US3265292A - Screw rotor machine - Google Patents

Screw rotor machine Download PDF

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Publication number
US3265292A
US3265292A US518394A US51839466A US3265292A US 3265292 A US3265292 A US 3265292A US 518394 A US518394 A US 518394A US 51839466 A US51839466 A US 51839466A US 3265292 A US3265292 A US 3265292A
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United States
Prior art keywords
rotor
rotors
stud
female
coaxial
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Expired - Lifetime
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US518394A
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English (en)
Inventor
Schibbye Lauritz Benedictus
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Svenska Rotor Maskiner AB
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Svenska Rotor Maskiner AB
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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
    • F04C2/16—Rotary-piston machines or pumps 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
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2730/00—Internal-combustion engines with pistons rotating or oscillating with relation to the housing
    • F02B2730/05—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with pistons intermeshing as gear wheels; with helicoidal rotors
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/70—Disassembly methods
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a screw rotor machine for an elastic working fluid which comprises co-axial rotors journalled in a housing in parallel groups and provided with helical lands and intervening grooves having wrap angles of less than 360 C.
  • one rotor in a group cooperates with a rotor in another group within each set of axially equally located rotors of the different groups.
  • At least in one set one of said cooperating rotors is of male rotor type and the other of female rotor type which means that in a plane transverse to the rotor axes the lands and grooves of the male rotor are located at least mainly outside the pitch circle of the rotor and provided with substantially convex flanks and that the lands and grooves of the female rotor are located at least mainly inside the pitch circle of the rotor and provided with substantially concave flanks.
  • the housing has at least one working space provided with low pressure and high pressure ports and barrel and end walls which sealingly enclose the rotors provided therein.
  • the rotors When the rotors rotate they cooperate with each other and with the walls of the working space such -that there are formed Chevron-shaped chambers each of which comprises communicating portions a groove in each rotor.
  • the base ends of these chambers lie in a stationary plane transverse to the rotor axes and located atthe high pressure port while the apices lie at the intermeshes between cooperating lands and thus move relatively to the stationary transverse plane during the rotation of the rotors so that the volume of each Chevron-shaped chamber varies.
  • Machines of this type are mainly intended for use as multistage compressors but also compressors and expanders and compressors directly driven by expanders may be built in similar manner. It is also possible to provide compressors and expanders with synchronizing gears in this manner, said synchronizing gears being regarded as rotors. Even though in the following part of the specil cation only multistage compressors are described for the sake of simplicity the invention is thus not limited to such compressors.
  • the present invention has for its object to provide a screw rotor machine of the type described in which the rotors are effectively journalled in the housing causing the smallest possible deflection, the different coaxial rotors may be designed with different screw pitch angles and with opposite thread directions and in which the different coaxial rotors in a simple manner may be adjusted and locked in relation to each other.
  • the invention thus eliminates the drawbacks of the above mentioned previously suggested compress-or types.
  • FIG. 1 is a longitudinal section of a compressor along line 11 in FIG. 2,
  • FIG. 2 is a transverse section along line 2--2 in FIG. 3,
  • FIG. 2a shows a detail of FIG. 2 on a larger scale
  • FIG. 3 is a horizontal section along line 3-3 in FIG. 2 and FIG. 3a shows a detail of FIG. 3 on a larger scale.
  • the compressor shown in the drawing comprises a housing composed of a first end plate 10, a first casing 12, and intermediate plate 14, asecond casing 16 and a second end plate 18.
  • the first and second casings 12. and 16 surround a first working space 20 and a second working space 22, respectively, in the form of two intersecting bores having parallel axes and the bores in the two working spaces being coaxial.
  • the first working space is axially closed by the first end plate and the intermediate plate 14 while the second working space is axially closed by the other end plate 18 and the intermediate plate 14.
  • first working space 20 is provided with a low pressure port 24 and a high pressure port 26 while the second working space 22 is provided with a low pressure port 28 which communicates with the "high pressure port 26 of the first working space through channels 30 in the first casing 12, through openings 32 in the intermediate plate 14 and through channels 34 in the othercasing 16, and with a high pressure port 36.
  • the two high pressure ports 26, 36 are located adjacent to and on either side of the intermediate plate 14 and on the same side of the plane defined by the axes of the bores which form the working spaces 20, 22 so that the axial forces acting on the rotors partially counterbalance each other.
  • first female rotor 38 provided with six helical lands and intervening grooves of a wrap angle of about 160 said lands and grooves lying mainly inside the pitch circle of .the rotor 38 and having substantialy concave flanks
  • a first male rotor 40 provided with four helical lands and intervening grooves of a wrap angle of about 240 said lands and grooves lying mainly outside the pitch circle of the rotor 40 and having substantially convex flanks.
  • the rotors 38, 40 which constitute a first set of cooperating rotors are substantialy shaped with profiles of the type described in US.
  • Patent 2,622,787 have the same outer diameter and an axial length which is about twice as great as the outer diameter of the rotors.
  • the invention is not limited to these numbers of lands or to this profile type or to these ratios between the outer diameters and between the length and the outer diameter but the male and female rotors can with regard to their form be varied in dependence on the actual conditions for each individual machine.
  • the first female rotor 38 is provided with a first stud 42 which is journalled in a radial bearing 44 of ballbearing type provided in the first end plate 10 and a second stud 46 which extends through the intermediate plate 14 and the second working space 22 and is journalled in a combined thrust and radial bearing 48 of ball-bearing type provided in the second end plate 18 and adapted for axial zero clearance.
  • first male rotor 40 is provided with a first stud 50 which extends through the first end plate 10 and serves as the drive shaft of the compressor and is journalled in radial bearing 52 of ball-bearing type provided in the first end plate 10, and a second stud 54 which extends through the intermediate plate 14 and the second working space 22 and is journalled in a combined thrust and radial bearing 56 of ball-bearing ty-pe provided in the second end plate 18 and adapted for axial zero clearance.
  • the first working space 20 and the first rotor set comprising the first female rotor 38 and the first male rotor 40 constitute the first stage, i.e. the low pressure stage of the compressor.
  • the second or high pressure stage of the compressor comprises the second working space 22 and the second set of cooperating rotors including a second female rotor 58 and a second male rotor 60 provided in said second working space.
  • these rotors are shaped in the same manner as the first female and male rotors 38, 40 but they have greater screw pitch angles and opposite screw thread directions and the ratio between length and outer diameter amounting only to about 0.8 and a pcripheral flank clearance between the rotors 58, 60 which is about half as large as the peripheral flank clearance between the rotors 38, 40 of the first stage.
  • the second female rotor 58 is provided with a central through bore 62 which surrounds the second stud 46 of the first female rotor 38 and is provided with two internal cylindrical projections 64, 66 which are accurately machined. These projections 64, 66 cooperate with two accurately machined projections 68, 70 on the stud 46.
  • the stud projection 68 located nearest to the intermediate plate 14 has a somewhat larger diameter than the projection 64 in the bore 62 cooperating therewith so that an interference is obtained between these projections 64, 68.
  • the other projection 70 at the free end of the stud 46 has a diameter which is somewhat less than the diameter of the bore projection 64 just mentioned so that at assembly and disassembly the second female rotor 58 can be pushed on to and pulled away, respectively, from the stud 46 without these projections 64, 70 contacting each other, while the diameter of the projection 70 is somewhat larger than the diameter of the cooperating 'bore projection 66 so that an interference is obtained also between these projections 66, 70.
  • each of the projections 68, 70 of the stud 46 there is an annular groove 72 and 74, respectively.
  • the stud 46 there are provided two channels 76 and 78 each communicating at one end thereof individually with said grooves 72, and 74, respectively, and at the other end thereof opening at the free end of the stud 46 where the channels are provided with threads 80 and 82, respectively, for connection to a liquid pump not shown.
  • a further channel 84 one opening of said channel being located at the outer surface of the stud 46 between the projections 68, '70, thereof while the other opening of the channel 84 is located at the free end of the stud 46 and provided with a thread 86 so that it can be connected to a liquid pump.
  • the interference between the projections can be eliminated so that the second female rotor 58 can be rotated on the stud 46 of the first female rotor without being subjected to axial forces and their relative positions and particularly their relative angular positions may be adjusted without any risk of deforming the surfaces of the projections 64, 68 and 66, 70, respectively.
  • the second stud 46 of the first female rotor 38 is provided with a shoulder 88 adapted to determine the axial position of the second female rotor 58 and with a nut 98 adapted to press the second female rotor 58 against the shoulder 88 on the stud 46.
  • the nut is loosened a little in order not to prevent the angular adjustment of the second female rotor 58 on the stud 46.
  • the second male rotor 60 is provided with a through bore 92 having internal cylindrical projections 94, 96 in the same manner as the second female rotor 58 and this bore 92 surrounds the second stud 54 of the first male rotor 40 which likewise is provided with cylindrical projections 98, 100 having grooves 102, 184 communicating with channels 106, 108 in the stud 54, these channels being provided with threaded connecting means 110, 112 at the free end of the stud.
  • the stud 54 further contains a draining and disassembly channel 114 with a threaded connection 116 and is provided with a shoulder 118 and a nut 120 for holding the second male rotor 68 axially on the stud 54 of the first male rotor.
  • a locking pin 122 is further inserted into a bore in the stud 54 and in the second male rotor 60 which guarantees that the torque transmitting capacity between the stud and the rotor is sufiicient for the considerably greater torque which must be transmitted between the two male rotors as compared with the two female rotors.
  • a locking pin can also be provided between the stud 46 of the first female rotor 38 and the second female rotor 58 if such a measure should be necessary for guaranteeing the torque transmission therebetween.
  • the addendum of the female rotor outside its pitch circle amounts to two percent of the outer diameter and the total pressure increase is from 1 kp./cm. -9 kp./cm.
  • the power to be transmitted between the stud 54 of the first male rotor and the second male rotor 60 is about thirty times larger than the power transmitted between the second female rotor 58 and the stud 46 of the first female rotor and therefore, normally, it is sufiicient to provide a locking pin only between the male rotors of such a machine. If a locking pin is to be used between the female rotors the relative angular position of these rotors must be adjusted before the bore for the pin is drilled. The nut 12!) serves to lock the locking pin 122 and is tightened into contact with the second male rotor 60 as an angular adjustment can not take place after the insertion of the locking pin 118 in its bore.
  • liquid injecting openings 124 located adjacent to the high pressure port 36 and spaced along the line of intersection between the two bores of the second working space 22.
  • the liquid injected therethrough is supplied from a liquid chamber 126 provided in the second end plate 18 and being in communication with an oil pump 128 directly driven by the second stud 46 of the first female rotor 38.
  • the liquid chamber 126 also communicates with a second liquid chamber 134 in the first casing 12 through channels 138 in the second casing and a channel 132 in the intermediate plate 14. Liquid from the second liquid chamber 134 is injected into the first working space 28 through liquid injection openings 136 provided in the barrel wall of the first working space 20.
  • Liquid is further supplied to two annular chambers 140, 142 in the intermediate plate 14 through a channel 138 in said intermediate plate 14 communicating with the channel 132, each of said annular chambers surrounding one of the second studs 46, 54. of the first rotors 38, 48.
  • sealing means 144, 146 are further provided in the intermediate plate 14 in the intermediate plate 14 in the intermediate plate 14 in the intermediate plate 14 in the intermediate plate 14 in the intermediate plate 14 in the intermediate plate 14 there are further provided sealing means 144, 146
  • Oil is further supplied from the first liquid chamber 126 through a channel 148 to a bearing chamber 150 in the second end plate 18 enclosing the combined thrust and radial bearings 48, 56 and being drained to the low pressure port 28 of the second stage through channels 152.
  • Oil from the second liquid chamber 134 is also supplied through a channel 154 to a bearing chamber 156 in the first end plate 10 enclosing the radial bearings 44, 52 and being drained to the low pressure port 24 of the first stage through channels 158.
  • the assembly of the compressor described takes place in the following way.
  • the two first rotors 38, 40 are inserted in the compressor housing and the bearings 44, 52 are mounted in their seats in the first end plate 10.
  • the two second rotors 58 are heated to such a temperature that they can readily be pushed on to the corresponding studs 46, 54 on the first rotors 38, 40.
  • the second rotors 58, 60 are mounted on the studs 46, 54 and the second male rotor 60 is mounted in such an angular position relatively to the stud 54 that the lands of the rotor 68 at the rotor end facing the intermediate plate 14 will lie approximately in alignment with the grooves of the first male rotor 40 at the end of this rotor facing the intermediate plate 14 in order to reduce the risk of rotor oscillations and the second rotors 58, 60 are then left to cool down.
  • pressure liquid is supplied to the channels 76, 78, 106, 108 from a liquid pump while the channels 84, 114 are kept open so that the interference between the lands 64, 68; 66, 94, 98; 96, 180 is eliminated and the second rotors 58, 60 can be adjusted on the studs 46, 54. If necessary the relative angular position of the two male rotors 40, 61] is then adjusted and the two second rotors 58, 60 are. locked axially against their shoulders 88, 118 by tightening of the nuts 90, 128.
  • the thrust bearings 48, 56 which are adjusted for zero clearance are then mounted such that the desired axial clearance between the rotors and the housing is obtained whereafter pressure liquid is again supplied to the channels 76, 78 in the stud 46 of the first female rotor while the channel 84 is kept open.
  • the first rotors 38, 40 are adjusted angularly in their bearings 44, 48, 52, 56 such that flank contact is obtained between the trailing flank of each male rotor land and the leading flank of each female rotor land and the second female rotor 58 is angularly adjusted on the stud 46 of the first female rotor 38 such that a corresponding flank contact is obtained between the second rotors 58, 60 and thereafter the liquid pressure in the channels 76, 78 is relieved.
  • the invention is of course not limited to the embodiment shown but covers also machines in which the different groups of coaxial rotors are interconnected by means of synchronizing gears.
  • the clearances are preferably equal in all stages and the angular adjustment of coaxial rotors is carried out in one operation under pressure liquid supply to release the interference while the angular adjustment of the coaxial rotor grooves may be carried out in suitable manner by means of the synchronizing gears in a second operation.
  • a screw rotor machine for an elastic working fiuid comprising coaxial rotors journalled in a housing in parallel groups and provided with helical lands and intervening grooves having wrap angles of less than 360, one rotor in a group cooperating with a rotor in another group within each set of axially equally located rotors of the different groups and one of said cooperating rotors at least in one set being of male rotor type and the other of female rotor type, the housing having at least one working space provided with low pressure and high pressure ports and barrel and end walls sealingly enclosing rotors provided therein, one rotor at least in a first coaxial rotor group comprising at least one axially projecting stud, at least one further rotor having a central bore surrounding and connected with said stud by the interference between at least one pair of rotationally symmetrical surfaces located on the stud and in the bore, respectively, said interconnected rotors being provided with means for accurately determining their relative axial position, and at
  • a screw rotor machine as defined in claim 6, having annular grooves in the rotationally symmetrical surfaces of said stud and further channels having openings located such that said channels open into said grooves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
  • Rotary Pumps (AREA)
US518394A 1965-01-13 1966-01-03 Screw rotor machine Expired - Lifetime US3265292A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE373/65A SE302815B (enrdf_load_stackoverflow) 1965-01-13 1965-01-13

Publications (1)

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US3265292A true US3265292A (en) 1966-08-09

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Application Number Title Priority Date Filing Date
US518394A Expired - Lifetime US3265292A (en) 1965-01-13 1966-01-03 Screw rotor machine

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US (1) US3265292A (enrdf_load_stackoverflow)
JP (1) JPS536364B1 (enrdf_load_stackoverflow)
BE (1) BE675021A (enrdf_load_stackoverflow)
DE (1) DE1551144A1 (enrdf_load_stackoverflow)
FR (1) FR1463446A (enrdf_load_stackoverflow)
GB (1) GB1137257A (enrdf_load_stackoverflow)
SE (1) SE302815B (enrdf_load_stackoverflow)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3407996A (en) * 1966-06-22 1968-10-29 Atlas Copco Ab Screw compressor units
US3462072A (en) * 1967-05-03 1969-08-19 Svenska Rotor Maskiner Ab Screw rotor machine
US3467300A (en) * 1967-02-06 1969-09-16 Svenska Rotor Maskiner Ab Two-stage compressor
JPS5272902A (en) * 1975-12-11 1977-06-18 Maag Zahnraeder & Maschinen Ag Gear pumps with auxiliary driving means
US4068984A (en) * 1974-12-03 1978-01-17 H & H Licensing Corporation Multi-stage screw-compressor with different tooth profiles
EP0198936A1 (de) * 1985-04-24 1986-10-29 Leybold Aktiengesellschaft Mehrstufige Vakuumpumpe
FR2582741A1 (fr) * 1985-05-30 1986-12-05 Boc Group Plc Pompe mecanique a plusieurs etages comportant des conduits centraux pour empecher les fuites de gaz
US4943215A (en) * 1988-02-29 1990-07-24 Leybold Aktiengesellschaft Multistage vacuum pump with bore for fouling removal
DE102009019220A1 (de) * 2009-04-30 2010-11-11 Leistritz Ag Schraubenspindelpumpe
CN102251851A (zh) * 2011-06-15 2011-11-23 毛中义 一种涡轮转子发动机
US20130236348A1 (en) * 2010-11-16 2013-09-12 Hugo Vogelsang Rotary piston pump and casing half-shells for same
EP2921645A1 (fr) 2014-03-17 2015-09-23 Antoine Warnery Turbine avec des rotors torsadés.
CN105756925A (zh) * 2016-04-28 2016-07-13 天津市曌林机泵设备有限公司 一种单套机械密封胶液泵
US11293435B2 (en) * 2016-08-30 2022-04-05 Leybold Gmbh Vacuum pump screw rotors with symmetrical profiles on low pitch sections

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Publication number Priority date Publication date Assignee Title
CN107387169A (zh) * 2017-08-16 2017-11-24 无锡锡压压缩机有限公司 一种两级螺杆膨胀机级间加热结构
CN107461221A (zh) * 2017-08-16 2017-12-12 无锡锡压压缩机有限公司 一种大功率柴油机余热回收用两级螺杆膨胀机结构
CN114658662A (zh) * 2020-12-23 2022-06-24 复盛实业(上海)有限公司 双级转子压缩机
CA3224839A1 (en) * 2021-08-12 2023-02-16 Thomas Luc SWERTS Compressor assembly

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US2504230A (en) * 1944-08-11 1950-04-18 Frank E Smith Rotary helical compressor or engine
US2622787A (en) * 1947-07-16 1952-12-23 Jarvis C Marble Helical rotary engine
US2659239A (en) * 1949-10-07 1953-11-17 Jarvis C Marble Independent synchronization
US2683994A (en) * 1951-05-17 1954-07-20 Read Standard Corp Adjusting device
US2775204A (en) * 1953-03-23 1956-12-25 Roper Corp Geo D Dual pump drive with overrunning clutches
US2975963A (en) * 1958-02-27 1961-03-21 Svenska Rotor Maskiner Ab Rotor device
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Publication number Priority date Publication date Assignee Title
US1132747A (en) * 1910-02-18 1915-03-23 Otis Elevator Co Rotary gear-pump.
US1677980A (en) * 1925-08-05 1928-07-24 Montelius Carl Oscar Josef Rotary pump, motor, meter, or the like
US2459709A (en) * 1936-03-28 1949-01-18 Jarvis C Marble Gas turbine system embodying rotary positive displacement compressor apparatus
US2441771A (en) * 1941-05-31 1948-05-18 Jarvis C Marble Yieldable drive for rotors
US2504230A (en) * 1944-08-11 1950-04-18 Frank E Smith Rotary helical compressor or engine
US2477004A (en) * 1945-10-20 1949-07-26 Joy Mfg Co Screw type air pump
US2622787A (en) * 1947-07-16 1952-12-23 Jarvis C Marble Helical rotary engine
US2659239A (en) * 1949-10-07 1953-11-17 Jarvis C Marble Independent synchronization
US2683994A (en) * 1951-05-17 1954-07-20 Read Standard Corp Adjusting device
US2775204A (en) * 1953-03-23 1956-12-25 Roper Corp Geo D Dual pump drive with overrunning clutches
US2975963A (en) * 1958-02-27 1961-03-21 Svenska Rotor Maskiner Ab Rotor device
US3074624A (en) * 1960-03-11 1963-01-22 Svenska Rotor Maskiner Ab Rotary machine

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3407996A (en) * 1966-06-22 1968-10-29 Atlas Copco Ab Screw compressor units
US3467300A (en) * 1967-02-06 1969-09-16 Svenska Rotor Maskiner Ab Two-stage compressor
US3462072A (en) * 1967-05-03 1969-08-19 Svenska Rotor Maskiner Ab Screw rotor machine
US4068984A (en) * 1974-12-03 1978-01-17 H & H Licensing Corporation Multi-stage screw-compressor with different tooth profiles
JPS5272902A (en) * 1975-12-11 1977-06-18 Maag Zahnraeder & Maschinen Ag Gear pumps with auxiliary driving means
EP0198936A1 (de) * 1985-04-24 1986-10-29 Leybold Aktiengesellschaft Mehrstufige Vakuumpumpe
FR2582741A1 (fr) * 1985-05-30 1986-12-05 Boc Group Plc Pompe mecanique a plusieurs etages comportant des conduits centraux pour empecher les fuites de gaz
US4943215A (en) * 1988-02-29 1990-07-24 Leybold Aktiengesellschaft Multistage vacuum pump with bore for fouling removal
DE102009019220A1 (de) * 2009-04-30 2010-11-11 Leistritz Ag Schraubenspindelpumpe
DE102009019220B4 (de) * 2009-04-30 2013-04-11 Leistritz Pumpen Gmbh Schraubenspindelpumpe
US20130236348A1 (en) * 2010-11-16 2013-09-12 Hugo Vogelsang Rotary piston pump and casing half-shells for same
US9702362B2 (en) * 2010-11-16 2017-07-11 Hugo Vogelsang Maschinenbau Gmbh Rotary piston pump and casing half-shells for same
CN102251851A (zh) * 2011-06-15 2011-11-23 毛中义 一种涡轮转子发动机
CN102251851B (zh) * 2011-06-15 2012-10-10 毛中义 一种涡轮转子发动机
EP2921645A1 (fr) 2014-03-17 2015-09-23 Antoine Warnery Turbine avec des rotors torsadés.
CN105756925A (zh) * 2016-04-28 2016-07-13 天津市曌林机泵设备有限公司 一种单套机械密封胶液泵
US11293435B2 (en) * 2016-08-30 2022-04-05 Leybold Gmbh Vacuum pump screw rotors with symmetrical profiles on low pitch sections

Also Published As

Publication number Publication date
DE1551144A1 (de) 1969-09-25
JPS536364B1 (enrdf_load_stackoverflow) 1978-03-07
SE302815B (enrdf_load_stackoverflow) 1968-08-05
FR1463446A (fr) 1966-12-23
GB1137257A (en) 1968-12-18
BE675021A (enrdf_load_stackoverflow) 1966-05-03

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