EP1303702A1 - Rotors a vis jumelles et machines volumetriques les contenant - Google Patents

Rotors a vis jumelles et machines volumetriques les contenant

Info

Publication number
EP1303702A1
EP1303702A1 EP01944852A EP01944852A EP1303702A1 EP 1303702 A1 EP1303702 A1 EP 1303702A1 EP 01944852 A EP01944852 A EP 01944852A EP 01944852 A EP01944852 A EP 01944852A EP 1303702 A1 EP1303702 A1 EP 1303702A1
Authority
EP
European Patent Office
Prior art keywords
pitch
twin screw
gradient
screw rotors
rotors
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
EP01944852A
Other languages
German (de)
English (en)
Other versions
EP1303702B1 (fr
Inventor
Ulrich Becher
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.)
Busch SA Atel
Ateliers Busch SA
Original Assignee
Busch SA Atel
Ateliers Busch SA
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 Busch SA Atel, Ateliers Busch SA filed Critical Busch SA Atel
Publication of EP1303702A1 publication Critical patent/EP1303702A1/fr
Application granted granted Critical
Publication of EP1303702B1 publication Critical patent/EP1303702B1/fr
Priority to CY20101101166T priority Critical patent/CY1110996T1/el
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/605—Balancing

Definitions

  • Rotors are described in which rotors and / or housings are composed of profile disks of different thicknesses and / or contours arranged axially one behind the other, and in this way bring about an internal compression. Since damaged areas and vortex zones arise due to the stepped structure, there is a reduced efficiency compared to screw rotors. In addition, problems regarding the constancy of shape during heating during operation are to be expected.
  • Screw compressors with external engagement of the counter-rotating screw rotors are represented by several publications:
  • DE 609405 describes pairs of screws with variable pitch and depth for the operation of compressors and expansion devices in air cooling machines.
  • a special front profile is not specified, the visual impression indicating a 1-start trapezoidal axial cut. There is no indication of balancing, although high speeds are to be used.
  • DE 4 445 958 describes a screw compressor with counter-rotating, intermeshing screw elements "which continuously decrease in size from one axial end to the second axial end distant therefrom ". They are used in vacuum pumps, motors or gas turbines. The profile is shown as a rectangular profile; an embodiment with a trapezoidal thread is optionally proposed. There is no evidence of balancing here either.
  • EP 0697523 describes a compressor type with screw rotors with multi-start, intermeshing profiles and continuous change in pitch.
  • the point-symmetrical profiles (S.R.M. profiles) directly effect a static and dynamic balancing.
  • DE19530662 discloses a screw suction pump with externally intermeshing screw elements, "wherein the pitch of the screw elements continuously decreases from their inlet end to their outlet end in order to cause the gas to be released to be compressed".
  • the shape of the teeth of the screw rotor has an epitrochoidal and / or Archimedean curve.
  • the disadvantage of such rotors is that the internal compression that can be achieved is massive.
  • twin screws are proposed, the gradient of which is not monotonous, but first increasing, then decreasing and finally remaining the same.
  • the front profile is catchy and asymmetrical and has a hollow flank.
  • the outside diameter is constant, and profile variation is possible.
  • the ratio of aisle depth / aisle height is limited to values c / d ⁇ 4, which limits the compression rates that can be achieved or increases the installation space.
  • the problem worsens as the number of gears increases.
  • the manufacturing effort increases with an increasing number of gears, so that in principle single-speed rotors would be desirable, provided that the problem of balancing can then still be solved satisfactorily, and multi-speed rotors are not altogether more advantageous or necessary for other reasons (for example rotor cooling).
  • - Material can be chosen as freely as possible (production, application).
  • the above-mentioned object is achieved in that in the case of the twin screw rotors, static and dynamic balancing is achieved or at least 80% achieved or at least 80% by changing the geometry in the area of the Screw ends is added.
  • Such rotors offer the best prerequisites for reducing energy requirements, temperature, size and costs, as well as for a free choice of materials for use in chemistry and semiconductor technology.
  • the following calculations represent the theoretical basics, which show that a screw rotor according to the present invention fulfills the condition of the balancing due to its shape.
  • FIG. 1 shows a set of single-start twin screw rotors in a first embodiment according to the invention in a view from the front
  • FIG. 2 shows the set of twin screw rotors of FIG. 1 in an end view
  • 3 shows the right-handed screw rotor in an axial section along the line A - A of FIG. 2
  • FIG. 11 shows a set of twin screw rotors according to a further exemplary embodiment of the invention in a view from the front
  • FIG. 12 shows the set of twin screw rotors from FIG. 11 in an end view
  • 13 shows the most general case of a gradient course according to the invention
  • 14 shows a possible gradient profile of a pair of twin screw rotors according to FIG. 11,
  • FIG. 16 shows a set of two-speed twin screw rotors according to a further exemplary embodiment of the invention in a view from the front
  • Fig. 18 seen the pair of screws of Figure 16 in an end view from the suction side
  • FIG. 19 shows the screw pair from FIG. 16 in an axial section along the line BB from FIG. 17.
  • Li, L 2 mean slopes of the areas T ⁇ , T 2 [cm]
  • FIG. 13 The most general case of a gradient course which effects a balancing in the sense of the invention is shown in FIG. 13:
  • the slope at the suction end is not the same as the slope at the pressure end. (L (1-A) ⁇ L 2 (1-B)).
  • the function h h ⁇ a> can be selected as required, while observing the symmetry properties and boundary conditions above. Once determined, A can be calculated from (*) in general.
  • a or V d are variable (FIG. 15).
  • the measures used here can be defined in a form that also applies to the above-mentioned corrections to the reduction of the helical flank edges that end in a pointed manner.
  • Measure 1 Additional values by increasing the wrap angle on both sides ⁇ .
  • the twin screw rotors 1 and 1 ' are cylindrical and have helical threads 3 and 3' which define a constant outside diameter which is limited by the lateral surfaces 6 and 6 '.
  • the twin rotors are arranged in parallel in such a way that the helical threads mesh with one another.
  • the outer surfaces 6 and 6 'of the rotors which describe two parallel intersecting cylinder surfaces during rotation, move adjacent to the housing 9 (shown in FIG. 2).
  • a sequence of chambers is defined between the core cylindrical surfaces 5, 5 ', the flanks 4, 4' and the housing wall 10, which moves from one axial end to the other when the rotors rotate in opposite directions, the chamber volume depending changed by the angle of rotation and the gradient: in the intake phase the volume increases to a maximum value, then in the compression phase the volume is reduced and finally after the Opening the chamber during the ejection phase reduces the volume to zero.
  • the end faces of the rotors are designated 7 and 7 'on the intake side and 8 and 8' on the discharge side.
  • FIG. 2 shows a view of the end faces of the twin rotors on the ejection side (view from above in FIG. 1).
  • the illustration shows a projection of two intersecting parallel cylinders.
  • 2 and 2 ' represent the parallel axes of rotation of the rotors 1 and 1'.
  • the flanks are designated 4 and 4 ', while 8 and 8' are the adjacent end faces which delimit the rotors in the longitudinal direction.
  • 5 and 5 ' are the core cylindrical surfaces of the rotors which have a constant diameter.
  • the rotors are installed in a housing 9 with an inner wall 10; for the contactless operation of such machines, the column heights between the two rotors and between the rotors and the inner wall 10 are each about 1/10 mm.
  • the plane A - A is a sectional plane that defines a longitudinal section of the rotor according to FIG. 3.
  • Fig. 3 is the mentioned longitudinal sectional view through the plane A - A of Fig. 2.
  • the reference numerals correspond to those of Figs. 1 and 2.
  • the axis of rotation is here designated W (2 1 in Fig. 1 and 2).
  • W and U belong to the coordinate system U, V, W, which was used for the calculations.
  • the zero point of the coordinate system is located at that point on the axis W where the slope has a maximum value (turning point in the diagram in FIG. 4, w ⁇ >).
  • the pitch c is constant, while the pitch d is variable depending on the pitch of the helix.
  • FIG. 4 shows the right-handed screw rotor in a view from the front corresponding to the rotor on the right positioned in FIG. 1, as well as the associated development of the front profile center of gravity locus curve, which represents the dependence of the axial position (w) on the wrap angle ( ⁇ ). Since the cross-section of the sight-robbing rotor is constant regardless of the pitch of the helix, the cross-sections differ over the entire length of the rotor only by the angular position ⁇ with respect to the U-axis. The focus of the cross sections is not identical to the axis position W, but is positioned at a constant distance ro. That is why the common place describes all focal points of the cross sections a spiral line (see FIG.
  • the symbols given correspond to the definitions given earlier for the calculations ,
  • the wrap angle increase ⁇ and the relative position angle ⁇ of the balancing volume go are shown above and below.
  • FIG. 7 is a diagram showing the cross-sectional values (area F) of a closed chamber as a function of the angle ( ⁇ 0 ) of the geometric reference spiral and the angle of rotation ( ⁇ ).
  • FIG. 8 is a diagram illustrating the course of compression (% of the initial volume) in a closed chamber as a function of the angle of rotation ( ⁇ ).
  • the same reference numbers were used for the same parts as in FIGS. 1 and 2.
  • FIG. 10 shows a block diagram that shows influencing variables and relationships that are important in the dimensioning of the rotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
  • Mixers Of The Rotary Stirring Type (AREA)
  • Rotary Pumps (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne des rotors à vis jumelles destinés à être montés de façon axialement parallèle dans des machines volumétriques destinées à des substances compressibles. Lesdits rotors présentent des profils apparents asymétriques et des nombres d'enroulements qui sont ≥ 2. De l'angle d'enroulement (α) dépend le pas (L) qui augmente dans une première partie (T1) à partir de l'extrémité de vis côté aspiration, atteint une valeur maximale (Lmax) après un enroulement, diminue dans une deuxième partie (T2) jusqu'à une valeur minimale (Lmin), et reste constant dans une troisième partie (T3). Le pas de vis dans la première partie (T1) présente de préférence une symétrie par rapport à un miroir par rapport à celui de la deuxième partie (T2). A l'intérieur des parties T1 à T2, le pas de vis présente pratiquement dans tous les cas une symétrie par rapport à un point jusqu'aux valeurs moyennes. Il est possible de réaliser, également sans variation de profil, des rotors à vis compacts complètement dépourvus de défaut d'équilibrage, ayant des taux de compression de 1,0...10,0. Des rotors de ce type présentent des avantages vis-à-vis de la diminution du besoin en énergie, de la température, de l'espace de montage, des coûts ainsi que du choix libre du matériau, et trouvent des applications en chimie, en pharmacie, dans le domaine des emballages et dans la technologie des semi-conducteurs.
EP01944852A 2000-07-25 2001-07-06 Rotors a vis jumelles et machines volumetriques les contenant Expired - Lifetime EP1303702B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CY20101101166T CY1110996T1 (el) 2000-07-25 2010-12-17 Διδυμοι κοχλιοφοροι ροτορες, του ειδους που εμπεριεχονται στις εκτοπιστικες μηχανες

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH01472/00A CH694339A9 (de) 2000-07-25 2000-07-25 Zwillingsschraubenrotoren und solche enthaltende Ve rdraengermaschinen.
CH147200 2000-07-25
PCT/CH2001/000421 WO2002008609A1 (fr) 2000-07-25 2001-07-06 Rotors a vis jumelles et machines volumetriques les contenant

Publications (2)

Publication Number Publication Date
EP1303702A1 true EP1303702A1 (fr) 2003-04-23
EP1303702B1 EP1303702B1 (fr) 2010-09-29

Family

ID=4565505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01944852A Expired - Lifetime EP1303702B1 (fr) 2000-07-25 2001-07-06 Rotors a vis jumelles et machines volumetriques les contenant

Country Status (22)

Country Link
US (1) US6702558B2 (fr)
EP (1) EP1303702B1 (fr)
JP (2) JP4162485B2 (fr)
KR (1) KR100737321B1 (fr)
CN (1) CN1242172C (fr)
AT (1) ATE483110T1 (fr)
AU (2) AU6724701A (fr)
BR (1) BR0112776A (fr)
CA (1) CA2417051C (fr)
CH (1) CH694339A9 (fr)
CY (1) CY1110996T1 (fr)
CZ (1) CZ305182B6 (fr)
DE (1) DE50115648D1 (fr)
DK (1) DK1303702T3 (fr)
ES (1) ES2353460T3 (fr)
HK (1) HK1058814A1 (fr)
HU (1) HUP0301145A2 (fr)
NO (1) NO20030357L (fr)
PL (1) PL202364B1 (fr)
PT (1) PT1303702E (fr)
TW (1) TW587128B (fr)
WO (1) WO2002008609A1 (fr)

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DE102005022470B4 (de) * 2005-05-14 2015-04-02 Pfeiffer Vacuum Gmbh Rotorpaar für Schraubenverdichter
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DE102010019402A1 (de) * 2010-05-04 2011-11-10 Oerlikon Leybold Vacuum Gmbh Schrauben-Vakuumpumpe
US8764424B2 (en) 2010-05-17 2014-07-01 Tuthill Corporation Screw pump with field refurbishment provisions
DE102011118050A1 (de) 2011-11-05 2013-05-08 Ralf Steffens Spindelverdichter-Profilkontur
CN102808771B (zh) * 2012-08-14 2015-01-07 东北大学 等齿顶宽的单头变螺距螺杆转子
CN102937094B (zh) * 2012-10-22 2016-05-04 台州职业技术学院 一种干式螺杆真空泵变螺距螺杆
CN103062057B (zh) * 2013-01-06 2015-11-25 南通大学 一种螺杆式真空泵
CN103982428A (zh) * 2013-02-07 2014-08-13 汉钟精机股份有限公司 一种双段螺旋导程真空泵
US11009034B2 (en) 2014-01-15 2021-05-18 Eaton Intelligent Power Limited Method of optimizing supercharger performance
CN105917100A (zh) * 2014-01-15 2016-08-31 伊顿公司 优化增压器性能的方法
CN105697373B (zh) * 2014-11-25 2017-08-25 巫修海 一种螺杆真空泵的螺杆
CN104696223B (zh) * 2015-03-27 2016-12-28 巫修海 螺杆真空泵自平衡螺杆转子
KR101712164B1 (ko) * 2015-06-11 2017-03-03 주식회사 와이엘테크 수직형 진공 펌프
CA3179438A1 (fr) * 2015-10-30 2017-05-04 Gardner Denver, Inc. Rotors a vis complexes
CN105485014B (zh) * 2016-01-05 2017-06-30 中国石油大学(华东) 一种等螺距变齿宽的螺杆转子
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
DE102016216279A1 (de) * 2016-08-30 2018-03-01 Leybold Gmbh Vakuumpumpen-Schraubenrotor
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Also Published As

Publication number Publication date
BR0112776A (pt) 2003-07-08
CZ20024019A3 (cs) 2003-05-14
TW587128B (en) 2004-05-11
KR20030026988A (ko) 2003-04-03
JP2004504546A (ja) 2004-02-12
US6702558B2 (en) 2004-03-09
JP4162485B2 (ja) 2008-10-08
NO20030357D0 (no) 2003-01-23
EP1303702B1 (fr) 2010-09-29
ES2353460T3 (es) 2011-03-02
ATE483110T1 (de) 2010-10-15
DK1303702T3 (da) 2011-01-24
NO20030357L (no) 2003-01-23
WO2002008609A1 (fr) 2002-01-31
CN1242172C (zh) 2006-02-15
CY1110996T1 (el) 2015-06-11
AU6724701A (en) 2002-02-05
HK1058814A1 (en) 2004-06-04
AU2001267247B2 (en) 2005-07-07
CZ305182B6 (cs) 2015-06-03
PT1303702E (pt) 2010-12-23
JP2008196505A (ja) 2008-08-28
PL202364B1 (pl) 2009-06-30
PL362974A1 (en) 2004-11-02
CH694339A5 (de) 2004-11-30
JP4677469B2 (ja) 2011-04-27
CA2417051A1 (fr) 2002-01-31
CA2417051C (fr) 2008-09-16
CN1444700A (zh) 2003-09-24
HUP0301145A2 (en) 2003-08-28
DE50115648D1 (de) 2010-11-11
US20030152475A1 (en) 2003-08-14
CH694339A9 (de) 2005-03-15
KR100737321B1 (ko) 2007-07-09

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