US3807911A - Multiple lead screw compressor - Google Patents
Multiple lead screw compressor Download PDFInfo
- Publication number
- US3807911A US3807911A US00359665A US35966573A US3807911A US 3807911 A US3807911 A US 3807911A US 00359665 A US00359665 A US 00359665A US 35966573 A US35966573 A US 35966573A US 3807911 A US3807911 A US 3807911A
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- Prior art keywords
- portions
- rotors
- lands
- grooves
- helical
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- 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
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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
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
Definitions
- a rotor structure for a fluid compressor of the character having a pair of complementary, intermeshing rotatable rotors for transferring and compressing a fluid from an inlet into the compressor to an outlet from the compressor.
- the rotor includes helical land and intervening helical groove means for intermeshing with complementary helical land and groove means of a complementary rotor.
- the helical land and groove means includes a first portion having a first constant helix angle and a second portion having a second constant helix angle which is different from the first helix angle.
- the two helical portions are disposed on shaft means and meet in a transition area intermediate the opposite ends of the shaft means and in which area the lands and grooves are disposed in mating relationship.
- One of the helical portions is integral with the shaft means, and the other helical portion is defined by a separate component adapted to be mounted on the shaft means and suitably interconnected with the one helical portion.
- This invention relates to the art of helical screw-type compressors and, more particularly, to helical screw or rotor components for such compressors.
- Rotary screw-type compressors have been provided heretofore and generally include a pair of intermeshing, complementary rotors positioned within a compressor housing, and means for rotating the intermeshed rotors relative to one another.
- the compressor housing includes an inlet opening into which fluid such as air, flows and an outlet opening through which compressed fluid flows as a result of rotation of the intermeshing rotors which operate to transfer and compress the fluid from the inletto the outlet of the compressor.
- Compressors of this type are employed for compressing gases which, during transfer and compression, move axially along the rotors.
- Such rotary screw compressors may beoperated dry or wet. In wet operated compressors, liquid is introduced into the compression chamber to effect a seal between the rotors.
- Dry compressors on the other hand, rely upon extremely close tolerances between intermeshing lands and grooves of the rotors to effect a seal therebetween.
- the introduction of liquids into the compression chamber of a screw compressor provides for additional sealing between the rotor components and serves further to dissipate the heat of compression.
- the compression ratio which can be realistically achieved under dry operation is about 3:l or 4:1 whereas a wet operated compressor may have a compression ratio of up to 8:1 or 9:1.
- Prior art screw compressors of the above character have generally been constructed with constant lead helical lands and intervening grooves on the complementary intermeshing rotors. Such construction limits the efficiency and performance of the compressors, especially at higher compression ratios. In this respect, the discharge velocity from a screw compressor having compressor. Efforts have been made in the past to provide rotary screw-type compressors with rotors having lands and grooves which continuously vary'in lead from one end of the rotor to the other. While such rotor components may provide for increasing the discharge areaof a compressor to relieve backflow and the resultant overworking of the compressor, it remains that a continuously variable lead rotor-is both extremely difficult and expensive to manufacture.
- Backflow advantageously is relieved in accordance with the present invention by employing rotors or screws having helical lands and intervening grooves which have a different helix angle or lead at the intake end of the rotor from the lead thereof at the discharge end.
- rotors or screws having helical lands and intervening grooves which have a different helix angle or lead at the intake end of the rotor from the lead thereof at the discharge end.
- a further object of the present invention is the provision of a rotor component of the above character which includes helical lands and intervening grooves in portions having different leads and in each of which portions the lead is constant along the length thereof.
- Yet another object of the present invention is the provision of a rotor component of the above character which is reasonably simple and inexpensive to manufacture.
- Still another object of the present invention is the provision of a screw compressor rotor of the above character wherein the two helical portions are defined by separate components, each having helical lands and intervening grooves and wherein the lead of each portion is constant along'its length, thus facilitating the manufacture thereof.
- Still another object of the present invention is the provision of a rotor of the above character wherein the separate portions are adapted to be readily interconnected to define a rotor component having helical lands and intervening grooves in portions having different leads, and which portions are interconnected in a manner whereby they meet in a transition area in which the lands and grooves of the two portions are disposed in mating relationship.
- FIG. 1 is a plan view, partially in section, illustrating a rotary screw-type compressor having a pair of rotor components made in accordance with the present invention
- FIG. 2 is a sectional elevation of the compressor of FIG. 1, the section being taken along line 2--2 in FIG.
- FIG. 3 is a plan view of a male rotor made in accordance with the present invention.
- FIG. 4 is a plan view of a female rotor made in accordance with the present invention.
- FIG. 5 is a view in cross-section of the rotor illustrated in FIG. 3, the section being taken along line 55 in FIG. 3;
- FIG. 6 is a schematic projection of complementary male and female rotors made in accordance with the present invention.
- FIGS. I and 2 a rotary screw-type compressor assembly 10 is illustrated in FIGS. I and 2 which is comprised of a housing 12 having an inlet port 14 at one end thereof and an outlet port 16 at the other end "thereof.
- Housing 12 includes cylindrical chambers 18 drawings in greater detail,
- shaft portion 28 projects outwardly of housing 12 for suitable interconnection thereof with suitable drive means which is not illustrated.
- the intermeshing relationship between rotors 22 and 24 provides for rotor 24 to be rotated in response to rotation of rotor 22 through shaft portion 28.
- shaft portion 32 could be extended exteriorly of housing 12 and that shaft portions 28 and 32 could be suitably interconnected such as by gear means to achieve rotation of rotor 24.
- Male rotor 22 as best illustrated in FIGS. 2 and 3, includes helical land means 34 and intervening helical groove means 36.
- the helical land means of the male rotor are in the form of lobes having convex outer side surfaces 40.
- the helical land means and intervening groove means of the male rotor is defined by two portions designated A Portion A extends from the inlet end of the compressor toward transition area E, and portion B extends from transition area E toward the outlet end of the compressor.
- the helical land and groove means of portions A and B each have a constant lead throughout the length thereof and, as is best illustrated in FIG. 3, the lead of portion A is greater than the lead of portion B.
- the lead ratio of portion A' to portion B is approximately 3:1. It will be appreciated, however, that the lead ratio can be of any value greater or lesser than 3:1 and is limited only by manufacturing or strength considerations.
- the inner ends of portions A and B are interrelated in transition area E in a manner whereby the helical land and groove means of portions A and B are disposed in mating relationship. Thus, continuous but angularly related helical land and groove means are provided'which extend along the length of the rotor component.
- helical groove means 44 are complementary to helical land means 34 of male rotor 22.
- rotors 22 and 24 are adapted to be disposed in side by side intermeshing reand B which meet in transition area designated by line gle, of course, is the angle circumscribed by the helical land and intervening groove means of both portions between the longitudinally oppositeends thereof.
- portion A has a wrap angle which is defined by the angle circumscribed by the helical land and groove means thereof in extending from the ends thereof adjacent shaft portion 28 to transition area E
- portion B has a wrap angle which is defined by the angle circumscribed by the helical land and groove means thereof in extending from transition area E to the ends thereof adjacent shaft portion 26.
- portions A and B have a lead ratio of 3:1, as mentioned above, and the wrap angle of the helical land and groove means of each portion is approximately 135.
- female rotor 24 The structure of female rotor 24 is, of course, complementary to that of male rotor 22.
- the female rotor includes helical land means 42-and intervening helical groove means 44.
- Helical land means 42 are complementary to helicalgroove means 36 of the male rotor and, accordingly, helical land means 42 include lationship.
- the helical land and groove means of female rotor 24 include portions C and D corresponding respectively to portions A and B of male rotor 22. Portions C and D of the helical land and groove means are interrelated in a transition area therebetween denoted by line F. The transition areas of rotors 22 and 24, of course, coincide in location relative to the opposite ends of the rotors. Since the helical land and groove means of the male and female rotors are complementary, it will be appreciated, that the helical land and groove means of portion C have a lead corresponding to that of portion A of male rotor 22, and that the helical land and groove means of portion D have a lead corresponding to the lead of portion B of male rotor 22. Further, it will be appreciated that the lead ratio of portion C to portion D, the wrap angles of each portion and the total wrap angle will correspond with that of the male rotor, or vice versa.
- the rotor members may be formed or produced in any suitable manner and preferably, are constructed in the manner illustrated in FIG. 5.
- a male rotor 50 is illustrated which includes shaft means 52 carrying helical land and intervening helical groove means 54 defined by helical land and groove means portions 56 and 58.
- Portion 56 is integral with shaft means 52, and portion 58 is defined by a separate component suitably interconnected with portion 56.
- portion 58 is an annular component having helical land and groove means in the outer surface thereof and having a cylindrical aperture 60 therethrough which is adapted to receive a cylindrical portion 62 of shaft means 52 which projects from the corresponding end of land and groove portion 56.
- Portion 58 is interconnected with portion 56 by bolt means 64, or the like, which extends through aperture 65 in portion.58 and has a threaded inner end disposed in a cooperatively threaded recess 66 in portion 56. Further, means is provided to assure that portion 58 is oriented relative to portion 56 so that the helical land and groove means of the two portions are disposed in mating relationship in the transition area therebetween defined by a line of juncture G. In this respect, portions 56 and 58 may be provided with a recess 68 and aperture 70, respectively, adapted to be aligned to receive a suitable dowel pin 72.
- recess 68 and aperture 70 are provided in the corresponding portions 56 and 58 so as to assure properalignment of the lands and grooves of the two portions uponinsertion of dowel 72 thereinto; After proper positioning is thus assured, aperture 65 and recess 66 can be provided in the corresponding portions 58 and 56, and bolt means 64 inserted thereinto to complete the assembly.
- a rotor constructed as'illustrated in FIG. 5 is very economical to produce in'that the shaft means and portion 56 of the helical land and groove means of the rotor can be turned or otherwise produced as an integral unit, while portion 58 having helical land and groove means of a different lead which is constant along its entire length can readily be turned or otherwise produced as a separate element or component. Thereafter, itis only necessary to position portion 58 on the shaft means and against portion 56, orient the two portions for the land and groove means thereof to mate, fix the positions thereof by means of -the dowel pin and interconnect the two portions by bolt means 64.
- the projecting portion of the shaft could be provided with a flat and the opening through the separate component could be provided with a flat side interrupting the cylindrical contour thereof and which flat side would cooperate with the flat on the shaft to properly align the rotor'portions.
- portion 56 of the rotor is illustrated as being integral with shaft means 52, portion 56 could also be a separate component from the shaft means suitably interconnected therewith. It is also contemplated that portions 56 and 58 could be separate portions each integral with a corresponding shaft portion. In this instance, the two rotor portions would be suitably interconnected with the helical land and groove means thereof in mating relationship and the shaft portions thereof would together define shaft means for the rotor unit.
- complementary male and female rotor elements are disposed in a compressor housing in intermeshing relationship with one another and with high lead portions A and C thereof toward the'compressor inlet and low lead portions B and D thereof toward the compressor outlet.
- fluid such as air enters the compressor inlet and is transferred therefrom to the compressor outlet by being captured in pockets or cells defined by the helical land and groove means of the rotating male and female rotors together with the chambers in which the rotors are di'sposed.
- the pockets in which the fluid is trapped gradually decrease in volume whereby the fluid is gradually compressed and is ultimately exhausted through the compressor-outlet under high pressure and velocity.
- male and female rotors made in accordance with the present invention is scheare numbered 1 through 4.
- female rotor 24 has helical land and groove me'ans portions C, and D having different leads corresponding, respectively, to the leads of portions A and B of the male rotor. Further, the helical lands and grooves of portions C and D are disposed in mating relationship.
- the grooves of female rotor 24 are numbered 1 through 6. The space be tween lines 73 and 74 of male rotor 22 together with.
- the space between lines 75 and 76 of female rotor 24 define the width of the compressor inlet-If the leads of the helical land and groove means of the rotors were constant throughout the lengths thereof the compressor outlet would have a width designated by lines .78.
- a compressor outlet of greater width or size as designated by lines 80 advantageously is provided for.
- the small outlet opening necessitated by the use of constant lead rotors produces an undesirably.
- the low lead feature provided for the outlet ends of the male and female rotors in accordancewith the present invention allows for the size of the discharge opening to be increased to reduce the output velocity of the compressor without the resultant backflow and loss of efficiency.
- a rotary fluid compressor of the character comprising a housing having laterally communicating cylindrical chambers in which a pair of intermeshing male and female rotors are disposed for progressively compressing fluid between an inlet port at one end of said chambers and an outlet port at the other end of said chambers, said rotors having corresponding inlet and outlet ends with respect to said inlet and outlet ports, said male rotor having arcuately convex helical lands and said female rotor having complementaryv arcuately concave helical grooves, said lands andg'rooves being cooperable in response to rotation of said male and female rotors to progressively and continuously compress fluid between said inlet and outlet ports within a total wrap angle of the lands and grooves less than 360 and wherein the discharge port opens into said chambers peripherally of and laterally therebetween at the discharge ends of the rotors and the lead of said lands and grooves adjacent said outlet port is less than the lead of said lands and grooves adjacent said inlet port, the discharge
- a rotary fluid compressor of the character comprising a housing having laterally communicating cylindrical chambers in which a pair of intermeshing male and female rotors are disposed for progressively compressing fluid between an inlet port at one end of said chambers and an outlet port at the other end of said chambers, said rotors having corresponding inlet and outlet ends with respect to said inlet and outlet ports, said male rotor having arcuately convex helical lands and said female rotor having complementary arcuately concave helical grooves, said lands and grooves being cooperable in response to rotation of said male and female rotors to progressively and continuously compress fluid between said inlet and outlet ports within a total wrap angle of the lands and grooves less than 360, and wherein the discharge port opens into said chambers peripherally of and laterally therebetween at the discharge ends of the rotors and the lead of said lands and grooves adjacent said outlet port is less than the lead of said lands and grooves adjacent said inlet port, the improvement comprising: said
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Abstract
Description
Claims (5)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US00359665A US3807911A (en) | 1971-08-02 | 1973-05-14 | Multiple lead screw compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16802371A | 1971-08-02 | 1971-08-02 | |
US00359665A US3807911A (en) | 1971-08-02 | 1973-05-14 | Multiple lead screw compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US3807911A true US3807911A (en) | 1974-04-30 |
Family
ID=26863730
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US00359665A Expired - Lifetime US3807911A (en) | 1971-08-02 | 1973-05-14 | Multiple lead screw compressor |
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US (1) | US3807911A (en) |
Cited By (37)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4302165A (en) * | 1978-08-22 | 1981-11-24 | Imo-Industri Ab | Interengaging screw machine with radial inlet and/or outlet bore |
US4792294A (en) * | 1986-04-11 | 1988-12-20 | Mowli John C | Two-stage screw auger pumping apparatus |
US4797077A (en) * | 1984-09-27 | 1989-01-10 | Anderson Dean R G | Rotary expansible chamber device |
US4944657A (en) * | 1989-03-01 | 1990-07-31 | Mowli John C | Two-stage pumping apparatus with low shear first stage |
US4952125A (en) * | 1988-04-06 | 1990-08-28 | Hitachi, Ltd. | Nonlubricated screw fluid machine |
US5129276A (en) * | 1989-09-28 | 1992-07-14 | Ivg Australia Pty. Limited | Meshing gear members |
US5192199A (en) * | 1988-10-11 | 1993-03-09 | Svenska Rotor Maskiner Ab | Machine for a gaseous medium |
US5267837A (en) * | 1992-09-23 | 1993-12-07 | Mowli John C | Two-stage pumping apparatus with non-meshing first stage augers |
US5478210A (en) * | 1992-01-31 | 1995-12-26 | Matsushita Electric Industrial Co., Ltd. | Multi-stage vacuum pump |
US5667370A (en) * | 1994-08-22 | 1997-09-16 | Kowel Precision Co., Ltd. | Screw vacuum pump having a decreasing pitch for the screw members |
US5674063A (en) * | 1994-08-19 | 1997-10-07 | Diavac Limited | Screw fluid machine and screw gear used in the same |
US5709537A (en) * | 1992-09-03 | 1998-01-20 | Matsushita Electric Industrial Co., Ltd. | Evacuating apparatus |
DE19745615A1 (en) * | 1997-10-10 | 1999-04-15 | Leybold Vakuum Gmbh | Screw vacuum pump with rotors |
WO1999019630A1 (en) * | 1997-10-10 | 1999-04-22 | Leybold Vakuum Gmbh | Cooled screw vacuum pump |
EP0995879A1 (en) * | 1998-10-23 | 2000-04-26 | Ateliers Busch S.A. | Twin feed screw rotors |
US6244844B1 (en) * | 1999-03-31 | 2001-06-12 | Emerson Electric Co. | Fluid displacement apparatus with improved helical rotor structure |
US6257195B1 (en) | 2000-02-14 | 2001-07-10 | Arthur Vanmoor | Internal combustion engine with substantially continuous fuel feed and power output |
US6341951B1 (en) * | 2000-05-26 | 2002-01-29 | Industrial Technology Research Institute | Combination double screw rotor assembly |
US6508639B2 (en) * | 2000-05-26 | 2003-01-21 | Industrial Technology Research Institute | Combination double screw rotor assembly |
US20030206809A1 (en) * | 2002-05-03 | 2003-11-06 | Walker Thomas A. | Method for creating an air pressure |
US20050147519A1 (en) * | 2003-01-15 | 2005-07-07 | Kazuhiro Matsumoto | Screw compressor and method of manufacturing rotors thereof |
US20060216189A1 (en) * | 2003-03-03 | 2006-09-28 | Tadahiro Ohmi | Screw vacuum pump |
US20070184321A1 (en) * | 2006-02-06 | 2007-08-09 | Nucellsys Gmbh | Compression device for a fuel cell stack |
US20080031762A1 (en) * | 2006-08-01 | 2008-02-07 | Dieter Mosemann | Screw compressor for extremely high working pressure |
US20080044304A1 (en) * | 2006-08-11 | 2008-02-21 | Yuya Izawa | Screw pump |
US20080193315A1 (en) * | 2007-02-08 | 2008-08-14 | Kabushiki Kaisha Toyota Jidoshokki | Roots-type fluid machine |
US20090016920A1 (en) * | 2004-06-15 | 2009-01-15 | Shinya Yamamoto | Screw pump and screw gear |
US20100166591A1 (en) * | 2008-12-31 | 2010-07-01 | Kurt David Murrow | Positive displacement rotary components having main and gate rotors with axial flow inlets and outlets |
WO2011004257A3 (en) * | 2009-07-10 | 2011-10-27 | Robuschi S.P.A. | Dry screw driver |
RU2448273C2 (en) * | 2009-08-03 | 2012-04-20 | Открытое акционерное общество "УРАЛЬСКИЙ ЭЛЕКТРОХИМИЧЕСКИЙ КОМБИНАТ" | Rotary screw machine |
US8764424B2 (en) | 2010-05-17 | 2014-07-01 | Tuthill Corporation | Screw pump with field refurbishment provisions |
US20150086392A1 (en) * | 2013-09-20 | 2015-03-26 | Gardner Denver Deutschland Gmbh | Dry running compressor for creating compressed air |
US20160319817A1 (en) * | 2014-01-15 | 2016-11-03 | Eaton Corporation | Method of optimizing supercharger performance |
US10975867B2 (en) | 2015-10-30 | 2021-04-13 | Gardner Denver, Inc. | Complex screw rotors |
US11009034B2 (en) | 2014-01-15 | 2021-05-18 | Eaton Intelligent Power Limited | Method of optimizing supercharger performance |
CN114423947A (en) * | 2019-10-07 | 2022-04-29 | 株式会社日立产机系统 | Screw compressor |
US20220356876A1 (en) * | 2021-05-05 | 2022-11-10 | Boundary Lubrication Systems LLC | 3-dimensional pump rotor profile |
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Cited By (61)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4302165A (en) * | 1978-08-22 | 1981-11-24 | Imo-Industri Ab | Interengaging screw machine with radial inlet and/or outlet bore |
US4797077A (en) * | 1984-09-27 | 1989-01-10 | Anderson Dean R G | Rotary expansible chamber device |
US4792294A (en) * | 1986-04-11 | 1988-12-20 | Mowli John C | Two-stage screw auger pumping apparatus |
US4952125A (en) * | 1988-04-06 | 1990-08-28 | Hitachi, Ltd. | Nonlubricated screw fluid machine |
US5064363A (en) * | 1988-04-06 | 1991-11-12 | Hitachi, Ltd. | Non-lubricated screw machine with a rotor having a taper and varied helical angle |
US5192199A (en) * | 1988-10-11 | 1993-03-09 | Svenska Rotor Maskiner Ab | Machine for a gaseous medium |
US4944657A (en) * | 1989-03-01 | 1990-07-31 | Mowli John C | Two-stage pumping apparatus with low shear first stage |
US5129276A (en) * | 1989-09-28 | 1992-07-14 | Ivg Australia Pty. Limited | Meshing gear members |
US5478210A (en) * | 1992-01-31 | 1995-12-26 | Matsushita Electric Industrial Co., Ltd. | Multi-stage vacuum pump |
US5709537A (en) * | 1992-09-03 | 1998-01-20 | Matsushita Electric Industrial Co., Ltd. | Evacuating apparatus |
US5951266A (en) * | 1992-09-03 | 1999-09-14 | Matsushita Electric Industrial Co., Ltd. | Evacuating apparatus having interengaging rotors with threads having a decreasing pitch at the exhaust side |
US5267837A (en) * | 1992-09-23 | 1993-12-07 | Mowli John C | Two-stage pumping apparatus with non-meshing first stage augers |
US5674063A (en) * | 1994-08-19 | 1997-10-07 | Diavac Limited | Screw fluid machine and screw gear used in the same |
EP0937895A2 (en) * | 1994-08-19 | 1999-08-25 | Diavac Limited | Screw fluid machine |
US5829957A (en) * | 1994-08-19 | 1998-11-03 | Diavac Limited | Screw fluid machine and screw gear used in the same |
US5836754A (en) * | 1994-08-19 | 1998-11-17 | Diavac Limited | Screw fluid machine and screw gear used in the same |
EP0937895A3 (en) * | 1994-08-19 | 2000-01-05 | Diavac Limited | Screw fluid machine |
US5667370A (en) * | 1994-08-22 | 1997-09-16 | Kowel Precision Co., Ltd. | Screw vacuum pump having a decreasing pitch for the screw members |
WO1999019630A1 (en) * | 1997-10-10 | 1999-04-22 | Leybold Vakuum Gmbh | Cooled screw vacuum pump |
WO1999019631A1 (en) * | 1997-10-10 | 1999-04-22 | Leybold Vakuum Gmbh | Screw vacuum pump provided with rotors |
DE19745615A1 (en) * | 1997-10-10 | 1999-04-15 | Leybold Vakuum Gmbh | Screw vacuum pump with rotors |
US6382930B1 (en) | 1997-10-10 | 2002-05-07 | Leybold Vakuum Gmbh | Screw vacuum pump provided with rotors |
US6544020B1 (en) | 1997-10-10 | 2003-04-08 | Leybold Vakuum Gmbh | Cooled screw vacuum pump |
CN1113151C (en) * | 1998-10-23 | 2003-07-02 | 阿特里尔斯布希股份有限公司 | Twin helical rotors installated in displacement machines for compressible media |
US6447276B1 (en) | 1998-10-23 | 2002-09-10 | Ateliers Busch Sa | Twin screw rotors for installation in displacement machines for compressible media |
WO2000025004A1 (en) * | 1998-10-23 | 2000-05-04 | Ateliers Busch S.A. | Twin helical rotors for installation in displacement machines for compressible media |
EP0995879A1 (en) * | 1998-10-23 | 2000-04-26 | Ateliers Busch S.A. | Twin feed screw rotors |
US6244844B1 (en) * | 1999-03-31 | 2001-06-12 | Emerson Electric Co. | Fluid displacement apparatus with improved helical rotor structure |
US6530365B2 (en) | 1999-05-18 | 2003-03-11 | Arthur Vanmoor | Fluid displacement pump with backpressure stop |
US6257195B1 (en) | 2000-02-14 | 2001-07-10 | Arthur Vanmoor | Internal combustion engine with substantially continuous fuel feed and power output |
US6341951B1 (en) * | 2000-05-26 | 2002-01-29 | Industrial Technology Research Institute | Combination double screw rotor assembly |
US6508639B2 (en) * | 2000-05-26 | 2003-01-21 | Industrial Technology Research Institute | Combination double screw rotor assembly |
US20030206809A1 (en) * | 2002-05-03 | 2003-11-06 | Walker Thomas A. | Method for creating an air pressure |
US20050147519A1 (en) * | 2003-01-15 | 2005-07-07 | Kazuhiro Matsumoto | Screw compressor and method of manufacturing rotors thereof |
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