EP3676496B1 - Pompe à anneau liquide - Google Patents

Pompe à anneau liquide Download PDF

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Publication number
EP3676496B1
EP3676496B1 EP18772737.5A EP18772737A EP3676496B1 EP 3676496 B1 EP3676496 B1 EP 3676496B1 EP 18772737 A EP18772737 A EP 18772737A EP 3676496 B1 EP3676496 B1 EP 3676496B1
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EP
European Patent Office
Prior art keywords
pump
liquid
chamber
ring
outlet
Prior art date
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Application number
EP18772737.5A
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German (de)
English (en)
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EP3676496A1 (fr
Inventor
Bernhard Herrmann
Eberhard Schlücker
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Hydrogenious Technologies GmbH
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Hydrogenious LOHC Technologies GmbH
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Publication of EP3676496A1 publication Critical patent/EP3676496A1/fr
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    • 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 is used, for example, to convey gases or to generate a vacuum.
  • Liquid ring pumps are usually used to convey gaseous media and usually include an approximately circular-cylindrical pump housing in which a pump wheel is eccentrically rotatable.
  • the impeller is usually an impeller that is approximately star-shaped when viewed in cross section.
  • a pump liquid (also referred to as "ring liquid”) is also arranged in the pump housing. This is circulated by rotation of the pump wheel in the circumferential direction of the pump wheel within the pump housing and forms a liquid ring along the inner circumference of the pump housing due to centrifugal force when the pump wheel rotates at a sufficient speed. Due to the eccentricity of the impeller, the individual blades in the circumferential direction are immersed to different depths in the ring liquid, specifically the liquid ring.
  • the gas standing between the individual vanes during operation of the liquid ring pump is thus compressed and/or displaced from the interspaces between the guide vanes as the impeller rotates due to the ever deeper immersion of the vanes in the liquid ring.
  • This compression or displacement effect is used by a suitable design of the pump housing in order to convey the gas out of the respective intermediate space through an associated housing opening.
  • the impeller is sealed off from the pump housing by means of the pump liquid and therefore there are hardly any components that slide against one another are present, sparking during operation of the liquid ring pump can be effectively prevented and thus explosive gases can be conveyed comparatively safely.
  • the pump liquid also serves as a cooling medium and, in particular, absorbs the thermal energy that occurs during the compression of the gases. This, in turn, is advantageous when conveying 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).
  • the achievable suction pressure (value) is therefore around 30 mbar. The deflagration also leads to a comparatively high level of noise, which makes operation of the liquid ring pumps unattractive, particularly in laboratories.
  • the invention is based on the object of specifying an improved liquid ring pump.
  • the liquid ring pump comprises a pump housing surrounding a pump chamber, with a pump liquid, also referred to below as ring liquid, being filled into the pump chamber in the intended operating state.
  • the liquid ring pump includes an impeller, which is arranged within the pump chamber and around a Axis of rotation is rotatable.
  • the impeller serves to convey a gaseous working medium.
  • the impeller has on its outer circumference a number of pumping chambers that are separated from one another at least in the circumferential direction.
  • the conveying chambers are preferably separated from one another by partition walls that run radially to the axis of rotation or are inclined in the circumferential direction.
  • the impeller also has an outlet opening assigned to each delivery chamber and made locally in a bottom wall of the impeller that delimits the respective delivery chamber radially on the inside for fluidic connection of the respective delivery chamber to a pressure area (also: "high-pressure area") of the pump chamber.
  • the bottom wall in each delivery chamber is inclined along the axis of rotation (ie viewed in the axial direction) on both sides of the outlet opening, at least in sections to the axis of rotation (and preferably also to the radial direction) and runs (from both sides) in the direction of the outlet opening.
  • the outlet opening is in each case arranged at a point in the respective delivery chamber which has the smallest radial distance from the axis of rotation.
  • the term “local” is understood here and in the following in particular to mean that the outlet opening is small compared to the areal extension (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 the outlet opening does not extend over the entire surface of the respective delivery chamber running along the axial direction.
  • outlet opening is preferably arranged centrally in the bottom wall of the conveying chamber, viewed in the axial direction.
  • inclined is understood here and in the following in particular to mean that the bottom wall (at least in sections) is set at an angle to the axis of rotation or - viewed in a section along the axis of rotation - has a curved course (and is therefore locally inclined).
  • the outlet opening is therefore arranged in the respective pumping chamber in such a way that - when the impeller rotates, which is positioned eccentrically to the pump housing, and thus when the corresponding pumping chamber is increasingly immersed in the ring liquid, in particular in a liquid ring formed by the ring liquid - first the to conveying working medium (in particular a gas) and then a preferably small, in particular adjustable amount of ring liquid enters the outlet opening. It can thus advantageously be made possible for the working medium to be conveyed to be expelled as completely as possible from the respective conveying chamber by the following ring liquid.
  • the working medium in particular a gas
  • a streamlined chamber shape is made possible, which prevents or at least reduces a (wave-like) impact of the ring liquid on the bottom wall that contributes to the formation of the mixture (in particular to the formation of foam), and rather a directed flow in Supported towards the outlet opening.
  • the bottom wall tapering towards the outlet opening also ensures that the ring liquid "pushes" the working medium to be conveyed in front of it in the direction of the outlet opening and the risk of mixing of the ring liquid and the working medium is reduced.
  • suction pressures can be achieved which come particularly close to the value range of the respective vapor pressure of the ring liquid.
  • the impeller is arranged eccentrically in the pump chamber (and this is preferably also filled with ring liquid) such that a liquid ring formed by the pump liquid during normal operation, particularly in the pressure area the pump chamber completely covers at least one of the pumping chambers (in particular the "last" one or also the one ejecting the working medium) in the radial direction (on the inside).
  • the impeller in the region of this delivery chamber ie in the pressure region
  • the respective outlet opening is at least partially below the "level" of the liquid ring.
  • the respective outlet opening is preferably arranged and designed in such a way that (preferably in combination with the eccentricity selected above and the fill level of the ring liquid) in normal operation after the working medium has been ejected, at least a small proportion of the ring liquid flowing through the pumping chamber is also ejected . This enables the working medium to be conveyed “completely” out of the respective conveying chamber in a simple manner.
  • each delivery chamber is formed symmetrically to a radial plane of the impeller, which in this case at least partially represents a mirror surface.
  • the exit opening is advantageously arranged in the mirror surface, touching at least this mirror surface.
  • the ring liquid can flow in the direction of the outlet opening in a particularly orderly manner and while avoiding the formation of mixtures as completely as possible.
  • the outlet opening is at the ("geodesically") lowest point - ie at the point with the smallest radial distance to the axis of rotation - the pumping chamber.
  • the inclined bottom wall along the axis of rotation is essentially (i.e. exactly or approximately) U-shaped or V-shaped.
  • the outlet opening is arranged in particular at the lowest point of the U or the V.
  • the bottom wall thus runs curved on both sides to the mirror surface (in the case of the U's) or in a straight line at an angle ("funnel-like"; in the case of the V's) towards the outlet opening.
  • each delivery chamber is delimited at the front (i.e. 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 in the circumferential direction by the partition walls described above.
  • the side walls preferably run in a radial direction.
  • the side walls serve to delimit the respective delivery chamber from the pump chamber.
  • both side walls or at least one of the two side walls are formed integrally (i.e. monolithically) from an impeller body forming at least the bottom wall of the pumping chambers.
  • the other side wall or alternatively both side walls are optionally designed as "side shields" or “cover plates” and placed on the impeller body.
  • the impeller has, for each delivery chamber, an inflow opening locally in one of the walls delimiting the delivery chamber, in particular in the bottom wall or the side wall or one of the side walls, for the fluidic connection of the respective delivery chamber with a suction area (or "low-pressure area") of the pump chamber . i.e. When the liquid ring pump is in operation, the working medium to be pumped flows through this inflow opening into the respective pumping chamber.
  • this delivery chamber in particular this inflow opening, is covered, for example, by the ring liquid, so that the working medium is prevented from flowing out of the corresponding delivery chamber through this very inflow opening.
  • the working medium to be conveyed can also flow into the impeller via the conveying chamber, which is preferably open on the (outer) circumference of the impeller.
  • the working medium to be conveyed can flow into the respective conveying chamber even if one or both side walls are missing and/or if at least one of the side walls has a correspondingly shortened radial extent, even without a specifically designed inflow opening.
  • a non-return valve which preferably limits the delivery chamber (in particular on the outlet side)
  • This check valve is designed to open in the exit direction from the respective delivery chamber and to seal against the exit direction.
  • the check valve arranged in the outlet opening (also referred to as "outlet valve") is also set up to only open above a predetermined value of a delivery pressure (or: compression pressure) within the delivery chamber. This makes it possible to specify (adjust) a pressure difference between the suction area and the pressure area in the pump chamber in a targeted manner.
  • such a non-return valve can prevent or at least significantly reduce deflagration effects out of the delivery chamber or back into it.
  • the noise generated by the liquid ring pump during operation can advantageously be reduced.
  • this is in the respective outlet opening
  • the built-in outlet valve is designed for the lowest possible pressure loss (value).
  • the outlet valve preferably also has a high sealing effect.
  • the respective outlet valve is preferably mounted in the impeller in such a way that its closing function is brought about, or at least supported, by the centrifugal force (occurring due to the rotation of the impeller) during operation of the liquid ring pump.
  • valve springs or comparable means for closing the respective outlet valve are optionally omitted.
  • a check valve which preferably delimits the delivery chamber (in particular on the inflow side) is arranged inside the inflow opening.
  • This is designed in such a way that a backflow of the working medium (and possibly also the ring liquid) from the delivery chamber into the suction area of the pump chamber is prevented.
  • the “loading” (ie the filling) of the delivery chamber with working medium can thus advantageously be controlled by means of this “inflow valve”.
  • a particularly precise control of the loading and unloading of the respective delivery chamber is possible, preferably purely as a function of the pressure.
  • the respective inflow valve is mounted in the impeller in such a way that its function is supported by the centrifugal force.
  • the respective inflow valve is here installed in such a way that opening of the inflow valve in the inflow direction is supported by 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 printing process) or the like.
  • the outlet openings of the pumping chambers open into a (preferably common) outlet chamber arranged on the impeller (in particular on the outlet side).
  • This outlet chamber is preferably designed for the centrifugal force-related separation of the working medium from the ring liquid.
  • the outlet chamber is set up for the separation ("separation") of gases and liquids.
  • the outlet chamber has an outer wall running parallel or preferably obliquely to the axis of rotation and thus in the latter case approximately a hollow conical shape.
  • this outer wall rotates with the impeller, so that due to the centrifugal effect, the ring liquid is deposited on the outer wall and can flow off along it, in particular along its sloping course.
  • the ring liquid separated off in this way is preferably (directly or indirectly via a reservoir) fed back to the liquid ring, so that it is at least not continuously reduced in size during normal operation.
  • the respective outlet chamber can also be omitted.
  • the reservoir described above also has a cooling device, by means of which the separated ring liquid is cooled before it is returned to the liquid ring during normal operation.
  • means for supporting the separation of the working medium from the ring liquid are arranged in the outlet chamber.
  • These means are, for example, guide vanes or, in particular, radially aligned guide disks, which promote the separation caused by centrifugal force, for example, by means of targeted guidance in particular of the ring liquid.
  • a device downstream of the liquid ring pump (on the pressure side) for separating the working medium from the ring liquid can be dispensed with or at least simplified.
  • the above-described outer wall of the outlet chamber and a drain device (or: “liquid drain”) optionally used to drain the separated ring liquid are arranged in such a way that the ring liquid is guided over a gap between the impeller and the pump housing during operation and thereby acts as a gas barrier Sealing of the gap causes.
  • the liquid ring pump comprises a control ring which can be rotated relative to the impeller and is preferably arranged in a stationary manner relative to the impeller during normal operation.
  • This control ring closes a large number of the outlet openings of the impeller in sections against the impeller on the output side.
  • at least one of the outlet openings namely preferably the ejecting outlet opening or additionally also a number of the outlet openings trailing behind the ejecting outlet opening in the direction of rotation of the impeller—is open for the outflow of the working medium.
  • the control ring can be adjusted so that it releases a different number of outlet openings.
  • the liquid ring pump comprises in this case also an adjusting device for adjusting this control ring.
  • the control ring for adjusting the released number of outlet openings comprises two partial rings that can be rotated in relation to one another and lie one above the other with bores that form a through-opening that can be adjusted in size (by rotating the partial rings in relation to one another).
  • the control ring (which in particular carries bores) (or only ring sectors thereof) can also be displaced radially or axially in order to release a different number of outlet openings.
  • the control ring also has bores of different sizes.
  • the liquid ring pump includes means for throttling the suction flow in addition to this control ring.
  • a throttle in particular a throttle valve, is arranged on the inlet side of the pump chamber to reduce the pressure value present in the suction area of the pump chamber.
  • the delivery pressure value that can be achieved in the delivery chamber in the pressure region of the pump chamber can also be set, in particular lowered, as a result of which deflagration effects from the respective delivery chamber can advantageously be reduced or avoided.
  • a poly-alpha-olefin is used as the ring liquid.
  • a poly-alpha-olefin advantageously has a vapor pressure value that is significantly lower (in particular by a multiple, for example at least ten times) compared to water, so that suction pressure values in the range below 1 mbar are also possible. It is thus advantageously possible to also use the liquid ring pump described above for the so-called fine vacuum range.
  • the poly-alpha-olefin can also have a lubricating effect and/or contribute to sealing gaps between components due to its comparatively high viscosity.
  • the liquid ring pump 1 comprises a pump housing 2 (represented schematically as a hollow cylinder) which encloses an interior space referred to as the pump chamber 3 .
  • the liquid ring pump 1 also includes a pump wheel 4 , which is arranged inside the pump chamber 3 such that it can rotate about an axis of rotation 6 .
  • the pump wheel 4 is arranged eccentrically to the pump housing 2 with its axis of rotation 6 .
  • the impeller 4 serves to convey a gaseous working medium, specifically a gas.
  • the impeller 4 has on its outer circumference a number of delivery chambers 8 which are separated from one another in the circumferential direction.
  • the delivery chambers 8 are separated from one another in the circumferential direction by intermediate walls 10 .
  • Each delivery chamber 8 also has an outlet opening 12 which is arranged at a point in the respective delivery chamber 8 which is at the smallest radial distance from the axis of rotation 6 .
  • a pump liquid called ring liquid 14 is filled into the pump chamber 3 .
  • the ring liquid 14 is also set in rotation along the inner wall of the pump housing 2 and forms there due to the centrifugal force an in 1 schematically indicated liquid ring 18 from. Due to the eccentricity of the axis of rotation 6 in relation to the pump housing 2 , the impeller 4 and thus also the individual delivery chambers 12 dip into the liquid ring 18 at different depths along the direction of rotation 16 .
  • the liquid ring 18 seals the delivery chambers 8 that are open on the outer circumference of the impeller 4 (cf. partial section II-II in 2 ) and pushes the gas in the pump chamber 3 and the respective pumping chamber 8 in front of it in the direction of the respective outlet opening 12 with increasing immersion depth of the impeller 6 in the liquid ring 18 .
  • the gas In order to convey the gas, in an area in which the impeller 4 only dips slightly into the liquid ring 18 (in 1 the position at about 11:00 a.m.) the gas is introduced into the pump chamber 3 via a supply opening (not shown in detail). This area is also referred to as the suction area 20 of the pump chamber 3 .
  • the gas enters the respective pumping chamber 8, which is located in the suction area 20 at this point in time, and when the pump wheel 4 rotates due to the "rising" liquid level of the ring liquid 14 in the respective pumping chamber 8 - due to the progressive immersion of the pump wheel 4 the ring liquid 14 flows into the liquid ring 18 in a radial direction into the respective delivery chamber 8 -- pressed 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 are initially closed on the outlet side. Only in a pressure area 22 that is essentially diametrically opposite the suction area 20 and in which the liquid level of the liquid ring 18 reaches up to a bottom wall 24 that delimits the respective delivery chamber 8 radially on the inside (in 1 in the range of about 5:00 a.m.) or even radially inside exceeds (or: “covers"; cf. 2 ), the respective outlet opening 12 is open and the compressed gas can flow out of the respective pumping chamber 8 and out of the pump housing 2 via a corresponding gas guide line, not shown in detail.
  • the outlet opening 12 thus serves to fluidically connect the respective delivery chamber 8 to the pressure area 22 of the pump chamber 3.
  • the impeller 4 comprises two side walls 26 for covering the respective pumping chamber 8 at the front (or: axial end) and which in the exemplary embodiment shown are formed in one piece (ie monolithically) from an impeller body 28 forming the impeller 4 .
  • the side walls 26 merge into the bottom wall 24, which is U-shaped. i.e. the bottom wall 24 runs in an arc along the axis of rotation 6 from two sides in the direction of the "geodetically lowest" point (ie the point with the smallest radial distance from the axis of rotation 6) of the pumping chamber 8.
  • the outlet opening 12 is arranged.
  • the respective pumping chamber 8 specifically its geometric structure symmetrical to a mirror surface 30, which is formed by a radial plane to the axis of rotation 6.
  • a uniform flow of the ring liquid 14 in the direction of the outlet opening 12 is thereby achieved.
  • the outlet opening 12 is designed as a right-angled bore and thus represents a channel that first leads in the radial direction out of the respective pumping chamber 8 and then out of the impeller 4 parallel to the axis of rotation 6 on an end face 32 .
  • an inflow opening 36 is made in 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 expedient when the liquid level of the ring liquid 14 is selected in such a way that the outer circumference of the impeller 4 is constantly immersed in the liquid ring 18 .
  • the illustrated shape of the bottom wall 24 enables an approximately linear increase in speed of the annular liquid 14 flowing into the conveying chamber 8 .
  • the arched or inclined bottom wall 24 positioned against the axis of rotation 6 also prevents the annular liquid 14 from hitting the bottom wall 24 abruptly and the development of foam (ie mixture) and noise associated therewith.
  • the fact that the outlet opening 12 is arranged at the lowest point of the pumping chamber 8 also makes it possible for the ring liquid 14 to push the gas in front of it and in the pressure region 22 of the pump chamber 3 the gas can initially flow out via the outlet opening 12 .
  • the filling quantity of the ring liquid 14 and the eccentricity of the axis of rotation 6 in the pump housing 2 are selected such that the liquid level of the liquid ring 18 in the pressure area 22 completely covers the outlet opening 12. This makes it possible for the gas standing in the conveying chamber 8 and the outlet opening 12 to be completely expelled through the ring liquid 14 and even for a portion of the ring liquid 14 to also be conveyed out of the conveying chamber 8 .
  • the measures described above make it possible to pump the gas out of the respective pumping chamber 8 to a negligible proportion, so that a suction pressure value in the range of the vapor pressure of the ring liquid can be achieved.
  • the side walls 26 are formed by plates or shields placed on both sides of the impeller body 28 (and thus produced separately from it).
  • the bottom wall 24 is V-shaped and thus has two straight sections running obliquely to the axis of rotation 6 (ie one section on each side of the mirror surface). Consequently, the bottom wall 24 runs in section according to FIG 2 viewed like a funnel towards the outlet opening 12 .
  • the outlet opening 12 specifically its channel section leading out of the impeller body 28 , is also set at an angle to the axis of rotation 6 . This makes it possible for the annular liquid 14 to always push the gas in front of it, even within the outlet opening 12 . The risk of (turbulent) mixing of the ring liquid 14 with the gas is thus further reduced.
  • the side walls 26 can also be omitted, in particular if the "V" of the bottom wall 24 is raised laterally.
  • a control ring 40 serves to release the outlet openings 12 into the pressure area 22 .
  • the ring body of the control ring 40 covers the outlet openings 12 on the outlet side against the impeller 4 .
  • 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 about the axis of rotation 6 with respect to the pump wheel 4 . The more the outlet openings 12 are open in the pressure area 22, the lower the pressure difference.
  • FIG 5 is a to 4 alternative embodiment of the liquid ring pump 1, specifically the impeller 4, shown.
  • the outlet valve 50 To control the pressure ratio between the suction area 20 and the pressure area 22 and for the targeted discharge of the gas in the delivery chamber 8 and compressed by the rising ring liquid 14, there is a check valve in the respective outlet opening 12 of each delivery chamber 8, referred to below as the outlet valve 50 , arranged. the inside 4 illustrated control ring 40 can thus be omitted.
  • the outlet valve 50 advantageously also prevents gas that has already been expelled from the pressure area 22 from flowing back into the already discharged delivery chamber 8 or even deflagrating back into this delivery chamber 8 as the impeller 4 rotates further and the liquid level of the ring liquid 14 decreases.
  • each pumping chamber behaves in isolation like an oscillating positive displacement pump (where the liquid ring 18 locally forms a liquid piston).
  • the respective outlet valve 50 is set up in such a way that it opens when the delivery pressure value present in the delivery chamber is sufficiently high, for example corresponds to the pressure value required on the output side of the liquid ring pump 1 .
  • the outlet opening 12 leads via the outlet valve 50 into an outlet chamber 54 which is arranged on the impeller body 28 and is specifically formed therein.
  • the outlet chamber 54 has at least one chamber surface 56 inclined to the axis of rotation 6 . Due to the centrifugal force acting on the ring liquid 14, the ring liquid 14 that is also ejected is separated from the gas at this chamber surface 56, in that the ring liquid 14 is deposited on this chamber surface 56 and flows along it to the (front) side 32 of the impeller 4.
  • the gas supply line which is not shown in detail
  • a liquid discharge line in the form of a pipeline (optionally integrated in the gas supply line) on this side 32, via which the ring liquid 14 separated from the gas is discharged during operation, fed to a cooling device and then returned to the pump chamber 3 becomes.
  • the chamber surface 56 runs parallel to the axis of rotation 6 and thus represents an inner surface of a circular cylinder.
  • means for supporting the gas-liquid separation are additionally arranged in the outlet chamber 54 . These are guide vanes that 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 pumping chamber 8.
  • inflow valve 58 a non-return valve which prevents the gas from flowing back and thus also deflagrating from the delivery chamber 8 in the suction area 20 prevents.
  • the use of the inflow valve 58 and the outlet valve 50 enables particularly precise control of the loading and unloading of the pumping chamber 8 with the gas to be pumped.
  • the development of noise as a result of dynamic pressure relief in or out of the respective delivery chamber and any associated foaming between the gas and the ring liquid 14 are effectively prevented.
  • the inflow valves 58 and the outlet valves 50 are each designed as membrane valves. Due to the arrangement in the bottom wall 24 described above, the sealing or closing effect of the outlet valves 50 is supported by the centrifugal force. Correspondingly, in this arrangement, the opening of the inflow valves 58 is also assisted by the centrifugal force.
  • a guide disk 60 is arranged in the (common) outlet chamber 54, which supports the centrifugal force-induced separation of the annular liquid 14.
  • the guide disk 60 is coupled to the pump base body 28 in a torque-proof manner.
  • the outlet opening 12 (in particular the channel formed by it) and/or the outlet valve 50 are aligned in such a way that the outflowing gas and the following annular liquid 14 impinge on the guide disk 60 rotating with the impeller 4 .
  • Passage openings 62 for the gas are arranged radially on the inside in guide disk 60 (distributed over its circumference). Due to the centrifugal force caused by the rotation of the guide disk 60 , the annular liquid 14 runs off radially outwards on the guide disk 60 . The ring liquid 14 then runs off to the side 32 on the (conically widening and rotating) chamber surface 56 . Across a gap 64 , which is sufficiently small to prevent at least excessive inflow of the ring liquid 14 into the gap 64 , the ring liquid 14 flows onto the stationary region of the liquid ring pump 1 , specifically onto the pump housing 2 .
  • An annular channel 66 is formed in the pump housing 2 , which is designed as a kind of drainage channel for the annular liquid 14 , which runs off the chamber surface 56 onto the pump housing 2 .
  • an outlet is formed in the ring channel 66, which represents the liquid discharge described above.
  • the drain is designed in such a way that the passage of gas is prevented.
  • the outlet is designed like a siphon or has such a small diameter that there is always a residual liquid level of the ring liquid 14 at the outlet and thus closes it against the passage of gas.

Claims (11)

  1. Pompe à anneau liquide (1), avec un corps de pompe (2) qui entoure une chambre de pompe (3) qui, dans l'état de fonctionnement conforme à la destination, est remplie d'un liquide de pompe (14), et avec une roue de pompe (4) disposée à l'intérieur de la chambre de pompe (3) et pouvant tourner autour d'un axe de rotation (6) pour le refoulement d'un fluide de travail gazeux,
    - la roue de pompe (4) présentant sur sa périphérie extérieure un certain nombre de chambres de refoulement (8) séparées les unes des autres au moins dans la direction périphérique,
    - la roue de pompe (4) présentant une ouverture de sortie respective (12) associée à chaque chambre de refoulement (8) et ménagée localement dans une paroi de fond (24) de la roue de pompe (4) délimitant radialement à l'intérieur la chambre de refoulement respective (8), pour la liaison fluidique de la chambre de refoulement respective (8) avec une zone de pression (20) de la chambre de pompe (3),
    - la paroi de fond (24) s'étendant le long de l'axe de rotation (6) des deux côtés de l'ouverture de sortie (12), en étant inclinée par rapport à l'axe de rotation (6) au moins par endroits, en direction de l'ouverture de sortie (12),
    - l'ouverture de sortie respective (12) étant disposée à un emplacement de la chambre de refoulement respective (8) présentant la plus petite distance radiale à l'axe de rotation (6),
    caractérisée en ce que
    la roue de pompe (4) présente, pour chaque chambre de refoulement (8), une ouverture d'entrée (36) ménagée localement dans l'une des parois délimitant la chambre de refoulement (8) pour la liaison fluidique de la chambre de refoulement respective (8) avec une zone d'aspiration (20) de la chambre de pompe (3).
  2. Pompe à anneau liquide (1) selon la revendication 1,
    dans laquelle la roue de pompe (4) est disposée de manière excentrée dans la chambre de pompe (3) de telle sorte qu'un anneau liquide (18) du liquide de pompe (14) se formant, en fonctionnement conforme à la destination, dans la zone de pression (20) de la chambre de pompe (3) recouvre complètement au moins une chambre de refoulement (8) dans la direction radiale.
  3. Pompe à anneau liquide (1) selon la revendication 1 ou 2,
    dans laquelle chaque chambre de refoulement (8) est réalisée symétriquement par rapport à un plan radial de là roue de pompe (4) formant une surface miroir (30), et dans laquelle l'ouverture de sortie (12) est disposé dans la surface miroir (30).
  4. Pompe à anneau liquide (1) selon l'une des revendications 1 à 3,
    dans laquelle la paroi de fond respective (24) délimitant la chambre de refoulement (8) radialement à l'intérieur est réalisée sensiblement en forme de U ou de V le long de l'axe de rotation (6).
  5. Pompe à anneau liquide (1) selon l'une des revendications précédentes,
    dans laquelle l'ouverture d'entrée (36) est ménagée dans la paroi de fond (24) ou dans une paroi latérale (26) délimitant frontalement la chambre de refoulement respective (8).
  6. Pompe à anneau liquide (1) selon l'une des revendications précédentes,
    dans laquelle un clapet anti-retour (50) est disposé à l'intérieur de l'ouverture de sortie (12).
  7. Pompe à anneau liquide (1) selon l'une des revendications précédentes,
    dans laquelle un clapet anti-retour (58) est disposé à l'intérieur de l'ouverture d'entrée (36).
  8. Pompe à anneau liquide (1) selon l'une des revendications précédentes,
    dans laquelle l'ouverture de sortie respective (12) débouche dans une chambre de sortie (54) disposée sur la roue de pompe (4), qui est conçue pour séparer le fluide de travail du liquide de pompe (14) sous l'effet de la force centrifuge.
  9. Pompe à anneau liquide (1) selon la revendication 8,
    dans laquelle des moyens, en particulier des aubes directrices ou des disques directeurs, sont disposés dans la chambre de sortie (54) pour assister la séparation du fluide de travail du liquide de pompe (14).
  10. Pompe à anneau liquide (1) selon l'une des revendications 1 à 5,
    avec une bague de commande (40) pouvant tourner par rapport à la roue de pompe (4), qui obture les ouvertures de sortie (12) de la roue de pompe (4) par endroits côté sortie contre la roue de pompe (4).
  11. Pompe à anneau liquide (1) selon l'une des revendications précédentes,
    dans laquelle on utilise une poly-alpha-oléfine comme liquide de pompe (14).
EP18772737.5A 2017-08-29 2018-08-29 Pompe à anneau liquide Active EP3676496B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017215080.7A DE102017215080A1 (de) 2017-08-29 2017-08-29 Flüssigkeitsringpumpe
PCT/EP2018/073206 WO2019043044A1 (fr) 2017-08-29 2018-08-29 Pompe à anneau liquide

Publications (2)

Publication Number Publication Date
EP3676496A1 EP3676496A1 (fr) 2020-07-08
EP3676496B1 true EP3676496B1 (fr) 2022-10-05

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ID=63637851

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

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EP (1) EP3676496B1 (fr)
DE (1) DE102017215080A1 (fr)
WO (1) WO2019043044A1 (fr)

Family Cites Families (12)

* 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
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
JPS4964910A (fr) * 1972-09-05 1974-06-24
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
IT1292483B1 (it) * 1997-07-04 1999-02-08 Garo Roberto Gabbioneta S P A Compressore ad anello liquido a rendimento elevato
DE20015709U1 (de) * 2000-09-11 2002-01-31 Speck Pumpenfabrik Walter Spec Flüssigkeitsringpumpe mit Nabensteuerung
NO316638B1 (no) * 2002-04-19 2004-03-15 Compressor Systems As Vaeskeringkompressor
EP1794458A1 (fr) * 2004-09-17 2007-06-13 Basf Aktiengesellschaft Procede permettant de faire fonctionner un compresseur a anneau liquide

Also Published As

Publication number Publication date
EP3676496A1 (fr) 2020-07-08
DE102017215080A1 (de) 2019-02-28
WO2019043044A1 (fr) 2019-03-07

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