WO2000047897A1 - Zwillings-förderschrauben zum einbau in verdrängermaschinen, insbesondere pumpen - Google Patents
Zwillings-förderschrauben zum einbau in verdrängermaschinen, insbesondere pumpen Download PDFInfo
- Publication number
- WO2000047897A1 WO2000047897A1 PCT/CH1999/000587 CH9900587W WO0047897A1 WO 2000047897 A1 WO2000047897 A1 WO 2000047897A1 CH 9900587 W CH9900587 W CH 9900587W WO 0047897 A1 WO0047897 A1 WO 0047897A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- twin
- flank
- screws according
- profile
- screw
- Prior art date
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
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000598773A JP2002536593A (ja) | 1999-02-08 | 1999-12-07 | 容積形機械、特にポンプに搭載される複式送出しスクリュー |
EP99973677A EP1151199A1 (de) | 1999-02-08 | 1999-12-07 | Zwillings-förderschrauben zum einbau in verdrängermaschinen, insbesondere pumpen |
CA002362075A CA2362075A1 (en) | 1999-02-08 | 1999-12-07 | Twin delivery screws provided for installation in positive-displacement machines, especially pumps |
AU13714/00A AU1371400A (en) | 1999-02-08 | 1999-12-07 | Twin delivery screws provided for installation in positive-displacement machines, especially pumps |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP99810101A EP1026399A1 (de) | 1999-02-08 | 1999-02-08 | Zwillings-Förderschrauben |
EP99810101.8 | 1999-02-08 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000047897A1 true WO2000047897A1 (de) | 2000-08-17 |
Family
ID=8242666
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CH1999/000587 WO2000047897A1 (de) | 1999-02-08 | 1999-12-07 | Zwillings-förderschrauben zum einbau in verdrängermaschinen, insbesondere pumpen |
Country Status (6)
Country | Link |
---|---|
EP (2) | EP1026399A1 (de) |
JP (1) | JP2002536593A (de) |
CN (1) | CN1334904A (de) |
AU (1) | AU1371400A (de) |
CA (1) | CA2362075A1 (de) |
WO (1) | WO2000047897A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6702558B2 (en) | 2000-07-25 | 2004-03-09 | Ateliers Busch Sa | Twin screw rotors and displacement machines containing the same |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10300203A1 (de) * | 2003-01-08 | 2004-07-22 | Pfeiffer Vacuum Gmbh | Zweiwellenvakuumpumpe sowie Verfahren zur Herstellung einer Zweiwellenvakuumpumpe |
CA2596603C (fr) * | 2005-02-16 | 2012-08-21 | Ateliers Busch Sa | Machine rotative volumetrique avec rotors a profils asymetriques |
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 |
US9683569B2 (en) | 2015-08-27 | 2017-06-20 | Ingersoll-Rand Company | Compressor system having rotor with distributed coolant conduits and method |
US10495090B2 (en) | 2015-08-27 | 2019-12-03 | Ingersoll-Rand Company | Rotor for a compressor system having internal coolant manifold |
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 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB527339A (en) * | 1939-04-06 | 1940-10-07 | Paul Leistritz | Improvements in screw pumps or screw motors |
DE1289433B (de) * | 1960-07-08 | 1969-02-13 | Prinz Fritz | Schraubenrotor fuer Schraubenpumpen od. dgl. mit hohlen Schraubengaengen |
EP0736667A2 (de) * | 1995-04-05 | 1996-10-09 | Ebara Corporation | Schraubenrotor und Verfahren zur Profilerzeugung seiner Zähne |
WO1998011351A1 (de) * | 1996-09-12 | 1998-03-19 | Ateliers Busch S.A. | Schraubenrotorsatz |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB112104A (en) | 1917-07-05 | 1917-12-27 | Edward Nuebling | Improvements in or relating to Rotary Meters, Pumps and 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 |
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− |
JPS6336086A (ja) | 1986-07-30 | 1988-02-16 | Taiko Kikai Kogyo Kk | 多段型スクリユウ式真空ポンプ |
JPH02305393A (ja) | 1989-05-19 | 1990-12-18 | Hitachi Ltd | スクリユーロータおよびスクリユー真空ポンプ |
CA2058325A1 (en) | 1990-12-24 | 1992-06-25 | Mark E. Baran | Positive displacement pumps |
DE4224969C1 (de) | 1992-07-29 | 1993-09-30 | Heinrich Moeller | Förderschraubenpaar für rotierende Verdrängerpumpen |
DE4316735C2 (de) | 1993-05-19 | 1996-01-18 | Bornemann J H Gmbh & Co | Pumpverfahren zum Betreiben einer Multiphasen-Schraubenspindelpumpe und Pumpe |
CA2174032A1 (en) | 1995-04-13 | 1996-10-14 | Allan J. Prang | Dual pitch multiphase screw pump |
DE19522560A1 (de) | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Vakuumpumpe mit einem Paar innerhalb eines axial durchströmten Schöpfraums umlaufender Verdrängerrotoren |
DE19522559A1 (de) | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Verdichter mit axialer Förderrichtung, insbesondere in Schraubenspindel-Bauweise |
CN1083536C (zh) | 1995-12-11 | 2002-04-24 | 爱特里尔斯布时股份公司 | 双螺杆组 |
CZ289348B6 (cs) | 1995-12-11 | 2002-01-16 | Ateliers Busch S. A. | Dvojice dopravních ąroubů |
-
1999
- 1999-02-08 EP EP99810101A patent/EP1026399A1/de not_active Withdrawn
- 1999-12-07 JP JP2000598773A patent/JP2002536593A/ja active Pending
- 1999-12-07 EP EP99973677A patent/EP1151199A1/de not_active Withdrawn
- 1999-12-07 CN CN99816093.8A patent/CN1334904A/zh active Pending
- 1999-12-07 AU AU13714/00A patent/AU1371400A/en not_active Abandoned
- 1999-12-07 CA CA002362075A patent/CA2362075A1/en not_active Abandoned
- 1999-12-07 WO PCT/CH1999/000587 patent/WO2000047897A1/de not_active Application Discontinuation
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB527339A (en) * | 1939-04-06 | 1940-10-07 | Paul Leistritz | Improvements in screw pumps or screw motors |
DE1289433B (de) * | 1960-07-08 | 1969-02-13 | Prinz Fritz | Schraubenrotor fuer Schraubenpumpen od. dgl. mit hohlen Schraubengaengen |
EP0736667A2 (de) * | 1995-04-05 | 1996-10-09 | Ebara Corporation | Schraubenrotor und Verfahren zur Profilerzeugung seiner Zähne |
WO1998011351A1 (de) * | 1996-09-12 | 1998-03-19 | Ateliers Busch S.A. | Schraubenrotorsatz |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6702558B2 (en) | 2000-07-25 | 2004-03-09 | Ateliers Busch Sa | Twin screw rotors and displacement machines containing the same |
Also Published As
Publication number | Publication date |
---|---|
JP2002536593A (ja) | 2002-10-29 |
CN1334904A (zh) | 2002-02-06 |
EP1151199A1 (de) | 2001-11-07 |
EP1026399A1 (de) | 2000-08-09 |
AU1371400A (en) | 2000-08-29 |
CA2362075A1 (en) | 2000-08-17 |
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