US3414189A - Screw rotor machines and profiles - Google Patents

Screw rotor machines and profiles Download PDF

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Publication number
US3414189A
US3414189A US564469A US56446966A US3414189A US 3414189 A US3414189 A US 3414189A US 564469 A US564469 A US 564469A US 56446966 A US56446966 A US 56446966A US 3414189 A US3414189 A US 3414189A
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United States
Prior art keywords
rotor
gate
main
thread
gate rotor
Prior art date
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Expired - Lifetime
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US564469A
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English (en)
Inventor
Jan Edvard Persson
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Atlas Copco AB
Original Assignee
Atlas Copco AB
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 Atlas Copco AB filed Critical Atlas Copco AB
Priority to US564469A priority Critical patent/US3414189A/en
Priority to GB25352/67A priority patent/GB1189856A/en
Priority to NO168531A priority patent/NO118932B/no
Priority to DK309767AA priority patent/DK134412B/da
Priority to AT05618/67A priority patent/AT279024B/de
Priority to BE700077D priority patent/BE700077A/xx
Priority to CS4486A priority patent/CS161695B2/cs
Priority to FR111108A priority patent/FR1535573A/fr
Priority to DE19671551072 priority patent/DE1551072A1/de
Priority to ES342045A priority patent/ES342045A1/es
Priority to YU1243/67A priority patent/YU31658B/xx
Priority to DD12545367A priority patent/DD72218A5/de
Priority to CH880367A priority patent/CH495509A/de
Priority to FI671752A priority patent/FI47134C/fi
Priority to NL6708716.A priority patent/NL156480B/xx
Application granted granted Critical
Publication of US3414189A publication Critical patent/US3414189A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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

  • This invention relates to screw rotor machines comprisring a housing with intersecting parallel bores and inlet and outlet passages communicating with said bores through inlet and outlet ports arranged in the housing and having main and gate rotors with at least three helical threads and grooves on the main rotor intermeshing with at least four helical threads and grooves on the gate rotor.
  • Said main and gate rotors cooperate with one another and with the walls of said bores to define pockets for a working fluid moving from the inlet towards the outlet ports of the housing.
  • said threads and grooves of the main rotor lie substantially outside the pitch circle of the main rotor and said main rotor threads have a generally convex profile on the leading and trailing flanks
  • said threads and grooves of the gate rotor being at least one more than the main rotor threads and grooves and lie substantially inside the pitch circle of the gate rotor and said gate rotor threads have generally concavely curved profiles on the leading and trailing flanks.
  • Screw rotor machines of this type may also operate as vacuum pumps, gas meters and similar devices, or as pumps or motors operating on incompressible fluids such as oil, water or other material.
  • Montelius suggests a screw rotor machine with a main and a gate rotor with threads of the above type and in which a root portion of the main rotor thread cooperates with a crest portion of the gate rotor thread to provide rolling contact along said portions which are situated close to the pitch circles. Between said portions a band seal is consequently obtained and the root portion is in a manner well known from cycloid gears produced by travelling generation i.e. by points moving along the crest portion of the gate rotor thread.
  • Montelius discloses a single threaded main screw rotor and a double threaded gate screw rotor which for this and other reasons is not suitable for screw rotor machines according to the invention.
  • Lysholm has suggested a screw rotor machine in which the main rotor has threads with convex profile which are situated outside the pitch circle of the main rotor and the gate rotor has threads with concave profile which lie inside the pitch circle of the gate rotor.
  • the leading flank of the main rotor thread in Lysholms machine has circular profile and the trailing flank of said thread has a profile generated by the outermost edge of the leading flank of the gate rotor.
  • the trailing flank of the gate rotor threads in Lysholms machine has a circular profile corresponding to the circular profile of the leading flank of the main rotor thread.
  • Lysholms profile as above described and illustrated in FIGS. 2-5 in his patent has the advantage that it produces a continuous sealing line between high and low pressure spaces in the machine thus avoiding leakage except through said seal during the operation of the machine.
  • Lysholms profile however, has the disadvantage that the edges of the gate rotor thread which generate the trailing flanks and part of the leading flanks of the main rotor profile and during operation are intended to form space packing between the rotors are very difficult to manufacture with enough accuracy to give the sealing characteristics which are needed to obtain an acceptable efficiency of the machine. Also the same edges are extremely exposed to damage during operation and any damage done to said edges spoils a considerable length of the sealing line and thereby reduces the eificiency of the machine.
  • r is the radius of the circular main and gate rotor flank portions b c and b c
  • the portion c -di of the main rotor flank is generated by 0 on the gate rotor thread.
  • Addendum f fits in dedendum f
  • the addendum beyond the pitch circle of the gate rotor and the dedendum inside the pitch circle of the main rotor are shown very much larger in proportion to the radii of the rotors than would be desirable in practice. This is what Lysholm says about the size of this modification.
  • the arrows WM and w indicate main and gate rotor directions of rotation.
  • Lysholm machine is designed to operate with small clearances everywhere between the main and gate rotors and between the housing and the rotors to form the above mentioned space packing alongthe sealing line.
  • FIG. 4 is a cross section contour similar to FIG. 3 of a main rotor thread and meshing gate rotor groove end threads of one embodiment of Nilssons machine.
  • the profiles of both rotors have symmetrically shaped leading and trailing flanks.
  • the gate rotor profile is shaped as a circular arc a -c d with the radius 1' inside the pitch circle and has the above mentioned addendum portion f outside the pitch circle.
  • the main rotor profile complements the gate rotor profile in so far as the main potrion of the flanks adjacent the crest is a circular arc b c d mating the one on the gate rotor.
  • the root portions ti -b and dr-1 of the main rotor flanks are generated by the points a and d on the gate rotor pitch circle and the dedendum portion f inside the pitch circle fits the addendum portion of the gate rotor profile.
  • M and G again indicate main and gate rotor axes.
  • R and R are again main and gate rotor pitch circle radii and R and R bore radii of main and gate rotor bores.
  • Nilssons machine is also designed to operate with small clearances to form a space packing everywhere between the main and gate rotors as well as between the rotors and the housing.
  • e f is a leading root portion of the main rotor thread generated by a straight line portion d e of the gate rotor thread.
  • b -c on the main rotor thread is generated by the point b of the gate rotor thread and b c on the gate rotor thread by the summit c of the main rotor thread.
  • c -d on the main rotor thread and c -d on the gate rotor thread are circles with radius r struck on the point P.
  • d e on the main rotor thread is generated by the point d of the gate rotor thread.
  • Lysholms original profile is that in the LS1 profile the point b on the gate rotor profile which is generating the trailing flank of the main rotor profile is moved inside the pitch circle.
  • the corresponding part (1 -12 of the main rotor profile is generated by the line a b i.e. by a point continuously moving along said line.
  • One object of the present invention is to obtain a screw rotor machine in which seizing of the rotors is practically avoided by providing a profile wherein:
  • the gate rotor does not need to be driven externally but is continuously driven in the rotation direction by the internal fluid pressure and this internal driving torque does not exceed what the gear portions of the profiles may safely carry. This also means that in oilflooded compressors or other machines handling a lubricating medium synchronizing gears may be dispensed with without any risk of wear of the rotor profiles.
  • Another object of the invention is to increase the eificiency of the screw rotor machine by providing a profile wherein:
  • FIG. 1 is a longitudinal vertical section and FIG. 2 a plan view of a typical screw compressor, the rotors of which can be carried out with the above mentioned known profiles as well as with a profile according to the present invention.
  • FIGS. 3-5 illustrate as above described the Lysholm, Nilsson and LSI profiles, respectively, in order to give substantially the present state of the art.
  • FIGS. 6a and b show diagrammatically and with a heavy line the sealing lines on the main and gate rotors of the LS1 profile shown in FIG. 5.
  • FIG. 60 is a transverse section through the rotor of FIG. 6a.
  • FIG. 6d is a transverse section through the rotor of FIG. 6b.
  • FIG. 7 illutrates a cross section contour similarly as in FIGS. 3-5 of a main rotor thread and meshing gate rotor groove and threads of what might preferably be called the basic profile according to the present invention.
  • FIGS. 8a and b are views of the sealing lines or areas on the main and gate rotors with the profile shown in FIG. 7.
  • FIG. 80 is a transverse section through the rotor of FIG. 8a.
  • FIG. 8d is a transverse section through the rotor of FIG. 8b.
  • FIG. 9 shows on an exaggerated scale the gate rotor profile of the invention together with a theoretical profile with constant clearance in order to indicate the variations of the clearances according to the invention.
  • FIGS. 10a;f show diagrammatically the meshing main and gate rotors in different relative rotor positions.
  • FIG. ll shows diagrammatically a cross section and FIG. 12 a longitudinal section of the rotors of the invention with the sealing lines between volumes of different pressures indicated in rotational projection with a view to illustrate the surfaces on the gate rotor profile where two opposite flanks of the engaging threads are exposed to different pressures which cause driving or braking torques on the rotors.
  • Screw rotor compressors according to the invention may have one or more main rotors and one or more gate rotors cooperating therewith and with the housing to provide working pockets which change volume as they move along the screw rotors from an inlet port to an outlet port.
  • Screw rotor machines according to the invention may, furthermore, be singlestage, two-stage or multiple-stage machines, and the number of compression stages, for instance, does not influence the character of the screw rotors according to the invention.
  • the illustrated machine is a single-stage screw rotor compressor with one main rotor and one gate rotor mounted for rotation in intersecting bores with parallel axes in a housing and having intermeshing helical threads and grooves.
  • the screw compressor illustrated in FIGS. 1 and 2 consists of a housing which comprises a lower portion 31, an upper portion 32, a two-piece inlet end portion 33, 34, and a synchronizing end portion 35. Air or other gaseous fluid is supplied to the screw compressor housing 31, 32 through the inlet connection 36 and compressed air or other gaseous fluid handled by the compressor leaves the compressor through the outlet connection 37.
  • two screw type rotors 38 and 39 are mounted for rotation in the intersecting bores 10 and 11, the rotor shafts being carried in bearings 12 and 13, which may be plain hearings or hell or roller bearings.
  • the rotors are fixed in position endwise by thrust bearings 14, which may be plain cam hearings or ball or roller bearings capable of taking axial thrust.
  • Conventional sealing rings 15 and 16 are provided around the shafts at the rotor ends to prevent leakage into or from the compression chambers.
  • the compressor is provided with synchronizing gears 17, 18. 19 and 20 are oil sealing rings which prevent oil leakage from the bearing housings.
  • From the inlet connection 36 an inlet passage 21 which is carried out with two branches around the rotor shafts leads to an inlet port 22 communicating with the bores 10, 11.
  • An outlet port indicated at 23 in the lower end portion and the bottom of the housing 31 communicates with an outlet passage 24- and the outlet connection 37 of the compressor.
  • the compressor may be driven by any suitable source of power, such as a diesel engine or an electric motor, over a shaft connection 25.
  • the inlet and outlet ports may be shaped in various different ways and, for instance, as illustrated in my application for Screw Rotor Machines filed concurrently with this application.
  • FIGS. 712 The shape of the main and gate rotors 38, 39 which is characteristic of the present invention is disclosed in FIGS. 712.
  • FIG. 7 is a cross section of a portion of the housing 31, 32 and intermeshing threads and grooves of the rotors 38 and 39 and shows the general shape of the profiles without consideration to the clearances and seals which are more particularly illustrated in connection with FIGS. 810.
  • the same reference letters have been used in FIG. 7 as in the cross section contours of known screw rotor machines illustrated in FIGS.
  • R and R are the main and gate rotor pitch circle radii and R and R are the bore radii of the main and gate rotor bores.
  • the bore radius R of the gate rotor is in the illustrated embodiment the same as the pitch circle radius R of the gate rotor.
  • a b -c is the main rotor trailing flank and a b c the leading flank of the gate rotor.
  • a b is a band seal portion formed as a straight line and is a portion of a radius of the gate rotor.
  • b2C2 is without consideration to the clearances generated by the summit c of the main rotor thread.
  • (l -b is the trailing root portion of the main rotor thread and is without consideration to the clearances generated by the straight line portion a b of the gate rotor thread so that a band seal is obtrined between said portions.
  • the point a is generated by a and the point b by b also without consideration of clearances.
  • the portion b c of the main rotor trailing flank is generated by the point 11 or the inner end portion of the band seal portion a b on the gate rotor also without consideration to the clearances.
  • the portion of the main rotor thread from c d is circular with a radius r struck on the point P which is the point of intersection between the pitch circles.
  • the portion ai -e of the leading main rotor thread is without consideration to the clearances generated by a portion d e which is a straight radial portion of the trailing gate rotor thread.
  • the portion c d of the trailing gate rotor thread is a circular arc with substantially radius r which with suitable clearance conforms with the arc c d
  • FIGS. 8a and 1) illustrate the sealing between a pair of screw rotors such as disclosed in FIG. 7 and it should be noted that an uninterrupted sealing line is obtained substantially all the way to the line of intersection 26 between the intersecting bores 10 and 11.
  • the blow hole obtained in connection with the above mentioned known compressor is here as in the above mentioned LSI-compressor reduced to a minimum of no importance since the sealing lines between the rotors meet substantially with the line of intersection 26.
  • the relative quality of the seal along the sealing lines of the profiles according to the invention are indicated by the number of parallel dot and dash lines in FIGS. 8a and b and are referred to later on for comparison with FIGS. 11 and 12.
  • FIG. 9 shows in somewhat exaggerated scale an example of a gate rotor profile according to the invention and a constant clearance profile shown in dotted lines and illustrates the intended variations in clearances for a gate rotor as compared with a conventional thread when cooperating with a main rotor profile.
  • the same clearance variations may of course be obtained by suitable modification of the main rotor profile instead or even by different combinations of modifications of both rotor profiles and all such combinations which give the cooperating characteristics according to this invention are intended to be included under the scope of this patent.
  • FIG. 10 shows cooperating parts of rotor profiles according to the invention in different angular positions and illustrates the varying clearances.
  • the clearances in various portions of the profiles are marked Cl in FIGS. 10af with a number and in a suitable embodiment Cl 1 is smaller than Cl 7, Cl 5 and Cl 4; Cl 2 is smaller than Cl 4 and Cl 8 is smaller than Cl 5 and Cl 6.
  • the clearance Cl 4 between the circular arc portions c d and c d is according to the invention made large enough to prevent seizing in this area, and the clearance Cl 2 is smaller than the clearance Cl 4 so that any contact due to disturbances in the synchronization, for example, occurs between the root portion d e and the portion d 2 of the gate rotor in areas where the relative movement between said portions is small. Furthermore, the clearance Cl 1 is made less than Cl 7 and consequently any contact due to bearing wear or distortion of the rotors transversely to the rotor axes results in nondangerous rolling contact between the gate rotor crests and the cylindrical bottom of the main rotor grooves.
  • the size of the variations of the clearances in the different areas as compared to conventional constant clearance machines may amount to about :30%. This means that the clearance between a "e and the bottom of the main rotor grooves, between a "-b and a b on the main rotor trailing flank, and between d e and al -e on the main rotor leading flank is about of the clearance in conventional constant clearance machines.
  • FIGS. 11 and 12 illustrate in axial view and rotational projection the sealing lines between the intermeshing portions of the rotors 38, 39 and show how the compressed gas acts on the gate rotor lobes in the rotation direction. For this purpose all points on the sealing lines are shown at their correct radial distances from the gate rotor centerline as indicated by the arrows x, y, z.
  • FIGS. 11 and 12 corresponds to the point P (2 in FIG. 7, 2 to d 3 to c 4 to b 5 to I2 and 6 to P (a The same numbers as in FIGS. 11 and 12 are used in FIG. 8b to facilitate the comparison between the sealing lines in these views.
  • the profile parts a b and d -e in FIG. 7 serve to show how the projections on the side views are taken looking on the respective rotor. It would be obvious that with the rotational direction Wm, Wg indicated in FIG. 7 the pressure difference within the area A will cause a driving action and the pressure difference within the area B will cause a braking action on the gate rotor.
  • the profile part a b may preferably be chosen 550% of the depth of the gate rotor thread and d e may be chosen 525% of Said depth. To make the profile portion a b short means that the blow hole area is small and the sealing line long.
  • a long portion a -b means a bigger blow hole and a shorter sealing line of better quality.
  • the blow hole area will increase in proportion to the square of the diameter whereas the length of the sealing tline increases in proportion to the diameter.
  • the optimum length of the profile part a b depends upon the rotor dimensions.
  • the manufacturing tolerances which will influence the leakage through the space packing along the sealing line more than the leakage through the blow hole has to be taken into consideration when choosing the length of the part a b As an example it may be mentioned that for a rotor diameter of 200 mm.
  • the best length of the profile part a b has been found to be about 10% of the depth of the gate rotor thread.
  • the length of the profile portion d -e may thereafter be chosen to give the desired size of the area A so that a suitable driving torque is obtained on the gate rotor. Since the torque required depends upon the rotor bearing friction the use of antifn'ction bearings will be advantageous for the efflciency of the compressor also by indirectly reducing the internal leakage by allowing the profile portion 12-62 to be increased, which also results in a somewhat shorter sealing line.
  • the length of the profile part d e may preferably be about 25% of the gate rotor thread depth.
  • the number of threads of a compressor according to the invention must on the main rotor be at least three and the rotor length and lead such that the main rotor root portion (l -b is in constant mesh with the band seal portion a b of the gate rotor at least in three cross sections along the rotors.
  • the gate rotor must have at least one more thread than the main rotor.
  • the present invention has given the surprising result that the efiiciency of a screw compressor built with normal manufacturing tolerances for serial production is increased by several percents so that a screw compressor may be built according to the invention which is almost competitive with a reciprocating piston compressor with regard to efliciency. It has also been found that in the case of oil flooded compressors in which cooling and lubricating and sealing oil is injected for taking care of the compression heat and for providing a seal between the rotors and the housing synchronizing gears may be dispensed with without causing any wear of the rotor portions a b (l -b or d e d e which can destroy the important clearances.
  • a screw rotor machine comprising (a) a housing with intersecting parallel bores and inlet and outlet passages communicating with said bores through inlet and outlet ports arranged in the housing (b) main and gate rotors mounted for rotation in said housing in said bores and having at least three intermeshing helical threads and grooves, sai-d main and gate rotors cooperating to define with one another and with the walls of said bores pockets for a working fluid moving from the inlet towards the outlet ports of the housing (c) said threads and grooves of the main rotor lying substantially outside the pitch circle of the main rotor and said main rotor threads having a generally convex profile on the leading and trailing flanks, and said threads and grooves of the gate rotor being at least one more than the main rotor threads and grooves and lying substantially inside the pitch circle of the gate rotor and said gate rotor threads having generally concavely curved profiles on the leading and trailing flanks, and
  • a screw rotor machine in which the radial length of said first and second band seal portions on the leading and trailing gate rotor flanks is so large that first areas are formed on the gate rotor flanks which are subjected to a driving fluid pressure and second areas are formed on the gate rotor flanks which are subjected to a braking fluid pressure, said first areas being so much larger than said second areas that the frictional resistance of the gate rotor is substantially overcome and the gate rotor is substantially driven by fluid pressure.
  • a screw rotor machine comprising (a) a housing with intersecting parallel bores and inlet and outlet passages communicating with said bores through inlet and outlet ports arranged in the housing (b) main and gate rotors mounted for rotation in said housing in said bores and having at least three intermeshing helical threads and grooves, said main and gate rotors cooperating to define with one another and with the walls of said bores pockets for a working fluid moving from the inlet towards the outlet ports of the housing (0) said threads and grooves of the main rotor lying substantially outside the pitch circle of the main rotor and said main rotor threads having a generally convex profile on the leading and trailing flanks, and said threads and grooves of the gate rotor being at least one more than the main rotor threads and grooves and lying substantially inside the pitch circle of the gate rotor and said gate rotor threads having generally concavely curved profiles on the leading and trailing flanks, and
  • a screw rotor machine comprising:
  • a screw rotor machine in which a band seal portion is provided on the trailing flank of the gate rotor thread extending from the crest of the gate rotor thread a short distance towards the gate rotor axis, a cooperating first portion of the leading flank of the main rotor thread extending from the root of the main rotor thread to form a first root portion generated with minimum clearance by said band seal portion on the trailing gate vrotor flank, and a second portion between said first root portion and the summit of the main rotor thread substantially formed as a circular arc and cooperating with a portion of the trailing gate rotor flank formed as a circular arc conforming with said second portion on the leading main rotor thread and cooperating therewith with a third clearance substantially larger than said minimum clearance.
  • a screw rotor machine in which the radial length of the band seal portions of the leading and trailing gate rotor thread flanks is so large, that first areas are formed on the gate rotor thread flanks which are subjected to a driving fluid pressure, and that second areas are formed on the gate rotor thread flanks which are subjected to a braking fluid pressure, said first areas being so much larger than said second areas that the frictional resistance of the gate rotor is substantially overcome and the gate rotor is substantially driven by fluid pressure.
  • a screw rotor machine in which the band seal portions on the leading and trailing gate rotor thread flanks are formed by straight portions of gate rotor radii.
  • a screw rotor machine in which a cylindrical portion at the crest of the gate rotor thread and a cylindrical portion at the bottom of the main rotor groove said cylindrical portions are lying on the pitch circles of the gate and main rotors, respectively, so that they can cooperate with rolling contact, a sixth clearance between said cylindrical portions being at least 30% less than a seventh clearance between the summit of the main rotor thread and the bottom of the gate rotor groove, whereby contact is avoided between the main rotor thread summit and the bottom of the gate rotor grooves.
  • a pair of cooperating screw rotors according to claim 11 in which a cylindrical portion at the crest of the gate rotor thread and a cylindrical portion at the bottom of the main rotor groove said cylindrical portions are lying on the pitch circles of the gate and main rotors, respectively, so that they can cooperate with rolling contact, a sixth clearance between said cylindrical portions being at least 30% less than a seventh clearance between the summit of the main rotor thread and the bottom of the gate rotor groove, whereby contact is avoided between the main rotor thread summit and the bottom of the gate rotor grooves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US564469A 1966-06-22 1966-06-22 Screw rotor machines and profiles Expired - Lifetime US3414189A (en)

Priority Applications (15)

Application Number Priority Date Filing Date Title
US564469A US3414189A (en) 1966-06-22 1966-06-22 Screw rotor machines and profiles
GB25352/67A GB1189856A (en) 1966-06-22 1967-06-01 Improvements in Screw Rotor Machines and Profiles
NO168531A NO118932B (xx) 1966-06-22 1967-06-09
DK309767AA DK134412B (da) 1966-06-22 1967-06-15 Skruerotormaskine.
AT05618/67A AT279024B (de) 1966-06-22 1967-06-16 Schneckenmaschine
BE700077D BE700077A (xx) 1966-06-22 1967-06-16
CS4486A CS161695B2 (xx) 1966-06-22 1967-06-19
DE19671551072 DE1551072A1 (de) 1966-06-22 1967-06-20 Schneckenmaschine
FR111108A FR1535573A (fr) 1966-06-22 1967-06-20 Machines à rotors hélicoïdaux
ES342045A ES342045A1 (es) 1966-06-22 1967-06-20 Maquina accionadora por rotores de tornillo.
YU1243/67A YU31658B (en) 1966-06-22 1967-06-21 Masina s puzevima
DD12545367A DD72218A5 (de) 1966-06-22 1967-06-21 Schneckenmaschine
CH880367A CH495509A (de) 1966-06-22 1967-06-21 Schneckenmaschine
FI671752A FI47134C (fi) 1966-06-22 1967-06-21 Ruuvikompressori.
NL6708716.A NL156480B (nl) 1966-06-22 1967-06-22 Schroefrotormachine.

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Application Number Priority Date Filing Date Title
US564469A US3414189A (en) 1966-06-22 1966-06-22 Screw rotor machines and profiles

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US3414189A true US3414189A (en) 1968-12-03

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US564469A Expired - Lifetime US3414189A (en) 1966-06-22 1966-06-22 Screw rotor machines and profiles

Country Status (15)

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US (1) US3414189A (xx)
AT (1) AT279024B (xx)
BE (1) BE700077A (xx)
CH (1) CH495509A (xx)
CS (1) CS161695B2 (xx)
DD (1) DD72218A5 (xx)
DE (1) DE1551072A1 (xx)
DK (1) DK134412B (xx)
ES (1) ES342045A1 (xx)
FI (1) FI47134C (xx)
FR (1) FR1535573A (xx)
GB (1) GB1189856A (xx)
NL (1) NL156480B (xx)
NO (1) NO118932B (xx)
YU (1) YU31658B (xx)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3535057A (en) * 1968-09-06 1970-10-20 Esper Kodra Screw compressor
US3623830A (en) * 1970-04-01 1971-11-30 Bird Island Inc Rotor with helical teeth for displacing compressible fluid
US3640649A (en) * 1969-09-23 1972-02-08 Jan Edvard Persson Screw rotors
US3773444A (en) * 1972-06-19 1973-11-20 Fuller Co Screw rotor machine and rotors therefor
US3787154A (en) * 1972-05-24 1974-01-22 Gardner Denver Co Rotor profiles for helical screw rotor machines
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
US4088427A (en) * 1974-06-24 1978-05-09 Atlas Copco Aktiebolag Rotors for a screw rotor machine
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
US4224015A (en) * 1977-01-19 1980-09-23 Oval Engineering Co., Ltd. Positive displacement flow meter with helical-toothed rotors
DE2911415A1 (de) * 1979-03-23 1981-01-15 Bammert Karl Rotationskolbenmaschine
US4460322A (en) * 1981-12-22 1984-07-17 Sullair Technology Ab Rotors for a rotary screw machine
US4588363A (en) * 1984-03-28 1986-05-13 Societe Anonyme D.B.A. Volumetric screw compressor
DE19850030A1 (de) * 1998-10-30 2000-05-11 Kraeutler Ges M B H & Co Vorrichtung zum Messen von Flüssigkeitsmengen in Zapfsäulen von Kraftfahrzeug-Tankstellen
US20040155056A1 (en) * 2000-01-25 2004-08-12 Gotit Ltd. Spray dispenser
US20070217935A1 (en) * 2006-03-14 2007-09-20 Shinji Kawazoe Positive-displacement fluid machine
US7828536B2 (en) 2005-08-25 2010-11-09 Atlas Copco Airpower, Naamloze Vennootschap Low-pressure screw compressor
US9057373B2 (en) 2011-11-22 2015-06-16 Vilter Manufacturing Llc Single screw compressor with high output
US20170227009A1 (en) * 2014-06-26 2017-08-10 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6117191U (ja) * 1984-07-04 1986-01-31 株式会社神戸製鋼所 スクリユ圧縮機
DE10101512C2 (de) * 2001-01-12 2002-11-21 Schiedel Gmbh & Co Vorrichtung zur Wärmerückgewinnung aus Abluft
DE102005005347A1 (de) * 2005-01-31 2006-10-26 Kayser, Albrecht, Dipl.-Ing. Rotorprofile für trockene Schraubenverdichter

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US2457314A (en) * 1943-08-12 1948-12-28 Jarvis C Marble Rotary screw wheel device
US2473234A (en) * 1943-10-06 1949-06-14 Joseph E Whitfield Helical asymmetrical thread forms for fluid devices
US2477002A (en) * 1942-07-25 1949-07-26 Joy Mfg Co Gear type air pump with changespeed gearing and lubrication
US2486770A (en) * 1946-08-21 1949-11-01 Joseph E Whitfield Arc generated thread form for helical rotary members
US2622787A (en) * 1947-07-16 1952-12-23 Jarvis C Marble Helical rotary engine
CH324301A (de) * 1953-10-24 1957-09-15 Saurer Ag Adolph Umlaufverdichter mit schraubenförmig verzahnten Rotoren
US2922377A (en) * 1957-09-26 1960-01-26 Joseph E Whitfield Multiple arc generated rotors having diagonally directed fluid discharge flow
US3245612A (en) * 1965-05-17 1966-04-12 Svenska Rotor Maskiner Ab Rotary piston engines
US3314598A (en) * 1965-05-10 1967-04-18 Lysholm Alf Screw rotor machine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2477002A (en) * 1942-07-25 1949-07-26 Joy Mfg Co Gear type air pump with changespeed gearing and lubrication
US2457314A (en) * 1943-08-12 1948-12-28 Jarvis C Marble Rotary screw wheel device
US2473234A (en) * 1943-10-06 1949-06-14 Joseph E Whitfield Helical asymmetrical thread forms for fluid devices
US2486770A (en) * 1946-08-21 1949-11-01 Joseph E Whitfield Arc generated thread form for helical rotary members
US2622787A (en) * 1947-07-16 1952-12-23 Jarvis C Marble Helical rotary engine
CH324301A (de) * 1953-10-24 1957-09-15 Saurer Ag Adolph Umlaufverdichter mit schraubenförmig verzahnten Rotoren
US2922377A (en) * 1957-09-26 1960-01-26 Joseph E Whitfield Multiple arc generated rotors having diagonally directed fluid discharge flow
US3314598A (en) * 1965-05-10 1967-04-18 Lysholm Alf Screw rotor machine
US3245612A (en) * 1965-05-17 1966-04-12 Svenska Rotor Maskiner Ab Rotary piston engines

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3535057A (en) * 1968-09-06 1970-10-20 Esper Kodra Screw compressor
US3640649A (en) * 1969-09-23 1972-02-08 Jan Edvard Persson Screw rotors
US3623830A (en) * 1970-04-01 1971-11-30 Bird Island Inc Rotor with helical teeth for displacing compressible fluid
US3787154A (en) * 1972-05-24 1974-01-22 Gardner Denver Co Rotor profiles for helical screw rotor machines
US3773444A (en) * 1972-06-19 1973-11-20 Fuller Co Screw rotor machine and rotors therefor
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
US4088427A (en) * 1974-06-24 1978-05-09 Atlas Copco Aktiebolag Rotors for a screw rotor machine
US4109362A (en) * 1976-01-02 1978-08-29 Joy Manufacturing Company Method of making screw rotor machine rotors
US4224015A (en) * 1977-01-19 1980-09-23 Oval Engineering Co., Ltd. Positive displacement flow meter with helical-toothed rotors
DE2911415A1 (de) * 1979-03-23 1981-01-15 Bammert Karl Rotationskolbenmaschine
US4350480A (en) * 1979-03-23 1982-09-21 Karl Bammert Intermeshing screw rotor machine with specific thread profile
US4460322A (en) * 1981-12-22 1984-07-17 Sullair Technology Ab Rotors for a rotary screw machine
US4588363A (en) * 1984-03-28 1986-05-13 Societe Anonyme D.B.A. Volumetric screw compressor
DE19850030A1 (de) * 1998-10-30 2000-05-11 Kraeutler Ges M B H & Co Vorrichtung zum Messen von Flüssigkeitsmengen in Zapfsäulen von Kraftfahrzeug-Tankstellen
US20040155056A1 (en) * 2000-01-25 2004-08-12 Gotit Ltd. Spray dispenser
US7828536B2 (en) 2005-08-25 2010-11-09 Atlas Copco Airpower, Naamloze Vennootschap Low-pressure screw compressor
US20070217935A1 (en) * 2006-03-14 2007-09-20 Shinji Kawazoe Positive-displacement fluid machine
US7520737B2 (en) * 2006-03-14 2009-04-21 Scroll Giken Llc Positive-displacement fluid machine
US9057373B2 (en) 2011-11-22 2015-06-16 Vilter Manufacturing Llc Single screw compressor with high output
US20170227009A1 (en) * 2014-06-26 2017-08-10 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors
US10451065B2 (en) * 2014-06-26 2019-10-22 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors

Also Published As

Publication number Publication date
NO118932B (xx) 1970-03-02
NL6708716A (xx) 1967-12-27
DK134412C (xx) 1977-04-04
CH495509A (de) 1970-08-31
DK134412B (da) 1976-11-01
ES342045A1 (es) 1968-07-16
YU124367A (en) 1973-04-30
CS161695B2 (xx) 1975-06-10
FI47134C (fi) 1973-09-10
AT279024B (de) 1970-02-25
GB1189856A (en) 1970-04-29
YU31658B (en) 1973-10-31
BE700077A (xx) 1967-12-18
FI47134B (xx) 1973-05-31
NL156480B (nl) 1978-04-17
DE1551072A1 (de) 1970-03-05
DD72218A5 (de) 1970-04-05
FR1535573A (fr) 1968-08-09

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