pressure source having a fluid ingress inhibition component
US11305047B2 (en) 2016-05-03 2022-04-19 Smith & Nephew Plc Systems and methods for driving negative pressure sources in negative pressure therapy systems
US11497653B2 (en) 2017-11-01 2022-11-15 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11554203B2 (en) 2017-11-01 2023-01-17 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11564847B2 (en) 2016-09-30 2023-01-31 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11564845B2 (en) 2017-09-13 2023-01-31 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11701265B2 (en) 2017-09-13 2023-07-18 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11707564B2 (en) 2017-11-01 2023-07-25 Smith & Nephew Plc Safe operation of integrated negative pressure wound treatment apparatuses
US11723809B2 (en) 2016-03-07 2023-08-15 Smith & Nephew Plc Wound treatment apparatuses and methods with negative pressure source integrated into wound dressing
US12005181B2 (en) 2016-12-12 2024-06-11 Smith & Nephew Plc Pressure wound therapy status indication via external device
US12005182B2 (en) 2019-05-31 2024-06-11 T.J.Smith And Nephew, Limited Systems and methods for extending operational time of negative pressure wound treatment apparatuses
US12083263B2 (en) 2019-03-20 2024-09-10 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US12121420B2 (en) 2022-03-02 2024-10-22 Smith & Nephew Plc Wound dressings and methods of use with integrated negative pressure source having a fluid ingress inhibition component

Families Citing this family (48)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8646479B2 (en) * 2010-02-03 2014-02-11 Kci Licensing, Inc. Singulation of valves
GB201101870D0 (en) 2011-02-03 2011-03-23 The Technology Partnership Plc Pump
JP5528404B2 (ja) † 2011-09-06 2014-06-25 株式会社村田製作所 流体制御装置
CA2845880C (fr) 2011-09-21 2019-08-20 Kci Licensing, Inc. Structure de pompe a disque et de valve
CN103339380B (zh) 2011-10-11 2015-11-25 株式会社村田制作所 流体控制装置、流体控制装置的调节方法
GB201120887D0 (en) 2011-12-06 2012-01-18 The Technology Partnership Plc Acoustic sensor
GB201202346D0 (en) * 2012-02-10 2012-03-28 The Technology Partnership Plc Disc pump with advanced actuator
CN104066990B (zh) 2012-03-07 2017-02-22 凯希特许有限公司 带有高级致动器的盘泵
CA2878279C (fr) * 2012-07-05 2020-06-30 Kci Licensing, Inc. Systemes et procedes destines a reguler la frequence de resonance d'une cavite de pompe a membrane
CN102966520B (zh) * 2012-11-07 2016-04-06 广州市番禺奥迪威电子有限公司 一种压电泵
CN105026050A (zh) 2013-03-14 2015-11-04 通用电气公司 低共振声音合成喷射器结构
CN105307776B (zh) * 2013-03-15 2019-07-16 通用电气公司 合成喷射器装置及其制作方法
GB2513884B (en) 2013-05-08 2015-06-17 Univ Bristol Method and apparatus for producing an acoustic field
GB201322103D0 (en) 2013-12-13 2014-01-29 The Technology Partnership Plc Fluid pump
CN106062364B (zh) * 2014-02-21 2018-03-13 株式会社村田制作所 鼓风机
GB2538413B (en) 2014-03-07 2020-08-05 Murata Manufacturing Co Blower
JP6103151B2 (ja) * 2014-07-25 2017-03-29 株式会社村田製作所 気体制御装置
CN206903844U (zh) * 2014-08-20 2018-01-19 株式会社村田制作所 鼓风机
GB2530036A (en) 2014-09-09 2016-03-16 Ultrahaptics Ltd Method and apparatus for modulating haptic feedback
JP6380075B2 (ja) * 2014-12-15 2018-08-29 株式会社村田製作所 ブロア
KR102524966B1 (ko) 2015-02-20 2023-04-21 울트라햅틱스 아이피 엘티디 햅틱 시스템에서의 알고리즘 개선
US9841819B2 (en) 2015-02-20 2017-12-12 Ultrahaptics Ip Ltd Perceptions in a haptic system
US10818162B2 (en) 2015-07-16 2020-10-27 Ultrahaptics Ip Ltd Calibration techniques in haptic systems
US11189140B2 (en) 2016-01-05 2021-11-30 Ultrahaptics Ip Ltd Calibration and detection techniques in haptic systems
US10268275B2 (en) 2016-08-03 2019-04-23 Ultrahaptics Ip Ltd Three-dimensional perceptions in haptic systems
US10943578B2 (en) 2016-12-13 2021-03-09 Ultrahaptics Ip Ltd Driving techniques for phased-array systems
GB2579954B (en) 2017-10-10 2022-08-10 Murata Manufacturing Co Pump and fluid control apparatus
US11531395B2 (en) 2017-11-26 2022-12-20 Ultrahaptics Ip Ltd Haptic effects from focused acoustic fields
WO2019122912A1 (fr) 2017-12-22 2019-06-27 Ultrahaptics Limited Suivi dans des systèmes haptiques
JP7483610B2 (ja) 2017-12-22 2024-05-15 ウルトラハプティクス アイピー リミテッド 触覚システムにおける不要な応答の最小化
WO2019130853A1 (fr) 2017-12-26 2019-07-04 株式会社村田製作所 Pompe et dispositif de régulation de fluide
SG11202010752VA (en) 2018-05-02 2020-11-27 Ultrahaptics Ip Ltd Blocking plate structure for improved acoustic transmission efficiency
US11098951B2 (en) 2018-09-09 2021-08-24 Ultrahaptics Ip Ltd Ultrasonic-assisted liquid manipulation
US11378997B2 (en) 2018-10-12 2022-07-05 Ultrahaptics Ip Ltd Variable phase and frequency pulse-width modulation technique
JP7047937B2 (ja) * 2018-11-27 2022-04-05 株式会社村田製作所 ポンプ
JP7031758B2 (ja) * 2018-11-27 2022-03-08 株式会社村田製作所 ポンプ
US11550395B2 (en) 2019-01-04 2023-01-10 Ultrahaptics Ip Ltd Mid-air haptic textures
US11842517B2 (en) 2019-04-12 2023-12-12 Ultrahaptics Ip Ltd Using iterative 3D-model fitting for domain adaptation of a hand-pose-estimation neural network
US20220260067A1 (en) * 2019-06-03 2022-08-18 Sony Group Corporation Fluid control apparatus and electronic apparatus
US11374586B2 (en) 2019-10-13 2022-06-28 Ultraleap Limited Reducing harmonic distortion by dithering
US11553295B2 (en) 2019-10-13 2023-01-10 Ultraleap Limited Dynamic capping with virtual microphones
WO2021090028A1 (fr) 2019-11-08 2021-05-14 Ultraleap Limited Techniques de suivi dans des systèmes haptiques
US11715453B2 (en) 2019-12-25 2023-08-01 Ultraleap Limited Acoustic transducer structures
US11816267B2 (en) 2020-06-23 2023-11-14 Ultraleap Limited Features of airborne ultrasonic fields
GB2583880A (en) 2020-07-31 2020-11-11 Ttp Ventus Ltd Actuator for a resonant acoustic pump
WO2022058738A1 (fr) 2020-09-17 2022-03-24 Ultraleap Limited Ultrahapticons
GB2622575A (en) 2022-09-11 2024-03-27 Bioliberty Ltd Soft robotic assistive device
CN115822933A (zh) * 2022-12-23 2023-03-21 吉林大学 一种压电喷流泵

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5065978A (en) * 1988-04-27 1991-11-19 Dragerwerk Aktiengesellschaft Valve arrangement of microstructured components
CN1051073A (zh) * 1989-10-17 1991-05-01 精工爱普生株式会社 微电化泵
SE508435C2 (sv) * 1993-02-23 1998-10-05 Erik Stemme Förträngningspump av membranpumptyp
DE4422743A1 (de) * 1994-06-29 1996-01-04 Torsten Gerlach Mikropumpe
US5828394A (en) * 1995-09-20 1998-10-27 The Board Of Trustees Of The Leland Stanford Junior University Fluid drop ejector and method
US6074178A (en) * 1997-04-15 2000-06-13 Face International Corp. Piezoelectrically actuated peristaltic pump
JP2004517240A (ja) * 2000-09-18 2004-06-10 パー テクノロジーズ エルエルシー． 圧電アクチュエータおよびそれを用いたポンプ
US7198250B2 (en) * 2000-09-18 2007-04-03 Par Technologies, Llc Piezoelectric actuator and pump using same
GB0308197D0 (en) 2003-04-09 2003-05-14 The Technology Partnership Plc Gas flow generator
JP2007518910A (ja) * 2003-06-30 2007-07-12 コーニンクレッカ フィリップス エレクトロニクス エヌ ヴィ 媒体流生成装置
TWI256374B (en) * 2004-10-12 2006-06-11 Ind Tech Res Inst PDMS valve-less micro pump structure and method for producing the same
GB0508194D0 (en) * 2005-04-22 2005-06-01 The Technology Partnership Plc Pump
CN200989293Y (zh) * 2006-10-19 2007-12-12 吉林大学 微型喷水推进泵

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10660994B2 (en) 2012-03-12 2020-05-26 Smith & Nephew Plc Reduced pressure apparatus and methods
US11903798B2 (en) 2012-03-12 2024-02-20 Smith & Nephew Plc Reduced pressure apparatus and methods
US11129931B2 (en) 2012-03-12 2021-09-28 Smith & Nephew Plc Reduced pressure apparatus and methods
US12059325B2 (en) 2015-04-27 2024-08-13 Smith & Nephew Plc Reduced pressure apparatuses and methods
US10898388B2 (en) 2015-04-27 2021-01-26 Smith & Nephew Plc Reduced pressure apparatuses and methods
US11723809B2 (en) 2016-03-07 2023-08-15 Smith & Nephew Plc Wound treatment apparatuses and methods with negative pressure source integrated into wound dressing
US11285047B2 (en) 2016-04-26 2022-03-29 Smith & Nephew Plc Wound dressings and methods of use with integrated negative pressure source having a fluid ingress inhibition component
US11173240B2 (en) 2016-05-03 2021-11-16 Smith & Nephew Plc Optimizing power transfer to negative pressure sources in negative pressure therapy systems
US11305047B2 (en) 2016-05-03 2022-04-19 Smith & Nephew Plc Systems and methods for driving negative pressure sources in negative pressure therapy systems
US11096831B2 (en) 2016-05-03 2021-08-24 Smith & Nephew Plc Negative pressure wound therapy device activation and control
US11896465B2 (en) 2016-05-03 2024-02-13 Smith & Nephew Plc Negative pressure wound therapy device activation and control
US11116669B2 (en) 2016-08-25 2021-09-14 Smith & Nephew Plc Absorbent negative pressure wound therapy dressing
US11648152B2 (en) 2016-08-25 2023-05-16 Smith & Nephew Plc Absorbent negative pressure wound therapy dressing
US11564847B2 (en) 2016-09-30 2023-01-31 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US12005181B2 (en) 2016-12-12 2024-06-11 Smith & Nephew Plc Pressure wound therapy status indication via external device
US11123471B2 (en) 2017-03-08 2021-09-21 Smith & Nephew Plc Negative pressure wound therapy device control in presence of fault condition
US11160915B2 (en) 2017-05-09 2021-11-02 Smith & Nephew Plc Redundant controls for negative pressure wound therapy systems
US11701265B2 (en) 2017-09-13 2023-07-18 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11564845B2 (en) 2017-09-13 2023-01-31 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US12097097B2 (en) 2017-09-13 2024-09-24 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11707564B2 (en) 2017-11-01 2023-07-25 Smith & Nephew Plc Safe operation of integrated negative pressure wound treatment apparatuses
US11554203B2 (en) 2017-11-01 2023-01-17 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11992392B2 (en) 2017-11-01 2024-05-28 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US11497653B2 (en) 2017-11-01 2022-11-15 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
USD999914S1 (en) 2018-09-13 2023-09-26 Smith & Nephew Plc Medical dressing
USD898925S1 (en) 2018-09-13 2020-10-13 Smith & Nephew Plc Medical dressing
US12083263B2 (en) 2019-03-20 2024-09-10 Smith & Nephew Plc Negative pressure wound treatment apparatuses and methods with integrated electronics
US12005182B2 (en) 2019-05-31 2024-06-11 T.J.Smith And Nephew, Limited Systems and methods for extending operational time of negative pressure wound treatment apparatuses
US12121420B2 (en) 2022-03-02 2024-10-22 Smith & Nephew Plc Wound dressings and methods of use with integrated negative pressure source having a fluid ingress inhibition component

Also Published As

Publication number Publication date
JP2012528980A (ja) 2012-11-15
WO2010139916A1 (fr) 2010-12-09
CA2764332C (fr) 2016-11-01
AU2009347420A1 (en) 2011-12-15
CN102459900A (zh) 2012-05-16
RU2011154213A (ru) 2013-07-20
EP2438301A1 (fr) 2012-04-11
CA2764332A1 (fr) 2010-12-09
MX2011012975A (es) 2012-04-02
AU2009347420B2 (en) 2016-02-11
SG176226A1 (en) 2011-12-29

Similar Documents

Publication Publication Date Title
EP2438301B1 (fr) Pompe a disques
US8821134B2 (en) Fluid disc pump
AU2016200869B2 (en) Pump with disc-shaped cavity
US8297947B2 (en) Fluid disc pump
EP2812573B1 (fr) Pompe a disques avec actionneur avancé
AU2012312898B2 (en) Dual -cavity pump
EP1875081B1 (fr) Pompe
EP3660308B1 (fr) Pompe à disque à deux cavités
EP2531160B1 (fr) Dispositif d'entraînement d'ondes carrées pour pompe à fluide cylindrique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20111223

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20131023

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150428

RIN1 Information on inventor provided before grant (corrected)

Inventor name: JANSE VAN RENSBURG, RICHARD

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

INTG Intention to grant announced

Effective date: 20150904

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 758107

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151115

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602009034517

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 758107

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151028

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160228

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160128

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160129

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160229

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602009034517

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20160729

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160630

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20090603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160630

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160603

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151028

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 602009034517

Country of ref document: DE

Owner name: TTP VENTUS LIMITED, ROYSTON, GB

Free format text: FORMER OWNER: THE TECHNOLOGY PARTNERSHIP PLC, MELBOURN, ROYSTON, HERTFORDSHIRE, GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20210715 AND 20210721

REG Reference to a national code

Ref country code: NL

Ref legal event code: PD

Owner name: TTP VENTUS LIMITED; GB

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), ASSIGNMENT; FORMER OWNER NAME: TTP PLC

Effective date: 20220222

Ref country code: NL

Ref legal event code: HC

Owner name: TTP PLC; GB

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), CHANGE OF OWNER(S) NAME; FORMER OWNER NAME: THE TECHNOLOGY PARTNERSHIP PLC

Effective date: 20220222

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230523

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20240415

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20240328

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IE

Payment date: 20240410

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20240402

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240328

Year of fee payment: 16