EP1303702B1 - Zwillingsschraubenrotoren und solche enthaltende verdrängermaschinen - Google Patents

Zwillingsschraubenrotoren und solche enthaltende verdrängermaschinen Download PDF

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Publication number
EP1303702B1
EP1303702B1 EP01944852A EP01944852A EP1303702B1 EP 1303702 B1 EP1303702 B1 EP 1303702B1 EP 01944852 A EP01944852 A EP 01944852A EP 01944852 A EP01944852 A EP 01944852A EP 1303702 B1 EP1303702 B1 EP 1303702B1
Authority
EP
European Patent Office
Prior art keywords
pitch
rotors
twin screw
wrap
screw 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.)
Expired - Lifetime
Application number
EP01944852A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1303702A1 (de
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.)
Ateliers Busch SA
Original Assignee
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 Ateliers Busch SA filed Critical Ateliers Busch SA
Publication of EP1303702A1 publication Critical patent/EP1303702A1/de
Application granted granted Critical
Publication of EP1303702B1 publication Critical patent/EP1303702B1/de
Priority to CY20101101166T priority Critical patent/CY1110996T1/el
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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

  • Screw compressors with external engagement of counter-rotating screw rotors are represented by several publications:
  • DE 4 445 958 describes a screw compressor with counter rotating, outwardly meshing screw elements "which continuously decrease from one axial end to the second axial end remote therefrom ". They are used in vacuum pumps, motors or gas turbines. The profile is shown as a rectangular profile, optionally an embodiment with a trapezoidal thread is proposed. Again, there is no evidence of balancing.
  • EP 0697523 describes a type of compressor with screw rotors with multi-course external meshing profiles and continuous change of pitch.
  • the point-symmetric profiles (SRM profiles) directly effect static and dynamic balancing.
  • EP 1 070 848 are shown helical profile body with variable pitch, in two-speed design, "... to be better balanced ".
  • the reference to a special profile geometry is missing, the drawing shows a symmetrical rectangular profile in axial section.
  • DE19530662 discloses a screw suction pump with external meshing screw elements, "wherein the pitch of the screw elements continuously decreases from their inlet end to their outlet end to cause the compression of the gas to be delivered."
  • the shape of the teeth of the screw rotor has an epitrochoidal and / or Archimedian curve.
  • the pitch curve is not monotonous, but first rising, then sloping and last consistently.
  • the front profile is catchy and asymmetrical and has a hollow flank.
  • the outer diameter is constant, with a profile variation is possible.
  • the ratio of flight depth / pitch is limited to values c / d ⁇ 4, which leads to a limitation of the achievable compression rates or to an increase in the installation space.
  • the problem gets worse with increasing number of gears.
  • the production cost increases with increasing number of gears, so that in principle 1-speed rotors would be desirable, if the problem balancing can then be satisfactorily resolved, and not for other reasons (for example, rotor cooling) multi-speed rotors are more advantageous or necessary.
  • Such rotors offer the best conditions for the reduction of energy requirements, temperature, size and cost, and for a free choice of materials with application in chemistry and semiconductor technology.
  • the following calculations represent the theoretical principles showing that a screw rotor according to the present invention satisfies the condition of balance due to its shape.
  • w ⁇ 2 ⁇ G 0 - K - 2 ⁇ L 0 2 ⁇ 1 - A 2 / 2 ⁇ ⁇ + ⁇ - 2 ⁇ ⁇ + 2 ⁇ ⁇ w ⁇ ⁇ > w ' ⁇ ⁇ > sin ⁇ d ⁇ M u .
  • w ⁇ 2 ⁇ G 0 ⁇ - 2 ⁇ ⁇ + 2 ⁇ ⁇ w ⁇ ⁇ > w ' ⁇ ⁇ > cos ⁇ d ⁇
  • a or V d are variable ( FIG. 15 ).
  • Fig. 1 shows a representation of a first embodiment of the twin screw rotors 1 and 1 ', wherein the axes 2 and 2' are in the plane of the drawing.
  • the two rotors 1 and 1 ' are cylindrical and have thread helices 3 and 3', which define a constant outer diameter, which is bounded by the lateral surfaces 6 and 6 '.
  • the twin rotors are arranged in parallel in such a way that the thread helices intermesh with each other.
  • the housing 9 between the core cylinder surfaces 5, 5 'the flanks 4, 4' and the housing wall 10 defines a sequence of chambers, which moves in the opposite rotation of the rotors from one axial end to the other, wherein the chamber volume in dependence In the intake phase, the volume increases up 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 on the suction side with 7 and 7 'and on the ejection side with 8 and 8'.
  • Fig. 2 shows a view of the end faces of the twin rotors on the ejection side (top view in FIG 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 cylinder surfaces of the rotors having a constant diameter.
  • the rotors are installed in a housing 9 with an inner wall 10; for the non-contact operation of such machines, the gap 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 corresponding to a longitudinal section of the rotor Fig. 3 Are defined.
  • Fig. 3 is the mentioned longitudinal section through the plane A - A of Fig. 2 , The reference numerals correspond to those of Fig. 1 and 2 ,
  • the axis of rotation is here designated by W (2 '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 the position of the axis W, where the slope has a maximum value (inflection point in the diagram FIG. 4 , w ⁇ >).
  • the flight depth c is constant, while the pitch d, depending on the pitch of the helix, is variable.
  • Fig. 4 shows the right-hand screw rotor in a view from the front corresponding to the right-positioned rotor of Fig. 1 , as well as the associated development of the forehead profile centroid locus, which represents the dependence of the axial position (w) of the wrap angle ( ⁇ ). Since the cross section of the screw rotor is constant irrespective of the pitch of the helix, the cross sections over the entire length of the rotor differ only in the angular position ⁇ with respect to the U-axis. The center of gravity of the cross sections is not identical with the axis position W, but is positioned at a constant distance r 0 . That is why the common place describes all focal points of the cross sections a spiral line (cf. Fig.
  • the symbols given correspond to the definitions given earlier for the calculations.
  • the wrap angle increase ⁇ and the relative position angle ⁇ of the balance volume g Q are shown at the top and bottom.
  • 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 rotation angle ( ⁇ ).
  • Fig. 8 is a diagram showing the compression curve (% of the initial volume) in a sealed chamber as a function of the rotation angle ( ⁇ ).
  • Fig. 9 shows the symmetrical course of individual sub-functions of the slope and balance calculation (cos ⁇ , sin ⁇ , h ⁇ >, h ' ⁇ >, h " ⁇ >).
  • the same reference numbers were used for the same parts as in the Figures 1 and 2 , In these screws coincide the times of closure against the suction side and the opening to the pressure side for the central, fully formed chamber together, so that such equipped Verdrängermaschine works isochoric.
  • the time of opening to the pressure side can be delayed by a front-side end plate 11 with an outlet opening 12 which is closed and released by the rotor 1, as is known from the prior art.
  • an internal compression can be realized.
  • the reference 13 'in FIG. 16 denotes such a machined surface.
  • the large rotor surface, here by Mehrersonkeit and large Umschlingungskohl realized and coaxial cylinder bores (14, 14 ') in the rotors (1, 1'), through which a coolant flows, create the conditions for special applications in positive displacement pumps for the chemical, at which low gas temperatures are required.
  • the values Q and ⁇ in formulas (1c), (3c) and (4c) are compounded because the two-flighted screws at each end were removed at two locations 13 'material.

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)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
EP01944852A 2000-07-25 2001-07-06 Zwillingsschraubenrotoren und solche enthaltende verdrängermaschinen Expired - Lifetime EP1303702B1 (de)

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 (de) 2000-07-25 2001-07-06 Zwillingsschraubenrotoren und solche enthaltende verdrängermaschinen

Publications (2)

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

Family

ID=4565505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01944852A Expired - Lifetime EP1303702B1 (de) 2000-07-25 2001-07-06 Zwillingsschraubenrotoren und solche enthaltende verdrängermaschinen

Country Status (22)

Country Link
US (1) US6702558B2 (ja)
EP (1) EP1303702B1 (ja)
JP (2) JP4162485B2 (ja)
KR (1) KR100737321B1 (ja)
CN (1) CN1242172C (ja)
AT (1) ATE483110T1 (ja)
AU (2) AU2001267247B2 (ja)
BR (1) BR0112776A (ja)
CA (1) CA2417051C (ja)
CH (1) CH694339A9 (ja)
CY (1) CY1110996T1 (ja)
CZ (1) CZ305182B6 (ja)
DE (1) DE50115648D1 (ja)
DK (1) DK1303702T3 (ja)
ES (1) ES2353460T3 (ja)
HK (1) HK1058814A1 (ja)
HU (1) HUP0301145A2 (ja)
NO (1) NO20030357L (ja)
PL (1) PL202364B1 (ja)
PT (1) PT1303702E (ja)
TW (1) TW587128B (ja)
WO (1) WO2002008609A1 (ja)

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US20080190392A1 (en) * 2006-06-29 2008-08-14 Victor Michel N Peristaltic engine
US8748151B2 (en) 2008-08-29 2014-06-10 Merz Pharma Gmbh & Co. Kgaa Clostridial neurotoxins with altered persistency
US8328542B2 (en) * 2008-12-31 2012-12-11 General Electric Company Positive displacement rotary components having main and gate rotors with axial flow inlets and outlets
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
EP3094849A4 (en) * 2014-01-15 2017-11-15 Eaton Corporation Method of optimizing supercharger performance
CN104454523B (zh) * 2014-11-25 2016-07-20 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
CA3003677C (en) * 2015-10-30 2023-09-19 Gardner Denver, Inc. Complex screw rotors
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
DE202018000178U1 (de) * 2018-01-12 2019-04-15 Leybold Gmbh Kompressor
TW202040004A (zh) * 2019-04-19 2020-11-01 亞台富士精機股份有限公司 轉子及螺旋式幫浦
GB2607936A (en) * 2021-06-17 2022-12-21 Edwards Ltd Screw-type vacuum pump
KR20240020695A (ko) 2022-08-08 2024-02-15 주식회사 플랜 진공펌프용 스크류 로터
CN117514806B (zh) * 2023-12-18 2024-06-04 坚固工业设备(杭州)有限公司 立式爪型干式真空泵转子结构、立式真空泵及使用方法

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Also Published As

Publication number Publication date
AU6724701A (en) 2002-02-05
KR20030026988A (ko) 2003-04-03
CY1110996T1 (el) 2015-06-11
PL202364B1 (pl) 2009-06-30
PT1303702E (pt) 2010-12-23
CZ20024019A3 (cs) 2003-05-14
JP2004504546A (ja) 2004-02-12
AU2001267247B2 (en) 2005-07-07
HUP0301145A2 (en) 2003-08-28
CN1242172C (zh) 2006-02-15
HK1058814A1 (en) 2004-06-04
TW587128B (en) 2004-05-11
PL362974A1 (en) 2004-11-02
JP4162485B2 (ja) 2008-10-08
ATE483110T1 (de) 2010-10-15
DE50115648D1 (de) 2010-11-11
ES2353460T3 (es) 2011-03-02
CA2417051A1 (en) 2002-01-31
CA2417051C (en) 2008-09-16
BR0112776A (pt) 2003-07-08
KR100737321B1 (ko) 2007-07-09
CH694339A9 (de) 2005-03-15
NO20030357D0 (no) 2003-01-23
US6702558B2 (en) 2004-03-09
CH694339A5 (de) 2004-11-30
US20030152475A1 (en) 2003-08-14
NO20030357L (no) 2003-01-23
CN1444700A (zh) 2003-09-24
EP1303702A1 (de) 2003-04-23
JP4677469B2 (ja) 2011-04-27
WO2002008609A1 (de) 2002-01-31
DK1303702T3 (da) 2011-01-24
JP2008196505A (ja) 2008-08-28
CZ305182B6 (cs) 2015-06-03

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