EP3698047A1 - Rotor à vis - Google Patents

Rotor à vis

Info

Publication number
EP3698047A1
EP3698047A1 EP18785346.0A EP18785346A EP3698047A1 EP 3698047 A1 EP3698047 A1 EP 3698047A1 EP 18785346 A EP18785346 A EP 18785346A EP 3698047 A1 EP3698047 A1 EP 3698047A1
Authority
EP
European Patent Office
Prior art keywords
displacement element
screw rotor
rotor according
screw
diameter
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.)
Granted
Application number
EP18785346.0A
Other languages
German (de)
English (en)
Other versions
EP3698047B1 (fr
Inventor
Thomas Dreifert
Stefan Wolter
Nils OLESEN
Roland Müller
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.)
Leybold GmbH
Original Assignee
Leybold GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Leybold GmbH filed Critical Leybold GmbH
Publication of EP3698047A1 publication Critical patent/EP3698047A1/fr
Application granted granted Critical
Publication of EP3698047B1 publication Critical patent/EP3698047B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type

Definitions

  • the invention relates to a screw rotor for a screw vacuum pump.
  • Screw vacuum pumps have a pump chamber in a housing, in which two screw rotors are arranged. Each screw rotor has at least one displacement element with a helical recess. As a result, a plurality of turns is formed.
  • the internal volume ratio is the ratio of the volume at the inlet of the vacuum pump to the volume at the outlet of the vacuum pump.
  • Screw-type vacuum pumps of the first generation such as the pumps LEYBOLD Screwiine or BUSCH Cobra have an internal volume ratio of approximately 3 to 4. With vacuum pumps currently on the market, such as the screw vacuum pump LEYBOLD DRYVAC or Edwards GXS, the volume ratio is 5 to 7.
  • the object of the invention is to provide a screw rotor for screw vacuum pumps, with which the power consumption can be reduced.
  • the invention is based on the finding that a reduction in energy consumption, by increasing the internal volume ratio is possible.
  • the outlet stages of the pump must have a small delivery volume.
  • small outlet stages have an unfavorable ratio of transport stream to backflow, i. they are relatively leaky. This means that only a relatively small increase in pressure can be generated with each individual stage. Nevertheless, in order to realize the majority of the compression in the small outlet stages, a high number of outlet turns is required.
  • screw rotors Basically, two types of screw rotors are known. These are screw rotors with a cylindrical or a conical outer dimension.
  • the gap at the outlet must be small at high internal volume ratios.
  • the tooth height is relatively large compared to the tooth gap width, which can be realized in the production only with great effort and high costs.
  • this rotor concept it is easily possible to integrate a large number of small outlet stages into the rotor (provided that the ratio of tooth height to tooth gap allows economic production).
  • the geometrically incorporated volume ratio is also thermodynamically effective.
  • the screw rotor according to the invention has a rotor shaft which is connected to at least two displacement elements, wherein each displacement element in each case has at least one helical recess.
  • a suction-side that is arranged in the direction of the pump inlet in particular at the pump inlet displacement element is formed tapering in the conveying direction.
  • the displacement element is arranged such that it tapers in the conveying direction, ie in the direction of the pump outlet.
  • the suction-side displacement element has an outer contour which is formed continuously decreasing in the conveying direction.
  • the cone angle is in this case a range of 2 ° to 8 °.
  • a pressure-side that is provided in the direction of the pump outlet in particular at the pump outlet displacement element is substantially cylindrical.
  • the pressure-side displacement element can also be slightly conical or slightly steadily decreasing in the conveying direction his.
  • the substantially cylindrically shaped pressure-side displacement element has in particular a diameter ratio of the suction-side, pointing in the direction of the pump inlet diameter to the pressure-side, pointing in the direction of the pump outlet diameter of 1.1 to 1.0.
  • further cylindrical and / or conical displacement elements can be arranged on the rotor shaft.
  • Essential according to the invention is the combination of a suction-side tapering, in particular conical displacement element with a pressure-side, substantially cylindrical displacement element.
  • a suction-side tapering, in particular conical displacement element with a pressure-side, substantially cylindrical displacement element.
  • the tooth height is reduced so that a large number of outlet turns with small delivery volumes can be realized with a low ratio of tooth height to tooth width in the flow or conveying direction following, substantially cylindrical displacement element.
  • a conical suction-side arranged displacement element and a cylindrical pressure side arranged displacement element are provided in a particularly preferred embodiment.
  • the invention will be described with reference to this preferred embodiment, wherein in each case further displacement elements can be provided.
  • the adjacent displacement elements abut against each other at the end faces directed towards one another, in particular, or touch each other and have substantially the same diameter.
  • a substantially stepless transition is realized.
  • the provision of two displacement elements thus reduces starting from the pump peneinlass the diameter of the conical displacement element to a diameter corresponding to the diameter of the cylindrical displacement element.
  • the diameter of the cylindrical displacement element is smaller by 5 to 35%, preferably 10 to 25%, than the suction-side diameter of the conical displacement element, that is to say in particular the diameter of the conical displacement element provided at the inlet of the pump.
  • the lengths and diameters of the conical and the cylindrical displacement element are selected such that a large part of the compression takes place at low suction pressure through the cylindrical displacement element. In particular, more than 70 percent of the compaction performance is performed by the cylindrical displacement element.
  • the conical displacement element has an inner volume ratio of more than 4, in particular more than 8
  • the cylindrical displacement element has an inner volume ratio of more than 1, in particular more than 3.
  • the internal compression is preferably carried out by reducing the pitch.
  • the ratio of the tooth height to the tooth width in the outlet region of the vacuum pump is less than 3. It is a cheap production possible. In particular, the ratio is in the range of 1.8-2.2. In a further preferred embodiment of the invention, the length of the substantially cylindrical displacement element is 25-50% of the entire profile length of the screw rotor.
  • the ratio of the outer diameter of the displacement element at the pump outlet to the outer diameter of the displacement element at the pump inlet is less than 0.9, in particular less than 0.85.
  • the diameter of the tapered displacement element in the region of the pump inlet is 80-300 mm.
  • the diameter is preferably 65-180 mm.
  • the outer diameter of the substantially cylindrical displacement element is also 65-180 mm, wherein in the case of a possibly slightly tapering cylindrical displacement element, this diameter may also be slightly smaller than the diameter in the transition region.
  • the number of turns of the cylindrical displacement element is at least 6 or preferably at least 10 and more preferably at least 12. By a high number of turns of the cylindrical displacement element can be done by this much of the compression.
  • the particular conical suction-side displacement element has in a preferred embodiment 3 to 6 turns.
  • the individual displacement elements are preferably formed as separate components and connected, for example by pressing with the rotor shaft.
  • individual or all connecting elements are integrally formed with the rotor shaft.
  • the rotor shaft further preferably has at both ends cylindrical lugs, which serve as a bearing mounts.
  • cylindrical lugs which serve as a bearing mounts.
  • the screw rotor according to the invention can be produced from the known materials, such as steel, cast iron or aluminum, the advantages of the invention being able to be realized in particular with screw rotors made of steel or cast iron.
  • a further displacement element is provided on the suction side.
  • the further displacement element is thus preceded by the tapered in the conveying direction in particular conical displacement element.
  • the further displacement element is preferably a displacement element which is likewise essentially cylindrical. It is preferred here that the pitch of the turns of this further displacement element decrease in the conveying direction.
  • the invention relates to a screw vacuum pump having two screw rotors arranged in a pump chamber formed by a housing.
  • the two screw rotors are designed or developed according to the invention. The invention will be explained in more detail with reference to a preferred embodiment with reference to the accompanying drawings.
  • the FIGURE shows a schematic side view of an embodiment of a screw rotor according to the invention.
  • the illustrated screw rotor has a rotor shaft 10, which carries two displacement elements 12, 14.
  • the two cylindrical ends 16, 18 of the rotor shaft serve to receive bearings, for mounting the screw rotor in a pump housing. It is also possible to fly the rotor shaft, i. one-sided store.
  • the right-hand displacement element 12 in FIG. 1 is conical and tapers in the direction of a pump outlet 24 (not shown) on the right-hand side, starting from a pump inlet 20, not shown in FIG.
  • a helical recess 26 of the conical displacement element 12 is formed such that the volume decreases.
  • this is realized on account of the conical outer shape of the displacement element 12 and, on the other hand, it is realized on account of the inner region 28 of the displacement element 12 which widens in the conveying direction.
  • Individual chamber volumes which are formed by the two meshing screw rotors thus reduce their volume in the conveying direction 22.
  • the cylindrical displacement element 14 has a likewise helical recess 34. In the illustrated embodiment, this has a constant slope, wherein for further compression in the conveying direction 22 and a reduction of the slope is possible. Through the recess 34 8 turns are formed in the illustrated embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un rotor à vis pour pompes à vide à vis, qui comprend un arbre de rotor (10) portant au moins deux éléments de déplacement (12, 14). Dans le sens de refoulement (22), l'élément de déplacement (12) est conique et l'élément de refoulement (14) se trouvant dans son prolongement est cylindrique.
EP18785346.0A 2017-10-17 2018-10-09 Rotor à vis Active EP3698047B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202017005336.5U DE202017005336U1 (de) 2017-10-17 2017-10-17 Schraubenrotor
PCT/EP2018/077471 WO2019076684A1 (fr) 2017-10-17 2018-10-09 Rotor à vis

Publications (2)

Publication Number Publication Date
EP3698047A1 true EP3698047A1 (fr) 2020-08-26
EP3698047B1 EP3698047B1 (fr) 2024-06-26

Family

ID=63832426

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18785346.0A Active EP3698047B1 (fr) 2017-10-17 2018-10-09 Rotor à vis

Country Status (7)

Country Link
US (1) US20200325897A1 (fr)
EP (1) EP3698047B1 (fr)
JP (1) JP2020537084A (fr)
KR (1) KR20200067143A (fr)
CN (1) CN111247341A (fr)
DE (1) DE202017005336U1 (fr)
WO (1) WO2019076684A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2608630A (en) * 2021-07-08 2023-01-11 Leybold Gmbh Screw pump, screw rotor, method of manufacturing a screw rotor, and use of a screw pump or a screw rotor

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE879861C (de) * 1950-08-04 1953-06-15 August Georg Schaefer Fuellwalze fuer Schneckenpressen zur Herstellung von duennwandigen, masshaltigen Strangartikeln, insbesondere von Umhuellungen fuer elektrische Leitungen
DE1281681B (de) * 1966-09-10 1968-10-31 Vickers Zimmer Ag Schneckenfoerdervorrichtung
US4132845A (en) * 1977-05-27 1979-01-02 E. I. Du Pont De Nemours And Company Mechanical dewatering process for elastomer slurries
US4792294A (en) * 1986-04-11 1988-12-20 Mowli John C Two-stage screw auger pumping apparatus
DE19800711A1 (de) * 1998-01-10 1999-07-29 Hermann Dipl Ing Lang Trockene Schraubenspindel Vakuumpumpe mit innerer Vorverdichtung
DK1070848T3 (da) * 1999-07-19 2004-08-09 Sterling Fluid Sys Gmbh Fortrængningsmaskine til kompressible medier
GB9930556D0 (en) * 1999-12-23 2000-02-16 Boc Group Plc Improvements in vacuum pumps
DE10334484A1 (de) * 2003-07-29 2005-03-24 Steffens, Ralf, Dr. Trockenverdichtende Spindelvakuumpumpe
CN201368025Y (zh) * 2009-03-16 2009-12-23 台州市星光真空设备制造有限公司 螺杆真空泵的改进结构
DE102012009103A1 (de) * 2012-05-08 2013-11-14 Ralf Steffens Spindelverdichter
CN103423160B (zh) * 2013-09-04 2015-11-25 张周卫 螺旋压缩膨胀制冷机用变螺距螺旋压缩机头
JP2015183572A (ja) * 2014-03-24 2015-10-22 樫山工業株式会社 真空ドライポンプのローターアセンブリおよびドライスクリューポンプ
CN105971877B (zh) * 2016-07-11 2017-11-14 中国石油大学(华东) 一种锥形螺杆转子及其双螺杆真空泵
CN106089708A (zh) * 2016-07-29 2016-11-09 扬州日上真空设备有限公司 复合双螺杆真空泵

Also Published As

Publication number Publication date
US20200325897A1 (en) 2020-10-15
WO2019076684A1 (fr) 2019-04-25
JP2020537084A (ja) 2020-12-17
KR20200067143A (ko) 2020-06-11
CN111247341A (zh) 2020-06-05
DE202017005336U1 (de) 2019-01-21
EP3698047B1 (fr) 2024-06-26

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