EP0242044A2 - Gaskompressoren - Google Patents

Gaskompressoren Download PDF

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Publication number
EP0242044A2
EP0242044A2 EP87302032A EP87302032A EP0242044A2 EP 0242044 A2 EP0242044 A2 EP 0242044A2 EP 87302032 A EP87302032 A EP 87302032A EP 87302032 A EP87302032 A EP 87302032A EP 0242044 A2 EP0242044 A2 EP 0242044A2
Authority
EP
European Patent Office
Prior art keywords
crankcase
gas compressor
crankshaft
valve
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
EP87302032A
Other languages
English (en)
French (fr)
Other versions
EP0242044B1 (de
EP0242044A3 (en
Inventor
Jeremy James Durrant
Patrick Ronald Oliver
Nigel James Carver
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.)
Honeywell UK Ltd
Original Assignee
Bendix Ltd
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 Bendix Ltd filed Critical Bendix Ltd
Publication of EP0242044A2 publication Critical patent/EP0242044A2/de
Publication of EP0242044A3 publication Critical patent/EP0242044A3/en
Application granted granted Critical
Publication of EP0242044B1 publication Critical patent/EP0242044B1/de
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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/04—Pressure lubrication using pressure in working cylinder or crankcase to operate lubricant feeding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores

Definitions

  • This invention relates to gas compressors and relates more particularly to gas compressors which utilise a reciprocating piston in a cylinder.
  • a common form of gas compressor relies upon one or more reciprocating pistons in a cylinder.
  • Such gas compressors are used to charge reservoirs of compressed air braking systems of heavy road vehicles.
  • the bearings of such compressors are usually lubricated by oil under pressure from the vehicle engine lubrication system and one problem encountered is that accumulation of oil drained into the compressor crankcase from the bearings can cause over-lubrication of the cylinder bores and resultant oil carry-over into the system can be excessive.
  • Such oil carry-over can be detrimental to the system and is preferably to be removed or prevented.
  • One obvious way to reduce such oil carry-over is to limit the flow of oil to the compressor bearings but this can seriously impair the working life of the compressor.
  • the present invention seeks to provide an improved gas compressor wherein oil carry-over can be substantially reduced without undesirably reducing the oil flow to the bearings.
  • a gas compressor comprising a crankcase and cylinder assembly having a rotatable crankshaft with a crankpin connected to a piston for reciprocating a piston in the cylinder for alternatively effecting induction and compression strokes said crankshaft rotating in bearings whicn are supplied with lubrication under pressure from a source of lubricant and characterised by said crankcase being provided with a valve which closes during induction strokes to create pressure elevations in the crankcase to scavenge surplus lubricant therefrom via a lubricant outlet passage.
  • the valve which closes during induction strokes may comprise a check valve arranged to freely permit air flow into the crankcase during compression strokes but to close during induction strokes. Furthermore, said check valve may have a restricted flow by-pass to limit the pressure elevations which may be produced in the crankcase.
  • valve may comprise a passage which is obscured by a part of the crankshaft over a part of the induction stroke.
  • a single cylinder piston compressor shown in sectional form therein comprises a cylinder and crankcase casting 1 provided with a valve plate 2 and a cylinder head 3.
  • the casting 1 has a cylinder bore 4 within which a piston 5 is reciprocated by means of a crankshaft 6 connected to the piston via a connecting rod 7 and a gudgeon pin 8.
  • the crankshaft is rotatable in respective bearings 9 and 10 which are pressure fed from the right-hand end of the crankcase wherein an oil pressure chamber 11 is provided.
  • This chamber is pressure fed with oil from an engine to which the compressor is mounted by a suitable flange 12.
  • the inner end 13 of the crankshaft is provided with a drive pinnion (not shown) engageable with a gear train in the crankcase of the engine.
  • this air passage 19 in relation to the crankshaft rotation is chosen so that it is substantially obscured by close proximity of an outer face 20 of the crankweb counterweight 21 during induction strokes of the crankshaft and piston assembly. Since passages 18 and 19 are the only breathing passages for the crankcase, the inner . end of the passage 19 and outer face 20 of the crankweb 21 comprise a timed valve which can impede breathing of the crankcase over predetermined intervals during the rotation cycle.
  • the direction of rotation of the crankshaft is denoted by an arrow 22, the crankweb 21 being shown in dotted outline. It is seen moreover that at a suitable angular position moving away from top dead centre l after completion of a compression stroke the surface 20 of the counterweight of the crankweb is about to obscure the inner end of the passage 19. The effect of this is to immediately impede the formerly free flow of air into and out of the crankcase so that the downward movement of the piston is able to create a suitable pressure elevation which acts in a sense to drive oil above the plate 16 out into the gear housing upwards via the small passage 18. By such means, the level of drained- out oil in the crankcase of the compressor is effectively limited to a level determined by the position of the passage 18.
  • the size of the passage 18 and the larger passage 19 are selected, along with the range of angular positions of the crankshaft for which the passage 19 is closed during induction strokes, to ensure that any tendency for oil build-up in the crankcase is prevented.
  • -it is undesirable to create more than minimal cyclic pressure elevations in the crankcase because this can not only reduce the efficiency of the compressor but it may also be counter effective in that it will tend to drive lubricant upwards past the piston rings into the compression chamber of the compressor.
  • an alternative method of achieving the same result as that described above with reference to Figs. 1 and 2 would comprise the provision of a suitable check valve 23 in place of the passage 19 but it may be appreciated that careful selection of the check valve characteristics and the provision of a possible by-pass path around it is desirable to avoid high cyclic crankcase pressure elevations during operation as these are undesirable for reasons already given above.
  • crankcase may be provided with a plurality of passages such as 19 all but the lowest of which for the selected compressor attitude, being plugged-off as required.
  • the present invention relies upon the production of an acceptable crankcase pressure to drive out surplus oil.
  • this is effected by closing a valve during an induction stroke but in the case of multiple cylinders with a common crankcase volume it may be necessary to arrange the relative cyclic positions of the pistons such that there is an interval of net reducing crankcase volume and to arrange for the valve device to close during that particular interval. This will inevitably still occur during an induction stroke of at least one such cylinder. 25

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP87302032A 1986-03-14 1987-03-10 Gaskompressoren Expired - Lifetime EP0242044B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB8606381 1986-03-14
GB8606381A GB2187801B (en) 1986-03-14 1986-03-14 Gas compressors
IN193DE1987 IN172401B (de) 1986-03-14 1987-03-04

Publications (3)

Publication Number Publication Date
EP0242044A2 true EP0242044A2 (de) 1987-10-21
EP0242044A3 EP0242044A3 (en) 1988-02-10
EP0242044B1 EP0242044B1 (de) 1991-10-30

Family

ID=26290491

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87302032A Expired - Lifetime EP0242044B1 (de) 1986-03-14 1987-03-10 Gaskompressoren

Country Status (6)

Country Link
EP (1) EP0242044B1 (de)
JP (1) JPS62240484A (de)
DE (1) DE3774158D1 (de)
ES (1) ES2026527T3 (de)
GB (1) GB2187801B (de)
IN (1) IN172401B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762555A (zh) * 2017-01-04 2017-05-31 江苏亚太工业泵科技发展有限公司 往复式真空泵外置润滑油站旋转进油装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2983334A (en) * 1957-11-18 1961-05-09 William P Dalrymple 2-cycle engine
DE3401998A1 (de) * 1983-01-19 1984-07-19 Orbital Engine Co. Pty. Ltd., Balcatta Brennkraftmaschine
AT380541B (de) * 1984-04-06 1986-06-10 Hoerbiger Ventilwerke Ag Kolbenverdichter

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2983334A (en) * 1957-11-18 1961-05-09 William P Dalrymple 2-cycle engine
DE3401998A1 (de) * 1983-01-19 1984-07-19 Orbital Engine Co. Pty. Ltd., Balcatta Brennkraftmaschine
AT380541B (de) * 1984-04-06 1986-06-10 Hoerbiger Ventilwerke Ag Kolbenverdichter

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762555A (zh) * 2017-01-04 2017-05-31 江苏亚太工业泵科技发展有限公司 往复式真空泵外置润滑油站旋转进油装置
CN106762555B (zh) * 2017-01-04 2020-08-14 江苏亚太工业泵科技发展有限公司 往复式真空泵外置润滑油站旋转进油装置

Also Published As

Publication number Publication date
JPS62240484A (ja) 1987-10-21
GB2187801B (en) 1989-11-22
IN172401B (de) 1993-07-17
EP0242044B1 (de) 1991-10-30
ES2026527T3 (es) 1992-05-01
GB2187801A (en) 1987-09-16
EP0242044A3 (en) 1988-02-10
DE3774158D1 (de) 1991-12-05
GB8606381D0 (en) 1986-04-23

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