EP3568596B1 - Regelung der spaltgeometrie in einer exzenterschneckenpumpe - Google Patents

Regelung der spaltgeometrie in einer exzenterschneckenpumpe Download PDF

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Publication number
EP3568596B1
EP3568596B1 EP18701291.9A EP18701291A EP3568596B1 EP 3568596 B1 EP3568596 B1 EP 3568596B1 EP 18701291 A EP18701291 A EP 18701291A EP 3568596 B1 EP3568596 B1 EP 3568596B1
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EP
European Patent Office
Prior art keywords
rotor
stator
constriction
adjusting device
relative
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EP18701291.9A
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German (de)
English (en)
French (fr)
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EP3568596C0 (de
EP3568596A1 (de
Inventor
Paul Krampe
Michael ROLFES
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Vogelsang GmbH and Co KG
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Vogelsang GmbH and Co KG
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Application filed by Vogelsang GmbH and Co KG filed Critical Vogelsang GmbH and Co KG
Priority to EP22195723.6A priority Critical patent/EP4137698A1/de
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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
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau 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
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • 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
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/003—Sealings for working fluid between radially and axially moving parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2250/201—Geometry of the rotor conical shape

Definitions

  • the invention relates to an eccentric screw pump for conveying liquids laden with solids, with a helically wound rotor, a conical stator, with an inlet and an outlet, in which the rotor is arranged rotatably about a longitudinal axis of the stator, and the one corresponding to the rotor has a helical inner wall, the rotor having a preferably conical shape that tapers towards the outlet or inlet and/or a changing eccentricity, and the rotor and stator being arranged and designed in relation to one another in such a way that at least one chamber is formed, which is used for conveying which is used for liquids, and the chamber is separated by a constriction, in particular a sealing line.
  • the invention also relates to a method for operating such an eccentric screw pump.
  • Eccentric screw pumps of the type mentioned have been known for a number of years and are used in particular to gently convey and meter liquids laden with solids, abrasive liquids, or generally liquids with high viscosity. They use a single or multi-threaded helical rotor, which is arranged in a corresponding double or multi-threaded chamber of a stator and rotates in it.
  • the worm rotates about a worm axis of rotation, which in turn rotates about a longitudinal stator axis that is generally parallel to it, which is guided eccentrically on a circular path Rotational movement of the screw results and from which the term "eccentric" screw pump is derived.
  • the screw of an eccentric screw pump is often driven by a wobble shaft, which is formed by a shaft between the drive motor and the rotor that is provided with cardan joints at both ends.
  • a wobble shaft which is formed by a shaft between the drive motor and the rotor that is provided with cardan joints at both ends.
  • Appropriate design of the outer profile of the rotor and the inner profile of the stator results in a constriction, in particular a sealing line, which seals the at least one chamber, but preferably individual chambers of a plurality of chambers, against one another.
  • the rotor and the stator can be in direct contact with one another and form a sealing line, or they can also have a sealing gap separating the chambers in the constriction.
  • the rotor is designed as a single-threaded worm and the stator as a double-threaded worm with a double pitch, resulting in the sealing of the individual chambers.
  • a worm pump which has a conical worm and a conical pressure jacket.
  • the worm has a conicity of about 30° cone angle, with which an increase in the conveying pressure is to be achieved over a short worm length.
  • Screw and pressure jacket are axially movable relative to each other in that the pressure jacket is guided in a sleeve so that it can move axially. This is to keep a constant pressure by displacing the pressure jacket under the action of fluid pressure on an annular part of the pressure jacket in the pump.
  • an increase in pressure at the outlet can only bring about a vertical infeed and thus the pressure jacket being pressed against the screw.
  • a screw pump which has a conical stator and rotor.
  • the rotor By means of a screw sleeve inserted between the rotor and the output shaft, the rotor can be adjusted axially in relation to the stator in this worm pump by a user turning the sleeve manually through a hand hole with a tool when the pump is stationary. In this way, both a jamming and an excessive play between the stator and the rotor, caused by swelling of the stator or wear of the rotor and/or stator, can be compensated for.
  • DE 102014117483 A1 discloses an adjustable pump unit for a progressive cavity pump.
  • the stator is at least partially formed from an electroactive and/or temperature-active material and/or is coupled or equipped with at least one electroactive and/or temperature-active means, the means being usable as sensors, so that parameters of the displacement pump can be measured by a control device can be adjusted based on the sensors.
  • the stator can be moved in a desired direction upon activation of the electroactive means.
  • conical progressing cavity pumps are also known, since they allow both simple assembly and readjustment of the rotor in relation to the stator in the event of wear.
  • Such an eccentric screw pump is, for example, from WO 2010/100134 A2 known.
  • this document proposes an eccentric screw pump with a conical rotor, which is designed in such a way that the individual chambers all have the same volume. If signs of wear then form during operation, in particular so-called cavitations, it is possible to move the rotor axially in relation to the stator in such a way that the chamber volumes are the same size again and tightness is achieved.
  • the invention has an adjustment device for adjusting an axial relative position of rotor and stator, which is designed to optimize the gap geometry between rotor and stator by being set up to widen the constriction between rotor and stator.
  • the invention is based on the finding that the gap geometry, i.e. the geometry of the constriction that separates the chamber(s), is important on the one hand in order to form the seal sufficiently so that pumping is possible, on the other hand there is friction during operation of the eccentric screw pump, which the individual parts, in particular the rotor and stator, heat up and then, due to the material expansion, a prestress between the rotor and stator is increased, or the constriction becomes too small. The increased preload then leads to further wear.
  • the gap geometry i.e. the geometry of the constriction that separates the chamber(s)
  • the invention has recognized that any wear can be avoided or reduced if the constriction is widened during operation and the gap geometry can thereby be adapted to the operating conditions and thus optimized.
  • the present invention therefore proposes an adjusting device which is designed to widen the constriction between the rotor and the stator. When the constriction widens again, there is less preload contact or no contact, and therefore less friction between the rotor and stator, which in turn leads to less wear. When pumping liquid, there is also a cooling effect, so that the parts can cool down again when the preload is reduced. This also makes it possible, for example, to set a larger gap when the eccentric screw pump starts up, in order to keep friction low in the dry state.
  • the rotor has a shape that tapers towards the outlet or inlet.
  • the shape is determined by the envelope that encloses the rotor.
  • the shape is preferably conical.
  • the rotor thus has a diameter that becomes smaller in the direction of the outlet or the inlet.
  • the rotor preferably tapers linearly.
  • it is also preferred that the rotor has a shape that tapers according to a predetermined function, for example a function of the 2nd, 3rd, or 4th degree.
  • the diameter then decreases progressively or degressively. Depending on the load on the rotor, this has advantages in order to avoid excessive wear.
  • the choice of whether the rotor tapers towards the inlet or outlet depends in particular on structural conditions, and should be made dependent on the type of assembly.
  • the direction of the taper determines the direction in which the rotor is inserted into the stator.
  • the rotor has an eccentricity that changes in the direction of the inlet or the outlet.
  • the eccentricity preferably changes linearly, i.e. increases or decreases linearly.
  • the rotor has an eccentricity that changes according to a predetermined function, for example a function of the 2nd, 3rd or 4th degree. The eccentricity then decreases progressively or degressively.
  • stator is adapted to the rotor and consequently has a corresponding inner contour.
  • the taper and/or the eccentricity of the rotor, which changes in the longitudinal direction is so small in the conveying direction that this does not cause any significant reduction in the gap cross section in the conveying direction, in order to avoid an undesired increase in pressure.
  • This can be achieved, for example, by selecting the taper so that two straight lines averaging the envelope in a longitudinal section on both sides form a cone angle of less than 20°, preferably less than 10° and in particular less than 5° to one another.
  • the area difference caused by the taper between the gap cross-sectional area in the outlet of the stator to the gap cross-sectional area in the inlet of the stator is less than 10%, preferably less than 5% of the gap cross-sectional area in the inlet of the stator.
  • the adjusting device is set up to widen the constriction between the rotor and the stator to such an extent that a leakage gap is formed between the rotor and the stator.
  • constriction is not formed by a contact between rotor and stator, but by a small gap, the Leakage gap that still provides some sealing.
  • the flow rate decreases, due to the fact that there is no longer physical contact between the rotor and stator and the liquid film between these parts, further cooling takes place and wear is further reduced. It can be provided that such a leakage gap is not permanently present during operation, but is only set during or after particular loads.
  • the adjusting device is set up to widen the constriction as a function of one or more predetermined operating parameters. It is conceivable, for example, that an expansion of the constriction is automatically stopped after a certain period of operation. It is also conceivable to measure the power consumption of a drive motor and to widen the constriction as the power consumption increases. The widening of the constriction preferably takes place as a function of a number of operating parameters. Although it is also conceivable and preferred to use only a single operating parameter, wear can be reduced more effectively by using a plurality of operating parameters.
  • the temperature of the stator is preferably measured.
  • the eccentric screw pump preferably has at least one sensor, which is arranged in or on the stator and measures the temperature of the stator.
  • the temperature is preferably measured at several points in order to be able to reduce wear particularly effectively. A continuous widening of the narrowing as a function of the temperature preferably takes place.
  • one or more thresholds are predetermined, and when the one or more thresholds are exceeded, a gradual widening of the constriction is performed.
  • One, in particular another, of the operating parameters is preferably the pumped volume of liquid.
  • the volume of liquid conveyed is preferably the volume of liquid per revolution. If the pumped liquid volume per revolution decreases, this means that more gas or air is pumped.
  • the cooling effect that the medium exerts on the progressing cavity pump is less than when pumping a liquid. Therefore, in this case, it is also preferable to widen the constriction to prevent wear.
  • a flow meter is arranged at the inlet or the outlet of the stator.
  • one of the operating parameters is a liquid level at the inlet of the stator.
  • a liquid sensor or several liquid sensors are preferably provided for this purpose. It can be preferred to measure only a specific fill level as a threshold value. Alternatively, continuous measurement of the filling level at the stator inlet is also preferred. If the liquid level at the stator inlet is low, the progressing cavity pump is more likely to run dry, resulting in higher friction and less cooling of the progressing cavity pump. This in turn leads to faster heating and thus material expansion, whereby the constriction is further reduced and prestressing can increase. Therefore, it is preferred that in case a low liquid level is measured at the inlet of the stator, the constriction between the rotor and the stator is widened.
  • Another conceivable parameter is the pressure at the outlet. If this remains the same or decreases while the torque increases at the same time, this is an indicator of increased friction between the rotor and stator and thus a sign of swelling of the stator material. In such a case, too, it is preferable to widen the constriction in order to adapt the gap geometry to the changed framework conditions.
  • the stator is mounted in an axially displaceable manner and the adjusting device is set up to displace the stator axially in order to at least partially widen the constriction between the rotor and the stator.
  • the rotor is usually coupled to a drive and the stator is fixed in the direction of rotation. In the event of wear, it is primarily the stator that must be replaced, since this is usually made of a softer material than the rotor. Since the stator must be arranged so that it can be easily replaced for this reason, it is proposed in this embodiment to mount the stator in such a way that it can be displaced axially in order to at least partially widen the constriction between the rotor and the stator.
  • the adjusting device is preferably coupled to the stator in order to displace it.
  • the adjusting device can be coupled to a drive of the stator provided for this purpose.
  • a drive of the stator is designed as a hydraulic drive, rack and pinion drive, chain drive, spindle drive or the like.
  • the drive of the stator is preferably designed in such a way that an axial position of the stator can be maintained. This is preferably realized in that the drive of the stator is designed to be self-locking.
  • the rotor is mounted in an axially displaceable manner and the adjusting device is set up to displace the rotor axially in order to at least partially widen the constriction between the rotor and the stator.
  • the adjusting device is set up to displace the rotor axially in order to at least partially widen the constriction between the rotor and the stator.
  • a drive train comprising a drive motor and a drive shaft, of the rotor can be displaced together with the rotor.
  • the rotor is usually coupled to a drive motor, which is usually designed as an electric motor, by means of a shaft. Since the rotor rotates eccentrically around a central axis of the stator, i.e. its central axis describes a circular path around the central axis of the stator, such a drive shaft usually also includes at least one cardan joint or flexible rod to allow eccentric torque transmission.
  • both the drive motor and the drive shaft, which belong to the drive train are movably mounted together with the rotor. This simplifies the design of the drive train and, for example, a linear bearing is provided for the drive motor, which, as described above with reference to the stator, can be provided with a drive provided for this purpose.
  • the rotor together with the drive shaft can be displaced in relation to the drive motor.
  • a transmission is arranged between the drive shaft and the drive motor, which allows an axial displacement of the drive shaft.
  • gear wheels of the transmission are designed in such a way that an axial displacement is permitted.
  • the arrangement of the drive motor is simplified, while the construction of the gearbox is more complex than that of the previously described embodiment. As a further advantage, however, this results in the fact that the mass of the movable parts is lower. It is also possible to store the drive motor separately.
  • the drive shaft is designed in at least two parts and has an expansion member which allows the drive shaft to be lengthened and shortened for the purpose of axial displacement of the rotor.
  • the drive shaft can be made telescopic and can automatically extend it, or a separate drive for moving the rotor is provided for the rotor.
  • a hydraulically operated in the drive shaft Expansion member is arranged, which allows an axial adjustment by applying hydraulic pressure.
  • a mechanically acting expansion member for example in the form of a spindle drive, can also be provided.
  • a separate drive unit is provided for the rotor, which displaces the rotor axially while the expansion member is passive and allows this displacement. This further simplifies the construction.
  • the longitudinal axis of the stator is oriented substantially vertically or upright during operation and the outlet of the stator is arranged at the top.
  • the vertical arrangement also saves space and the progressing cavity pump is particularly easy to install in existing systems.
  • the vertical arrangement is made possible by the fact that the constriction can be expanded.
  • the stator is formed from a flexible material, in particular an elastomer, at least in the area of the inner wall. On the one hand, this simplifies the manufacture of the stator and, on the other hand, it also creates a good seal between the stator and the rotor.
  • the inner wall of the stator is lined with a layer of elastomer material that is essentially of uniform thickness.
  • the entire stator is made of elastomer material and is externally provided with a sleeve for stabilization.
  • the adjusting device is designed to precede the constriction between the rotor and the stator at the beginning of a start-up process or during or after a coast-down process of a drive motor for rotation of the rotor, and to reduce the constriction between the rotor and stator before the start during the start-up process of the drive motor.
  • the constriction between rotor and stator is adjusted from an enlarged constriction to an extended constriction during the start of a delivery process of the eccentric screw pump, i.e. when starting or after starting a drive motor that generates the rotational movement of the rotor relative to the stator.
  • the eccentric screw pump is adjusted from an initially high internal leakage flow to a reduced leakage flow.
  • This adjustment movement serves to ensure that the delivery volume and/or the delivery pressure of the eccentric screw pump does not suddenly build up when the delivery process starts, which would cause a high load on the eccentric screw pump and the connected lines, but rather build up continuously over a starting period.
  • This start period can be in the range of one second to several seconds.
  • this embodiment is advantageous when a drive motor is used that does not have a speed control controlled by a frequency converter, but instead has an immediate increase to the nominal speed when starting.
  • the constriction between the stator and rotor can be widened at the end of a conveying process, so that it is in an expanded state at the subsequent start of a conveying process, or that before the drive motor starts up when a conveying process is started a corresponding expansion of the constriction is carried out in order to then start this drive motor after this expansion has been carried out.
  • the constriction between the stator and rotor can be widened at the end of a conveying process, so that it is in an expanded state at the subsequent start of a conveying process, or that before the drive motor starts up when a conveying process is started a corresponding expansion of the constriction is carried out in order to then start this drive motor after this expansion has been carried out.
  • the adjustment device has an input interface for receiving a pressure signal and is designed to widen or reduce the constriction between rotor and stator depending on the pressure signal.
  • the adjusting device which can basically have a corresponding control unit, which can be designed as an electronic control unit, is designed to change the constriction between the rotor and stator as a function of a pressure signal.
  • the pressure signal can be a pressure on the input side, a pressure inside the stator or a pressure on the output side of the stator, in particular also a pressure on the pressure side of the progressing cavity pump. In this way, an exact setting of a pressure can take place, and a predetermined pressure profile can also be adjusted as an actual value profile by appropriately setting the constriction.
  • this setting or regulation is carried out by extending or reducing the lengthening between the rotor and stator, which enables a much more precise, spontaneous and low-inertia setting or regulation compared to any possible regulation of the rotational speed of the rotor and stator.
  • this embodiment can also be used to provide overpressure protection. In this case, when a specific pressure is reached or the specific pressure is exceeded, the constriction between the rotor and the stator is widened and this prevents the pressure from rising above a specific maximum pressure.
  • the eccentric screw pump according to the invention can be further developed in that the adjusting device has an input interface for receiving a volume quantity signal and is designed to widen the constriction between rotor and stator depending on the volume quantity signal in such a way that at a value of the volume quantity signal that signals that a volume delivered since the start of a delivery process corresponds to a target volume, the constriction between the rotor and the stator is widened in such a way that no further delivery of a volume from the outlet of the stator takes place.
  • the adjustment device is designed to receive a volume quantity signal. In principle, this volume quantity signal can characterize a target volume that is to be conveyed by the eccentric screw pump.
  • the constriction between rotor and stator can be set or adjusted in such a way that when only a small proportion of the desired setpoint volume is to be conveyed is, a widening of the constriction between rotor and stator is adjusted and in this way the flow rate is reduced in one or two stages or continuously.
  • the actual volume can be recorded by a corresponding volume flow meter or can be calculated from the number of revolutions of the eccentric screw pump and the extent of the constriction between the rotor and stator over the delivery period.
  • a setpoint signal can be recorded by the adjustment device or entered into the adjustment device as a volume quantity signal.
  • the manipulated variable for the constriction between rotor and stator is calculated within the adjustment device and can be carried out by internal calculation or additional input of actual values into the adjustment device become.
  • the volume quantity signal can also be a differential signal that was determined from the desired value and the actual value in order to enable a manipulated variable to be calculated directly from this within the adjusting device.
  • the adjustment device is designed to adjust the axial relative position of the rotor to the stator while the rotor rotates relative to the stator. This configuration for axial adjustment during ongoing operation of the pump can be implemented, for example, by an adjustment device that is accessible from the outside or can be controlled from the outside.
  • the adjusting device can be designed as a power-operated actuator and thus enable the adjustment during the rotation of the rotor, for example by providing a hydraulically, pneumatically or electrically operated actuator on the pump for the axial adjustment between the rotor and the stator.
  • the object mentioned at the outset is achieved by a method for operating an eccentric screw pump according to at least one of the above-described preferred embodiments of an eccentric screw pump according to the first aspect of the invention, with the steps: driving the rotor to convey a liquid; Expanding the constriction between the rotor and stator by axially shifting the rotor and stator relative to one another.
  • the progressing cavity pump according to a first aspect of the invention and the method according to the second aspect of the invention have the same and similar preferred configurations as are laid down in particular in the dependent claims. In this respect, reference is made in full to the above description of the first aspect of the invention.
  • the method also preferably has the step of setting a leakage gap between the rotor and the stator.
  • the adjustment of the leakage gap is preferably performed while driving the rotor to pump a liquid. That means that Displacement of the rotor and stator relative to each other, as well as setting a leakage gap, preferably takes place during operation, namely preferably when an operating parameter reaches or exceeds a threshold value.
  • the method preferably also includes the step of: measuring a temperature of the rotor and/or the stator; and depending on the measured temperature, relative axial displacement of the rotor and stator. If, for example, a threshold temperature that is predetermined is exceeded, the rotor and stator are axially displaced relative to one another as a function of this exceeding, so that the constriction is widened. It can also be provided that when the temperature drops, the constriction is again reduced, up to a contact under prestress, in order to keep a leakage low.
  • the temperature of the rotor and/or the stator is preferably measured continuously, preferably at predetermined small time intervals. Depending on these measurements, a displacement between rotor and stator is then preferably performed dynamically, so that the constriction present between rotor and stator and thus the gap geometry is always consistent with the measured temperature, so that wear can be prevented.
  • the steps are preferably also carried out: determining a liquid level at the inlet of the stator; and depending on the determined liquid level, relatively axially shifting the rotor and stator.
  • the liquid level is preferably determined by means of a liquid sensor. Provision can be made for the liquid level to be determined only in relation to a certain threshold, for example half of the maximum inlet flow.
  • a relative axial displacement of the rotor and stator is then carried out, preferably by a predetermined fixed value. This widens the constriction and prevents wear. It can also be provided that when the liquid level rises again, the constriction is reduced again, i.e. a small gap or contact is set in order to achieve an optimal gap geometry and delivery.
  • the method also includes: determining a pumped volume of liquid per revolution of the rotor; and depending on the determined volume of liquid, relative axial displacement of the rotor and stator.
  • a low pumped volume of liquid per revolution of the rotor indicates that a relatively high proportion of gas is pumped. Promoting gas on the one hand prevents lubrication between the parts that are in contact and on the other hand also prevents cooling. In this case, when a relatively large amount of gas is pumped and little fluid per revolution of the rotor, it is preferred that the restriction be widened so as to prevent wear.
  • the method can be further developed by widening the constriction between the rotor and stator at the beginning of a start-up of a drive motor for rotating the rotor, and reducing the constriction between the rotor and stator after the start-up of the drive motor.
  • a pressure is detected by means of a pressure sensor and the constriction between the rotor and the stator is widened or narrowed as a function of the pressure.
  • the eccentric screw pump is controlled or adjusted as an exact dosing pump.
  • a target volume is entered or taken up by the eccentric screw pump and the constriction between rotor and stator is widened or reduced depending on this target volume.
  • This expansion or reduction of the constriction between the rotor and the stator is adjusted in such a way that the delivery volume is reduced to 0 when the desired volume quantity is reached. This can be done by appropriate widening of the constriction, or can be done in conjunction with such widening and stopping the rotation of the rotor.
  • an exact dosing to the desired target volume can be done by a gradual or continuous expansion or narrowing if such an expansion is carried out when only a small proportion of the target volume has to be promoted to reach the target volume.
  • An eccentric screw pump 1 has a stator 2 and a rotor 4 .
  • the stator has a central axis L 1 extending centrally through an inner cavity 6 of the stator 2 .
  • the stator 2 has an inner wall 8 delimiting the cavity 6 and made of an elastomeric material.
  • the inner contour of the wall 8 is formed to define a double helix.
  • the rotor 4 is also formed helically as a whole, with the pitch of the helical shape of the stator 2 having a double pitch with respect to the rotor 4 .
  • individual chambers 5 are formed, which are separated by a constriction 7 .
  • the stator 2 also has an inlet 10 and an outlet 12 .
  • the inlet 10 is connected to an inlet housing 14 which has an inlet flange 16 to which an inlet pipe 18 is flanged.
  • the outlet 12 is also provided with an outlet housing 20 which has an outlet flange 22 to which an outlet pipe 24 is flanged.
  • a drive shaft 26 extends through the inlet housing 14 and is connected to the rotor 4 via a first universal joint 28 and is connected to an output shaft 32 of a transmission 34 by a second universal joint 30 .
  • the transmission 34 is connected on the input side to a drive motor 36 which, according to this exemplary embodiment, is designed as an electric motor.
  • the eccentric screw pump 1 has an adjusting device 39 for widening the constriction 7 between the rotor 4 and the stator 2 in order to set an optimal gap geometry.
  • the adjusting device 39 is designed in such a way that the stator 2 is mounted in an axially displaceable manner.
  • the stator 2 is slidable along the longitudinal axis L 1 as indicated by the arrow 38 .
  • the stator 2 is accommodated in sections of the inlet housing 14 and the outlet housing 20, which are sealed with a seal 40, 42.
  • the adjusting device 39 has an engagement section 44 which can be connected to a drive provided for this purpose.
  • Figures 2a - 2c show a gap geometry with a sealing gap in which there is contact between the rotor 4 and the stator 2, illustrate the Figures 3a - 3c an expansion of the constriction 7, so that a leakage gap S is set.
  • Figure 2b shows a section along the longitudinal axis L 1 , as in FIG 1 shown.
  • the rotor 4 is in a maximum upper position based on the Figures 2a - 2c , which is particularly evident from the Figures 2a and 2c can be seen, each showing sections perpendicular to the longitudinal axis L 1 .
  • Figure 2a shows a section near the inlet 10 and Figure 2c a cut at the outlet 12.
  • the rotor 4 rests with a section of its peripheral surface 3 on an inner wall 9 of the stator 2 .
  • a sealing line D in the constriction 7 is formed by the contact.
  • the stator 2 is formed from a flexible material such as an elastomer in particular. Prestressing in the radial direction consequently leads to an elastic deformation of the stator 4 in the area of the sealing line D. In this case, the friction is relatively high. High friction also leads to high wear.
  • this radial preload can increase further, for example due to swelling of the material of the stator 2 or due to expansion of the materials due to heat input.
  • shear-sensitive media it is preferred, for example, to form a sealing line D and at the same time to achieve a relatively high radial prestress, so that the medium is clearly separated at the sealing lines D between the chambers 5 and there is little shearing.
  • the eccentricity e 1 , e 2 is in this embodiment ( Figures 2a-3c ) constant while the diameter D 1 , D 2 of the rotor 4 decreases towards the outlet 12 . That is, e 1 , and e 2 are identical, while D 1 , is greater than D 2 . However, embodiments are also included in which the diameter is constant, ie D 1 is identical to D 2 , and the eccentricity changes, ie for example e 1 is greater than e 2 . The effect of axial displacement is then corresponding.
  • the adjusting device 39 is designed in such a way that the rotor 4 can be displaced axially, together with the complete drive train 25 which, according to this exemplary embodiment, consists of the drive shaft 26, the gear 34 and the drive motor 36.
  • the arrow 37 indicates that the drive motor 36 is also displaced.
  • the housing 46 of the transmission 34 is displaceably mounted in a section 48 of the inlet housing 14 opposite the inlet 10 of the stator 2 and is sealed off from the environment by a seal 50 .
  • a separate drive 52 is provided for this purpose, which can move the drive train 25 via a spindle drive 54 (shown only schematically) in such a way that the constriction 7 between the rotor 4 and the stator 2 is widened. If this is required, the constriction 7 can be widened to such an extent that there is a leakage gap S in the area of the sealing line D between the rotor 4 and the stator 2. In this case, a preload between the rotor 4 and the stator 2 is usually not completely eliminated, since there is a back pressure from the liquid being pumped.
  • the drive 52 is preferably connected to a controller via a signal line 56 .
  • the controller is preferably integrated or connected to a controller 58, for example via the signal line 60.
  • the controller preferably has an input interface via which control or regulation data is input and is designed to control or regulate depending on this control or execute control data. For example, a target volume or a difference between a target volume and an actual volume can be entered into the controller via this interface.
  • the interface can be a user interface or an interface for connecting a sensor or switch.
  • the controller 58 is used to determine whether and to what extent the gap geometry is changed, ie the constriction 7 between the rotor 4 and the stator 2 is to be widened.
  • the controller 58 is initially connected to a sensor 62 which is arranged in the stator 2 .
  • the sensor 62 is designed as a temperature sensor and is used to record the temperature of the stator 2 . It should be understood that the sensor 62 can also be arranged to sense the temperature of the rotor 4 . For this purpose, the sensor 62 can either detect the outer surface of the rotor 4 , or this sensor or an additional one can be arranged in the rotor 4 .
  • the controller 58 determines whether a threshold temperature has been reached based on the temperature measured by the sensor 62 and whether and how much to change the gap geometry. This result is sent to the drive 52 in the form of a displacement signal via the lines 60 and 56 so that the drive train 25 is displaced in order to widen the constriction 7 between the rotor 4 and the stator 2 .
  • the eccentric screw pump 1 also has a level sensor 64 which determines the level of liquid at the inlet 10 of the stator 2 .
  • This sensor 64 is also connected to the controller 58 . Based on the fill level received, the controller 58 determines a displacement of the rotor 4 relative to the stator 2 and sends a corresponding signal to the drive 52 for adjusting the drive train 25.
  • the eccentric screw pump 1 according to this embodiment ( 4 )
  • a flow sensor 66 which a flow of liquid through the Stator 2 measures.
  • This sensor 66 is also connected to the controller 58, the controller 58 determines the flow rate or the flow volume per revolution based on the signal from the sensor 66 and the speed of the rotor 4. If this is low, this also suggests that a relatively large amount of gas is being conveyed, as a result of which the friction between rotor 4 and stator 2 is increased and cooling is also reduced at the same time. As a rule, this leads to greater material expansion and, in turn, to increased prestressing between the rotor 4 and stator 2 and, as a result, to increased wear. An adaptation of the gap geometry is then preferred.
  • a pressure sensor 66 can also be provided, which enables the pressure to be regulated by adjusting the constriction between the rotor and the stator. With such a pressure sensor, maintaining a minimum pressure or a maximum pressure can also be adjusted or controlled by adjusting the constriction. In principle, it should be understood that such a pressure sensor can also be provided in addition to the flow sensor 66 .
  • the pressure sensor can also be arranged in the area of the stator or on the inlet side.
  • controller 58 may also be integrated into the controller of the drive 52 and/or into the controller of the drive motor 36 .
  • FIG. 12 shows another embodiment that is basically similar to the embodiment of FIG 4 is. Identical and similar elements are in turn provided with the same reference symbols, so that reference is made in full to the above description. It is to be understood that the sensors 62, 64, 66 referred to in FIG 4 were described, as well as in the embodiments of figures 1 , 5 , 6 and 7 can be used separately or in combination.
  • the rotor 4 is arranged to be displaceable relative to the stationary stator 2.
  • the drive motor 36 is also stationary and cannot be moved.
  • the drive shaft 26 is in turn coupled to the output shaft 32 of the drive motor 36 via a cardan joint 30 .
  • output shaft 32 is mounted in axially displaceable manner in output gear wheel 68 of transmission 34 .
  • the gear 68 is coupled to the output shaft 32 with an axially displaceable shaft-hub connection.
  • the transmission 34 is therefore equipped with a gear 68 designed as a hollow shaft, in which the shaft 32 can be displaced.
  • the output shaft 32 is in turn guided through a seal 70 so that no liquid can penetrate from the drive inlet housing 14 into the transmission 34 .
  • a drive 52 (cf. 4 ) be arranged to allow the axial displacement of the output shaft 32 and consequently the rotor 4.
  • the rotor 4 is displaceable, while the stator 2 is held stationary in the inlet housing 4 and the outlet housing 20.
  • the drive shaft 26 is designed in two parts and has a first part 74 and a second part 76 .
  • the two parts 74, 76 are telescoped into one another and an expansion member 80 is formed between the two parts 74, 76 in a recess 78 in the first member 74.
  • the expansion member 80 serves to allow the axial length of the drive shaft 26 by shifting the second shaft part 76 to the first shaft part 74 .
  • the expansion of the expansion member 80 or the reduction in size of the expansion member 80 enables the rotor 4 to be displaced.
  • the expansion member 80 is a passive expansion member, such as hydraulics in particular.
  • a hydraulic system is used to keep a preload between the rotor 4 and the stator 2 approximately the same, so that the preload force that acts on the rotor 4 is essentially constant.
  • the rotor 4 with respect to 4 can dodge to the left, compensation by means of the hydraulics in the expansion member 80. This prevents excessive wear as well as an active, controlled by a drive adjustment of rotor 4 and / or stator 2.
  • the pressure acting in the hydraulics can then to the pump pressure can be adjusted.
  • FIG. 7 finally shows an embodiment of the eccentric screw pump 1, which in turn allows a displacement of the rotor 4 relative to the stator 2.
  • the drive shaft 26 is again as in the first three embodiments figures 1 , 4 and 5 formed in one piece.
  • the input shaft 26 is connected to the output shaft 32 by means of a cardan joint 30 .
  • the stub shaft 82 which connects the universal joint 28 to the rotor 4 is formed in two parts and has a first part 84 which is rigidly connected to the rotor 4 and a second part 86 which is connected to the universal joint 28 .
  • the parts 84 and 86 are telescoped into each other and in the part 84 is an expansion member 80, corresponding to the expansion member 80 according to FIG 4 , educated.
  • This expansion member 80 can in turn be active or passive, passive for example in the form of hydraulics.
  • a drive which displaces the rotor 4 axially, acts on the end face 88 of the rotor 4 .
  • step 100 the eccentric screw pump 1 is started and the rotor 4 is rotated.
  • step 102 designates the delivery of liquid from the inlet 10 to the outlet 12 of the stator 2 by rotation of the rotor 4.
  • step 104 the temperature of the stator 2 is measured in step 104 by means of a temperature sensor.
  • step 106 This measured temperature is compared to one or more thresholds in step 106 .
  • step 108 it is then determined whether one or which of the several threshold values has been exceeded and if no threshold value has been exceeded, or already the preload, i.e. also the axial position of the rotor relative to the stator and thus the gap geometry, i.e. the geometry of the constriction 7 with corresponds to the threshold value determined in step 106, made the choice in step 108 to continue pumping liquid and returned to step 102. Otherwise, in step 110, an appropriate preload is set. After the gap geometry has been readjusted if necessary in step S110, the process can return to step S102.
  • step 106 the temperature measured in step 104 is determined against a plurality of threshold values, each threshold value representing an equivalent to a relative axial position of rotor 4 and stator 2 to one another.
  • step 110 the corresponding axial position provided for the threshold value determined in 106 is then adjusted.
  • liquid continues to be pumped in step 102 .
  • the constriction between the rotor and the stator is widened so much that there is no or only a low pumping rate due to the internal leakage.
  • the constriction is then reduced over a time-limited start-up process of approx. 1.5 seconds to such an extent that a desired delivery rate or a desired delivery pressure is achieved.

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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)
EP18701291.9A 2017-01-16 2018-01-16 Regelung der spaltgeometrie in einer exzenterschneckenpumpe Active EP3568596B1 (de)

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Application Number Priority Date Filing Date Title
EP22195723.6A EP4137698A1 (de) 2017-01-16 2018-01-16 Regelung der spaltgeometrie in einer exzenterschneckenpumpe

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DE102017100715.6A DE102017100715A1 (de) 2017-01-16 2017-01-16 Regelung der Spaltgeometrie in einer Exzenterschneckenpumpe
PCT/EP2018/050986 WO2018130718A1 (de) 2017-01-16 2018-01-16 Regelung der spaltgeometrie in einer exzenterschneckenpumpe

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AU (1) AU2018208543B2 (zh)
BR (1) BR112019014558B1 (zh)
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CN113107835A (zh) 2021-07-13
CN110392785B (zh) 2021-03-30
CA3050182A1 (en) 2018-07-19
BR112019014558B1 (pt) 2023-10-31
AU2018208543B2 (en) 2021-08-12
WO2018130718A1 (de) 2018-07-19
KR20190105632A (ko) 2019-09-17
PL3568596T3 (pl) 2024-02-12
US20200124046A1 (en) 2020-04-23
BR112019014558A2 (pt) 2020-02-18
EP4137698A1 (de) 2023-02-22
EP3568596C0 (de) 2023-08-09
JP7015839B2 (ja) 2022-02-03
ES2957935T3 (es) 2024-01-30
JP2020504266A (ja) 2020-02-06
CN113107835B (zh) 2023-08-18
KR102356133B1 (ko) 2022-01-26
CN110392785A (zh) 2019-10-29
AU2018208543A1 (en) 2019-08-01
EP3568596A1 (de) 2019-11-20
US11286928B2 (en) 2022-03-29
MX2019008481A (es) 2019-11-28
DE102017100715A1 (de) 2018-07-19

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