EP0378967B1 - Piston compressor - Google Patents
Piston compressor Download PDFInfo
- Publication number
- EP0378967B1 EP0378967B1 EP89810937A EP89810937A EP0378967B1 EP 0378967 B1 EP0378967 B1 EP 0378967B1 EP 89810937 A EP89810937 A EP 89810937A EP 89810937 A EP89810937 A EP 89810937A EP 0378967 B1 EP0378967 B1 EP 0378967B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- cylinder
- compressor according
- yoke
- connecting element
- 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
Links
- 239000000463 material Substances 0.000 claims description 15
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 8
- 239000007789 gas Substances 0.000 claims description 7
- 229910010293 ceramic material Inorganic materials 0.000 claims description 6
- 239000000314 lubricant Substances 0.000 claims description 4
- 229910052751 metal Inorganic materials 0.000 claims description 4
- 239000002184 metal Substances 0.000 claims description 4
- 239000003345 natural gas Substances 0.000 claims description 4
- 229910052581 Si3N4 Inorganic materials 0.000 claims description 2
- 238000006073 displacement reaction Methods 0.000 claims description 2
- RVTZCBVAJQQJTK-UHFFFAOYSA-N oxygen(2-);zirconium(4+) Chemical compound [O-2].[O-2].[Zr+4] RVTZCBVAJQQJTK-UHFFFAOYSA-N 0.000 claims description 2
- 238000005096 rolling process Methods 0.000 claims description 2
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 claims description 2
- 229910010271 silicon carbide Inorganic materials 0.000 claims description 2
- HQVNEWCFYHHQES-UHFFFAOYSA-N silicon nitride Chemical compound N12[Si]34N5[Si]62N3[Si]51N64 HQVNEWCFYHHQES-UHFFFAOYSA-N 0.000 claims description 2
- 229910001928 zirconium oxide Inorganic materials 0.000 claims description 2
- 239000000446 fuel Substances 0.000 claims 1
- 239000000565 sealant Substances 0.000 claims 1
- 230000006835 compression Effects 0.000 description 17
- 238000007906 compression Methods 0.000 description 17
- 238000007789 sealing Methods 0.000 description 4
- 229910052799 carbon Inorganic materials 0.000 description 3
- 210000002445 nipple Anatomy 0.000 description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 229910003271 Ni-Fe Inorganic materials 0.000 description 1
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 239000012876 carrier material Substances 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 150000002736 metal compounds Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000029058 respiratory gaseous exchange Effects 0.000 description 1
Images
Classifications
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- 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.
- a pump or a compressor of another type in which a piston lubricated by a lubricant is guided in a liner which is designed with an inner diameter which is around a Dimension of 0.0025 mm is larger than the outside diameter of the piston. This is to prevent the liquid pressure in the displacement of the pump or the compressor from overcoming the viscosity of the lubricant in the space between the piston and the liner, and to effectively seal this space.
- the piston is positively coupled via a drive rod with a spherical end to a spherical bearing which is mounted in a bore of the crosshead with radial play, movable transversely to the axis of the bore.
- the vibrations of the bearing transmitted via the drive rod can impair the guidance of the piston.
- This known embodiment also requires a structurally relatively complex seal and guide arrangement in order to relieve the liner, to prevent the piston from getting stuck and to ensure the supply of lubricant. Dry running of the relatively narrowly guided piston of the known design is not possible.
- the invention has for its object an improved high-pressure reciprocating compressor of the type mentioned in a simplified compared to previous versions 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, for example, up to 500 bar.
- 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 of the connecting part slidingly guided in the cylinder housing, so that parallel guidance of the piston that is not influenced by such vibrations 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 guided transversely to the axis 10 between two guideways 18 formed in the yoke.
- the pistons 6 and 8 are coupled via a yoke 22 connecting their piston rods 20 and 21 to a second slider, not shown, mounted on the crank pin 16, which is displaceably guided transversely to the axis 11 in the yoke 22 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 the suction stroke of the piston 5, a connection between the compression space 31 and a central space 43 separated therefrom by the piston 5 is made, which is connected to a supply 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.
- the rotationally movably mounted ball 63 also prevents the transverse forces of the yokes 22 slidingly 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.
- 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 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 rotatable rolling element, for example one with cylindrical or with spherical support surfaces, can be provided in the holder.
- another rotatable 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 simplified representation of the holder 61, it is also possible to provide a two-piece sleeve which can be suitably attached to the yoke 22 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 of amorphous diamond-like carbon ("amorphous diamond-like carbon"). Such layers can each be produced in a cost-effective process suitable for mass production and at a relatively low treatment temperature which is gentle on the carrier material, e.g. approx. 200 ° C, be applied to the relevant part or to both parts. If the thermal expansion coefficients of the cylinder material and the piston material are approximately the same, an embodiment is also possible in which such a layer is applied directly to the cylinder bore.
- 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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
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 aus der EP-Patentanmeldung 0 269 882 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 a four-stage small compressor of the type mentioned, which is known from EP patent application 0 269 882, natural gas is produced in a cylinder / piston unit which forms the final pressure stage by 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.
Aus der DE-C-963748 ist eine Pumpe bzw. ein Kompressor anderer Art bekannt, bei dem ein durch ein Schmiermittel geschmierter Kolben in einer Laufbüchse geführt ist, welche mit einem Innendurchmesser ausgeführt ist, der um ein Mass von 0,0025 mm grösser ist als der Aussendurchmesser des Kolbens. Dadurch soll verhindert werden, dass der Flüssigkeitsdruck im Hubraum der Pumpe bzw. des Kompressors die Viskosität des Schmiermittels in dem Zwischenraum zwischen Kolben und Laufbüchse überwindet, und es soll eine wirksame Abdichtung dieses Zwischenraums erzielt werden. Der Kolben ist über eine Triebstange mit einem kugelförmigen Ende formschlüssig mit einem kugelförmigen Lager gekoppelt, welches in einer Bohrung des Kreuzkopfs mit einem radialen Spiel, quer zur Achse der Bohrung beweglich, gelagert ist. Entsprechend kann, durch über die Triebstange übertragene Schwingungen des Lagers, die Führung des Kolbens beeinträchtigt werden. Auch diese bekannte Ausführung erfordert eine konstruktiv relativ aufwendige Dichtungs- und Führungsanordnung, um die Laufbüchse zu entlasten, ein Steckenbleiben des Kolbens zu verhindern und die Zufuhr von Schmiermittel zu gewährleisten. Ein Trockenlauf des relativ eng geführten Kolbens der bekannten Ausführung ist nicht möglich.From DE-C-963748 a pump or a compressor of another type is known, in which a piston lubricated by a lubricant is guided in a liner which is designed with an inner diameter which is around a Dimension of 0.0025 mm is larger than the outside diameter of the piston. This is to prevent the liquid pressure in the displacement of the pump or the compressor from overcoming the viscosity of the lubricant in the space between the piston and the liner, and to effectively seal this space. The piston is positively coupled via a drive rod with a spherical end to a spherical bearing which is mounted in a bore of the crosshead with radial play, movable transversely to the axis of the bore. Correspondingly, the vibrations of the bearing transmitted via the drive rod can impair the guidance of the piston. This known embodiment also requires a structurally relatively complex seal and guide arrangement in order to relieve the liner, to prevent the piston from getting stuck and to ensure the supply of lubricant. Dry running of the relatively narrowly guided piston of the known design is not possible.
Der Erfindung liegt die Aufgabe zugrunde, einen verbesserten Hochdruck-Hubkolbenkompressor der eingangs genannten Art in einer gegenüber bisherigen Ausführungen vereinfachten 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 an improved high-pressure reciprocating compressor of the type mentioned in a simplified compared to previous versions 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, for example, up to 500 bar.
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 of the connecting part slidingly guided in the cylinder housing, so that parallel guidance of the piston that is not influenced by such vibrations 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
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
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
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
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
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
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
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
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
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
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
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
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
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 rotatable rolling element, for example one with cylindrical or with spherical support surfaces, can be provided in the holder. Instead of the one-
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 schonenden, 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
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)
- A high-pressure reciprocating piston compressor, comprising at least one cylinder (4) formed in the cylinder housing, and a piston (8) non-lubricatingly guided therein and coupled to a crankshaft (17) of a drive system by way of a connecting element (yoke 22) guided in the cylinder housing for displacement in the direction of the longitudinal axis (11) of the cylinder (4), characterised in that the piston (8) is coupled to the connecting element (22) via a mounting (61) which comprises at least one support element movable relatively to the piston (8) and to the connecting element (yoke 22) transversely of the longitudinal axis (11) of the cylinder (4), and in that the cylinder (4) together with the piston (8) defines a narrow annular gap which is open over the entire common length and which is free of sealants and lubricants and which permits a predetermined leakage flow of the compressed medium.
- A compressor according to claim 1, characterised in that the support element cooperates with the piston (8) and with the connecting element (yoke 22) via a convex support surface in each case.
- A compressor according to claim 1 or 2, characterised in that the support element is formed by a rolling element , e.g. a ball (63), which is introducible between the piston (8) and the connecting element (yoke 22) and which is mounted to be rotationally movable in the mounting (61).
- A compressor according to any one of the preceding claims, characterised in that the piston (8) and the cylinder (4) are each constructed with the bearing surface formed from a wear-resistant material, and in that at least that part of the cylinder (4) which contains the bearing surface consists of a material whose coefficient of thermal expansion is at least substantially equal to or greater than the coefficient of thermal expansion of the material of the piston (8).
- A compressor according to claim 4, characterised in that at least the edge zone of the piston (8) containing the bearing surface consists of hard metal and in that the bearing surface of the cylinder (4) is formed on a cylinder liner (26) consisting of ceramic material.
- A compressor according to claim 5, characterised in that the cyliner liner (26) is disposed in a bush (67) which is introducible into the cylinder (4) and which at least partially compensates for the thermal expansion of the cylinder liner (26).
- A compressor according to any one of the preceding claims, characterised in that the diference between the inside diameter of the cylinder (4) or cylinder liner (26) and the outside diameter of the piston (8) is in the range of about 0̸.0̸0̸4 to 0.01 mm.
- A compressor according to any one of claims 5 to 7, characterised in that the ceramic material consists essentially of silicon carbide.
- A compressor according to any one of claims 5 to 7, characterised in that the ceramic material consists essentially of silicon nitride.
- A compressor according to any one of claims 5 to 7, characterised in that the ceramic material consists essentially of zirconium oxide.
- Use of a compressor according to any one of the preceding claims as a final pressure stage in a system consisting of a plurality of series-connected cylinder and piston units for compressing gas, more particularly natural gas for storage as fuel in a vehicle.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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CH163/89 | 1989-01-19 | ||
CH16389 | 1989-01-19 |
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EP0378967A1 EP0378967A1 (en) | 1990-07-25 |
EP0378967B1 true EP0378967B1 (en) | 1993-01-27 |
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ID=4180694
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EP89810937A Expired - Lifetime EP0378967B1 (en) | 1989-01-19 | 1989-12-12 | Piston compressor |
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US (1) | US5033940A (en) |
EP (1) | EP0378967B1 (en) |
AU (1) | AU621974B2 (en) |
CA (1) | CA2008202C (en) |
DE (1) | DE58903407D1 (en) |
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---|---|---|---|---|
CH253326A (en) * | 1944-10-28 | 1948-02-29 | Pauget Georges | Radial piston liquid pump. |
FR1018769A (en) * | 1949-12-22 | 1953-01-13 | Sealed fuel pump, with regulator, for heavy oil engine | |
DE963748C (en) * | 1953-08-03 | 1957-05-09 | Gerhard Paul Krause | Pump or compressor |
US4211092A (en) * | 1977-09-22 | 1980-07-08 | Karsten Laing | Space heating installation |
US4366747A (en) * | 1980-08-11 | 1983-01-04 | J. I. Case Company | Slipper arrangement for hydraulic pump |
EP0046585B2 (en) * | 1980-08-25 | 1992-12-09 | Helix Technology Corporation | Refrigerator with a clearance seal compressor |
DE3135726A1 (en) * | 1980-09-09 | 1982-04-22 | Ernst 6230 Frankfurt Scraback | High-pressure piston pump |
US4551074A (en) * | 1981-10-01 | 1985-11-05 | Honda Giken Kogyo Kabushiki Kaisha | Air pump apparatus |
US4790236A (en) * | 1983-09-12 | 1988-12-13 | Beckman Instruments, Inc. | Floating piston coupling for plunger type pumps |
CH671610A5 (en) * | 1986-11-14 | 1989-09-15 | Sulzer Ag | |
EP0309596B1 (en) * | 1987-09-26 | 1993-03-31 | Hewlett-Packard GmbH | Pumping apparatus for delivering liquid at high pressure |
-
1989
- 1989-12-12 EP EP89810937A patent/EP0378967B1/en not_active Expired - Lifetime
- 1989-12-12 DE DE8989810937T patent/DE58903407D1/en not_active Expired - Lifetime
-
1990
- 1990-01-17 AU AU48533/90A patent/AU621974B2/en not_active Expired
- 1990-01-18 US US07/467,021 patent/US5033940A/en not_active Expired - Lifetime
- 1990-01-19 CA CA002008202A patent/CA2008202C/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018129747A1 (en) | 2018-11-26 | 2020-05-28 | Wabco Europe Bvba | Reciprocating compressor in a compressed air supply system |
Also Published As
Publication number | Publication date |
---|---|
DE58903407D1 (en) | 1993-03-11 |
CA2008202A1 (en) | 1990-07-19 |
US5033940A (en) | 1991-07-23 |
AU621974B2 (en) | 1992-03-26 |
AU4853390A (en) | 1990-07-26 |
CA2008202C (en) | 1998-04-07 |
EP0378967A1 (en) | 1990-07-25 |
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