EP1025361B1 - Pumpvorrichtung - Google Patents

Pumpvorrichtung Download PDF

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Publication number
EP1025361B1
EP1025361B1 EP98949147A EP98949147A EP1025361B1 EP 1025361 B1 EP1025361 B1 EP 1025361B1 EP 98949147 A EP98949147 A EP 98949147A EP 98949147 A EP98949147 A EP 98949147A EP 1025361 B1 EP1025361 B1 EP 1025361B1
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EP
European Patent Office
Prior art keywords
pump
rotor
inner rotor
moineau
profile
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.)
Expired - Lifetime
Application number
EP98949147A
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English (en)
French (fr)
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EP1025361A2 (de
Inventor
John Leishman Sneddon
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Individual
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Individual
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Filing date
Publication date
Priority claimed from GBGB9722463.8A external-priority patent/GB9722463D0/en
Priority claimed from GBGB9723387.8A external-priority patent/GB9723387D0/en
Application filed by Individual filed Critical Individual
Publication of EP1025361A2 publication Critical patent/EP1025361A2/de
Application granted granted Critical
Publication of EP1025361B1 publication Critical patent/EP1025361B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • 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

Definitions

  • the present invention relates to a pumping apparatus and in particular, but not exclusively, to a pumping apparatus which not only functions as a conventional pump but may also be used for propelling marine, or submarine, vehicles.
  • the invention also relates to a motor having a design based on Moineau principles.
  • US 5 611 397 A discloses a pumping apparatus according to the preamble of claim 1.
  • the Moineau pump comprises an outer and an inner rotor, wherein the lobe ratio (or number of teeth) of the inner and outer rotors are in the ratio of n:n+1, where n is any whole number.
  • a centrifugal pump may be coupled to the Moineau pump at or near a fluid intake of the Moineau pump. This, when loaded, provides a higher than normal pressure fluid feed to the Moineau pump. Alternatively, it may be mounted at or near a fluid outlet.
  • the outer rotor is rotatably mounted using an outer bearing.
  • the inner rotor may typically be mounted on a static central shaft which acts as a bearing.
  • the inner rotor may be rotatably mounted using an integral shaft which rotates on a bearing.
  • the lobe ratio of the Moineau pump is 1:2 and the inner rotor defines a cantilever.
  • the cantilever comprises three portions.
  • the portions are a pumping profile, a support profile and a shaft profile.
  • the pumping profile typically is an axial three dimensional sinusoid.
  • the sinusoid has a specific rolling diameter and most preferably has a rolling diameter which is one and a half times the diameter of the inner rotor.
  • the support profile is typically a continuation of the pumping profile which extends axially in a two dimensional sinusoid.
  • the shaft profile is a continuation of the support profile axially in one dimension only.
  • the shaft profile is a cylinder.
  • the centre of the inner rotor shaft is also the centre of the rolling diameter.
  • the primemover is an electric motor.
  • the primemover may comprise a hydraulic, pneumatic or an internal combustion engine.
  • a pumping apparatus generally designated 10, which comprises a Moineau pump 12 and a centrifugal pump 14 in combination.
  • the Moineau pump 12 is driven by an electric motor which has a stator 16 and a rotor 18, in keeping with conventional notation and operates in the conventional manner. It will be appreciated that any type of motor could be used and the electric motor of this embodiment is by way of example only.
  • the rotor 18 is coupled to an outer rotor 20 of the pump 12. As the rotor 18 is rotated by the electromagnetic force of the electric motor, the outer rotor 20 is caused to rotate in synchronisation with the rotor 18 of the electric motor. Rotation of the outer rotor 20 causes a subsequent rotation of an inner rotor 22.
  • Moineau pumps operate on the basis that the outer rotor 20 and the inner rotor 22 come into sliding contact at certain points along the length of the pump 12. The number of points at which they contact is governed by the lobe ratio of the inner rotor 22 to the outer rotor 20.
  • the lobe ratio of the Moineau pump 12 shown in Fig.1 is 3:4, as will be appreciated by those skilled in the art.
  • Figs 3a to c a number of different lobe ratios are shown as examples.
  • Fig. 3a shows a lobe ratio of 1:2 whereas Figs 3b and 3c show 2:3 and 3:4 ratios respectively.
  • the inner rotor 22 is an axial three-dimensional sinusoid or a spiral. Any vertical section of the spiral gives a circle which has a centre offset from the centre 24 of the inner rotor shaft 26.
  • the outer rotor 20 has a slot 28 which spirals in a similar manner to that of the inner rotor 22, the inner rotor 22 being engaged in the slot 28.
  • the dimensions of the inner 22 and outer 20 rotors are optional.
  • the slot 28 has two semi-circular ends which are connected by a substantially straight portion.
  • the distance between the centres of the semi-circular sections which define radiused ends is d, that is the same as the inner rotor diameter.
  • the radius of the curves is d/2 giving the slot 28 an over-all length of 2d.
  • the inner rotor 22 as shown in Fig. 4b has the radius of the circles (which are cross-sections of the spiral) as d/2.
  • the centre of this circle is offset from the centre of the inner rotor shaft 26, the distance being labelled as e (the eccentricity) and is expressed in terms of d as d/4.
  • the inner rotor 22 has a rolling diameter of 1.5d.
  • Figs 5a and 5b The principle of the Moineau pump 12 with a lobe ratio of 1:2 is best described with reference to Figs 5a and 5b.
  • Fig. 5b the numbered sequence of drawings shows the outer rotor 20 rotating one revolution anticlockwise.
  • the outer rotor 20 is rotated by the rotor 18 of the electric motor.
  • the inner rotor 22 rotates due to the inter-engagement of the inner 22 and outer 20 rotor profiles.
  • the 1:2 lobe ratio could be viewed as a standard gearing, where the inner rotor 22 has one elongated tooth and the outer rotor 20 has two.
  • the electric motor drives the outer rotor 20 which in turn causes the inner rotor 22 to rotate due to the inter-engagement of the rotors 20, 22.
  • Figs 6a to c show the configuration of the inner rotor 22 and also a static inner rotor shaft 26 of a 1:2 lobed Moineau pump.
  • Fig. 6a shows the offset of the inner rotor shaft 26 in comparison to the centre line of the spiral, when the inner rotor is supported by a static shaft.
  • a number of options for mounting the inner rotor 22 in the pumping apparatus 10 are available. Firstly, as shown in Figs 6b and c, the inner rotor 22 is mounted onto a static shaft 26. The static shaft 26 is then mounted within the apparatus of Fig. 7 which will be described hereinafter, using an internal bearing surface 23, as best shown in Fig. 6b.
  • the inner rotor 22 is mounted on a rotatable inner support shaft 27 using a bearing 30 (see Figs 8a and 8b), the inner shaft 27 being rotatably mounted as part of the pumping apparatus 10.
  • a cantilever support system which will be described hereinafter with reference to Figs l0a and 10b, the shaft 27 is not required as the cantilever support provides the shaft.
  • the cantilever support is generally for use with a 1:2 lobed Moineau configuration.
  • Fig. 6d shows the inner rotor 22 of a 1:2 lobed Moineau pump with a centrifugal rotor 21 of the centrifugal pump 14 attached thereto.
  • the inner rotor 22 is mounted in the apparatus 10 using the rotatable shaft 26 as will be described hereinafter.
  • the centrifugal rotor 21 is attached to the inner rotor 22 using a key 27 on the inner rotor 22.
  • a boss 25 is then removably attached to the front end of the rotor 22 using a screw thread, thereby securing the centrifugal rotor 21 in place.
  • Fig. 6e shows the alternative arrangement where the inner rotor 22 is rotatably mounted onto a static inner shaft 27 which acts as an internal bearing.
  • the centrifugal rotor 21 is welded onto the static inner shaft 27. Note that there is no requirement for a boss to be screwed on to the static shaft 27 to hold the rotor 21 in position.
  • Fig 7 there is shown an over-all view of the Moineau pump 12 for use with the present invention.
  • This particular embodiment uses a static inner rotor shaft 27.
  • the inner rotor shaft 27 is non-rotatably mounted using two pins 32.
  • Rotatably mounted on the shaft 27 is the inner rotor 22.
  • the outer rotor 20 spirals around the inner rotor 22 as previously described.
  • the electric motor In order to drive the outer rotor 20, the electric motor consists of a stator 16 and a rotor 18 as will be appreciated by those skilled in the art.
  • the outer rotor 20 rotates on a series of bearings 34, two in this particular embodiment.
  • a plurality of seals 36 prevent fluid from entering the pump 12 and subsequently damaging the electric motor.
  • the apparatus 10 of the present invention provides that a Moineau pump 12 has a centrifugal pump 14 coupled at the leading end of the Moineau pump 12.
  • the centrifugal pump 14 is attached to the inner rotor shaft 26 of the Moineau pump 14 using conventional means, such as welding or the use of a boss and keyway as described previously.
  • the centrifugal pump 14 is attached by way of a boss and keyway.
  • the centrifugal rotor 21 (sometimes referred to as an impeller) is basically a wheel fitted with vanes.
  • the purpose of the centrifugal pump 14 is to, in effect, create a supercharge for the Moineau pump 14.
  • centrifugal pump 14 is only one example of a specific speed pump as will be appreciated by those skilled in the art. Any specific speed pump may be used in place of the centrifugal pump as shown, and the present invention is not limited to such use.
  • fluid flows axially towards the centrifugal rotor 21, is deflected by it, and flows out of the apertures between the vanes.
  • the vanes produce a centrifugal acceleration (that is to say a change in direction and acceleration) of the fluid as it passes, thereby creating a higher pressure after the centrifugal pump outlet or diffuser 46.
  • the Moineau pump 12 is an example of a positive displacement pump, which operate on the principle of taking in fluid at a low pressure and expunging the same fluid at a higher pressure. Therefore, the effect of increasing the pressure at the diffuser 46, which feeds directly into the Moineau pump inlet 40 gives an increase in pressure at the Moineau pump outlet 42. It therefore follows that if the pressure at the inlet 40 can be increased, a similar increase in pressure at the outlet 42 can be expected. Hence, the centrifugal pump 14 creates an increase in pressure at the Moineau pump inlet 40, and has a function similar to that of a supercharger in a vehicle.
  • FIGs 8a and b there is shown an alternative embodiment of the 3:4 lobed configuration of Fig. 1.
  • the apparatus in Figs 8a and b uses a bearing 30 on which the shaft 26 of the inner rotor 22 rotates.
  • the apparatus is generally the same as that shown in Fig. 1 with the addition of two ducts 48 which are in fluid communication with the volutes 46. Fluid flow into the ducts 48 is controlled by a plurality of one-way valves 50.
  • the centrifugal pump 14 and the Moineau pump 12 are not hydraulically matched, that is to say the centrifugal pump 14 is drawing in more fluid than the Moineau pump 12 can cope with, then the vacuum at the diffuser 46 reduces and the non-return valves 50 open. This allows fluid to flow though the ducts 48 as shown in Fig. 8b and exit the apparatus 10 at secondary outlets 52.
  • the inclusion of the non-return valves 50 is required if the capacity of the centrifugal pump 14 is greater than that of the Moineau pump 12.
  • Fig. 8c shows the same apparatus of that of Figs 8a and b but the inner rotor 22 of the Moineau pump 12 is coupled using a static inner shaft 26 as described above. Note that because there are no dynamic bearings on which the inner rotor 26 rotates, an overall reduction in cost is possible.
  • Figs 9a to c The apparatus 10 is shown in progressive stages of pumping in Figs 9a to c.
  • Fig. 9a shows the apparatus 10 in a static condition, with the fluid 54 at a distance from the apparatus 10.
  • Fig. 9b shows that the air within and in front of the apparatus 10 has been expelled through the outlet 42 and the fluid 54 has entered the eye of the centrifugal pump 14.
  • Fig. 9c shows the apparatus 10 in operation where the centrifugal pump 14 is providing an excess flow of water to the Moineau pump 12 and the fluid 54 is being discharged from the outlet 42.
  • the non-return valves 50 are open in this particular embodiment and the ducts 48 are conveying excess fluid 54 to the secondary outlets 52.
  • Figs 10a and b there is shown in more detail the profile of the inner rotor 22 of a 1:2 arrangement.
  • the inner rotor 22 depicted in the drawings is formed as a cantilever. As the rotor 22 only has this one cantilever support then the number of bearings required for it to rotate on can be reduced to less than three; three being the conventional minimum number of bearings required for this type of application.
  • the inner rotor 22 comprises three distinct profiles; a shaft profile 56, a support profile 58 and a pumping profile 60.
  • the pumping profile 60 is axially machined in three dimensions to be a spiralling sinusoid.
  • the spiral is contained within a rolling diameter of 1.5d, where d is the diameter of the inner rotor 22, as previously explained.
  • the support profile 58 is a continuation of the sinusoid of the pumping profile 60 but in two-dimensions only. That is to say that the support profile 58 does not spiral, as best seen in Fig. 10b.
  • the shaft profile 56 is a continuation of the support profile 58 in one dimension only, that is to say it is a cylinder.
  • Figs 11a to c there is shown sample relationships between the axial length of the support profile 58 and pitch of the inner rotor 22. It is found that the 1:2 embodiment of inner rotor 22 has a pitch which is a number times the diameter d of the inner rotor 22 and the length of support profile 58 which is given by the same number times the eccentricity e. Note that the variable e has previously been defined as the eccentricity, that is to say the offset distance between the inner rotor 22 rolling diameter centre and the centre if the inner rotor shaft 24.
  • the profile of the inner rotor 22 allows one end to rotate freely. As such, only one bearing at the shaft profile 56 is required, thereby reducing the weight, cost and complexity of the design.
  • Figs 12a to e shows an alternative arrangement for the inner 22 and outer 20 rotors.
  • the ratio of inner to outer rotor diameters is 1:4.
  • the cantilever support profile as described above, allows the inner and outer rotor diameters to be equal to and/or greater or less than 1:2, providing that the inner rotor 22 has a specific rolling diameter.
  • This particular embodiment has an inner rotor pitch of 3d, a rolling diameter of 2.5d and a cantilever support of 0.75d, where d is the diameter of the shaft, as best seen in Fig. 12e. It should be noted that in cases where the outer rotor diameter progresses beyond twice that of the inner rotor diameter d, it will be possible to operate at a reduced angular velocity and attain the same volumetric throughput for specific requirements.
  • Figs 13a to d show a variety of views of the 1:2 lobed arrangement with an inner to outer rotor diameter ratio of 1:4.
  • Figs 14a to f there is shown a number of alternative arrangements of bearings, seals and the position of the electric motor or primemover.
  • Figs 14a to c have seals 62 at either end of the outer rotor 20 as shown.
  • the inner rotor shaft 26 is rotatable mounted using an inner rotor bearing 64 which is located at the same position in each of the figures. The position of the bearing 64 is dependent upon the use of the cantilever support structure as previously discussed. Note that the inner rotor 22 has a free end which results in one of the dynamic bearings being unnecessary.
  • the position of the electric motor which comprises a stator 16 and rotor 18 varies between a substantially central location in Fig, 14b, to a position where it is near the inner rotor bearing 64 in Fig 14a, to a position near the opposite end.
  • the outer rotor 20 rotates on a bearing 66, which can be placed in any of the positions shown in Figs 14a to c.
  • a bearing 66 which can be placed in any of the positions shown in Figs 14a to c.
  • Figs 14e and f are similar arrangements to those shown in Figs 14a to c, except that the seals 62 are positioned near the cantilever support and substantially in the centre of the apparatus.
  • Figs 15a and 15b show an example of a marine propulsion unit which incorporates the present invention.
  • a 1:2 ratio Moineau pump 12 is used.
  • a ceramic bearing 70 is used to support the cantilever profile. With this type of bearing, some of the fluid from the outlet 72 is fed back to the bearing 70 via a central duct 74 in the inner rotor 22 to lubricate the faces of the bearing 70 which are in sliding contact with one another. Note that the ceramic bearing 70 is supported by aerodynamic vanes 76 and that the intake 78 is parabolic.
  • the use of the ceramic bearing 70 obviates the necessity to use seals, although it may be desirable to seal off a chamber 80 in which the electric motor is housed.
  • the outlet 72 comprises a variable area nozzle 82.
  • the nozzle 82 allows greater control of the thrust which the apparatus can supply.
  • a propeller propulsion device 100 and a marine propulsion device 110 there is shown respectively a propeller propulsion device 100 and a marine propulsion device 110 according to the present invention.
  • the propeller device 100 has a forward velocity of V c , as shown by arrow 112 and a thrust having a velocity component value of V j .
  • the marine propulsion device 110 similarly has a craft velocity of V c , as shown by arrow 114 and a thrust having a velocity component value of V j .
  • both devices 100, 110 have an associated velocity acting in the opposite direction which is of the same magnitude as the craft velocity V c , as shown by arrow 116.
  • V c the component of V c acting in the opposite direction to the direction of the devices 100, 110 produces internal drag on the propeller device 100.
  • the actual magnitude of the propulsion at the outlet of the device 100 is proportional to V j minus V c , as given by arrow 118.
  • the propulsion unit 110 of the present invention has, by the inherent design of the pumping system, very little or no internal drag. As a result, a pressure front is built-up in front of the device 110 and the thrust produced by the device 110 is therefore directly proportional to V j , as shown by arrow 120.
  • a modified pump where in the inner rotor 122 is formed of a hollow member mounted on a static shaft 126.
  • a spiral path 128 which forms a dynamic seal between the static shaft 126 and the rotating inside skin 122A of the inner rotor 122.
  • the present invention provides a pumping apparatus which uses a particular ratio Moineau pump to drive a centrifugal pump.
  • the Moineau pump can be of any lobe configuration.
  • the centrifugal pump functions as a type of supercharger to provide a higher pressure input to the Moineau pump thereby increasing the efficiency of the Moineau pump and also the power output of it.
  • centrifugal pump is one type of rotor pump which may be coupled to the Moineau pump as described. Other types of Specific Speed rotors may be used.
  • the centrifugal pump is used as an example only and the present invention is not limited to such use.
  • the centrifugal pump may be positioned at the fluid outlet of the Moineau pump, as opposed to the fluid inlet.
  • the present invention provides a marine propulsion unit which has very little or no internal drag, giving a higher thrust output of similarly rated conventional devices coupled with an increase in efficiency. Note that it is possible to use the present invention in all types of fluid and hence the present invention may be used to propel aircraft through air for example, and should not be limited to marine, or submarine, applications.
  • FIG. 19 With reference to Fig. 19 there is shown a single pump rotor embodiment of the invention.
  • a single pump rotor 190 is provided with a profiled inner chamber 191 which is lined with an elastomer seal 192.
  • the elastomer seal 192 spirally contacts the surface of a static shaft 194 to define a sliding pumping seal. Rotation of the pump rotor 190 which is attached to a motor rotor 195 effects the necessary pumping action.
  • a mud motor having design features based on pumping apparatus herebefore described.
  • an MWD mud motor 200 comprises an inner rotor 201 mounted for rotation within an outer rotor assembly, the inner rotor and outer rotor assembly being located within an external housing 210 constituted by drill tubing.
  • the outer rotor assembly rotates within the outer housing on bearings 208.
  • the outer rotor assembly comprises a first outer rotor 203 which interacts within the inner rotor 201 in the same manner as has been described hereabove in relation to the pumping apparatus.
  • the outer rotor assembly further comprises a second outer rotor 205 which is mechanically coupled to the first outer rotor 203 and carries a drill bit 206.
  • the inner rotor 201 is mounted for rotation upon an eccentrically mounted static inner bearing 220.
  • the inner bearing 220 is in the form of a cantilever mounted shaft fixed to a support arrangement 222 in the form of a "spider" mounted within the external housing 210.
  • the support bearing 220 may be retained within a suitable spigot mounted on the spider by means of a fixing pin 223.
  • the external housing 210 is provided with sample windows 230 through which the required information is communicated to acoustic data telemetry (ADT) transducers 240 carried on the outer surface of the second outer rotor 205.
  • ADT acoustic data telemetry
  • the ADT transducers are thus arranged to rotate past the windows 230 and as they do so, they gather the required information from the part of the hole being drilled at a particular depth at that instant. This information is transformed into acoustic signals which are relayed via the steel of the drill tubing to a receiver on the parent installation which will interpret them.
  • mud is pumped from the parent installation into a mud entry 250 of the motor 200, thus causing the inner and outer rotors to rotate, whereafter the mud exits through a mud exit formed on the outer rotor 205.
  • the inner rotor 201 has a single lobe and the outer rotor 203 has two lobes resulting in the inner rotor 201 rotating at twice the speed of the outer rotor 203.
  • the mud exit hole 260 will shut off mud flow once in every revolution of the outer rotor 205. This will cause a momentary pressure pulse to travel back up the mud to the parent installation where it will be detected. The number of these pulses received per minute will represent the revolutions per minute of the outer rotor 205 and half the revolutions per minute of the inner rotor 201. In the current drawing the outer drill bit carrying rotor will be in synchronism with the speed of the outer rotor 205.
  • outer rotor assembly Whilst the outer rotor assembly is described as being formed of a first outer rotor 203 and a second outer rotor 205, these elements can be formed integrally.
  • the design permits additional instrumentation to be located in the static support bearing 220.
  • the mud motor described provides the advantage of reduced motor vibration permitting increased rotational speeds and improved penetration as well as increased instrumentational accuracy by extended positioning of the MWD instrumentation closer to the drill bit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Massaging Devices (AREA)
  • Eye Examination Apparatus (AREA)
  • Fluid-Driven Valves (AREA)
  • Seal Device For Vehicle (AREA)

Claims (15)

  1. Eine Moineau-Pumpe, die ein äußeres Gehäuse, einen äußeren Rotor (20), der zur Drehung innerhalb des äußeren Gehäuses montiert ist, einen inneren Rotor (22), der zur Drehung innerhalb des äußeren Rotors (20) montiert ist, beinhaltet, wobei der innere und der äußere Rotor (20, 22) von einer Moineau-Konstruktion sind, wodurch das Flügelverhältnis des inneren und des äußeren Rotors n:n+1 beträgt, wobei n jede beliebige ganze Zahl ist;
    dadurch gekennzeichnet, dass der innere Rotor (22) einen Rolldurchmesser von eineinhalbmal des Durchmessers des inneren Rotors aufweist.
  2. Pumpe gemäß Anspruch 1, wobei das Flügelverhältnis 1:2 beträgt.
  3. Pumpe gemäß einem der Ansprüche 1 oder 2, wobei der innere Rotor (22) auf einer statischen zentralen Welle (27) montiert ist, die als ein Lager wirkt.
  4. Pumpe gemäß einem der Ansprüche 1 oder 2, wobei der innere Rotor (22) auf einer integralen Welle (26) montiert ist, die sich auf mindestens einem Lager dreht.
  5. Pumpe gemäß einem der vorhergehenden Ansprüche, wobei der innere Rotor einen Ausleger definiert.
  6. Pumpe gemäß Anspruch 5, wobei der Ausleger ein Pumpprofil (60), ein Stützprofil (58) und ein Wellenprofil (56) beinhaltet.
  7. Pumpe gemäß Anspruch 6, wobei das Pumpprofil (60) eine axiale dreidimensionale Sinuskurve ist, die einen Rolldurchmesser aufweist, der eineinhalbmal der Durchmesser des inneren Rotors ist.
  8. Pumpe gemäß einem der Anprüche 6 oder 7, wobei das Stützprofil (58) eine Fortsetzung des Pumpprofils (60) ist, das sich axial in einer zweidimensionalen Sinuskurve erstreckt.
  9. Pumpe gemäß einem der Ansprüche 6 bis 8, wobei das Wellenprofil (56) eine Fortsetzung des Stützprofils (58) axial in lediglich einer Dimension ist.
  10. Pumpe gemäß einem der Ansprüche 6 bis 9, wobei das Wellenprofil (56) ein Zylinder ist.
  11. Pumpe gemäß einem der vorhergehenden Ansprüche, wobei eine Fluidpumpe (14) an die Moineau-Pumpe an oder nahe einem Fluideinlass der Moineau-Pumpe gekoppelt ist.
  12. Pumpe gemäß einem der Anprüche 1 bis 10, wobei eine Fluidpumpe (14) an oder nahe einem Fluidauslass der Moineau-Pumpe montiert ist.
  13. Pumpe gemäß Anspruch 11 oder Anspruch 12 , wobei die Fluidpumpe eine Zentrifugalpumpe beinhaltet.
  14. Pumpe gemäß einem der vorhergehenden Ansprüche, die des Weiteren einen Antriebsmotor zum Bereitstellen von Drehbewegung des äußeren Rotors (20) beinhaltet.
  15. Pumpe gemäß Anspruch 14, wobei der Antriebsmotor ein Elektromotor, ein Hydraulikmotor, ein Druckluftmotor oder ein Verbrennungsmotor ist.
EP98949147A 1997-10-24 1998-10-26 Pumpvorrichtung Expired - Lifetime EP1025361B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
GB9722463 1997-10-24
GBGB9722463.8A GB9722463D0 (en) 1997-10-24 1997-10-24 Pumping apparatus
GB9723387 1997-11-06
GBGB9723387.8A GB9723387D0 (en) 1997-11-06 1997-11-06 Pumping apparatus
PCT/GB1998/003181 WO1999022141A2 (en) 1997-10-24 1998-10-26 Pumping apparatus

Publications (2)

Publication Number Publication Date
EP1025361A2 EP1025361A2 (de) 2000-08-09
EP1025361B1 true EP1025361B1 (de) 2008-01-30

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ID=26312482

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98949147A Expired - Lifetime EP1025361B1 (de) 1997-10-24 1998-10-26 Pumpvorrichtung

Country Status (5)

Country Link
EP (1) EP1025361B1 (de)
AT (1) ATE385289T1 (de)
AU (1) AU9552198A (de)
DE (1) DE69839078T2 (de)
WO (1) WO1999022141A2 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101484703B (zh) * 2006-06-30 2011-10-19 格伦德福斯管理联合股份公司 螺杆泵
NO327505B1 (no) 2007-09-11 2009-07-27 Agr Subsea As Eksenterskruepumpe tilpasset pumping av kompressible fluider
NO327503B1 (no) 2007-09-20 2009-07-27 Agr Subsea As Eksenterskruepumpe med flere pumpeseksjoner
NO329714B1 (no) 2008-08-21 2010-12-06 Agr Subsea As Ytre rotor i eksenterskruepumpe med en indre og en ytre rotor
NO329713B1 (no) 2008-08-21 2010-12-06 Agr Subsea As Eksenterskruepumpe med en indre og en ytre rotor

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Also Published As

Publication number Publication date
EP1025361A2 (de) 2000-08-09
DE69839078T2 (de) 2009-01-22
ATE385289T1 (de) 2008-02-15
WO1999022141A2 (en) 1999-05-06
AU9552198A (en) 1999-05-17
WO1999022141A3 (en) 1999-07-15
DE69839078D1 (de) 2008-03-20

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