EP3610154B1 - Pompe à vis excentrique - Google Patents

Pompe à vis excentrique Download PDF

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Publication number
EP3610154B1
EP3610154B1 EP18724439.7A EP18724439A EP3610154B1 EP 3610154 B1 EP3610154 B1 EP 3610154B1 EP 18724439 A EP18724439 A EP 18724439A EP 3610154 B1 EP3610154 B1 EP 3610154B1
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EP
European Patent Office
Prior art keywords
stator
rotor
eccentric screw
screw pump
pump
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.)
Active
Application number
EP18724439.7A
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German (de)
English (en)
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EP3610154A1 (fr
Inventor
Josef Hauck
Hisham Kamal
Reinhard Denk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme GmbH
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Publication date
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Publication of EP3610154A1 publication Critical patent/EP3610154A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2/1076—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 orbits or wobbles relative to the other member which rotates around a fixed axis
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]

Definitions

  • the present invention relates to an eccentric screw pump, in particular a wobble pump, according to the features of the preamble of claim 1.
  • Eccentric screw pumps are pumps for pumping a variety of media, especially viscous, highly viscous and abrasive media such as sludge, liquid manure, petroleum and fats.
  • Eccentric screw pumps known from the prior art are formed from a rotor and a stator, with the rotor being accommodated in the stator and moving eccentrically in the stator.
  • the stator has an inner side that is coiled in the shape of a snail. From the movement of the rotor and the mutual contact of the stator and rotor in so-called sealing areas or sealing contact surfaces, migrating conveying chambers are formed between the stator and the rotor, by means of which liquid media can be transported along the stator.
  • the rotor performs an eccentric rotary movement around the longitudinal axis of the stator or around the longitudinal axis of the progressing cavity pump.
  • the outer worm ie the stator, has, for example, the form of a two-start thread, while the rotor worm has only one thread.
  • progressing cavity pumps are suitable for pumping water, petroleum and a large number of other liquids.
  • the shape of the pumping chambers is constant during the movement of the rotor within the stator, so that the pumped medium is not squeezed. With the right design, not only fluids but also solids can be pumped with progressing cavity pumps.
  • the pumping efficiency of an eccentric screw pump is particularly determined by the quality of the seal between the pressure chambers or pumping chambers of the stator and the profile of the displacing rotor, which is achieved in particular by the pressure chamber walls of the stator a preload in the sealing areas or in the area of the sealing contact surfaces can be pressed elastically onto the rotor.
  • This initial overlap is necessary in particular in order to prevent the pump pressure that builds up when the eccentric screw pump is started from pressing the elastically deformable material of the stator radially outwards. If this overlap is missing, the frictional contact between the rotor and the stator is lost as a result of the pump pressure building up.
  • Coverage means in particular that the outer dimensions of the rotor in the contact areas or along the sealing areas or sealing contact surfaces between the rotor and stator is larger than the inner dimensions of the stator.
  • eccentric screw pumps which have an unreinforced elastomer stator. These are usually progressing cavity pumps in which the stator is surrounded by a pressure medium.
  • the stator is fixed within the eccentric screw pump, while the other end of the stator is arranged so that it can swing freely. This enables the stator to absorb the eccentric movement of the rotor-stator system.
  • the stator is surrounded by the pumped medium.
  • the conveying direction is selected in such a way that the conveying medium surrounding the stator has the pressure on the pressure side of the eccentric screw pump.
  • the stator is pressed onto the rotor by the resulting pressure difference between the pumping chambers connected to the suction side and the pressure on the pressure side on the outer surface of the stator. Comparatively high pressures can thus be generated even with very soft stators.
  • These eccentric worm pumps are referred to in particular as wobble pumps.
  • wobble pumps There are two types of wobble pumps. Some are articulated and others are non-articulated.
  • the axis of the flexible rubber stator describes a cylinder shape, ie the stator is pushed away to the side.
  • the eccentric movement between the rotor and stator (eccentricity) is compensated for by the fact that between the stationary axis of the drive shaft and the rotor worm a cardanic joint for torque transmission is arranged.
  • the stator is flexibly clamped at the opposite end, which allows a further cardanic degree of freedom.
  • the eccentricity e can be compensated for by the distance between these two cardanic degrees of freedom, each with an angle ⁇ .
  • the axis of the stator essentially describes a cone shape.
  • a particular disadvantage is that due to the contact between the rotor and stator with overlap along the sealing areas or sealing contact surfaces, a high breakaway torque has to be overcome when the eccentric screw pump is started up.
  • the drive used for the rotor must be dimensioned sufficiently to apply the appropriate force for breaking loose the eccentric screw pump and accelerating the eccentric screw pump over the low speed range.
  • U.S. 2,826,152 A discloses an eccentric screw pump that includes a stator with a bellows-shaped section that is fixed to the annular web by means of the housing.
  • a rotor is provided within the stator and is operatively connected to the stator.
  • a screw pump having a housing. Inside the housing, a shaft is provided with a sleeve-like part which contacts an inner sleeve portion of a flexible sleeve. The diameters of the two frictionally engaged surfaces are chosen so that an appropriate contact can take place.
  • U.S. 6,358,027 discloses a progressive cavity pump capable of draining fluid by axial displacement of the rotor at rest to facilitate pump starting.
  • the object of the invention is to provide an eccentric screw pump, in particular a wobble pump, whose starting when it is put into operation is improved.
  • the invention relates to an eccentric screw pump, in particular a wobble pump, for pumping fluid or free-flowing conveyed media from a suction side to a pressure side.
  • the wobble pump comprises an inner pump part and an outer pump part, for example the wobble pump comprises a rotor as the inner pump part and a stator, in particular a wobble stator, as the outer pump part.
  • the outer pump part is arranged to rotate, while the inner pump part is fixed.
  • a further embodiment can provide that the inner and the outer pump part are arranged to rotate in opposite directions.
  • the progressive cavity pump comprises a rotor and a stator.
  • the rotor of the wobble pump is connected to a drive shaft and thus to the drive via a joint.
  • the joint can also be connected directly to the motor shaft of the drive.
  • the stator is designed to be flexible and is fixed on one side, particularly on the suction side, to the housing of the eccentric screw pump or pump housing, while the other end of the stator is arranged in a freely swinging manner within the pump housing and can thus absorb the eccentric movement of the rotor.
  • wobble pumps are preferably spoken of in order to describe such an eccentric screw pump.
  • the stator is preferably designed to be flexible, for example it can consist of an elastomeric material.
  • the stator and the rotor of the wobble pump are brought into contact along what are known as sealing lines or sealing areas, so that pumping chambers for the pumped medium that are separate from one another are formed.
  • the wobble pump When the wobble pump is at rest, on the other hand, there is no sealing contact between the rotor and the stator, at least in some areas, in the sealing areas or in the area of the sealing contact surfaces.
  • the stator which is also referred to below as the wobble stator, is at least partially and/or essentially completely surrounded by the pumped medium in an operating state of the wobble pump or working mode of the wobble pump. This causes pressure on the outer surface of the stator.
  • the stator is pressed radially against the rotor and brought into sealing contact with it, particularly in the sealing areas or in the area of the sealing contact surfaces, as a result of which adjacent pumping chambers for the pumped medium are formed that are separate from one another.
  • wobble pump in which the outer pump part is designed as a wobble stator and the inner pump part is designed as a rotor. It goes without saying It goes without saying that the person skilled in the art can apply this analogously to wobble pumps that have a static inner pump part and a rotating outer pump part or to wobble pumps in which the inner and outer pump parts are designed to rotate in opposite directions.
  • the flexible area on the wobblestator which is responsible for compensating for the eccentricity, is one of the most heavily loaded areas of the wobblestator.
  • the constant bending of the wobble stator results in tensile or compressive forces or shearing forces in this area.
  • the operating torque and the axial force due to the differential pressure can also cause tensile, compressive or shear forces.
  • the drive torque creates high shear stresses on the wobble stator. It is known that elastomers can withstand tensile and shear forces for a long time if the elastomeric material is "prestressed" or compressive stresses are introduced.
  • the eccentric screw pump according to the invention with a wobble stator and with play between the wobble stator and the rotor which is formed at least in certain areas in the idle state thus has flexible areas in the wobble stator which, at higher torque loads, have a higher pretension to match. Due to the play, the starting torque is approximately zero and the operating torque is also very low at small differential pressures.
  • the rotor has, at least in some areas, smaller external dimensions than the wobble stator has internal dimensions.
  • no sealing contact is formed between the rotor and the wobble stator in the idle state along an area that corresponds approximately between 50%-100% of the sealing areas or sealing contact surfaces.
  • this area there is play or a distance between the rotor and the wobble stator.
  • the wobble pump has a suction side with a suction-side pressure.
  • the pumped medium entered the wobble pump via an inlet and is transported through the pumping chambers between the wobble stator and the rotor to the pressure side.
  • Inside the wobble pump there is a first suction side pressure on the suction side and a second pressure side pressure on the pressure side.
  • the pressure builds up from the suction side towards the pressure side.
  • pumping chambers are created which, depending on the current angle of rotation between the rotor and the wobblestator, essentially have either the suction pressure or the pumping pressure of the wobble pump.
  • suction-side pressure In the case of a single-stage wobble pump, you can see pumping chambers that have the suction-side pressure and other pumping chambers that have the pressure-side pressure in a snapshot.
  • the stator is pushed outwards by pressure differences between the pumping chambers; the pumped medium tries to push the stator outwards so that it can flow into a lower-pressure pumping chamber.
  • This outward pressure is roughly the same anywhere on the stator.
  • This radially outward pressure within the pumping chambers causes the elastomeric wobblestator to be forced radially outward.
  • the external pressure is thus applied by the pumped medium conveyed to the pressure side, so that the free end of the wobble stator, which is freely arranged within the pump housing, is flushed with the pressure on the pressure side and this results in a radial pressing of the stator on the rotor and a sealing contact between the stator and the rotor in the area of the sealing contact surfaces.
  • the wobble pump when the wobble pump is in the idle state, there is a first clearance between the rotor and the wobblestator on the suction side and a second clearance between the rotor and the wobblestator on the pressure side.
  • the first game on the suction side is larger than the second game on the pressure side.
  • the idle state there is no differential pressure between the suction side and the pressure side via the wobble pump.
  • the wobblestator becomes in the area of the pressure side pressed less strongly on the rotor than on the suction side. In one embodiment, in which there is less play between the rotor and the wobblestator on the pressure side than on the suction side when at rest, this can be compensated for better so that the frictional contact between the wobblestator and the rotor along the sealing areas or sealing contact surfaces in the essentially the same everywhere.
  • the geometry of the rotor and/or the wobblestator is therefore selected in such a way that the preload between the rotor and the wobblestator is reduced on the suction side compared to the pressure side.
  • the clearance between the rotor and wobblestator can decrease substantially continuously along the sealing areas or sealing contact surfaces between the rotor and the wobblestator from the suction side to the pressure side in order to compensate for the pressure difference increasing from the suction side to the pressure side.
  • an annular space, into which the pumped medium flows, is formed at least in regions on the pressure side between the wobble stator and the pump housing.
  • the pumped medium in the annular space thus presses on the outer surface of the wobble stator with pressure on the pressure side.
  • Eccentric screw pumps with stators clamped on both sides are already known, in which pumping medium is used to generate sufficient contact pressure between the stator and rotor during operation.
  • a dead space is formed in the supply line of the pumped medium to the stator and around the stator.
  • deposits can form within these dead spaces, which then block and/or destroy the corresponding components within a relatively short time.
  • the prior art already provides a solution here, whereby the contact pressure between the rotor and a stator clamped on two sides can be adapted to the differential pressure.
  • the differential pressure between the fluid on the pressure side and the interior of the stator is not the same everywhere.
  • the pressure inside the stator clamped at two ends and the surrounding pressure of the pressure-side fluid are approximately the same.
  • the suction pressure is essentially the same inside the stator, which results in a very high pressure difference compared to the fluid on the pressure side.
  • the mobility of the stator is restricted on one side.
  • the stator is clamped at the suction-side end and has limited mobility in this area.
  • the wobble stator at the pressure-side end can move radially without restriction. If the contact pressure force is calculated as a function of differential pressure and radial stability, the wobblestator is evenly pressed against the rotor over large areas of the stator length due to an advantageous distribution of the contact pressure forces.
  • the one-sided clamping of the stator takes place at the end, for example directly via an annular widening formed at the free end of the stator.
  • a rim can be formed, which is used to fasten the stator to the pump housing.
  • the pressure difference of the wobble pump during operation results in a high axial force on the stator in the opposite direction to the conveying direction, ie directed away from the drive of the rotor.
  • end-side, one-sided clamping especially with direct end-side Clamping or clamping at the end with a flange creates a compressive stress in the elastomer at the highly stressed bending point due to the axial force. This is advantageous for the service life of the stator material.
  • the clamping point of the wobblestator is less heavily loaded in the wobble pump according to the invention, since the torque is only applied when a superimposed compressive stress is formed.
  • wobble stators are limited in their speed.
  • wobble stators can only be operated at lower speeds, since excessive speeds result in strong vibrations that can damage parts of the wobble pump. It has been proven that clearance between the rotor and the wobble stator results in lower vibrations.
  • a wobble pump according to the invention can thus be operated at higher speeds than conventionally known wobble pumps. This advantageous reduction in the vibrations results from the lower drive torques due to the play formed between the rotor and the wobble stator, since the oscillatable system is less strongly excited in the rotational direction.
  • variable-speed pumps with a given output, such as solar pumps only low differential pressures can be overcome at high speeds. This means that in the case of wobble pumps with play formed between the rotor and the wobble stator in the idle state, there is only a small drive torque. The excitation of the oscillatable system is thus even lower.
  • the advantage of a wobble stator described here with play in relation to the rotor also lies in the fact that such a stator can be made shorter than a stator clamped in at two ends. Since there is no second clamping point, the inlet side and the pressure connection can be accommodated in the same installation space of the pump housing. In particular, the pressure connection can be implemented at least partially in the stator area.
  • the wobble stator can have a spiral-shaped outer contour, which corresponds in particular to the spiral-shaped inner contour.
  • a wobble stator can be produced more cost-effectively, since less material is required and the vulcanization time is shortened due to the reduced wall thickness, so that production is faster and more stators can therefore be produced in a defined period of time.
  • the stability of such a wobble stator is more uniform in the circumferential direction.
  • a joint for a wobble pump which comprises a reinforced elastomer part.
  • Various articulated shafts for eccentric screw pumps in the form of fiber or wire-reinforced plastic or elastomer bodies are known. These serve to compensate for the eccentric movement between a fixed stator and a fixed drive shaft.
  • the disadvantage of the articulation designs known from the prior art is that a large, flexible length is required to compensate for the axial offset. As a result, there is a tendency for lateral vibrations at higher speeds. These vibrations reduce the life of the joint and result in unwanted noise and harmful vibrations.
  • an internal support structure in the form of a shaft, a tube, a spring or a granulate is required to transmit significant pressure forces (in the conveying direction away from the motor). All of these support structures result in undesirable friction and wear in and/or on the joints.
  • the advantageous vibration properties and the ability to transmit compressive forces of the short joint body can be combined with the inner support bodies known from the prior art or with additional outer support bodies.
  • Supporting bodies can be e.g. a sphere, granules, a spiral spring, a cylindrical shaft piece or a flexible elastomer or plastic body.
  • the combination of support body with a lubricant is recommended here.
  • a more or less viscous supporting liquid can also be used.
  • the joint comprises an at least partially movable central part which is formed from a reinforced elastomeric or plastic material.
  • the reinforcement of the elastomer or plastic material is preferably formed by a fiber reinforcement or wire reinforcement integrated into the material.
  • the actual articulated body consists of a commercially available hydraulic hose or another suitable hose with an internal reinforcing structure.
  • the hose or hydraulic hose consists, for example, of a flexible material, for example elastomer or the like, which is reinforced in one or more layers with reinforcements that are preferably crossed in the shape of a cross.
  • the reinforcement can be made of steel, plastic fibers or textile fibers.
  • the center piece is bordered on both sides by connecting pieces for fastening the rotor and/or the drive shaft.
  • a connecting piece is attached to each of the two free ends of the hose piece.
  • the two connection pieces are preferably designed with retaining grooves in the axial direction and/or possibly also in the radial direction.
  • the connecting pieces preferably have an n-edged area, where n corresponds to the number of jaws on the hose press used later (hose presses usually have six or eight jaws).
  • the connecting pieces each comprise, for example, a sleeve for holding the respective end of the hose piece. The sleeves are compressed using a hose press so that the hose is fixed between the two connectors.
  • the n-edged area on the connecting piece is angled with the jaws of the Align hose press. After pressing, a secure connection is created between the respective connection piece and the respective sleeve and thus also a secure connection between the respective connection piece and the respective free end of the hose piece.
  • connection piece instead of an n-edged area on the connection piece, a thin cylindrical area can also be used. During the pressing process, this thin area can then also be brought into the n-edged shape.
  • At least two sleeves are pressed simultaneously in a suitable jaw construction. Due to the n-edged compression between the sleeve and the connection piece, a higher moment can be permitted for the construction, since a relative movement between the hose and sleeve as well as between the hose and the connection piece must take place at the same time for the hose to slip.
  • the n-edged shape on the outside can also be used as a gripping surface for tools, for example if detachable threads are used to connect to the neighboring parts.
  • a sealing and/or adhesive compound can also be used, which is particularly effective between the free ends of the hose piece and the respective sleeve is introduced.
  • connection piece can possibly be dispensed with.
  • grub screws may be used herein to provide external threads.
  • An advantage of using a joint between the rotor and the drive is that the rotor can thus be positioned within the stator that the clearance between stator and rotor is the same everywhere along the pressure areas.
  • a further embodiment of a wobble pump can provide that the rotor-stator system has an inlet-side end section in which an inlet funnel free of sealing lines is formed between the stator and the rotor along a funnel length, the helical inner peripheral surface of the stator being in a central main section of the rotor Stator system and is formed in the inlet-side end portion.
  • the inlet funnel is designed in such a way as in the application with the reference number DE 10 2016 009 028 is described.
  • Such an inlet funnel which on the one hand comprises a continuation of the helical inner peripheral surface of the stator and on the other hand is free of sealing lines, achieves advantageous flow effects.
  • the invention thus relates to eccentric screw pumps with an unreinforced elastomer stator, with the delivery medium surrounding the stator serving as pressure medium in order to create the sealing contact between the rotor and stator during ongoing pump operation.
  • the stator can also be supported by inserts of a largely rigid material, with the flexible one-sided clamping point having to be retained.
  • a certain differential pressure arises, as a result of which the wobble stator is pressed onto the rotor by the delivery medium acting on the wobble stator from the outside with pressure on the pressure side, resulting in a real separation of the pressure side from the suction side of the wobble pump due to the forced solid-body contact between the rotor and the stator.
  • This offers various advantages.
  • a wobble pump according to the invention with a gap between the stator and rotor can easily break away, since there is still no differential pressure when the wobble pump is at a standstill.
  • the differential pressure between the interior and the exterior of the wobble stator only builds up with increasing speed and thus closes the sealing contact at so-called sealing areas or sealing contact surfaces.
  • the wobble pump according to the invention can thus be used advantageously as a photovoltaically operated water pump.
  • breaking loose of the wobble pump and accelerating the wobble pump over the low speed range are critical, since the motor torque available is lower compared to mains-connected pumps.
  • the amount of energy available and thus the driving force also depends on the amount of light available and/or the angle of incidence of the solar radiation.
  • the position of the sun plays an important role. The sun's rays, which are still weak and falling very obliquely on the photovoltaic panels in the morning, provide little energy, which again leads to reduced engine torque.
  • FIG 1 shows a schematic view of an eccentric screw pump 1, in particular a wobble pump 2, in a state of rest and figure 2 shows the eccentric screw pump 1 in an operating state AZ.
  • the eccentric screw pump 1 comprises an elastomeric stator 3 with an inner side which is coiled in the shape of a snail and a rotor 4 .
  • the stator 3 has one more thread than the rotor 4 .
  • the rotor 4 is accommodated in the stator 3 .
  • the rotor 4 and the stator 3 form the rotor-stator system 11.
  • the rotor-stator system 11 is arranged in the pump housing 6, with an annular space 12 being formed between the pump housing 6 and the outer lateral surface of the stator 3.
  • the rotor 4 is coupled to the drive shaft 7 of a drive (not shown), for example an electric motor, and rotates about the longitudinal axis of the stator or about the longitudinal axis L of the eccentric screw pump 1 and at the same time performs a circular translation determined by the eccentricity e of the rotor-stator Systems 11. This means that the rotor 4 moves eccentrically in the stator 3.
  • a drive for example an electric motor
  • the rotor 4 is coupled to the drive shaft 7 via a universal joint 5 .
  • the cardanic joint 5 compensates for the eccentric movement or eccentricity e between the rotor 4 and the stator 3 by torque transmission.
  • the free end 8 of the stator 3, which is opposite the cardanic joint 5, is fixed on one side to the pump housing 6 of the eccentric screw pump 1, in particular flexibly clamped. This leaves another gimbal degree of freedom to.
  • the eccentricity e can be compensated for by the distance between these two cardanic degrees of freedom, each with an angle ⁇ .
  • the axis of the stator essentially describes a cone shape.
  • the free end 8 of the stator 3 has, for example, an annular widening 9 for fixing to the pump housing 6, which is held on the pump housing 6, for example by clamping. If necessary, the annular widening 9 can serve as a flange 10, via which the stator 3 can be connected to the pump housing 6, for example screwed.
  • the stator 3 and the rotor 4 are dimensioned such that in a first idle state according to RZ figure 1 of the eccentric screw pump 1 along the at least two sealing contact surfaces 14 between the rotor 4 and the stator 3 at least in some areas a game 100 or distance is formed.
  • the rotor 4 has, at least in some areas, smaller external dimensions A(4) than the stator 3 has internal dimensions I(3).
  • the pumped medium FM enters the eccentric screw pump 1 via an inlet 15 and is transported by the moving pumping chambers FR formed by the movement of the rotor 4 and the mutual contact of the stator 3 and rotor 4 on the sealing contact surfaces 14 from the suction side S to the pressure side D of the eccentric screw pump 1 transported in the conveying direction TR.
  • the pumped medium FM is discharged from the eccentric screw pump 1 via the outlet 16 and fed to its further use or processing.
  • the conveying medium FM is pumped through the progressing cavity pump 1 ( figure 2 )
  • the pumped medium FM in the pumping chambers FR formed between the rotor 4 and the stator 3 causes a radially outward pressure on the stator 3, as a result of which the elastically deformable material of the stator 3 is pressed radially outward.
  • conventionally known wobble pumps have an overlap between the stator and the rotor when at rest. That is, there is a bias voltage between the stator and the rotor. In particular, this achieves that the outer dimensions of the rotor are larger than the inner dimensions of the elastomeric stator.
  • the pressure of the pumped medium FM(FR) within the pumping chambers FR is counteracted in the operating state AZ via the pumped medium FM(D) already pumped to the pressure side D.
  • the pumped medium FM(D) which has the pressure on the pressure side, flows around the stator 3 protruding into the pressure side area D and in doing so presses the stator 3 against the rotor 4. Due to the play 100 formed between the stator 3 and the rotor 4 in the idle state RZ, the starting of the eccentric screw pump 1 without the disadvantageous high starting torque of wobble pumps with overlap between rotor and stator formed in the agitation state.
  • the conveying effect can then start with a very low value and be increased with the increase in the conveyed medium FM(D) conveyed by the eccentric screw pump 1 .
  • the pressure exerted on the stator 3 by the pumped medium FM(D) presses the latter against the rotor 4 in the area of the at least two sealing contact surfaces 14, as a result of which the individual pumping chambers FR are securely spatially separated from one another. Due to the solid-state contact between the rotor 4 and the stator 3 formed in the operating state AZ, a real separation of the pumping chambers FR and a separation between the suction side S of the eccentric screw pump 1 and the pressure side D of the eccentric screw pump 1 is achieved.
  • a significant advantage of such an eccentric screw pump 1 or wobble pump 2 is, in particular, that when the eccentric screw pump 1 is transferred from a standstill or from the idle state RZ to an operating state AZ, due to the play between the rotor 4 and the stator 3 in the idle state RZ, at least in certain areas 100 when starting the eccentric screw pump 1, less effort is required to overcome the breakaway torque.
  • figure 3 shows a further stylized representation of an eccentric screw pump according to the invention 1 and figure 4 shows the on the progressing cavity pump 1 forces acting in operating state AZ.
  • the flexible area 20 of the stator 3 is marked at the free end area 8 . Due to the RZ between rotor 4 and stator 3 in the idle state (cf figure 1 ) Formed game 100, the rotor-stator system 11 in the idle state RZ on no bias.
  • the starting torque is approximately zero and the operating torque is also low at small differential pressures between the suction side S and the pressure side D. It increases with increasing flow rate up to the discharge side pressure p(D).
  • the flexible region 20 of the stator 3 has a correspondingly higher preload at higher torque loads due to the increasing differential pressure between the suction side S and the pressure side D.
  • the stator 3 Since the stator 3 is only fixed to the pump housing 6 on one side, the mobility of the stator 3 is only restricted on one side. If the contact pressure force F is calculated as a function of the differential pressure ⁇ p and the radial stability rS, the result is a largely uniform contact pressure of the stator 3 on the rotor 4 between the pressure side D and the suction side S.
  • wobble stators 3 can advantageously be used in variable-speed eccentric screw pumps 1 with a predetermined output, for example solar-powered wobble pumps 2, in which only small differential pressures ⁇ p can usually be overcome at higher speeds.
  • FIG figure 5 shows a first embodiment of an end attachment of the stator 3 of an eccentric screw pump 1 and figure 6 shows a second embodiment of an end attachment of the stator 3 of an eccentric screw pump 1.
  • the stator 3 has an annular widening 9 at its free end region 8, via which the stator 3 is fixed to the pump housing 6.
  • the annular widening 9 as a flange 10 to screw the stator 3 to the pump housing 6 or the like.
  • the free end area 8 of the stator 3 has a rim structure 17 which extends in the direction of the opposite end area 13 on the suction side and which encloses the stator 3 in some areas, with an annular space 19 being formed between the outer lateral surface of the stator 3 and the rim structure 17, which is in fluid communication with the annular space 12 formed between the stator 3 and the pump housing 6 as described above.
  • the brim structure 17 extending in the direction of the opposite end area 13 on the suction side transitions into a free end area 18 .
  • the free end area 18 is fixed to the pump housing 6, in particular the stator 3 is fastened to the pump housing 6 in a central area 6M of the pump housing 6 via the free end area 18 of the flange structure 17.
  • stator 3 can in each case be almost completely surrounded by the conveying medium FM from the suction-side end area 8 to the pressure-side end area 13 (compare in particular figure 2 ).
  • figure 7 shows a perspective view of a first embodiment of a cardanic joint 5, 5a and figure 8 shows a sectional view.
  • figure 9 shows a perspective representation of an intermediate product 5*, 5a* during the production of the first embodiment of a universal joint 5, 5a according to FIG Figure 7 and Figure 10 shows a sectional view.
  • figure 11 shows a connecting piece 60 of a joint 5, 5a according to FIG figure 7 .
  • the joint 5, 5a includes an internally reinforced elastomer part 50. Tests have shown that 0.5 to 1.5 times the outer diameter dA as the free bending length LB is sufficient to compensate for an angular offset ⁇ of 1 to 2° that is usual in wobble pumps 2. This short length of the joint 5, 5a results in fewer vibrations, which also leads to an increased efficiency of the wobble pump 2, a longer service life for the components of the wobble pump 2 and higher possible maximum speeds of the wobble pump 2.
  • Internal support bodies can be e.g. a sphere, granules, a spiral spring, a cylindrical shaft piece or a flexible elastomer or plastic body.
  • the combination of support body with a lubricant is recommended here.
  • a more or less viscous supporting liquid can also be used.
  • the elastomeric part 50 of the joint 5a preferably consists of a commercially available hydraulic hose or other suitable hose with an internal reinforcing structure.
  • the internal reinforcing structure can be formed, for example, by means of reinforcements interlocked in the shape of a cross in one or more layers.
  • the reinforcement can be formed from metal fibers or wires, plastic fibers and/or textile fibers or the like.
  • a connecting piece 60 is fastened to each of the two free ends of the hose piece 51 forming the elastomer part 50 .
  • the two connecting pieces 60 are preferably designed with retaining grooves 62 in the axial direction and/or possibly also in the radial direction and may have further retaining means (not shown) for fastening and fixing in and/or on the free end areas of the hose piece 51.
  • the connecting pieces 60 preferably have an n-edged attachment area 63, where n corresponds to the number of jaws of the hose press used later (hose presses usually have six or eight jaws).
  • the connecting pieces 60 are in particular assigned a sleeve 52 for holding the respective end of the tube piece 51 (cf Figures 9 and 10 ).
  • the sleeves 52 are compressed using a hose press, in particular the sleeves 53 compressed in this way (cf Figures 7 and 8 ) has an outer contour, at least in some areas, which corresponds to the outer contour of the n-sided contact area 63 of the respective connection piece 60 .
  • the tube piece 51 is fixed between the two connection pieces 60 .
  • the n-edged area 63 on the connecting piece 60 must be aligned at an angle with the jaws of the hose press. After pressing, a secure connection between the respective connection piece 60 and the respective sleeve 53 and thus also a secure connection between the respective connection piece 60 and the respective free end of the hose piece 51.
  • n-edged outer contour of the n-edged contact area 63 can also be used as a working surface for tools if, for example, detachable threads are used as a connection to the adjacent parts, in particular the rotor 4 and/or the drive shaft 7 (cf Figures 1 and 2 ) be used.
  • a thin cylindrical area can also be used. During the pressing process, this thin area can then also be brought into the n-edged shape.
  • a sealing compound and/or adhesive compound can also be used be used, which is introduced in particular between the free ends of the hose piece 51 and the respective sleeve 52, 53.
  • figure 12 shows a perspective view of a second embodiment of a cardanic joint 5, 5b and figure 13 shows a sectional representation.
  • figure 14 shows a component 65 of the second embodiment of a cardanic joint 5b according to FIG figure 12 .
  • This embodiment envisages using a commercially available metallic insert for injection-molded parts 66 as component 65 .
  • the n-edged connection between the connection piece 60 and the pressed sleeve 52 can possibly be dispensed with here.
  • the connecting piece 60 is in the form of a threaded pin 64 with an internal thread for attachment to the rotor 4 and/or the drive shaft 7 (cf Figures 1 and 2 ) educated.
  • grub screws can be used to provide external threads for attachment to rotor 4 and/or drive shaft 7 .

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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)

Claims (15)

  1. Pompe à vis excentrée (1), destinée à pomper des agents (FM) refoulés fluides ou coulants d'un côté aspiration (S) vers un côté pression (D), la pompe à vis excentrée (1) comprenant un rotor (4) et un stator (3), le stator (3) étant créé en version souple et étant immobilisé unilatéralement, notamment sur le côté aspiration (S) sur le carter de pompe (6), le rotor (4) étant relié par l'intermédiaire d'une articulation (5) avec un arbre d'entraînement (7), la pompe à vis excentrée (1) étant susceptible d'adopter un état de repos (RZ) et un état de fonctionnement, caractérisée en ce que dans l'état de repos (RZ) de la pompe à vis excentrée (1) au moins par endroits, aucun contact d'étanchéité n'est créé entre le rotor (4) et le stator (3) dans des zones étanches (14), dans l'état de fonctionnement (AZ) de la pompe à vis excentrée (1), le stator (3) étant entouré au moins par endroits et/ou de manière sensiblement intégrale par l'agent (FM) refoulé, dans l'état de fonctionnement (AZ), le rotor (4) et le stator (3) étant amenés en appui le long des zones étanches (14) par l'agent (FM) refoulé agissant par l'extérieur sur des surfaces d'enveloppe externe du stator.
  2. Pompe à vis excentrée (1) selon la revendication 1, dans l'état de repos (RZ) un jeu (100) étant créé au moins par endroits dans les zones étanches (14) entre le rotor (4) et le stator (3).
  3. Pompe à vis excentrée (1) selon la revendication 1 ou 2, dans l'état de repos (RZ) dans un ordre compris entre 50 % à 100 % des zones étanches (14), aucun contact d'étanchéité n'étant créé, respectivement un jeu (100) étant créé entre le rotor (4) et le stator (3) et dans l'état de fonctionnement (AZ), un chevauchement étant créé entre le rotor (4) et le stator (3) dans les zones étanches (14).
  4. Pompe à vis excentrée (1) selon l'une quelconque des revendications précédentes, dans le premier état de repos (RZ) de la pompe à vis excentrée (1), sur le côté aspiration (S), un premier jeu (100) étant créé entre le rotor (4) et le stator (3) et sur le côté pression (D), un deuxième jeu (100) étant créé entre le rotor (4) et le stator (3).
  5. Pompe à vis excentrée (1) selon l'une quelconque des revendications 1 à 3, dans le premier état de repos (RZ) de la pompe à vis excentrée (1), sur le côté aspiration (S), un jeu (100) étant créé entre le rotor (4) et le stator (3) et sur le côté pression (D), un recouvrement étant créé entre le rotor (4) et le stator (3) .
  6. Pompe à vis excentrée (1) selon la revendication 4, le premier jeu (100) étant créé en étant supérieur au deuxième jeu (100).
  7. Pompe à vis excentrée (1) selon l'une quelconque des revendications 4 ou 6, le jeu (100) décroissant de manière sensiblement continue le long des zones étanches (14) entre le rotor (4) et le stator (3), d'un côté aspiration (S) de la pompe à vis excentrée (1) vers un côté pression (0) de la pompe à vis excentrée (1) .
  8. Pompe à vis excentrée (1) selon l'une quelconque des revendications précédentes, l'agent (FM) refoulé qui entoure au moins partiellement le stator (3) dans un état de fonctionnement (AZ) présentant la pression (p(D)) côté aspiration.
  9. Pompe à vis excentrée (1) selon l'une quelconque des revendications précédentes, le stator (3) étant immobilisé unilatéralement sur le carter de pompe (6) directement par l'intermédiaire d'une zone d'extrémité (8) libre du stator (3).
  10. Pompe à vis excentrée (1) selon la revendication 9, pour l'immobilisation sur le carter de pompe (6), la zone d'extrémité (8) libre du stator (3) comportant (9) un élargissement de forme annulaire ou pour l'immobilisation sur le carter de pompe (6), la zone d'extrémité (8) libre du stator (3) étant créée sous la forme d'un bord (17).
  11. Pompe à vis excentrée (1) selon l'une quelconque des revendications précédentes, l'articulation (5) comprenant une partie centrale (50) créée au moins pour être en partie de manière mobile, qui est réalisée en une matière élastomère ou matière plastique renforcée.
  12. Pompe à vis excentrée (1) selon la revendication 11, le renfort de la matière élastomère ou matière plastique étant réalisé par un renfort par fibres ou renfort par fil métallique intégré dans la matière.
  13. Pompe à vis excentrée (1) selon la revendication 11 ou 12, la partie centrale (50) étant délimitée des deux côtés par des pièces de raccord (60), destinées à fixer le rotor (4) et/ou l'arbre d'entraînement (7).
  14. Pompe à vis excentrée (1) selon l'une quelconque des revendications précédentes, le stator (3) comportant une surface périphérique intérieure de forme hélicoïdale et comprenant un entonnoir pour l'agent (FM) refoulé sur la zone d'extrémité (8) immobilisée unilatéralement du stator (3), l'entonnoir étant un prolongement de l'une surface périphérique intérieure hélicoïdale du stator (3) et étant créé en étant exempt de lignes d'étanchéité par rapport au rotor (4).
  15. Pompe à vis excentrée (1) selon l'une quelconque des revendications précédentes, à la pompe à vis excentrée (1) étant associé au moins un module solaire, l'entraînement étant exploitable par énergie solaire.
EP18724439.7A 2017-04-12 2018-04-10 Pompe à vis excentrique Active EP3610154B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017107962.9A DE102017107962B3 (de) 2017-04-12 2017-04-12 Exzenterschneckenpumpe
PCT/DE2018/100322 WO2018188694A1 (fr) 2017-04-12 2018-04-10 Pompe à vis excentrique

Publications (2)

Publication Number Publication Date
EP3610154A1 EP3610154A1 (fr) 2020-02-19
EP3610154B1 true EP3610154B1 (fr) 2023-01-18

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EP18724439.7A Active EP3610154B1 (fr) 2017-04-12 2018-04-10 Pompe à vis excentrique

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US (1) US11236747B2 (fr)
EP (1) EP3610154B1 (fr)
AU (1) AU2018253007B2 (fr)
BR (1) BR112019019152B1 (fr)
DE (1) DE102017107962B3 (fr)
WO (1) WO2018188694A1 (fr)
ZA (1) ZA201906631B (fr)

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CN110303306B (zh) * 2019-07-23 2021-05-28 江苏技先机械科技有限公司 单螺旋金属螺杆泵定子加工方法
EP3825552B1 (fr) * 2019-11-22 2025-03-12 Grundfos Holding A/S Pompe à vis excentrique
DE102020114937B4 (de) 2020-06-05 2026-04-23 Netzsch Pumpen & Systeme Gmbh Exzenterschneckenpumpe in modularer bauweise
CN114151328B (zh) * 2021-12-31 2024-04-30 富奥汽车零部件股份有限公司 一种缓速装置
CN116292268A (zh) * 2023-03-24 2023-06-23 黄山黄泵单螺杆泵有限公司 一种微型单螺杆泵及其安装方法
US12152588B1 (en) 2023-05-26 2024-11-26 Grant Prideco, Inc. Free-mold stator for a progressing cavity pump
DE102023115951A1 (de) * 2023-06-19 2024-12-19 Ralf Daunheimer Statorauskleidung, Stator sowie Verfahren zum Herstellen einer Statorauskleidung

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US6358027B1 (en) * 2000-06-23 2002-03-19 Weatherford/Lamb, Inc. Adjustable fit progressive cavity pump/motor apparatus and method

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US2612845A (en) * 1950-04-29 1952-10-07 Robbins & Myers Helical gear pump with nonrigid casing
US2765114A (en) * 1953-06-15 1956-10-02 Robbins & Myers Cone type compressor
US2826152A (en) 1955-08-30 1958-03-11 Robbins & Myers Helical gear pump with bellows stator
DE2139949A1 (de) 1970-08-31 1972-03-02 Environment/One Corp., Schenectady, N.Y. (V.St.A.) Schraubenpumpe
DE2158009A1 (de) * 1971-11-23 1973-05-24 Seeberger Kg Maschinen Und Ger Exzenterschneckenpumpe
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US4923376A (en) * 1988-03-24 1990-05-08 Wright John L Moineau pump with rotating closed end outer member and nonrotating hollow inner member
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US7380608B2 (en) * 2004-12-14 2008-06-03 Howard Geier Pumping water from a natural gas well
PT2944819T (pt) * 2014-05-12 2017-10-02 Hugo Vogelsang Maschb Gmbh Bomba de parafuso excêntrico
DE102016009028A1 (de) * 2016-07-26 2018-02-01 Netzsch Pumpen & Systeme Gmbh Rotor-Stator-System mit einem Einlauftrichter für eine Exzenterschneckenpumpe
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Also Published As

Publication number Publication date
US11236747B2 (en) 2022-02-01
BR112019019152A2 (pt) 2020-04-14
BR112019019152B1 (pt) 2023-10-31
US20200056609A1 (en) 2020-02-20
AU2018253007A1 (en) 2019-10-24
ZA201906631B (en) 2022-05-25
EP3610154A1 (fr) 2020-02-19
DE102017107962B3 (de) 2018-09-13
WO2018188694A1 (fr) 2018-10-18
AU2018253007B2 (en) 2021-07-15

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