EP1831552A1 - Dry-running compressor, particularly a swash-plate compressor, with a piston-rod mounting - Google Patents

Dry-running compressor, particularly a swash-plate compressor, with a piston-rod mounting

Info

Publication number
EP1831552A1
EP1831552A1 EP05819263A EP05819263A EP1831552A1 EP 1831552 A1 EP1831552 A1 EP 1831552A1 EP 05819263 A EP05819263 A EP 05819263A EP 05819263 A EP05819263 A EP 05819263A EP 1831552 A1 EP1831552 A1 EP 1831552A1
Authority
EP
European Patent Office
Prior art keywords
dry
sealing
plain bearing
bearing bush
compressor according
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
EP05819263A
Other languages
German (de)
French (fr)
Other versions
EP1831552B1 (en
Inventor
Dieter Spurny
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP1831552A1 publication Critical patent/EP1831552A1/en
Application granted granted Critical
Publication of EP1831552B1 publication Critical patent/EP1831552B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
    • 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

Definitions

  • Dry running compressor in particular swash plate compressor, with a piston rod storage
  • the present invention relates to a dry-running compressor, in particular a swash plate compressor, with at least one axially movable driving piston rod, which forwards the driving force to a cylinder in the associated piston for generating the compressed air, wherein the axially movable piston rod is guided over a bearing housing arranged fixedly to the bearing bore ,
  • linear compressors which are driven as a linear compressor via an axially movable piston rod, extends primarily to the commercial vehicle technology.
  • Other linear compressors include crankcase compressors, crosshead compressors and, in particular, swash plate compressors.
  • hi commercial vehicles are compressors used, which are usually driven directly by the engine of Nutzfabrzeuges and supply compressed air to feed the compressed air system.
  • the compressed air thus generated is used for example for operating a compressed air brake system.
  • EP 0 859 151 A2 discloses a compressor for generating compressed air in commercial vehicles, which solves this problem in that the compressor is designed here to run as dry as possible.
  • the compressor is constructed in the manner of a swash plate compressor and has only a conventional oil-lubricated engine, which consists essentially of a arranged on a drive shaft swash plate with hemispheres in bearing cups, which form a bearing assembly for transmitting the rotational movement in an oscillating stroke. From the bearing assembly extend piston rods to various pistons, which generate by a reciprocating motion in associated cylinders in a conventional manner, the compressed air.
  • Usually several pistons are arranged on a circumferential circle adjacent to each other in order to realize the highest possible delivery of the swash plate compressor.
  • the bearing of the piston rods stationary to the compressor housing via bearing bores on the oil-lubricated engine side.
  • the bearing bores extend on a circumferential circle at an angular distance from each other parallel to the longitudinal axis of the compressor through a central housing portion, on which the piston facing individual öbelbstMailde sealing elements are provided.
  • suction chambers At the rear of the pistons are suction chambers, which are connected by an annular space to a common suction space, in which a suction port opens to the atmosphere.
  • the invention includes the technical teaching that the bearing bore in the region of the swash plate end facing is equipped with a first lubricious plain bearing bush, which is in communication with means for oil supply, and the bearing bore in the region of the piston end facing with a second especially dry-running - plain bearing bush is equipped.
  • the advantage of the solution according to the invention is, in particular, that the highly stressed bearing point can be reliably cooled and lubricated by the lubricious plain bearing bush with external oil supply. For this it is then no longer necessary to use oil from the engine area.
  • Oil supply to the bearing which is reinforced by a plain bearing bush, contributes to dry running the entire area of the engine, d. H. by local permanent lubrication measures, to obtain a completely dry running swash plate compressor.
  • first lubricious plain bearing bush By using the first lubricious plain bearing bush according to the invention, mixed friction states in this area are also largely excluded. Since the point at which the second plain bearing bush is arranged anyway has oil supply problems due to the longitudinal movement of the piston rod, this is another, namely dry-running plain bearing bush, provided.
  • the dry-running plain bearing bush simultaneously acts as a scraper before downstream sealing elements to the interior of the cylinder.
  • the combination of the special plain bearing bushes within the bearing bore enables a long-lasting rod bearing.
  • the means for own oil supply of the first lubricious plain bearing bushing a stationary to the compressor housing extending oil passage.
  • the oil channel leads, starting from a refillable oil reservoir in the compressor housing, the oil to the first plain bearing bushing.
  • the advantage here is that oil escaping from the lubricious plain bearing bush in the direction of the engine, is converted by rotation of the drive shaft in spray oil, which contributes to a lubrication of the bearing assembly between the swash plate and the piston rod.
  • the oil reservoir for feeding the oil channel can be connected to a lubricant circuit of the swash plate compressor or a commercial vehicle. This is done by refilling the oil reservoir then automatically.
  • Multi-material bush made of a steel-aluminum alloy.
  • the second, dry-running plain bearing bushing can be made of PTFE (Teflon). This material ensures the storage properties specifically required at the storage location.
  • PTFE Teflon
  • This material ensures the storage properties specifically required at the storage location.
  • a further improvement of the invention measure is provided for sealing the boundary point between the cylinder containing compressed air and the swashplate comprising the engine either a single sealing ring or advantageously a acting between the second dry-run plain bearing bush and the interior of the cylinder on the piston rod seal assembly.
  • a requirement of this bar seal is that it must seal compressed air to the sides of the engine oil and to the sides of the cylinder, and to separate the two areas of the swash plate compressor so far reliable.
  • a sealing arrangement provides the desired result.
  • a sealing arrangement which consists of a first sealing element for oil seal, which is adjacent to the second dry-run plain bearing bush, and which cooperates with a second axially spaced apart sealing element for compressed air sealing, which is disposed adjacent to the interior of the cylinder, wherein the Region between the two sealing elements via a vent channel communicates with the atmosphere.
  • both sealing elements can function properly and a reliable separation of the adjacent regions of the swash plate compressor can be implemented in a simple manner. A mutual influence of the sealing elements by oil or compressed air is thus excluded.
  • the venting channel arranged between the two sealing elements should, starting from the region of the sealing arrangement, open into a suction chamber arranged below the piston and communicating with the atmosphere.
  • a suction of the compressed air in the swash plate compressor is performed by a check valve integrated in the piston. This results in the position of the suction chamber below the piston in a region of the swash plate compressor so that allows a short channel guide the vent channel. Because the seal assembly is in close proximity to the suction chamber Such a short venting channel can be easily produced by drilling.
  • first sealing element for oil sealing and also the second sealing element are formed as a profiled sealing ring with an inner radial sealing lip.
  • comparable sealing elements can be used as long as they ensure a reliable sealing of the axially mutually movable components.
  • piston rod made of steel is provided with a surface which has a similar surface quality as piston rods of pneumatic cylinders, preferably a maximum of 4 ⁇ m.
  • Figure 1 shows a longitudinal section through a dry-running swash plate compressor
  • FIG. 2 shows an enlarged detail of Figure 1 in the region of one of the piston rods.
  • the dry running swash plate compressor shown in Figure 1 has on the part of the engine to a drive shaft 1, which is offset by a - not shown here - engine in rotary motion.
  • a swash plate 2 is fixed in a conventional manner.
  • the swash plate 2 is about a bearing assembly 3, the rotational movement of the drive shaft 1 in an oscillating stroke movement.
  • the lifting movement is transmitted to a mounted on the bearing assembly 3 piston rod 4.
  • piston rod 4 In addition to the piston rod 4 are still more piston rods associated with Bearing arrangements available; The following description is thus to be understood as an example.
  • the piston rod 4 forwards the reciprocating motion generated due to the rotation of the swash plate 2 to a piston 5 which is coaxially fixed to the end of the piston rod 4 opposite the bearing assembly 3.
  • the piston 5 runs within an associated cylinder 6, in which the compressed air is generated due to the movement of the piston 5.
  • a suction of air from the atmosphere takes place through the piston, which has a check valve device 7 for this purpose.
  • the compressed compressed air leaves the cylinder 6 via a further correspondingly connected check valve device 8 on the cylinder head 9, which is attached to the valve housing 10.
  • the plain bearing bush 12 is lubricated by oil supply means.
  • the means for supplying oil to the lubricious plain bearing bush 12 consist of an oil passage 13 for supplying oil to the lubricious slide bearing bushing 12, starting from an oil reservoir 14, which is arranged in the region of the valve housing 10 and can be refilled via the lubrication circuit of the swash plate compressor.
  • the lubricious plain bearing bush 12 is made of a copper-lead alloy.
  • the bearing bore 11 is provided in the region of the end facing the piston 5 with a second, dry-running plain bearing bush 15.
  • the dry-running plain bearing bush 15 here has a sliding bearing layer made of PTFE.
  • the compressed air-containing cylinder 6 is sealed with respect to the swash plate 2 comprising the engine with a sealing arrangement which between the second dry-running plain bearing bush 15 and the interior of the cylinder 2 sealingly acts on the piston rod 4.
  • the sealing arrangement here consists of a first sealing element 16 for sealing oil, which is so far adjacent to the second dry-running plain bearing bush 15 and prevents penetration of the first plain bearing bush 12 supplied oil due to the reciprocating motion of the piston rod 4 in the region of the cylinder 2 , Adjacent to the first sealing element 16 is a second, this axially spaced-apart sealing element 17 is provided.
  • the second sealing element 17 has the task of avoiding an outflow of compressed air from the interior of the cylinder 2.
  • Media separation is the area between the two sealing elements 16 and 17 connected via a vent channel 18 with the atmosphere.
  • the venting channel 18, starting from the region of the sealing arrangement, extends into a suction chamber 19 provided below the piston 5 and communicating with the atmosphere for improving the sealing action between the profiled sealing rings
  • Sealing elements 16 and 17 and the piston rod 4 consists of steel with a polished surface, which corresponds in its surface quality of the surface of a pneumatic cylinder.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

The invention relates to a dry-running swash-plate compressor, particularly for generating compressed air in goods-carrying vehicles, comprising a swash-plate (2), which is coaxially fastened to a drive shaft (1) and which, via a bearing arrangement (3), converts the driving rotational motion into a reciprocating motion that displaces at least one piston rod (4), which is mounted on the bearing arrangement (3) and which is mounted on a piston (5) running inside an associated cylinder (6), in order to generate the compressed air. The axially displaceable piston rod (4) is guided via a bearing bore (11) whose position is fixed with regard to the compressor housing (10). This bearing bore (11), in the vicinity of the end facing the swash-plate (2), is provided with a first lubricatable plain bearing bush (12), which is connected to means for supplying oil, and the bearing bore (11), in the vicinity of the end facing the piston (5), is provided with a second plain bearing bush (15) that is capable of dry-running.

Description

Trockenlaufender Verdichter, insbesondere Taumelscheibenverdichter, mit einer Kolbenstangenlagerung Dry running compressor, in particular swash plate compressor, with a piston rod storage
Die vorliegende Erfindung betrifft einen trockenlaufenden Verdichter, insbesondere einen Taumelscheibenverdichter, mit mindestens einer axial bewegbaren antreibenden Kolbenstange, welche die Antriebskraft an in einem zugeordneten Zylinder laufenden Kolben zur Erzeugung der Druckluft weiterleitet, wobei die axial bewegbare Kolbenstange über eine ortsfest zum Verdichtergehäuse angeordnete Lagerbohrung geführt ist.The present invention relates to a dry-running compressor, in particular a swash plate compressor, with at least one axially movable driving piston rod, which forwards the driving force to a cylinder in the associated piston for generating the compressed air, wherein the axially movable piston rod is guided over a bearing housing arranged fixedly to the bearing bore ,
Das Einsatzgebiet eines derartigen Verdichters, welcher als Linearverdichter über eine axial bewegbare Kolbenstange angetrieben wird, erstreckt sich vornehmlich auf die Nutzfahrzeugtechnik. Weitere Linearverdichter sind: Kurbelschleifenverdichter, KreuzkopfVerdichter und insbesondere Taumelscheibenverdichter.The field of application of such a compressor, which is driven as a linear compressor via an axially movable piston rod, extends primarily to the commercial vehicle technology. Other linear compressors include crankcase compressors, crosshead compressors and, in particular, swash plate compressors.
hi Nutzfahrzeugen kommen Verdichter zum Einsatz, welche meist direkt über den Motor des Nutzfabrzeuges angetrieben werden und Druckluft zur Speisung des Druckluft-Bordnetzes liefern. Bei Nutzfahrzeugen wird die so erzeugte Druckluft beispielsweise zum Betrieb einer Druckluft-Bremsanlage genutzt.hi commercial vehicles are compressors used, which are usually driven directly by the engine of Nutzfabrzeuges and supply compressed air to feed the compressed air system. In commercial vehicles, the compressed air thus generated is used for example for operating a compressed air brake system.
In allgemein bekannter Weise werden für die Drucklufterzeugung in Nutzfahrzeugen vornehmlich ölgeschmierte Kolbenverdichter eingesetzt. Die Schmierung dieser Verdichter erfolgt meist aus dem Ölkreislauf des Motors. Hierbei gelangt allerdings zwangsläufig Öl über die Kolben des Verdichters in die erzeugte Druckluft. Je nach Alter und Wartungszustand des Verdichters können erhebliche Ölmengen über die Druckluft in dieIn a generally known manner, primarily oil-lubricated reciprocating compressors are used for the production of compressed air in commercial vehicles. The lubrication of these compressors usually takes place from the oil circuit of the engine. In this case, however, inevitably oil passes through the pistons of the compressor in the generated compressed air. Depending on the age and maintenance condition of the compressor, significant amounts of oil can be injected via the compressed air
Umwelt gelangen, nämlich über diverse Entlüftungsöffhungen des Druckluft-Bordnetzes. Ein weiteres Problem ölgeschmierter Kolbenverdichter im Nutzfahrzeugbereich besteht darin, dass immer höhere Betriebsdrücke vom Verdichter abverlangt, womit recht hohe thermische Beanspruchungen einhergehen, welche zu Verkokungen eines Teils des in die Druckluft gelangten Öls führt. Diese Ölkohle lagert sich innerhalb des Innenraums des Zylinders im Verdichter und nachgeschalteten Druckluftgeräten ab und beeinflusst dort sehr nachhaltig deren Standzeit.Environment, namely on various ventilation openings of the compressed air electrical system. Another problem of oil-lubricated reciprocating compressors in the commercial vehicle sector is that ever higher operating pressures demanded from the compressor, which is accompanied by quite high thermal stresses, which leads to coking of a part of the oil passed into the compressed air. This carbon builds up inside the cylinder inside the cylinder Compressors and downstream compressed air devices from and influenced there very sustainable their life.
Aus der EP 0 859 151 A2 geht ein Verdichter zur Drucklufterzeugung in Nutzfahrzeugen hervor, welcher dieses Problem dadurch löst, in dem der Verdichter hier weitestgehend trockenlaufend konstruiert ist. Der Verdichter ist nach Art eines Taumelscheibenverdichters aufgebaut und weist lediglich ein herkömmliches ölgeschmiertes Triebwerk auf, welches im Wesentlichen aus einer auf einer Antriebswelle angeordneten Taumelscheibe mit Halbkugeln in Lagerpfannen besteht, die eine Lageranordnung zu Übertragung der Drehbewegung in eine oszillierende Hubbewegung bilden. Von der Lageranordnung aus verlaufen Kolbenstangen zu diversen Kolben, welche durch eine Hin- und Herbewegung in zugeordneten Zylindern in an sich bekannter Weise die Druckluft erzeugen. Gewöhnlich sind mehrere Kolben auf einem Umfangskreis benachbart zueinander angeordnet, um eine möglichst hohe Förderleistung des Taumelscheibenverdichters zu realisieren.EP 0 859 151 A2 discloses a compressor for generating compressed air in commercial vehicles, which solves this problem in that the compressor is designed here to run as dry as possible. The compressor is constructed in the manner of a swash plate compressor and has only a conventional oil-lubricated engine, which consists essentially of a arranged on a drive shaft swash plate with hemispheres in bearing cups, which form a bearing assembly for transmitting the rotational movement in an oscillating stroke. From the bearing assembly extend piston rods to various pistons, which generate by a reciprocating motion in associated cylinders in a conventional manner, the compressed air. Usually several pistons are arranged on a circumferential circle adjacent to each other in order to realize the highest possible delivery of the swash plate compressor.
Die Lagerung der Kolbenstangen ortsfest zum Verdichtergehäuse erfolgt über Lagerbohrungen auf der ölgeschmierten Triebwerkseite. Die Lagerbohrungen erstrecken sich auf einem Umfangskreis unter Winkelabstand zueinander parallel zur Längsachse des Kompressors durch einen mittleren Gehäuseabschnitt, an welchem den Kolben zugewandt einzelne öläbstreifende Abdichtelemente vorgesehen sind. An der Rückseite der Kolben befinden sich Ansaugkammern, die durch einen Ringraum zu einem gemeinsamen Ansaugraum verbunden sind, in welchen ein Ansauganschluss an die Atmosphäre mündet.The bearing of the piston rods stationary to the compressor housing via bearing bores on the oil-lubricated engine side. The bearing bores extend on a circumferential circle at an angular distance from each other parallel to the longitudinal axis of the compressor through a central housing portion, on which the piston facing individual öbelbstreifende sealing elements are provided. At the rear of the pistons are suction chambers, which are connected by an annular space to a common suction space, in which a suction port opens to the atmosphere.
Ein Problem dieses Standes der Technik resultiert aus der Tatsache, dass an den Bereich der Führung der Kolbenstange aufgrund der hierauf einwirkenden unterschiedlichen Kräfte besonders hohe Anforderungen gestellt sind. So kann es beispielsweise im Laufe der Lebenszeit des Taumelscheibenverdichters an dieser Stelle zu einem Ausschlagen der Lagerbohrung kommen, da diese aus der Drehung der Taumelscheibe resultierende Radialkräfte aufzunehmen hat. Diese Kräfte treten insbesondere an dem der Taumelscheibe zugeordneten Endbereich der Lagerbohrung auf. Einem Verschleiß der Lagerbohrung wurde bisher dadurch entgegengewirkt, indem die Lagerbohrung mit einer großen Länge und geringen Toleranzen dimensioniert wurde. Diese Maßnahmen führen jedoch zu einer unerwünschten Vergrößerung der geometrischen Abmessungen des gesamten Verdichters bzw. zu einem erhöhten Fertigungsaufwand für die Herstellung der langen, eng tolerierten Passung. Die Paarung Kolbenstange zu Lagerbohrung muss zuverlässig ein Eindringen von Öl aus der Triebwerksseite in den Innenraum des Zylinders vermeiden. Gleichzeitig ist die Gleitreibung zwischen den beiden relativ zu einander bewegten Bauteilen gering zu halten, um den Wirkungsgrad des Taumelscheibenverdichters nicht negativ zu beeinflussen. Des Weiteren sollte verhindert werden, dass Druckluft aus dem Innenraum des Zylinders nicht in den Bereich des Triebwerks gelangt.A problem of this prior art results from the fact that particularly high demands are placed on the region of the guidance of the piston rod due to the different forces acting thereon. Thus, for example, in the course of the lifetime of the swash plate compressor at this point come to a deflection of the bearing bore, since this has to absorb resulting from the rotation of the swash plate radial forces. These forces occur in particular on the end of the bearing bore assigned to the swashplate. Wear of the bearing bore was previously counteracted by the bearing bore was dimensioned with a large length and low tolerances. However, these measures lead to an undesirable increase in the geometric dimensions of the entire compressor or to increased manufacturing costs for the production of long, tight tolerance fit. The mating piston rod to bearing bore must reliably prevent oil from entering the engine inside the cylinder. At the same time, the sliding friction between the two components moving relative to one another is to be kept low in order not to negatively influence the efficiency of the swashplate compressor. Furthermore, it should be prevented that compressed air from the interior of the cylinder does not reach the area of the engine.
Es ist daher die Aufgabe der vorliegenden Erfindung einen gattungsgemäßen trockenlaufenden Taumelscheibenverdichter dahingehend weiter zu verbessern, dass eine zuverlässige Kolbenstangenlagerung über eine möglichst lange Betriebszeit sichergestellt ist.It is therefore the object of the present invention to further improve a generic dry-running swash plate compressor to the effect that a reliable piston rod storage is ensured over the longest possible operating time.
Die Aufgabe wird ausgehend von einem trockenlaufenden Taumelscheibenverdichter gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of a dry running swash plate compressor according to the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give advantageous developments of the invention.
Die Erfindung schließt die technische Lehre ein, das die Lagerbohrung im Bereich des der Taumelscheibe zugewandten Endes mit einer ersten schmierbaren Gleitlagerbuchse ausgestattet ist, welche mit Mitteln zur Ölversorgung in Verbindung steht, und das die Lagerbohrung im Bereich des dem Kolben zugewandten Endes mit einer zweiten - insbesondere trockenlauffähigen - Gleitlagerbuchse ausgestattet ist.The invention includes the technical teaching that the bearing bore in the region of the swash plate end facing is equipped with a first lubricious plain bearing bush, which is in communication with means for oil supply, and the bearing bore in the region of the piston end facing with a second especially dry-running - plain bearing bush is equipped.
Der Vorteil der erfindungsgemäßen Lösung besteht insbesondere darin, dass die hochbeanspruchte Lagerstelle durch die schmierbare Gleitlagerbuchse mit externer Ölversorgung zuverlässig gekühlt und geschmiert werden kann. Hierfür ist es dann nicht mehr erforderlich, Öl aus dem Bereich des Triebwerks zu verwenden. Durch die separate - A -The advantage of the solution according to the invention is, in particular, that the highly stressed bearing point can be reliably cooled and lubricated by the lubricious plain bearing bush with external oil supply. For this it is then no longer necessary to use oil from the engine area. By the separate - A -
Ölversorgung der Lagerstelle, welche durch eine Gleitlagerbuchse verstärkt ist, leistet einen Beitrag dafür, den gesamten Bereich des Triebwerks trockenlaufend, d. h. durch örtliche Dauerschmierungsmaßnahmen, auszubilden, um einen vollständig trockenlaufenden Taumelscheibenverdichter zu erhalten. Durch die Verwendung der erfindungsgemäßen ersten schmierbaren Gleitlagerbuchse sind auch Mischreibungszustände in diesem Bereich weitgehend ausgeschlossen. Da die Stelle, an der die zweite Gleitlagerbuchse angeordnet ist sowieso Ölversorgungsprobleme infolge der Längsbewegung der Kolbenstange hat, ist hierfür eine andere, nämlich trockenlauffahige Gleitlagerbuchse, vorgesehen. Die trockenlauffähige Gleitlagerbuchse fungiert gleichzeitig als Abstreifer vor nachgeschalteten Dichtungselementen zum Innenraum des Zylinders hin. Die Kombination der speziellen Gleitlagerbuchsen innerhalb der Lagerbohrung ermöglicht insgesamt eine langlebige Stangenlagerung.Oil supply to the bearing, which is reinforced by a plain bearing bush, contributes to dry running the entire area of the engine, d. H. by local permanent lubrication measures, to obtain a completely dry running swash plate compressor. By using the first lubricious plain bearing bush according to the invention, mixed friction states in this area are also largely excluded. Since the point at which the second plain bearing bush is arranged anyway has oil supply problems due to the longitudinal movement of the piston rod, this is another, namely dry-running plain bearing bush, provided. The dry-running plain bearing bush simultaneously acts as a scraper before downstream sealing elements to the interior of the cylinder. The combination of the special plain bearing bushes within the bearing bore enables a long-lasting rod bearing.
Vorzugsweise umfassen die Mittel zur eigenen Ölversorgung der ersten schmierbaren Gleitlagerbuchse einen ortsfest zum Verdichtergehäuse verlaufenden Ölkanal. Der Ölkanal führt ausgehend von einem wiederbefüllbaren Ölreservoir im Verdichtergehäuse das Öl an die erste Gleitlagerbuchse. Vorteilhaft hierbei ist, dass Öl, welches aus der schmierbaren Gleitlagerbuchse in Richtung des Triebwerks entweicht, durch Drehung der Antriebswelle in Spritzöl umgewandelt wird, welches zu einer Schmierung der Lageranordnung zwischen Taumelscheibe und Kolbenstange beiträgt. Das Ölreservoir zu Speisung des Ölkanals kann an einen Schmiermittelkreislauf des Taumelscheibenverdichters oder eines Nutzfahrzeuges angeschlossen werden. Hierüber erfolgt das Wiederauffüllen des Ölreservoirs dann automatisch.Preferably, the means for own oil supply of the first lubricious plain bearing bushing a stationary to the compressor housing extending oil passage. The oil channel leads, starting from a refillable oil reservoir in the compressor housing, the oil to the first plain bearing bushing. The advantage here is that oil escaping from the lubricious plain bearing bush in the direction of the engine, is converted by rotation of the drive shaft in spray oil, which contributes to a lubrication of the bearing assembly between the swash plate and the piston rod. The oil reservoir for feeding the oil channel can be connected to a lubricant circuit of the swash plate compressor or a commercial vehicle. This is done by refilling the oil reservoir then automatically.
Als schmierbare Gleitlagerbuchse eignet sich im Rahmen der Erfindung besonders eineAs a lubricious plain bearing bush is particularly suitable in the context of the invention
Mehrstoffbuchse aus einer Stahl-Aluminium-Legierung. Bei der zweiten, trockenlaufenden Gleitlagerbuchse kann das Material PTFE (Teflon) zur Anwendung kommen. Dieses Material gewährleistet die an der Lagerstelle speziell benötigten Lagereigenschaften. Gemäß einer weiteren die Erfindung verbessernde Maßnahme ist zur Abdichtung der Grenzstelle zwischen dem Druckluft enthaltenden Zylinder und dem die Taumelscheibe umfassenden Triebwerk entweder ein einziger Dichtring oder vorteilhafter Weise eine zwischen der zweiten trockenlauffähigen Gleitlagerbuchse und dem Innenraum des Zylinders auf die Kolbenstange wirkende Dichtungsanordnung vorgesehen. Eine Anforderung an diese Stangenabdichtung besteht darin, dass diese zu Seiten des Triebwerks Öl und zu Seiten des Zylinders Druckluft abdichten muss, und die beiden Bereiche des Taumelscheibenverdichters insoweit zuverlässig trennen muss. An der vorstehend angegebenen Stelle liefert eine Dichtungsanordnung das gewünschte Ergebnis.Multi-material bush made of a steel-aluminum alloy. The second, dry-running plain bearing bushing can be made of PTFE (Teflon). This material ensures the storage properties specifically required at the storage location. According to a further improvement of the invention measure is provided for sealing the boundary point between the cylinder containing compressed air and the swashplate comprising the engine either a single sealing ring or advantageously a acting between the second dry-run plain bearing bush and the interior of the cylinder on the piston rod seal assembly. A requirement of this bar seal is that it must seal compressed air to the sides of the engine oil and to the sides of the cylinder, and to separate the two areas of the swash plate compressor so far reliable. At the point indicated above, a sealing arrangement provides the desired result.
Besonders eignet sich hierfür eine Dichtungsanordnung, die aus einem ersten Dichtelement zur Ölabdichtung besteht, das benachbart zu der zweiten trockenlauffähigen Gleitlagerbuchse angeordnet ist, und das mit einem zweiten hierzu axial beabstandeten Dichtelement zur Druckluftabdichtung zusammenwirkt, das benachbart zum Innenraum des Zylinders angeordnet ist, wobei der Bereich zwischen beiden Dichtelementen über einen Entlüftungskanal mit der Atmosphäre in Verbindung steht.Particularly suitable for this purpose is a sealing arrangement, which consists of a first sealing element for oil seal, which is adjacent to the second dry-run plain bearing bush, and which cooperates with a second axially spaced apart sealing element for compressed air sealing, which is disposed adjacent to the interior of the cylinder, wherein the Region between the two sealing elements via a vent channel communicates with the atmosphere.
Infolge der Atmosphärenverbindung können beide Dichtelemente einwandfrei funktionieren und eine zuverlässige Abtrennung der benachbarten Bereiche des Taumelscheibenverdichters ist in einfacher Weise umsetzbar. Eine gegenseitige Beeinflussung der Dichtelemente durch Öl bzw. Druckluft wird somit ausgeschlossen.As a result of the atmosphere connection, both sealing elements can function properly and a reliable separation of the adjacent regions of the swash plate compressor can be implemented in a simple manner. A mutual influence of the sealing elements by oil or compressed air is thus excluded.
Vorzugsweise sollte der zwischen beiden Dichtelementen angeordnete Entlüftungskanal ausgehend vom Bereich der Dichtungsanordnung in eine unterhalb des Kolbens angeordneten und mit der Atmosphäre in Verbindung stehenden Ansaugkammer einmünden. DiesePreferably, the venting channel arranged between the two sealing elements should, starting from the region of the sealing arrangement, open into a suction chamber arranged below the piston and communicating with the atmosphere. These
Maßnahme bedingt, dass ein Ansaugen der Druckluft bei dem Taumelscheibenverdichter durch ein im Kolben integriertes Rückschlagventil durchgeführt wird. Hierdurch ergibt sich die Lage der Ansaugkammer unterhalb des Kolbens in einem Bereich des Taumelscheibenverdichters also, der eine kurze Kanalführung des Entlüftungskanals ermöglicht. Denn die Dichtungsanordnung ist in unmittelbarer Nähe zu der Ansaugkammer platziert Ein derart kurzer Entlüftungskanal lässt sich in einfacher Weise durch Bohren herstellen.Measure requires that a suction of the compressed air in the swash plate compressor is performed by a check valve integrated in the piston. This results in the position of the suction chamber below the piston in a region of the swash plate compressor so that allows a short channel guide the vent channel. Because the seal assembly is in close proximity to the suction chamber Such a short venting channel can be easily produced by drilling.
Gemäß einer weiteren die Erfindung verbessernde Maßnahme werden optimale Dichtergebnisse dadurch erreicht, dass das erste Dichtelement zur Ölabdichtung und auch das zweite Dichtelement als Profildichtring mit einer innenradialen Dichtlippe ausgebildet sind. Natürlich lassen sich auch vergleichbare Dichtelemente verwenden, sofern diese eine zuverlässige Abdichtung der axial zueinander bewegbaren Bauteile gewährleisten.According to a further measure improving the invention, optimum sealing results are achieved in that the first sealing element for oil sealing and also the second sealing element are formed as a profiled sealing ring with an inner radial sealing lip. Of course, comparable sealing elements can be used as long as they ensure a reliable sealing of the axially mutually movable components.
Eine weitere, die Dichtwirkung verbessernde Maßnahme besteht darin, dass die aus Stahl bestehende Kolbenstange mit einer Oberfläche versehen ist, welche eine ähnliche Oberflächengüte wie Kolbenstangen von Pneumatikzylindern aufweist, vorzugsweise maximal 4 μm.Another measure improving the sealing effect is that the piston rod made of steel is provided with a surface which has a similar surface quality as piston rods of pneumatic cylinders, preferably a maximum of 4 μm.
Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt:Further measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS. It shows:
Figur 1 einen Längsschnitt durch einen trockenlaufenden Taumelscheibenverdichter, undFigure 1 shows a longitudinal section through a dry-running swash plate compressor, and
Figur 2 eine Detailvergrößerung aus Figur 1 im Bereich einer der Kolbenstangen.2 shows an enlarged detail of Figure 1 in the region of one of the piston rods.
Der in Figur 1 dargestellte trockenlaufende Taumelscheibenverdichter weist seitens des Triebwerkes eine Antriebswelle 1 auf, welche durch einen — hier nicht weiter dargestellten - Motor in Drehbewegung versetzt wird. An der Antriebswelle 1 ist eine Taumelscheibe 2 in an sich bekannter Weise befestigt. Die Taumelscheibe 2 setzt über eine Lageranordnung 3 die Drehbewegung der Antriebswelle 1 in eine oszillierende Hubbewegung um. Die Hubbewegung wird auf eine an der Lageranordnung 3 angebrachten Kolbenstange 4 übertragen. Neben der Kolbenstange 4 sind noch weitere Kolbenstangen mit zugeordneten Lageranordnungen vorhanden; die nachfolgende Beschreibung ist also exemplarisch zu verstehen. Die Kolbenstange 4 leitet die aufgrund der Drehung der Taumelscheibe 2 erzeugte Hin- und Herbewegung an einen Kolben 5 weiter, welcher an dem der Lageranordnung 3 gegenüberliegenden Ende der Kolbenstange 4 koaxial befestigt ist. Der Kolben 5 läuft innerhalb eines zugeordneten Zylinders 6, in welchem die Druckluft aufgrund der Bewegung des Kolbens 5 erzeugt wird. Eine Ansaugung von Luft aus der Atmosphäre erfolgt durch den Kolben hindurch, welcher zu diesem Zwecke eine Rückschlagventileinrichtung 7 besitzt. Die komprimierte Druckluft verlässt den Zylinder 6 über eine weitere entsprechend geschaltete Rückschlagventileinrichtung 8 am Zylinderkopf 9, die an das Ventilgehäuse 10 angebracht ist.The dry running swash plate compressor shown in Figure 1 has on the part of the engine to a drive shaft 1, which is offset by a - not shown here - engine in rotary motion. On the drive shaft 1, a swash plate 2 is fixed in a conventional manner. The swash plate 2 is about a bearing assembly 3, the rotational movement of the drive shaft 1 in an oscillating stroke movement. The lifting movement is transmitted to a mounted on the bearing assembly 3 piston rod 4. In addition to the piston rod 4 are still more piston rods associated with Bearing arrangements available; The following description is thus to be understood as an example. The piston rod 4 forwards the reciprocating motion generated due to the rotation of the swash plate 2 to a piston 5 which is coaxially fixed to the end of the piston rod 4 opposite the bearing assembly 3. The piston 5 runs within an associated cylinder 6, in which the compressed air is generated due to the movement of the piston 5. A suction of air from the atmosphere takes place through the piston, which has a check valve device 7 for this purpose. The compressed compressed air leaves the cylinder 6 via a further correspondingly connected check valve device 8 on the cylinder head 9, which is attached to the valve housing 10.
Die axiale Führung der Kolbenstange 4 erfolgt über eine ortsfest zum Verdichtergehäuse 10 angeordnete Lagerbohrung 11.The axial guidance of the piston rod 4 via a stationary to the compressor housing 10 arranged bearing bore eleventh
Wie im einzelnen aus Figur 2 ersichtlich ist, ist die Lagerbohrung 11 im Bereich des derAs can be seen in detail from Figure 2, the bearing bore 11 in the region of the
Taumelscheibe 2 zugewandeten Endes mit einer ersten Gleitlagerbuchse 12 ausgestattet. Die Gleitlagerbuchse 12 ist über Mittel zur Ölversorgung schmierbar. Die Mittel zur Ölversorgung der schmierbaren Gleitlagerbuchse 12 bestehen aus einem Ölkanal 13 zur Zuführung von Öl zu der schmierbaren Gleitlagerbuchse 12 ausgehend von einem Ölreservoir 14, welches im Bereich des Ventilgehäuses 10 angeordnet ist und über den Schmierkreislauf des Taumelscheibenverdichters wiederbefüllbar ist. Die schmierbare Gleitlagerbuchse 12 besteht aus einer Kupfer-Blei-Legierung.Swash plate 2 facing end equipped with a first plain bearing bush 12. The plain bearing bush 12 is lubricated by oil supply means. The means for supplying oil to the lubricious plain bearing bush 12 consist of an oil passage 13 for supplying oil to the lubricious slide bearing bushing 12, starting from an oil reservoir 14, which is arranged in the region of the valve housing 10 and can be refilled via the lubrication circuit of the swash plate compressor. The lubricious plain bearing bush 12 is made of a copper-lead alloy.
Außerdem ist die Lagerbohrung 11 im Bereich des dem Kolben 5 zugewandten Endes mit einer zweiten, trockenlauffähigen Gleitlagerbuchse 15 ausgestattet. Die trockenlauffähige Gleitlagerbuchse 15 besitzt hier eine Gleitlagerschicht aus PTFE.In addition, the bearing bore 11 is provided in the region of the end facing the piston 5 with a second, dry-running plain bearing bush 15. The dry-running plain bearing bush 15 here has a sliding bearing layer made of PTFE.
Der Druckluft enthaltende Zylinder 6 ist gegenüber des die Taumelscheibe 2 umfassenden Triebwerks mit einer Dichtungsanordnung abgedichtet, welche zwischen der zweiten trockenlauffähigen Gleitlagerbuchse 15 und dem Innenraum des Zylinders 2 dichtend auf die Kolbenstange 4 wirkt.The compressed air-containing cylinder 6 is sealed with respect to the swash plate 2 comprising the engine with a sealing arrangement which between the second dry-running plain bearing bush 15 and the interior of the cylinder 2 sealingly acts on the piston rod 4.
Die Dichtungsanordnung besteht hier aus einem ersten Dichtelement 16 zur Ölabdichtung, welches insoweit benachbart zu der zweiten trockenlaufenden Gleitlagerbuchse 15 angeordnet ist und ein Eindringen von dem der ersten Gleitlagerbuchse 12 zugeführten Öl infolge der Hin- und Herbewegung der Kolbenstange 4 in den Bereich des Zylinders 2 vermeidet. Benachbart zum ersten Dichtelement 16 ist ein zweites, hierzu axial beabstandet angeordnetes Dichtelement 17 vorgesehen. Das zweite Dichtelement 17 hat die Aufgabe, einen Abfluss von Druckluft aus dem Innenraum des Zylinders 2 zu vermeiden. Zur zuverlässigenThe sealing arrangement here consists of a first sealing element 16 for sealing oil, which is so far adjacent to the second dry-running plain bearing bush 15 and prevents penetration of the first plain bearing bush 12 supplied oil due to the reciprocating motion of the piston rod 4 in the region of the cylinder 2 , Adjacent to the first sealing element 16 is a second, this axially spaced-apart sealing element 17 is provided. The second sealing element 17 has the task of avoiding an outflow of compressed air from the interior of the cylinder 2. To reliable
Medienabtrennung ist der Bereich zwischen beiden Dichtelementen 16 und 17 über einen Entlüftungskanal 18 mit der Atmosphäre verbunden. Der Entlüftungskanal 18 verläuft konkret ausgehend vom Bereich der Dichtungsanordnung in eine unterhalb des Kolbens 5 vorgesehene und mit der Atmosphäre in Verbindung stehende Ansaugkammer 19 zur Verbesserung der Dichtwirkung zwischen den als Profildichtring ausgebildetenMedia separation is the area between the two sealing elements 16 and 17 connected via a vent channel 18 with the atmosphere. Concretely, the venting channel 18, starting from the region of the sealing arrangement, extends into a suction chamber 19 provided below the piston 5 and communicating with the atmosphere for improving the sealing action between the profiled sealing rings
Dichtelementen 16 und 17 und der Kolbenstange 4 besteht letztere aus Stahl mit einer polierten Oberfläche, welche in ihrer Oberflächengüte der Oberfläche eines Pneumatikzylinders entspricht.Sealing elements 16 and 17 and the piston rod 4, the latter consists of steel with a polished surface, which corresponds in its surface quality of the surface of a pneumatic cylinder.
Die vorliegende Erfindung ist nicht beschränkt auf das vorstehend beschriebene bevorzugte Ausführungsbeispiel. Es sind vielmehr auch Abwandlungen hiervor denkbar, die vom Schutzbereich der nachfolgenden Ansprüche umfasst sind. So ist es auch möglich, erforderlichenfalls weitere Gleitlagerbuchsen in der Lagerbohrung für die Kolbenstange unterzubringen oder diese mit einer durchgängigen Gleitlagerbuchse mit unterschiedlichen Funktionsbereichen entsprechend dieser Erfindung zu versehen. BezugszeichenlisteThe present invention is not limited to the preferred embodiment described above. On the contrary, modifications are also conceivable which are encompassed by the scope of protection of the following claims. So it is also possible, if necessary, to accommodate further plain bearing bushes in the bearing bore for the piston rod or to provide them with a continuous plain bearing bush with different functional areas according to this invention. LIST OF REFERENCE NUMBERS
1 Antriebswelle1 drive shaft
2 Taumelscheibe2 swash plate
3 Lageranordnung3 bearing arrangement
4 Kolbenstange4 piston rod
5 Kolben5 pistons
6 Zylinder6 cylinders
7 Rückschlagventileinrichtung7 check valve device
8 Rückschlagventileinrichtung8 check valve device
9 Zylinderkopf9 cylinder head
10 Verdichtergehäuse10 compressor housing
11 Lagerbohrung11 bearing bore
12 Gleitlagerbuchse12 plain bearing bush
13 Ölkanal13 oil channel
14 Ölreservoir14 oil reservoir
15 Gleitlagerbuchse15 plain bearing bush
16 Dichtelement16 sealing element
17 Dichtelement17 sealing element
18 Entlüftungskanal18 ventilation duct
19 Ansaugkammer 19 suction chamber

Claims

A n s p r tt c h e A nspr tt che
1. Trockenlaufender Verdichter, insbesondere Taumelscheibenverdichter, mit mindestens einer axial bewegbaren antreibenden Kolbenstange (4), welche die Antriebskraft an in einem zugeordneten Zylinder (6) laufenden Kolben (5) zur Erzeugung der Druckluft weiterleitet, wobei die axial bewegbare Kolbenstange (4) über eine ortsfest zum Verdichtergehäuse (10) angeordnete Lagerbohrung (11) geführt ist, dadurch gekennzeichnet, dass die Lagerbohrung (11) im Bereich des der Taumelscheibe (2) zugewandten Endes mit einer ersten schmierbaren Gleitlagerbuchse (12) ausgestattet ist, welche mit Mitteln zur Ölversorgung in Verbindung steht, und dass die Lagerbohrung (11) im Bereich des dem Kolben (5) zugewandten Endes mit einer zweiten Gleitlagerbuchse (15) ausgestattet ist.1. Dry running compressor, in particular swash plate compressor, with at least one axially movable driving piston rod (4), which transmits the driving force in an associated cylinder (6) running piston (5) for generating the compressed air, wherein the axially movable piston rod (4) via a stationary to the compressor housing (10) arranged bearing bore (11) is guided, characterized in that the bearing bore (11) in the region of the swash plate (2) end facing with a first lubricious slide bearing bush (12) is provided, which means for oil supply is in communication, and that the bearing bore (11) in the region of the piston (5) facing the end with a second plain bearing bush (15) is equipped.
2. Trockenlaufender Verdichter nach Anspruch 1 , dadurch gekennzeichnet, dass die zweite Gleitlagerbuchse (15) nach Art einer trockenlauffähigen Gleitlagerbuchse ausgeführt ist.2. Dry running compressor according to claim 1, characterized in that the second plain bearing bush (15) is designed in the manner of a dry-running plain bearing bush.
3. Trockenlaufender Verdichter nach Anspruch 1 , dadurch gekennzeichnet, dass die Mittel zur Ölversorgung einen Ölkanal (13) zur Zuführung von Öl ausgehend von einem wiederbefüllbaren Ölreservoir (14) im Verdichtergehäuse (10) an die erste Gleitlagerbuchse (12) umfassen.3. Dry running compressor according to claim 1, characterized in that the means for oil supply comprise an oil passage (13) for supplying oil from a refillable oil reservoir (14) in the compressor housing (10) to the first plain bearing bush (12).
4. Trockenlaufender Verdichter nach Anspruch 1 , dadurch gekennzeichnet, dass die erste Gleitlagerbuchse (12) nach Art einer Mehrstoffbuchse ausgeführt ist.4. Dry running compressor according to claim 1, characterized in that the first plain bearing bush (12) is designed in the manner of a multi-material bushing.
5. Trockenlaufender Verdichter nach Anspruch 2, dadurch gekennzeichnet, dass die Gleitlagerschicht der zweiten, trockenlauffähigen Gleitlagerbuchse (15) als PTFE-Beschichtung ausgeführt ist. 5. Dry running compressor according to claim 2, characterized in that the plain bearing layer of the second, dry-running plain bearing bush (15) is designed as a PTFE coating.
6. Trockenlaufender Verdichter nach Anspruch 2, dadurch gekennzeichnet, dass auf der Kolbenstange (4) mindestens ein Dichtrinng an der dem Innenraum des Zylinders (6) zugewandten Seite der trockenlauffähigen Gleitlagerbuchse (15) vorgesehen ist.6. Dry running compressor according to claim 2, characterized in that on the piston rod (4) at least one Dichtrinng on the interior of the cylinder (6) facing side of the dry-running plain bearing bush (15) is provided.
7. Trockenlaufender Verdichter nach Anspruch 2, dadurch gekennzeichnet, dass zur Abdichtung der Grenzstelle zwischen dem Druckluft enthaltenden Zylinder (6) und dem die Taumelscheibe (2) umfassenden Triebwerk eine zwischen der zweiten trockenlauffähigen Gleitlagerbuchse (15) und dem Innenraum des Zylinders (2) auf die Kolbenstange (4) wirkende Dichtungsanordnung vorgesehen ist.7. Dry running compressor according to claim 2, characterized in that for sealing the boundary point between the compressed air cylinder (6) and the swash plate (2) comprising an engine between the second dry-run plain bearing bush (15) and the interior of the cylinder (2). is provided on the piston rod (4) acting sealing arrangement.
8. Trockenlaufender Verdichter nach Anspruch 7, dadurch gekennzeichnet, dass die Dichtungsanordnung aus einem ersten Dichtelement (16) zur Ölabdichtung besteht, das benachbart zu der zweiten trockenlauffähigen Gleitlagerbuchse (15) angeordnet ist und das mit einem zweiten hierzu axial beäbstandeten Dichtelement (17) zur Druckluftabdichtung zusammenwirkt, das benachbart zum Innenraum des Zylinders (2) angeordnet ist, wobei der Bereich zwischen beiden Dichtelementen (16, 17) über einen Entlüftungskanal (18) mit der Atmosphäre in Verbindung steht.8. Dry running compressor according to claim 7, characterized in that the sealing arrangement consists of a first sealing element (16) for oil sealing, which is adjacent to the second dry-run plain bearing bush (15) and arranged with a second axially thereto beäbichteteten sealing element (17) Compressed air seal cooperates, which is adjacent to the interior of the cylinder (2), wherein the area between the two sealing elements (16, 17) via a vent channel (18) communicates with the atmosphere.
9. Trockenlaufender Verdichter nach Anspruch 8, dadurch gekennzeichnet, dass der Entlüftungskanal (18) ausgehend vom Bereich der Dichtungsanordnung in eine unterhalb des Kolbens (5) angeordneten und mit der Atmosphäre in Verbindung stehenden Ansaugkammer (19) einmündet.9. Dry running compressor according to claim 8, characterized in that the venting channel (18), starting from the region of the sealing arrangement into a below the piston (5) and arranged in communication with the atmosphere suction chamber (19) opens.
10. Trockenlaufender Verdichter nach Anspruch 8, dadurch gekennzeichnet, dass das erste Dichtelement (16) zur Ölabdichtung nach Art eines Profildichtrings mit innenradialer Dichtlippe ausgebildet ist. 10. Dry running compressor according to claim 8, characterized in that the first sealing element (16) is designed for oil sealing in the manner of a profile sealing ring with inner radial sealing lip.
11. Trockenlaufender Verdichter nach Anspruch 8, dadurch gekennzeichnet, dass das zweite Dichtelement (17) zur Druckluftabdichtung ebenfalls nach Art eines Profildichtrings mit innenradialer Dichtlippe ausgebildet ist.11. Dry running compressor according to claim 8, characterized in that the second sealing element (17) for compressed air sealing is also formed in the manner of a profile sealing ring with inner radial sealing lip.
12. Trockenlaufender Verdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Kolbenstange (4) aus Stahl besteht und eine durchschnittliche Oberflächenrauheit von maximal 4 μm aufweist.12. Dry running compressor according to one of the preceding claims, characterized in that the piston rod (4) consists of steel and has an average surface roughness of not more than 4 microns.
13. Trockenlaufender Verdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass dieser als Taumelscheibenverdichter ausgebildet ist und mit einer an einer Antriebswelle (1) befestigten Taumelscheibe (2) und über eine Lageranordnung13. Dry running compressor according to one of the preceding claims, characterized in that it is designed as a swash plate compressor and with a on a drive shaft (1) fixed swash plate (2) and a bearing assembly
(3) die antreibende Drehbewegung in eine oszillierende Hubbewegung für die Kolbenstange(3) The driving rotary motion into an oscillating stroke motion for the piston rod
(4) umsetzt. (4) implements.
EP05819263A 2004-12-20 2005-12-16 Dry-running swash plate compressor with a piston-rod mounting Not-in-force EP1831552B1 (en)

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DE102004061233A DE102004061233B3 (en) 2004-12-20 2004-12-20 Dry running compressor, in particular swash plate compressor, with a piston rod storage
PCT/EP2005/013604 WO2006066830A1 (en) 2004-12-20 2005-12-16 Dry-running compressor, particularly a swash-plate compressor, with a piston-rod mounting

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JP4505482B2 (en) * 2007-06-27 2010-07-21 カルソニックカンセイ株式会社 Compressor
DE102009044930A1 (en) * 2009-09-24 2011-04-07 Ernst Beck Pneumatic motor
DE102017102028A1 (en) 2017-02-02 2018-08-02 Nidec Gpm Gmbh Device for guiding a power transmission element
CN107829910B (en) * 2017-11-07 2019-12-03 蚌埠高科瑞力压缩机有限公司 A kind of piston compressor spiral fixed fastening-connecting device
CN107882715B (en) * 2017-11-07 2020-06-26 蚌埠高科瑞力压缩机有限公司 Fastening device with overhead telescopic crosshead part
DE102020112664A1 (en) 2020-05-11 2021-11-11 OET GmbH Reciprocating compressor for generating oil-free compressed air

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2184186A5 (en) * 1972-05-10 1973-12-21 Thomson Csf
DE19501220A1 (en) * 1995-01-17 1996-07-18 Knorr Bremse Systeme compressor
DE19706066A1 (en) * 1997-02-17 1997-11-20 Hans Dipl Ing Unger Compressor providing compressed air in vehicle
DE19922511B4 (en) * 1998-05-18 2004-07-08 Lg Electronics Inc. Oil circulation structure for a linear compressor
DE19847159C2 (en) * 1998-10-13 2001-12-06 Hans Unger Compressor for generating oil-free compressed air
EP1273799A1 (en) * 2001-06-27 2003-01-08 Zexel Valeo Climate Control Corporation A piston guide means for a compressor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006066830A1 *

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EP1831552B1 (en) 2009-04-29

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