US3787154A - Rotor profiles for helical screw rotor machines - Google Patents

Rotor profiles for helical screw rotor machines Download PDF

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Publication number
US3787154A
US3787154A US00256237A US3787154DA US3787154A US 3787154 A US3787154 A US 3787154A US 00256237 A US00256237 A US 00256237A US 3787154D A US3787154D A US 3787154DA US 3787154 A US3787154 A US 3787154A
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rotor
flank
curved portion
main
gate
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S Edstrom
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Gardner Denver Inc
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Gardner Denver Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels

Definitions

  • Helical screw type fluid working machines are well known in the art of expansible chamber devices.
  • Helical screw compressors both liquid injected and socalled dry types, have been well developed and special attention has been given to the development of the form of the cooperating screw rotors in seeking to provide more efficient and reliable machines.
  • the shape or profile of the grooves of the main and gate rotors, sometimes called male and female rotors, respectively, in the plane transverse to the rotational axes of the rotors are of special importance.
  • 3,245,612 to Nilsson et al discloses profiles for helical screw rotors in which traveling generation is used to form the main rotor lobe flanks.
  • a longstanding problem in the art of helical screw rotor machines has been the inability to provide a set of rotors having profiles which will give satisfactory solutions to the abovementioned problems and at the same time be capable of reasonably economical manufacture.
  • This latter problem concerns the provision of a profile which will be tolerant of manufacturing errors without sacrificing performance and long life of a rotor pair.
  • the present invention provides an improved rotor profile for helical screw rotor fluid machines which results in machines of high efficiency and for certain applications negligible rotor wear due to improved conditions of rotor interengagement.
  • the rotor profile of the present invention comprises a basic profile which may be easily modified to suit different applications of screw rotor machines without causing undue expense in design and manufacturing.
  • rotor profiles which are formed by traveling generation over substantially the entire main rotor profile and a major portion of the gate rotor profile a more effective fluid seal is formed resulting in more efficient helical screw rotor machines.
  • the profiles of the present invention also provide for relatively large area contact between the flanks of engaged rotors and the development of a suitable liquid lubricant film on the contact area when used in liquid injected compressors operating without synchronizing gears.
  • the rotor profiles of the present invention are formed largely of curved surfaces each of which is tangent to the adjacent curved surface at the meeting point.
  • the rotor profiles of the present invention comprise a basic profile form, the proportions of which may be easily modified to provide desired characteristics for rotors used in various types of compressors and expanders.
  • the provision of a basic profile form which may be altered in proportion reduces the expense and time involved in calculating profiles in terms of sets of coordinate points for use in checking profile accuracy and in programming numerically controlled cutter grinding equipment.
  • FIG. I is a longitudinal section view of a rotary helical screw compressor having rotors with profiles according to the present invention
  • FIG. 2 is a transverse section taken along the line 2-2 of FIG. I;
  • FIG. 3 is a view taken along the line 22 of FIG. 1 showing on a larger scale a portion of a pair of main and gate rotors having profiles according to the present invention
  • FIG. 4 is a detail view of the main rotor tip and a portion of the gate rotor groove showing both a theoretical profile and a modified profile with clearances and is taken along the same line as the view of FIG. 3;
  • FIG. 5 is a view taken in the same direction as the view of FIG. 3 and showing an embodiment of the present invention suitable for use in dry type compressors;
  • FIG. 6 is a detail view of a modification of the gate rotor tip portion of the profile of FIG. 3.
  • FIGS. 1 and 2 of the drawings helical screw rotors having rotor profiles according to the present invention are shown in use in a compressor I0.
  • the compressor I0 includes a housing 12 having parallel intersecting bores 14 and I6, and a housing portion 18 forming a low pressure end wall 20.
  • a separate housing portion 22 forms a high pressure end wall of the bores 14 and I6.
  • the compressor also includes an inlet opening 24 and an outlet opening 26 for respectively admitting compressible fluid to and conducting compressible fluid from the bores 14 and 16.
  • a pair of cooperating main and gate rotors 28 and 30 are disposed in the bores 14 and 16, respectively, and are supported for rotation by suitable bearings 3I.
  • the rotors 28 and 30 cooperate with the housing 12 to form chambers which decrease in volume as the rotors rotate to compress fluid admitted through the inlet opening 24 and discharge fluid through the opening 26 when the aforementioned chambers are in registration with the latter opening.
  • the compressor I0 is suitable for injection of liquid into the bores I4 and 16 for sealing the spaces formed between the rotors 28 and 30, for cooling the compressor, and for lubricating the rotor flanks which are interengaged.
  • the compressor 10 is exemplary of helical screw rotor compressors.
  • the rotor 28 is provided with four lobes 32 and intervening grooves 34 having a wrap angle or twist of approximately 300.
  • the gate rotor 30 is provided with six lobes 36 and intervening grooves 38 having a wrap angle of approximately 200. It will be understood that the basic profile form of the present invention can be advantageously used on helical screw rotors having other combinations of lobes and grooves and wrap angles.
  • FIG. 3 the profiles of the flanks of the grooves 34 and 38 of the main and gate rotors 28 and 30 respectively are shown in the plane perpendicular to the rotational axes of the rotors.
  • the direction of rotation of the respective rotors 28 and 30 are indicated by arrows 40 and 42, respectively.
  • the tips 43 of the gate rotor lobes are defined by the pitch circle 44 having its center on the rotational axis 46.
  • a first flank 47 of a gate rotor groove 38 is defined in part by a concave curved portion comprising a circular arc of radius R, having its center 50 on a line 52 extending from the axis 46 to the main rotor axis 48 and lying outside the pitch circle 44.
  • the radius R extends from a point of intersection with the line 52 through a predetermined angle A, to a point 54.
  • the remaining radially outermost portion of the flank 47 is defined by a convex curved portion formed by a radius R having its center 56 on the straight line passing through points 50 and 54.
  • the curved portions formed by the radii R, and R are tangent at point 54.
  • a second flank 58 defining the remaining portion of the gate rotor groove 38, extends from the point of intersection with the line 52 to the pitch circle 44 of the gate rotor.
  • a small portion of the flank 58 is formed by a circular are having its radius center at the axis 48 and extending from line 52 to a point 60.
  • a further small portion of the flank 58 extending from the point 60 to a point 62 is generated by point 64 on the tip of the main rotor lobe 32. In the position of the rotors 28 and 30 shown in FIGS. 3 and 4 the points 62 and 64 are coincident.
  • flank portion formed between the line 52 and point 60 is tangent to the flank 47 and the flank portion formed between the points 60 and 62 is tangent to the first mentioned flank portion at point 60.
  • the profile of the bottom of the gate rotor groove from point 62 to the line 52 is exaggerated somewhat for clarity as shown in FIG. 4. Accordingly, the flank 58 may be defined between the line 52 and point 62 by a circular arc having its radius center to the axis 48 of the main rotor. The deviation from a true tangency condition at point 62 is negligible.
  • a major portion of the flank 58 from the point 62 to a point 66 is traveling generated by a portion of the main rotor lobe trip which, in FIG. 3, is a curved surface comprising a circular arc portion of radius R, extending from point 64 to a point 68 on the main rotor lobe 32.
  • the radius R has its center at 70 on a straight line extending from a point 72 which is on the pitch circle 74.
  • the radially outermost portion of the flank 58 from the point 66 to the pitch circle 44 is formed as a convex curved portion defined by a radius R, having its center at 76 on a line extending from the pitch point 72 at an Angle A with respect to the line 52.
  • the curved portion formed by the radius R is tangent to the traveling generated portion of the flank 58 at point 66. Accordingly, the entire profile of the gate rotor groove 38 is formed by curved surfaces which, for the most part, are tangent to one another at their respective meeting points.
  • the flanks 78 and 80 of the main rotor 28 are largely traveling generated by the flank portions of the gate rotor 30. Traveling generation is discussed in some detail in US. Pat. No. 3,245,6l2 to Nilsson et al.
  • the flank 78 is traveling generated from the pitch circle 74 of the main rotor to point 68 as by the convex curved portion of the gate rotor flank between the point 66 and the main pitch circle 44.
  • the tip of the main rotor lobe 32 is formed by the radius R;,.
  • the line on which the radius center 70 is located is disposed at an angle A, with respect to the line 52 and intersects point 64. The location of the center 70 provides for a curved portion extending from point 64 to line 52, see FIG.
  • This circular arc tip portion between point 64 and line 52 provides a surface which may be ground to its final dimension before the main rotor profiles are cut and thereafter serve as a visual indicator to aid in preventing the cutting of the main rotor groove too deeply.
  • the flank 80 of the main rotor from the point 82 to the pitch circle 74 is traveling generated by the convex circular arc portion between the point 54 and the pitch circle 44.
  • the main rotor 28 thus has a lobe profile which is formed entirely of curved surfaces which for the most part are tangent to each other at their meeting points.
  • a gate rotor profile which is made up entirely of curved surfaces which traveling generates a major portion of the main rotor profile, and also a main rotor profile which traveling generates a large portion of one flank of a gate rotor groove, more effective sealing areas for the enmeshed rotors are provided than is the case for point generated profiles.
  • the convex curved flank portions of the gate rotor formed by the radii R and R provide more uniform movement of the contact point between the rotor lobes 32 and 36 and greater distribution of the driving forces of one rotor against the other than is the case with straight line flank portions as found in prior art asymmetric profiles.
  • the angle formed between the milling cutter axis and the rotor longitudinal axis can be varied slightly without spoiling the desired profile shape.
  • the rotor tip portions on the main and gate rotors can also be accurately formed by a grinding operation rather than by milling.
  • FIG. 6 an embodiment of a gate rotor lobe tip is shown wherein a portion between points 86 and 88 is formed by the radius of the pitch circle 44. Additional tip portions 90 and 92 are formed between the point 86 and a point 94 and between point 88 and a point 96, respectively.
  • the tip portions 90 and 92 may be formed as straight line portions or as curved surfaces each having a radius of curvature equal to the pitch radius but having their radius centers located offset slightly from the axis 46 as shown by points 98 and 100 in FIG. 6.
  • the tip portions 90 and 92 slope radially inwardly from the pitch circle 44 from their meeting points with the tip portion between points 86 and 88.
  • the 6 further has a curved portion 101 extending from point 94 to a point 102 on the flank 58.
  • the opposite corner of the lobe tip from point 96 to a point 103 is similarly formed.
  • the curved portions 101 are equivalent to a circular arc portion formed on a milling cutter, said cutter being used for cutting the gate rotor flanks and the tip portions from point 102 to point 86 and from point 103 to point 88.
  • the main rotor profile at the bottom of the groove 34 is traveling generated by the gate rotor tip. As shown in FIG.
  • the groove portion from a point 106 to a point 108 is on the pitch circle 74, the portion from point 108 to point 110 is traveling generated by the tip portion 90, and the curved corner portion from point 110 to a point 112 is traveling generated by the curved portion 101 on the gate rotor tip.
  • the opposite bottom corner portion of the groove 34 is similarly traveling generated by the gate rotor tip portion between points 88 and 103.
  • the modification of the profile as shown in FIG. 6 does result in a slight increase in the area of the well known blowhole formed at the intersection of the hous' ing bores 14 and 16.
  • the provision of a curved portion 101 on both corners of the gate rotor lobe tip which is equivalent to a circular arc radius on the milling cutter used to cut the gate rotors eliminates sharp corners on the milling cutter for the main rotor which are subject to concentrated wear and frequent breakage.
  • the tip portion of the gate rotor between points 86 and 88 may be used as a visual indicator to aid in determining if the milling cutter forming the flanks of the gate rotor groove is cutting too deep.
  • the tip portion between points 86 and 88 also can operate as a wear strip for certain rotor applications.
  • the rotor profiles as shown in FIG. 3 are provided without clearance between the generating portions of the curved surfaces. In actual practice, however, to compensate for unavoidable errors in manufacturing and thermal expansion of the rotor lobes, it is desirable to provide predetermined clearances by modifying the theoretical profiles. For the profile shown in FIG. 4 all of the clearance is provided by modifying the profile of the main rotor and is provided by a measurement perpendicular to the profile. Referring to FIG. 4, the main rotor tip profile is modified, as shown by the dashed line, by providing clearance on a curved portion formed by the radius R The main rotor profile is further modified by forming a straight line portion between points 116 and [I8 which is tangent to the flank at point I18.
  • Point 118 is located on a straight line passing through point 72 and disposed at an angle A, with respect to the line 52.
  • the straight line portion between points 116 and 118 intersects a curved portion formed between points 116 and 64'and having a radius center at the axis 48.
  • This straight line portion is provided to allow for some amount of error in setting the depth of the cutting or milling operation when forming the main rotor flank 80' without, for example, forming a ledge or severe discontinuity in the profile at point 116 if the milling cutter is set to cut too deep.
  • the dashed line designated by numeral 117 defines the outline of the bottom portion of a milling cutter which could be used to cut the flank 80' of the main rotor in a position which would produce the minimum cutting depth.
  • the point 116 would be located closer to point 64' and the curved portion between points 116 and 64' would be shortened.
  • no abrupt step, ledge, or similar discontinuity would be formed in the profile of the main rotor flank 80'.
  • the modified main rotor profile may be provided with suitable clearances along the flanks 78' and 80 from the respective points 68' and 118 to the pitch circle 74.
  • the curved portion between point 116 and point 64' also serves as the aformentioned visual indicator of cutting depth referred to for the portion between point 64 and line 52.
  • the basic rotor profiles disclosed herein can be modified to suit the diverse requirements of, for example, liquid injected gas compressors versus dry type compressors.
  • a profile can be obtained which has a small blowhole which is desirable for liquid injected compressor operating without synchronizing gears.
  • Such a profile for liquid injected compressors without synchronizing gears can also be formed to yield a so-called negative torque on the gate rotor which reduces the clearance along the relatively long portion of the rotor sealing line, the latter necessarily resulting from selection of a small blowhole profile.
  • rotor profiles are shown in the plane transverse to the axes of rotation which are advantageously used in relatively high pressure and high temperature dry type compressors.
  • a main rotor 116 having four lobes 118 and intervening grooves 120 and a gate rotor 122 having six lobes 124 and intervening grooves 126 are discolsed.
  • the rotors 122 and 116 include longitudinal passages 125 and 123 for circulating cooling fluid through the interior of the rotor.
  • the gate rotor profile is formed in part by a concave circular arc portion of radius R said radius having its center at point 127 which is the point of tangency of the respective main and gate rotor pitch circles 128 and 130.
  • the radius R extends through an angle A on one side of the line 132 to a point 134 and through angle A,, on the other side of the line 132 to a point 136.
  • the line 132 is a straight line intersecting the axes of rotation 137 and 139 of the main and gate rotors 116 and 122, respectively.
  • the radius center for the arc portion between points 134 and 136 is located at point 127 rather than at the axis of rotation 137 of the main rotor 116 so that the main rotor tip may be suitably relieved to form a sealing strip 138 while retaining sealing points at points 134 and 136 also.
  • a first flank 140 of the gate rotor groove is formed in part by a concave curved portion of radius R having a radius center at point 142 slightly off the line 132 so as to be tangent to the circular arc portion of radius R; at point 136.
  • the circular are formed by radius R extends from point 136 to a point 144.
  • the remaining portion of the flank is formed largely by a convex curved portion comprising a circular arc of radius R having its center at a point 146 on a line through the points 142 and 144 and forming the angle A. with respect to line 132.
  • the radius R extends from point 144 toward the pitch circle 130.
  • the gate rotor 122 is formed with addendum portions 148 extending radially outside the pitch circle 130 to provide for increased displacement of a compressor using the rotors 116 and 122, as is well known.
  • This addendum portion 148 may be used in dry type compressors wherein the increase in the blowhole and the effects of addendum on gate rotor torque are relatively unimportant.
  • the addendum portions 148 are formed with curved portions 150 similar to the curved portions 101 of the gate rotor tip shown in FIG. 6.
  • the gate rotor tip ogG 5 also formed with sealing strips 152.
  • a second flank 154 of the gate rotor groove 126 comprises a concave curved portion formed from point 134 to a point 156 by traveling generation by a curved portion on the tip of the main rotor lobe 118.
  • Te curved portion on the lobe 118 is formed by a radius R;, with its center 158 on a line defining, in part, the angle A
  • the remaining portion of flank 154 from point 156 to a point approximately on the pitch circle 130 is a convex curved portion defined by a radius R. tangent to the traveling generated portion at point 156.
  • the radius R. has a center 160 on a line through point 127 and forming an angle A with the line 132.
  • the main rotor 116 has a profile on the flank 162 formed between the pitch circle 128 and a point 164 which is traveling generated by the gate rotor circular arc portion defined by radius R...
  • the traveling generated portion of the flank 162 of the main rotor is tangent to the radius R at point 164.
  • the main rotor tip from point 164 to point 134 is formed by the radius R
  • the flank portion of the main rotor 116 from point 136 to a point 166 is traveling generated by the portion of the gate rotor formed by the radius R and the flank portion of the main rotor from point 166 toward the pitch circle 128 is traveling generated by the gate rotor portion defined by the radius R
  • the curved portions 168 radially inward of the pitch circle 128 are generated by the corresponding curved portions 150 on the gate rotor 122.
  • the profiles shown in FIG. 5 are the theoretical zero clearance profiles. These profiles may also be modified to provide suitable clearances.
  • FIG. 3 Radius: R, 0.2eooc 0.2aooc R, 0.2oooc 0.400oc R 0.0650C 0. l 000C R, 0.200UC 0.4000C R 0.2 l 70C Angle: A 68 54' What is claimed is:
  • a pair of cooperating main and gate rotors having helical lobes and intervening grooves and adapted for rotation about parallel axes within a chamber formed in a helical screw rotor machine, said rotors having profiles defining the shape of said grooves and lobes formed in such a way that, in a plane transverse to the axes of rotation, said gate rotor grooves are formed to have:
  • a concave curved portion forming at least a part of a first groove flank and defined by a radius having its center outside the gate rotor pitch circle;
  • said main rotor lobes having flanks which are substantially formed by traveling generation by said concave curved portion of said first flank and said convex curved portions forming said gate rotor grooves.
  • said convex curved portion on said first flank extends from said gate rotor pitch circle to a meeting point with said concave curved portion on said first flank.
  • said concave and convex curved portions on said first flank are tangent at said meeting point.
  • said convex curved portion on said first flank is formed as a circular arc.
  • said convex curved portion on said second flank extends from said gate rotor pitch circle to a meeting point with said concave curved portion which is traveling generated.
  • said concave and convex curved portions on said second flank are tangent at said meeting point.
  • said convex curved portion on said second flank is formed as a circular arc.
  • said profile on said gate rotor groove comprises a concave curved portion forming the radially innermost part of said gate rotor groove which meets said concave curved portions on said first and second flanks and is tangent to said concave curved portions on said first and second flanks.
  • said portion of said main rotor lobe tip comprises a curved portion which traveling generates said concave curved portion on said second flank.
  • said curved portion on said main rotor lobe tip comprises a circular arc having a radius center located have
  • the profile of a gate rotor lobe includes a lobe tip portion formed as a curved surface defined by the pitch circle of said gate rotor and portions on said lobe tip on each side of said curved surface which slope radially inwardly from said pitch circle from respective meeting points with said curved surface.
  • a pair of cooperating main and gate rofors having helical lobes and intervening groove and adapted for rotation about parallel axes within a chamber formed in a helical screw rotor machine, said rotors having profiles defining the shape of said grooves and lobes formed in such a way that, in a plane transverse to the axes of rotation, said gate rotor grooves are formed to have:
  • a concave curved portion forming at least a part of a first groove flank and defined by a radius having its center outside the gate rotor pitch circle; b. a convex curved portion on said first flank; c. a concave curved portion forming at least a part of a second groove flank and being generated by a curved portion of said main rotor lobe tip; and, d.
  • said main motor lobes have flanks which are substantially formed by traveling generation by said convex curved portion of said first flank and said convex curved portions forming said gate rotor grooves;
  • said curved portion on said main rotor lobe tip comprises a circular are having a radius center located on a line which passes through the meeting point of the main and gate rotor pitch circles, said line forming an angle with a straight line passing through the main and gate rotor axes of rotation, and said profile of said main rotor includes a flank portion which is traveling generated by said first flank and a straight line portion formed on said main rotor lobe tip, said straight line portion meeting said flank portion.
  • said main rotor lobe tip includes a curved portion forming the radially outermost portion of said main rotor lobe which is disposed between said circular are formed on said main rotor lobe tip and said straight line portion formed on said main rotor lobe tip.
  • said curved portion forming the radially outermost portion of said main rotor lobe is a circular arc with a radius center at the main rotor axis of rotation.
  • a pair of cooperating main and gate rotors having helical lobes and intervening grooves and adapted for rotation about parallel axes within a chamber formed in a helical screw rotor machine, said rotors having profiles defining the shape of said grooves and lobes formed in such a way that, in a plane transverse to the axes of rotation, said gate rotor grooves are formed to a.
  • a concave curved portion forming at least a part of curved portibns forming said gate rotor grooves; and, a Second groove flank and being generated y a said profile of said main rotor includes a flank portion Curved Portion of Said main rotor lobe tip; which is traveling generated by said first flank and a d. a convex curved portion on said second flank; said main rotor lobes have flanks which are substantially formed by traveling generation by said concave curved portion of said first flank and said convex straight line portion formed on said main rotor lobe tip, said straight line portion meeting said flank portion.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary-Type Compressors (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Milling Processes (AREA)
US00256237A 1972-05-24 1972-05-24 Rotor profiles for helical screw rotor machines Expired - Lifetime US3787154A (en)

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JP (1) JPS524764B2 (xx)
AU (1) AU461570B2 (xx)
BE (1) BE792576A (xx)
CA (1) CA975336A (xx)
GB (1) GB1358505A (xx)
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US4053263A (en) * 1973-06-27 1977-10-11 Joy Manufacturing Company Screw rotor machine rotors and method of making
FR2365711A1 (fr) * 1976-09-27 1978-04-21 Kuehlautomat Veb Paire de rotors pour machine a rotors a vis
US4109362A (en) * 1976-01-02 1978-08-29 Joy Manufacturing Company Method of making screw rotor machine rotors
US4140445A (en) * 1974-03-06 1979-02-20 Svenka Rotor Haskiner Aktiebolag Screw-rotor machine with straight flank sections
US4142765A (en) * 1977-02-10 1979-03-06 Sullair Corporation Rotor bearing assembly for rotary gas machine
DE3034299A1 (de) * 1979-09-14 1981-04-02 Hitachi, Ltd., Tokyo Schraubenverdichter bzw. -motor
DE3246685A1 (de) * 1981-12-22 1983-06-30 Sullair Technology AB, 11653 Stockholm Rotoren fuer eine schraubenrotormaschine
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EP0104265A1 (en) * 1982-09-24 1984-04-04 Hitachi, Ltd. Method for producing a pair of screw rotors of a screw compressor
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EP0122725A1 (en) * 1983-03-16 1984-10-24 KABUSHIKI KAISHA KOBE SEIKO SHO also known as Kobe Steel Ltd. Screw rotors for compressors or the like
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EP0158514A2 (en) * 1984-04-07 1985-10-16 Hokuetsu Industries Co., Ltd. Screw rotors
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US6098266A (en) * 1995-01-26 2000-08-08 Kirsten; Guenter Method for the production of rotors for screw-type compressors
US6599112B2 (en) 2001-10-19 2003-07-29 Imperial Research Llc Offset thread screw rotor device
US20060078453A1 (en) * 2004-10-12 2006-04-13 Fu Sheng Industrial Co. , Ltd. Mechanism of the screw rotor
BE1016701A5 (fr) * 2003-01-15 2007-05-08 Hitachi Ind Co Ltd Compresseur a vis et procede de fabrication de rotors adequats.
US20080031762A1 (en) * 2006-08-01 2008-02-07 Dieter Mosemann Screw compressor for extremely high working pressure
US20100260637A1 (en) * 2007-12-07 2010-10-14 Daikin Industries, Ltd. Single-screw compressor
US20110058974A1 (en) * 2005-05-23 2011-03-10 Eaton Corporation Optimized helix angle rotors for roots-style supercharger
CN102678181A (zh) * 2012-05-28 2012-09-19 上海齐耀膨胀机有限公司 一种双螺杆膨胀机转子型线
CN103291619A (zh) * 2013-07-03 2013-09-11 上海齐耀螺杆机械有限公司 一种喷油的双螺杆压缩机转子型线
US9057373B2 (en) 2011-11-22 2015-06-16 Vilter Manufacturing Llc Single screw compressor with high output
WO2015197123A1 (en) * 2014-06-26 2015-12-30 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors
US9822781B2 (en) 2005-05-23 2017-11-21 Eaton Corporation Optimized helix angle rotors for roots-style supercharger
US10436197B2 (en) 2005-05-23 2019-10-08 Eaton Intelligent Power Limited Optimized helix angle rotors for roots-style supercharger
CN113732738A (zh) * 2021-09-18 2021-12-03 自贡硬质合金有限责任公司 一种外圆加工方法及辅助工装
US11286932B2 (en) 2005-05-23 2022-03-29 Eaton Intelligent Power Limited Optimized helix angle rotors for roots-style supercharger

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JPS5611143A (en) * 1979-07-10 1981-02-04 Nippon Kokan Kk <Nkk> Horizontal continuous casting method
IN157732B (xx) 1981-02-06 1986-05-24 Svenska Rotor Maskiner Ab
JPS58191663U (ja) * 1982-06-15 1983-12-20 ヤマハ株式会社 電気機器における電気部品の取付装置
JP2684458B2 (ja) * 1991-02-19 1997-12-03 川崎重工業株式会社 水平連続鋳造設備の引抜き制御システム

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Cited By (47)

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US4028026A (en) * 1972-07-14 1977-06-07 Linde Aktiengesellschaft Screw compressor with involute profiled teeth
US4053263A (en) * 1973-06-27 1977-10-11 Joy Manufacturing Company Screw rotor machine rotors and method of making
US4140445A (en) * 1974-03-06 1979-02-20 Svenka Rotor Haskiner Aktiebolag Screw-rotor machine with straight flank sections
US4109362A (en) * 1976-01-02 1978-08-29 Joy Manufacturing Company Method of making screw rotor machine rotors
FR2365711A1 (fr) * 1976-09-27 1978-04-21 Kuehlautomat Veb Paire de rotors pour machine a rotors a vis
US4142765A (en) * 1977-02-10 1979-03-06 Sullair Corporation Rotor bearing assembly for rotary gas machine
DE3034299A1 (de) * 1979-09-14 1981-04-02 Hitachi, Ltd., Tokyo Schraubenverdichter bzw. -motor
US4401420A (en) * 1979-09-14 1983-08-30 Hitachi, Ltd. Male and female screw rotor assembly with specific tooth flanks
US4406602A (en) * 1980-12-03 1983-09-27 Hitachi, Ltd. Screw rotor with specific tooth profile
US4460322A (en) * 1981-12-22 1984-07-17 Sullair Technology Ab Rotors for a rotary screw machine
DE3246685A1 (de) * 1981-12-22 1983-06-30 Sullair Technology AB, 11653 Stockholm Rotoren fuer eine schraubenrotormaschine
EP0104265A1 (en) * 1982-09-24 1984-04-04 Hitachi, Ltd. Method for producing a pair of screw rotors of a screw compressor
EP0122725A1 (en) * 1983-03-16 1984-10-24 KABUSHIKI KAISHA KOBE SEIKO SHO also known as Kobe Steel Ltd. Screw rotors for compressors or the like
US4583927A (en) * 1983-03-16 1986-04-22 Kabushiki Kaisha Kobe Seiko Sho Screw rotor mechanism
US4457680A (en) * 1983-04-27 1984-07-03 Paget Win W Rotary compressor
US4508496A (en) * 1984-01-16 1985-04-02 Ingersoll-Rand Co. Rotary, positive-displacement machine, of the helical-rotor type, and rotors therefor
EP0158514A2 (en) * 1984-04-07 1985-10-16 Hokuetsu Industries Co., Ltd. Screw rotors
US4576558A (en) * 1984-04-07 1986-03-18 Hokuetsu Industries Co., Ltd. Screw rotor assembly
EP0158514A3 (en) * 1984-04-07 1987-01-07 Hokuetsu Industries Co., Ltd. Screw rotors
EP0174081A2 (en) * 1984-08-31 1986-03-12 Dunham-Bush Inc. Screw rotor compressor or expander
EP0174081A3 (en) * 1984-08-31 1986-03-26 Dunham-Bush Inc. Screw rotor compressor or expander
US6098266A (en) * 1995-01-26 2000-08-08 Kirsten; Guenter Method for the production of rotors for screw-type compressors
US6599112B2 (en) 2001-10-19 2003-07-29 Imperial Research Llc Offset thread screw rotor device
US20040151609A1 (en) * 2001-10-19 2004-08-05 Heizer Charles K. Offset thread screw rotor device
US6913452B2 (en) 2001-10-19 2005-07-05 Imperial Research Llc Offset thread screw rotor device
US6719547B2 (en) 2001-10-19 2004-04-13 Imperial Research Llc Offset thread screw rotor device
BE1016701A5 (fr) * 2003-01-15 2007-05-08 Hitachi Ind Co Ltd Compresseur a vis et procede de fabrication de rotors adequats.
US20060078453A1 (en) * 2004-10-12 2006-04-13 Fu Sheng Industrial Co. , Ltd. Mechanism of the screw rotor
US8632324B2 (en) * 2005-05-23 2014-01-21 Eaton Corporation Optimized helix angle rotors for roots-style supercharger
US11286932B2 (en) 2005-05-23 2022-03-29 Eaton Intelligent Power Limited Optimized helix angle rotors for roots-style supercharger
US10436197B2 (en) 2005-05-23 2019-10-08 Eaton Intelligent Power Limited Optimized helix angle rotors for roots-style supercharger
US20110058974A1 (en) * 2005-05-23 2011-03-10 Eaton Corporation Optimized helix angle rotors for roots-style supercharger
US9822781B2 (en) 2005-05-23 2017-11-21 Eaton Corporation Optimized helix angle rotors for roots-style supercharger
US7753665B2 (en) * 2006-08-01 2010-07-13 Grasso Gmbh Refrigeration Technology Screw compressor for working pressures above 80 bar
US20080031762A1 (en) * 2006-08-01 2008-02-07 Dieter Mosemann Screw compressor for extremely high working pressure
US8568119B2 (en) * 2007-12-07 2013-10-29 Daikin Industries, Ltd. Single screw compressor
US20100260637A1 (en) * 2007-12-07 2010-10-14 Daikin Industries, Ltd. Single-screw compressor
US9057373B2 (en) 2011-11-22 2015-06-16 Vilter Manufacturing Llc Single screw compressor with high output
CN102678181A (zh) * 2012-05-28 2012-09-19 上海齐耀膨胀机有限公司 一种双螺杆膨胀机转子型线
CN102678181B (zh) * 2012-05-28 2014-05-14 上海齐耀膨胀机有限公司 一种双螺杆膨胀机转子型线
CN103291619B (zh) * 2013-07-03 2015-06-17 上海齐耀螺杆机械有限公司 一种喷油的双螺杆压缩机转子型线
CN103291619A (zh) * 2013-07-03 2013-09-11 上海齐耀螺杆机械有限公司 一种喷油的双螺杆压缩机转子型线
WO2015197123A1 (en) * 2014-06-26 2015-12-30 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors
RU2667572C2 (ru) * 2014-06-26 2018-09-21 Свенска Ротор Машинер Аб Пара взаимодействующих винтовых роторов
US10451065B2 (en) 2014-06-26 2019-10-22 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors
CN113732738A (zh) * 2021-09-18 2021-12-03 自贡硬质合金有限责任公司 一种外圆加工方法及辅助工装
CN113732738B (zh) * 2021-09-18 2022-08-05 自贡硬质合金有限责任公司 一种外圆加工方法及辅助工装

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GB1358505A (en) 1974-07-03
AU461570B2 (en) 1975-05-29
CA975336A (en) 1975-09-30
JPS4926812A (xx) 1974-03-09
AU4712472A (en) 1974-04-04
BE792576A (fr) 1973-03-30
JPS524764B2 (xx) 1977-02-07
ZA726577B (en) 1973-06-27

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