EP0373521B1 - Trockenlauf-Hochdruckstufe eines mehrstufigen Kolbenverdichters - Google Patents

Trockenlauf-Hochdruckstufe eines mehrstufigen Kolbenverdichters Download PDF

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Publication number
EP0373521B1
EP0373521B1 EP89122633A EP89122633A EP0373521B1 EP 0373521 B1 EP0373521 B1 EP 0373521B1 EP 89122633 A EP89122633 A EP 89122633A EP 89122633 A EP89122633 A EP 89122633A EP 0373521 B1 EP0373521 B1 EP 0373521B1
Authority
EP
European Patent Office
Prior art keywords
dry
sealing elements
cylinder
piston
pressure phase
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
EP89122633A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0373521A2 (de
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/de
Publication of EP0373521A3 publication Critical patent/EP0373521A3/de
Application granted granted Critical
Publication of EP0373521B1 publication Critical patent/EP0373521B1/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
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0865—Oxide ceramics
    • F05C2203/0882—Carbon, e.g. graphite
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/042—Expansivity

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.
  • a dry-running high-pressure piston compressor of this type is known, for example, from GB-A-1 487 311.
  • this known high-pressure piston compressor it is not 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, ie to permanently lubricate with oil, since graphite is used for the running surface and self-lubricating and for the actual sealing part suitable plastic for 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 the cylinder running surface, a large number of piston rings must be provided in corresponding ring grooves on the piston.
  • the piston rings seated in the ring grooves of the piston must have a certain amount of play with respect to them, and care must still be taken to ensure that the piston rings are always in contact with the cylinder running surface. This is inevitable with leakage losses. Wear and additional leakage losses resulting from wear.
  • a high-pressure compressor is also known from CH-A 430 933, the piston of which is constructed from a tappet and from a sealing part which is separate from the tappet and is arranged loosely in front of the free tappet end.
  • the sealing part consists of a central piston shaft, on which a front and rear guide ring and between these guide rings a plurality of sealing rings radially supported by spacer rings are arranged. This ring packing is clamped axially on the piston skirt.
  • 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.
  • the solution according to the invention is based on a special selection of materials for the cylinder and of self-lubricating sealing elements for dry running, but is decisive for the special design and arrangement of the sealing elements which are simply placed on at least two loose ends of the piston in the cylinder. It is essential for these elements that their material has a relatively low specific weight and that the two sealing elements lying on top of one another form a circumferential groove which forms the access to the gap between the sealing 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 tolerance to be specified is a maximum of 0.01 to 0.05 mm.
  • the material of the sealing elements initially being one is set smaller coefficient of thermal expansion than the material of the cylinder tread, and preferably in that the coefficient of thermal expansion of the sealing elements is set 20 to 25% lower than that of the cylinder tread.
  • the sealing elements are formed as a whole or in a tread-side coating made of modified plastic or a suitable ceramic, and the tread of the cylinder or the tread bushing used therein is made of silicon carbide or other suitable ceramic material.
  • suitable materials are not a problem insofar as such or similar suitable materials for pump and compressor construction, for example according to AT-A-276 956, DE-A-2 138 845, CH-PS 359 825 and DE -A-3 607 497 have been considered earlier.
  • 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 tappet contact surface. Due to the weak crowning, the labyrinth-like relaxation spaces between the elements are enlarged and, on the other hand, space is created for trace-like coking approaches of the oil which are then 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 2 having the smallest diameter in high-pressure stage I and as Ram is guided in the cylinder 1 displacement.
  • three cylindrical sealing elements 3 are loosely superimposed on the piston 2 in the cylinder 1 and 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 widened 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 formed at least in their running surfaces (ie in the form of coatings) from materials, for example on the basis of modified carbon, ceramic 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 likewise made of suitable ceramic material.
  • materials for example on the basis of modified carbon, ceramic 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 likewise made of suitable ceramic material.
  • 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. Regardless of the larger expansion of the cylinder running surface that arises during operation due to the temperature load, the previously 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, which, as can be seen from FIG. 3, result in cross-sectionally V-shaped and circumferential grooves, between which, however, there is the contact gap 7 '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 with a circumferential groove 7 at half the height, 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 crowning advantageously not covering the central region 5 '' in order to avoid punctiform or small-area load regions there, that is, as shown in Fig. 5 can be seen, the end faces 5 are flat there.
  • the sealing elements 3 between their tread guides 3 'can also run with a concave (top) or convex (bottom) Circumferential surface 3 ′′ or 3 ′′ ′′ may be provided, it also being possible to make the circumferential surface of a sealing element 3 alternately concave and convex, that is to say wave-shaped, 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP89122633A 1988-12-13 1989-12-08 Trockenlauf-Hochdruckstufe eines mehrstufigen Kolbenverdichters Expired - Lifetime EP0373521B1 (de)

Applications Claiming Priority (2)

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

Publications (3)

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

Family

ID=6368995

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89122633A Expired - Lifetime EP0373521B1 (de) 1988-12-13 1989-12-08 Trockenlauf-Hochdruckstufe eines mehrstufigen Kolbenverdichters

Country Status (3)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014059149A (ja) * 2012-09-14 2014-04-03 Mitsubishi Heavy Ind Ltd 熱交換器の解体方法

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
JP5617196B2 (ja) * 2009-07-02 2014-11-05 マックス株式会社 多段圧縮機
EP2612035A2 (en) 2010-08-30 2013-07-10 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
DE102015001366A1 (de) * 2015-02-03 2016-08-04 Linde Aktiengesellschaft Zylinderlaufflächen in Fluidarbeitsmaschinen

Family Cites Families (15)

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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
GB1067362A (en) * 1964-02-10 1967-05-03 Ici Ltd Improvements in and relating to high compression pumps and compressors
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
US3618475A (en) * 1970-06-01 1971-11-09 Cooper Ind Inc Load controlling device for compressors
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014059149A (ja) * 2012-09-14 2014-04-03 Mitsubishi Heavy Ind Ltd 熱交換器の解体方法

Also Published As

Publication number Publication date
US5007331A (en) 1991-04-16
EP0373521A2 (de) 1990-06-20
EP0373521A3 (en) 1990-06-27
DE3841833C1 (enrdf_load_stackoverflow) 1990-05-17

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