EP1151199A1 - Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes - Google Patents

Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes

Info

Publication number
EP1151199A1
EP1151199A1 EP99973677A EP99973677A EP1151199A1 EP 1151199 A1 EP1151199 A1 EP 1151199A1 EP 99973677 A EP99973677 A EP 99973677A EP 99973677 A EP99973677 A EP 99973677A EP 1151199 A1 EP1151199 A1 EP 1151199A1
Authority
EP
European Patent Office
Prior art keywords
twin
flank
screws according
profile
screw
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.)
Withdrawn
Application number
EP99973677A
Other languages
German (de)
English (en)
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
Priority to EP99973677A priority Critical patent/EP1151199A1/fr
Publication of EP1151199A1 publication Critical patent/EP1151199A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04C2/084—Toothed wheels

Definitions

  • the invention relates to twin conveyor screws for installation in positive displacement machines, in particular pumps, for axially parallel, opposing external engagement with wrap angles> 720 ° and carried out with the same end profiles, each with a cycloid-shaped hollow flank, which form a well-sealed axial chamber sequence without blow hole connections in a housing.
  • each feed screw has a plurality of screw bodies arranged axially one behind the other on a common shaft.
  • twin screws shown in documents EP 0496 170 A2 and DE 43 16 735 A1 have screw bodies with different winding directions.
  • the volume flow is divided, which saves critical dynamic seals.
  • Dynamic balancing is also guaranteed for catchy, non-point-symmetrical profiles.
  • the screw pump according to DE 196 14 562 A1 combines the two features mentioned, namely different winding directions and different pitches of the screw bodies arranged one behind the other on a shaft.
  • the disadvantages of this first type of twin screw consist in particular in an increased construction effort compared to those with a single screw body per spindle.
  • all of the publications mentioned above have catchy rotors which, despite being 100% balanced due to their great length, have a strong tendency to vibrate, which precludes the operation of corresponding pumps at high speeds.
  • the screws are multi-start and the profiles are point-symmetrical.
  • SRM profiles named after the company "Svenska Rotor Maskiner Aktiebolag", in which the two rotors have an uneven number of teeth and in which one of the rotors is referred to as “male” and the other as “female” Profiles do not have any imbalance problems because they are point-symmetrical. This applies both to the profile called “symmetrical” with mirror-image tooth flanks and to that called “asymmetrical” with different tooth flanks.
  • Cooling options for such rotors are, on the one hand, the generally known and widespread “fluid injection”, which is not suitable for all applications, on the other hand, and on the other hand an internal cooling system in which a cooling medium is passed through the rotors.
  • the patent documents DE 914 886, US 2,714,314 and US 2,441,771 show cooling systems of the latter type.
  • the twin screws of a third type described below also belong to the point-symmetrical profiles.
  • the patent applications DE 195 22 559 A1 and DE 19522 560 A1 describe twin screws with a two-start rectangular profile.
  • the pump concept realized with these feed screws is the most advanced and most flexible concept at the moment.
  • the two-course rectangular profile allows high speeds without bending vibrations and operates without a front end cover.
  • precisely because of this rectangular profile the formation of sufficiently well partitioned, axial chamber sequences with little leakage is only achieved at low gradients and large wrap angles in combination with high speed (8000 min "1 ), ie operation in the low and medium speed range results
  • the pump is cooled here on the stationary part conventionally by coolant.
  • the rotors are cooled according to the principle of heat radiation in the area of the pressure-side coaxial bores. This rotor geometry offers no space for an effective internal cooling system with flowing cooling medium.
  • the fourth and last type of twin screw to be described here has catchy profiles.
  • a known pump with rotors of this type is manufactured by Kashiyama and has rotors mounted on one side with a catchy rectangular profile.
  • the additional problem of balancing is solved by recesses in the core area at the front. In the opinion of the manufacturer, the severely restricted area of application and the small size make cooling unnecessary.
  • twin screws with catchy profiles with a hollow flank are disclosed.
  • one flank of the catchy profiles as an elongated cycloid (hollow flank)
  • symmetrical lines of engagement are alternately formed, which run from the inner edges of the housing to the core circles along the outer contours of the screws.
  • These lines of engagement divide the interior of the pump into axially moving work cells with twice the length of the slope in an overlapping arrangement.
  • Versions with large wrap angles (> 720 °) bring the good isolation without a blow hole to full effect and good efficiency and very good final vacuum are also achieved for medium (3000 min "1 ) and low speeds.
  • the output control is not necessarily carried out via a front cover
  • the screws themselves can do this alone.
  • the balancing method is important in the implementation of such catchy conveyor screws - by forming frontal and / or internal cavities, cutting away outer, insignificant screw parts, using materials of different densities and varying the wrap angle, static and dynamic Documents representing the prior art with regard to such methods are JP 62 291 486, WO 97/21925, JP 0 230 5393 and WO 98/11351.
  • the present invention has for its object to provide a set of conveyor screws, which is suitable for problem-free operation in a wide speed range (approx. 1'000 - 800 min "1 ) and with which a good vacuum even at low speeds and a vibration-free operation can be achieved up to the upper range.
  • the conveyor screws are intended to install an effective Enable internal rotor cooling, which is becoming increasingly important, especially for larger pumps (> 200 m 3 / h).
  • the twin conveyor screws according to the invention are characterized in that the end profile is multi-start but not point-symmetrical, that exactly one flank of a single tooth is designed as a cycloid-shaped hollow flank and that all other flanks are essentially convexly curved and that they are formed accordingly individual stimulus profile limitation curves there is agreement between the center of gravity and the pivot point.
  • helical channels are provided in the interior of the rotor, in the areas of the teeth, through which a cooling medium flows.
  • FIG. 1 shows a set of twin conveyor screws in a housing, in an end cut, along the line I - 1 from FIG. 3,
  • Figure 2 shows a twin screw set with unequal arches, in an end cut and 3 shows a twin screw set with internal cooling channels, in a partially sectioned view in the direction of arrow III in FIG. 1.
  • FIG. 1 schematically shows a cross section through a housing, indicated by 3, in which there is a first exemplary embodiment of the twin conveyor screws 1 and 2 according to the invention.
  • the view according to FIG. 1 is cut along the line I - I in FIG. 3, but the channel denoted by 11 in FIG. 3 is not shown.
  • Each of the screws shown has a uniform, coherent screw body and is preferably intended for a dry-running pump with an externally arranged synchronization device.
  • the profile of the screws is composed of the following limitation curves:
  • a single hollow flank 6 merges at its radially outer end over an edge 7 into a circular arc K.
  • the cycloid-shaped hollow flank 6 merges tangentially into a circular arc F.
  • a first convex flank 8 is connected via a transition radius, at the radially outer end of which a further tip arc K is connected.
  • a second convex flank 9 which in turn merges into a further root arc F via a transition radius.
  • the contour merges again via a transition radius into a third convex flank 10, which abuts the already mentioned tip circle at its radially outer end.
  • FIG. 2 shows, based on a second exemplary embodiment of the twin conveyor screws according to the invention, that the radii rK1, rK2 of the two circular arcs bK1 and bK2 of each conveyor screw are not the same as in FIG have to be.
  • rK1 is greater than rK2, so that there is a clear gap between the head arc K adjacent to the convex flanks 8 and 9 and the inner wall of the housing.
  • this gap is of minimal importance for the partitioning of the work cells, because this takes place at the edge 7 and the adjacent circular arc.
  • the different root circle radii rF1, rF2 inevitably result from the center distance and the tip circle radii rK1, rK2.
  • the surfaces of the housing 3 and the rotors 1, 2 forming the working space are enlarged, which is advantageous in combination with the internal rotor cooling.
  • FIG 3 shows the twin screw set according to Figure 1 in a partially sectioned view in the direction of arrow III in Figure 1.
  • the two-speed rotors are mirror images and are in engagement with each other.
  • a helical channel 11 is formed in its interior, through which a cooling medium flows during operation.
  • Each rotor is made in one piece.
  • each rotor could also be composed of a rotor shaft 4 and a screw body 5, which can be made of the same or different materials. Because of the favorable end profile geometry, materials of low strength can also be used in this case. Non-castable special materials can also be used if the internal rotor cooling is not used.

Landscapes

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

Abstract

Les vis sans fin jumelles à filetage multiple selon l'art antérieur possèdent des profils à symétrie ponctuelle, de faibles inclinaisons et des angles de contact très larges, et doivent fonctionner à des vitesses de rotation élevées en raison des pertes résiduelles par trou d'air entre les cellules de travail. Dans les modes de réalisation selon l'art antérieur à filetage unique, le cloisonnement des cellules de travail est obtenu sans liaisons par trou d'air, et un vide et un degré de rendement satisfaisants sont obtenus pour des nombres de tours moyen ou faible, mais des flexions alternées non désirées tendent à apparaître en cas de nombre de tours plus élevé. Pour des raisons de géométrie, aucun de ces modes de réalisation ne permet un refroidissement interne efficace. La présente invention élimine cette lacune et combine les avantages des modes de réalisation selon l'art antérieur précités. La présente invention offre une solution uniforme pour une large plage de nombres de tours, grâce à des vis sans fin (1, 2) à position centrale du centre de gravité, dont les profils sont à filetage multiple et exempts de symétrie ponctuelle. Les vis sans fin de ce type fonctionnent d'une part sans perte par trou d'air et sont d'autre part adaptées pour fonctionner à un nombre de tours élevé en raison de la position centrale du centre de gravité. En outre, en raison de l'absence de trous d'équilibrage pour des inclinaisons moyennes, elles peuvent être équipées d'un refroidissement interne. Ces excellentes possibilités d'adaptation à la commande des processus ouvrent un large champ d'application en médecine, en chimie et dans la technique des semi-conducteurs.
EP99973677A 1999-02-08 1999-12-07 Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes Withdrawn EP1151199A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP99973677A EP1151199A1 (fr) 1999-02-08 1999-12-07 Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP99810101 1999-02-08
EP99810101A EP1026399A1 (fr) 1999-02-08 1999-02-08 Vis transporteuses jumelées
EP99973677A EP1151199A1 (fr) 1999-02-08 1999-12-07 Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes
PCT/CH1999/000587 WO2000047897A1 (fr) 1999-02-08 1999-12-07 Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes

Publications (1)

Publication Number Publication Date
EP1151199A1 true EP1151199A1 (fr) 2001-11-07

Family

ID=8242666

Family Applications (2)

Application Number Title Priority Date Filing Date
EP99810101A Withdrawn EP1026399A1 (fr) 1999-02-08 1999-02-08 Vis transporteuses jumelées
EP99973677A Withdrawn EP1151199A1 (fr) 1999-02-08 1999-12-07 Vis sans fin jumelles destinees a etre installees dans des machines de deplacement, en particulier des pompes

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP99810101A Withdrawn EP1026399A1 (fr) 1999-02-08 1999-02-08 Vis transporteuses jumelées

Country Status (6)

Country Link
EP (2) EP1026399A1 (fr)
JP (1) JP2002536593A (fr)
CN (1) CN1334904A (fr)
AU (1) AU1371400A (fr)
CA (1) CA2362075A1 (fr)
WO (1) WO2000047897A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH694339A9 (de) 2000-07-25 2005-03-15 Busch Sa Atel Zwillingsschraubenrotoren und solche enthaltende Ve rdraengermaschinen.
DE10300203A1 (de) 2003-01-08 2004-07-22 Pfeiffer Vacuum Gmbh Zweiwellenvakuumpumpe sowie Verfahren zur Herstellung einer Zweiwellenvakuumpumpe
KR101176980B1 (ko) * 2005-02-16 2012-08-24 아뜰리에 부쉬 에스.아. 비대칭 형상을 가지는 회전자들을 구비한 체적형 회전 장치
CN1904365B (zh) * 2005-07-29 2010-06-16 良峰塑胶机械股份有限公司 爪式转子设计方法
JP5353521B2 (ja) * 2009-07-22 2013-11-27 株式会社豊田自動織機 スクリューロータ
JP2012207660A (ja) * 2011-03-11 2012-10-25 Toyota Industries Corp スクリュポンプ
DE102011118050A1 (de) 2011-11-05 2013-05-08 Ralf Steffens Spindelverdichter-Profilkontur
CN103452846B (zh) * 2013-10-08 2016-08-03 李锦上 塞杆压缩机
US10495090B2 (en) 2015-08-27 2019-12-03 Ingersoll-Rand Company Rotor for a compressor system having internal coolant manifold
US9683569B2 (en) 2015-08-27 2017-06-20 Ingersoll-Rand Company Compressor system having rotor with distributed coolant conduits and method
CN107882735B (zh) * 2017-11-02 2019-05-24 西安交通大学 一种具有严格密封型转子线的双齿双螺杆真空泵
JP7096044B2 (ja) * 2018-03-30 2022-07-05 株式会社日立産機システム スクリューロータ及び流体機械本体
CN111396311A (zh) * 2020-04-26 2020-07-10 陕西理工大学 一种空心螺杆转子及其加工方法
CN111779676B (zh) * 2020-07-15 2021-11-19 西安交通大学 一种双齿转子压缩机转子型线及双齿转子和压缩机
CN111828327B (zh) * 2020-07-15 2021-11-30 高秀峰 一种多齿转子压缩机转子型线及多齿转子和压缩机

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GB112104A (en) 1917-07-05 1917-12-27 Edward Nuebling Improvements in or relating to Rotary Meters, Pumps and Motors.
GB527339A (en) * 1939-04-06 1940-10-07 Paul Leistritz Improvements in screw pumps or screw motors
US2441771A (en) 1941-05-31 1948-05-18 Jarvis C Marble Yieldable drive for rotors
DE914886C (de) 1949-09-15 1954-07-12 Svenska Rotor Maskiner Ab Kuehleinrichtung fuer mehrteilige Gehaeuse oder Laeufer, insbesondere von Drehkolbenmaschinen mit Schraubenraedern
GB670395A (en) 1950-01-16 1952-04-16 Roots Connersville Blower Corp Improvements in or relating to rotary screw-pumps and motors
US2714314A (en) 1951-05-15 1955-08-02 Howden James & Co Ltd Rotors for rotary gas compressors and motors
GB746628A (en) 1953-04-06 1956-03-14 Dresser Ind Improvements in pumps or motors of the meshing screw type
DE1289433B (de) * 1960-07-08 1969-02-13 Prinz Fritz Schraubenrotor fuer Schraubenpumpen od. dgl. mit hohlen Schraubengaengen
US4224016A (en) 1978-09-27 1980-09-23 Brown Arthur E Rotary positive displacement machines
JPS62291486A (ja) 1986-06-12 1987-12-18 Taiko Kikai Kogyo Kk スクリユ−コンプレツサ−
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CA2058325A1 (fr) 1990-12-24 1992-06-25 Mark E. Baran Pompes volumetriques
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See references of WO0047897A1 *

Also Published As

Publication number Publication date
CA2362075A1 (fr) 2000-08-17
JP2002536593A (ja) 2002-10-29
EP1026399A1 (fr) 2000-08-09
AU1371400A (en) 2000-08-29
CN1334904A (zh) 2002-02-06
WO2000047897A1 (fr) 2000-08-17

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