EP0276252A1 - Screw rotor compressor. - Google Patents

Screw rotor compressor.

Info

Publication number
EP0276252A1
EP0276252A1 EP87904634A EP87904634A EP0276252A1 EP 0276252 A1 EP0276252 A1 EP 0276252A1 EP 87904634 A EP87904634 A EP 87904634A EP 87904634 A EP87904634 A EP 87904634A EP 0276252 A1 EP0276252 A1 EP 0276252A1
Authority
EP
European Patent Office
Prior art keywords
low pressure
port
working space
rotor
compressor
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.)
Granted
Application number
EP87904634A
Other languages
German (de)
French (fr)
Other versions
EP0276252B1 (en
Inventor
Lars Sjoholm
Soren Edstrom
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Svenska Rotor Maskiner AB
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 AT87904634T priority Critical patent/ATE49265T1/en
Publication of EP0276252A1 publication Critical patent/EP0276252A1/en
Application granted granted Critical
Publication of EP0276252B1 publication Critical patent/EP0276252B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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.Screw compressor driven by a variable speed motor, fitted with an inlet orifice, part of which serves as a bypass only at reduced rotor speeds.

Description

SCREW ROTOR COMPRESSOR
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. During the rota¬ tion of the rotors 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.
Owing to the centrifugal forces acting upon the gas en- closed in a groove when the rotors revolve, 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. In order to reduce the volumetric capacity of a compres¬ sor running at low speed beyond the reduction corresponding to the speed reduction 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. At low rotor speed there will be a considerable pressure difference over this cut away portion between the groove and the low pressure channel, simultaneously as the time before the closing thereof by the male rotor land is also considerable. This means that a certain amount of the gas in the groove may be passed back to the low pressure chan¬ nel without the consumption of any significant power for the compression thereof. At high rotor speed on the other hand the pressure difference is negligible simultaneously as the time for closing the wedge-shaped portion is reduced which means that practically no leakage back to the low pressure channel will take place under such conditions.
The invention will now be described more in detail in connection with the embodiment of a compressor shown in the annexed drawings, where
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, and
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.
In the compressor shown 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.
In the working space 12 are provided two cooperating rotors, viz. a male rotor 28 and a female rotor 30, located with their axes coinciding with the axes of the bores.
These 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* . In the barrel wall 26 of the working space 12 are pro¬ vided 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. In Fig. 2A 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.
In 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.
As already stated above in the introduction of the spe- cification 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.
In 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.
As the losses in the by-pass port are very low compared with the losses for decreasing the speed of a frequency controlled motor the torque for driving the rotors with a port according to the invention will be considerably less than that with a standard port.
In 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.
The efficiency of the compressor at low speed will con¬ sequently be considerably higher with the new port compared to a standard one, which is shown in Fig. 5 shown by a con¬ tinuous line and a dashed line, respectively.

Claims

CLAIM
Screw compressor drivingly connected to a prime mover with variable speed and comprising a casing with a working space having a barrel and a low pressure and a high pres¬ sure end wall and provided with spaced apart low pressure and high pressure ports at least partially disposed in said end walls, and a pair of intermeshing male and female ro¬ tors having external helical lands and grooves disposed in said working space, characterized in that the closing edge of the axial low pressure port on the male rotor side at the inner periphery of the port is provided with a wedge- shaped notch extending into the area of the end wall bound¬ ing the compression phase of the compressor.
EP87904634A 1986-07-08 1987-06-26 Screw rotor compressor Expired - Lifetime EP0276252B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87904634T ATE49265T1 (en) 1986-07-08 1987-06-26 ROTARY SCREW COMPRESSOR.

Applications Claiming Priority (2)

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

Publications (2)

Publication Number Publication Date
EP0276252A1 true EP0276252A1 (en) 1988-08-03
EP0276252B1 EP0276252B1 (en) 1990-01-03

Family

ID=10600719

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87904634A Expired - Lifetime EP0276252B1 (en) 1986-07-08 1987-06-26 Screw rotor compressor

Country Status (3)

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

Families Citing this family (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
US6705849B2 (en) * 2002-07-22 2004-03-16 Carrier Corporation Discharge porting design for screw compressor
US6821098B2 (en) * 2003-02-11 2004-11-23 Carrier Corporation Screw compressor having compression pockets closed for unequal durations

Family Cites Families (8)

* 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
GB966529A (en) * 1959-09-01 1964-08-12 Svenska Rotor Maskiner Ab Screw rotor compressor
US3622256A (en) * 1969-10-14 1971-11-23 Alexandr Ivanovich Borisoglebs Screw-rotor machine
IN157732B (en) * 1981-02-06 1986-05-24 Svenska Rotor Maskiner Ab
SE428043C (en) * 1981-09-15 1989-12-14 Stal Refrigeration Ab COMPRESSOR WITH RADIAL INPUT TO A SCREW ROTOR
SE428312B (en) * 1982-09-20 1983-06-20 Svenska Rotor Maskiner Ab Rotor pair for screw-rotor machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8800294A1 *

Also Published As

Publication number Publication date
WO1988000294A1 (en) 1988-01-14
GB8616596D0 (en) 1986-08-13
EP0276252B1 (en) 1990-01-03

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