WO1988000294A1 - Compresseur rotatif a vis - Google Patents

Compresseur rotatif a vis Download PDF

Info

Publication number
WO1988000294A1
WO1988000294A1 PCT/SE1987/000305 SE8700305W WO8800294A1 WO 1988000294 A1 WO1988000294 A1 WO 1988000294A1 SE 8700305 W SE8700305 W SE 8700305W WO 8800294 A1 WO8800294 A1 WO 8800294A1
Authority
WO
WIPO (PCT)
Prior art keywords
low pressure
port
working space
rotor
compressor
Prior art date
Application number
PCT/SE1987/000305
Other languages
English (en)
Inventor
Lars SJÖHOLM
Sören EDSTRÖM
Original Assignee
Svenska Rotor Maskiner 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 Svenska Rotor Maskiner Ab filed Critical Svenska Rotor Maskiner Ab
Priority to DE8787904634T priority Critical patent/DE3761322D1/de
Priority to AT87904634T priority patent/ATE49265T1/de
Publication of WO1988000294A1 publication Critical patent/WO1988000294A1/fr

Links

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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber

Definitions

  • the present invention relates to a screw rotor compres ⁇ sor drivingly connected to a prime mover with variable speed, especially a frequency controlled electric motor, and having a port arrangement for variation of the volu et- ric capacity over a wider range than that corresponding to the speed ratio.
  • a screw rotor compressor is disclosed ' in US patent No. 4 435 139 and comprises a casing composed of a barrel portion and two end plate portions enclosing a working space generally in the shape of two intersecting bores and provided with low pressure and high pressure ports.
  • a pair of intermeshing male and female rotors provided with exter ⁇ nal helical lands and grooves are rotatably mounted within the working space for sealing cooperation with each other and with the walls of the working space.
  • a pair of rotor grooves are brought into communication with the low pressure port and continuously filled with low pressure gas.
  • Two such grooves brought out of communication with the low pressure port are then brought into communication with each other at the low pressure end wall, as a land of the female rotor starts to enter the male rotor groove, whereby the free volume of the male rotor groove decreases to a certain value before a male rotor land starts to enter the female rotor groove.
  • the total volume of the two grooves combined in a chevron- shaped chamber will thus be reduced by about 20 % before the full intermesh of the rotors completely takes over the sealing at the axial low pressure end of the chamber.
  • the pressure at the outer periphery will be higher than that at the bottom of the groove.
  • This pressure differential increases with the speed of the rotor which means that the pressure rise at the bottom of the groove owing to the initial volume re ⁇ duction may be negligible at high speed whereas it may be significant at low speed.
  • the actual invention comprises an extension of the low pressure port into the compression, phase area by cutting away a wedge-shaped portion of the end wall facing the bottom portion of a male rotor groove.
  • Fig. 1 is a vertical section through a screw compressor
  • Fig. 2A is a partial transverse section taken along line 2-2 in Fig. 1 and showing a normal low pressure port
  • Fig. 2B is a partial transverse section taken along line 2-2 in Fig. 1 and showing a low pressure port according to the invention
  • Fig. 3 shows the volumetric capacity as a function of the rotor speed
  • Fig. 4 shows the torque required as a function of the rotor speed
  • Fig. 5 shows the efficiency of the compressor as a func ⁇ tion of the capacity.
  • the screw compressor shown in Figs. 1 and 2 comprises a casing 10 forming a working space 12 substantially in the form of two intersecting cylindrical bores having parallel axes.
  • the casing 10 is further provided with a low pressure channel 14 and a high pressure channel 16 for the working fluid which channels communicate with the working space 12 through a low pressure port 18 and a high pressure port 20, respectively.
  • the low pressure port 18 is lo- cated in its entirety in the low pressure end wall 22 of the working space 12 and extends mainly on one side of the plane containing the axes of the bores.
  • the high pressure port 20 of the compressor shown is located partly in the high pressure end wall 24 of the working space 12 and part- ly in its barrel wall 26 and it is in its entirety located on the side of the plane through the axes of the bores opposite to the low pressure port 18.
  • a male rotor 28 and a female rotor 30 located with their axes coinciding with the axes of the bores.
  • rotors are journaled in the casing 10 in cylindrical roller bearings 32 in the low pressure end wall and in pairs of ball bearings 34 with shoulders in the high pres ⁇ sure end wall 24.
  • One rotor is further provided with a stub shaft 36 projecting outside the casing 10.
  • the male rotor 28 has five helical lands 38 and inter ⁇ vening grooves 40 having a wrap angle of about 300".
  • the female rotor 30 has six helical lands 42 and intervening grooves 44 having a wrap angle of about 250 * .
  • a plurality of oil injection channels 54 opening at the intersection line 56 between the two bores forming the working space 12. These channels 54 form communications between an oil supply chamber 58 and the working space 12. Oil is supplied to this chamber from a pressure oil source not shown through a supply opening 60 under a pressure higher than the pressure prevailing in the working space 12 at the openings of the channels 54.
  • a standard inlet port 18 is shown where the closing edge 64 thereof on the male rotor side is shaped correspondingly to the leading flank 62 of a male rotor land 38 which means that the groove 40 preceeding the land 38 is cut off simultaneously along its complete radial ex ⁇ tent.
  • FIG. 2B an inlet port 18 according to the invention is shown.
  • the closing edge on the male rotor side is com ⁇ posed of two sections, an outer one 66 extending over about 2/3 of the radial extent of the port 18 and having a shape corresponding to that of the edge 64 in Fig. 2A and inner portion 68 providing a wedge-shaped extension 70 of the port 18 along the inner periphery thereof.
  • the extension 70 acts as a by-pass port at low rotor speeds whereas at high rotor speeds the extension 70 will not influence upon the function of the compressor.
  • Fig. 3 the variation of the capacity as a function of the rotor speed is shown by a continuous line compared with the corresponding variation when using a standard port shown by a dashed line.
  • the torque for driving the rotors with a port according to the invention will be considerably less than that with a standard port.
  • Fig. 4 the variation of the torque as a function of the rotor speed is shown by a continuous line compared with the corresponding variation when using a standard port shown by a dashed line.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Compresseur à vis entraîné par une machine motrice à vitesse variable, muni d'un orifice d'entrée dont une partie sert de dérivation seulement à des vitesses réduites du rotor.
PCT/SE1987/000305 1986-07-08 1987-06-26 Compresseur rotatif a vis WO1988000294A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8787904634T DE3761322D1 (de) 1986-07-08 1987-06-26 Rotierender schraubenverdichter.
AT87904634T ATE49265T1 (de) 1986-07-08 1987-06-26 Rotierender schraubenverdichter.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8616596 1986-07-08
GB868616596A GB8616596D0 (en) 1986-07-08 1986-07-08 Screw rotor compressor

Publications (1)

Publication Number Publication Date
WO1988000294A1 true WO1988000294A1 (fr) 1988-01-14

Family

ID=10600719

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1987/000305 WO1988000294A1 (fr) 1986-07-08 1987-06-26 Compresseur rotatif a vis

Country Status (3)

Country Link
EP (1) EP0276252B1 (fr)
GB (1) GB8616596D0 (fr)
WO (1) WO1988000294A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5228301A (en) * 1992-07-27 1993-07-20 Thermo King Corporation Methods and apparatus for operating a refrigeration system
US5246357A (en) * 1992-07-27 1993-09-21 Westinghouse Electric Corp. Screw compressor with oil-gas separation means
US5857683A (en) * 1996-04-03 1999-01-12 Carl Clark Auel Living Will Creeper having lever arms providing variable mechanical advantage for inclining a back portion
WO2004010002A1 (fr) * 2002-07-22 2004-01-29 Carrier Corporation Modele d'orifice de refoulement pour compresseur a vis
US6821098B2 (en) * 2003-02-11 2004-11-23 Carrier Corporation Screw compressor having compression pockets closed for unequal durations

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2457314A (en) * 1943-08-12 1948-12-28 Jarvis C Marble Rotary screw wheel device
US2474653A (en) * 1945-04-26 1949-06-28 Jarvis C Marble Helical gear compressor or motor
US2642003A (en) * 1949-12-16 1953-06-16 Read Standard Corp Blower intake port
US3241744A (en) * 1959-09-01 1966-03-22 Svenska Rotor Maskiner Ab Rotary piston, positive displacement compressors
US3622256A (en) * 1969-10-14 1971-11-23 Alexandr Ivanovich Borisoglebs Screw-rotor machine
SE428043B (sv) * 1981-09-15 1983-05-30 Stal Refrigeration Ab Kompressor med radiellt inlopp till en skruvformig rotor
SE428312B (sv) * 1982-09-20 1983-06-20 Svenska Rotor Maskiner Ab Rotorpar for skruvrotormaskin

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IN157732B (fr) * 1981-02-06 1986-05-24 Svenska Rotor Maskiner Ab

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2457314A (en) * 1943-08-12 1948-12-28 Jarvis C Marble Rotary screw wheel device
US2474653A (en) * 1945-04-26 1949-06-28 Jarvis C Marble Helical gear compressor or motor
US2642003A (en) * 1949-12-16 1953-06-16 Read Standard Corp Blower intake port
US3241744A (en) * 1959-09-01 1966-03-22 Svenska Rotor Maskiner Ab Rotary piston, positive displacement compressors
US3622256A (en) * 1969-10-14 1971-11-23 Alexandr Ivanovich Borisoglebs Screw-rotor machine
SE428043B (sv) * 1981-09-15 1983-05-30 Stal Refrigeration Ab Kompressor med radiellt inlopp till en skruvformig rotor
SE428312B (sv) * 1982-09-20 1983-06-20 Svenska Rotor Maskiner Ab Rotorpar for skruvrotormaskin

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5228301A (en) * 1992-07-27 1993-07-20 Thermo King Corporation Methods and apparatus for operating a refrigeration system
US5246357A (en) * 1992-07-27 1993-09-21 Westinghouse Electric Corp. Screw compressor with oil-gas separation means
US5857683A (en) * 1996-04-03 1999-01-12 Carl Clark Auel Living Will Creeper having lever arms providing variable mechanical advantage for inclining a back portion
WO2004010002A1 (fr) * 2002-07-22 2004-01-29 Carrier Corporation Modele d'orifice de refoulement pour compresseur a vis
CN100335791C (zh) * 2002-07-22 2007-09-05 开利公司 螺杆式压缩机的排放端口设计
US6821098B2 (en) * 2003-02-11 2004-11-23 Carrier Corporation Screw compressor having compression pockets closed for unequal durations

Also Published As

Publication number Publication date
EP0276252B1 (fr) 1990-01-03
GB8616596D0 (en) 1986-08-13
EP0276252A1 (fr) 1988-08-03

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