EP0378967A1 - Piston compressor - Google Patents

Piston compressor Download PDF

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Publication number
EP0378967A1
EP0378967A1 EP89810937A EP89810937A EP0378967A1 EP 0378967 A1 EP0378967 A1 EP 0378967A1 EP 89810937 A EP89810937 A EP 89810937A EP 89810937 A EP89810937 A EP 89810937A EP 0378967 A1 EP0378967 A1 EP 0378967A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
compressor according
yoke
insert
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
EP89810937A
Other languages
German (de)
French (fr)
Other versions
EP0378967B1 (en
Inventor
Heinz Baumann
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.)
Atlas Copco Schweiz AG
Original Assignee
Sulzer AG
Gebrueder Sulzer AG
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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0378967A1 publication Critical patent/EP0378967A1/en
Application granted granted Critical
Publication of EP0378967B1 publication Critical patent/EP0378967B1/en
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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/147—Mounting or detaching of piston rod
    • 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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/008—Spacing or clearance between cylinder and piston
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • 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
    • F05C2203/0804—Non-oxide ceramics
    • F05C2203/0813—Carbides
    • F05C2203/0817—Carbides of silicon
    • 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
    • F05C2203/0804—Non-oxide ceramics
    • F05C2203/083—Nitrides
    • F05C2203/0843—Nitrides of silicon
    • 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
    • F05C2203/0895—Zirconium oxide
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/01—Materials digest

Definitions

  • the invention relates to a reciprocating compressor for high pressure, with at least one cylinder formed in a cylinder housing and a piston which runs dry-running therein and which is coupled to a crankshaft of a drive device via a connecting part displaceably guided in the cylinder housing in the direction of the longitudinal axis of the cylinder.
  • the invention has for its object a simple, in particular in this respect improved high-pressure reciprocating compressor of the type mentioned To create construction that ensures automatic operation of the piston compressor with relatively long maintenance intervals, especially in versions that are designed for a high pressure of up to 500 bar, for example.
  • the piston is decoupled in a simple manner, in particular without additional, complex guiding means, from any vibrations that may occur and act transversely to the longitudinal axis of the cylinder in the cylinder, and thus the formation of a dry-running split ring seal with a correspondingly small clearance between the piston and the cylinder is ensured.
  • the embodiment according to claim 4 results in a dry-running split ring seal which, within an operationally predetermined temperature range, is characterized by an essentially constant, minimal play between the piston and cylinder, and thus by a correspondingly low leakage loss which remains essentially constant during the operating period.
  • the compressor shown a small compressor, has four cylinders 1, 2, 3 and 4, in which pistons 5, 6, 7 and 8 are guided.
  • the cylinders 1 and 3 have a common horizontal axis 10 lying in the plane of the drawing, while the cylinders 2 and 4 are arranged on a common horizontal axis 11 set back from the plane of the drawing.
  • the pistons 5 and 7 are coupled via a yoke 14 connecting their piston rods 12 and 13 to a slide piece 15 which is mounted on a crank pin 16 of a vertically arranged crankshaft 17.
  • the crankshaft 17 is equipped with an engine, not shown, e.g. an electric motor.
  • the slider 15 is slidably guided between two guide tracks 18 formed in the yoke 18 transversely to the axis 10.
  • the pistons 6 and 8 are coupled via a yoke 22 connecting their piston rods 20 and 21, respectively, to a second slider, not shown, mounted on the crank pin 16, which is displaceable transversely to the axis 11 in the yoke 22, which is offset by 90 ° relative to the yoke 14 is.
  • the pistons 5, 6, 7 and 8 are guided by cylinder inserts 23, 24, 25 and 26 and each delimit a compression space 31, 32 in the cylinders 1, 2, 3 and 4 which are closed by detachably fastened cylinder covers 27, 28, 29 and 30. 33 and 34.
  • the compression space 31 of the cylinder 1 forming the first compression stage is delimited by an end plate 35 which is provided with several, for example four, pressure valves 37 each associated with a passage opening, only one of which is shown.
  • the piston 5 is provided with corresponding suction valves 41, each associated with a passage opening, through which suction valves 41 each of the suction stroke of the piston 5, a connection is established between the compression space 31 and a central space 43 which is separated from the latter by the piston 5 and which is connected to a feed line (not shown) for the natural gas to be compressed.
  • the compression spaces 32 and 33 are each delimited by an end plate 46 which is equipped with a central pressure valve 37 and a number, e.g. four, suction valves 41 is provided, of which only one is also shown.
  • a pressure valve 37 is arranged in a bore formed in the cylinder cover 30, which is connected via a connection nipple 50 to a pressure line 51 leading away from the compressor.
  • a suction valve 41 is arranged in a corresponding bore, which is connected via a nipple 52 to a flow channel 58 connected to the compression space 33.
  • the natural gas supplied to the central space 43 with a pressure of, for example, 10 mbar is sucked in through the opened suction valves 41.
  • the gas is compressed to a pressure of, for example, 5 bar and conveyed through the opened pressure valves 37 into a cylinder space 55 and fed via a flow channel 56 and an annular channel 48 to the second compression stage formed by the cylinder 2.
  • the gas sucked into the compression space 32 during the suction stroke of the piston 6 is reduced to a pressure of e.g. Compressed 20 bar and supplied with the pressure valve 37 open via a flow channel 57 to the third compression stage formed by the cylinder 3, the piston 7 of which is shown in the bottom dead center position.
  • the gas sucked into the compression space 33 during the suction stroke of the piston 7 is reduced to a pressure of e.g. Compressed 60 bar and supplied to the final pressure stage formed by the cylinder 4 via the flow channel 58 and through connecting channels formed in the nipple 52.
  • the gas sucked into the compression space 34 during the suction stroke of the piston 8 is brought to a pressure of e.g. 180 bar compressed and supplied with the pressure valve 37 open via the pressure line 51 to a gas fuel tank, not shown, which e.g. can be designed as a fuel tank of a motor vehicle.
  • the pistons 5, 6, 7 and 8 are guided to run dry in the cylinder inserts 23, 24, 25 and 26, the pistons 5, 6 and 7 each having a sealing ring 53 and a guide ring 54 made of a self-lubricating material suitable for dry running, For example, Teflon are provided, while the piston 8, with the bore of the cylinder insert 26, delimits an annular gap which is open over the entire common length.
  • the pistons 5, 6 and 7 are each rigidly connected to the associated yoke 14 or 22, while the piston 8 of the compression stage designed for the final pressure is coupled to the yoke 22 via a bracket 61 rigidly connected to the latter, which relative movements of the yoke 22nd admits transverse to the longitudinal axis 11 of the piston 8.
  • the holder 61 contains a sleeve 62 which can be fastened to the yoke 22 and a support element which is arranged such that it can rotate, and is represented by a ball 63, by means of which a support part formed on the yoke 22 with a support member formed on the piston rod 21 of the piston 8 can be inserted into the sleeve 62 Interacting head part 64 slidably transversely to the longitudinal axis 11. The head part 64 is held transversely to the longitudinal axis 11 by a collar portion 65 of the sleeve 62 surrounding the piston rod 21 with play.
  • the yoke 22 is guided so as to be displaceable in the direction of the longitudinal axis 11 via the sleeve 62 in a guide part 66 held in the cylinder block of the compressor. Via the ball 63, the yoke 22 is connected to the piston 8 under the respective operating pressure without play in the direction of the longitudinal axis 11. Due to the rotationally movably mounted ball 63, a transmission of transverse forces of the yoke 22, which is guided on the one hand by the piston 6 in the cylinder insert 24 and on the other hand by the sleeve 62 in the guide part 66 with corresponding lateral play, is prevented on the piston 8.
  • the piston 8 and the cylinder insert 26 are each made of a wear-resistant material.
  • the piston 8 is made of hard metal
  • the cylinder insert 26 is made of a correspondingly wear-resistant ceramic material, e.g. Silicon carbide or silicon nitride, is carried out, whose thermal expansion coefficient corresponds at least approximately to the thermal expansion coefficient of the material of the piston 8.
  • a correspondingly wear-resistant ceramic material e.g. Silicon carbide or silicon nitride
  • the cylinder insert 26 which can be inserted directly into a bore in the cylinder cover 30 or, as shown, can be arranged in a bush 67 which can be inserted into a corresponding bore, is fastened in the cylinder cover 30 by a retaining ring 68 which can be screwed into the latter.
  • the cylinder insert 26 arranged in the bush 67 for example held by a shrink connection, can also be made of a material, for example zirconium oxide, whose coefficient of thermal expansion is greater than that of the material of the piston 8.
  • the sleeve 67 can be used as a compensating sleeve, through which the thermal expansion of the cylinder insert 26 on the inside each compensates for a predetermined amount corresponding to the thermal expansion of the piston 8 and thus the intended play can be kept substantially constant between the piston 8 and the cylinder insert 26.
  • the function of the dry-running piston ring seals formed between the pistons 5, 6 and 7 and the associated cylinder inserts 23, 24, 25 is also caused by vibrations of the yoke 14 guided via the pistons 5 and 7 in the cylinder inserts 23 and 25 and of the yoke 14 Piston 6 and the sleeve 62 in the cylinder insert 24 or yoke 22 guided in the guide part 66 are not significantly impaired, so that no impermissible leakage losses occur.
  • a spherical support element instead of a spherical support element, another rotationally movable rolling element, for example one with cylindrical or with spherical support surfaces, can be provided in the holder.
  • another rotationally movable rolling element for example one with cylindrical or with spherical support surfaces, can be provided in the holder.
  • the one-piece sleeve 62 provided in the holder 61 shown in simplified form it is also possible to provide a two-piece sleeve which can be attached to the yoke 22 in a suitable manner or another, structurally different holding arrangement.
  • the piston 8 can be designed with a relatively soft core and a coating of hard metal or a corresponding wear-resistant material surrounding it, or it can also consist of a ceramic material. It can also be expedient to design the cylinder insert 26 from hard metal. Likewise, for the design of the piston 8 and / or the cylinder insert 26, materials other than those described, e.g. Metal compounds which have corresponding thermal expansion coefficients can be used. At least one of the running surfaces of the piston 8 and the cylinder insert 26 can also be formed by a thin homogeneous layer made of amorphous diamond-like carbon ("amorphous diamond-like carbon"). Such layers can each be produced in an inexpensive process suitable for mass production and at a relatively low treatment temperature which protects the substrate material, e.g. approx. 200 ° C, be applied to the relevant part or to both parts. With approximately the same thermal expansion coefficient of the cylinder material and the piston material, an embodiment is also possible in which such a layer is applied directly to the cylinder bore.
  • amorphous diamond-like carbon
  • the invention is not limited to compressors of the type described and illustrated above, but is also for other, single or multi-stage designs, as well as for other applications, e.g. on breathing air compressors or compressors for low-temperature technology.
  • at least one further piston / cylinder unit can also be designed with a holder designed according to the invention and / or with interacting parts consisting of wear-resistant material.

Abstract

Der Kompressor enthält mindestens ein für Hochdruck ausgelegtes Kolben/Zylinder-Aggregat mit einem in einem Zylindereinsatz (26) geführten Kolben (8), welcher über einen im Zylindergehäuse in Richtung der Längsachse (11) des Zylinders (4) verschiebbar geführten Verbindungsteil (Joch 22) mit einer Kurbelwelle (17) gekoppelt ist. Der Kolben (8) ist mit dem Verbindungsteil (22) über eine Halterung (61) gekoppelt, welche quer zur Längsachse (11) verlaufende Relativbewegungen des Verbindungsteils (22) gegenüber dem Kolben (8) zulässt. Entsprechend wird eine von Schwingungen des Antriebsteils (Joch 22) unbeeinflusste Führung des Kolbens (8) erzielt, der mit dem Zylindereinsatz (26) einen jeweils über den ganzen gemeinsamen Längenabschnitt offenen, von Schmiermittel freien Ringspalt begrenzt. Diese Ausführung gestattet die Ausbildung einer trockenlaufenden Spaltringdichtung zwischen Kolben (8) und Zylindereinsatz (26), welche auch bei Drücken von über 60 bar die Abdichtung des Kompressionsraums (34) gewährleistet. Vorzugsweise sind der Kolben (8) und der Zylindereinsatz (26) je aus einem verschleissfesten, metallischen oder keramischen Werkstoff hergestellt. Die erfindungsgemässe Ausführung ist insbesondere für Kleinkompressoren geeignet.The compressor contains at least one piston / cylinder unit designed for high pressure with a piston (8) guided in a cylinder insert (26), which piston (yoke 22) is guided in the cylinder housing in the direction of the longitudinal axis (11) of the cylinder (4) ) is coupled to a crankshaft (17). The piston (8) is coupled to the connecting part (22) by means of a holder (61) which permits relative movements of the connecting part (22) with respect to the piston (8) which run transverse to the longitudinal axis (11). Accordingly, a guidance of the piston (8) which is unaffected by vibrations of the drive part (yoke 22) is achieved, which limits with the cylinder insert (26) an annular gap which is open over the entire common length and is free of lubricant. This design allows the formation of a dry-running split ring seal between the piston (8) and cylinder insert (26), which ensures the sealing of the compression chamber (34) even at pressures of over 60 bar. The piston (8) and the cylinder insert (26) are preferably each made of a wear-resistant, metallic or ceramic material. The embodiment according to the invention is particularly suitable for small compressors.

Description

Die Erfindung betrifft einen Hubkolbenkompressor für Hoch­druck, mit mindestens einem in einem Zylindergehäuse aus­gebildeten Zylinder und einem in diesem trockenlaufend geführten Kolben, welcher über einen im Zylindergehäuse in Richtung der Längsachse des Zylinders verschiebbar geführ­ten Verbindungsteil mit einer Kurbelwelle einer Antriebs­einrichtung gekoppelt ist.The invention relates to a reciprocating compressor for high pressure, with at least one cylinder formed in a cylinder housing and a piston which runs dry-running therein and which is coupled to a crankshaft of a drive device via a connecting part displaceably guided in the cylinder housing in the direction of the longitudinal axis of the cylinder.

Bei einem ist aus der EP-Patentanmeldung 0 269 082 (P.6073) bekannten, vierstufigen Kleinkompressor der genannten Art wird Erdgas in einem die Enddruckstufe bil­denden Zylinder/Kolben-Aggregat von einem Druck von z.B. 60 bar auf einen Druck von z.B. 180 bar verdichtet. Trok­kenlaufende Kompressoren mit für Hochdruck von über 60 bar ausgelegten Zylinder/Kolben-Aggregaten sind bisher mit konstruktiv relativ aufwendigen Dichtungs- und Schmieran­ordnungen ausgeführt, welche zudem eine relativ häufige Wartung erfordern.In one known from EP patent application 0 269 082 (P.6073), four-stage small compressor of the type mentioned, natural gas is in a cylinder / piston unit forming the final pressure stage from a pressure of e.g. 60 bar to a pressure of e.g. 180 bar compressed. Dry-running compressors with cylinders / piston units designed for high pressure of more than 60 bar have hitherto been designed with relatively complex sealing and lubrication arrangements, which also require relatively frequent maintenance.

Der Erfindung liegt die Aufgabe zugrunde, einen insbeson­dere in dieser Hinsicht verbesserten Hochdruck-Hubkolben­kompressor der eingangs genannten Art in einer einfachen Bauweise zu schaffen, welche insbesondere bei Ausführun­gen, die für einen Hochdruck von z.B. bis 500 bar ausge­legt sind, einen automatischen Betrieb des Kolbenkompres­sors mit relativ langen Wartungsintervallen gewährleistet.The invention has for its object a simple, in particular in this respect improved high-pressure reciprocating compressor of the type mentioned To create construction that ensures automatic operation of the piston compressor with relatively long maintenance intervals, especially in versions that are designed for a high pressure of up to 500 bar, for example.

Diese Aufgabe wird durch die im kennzeichnenden Teil des Anspruchs 1 angegebenen Merkmale gelöst. Durch die erfin­dungsgemäss vorgesehene Halterung wird auf einfache Weise, insbesondere ohne zusätzliche, aufwendige Führungseinrich­tung, eine Entkoppelung des Kolbens von gegebenenfalls auftretenden, quer zur Längsachse des Zylinders wirksamen Schwingungen des im Zylindergehäuse gleitend geführten Verbindungsteils erzielt, so dass eine von derartigen Schwingungen unbeeinflusste Parallelführung des Kolbens im Zylinder, und damit die Ausbildung einer trockenlaufenden Spaltringdichtung mit entsprechend geringem Spiel zwischen Kolben und Zylinder gewährleistet wird.This object is achieved by the features specified in the characterizing part of claim 1. By means of the holder provided according to the invention, the piston is decoupled in a simple manner, in particular without additional, complex guiding means, from any vibrations that may occur and act transversely to the longitudinal axis of the cylinder in the cylinder, and thus the formation of a dry-running split ring seal with a correspondingly small clearance between the piston and the cylinder is ensured.

In den abhängigen Ansprüchen sind weitere Ausgestaltungen der Erfindung hervorgehoben.Further embodiments of the invention are emphasized in the dependent claims.

Die Ausführung nach Anspruch 4 ergibt eine trockenlaufende Spaltringdichtung, welche sich, innerhalb eines betriebs­mässig vorbestimmten Temperaturbereichs, durch ein im we­sentlichen konstantes, minimales Spiel zwischen Kolben und Zylinder, und damit durch einen entsprechend geringen Leckageverlust auszeichnet, der während der Betriebsdauer im wesentlichen konstant bleibt.The embodiment according to claim 4 results in a dry-running split ring seal which, within an operationally predetermined temperature range, is characterized by an essentially constant, minimal play between the piston and cylinder, and thus by a correspondingly low leakage loss which remains essentially constant during the operating period.

Weitere Einzelheiten und Merkmale ergeben sich aus der folgenden Beschreibung eines in der Zeichnung schematisch dargestellten Ausführungsbeispiels der Erfindung.Further details and features emerge from the following description of an exemplary embodiment of the invention shown schematically in the drawing.

Die einzige Figur der Zeichnung zeigt einen erfindungsge­mäss ausgeführten Hubkolbenkompressor in einem durch zwei Horizontalebenen geführten Schnitt.The only figure in the drawing shows a reciprocating compressor designed according to the invention in a section taken through two horizontal planes.

Der dargestellte Kompressor, ein Kleinkompressor weist vier Zylinder 1, 2, 3 und 4 auf, in denen Kolben 5, 6, 7 und 8 geführt sind. Die Zylinder 1 und 3 weisen eine in der Zeichnungsebene liegende, gemeinsame horizontale Achse 10 auf, während die Zylinder 2 und 4 auf einer gegenüber der Zeichnungsebene zurückversetzten gemeinsamen horizon­talen Achse 11 angeordnet sind. Die Kolben 5 und 7 sind über ein ihre Kolbenstangen 12 bzw. 13 verbindendes Joch 14 mit einem Gleitstück 15 gekoppelt, welches auf einem Kurbelzapfen 16 einer vertikal angeordneten Kurbelwelle 17 gelagert ist. Die Kurbelwelle 17 ist mit einem nicht dar­gestellten Motor, z.B. einem Elektromotor, verbunden. Das Gleitstück 15 ist zwischen zwei im Joch ausgebildeten Füh­rungsbahnen 18 quer zur Achse 10 verschiebbar geführt. Die Kolben 6 und 8 sind über ein ihre Kolbenstangen 20 bzw. 21 verbindendes Joch 22 mit einem auf dem Kurbelzapfen 16 gelagerten, nicht dargestellten zweiten Gleitstück gekop­pelt, welches in dem gegenüber dem Joch 14 um 90° versetz­ten Joch 22 quer zur Achse 11 verschiebbar geführt ist.The compressor shown, a small compressor, has four cylinders 1, 2, 3 and 4, in which pistons 5, 6, 7 and 8 are guided. The cylinders 1 and 3 have a common horizontal axis 10 lying in the plane of the drawing, while the cylinders 2 and 4 are arranged on a common horizontal axis 11 set back from the plane of the drawing. The pistons 5 and 7 are coupled via a yoke 14 connecting their piston rods 12 and 13 to a slide piece 15 which is mounted on a crank pin 16 of a vertically arranged crankshaft 17. The crankshaft 17 is equipped with an engine, not shown, e.g. an electric motor. The slider 15 is slidably guided between two guide tracks 18 formed in the yoke 18 transversely to the axis 10. The pistons 6 and 8 are coupled via a yoke 22 connecting their piston rods 20 and 21, respectively, to a second slider, not shown, mounted on the crank pin 16, which is displaceable transversely to the axis 11 in the yoke 22, which is offset by 90 ° relative to the yoke 14 is.

Die Kolben 5, 6, 7 und 8 sind Zylindereinsätzen 23, 24, 25 und 26 geführt und begrenzen in den durch lösbar be­festigte Zylinderdeckel 27, 28, 29 und 30 abgeschlossenen Zylindern 1, 2, 3 und 4 je einen Kompressionsraum 31, 32, 33 bzw. 34. Der Kompressionsraum 31 des die erste Verdich­tungsstufe bildenden Zylinders 1 ist durch eine Stirnplat­te 35 begrenzt, die mit mehreren, z.B. vier, je einer Durchtrittsöffnung zugeordneten Druckventilen 37 versehen ist, von denen nur eines dargestellt ist. Der Kolben 5 ist mit entsprechenden, je einer Durchtrittsöffnung zugeordne­ten Saugventilen 41 versehen, durch welche jeweils während des Saughubes des Kolbens 5 eine Verbindung zwischen dem Kompressionsraum 31 und einem von diesem durch den Kolben 5 getrennten zentralen Raum 43 hergestellt wird, der an eine nicht dargestellte Zuführleitung für das zu kompri­mierende Erdgas angeschlossen ist.The pistons 5, 6, 7 and 8 are guided by cylinder inserts 23, 24, 25 and 26 and each delimit a compression space 31, 32 in the cylinders 1, 2, 3 and 4 which are closed by detachably fastened cylinder covers 27, 28, 29 and 30. 33 and 34. The compression space 31 of the cylinder 1 forming the first compression stage is delimited by an end plate 35 which is provided with several, for example four, pressure valves 37 each associated with a passage opening, only one of which is shown. The piston 5 is provided with corresponding suction valves 41, each associated with a passage opening, through which suction valves 41 each of the suction stroke of the piston 5, a connection is established between the compression space 31 and a central space 43 which is separated from the latter by the piston 5 and which is connected to a feed line (not shown) for the natural gas to be compressed.

In den Zylindern 2 und 3 sind die Kompressionsräume 32 und 33 je durch eine Stirnplatte 46 begrenzt, welche mit einem zentralen Druckventil 37 und einer Anzahl, z.B. vier, Saugventilen 41 versehen ist, von denen ebenfalls jeweils nur eines dargestellt ist.In the cylinders 2 and 3, the compression spaces 32 and 33 are each delimited by an end plate 46 which is equipped with a central pressure valve 37 and a number, e.g. four, suction valves 41 is provided, of which only one is also shown.

Im Zylinder 4 der für den Enddruck ausgelegten Verdich­tungsstufe ist ein Druckventil 37 in einer im Zylinder­deckel 30 ausgebildeten Bohrung angeordnet, welche über einen Anschlussnippel 50 mit einer vom Kompressor wegfüh­renden Druckleitung 51 in Verbindung steht. Ein Saugventil 41 ist in einer entsprechenden Bohrung angeordnet, welche über einen Nippel 52 an einen mit dem Kompressionsraum 33 verbundenen Strömungskanal 58 angeschlossen ist.In the cylinder 4 of the compression stage designed for the final pressure, a pressure valve 37 is arranged in a bore formed in the cylinder cover 30, which is connected via a connection nipple 50 to a pressure line 51 leading away from the compressor. A suction valve 41 is arranged in a corresponding bore, which is connected via a nipple 52 to a flow channel 58 connected to the compression space 33.

Entsprechende Druck- und Saugventile, deren Ausbildung nicht Gegenstand der vorliegenden Erfindung ist, sind z.B. in der CH-Patentanmeldung 02 209/88-9 (P.6196) näher be­schrieben.Corresponding pressure and suction valves, the design of which is not the subject of the present invention, are e.g. in the CH patent application 02 209 / 88-9 (P.6196) described in more detail.

Während des Saughubes des in seiner oberen Totpunktlage dargestellten Kolbens 5 wird das dem zentralen Raum 43 mit einem Druck von z.B. 10 mbar zugeführte Erdgas durch die geöffneten Saugventile 41 angesaugt. Während des Druckhu­bes wird das Gas auf einen Druck von z.B. 5 bar verdichtet und durch die geöffneten Druckventile 37 in einen Zylin­derraum 55 gefördert und über einen Strömungskanal 56 und einen Ringkanal 48 der durch den Zylinder 2 gebildeten zweiten Verdichtungsstufe zugeführt.During the suction stroke of the piston 5 shown in its top dead center position, the natural gas supplied to the central space 43 with a pressure of, for example, 10 mbar is sucked in through the opened suction valves 41. During the pressure stroke, the gas is compressed to a pressure of, for example, 5 bar and conveyed through the opened pressure valves 37 into a cylinder space 55 and fed via a flow channel 56 and an annular channel 48 to the second compression stage formed by the cylinder 2.

Das beim Saughub des Kolbens 6 in den Kompressionsraum 32 angesaugte Gas wird beim folgenden Druckhub auf einen Druck von z.B. 20 bar verdichtet und bei geöffnetem Druck­ventil 37 über einen Strömungskanal 57 der durch den Zy­linder 3 gebildeten dritten Verdichtungsstufe zugeführt, deren Kolben 7 in der unteren Totpunktlage dargestellt ist. Das beim Saughub des Kolbens 7 in den Kompressions­raum 33 angesaugte Gas wird beim folgenden Druckhub auf einen Druck von z.B. 60 bar verdichtet und über den Strö­mungskanal 58 sowie durch im Nippel 52 ausgebildete Ver­bindungskanäle der durch den Zylinder 4 gebildeten End­druckstufe zugeführt.The gas sucked into the compression space 32 during the suction stroke of the piston 6 is reduced to a pressure of e.g. Compressed 20 bar and supplied with the pressure valve 37 open via a flow channel 57 to the third compression stage formed by the cylinder 3, the piston 7 of which is shown in the bottom dead center position. The gas sucked into the compression space 33 during the suction stroke of the piston 7 is reduced to a pressure of e.g. Compressed 60 bar and supplied to the final pressure stage formed by the cylinder 4 via the flow channel 58 and through connecting channels formed in the nipple 52.

Das beim Saughub des Kolbens 8 in den Kompressionsraum 34 angesaugte Gas wird beim Druckhub auf einen Druck von z.B. 180 bar verdichtet und bei geöffnetem Druckventil 37 über die Druckleitung 51 einem nicht dargestellten Gasbrenn­stoffbehälter zugeführt, der z.B. als Treibstofftank eines Kraftfahrzeuges ausgebildet sein kann.The gas sucked into the compression space 34 during the suction stroke of the piston 8 is brought to a pressure of e.g. 180 bar compressed and supplied with the pressure valve 37 open via the pressure line 51 to a gas fuel tank, not shown, which e.g. can be designed as a fuel tank of a motor vehicle.

Die Kolben 5, 6, 7 und 8 sind in den Zylindereinsätzen 23, 24, 25 und 26 trockenlaufend geführt, wobei die Kolben 5, 6 und 7 je mit einem Dichtungsring 53 und einem Führungs­ring 54 aus einem für den Trockenlauf geeigneten, selbst­schmierenden Material, z.B. Teflon, versehen sind, während der Kolben 8 mit der Bohrung des Zylindereinsatzes 26 einen jeweils über die ganze gemeinsame Länge offenen Ring­spalt begrenzt. Die Kolben 5, 6 und 7 sind je mit dem zuge­hörigen Joch 14 bzw. 22 starr verbunden, während der Kolben 8 der für den Enddruck ausgelegten Verdichtungsstufe mit dem Joch 22 über eine mit diesem starr verbundene Halte­rung 61 gekoppelt ist, welche Relativbewegungen des Joches 22 quer zur Längsachse 11 des Kolbens 8 zulässt.The pistons 5, 6, 7 and 8 are guided to run dry in the cylinder inserts 23, 24, 25 and 26, the pistons 5, 6 and 7 each having a sealing ring 53 and a guide ring 54 made of a self-lubricating material suitable for dry running, For example, Teflon are provided, while the piston 8, with the bore of the cylinder insert 26, delimits an annular gap which is open over the entire common length. The pistons 5, 6 and 7 are each rigidly connected to the associated yoke 14 or 22, while the piston 8 of the compression stage designed for the final pressure is coupled to the yoke 22 via a bracket 61 rigidly connected to the latter, which relative movements of the yoke 22nd admits transverse to the longitudinal axis 11 of the piston 8.

Die Halterung 61 enthält eine am Joch 22 befestigbare Hül­se 62 und ein in dieser rotationsbeweglich angeordnetes, darstellungsgemäss durch eine Kugel 63 gebildetes Stütz­element, über welches eine am Joch 22 ausgebildete Stütz­partie mit einem an der Kolbenstange 21 des Kolbens 8 aus­gebildeten, in die Hülse 62 einführbaren Kopfteil 64 quer zur Längsachse 11 verschiebbar zusammenwirkt. Der Kopfteil 64 ist durch eine die Kolbenstange 21 mit Spiel umgebende Kragenpartie 65 der Hülse 62 quer zur Längsachse 11 beweg­lich gehalten.The holder 61 contains a sleeve 62 which can be fastened to the yoke 22 and a support element which is arranged such that it can rotate, and is represented by a ball 63, by means of which a support part formed on the yoke 22 with a support member formed on the piston rod 21 of the piston 8 can be inserted into the sleeve 62 Interacting head part 64 slidably transversely to the longitudinal axis 11. The head part 64 is held transversely to the longitudinal axis 11 by a collar portion 65 of the sleeve 62 surrounding the piston rod 21 with play.

Das Joch 22 ist über die Hülse 62 in einem im Zylinder­block des Kompressors gehaltenen Führungsteil 66 in Rich­tung der Längsachse 11 verschiebbar geführt. Ueber die Kugel 63 ist das Joch 22 in Richtung der Längsachse 11 spielfrei mit dem unter dem jeweiligen Betriebsdruck ste­henden Kolben 8 verbunden. Durch die rotationsbeweglich gelagerte Kugel 63 wird zugleich eine Uebertragung von Querkräften des einerseits durch den Kolben 6 im Zylin­dereinsatz 24 und anderseits durch die Hülse 62 im Füh­rungsteil 66 mit entsprechendem seitlichem Spiel gleitend geführten Joches 22 auf den Kolben 8 verhindert. Es hat sich gezeigt, dass durch die Halterung 61 auch bei einer Ausführung, bei der die Differenz zwischen dem Durchmesser der Bohrung des Zylindereinsatzes 26 und dem Durchmesser des Kolbens 8 etwa 0,004 bis 0,01 mm beträgt, eine von Schwingungen des Joches 22 unbeeinflusste, sichere Paral­lelführung des Kolbens 8 gewährleistet werden kann. Diese Anordnung gestattet die Ausbildung einer trockenlaufenden Spaltringrichtung zwischen dem Kolben 8 und dem Zylinder­einsatz 26, welche auch bei der in der Enddruckstufe der dargestellten Ausführung zwischen dem Kompressionsraum 34 und dem zentralen Raum 43 auftretenden Druckdifferenz von 180 bar - oder bei noch höheren Druckdifferenzen von z.B. bis 500 bar - die erforderliche Abdichtung des Kompressionsraums 34 gewährleistet. Dabei resultiert die Dichtwirkung aus der Reibung des den engen Ringspalt durch­strömenden Gases.The yoke 22 is guided so as to be displaceable in the direction of the longitudinal axis 11 via the sleeve 62 in a guide part 66 held in the cylinder block of the compressor. Via the ball 63, the yoke 22 is connected to the piston 8 under the respective operating pressure without play in the direction of the longitudinal axis 11. Due to the rotationally movably mounted ball 63, a transmission of transverse forces of the yoke 22, which is guided on the one hand by the piston 6 in the cylinder insert 24 and on the other hand by the sleeve 62 in the guide part 66 with corresponding lateral play, is prevented on the piston 8. It has been shown that, even in an embodiment in which the difference between the diameter of the bore of the cylinder insert 26 and the diameter of the piston 8 is approximately 0.004 to 0.01 mm, the holder 61 has an oscillation of the yoke 22 that is not influenced, safe parallel guidance of the piston 8 can be ensured. This arrangement allows the formation of a dry-running split ring direction between the piston 8 and the cylinder insert 26, which also occurs in the final pressure stage of the embodiment shown between the compression space 34 and the central space 43 pressure difference of 180 bar - or at even higher pressure differences from e.g. to 500 bar - the required sealing of the Compression room 34 guaranteed. The sealing effect results from the friction of the gas flowing through the narrow annular gap.

Der Kolben 8 und der Zylindereinsatz 26 sind je aus einem verschleissfesten Material hergestellt. Bei der dargestell­ten Ausführung besteht der Kolben 8 aus Hartmetall, während der Zylindereinsatz 26 aus einem entsprechend verschleiss­festen keramischen Material, z.B. Siliciumcarbid oder Sili­ciumnitrid, ausgeführt ist, dessen Wärmeausdehnungskoeffi­zient zumindest annähernd dem Wärmeausdehnungskoeffizien­ten des Materials des Kolbens 8 entspricht. Dadurch wird bei der betriebsbedingten Erwärmung der im Trockenlauf zusammenwirkenden Teile über den ganzen betriebsmässigen Temperaturbereich -- z.B. bei Umgebungstemperaturen zwi­schen -40°C und +50°C -- das vorgesehene Spiel zwischen dem Kolben 8 und dem Zylindereinsatz 26, und damit der durch dieses Spiel bedingte Leckageverlust im wesentlichen konstant gehalten. Bei den in der vorstehend beschriebenen Ausführung bestehenden Druckverhältnissen kann auf diese Weise ein zwischen dem Kompressionsraum 34 und dem zentra­len Raum 43 sich einstellender, betriebsmässig akzeptabler Leckageverlust von z.B. weniger als 10 % konstant gehalten werden.The piston 8 and the cylinder insert 26 are each made of a wear-resistant material. In the embodiment shown, the piston 8 is made of hard metal, while the cylinder insert 26 is made of a correspondingly wear-resistant ceramic material, e.g. Silicon carbide or silicon nitride, is carried out, whose thermal expansion coefficient corresponds at least approximately to the thermal expansion coefficient of the material of the piston 8. As a result, during operation-related heating of the parts interacting in dry running over the entire operational temperature range - e.g. at ambient temperatures between -40 ° C and + 50 ° C - the intended play between the piston 8 and the cylinder insert 26, and thus the leakage loss caused by this game kept essentially constant. With the pressure conditions existing in the embodiment described above, an operationally acceptable leakage loss of, for example, between the compression space 34 and the central space 43 can be achieved in this way. less than 10% are kept constant.

Der Zylindereinsatz 26, der unmittelbar in eine Bohrung des Zylinderdeckels 30 eingesetzt oder, wie dargestellt, in einer in eine entsprechende Bohrung einsetzbaren Büchse 67 angeordnet sein kann, ist im Zylinderdeckel 30 durch einen in diesen einschraubbaren Haltering 68 befestigt. Der in der Büchse 67 angeordnete, z.B. durch eine Schrumpfverbindung gehaltene Zylindereinsatz 26 kann auch aus einem Material, z.B. Zirkonoxid, ausgeführt sein, des­sen Wärmeausdehnungskoeffizient grösser ist als derjenige des Materials des Kolbens 8. Bei geeigneter Wahl des Materials der Büchse 67, z.B. einer Ni-Fe-Legierung,ist die Büchse 67 als Ausgleichshülse verwendbar, durch welche die Wärmeausdehnung des Zylindereinsatzes 26 an der Innen­seite jeweils bis auf ein der Wärmeausdehnung des Kolbens 8 entsprechendes, vorbestimmtes Mass kompensiert und damit das vorgesehene Spiel zwischen dem Kolben 8 und dem Zylin­dereinsatz 26 im wesentlichen konstant gehalten werden kann.The cylinder insert 26, which can be inserted directly into a bore in the cylinder cover 30 or, as shown, can be arranged in a bush 67 which can be inserted into a corresponding bore, is fastened in the cylinder cover 30 by a retaining ring 68 which can be screwed into the latter. The cylinder insert 26 arranged in the bush 67, for example held by a shrink connection, can also be made of a material, for example zirconium oxide, whose coefficient of thermal expansion is greater than that of the material of the piston 8. With a suitable choice of the Material of the sleeve 67, for example a Ni-Fe alloy, the sleeve 67 can be used as a compensating sleeve, through which the thermal expansion of the cylinder insert 26 on the inside each compensates for a predetermined amount corresponding to the thermal expansion of the piston 8 and thus the intended play can be kept substantially constant between the piston 8 and the cylinder insert 26.

Bei den in Bereich der Zylinder 1, 2 und 3 je zwischen den Kompressionsräumen 31, 32 und 33 und dem zentralen Raum 43 auftretenden, relativ geringen Druckdifferenzen von 5 bis 60 bar - oder bis z.B. 80 bar - erübrigt sich die für die Enddruckstufe vorgesehene Verwendung von Bauteilen aus verschleissfestem Material. Bei diesen Druckdifferenzen wird auch die Funktion der zwischen den Kolben 5, 6 und 7 und den zugehörigen Zylindereinsätzen 23, 24, 25 gebilde­ten trockenlaufenden Kolbenringdichtungen durch Schwingun­gen des über die Kolben 5 und 7 in den Zylindereinsätzen 23 und 25 geführten Joches 14 sowie des über den Kolben 6 und die Hülse 62 im Zylindereinsatz 24 bzw. im Führungs­teil 66 geführten Joches 22 nicht nennenswert beeinträch­tigt, so dass keine unzulässigen Leckageverluste auftre­ten.In the case of the relatively small pressure differences of 5 to 60 bar occurring in the area of cylinders 1, 2 and 3 between the compression spaces 31, 32 and 33 and the central space 43 - or up to e.g. 80 bar - there is no need to use components made of wear-resistant material for the final pressure stage. At these pressure differences, the function of the dry-running piston ring seals formed between the pistons 5, 6 and 7 and the associated cylinder inserts 23, 24, 25 is also caused by vibrations of the yoke 14 guided via the pistons 5 and 7 in the cylinder inserts 23 and 25 and of the yoke 14 Piston 6 and the sleeve 62 in the cylinder insert 24 or yoke 22 guided in the guide part 66 are not significantly impaired, so that no impermissible leakage losses occur.

Es sind zahlreiche abgewandelte Ausführungsformen der Er­findung möglich. So kann in der Halterung anstelle eines kugelförmigen Stützelementes ein anderer rotationsbeweg­licher Wälzkörper, z.B. ein solcher mit zylindrischen oder mit kalottenförmigen Stützflächen, vorgesehen sein. An­stelle der in der vereinfacht dargestellten Halterung 61 vorgesehenen einteiligen Hülse 62 kann auch eine am Joch 22 in geeigneter Weise anbringbare zweiteilige Hülse oder eine andere, konstruktiv abweichende Halteanordnung vorge­sehen sein.Numerous modified embodiments of the invention are possible. Instead of a spherical support element, another rotationally movable rolling element, for example one with cylindrical or with spherical support surfaces, can be provided in the holder. Instead of the one-piece sleeve 62 provided in the holder 61 shown in simplified form, it is also possible to provide a two-piece sleeve which can be attached to the yoke 22 in a suitable manner or another, structurally different holding arrangement.

Der Kolben 8 kann mit einem relativ weichen Kern und einer diesen umgebenden Beschichtung aus Hartmetall oder einem entsprechenden verschleissfesten Material ausgeführt sein oder auch aus einem keramischen Material bestehen. Es kann auch zweckmässig sein, der Zylindereinsatz 26 aus Hart­metall auszuführen. Ebenso können für die Ausführung des Kolbens 8 und/oder des Zylindereinsatzes 26 andere als die beschriebenen Materialien, z.B. Metallverbindungen, welche entsprechende Wärmeausdehnungskoeffizienten aufweisen, verwendet werden. Mindestens eine der Laufflächen des Kol­bens 8 und des Zylindereinsatzes 26 kann ferner durch eine dünne homogene Schicht aus amorphem diamantartigem Kohlen­stoff ("amorphous diamondlike carbon") gebildet sein. Der­artige Schichten können jeweils in einem kostengünstigen, für die Massenfertigung geeigneten Verfahren und bei einer das Trägermaterial schondenden, realtiv geringen Behand­lungstemperatur, z.B. ca. 200°C, auf den betreffenden Teil bzw. auf beide Teile aufgebracht werden. Bei annähernd gleichen Wärmeausdehnungskoeffizienten des Zylinderwerk­stoffs und des Kolbenwerkstoffs ist auch eine Ausführung möglich, bei der eine derartige Schicht unmittelbar auf die Zylinderbohrung aufgebracht ist.The piston 8 can be designed with a relatively soft core and a coating of hard metal or a corresponding wear-resistant material surrounding it, or it can also consist of a ceramic material. It can also be expedient to design the cylinder insert 26 from hard metal. Likewise, for the design of the piston 8 and / or the cylinder insert 26, materials other than those described, e.g. Metal compounds which have corresponding thermal expansion coefficients can be used. At least one of the running surfaces of the piston 8 and the cylinder insert 26 can also be formed by a thin homogeneous layer made of amorphous diamond-like carbon ("amorphous diamond-like carbon"). Such layers can each be produced in an inexpensive process suitable for mass production and at a relatively low treatment temperature which protects the substrate material, e.g. approx. 200 ° C, be applied to the relevant part or to both parts. With approximately the same thermal expansion coefficient of the cylinder material and the piston material, an embodiment is also possible in which such a layer is applied directly to the cylinder bore.

Die Erfindung ist nicht auf Kompressoren der vorstehend beschriebenen und dargestellten Art beschränkt, sondern ist auch für andere, ein- oder mehrstufige Ausführungen, sowie für andere Anwendung, z.B. an Atemluftkompressoren oder Kompressoren für die Tieftemperaturtechnik, geeignet. Bei mehrstufigen Kompressoren kann auch mindestens ein weiteres Kolben/Zylinder-Aggregat mit einem erfindungsge­mäss ausgebildeten Halterung und/oder mit aus verschleiss­festem Werkstoff bestehenden zusammenwirkenden Teilen aus­geführt sein.The invention is not limited to compressors of the type described and illustrated above, but is also for other, single or multi-stage designs, as well as for other applications, e.g. on breathing air compressors or compressors for low-temperature technology. In the case of multi-stage compressors, at least one further piston / cylinder unit can also be designed with a holder designed according to the invention and / or with interacting parts consisting of wear-resistant material.

Claims (11)

1. Hubkolbenkompressor für Hochdruck, mit mindestens einem in einem Zylindergehäuse ausgebildeten Zylinder (4) und einem in diesem trockenlaufend geführten Kolben (8), welcher über einem im Zylindergehäuse in Richtung der Längsachse (11) des Zylinders (4) verschiebbar geführ­ten Verbindungsteil (Joch 22) mit einer Kurbelwelle (17) einer Antriebseinrichtung gekoppelt ist, dadurch gekennzeichnet, dass der Kolben (8) mit dem Verbindungsteil (22) über eine Halterung (61) ge­koppelt ist, welche mindestens ein relativ zum Kolben (8) und zum Verbindungsteil (Joch 22) quer zur Längs­achse (11) des Zylinders (4) bewegliches Stützelement enthält, und dass der Zylinder (4) mit dem Kolben (8) einen jeweils über den ganzen gemeinsamen Längenab­schnitt offenen, von Dichtungsmitteln und von Schmier­mittel freien, engen Ringspalt begrenzt, der eine vor­bestimmte Leckströmung des verdichteten Mediums zulässt.1. Reciprocating compressor for high pressure, with at least one cylinder (4) formed in a cylinder housing and a piston (8) guided in this in a dry-running manner, which piston (yoke) is displaceably guided in the cylinder housing in the direction of the longitudinal axis (11) of the cylinder (4) 22) is coupled to a crankshaft (17) of a drive device, characterized in that the piston (8) is coupled to the connecting part (22) via a holder (61) which has at least one relative to the piston (8) and the connecting part ( Yoke 22) contains movable support element transverse to the longitudinal axis (11) of the cylinder (4), and that the cylinder (4) with the piston (8) delimits a narrow annular gap which is open over the entire common length section and is free of sealants and lubricants , which allows a predetermined leakage flow of the compressed medium. 2. Kompressor nach Anspruch 1, dadurch gekennzeichnet, dass das Stützelement mit dem Kolben (8) und mit dem Verbindungsteil (Joch 22) je über eine konvexe Stütz­fläche zusammenwirkt.2. Compressor according to claim 1, characterized in that the support element interacts with the piston (8) and with the connecting part (yoke 22) via a convex support surface. 3. Kompressor nach Anspruch 1 oder 2, dadurch gekennzeich­net, dass das Stützelement durch einen zwischen den Kolben (8) und den Verbindungsteil (Joch 22) einsetz­baren Wälzkörper, z.B. eine Kugel (63), gebildet ist, welcher in der Halterung (61) rotationsbeweglich ge­lagert ist.3. Compressor according to claim 1 or 2, characterized in that the supporting element is formed by a rolling element, for example a ball (63), which can be inserted between the piston (8) and the connecting part (yoke 22) and which is in the holder (61). is rotatably mounted. 4. Kompressor nach einem der vorangehenden Ansprüche, da­durch gekennzeichnet, dass der Kolben (8) und der Zylinder (4) je mit einer aus einem verschleissfesten Material gebildeten Lauffläche ausgeführt sind, und dass zumindest der die Lauffläche enthaltende Teil des Zylinders (4) aus einem Werkstoff besteht, dessen Wär­meausdehnungskoeffizient zumindest annähernd gleich oder grösser ist als der Wärmeausdehnungskoeffizient des Werkstoffs des Kolbens (8).4. Compressor according to one of the preceding claims, characterized in that the piston (8) and the cylinder (4) are each designed with a tread formed from a wear-resistant material, and that at least the part of the cylinder (4) containing the tread consists of a material whose coefficient of thermal expansion is at least approximately equal to or greater than the coefficient of thermal expansion of the material of the piston (8). 5. Kompressor nach Anspruch 4, dadurch gekennzeichnet, dass der Kolben (8) zumindest in seinem die Lauffläche enthaltenden Randbereich aus Hartmetall besteht und dass die Lauffläche des Zylinders (4) an einem Zylin­dereinsatz (26) ausgebildet ist, der aus einem kerami­schen Material besteht.5. Compressor according to claim 4, characterized in that the piston (8) consists at least in its edge area containing the tread of hard metal and that the tread of the cylinder (4) is formed on a cylinder insert (26) which consists of a ceramic material . 6. Kompressor nach Anspruch 5, dadurch gekennzeichnet, dass der Zylindereinsatz (26) in einer in den Zylinder (4) einsetzbaren, die Wärmeausdehnung des Zylinderein­satzes (26) zumindest teilweise kompensierenden Büchse (67) angeordnet ist.6. Compressor according to claim 5, characterized in that the cylinder insert (26) in a cylinder (4) insertable, the thermal expansion of the cylinder insert (26) at least partially compensating sleeve (67) is arranged. 7. Kompressor nach einem der vorangehenden Ansprüche, da­durch gekennzeichnet, dass die Differenz zwischen dem Innendurchmesser des Zylinders (4) bzw. Zylinderein­satzes (26) und dem Aussendurchmesser des Kolbens (8) im Bereich von etwa 0,004 bis 0,01 mm liegt.7. Compressor according to one of the preceding claims, characterized in that the difference between the inner diameter of the cylinder (4) or cylinder insert (26) and the outer diameter of the piston (8) is in the range of about 0.004 to 0.01 mm. 8. Kompressor nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass der keramische Werkstoff im we­sentlichen aus Siliciumcarbid besteht.8. Compressor according to one of claims 5 to 7, characterized in that the ceramic material consists essentially of silicon carbide. 9. Kompressor nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass der keramische Werkstoff im we­sentlichen aus Siliciumnitrid besteht.9. Compressor according to one of claims 5 to 7, characterized in that the ceramic material consists essentially of silicon nitride. 10. Kompressor nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass der keramische Werkstoff im we­sentlichen aus Zirkonoxid besteht.10. Compressor according to one of claims 5 to 7, characterized in that the ceramic material consists essentially of zirconium oxide. 11. Verwendung eines Kompressors nach einem der vorangehen­den Ansprüche als Enddruckstufe einer aus mehreren in Reihe geschalteten Zylinder/Kolben-Aggregaten bestehen­den Anordnung zum Verdichten von in einem Fahrzeug als Treibstoff zu speicherndem Gas, insbesondere Erdgas.11. Use of a compressor according to one of the preceding claims as the final pressure stage of an arrangement consisting of a plurality of cylinder / piston units connected in series for compressing gas to be stored in a vehicle as fuel, in particular natural gas.
EP89810937A 1989-01-19 1989-12-12 Piston compressor Expired - Lifetime EP0378967B1 (en)

Applications Claiming Priority (2)

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CH163/89 1989-01-19
CH16389 1989-01-19

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AU4853390A (en) 1990-07-26
US5033940A (en) 1991-07-23
CA2008202A1 (en) 1990-07-19
EP0378967B1 (en) 1993-01-27
AU621974B2 (en) 1992-03-26
DE58903407D1 (en) 1993-03-11
CA2008202C (en) 1998-04-07

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