WO2004031584A1 - Exzenterschneckenpumpe - Google Patents
Exzenterschneckenpumpe Download PDFInfo
- Publication number
- WO2004031584A1 WO2004031584A1 PCT/EP2003/010341 EP0310341W WO2004031584A1 WO 2004031584 A1 WO2004031584 A1 WO 2004031584A1 EP 0310341 W EP0310341 W EP 0310341W WO 2004031584 A1 WO2004031584 A1 WO 2004031584A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- teeth
- tooth
- bore
- eccentric screw
- ribs
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
Definitions
- Eccentric screw pumps or motors consist of a stator that has a helical bore or passage in which a helical rotor rotates.
- the helical rotor has a number of gears 1 lower than the number of gears in the stator bores. When the rotor rotates, it rolls in a form-fitting manner in the thread of the bore. From a geared point of view, it is a helical toothed pinion that rolls in a helically toothed ring gear, the pinion and ring gear differing by 1 in the number of teeth.
- the stator is provided with an elastomeric lining, i.e. the inner wall of the stator consists of an elastomeric material which is pressed onto the rotor in the area of contact with it.
- the relative movement between the stator and the rotor is not a pure rolling movement. According to the seal between the stator and the rotor, it is a sliding movement over long distances.
- an eccentric screw pump If an eccentric screw pump is pressurized with medium, it can also be used as an eccentric screw motor. This principle is used with underground drilling motors (Mud motors), as eccentric worm motors consist of very few components, are very slim in diameter and can still generate high torques.
- Mod motors underground drilling motors
- eccentric worm motors consist of very few components, are very slim in diameter and can still generate high torques.
- the medium that is pumped or used for the drive can contain particles without fear of damage to the pump or the motor, which is a further advantage of eccentric screw pumps and eccentric screw motors.
- Eccentric screw pumps are used to convey mortar. In other words, a material that contains a high proportion of solid particles.
- an eccentric screw pump or an eccentric screw motor results from the flow rate, the temperature and the specific heat of the medium passed through and the friction between the stator and the rotor.
- the friction generates heat that is dissipated through the medium.
- an eccentric screw pump reaches operating temperatures of up to 300 ° C. They must therefore be able to cope with a temperature jump of up to approx. 280 ° C if they are at room temperature in the initial state and are operated in a normal environment.
- the elastomeric lining consists of synthetic elastomer or mixtures thereof with natural rubber. Both materials show a strong temperature response, i.e. the coefficient of expansion is relatively large. The clear width in the stator thus changes considerably as a function of temperature. At low temperature, the rotor in the stator rotates slightly, while at high temperatures the material of the inner lining has expanded to such an extent that the stator is practically clamped. If it is turned from the outside with the help of the drive, the teeth of the elastomeric lining are torn away in the hole.
- the development of the bore of the stator shows a relative smooth undulating course.
- This wavy course can be calculated by the person skilled in the art on the basis of known geometric relationships and the desired pretensioning force at the sealing points.
- the teeth have the shape of cycloid teeth, with the teeth and the tooth spaces being rounded.
- stator jamming arises in the rotor by means of a disk-shaped cutout: it is assumed that the bore in the stator is five-thread, which means that the number of teeth on the rotor is 4. In one position, a tooth of the rotor dips into a tooth gap in the bore, while the opposite tooth of the rotor slides over the opposite tooth of the bore during the rolling motion. The more the elastomeric lining has grown radially inward due to the temperature expansion, the smaller the distance between the apex of the tooth and the bottom of the opposite tooth gap, which increases the clamping force of the rotor accordingly.
- Eccentric screw pumps are also increasingly used to pump pure water. Water itself is a relatively good lubricant for the material pairing rubber-metal. Due to the frictional movement between the rotor and the inner wall of the stator, however, the water film is wiped off and a relatively wide strip leads to a dry contact between the lining and the rotor, which gives rise to increased squeaking noises.
- the starting point is initially a profile of the inner bore, as is usually used for eccentric screw pumps or eccentric screw motors according to the prior art.
- this profile obtained in this way, shallow grooves are provided, which are rounded with flank merges into the other profile.
- the profile of the inner bore is composed, as it were, of adjacent ribs which are separated from one another by the grooves.
- Such grooves may be on the crest surfaces of the teeth or in the Nominal 'ndetälern the inner bore of the stator, or are used both on the crest surfaces of the teeth as well as in the tooth gaps.
- the distance over which the rotor is in frictional contact with the lining as seen in the circumferential direction is significantly reduced with the same sealing effect. At the same time, the contact pressure can be reduced.
- stator according to the invention is advantageous both in the case of eccentric screw arrangements which work as a pump and in those which work as a motor.
- the sheath that surrounds the elastomeric liner can optionally delimit a cylindrical interior or a helical interior.
- the thickness of the elastomeric lining is approximately the same at all points, while in the cylindrical interior in the area of the teeth of the bore it is significantly thicker and therefore more flexible.
- the additional ribs or grooves can be provided not only on the crowns of the teeth or in the tooth gaps but also on the flanks that connect the crowns of the teeth to the tooth gaps.
- the dimensions of the ribs or grooves, as seen in the circumferential direction, can be larger on the apex of the teeth than in the tooth gaps. Particularly favorable conditions result when the ribs on the teeth lie symmetrically with respect to an apex line which follows the contour of the tooth and which is at the smallest radial distance from the bore axis. There is therefore no rib directly on the apex line.
- the same structure can also be used in the tooth gap.
- a particularly favorable arrangement with regard to the tooth gap results if a rib runs directly in the valley line which is at the greatest radial distance from the axis of the bore. In this way, in the Tooth gap in which the tooth of the rotor nestles most can be supported particularly softly.
- the cross-sectional profile seen through the rib in the circumferential direction of the bore is largely symmetrical.
- the pitch of the ribs or grooves can be equal to the pitch of the stator or the pitch of the rotor, or can have a value in between.
- a different pitch has particular advantages if water is to be pumped or if water is used as the drive medium.
- the grooves create lubrication chambers, as it were, from which water can be released for lubrication.
- FIG. 1 is an overall perspective view of an eccentric screw pump according to the invention
- FIG. 2 shows a section through the stator of the eccentric screw pump, including a section of the rotor, in a longitudinal section
- 3 shows the eccentric screw pump according to FIG. 1, in a cross section perpendicular to the longitudinal axis
- FIG. 4 shows the cross section according to FIG. 3 with a part removed
- FIG. 5 shows the separated part according to FIG. 4 in an enlarged view
- FIG. 6 shows the detail according to FIG. 5, illustrating the ribs and grooves in relation to a flat profile
- Fig. 7-9 different engagement relationships between the rotor and the stator in the region of the tooth tip of the stator or the tooth space and
- Fig. 10 shows a stator with a cylindrical jacket, in a cross section.
- Figure 1 shows a schematic perspective view of an eccentric screw pump 1 according to the invention as an example of a corresponding displacement machine with the structure according to the invention.
- the device shown can also be an eccentric screw motor, as is used, for example, in oil wells.
- the center screw pump 1 includes a pump head 2, a stator 3, in which a rotor 4, shown broken off in FIG. 2, rotates, and a connection head 5.
- the pump head 2 has an essentially cylindrical cal 6 housing, which is provided at one end with an end cover 7, through which a drive shaft 8 is sealed to the outside.
- the end of the housing 6 remote from the cover 7 is provided with a clamping flange 12, the diameter of which is larger than the diameter of the essentially cylindrical housing 6.
- the clamping flange 12 contains a stepped bore 13 which is flush with the interior of the housing 6. In the stepped bore 13, a not recognizable stop shoulder is formed, against which the stator 3 is pressed in an essentially sealed manner.
- connection head 5 has a clamping flange 14 which interacts with the clamping flange 12 and also contains a stepped bore in which the other end of the stator 3 is inserted. A pipeline 15 leading away is aligned with the stepped bore.
- the stator 3 is tightly clamped between the two clamping flanges 12 and 14 with the aid of a total of four tie rods 16.
- the two clamping flanges 12 and 14 are each provided with four mutually aligned bores 17 which lie on a pitch circle which is larger than the outer diameter of the housing 6 or the tube 15 rod-shaped tie rod 16 therethrough.
- 16 nuts are on the tie rods
- the stator 3 consists of a tubular jacket 19 with a constant wall thickness, which surrounds an interior 20.
- the jacket 19 consists of plastic, steel, a steel alloy, light metal or a light metal alloy. It is shaped in such a way that an inner wall 21 takes the form of a multi-start screw. Its outside 22 has a correspondingly similar shape, with a diameter which is larger than the diameter of the interior 20 of the jacket 19 in accordance with the wall thickness of the jacket 19.
- the jacket 19 ends at its ends with end faces 23 and 24 which run at right angles with respect to its longitudinal axis 25.
- the longitudinal axis 25 is the axis of the interior 20.
- the interior 20 of the shape of a two-start screw.
- the cross section surrounded by the outer surface 22, viewed at right angles to the longitudinal axis 25, has the shape of an oval, similar to a racetrack.
- the ends can also be shaped into cylindrical tubes.
- the end ring 26 contains a through opening 27, which with the course of the outer surface 22 over the Length of the end ring 26 matches.
- the end ring 26 acts in the broadest sense like a nut which is screwed onto the thread which is defined by the jacket 19.
- the length of the thread corresponds to the thickness of the end ring -26.
- the end ring 26 is delimited radially outwards by a cylindrical surface 28 which merges in the axial direction into a flat surface 29 which points away from the jacket 19.
- the jacket 19 is provided with a continuous lining 32 over its entire length.
- the lining 32 consists of an elastically flexible, preferably elastomeric material, for example natural rubber or synthetic material, and has approximately the same wall thickness at each point.
- FIG. 3 shows a cross section through the stator 3 with the rotor 4 contained therein, however, in deviation from the previous exemplary embodiment, a stator with a 5-start internal bore and a rotor with a 4-start thread shape are used.
- Figure 3 suggests the allegory of a gear transmission, in which a four-toothed pinion rolls in a five-toothed ring gear.
- the ring gear and pinion are helically toothed and mesh with each other over the entire length. Accordingly, the areas that stand outward from the rotor 4 are referred to below as teeth 35 and the areas located therebetween as tooth gaps 36.
- the cross-sectional profile is similar to a rounded cycloid profile.
- the inwardly projecting regions of the stator 3 are also referred to as teeth 37 and the gaps between them as tooth gaps 38.
- stator 3 together with the rotor 4 produces several pump chambers which are separated in the circumferential and longitudinal directions during rotation, which have approximately a banana-shaped shape and, in the case of a pump, move towards the end with the higher pressure and move to the end with the lower pressure in the case of a motor.
- the wall thickness of the elastomeric lining 32 changes considerably with the temperature. Accordingly, the clear width of the space which is delimited by the elastomeric lining 32 is reduced. The distance between a tooth 37 and an opposite tooth gap 38 decreases, so that the pretension with which the elastomeric lining rests on the teeth 35 of the rotor 4 increases. With a corresponding increase in temperature, the change in the clear width can become so great until the rotor 4, when moving with a tooth 35, damages the tooth 37 of the elastomeric lining 32 in contact with it on the apex.
- each tooth 37 is provided with grooves 39 and / or ribs 41. hen.
- a section 42 is separated from the stator 3 according to FIG.
- Section 42 is shown enlarged in FIG.
- the ribs 41 and the grooves 39 lying between them can be clearly seen.
- the cutout 42 is shown stretched in FIG. the fundamental ripple, which the course of the teeth 37 and the tooth gaps 38 produces, is subtracted, with which the ideal profile line 43, which defines the teeth 37 and the tooth gaps 38 between them, is shown as a straight line.
- A the point which has the greatest radial distance from the axis 25 in the tooth gap 38 is designated by A and the apex line of the tooth 37 is denoted by N.
- the positions in between B to M fall with apexes of ribs, Vertex lines composed of grooves or intersections at which the actual contour line, the smoothed contour intersects in accordance with the straight line 43.
- Ribs 41a and 41b rise on both sides of the groove 39a. These ribs rise above the profile line 43, ie they protrude more into the interior than corresponds to the ideal contour line 44.
- Rib 41a there is again a groove 39b, on which the actual contour line 43 radially recedes compared to the smoothed contour line 44.
- the groove 39b ends at point E.
- the actual contour line 44 intersects the smoothed line 43 subsequently forming the rib 41c.
- the rib 41c ends at the point G on the smoothed contour line 43. This is followed by a rib 41d which merges into a groove 39c at E.
- the groove 39c is in turn deeper than it corresponds to the smoothed contour line 43.
- the actual contour line 44 meets the smoothed contour line 43, a small rib 41e still rising between this point and the groove 39c.
- grooves 39, 41 are located not only on the apex surfaces of the teeth 37 or in the deepest regions of the tooth spaces 38, but also in the flank surfaces which connect the apex surfaces with the valleys of the tooth spaces 38.
- the "wavelength” that arises due to the grooves 39 and the ribs 41 is significantly smaller than that of the "fundamental wave” formed by the teeth 37 and the ' tooth gaps 38. It is approximately that 8 times, ie between two tooth gaps 38 there are at least 8 depressions and / or elevations.
- the height ie the amplitude, measured between the lowest point between two ribs or a groove and the highest point of an adjacent rib, on the other hand, is only a fraction of the wall thickness of the elastomeric lining 32 at the relevant point,
- the amplitude is in the range between 0.1 mm and 5 mm, preferably between 0.1 mm and 2 mm, most preferably between 0.2 mm and 0.8 mm, or twice; in percentages based on the thickness of the elastomeric lining 32 between 1% and 50%, preferably between 1.5% and 30% and most preferably between 2% and 20%.
- 7-9 show several phases of the interaction between the rotor 4 and the inner wall of the elastomeric lining 32.
- a line 45 represents the outer contour of the rotor 4.
- the apex of the tooth 35 is directly opposite the apex of a tooth 37.
- the contour line 44 intersects the two ribs 41a and 41b while not reaching the bottom of the groove 39a. This creates space if, during the actual operation of the number 35, a shaft made of elastomeric material slides in front of it. This material can be displaced into the groove 39a for a short time. As a result, a lower contact pressure is generated while maintaining the sealing effect, which is achieved at this position by two ribs, namely the two ribs 41a and 41b.
- the contact pressure is the degree of coverage of the two the contour lines 44 and 45 are roughly proportional, ie the more the contour line 44 penetrates into the interior of the area delimited by the contour line 45, the more the elastomeric lining 32 must be deformed at the point in question when the tooth 35 passes. In the extreme position, as represented in FIG. 7, only a very slight deformation is evidently required. At the same time, a good sealing effect is achieved because ultimately two contact points are available for sealing between adjacent chambers, so that only half of the pressure difference is present at each rib.
- FIG. 7 also shows that the thermal expansion of the elastomeric lining 32 does not have such a strong effect on the Norspannkraft compared to a situation in which the 39ut 39a is missing and instead the previously smoothed contour profile corresponding to the contour line 43 occurs in this area , As a result of the groove 39a, the thickness of the elastomeric lining 32 can increase, and yet the space is kept free so that the bow wave running in front of the tooth 35 can be displaced into the groove without damaging the elastomeric lining 32 at this point.
- FIG. 8 shows a situation in which the tooth 35 has moved a little further, in a position in which there is a maximum overlap between the contour line 44 of the tooth 35 and the contour line 43 of the undeformed elastomeric lining 32.
- FIG. 9 finally illustrates the situation in which a tooth 35 penetrates maximally into a tooth gap 38 of the stator 3.
- the coverage between the vertex of the contour line 44 and the valley of the tooth gap 38 is extremely small, i.e. there is only a slight preload.
- the ribs 41d and 41c also produce only slight constraints.
- the inventive contour of the bore in the stator makes it possible to enlarge the working temperature range of the eccentric screw pump or of the eccentric screw motor. This means that a sensible seal occurs both in the cold state, while in the upper temperature range there are no excessive Tension arises.
- the contour according to the invention can not only be used in those arrangements in which the elastomeric lining 32 has approximately the same wall thickness at every point along the circumference. It can also be used in arrangements as shown in FIG.
- the jacket 19 has the shape of a cylindrical tube with a cylindrical interior.
- the outer contour of the elastomeric lining 32 is correspondingly cylindrical. The wall thickness in the area of a tooth is thus significantly greater than in the area of a tooth gap 38.
- the contour according to the invention consisting of ribs and grooves is nevertheless advantageous. If the temperature increased, the wall thickness in the area of the tooth would increase more than the wall thickness in the area of a tooth gap. As a result of the greater flexibility on the apex of the tooth, when using the rib and groove structure, the displacing effect emanating from the stronger tooth is reduced. The path disturbance which the axis of the rotor 4 suffers during the rolling motion remains smaller.
- eccentric screw pumps and eccentric screw motors ultimately differ only in the direction of flow of the medium and, if appropriate, in the pitch of the thread that defines the teeth, with cases also occurring in which the pitch of the pump is equal to the pitch of motors.
- pitch of the thread that defines the teeth With cases also occurring in which the pitch of the pump is equal to the pitch of motors.
- the teeth protruding inwards in the stator and the tooth gaps located in between are provided with an additional groove and rib structure.
- the friction between the stator and the rotor is reduced because the contact pressure can be reduced while the sealing effect remains the same, or the contact area is reduced when the contact pressure is increased.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2003267376A AU2003267376A1 (en) | 2002-09-27 | 2003-09-17 | Eccentric screw pump |
CA2499833A CA2499833C (en) | 2002-09-27 | 2003-09-17 | Eccentric screw pump with increased temperature range |
GB0506291A GB2408777B (en) | 2002-09-27 | 2003-09-17 | Eccentric screw pump with increased temperature range |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10245497.3 | 2002-09-27 | ||
DE10245497A DE10245497C5 (de) | 2002-09-27 | 2002-09-27 | Exzenterschneckenpumpe mit vergrößertem Temperaturbereich |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004031584A1 true WO2004031584A1 (de) | 2004-04-15 |
Family
ID=29762152
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/010341 WO2004031584A1 (de) | 2002-09-27 | 2003-09-17 | Exzenterschneckenpumpe |
Country Status (7)
Country | Link |
---|---|
US (1) | US6716008B1 (de) |
AU (1) | AU2003267376A1 (de) |
CA (1) | CA2499833C (de) |
DE (1) | DE10245497C5 (de) |
GB (1) | GB2408777B (de) |
RU (1) | RU2318134C2 (de) |
WO (1) | WO2004031584A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017104768A1 (de) | 2017-03-07 | 2018-09-13 | Seepex Gmbh | Exzenterschneckenpumpe |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA2543554C (en) * | 2003-10-27 | 2010-03-09 | Dyna-Drill Technologies, Inc. | Asymmetric contouring of elastomer liner on lobes in a moineau style power section stator |
US9051780B2 (en) | 2007-01-09 | 2015-06-09 | Schlumberger Technology Corporation | Progressive cavity hydraulic machine |
CA2673720C (en) * | 2007-01-24 | 2013-04-16 | Halliburton Energy Services, Inc. | Electroformed stator tube for a progressing cavity apparatus |
EP2136962B1 (de) * | 2007-04-18 | 2010-10-20 | National Oilwell Varco, L.P. | Antriebssysteme und-verfahren mit einer spindel mit langer reichweite |
US7837451B2 (en) * | 2008-02-29 | 2010-11-23 | General Electric Company | Non-contact seal for positive displacement capture device |
RU2471076C2 (ru) * | 2008-05-16 | 2012-12-27 | Шлюмбергер Текнолоджи Б.В. | Винтовая гидромашина |
US20110058930A1 (en) * | 2009-09-04 | 2011-03-10 | Robbins & Myers Energy Systems L.P. | Motor/pump with spiral wound stator tube |
US8523545B2 (en) * | 2009-12-21 | 2013-09-03 | Baker Hughes Incorporated | Stator to housing lock in a progressing cavity pump |
JP5605776B2 (ja) * | 2010-06-07 | 2014-10-15 | 兵神装備株式会社 | 一軸偏心ねじポンプ |
US8905733B2 (en) * | 2011-04-07 | 2014-12-09 | Robbins & Myers Energy Systems L.P. | Progressing cavity pump/motor |
US20130052067A1 (en) * | 2011-08-26 | 2013-02-28 | Baker Hughes Incorporated | Downhole Motors and Pumps with Improved Stators and Methods of Making and Using Same |
US8888474B2 (en) * | 2011-09-08 | 2014-11-18 | Baker Hughes Incorporated | Downhole motors and pumps with asymmetric lobes |
DE102012001417A1 (de) * | 2012-01-26 | 2013-08-01 | Netzsch-Feinmahltechnik Gmbh | Verfahren zum Herstellen von Fettmassen |
CN102705233A (zh) * | 2012-06-04 | 2012-10-03 | 中国石油天然气股份有限公司 | 采油等壁厚螺杆泵定转子间配合方法 |
DE102013102979B4 (de) | 2013-03-22 | 2017-03-30 | Wilhelm Kächele GmbH | Exzenterschneckenmaschine |
DE102015104549A1 (de) * | 2015-03-26 | 2016-09-29 | Netzsch Pumpen & Systeme Gmbh | Dichtlinienoptimierte Exzenterschneckenpumpe |
FR3081519B1 (fr) * | 2018-05-23 | 2020-05-29 | Pcm Technologies | Element de stator d'une pompe a cavites progressives et pompe a cavites progressives |
DE102019005367B4 (de) * | 2019-07-31 | 2023-01-19 | Pumpenfabrik Wangen Gmbh | Verfahren zur Herstellung eines Statorbauteil für eine Exzenterschneckenpumpe, Statorbauteil und Exzenterschneckenpumpe |
FR3108345B1 (fr) * | 2020-03-20 | 2023-04-21 | Pl2M | Machine de chantier |
DE102020004334A1 (de) | 2020-07-20 | 2022-01-20 | Wilhelm Kächele GmbH | Stator für Exzenterschneckenmaschine |
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US4764094A (en) * | 1985-07-22 | 1988-08-16 | Vsesojuzny Nauchno-Issledovatelsky Institut Burovoi Tekhniki | Screw machine having a plurality of symmetrically arranged rotors |
DE19534774A1 (de) * | 1995-09-19 | 1997-03-20 | Artemis Kautschuk Kunststoff | Exzenterschneckenpumpe |
DE29911031U1 (de) * | 1999-06-24 | 2000-11-23 | Artemis Kautschuk- und Kunststofftechnik GmbH & Cie, 30559 Hannover | Nach dem Moineau-Prinzip arbeitender Bohrmotor für Tiefbohrungen |
DE19950257A1 (de) * | 1999-10-18 | 2001-04-26 | Wilhelm Kaechele Gmbh Elastome | Exzenterschneckenpumpe mit vollausgekleidetem Stator |
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DE1916195U (de) * | 1962-07-26 | 1965-05-20 | Eugen Soeding | Exzenterschnekkenpumpe. |
DE1553149A1 (de) * | 1966-04-20 | 1970-10-08 | Netzsch Maschinenfabrik | Speisevorrichtung fuer Schneckenpumpen |
US3499389A (en) * | 1967-04-19 | 1970-03-10 | Seeberger Kg | Worm pump |
DE2017620C3 (de) * | 1970-04-13 | 1981-07-16 | Gummi-Jäger KG GmbH & Cie, 3000 Hannover | Exzenterschneckenpumpe |
DE2259125A1 (de) * | 1972-12-02 | 1974-06-06 | Streicher Foerdertech | Exzenterschneckenpumpe |
FR2343906A1 (fr) * | 1976-03-09 | 1977-10-07 | Mecanique Metallurgie Ste Gle | Perfectionnements aux stators de pompes a vis |
CA1208072A (en) * | 1983-08-16 | 1986-07-22 | Minoru Saruwatari | Progressive cavity pump |
DE3724023A1 (de) * | 1987-07-21 | 1989-02-02 | Gummi Jaeger Kg Gmbh & Cie | Verfahren zur herstellung von statoren fuer exzenterschneckenpumpen |
-
2002
- 2002-09-27 DE DE10245497A patent/DE10245497C5/de not_active Expired - Lifetime
- 2002-10-09 US US10/267,617 patent/US6716008B1/en not_active Expired - Lifetime
-
2003
- 2003-09-17 AU AU2003267376A patent/AU2003267376A1/en not_active Abandoned
- 2003-09-17 WO PCT/EP2003/010341 patent/WO2004031584A1/de not_active Application Discontinuation
- 2003-09-17 CA CA2499833A patent/CA2499833C/en not_active Expired - Lifetime
- 2003-09-17 RU RU2005112737/06A patent/RU2318134C2/ru active
- 2003-09-17 GB GB0506291A patent/GB2408777B/en not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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US4764094A (en) * | 1985-07-22 | 1988-08-16 | Vsesojuzny Nauchno-Issledovatelsky Institut Burovoi Tekhniki | Screw machine having a plurality of symmetrically arranged rotors |
DE19534774A1 (de) * | 1995-09-19 | 1997-03-20 | Artemis Kautschuk Kunststoff | Exzenterschneckenpumpe |
DE29911031U1 (de) * | 1999-06-24 | 2000-11-23 | Artemis Kautschuk- und Kunststofftechnik GmbH & Cie, 30559 Hannover | Nach dem Moineau-Prinzip arbeitender Bohrmotor für Tiefbohrungen |
DE19950257A1 (de) * | 1999-10-18 | 2001-04-26 | Wilhelm Kaechele Gmbh Elastome | Exzenterschneckenpumpe mit vollausgekleidetem Stator |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017104768A1 (de) | 2017-03-07 | 2018-09-13 | Seepex Gmbh | Exzenterschneckenpumpe |
WO2018162360A1 (de) | 2017-03-07 | 2018-09-13 | Seepex Gmbh | Exzenterschneckenpumpe |
Also Published As
Publication number | Publication date |
---|---|
GB0506291D0 (en) | 2005-05-04 |
AU2003267376A1 (en) | 2004-04-23 |
DE10245497C5 (de) | 2009-02-19 |
CA2499833A1 (en) | 2004-04-15 |
US6716008B1 (en) | 2004-04-06 |
DE10245497B3 (de) | 2004-01-22 |
GB2408777B (en) | 2006-01-11 |
RU2318134C2 (ru) | 2008-02-27 |
CA2499833C (en) | 2010-11-23 |
GB2408777A (en) | 2005-06-08 |
RU2005112737A (ru) | 2005-09-20 |
US20040062669A1 (en) | 2004-04-01 |
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