EP4196683A1 - Pompe à lame de liquide - Google Patents

Pompe à lame de liquide

Info

Publication number
EP4196683A1
EP4196683A1 EP21755039.1A EP21755039A EP4196683A1 EP 4196683 A1 EP4196683 A1 EP 4196683A1 EP 21755039 A EP21755039 A EP 21755039A EP 4196683 A1 EP4196683 A1 EP 4196683A1
Authority
EP
European Patent Office
Prior art keywords
liquid
rotor
stator
pump
gas
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.)
Withdrawn
Application number
EP21755039.1A
Other languages
German (de)
English (en)
Inventor
Paul David Smith
Peter Anthony Mcbrien
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.)
Edwards Ltd
Original Assignee
Edwards Ltd
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 Edwards Ltd filed Critical Edwards Ltd
Publication of EP4196683A1 publication Critical patent/EP4196683A1/fr
Withdrawn legal-status Critical Current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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/02—Liquid sealing for high-vacuum pumps or for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/22—Rotary-piston pumps specially adapted for elastic fluids of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/18—Centrifugal pumps characterised by use of centrifugal force of liquids entrained in pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/008—Details of the stator, e.g. channel shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
    • F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
    • F04F5/06—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/42—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow characterised by the input flow of inducing fluid medium being radial or tangential to output flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F99/00—Subject matter not provided for in other groups of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/12—Fluid auxiliary
    • F04C2210/128—Water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • F04C2240/102—Stators with means for discharging condensate or liquid separated from the gas pumped
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the field of the invention relates to pumps.
  • entrapment type pumps where a gas is captured on a surface inside the pump prior to being removed
  • kinetic or momentum transfer pumps such as turbomolecular pumps where the molecules of the gas are accelerated from the inlet side towards the outlet or exhaust side
  • positive displacement pumps where gas is trapped and moved from the inlet towards the outlet of the pump.
  • Positive displacement pumps provide moving pumping chambers generally formed between one or more rotors and a stator, the movement of the rotors causing the effective pumping chamber to move. Gas received at an inlet enters and is trapped in the pumping chamber and moved to an outlet. In some cases the volume of the gas pocket reduces during movement to improve efficiency.
  • Such pumps include roots, and rotary vane type pumps. In order to draw the gas into the chamber, the chamber generally expands and to expel the gas from the chamber, the chamber volume generally contracts.
  • This change in volume can be achieved for example in a rotary vane pump by blades that extend in and out of the pump chamber using devices such as springs, which are themselves subject to wear, or using two synchronised rotors in a roots or screw pump which cooperate with each other and a stator to move a pocket of gas and generate the volumetric changes between inlet and outlet.
  • An additional rotor requires an additional shaft, bearings and timing methods such as gears to synchronise the rotor movements.
  • the moving parts need to form a close seal with each other and with the static parts which form the trapped volume of gas.
  • Some pumps use a liquid such as oil to seal between the surfaces of the trapped volume whilst others rely on tight non-contacting clearances which can lead to increased manufacturing costs and can also lead to pumps that are sensitive to locking or seizure if the parts come into contact or where particulates or impurities are present in the fluid being pumped.
  • GB2565579 discloses a pump that uses a liquid to form the pump blade and thereby addresses some of the problems above.
  • a liquid blade is by its nature deformable and can be distorted, and distortion in the liquid blade can lead to leakage between the distorted portion of the blade and the solid surface of the rotor or stator to which it should seal.
  • a first aspect provides a pump for pumping a gas, said pump comprising: a rotor and a stator; one of said rotor or stator comprising at least one liquid opening configured for fluid communication with a liquid source; said liquid opening being configured such that in response to a driving force a stream of liquid is output from said opening, said stream of liquid forming a liquid blade between said rotor and said stator, gas confined by said stator, said rotor and said liquid blade being driven through said pump along a pumping channel from a gas inlet towards a gas outlet in response to relative rotational motion of said rotor and said stator; wherein said pump is configured such that said pumping channel comprises side walls that slope towards each other from said rotor or stator that comprises said liquid opening towards a further wall of said pumping channel remote from said rotor or stator comprising said liquid opening, such that a distance between said side walls decreases with increasing distance from said liquid opening, a tangent to a mid point of said side walls having an angle of between 5 Q
  • the inventors of the present invention recognised that were the elements of a pump to be configured with liquid opening(s) such that liquid output through the openings formed a surface or blade between the elements of the pump, then on rotation of one of the elements with respect to the other, the liquid blade could be used to drive the gas through the pump.
  • Such a liquid blade is by its nature, deformable, low cost, and generally able to provide good sealing between surfaces of the trapped volume without the need for tight manufacturing tolerances. Furthermore, such a blade is not subject to wear itself and provides very little wear on the surfaces that it contacts.
  • the blade is formed of a flowing liquid such that the liquid forming the blade is continuously replenished.
  • a surface of the blade acts along with a surface of the elements to confine, trap, isolate or enclose the gas to be pumped.
  • Relative rotation of the rotor and stator cause the trapped gas to be moved from a gas inlet to a gas outlet along a pumping path or channel.
  • Gas to be pumped is located on either side of the blade.
  • the liquid blade is by its nature deformable and can be distorted, and this may lead to leakage between the distorted portion of the blade and a solid surface of the rotor or stator to which it should seal.
  • there is tapering of the liquid sheet or blade away from the liquid opening(s) and thus, there is an opportunity for gas leakage between the side walls of the pumping channel and the edges of the liquid blade, particularly at radial distances remote from the liquid openings where the cumulative effect of the tapering of the blade is greater.
  • This has been addressed by providing side walls to the pumping channel that are themselves tapered, so that they slope towards each other to compensate for the tapering of the liquid blade, providing for improved sealing along the edge of the liquid blade.
  • the angle of the side wall is selected to be slightly greater than the angle of taper of the liquid blade such that there is not a gap between the blade and the side wall.
  • the angle of taper of a liquid blade will depend on the type of liquid and in particular, its surface tension and viscosity and on the speed of rotation and the driving force pushing the liquid out through the liquid openings.
  • a surface of the liquid blade comprises a radial dimension between said rotor and stator and an axial dimension perpendicular to said radial dimension and parallel to an axis of rotation.
  • the pump is configured such that a dimension of said pumping channel parallel to said axial dimension of said liquid blade decreases with increasing radial distance from said liquid opening.
  • the angle of the side wall is configured to be similar to but slightly greater than the predicted angle of taper of the liquid blade. It is configured such that a tangent to a mid point of the side walls have an angle of between 5 s and 40 2 with respect to a line perpendicular to an axis of rotation of said rotor. Preferably between 8 Q and 25 Q more preferably, between 10 Q and 15 Q .
  • the sloped angle is the angle of much of the side wall, in some embodiments, the middle section of the side wall is straight and sloped at this angle with curved sections at either end.
  • said pump is configured such that said side walls of said pumping channel flare outwards towards a junction with said rotor or stator comprising said liquid opening.
  • the liquid blade tapering there may also be distortion of the liquid blade where it first impinges on the sealing edges of the side walls of the pumping channel.
  • This distortion and deviation from its original path can be reduced by flaring the walls outwards such that the sealing gap for the liquid blade is smaller and any deviation has a smaller effect towards the edges.
  • the flaring outwards means that the distance between side wall increases close to and in a direction towards the junction between the stator and rotor, the flaring providing a curved side wall surface.
  • said side walls are configured such that a junction between each of said side walls and said further wall is curved.
  • the further wall faces the rotor and in some embodiments, is substantially parallel to the axis of rotation of the rotor at its mid point.
  • said side walls are symmetrical about an axis perpendicular to a mid point of said further wall.
  • said rotor comprises said liquid opening and is mounted to rotate within said stator.
  • the rotor may in some embodiments, be a hollow cylinder rotationally mounted such that a lower end extends into a liquid reservoir or sump.
  • Rotational motion helps draw the liquid up the cylinder and expels it through the liquid openings, the liquid forming a blade which on impact with the stator wall runs down the stator walls, along the pumping channel and is collected in the sump to be reused.
  • said liquid opening comprises at least one slit, extending longitudinally parallel to an axis of rotation of said rotor.
  • the liquid opening may have a number of forms, in some embodiments it comprises a slit which when liquid exits the slit forms a substantially planar liquid blade.
  • the slit may be angled with respect to the rotational axis but in some embodiments extends longitudinally parallel to the axis of rotation of the rotor.
  • the liquid opening(s) may comprise a plurality of openings arranged along a line.
  • said rotor comprises a plurality of slits extending longitudinally parallel to an axis of rotation of said rotor at different positions around an outer circumference of said rotor.
  • said stator and rotor are configured such that said pumping channel runs around a circumference of an inner one of said rotor or stator, said gas inlet being arranged to be vertically higher than said gas outlet in operation.
  • the pumping channel is configured such that the gas inlet is higher than the gas outlet when the pump is in operation such that the liquid will drain out through the gas outlet.
  • the pumping channel runs around the circumference of the stator a single time, or rather slightly less than a whole turn around the circumference. In other embodiments, the pumping channel may run around the circumference of the stator multiple times.
  • a lower surface of said pumping channel at said gas outlet is lower than a lower surface of said pumping channel at said gas inlet, and a higher surface of said pumping channel at said gas outlet is higher than a lower surface of said pumping channel at said gas inlet
  • the liquid blade pushes the gas in a substantially circumferential direction along the direction of rotation of the rotor.
  • the pumping channel and gas outlet are also arranged along this path.
  • the gas outlet should be below the gas inlet to allow draining of the liquid, it is advantageous if it is only slightly below the gas inlet such that gas is effectively driven by the liquid blade as it rotates.
  • a cross sectional area of said pumping channel is configured to increase from said gas inlet to said gas outlet.
  • the cross-sectional area of the pumping channel may decrease from gas inlet to gas outlet to provide some compression of the gas, in some embodiments, the cross-sectional area increases.
  • the liquid that forms the liquid blade is continuously replenished, such that liquid collects within the pumping channel. Draining of the liquid from the pumping channel is required to maintain a free volume for pumping gas, and the liquid while it is within the pumping channel will decrease the volume available for the gas being pumped.
  • said pump is configured such that said increase in cross sectional area from said gas inlet to said gas outlet and an amount of liquid supplied to said pump during normal operation are selected, such that although the overall cross sectional area increases, the cross sectional area available to gas decreases from said gas inlet to said gas outlet and said gas being pumped is compressed. It may be advantageous to design the pump so that the increasing cross- sectional area and amount of liquid supplied to the pump to form the liquid blade in operation are linked so that the decrease in pumping channel volume that occurs due to the liquid collecting in the pumping channel can be compensated for to some extent by the increase in cross-sectional area but in such a way that the cross-sectional area available to the gas being pumped decreases slightly such that there is some amount of compression of the gas.
  • the pump further comprises sealing means between said side walls and said rotor or stator comprising said liquid opening.
  • sealing means may be applied between the side walls of the pumping channel and the rotor or stator comprising the liquid opening.
  • the width of the pumping channel from gas inlet to gas outlet decreases, close to the gas inlet the liquid opening will extend beyond the width of the narrower pumping channel and thus, providing sealing means to reduce the amount of liquid that exits the portion of the liquid opening(s) that do not open into the narrower channel close to the inlet is advantageous.
  • said pump comprises a vacuum pump.
  • Figure 1 shows a liquid blade in a pump according to an embodiment
  • Figure 2 shows a pump according to an embodiment
  • Figure 3 shows a cross-section through a pumping channel of a pump according to an embodiment.
  • Embodiments relate to a pump where the blade of the pump is formed by a liquid such as water that is expelled from one or more apertures in one of the rotor or stator to form a sheet of water that acts as a blade for pushing the fluid to be pumped through the pump.
  • a liquid such as water that is expelled from one or more apertures in one of the rotor or stator to form a sheet of water that acts as a blade for pushing the fluid to be pumped through the pump.
  • Relative rotation of the stator and rotor cause the fluid to be urged from an inlet to an outlet.
  • When liquid is expelled from the apertures to form a sheet this tapers away from the apertures such that the sheet narrows. This can cause problems of fluid leakage around the edges of the sheet which acts as the blade.
  • Embodiments address this by defining a similarly tapered shaped pumping channel such that the liquid blade adheres to the surface of the pumping channel walls and gaps are avoided or at least inhibited.
  • discrete volumes of gas to be pumped are defined within a stator structure by an upper and lower sealing edge and vertical water sheets. These sealed volumes are then driven radially from the inlet to the outlet in a mechanism analogous to a rotary vane pump.
  • One technical challenge is to maintain an effective gas seal between the water sheet and the sealing faces defined by the stator walls.
  • the pump comprises a hollow cylindrical rotor that carries water up from a sump and out through vertical slits to generating rotating sheets of water. As the water exits the slit the top and bottom edges of the sheet taper inwards towards the centre of the sheet as it travels out from the rotor to stator outer wall.
  • Figure 1 schematically shows the tapering of blade 40 formed of a sheet of liquid expelled through liquid opening 12, which in this embodiment has the form of a slit formed in rotor 10, the edges of the slit defining either edge of the blade 40.
  • the tapering angle is shown as 20° It should be understood that this angle may vary depending on both the length and the width of the aperture and the force with which the liquid is expelled through the aperture along with the viscosity and surface tension of the liquid.
  • the liquid is in this embodiment water.
  • FIG 2 schematically shows a pump according to an embodiment.
  • rotor 10 is mounted to rotate within stator 20.
  • Rotor 10 has a slit 12 through which water is expelled forming blade 40 such as is shown in Figure 1 .
  • the blade pushes gas around through the pumping channel 38 within stator 20 from an inlet 52 to an outlet 54.
  • inlet 52 is slightly higher than the base of outlet 54 which allows liquid from the liquid blade that collects within the pumping channel 38 during the pumping of the gas, to flow from inlet 52 to outlet 54 where it is exhausted.
  • rotor 10 is a hollow cylinder and the centrifugal force caused by rotation of the rotor causes liquid to rise up from a sump and be expelled through liquid slit 12.
  • the cross-sectional area of inlet 52 is smaller than the cross-sectional area of outlet 54 in this embodiment and this increase in cross sectional area from inlet to outlet helps compensate for the decrease in available volume for any fluid or gas being pumped that occurs due to the accumulation of the liquid from the liquid blade within the pumping channel 38.
  • the side walls of the pumping channel 38 are sloped such that the cross section of the pumping channel tapers in a corresponding way to the liquid blade of Figure 1 . This avoids or at least inhibits gaps being formed between the side walls and the liquid blade towards the outer edges of the pumping channel, further from the rotor, where the tapering is most pronounced.
  • Figure 3 shows a cross-sectional view of pumping channel 38 where the form of this channel can be seen more clearly.
  • the side walls 34 are sloped at an angle of 25° when taken from a tangent at the midpoint 34b of the side walls.
  • the side walls towards the rotor 34a have a more pronounced taper, such that they flare outwards in a curved manner and are further apart than they are towards the middle of the walls.
  • the ends of the side walls 34c towards the further wall 36 are curved so that there are no sharp angles as the side walls curve round to form the further wall and disruptions in the flow are reduced.
  • the side walls are those that extend substantially radially, while the further wall faces the rotor and runs substantially axially, parallel to the axis of rotation.
  • the top and bottom edges of the blade taper inwards towards the centre of the blade as it travels out from the rotor towards the further wall 36.
  • This tapering is matched and compensated for by appropriately sloping the upper and lower side walls 34 of the stator that along with further wall 36 form the pumping channel 38.
  • This tapering is designed to substantially match the tapering of the water sheet with slightly more taper to avoid or at least reduce any gaps.
  • the slit 12 is longer than the width of channel 38 closer to the inlet, as the channel has a smaller axial dimension here, sealing means 32 are provided between the stator and rotor on either side of the pumping channel, to avoid or at least inhibit liquid leakage from the pumping channel.
  • the lower side wall slopes vertically downwards from the inlet to the outlet, such that liquid accumulating in the pumping channel 38 drains at the outlet.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une pompe pour pomper un gaz, la pompe comprenant : un rotor et un stator ; le rotor comportant au moins une ouverture de liquide conçue pour une communication fluidique avec une source de liquide. L'ouverture de liquide est conçue de telle sorte que, en réponse à une force d'entraînement, un flux de liquide soit délivré à partir de l'ouverture. Le flux de liquide forme une lame de liquide entre le rotor et le stator, un gaz étant confiné par le stator, le rotor et la lame de liquide étant entraînés à travers la pompe le long d'un canal de pompage, d'une entrée de gaz vers une sortie de gaz en réponse à un mouvement de rotation réciproque du rotor et du stator. La pompe est conçue de telle sorte que le canal de pompage comprenne des parois latérales qui s'inclinent l'une vers l'autre à partir du rotor qui comprend l'ouverture de liquide vers une autre paroi du canal de pompage à distance du rotor, de telle sorte qu'une distance entre les parois latérales diminue tandis que la distance augmente par rapport à l'ouverture de liquide, une tangente à un point médian des parois latérales ayant un angle compris entre 5º et 40º par rapport à une ligne perpendiculaire à un axe de rotation du rotor.
EP21755039.1A 2020-08-11 2021-08-05 Pompe à lame de liquide Withdrawn EP4196683A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB2012474.9A GB2597951A (en) 2020-08-11 2020-08-11 Liquid blade pump
PCT/GB2021/052024 WO2022034291A1 (fr) 2020-08-11 2021-08-05 Pompe à lame de liquide

Publications (1)

Publication Number Publication Date
EP4196683A1 true EP4196683A1 (fr) 2023-06-21

Family

ID=72520064

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21755039.1A Withdrawn EP4196683A1 (fr) 2020-08-11 2021-08-05 Pompe à lame de liquide

Country Status (8)

Country Link
US (1) US20230279875A1 (fr)
EP (1) EP4196683A1 (fr)
JP (1) JP2023537076A (fr)
KR (1) KR20230047388A (fr)
CN (1) CN116057277A (fr)
GB (1) GB2597951A (fr)
TW (1) TW202219388A (fr)
WO (1) WO2022034291A1 (fr)

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FR1200145A (fr) * 1958-01-09 1959-12-18 Bertin & Cie Perfectionnements aux appareils à jet pour l'entraînement d'un fluide ou la compression d'un fluide gazeux
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TW202219388A (zh) 2022-05-16
WO2022034291A1 (fr) 2022-02-17
CN116057277A (zh) 2023-05-02
JP2023537076A (ja) 2023-08-30
US20230279875A1 (en) 2023-09-07
GB2597951A (en) 2022-02-16
KR20230047388A (ko) 2023-04-07
GB202012474D0 (en) 2020-09-23

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