EP2063125B1 - Pompe Moineau - Google Patents

Pompe Moineau Download PDF

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Publication number
EP2063125B1
EP2063125B1 EP07021379A EP07021379A EP2063125B1 EP 2063125 B1 EP2063125 B1 EP 2063125B1 EP 07021379 A EP07021379 A EP 07021379A EP 07021379 A EP07021379 A EP 07021379A EP 2063125 B1 EP2063125 B1 EP 2063125B1
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EP
European Patent Office
Prior art keywords
section
parts
inner element
sections
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
EP07021379A
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German (de)
English (en)
Other versions
EP2063125A1 (fr
Inventor
Helge Grann
Sébastien D`Antonio
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.)
Grundfos Management AS
Original Assignee
Grundfos Management AS
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Filing date
Publication date
Application filed by Grundfos Management AS filed Critical Grundfos Management AS
Priority to EP07021379A priority Critical patent/EP2063125B1/fr
Priority to AT07021379T priority patent/ATE445782T1/de
Priority to DE502007001761T priority patent/DE502007001761D1/de
Priority to CN2008801144084A priority patent/CN101842595B/zh
Priority to US12/740,731 priority patent/US8308459B2/en
Priority to PCT/EP2008/008120 priority patent/WO2009056200A1/fr
Publication of EP2063125A1 publication Critical patent/EP2063125A1/fr
Application granted granted Critical
Publication of EP2063125B1 publication Critical patent/EP2063125B1/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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape

Definitions

  • the invention relates to a Moineau pump or a progressing cavity pump or eccentric screw compressor.
  • Moineau or progressing cavity pumps are z. B. off US 1,892,217 known as the next state of Tecknik.
  • These pumps have an annular outer member and an inner member disposed inside the outer member. Both the inside of the outer member and the outer side of the inner member have a helical structure, and the structure of the outer member has one more helix or one tooth.
  • the inner element moves in the interior of the outer element relative to this on an eccentric path, for which purpose the inner and / or the outer element can be moved.
  • the Moineau pump according to the invention or the Moineau compressor has a conically formed inner and a conically formed outer element.
  • the inner element has a central conical recess.
  • the outer element is annular in a known manner and has on its inner circumference a helical or helical structure.
  • the inner element is correspondingly formed helically on its outer circumference, wherein the helical structure of the outer element has a tooth or thread more than the structure on the outer circumference of the inner element.
  • the inner and outer members are arranged relative to one another such that their respective longitudinal axes are at an angle to each other and intersect at a point.
  • the pump is divided in the axial direction, ie in the conveying direction into at least two sections.
  • each section has a part of the outer element and a part of the inner element.
  • the parts of the inner element and the parts of the outer element are arranged rotated in the at least two sections against each other. That is, the portion of the inner member located in the second portion is twisted about the longitudinal axis of the inner member by a predetermined angle from the portion of the inner member located in the first portion.
  • the part of the outer element located in the second section is rotated by a certain angle relative to the part of the outer element located in the first section about the longitudinal axis of the outer element.
  • the offset in the rotational direction or twisted arrangement of the several sections or stages of the Moineau pump is achieved in that the axial force peaks do not occur at the same angular position of a drive shaft and the inner and outer element to each other, but rather occur the Axialkraftspitzen in both sections at different angles of rotation. In this way, the maximum occurring axial force is reduced because the axial force peaks do not add to the same angular position. Rather, the course of the axial force over the rotation angle of the drive shaft with twisted arrangement of the sections to each other so that a larger number of Axialkraftspitzen, but with lower amplitude occurs. Overall, a smoothed Axialkraftverlauf is thus achieved over the rotation angle. This reduces the overall load on the pump drive.
  • the pump has more than two sections or steps, wherein in each case in two adjoining sections, the part of the inner element located in a second section is arranged rotated relative to the part of the inner element situated in a first section about the longitudinal axis of the inner element is. Accordingly, the portion of the outer member located in the second portion is opposite the portion of the outer member located in the first portion about the longitudinal axis of the outer member arranged twisted.
  • all adjacent sections are preferably formed such that they form a first and a second section, in which the outer and inner elements are arranged rotated relative to one another as described.
  • the outer and inner members in the second portion opposite the inner and outer members in the first portion and then again in the third portion are the outer and inner members opposite the outer and inner members in the second Section twisted. Accordingly, in turn, in the fourth section, the outer and inner elements are then rotated relative to the outer and inner elements in the third section. In the case of even more sections, this continues accordingly.
  • the rotation from section to section preferably takes place in the same direction of rotation, so that overall all sections are rotated relative to one another and there are no two sections in which the outer or inner elements are arranged in the same angular orientation with respect to their longitudinal axis. This means that the angle by which the parts are rotated relative to each other can be dependent on the number of sections, so that between the first and last section the rotation of the parts is less than 360 °.
  • the parts of the inner element are rotated by a different angle to each other than the parts of the outer element. Due to the different number of threads on the inner and outer element, a particularly uniform running of the pump can be achieved.
  • the helical contour on the outer circumference of the inner element in all sections of the pump on the same slope. Accordingly, it is preferred that the helical contour on the inner circumference of the outer element in all sections of the Pump has the same slope. That is, the pitch of the thread of the inner and outer members is constant over the entire pump. More preferably, the number of revolutions of the threads in each section is the same.
  • n is the number of sections of the pump
  • m is the number of threads or teeth of the inner element.
  • these parts are respectively formed on the abutting front ends such that the largest cross-sectional area of the smaller part is completely within the smallest cross-sectional area of the larger part is located. In this way, it is ensured that the smaller part does not protrude beyond the outer circumference of the adjacent larger part at any point.
  • these parts are formed on the abutting end faces such that the maximum radius at the end side of the part located in the second section is smaller than the minimum radius at the front side of the part located in the first section is.
  • a spacer element between e.g. two adjacent parts of the inner element, e.g. arranged a spacer, which keeps the two parts spaced apart in the direction of the longitudinal axis. This ensures that a part of the inner element of a first section does not collide or come into contact with a part of the outer element in a second section. This means that it is ensured that a part of the inner element always only comes into contact exclusively with the associated part of the outer element. This is particularly important when the inner and outer elements are movable in the axial direction to each other.
  • the inner element is integrally formed over at least two sections, preferably over all sections. That is, the parts of the inner element, which are located in these two sections of the pump, are integrally formed, for example, metal or ceramic. This simplifies the production because no assembly and alignment of several items to form the inner member are required.
  • FIG. 2a shows in a side view and FIG. 2b in a perspective view of an inner element of a Moineau pump according to the invention.
  • the pump is divided into four sections, which are arranged one behind the other in the axial direction, ie in the longitudinal direction or conveying direction of the pump. This is in FIG. 3 shown.
  • the inner element 4 is correspondingly divided into four parts 4a, 4b, 4c, and 4d, the part 4a in the section 2a, the part 4b in the section 2b, the part 4c in the section 2c, and the part 4d in the section 2d of the pump is arranged.
  • the shape of the inner element according to Figures 2 and 3 arises starting from an inner element, as in FIGS. 1 a and 1 b is shown. It is in FIGS. 1 a and 1b, the inner element 4 with its four in the axial direction X 1 successively lined-up parts 4a to 4d formed without rotation between these parts. In this state, the outer periphery of the inner member 4 has a continuous helical structure.
  • the one or more screw threads 6 extend as a continuous helical shape over the entire axial length X 1 of the inner element 4, that is continuously over the four parts 4a to 4b.
  • the inner element 4 has a conical shape, ie, tapering from the axial end on the part 4b to the opposite axial end at the end of the part 4a.
  • the parts 4a to 4d are formed, or arranged to each other, that they are each rotated relative to each other about the longitudinal axis X 1 of the inner member 4 to each other. It is based on the state according to FIG. 1 the part 4c relative to the part 4d, the part 4b relative to the part 4c and the part 4c relative to the part 4b each rotated by the same angle in the same direction of rotation about the longitudinal axis X 1 .
  • the parts 4d are each rotated by 90 ° to the adjacent parts, ie, the portion 4c is 90 ° about the longitudinal axis X 1 twisted relative to part 4d.
  • the part 4b is rotated by 90 ° relative to the part 4c and corresponding to the part 4a by 90 ° relative to the part 4b.
  • the parts 4a to 4d need not be manufactured as individual parts and assembled, but rather the entire element 4, as in FIG. 2 is shown, also be made in one piece directly in the form shown there. At the in FIG.
  • the adjacent end faces of the parts 4a to 4d each have the same diameter. That is, for example, the diameter 22 of the part 4d on its side facing the part 4c is equal to the diameter 20 of the part 4c on its side facing the part 4d.
  • the outer element 8 is subdivided into four parts 8a, 8b, 8c and 8d, the part 8a in the section 2a, the part 8b in the section 2b, part 8c is located in section 2c and part 8b is located in section 2d of the pump. That is, in the part 8a of the outer member 8, the part 4a of the inner member 4 rotates. Accordingly, in the part 8b, the part 4b and so forth rotate.
  • the outer element 8 is annular in a known manner and has in its interior a recess 10 into which the inner element 4 is inserted.
  • the recess 10 is correspondingly formed conically with the inner element 4 and has on its inner circumference a helical structure with screw 12 on.
  • a helix is provided more than on the outer circumference of the outer element 4, ie in the case that the inner element 4 has two screw threads, the outer element 8 has on its inner circumference three screw threads.
  • the arrangement of the parts 8a to 8d of the outer member 8 is also formed from an outer member 8 with continuous threads from one axial end to the opposite axial end of the outer member 8.
  • the parts 8a to 8d are each rotated about the longitudinal axis X 2 of the outer element 8 to each other.
  • the longitudinal axis X 2 of the outer element is inclined, ie at an angle to the longitudinal axis X1 of the inner element. Both axes X 1 , X 2 intersect in a known manner in one point.
  • the part 8c of the outer element 8 is also opposite the part 8d by a certain angle about the longitudinal axis X 2 and corresponding part 8b relative to the part 8c by the same angle about the longitudinal axis X 2 and the part 8a relative to the part 8b also the same angle about the longitudinal axis X 2 arranged rotated or formed.
  • the direction of rotation of the rotation between the individual parts is the same.
  • the parts 8a to 8d of the outer element 8 can be manufactured as individual parts, which are then twisted together accordingly. Alternatively, it is also possible to form the parts in one piece directly in the twisted arrangement.
  • FIG. 4 schematically shows an inner element 4 consisting of four parts 4a, 4b, 4c and 4d, wherein in this arrangement different embodiments are combined with each other for explanation only.
  • the parts 4a, 4b, 4c and 4d in the direction of the longitudinal axis X 1 have different heights 14, 16 have. It should be understood that this is not limited to only parts 4a and 4d. Also, the parts 4d and / or 4c may have different heights.
  • the part 4c has, at its axial end facing the part 4d, a diameter 20 which is smaller in each direction than the diameter 22 at the axial end of the part 4d facing the part 4c.
  • the part 4c in the radial direction does not protrude beyond the outer periphery of the part 4d at its front end facing the part 4c.
  • the radial distance 24, 26 between the outer periphery of the part 4c at the end face thereof having the larger cross-sectional area and the outer periphery of the part 4d at the end face thereof having the smaller cross-sectional area is over the whole Scope greater than or equal to 0, but not less than 0. It is understood that the transition between the parts 4c and 4b and / or the part 4d and the part 4a can be designed accordingly. These embodiments ensure that the parts of the inner element 4 at the interfaces between the individual parts do not undesirably collide with the wrong, ie non-associated, parts of the outer element 8.
  • the inner part 4 c does not come into contact with the part 8 d of the outer element 8 and correspondingly the part 4 d of the inner element 4 can not come into contact with the part 8 c of the outer element 8.
  • FIG. 5 shows first the axial force which acts between the inner member 4 and the outer member 8, when the parts 4a to 4d and correspondingly the parts 8a to 8d are not rotated against each other, ie the pump according to an embodiment FIG. 1 having.
  • the axial force is plotted over the angle of rotation ⁇ .
  • individual curves 28a to 28d are shown which correspond to the forces acting on the individual parts 4a, 4b, 4c and 4d of the inner element 4.
  • the curve 30 shows the total force which acts on the inner element 4 or between inner 4 and outer 8 element. It can be seen that in the sawtooth course of the Force curves 28a to 28d the peaks, ie the maximum forces occurring all at the same angle, here at about 180 ° occur. This leads to a high total force 30 occurring at this angle.
  • FIG. 6 now shows a corresponding diagram for the arrangement according to FIG. 3 in which the parts 4a to 4d of the inner element and correspondingly the parts 8a to 8d of the outer element 8 are twisted against each other in the manner described above. It can be seen that, as a result, the courses 28a to 28d of the axial forces acting on the individual parts 4a to 4d are also shifted relative to each other by corresponding angles. This means that the force peaks or maximum forces, which act on the individual parts of the inner Eiementes 4, no longer occur all at the same angle of rotation ⁇ , but offset by corresponding angle.
  • Said axial forces are those axial forces which act through the fluid pressure in the interior of the pump between the inner element 4 and the outer element 8. That is, corresponding external forces must be applied to hold the inner member 4 against the outer member 8. By reducing the force peaks and reducing the total force, this pressure force can be reduced, thereby reducing friction and wear inside the pump.

Claims (10)

  1. Pompe ou compresseur Moineau comprenant un élément intérieur (4) de forme conique et un élément extérieur (8) de forme conique dont les axes longitudinaux (X1, X2) forment un angle l'un par rapport à l'autre et se coupent en un point,
    caractérisée en ce que
    la pompe présente, en direction axiale, au moins deux sections (2a, 2b, 2c, 2d),
    la partie (4b), située dans la deuxième section (2b), de l'élément intérieur (4) étant disposée décalée en rotation par rapport à la partie (4a), située dans la première section (2a), de l'élément intérieur (4) autour de l'axe longitudinal (X1) de l'élément intérieur (4),
    et
    la partie (8b), située dans la deuxième section (2b), de l'élément extérieur (8) étant disposée décalée en rotation par rapport à la partie (8a), située dans la première section (2a), de l'élément extérieur (8) autour de l'axe longitudinal (X2) de l'élément extérieur (8).
  2. Pompe Moineau selon la revendication 1, caractérisée en ce que la pompe présente plus de deux sections (2a-2d), où dans deux sections (2a-2b) contiguës,
    la partie (4b), située dans la deuxième section (2b), de l'élément intérieur (4) est disposée décalée en rotation par rapport à la partie (4a), située dans la première section (2a), de l'élément intérieur (4) autour de l'axe longitudinal (X1) de l'élément intérieur (4),
    et
    la partie (8b), située dans la deuxième section (2b), de l'élément extérieur (8) est disposée décalée en rotation par rapport à la partie (8a), située dans la première section (2a), de l'élément extérieur (8) autour de l'axe longitudinal (X2) de l'élément extérieur (8).
  3. Pompe Moineau selon la revendication 1 ou 2, caractérisée en ce que les parties (4a-4d) de l'élément intérieur (4) sont décalées en rotation l'une par rapport à l'autre d'une valeur angulaire différente de celle des parties (8a-8d) de l'élément extérieur (8).
  4. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce qu'un contour hélicoïdal (6) sur la périphérie extérieure de l'élément intérieur (4) présente le même pas dans toutes les sections (2a-2d) de la pompe.
  5. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce qu'un contour hélicoïdal (12) sur la périphérie intérieure de l'élément extérieur (8) présente le même pas dans toutes les sections (2a-2d) de la pompe.
  6. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce que la partie (4b), située dans la deuxième section (2b), de l'élément intérieur (4) est décalée en rotation relativement par rapport à la partie (4a), située dans la première section (2a), de l'élément intérieur (4) d'un angle a = 360 n × m
    Figure imgb0009
     et
    en ce que la partie (8b), située dans la deuxième section (2b), de l'élément extérieur (8) est décalée en rotation relativement par rapport à la partie (8a), située dans la première section (2a), de l'élément extérieur (8) d'un angle a = 360 n × m + 1 ,
    Figure imgb0010
     n étant le nombre des sections (2a-2d) de la pompe et m étant le nombre des pas de vis (6) de l'élément intérieur.
  7. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce que, s'agissant de deux parties (4c-4d) contiguës de l'élément intérieur (4), ces parties, au niveau des extrémités adjacentes, sont réalisées de façon telle que la plus grande surface de section transversale de la partie la plus petite est entièrement située à l'intérieur de la plus petite surface de section transversale de la partie la plus grande.
  8. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce que, s'agissant de deux parties (4c-4d) contiguës de l'élément intérieur (4), ces parties, au niveau des faces frontales adjacentes, sont réalisées de façon telle que le rayon maximum (20) sur la face frontale de la partie (4c) située dans la deuxième section (2c) est plus petit que le rayon minimum (22) sur la face frontale de la partie (4d) située dans la première section (2d).
  9. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce qu'est disposé, entre deux parties contiguës (4b, 4c) de l'élément intérieur (4), un élément d'écartement (18) qui maintient distantes les deux parties (4b, 4c) dans la direction de l'axe longitudinal (X1).
  10. Pompe Moineau selon l'une des revendications précédentes, caractérisée en ce que l'élément intérieur (4) est réalisé d'une seule pièce sur les sections, au moins au nombre de deux, (2a-2d).
EP07021379A 2007-11-02 2007-11-02 Pompe Moineau Active EP2063125B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP07021379A EP2063125B1 (fr) 2007-11-02 2007-11-02 Pompe Moineau
AT07021379T ATE445782T1 (de) 2007-11-02 2007-11-02 Moineau-pumpe
DE502007001761T DE502007001761D1 (de) 2007-11-02 2007-11-02 Moineau-Pumpe
CN2008801144084A CN101842595B (zh) 2007-11-02 2008-09-25 螺杆泵
US12/740,731 US8308459B2 (en) 2007-11-02 2008-09-25 Moineau pump
PCT/EP2008/008120 WO2009056200A1 (fr) 2007-11-02 2008-09-25 Pompe moineau

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07021379A EP2063125B1 (fr) 2007-11-02 2007-11-02 Pompe Moineau

Publications (2)

Publication Number Publication Date
EP2063125A1 EP2063125A1 (fr) 2009-05-27
EP2063125B1 true EP2063125B1 (fr) 2009-10-14

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Family Applications (1)

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EP07021379A Active EP2063125B1 (fr) 2007-11-02 2007-11-02 Pompe Moineau

Country Status (6)

Country Link
US (1) US8308459B2 (fr)
EP (1) EP2063125B1 (fr)
CN (1) CN101842595B (fr)
AT (1) ATE445782T1 (fr)
DE (1) DE502007001761D1 (fr)
WO (1) WO2009056200A1 (fr)

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CN107131142A (zh) * 2017-07-07 2017-09-05 中国科学院工程热物理研究所 离心式压缩机的启动控制装置及方法

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EP2532833B1 (fr) * 2011-06-10 2015-07-29 ViscoTec Pumpen-u. Dosiertechnik GmbH Elément de transport pour une pompe à vis sans fin excentrique et pompe à vis sans fin excentrique
US20130224053A1 (en) * 2011-10-03 2013-08-29 Jan Hendrik Ate Wiekamp Coaxial progressive cavity pump
CN102619747B (zh) * 2012-04-06 2014-11-05 北京工业大学 双锥对置锥螺杆高压海水液压泵
EP3108142B1 (fr) 2014-02-18 2017-11-15 Vert Rotors UK Limited Machine volumétrique rotative
CN103883522B (zh) * 2014-03-17 2016-03-02 北京工业大学 一种锥螺杆-衬套副的曲面成形方法
CN103862718B (zh) * 2014-04-02 2016-04-13 三能器具（无锡）有限公司 土司盒自动包边包角装置
FR3031786B1 (fr) 2015-01-19 2018-11-02 Safran Transmission Systems Integration d'une pompe en fut de pignon
US9776739B2 (en) 2015-08-27 2017-10-03 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
US10174973B2 (en) 2015-08-27 2019-01-08 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
DE202018104142U1 (de) 2018-07-18 2019-10-22 Vogelsang Gmbh & Co. Kg Rotor für eine Exzenterschneckenpumpe
US20220364559A1 (en) * 2019-05-14 2022-11-17 Schlumberger Technology Corporation Mud motor or progressive cavity pump with varying pitch and taper

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CN107131142A (zh) * 2017-07-07 2017-09-05 中国科学院工程热物理研究所 离心式压缩机的启动控制装置及方法
CN107131142B (zh) * 2017-07-07 2018-07-06 中国科学院工程热物理研究所 离心式压缩机的启动控制装置及方法

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Publication number Publication date
EP2063125A1 (fr) 2009-05-27
US8308459B2 (en) 2012-11-13
US20100260636A1 (en) 2010-10-14
CN101842595B (zh) 2013-06-05
WO2009056200A1 (fr) 2009-05-07
CN101842595A (zh) 2010-09-22
DE502007001761D1 (de) 2009-11-26
ATE445782T1 (de) 2009-10-15

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