EP0242044B1 - Gaskompressoren - Google Patents

Gaskompressoren Download PDF

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Publication number
EP0242044B1
EP0242044B1 EP87302032A EP87302032A EP0242044B1 EP 0242044 B1 EP0242044 B1 EP 0242044B1 EP 87302032 A EP87302032 A EP 87302032A EP 87302032 A EP87302032 A EP 87302032A EP 0242044 B1 EP0242044 B1 EP 0242044B1
Authority
EP
European Patent Office
Prior art keywords
passage
crankcase
lubricant
sump
piston
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
EP87302032A
Other languages
English (en)
French (fr)
Other versions
EP0242044A3 (en
EP0242044A2 (de
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, according to the preamble of claim 1.
  • a common form of gas compressor relies upon one or more reciprocating pistons in cylinders.
  • Such gas compressors are used to charge reservoirs of compressed air braking systems of heavy road vehicles.
  • the bearings of such a compressor are usually lubricated by oil under pressure from the lubrication system of a vehicle engine upon which it is drivingly mounted.
  • 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 brake system and is prefereably 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 thus 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 to reciprocate the piston in the cylinder for alternatively effecting induction and compression strokes said crankshaft rotating in a bearing supplied with lubrication by a source of lubricant and said crankcase being provided with a sump into which lubricant can drain from said bearing a sump outflow passage for lubricant in the sump and a breather passage having valve means which restricts said breather passage creating crankcase pressure during induction strokes to scavenge lubricant therefrom via said outflow passage characterised in that said outflow passage is a free passage and the inner end thereof is below a predetermined level of lubricant in the sump and said valve means (19, 21; 23) is timed by cooperation of an outer surface (20) of a crank web (21) with the inner end of the breather passage (19) to restrict said breather passage during predetermined portions of said induction strokes
  • 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 pinion (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 predetermined portions of 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 the breathing of the crankcase over a predetermined portion of the compressor induction stroke during the crankshaft 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 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 through passage 19 so that the further downward movement of the piston is now 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 sizes of the passage 18 and the larger passage 19 are selected, along with the range of angular position 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.
  • pressure elevations in the crankcase are minimised. This is advantageous as it is undesirable to create more than minimal cyclic pressure elevations in the crankcase. Such elevations may not only reduce the efficiency of the compressor but as discussed earlier they can tend to drive lubricant upwards past the piston into the compression chamber of the compressor and result in oil carry-over in the compressor output.
  • crankcase pressure elevations to drive out surplus oil from pressure fed bearings.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (2)

  1. Gaskompressor, umfassend ein Gebilde (1) aus Kurbelgehäuse und Zylinder, welches eine drehbare Kurbelwelle (6) hat mit einem Kurbelzapfen, der mit einem Kolben (5) verbunden ist zum Hin- und Herbewegen des Kolbens in dem Zylinder zum abwechselnden Hervorrufen von Einlaß- und Kompressionshüben, wobei die Kurbelwelle (6) sich in einem Lager (9,10) dreht, welchem Schmiermittel von einer Schmiermittelquelle zugeführt wird, das Kurbelgehäuse mit einem Sumpf, in welchen Schmiermittel von dem Lager abfließen kann, einem Sumpfauslaßdurchgang (18) für Schmiermittel in dem Sumpf, und einem Entlüftungsdurchgang (19) versehen ist, der eine Ventileinrichtung hat, welche den Entlüftungsdurchgang verengt bzw. versperrt, wodurch in dem Kurbelgehäuse Druck während der Einlaßhübe erzeugt wird, um Schmiermittel aus dem Kurbelgehäuse über den Auslaßdurchgang auszuspülen,
    dadurch gekennzeichnet, daß der Auslaßdurchgang (18) ein freier Durchgang ist und sein Innenende sich unterhalb einer vorbestimmten Schmiermittelhöhe in dem Sumpf befindet, und die Ventileinrichtung (19,21;23) zeitgesteuert ist durch Zusammenarbeiten einer Außenfläche (20) eines Kurbelsteges (21) mit dem Innenende des Entlüftungsdurchganges (19), um den Entlüftungsdurchgang während vorbestimmter Abschnitte der Einlaßhübe zu verengen bzw. zu versperren, um ausreichende Erhöhung des Drucks im Kurbelgehäuse zu erzeugen, um Schmiermittel über den Auslaßdurchgang auszuspülen.
  2. Gaskompressor nach Anspruch 1, dadurch gekennzeichnet, daß der Sumpfauslaßdurchgang (18) von der vorbestimmten Höhe nach oben gerichtet ist.
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 EP0242044A2 (de) 1987-10-21
EP0242044A3 EP0242044A3 (en) 1988-02-10
EP0242044B1 true 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)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Family Cites Families (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
US4527520A (en) * 1983-01-19 1985-07-09 Orbital Engine Company Proprietary Limited Lubrication of an ancillary pump fitted to an engine
AT380541B (de) * 1984-04-06 1986-06-10 Hoerbiger Ventilwerke Ag Kolbenverdichter

Also Published As

Publication number Publication date
JPS62240484A (ja) 1987-10-21
GB2187801B (en) 1989-11-22
IN172401B (de) 1993-07-17
ES2026527T3 (es) 1992-05-01
GB2187801A (en) 1987-09-16
EP0242044A3 (en) 1988-02-10
DE3774158D1 (de) 1991-12-05
EP0242044A2 (de) 1987-10-21
GB8606381D0 (en) 1986-04-23

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