US2975963A - Rotor device - Google Patents
Rotor device Download PDFInfo
- Publication number
- US2975963A US2975963A US795534A US79553459A US2975963A US 2975963 A US2975963 A US 2975963A US 795534 A US795534 A US 795534A US 79553459 A US79553459 A US 79553459A US 2975963 A US2975963 A US 2975963A
- Authority
- US
- United States
- Prior art keywords
- rotor
- section
- male
- female
- sections
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- 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
- F04C18/12—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 of other than internal-axis type
- F04C18/14—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 of other than internal-axis type with toothed rotary pistons
- F04C18/16—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 of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
Definitions
- the present invention relates to a rotor device operating with at least two pressure stages and provided with male and female rotors, each one consisting of male and female sections corresponding to the number of stages.
- the male rotors are provided with helical convex lands and intermediate grooves and the female rotors are provided with helical concave lands and intermediate grooves.
- This rotor device is particularly intended for compression or expansion of gaseous media in several stages.
- a characteristic feature of the present invention is that the cross section of the male rotor sections show a common basic profile and that likewise the cross sections of the female rotor sections show a common basic profile. Furthermore, the lands of the female sections are, in a lower pressure stage, provided with addendum portions outside the profile of the lands of the female section in the next higher pressure stage, the grooves of the corresponding male section being provided with recesses or dedendums in their bottoms corresponding to these addendum portions in order to obtain a suction volume corresponding to the gas pressure.
- the female section of the second stage i.e. the stage with higher pressure
- the male section shows a basic profile without bottom recesses or dedendums.
- Another characteristic feature of the invention is that the addendum portions of the female section are located outside the pitch circle of the female section and that the recesses in the grooves of the male section corresponding to these addendum portions are located inside the pitch .circle of the male section.
- the invention is further characterized in that in each rotor the sections show the same pitch diameter.
- respective rotor consists of integral rotor sections so that each rotor can be journalled only at its outer ends while the sections of said rotor are mutually sealed.
- the male rotor is fourthreaded and has a wrap angle for its lands in respective stage below 360. In the low pressure stage, such wrap angle can be lying within the limits 275-325 and preferably be maximum 300". In the high pressure stage such wrap angle can be lying within the limits l50-l90 and preferably be minimum 170.
- the ratio or relation between rotor length and rotor diameter is in the low pressure stage preferably lying be tween 1.1 and 1.4 and in the high pressure stage between 0.6 and 0.8 and preferably said relation can be about 1.25 and 0.7 in respective stage.
- the land profiles of the male sections respectively the groove profiles of the female sections are formed by corresponding equal circular arcs in the two stages and that the addendum por- 2,975,963 Patented Mar. 21, 1961 ice.
- tions of the side section and the recesses of the male section show profiles likewise formed by circular arcs.
- a further characteristic feature of the invention is that the male and female rotors run with a clearance against each other, which clearance at full meshing between male land and female groove preferably is 0.08-0.1'1 mm. in both the low pressure section and the high pressure sectiori and that the rotors have a common synchronising gear for their rotor sections.
- Fig. 1 sows a vertical central longitudinal section through a compressor designed according to the invention.
- Fig. 2 shows the compressor rotors in a horizontal longitudinal section through the compressor in Fig. 1.
- Fig. 3 shows a transverse section through the rotors in the high pressure side taken on the line '3-3 in Fig. 1.
- Fig. 4 shows transverse section through the low pressure rotors taken on the line 4-4 in Fig. 1.
- Fig. 1 shows a two stage compressor.
- This compressor has a housing consisting of a 'low pressure end 10, an upper shell 12, a lower shell 14 and a high pressure end 16.
- a low-pressure inlet 18 is arranged in the low pressure end 10 and in the lower shell 14.
- an intermediate pressure outlet 20 is arranged in the upper shell 12
- an intermediate pressure inlet 22 is arranged in the lower shell 14
- a high pressure outlet 24 is arranged in the upper shell 12 and in the high pressure end 16.
- the upper and lower shells 12 and 14 encircles two working chambers each consisting of two intersecting cylindrical borings in which are arranged a male rotor 26 and a female rotor 28.
- the high pressure section 32 of the male rotor 26 comprises four helical convex lands 42 located mainly outside the pitch circle of the male rotor44 and the intermediate grooves 46.
- the high pressure section 36 of the female rotor 28 comprises six helical concave lands located mainly inside the pitch circle 50 of the female rotor and the intermediate grooves 52.
- the low pressure section of the male rotor 26 comprises likewise four helical concex lands 54 located mainly outside the pitch circle 44 of the male rotor and the intermediate grooves 56 of which each one, however, is provided with a recess 58 inside the pitch circle 44.
- the low pressure section 34 of the female rotor 28 comprises six helical, substantially concave lands 60 located mainly inside the pitch circle 50 of the female rotor and provided with addendum portions '62 outside the pitch circle 50 and the intermediate grooves 64.
- the cross sections of the male rotor 26 in the low pressure section 30 and the high pressure section 32 are identical except for the recesses 58 in the groove bottoms in the low pressure section.
- the cross sections of the female rotor 28 in the low pressure section 34 and the high pressure section 36 are identical except for the addendum portions 62 on the rotor lands in the low pressure section.
- the pitch angle is the same on both sections of the same rotor.
- the male rotor is furthermore designed in such a way that in the low pressure section the wrap angle for each land is about 300 and the ratio between section length and section diameter is about 1.25 and in the high pressure section the wrap angle for each land is about 170 and the ratio between section length and section diameter is about 0.7.
- the rotors are designed with land profiles even in the addendum portions and recesses substantially consisting of circular arcs which are equal on the male and the female rotors, except for a little difierence for providing a clearance of 0.080.11 mm. between the rotors in the low pressure section as well as in the high pressure'section, in order to prevent direct meshing between these and therefrom arising risk for seizing.
- the male rotor is direct driven from a motor shaft
- the female rotor in a manner known per se for compressors of the present type, is driven by the male rotor by means of an additional synchronizing gearing.
- the compressor operates in the following manner.
- Low pressure gas is suctioned-in through the low pressure inlet 18 and is being compressed to an intermediate pressure in the low pressure section 30, 34 and is blown out through the intermediate pressure outlet 20.
- the gas is thereupon suctioned-in through the intermediate pressure inlet 22 in the high pressure section 32, 36 and is therein further compressed to high pressure gas before it is blown out through the high pressure outlet 24.
- the size of the addendum portions 52 and the recesses 58 preferably is dimensioned in such a way that the two compressor stages operate with the same weight quantity of gas per time unit, so that no special accumulating vessel between the two pressure stages is necessary.
- a builtup with an intermediate cooler between the two pressure stages may be advantageous in other forms of constructions. However, consideration must then be taken to such cooling-down at the dimensioning of the addendum portions and the recesses.
- Rotor device operating with at least two pressure stages and provided with male and female rotors each one comprising male and female sections corresponding to the number of stages, the male sections being provided with helical convex lands and intermediate grooves and the female sections with helical concave lands and intermediate grooves, the cross sections of the male sections having a common basic profile and the cross sections of the female sections having a common basic profile, and in a lower pressure stage the lands of the female section being provided with addendum portions outside the profile of the lands of the adjacent female section, the grooves of the corresponding male section being provided with recesses in their bottoms corresponding to these addendum portions, similar sections of each pressure stage having the same land angle.
- Rotor device having two stages, female section of the second higher pressure stage having a profile with lands substantially on its pitch circle and the male section having a profile with grooves adjacent the inside of its pitch circle.
- Rotor device according to claim 1 the sections of each rotor having the same pitch diameter.
- Rotor device each rotor comprising integral rotor sections.
- Rotor device the male and female rotors run with a clearance therebetween, which clearance at full meshing between male lands and female grooves preferably is 0.08-0.11 mm. in both the high pressure and low pressure sections, and that the said rotors have a common synchronizing gear for their rotor sections.
- a rotor device according to claim 1 the wrap angle for the lands of the low pressure stage of the male rotor lying within the limits 275-325, the wrap angle for the lands of the high pressure stage of the male rotor lying within the limits ISO-, the ratio between rotor length and rotor diameter in the low pressure stage lying between 1.1 and 1.4 and in the high pressure stage between 0.6 and 0.8.
- a rotor device according to claim 1, the male sections having the same external diameter.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE193958 | 1958-02-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
US2975963A true US2975963A (en) | 1961-03-21 |
Family
ID=20259105
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US795534A Expired - Lifetime US2975963A (en) | 1958-02-27 | 1959-02-25 | Rotor device |
Country Status (8)
Country | Link |
---|---|
US (1) | US2975963A (de) |
AT (1) | AT211945B (de) |
BE (1) | BE576046A (de) |
CH (1) | CH375474A (de) |
DE (1) | DE1109704B (de) |
DK (1) | DK98144C (de) |
FR (1) | FR1224330A (de) |
GB (1) | GB851262A (de) |
Cited By (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3265293A (en) * | 1959-09-08 | 1966-08-09 | Svenska Rotor Maskiner Ab | Vacuum pump of the screw rotor type and method for operating the same |
US3265292A (en) * | 1965-01-13 | 1966-08-09 | Svenska Rotor Maskiner Ab | Screw rotor machine |
US3279682A (en) * | 1963-02-23 | 1966-10-18 | Howden James & Co Ltd | Screw air compressors |
US3283996A (en) * | 1963-09-12 | 1966-11-08 | Svenska Rotor Maskiner Ab | Screw rotor machine for elastic working fluid |
US3307777A (en) * | 1963-12-23 | 1967-03-07 | Svenska Rotor Maskiner Ab | Screw rotor machine with an elastic working fluid |
US3405604A (en) * | 1965-05-14 | 1968-10-15 | Lysholm Alf | Method of driving a screw engine power unit and a power unit to be driven according to such method |
US3577742A (en) * | 1969-06-13 | 1971-05-04 | Vilter Manufacturing Corp | Refrigeration system having a screw compressor with an auxiliary high pressure suction inlet |
US3807911A (en) * | 1971-08-02 | 1974-04-30 | Davey Compressor Co | Multiple lead screw compressor |
US4068984A (en) * | 1974-12-03 | 1978-01-17 | H & H Licensing Corporation | Multi-stage screw-compressor with different tooth profiles |
US4776779A (en) * | 1984-03-21 | 1988-10-11 | Wassan Pty Ltd. | Fluid motor or pump |
US4792294A (en) * | 1986-04-11 | 1988-12-20 | Mowli John C | Two-stage screw auger pumping apparatus |
US4944657A (en) * | 1989-03-01 | 1990-07-31 | Mowli John C | Two-stage pumping apparatus with low shear first stage |
US5267837A (en) * | 1992-09-23 | 1993-12-07 | Mowli John C | Two-stage pumping apparatus with non-meshing first stage augers |
US6257195B1 (en) | 2000-02-14 | 2001-07-10 | Arthur Vanmoor | Internal combustion engine with substantially continuous fuel feed and power output |
US6666666B1 (en) * | 2002-05-28 | 2003-12-23 | Denis Gilbert | Multi-chamber positive displacement fluid device |
US20090288648A1 (en) * | 2008-05-21 | 2009-11-26 | Gm Global Technology Operations, Inc. | Superchargers with dual integral rotors |
US20140283797A1 (en) * | 2011-09-30 | 2014-09-25 | Eaton Corporation | Supercharger assembly with two rotor sets |
US9534531B2 (en) | 2011-09-30 | 2017-01-03 | Eaton Corporation | Supercharger assembly for regeneration of throttling losses and method of control |
CN106704179A (zh) * | 2017-03-09 | 2017-05-24 | 上海格什特螺杆科技有限公司 | 一种新型直连双螺杆压缩机 |
US9751411B2 (en) | 2012-03-29 | 2017-09-05 | Eaton Corporation | Variable speed hybrid electric supercharger assembly and method of control of vehicle having same |
US9856781B2 (en) | 2011-09-30 | 2018-01-02 | Eaton Corporation | Supercharger assembly with independent superchargers and motor/generator |
US10934951B2 (en) | 2013-03-12 | 2021-03-02 | Eaton Intelligent Power Limited | Adaptive state of charge regulation and control of variable speed hybrid electric supercharger assembly for efficient vehicle operation |
US11149732B2 (en) | 2017-11-02 | 2021-10-19 | Carrier Corporation | Opposed screw compressor having non-interference system |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005005347A1 (de) * | 2005-01-31 | 2006-10-26 | Kayser, Albrecht, Dipl.-Ing. | Rotorprofile für trockene Schraubenverdichter |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2659239A (en) * | 1949-10-07 | 1953-11-17 | Jarvis C Marble | Independent synchronization |
US2714857A (en) * | 1951-09-04 | 1955-08-09 | Roper Corp Geo D | Gear pump |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1317370A (en) * | 1918-04-15 | 1919-09-30 | William S Holdaway | Pump. |
GB384355A (en) * | 1931-08-05 | 1932-12-08 | Frederick Charles Greenfield | Improvements in and relating to rotary machines for the compression and propulsion of |
DE723315C (de) * | 1940-02-20 | 1942-08-03 | Franz Burghauser Dipl Ing | Hochdruckschraubenpumpe |
DE903500C (de) * | 1949-10-07 | 1954-02-08 | Svenska Rotor Maskiner Ab | Einrichtung zur Synchronisierung von Maschinenlaeufern |
DE934605C (de) * | 1952-04-19 | 1955-10-27 | Svenska Rotor Maskiner Ab | Drehkolbenmaschine |
-
1959
- 1959-02-24 DK DK69159AA patent/DK98144C/da active
- 1959-02-24 AT AT144959A patent/AT211945B/de active
- 1959-02-24 BE BE576046A patent/BE576046A/fr unknown
- 1959-02-25 FR FR787846A patent/FR1224330A/fr not_active Expired
- 1959-02-25 CH CH7005259A patent/CH375474A/de unknown
- 1959-02-25 US US795534A patent/US2975963A/en not_active Expired - Lifetime
- 1959-02-26 DE DES61939A patent/DE1109704B/de active Pending
- 1959-02-27 GB GB6868/59A patent/GB851262A/en not_active Expired
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2659239A (en) * | 1949-10-07 | 1953-11-17 | Jarvis C Marble | Independent synchronization |
US2714857A (en) * | 1951-09-04 | 1955-08-09 | Roper Corp Geo D | Gear pump |
Cited By (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3265293A (en) * | 1959-09-08 | 1966-08-09 | Svenska Rotor Maskiner Ab | Vacuum pump of the screw rotor type and method for operating the same |
US3279682A (en) * | 1963-02-23 | 1966-10-18 | Howden James & Co Ltd | Screw air compressors |
US3283996A (en) * | 1963-09-12 | 1966-11-08 | Svenska Rotor Maskiner Ab | Screw rotor machine for elastic working fluid |
US3307777A (en) * | 1963-12-23 | 1967-03-07 | Svenska Rotor Maskiner Ab | Screw rotor machine with an elastic working fluid |
US3265292A (en) * | 1965-01-13 | 1966-08-09 | Svenska Rotor Maskiner Ab | Screw rotor machine |
US3405604A (en) * | 1965-05-14 | 1968-10-15 | Lysholm Alf | Method of driving a screw engine power unit and a power unit to be driven according to such method |
US3577742A (en) * | 1969-06-13 | 1971-05-04 | Vilter Manufacturing Corp | Refrigeration system having a screw compressor with an auxiliary high pressure suction inlet |
US3807911A (en) * | 1971-08-02 | 1974-04-30 | Davey Compressor Co | Multiple lead screw compressor |
US4068984A (en) * | 1974-12-03 | 1978-01-17 | H & H Licensing Corporation | Multi-stage screw-compressor with different tooth profiles |
US4776779A (en) * | 1984-03-21 | 1988-10-11 | Wassan Pty Ltd. | Fluid motor or pump |
US4792294A (en) * | 1986-04-11 | 1988-12-20 | Mowli John C | Two-stage screw auger pumping apparatus |
US4944657A (en) * | 1989-03-01 | 1990-07-31 | Mowli John C | Two-stage pumping apparatus with low shear first stage |
US5267837A (en) * | 1992-09-23 | 1993-12-07 | Mowli John C | Two-stage pumping apparatus with non-meshing first stage augers |
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 |
US6666666B1 (en) * | 2002-05-28 | 2003-12-23 | Denis Gilbert | Multi-chamber positive displacement fluid device |
US20090288648A1 (en) * | 2008-05-21 | 2009-11-26 | Gm Global Technology Operations, Inc. | Superchargers with dual integral rotors |
US20140283797A1 (en) * | 2011-09-30 | 2014-09-25 | Eaton Corporation | Supercharger assembly with two rotor sets |
US9534531B2 (en) | 2011-09-30 | 2017-01-03 | Eaton Corporation | Supercharger assembly for regeneration of throttling losses and method of control |
US9534532B2 (en) * | 2011-09-30 | 2017-01-03 | Eaton Corporation | Supercharger assembly with two rotor sets |
US9856781B2 (en) | 2011-09-30 | 2018-01-02 | Eaton Corporation | Supercharger assembly with independent superchargers and motor/generator |
US9751411B2 (en) | 2012-03-29 | 2017-09-05 | Eaton Corporation | Variable speed hybrid electric supercharger assembly and method of control of vehicle having same |
US10934951B2 (en) | 2013-03-12 | 2021-03-02 | Eaton Intelligent Power Limited | Adaptive state of charge regulation and control of variable speed hybrid electric supercharger assembly for efficient vehicle operation |
CN106704179A (zh) * | 2017-03-09 | 2017-05-24 | 上海格什特螺杆科技有限公司 | 一种新型直连双螺杆压缩机 |
US11149732B2 (en) | 2017-11-02 | 2021-10-19 | Carrier Corporation | Opposed screw compressor having non-interference system |
Also Published As
Publication number | Publication date |
---|---|
CH375474A (de) | 1964-02-29 |
DE1109704B (de) | 1961-06-29 |
FR1224330A (fr) | 1960-06-23 |
DK98144C (da) | 1964-03-02 |
BE576046A (fr) | 1959-06-15 |
AT211945B (de) | 1960-11-10 |
GB851262A (en) | 1960-10-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US2975963A (en) | Rotor device | |
US3467300A (en) | Two-stage compressor | |
US2481527A (en) | Rotary multiple helical rotor machine | |
EP0301273B1 (de) | Flüssigkeitsverdichter | |
US3314597A (en) | Screw compressor | |
US3011694A (en) | Encapsuling device for expanders, compressors or the like | |
US4157234A (en) | Scroll-type two stage positive fluid displacement apparatus | |
US3910731A (en) | Screw rotor machine with multiple working spaces interconnected via communication channel in common end plate | |
US2111568A (en) | Rotary compressor | |
US2804260A (en) | Engines of screw rotor type | |
US4382754A (en) | Scroll-type, positive fluid displacement apparatus with diverse clearances between scroll elements | |
US3184155A (en) | Motor compressor unit | |
US3414189A (en) | Screw rotor machines and profiles | |
US4076468A (en) | Multi-stage screw compressor interconnected via communication channel in common end plate | |
US3632239A (en) | Rotatable worm fluid compression-expansion machine | |
WO1992015774A1 (en) | Thermodynamic systems including gear type machines for compression or expansion of gases and vapors | |
CA2885727C (en) | Apparatus and method for enhancing compressor efficiency | |
US2705922A (en) | Fluid pump or motor of the rotary screw type | |
US5174737A (en) | Fluid compressor with spiral blade | |
US3182900A (en) | Twin rotor compressor with mating external teeth | |
US4417863A (en) | Scroll member assembly of scroll-type fluid machine | |
US3773444A (en) | Screw rotor machine and rotors therefor | |
US3138320A (en) | Fluid seal for compressor | |
US3922117A (en) | Two-stage roots type compressor | |
GB2111126A (en) | Rotary positive-displacement fluid-machines |