WO2019043044A1 - Pompe à anneau liquide - Google Patents

Pompe à anneau liquide Download PDF

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Publication number
WO2019043044A1
WO2019043044A1 PCT/EP2018/073206 EP2018073206W WO2019043044A1 WO 2019043044 A1 WO2019043044 A1 WO 2019043044A1 EP 2018073206 W EP2018073206 W EP 2018073206W WO 2019043044 A1 WO2019043044 A1 WO 2019043044A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
chamber
impeller
liquid
liquid ring
Prior art date
Application number
PCT/EP2018/073206
Other languages
German (de)
English (en)
Inventor
Bernhard Herrmann
Eberhard Schlücker
Original Assignee
Friedrich-Alexander-Universität Erlangen-Nürnberg
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 Friedrich-Alexander-Universität Erlangen-Nürnberg filed Critical Friedrich-Alexander-Universität Erlangen-Nürnberg
Priority to EP18772737.5A priority Critical patent/EP3676496B1/fr
Publication of WO2019043044A1 publication Critical patent/WO2019043044A1/fr

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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
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • 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
    • F04C19/005—Details concerning the admission or discharge
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the invention relates to a liquid ring pump, which serves for example for the promotion of gases or the generation of a vacuum.
  • Liquid ring pumps usually serve to convey gaseous media and usually comprise an approximately circular-cylindrical pump housing in which an impeller is rotatably arranged eccentrically.
  • the pump wheel is usually a fan wheel, which is approximately star-shaped in cross-section.
  • a pump liquid (also referred to as “ring liquid”) is also circulated in the pump housing, which is circulated by rotation of the pump wheel in the circumferential direction of the impeller within the pump housing and forms a liquid ring along the inner circumference of the pump housing with sufficient rotational speed of the impeller due to centrifugal force
  • the eccentricity of the impeller immerses the individual blades at different depths into the annular liquid, specifically the liquid ring.
  • the gas standing between the individual blades during operation of the liquid ring pump therefore becomes smaller during rotation of the impeller due to the ever deeper immersion of the blades compresses and / or displaces the liquid ring in the spaces between the vanes.
  • This compression or displacement effect is utilized by suitable design of the pump housing to pass the gas through to promote an associated housing opening from the respective space.
  • the impeller is sealed against the pump housing by means of the pump liquid and thus little or nogearedg qualifyingden components are present, sparking can effectively prevent the operation of the liquid ring pump and thus also explosive gases are relatively reliably promoted.
  • the pump liquid also serves as a cooling medium and absorbs in particular the heat energy resulting from the compression of the gases. Again, this is advantageous in the promotion of heat-sensitive gases.
  • a disadvantage of liquid ring pumps is that the vapor pressure (value) of the ring liquid limits the achievable suction pressure (specifically its value).
  • it is due in particular to dynamic flow processes in the pump housing, in particular due to shock pressure relief, inter alia, to form a liquid-gas mixture which is conveyed from the respective space, which also contributes to limiting the achievable suction pressure, and depending on the pressure difference to deflagration from the respective space out or in the respective space inside.
  • the achievable suction pressure (value) is therefore about 30 mbar.
  • the deflagrations also lead to a relatively strong noise, which makes an operation of the liquid ring pumps, especially in laboratories unattractive.
  • the invention has for its object to provide an improved liquid ring pump.
  • the liquid ring pump comprises a pump housing surrounding a pump housing, wherein in the pump chamber in the intended operating condition, a pump liquid, hereinafter also referred to as ring liquid, is filled. Furthermore, the liquid ring pump comprises a pump wheel, which is arranged within the pump chamber and a Rotary axis is rotatable.
  • the impeller serves to promote a gaseous working medium.
  • the impeller has at its outer periphery a number of at least circumferentially separated feed chambers.
  • the delivery chambers are separated from each other in particular by radially extending from the axis of rotation or in the circumferential direction inclined partitions.
  • the pump wheel also has a respective outlet opening assigned to each delivery chamber and locally introduced into a bottom wall of the impeller radially inwardly bounding the fluid chamber for connecting the respective delivery chamber to a pressure region (also: “high pressure region”) of the pump chamber each delivery chamber along the axis of rotation (ie seen in the axial direction) inclined at both sides to the outlet opening at least in sections to the axis of rotation (and preferably also to the radial direction) and extends (from both sides) in the direction of the outlet opening arranged, which has the smallest radial distance from the axis of rotation.
  • a pressure region also: "high pressure region”
  • the term "local” is understood here and below to mean in particular that the outlet opening is small in comparison to the planar extent (for example along the axial direction) of the bottom wall and thus also of the delivery chamber, in other words the term “local” describes that in particular, the outlet opening does not extend over the entire area along the axial direction of the respective delivery chamber.
  • the outlet opening is also arranged centrally in the bottom wall of the delivery chamber viewed in the axial direction.
  • inclined is understood here and below as meaning, in particular, that the bottom wall (at least in sections) is inclined at an angle to the axis of rotation. represents or - seen in a section along the axis of rotation - has a curved course (and thus is employed locally obliquely).
  • the outlet opening according to the invention is thus arranged in the respective delivery chamber, that - with rotation of the impeller, which is positioned eccentrically to the pump housing, and thus with increasing immersion of the corresponding delivery chamber in the ring liquid, in particular in a liquid ring formed by the liquid ring - first to promoting working medium (in particular a gas) and then a preferably small, in particular adjustable amount of ring liquid enters the outlet opening.
  • working medium in particular a gas
  • suction pressures can be achieved which approach particularly close to the value range of the respective vapor pressure of the annular fluid.
  • the impeller is arranged eccentrically in the pump chamber (and this preferably also filled with annular fluid), that in the normal operation by the pump liquid forming liquid ring in particular in the pressure range the pump chamber completely covers at least one of the delivery chambers (in particular the "last" or also the working medium) in the radial direction (inside), ie the pump wheel dives so deeply into the liquid ring in the region of this delivery chamber (ie in the pressure region)
  • the bottom wall of this delivery chamber is likewise immersed in the liquid ring, whereby the respective outlet opening is also preferably at least partially below the "level" of the liquid ring.
  • the respective outlet opening is arranged and designed such that (in combination with the above-described selected eccentricity and the level of the ring liquid) in normal operation after ejection of the working medium also an at least minor portion of the annular liquid flowing through the feed chamber is also ejected ,
  • a "complete" promotion of the working medium from the respective delivery chamber is made possible in a simple manner.
  • each delivery chamber is formed symmetrically to a radial plane of the impeller, which in this case represents a mirror surface at least in sections.
  • the outlet opening is advantageously arranged in the mirror surface, at least touching this mirror surface.
  • the inclined bottom wall along the axis of rotation is substantially (i.e., exactly or approximately) U- or V-shaped.
  • the outlet opening is arranged in particular at the lowest point of the U or the V's.
  • the bottom wall thus extends on both sides to the mirror surface curved (in the case of the U's) or straight obliquely ("funnel-like", in the case of the V's) to the outlet opening.
  • each delivery chamber is delimited on the front side (that is to say in the axial direction) by at least one side wall (also referred to as front or end wall), preferably by one side wall each.
  • the or the respective side wall preferably connects to the bottom wall.
  • the individual delivery chambers are delimited from one another by the intermediate walls described above.
  • the side walls preferably extend in the radial direction.
  • the side walls serve to delimit the respective delivery chamber relative to the pump chamber.
  • both side walls or at least one of the two side walls are formed integrally (i.e., monolithically) from a pump wheel body forming at least the bottom wall of the delivery chambers.
  • the other side wall or alternatively also both side walls are optionally designed as "side shields" or “cover plates” and placed on the impeller body.
  • the impeller for each delivery chamber in each case a locally in one of the conveying chamber limiting walls, in particular in the bottom wall or the side wall or one of the side walls introduced inflow opening for the fluidic connection of the respective delivery chamber with a suction (or "low pressure area"
  • this delivery chamber in particular this inflow, for example, covered by the annular fluid, so that an outflow of the working medium from the corresponding delivery chamber is prevented by just this inflow.
  • the working medium to be conveyed via the preferably on the (outer) circumference of the impeller open delivery chamber in this flow.
  • the working medium to be pumped can also flow into the respective delivery chamber even without a specifically formed inflow opening even in the absence of one or both side walls and / or a correspondingly shortened radial extent of at least one of the side walls.
  • a check valve preferably defining the delivery chamber (in particular on the outlet side) is arranged within the respective outlet opening. This check valve is in the discharge direction from the respective delivery chamber opening and executed against the outlet direction sealing.
  • the non-return valve (also referred to as "outlet valve") arranged in the outlet opening is also configured to open only within a predetermined value of a delivery pressure (or compression pressure) within the delivery chamber
  • a check valve can be used to avoid or at least significantly reduce the effect of purging out of the delivery chamber or back into it, thereby advantageously reducing the noise of the liquid ring pump during operation high efficiency of the liquid ring pump in operation (for example, when using the liquid ring pump to promote the working fluid in a standing under a relative to atmospheric pressure pressure chamber space), that is in the ever the usual exit outlet valve designed for the lowest possible pressure loss (value).
  • the outlet valve preferably also has a high sealing effect.
  • the respective outlet valve is mounted in the impeller such that its closing function in the operation of the liquid ring pump by the (due to the rotation of the impeller) occurring centrifugal force causes, but at least supported.
  • valve springs or similar means for closing the respective outlet valve are optionally omitted in this case.
  • the respective inflow valve is designed to increase the efficiency advantageously to the lowest possible pressure loss (value).
  • the respective inflow valve is mounted in the impeller such that its function is assisted by the centrifugal force.
  • the respective inflow valve is in this case installed so that an opening of the inflow valve in the inflow direction is supported by the centrifugal force.
  • the inflow valves and optionally also the outlet valves are preferably designed as diaphragm valves.
  • the inflow valves and / or the outlet valves are formed by flaps, pressure-controlled valves (for example valves produced by a pressure method) or the like.
  • the outlet openings of the delivery chambers open into a (preferably common) outlet chamber arranged on the impeller (in particular on the outlet side).
  • This outlet chamber is preferably formed for the centrifugal force-related separation of the working fluid from the annular fluid.
  • the outlet chamber has an outer wall running parallel or preferably obliquely to the axis of rotation, and thus in the latter case has approximately a hollow conical shape, which rotates as intended Due to the centrifugal effect, the annular liquid can deposit on the outer wall and flow along it, in particular its oblique course
  • the or the respective outlet chamber can also be dispensed with.
  • the reservoir described above also has a cooling device, by means of which the separated ring liquid is cooled in the normal operation before returning to the liquid ring.
  • means for assisting the separation of the working fluid from the annular fluid are arranged in the outlet chamber. These means are, for example, guide vanes or, in particular, radially aligned guide disks, which, for example, promote the centrifugal force-dependent separation by means of targeted steering, in particular of the annular fluid.
  • one of the liquid ring pump (on the pressure side) downstream device for separating the working fluid from the annular fluid omitted or at least simplified.
  • the above-described outer wall of the discharge chamber and an optional discharge device for removing the deposited annular liquid discharge device is arranged such that the ring liquid is guided in operation via a gap between the impeller and the pump housing and thereby as a gas barrier Sealing the gap causes.
  • the liquid ring pump comprises a control ring, which is rotatable relative to the impeller and, in normal operation, is preferably arranged stationarily in relation to the impeller.
  • This control ring closes a large number of the outlet openings of the pump impeller on the output side in sections against the impeller.
  • at least one of the outlet openings namely preferably the ejecting outlet opening or additionally also a number of the outlet openings trailing in the direction of rotation of the impeller-opens to the outlet of the working medium.
  • the control ring can be adjusted so that it releases a different number of outlet openings.
  • the liquid ring pump in this case, an adjusting device for adjusting this control ring.
  • the control ring for adjusting the approved number of outlet openings comprises two mutually rotatable and superposed sub-rings with holes that form a (by turning the sub-rings against each other) size-adjustable passage opening.
  • the (in particular bore borne) control ring (or even ring sectors thereof) can also be moved radially or axially, to release a different number of outlet openings.
  • the control ring also has different sized holes.
  • the liquid ring pump in addition to this control ring means for throttling the suction flow.
  • a throttle in particular a throttle valve arranged to reduce the present in the suction region of the pump chamber pressure value.
  • a polyalpha-olefin is used as ring liquid.
  • a poly-alpha-olefin advantageously has a significantly lower vapor pressure value than water (in particular by a multiple, for example at least ten times), so that suction pressure values are also made possible in the range below 1 mbar.
  • the poly-alpha-olefin may also act lubricating and / or contribute to sealing gaps between components due to its comparatively high viscosity.
  • FIG. 1 in a schematic representation of a liquid ring pump
  • FIG. 4 in view of FIG. 1, a further embodiment of the liquid ring pump, and
  • FIG. 5 to 7 in view of FIG. 2 each in turn an alternative embodiment of the impeller.
  • a liquid ring pump 1 is shown schematically.
  • the liquid ring pump 1 comprises a pump housing 2 (shown schematically as a hollow cylinder) which encloses an interior designated as a pump chamber 3.
  • the liquid ring pump 1 further comprises an impeller 4, which is arranged rotatable about an axis of rotation 6 within the pump chamber 3.
  • the impeller 4 is arranged with its axis of rotation 6 eccentrically to the pump housing 2.
  • the impeller 4 serves to convey a gaseous working medium, specifically a gas.
  • the impeller 4 on its outer circumference a number of circumferentially separated from each other delivery chambers 8.
  • the delivery chambers 8 are separated from each other in the circumferential direction by intermediate walls 10.
  • Each delivery chamber 8 also has an outlet opening 12, which is arranged at a location of the respective delivery chamber 8 at the smallest radial distance from the axis of rotation 6.
  • a pump liquid designated as ring liquid 14 is filled in the pump chamber 3.
  • the annular fluid 14 is also set in rotation along the inner wall of the pump housing 2 and forms there due to the centrifugal force in Fig. 1 schematically indicated liquid ring 18 from , Due to the eccentricity of the axis of rotation 6 relative to the pump housing 2, the impeller 4 and thus also the individual delivery chambers 12 dive along the direction of rotation 16 at different depths into the liquid ring 18.
  • the liquid ring 18 seals the delivery chambers 8 which are open on the outer circumference of the impeller 4 (see partial section II-II in FIG. 2) and pushes the gas located in the pump chamber 3 and the respective delivery chamber 8 into the immersion depth of the impeller 6 Liquid ring 18 in the direction of the respective outlet opening 12 in front of him.
  • the pump wheel 4 is now only slightly immersed in the liquid ring 18 (in FIG. 1 the position at about 1 o'clock) via a feed opening (not shown in more detail) the gas into the pump chamber 3 initiated.
  • This area is also referred to as the suction area 20 of the pump chamber 3.
  • the gas enters the respective, at this time in the suction region 20 arranged delivery chamber 8 and is upon rotation of the impeller 4 by the in the respective delivery chamber 8 "rising" liquid level of the ring liquid 14 - due to the progressive immersion of the impeller. 4 the annular liquid 14 flows into the respective delivery chamber 8 in the radial direction in the direction of the outlet opening 12.
  • the liquid ring pump 1 is designed in such a way that the outlet openings 12 of the impeller 4 exit first Only in a pressure region 22 which is substantially diametrically opposed to the suction region 20 and in which the liquid level of the liquid ring 18 reaches as far as a bottom wall 24 delimiting the respective delivery chamber 8 radially inside (in the region of approximately 5:00 o'clock in FIG. or this so-called ar radially in 2), the respective outlet opening 12 is open and the compressed gas can flow out of the respective delivery chamber 8 and out of the pump housing 2 via a corresponding gas guide line (not shown in more detail)
  • a corresponding gas guide line not shown in more detail
  • the pump impeller 4 comprises two side walls 26, which are integrally (ie monolithically) formed from a pump wheel body 28 forming the impeller 4 in the illustrated embodiment. Radially inside the side walls 26 go into the bottom wall 24, which is U-shaped. Ie. the bottom wall 24 extends arcuately curved along the axis of rotation 6 from two sides in the direction of the "geodetically deepest point" (ie the point with the smallest radial distance to the axis of rotation 6) of the delivery chamber 8.
  • the respective delivery chamber 8 is symmetrical with respect to a mirror surface 30, which is formed by a plane standing radially to the axis of rotation 6.
  • the outlet opening 12 is formed in the illustrated embodiment as a right angle angled bore and thus represents a channel which initially leads in the radial direction from the respective delivery chamber 8 and then parallel to the rotation axis 6 on an end face 32 of the impeller takeout
  • an inflow opening 36 is introduced into the side wall 26 there, which allows the gas to flow into the delivery chamber 8 in the suction area 20.
  • This inflow opening 36 is particularly useful when the liquid level of the annular fluid 14 is selected such that the impeller 4 is immersed with its outer periphery constantly in the liquid ring 18. Due to the shape of the bottom wall 24 shown in FIG. 2, an approximately linear increase in speed of the annular fluid 14 flowing into the delivery chamber 8 is made possible. Due to the curved or tilted against the rotation axis 6 employed bottom wall 24 also a sudden impact of the ring liquid 14 is prevented on the bottom wall 24 and a concomitant foam (ie mixture) and noise. The fact that the outlet opening 12 is arranged at the lowest point of the delivery chamber 8, also allows the annular liquid 14 pushes the gas in front of him and in the pressure region 22 of the pump chamber 3, the gas can first flow out through the outlet opening 12.
  • the filling amount of the annular fluid 14 and the eccentricity of the axis of rotation 6 in the pump housing 2 selected such that the liquid level of the liquid ring 18 in the pressure region 22, the outlet opening 12 completely covers.
  • This makes it possible that the standing in the delivery chamber 8 and the outlet opening 12 gas completely expelled through the annular fluid 14 and even a portion of the annular fluid 14 are also conveyed from the delivery chamber 8.
  • the measures described above make it possible to deliver the gas to negligible proportions from the respective delivery chamber 8, so that a suction pressure value in the region of the vapor pressure of the annular liquid can be achieved.
  • FIG. 3 an alternative embodiment of the impeller 4 is shown.
  • the side walls 26 are in this case formed by plates or shields placed on both sides of the impeller body 28 (and thus produced separately therefrom).
  • the bottom wall 24 is formed V-like and thus has two rectilinear obliquely to the axis of rotation 6 extending portions (ie each side of the mirror surface in each case a section).
  • the bottom wall 24 runs in the manner of a funnel toward the outlet opening 12 in the section according to FIG.
  • the outlet opening 12, specifically its leading from the pump body 28 channel section also obliquely to the rotation axis 6 employed. This makes it possible that even within the outlet opening 12, the annular fluid 14 always pushes the gas in front of him. The risk of (turbulent) mixing of the ring liquid 14 with the gas is thus further reduced.
  • the side walls 26 may also be omitted, especially if the "V" of the bottom wall 24 is pulled laterally higher.
  • control ring 40 for releasing the outlet openings 12 in the pressure region 22 is used.
  • the control ring 40 covers with its annular body the outlet openings 12 on the output side against the impeller 4 from.
  • the control ring 40 has an annular gap 42, within which the outlet openings 12 are not covered.
  • the control ring 40 can be rotated relative to the impeller 4 about the axis of rotation 6. The more of the outlet openings 12 are open in the pressure region 22, the lower the pressure difference.
  • Fig. 5 is an alternative to Fig. 4 embodiment of the liquid ring pump 1, specifically the impeller 4, is shown.
  • a check valve hereinafter referred to as exit valve 50, is provided in the respective discharge opening 12 of each delivery chamber 8 arranged.
  • the control ring 40 shown in Fig. 4 can thus be omitted.
  • the outlet valve 50 is advantageously prevented that already ejected gas from the pressure region 22 with further rotation of the impeller 4 and thus decreasing liquid level of the annular fluid 14 flows back into the already discharged delivery chamber 8 or even fumes back into this delivery chamber 8.
  • each delivery chamber behaves in isolation like an oscillating positive displacement pump (the liquid ring 18 locally forms a liquid piston).
  • the respective outlet valve 50 is configured to open when the delivery pressure value present in the delivery chamber is sufficiently high, for example, coincides with the pressure value required on the output side for the liquid ring pump 1.
  • the outlet opening 12 leads via the outlet valve 50 into a discharge chamber 54 that is arranged on the impeller body 28 and specifically formed in it.
  • This outlet chamber 54 is geometrically designed such that a centrifugal force-dependent separation of the gas from the annular liquid 14 is made possible.
  • the outlet chamber 54 has at least one obliquely inclined to the axis of rotation 6 chamber surface 56.
  • the chamber liquid 56 is separated from the gas by the ring liquid 14 precipitating on this chamber surface 56 and flowing along it to the (front) side 32 of the impeller 4 ,
  • a liquid discharge in the form of a (optionally integrated into the gas guide line) arranged via the discharged during the operation of the gas ring fluid 14 fed to a cooling device and then fed back into the pump chamber 3 becomes.
  • the chamber surface 56 extends parallel to the axis of rotation 6 and thus represents a circular cylinder inner surface.
  • additional means for supporting the gas-liquid separation are arranged in the outlet chamber 54. These are guide vanes which support the centrifugal force-related separation of the ring liquid 14.
  • the inflow opening 36 is also formed in the bottom wall 24 of the delivery chamber 8 in the embodiment shown in FIG.
  • a non-return valve (hereinafter referred to as inflow valve 58) is arranged in the inflow opening 36, which serves for a backflow and thus also a deflagration of the gas from the feed line.
  • Chamber 8 in the suction area 20 prevents.
  • the inflow valves 58 and the outflow valves 50 are each formed as diaphragm valves. Due to the above-described arrangement in the bottom wall 24, the sealing or closing action of the outlet valves 50 is assisted by the centrifugal force. Accordingly, in this arrangement, the opening of the inflow valves 58 is also assisted by the centrifugal force.
  • a guide plate 60 is arranged, which supports the centrifugal force-induced deposition of the annular liquid 14.
  • the guide plate 60 is rotatably coupled to the pump body 28.
  • the outlet opening 12 (in particular the channel formed by this) and / or the outlet valve 50 are aligned such that the outflowing gas and the inflowing annular fluid 14 impinge on the co-rotating with the impeller 4 Leitusion 60.
  • annular fluid 14 Radially inside passages 62 for the gas are arranged in the guide disk 60 (distributed over the circumference thereof). Due to the centrifugal force caused by the rotation of the guide disk 60, the annular liquid 14 runs radially outward on the guide disk 60. Subsequently, the ring liquid 14 runs on the (conically widening and rotating) chamber surface 56 to the side 32 out. Through a gap 64, which is sufficiently small to prevent an at least excessive inflow of the annular fluid 14 into the gap 64, the annular fluid 14 flows to the stationary region of the liquid ring pump 1, specifically to the pump housing 2. In the pump housing 2, an annular channel 66 is formed, which is designed as a kind of drainage channel for the annular liquid 14, which runs from the chamber surface 56 to the pump housing 2.
  • a drain is formed in the annular channel 66, which represents the liquid discharge described above.
  • the process is designed such that a passage of gas is prevented.
  • the process is designed in the manner of a siphon or has such a small diameter that always a residual liquid level of the ring liquid 14 is present at the outlet and thus closes it against the passage of gas.
  • Pump chamber (3) surrounds, in which a pump liquid (14) is filled in the normal operating condition, and with a within the pump chamber (3) arranged and about a rotation axis (6) rotatable impeller (4) for conveying a gaseous working medium,
  • impeller (4) has on its outer circumference a number of at least circumferentially separated from each other conveying chambers (8),
  • each delivery chamber (8) associated and locally in a respective delivery chamber (8) radially inwardly bounding bottom wall (24) of the impeller (4) inserted has an outlet opening (12) for the fluidic connection of the respective delivery chamber (8) to a pressure region (20) of the pump chamber (3)
  • the respective outlet opening (12) is arranged at a location of the respective delivery chamber (8) with the smallest radial distance from the axis of rotation (6).
  • impeller (4) is arranged eccentrically in the pump chamber (3) such that a liquid ring (18) of the pump liquid (14) forming in normal operation comprises at least one delivery chamber (8) in the pressure region (20) of the pump chamber (3) Radial direction completely covered.
  • each delivery chamber (8) is formed symmetrically to a radial plane of the impeller (4) forming a mirror surface (30), and wherein the outlet opening (12) is arranged in the mirror surface (30).
  • each of the conveying chamber (8) radially inwardly bounding bottom wall (24) along the axis of rotation (6) is substantially U- or V-shaped.
  • Digit E Liquid ring pump (1) according to one of the combinations of features according to A) to D), wherein the impeller (4) for each delivery chamber (8) each with a locally in the bottom wall (24) or the respective delivery chamber (8) frontally limiting side wall (26) introduced inflow opening (36) for fluidic connection of the respective delivery chamber (8) a suction region (20) of the pump chamber (3).
  • a check valve (50) is arranged inside the outlet opening (12).
  • a check valve (58) is arranged within the inflow opening (36) wherein within the inflow opening (36) a check valve (58) is arranged.
  • outlet chamber (54) means, in particular guide vanes or guide disks for supporting the separation of the working medium from the pump liquid (14) are arranged.

Abstract

L'invention concerne une pompe à anneau liquide (1) qui comporte un carter (2) de pompe qui entoure une chambre (3) de pompe dans laquelle un liquide de pompage (14) est rempli dans l'état de fonctionnement conforme à l'usage prévu. La pompe à anneau liquide (1) comporte par ailleurs une roue (4) de pompe disposée à l'intérieur de la chambre (3) de pompe et pouvant tourner autour d'un axe de rotation (6), servant à refouler un milieu de travail sous forme gazeuse. La roue (4) de pompe comporte ce faisant, sur sa périphérie extérieure, un nombre donné de chambres de refoulement (8) séparées les unes des autres au moins dans la direction périphérique. La roue (4) de pompe comporte par ailleurs respectivement une ouverture de sortie (12) associée à chaque chambre de refoulement (8) et pratiquée localement dans une paroi de fond (24), délimitant radialement côté intérieur la chambre de refoulement (8) respective, de la roue (4) de pompe aux fins de la communication fluidique de la chambre de refoulement (8) respective avec une zone de pression (20) de la chambre (3) de pompe. La paroi de fond (24) s'étend ce faisant le long de l'axe de rotation (6) de part et d'autre de l'ouverture de sortie (12) de manière inclinée au moins par endroits par rapport à l'axe de rotation (6) en direction de l'ouverture de sortie (12). L'ouverture de sortie (12) est disposée ce faisant sur un emplacement de la chambre de refoulement (8) respective selon la plus petite distance radiale par rapport à l'axe de rotation (6).
PCT/EP2018/073206 2017-08-29 2018-08-29 Pompe à anneau liquide WO2019043044A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18772737.5A EP3676496B1 (fr) 2017-08-29 2018-08-29 Pompe à anneau liquide

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017215080.7 2017-08-29
DE102017215080.7A DE102017215080A1 (de) 2017-08-29 2017-08-29 Flüssigkeitsringpumpe

Publications (1)

Publication Number Publication Date
WO2019043044A1 true WO2019043044A1 (fr) 2019-03-07

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ID=63637851

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PCT/EP2018/073206 WO2019043044A1 (fr) 2017-08-29 2018-08-29 Pompe à anneau liquide

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EP (1) EP3676496B1 (fr)
DE (1) DE102017215080A1 (fr)
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Citations (5)

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DE648731C (de) * 1935-02-08 1937-08-07 Voith Gmbh J M Umlaufender Verdichter mit Hilfsfluessigkeit
US2201575A (en) * 1938-03-04 1940-05-21 Ernest R Corneil Machine for transferring fluids
DE2309474A1 (de) * 1972-09-05 1974-03-14 Irving Jennings Fluessigkeitsringpumpe
EP0889242A1 (fr) * 1997-07-04 1999-01-07 GARO Dott.Ing.Roberto Gabbioneta S.p.A. Compresseur à anneau liquide
WO2003102423A1 (fr) * 2002-04-19 2003-12-11 Compressor Systems As Compresseur a anneau liquide

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DE890256C (de) * 1943-05-07 1953-09-17 Siemens Ag Fluessigkeitsring-Verdichter
DE1015691B (de) * 1955-02-05 1957-09-12 Siemens Ag Fluessigkeitsringpumpe mit umlaufendem Gehaeuse
GB1081898A (en) * 1963-08-29 1967-09-06 John Llewellyn Lewis Improved rotary pump
DE3207507C2 (de) * 1982-03-02 1984-12-20 Siemens AG, 1000 Berlin und 8000 München Flüssigkeitsringverdichter
US4521161A (en) * 1983-12-23 1985-06-04 The Nash Engineering Company Noise control for conically ported liquid ring pumps
DE20015709U1 (de) * 2000-09-11 2002-01-31 Speck Pumpenfabrik Walter Spec Flüssigkeitsringpumpe mit Nabensteuerung
KR20070053265A (ko) * 2004-09-17 2007-05-23 바스프 악티엔게젤샤프트 액체 고리 압축기의 작동 방법

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE648731C (de) * 1935-02-08 1937-08-07 Voith Gmbh J M Umlaufender Verdichter mit Hilfsfluessigkeit
US2201575A (en) * 1938-03-04 1940-05-21 Ernest R Corneil Machine for transferring fluids
DE2309474A1 (de) * 1972-09-05 1974-03-14 Irving Jennings Fluessigkeitsringpumpe
EP0889242A1 (fr) * 1997-07-04 1999-01-07 GARO Dott.Ing.Roberto Gabbioneta S.p.A. Compresseur à anneau liquide
WO2003102423A1 (fr) * 2002-04-19 2003-12-11 Compressor Systems As Compresseur a anneau liquide

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EP3676496B1 (fr) 2022-10-05
EP3676496A1 (fr) 2020-07-08
DE102017215080A1 (de) 2019-02-28

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