EP4187095A1 - Pompe à vis sans fin excentrique avec sortie de travail et sortie au repos et procédé de commande de la pompe à vis sans fin excentrique - Google Patents

Pompe à vis sans fin excentrique avec sortie de travail et sortie au repos et procédé de commande de la pompe à vis sans fin excentrique Download PDF

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Publication number
EP4187095A1
EP4187095A1 EP22209222.3A EP22209222A EP4187095A1 EP 4187095 A1 EP4187095 A1 EP 4187095A1 EP 22209222 A EP22209222 A EP 22209222A EP 4187095 A1 EP4187095 A1 EP 4187095A1
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EP
European Patent Office
Prior art keywords
rotor
stator
delivery
infeed
working
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
EP22209222.3A
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German (de)
English (en)
Inventor
Michael ROLFES
Paul Krampe
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Vogelsang GmbH and Co KG
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Vogelsang GmbH and Co KG
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Filing date
Publication date
Application filed by Vogelsang GmbH and Co KG filed Critical Vogelsang GmbH and Co KG
Publication of EP4187095A1 publication Critical patent/EP4187095A1/fr
Pending legal-status Critical Current

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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
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C2/1075—Construction of the stationary member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/601—Adjustment
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/80—Other components
    • F04C2240/811—Actuator for control, e.g. pneumatic, hydraulic, electric
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors

Definitions

  • the invention relates to an eccentric screw pump for conveying liquids laden with solids, with a helically wound rotor, a stator with an inlet and an outlet, in which the rotor is arranged so that it can rotate about a longitudinal axis of the stator, and which has a helical inner wall corresponding to the rotor comprises, wherein the rotor and stator are arranged and designed to each other such that at least one chamber is formed, which is used to convey the liquid, and the chamber is separated by a sealing line.
  • the progressing cavity pump has a drive motor for driving the rotor in rotation and a control device for controlling the drive motor at least in a working state in which the rotor is driven in rotation and in a rest state in which the rotor does not rotate.
  • the invention also relates to a method for controlling an eccentric screw pump and a computer program for an electronic control unit of 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.
  • 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.
  • 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 shell are axially adjustable relative to each other, in that the pressure shell 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.
  • a disadvantage of this previously known system is that it is designed solely for the constancy of the increased pressure that is generated by the reduction in cross-sectional area in the conveying direction of the conical pump gap and does not allow any axial displacement as a function of other influencing variables.
  • 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 jamming and 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.
  • the progressing cavity pump has at least one stator made of an elastic material and a rotor that can be rotated in the stator, the stator being surrounded at least in regions by a stator casing, the stator casing being a longitudinally divided casing consisting of at least two casing segments and forming a stator clamping device with which the stator in can be clamped in the radial direction against the rotor, the stator clamping device having one or more movable adjusting elements which work on the casing segments for setting and clamping the stator.
  • This pump is characterized in that the stator clamping device has one or more actuators, which are connected to the actuators or are equipped with actuators for automated infeed of the stator.
  • 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.
  • An adjustable pump unit for a displacement pump in particular for an eccentric screw pump or for a rotary lobe pump, should be adaptable to a wide variety of operating conditions and pumping tasks.
  • the pump unit 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 for its adjustment.
  • Parameters of the positive displacement pump are preferably adjusted by means of a control device and an electrically and/or temperature-active pump unit coupled to it, and preferably the elastomer body or the elastomeric lining is at least partially formed from an electroactive material and/or is coupled or equipped with at least one electroactive means and the elastomer body or the liner and / or the at least one electroactive means replaceable as sensors, wherein the Measurement signals for measurement value acquisition and/or processing are transmitted to a control device of the displacement pump.
  • an eccentric screw pump known that allows an axial adjustability of the rotor.
  • Various structural options are disclosed herein as to how an axial adjustment of the rotor and stator relative to one another can be made possible.
  • this document teaches that it is advantageous to temporarily widen the sealing gap between rotor and stator during operation in order to allow a targeted leakage flow. This reduces friction between the rotor and stator, which reduces wear.
  • the leakage current can advantageously be used for cooling. 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 invention solves the problem with an eccentric screw pump of the type mentioned at the outset by an infeed unit that is set up to set an infeed between the rotor and stator to a rest infeed in the idle state and to a working infeed in the working state, with the rest infeed being less than the working infeed.
  • the invention is based on the finding that, in the case of an eccentric screw pump that is idle for a longer period of time, such as several hours, days or even weeks now and then, relaxation of the elastomer material of the stator occurs at the contact points between the rotor and a stator made of an elastomer material can, in some cases even creep.
  • a preload is set between the rotor and the stator so that during operation, in which not inconsiderable back pressures can occur, adequate tightness and corresponding pump performance is ensured.
  • the stator is usually formed from a material which is resilient and which can yield in particular under sustained stress.
  • indentations are formed on the stator when the prestressing continues at the contact points between the rotor and the stator in the resting state, and these indentations can have a disadvantageous effect on the operation of the eccentric screw pump, particularly during start-up. Because when the progressing cavity pump starts up, which has been idle for a longer period of time, not only does the typical starting torque caused by friction have to be overcome, but also the bulge at the edges of the indentation in the material of the stator caused by the longer contact. This is particularly disadvantageous when motors with a limited torque are used as the drive motor.
  • the invention proposes reducing the preload between the rotor and stator in the idle state by changing the infeed from the working infeed to the inactive infeed and in the same way from a working preload to a rest preload and increasing it back to a working preload in the working state.
  • the problem of relaxation in the case of elastomeric stators in the rest state is reduced or completely avoided.
  • the eccentric screw pump can be started with the rest preload and after one or more revolutions, especially when the first fluid is already being pumped, the preload can be Change in delivery to the working preload can be increased. This also simplifies the start-up of the progressing cavity pump and makes it possible with a low torque.
  • the delivery between the rotor and stator is always reduced at rest.
  • the delivery is reduced from the working delivery to the idle delivery after the end of the operation of the eccentric screw pump.
  • the delivery is automatically set to the idle delivery in the idle state and automatically set to the working delivery in the working state.
  • the stator can also be in the form of a solid stator and can preferably be made of a metallic material.
  • no preload is set between the rotor and stator during operation, but rather a sealing line that is as complete or continuous as possible.
  • the rotor and stator heat up, which can lead to expansion.
  • the rotor and stator are usually made of different materials, so the thermal expansion can vary. With a close contact between the rotor and stator with a largely complete sealing line, it can cause tension when it cools down after operation occur, which can result in deformation of the components, up to and including the rotor seizing in the stator.
  • the resting bias is lower than the working bias.
  • the off-load bias is reduced by 10, 20, 30, 40, 50, 60, 70, 80, 90, 100% from the on-load bias.
  • the quiescent bias is set in such a way that a contact between the rotor and the stator is largely free of voltage.
  • a (largely) de-energized condition is understood to mean a state in which the rotor is only in contact with the stator due to its weight, but there is no pre-tension between the rotor and stator due to the infeed.
  • a complete sealing line is preferably not formed during the infeed at rest.
  • a complete sealing line is preferably formed between the rotor and the stator. At rest, the progressive cavity pump does not form a completely tight seal and fluid can flow through the progressive cavity pump from inlet to outlet or vice versa.
  • the control device preferably an electronic control device, is preferably part of the eccentric screw pump, but does not necessarily have to be integrated into a housing with it.
  • An external control device can also be provided, which is part of a control station or is connected to it, for example.
  • the progressing cavity pump preferably has a housing on which or in which a control box with the electronic control is accommodated.
  • the infeed unit is provided for setting the infeed between the rotor and stator in the rest state to the rest infeed and in the working state to the working infeed. This is preferably done automatically.
  • the delivery unit can be designed to receive a stop signal for the eccentric screw pump and to reduce the delivery from the working delivery to the idle delivery in response to the receipt of the stop signal. It can also be designed to receive a start signal for the eccentric screw pump and to increase the delivery from the idle delivery to the working delivery in response to the receipt of the start signal.
  • the electronic control device is provided both for controlling the drive motor and for changing the pretension.
  • the electronic control device can include the delivery unit, which can be embodied as a software module, for example.
  • the delivery unit can also include an electronic delivery control and preferably a delivery drive, which is controlled by the electronic delivery control to change the delivery.
  • the control unit for controlling the drive motor and the infeed controller do not have to be provided at the same place.
  • the control device for the drive motor is in the form of hard-wired switches.
  • the delivery unit automatically reduces the delivery from the working delivery to the idle delivery when the drive motor changes from the working state to the idle state. If, for example, an operator presses a start button on the eccentric screw pump, the electronic control unit controls the drive motor in such a way that it changes from the idle state to the working state and the rotor rotates.
  • the delivery unit increases the delivery from idle delivery to working delivery. If an operator then actuates a switch to stop the eccentric screw pump or if this is triggered by a higher-level control unit, the electronic control unit controls the drive motor in such a way that the rotor stops rotating and the drive motor changes from the working state to the idle state. At the same time, the delivery unit automatically controls the delivery in such a way that it is reduced from working delivery to idle delivery.
  • the delivery unit is preferably designed to set the delivery from the working delivery to the idle delivery in a run-out time range or thereafter.
  • the run-down time range preferably includes a change from the working state to the idle state.
  • the run-down time range is defined from a point in time at which a stop signal is received until the rotor comes to a complete standstill. It typically takes several to a few revolutions of the rotor for the rotor to come to a complete standstill after receiving a stop signal.
  • the delivery is preferably reduced from the working delivery to the idle delivery within this run-out time range.
  • the delivery unit is designed to adjust the delivery from the working delivery to the rest delivery when the rotor has come to a complete standstill, in particular immediately thereafter, or after a first predetermined rest period after the complete standstill has been reached .
  • the delivery from working delivery to idle delivery within 1, 2, 3, 4, 5, 10, 15, 20, 30, 60 seconds, or 1, 2, 3, 5, 10, 20, 30 minutes. It can be advantageous not to stop the infeed from the working infeed to the idle infeed immediately after the rotation has ended and the complete standstill has been reached, since it is possible that the eccentric screw pump will be put into operation again shortly afterwards and the rotor will be set in rotation.
  • a first predetermined idle time can be provided, which must first elapse before the delivery is reduced from the working delivery to the idle delivery. This is particularly useful if the pump is designed for a higher operating pressure.
  • the delivery unit is preferably designed to adjust the delivery from the idle delivery to the working delivery in a run-in time range or afterwards.
  • the running-in period preferably includes a change from the idle state to the working state. If the eccentric screw pump is in the idle state and the delivery is reduced from the working delivery to the idle delivery and the eccentric screw pump is now started in such a way that the rotor is to rotate, the delivery is also increased from the idle delivery to the working delivery.
  • the run-in time range can be defined as a time range, beginning with the receipt of a start signal until a target speed is reached. Within this run-in time range, the delivery is preferably also increased from the idle delivery to the working delivery.
  • the electronic delivery control can also receive a start signal from a higher-level control station and output a release signal to the control station when the delivery is in idle delivery.
  • the start signal and also the stop signal can also simply be looped through and the electronic delivery control receives this independently of the control station or the electronic control device for the drive motor and automatically adjusts the delivery according to the operating status.
  • the delivery unit is hydraulic. This is particularly preferred when the drive motor is also hydraulic.
  • the delivery unit includes a hydraulic path via which a hydraulic medium can be received, and a hydraulic drive, which is coupled to the rotor and / or stator for adjusting the delivery.
  • the rotor is tapered and preferably has a conical shape.
  • the rotor can also have varying eccentricities.
  • the rotor preferably tapers towards the outlet. It can also be preferred that the eccentricities decrease or increase toward the outlet.
  • the reverse configuration is also possible, with the rotor tapering towards the inlet and eccentricities increasing or decreasing towards the inlet.
  • the infeed can be adjusted by axially displacing the rotor and stator relative to one another.
  • the rotor and stator are conical, the rotor can be shifted toward the tapered end with respect to the stator to increase delivery.
  • the stator can be shifted toward the flared end of the rotor to increase delivery.
  • shifting the rotor can have certain structural advantages. When moving the stator, it is particularly important to ensure that the stator is still sealed off from the housing parts that are connected.
  • the rotor can be adjusted, for example, simply by using the in WO 2018/130718 achieve the measures described. These measures can also be combined.
  • the stator can be advanced radially in order to adjust the infeed between the working infeed and the rest infeed.
  • This embodiment is based on the idea that an infeed between the rotor and the stator can also be adjusted or increased by radially compressing the stator.
  • the stator comprises a support element and an elastomer part, with the support element completely enclosing the elastomer part at least in regions.
  • the support element is preferably formed from a metal and radially supports the elastomer part.
  • two adjustment elements to be provided on the stator, for example on the axial front ends of the stator, the distance between which can be varied.
  • a mechanical coupling and/or a connection is preferably provided between the setting elements and the stator, so that a change in the relative distance between the two setting elements can be used to change the cross section and the length of the elastomer part of the stator. So if the two adjustment elements are moved towards each other, for example, the elastomer part is axially compressed, whereby a radial expansion of the elastomer part occurs both radially outwards and radially inwards. Since the support element is provided radially on the outside, the axial compression of the elastomeric part causes only a radially inward expansion of the elastomeric part, so that the preload between rotor and stator is increased.
  • the axial length of the elastomeric part is preferably selected here such that the rest preload is set without compression of the elastomeric part or with the adjusting elements in a neutral position.
  • the invention achieves the object mentioned at the outset by a method of the type mentioned at the outset for controlling an eccentric screw pump, preferably an eccentric screw pump according to one of the above-described preferred embodiments of an eccentric screw pump according to the first aspect of the invention.
  • the method preferably comprises the steps: operating the progressing cavity pump in a working state comprising rotatingly driving a rotor in a stator of the progressing cavity pump with a working infeed between rotor and stator; outputting a stop signal, and in response to the stop signal: stopping rotating driving and changing to a rest state of the progressing cavity pump; and reducing the infeed between the rotor and stator from the working infeed to a rest infeed.
  • the stop signal can be provided, for example, by an operator of the eccentric screw pump, a higher-level control unit, a program part of the electronic control unit of the eccentric screw pump or the like.
  • An operator can, for example, use a button or a remote control to output the stop signal, which is then received at an electronic control unit of the eccentric screw pump and/or a drive motor of the eccentric screw pump.
  • Provision can also be made for a higher-level controller, such as a system controller, a control station or the controller of a vehicle to which the eccentric screw pump is attached, to output the stop signal.
  • an operating plan is laid in the electronic control unit of the eccentric screw pump itself, which causes the operation of the eccentric screw pump according to predetermined criteria, for example a schedule.
  • a stop signal can also be output, for example, by a sensor of the eccentric screw pump or an upstream or downstream unit.
  • the steps of stopping the rotary driving and reducing the infeed may be performed simultaneously or partially or fully sequentially. They preferably follow immediately after and in response to the issuance of the stop signal.
  • the eccentric screw pump remains in a position that corresponds to the idle position until the next time the eccentric screw pump is started.
  • the progressing cavity pump is always stored with the idle delivery when switched off. This achieves the advantages mentioned above and in particular avoids the relaxation due to a prestressed contact between the rotor and the stator.
  • the working position and the resting position are at least 1/50, 1/40, Spaced 1/30, 1/10, 1/5, 1 ⁇ 4 of the pitch of the rotor.
  • the resting bias is lower than the working bias.
  • the off-load bias is reduced by 10, 20, 30, 40, 50, 60, 70, 80, 90, 100% from the on-load bias.
  • the method comprises the steps of: outputting a start signal and in response to the start signal: starting to drive the rotor in rotation and changing the progressing cavity pump from the rest state to the working state.
  • the method comprises: increasing the infeed between the rotor and stator from the rest infeed to the working infeed.
  • the steps of beginning rotary driving and increasing infeed may be performed simultaneously, or performed partially or fully sequentially.
  • the invention achieves the object mentioned at the outset by a computer program comprising program codes, which, executed on an electronic control unit of an eccentric screw pump, preferably an eccentric screw pump according to one of the above-described preferred embodiments of an eccentric screw pump according to the first aspect of the invention, causes the electronic control unit to Carrying out a method according to any of the above preferred embodiments of a method according to the second aspect of the invention.
  • An eccentric screw pump 1 has a stator 2 and a rotor 4 .
  • the stator has a central axis L1 that extends 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.
  • in the in 1 shown embodiment is a stationary eccentric screw pump, which is in particular permanently installed in a system.
  • the inlet pipe 18 can merge into another pipe, for example sewage pipe, and the outlet pipe merge into another further pipe or a collection tank.
  • a drive shaft 26 extends through the inlet housing 14 and is connected to the rotor 4 via a first cardan joint 28 and is connected to an output shaft 32 of a transmission 34 via a second cardan joint 30 .
  • the transmission 34 is connected on the input side to a drive motor 36, which according to this embodiment as Electric motor is formed.
  • the drive motor 36 can also be connected directly to the output shaft 32 without the interposition of a gear 34 .
  • the drive motor 36 can also be arranged at a distance or axially offset from the output shaft 32 and/or the transmission 34 and can be connected to this or this, for example, via a belt drive.
  • Another alternative is the drive motor 36 as a hydraulic machine 204 (cf. 6 ) formed, for example as a gerotor motor.
  • the eccentric screw pump 1 has an infeed unit 39 for adjusting the infeed between the rotor 4 and the stator 2 .
  • the infeed unit 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 L1 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 feed unit 39 has an engagement section 44 which is connected to a feed drive provided for this purpose (in 1 not shown) may be related.
  • Figures 2a - 2c show a delivery between the rotor 4 and the stator 2, which corresponds to a working delivery and in which there is contact between the rotor 4 and the stator 2, illustrate the Figures 3a - 3c a rest infeed with an extension such that a gap S is set.
  • Figure 2b shows a section along the longitudinal axis L1, 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 L1.
  • Figure 2a shows a section close to 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 working infeed which is a working preload between the rotor 4 and the stator 2 here, ensures that the sealing line D is essentially continuous during operation.
  • 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 particular at points with more punctiform contact or a smaller contact area compared to points with more extensive contact.
  • Figure 2b are the working position PA and in Figure 3b the rest position PR of the rotor 4 applied relative to the stator 2.
  • the working position PA and the rest position PR are spaced apart by 1 ⁇ 4 of the pitch of the rotor 4 (the distance between two peaks or two valleys on average is understood as pitch). This distance is usually sufficient to ensure a safe rest delivery.
  • Figures 2a-2c can be seen, particularly at points where the contour of the rotor runs in the opposite direction to the contour of the stator (in Figure 2b especially at the points that are denoted by 7, D in the lower area) a high pressure.
  • the invention provides that the infeed and thus also the preload between the rotor 4 and stator 2 in the rest state is set to the rest infeed or rest preload and in the working state to the working infeed or work preload, with the rest infeed or rest preload being lower as the work delivery or work preload.
  • the eccentricity e1, e2 is in this embodiment ( Figures 2a-3c ) constant while the diameter D1, D2 of the rotor 4 decreases towards the outlet 12. That is, e1, and e2 are identical, while D1, is greater than D2. However, it also includes embodiments in which the diameter is constant, ie D1 is identical to D2, and the eccentricity changes, ie, for example, that e1 is greater than e2. The effect of axial displacement is then corresponding. It is also possible that both the diameter and the eccentricity are changed over the length.
  • the infeed and thus the preload can also be adjusted by pressing the stator 2 in the axial direction in order to generate a radial expansion of the stator 2 in this way.
  • adjustment elements (not shown here) can be provided, for example, on axial front ends of the stator, the distance between which can be varied, with there being a mechanical coupling and/or connection between the adjustment elements and the stator, so that by changing the relative distance between the two adjustment elements a change in the cross section and the length of the elastomer part of the stator can be brought about.
  • the adjustment elements can be designed, for example, as circular pressure plates that are connected to one another by means of tie rods. It is also possible to integrate electroactive polymers into the stator 2, which cause a radial expansion of the stator 2 when a voltage is applied.
  • the infeed unit 39 is designed in such a way that the rotor 4 can be displaced axially, including the complete drive train 25, which, according to this exemplary embodiment, consists of the drive shaft 26, the gearbox 34 and the drive motor 36, even if all three of these elements are optional .
  • 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 .
  • the drive motor 36 can also be mounted on the section 48 directly or by means of a motor mount.
  • a separate feed drive 52 is provided for this purpose, which drives the drive train 25 (or only the drive motor 36 if no gear 34 is provided) via a spindle drive 54 (shown only schematically). is) can move so that the delivery between the rotor 4 and the stator 2 can be adjusted from the working delivery to the idle delivery and vice versa.
  • an electronic delivery control 53 is preferably connected to an electronic control device 58 of the eccentric screw pump 1 or of the drive motor 36 via a signal line 56 .
  • the drive motor 36 is also connected to the electronic control device 58 via a signal line 60 .
  • the electronic control device 58 can be part of a control station, for example, or receives via a reception or input interface 200, via which control or regulation data is entered or received, and is designed to carry out the control or regulation as a function of this control or regulation data. For example, a target volume or a difference between a target volume and an actual volume can be entered into the electronic control device 58 via this input interface 200 .
  • the input interface 200 can be a user interface or an interface to a superordinate unit, such as a control station.
  • an input connection 202 can be provided for connecting a sensor, switch and/or higher-level control unit.
  • the electronic delivery controller 53 receives a start signal from the electronic control unit or directly from a higher-level unit, which causes the drive motor 36 to start and automatically controls the delivery drive 52 based on this, which then adjusts the delivery to the working delivery.
  • the electronic delivery control 53 also receives a stop signal, which causes the drive motor 36 to stop and automatically controls the delivery drive 52 based on this, which then sets the delivery to the idle delivery.
  • the electronic control unit 58 and the delivery controller 53 can also be integrated into one controller.
  • 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 should be understood that with reference to 4 described electronic control device 58 also in the eccentric screw pump 1 according to figure 5 is provided.
  • 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 .
  • the output shaft 32 is mounted in the transmission 34, in particular in an output gear wheel 68 of the transmission 34, so that it can be displaced axially.
  • 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 output shaft 32 can be displaced.
  • gearwheel 68 can also be slidably connected in the transmission 34 and rigidly connected to the output shaft 32 .
  • 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 eccentric screw pump 1 initially not designed as a stationary pump, but is part of an agricultural trailer that carries a liquid manure tank 206.
  • the slurry tanker 206 is connected to the inlet pipe 18 .
  • the outlet tube 24 is connected to a manifold 208 and a dribble bar linkage 210 .
  • An eccentric screw pump is particularly suitable for pumping liquid manure, since liquid manure has solid components and is therefore not easily pumpable.
  • Hydraulic machine 204 may be connected to a hydraulic source (not shown; see Fig 8 and 9 ) of the agricultural trailer must be connected and thus supplied with hydraulic medium under pressure.
  • the hydraulic machine 204 can in one example as well as the drive motor 36 according to the embodiment of FIG 4 be slidably mounted on the pump housing 14 and be axially displaced via a drive 52 to move the rotor 4 to the working position PA ( 6 ) and the rest position PR ( 7 ) to spend in order to be able to set the working delivery or working prestress and rest delivery or rest prestressing.
  • the delivery drive 52 is then in turn connected to the electronic delivery control 53 (in 6 , 7 Not shown).
  • the hydraulic machine 204 can be driven solely via the pressure provided, so that the electronic control device 58 does not directly control the hydraulic machine 203, but rather a hydraulic pump (not shown here) for providing a hydraulic pressure.
  • a hydraulic output shaft 212 is displaceably mounted in the hydraulic machine 204 .
  • the hydraulic output shaft 212 is then in turn connected to the drive shaft 26 via the second cardan joint 30 .
  • the hydraulic output shaft 212 is therefore slidably mounted in a hollow shaft of the hydraulic machine.
  • a hydraulic pump 220 forms a hydraulic pressure source here. This is connected via a directional valve 224 to a first hydraulic line 226 and a second hydraulic line 228 and supplies them with hydraulic pressure.
  • the first hydraulic line 226 leads to the hydraulic machine 204, which is initially connected to a transmission 34 in the exemplary embodiment shown here.
  • the transmission 34 is as with reference to FIG figure 5 described equipped with a hollow shaft through which the output shaft 32 runs axially displaceable. As soon as the directional control valve 224 switches, hydraulic medium is conveyed and the hydraulic machine 204 drives the output shaft 32 .
  • the infeed unit 39 includes the second hydraulic line 228 and a hydraulic drive 230 which forms the infeed drive 52 .
  • the hydraulic drive 230 is here a hydraulic lifting cylinder 232 with a cylinder chamber 234 and a piston 236, which in turn is connected to the output shaft 32, preferably with the interposition of an axial bearing, and the output shaft 32 can move axially.
  • a return spring 238 is provided, which the piston 236 with respect to 8 charged to the left. The return spring 238 is therefore used to Adjust delivery to the rest delivery, and the pressure in the cylinder chamber 234 delivery can be adjusted to the working delivery.
  • a throttle 240 is provided in the second hydraulic line 228, which is used to reduce the volume flow somewhat in order to achieve the desired travel speed and thus time for the travel from the rest position to the working position and vice versa.
  • the delivery is always automatically set to the working delivery and the idle delivery.
  • the directional valve 224 switches, hydraulic pressure is supplied to the hydraulic machine 204, which subsequently drives the rotor 4, but also to the hydraulic drive 230, which then adjusts the delivery to the working delivery. If the directional control valve 224 is switched in such a way that the hydraulic machine is at a standstill, the return spring 238 ensures that the infeed is set to the rest infeed.
  • the rotor 4 is displaceable, while the stator 2 is stationary in the inlet housing 14 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 purpose of the expansion member 80 is to allow the axial length of the drive shaft 26 to be changed by shifting the second shaft part 76 relative 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 a spindle, a piston, a movable magnetic core, electroactive polymers or the like, which enable movement by activation.
  • An electrical connection can be implemented via the output shaft 32 or implemented inductively and/or by radio.
  • a sliding contact can also be considered.
  • FIG. 11 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 four embodiments figures 1 , 4 , 5 and 6 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 .
  • Sections 84 and 86 are telescopically nested and within section 84 is an expansion member 80, corresponding to expansion member 80 in FIG 10 , educated.
  • a drive which displaces the rotor 4 axially, acts on the end face 88 of the rotor 4 .
  • the fact that the value F0 does not lie on the abscissa does not necessarily mean that the rest delivery or rest preload is positive; rather, the rotor 4 and stator 2 cannot touch at all or only marginally, so that the stator 2 is completely or essentially stress-free .
  • the rest infeed or rest prestressing F0 should be selected such that there is essentially no relaxation and no creeping of material of the stator 2 at contact points with the stator 2 or a sufficiently large gap is set if it is a solid stator.
  • a start signal is output, for example via the input interface 200.
  • the electronic control device 58 controls the drive motor 36 and this drives the rotor 4, which begins to rotate.
  • the speed n of the rotor 4 increases up to the target speed nN, which is reached at the time tn2.
  • the working condition (in terms of speed) is also reached here.
  • the period of time between tn1 and tn2 can be referred to as the warm-up time range, run-up time range or start-up time.
  • the delivery F is partially increased within the run-in time range from the idle delivery F0 to the working delivery FB. This is done automatically by the delivery unit 39, also in response to the start signal.
  • a time interval is provided between the point in time tn1 and a point in time tF1 at which the infeed unit 39 begins to increase the infeed F, for example by axially adjusting the rotor 4 .
  • This is not absolutely necessary, it could also be provided that the times tn1 and tF1 coincide, or tF1 is before tn1.
  • the latter is particularly preferred when the rotor 4 is placed on the stator 2 and the weight of the rotor 4 on the stator 2 causes a certain relaxation at the contact points. In this case, it is preferred, for example, to initially move the rotor 4 a little axially before the rotation of the rotor 4 is started.
  • Time tF1 is preferably after time tn2, preferably offset by a predetermined waiting time of, for example, 1, 2, 3, 5, or 10 seconds.
  • a predetermined waiting time for example, 1, 2, 3, 5, or 10 seconds.
  • the gradient of the infeed is lower than the gradient of the speed. This is also not necessary and these can be adapted and selected according to the operating mode, pump fluid, material and material pairing.
  • a stop signal is output at time tn3, for example again via the input interface 200.
  • it can also be an automatically generated stop signal, for example due to the time difference between tn2 and tn3 or due to a sensor signal.
  • the speed n of the rotor 4 is reduced again by the electronic control device 58 and falls here with the same gradient with which it also rose. Again, this is not mandatory and the gradients can differ. In particular, it is often preferred that standstill is reached as quickly as possible.
  • the delivery unit 39 reduces the delivery F from the working delivery FB to the idle delivery F0.
  • the idle delivery F0 is then reached at time tF4, which is after time tn4.
  • the period between tn3 and tn4 can be referred to as the run-down period.
  • the change in infeed F from working infeed FB to idle infeed F0 is therefore partly in the run-out time range.
  • the areas can also completely overlap, tF3 can coincide with tn3 and tF4 with tn4.
  • Time tF3 can also be before time tn3 or before time tn4. It is also conceivable and preferred if time tF4 is before or after time tn3 and/or before or after time tn4.
  • a latency can also be provided between tn3 and tF3 if a start signal is received again shortly after the stop signal has been output (at tn3).
  • This latency can be specified for each specific application and can be several seconds or minutes.

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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)
EP22209222.3A 2021-11-30 2022-11-23 Pompe à vis sans fin excentrique avec sortie de travail et sortie au repos et procédé de commande de la pompe à vis sans fin excentrique Pending EP4187095A1 (fr)

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DE102021131427.5A DE102021131427A1 (de) 2021-11-30 2021-11-30 Exzenterschneckenpumpe mit Arbeitszustellung und Ruhezustellung sowie Verfahren zum Steuern der Exzenterschneckenpumpe

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EP (1) EP4187095A1 (fr)
JP (1) JP2023081354A (fr)
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DE102022134734A1 (de) 2022-12-23 2024-07-04 Ruhr-Universität Bochum, Körperschaft des öffentlichen Rechts Verfahren zur Steuerung einer Exzenterschneckenpumpe
CN117023013A (zh) * 2023-08-16 2023-11-10 无锡恒信北石科技有限公司 一体式输送结构及包含该结构的控制装置及方法

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CA3181528A1 (fr) 2023-05-30
US12129851B2 (en) 2024-10-29
MX2022014206A (es) 2023-06-01
US20230167818A1 (en) 2023-06-01
CN116201727A (zh) 2023-06-02
KR20230081669A (ko) 2023-06-07

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