EP0607890B1 - Elastic bearing for suspension arms in form of connecting rods for axle bearings of railway vehicles - Google Patents
Elastic bearing for suspension arms in form of connecting rods for axle bearings of railway vehicles Download PDFInfo
- Publication number
- EP0607890B1 EP0607890B1 EP94100548A EP94100548A EP0607890B1 EP 0607890 B1 EP0607890 B1 EP 0607890B1 EP 94100548 A EP94100548 A EP 94100548A EP 94100548 A EP94100548 A EP 94100548A EP 0607890 B1 EP0607890 B1 EP 0607890B1
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- European Patent Office
- Prior art keywords
- bearing
- resilient
- faces
- bodies
- portions
- 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.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
- B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
- B61F5/26—Mounting or securing axle-boxes in vehicle or bogie underframes
- B61F5/30—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes
- B61F5/32—Guides, e.g. plates, for axle-boxes
Definitions
- the invention relates to elastic bearings for the connecting rod-type link for axle bearings of the type shown schematically in FIG. 1 of the accompanying drawing on rail vehicles according to the preamble of patent claim 1.
- Such bearings are widely used for the resiliently vertically movable support of the axles of rail vehicles with respect to the vehicle frame - in particular with respect to the bogie frame of such vehicles.
- Said connecting rod-like links are responsible, on the one hand, for the stable running of the vehicle axles in the longitudinal and transverse directions, and, on the other hand, they enable their resilient deflection in the vertical direction.
- the elastic mounting of the connecting rod bearing axles in the connecting rod bearing eyes must be relatively hard with respect to axial and radial deflections and in particular with regard to cardanic deflections around the center of the bearing, but must be as soft as possible with regard to torsional movements.
- the elastic bearings previously used on the connecting rod-type links in question were only unsatisfactorily able to meet these requirements.
- the spring elements that determine the elastic properties of the known connecting rod bearings were namely designed as rubber bodies, which are rotationally symmetrical cylindrical or approximately cylindrical between the bearing axis and bearing eye of the connecting rod and were not sufficiently rigid, particularly with regard to cardanic deflections, and no longer met the constantly increasing requirements.
- Connecting rod-type handlebars with elastic bearings are also known from GB-A-725.914.
- the inventive approximately double-cone design and arrangement of the rubber-elastic spring bodies and their centering on the center of the bearing ensures that the cardanic deflections, which are particularly difficult to control in conventional bearings, act in the direction of the surface normals on the conical outer surfaces of the rubber-elastic spring bodies and thereby the surface bond between the spring bodies and load the metal parts connected to them evenly over the entire surface. This avoids local increases in load, which can lead to the destruction of the rubber or the loosening of the rubber / metal bond and thus to the defect of the bearing in continuous operation.
- the apices of the imaginary conical central surfaces of the two rubber-elastic spring bodies lie on the bearing center line corresponding to the axis of rotational symmetry of the bearing no more than 10% of the axial width of the elastic bearing.
- the two vertices preferably coincide at the center of the bearing.
- intermediate plates in the form of conical rings which are parallel to the conical inner and outer surfaces of the spring bodies are preferably adhesively embedded in the spring bodies of the bearings according to the invention.
- the axial width of these rings decreases from the inside to the outside and, like the axial width of the conical outer and inner surfaces of the metallic connecting parts of the spring body, is dimensioned in such a way that the same force-transmitting elements Adhesive surfaces to the adjacent rubber layers of the spring body result, while the thickness of the rubber layers of the spring body produced in this way, decreasing from the inside to the outside, is chosen in particular so that all rubber layers have the same form factor.
- the wheel axle bearing 4 receiving the wheel axle 3 is supported by springs 5 on the vehicle or bogie frame indicated by hatching.
- springs 5 On guide the wheel axle bearing 4 in the longitudinal, transverse and vertical directions serve two connecting rod-like links 1, which are each connected via elastic bearings 2 on the one hand to the wheel axle bearing 4 and on the other hand to the vehicle or bogie frame.
- each of the connecting rod-like links 1 contains two bearing eyes 7, into each of which an elastic bearing 2 according to the invention is inserted.
- the respective bearing axis 6 is supported by two bearing bushes 8 which are inserted coaxially into the bearing eye 7 and axially preloaded against one another in this in an axially mirror-inverted orientation.
- the bearing bushes 8 each consist of an inner part 8.1 and an outer part 8.2 and a spring body 8.3, the outer surface 8.11 of the inner part 8.1 and the inner surface 8.21 of the outer part 8.2 are vulcanized together with the spring body 8.3 formed from a rubber-elastic material.
- the spring bodies 8.3 are conical, and their imaginary central surfaces F1, F2 lie on conical shells, the vertices S1, S2 of which lie after the axial preloading of the bearing bushes in the immediate area of the bearing center point M and which have the same apex angle ⁇ .
- Figures 3, 4 and 5 do not require any further explanation except for the fact that in Figure 5 the spring bodies 8.3 are divided by vulcanized intermediate plates in the form of conical rings 8.31, which increases their hardness counteracting the cardanic deflections of the bearing axis 6 becomes.
- the person skilled in the art has it in hand in the usual way - in particular by selecting rubber mixtures suitable for the spring body 8.3 - to the requirements of to adapt to the respective application.
- Advantageous developments of the invention may consist in not configuring the conical spring bodies 8.3 to be completely rotationally symmetrical, but in such a way that they have different hardnesses and / or damping in sectors depending on the different static or dynamic forces acting on them in the different radial directions.
- the spring bodies 8.3 can be constructed in sectors from different rubber mixtures, and / or they have a non-rotationally symmetrical, sectorally different spatial shape - in particular with sector-like recesses.
- an elastic bearing is created which decisively improves the axle bearings according to FIG. 1 of rail vehicles - especially with regard to the perfect axle guidance. But also with regard to the vertical spring behavior in connection with the vehicle springs 5 and thus with regard to the overall suspension comfort of the vehicles as well as the wear resistance and service life of both the bearing itself and the entire axle bearing, considerable improvements are achieved.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
- Support Of The Bearing (AREA)
Description
Die Erfindung betrifft elastische Lager für die pleuelartigen Lenker für Achslagerungen der in Fig. 1 der beigefügten Zeichnung schematisch dargestellten Art an Schienenfahrzeugen gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to elastic bearings for the connecting rod-type link for axle bearings of the type shown schematically in FIG. 1 of the accompanying drawing on rail vehicles according to the preamble of
Derartige Lager werden in großem Umfang zur federnd vertikal beweglichen Abstützung der Achsen von Schienenfahrzeugen gegenüber dem Fahrzeugrahmen - insbesondere gegenüber den Drehgestellrahmen solcher Fahrzeuge - verwendet. Dabei sind die besagten pleuelartigen Lenker zum einen für die laufstabile Führung der Fahrzeugachsen in Längs- und Querrichtung verantwortlich, und zum andern ermöglichen sie deren federnde Auslenkung in Vertikalrichtung. Zur Erzielung einer optimalen Fahrstabilität der Fahrzeuge - auch bei hohen Fahrgeschwindigkeiten - muß daher die elastische Lagerung der Lagerachsen der Pleuel in den Lageraugen der Pleuel bezüglich axialer und radialer Auslenkungen und insbesondere bezüglich kardanischer Auslenkungen um den Lagermittelpunkt verhältnismäßig hart, dagegen bezüglich Torsionsbewegungen möglichst weich sein.Such bearings are widely used for the resiliently vertically movable support of the axles of rail vehicles with respect to the vehicle frame - in particular with respect to the bogie frame of such vehicles. Said connecting rod-like links are responsible, on the one hand, for the stable running of the vehicle axles in the longitudinal and transverse directions, and, on the other hand, they enable their resilient deflection in the vertical direction. In order to achieve optimum driving stability of the vehicles - even at high driving speeds - the elastic mounting of the connecting rod bearing axles in the connecting rod bearing eyes must be relatively hard with respect to axial and radial deflections and in particular with regard to cardanic deflections around the center of the bearing, but must be as soft as possible with regard to torsional movements.
Diesen Forderungen wurden die bisher an den in Rede stehenden pleuelartigen Lenkern verwendeten elastischen Lager nur in unbefriedigender Weise gerecht. Die die elastischen Eigenschaften der bekannten Pleuellager bestimmenden Federelemente waren nämlich als Gummikörper ausgebildet, die rotationssymetrisch zylindrisch oder annähernd zylindrisch zwischen Lagerachse und Lagerauge des Pleuels angeordnet waren und insbesondere bezüglich kardanischer Auslenkungen keine ausreichende Steifheit aufwiesen und den stetig steigenden Anforderungen nicht mehr genügten.The elastic bearings previously used on the connecting rod-type links in question were only unsatisfactorily able to meet these requirements. The spring elements that determine the elastic properties of the known connecting rod bearings were namely designed as rubber bodies, which are rotationally symmetrical cylindrical or approximately cylindrical between the bearing axis and bearing eye of the connecting rod and were not sufficiently rigid, particularly with regard to cardanic deflections, and no longer met the constantly increasing requirements.
Pleuelartige Lenker mit elastischen Lagern sind auch durch die GB-A-725.914 bekannt geworden.Connecting rod-type handlebars with elastic bearings are also known from GB-A-725.914.
Es stellte sich daher die Aufgabe, ein elastisches Lager für die pleuelartigen Lenker an Achslagerungen der eingangs genannten Art an Schienenfahrzeugen aufzuzeigen, das unter Vermeidung der Nachteile der bekannten Lager und unter Berücksichtigung der vorgegebenen Einbauverhältnisse eine optimale Achsführung gewährleistet, indem es die o.a. Forderungen erfüllt.It was therefore the task of demonstrating an elastic bearing for the connecting rod-like handlebars on axle bearings of the type mentioned at the beginning of rail vehicles, which, while avoiding the disadvantages of the known bearings and taking into account the specified installation conditions, ensures optimal axle guidance by the above-mentioned. Requirements met.
Diese Aufgabe wird erfindungsgemäß durch ein gattungsgemäßes elastisches Lager gelöst, das die im kennzeichnenden Teil des Patentanspruchs 1 angegebenen Merkmale aufweist. Vorteilhafte Ausgestaltungen und bevorzugte Ausführungsformen der Erfindung sind in den Patentansprüchen 2 bis 8 angegeben.This object is achieved by a generic elastic bearing that has the features specified in the characterizing part of
Durch die erfindungsgemäße etwa doppelkegelige Gestaltung und Anordnung der gummielastischen Federkörper und ihre Zentrierung auf den Lagermittelpunkt wird erreicht, daß die bei herkömmlichen Lagern besonders schwer beherrschbaren kardanischen Auslenkungen jeweils in Richtung der Flächennormalen auf die konischen Mantelflächen der gummielastischen Federkörper einwirken und dabei die Flächenbindung zwischen den Federkörpern und den mit diesen verbundenen Metallteilen gleichmäßig vollflächig belasten. Hierdurch werden örtliche Belastungsüberhöhungen, die im Dauerbetrieb zur Zerstörung des Gummis oder zur Lösung der Gummi/Metall- Bindung und damit zum Defekt des Lagers führen können, vermieden.The inventive approximately double-cone design and arrangement of the rubber-elastic spring bodies and their centering on the center of the bearing ensures that the cardanic deflections, which are particularly difficult to control in conventional bearings, act in the direction of the surface normals on the conical outer surfaces of the rubber-elastic spring bodies and thereby the surface bond between the spring bodies and load the metal parts connected to them evenly over the entire surface. This avoids local increases in load, which can lead to the destruction of the rubber or the loosening of the rubber / metal bond and thus to the defect of the bearing in continuous operation.
In vorteilhaften Ausführungsformen der Erfindung liegen die Scheitel der gedachten kegeligen Mittelflächen der beiden gummielastischen Federkörper, auf der der Rotationssymmetrieachse des Lagers entsprechenden Lagermittellinie nicht mehr als 10 % der axialen Breite des elastischen Lagers auseinander. Vorzugsweise fallen die beiden Scheitel im Lagermittelpunkt zusammen.In advantageous embodiments of the invention, the apices of the imaginary conical central surfaces of the two rubber-elastic spring bodies lie on the bearing center line corresponding to the axis of rotational symmetry of the bearing no more than 10% of the axial width of the elastic bearing. The two vertices preferably coincide at the center of the bearing.
In der praktischen Ausführung hat es sich als vorteilhaft erwiesen für den Scheitelwinkel der gedachten kegeligen Mittelflächen der beiden gummielastischen Federkörper ebenso wie für denjenigen ihrer inneren und äußeren kegelmantelförmigen Oberflächen einen Wert von 60 bis 90° zu wählen. Vorzugsweise besitzt dieser Winkel einen Wert von 70 bis 80°.In practical implementation, it has proven to be advantageous to choose a value of 60 to 90 ° for the apex angle of the conical central surfaces of the two rubber-elastic spring bodies as well as for that of their inner and outer conical surface. This angle preferably has a value of 70 to 80 °.
In die Federkörper der erfindungsgemäßen Lager sind zur Erzielung der angestrebten extrem hohen Härte gegenüber kardanischen Auslenkungen vorzugsweise Zwischenbleche in Form von zu den konischen Innen- und Außenflächen der Federkörper flächenparallelen konischen Ringen haftend eingelagert. Um die Federkörper gleichmäßig zu belasten, nimmt die axiale Breite dieser Ringe wie auch diejenige der Federkörper von innen nach außen ab und ist ebenso wie die axiale Breite der konischen Außen- bzw. Innenflächen der metallischen Anschlußteile der Federkörper jeweils so bemessen, daß sich gleiche kraftübertragende Haftflächen zu den benachbarten Gummischichten des Federkörpers ergeben, während die Dicke der so erzeugten Gummischichten der Federkörper von innen nach außen abnehmend insbesondere so gewählt ist, daß alle Gummischichten den gleichen Formfaktor aufweisen.In order to achieve the desired extremely high hardness with regard to cardanic deflections, intermediate plates in the form of conical rings which are parallel to the conical inner and outer surfaces of the spring bodies are preferably adhesively embedded in the spring bodies of the bearings according to the invention. In order to load the spring body evenly, the axial width of these rings, like that of the spring body, decreases from the inside to the outside and, like the axial width of the conical outer and inner surfaces of the metallic connecting parts of the spring body, is dimensioned in such a way that the same force-transmitting elements Adhesive surfaces to the adjacent rubber layers of the spring body result, while the thickness of the rubber layers of the spring body produced in this way, decreasing from the inside to the outside, is chosen in particular so that all rubber layers have the same form factor.
Die beigefügte Zeichnung erläutert die vorliegende Erfindung anhand von Ausführungsbeispielen bzw. Prinzipdarstellungen; es zeigen:
Figur 1- die schematische Darstellung einer der vorliegenden Erfindung zugrundeliegenden Achslagerung von Schienenfahrzeugen,
Figur 2- einen pleuelartigen Längslenker einer solchen Achslagerung links im Axialschnitt und rechts in der Draufsicht,
Figur 3- links den Querschnitt III'-III' und rechts die seitliche Außenansicht III-III gemäß
Figur 2, - Figur 4 und
Figur 5 - bevorzugte Ausführungsformen des erfindungsgemäßen Lagers in Axialschnitten entsprechend der linken Seite von
Figur 2.
- Figure 1
- 1 shows the schematic representation of an axle bearing of rail vehicles on which the present invention is based,
- Figure 2
- a connecting rod-like trailing arm of such an axle bearing on the left in axial section and on the right in plan view,
- Figure 3
- on the left the cross section III'-III 'and on the right the side external view III-III according to FIG. 2,
- Figure 4 and Figure 5
- preferred embodiments of the bearing according to the invention in axial sections corresponding to the left side of FIG. 2.
Wie die Prinzipdarstellung einer Achslagerung von Schienenfahrzeugen in Figur 1 zeigt, ist das die Radachse 3 aufnehmende Radachslager 4 über Federn 5 an dem durch eine Schraffur angedeuteten Fahrzeug- bzw. Drehgestell- Rahmen abgestützt. Zur Führung des Radachslagers 4 in Längs-, Quer- und Vertikalrichtung dienen zwei pleuelartige Lenker 1, die jeweils über elastische Lager 2 einerseits mit dem Radachslager 4 und andererseits mit dem Fahrzeug- bzw. Drehgestellrahmen verbunden sind.As the basic illustration of an axle bearing of rail vehicles in FIG. 1 shows, the wheel axle bearing 4 receiving the
Wie in Figur 2 erkennbar ist, enthält jeder der pleuelartigen Lenker 1 zwei Lageraugen 7, in die je ein erfindungsgemäßes elastisches Lager 2 eingesetzt ist. Die jeweilige Lagerachse 6 stützt sich über zwei in axial spiegelverkehrter Ausrichtung koaxial in das Lagerauge 7 eingesetzte und gegeneinander axial vorgespannte Lagerbuchsen 8 in diesem ab. Die Lagerbuchsen 8 bestehen jeweils aus einem Innenteil 8.1 und einem Außenteil 8.2 sowie einem Federkörper 8.3, wobei die Außenfläche 8.11 des Innenteils 8.1 und die Innenfläche 8.21 des Außenteils 8.2 mit dem aus einem gummielastischen Werkstoff gebildeten Federkörper 8.3 zusammenvulkanisiert sind. Die Federkörper 8.3 sind konisch ausgebildet, und ihre gedachten Mittelflächen F1, F2 liegen auf Kegelmänteln, deren Scheitel S1, S2 nach der besagten Axial-Vorspannung der Lagerbuchsen im unmittelbaren Bereich des Lagermittelpunktes M liegen und die den gleichen Scheitelwinkel α aufweisen.As can be seen in FIG. 2, each of the connecting rod-
Aufgrund des geringen Abstandes der Scheitel S1, S2 der gedachten kegeligen Mittelflächen F1, F2 der Federkörper 8.3 bewirkt eine kardanische Auslenkung der Lagerachse 6 um den Lagermittelpunkt M eine Belastung der Federkörper 8.3 jeweils annähernd in Richtung der Flächennormalen ihrer konischen Mantelflächen. Diese vorteilhafte Belastungseinleitung in die Federkörper 8.3 wird optimiert, wenn die Scheitel S1, S2 im Lagermittelpunkt M zusammenfallen, wie die Darstellungen der bevorzugten Ausführungsformen gemäß Figur 4 und Figur 5 ohne weiteres zeigen.Due to the small distance between the apices S1, S2 of the imaginary conical central surfaces F1, F2 of the spring bodies 8.3, a cardanic deflection of the
Die Figuren 3, 4 und 5 bedürfen nach dem vorstehend Gesagten keiner weiteren Erläuterung bis auf die Tatsache, daß in Figur 5 die Federkörper 8.3 durch einvulkanisierte Zwischenbleche in Form von konischen Ringen 8.31 unterteilt sind, wodurch ihre den kardanischen Auslenkungen der Lagerachse 6 entgegenwirkende Härte erhöht wird.Figures 3, 4 and 5 do not require any further explanation except for the fact that in Figure 5 the spring bodies 8.3 are divided by vulcanized intermediate plates in the form of conical rings 8.31, which increases their hardness counteracting the cardanic deflections of the
Ergänzend zu der erfindungsgemäßen konstruktiven Optimierung der gattungsgemäßen elastischen Lager, hat der Fachmann es in der Hand, diese in üblicher Weise - insbesondere durch Auswahl von Gummimischungen geeigneter Härte für die Federkörper 8.3 - an die Erfordernisse des jeweiligen Einsatzfalles anzupassen. Vorteilhafte Weiterbildungen der Erfindung können darin bestehen, die konischen Federkörper 8.3 nicht vollständig rotationssymmetrisch auszubilden, sondern so, daß sie in Abhängigkeit von den in den verschiedenen radialen Richtungen auf sie einwirkenden unterschiedlichen statischen bzw. dynamischen Kräften sektorenmäßig unterschiedliche Härte und/oder Dämpfung aufweisen. Zu diesem Zweck können die Federkörper 8.3 sektorenmäßig aus unterschiedlichen Gummimischungen aufgebaut sein, und/oder sie weisen eine nicht rotationssymmetrische, sektorenmäßig unterschiedliche Raumform - insbesondere mit sektorenartigen Aussparungen - auf.In addition to the design optimization of the generic elastic bearings according to the invention, the person skilled in the art has it in hand in the usual way - in particular by selecting rubber mixtures suitable for the spring body 8.3 - to the requirements of to adapt to the respective application. Advantageous developments of the invention may consist in not configuring the conical spring bodies 8.3 to be completely rotationally symmetrical, but in such a way that they have different hardnesses and / or damping in sectors depending on the different static or dynamic forces acting on them in the different radial directions. For this purpose, the spring bodies 8.3 can be constructed in sectors from different rubber mixtures, and / or they have a non-rotationally symmetrical, sectorally different spatial shape - in particular with sector-like recesses.
Mit der vorliegenden Erfindung wird ein elastisches Lager geschaffen, das Achslagerungen nach Figur 1 von Schienenfahrzeugen - vor allem bezüglich der einwandfreien Achsführung - entscheidend verbessert. Aber auch bezüglich des Vertikal-Federverhaltens in Verbindung mit den Fahrzeugfedern 5 und damit im Hinblick auf den gesamten Federungskomfort der Fahrzeuge sowie auf die Verschleißfestigkeit und Lebensdauer sowohl des Lagers selbst als auch der gesamten Achslagerung werden erhebliche Verbesserungen erzielt.With the present invention, an elastic bearing is created which decisively improves the axle bearings according to FIG. 1 of rail vehicles - especially with regard to the perfect axle guidance. But also with regard to the vertical spring behavior in connection with the
Claims (8)
- Resilient bearing for suspension arms, in the form of connecting rods, at axle mountings of rail-guided vehicles, having resilient elements which are disposed between the bearing shaft (6) and the bearing boss (7) of the suspension arm (1), support said component parts against each other and are coaxial relative to the bearing shaft (6), characterised- in that two rubber/metal bearing bushes (8) are provided as the resilient element,- each of said bushes includes a metallic inner portion (8.1) and a metallic outer portion (8.2) as well as a rubber-elastic resilient body (8.3), which fills the annular gap between the inner and outer portions and is connected to these portions,- and in that these bearing bushes (8) are inserted into the bearing boss (7) on each side in an orientation, which is axially mirror-inverted relative to each other, coaxially with the bearing shaft,- and said bushes are non-rotatably connected in a force- and/or form-locking manner to the bearing boss (7) via their outer portions (8.2) and to the bearing shaft (6) via their inner portions (8.1) and are axially prestressed relative to one another,- the outer faces (8.11) of the inner portions (8.1) and the inner faces (8.21) of the outer portions (8.2) of the bearing bushes as well as the inner and outer faces of the rubber-elastic resilient bodies (8.3), which are disposed between these portions, are conically configured in such a manner that their radius increases proportionally to the axial spacing from the bearing centre (M),- and the apexes (S1, S2) of the imaginary conical central faces (F1, F2) of the two resilient bodies (8.3) lying in the region of the bearing centre (M) on the bearing centre line (A).
- Resilient bearing according to claim 1, characterised in that the spacing between the apexes (S1, S2) of the imaginary conical central faces (F1, F2) on the bearing centre line (A) is at most 10 % of the axial width (B) of the resilient bearing.
- Resilient bearing according to claim 1, characterised in that the imaginary conical central faces (F1, F2) of the two resilient bodies (8.3) form a double cone, the apex of which lies in the bearing centre (M).
- Resilient bearing according to one of claims 1 to 3, characterised in that the apex angle (α) of the imaginary conical central faces (F1, F2) of the two resilient bodies (8.3) has a value of between 60° and 90°.
- Resilient bearing according to claim 4, characterised in that the apex angle (α) has a value of between 70° and 80°.
- Resilient bearing according to one of claims 1 to 5, characterised in that intermediate plates, in the form of conical rings (8.31) which lie in a surface-parallel manner relative to the conical faces (8.11, 8.21) of the inner and outer portions (8.1, 8.2), are firmly incorporated in the resilient bodies (8.3) and divide the resilient bodies (8.3) into a plurality of rubber layers, the axial width of these rings (8.31) and that of the resilient bodies (8.3) decreasing outwardly from the inside and, just like the axial width of the conical outer and inner faces (8.11, 8.21) of the inner and outer portions (8.1, 8.2), being so dimensioned that identical force-transmitting adhesive faces to the adjacent rubber layers of the resilient body (8.3) are produced, and the thickness of the rubber layers of the resilient bodies (8.3) thus produced being selected, more especially, to decrease outwardly from the inside so that all of the rubber layers have the same form factor.
- Resilient bearing according to one of claims 1 to 6, characterised in that the resilient bodies (8.3) are provided in sectors with variable hardness and/or damping in dependence on the static or dynamic forces acting thereon in the radial direction.
- Resilient bearing according to claim 7, characterised in that the resilient bodies (8.3) have sector-like recesses.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4301652A DE4301652C1 (en) | 1993-01-22 | 1993-01-22 | Elastic bearing for rail-vehicle axle bearing link - has springs formed by two mirror-image bushes each with rubber body bonded between inner and outer metal components in bearing eye |
| DE4301652 | 1993-01-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0607890A1 EP0607890A1 (en) | 1994-07-27 |
| EP0607890B1 true EP0607890B1 (en) | 1997-05-14 |
Family
ID=6478701
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP94100548A Expired - Lifetime EP0607890B1 (en) | 1993-01-22 | 1994-01-15 | Elastic bearing for suspension arms in form of connecting rods for axle bearings of railway vehicles |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0607890B1 (en) |
| DE (2) | DE4301652C1 (en) |
| ES (1) | ES2102077T3 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4431379C2 (en) * | 1994-08-26 | 1998-02-12 | Deutsche Waggonbau Ag | Running gear for rail vehicles |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE746640C (en) * | 1939-03-09 | 1944-08-18 | Continental Gummi Werke Ag | Axle bushing for rail vehicles by means of rubber springs |
| GB725914A (en) * | 1953-01-20 | 1955-03-09 | Vickers Electrical Co Ltd | Improvements relating to axle box arrangements for railway vehicles |
| DE2029329B2 (en) * | 1970-06-13 | 1976-05-06 | Rheinstahl Ag Transporttechnik, 3500 Kassel | AXLE BEARING GUIDE FOR RAIL VEHICLES, IN PARTICULAR FOR BOGY LOCOMOTIVES |
| IT1248852B (en) * | 1990-06-14 | 1995-01-30 | Pirelli Sistemi Antivibranti | ELASTIC JOINT |
-
1993
- 1993-01-22 DE DE4301652A patent/DE4301652C1/en not_active Expired - Fee Related
-
1994
- 1994-01-15 EP EP94100548A patent/EP0607890B1/en not_active Expired - Lifetime
- 1994-01-15 DE DE59402686T patent/DE59402686D1/en not_active Expired - Fee Related
- 1994-01-15 ES ES94100548T patent/ES2102077T3/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE59402686D1 (en) | 1997-06-19 |
| EP0607890A1 (en) | 1994-07-27 |
| ES2102077T3 (en) | 1997-07-16 |
| DE4301652C1 (en) | 1994-01-27 |
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