EP0373521A2 - Etage à haute pression et à marche à sec d'un compresseur à pistons à plusieurs étages - Google Patents

Etage à haute pression et à marche à sec d'un compresseur à pistons à plusieurs étages Download PDF

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Publication number
EP0373521A2
EP0373521A2 EP89122633A EP89122633A EP0373521A2 EP 0373521 A2 EP0373521 A2 EP 0373521A2 EP 89122633 A EP89122633 A EP 89122633A EP 89122633 A EP89122633 A EP 89122633A EP 0373521 A2 EP0373521 A2 EP 0373521A2
Authority
EP
European Patent Office
Prior art keywords
sealing elements
pressure stage
cylinder
dry
high pressure
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
EP89122633A
Other languages
German (de)
English (en)
Other versions
EP0373521B1 (fr
EP0373521A3 (en
Inventor
Peter Greiner
Hubert Pflüger
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0373521A2 publication Critical patent/EP0373521A2/fr
Publication of EP0373521A3 publication Critical patent/EP0373521A3/de
Application granted granted Critical
Publication of EP0373521B1 publication Critical patent/EP0373521B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component 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
    • F04B39/04Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045Labyrinth-sealing between piston and cylinder
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component 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
    • F04B39/0005Component 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 adaptations of pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00Non-metallic inorganic materials
    • F05C2203/08Ceramics; Oxides
    • F05C2203/0865Oxide ceramics
    • F05C2203/0882Carbon, e.g. graphite
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00Material properties
    • F05C2251/04Thermal properties
    • F05C2251/042Expansivity

Definitions

  • the invention relates to the dry-running high-pressure stage of a multi-stage piston compressor according to the preamble of the main claim.
  • High-pressure stages of multi-stage piston compressors are known, for example, from GB-A-1 487 311.
  • this known high-pressure piston compressor it is no longer necessary to maintain an oil film between the piston and the cylinder running surface of the high-pressure stage for the purpose of sealing and lubrication, i.e. to permanently lubricate with oil, since graphite is used for the running surface and for the actual sealing elements, self-lubricating and for suitable plastic in this case.
  • nothing has changed in the previously known and customary design of the piston in the high-pressure stage i.e. in order to achieve sufficient tightness between the piston and cylinder running surface, a large number of piston rings must be provided in corresponding ring grooves on the piston.
  • the invention has for its object to provide a piston seal for the dry-running high-pressure stage of a multi-stage piston compressor with the simplest design, which at low wear, the lowest possible leak rate and a long service life.
  • This solution according to the invention is also based on a special selection of materials for cylinders and self-lubricating sealing elements, but is crucially based on the special design and arrangement of the sealing elements, which are simply placed on at least two loose ends of the plunger located in the cylinder. It is essential for these elements that they have a relatively low specific weight in terms of material and that the two sealing elements lying on top of one another form a circumferential groove with otherwise dense mutual contact, the groove forming the access to the gap between the saddle elements.
  • the relatively low specific weight of the material ensures that the sealing elements do not fly upward into the cylinder head space when the working stroke is accelerated and are retained by the medium which is already under pressure and is to be compressed further.
  • the sealing elements in their peripheral surface with at least one circumferential groove, which is preferably V-shaped in cross-section and at least in the groove bottom area with continuously running contours is designed to provide as few conditions as possible for the sealing elements to break in this area.
  • the spherical end faces in the central area are expediently designed to be flat in order to avoid punctiform or small-area loading areas between the elements or between the lowermost sealing element and the plunger contact surface.
  • the labyrinthine relaxation spaces between the elements are enlarged and, on the other hand, space is created for trace-like coking approaches of the oil that are released, but are then easily released due to the pulsating movements of the sealing elements, discharged as solid trace particles and easily in the downstream filter can be intercepted.
  • the high-pressure piston compressor consists of a plurality of pistons, which are movable by the same drive 8 and provided with inflow and outflow valves (not shown), the piston having the smallest diameter in high-pressure stage I and as a tappet 2 is guided in the displacement of the high pressure cylinder 1.
  • three cylindrical sealing elements 3 are loosely superimposed in the cylinder 1 on the tappet 2, which are provided with chamfers 6 on their peripheral edge regions 4 of their superimposed surfaces 5 (see in particular FIG. 5).
  • These sealing elements 3 have, with respect to the cylinder running surface, a play ensuring their parallel guidance in the cylinder 1, which is only 0.002 to 0.005 mm. Since the sealing elements 3 are cylindrical except for the chamfers 6, the entire circumferential surfaces in this case form the tread guides 3 'of these elements.
  • the gap 9 located between the sealing elements 3 and the running surface 1 'of the cylinder 1 is thus extended to one another in the contact area 10 of the sealing elements by the chamfers 6 and there has larger cross sections.
  • the sealing elements 3 and the cylinder 1 or the cylinder liner 1 ⁇ are at least in their running surfaces (ie in the form of coatings) made of materials, for example. Based on modified carbons, ceramics and / or silicon carbide, to the extent that the sealing elements 3 in Whole or in a tread-side coating made of modified carbon or ceramic and the tread 1 'of the cylinder 1 made of silicon carbide or also made of suitable ceramic material. Such a selection of materials ensures, despite the small amount of play, with oil-free operation and optimal sealing, that the entire high-pressure stage operates properly without, as long-term trials over hundreds of hours have shown, "eating" of the elements involved.
  • the selection of such elements is made such that the sealing elements 3 have a 20 to 25 lower thermal expansion coefficient than the material of the cylinder running surface. Irrespective of the larger expansion of the cylinder running surface that arises during operation due to the temperature load, the above-described sealing effect is fully retained.
  • each sealing element is provided with bevels 6 on both end faces 5, namely on its peripheral edge regions 4, as a result of which, as can be seen from FIG 'Between two elements, that is, the contact gap 7' extends to a certain extent membrane-like in the area delimited by a circumferential groove to the outside.
  • each sealing element can additionally be provided halfway up with a circumferential groove 7, which is expediently contoured, as mentioned in the introduction.
  • the possible and possibly to be provided spherical design of the end faces is indicated in dashed lines in Fig.
  • the extremely weak convexity advantageously not covering the central region 5 ⁇ in order to avoid punctiform or small-area load regions there, that is, as in Fig. 5 can be seen, the end faces 5 are flat there. 6, the sealing elements 3 between their tread guides 3 'with a concave (top) or convex (bottom) extending Circumferential surface 3 ⁇ or 3 ′′′ may be provided, wherein it is also possible to make the circumferential surface of an element 3 alternately concave and convex, that is to say wavy, in partial regions.
  • the relevant deviations from a cylindrical surface, ie the depth of the concavity or the height of the convexity are only of the order of magnitude of approximately 0.05 mm.
  • Material of the components of the barrel set -Liner bush made of SiSiC-SH 5311 or SiSiC-SK 6314 (SIGRI) - Steel plunger, hardened - Sealing elements made of modified carbon EK 3115 or EK 3105 (Ringsdorff quality).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP89122633A 1988-12-13 1989-12-08 Etage à haute pression et à marche à sec d'un compresseur à pistons à plusieurs étages Expired - Lifetime EP0373521B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3841833 1988-12-13
DE3841833A DE3841833C1 (fr) 1988-12-13 1988-12-13

Publications (3)

Publication Number Publication Date
EP0373521A2 true EP0373521A2 (fr) 1990-06-20
EP0373521A3 EP0373521A3 (en) 1990-06-27
EP0373521B1 EP0373521B1 (fr) 1994-09-07

Family

ID=6368995

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89122633A Expired - Lifetime EP0373521B1 (fr) 1988-12-13 1989-12-08 Etage à haute pression et à marche à sec d'un compresseur à pistons à plusieurs étages

Country Status (3)

Country Link
US (1) US5007331A (fr)
EP (1) EP0373521B1 (fr)
DE (1) DE3841833C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101943152A (zh) * 2009-07-02 2011-01-12 美克司株式会社 多级压缩机及摆动活塞

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4411059A1 (de) * 1994-03-30 1995-10-05 Ringsdorff Werke Gmbh Werkstoff für Kolben für Verbrennungskraftmaschinen
US6378418B1 (en) * 1997-10-06 2002-04-30 Mobil Oil Corporation Connecting rod assembly for high pressure injection pumps
US8794941B2 (en) 2010-08-30 2014-08-05 Oscomp Systems Inc. Compressor with liquid injection cooling
US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
US9856866B2 (en) 2011-01-28 2018-01-02 Wabtec Holding Corp. Oil-free air compressor for rail vehicles
CN102434435A (zh) * 2011-12-19 2012-05-02 安庆市佰联无油压缩机有限公司 全无油润滑高压空压机
JP6012350B2 (ja) * 2012-09-14 2016-10-25 三菱重工業株式会社 熱交換器の解体方法
DE102015001366A1 (de) * 2015-02-03 2016-08-04 Linde Aktiengesellschaft Zylinderlaufflächen in Fluidarbeitsmaschinen

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH430933A (de) * 1964-02-10 1967-02-28 Ici Ltd Hochdruckpumpe oder -kompressor
US3618475A (en) * 1970-06-01 1971-11-09 Cooper Ind Inc Load controlling device for compressors

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US334037A (en) * 1886-01-12 Lewis hallock nash
US2344687A (en) * 1939-10-30 1944-03-21 Charles A Fischer Pump plunger
US2550369A (en) * 1947-07-18 1951-04-24 Dunlop Rubber Co Single-acting reciprocating engine
DE829249C (de) * 1948-12-31 1952-01-24 Georg G Frederichs Abdichtung gegen Druckfluessigkeit fuer hin und her gehende, sowie umlaufende Maschinenteile
DE1043346B (de) * 1955-06-13 1958-11-13 Fritz Tolkien Dipl Ing Einrichtung zum Abdichten der gegeneinander beweglichen Teile einer Schiebersteuerung von Kolbendampfmaschinen
CH359825A (de) * 1958-05-19 1962-01-31 Lott Carl Luftkompressor
US3315881A (en) * 1965-07-23 1967-04-25 Worthington Corp Self-lubricating system particularly adaptable for use in high pressure compressors
GB1148398A (en) * 1966-11-25 1969-04-10 Steelweld Ltd Improvements relating to fluid-pressure-operated piston and cylinder devices
AT276956B (de) * 1967-02-22 1969-12-10 Schoeller Bleckmann Stahlwerke Manschettenloser Spezialkolben für Kolbentiefpumpen, insbesondere zum Fördern von Erdöl
DE2138845A1 (de) * 1970-08-08 1972-03-23 Toyoda Automatic Loom Works Gaskompressor
GB1487311A (en) * 1974-10-08 1977-09-28 Hardie Tynes Mfg Co Compressors
DE3607497A1 (de) * 1986-03-07 1987-09-10 Sigri Gmbh Kolbenmaschine
US4873913A (en) * 1986-09-12 1989-10-17 Helix Technology Corporation Dry roughing pump having a gas film bearing

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH430933A (de) * 1964-02-10 1967-02-28 Ici Ltd Hochdruckpumpe oder -kompressor
US3618475A (en) * 1970-06-01 1971-11-09 Cooper Ind Inc Load controlling device for compressors

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101943152A (zh) * 2009-07-02 2011-01-12 美克司株式会社 多级压缩机及摆动活塞
CN104265601A (zh) * 2009-07-02 2015-01-07 美克司株式会社 多级压缩机及摆动活塞
CN101943152B (zh) * 2009-07-02 2015-01-14 美克司株式会社 多级压缩机及摆动活塞
CN104265601B (zh) * 2009-07-02 2016-08-24 美克司株式会社 摆动活塞

Also Published As

Publication number Publication date
DE3841833C1 (fr) 1990-05-17
US5007331A (en) 1991-04-16
EP0373521B1 (fr) 1994-09-07
EP0373521A3 (en) 1990-06-27

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