EP0090953B1 - Hydraulic axial-piston machine - Google Patents

Hydraulic axial-piston machine Download PDF

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Publication number
EP0090953B1
EP0090953B1 EP83102220A EP83102220A EP0090953B1 EP 0090953 B1 EP0090953 B1 EP 0090953B1 EP 83102220 A EP83102220 A EP 83102220A EP 83102220 A EP83102220 A EP 83102220A EP 0090953 B1 EP0090953 B1 EP 0090953B1
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EP
European Patent Office
Prior art keywords
bearing
axial piston
piston machine
ring
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP83102220A
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German (de)
French (fr)
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EP0090953A2 (en
EP0090953A3 (en
Inventor
Wilhelm Nolden
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.)
PepsiAmericas Inc
Original Assignee
Abex Corp
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Filing date
Publication date
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Publication of EP0090953A2 publication Critical patent/EP0090953A2/en
Publication of EP0090953A3 publication Critical patent/EP0090953A3/en
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Publication of EP0090953B1 publication Critical patent/EP0090953B1/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014Details or component parts
    • F04B1/2064Housings
    • F04B1/2071Bearings for cylinder barrels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014Details or component parts
    • F04B1/2064Housings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00Other material characteristics; Treatment of material
    • F05C2253/12Coating

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • Hydraulic axial piston machines i.e. Pumps or motors are known in a wide variety of designs.
  • Such hydraulic axial piston machines have a permanent place in the drive technology due to the high power density, the possibility of continuously variable gear ratio to adapt to different operating data, a natural overload protection and the relatively large mobility between drive (pump) and drive (motor, cylinder).
  • They have the disadvantage that they generate strong operating noises.
  • the demand for higher capacities and power densities higher pressures, speeds and flow velocities with a reduced construction mass
  • stands in the way of effective noise reduction at the point of origin so that expensive and time-consuming secondary measures (encapsulation and isolated installation) are often necessary to keep the noise pollution bearable .
  • the hydraulic axial piston machines have a large number of different components, which, including the associated transmission lines, form a complicated vibration system with many excitation points, which mutually influence each other and, via complex transmission mechanisms, the vibratory components of such a machine - and that almost all components - cause vibrations in a variety of ways stimulate.
  • Known hydraulic axial piston machines have a housing made of gray cast iron or a light metal alloy, to which the vibrations are transmitted directly, so that the noise is also radiated directly here.
  • the force flow of the excitation forces, i.e. The forces generated during operation lead through the housing and thus cause the direct noise emission to the outside.
  • the invention has for its object to provide a hydraulic axial piston machine according to the preamble of claim 1, which runs quietly and at the same time enables a higher power and power density without the construction mass being increased by additional components.
  • a support frame which essentially consists of the central tube, the distributor and the control floor.
  • the distributor and the control floor are connected to the central pipe in a positive or non-positive manner.
  • the central tube also serves as the bearing for the radial bearing of the cylinder drum.
  • the central tube which is not a component that is visible from the outside - it lies in the housing cap - can be made of a material which is advantageous for its technical task and can be constructed in such a way as is necessary to absorb the forces and to support it.
  • the entire flow of power, which originates from the excitation forces - generated between the piston and the cylinder drum - remains in the distributor, in the central tube, in the control floor and in the swashplate. In addition to the piston and cylinder drum, these are the components through which the power flow takes place. The power flow does not take place through the housing, so that direct noise emission to the outside is prevented.
  • the noise damping is supported by the damping ring.
  • the axial piston pump shown in the drawing has a flange 1 which ensures the connection to the corresponding supply and discharge lines for the hydraulic oil.
  • the flange 1 is connected to a housing 2 by screws.
  • the axial piston machine can advantageously be designed as specified in claim 5.
  • the advantages of plain bearing technology can be exploited without having to accept disadvantages in terms of service life and the like.
  • the floating and freely rotating bearing ensures a correspondingly long service life.
  • the advantages of lower noise generation in relation to rolling bearings can be used in connection with the other measures for noise reduction and damping.
  • the bearing between the swash plate and the control base is constructed in such a way that a damping plate (claim 4) can be used, so that transmission of noise to the outside is suppressed in this area as well.
  • the drive shaft 5 is passed through the distributor 3 and the control plate 6.
  • the drive shaft drives a cylinder drum 7 with a piston 8.
  • the connection between the drive shaft 5 and the cylinder drum 7 takes place via a toothing sleeve 38 made of plastic or similar damping material with an internal and external tooth profile for transmitting the torque.
  • a helical spring 39 ensures a corresponding preload.
  • a housing cap 4 which surrounds the other components of the axial piston pump, is fastened to the housing 2 with the aid of a tensioning band 35 and with the interposition of a sealing ring 37.
  • the sliding shoes 11 are biased against the swash plate 10 by a pressure plate 9.
  • the drive shaft 5 led out of the housing 2 on one side is supported in a slide bearing 52 with corresponding bearing shells and bearing rings.
  • a sealing ring 53 which also rotates, ensures a corresponding seal. It is biased by several springs 56.
  • a pin 55 ensures that the sealing ring 53 also rotates.
  • a cover 54 forms the closure of the housing 2.
  • the actual stator of the axial piston pump is formed by a central tube 41 which is mounted in the housing 2 via two plastic damping rings 57.
  • This central tube 41 practically forms a support frame for absorbing all hydraulic forces, both in the axial and in the radial direction.
  • the central tube serves to support the cylinder drum 7 forming the rotor and a pin ring 42 for guiding the swash plate 10 and for fastening the control base 22, which absorbs the axial forces of the swivel body bearing.
  • the cylinder drum is supported by a freely rotating bearing ring 43 which has a number of radial lubrication bores 48.
  • the cylinder drum 7 is received by a sleeve 45 which is supported axially and radially against the bearing ring 43.
  • the sleeve forms a fit with the outer surface of the cylinder drum 7, which enables a relative axial movement.
  • a relative rotational movement is prevented by a pin 46.
  • Wave springs 47 which generate an axial preload, ensure that the bearing ring 43 runs smoothly.
  • the preload simultaneously forms the static pressure of the cylinder drum 7 on the control plate 6.
  • the freely rotating bearing ring 43 forms an inner lubricating gap Si with the sleeve 45 and an outer lubricating gap Sa with the central tube 41, so that two gaps functionally considered - are connected in series.
  • the mean resulting lateral force of all pistons loaded on the pressure side of the pump runs in the direction of arrow Z (FIG. 6) and loads the bearing ring 43 in the center.
  • the build-up of two heavy-duty hydrodynamic oil pressure films in the Si and Sa columns is supported by pressure oil from the high-pressure side of the pump, which is forced in front of the pressure zone via a flow restrictor.
  • the supply takes place via a supply line 51.
  • the lubrication gap Si is supplied by the radial lubrication holes 48 in the bearing ring 43.
  • appropriately designed lubrication channels 50 are formed on the bead 44 of the sleeve 45, depending on the direction of rotation. As a result, the bearing ring 43 is flooded with splash oil from the pump housing during operation.
  • the bearing ring 43 is supported on the other side against a support ring 49 provided with openings. Due to the flooding of the bearing ring 43 described, a highly loaded hydrodynamic lubricating film also forms in the gap to the support ring 49 during operation.
  • the central tube 41, the pin ring 42, the support ring 49 and the control plate 6 are to be considered as stator parts.
  • the cylinder drum 7 with the sleeve 45 rotate at the pump speed.
  • a drag torque acts on the bearing ring 43 during operation, so that it rotates at about half the pump drive speed under normal operating conditions (approx. 100 ° C.).
  • the swash plate 10 is pivotally mounted so that a variable piston stroke results when pivoted about a corresponding transverse axis.
  • the swash plate 10 is screwed onto a swivel body 12.
  • Lateral guide arms 13 of the swivel body 12 laterally each comprise a sliding block 15 which is rotatably mounted on the two pins 14 of the pin ring 42.
  • the axis of rotation is identical to the transverse or pin axis M-M.
  • the rear of the swivel body 12 has a radius R in the areas L, so that when the swivel body 12 is rotated about the pin axis MM, there is a linear movement of the running plate 16.
  • a frictional engagement occurs between the swivel body 12 and the running plate 16, similar to how a loaded roller rolls on a flat surface, with the only difference that the roller - i.e. swivel body 12 - is fixed in the MM axis here is, and the documents - ie running plate 16 - moves transversely to the axis MM.
  • the swivel body 12 and the running plate 16 are coupled via guide grooves and rollers 17.
  • the movement of the running plate 16 runs vertically.
  • the running plate 16 is in turn supported on two linear roller bearings 18 which roll on fixed plates 19.
  • a cage 20 is used which, like a frame, encompasses the linear roller bearings and secures them in the respective position without play.
  • the running plate 16 runs through twice the distance as the cage 20 or the linear roller bearing 18.
  • the fixed plates 19 rest on damping plates 21 made of plastic, which in turn are arranged in corresponding chambers in the control floor 22.
  • the control base 22 is screwed to the pin ring 42.
  • the pump regulator 24 with the adjusting piston 25 is accommodated in the control base 22.
  • the adjusting piston 25 is designed as a differential piston.
  • a yoke 26 is screwed onto the rod end of the adjusting piston and comprises a bolt 27 in the form of a fork.
  • the bolt is rotatably mounted in a bridge 28.
  • the bridge 28 is screwed to the swivel body 12.
  • control slots 32 and 33 are formed in the control plate, which ensure a connection to the suction line 30 and the pressure line 31, respectively.
  • Sleeves 34 made of plastic represent an acoustic decoupling of the distributor 3 from the housing 2 and therefore contribute to noise reduction.
  • a line 36 is supplied with pressure oil from the pressure side, which in turn supplies the pump regulator 24 and the channel 51 with pressure oil.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Description

Die Erfindung betrifft eine Axialkolbenmaschine nach dem Oberbegriff des Anspruches 1.The invention relates to an axial piston machine according to the preamble of claim 1.

Hydraulische Axialkolbenmaschinen, d.h. Pumpen oder Motoren, sind in der unterschiedlichsten Bauart bekannt. Derartige hydraulische Axialkolbenmaschinen haben aufgrund der hohen Leistungsdichte, der Möglichkeit der stufenlosen Getriebeübersetzung in Anpassung an verschiedene Betriebsdaten, eines natürlichen Überlastungsschutzes und der relativ großen Beweglichkeit zwischen Antrieb (Pumpe) und Abtrieb (Motor, Zylinder) einen festen Platz in der Antriebstechnik. Sie besitzen aber den Nachteil, daß sie starke Betriebsgeräusche erzeugen. Besonders die Forderung nach größeren Leistungen und Leistungsdichten (höheren Drücken, Drehzahlen und Strömungsgeschwindigkeiten bei reduzierter Baumasse) steht einer wirksamen Geräuschminderung an der Entstehungsstelle entgegen, so daß häufig teuere und aufwendige Sekundärmaßnahmen (Kapselung und isolierte Aufstellung) erforderlich sind, um die Geräuschbelästigung erträglich zu halten. Die hydraulischen Axialkolbenmaschinen weisen eine Vielzahl unterschiedlicher Bauteile auf, die einschließlich der dazugehörenden Übertragungsleitungen ein kompliziertes Schwingungssystem mit vielen Erregerstellen bilden, die sich gegenseitig beeinflußen und über komplexe Übertragungsmechanismen die schwingungsfähigen Bauteile einer solchen Maschine - und daß sind fast alle Bauteile - in vielfältiger Weise zu Schwingungen anregen.Hydraulic axial piston machines, i.e. Pumps or motors are known in a wide variety of designs. Such hydraulic axial piston machines have a permanent place in the drive technology due to the high power density, the possibility of continuously variable gear ratio to adapt to different operating data, a natural overload protection and the relatively large mobility between drive (pump) and drive (motor, cylinder). However, they have the disadvantage that they generate strong operating noises. In particular, the demand for higher capacities and power densities (higher pressures, speeds and flow velocities with a reduced construction mass) stands in the way of effective noise reduction at the point of origin, so that expensive and time-consuming secondary measures (encapsulation and isolated installation) are often necessary to keep the noise pollution bearable . The hydraulic axial piston machines have a large number of different components, which, including the associated transmission lines, form a complicated vibration system with many excitation points, which mutually influence each other and, via complex transmission mechanisms, the vibratory components of such a machine - and that almost all components - cause vibrations in a variety of ways stimulate.

Bekannte hydraulische Axialkolbenmaschinen nach dem Oberbegriff weisen ein Gehäuse aus Grauguss oder einer Leichtmetallegierung auf, auf das die Schwingungen unmittelbar übertragen werden, so daß hier auch eine direkte Abstrahlung der Geräusche erfolgt. Der Kraftfluß der Erregerkräfte, d.h. der während des Betriebes erzeugten Kräfte führt durch das Gehäuse und bedingt so die direkte Geräuschabstrahlung nach außen.Known hydraulic axial piston machines according to the preamble have a housing made of gray cast iron or a light metal alloy, to which the vibrations are transmitted directly, so that the noise is also radiated directly here. The force flow of the excitation forces, i.e. The forces generated during operation lead through the housing and thus cause the direct noise emission to the outside.

Der Erfindung liegt nun die Aufgabe zugrunde, eine hydraulische Axialkolbenmaschine nach dem Obergriff des Anspruches 1 zu schaffen, die geräuscharm läuft und dabei gleichzeitig eine höhere Leistung und Leistungsdichte ermöglicht, ohne daß die Baumasse durch zusätzliche Bauteile vergrößert wird.The invention has for its object to provide a hydraulic axial piston machine according to the preamble of claim 1, which runs quietly and at the same time enables a higher power and power density without the construction mass being increased by additional components.

Diese Aufgabe wird durch das Kennzeichen des Anspruches 1 gelöst.This object is achieved by the characterizing part of claim 1.

Erfindungsgemäß wird ein Stützrahmen geschaffen, der im wesentlichen aus dem Zentralrohr, dem Verteiler und dem Steuerboden besteht. Verteiler und Steuerboden sind formschlüssig oder kraftschlüssig mit dem Zentralrohr verbunden. Das Zentralrohr dient auch der Lagerung für das Radiallager der Zylindertrommel. Das Zentralrohr, das kein von außen sichtbares Bauteil ist - es liegt in der Gehäusekappe -, kann aus einem für seine technische Aufgabe vorteilhaften Werkstoff hergestellt und so konstruiert sein, wie es zur Aufnahme der Kräfte und zur Abstützung erforderlich ist. Der gesamte Kraftfluß, der von den Erregerkräften - erzeugt zwischen Kolben und Zylindertrommel - ausgeht, verbleibt im Verteiler, im Zentralrohr, im Steuerboden und in der Schrägscheibe. Dieses sind neben Kolben und Zylindertrommel die Bauteile, durch die der Kraftfluß stattfindet. Der Kraftfluß findet nicht durch das Gehäuse statt, so daß eine direkte Geräuschabstrahlung nach außen verhindert wird. Die Geräuschdämpfung wird noch durch den Dämpfungsring unterstützt.According to the invention, a support frame is created which essentially consists of the central tube, the distributor and the control floor. The distributor and the control floor are connected to the central pipe in a positive or non-positive manner. The central tube also serves as the bearing for the radial bearing of the cylinder drum. The central tube, which is not a component that is visible from the outside - it lies in the housing cap - can be made of a material which is advantageous for its technical task and can be constructed in such a way as is necessary to absorb the forces and to support it. The entire flow of power, which originates from the excitation forces - generated between the piston and the cylinder drum - remains in the distributor, in the central tube, in the control floor and in the swashplate. In addition to the piston and cylinder drum, these are the components through which the power flow takes place. The power flow does not take place through the housing, so that direct noise emission to the outside is prevented. The noise damping is supported by the damping ring.

Im folgenden wird die Erfindung unter Hinweis auf die Zeichnung näher erläutert.The invention is explained in more detail below with reference to the drawing.

Es zeigt:

  • Fig. 1 einen Längsschnitt durch eine Ausführungsform einer Axialkolbenmaschine nach der Erfindung, nämlich durch eine Axialkolbenpumpe;
  • Fig. 2 einen Längsschnitt durch die Axialkolbenpumpe der Fig. 1, jedoch um 90° gedreht;
  • Fig. 3 einen Querschnitt gemäß der Linie A-A der Fig. 1;
  • Fig. 4 einen Schnitt gemäß der Linie B-B der Fig. 2;
  • Fig. 5 eine Ansicht in Richtung des Pfeiles X der Fig. 2;
  • Fig. 6 eine Einzelheit aus dem Schnitt der Fig. 1;
  • Fig. 7 eine Seitenansicht der Darstellung der Fig. 6; und
  • Fig. 8 eine Ansicht, die derjenigen der Fig. 6 entspricht, jedoch die wesentlichen Bauteile im nichtgeschnittenen Zustand zeigt.
It shows:
  • 1 shows a longitudinal section through an embodiment of an axial piston machine according to the invention, namely by an axial piston pump.
  • FIG. 2 shows a longitudinal section through the axial piston pump of FIG. 1, but rotated through 90 °;
  • 3 shows a cross section along the line AA of FIG. 1.
  • 4 shows a section along the line BB of FIG. 2.
  • Fig. 5 is a view in the direction of arrow X of Fig. 2;
  • Fig. 6 shows a detail from the section of Fig. 1;
  • Fig. 7 is a side view of the illustration of Fig. 6; and
  • Fig. 8 is a view corresponding to that of Fig. 6, but showing the essential components in the uncut state.

Die in der Zeichnung dargestellt Axialkolbenpumpe besitzt einen Flansch 1, der für die Verbindung mit den entsprechenden Zu- und Ableitungen für das Hydrauliköl sorgt. Der Flansch 1 ist durch Schrauben mit einem Gehäuse 2 verbunden.The axial piston pump shown in the drawing has a flange 1 which ensures the connection to the corresponding supply and discharge lines for the hydraulic oil. The flange 1 is connected to a housing 2 by screws.

Zusätzlich ist es möglich, in die Leitungen zwischen Verteiler und Gehäuse Hülsen aus Kunststoff einzusetzen, um für eine weitere Geräuschdämpfung zu sorgen. Es besteht kein direkter metallischer Kontakt zwischen der Mechanik der Axialkolbenmaschine und dem Gehäuse. Es findet keine direkte Abstrahlung von Geräuschen an die Umgebung statt.In addition, it is possible to insert plastic sleeves in the lines between the distributor and the housing in order to provide further noise reduction. There is no direct metallic contact between the mechanical parts of the axial piston machine and the housing. There is no direct radiation of noise to the surroundings.

In vorteilhafter Weise kann die Axialkolbenmaschine so ausgebildet sein, wie in Anspruch 5 angegeben. Durch den Einsatz des Lagerringes können die Vorteile der Gleitlager-Technik ausgenutzt werden, ohne daß hierdurch Nachteile hinsichtlich Lebensdauer und dergleichen in Kauf genommen werden müssen. Die schwimmende und frei umlaufende Lagerung sorgt für eine entsprechend hohe Lebensdauer. Die Vorteile der geringeren Geräuscherzeugung im Verhältnis zu Wälzlagern können im Zusammenhang mit den anderen Maßnahmen zur Geräuschverminderung und -dämpfung genutzt werden.The axial piston machine can advantageously be designed as specified in claim 5. By using the bearing ring, the advantages of plain bearing technology can be exploited without having to accept disadvantages in terms of service life and the like. The floating and freely rotating bearing ensures a correspondingly long service life. The advantages of lower noise generation in relation to rolling bearings can be used in connection with the other measures for noise reduction and damping.

Wenn die Axialkolbenmaschine so aufgebaut ist, wie in Anspruch 3 angegeben, dann ist die Lagerung zwischen Schrägscheibe und Steuerboden so konstruiert, daß eine Dämpfungsplatte (Anspruch 4) eingesetzt werden kann, so daß auch in diesem Bereich eine Übertragung von Geräusch nach außen unterdrückt wird.If the axial piston machine is constructed as specified in claim 3, then the bearing between the swash plate and the control base is constructed in such a way that a damping plate (claim 4) can be used, so that transmission of noise to the outside is suppressed in this area as well.

Die grundsätzliche Maßnahme nach Anspruch 1, die bei Axialkolbenmaschinen der unterschiedlichsten Bauart eingesetzt werden kann, wird durch die vorteilhaften Ausgestaltungen nach den Ansprüchen 2 bis 6 je nach Bauart und technischer Anforderung unterstützt.The basic measure according to claim 1, the most varied in axial piston machines Type can be used is supported by the advantageous embodiments according to claims 2 to 6 depending on the type and technical requirements.

In dem Gehäuse 2 ist ein Verteiler 3 befestigt, der auch die Steuerplatte 6 trägt. Durch den Verteiler 3 und die Steuerplatte 6 ist die Antriebswelle 5 hindurchgeführt.A distributor 3, which also carries the control plate 6, is fastened in the housing 2. The drive shaft 5 is passed through the distributor 3 and the control plate 6.

Die Antriebswelle treibt eine Zylindertrommel 7 mit Kolben 8. Die Verbindung zwischen der Antriebswelle 5 und der Zylindertrommel 7 erfolgt über eine Verzahnungshülse 38 aus Kunststoff oder ähnlichem dämpfenden Werkstoff mit einem Innen- und Außenzahnprofil zur Übertrages des Drehmomentes. Für eine entsprechende Vorspannung sorgt eine Schraubenfeder 39.The drive shaft drives a cylinder drum 7 with a piston 8. The connection between the drive shaft 5 and the cylinder drum 7 takes place via a toothing sleeve 38 made of plastic or similar damping material with an internal and external tooth profile for transmitting the torque. A helical spring 39 ensures a corresponding preload.

An dem Gehäuse 2 ist mit Hilfe eines Spannbandes 35 und unter Zwischenschaltung eines Dichtungsringes 37 eine Gehäusekappe 4 befestigt, welche die übrigen Bauteile der Axialkolbenpumpe umgibt. Dieses sind insbesondere die Schrägscheibe 10, an der sich die Gleitschuhe 11 abstützen. Die Gleitschuhe 11 sind durch eine Andrückplatte 9 gegen die Schrägscheibe 10 vorgespannt.A housing cap 4, which surrounds the other components of the axial piston pump, is fastened to the housing 2 with the aid of a tensioning band 35 and with the interposition of a sealing ring 37. These are in particular the swash plate 10 on which the sliding shoes 11 are supported. The sliding shoes 11 are biased against the swash plate 10 by a pressure plate 9.

Die einseitig aus dem Gehäuse 2 herausgeführte Antriebswelle 5 ist in einem Gleitlager 52 mit entsprechenden Lagerschalen und Lagerringen gelagert. Ein Dichtungsring 53, der mitrotiert, sorgt für eine entsprechende Abdichtung. Er wird durch mehrere Federn 56 vorgespannt. Ein Stift 55 stellt sicher, daß sich der Dichtungsring 53 mitdreht. Ein Deckel 54 bilden den Verschluß des Gehäuses 2.The drive shaft 5 led out of the housing 2 on one side is supported in a slide bearing 52 with corresponding bearing shells and bearing rings. A sealing ring 53, which also rotates, ensures a corresponding seal. It is biased by several springs 56. A pin 55 ensures that the sealing ring 53 also rotates. A cover 54 forms the closure of the housing 2.

Der eigentliche Stator der Axialkolbenpumpe wird durch ein Zentralrohr 41 gebildet, das über zwei Dämpfungsringe 57 aus Kunststoff in dem Gehäuse 2 gelagert ist. Dieses Zentralrohr 41 bildet praktisch einen Stützrahmen zur Aufnahme sämtlicher hydraulischer Kräfte, und zwar sowohl in axialer als auch in radialer Richtung. Das Zentralrohr dient der Abstützung der den Rotor bildenden Zylindertrommel 7, und eines Zapfenringes 42 zur Führung der Schrägscheibe 10 sowie zur Befestigung des Steuerbodens 22, welcher die axialen Kräfte der Schwenkkörper-Lagerung aufnimmt.The actual stator of the axial piston pump is formed by a central tube 41 which is mounted in the housing 2 via two plastic damping rings 57. This central tube 41 practically forms a support frame for absorbing all hydraulic forces, both in the axial and in the radial direction. The central tube serves to support the cylinder drum 7 forming the rotor and a pin ring 42 for guiding the swash plate 10 and for fastening the control base 22, which absorbs the axial forces of the swivel body bearing.

Die Abstützung der Zylindertrommel erfolgt über einen frei umlaufenden Lagerring 43, der eine Anzahl radialer Schmierbohrungen 48 aufweist. Die Zylindertrommel 7 wird von einer Hülse 45 aufgenommen, die sich axial und radial gegen den Lagerring 43 abstützt. Die Hülse bildet mit der Außenfläche der Zylindertrommel 7 eine Passung, die eine relative axiale Bewegung ermöglicht. Eine relative Drehbewegung wird durch einen Stift 46 verhindert.The cylinder drum is supported by a freely rotating bearing ring 43 which has a number of radial lubrication bores 48. The cylinder drum 7 is received by a sleeve 45 which is supported axially and radially against the bearing ring 43. The sleeve forms a fit with the outer surface of the cylinder drum 7, which enables a relative axial movement. A relative rotational movement is prevented by a pin 46.

Für den ruhigen Lauf des Lagerringes 43 sorgen Wellenfedern 47, die eine axiale Vorspannung erzeugen. Die Vorspannung bildet gleichzeitig die statische Anpressung der Zylindertrommel 7 an die Steuerplatte 6.Wave springs 47, which generate an axial preload, ensure that the bearing ring 43 runs smoothly. The preload simultaneously forms the static pressure of the cylinder drum 7 on the control plate 6.

Der frei umlaufende Lagerring 43 bildet mit der Hülse 45 einen inneren Schmierspalt Si und mit dem Zentralrohr 41 einen äußeren Schmierspalt Sa, so daß zwei Spaltefunktionstechnich betrachtet - in Reihe geschaltet sind. Die mittlere resultierende Seitenkraft aller auf der Druckseite der Pumpe belasteten Kolben verläuft in Richtung des Pfeiles Z (Fig. 6) und belastet den Lagerring 43 mittig.The freely rotating bearing ring 43 forms an inner lubricating gap Si with the sleeve 45 and an outer lubricating gap Sa with the central tube 41, so that two gaps functionally considered - are connected in series. The mean resulting lateral force of all pistons loaded on the pressure side of the pump runs in the direction of arrow Z (FIG. 6) and loads the bearing ring 43 in the center.

Der Aufbau von zwei hochbelastbaren hydrodynamischen Öldruckfilmen in den Spalten Si und Sa wird unterstützt durch zwangsweise vor der Druckzone über eine Mengendrossel zugeführtes Drucköl von der Hochdruckseite der Pumpe. Die Zuführung geschieht über eine Versorgungsleitung 51. Durch die radialen Schmierbohrungen 48 in dem Lagerring 43 wird der Schmierspalt Si versorgt. Zum Aufbau eines tragfähigen hydrodynamischen Schmierfilms an den Seitenflächen des Lagerringes 43 sind entsprechend ausgebildete, drehrichtungsabhängig geformte Schmierkanäle 50 an dem Wulst 44 der Hülse 45 ausgebildet. Hierdurch wird der Lagerring 43 während des Betriebes mit Planschöl aus dem Pumpengehäuse umflutet.The build-up of two heavy-duty hydrodynamic oil pressure films in the Si and Sa columns is supported by pressure oil from the high-pressure side of the pump, which is forced in front of the pressure zone via a flow restrictor. The supply takes place via a supply line 51. The lubrication gap Si is supplied by the radial lubrication holes 48 in the bearing ring 43. To build a stable hydrodynamic lubricating film on the side surfaces of the bearing ring 43, appropriately designed lubrication channels 50 are formed on the bead 44 of the sleeve 45, depending on the direction of rotation. As a result, the bearing ring 43 is flooded with splash oil from the pump housing during operation.

Die Abstützung des Lagerringes 43 auf der anderen Seite erfolgt gegen einen mit Durchbrüchen versehenen Stützring 49. Bedingt durch die beschriebene Umflutung des Lageringes 43 bildet sich auch im Spalt zu dem Stützring 49 im Betrieb ein hochbelasteter hydrodynamischer Schmierfilm aus.The bearing ring 43 is supported on the other side against a support ring 49 provided with openings. Due to the flooding of the bearing ring 43 described, a highly loaded hydrodynamic lubricating film also forms in the gap to the support ring 49 during operation.

Das Zentralrohr 41, der Zapfenring 42, der Stützring 49 und die Steuerplatte 6 sind als Statorteile zu betrachten. Die Zylindertrommel 7 mit der Hülse 45 drehen sich mit Pumpendrehzahl. Infolge der viskosen Flüssigkeitsreibung in den Schmierspalten Si und Sa wirkt im Betrieb auf den Lagerring 43 ein Schleppmoment, so daß sich dieser bei normalen Betriebsbedingungen (ca. 100° C) etwa mit der halben Pumpenantriebsdrehzahl dreht.The central tube 41, the pin ring 42, the support ring 49 and the control plate 6 are to be considered as stator parts. The cylinder drum 7 with the sleeve 45 rotate at the pump speed. As a result of the viscous fluid friction in the lubrication gaps Si and Sa, a drag torque acts on the bearing ring 43 during operation, so that it rotates at about half the pump drive speed under normal operating conditions (approx. 100 ° C.).

Da es sich bei der veranschaulichten Axialkolbenpumpe um eine solche mit veränderlichem Hubvolumen handelt, ist die Schrägscheibe 10 schwenkbar gelagert, so daß sich bei Schwenkung um eine entsprechende Querachse ein veränderlicher Kolbenhub ergibt. Bei der dargestellten Ausführungsform ist die Schrägscheibe 10 auf einem Schwenkkörper 12 verschraubt. Seitliche Führungsarme 13 des Schwenkkörpers 12 umfassen seitlich jeweils einen auf den beiden Zapfen 14 des Zapfenringes 42 drehbar gelagerten Gleitstein 15. Die Drehachse ist identisch mit der Quer- oder Zapfenachse M-M. Die Rückseite des Schwenkkörpers 12 besitzt in den Bereichen L einen Radius R, so daß sich bei der Drehung des Schwenkkörpers 12 um die Zapfenachse MM eine Linearbewegung der Laufplatte 16 ergibt. Infolge der großen axialen Kolbenkräfte in der Druckzone entsteht zwischen dem Schwenkkörper 12 und der Laufplatte 16 ein Reibschluß, ähnlich wie eine belastete Walze auf einer ebenen Unterlage abrollt, nur mit dem Unterschied, daß hier die Walze - sprich Schwenkkörper 12 - in der Achse M-M fixiert ist, und die Unterlagen - sprich Laufplatte 16 - sich quer zur Achse M-M bewegt. Der Schwenkkörper 12 und die Laufplatte 16 sind über Führungsnuten und -rollen 17 gekoppelt.Since the illustrated axial piston pump is one with a variable stroke volume, the swash plate 10 is pivotally mounted so that a variable piston stroke results when pivoted about a corresponding transverse axis. In the embodiment shown, the swash plate 10 is screwed onto a swivel body 12. Lateral guide arms 13 of the swivel body 12 laterally each comprise a sliding block 15 which is rotatably mounted on the two pins 14 of the pin ring 42. The axis of rotation is identical to the transverse or pin axis M-M. The rear of the swivel body 12 has a radius R in the areas L, so that when the swivel body 12 is rotated about the pin axis MM, there is a linear movement of the running plate 16. As a result of the large axial piston forces in the pressure zone, a frictional engagement occurs between the swivel body 12 and the running plate 16, similar to how a loaded roller rolls on a flat surface, with the only difference that the roller - i.e. swivel body 12 - is fixed in the MM axis here is, and the documents - ie running plate 16 - moves transversely to the axis MM. The swivel body 12 and the running plate 16 are coupled via guide grooves and rollers 17.

Unter Zugrundelegung der Darstellung der Fig. 4 verläuft die Bewegung der Laufplatte 16 in der Vertikalen. Die Laufplatte 16 stützt sich wiederum auf zwei Linearrollenlager 18 ab, die auf Fixplatten 19 abrollen. Zur Lagesicherung der Linearrollenlager 18 dient ein Käfig 20, der wie ein Rahmen die Linearrollenlager umfaßt und spielfrei in der jeweiligen Stellung sichert.Based on the illustration in FIG. 4, the movement of the running plate 16 runs vertically. The running plate 16 is in turn supported on two linear roller bearings 18 which roll on fixed plates 19. To secure the position of the linear roller bearings 18, a cage 20 is used which, like a frame, encompasses the linear roller bearings and secures them in the respective position without play.

Bei Einleitung einer Schwenkbewegung durchläuft die Laufplatte 16 die doppelte Wegstrecke wie der Käfig 20 bzw. die Linearrollenlager 18.When a pivoting movement is initiated, the running plate 16 runs through twice the distance as the cage 20 or the linear roller bearing 18.

Die Fixplatten 19 liegen auf Dämpfungsplatten 21 aus Kunststoff auf, die wiederum in entsprechenden Kammern in dem Steuerboden 22 angeordnet sind. Der Steuerboden 22 ist mit dem Zapfenring 42 verschraubt. Durch entsprechende Berechnung der Steifigkeit der Laufplatte 16, der Fixplatten 19 und der Dämpfungsplatten 21, kann die elastische Durchbiegung dieser gesamten Lagerstelle so beeinflußt werden, daß sich die über eine Linienberührung (Hertz'sche Pressung) zwischen Schwenkkörper 12 und Laufplatte 16 eingeleitete Lagerkraft gleichmäßig auf alle Wälzkörper der Linearrollenlager verteilt. Durch die Dämpfungsplatten 21 aus Kunststoff werden die Betriebsgeräusche und die Schwingungen der Pumpenmechanik vom Steuerboden 22 isoliert.The fixed plates 19 rest on damping plates 21 made of plastic, which in turn are arranged in corresponding chambers in the control floor 22. The control base 22 is screwed to the pin ring 42. By appropriately calculating the rigidity of the running plate 16, the fixed plates 19 and the damping plates 21, the elastic deflection of this entire bearing point can be influenced in such a way that the bearing force introduced via a line contact (Hertzian pressure) between the swivel body 12 and the running plate 16 increases evenly distributed all rolling elements of the linear roller bearings. The operating noises and the vibrations of the pump mechanism are isolated from the control base 22 by the damping plates 21 made of plastic.

Die vom jeweiligen Schwenkwinkel des Schwenkkörpers 12 abhängige Stellung der Laufplatte 16 und des Käfigs 20 mit den beiden Linearrollenlagern 18 wird geometrisch eindeutig bestimmt durch zwei jeweils außen am Käfig 20 angeschraubte, drehbare Laschen 23. Die Laschen sind in den Kopplungspunkten auf Büchsen aus Kunststoff gelagert.The position of the running plate 16 and of the cage 20 with the two linear roller bearings 18, which is dependent on the respective pivoting angle of the pivoting body 12, is geometrically clearly determined by two rotatable tabs 23 screwed on the outside of the cage 20, respectively. The tabs are mounted on plastic bushings in the coupling points.

Im Steuerboden 22 ist der Pumpenregler 24 mit dem Verstellkolben 25 untergebracht. Der Verstellkolben 25 ist als Differentialkolben ausgebildet. Am Stangenende des Verstellkolbens ist ein Joch 26 angeschraubt, das in Form einer Gabel einen Bolzen 27 umfaßt. Der Bolzen ist in einer Brücke 28 drehbar gelagert. Die Brücke 28 ist mit dem Schwenkkörper 12 verschraubt.The pump regulator 24 with the adjusting piston 25 is accommodated in the control base 22. The adjusting piston 25 is designed as a differential piston. A yoke 26 is screwed onto the rod end of the adjusting piston and comprises a bolt 27 in the form of a fork. The bolt is rotatably mounted in a bridge 28. The bridge 28 is screwed to the swivel body 12.

Die druckabhängig vom Pumpenregler 24 geregelte Position des Verstellkolbens 25 wird somit formschlüssig auf den Schwenkkörper 12 übertragen, d.h. einer bestimmten Stellung des Verstellkolbens entspricht ein bestimmter Winkel der Schrägscheibe 10 und damit einem bestimmten Hubvolumen der Pumpe.The position of the adjusting piston 25, which is regulated in a pressure-dependent manner by the pump regulator 24, is thus transferred to the swivel body 12 in a form-fitting manner, i.e. a certain position of the adjusting piston corresponds to a certain angle of the swash plate 10 and thus a certain stroke volume of the pump.

Die Abstützung des Schwenkkörpers 12 über die beschriebene Lagerung mittels Linearrollenlager auf dem Steuerboden 22, in dem auch die komplette Pumpenregler mit Verstellkolben untergebracht ist, ergibt infolge der Verschraubung mit dem Zapfenring 42 und dem Zentralrohr 41 eine äußerst kompakte, steife und damit schwingungsarme Konstruktion, die auch insbesondere hinsichtlich der Geräuschemission erhebliche Vorteile bildet.The support of the swivel body 12 via the described bearing by means of linear roller bearings on the control base 22, in which the complete pump regulator with adjusting piston is accommodated, results in an extremely compact, rigid and thus low-vibration construction due to the screw connection with the journal ring 42 and the central tube 41 also forms considerable advantages, particularly with regard to noise emission.

Wie beim Betrachten der Fig. 3 deutlich wird, sind in der Steuerplatte 6 Steuerschlitze 32 und 33 ausgebildet, die für eine Verbindung mit der Saugleitung 30 bzw. der Druckleitung 31 sorgen. Hülsen 34 aus Kunststoff stellen eine schalltechnische Abkoppelung des Verteilers 3 vom Gehäuse 2 dar und tragen deshalb zur Geräuschdämpfung bei. Von der Druckseite wird eine Leitung 36 mit Drucköl versorgt, die wiederum den Pumpenregler 24 als auch den Kanal 51 mit Drucköl versorgt.As is clear when looking at FIG. 3, 6 control slots 32 and 33 are formed in the control plate, which ensure a connection to the suction line 30 and the pressure line 31, respectively. Sleeves 34 made of plastic represent an acoustic decoupling of the distributor 3 from the housing 2 and therefore contribute to noise reduction. A line 36 is supplied with pressure oil from the pressure side, which in turn supplies the pump regulator 24 and the channel 51 with pressure oil.

BezugszeichenReference numerals

  • 1 Flansch 36 Ölbohrung1 flange 36 oil hole
  • 2 Gehäuse 37 Dichtungsring2 housing 37 sealing ring
  • 3 Verteiler 38 Verzahnungshülse3 distributors 38 toothing sleeve
  • 4 Gehäusekappe 39 Schraubenfeder4 Housing cap 39 coil spring
  • 5 Antriebswelle 40 Gehäusekappe5 drive shaft 40 housing cap
  • 6 Steuerplatte 41 Zentralrohr6 Control plate 41 central tube
  • 7 Zylindertrommel 42 Zapfenring, zweiteilig7 cylinder drum 42 pin ring, two parts
  • 8 Kolben 43 Lagerring8 pistons 43 bearing ring
  • 9 Andrückplatte 44 Wulst an 459 pressure plate 44 bead on 45
  • 10 Schrägscheibe 45 Hülse10 swash plate 45 sleeve
  • 11 Gleitschuh 46 Stift11 slide shoe 46 pin
  • 12 Schwenkkörper 47 Wellenfeder12 swivel body 47 wave spring
  • 13 Führungsarm 48 Schmierbohrung13 guide arm 48 lubrication hole
  • 14 Zapfen 49 Stütztring14 pins 49 support ring
  • 15 Gleitstein 50 Schmierkanal15 sliding block 50 lubrication channel
  • 16 Laufplatte 51 Versorgungsleitung f. 5016 running plate 51 supply line f. 50
  • 17 Führungsrollen 52 Gleitlager17 guide rollers 52 plain bearings
  • 18 Rollenlager (linear) 53 Dichtungsring18 roller bearings (linear) 53 sealing ring
  • 19 Fixplatte 2 St 54 Deckel19 Fix plate 2 pieces 54 cover
  • 20 Käfig 55 Stift20 cage 55 pin
  • 21 Dämpfungsplatte 2 St 56 Federn21 damping plate 2 pcs. 56 springs
  • 22 Steuerboden 57 Dämpfungsring22 Control floor 57 Damping ring
  • 23 Laschen23 tabs
  • 24 Pumpenregler24 pump controllers
  • 25 Verstellkolben25 adjusting pistons
  • 26 Joch26 yoke
  • 27 Bolzen27 bolts
  • 28 Brücke28 bridge
  • 29 gekrümmte Fläche29 curved surface
  • 30 Saugleitung30 suction line
  • 31 Druckleitung31 pressure line
  • 32 und 33 Steuerschlitze32 and 33 control slots
  • 34 Hülse aus Kunststoff34 plastic sleeve
  • 35 Spannband35 tension strap

Claims (6)

1. A hydraulic axial piston machine of the swash plate type with a shaft for the cylinder barrel passed to the outside on one side, having a distributor and a radial bearing between the stator fixed to the housing and the cylinder barrel, characterized in that the stator is constructed as a central tube (41) on which is supported the radial bearing (43), the distributor (3) and a control base (22) used as a mounting support for the swash plate (10), in that between the housing (2) and the central tube (41) a damping ring (57) is provided, and in that the pump components not located in the housing (2) are covered by a non-load-bearing spring cap (40) connected to the housing.
2. An axial piston machine according to claim 1, characterized in that the spring cap (40) is made from a noise-damping material.
3. An axial piston machine according to claims 1 or 2, characterized in that the swash plate (10) is pivotably mounted in per se known manner by means of a tilting yoke (12) in the trunnion (14) of a trunnion ring, and in that the tilting yoke (12) is displaceable with the swash plate (10) at right angles to the trunnion axis (M-M) and rolls by means of a curved surface (29), whose radius of curvature (R) has its centre point on the trunnion axis (M-M), as well as on a rotary disk (16), which is in turn supported by means of a linear roller bearing (18, 19) on a control base (22) connected to the trunnion ring (42).
4. An axial piston machine according to claim 3, characterized in that a damping plate (21) made from plastic or the like is positioned between the linear roller bearing (18, 19) and the control base (22).
5. An axial piston machine according to one of the preceding claims, characterized in that between the central tube (41) and the cylinder barrel (7), the bearing has a floating bearing ring (43) arranged in freely rotatable manner.
6. An axial piston machine according to claim 5, characterized in that the bearing ring (43) is provided with radial lubrication holes (48), which are supplied with pressure oil (at 51).
EP83102220A 1982-04-02 1983-03-07 Hydraulic axial-piston machine Expired EP0090953B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823212429 DE3212429A1 (en) 1982-04-02 1982-04-02 HYDRAULIC AXIAL PISTON MACHINE
DE3212429 1983-04-02

Publications (3)

Publication Number Publication Date
EP0090953A2 EP0090953A2 (en) 1983-10-12
EP0090953A3 EP0090953A3 (en) 1984-03-28
EP0090953B1 true EP0090953B1 (en) 1987-02-04

Family

ID=6160147

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102220A Expired EP0090953B1 (en) 1982-04-02 1983-03-07 Hydraulic axial-piston machine

Country Status (3)

Country Link
EP (1) EP0090953B1 (en)
JP (1) JPS58185984A (en)
DE (2) DE3212429A1 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4203619C2 (en) * 1992-02-07 1996-07-25 Rexroth Mannesmann Gmbh Hydraulic system
DE19957565B4 (en) * 1999-11-30 2013-02-07 Linde Material Handling Gmbh Silenced hydrostatic piston engine
DE19957568B4 (en) * 1999-11-30 2014-02-13 Linde Hydraulics Gmbh & Co. Kg Arrangement with a flywheel and a hydrostatic axial piston machine
DE102010047431A1 (en) * 2010-10-04 2012-04-05 Robert Bosch Gmbh Axial piston machine with a control plate inserted into a groove of a housing part
DE102011009537A1 (en) 2011-01-27 2012-08-02 Robert Bosch Gmbh Hydrostatic machine, in particular axial piston machine
DE102012215238A1 (en) * 2012-08-28 2014-03-06 Robert Bosch Gmbh Swash plate machine
DE102013200729A1 (en) * 2013-01-18 2014-07-24 Robert Bosch Gmbh Swash plate machine
DE102013210070B3 (en) * 2013-05-29 2014-05-28 Sauer-Danfoss Gmbh & Co. Ohg Mounting structure for unpackaged assembly of hydraulic axial piston machine, has output shaft arranged at opposite side of axial piston, where structure receives supporting forces during working operation of axial piston
CH714321A1 (en) 2017-11-11 2019-05-15 Liebherr Machines Bulle Sa Adjusting device for an axial piston machine.
DE102019212074A1 (en) * 2019-08-13 2021-02-18 Robert Bosch Gmbh Motor-hydromachine unit for attachment to a hydraulic unit

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Publication number Priority date Publication date Assignee Title
FR1359244A (en) * 1963-03-12 1964-04-24 Hispano Suiza Sa Improvements made to cylinder-type piston machines, in particular to hydraulic pumps of this type
CH451853A (en) * 1966-03-10 1968-05-15 Bennes Marrel Hydraulic rotary barrel machine
JPS5735198B2 (en) * 1972-08-31 1982-07-27
JPS5948218B2 (en) * 1977-06-24 1984-11-24 住友化学工業株式会社 Method for reducing froth generation during gas transportation of synthetic resin pellets
DE3026765A1 (en) * 1980-07-15 1982-02-11 Linde Ag, 6200 Wiesbaden AXIAL PISTON PUMP FOR TWO FLOWERS

Also Published As

Publication number Publication date
DE3369719D1 (en) 1987-03-12
JPS58185984A (en) 1983-10-29
EP0090953A2 (en) 1983-10-12
EP0090953A3 (en) 1984-03-28
DE3212429A1 (en) 1983-10-13

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