USRE32055E - Method of operation for an oil-injected screw-compressor - Google Patents

Method of operation for an oil-injected screw-compressor Download PDF

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Publication number
USRE32055E
USRE32055E US06/694,125 US69412585A USRE32055E US RE32055 E USRE32055 E US RE32055E US 69412585 A US69412585 A US 69412585A US RE32055 E USRE32055 E US RE32055E
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US
United States
Prior art keywords
rotor
pressure
oil
space
bearing
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
Application number
US06/694,125
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English (en)
Inventor
(Lars) Lauritz B. Schibbye
Rolf A. Englund
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.)
Hitachi Global Air Power US LLC
Original Assignee
Sullair Technology AB
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Publication date
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Publication of USRE32055E publication Critical patent/USRE32055E/en
Assigned to SULLAIR CORPORATION, A INDIANA CORP. reassignment SULLAIR CORPORATION, A INDIANA CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SULLAIR TECHNOLOGY AB
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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

Definitions

  • This invention relates to a method at oil-injected screw-compressors for balancing axial forces at at least one of the compressor rotors and for sealing the gaps between the rotor shafts and the rotor housing in order to prevent leakage from the compression space of the screw-compressor through these gaps.
  • the balancing pressure is transferred along the rotor shaft inward to the rotor body and thereby acts also on the ring area formed by the end surface plane of the rotor body between the shaft diameter and the core diameter of the rotor.
  • the force hereby arising on this ring area acts in a direction opposed to the desired balancing force and, thus, reduces the desired balancing considerably.
  • One object of the invention is to provide a method of axially balancing the rotor shaft, whereby the aforesaid disadvantages of conventional arrangements are eliminated, and which method especially can be applied to screw-compressors operating with high pressure differences, of the magnitude 2 MPa and higher, over the compressor.
  • a further object of the invention is to provide a method of the aforesaid kind, by which sealing against leakage from the compression space of the compressor along the shafts of the rotors is obtained.
  • a still further object of the invention is a method of the aforesaid kind to simultaneously effect lubrication and cooling of the bearings provided for the respective shaft.
  • FIG. 1 is a horizontal section through a screw-compressor provided with an arrangement according to the invention
  • FIG. 2 is a cross-sectional view of typical rotors usable with the screw-compressor of FIG. 1.
  • the rotor housing 11 of the screw-compressor 10 includes a compression space in the form of two rotor barrels forming two intersecting bores, with a low-pressure port 12 at one end 13 and a high-pressure port (not shown) at the other end 14.
  • two meshing rotors viz. one screw or male rotor 15 and one slide or female rotor 16, are mounted rotatably.
  • a radial bearing 17, preferably of roller bearing type, and an axial bearing 18, preferably of angular contact ball bearing type, are built-in for supporting the male rotor 15.
  • a balancing piston 19 is located at the rotor shaft end 20 for balancing the main part of the axial forces acting on the high-pressure end of the male rotor 15.
  • Said balancing piston 19 is located in a pressure space 21, to which oil under pressure can be supplied from the outside through an oil inlet opening 22.
  • the oil under pressure can be supplied by any suitable means, such as by an external oil pump or from the oil separator conventionally used in the discharge pipe system of an oil injected screw compressor.
  • a mechanical seal 23 is located which ensures that a constant pressure of the oil supplied is maintained.
  • connections 24 are drilled from the pressure space 21 outside the balancing piston 19 into the bearing space at the rotor shaft. The oil can continue to pass from here along gaps 25 between the rotor shaft and the rotor housing into the compression space for sealing these gaps 25, thereby eliminating leakage from the compression space.
  • the screw-compressor 10 is driven via the drive shaft 26 of the male rotor 15 which extends outward through the rotor housing 11 on the high-pressure side of said housing and is supported in a radial bearing 27 located in a bearing space 28a.
  • a mechanical shaft seal 29 of the drive shaft 26 is provided in this bearing space.
  • the bearing space 28a on the high-pressure side of the male rotor 15 is in direct connection with a bearing space 28b on the high-pressure side of the female rotor 16.
  • a radial bearing 30 is located for supporting the shaft 31 of the female rotor on the high-pressure side.
  • Oil is supplied under pressure to the bearing spaces 28a,28b through a throttling 33, which is adjusted so as to deliver a pressure of the magnitude of the arithmetic mean value of the inlet and outlet pressure of the screw-compressor.
  • This oil pressure can also be supplied by any suitable means, such as by an external oil pump or an oil separator as previously mentioned.
  • a bearing package like the one for the male rotor 15 is built-in in the form of a radial bearing 34, preferably of roller bearing type, and an axial bearing 35, preferably of angular contact ball bearing type.
  • a balancing piston 36 is attached by screws (one screw 43 indicated in the Figure)to the shaft end 37 of the female rotor. (A corresponding attachment applies to the balancing piston 19 at the shaft end of the male rotor).
  • the balancing piston 36 is located in a pressure space 38, to which oil under pressure is supplied.
  • a mechanical seal 39 is provided to ensure that a constant pressure of the oil supplied is maintained.
  • connections 40 are drilled from the pressure space 38 into the bearing space at the shaft end 37 of the slide rotor.
  • the oil can continue to pass from here along gaps 41 between the rotor shaft and rotor housing into the compression space for sealing these gaps 41 against leakage from the compression space.
  • connection 42 is drilled axially along the central line of the female rotor, so that in the bearing space 28b of the female rotor and the pressure space 38 a common pressure is obtained.
  • the pressure space 21 for the balancing piston 19 of the male rotor 15 is supplied with oil, the pressure of which corresponds to the outlet pressure of the screw-compressor reduced by the pressure drop in the oil cooler and oil filter.
  • the oil pressure in this pressure space 21, thus, is substantially higher than in the corresponding pressure space 38 on the female rotor side. This higher pressure is desirable in view of the substantially higher axial forces acting on the male rotor 15 compared with those acting on the female rotor 16, the higher axial forces resulting from the larger area on the male rotor 15 then on the female rotor 16 on which the outlet gas forces act.
  • the hole area obtained by one or more bores is calculated on the basis of available oil pressure difference and oil viscosity, so that a suitable oil amount for cooling and lubricating the bearing package is obtained.
  • This oil amount normally is of the magnitude 5 liters/min per bearing package.
  • this is to be calculated so that the oil supply therethrough slightly exceeds the oil amount calculated for the flow in the aforesaid connections.
  • an oil supply along the gaps 32a, 32b on the high-pressure side into the compression space always is obtained.
  • a more accurate dimensioning of this throttling is not required, because an oil supply in excess of the aforesaid minimum amount implies only that the pressure in the bearing spaces 28a,28b and in the pressure space 38 of the female rotor increases relatively insignificantly, because due to the higher pressure the oil flow along the gaps 32a,32b on the high-pressure side increases simultaneously.
  • a further essential and characterizing advantage of the invention is that, if the pressure according to the aforesaid increases in the bearing spaces 28a,28b, this does not effect the axial forces neither of the male rotor nor of the female rotor, because the ingoing shaft 26 is the drive shaft, and the sealing area of the mechanical seal 29 is located on the same level as the diameter of the rotor shaft extending into the compression space and, therefore, the pressure in the bearing space 28a does not yield any axial force, but the axial forces on the rotor shaft 26 substantially completely balance each other in this space 28a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
US06/694,125 1980-12-12 1985-01-22 Method of operation for an oil-injected screw-compressor Expired - Lifetime USRE32055E (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8008760 1980-12-12
SE8008760A SE424760B (sv) 1980-12-12 1980-12-12 Forfarande vid en oljeinsprutad skruvkompressor for balansering av axialkrafter hos atminstone en av kompressorns rotorer, for tetning av spalterna mellan rotorhus och rotorernas axlar, samt for kylning och smorjning ..

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US06/326,602 Reissue US4462769A (en) 1981-12-02 1981-12-02 Method at an oil-injected screw-compressor

Publications (1)

Publication Number Publication Date
USRE32055E true USRE32055E (en) 1985-12-24

Family

ID=20342456

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/694,125 Expired - Lifetime USRE32055E (en) 1980-12-12 1985-01-22 Method of operation for an oil-injected screw-compressor

Country Status (5)

Country Link
US (1) USRE32055E (sv)
JP (1) JPS57122188A (sv)
DE (1) DE3148579A1 (sv)
GB (1) GB2089432B (sv)
SE (1) SE424760B (sv)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4964790A (en) * 1989-10-10 1990-10-23 Sundstrand Corporation Automatic regulation of balancing pressure in a screw compressor
US6241490B1 (en) * 1998-03-07 2001-06-05 Pfeiffer Vacuum Gmbh Multirotor vacuum pump
US6302667B1 (en) * 1997-08-25 2001-10-16 Svenska Rotor Maskiner Ab Oil-free screw rotor apparatus
US6520758B1 (en) 2001-10-24 2003-02-18 Ingersoll-Rand Company Screw compressor assembly and method including a rotor having a thrust piston
US6688868B2 (en) * 2000-01-11 2004-02-10 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor injected with water
US6860730B2 (en) 2002-05-20 2005-03-01 Driltech Mission, Llc Methods and apparatus for unloading a screw compressor
US20080031762A1 (en) * 2006-08-01 2008-02-07 Dieter Mosemann Screw compressor for extremely high working pressure
US20090016922A1 (en) * 2006-08-01 2009-01-15 Dieter Mosemann Screw compressor
US20100031695A1 (en) * 2008-08-08 2010-02-11 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel Ltd.) Refrigerating device
US8454334B2 (en) 2011-02-10 2013-06-04 Trane International Inc. Lubricant control valve for a screw compressor

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1698802A (en) * 1924-04-07 1929-01-15 Montelius Carl Oscar Josef Device for transferring energy to or from alpha fluid
US2082412A (en) * 1932-08-04 1937-06-01 B F Sturtevant Co Rotary compressor
US2111883A (en) * 1936-04-17 1938-03-22 Burghauser Franz Pump
US3462072A (en) * 1967-05-03 1969-08-19 Svenska Rotor Maskiner Ab Screw rotor machine
US3932073A (en) * 1973-07-05 1976-01-13 Svenska Rotor Maskiner Aktiebolag Screw rotor machine with spring and fluid biased balancing pistons
US4180089A (en) * 1977-09-30 1979-12-25 Ingersoll-Rand Company Thrust piston biasing means

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1698802A (en) * 1924-04-07 1929-01-15 Montelius Carl Oscar Josef Device for transferring energy to or from alpha fluid
US2082412A (en) * 1932-08-04 1937-06-01 B F Sturtevant Co Rotary compressor
US2111883A (en) * 1936-04-17 1938-03-22 Burghauser Franz Pump
US3462072A (en) * 1967-05-03 1969-08-19 Svenska Rotor Maskiner Ab Screw rotor machine
US3932073A (en) * 1973-07-05 1976-01-13 Svenska Rotor Maskiner Aktiebolag Screw rotor machine with spring and fluid biased balancing pistons
US4180089A (en) * 1977-09-30 1979-12-25 Ingersoll-Rand Company Thrust piston biasing means

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4964790A (en) * 1989-10-10 1990-10-23 Sundstrand Corporation Automatic regulation of balancing pressure in a screw compressor
US6302667B1 (en) * 1997-08-25 2001-10-16 Svenska Rotor Maskiner Ab Oil-free screw rotor apparatus
US6241490B1 (en) * 1998-03-07 2001-06-05 Pfeiffer Vacuum Gmbh Multirotor vacuum pump
US6688868B2 (en) * 2000-01-11 2004-02-10 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor injected with water
US6520758B1 (en) 2001-10-24 2003-02-18 Ingersoll-Rand Company Screw compressor assembly and method including a rotor having a thrust piston
US6860730B2 (en) 2002-05-20 2005-03-01 Driltech Mission, Llc Methods and apparatus for unloading a screw compressor
US20080031762A1 (en) * 2006-08-01 2008-02-07 Dieter Mosemann Screw compressor for extremely high working pressure
US20090016922A1 (en) * 2006-08-01 2009-01-15 Dieter Mosemann Screw compressor
US7753665B2 (en) * 2006-08-01 2010-07-13 Grasso Gmbh Refrigeration Technology Screw compressor for working pressures above 80 bar
US8215936B2 (en) * 2006-08-01 2012-07-10 Dieter Mosemann Screw compressor
US20100031695A1 (en) * 2008-08-08 2010-02-11 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel Ltd.) Refrigerating device
US8006514B2 (en) * 2008-08-08 2011-08-30 Kobe Steel, Ltd. Refrigerating device
US8454334B2 (en) 2011-02-10 2013-06-04 Trane International Inc. Lubricant control valve for a screw compressor

Also Published As

Publication number Publication date
GB2089432A (en) 1982-06-23
JPS57122188A (en) 1982-07-29
GB2089432B (en) 1984-08-01
SE424760B (sv) 1982-08-09
SE8008760L (sv) 1982-06-13
DE3148579A1 (de) 1982-07-01

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