EP1831553B1 - Dry-running swash-plate compressor with an antifriction bearing-mounted swash-plate - Google Patents

Dry-running swash-plate compressor with an antifriction bearing-mounted swash-plate Download PDF

Info

Publication number
EP1831553B1
EP1831553B1 EP05850294A EP05850294A EP1831553B1 EP 1831553 B1 EP1831553 B1 EP 1831553B1 EP 05850294 A EP05850294 A EP 05850294A EP 05850294 A EP05850294 A EP 05850294A EP 1831553 B1 EP1831553 B1 EP 1831553B1
Authority
EP
European Patent Office
Prior art keywords
swash
bearing
plate
dry
running
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.)
Not-in-force
Application number
EP05850294A
Other languages
German (de)
French (fr)
Other versions
EP1831553A1 (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
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH, Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP1831553A1 publication Critical patent/EP1831553A1/en
Application granted granted Critical
Publication of EP1831553B1 publication Critical patent/EP1831553B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04B27/1054—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
    • 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

Definitions

  • the invention relates to a dry-running swash plate compressor, in particular for compressed air generation in commercial vehicles, with a swash plate attached to a drive shaft, which converts the driving rotary motion into an oscillating lifting movement via a cooperating with the outer radial edge bearing arrangement, the at least one attached to the bearing assembly piston rod in a assigned cylinder running piston for generating the compressed air forwards.
  • 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.
  • oil passes through the pistons of the compressor in the generated compressed air.
  • significant quantities of oil can enter the environment via the compressed air, namely via various vents in the compressed air 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 deposits itself within the interior of the cylinder in the compressor and downstream compressed air devices and influences there very sustainably their life.
  • 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 attachment of the swash plate to the drive shaft is usually via a hub-shaft connection or by shrinking the central bore having a swash plate on the drive shaft.
  • the connection is detachable for repair purposes.
  • there is an insoluble compound insoluble compound.
  • a compressor with the features according to the preamble of claim 1 is made JP 10-159723 A known.
  • a critical issue in the prior design of the swashplate compressor engine is the design of the bearing assembly cooperating with the outer radial edge region of the swashplate. Because of the relative movement of the swash plate against the hemispheres of the bearing assembly here is a particularly high friction stress, which has previously been reduced by lubricating measures to a tolerable level. In particular, as a result of the startup caused by a start of the drive shaft from jerking movements, the bearing assembly is also heavily loaded. The bearing assembly is also exposed to heavy loads when the piston perform their working movements against a high back pressure.
  • the invention includes the technical teaching that the swash plate is secured via at least one axial and radial forces receiving rolling bearing on the drive shaft, which is arranged coaxially with the swash plate, so that the swash plate is rotatable about its longitudinal axis about the drive shaft wherein the at least one rolling bearing lubricated by spray oil emerging from spray oil openings in the region of the engine-side housing in the direction of the swash plate.
  • the advantage of the solution according to the invention consists, in particular, in that a more favorable distribution of forces of the driving force towards the bearing arrangement is realized via the roller bearing. Jerk movements of the drive shaft are compensated by a corresponding pivoting of the relative position of the swash plate to the drive shaft. This results in less friction on the cooperating with the outer radial edge region of the swash plate bearing assembly, which ultimately leads to less heat. This forms the precondition for the fact that the compressor according to the invention is no longer drivable only by the powerful vehicle engine, but also by a separate auxiliary engine or by a drive energy branched off from the drive train.
  • the rolling bearing is designed in the manner of a deep groove ball bearing.
  • the deep groove ball bearing can absorb both axial and radial forces and thus ensures a particularly compact design for the rolling bearing.
  • the rolling bearing from a combination of a radial bearing with a thrust bearing.
  • This separate storage proves to be considerably cheaper compared to a deep groove ball bearing.
  • such a bearing combination is more robust, so that a longer life can be achieved.
  • an axial bearing for such a combined roller bearing for example, an axial ball bearing is suitable.
  • other suitable thrust bearings are used.
  • the at least one roller bearing is lubricated via a running through the drive shaft to the rolling bearing pressure oil supply. This requires that pass through the drive shaft corresponding oil channels.
  • the at least one rolling bearing is lubricated by spray oil, which exits, for example, from the point of entry of the drive shaft into the compressed-air-side guide bore in the housing.
  • form at least one rolling bearing between the drive shaft and swash plate as a permanently lubricated roller bearing.
  • the Indian FIG. 1 shown dry-running swash plate compressor 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 drive shaft 1 On the drive shaft 1 is a swash plate 2 via a - not visible here - fixed bearings.
  • the swash plate 2 is about a bearing assembly 3, the rotational movement of a drive shaft 1 in an oscillating stroke movement.
  • the lifting movement is attached to a on the bearing assembly 3 Transfer piston rod 4.
  • piston rod 4 further piston rods with associated bearing arrangements are 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 fixed coaxially to the end of the piston rod 4 opposite the bearing assembly 3.
  • the piston 5 runs within an associated cylinder, 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 5, which has a check valve assembly 7 for this purpose.
  • the compressed air leaves the cylinder 6 via a further correspondingly designed check valve assembly 8 on the cylinder piston 9, the housing 10 is attached to the valve. Via a guide bore 11, the piston rod 4 is guided axially relative to the compressor housing 10.
  • the swash plate 2 is fixed by means of a deep groove ball bearing 12 designed rolling bearing, which is arranged coaxially with the swash plate 2 and ensures a so-called four-point storage.
  • the swash plate 2 is rotatable about the drive shaft 1 along its longitudinal axis.
  • the deep groove ball bearing 12 is lubricated by a through the drive shaft 1 to the deep groove ball bearing 12 extending pressure oil supply 15.
  • the rolling bearing between the drive shaft 1 and swash plate 2 consists of a combination of a radial bearing 13 with a thrust bearing 14.
  • the radial bearing 13 is formed here in the manner of a ball bearing
  • the thrust bearing 14 is formed in the manner of a thrust ball bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Drying Of Solid Materials (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 fastened to a drive shaft (1) and which, via a bearing arrangement (3) interacting with the outer radial edge area, converts the driving rotational motion into a reciprocating motion that displaces the 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 swash-plate (2) is fastened to the drive shaft (1) via at least one antifriction bearing, which absorbs axial and radial forces and which is mounted coaxial to the swash-plate (2) so that the swash-plate (2) can rotate about the drive shaft (1) along the longitudinal axis.

Description

Die Erfindung betrifft einen trockenlaufenden Taumelscheibenverdichter, insbesondere zur Drucklufterzeugung in Nutzfahrzeugen, mit einer an einer Antriebswelle befestigten Taumelscheibe, die über eine mit dem außenradialen Randbereich zusammenwirkende Lageranordnung die antreibende Drehbewegung in eine oszillierende Hubbewegung umsetzt, die mindestens eine an der Lageranordnung angebrachte Kolbenstange an in einem zugeordneten Zylinder laufenden Kolben zur Erzeugung der Druckluft weiterleitet.The invention relates to a dry-running swash plate compressor, in particular for compressed air generation in commercial vehicles, with a swash plate attached to a drive shaft, which converts the driving rotary motion into an oscillating lifting movement via a cooperating with the outer radial edge bearing arrangement, the at least one attached to the bearing assembly piston rod in a assigned cylinder running piston for generating the compressed air forwards.

Das Einsatzgebiet eines derartigen Taumelscheibenverdichters erstreckt sich vornehmlich auf die Nutzfahrzeugtechnik. In Nutzfahrzeugen kommen Verdichter zum Einsatz, welche meist direkt über den Motor des Nutzfahrzeuges angetrieben werden und Druckluft zur Speisung des Druckluft-Bordnetzes liefern. Bei Nutzfahrzeugen wird die so erzeugte Druckluft beispielsweise zum Betrieb einer Druckluft-Bremsanlage genutzt.The field of application of such a swash plate compressor extends primarily to commercial vehicle technology. In commercial vehicles come compressors are used, which are usually driven directly by the engine of the commercial vehicle and supply compressed air to feed the compressed air electrical 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 die Umwelt gelangen, nämlich über diverse Entlüftungsöffnungen 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.In 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 quantities of oil can enter the environment via the compressed air, namely via various vents in the compressed air 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 deposits itself within the interior of the cylinder in the compressor and downstream compressed air devices and influences there very sustainably 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.From the EP 0 859 151 A2 goes out a compressor for compressed air generation in commercial vehicles, which solves this problem in that the compressor is designed here largely dry running. 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 Befestigung der Taumelscheibe an der Antriebswelle erfolgt gewöhnlich über eine Nabe-Welle-Verbindung oder durch Aufschrumpfen der eine zentrale Bohrung aufweisenden Taumelscheibe auf die Antriebswelle. Ersterenfalls ist die Verbindung zu Reparaturzwecken lösbar. Letzerenfalls liegt eine unlösbare Verbindung vor. Stets erfolgt beim Stand der Technik jedoch eine ortsfeste Befestigung der Taumelscheibe gegenüber der Antriebswelle.The attachment of the swash plate to the drive shaft is usually via a hub-shaft connection or by shrinking the central bore having a swash plate on the drive shaft. In the first case, the connection is detachable for repair purposes. In the latter case, there is an insoluble compound. Always done in the prior art, however, a fixed attachment of the swash plate against the drive shaft.

Ein Verdichter mit den Merkmalen gemäß dem Oberbegriff von Anspruch 1 ist aus JP 10-159723 A bekannt.A compressor with the features according to the preamble of claim 1 is made JP 10-159723 A known.

Ein kritischer Punkt bei der bekannten Konstruktion des Triebwerks eines Taumelscheibenverdichters besteht in der Gestaltung der mit dem außenradialen Randbereich der Taumelscheibe zusammenwirkenden Lageranordnung. Wegen der relativen Bewegung der Taumelscheibe gegenüber den Halbkugeln der Lageranordnung entsteht hier eine besonders hohe Reibbeanspruchung, welche bisher durch Schmiermaßnahmen auf ein erträgliches Maß reduziert wird. Insbesondere in Folge der durch einen Anlauf der Antriebswelle aus dem Stillstand hervorgerufenen Ruckbewegungen wird die Lageranordnung zusätzlich stark belastet. Die Lageranordnung ist außerdem starken Belastungen dann ausgesetzt, wenn die Kolben ihre Arbeitsbewegungen gegen einen hohen Gegendruck ausführen.A critical issue in the prior design of the swashplate compressor engine is the design of the bearing assembly cooperating with the outer radial edge region of the swashplate. Because of the relative movement of the swash plate against the hemispheres of the bearing assembly here is a particularly high friction stress, which has previously been reduced by lubricating measures to a tolerable level. In particular, as a result of the startup caused by a start of the drive shaft from jerking movements, the bearing assembly is also heavily loaded. The bearing assembly is also exposed to heavy loads when the piston perform their working movements against a high back pressure.

Es ist daher die Aufgabe der vorliegenden Erfindung, die Belastung der Lageranordnung eines Taumelscheibenverdichters der vorstehenden Art zu reduzieren.It is therefore the object of the present invention to reduce the load on the bearing assembly of a swash plate type compressor of the above type.

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, dass die Taumelscheibe über mindestens ein Axial- und Radialkräfte aufnehmendes Wälzlager an der Antriebswelle befestigt ist, das koaxial zur Taumelscheibe angeordnet ist, so dass die Taumelscheibe entlang ihrer Längsachse um die Antriebswelle drehbar ist wobei des mindestens eine Wälzlager über Spritzöl geschmiert ist, das aus Spritzölöffnungen im Bereich des triebwerkseitigen Gehäuses in Richtung der Taumelscheibe austritt.The invention includes the technical teaching that the swash plate is secured via at least one axial and radial forces receiving rolling bearing on the drive shaft, which is arranged coaxially with the swash plate, so that the swash plate is rotatable about its longitudinal axis about the drive shaft wherein the at least one rolling bearing lubricated by spray oil emerging from spray oil openings in the region of the engine-side housing in the direction of the swash plate.

Der Vorteil der erfindungsgemäßen Lösung besteht insbesondere darin, dass über das Wälzlager eine günstigere Kräfteverteilung der Antriebskraft hin zu der Lageranordnung realisiert wird. Ruckbewegungen der Antriebswelle werden durch ein entsprechendes Verschwenken der relativen Lage der Taumelscheibe zur Antriebswelle ausgeglichen. Hierdurch entsteht weniger Reibung an der mit dem außenradialen Randbereich der Taumelscheibe zusammenwirkenden Lageranordnung, was letztendlich zu weniger Wärmeentwicklung führt. Das bildet die Voraussetzung dafür, dass der erfindungsgemäße Verdichter nicht mehr nur durch den kräftigen Fahrzeugmotor antreibbar ist, sondern auch durch einen separaten Hilfsmotor oder durch eine vom Antriebsstrang abgezweigte Antriebsenergie.The advantage of the solution according to the invention consists, in particular, in that a more favorable distribution of forces of the driving force towards the bearing arrangement is realized via the roller bearing. Jerk movements of the drive shaft are compensated by a corresponding pivoting of the relative position of the swash plate to the drive shaft. This results in less friction on the cooperating with the outer radial edge region of the swash plate bearing assembly, which ultimately leads to less heat. This forms the precondition for the fact that the compressor according to the invention is no longer drivable only by the powerful vehicle engine, but also by a separate auxiliary engine or by a drive energy branched off from the drive train.

Vorzugsweise ist das Wälzlager nach Art eines Rillenkugellagers ausgebildet. Das Rillenkugellager vermag sowohl axiale als auch radiale Kräfte aufzunehmen und gewährleistet somit eine besonders kompakte Bauform für das Wälzlager.Preferably, the rolling bearing is designed in the manner of a deep groove ball bearing. The deep groove ball bearing can absorb both axial and radial forces and thus ensures a particularly compact design for the rolling bearing.

Alternativ hierzu ist es jedoch auch möglich, das Wälzlager aus einer Kombination eines Radiallagers mit einem Axiallagers zu bilden. Diese getrennte Lagerung erweist sich im Vergleich zu einem Rillenkugellager als erheblich kostengünstiger. Weiterhin ist eine derartige Lagerkombination robuster, so dass eine längere Lebensdauer erzielt werden kann.Alternatively, however, it is also possible to form the rolling bearing from a combination of a radial bearing with a thrust bearing. This separate storage proves to be considerably cheaper compared to a deep groove ball bearing. Furthermore, such a bearing combination is more robust, so that a longer life can be achieved.

Als Axiallager für ein solches kombiniertes Wälzlager eignet sich beispielsweise ein Axialrillenkugellager. Es ist jedoch auch möglich, dass andere geeignete Axiallager zum Einsatz gebracht werden. Als Radiallager eignet sich vornehmlich ein Nadellager, da dieses sich platzsparend mit einem Axiallager kombinieren lässt. Eine Möglichkeit zur Schmierung des Wälzlagers wäre, dass das mindestens eine Wälzlager über eine durch die Antriebswelle zum Wälzlager hin verlaufende Druckölversorgung geschmiert wird. Dies bedingt, dass durch die Antriebswelle entsprechende ölkanäle verlaufen. Erfindungsgemäß wird das mindestens eine Wälzlager über Spritzöl geschmiert, das beispielsweise aus der Eintrittsstelle der Antriebswelle in die druckluftseitige Führungsbohrung im Gehäuse austritt. Ferner ist es auch denkbar, dass mindestens eine Wälzlager zwischen Antriebswelle und Taumelscheibe als dauergeschmiertes Wälzlager auszubilden.As an axial bearing for such a combined roller bearing, for example, an axial ball bearing is suitable. However, it is also possible that other suitable thrust bearings are used. As a radial bearing is primarily a needle roller bearing, since this can be combined to save space with a thrust bearing. One way to lubricate the bearing would be that the at least one roller bearing is lubricated via a running through the drive shaft to the rolling bearing pressure oil supply. This requires that pass through the drive shaft corresponding oil channels. According to the invention, the at least one rolling bearing is lubricated by spray oil, which exits, for example, from the point of entry of the drive shaft into the compressed-air-side guide bore in the housing. Furthermore, it is also conceivable that form at least one rolling bearing between the drive shaft and swash plate as a permanently lubricated roller bearing.

Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt:

Fig.1
einen Längsschnitt durch einen trockenlaufenden Taumelscheibenverdichter,
Fig.2
einen Längsschnitt als Detailvergrößerung im Bereich der Taumelscheiben, und
Fig.3
einen Längsschnitt als Detailvergrößerung im Bereich der Taumelscheiben.
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:
Fig.1
a longitudinal section through a dry-running swash plate compressor,
Fig.2
a longitudinal section as an enlarged detail in the field of swash plates, and
Figure 3
a longitudinal section as an enlargement of detail in the swash plate area.

Der in der Figur 1 dargestellte trockenlaufende Taumelscheibenverdichter weist seitens des Triebwerks eine Antriebswelle 1 auf, welche durch einen - hier nicht weiter dargestellten - Motor in Drehbewegung versetzt wird. An der Antriebswelle 1 ist einen Taumelscheibe 2 über ein - hier nicht erkennbares - Wälzlager befestigt. Die Taumelscheibe 2 setzt über eine Lageranordnung 3 die Drehbewegung einer Antriebswelle 1 in eine oszilierende 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, in welchem die Druckluft aufgrund der Bewegung des Kolbens 5 erzeugt wird. Eine Ansaugung von Luft aus der Atmosphäre erfolgt durch den Kolben 5 hindurch, welcher zu diesem Zwecke eine Rückschlagventilanordnung 7 besitzt. Die komprimierte Luft verlässt den Zylinder 6 über eine weitere entsprechend gestaltete Rückschlagventilanordnung 8 am Zylinderkolben 9, die an das Ventil gehäuse 10 angebracht ist. Über eine Führungsbohrung 11 ist die Kolbenstange 4 axial gegenüber dem Verdichtergehäuse 10 geführt.The Indian FIG. 1 shown dry-running swash plate compressor 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 is a swash plate 2 via a - not visible here - fixed bearings. The swash plate 2 is about a bearing assembly 3, the rotational movement of a drive shaft 1 in an oscillating stroke movement. The lifting movement is attached to a on the bearing assembly 3 Transfer piston rod 4. In addition to the piston rod 4 further piston rods with associated bearing arrangements are 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 fixed coaxially to the end of the piston rod 4 opposite the bearing assembly 3. The piston 5 runs within an associated cylinder, 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 5, which has a check valve assembly 7 for this purpose. The compressed air leaves the cylinder 6 via a further correspondingly designed check valve assembly 8 on the cylinder piston 9, the housing 10 is attached to the valve. Via a guide bore 11, the piston rod 4 is guided axially relative to the compressor housing 10.

Gemäß Fig.2 ist die Taumelscheibe 2 über nach Art eines Rillenkugellagers 12 ausgebildetes Wälzlager befestigt, welches koaxial zur Taumelscheibe 2 angeordnet ist und eine sogenannte Vierpunktlagerung gewährleistet. Hieraus resultiert, dass die Taumelscheibe 2 entlang ihrer Längsachse um die Antriebswelle 1 drehbar ist. Das Rillenkugellager 12 ist über eine durch die Antriebswelle 1 zu dem Rillenkugellager 12 hin verlaufende Druckölversorgung 15 geschmiert.According to Fig.2 the swash plate 2 is fixed by means of a deep groove ball bearing 12 designed rolling bearing, which is arranged coaxially with the swash plate 2 and ensures a so-called four-point storage. As a result, the swash plate 2 is rotatable about the drive shaft 1 along its longitudinal axis. The deep groove ball bearing 12 is lubricated by a through the drive shaft 1 to the deep groove ball bearing 12 extending pressure oil supply 15.

Gemäß der in der Fig.3 schematisch dargestellten Ausfiihrungsform besteht die Wälzlagerung zwischen Antriebswelle 1 und Taumelscheibe 2 aus einer Kombination eines Radiallagers 13 mit einem Axiallager 14. Das Radiallager 13 ist hier nach Art eines Kugellagers ausgebildet, wogegen das Axiallager 14 nach Art eines Axialrillenkugellagers ausgebildet ist.According to the in the Figure 3 schematically illustrated embodiment, the rolling bearing between the drive shaft 1 and swash plate 2 consists of a combination of a radial bearing 13 with a thrust bearing 14. The radial bearing 13 is formed here in the manner of a ball bearing, whereas the thrust bearing 14 is formed in the manner of a thrust ball bearing.

Die Erfindung beschränkt sich nicht auf die vorstehend beschriebenen beiden bevorzugten Ausführungsbeispiele. Es sind vielmehr auch Abwandlungen hiervon denkbar, die vom Schutzbereich der nachfolgenden Ansprüche umfasst sind. So ist es beispielsweise auch denkbar, die Wälzlagerung der Taumelscheibe an der Antriebswelle über andere Wälzlagertypen durchzuführen, solange die an dieser Stelle auftretenden Axial- und Radialkräfte hierdurch ausreichend abgefangen werden.The invention is not limited to the two preferred embodiments described above. On the contrary, modifications are conceivable which are encompassed by the scope of protection of the following claims. Thus, it is also conceivable, for example, to carry out the rolling bearing of the swash plate on the drive shaft via other types of rolling bearings, as long as the axial and radial forces occurring at this point are thereby adequately intercepted.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Antriebswelledrive shaft
22
Taumelscheibeswash plate
33
Lageranordnungbearing arrangement
44
Kolbenstangepiston rod
55
Kolbenpiston
66
Zylindercylinder
77
RückschlagventileinrichtungCheck valve means
88th
RückschlagventileinrichtungCheck valve means
99
Zylinderkopfcylinder head
1010
Gehäusecasing
1111
Führungsbohrungguide bore
1212
RillenkugellagerDeep groove ball bearings
1313
Radiallagerradial bearings
1414
Axiallagerthrust
1515
DruckölversorgungOil supply

Claims (6)

  1. Dry-running swash-plate compressor, in particular for the production of compressed air in commercial vehicles, with a swash-plate (2( attached on a driveshaft (1), which by virtue of a bearing arrangement (3) that co-operates with the outer radial edge area converts the driving rotary movement into an oscillating stroke movement which is passed on by at least one piston rod (4) attached to the bearing arrangement (3) to a piston (5) moving within an associated cylinder (6) for the production of compressed air, the swash-plate (2) being attached to the driveshaft (1) by at least one roller bearing that absorbs axial and radial forces, the said bearing being arranged coaxially with the swash-plate (2) so that the swash-plate (2) can be rotated around the driveshaft (1) along its longitudinal axis, characterised in that the at least one roller bearing is lubricated with sprayed oil which emerges from sprayed oil openings in the area of the housing (10) on the engine side in the direction of the swash-plate (2).
  2. Dry-running swash-plate compressor according to Claim 1,
    characterised in that the roller bearing is made in the manner of a grooved ball bearing (12).
  3. Dry-running swash-plate compressor according to Claim 1,
    characterised in that the roller bearing consists of a combination of a radial bearing (13) with an axial bearing (14).
  4. Dry-running swash-plate compressor according to Claim 3,
    characterised in that the radial bearing (13) is made in the manner of a needle bearing.
  5. Dry-running swash-plate compressor according to Claim 3,
    characterised in that the axial bearing (14) is made in the manner of an axial grooved ball bearing.
  6. Dry-running swash-plate compressor according to Claim 1,
    characterised in that the at least one roller bearing is permanently lubricated.
EP05850294A 2004-12-20 2005-12-16 Dry-running swash-plate compressor with an antifriction bearing-mounted swash-plate Not-in-force EP1831553B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004061235A DE102004061235A1 (en) 2004-12-20 2004-12-20 Dry-running swash plate compressor with a roller bearing swashplate
PCT/EP2005/013605 WO2006066831A1 (en) 2004-12-20 2005-12-16 Dry-running swash-plate compressor with an antifriction bearing-mounted swash-plate

Publications (2)

Publication Number Publication Date
EP1831553A1 EP1831553A1 (en) 2007-09-12
EP1831553B1 true EP1831553B1 (en) 2008-04-23

Family

ID=36127060

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05850294A Not-in-force EP1831553B1 (en) 2004-12-20 2005-12-16 Dry-running swash-plate compressor with an antifriction bearing-mounted swash-plate

Country Status (4)

Country Link
EP (1) EP1831553B1 (en)
AT (1) ATE393313T1 (en)
DE (2) DE102004061235A1 (en)
WO (1) WO2006066831A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014209894A1 (en) * 2014-05-23 2015-11-26 Mahle International Gmbh axial piston
CN114673645A (en) * 2022-03-14 2022-06-28 杭州新亚低温科技有限公司 Wear-resistant high-pressure compressor

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL83276C (en) *
JPH10159723A (en) * 1996-11-26 1998-06-16 Nippon Soken Inc Swash plate compressor
JPH10196525A (en) * 1997-01-09 1998-07-31 Sanden Corp Swash plate compressor
DE19706066A1 (en) * 1997-02-17 1997-11-20 Hans Dipl Ing Unger Compressor providing compressed air in vehicle
JPH10311276A (en) * 1997-05-13 1998-11-24 Zexel Corp Oscillation plate type compressor
DE10250649A1 (en) * 2002-10-30 2004-05-13 Zexel Valeo Compressor Europe Gmbh Axial piston compressor has supporting of swashplate provided by ring bearing which acts axially and radially at same time, with effective bearing planes of ring bearing crossing in relation to one another
US7153105B2 (en) * 2003-04-24 2006-12-26 Haldex Brake Corporation Compressor with swash plate housing inlet port
US20050207905A1 (en) * 2004-03-18 2005-09-22 Koelzer Robert L Fixed angle swash plate compressor

Also Published As

Publication number Publication date
WO2006066831A1 (en) 2006-06-29
ATE393313T1 (en) 2008-05-15
EP1831553A1 (en) 2007-09-12
DE102004061235A1 (en) 2006-07-06
DE502005003880D1 (en) 2008-06-05

Similar Documents

Publication Publication Date Title
WO2006037671A1 (en) Radial piston pump
DE4229069A1 (en) SWASHPLATE-REFRIGERANT COMPRESSOR FOR A COOLING SYSTEM
EP1831552B1 (en) Dry-running swash plate compressor with a piston-rod mounting
DE10063757B4 (en) Pump unit for a hydraulic vehicle brake system
EP1831553B1 (en) Dry-running swash-plate compressor with an antifriction bearing-mounted swash-plate
DE102010042484A1 (en) High pressure pump for a fuel injection device
EP0752530A1 (en) Reciprocating piston machine with swash plate mechanism
EP3615798B1 (en) Compressor device for the delivery of compressed air to a compressed air supply system
EP2662570A1 (en) Vacuum pump
DE102020128210B4 (en) A scroll compressor with a crank pin with an upper recess
EP1831551B1 (en) Dry running swashplate compressor comprising a coated swashplate
DE102017010095B4 (en) Dry-running compressor with engine room through which suction gas flows
DE19806077A1 (en) Rotor bearing for a motor pump unit
DE102008018035A1 (en) High efficiency radial piston pump, includes grooves carrying pressurized oil to form load-relieving hydrostatic sleeve bearing between moving parts
WO2008034808A1 (en) Radial piston pump
DE10222349B4 (en) Axial piston yankee with bearing of the drive shaft in the cylinder head
DE4312053A1 (en) Transmission with a positive displacement pump
EP1315906A1 (en) Piston compressor comprising a crankshaft whose mass is dynamically compensated, in particular for rail vehicles (detachable compensatory mass)
WO2006066833A1 (en) Dry-running piston compressor
WO2011082847A2 (en) Radial piston pump comprising an eccentric bearing, in particular for vehicle brake systems
DE102013221623A1 (en) axial piston
DE102008042380A1 (en) Eccentric drive mechanism for fuel-high pressure pump for engine, has piston operatively connected with rotatably mounted eccentric by sliding bearing element that is tiltably arranged relative to piston
DE102022206073A1 (en) Hydrostatic axial piston machine
DE102018005567A1 (en) Drive device for a motor vehicle, in particular for a motor vehicle
DE102009057387B4 (en) Rotary piston internal combustion engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070720

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 502005003880

Country of ref document: DE

Date of ref document: 20080605

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080803

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080823

ET Fr: translation filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090126

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

BERE Be: lapsed

Owner name: KNORR-BREMSE SYSTEME FUR NUTZFAHRZEUGE G.M.B.H.

Effective date: 20081231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081231

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20091218

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20091221

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20100105

Year of fee payment: 5

Ref country code: GB

Payment date: 20091221

Year of fee payment: 5

Ref country code: IT

Payment date: 20091224

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081216

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081024

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081216

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080423

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091231

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080724

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091231

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20110701

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20101216

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110831

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101216

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110701

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101216

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20151217

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005003880

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170701