EP3961035A1 - Procédé et pompe à broche hélicoïdale destinés au pompage d'un mélange gaz-liquide - Google Patents

Procédé et pompe à broche hélicoïdale destinés au pompage d'un mélange gaz-liquide Download PDF

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Publication number
EP3961035A1
EP3961035A1 EP21187900.2A EP21187900A EP3961035A1 EP 3961035 A1 EP3961035 A1 EP 3961035A1 EP 21187900 A EP21187900 A EP 21187900A EP 3961035 A1 EP3961035 A1 EP 3961035A1
Authority
EP
European Patent Office
Prior art keywords
pump
spindle
screw
drive
fluid outlet
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.)
Pending
Application number
EP21187900.2A
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German (de)
English (en)
Inventor
Roland Maurischat
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.)
Leistritz Pumpen GmbH
Original Assignee
Leistritz Pumpen GmbH
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 Leistritz Pumpen GmbH filed Critical Leistritz Pumpen GmbH
Publication of EP3961035A1 publication Critical patent/EP3961035A1/fr
Pending legal-status Critical Current

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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid
    • 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
    • F04C2250/20—Geometry of the rotor
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/054—Speed linear

Definitions

  • the invention relates to a method for conveying a fluid, which is a gas-liquid mixture, through a screw pump, which has a housing which forms at least one fluid inlet and one fluid outlet and in which at least one drive spindle and at least one running spindle of the screw pump, which is rotationally coupled thereto, are accommodated which, in every rotational position of the drive spindle together with the housing, delimit a plurality of pump chambers, the drive spindle being rotated by a drive in a drive direction, as a result of which one of the pump chambers which is initially open towards the respective fluid inlet is closed, the resulting closed pump chamber axially towards the fluid outlet moves and is opened there upon reaching an opening rotation angle to the fluid outlet.
  • the invention relates to a screw pump.
  • Screw pumps are used in many areas to convey fluids.
  • purely liquid media for example crude oil or petroleum
  • gases and liquids for example crude oil and natural gas, which are to be extracted.
  • a plurality of chambers are formed in the axial direction, between which chambers the pressure rises at least approximately linearly from a pressure at the fluid inlet to a pressure at the fluid outlet when purely fluid is conveyed.
  • relatively high pressure differences between the fluid inlet and the fluid outlet of, for example, 5 to 50 bar or even higher pressure differences are often used.
  • screw pumps can be used whose spindles have a variable screw pitch in order to compress the gas directly by reducing the chamber volume.
  • gas compressors are known which first convey the gas against a fixed wall and thus compress it by means of screw spindles, the gas only being able to escape from the conveying chamber after the desired compression has been achieved.
  • a disadvantage of the mentioned approaches to efficient gas compression is that the gas compression takes place in each case by changing the geometry of a compressor chamber.
  • these approaches cannot be used for applications in which a high liquid content, in particular a liquid content of almost 100%, can occur at least temporarily.
  • the fluid would have to be compressed, which would require forces that cannot typically be applied by corresponding compressors or that can lead to damage to the compressor.
  • the invention is therefore based on the object of improving the efficiency of conveying a gas-liquid mixture, while at the same time it should also remain possible to convey mixtures with a high proportion of liquid, at least temporarily.
  • the object is achieved by a method of the type mentioned at the outset, in which the drive spindle is driven in such a way that, given the pump geometry of the screw pump, the pressure in the respective pump chamber before and/or when the opening rotation angle is reached is higher than the suction pressure of the screw pump, which is in the area of the respective Fluid inlet is present, is increased by a maximum of 20% or by a maximum of 10% of a differential pressure between the suction pressure and the pressure in the region of the fluid outlet.
  • the pressure in the respective pump chamber before and/or when the opening rotation angle is reached can be at most 5% of the differential pressure above the suction pressure.
  • the hyperbolic pressure increase when pumping a gas-liquid mixture in conventional screw pumps results from the backflow of liquid through remaining gaps between the pump chambers. It was recognized that by suitably adapting the pump geometry and/or the speed of the pump, this backflow of the liquid can be reduced to such an extent that the majority of the pressure increase generated by the screw pump only takes place after the respective pump chamber has opened towards the fluid outlet.
  • the liquid already in the area of the fluid outlet essentially does not flow into the opening pump chamber due to its inertia, but can instead be viewed as a rigid wall against which the gas Liquid mixture is compressed with a particularly high proportion of gas.
  • the method according to the invention achieves a similarly good level of efficiency as with gas compressors that convey gas against a rigid wall of the housing.
  • the opening pump chamber is filled with a gas-liquid mixture with a very high proportion of liquid or even only with liquid
  • the liquid column in the fluid outlet area can be transported further as a result, which essentially results in the same behavior as when using the Screw pump for transporting pure liquids results.
  • the optimization of the operating parameters to achieve the above-described properties with high gas fractions can lead to a slight deterioration in the efficiency with high liquid fractions in the gas-liquid mixture. If sufficiently high gas proportions occur sufficiently frequently, a considerable energy saving is nevertheless achieved, since the power requirement for these periods of time is considerably below that of conventional screw pumps.
  • the respective pump chamber Before the opening rotation angle is reached, the respective pump chamber is sealed equally to the pump chamber adjacent in the direction of the fluid inlet and to the fluid outlet, apart from deviations caused by tolerances. A fluid exchange in both directions is thus essentially only possible via the radial and axial gaps of the pump.
  • the opening of the pump chamber towards the fluid outlet when the opening rotation angle is reached results from the passage of the respective spindle forming the pump chamber or the wall delimiting the respective passage towards the fluid outlet ending at a specific angular position that depends on the rotation angle of the spindle.
  • a gap results in the circumferential direction between this wall and another of the spindles, which delimits the pump chamber.
  • the pump chamber is opened towards the fluid outlet through this gap in the circumferential direction.
  • the opening rotation angle can thus be defined as the angle from which a gap results in the circumferential direction in addition to the axial or radial gaps.
  • the opening rotation angle could be defined via the flow cross section enabling a fluid exchange between the pump chamber and the fluid outlet. If this flow cross section is increased by 50% or 100% or 200% compared to the closed pump chamber, reaching this limit can be defined as reaching the opening rotation angle.
  • the screw pump according to the invention can be single- or double-flow, ie it can have one or two fluid inlets located opposite one another in the axial direction.
  • the screw pump can have two, three or more screws.
  • Individual spindles can be double-threaded, for example. However, some or all of the spindles can also be single-threaded or three-threaded or have more threads.
  • the screw profiles of the respective drive screw and idler screw can be chosen such that the mean value of the number of pump chambers per drive screw and idler screw, which are closed both to the fluid inlet and to the fluid outlet, over a rotation angle of the drive screw of 360° is a maximum of 1.5 . If, for example, exactly one drive spindle and exactly one idler spindle are used, a maximum of 3 pump chambers can be completely closed on average.
  • the mean value can be determined, for example, by integrating the number of closed chambers for a particular angle of rotation of the drive spindle over the angle of 360° and then dividing the result by 360°. At a constant speed, this corresponds to an integration of the number of simultaneously closed pump chambers over a rotation period of the drive spindle and a division by the rotation period.
  • a lower limit for the number of pump chambers that are maximally closed to both the fluid inlet and the fluid outlet, regardless of the state of rotation, results from the fact that for each pair of a spindle and a fluid inlet in at least one state of rotation, a pump chamber is closed to both the fluid inlet and the fluid outlet must be closed, since otherwise a transition from opening on the fluid inlet side to opening on the fluid outlet side would result in the pump chamber opening on both sides for a short time and thus in a direct connection of the fluid inlet and fluid outlet, which would result in very high, undesired leaks in the pump would lead.
  • a gas-liquid mixture with a gas content of at least 90% can be conveyed during at least one time interval.
  • a gas-liquid mixture with a liquid content of at least 70% can be conveyed during at least one further time interval as part of the method.
  • the method according to the invention is particularly suitable if fluids with mixing ratios that vary greatly over time are to be conveyed. The reduction in the power required is particularly high for high gas proportions. Thus, in particular, gas proportions of more than 95% can also be used.
  • fluids with a significantly higher liquid content can be transported.
  • a screw spindle pump can be used in the method according to the invention, which still allows the gas-liquid mixture to be pumped even if the gas-liquid mixture contains 90% or 100% liquid.
  • the pump geometry and the speed of the screw pump used can be selected in such a way that the axial speed of the respective pump chamber during the axial movement towards the fluid outlet is at least 4 m/s.
  • the axial speed depends both on the pitch of the gear or gears of the respective spindle and on the speed.
  • high axial speeds can be achieved through high speeds and/or high gradients or relatively long pump chambers.
  • High gradients or long pump chambers in turn lead to large chamber volumes and thus to a reduction in the influence of backflow of liquid on the pressure in the pump chamber.
  • the pump geometry of the screw pump used can be selected so that the inner diameter of the screw profile of the drive spindle or at least one of the drive spindles and/or the idler spindle or at least one of the idler spindles is less than 0.7 times the outer diameter of the respective screw profile.
  • this relationship can apply to all drive spindles and idler spindles.
  • the minimum extension of the core of the screw profile in the radial direction of the respective spindle is less than 0.7 times the maximum extension of the screw profile.
  • the pump geometry of the screw pump used can be selected so that the mean circumferential gap between the outer edge of the screw profile of the drive screw or at least one of the drive screws and/or the idler screw or at least one of the idler screws and the housing is less than 0.002 times the outer diameter of the respective screw profile is.
  • the mean value of the width of the circumferential gap along the length of the circumferential gap can be regarded as the mean circumferential gap.
  • an averaging can take place via a rotation of the drive spindle in order to take into account variations in the circumferential gap with the rotation of the spindles.
  • the mean width of the circumferential gap between a spindle and the housing is preferably less than 2 ⁇ m per millimeter of the outside diameter of the respective spindle.
  • the pump geometry and the speed of the screw pump used can be selected so that the peripheral speed at the outer profile diameter of the drive spindle or at least one of the drive spindles and/or the idler spindle or at least one of the idler spindles is at least 15 m/s. This can apply in particular to all drive and idler spindles.
  • the peripheral speed can be calculated as the product of the profile outside diameter, the speed and Pi. In this way, the specified condition can be achieved, especially when using high speeds or large outer diameters of the profile. Smaller profile inside diameters tend to lead to an increase in the volume of the respective pump chamber, as a result of which, as explained above, the influence of backflowing liquid on the pressure in the pump chamber can be reduced.
  • the invention relates to a screw spindle pump for pumping a fluid that is a gas-liquid mixture, the screw spindle pump having a housing that forms at least one fluid inlet and one fluid outlet and in which at least one drive spindle and at least one idler spindle of the screw pump are accommodated, which together with the housing delimit a plurality of pump chambers in every rotational position of the drive spindle, wherein the screw spindle pump has a drive which is set up to rotate the drive spindle in a drive direction, as a result of which one of the pump chambers which is initially open towards the respective fluid inlet is closed , the resulting closed pump chamber moves axially towards the fluid outlet and is opened there towards the fluid outlet upon reaching an opening rotation angle, the screw profiles of the respective drives bsspindel and idler spindle like that are chosen such that the mean value of the number of pump chambers per drive screw and idler screw, which are closed to both the fluid inlet and the fluid outlet, over
  • the screw pump can be set up in particular to carry out the method according to the invention. Irrespective of this, the features explained with regard to the method according to the invention can be transferred to the screw pump according to the invention and vice versa, with the advantages mentioned.
  • the drive or a control device controlling the drive can be set up in such a way that the drive spindle is operated in at least one operating state of the screw spindle pump at least at a minimum speed at which the pressure in the respective pump chamber before and/or when the opening rotation angle is reached in relation to the suction pressure of the screw spindle pump, which is present in the area of the respective fluid inlet, is increased by a maximum of 20% or by a maximum of 10% of a differential pressure between the suction pressure and the pressure in the area of the fluid outlet.
  • the speed-dependent conditions specified above for the method according to the invention can also be met in the operating state by appropriate configurations of the drive or the control device.
  • the inner diameter of the helical profile of the drive spindle or at least one of the drive spindles and/or the idler spindle or at least one of the idler spindles can be less than 0.7 times the outer diameter of the respective helical profile. Additionally or alternatively, the central circumferential gap between the outer edge of the screw profile of the drive spindle or at least one of the drive spindles and / or Lead screw or at least one of the lead screws and the housing must be less than 0.002 times the outer diameter of the respective screw profile.
  • the Figures 1, 2 and 3 show various detailed views of a screw pump, which is used to deliver a fluid that is a gas-liquid mixture.
  • a screw pump which is used to deliver a fluid that is a gas-liquid mixture.
  • 1 schematically a perspective view of the drive spindle 5 and the running spindle 6 of the screw pump 1, wherein for reasons of clarity the housing 2 in 1 is not shown. 1 clarifies in particular the shape of the screw profiles of the drive spindle 5 and the idler spindle 6 and their meshing.
  • FIG. 2 shows a front section, in which in particular the interaction of the drive spindle 5 and the running spindle 6 with the housing 2 can be seen in order to form a plurality of separate pump chambers 7, 8, 9, which in turn 1 are marked because they differ from the in 2 shown cutting plane also extend.
  • the running spindle 6 is rotationally coupled to the drive spindle 5 by a coupling device (not shown), a 1:1 transmission being assumed in the example.
  • a coupling device not shown
  • the running spindle 6 rotates in the opposite direction of rotation 12 and at the same speed.
  • the speed of the drive spindle 5 and thus also of the running spindle 6 can be specified by a control device 32 of the drive 10 .
  • the fluid located in the housing 2 is received in a plurality of pump chambers 7, 8, 9 which are separate from one another.
  • the separation or closure of the pump chambers 7, 8, 9 is not completely tight due to the radial gap 25 between the housing 2 and drive spindle 5 or idler spindle 6 and due to remaining axial gaps between the interlocking screw profiles, but allows a certain fluid exchange between the pump chambers 7 , 8, 9, which can also be considered as leakage.
  • the pump chamber 7 In the rotational position of the drive spindle 5 and the idler spindle 6 shown, the pump chamber 7 is open to the fluid inlet 3, since the free end 13 of the wall 17 of the screw thread of the drive spindle 5 is in 1 is directed upwards, leaving a gap in the circumferential direction between this free end 13 and the lead screw 6, through which the fluid can flow between the pump chamber 7 and the fluid inlet 3. Accordingly, the in 1 Pump chamber 8 highlighted by dots on its outer surface open to the fluid outlet 4, since the free end 14 of the wall 17 delimiting this is in turn spaced apart from the running spindle 6 due to the rotational position and thus forms a radial gap through which the fluid can flow. The pump chamber 9 is closed both to the fluid inlet 3 and to the fluid outlet 4 .
  • Screw pumps are often used in areas where significant pressure differences of, for example, 5 to 50 bar between the fluid inlet 3 and the fluid outlet 4 can occur. If a gas-liquid mixture is pumped, this results in a compression of the gas portion.
  • Conventional screw pumps are designed in such a way that a relatively large number of mutually sealed pump chambers, for example five to ten mutually sealed pump chambers, result in the axial direction.
  • the compression of the gas takes place in the individual pump chambers in that liquid from the respectively adjacent pump chamber in the direction of the fluid outlet, in which a higher pressure is already present prevails, flows back and thus reduces the volume available for the gas in the pump chamber, which leads to the compression of the gas.
  • such a compression of the gas component means that the power requirement of the screw pump is relatively high when the gas component is high, namely approximately as high as when conveying liquid.
  • the pressure in the pump chamber when opening can be at most 10% or at most 20% of the differential pressure above the suction pressure.
  • the pump chamber 8 At a time before the in 1 shown point in time, in which the drive spindle 5 compared to the 1 shown position is rotated by 90° counter to the drive direction 11, the pump chamber 8 is just closed and has the in 4 shape shown. This position corresponds to the opening rotation angle, since an infinitesimal rotation from this position in the drive direction 11 opens the pump chamber 8 .
  • the outer surface 24 of the pump chamber 8 is delimited by the housing 2, the inner surface 18 by the inner diameter 19 of the drive spindle 5, the end face 16 by the wall 17 of the passage of the screw spindle 5 that forms the pump chamber 8, and the covered surfaces 20, 21 through the spindle 6.
  • the pump chamber 8 opens by the free end with respect to the pump chamber 8 in the in figure 5 position 34 shown is shifted.
  • the pump chamber is thus delimited towards the fluid outlet 4 no longer by the wall 17 over the entire surface of the pump chamber, but rather the surface section 22 is exposed or is delimited by the fluid wall 33 . If the fluid wall 33 is assumed to be approximately rigid, as explained above, this leads to a compression of the gas in the pump chamber 8 by reducing the volume of the pump chamber 8.
  • a further rotation of the drive spindle 5 in the drive direction 11 by 90° leads to the 6 shown shape of the pump chamber 8 and thus to a further compression.
  • 7 shows another rotation state with even stronger compression.
  • the behavior described could be achieved simply by selecting a sufficiently high speed, even with conventional pump geometries, with the high speeds required possibly leading to high loads or high wear on the pump.
  • the screw pump 1 therefore uses a special pump geometry in which the behavior described can be achieved even at relatively low speeds, for example at 1000 revolutions per minute or 1800 revolutions per minute.
  • relatively few pump chambers or revolutions of the screw threads of the drive spindle 5 and the idler spindle 6 are used instead of the usual use of a large number of pump chambers following one another in the axial direction in screw pumps.
  • in the in 1 In the rotational position shown, only one pump chamber 9 is closed both from the fluid inlet 3 and from the fluid outlet 4 .
  • a maximum of one or a maximum of two simultaneously closed pump chambers can result, regardless of the rotational state of the drive spindle 5 and the running spindle 6 in the example shown.
  • the suitable maximum number of pump chambers that can be closed at the same time scales with the number of fluid inlets, so that with a double-flow pump typically twice as many pump chambers can be closed at the same time as with a single-flow pump.
  • the maximum number of simultaneously closed pump chambers can scale with the number of running or drive spindles used.
  • pump chambers that are relatively long axially and thus pump chambers with a relatively large volume can be realized, whereby the same quantity of liquid flowing back through gaps into the pump chamber has less of an influence on the pressure in the pump chamber.
  • the inner diameter 19 of the screw profile of the drive and idler spindles 5, 6, as in particular in 2 can be clearly seen is significantly smaller, smaller by a factor of approximately 2 in the example, than the outer diameter 24 of the respective spindle.
  • the radial gap 25 between the housing 2 and the respective outer diameter 24 of the drive spindle 5 or the idler spindle 6 can be narrower than two thousandths of the outer diameter 24.
  • the pump geometry of the screw pump 1 and a sufficiently high speed work together to achieve the effects explained above.
  • the speed should be selected in such a way that the axial speed of the movement of the respective pump chamber 7, 8, 9 towards the fluid outlet 4 is at least four meters per second and/or that the peripheral speed at the profile outer diameter 24 of the drive spindle 5 or the idler spindle 6 is at least 15 meters per second.
  • curves 30, 31 show the same relationship for a speed of 1800 revolutions per minute.
  • curve 30 relates to the transport of a pure liquid and curve 31 to the transport of a fluid with a gas content of 95%.
  • Choosing a sufficiently high speed means that if there is a high proportion of gas in the pumped fluid when the respective pump chamber is opened, the pressure in this chamber is only slightly above the suction pressure, which means that considerably less drive power is required for pumped fluid with a high gas content than for a pumping of liquids. In the example shown, around 25% less power is required to operate the screw pump. As explained above, this effect can also be achieved at lower speeds by suitable modification of the pump geometry.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
EP21187900.2A 2020-08-27 2021-07-27 Procédé et pompe à broche hélicoïdale destinés au pompage d'un mélange gaz-liquide Pending EP3961035A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020122460.5A DE102020122460A1 (de) 2020-08-27 2020-08-27 Verfahren und Schraubenspindelpumpe zur Förderung eines Gas-Flüssigkeitsgemischs

Publications (1)

Publication Number Publication Date
EP3961035A1 true EP3961035A1 (fr) 2022-03-02

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EP21187900.2A Pending EP3961035A1 (fr) 2020-08-27 2021-07-27 Procédé et pompe à broche hélicoïdale destinés au pompage d'un mélange gaz-liquide

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Country Link
US (1) US11486391B2 (fr)
EP (1) EP3961035A1 (fr)
CN (1) CN114109811A (fr)
BR (1) BR102021012613A2 (fr)
DE (1) DE102020122460A1 (fr)

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DE102022207330A1 (de) 2022-07-19 2024-01-25 Vitesco Technologies GmbH Spindelpumpenstufe, Fluidfördervorrichtung und Kraftfahrzeug

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DE102014102390B3 (de) 2014-02-25 2015-03-26 Leistritz Pumpen Gmbh Schraubenspindelpumpe
CN109578271B (zh) * 2018-09-18 2021-05-11 莱斯特里兹泵吸有限责任公司 螺杆泵
CN210397080U (zh) * 2019-07-08 2020-04-24 金龙机电设备贸易(天津)有限公司 一种新型内置气液分离循环补液双螺杆油气混输泵

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BR102021012613A2 (pt) 2022-03-08
CN114109811A (zh) 2022-03-01
US11486391B2 (en) 2022-11-01

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