EP1738985B1 - Damping device for drawing and/or buffing devices of railway vehicles - Google Patents

Damping device for drawing and/or buffing devices of railway vehicles Download PDF

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Publication number
EP1738985B1
EP1738985B1 EP06405264A EP06405264A EP1738985B1 EP 1738985 B1 EP1738985 B1 EP 1738985B1 EP 06405264 A EP06405264 A EP 06405264A EP 06405264 A EP06405264 A EP 06405264A EP 1738985 B1 EP1738985 B1 EP 1738985B1
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EP
European Patent Office
Prior art keywords
piston
pressure chamber
damping apparatus
channel
damping
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EP06405264A
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German (de)
French (fr)
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EP1738985A1 (en
Inventor
Otto Ziegler
Werner Maurer
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Schwab Verkehrstechnik AG
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Schwab Verkehrstechnik AG
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Publication of EP1738985A1 publication Critical patent/EP1738985A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61G—COUPLINGS; DRAUGHT AND BUFFING APPLIANCES
    • B61G11/00—Buffers
    • B61G11/12—Buffers with fluid springs or shock-absorbers; Combinations thereof

Definitions

  • the invention relates to a damping device for tensile and / or impact devices on rail vehicles according to the preamble of claim 1.
  • Generic damping devices are used for example in buffers or couplings on rail vehicles.
  • the shock absorber is equipped with a mechanical spring unit and a hydraulic damper.
  • the mechanical spring unit is formed by a plurality of individual springs.
  • the hydraulic damper consists of a pressure chamber arranged within a pressure chamber jacket, which is connected via radial throttle openings with a compensation chamber.
  • a piston is arranged, which is fastened by means of a screw to a bolt. The piston plunges during compression of the shock absorber in the pressure chamber and reduces it.
  • a part of the damping fluid absorbed in the pressure chamber is displaced and conveyed via the radial throttle openings into the compensation chamber.
  • the throttle cross-section should be changeable according to the requirements.
  • the buffer is provided with a gas-hydraulic damping device and an elastomeric spring arrangement.
  • the gas-hydraulic damping device is provided with a cylindrical pressure chamber and a receiving chamber connected thereto via at least one channel.
  • the pressure chamber decreases with increasing deflection of the buffer by a piston plunging into it.
  • an annular gap is formed between the piston and the inner circumference of the cylinder.
  • the piston is frontally provided with a recess which defines an annular wall which is elastically deformable depending on the internal pressure.
  • the damping device further comprises a horizontally arranged hydraulic damper.
  • This includes a bore provided with a damper housing having a filled with hydraulic fluid pressure chamber in the interior, in which a cylindrically shaped piston is immersed.
  • the piston is connected via a piston rod to the one pressure disk.
  • the pressure chamber is connected by means of overflow with a lying above the piston receiving space.
  • the invention aims to develop a damping device for tensile and / or impact devices on rail vehicles such that it consists of a few individual parts, is very simple and can be manufactured inexpensively.
  • a damping device for tensile and / or impact devices on rail vehicles according to claim 1 is provided.
  • a buffer for rail vehicles which is provided with an inventively designed damping device.
  • the buffer shown in the unloaded resting state has a sleeve 1 (not shown) to be fastened to the rail vehicle and a slide 2 that is displaceable relative thereto.
  • a buffer plate 3 On the front of the plunger 2 a buffer plate 3 is welded. Both the sleeve 1 and the plunger 2 are formed substantially hollow cylindrical.
  • the damping device comprises an elastomeric damping device in the form of a spring assembly 4 and a gas-hydraulic damping device 5.
  • the elastomeric spring assembly 4 consists of a plurality of elastomeric elements 4a, which are separated from each other by means of discs 4b.
  • the individual spring elements 4a are lined up in succession on a piston 7, which is supported on the sleeve 1 at the vehicle end.
  • the piston 7 has the shape of a bolt, which is integrally formed and preferably has a constant outer diameter and a smooth outer surface over its entire length.
  • the front end of the piston 7 is provided with a chamfer in the form of a circumferential phase.
  • Both the elastomer elements 4a as well as the discs 4b are each provided with a bore whose diameter is matched to the outer diameter of the piston 7, so that the piston 7 simultaneously serves to position and support the elastomeric elements 4a.
  • the discs 4b are held by the elastomeric members 4a so that they can not come into contact with the piston 7 and damage its surface.
  • the gas-hydraulic damping device 5 comprises a cylinder element 6, which is fixed to the rear side of the buffer plate 3.
  • centering pins 20 are provided.
  • Cylinder element 6 on the buffer plate 3 facing side provided with a spherical surface 31.
  • the cylinder element 6 is provided with a central pressure chamber 9 and a coaxially arranged, the pressure chamber 9 coaxially comprehensive receiving chamber 10 in the form of an annular space.
  • an annular cover 8 is attached, which limits the receiving chamber 10 to the outside and seals.
  • the pressure chamber 9 is cylindrical over about 90% of its length, the pressure chamber 9 in the opposite end of the immersion side of the piston 7, i. is provided in the region of its bottom 18, with a conically widening in diameter section 9a.
  • the pressure chamber 9 is completely filled with a hydraulic medium such as hydraulic oil, while the receiving chamber 10 is filled in the idle state shown here in majority with hydraulic medium and a gas under pressure.
  • the extending between the cylinder element 6 and the receiving chamber 10 cylinder wall is provided with the reference numeral 6a.
  • the wall thickness of the cylinder wall 6a increases toward the buffer plate 3. This overcompensates for the higher elasticity in the center of the cylinder and ensures that the annular gap area between the piston and the cylinder wall decreases over the stroke. This is intended to ensure that the pressure in the pressure chamber 9, despite a continuously decreasing immersion speed of the piston 7, is largely constant over a wide stroke range during dynamic compression of the plunger 2.
  • the recessed into the cylinder element 6 pressure chamber 9 is open on the side facing away from the buffer plate 3, wherein the piston 7 is guided into the pressure chamber 9 via this opening.
  • the pressure chamber 9 is bounded by the cylinder bottom 18.
  • two sealing rings 11 surrounding the piston 7 are embedded in the end region facing the vehicle.
  • a passage in the form of an annular gap 15 is not apparent from this illustration.
  • the size of this annular gap 15 can be selected according to the requirements, wherein it preferably moves in the range of a few thousandths of a millimeter to a few hundredths of a millimeter.
  • annular channel 13 is inserted, which is in communication with the annular gap 15. From this annular channel 13, a channel in the form of a bore 14 leads down into the receiving chamber 10. Between the annular channel 13 and the sealing rings 11 is a relief annular channel 16 in the cylinder wall 6a of the cylinder member 6 is inserted, which also has a radial relief hole 17 with the receiving chamber 10 communicates.
  • the cylinder member 6 is provided with a check valve 19 which connects the receiving chamber 10 with the pressure chamber 9 and allows backflow of hydraulic medium from the receiving chamber 10 into the pressure chamber 9, when the piston 7 during rebound of the buffer from the Retracts pressure chamber 9.
  • a check valve 19 is preferably embedded on the underside in the cylinder wall 6a, 7 hydraulic medium is fed into the pressure chamber 9 during rebound of the piston.
  • an overflow channel could also be provided, via which the hydraulic medium can flow past the piston 7 into the annular channel 13.
  • Such an overflow channel is preferably introduced on the upper side into the cylinder wall 6a, so that upon compression of the piston 7, the gas is first displaced and the pressure chamber 9 automatically vented.
  • the embodiment shown, in which the piston 7 is guided from the side facing away from the buffer plate 3 in the pressure chamber 9, has the further advantage that the hydraulic medium due to the inertia in a casserole at the cylinder bottom 18 collects, while small amounts of gas inadvertently in the pressure chamber 9 can get to collect at the end face of the piston 7.
  • the small amounts of gas would remain in the pressure chamber 9 and constantly multiply at several successive bumps, which would mean a large loss of energy absorption and damping capacity of the damping device and thus the whole buffer.
  • the piston 7 Since the piston 7 has a constant outer diameter and a smooth lateral surface, increases with increasing deflection of the plunger 2 of the throttle resistance in the piston 7 annular surrounding gap 15, whereby an increase in force is achieved via the insertion path.
  • this increase in force is not only determined by the static cross section of the annular gap 15, but possibly also via an elastic extension of the cylinder member 6, the cylinder wall 6a has a tendency especially in a casserole to bulge material elastic in the radial direction to the outside, bringing itself at the same time the annular gap 15 would increase.
  • This material-elastic expansion of the cylinder element 6 is influenced by the rigidity or wall thickness of the cylinder wall 6a, especially since the wall thickness of the cylinder wall 6a varies along the pressure chamber 9.
  • the pressure chamber 9 is provided in this end with the conically widening portion 9a. This section 9a is to ensure that in the extreme load case even against the stroke end sufficient hydraulic oil can flow past the piston 7.
  • the piston 7 is supported on its rear side not directly on the sleeve 1, but via an annular insert 22. While the sleeve 1 is preferably made of cast iron, the insert 22 is preferably made of a high-tempered steel.
  • the annular insert 22 is provided with an oblique pressure surface 25 which at a corresponding annular surface on the rear wall 21 of the sleeve 1 rests.
  • the insert 22 also has an extension 23 which has a spherical surface and a central through-bore 24. At this spherical surface, the piston 7 is supported with a corresponding pressure surface on its back.
  • the piston 7 is also provided on its back with a piston extension 26 which projects into the recessed into the insert 22 bore 24.
  • the outer diameter of the piston extension 26 is slightly smaller than the diameter of the inserted into the insert 22 bore 24, so that the piston 7 can be slightly deflected about the type of joint forming spherical surface of the insert 22 in the radial direction, which in the case of radially on the buffer plate 3 or ram 2 acting frictional forces is advantageous.
  • a closure arrangement 27 is provided, which serves to close off a channel 28 leading through the piston 7 in the longitudinal direction.
  • the closure assembly 27 is secured by unspecified means which are arranged in the bore 24 of the insert 22. Via the channel 28, the buffer can be filled after assembly with a gas and a hydraulic fluid.
  • the Fig. 2 shows a cross section through the buffer along the line AA in Fig. 1 .
  • the annular gap 15 between the piston 7 and the cylinder member 6 can be seen, which is shown exaggerated in this representation, however, for better visibility.
  • a recessed into the sleeve 1 groove 29 can be seen, in which a arranged on the plunger 2 guide wedge 30 engages to define the position of the sleeve 1 relative to the plunger 2 in the circumferential direction and to prevent rotation of the plunger 2 relative to the sleeve 1
  • four recessed in the rear wall 21 mounting holes can be seen, by means of which the sleeve 1 can be attached to a rail vehicle.
  • the annular channel 14 surrounding the piston 7 is in the resting state of the buffer behind the end face of the piston 7, ie it is covered by the piston 7, so that from the beginning of the Einfedervorgangs to the gas-hydraulic damping device 5 is active by the displaced from the pressure chamber 9 hydraulic medium can flow only through the annular gap 15 in the annular channel 13 and the channel 14, which is associated with a corresponding throttling action.
  • the piston 7 may be mentioned, which is integrally formed and has a constant outer diameter over its entire length. It is understood that such a piston 7 can be manufactured comparatively inexpensively.
  • spring arrangement consisting of elastomer elements
  • other spring arrangements such as, for example, mechanical spring arrangements or friction spring arrangements could also be used.
  • damping devices for example, for use in clutches on rail vehicles.

Abstract

An elastomeric or mechanical damping mechanism (4) and a gas hydraulic damping mechanism (5) support a tappet (2) in a case (1). The damping mechanism (5) includes a cylindrical pressure chamber (9) that becomes smaller when a piston (7) is driven into the pressure chamber. An outlet (15) formed between the cylinder wall (6a) of the pressure chamber and the piston leads to a receiving chamber (10) through a duct (14). The portion of the piston introduced into the pressure chamber is cylindrical and exhibits a constant outside diameter.

Description

Die Erfindung betrifft eine Dämpfungsvorrichtung für Zug- und/oder Stosseinrichtungen an Schienenfahrzeugen nach dem Oberbegriff des Anspruchs 1.The invention relates to a damping device for tensile and / or impact devices on rail vehicles according to the preamble of claim 1.

Gattungsgemässe Dämpfungsvorrichtungen kommen beispielsweise in Puffern oder Kupplungen an Schienenfahrzeugen zum Einsatz.Generic damping devices are used for example in buffers or couplings on rail vehicles.

So ist aus der DE-A-196 19 214 ein Stossdämpfer bekannt, der sich für den Einsatz in einem Puffer für Schienenfahrzeuge eignet. Der Stossdämpfer ist mit einer mechanischen Federeinheit und einem hydraulischen Dämpfer versehen. Die mechanische Federeinheit wird durch eine Vielzahl von Einzelfedern gebildet. Der hydraulische Dämpfer besteht aus einem innerhalb eines Druckraummantels angeordneten Druckraum, der über radiale Drosselöffnungen mit einer Ausgleichskammer verbunden ist. Im Druckraum ist ein Kolben angeordnet, der mittels einer Schraube an einem Bolzen befestigt ist. Der Kolben taucht beim Einfedern des Stossdämpfers in den Druckraum ein und verkleinert diesen. Dadurch wird ein Teil der im Druckraum aufgenommenen Dämpferflüssigkeit verdrängt und über die radialen Drosselöffnungen in die Ausgleichskammer gefördert. Je nach Anzahl, Ausbildung und Anordnung der Drosselöffnungen soll der Drosselquerschnitt den Anforderungen entsprechend veränderbar sein.So is out of the DE-A-196 19 214 a shock absorber known which is suitable for use in a buffer for rail vehicles. The shock absorber is equipped with a mechanical spring unit and a hydraulic damper. The mechanical spring unit is formed by a plurality of individual springs. The hydraulic damper consists of a pressure chamber arranged within a pressure chamber jacket, which is connected via radial throttle openings with a compensation chamber. In the pressure chamber, a piston is arranged, which is fastened by means of a screw to a bolt. The piston plunges during compression of the shock absorber in the pressure chamber and reduces it. As a result, a part of the damping fluid absorbed in the pressure chamber is displaced and conveyed via the radial throttle openings into the compensation chamber. Depending on the number, design and arrangement of the throttle openings, the throttle cross-section should be changeable according to the requirements.

Aus der EP-A 0 451 630 ist ein gattungsgemässer Puffer bekannt, der zur Verwendung bei Schienenfahrzeugen vorgesehen ist. Zum federnden Abstützen einer Pufferplatte ist der Puffer mit einer gashydraulischen Dämpfungseinrichtung sowie einer elastomerischen Federanordnung versehen. Die gashydraulische Dämpfungseinrichtung ist mit einer zylindrischen Druckkammer und einer über zumindest einen Kanal damit verbundenen Aufnahmekammer versehen. Die Druckkammer verkleinert sich mit zunehmender Einfederung des Puffers durch einen in sie eintauchenden Kolben. Zwischen dem Kolben und dem Innenumfang des Zylinders wird ein ringförmiger Spalt gebildet. Der Kolben ist stirnseitig mit einer Ausnehmung versehen, die eine ringförmige Wand begrenzt, die abhängig vom Innendruck elastisch verformbar ist. Durch diese Gestaltung soll erreicht werden, dass der genannte Spalt zwischen dem Kolben und dem Innenumfang des Zylinders bei Vergrösserung des Flüssigkeitsdrucks im Zylinder annähernd gleich gross bleibt oder sich verkleinert, so dass sich die Dämpfungswirkung auch bei Erhöhung des Flüssigkeits-Innendrucks nicht wesentlich verschlechtert.From the EP-A 0 451 630 is a generic buffer known, which is intended for use in rail vehicles. For resilient support of a buffer plate, the buffer is provided with a gas-hydraulic damping device and an elastomeric spring arrangement. The gas-hydraulic damping device is provided with a cylindrical pressure chamber and a receiving chamber connected thereto via at least one channel. The pressure chamber decreases with increasing deflection of the buffer by a piston plunging into it. Between the piston and the inner circumference of the cylinder, an annular gap is formed. The piston is frontally provided with a recess which defines an annular wall which is elastically deformable depending on the internal pressure. By this design is to be achieved that the said gap between the piston and the inner circumference of the cylinder when increasing the liquid pressure in the cylinder remains approximately the same size or decreases, so that the damping effect does not deteriorate significantly even when increasing the liquid internal pressure.

Schliesslich ist aus der DE-A-27 03 530 eine weitere, gattungsgemässe Dämpfungsvorrichtung bekannt. Diese ist mit einer äusseren Pufferhülse versehen, welche eine innere Pufferhülse umgreift. Innerhalb der inneren Pufferhülse ist ein Ringfederpaket angeordnet, das sich mit seinen Enden an je einer Druckscheibe abstützt. Die Dämpfungsvorrichtung weist im weiteren einen liegend angeordneten hydraulischen Dämpfer auf. Dieser umfasst ein mit einer Bohrung versehenes Dämpfergehäuse, das im Innern einen mit Hydraulikflüssigkeit gefüllten Druckraum aufweist, in den ein zylindrisch ausgebildeter Kolben eintaucht. Der Kolben ist über eine Kolbenstange mit der einen Druckscheibe verbunden. Der Druckraum ist mittels Überströmnuten mit einem oberhalb des Kolbens liegenden Aufnahmeraum verbunden.Finally is from the DE-A-27 03 530 another, generic damping device known. This is provided with an outer buffer sleeve which engages around an inner buffer sleeve. Within the inner buffer sleeve an annular spring packet is arranged, which is supported by its ends on a respective pressure disk. The damping device further comprises a horizontally arranged hydraulic damper. This includes a bore provided with a damper housing having a filled with hydraulic fluid pressure chamber in the interior, in which a cylindrically shaped piston is immersed. The piston is connected via a piston rod to the one pressure disk. The pressure chamber is connected by means of overflow with a lying above the piston receiving space.

Die Erfindung zielt darauf ab, eine Dämpfungsvorrichtung für Zug- und/oder Stosseinrichtungen an Schienenfahrzeugen derart weiterzubilden, dass sie aus wenigen Einzelteilen besteht, sehr einfach aufgebaut ist und kostengünstig hergestellt werden kann.The invention aims to develop a damping device for tensile and / or impact devices on rail vehicles such that it consists of a few individual parts, is very simple and can be manufactured inexpensively.

Hierzu wird nach der Erfindung eine Dämpfungsvorrichtung für Zug- und/oder Stosseinrichtungen an Schienenfahrzeugen gemäss dem Anspruch 1 bereitgestellt.For this purpose, according to the invention, a damping device for tensile and / or impact devices on rail vehicles according to claim 1 is provided.

Bevorzugte Ausführungsformen der Erfindung sind in den abhängigen Ansprüchen 2 bis 16 umschrieben.Preferred embodiments of the invention are described in the dependent claims 2 to 16.

Ein bevorzugtes Ausführungsbeispiel der Erfindung wird nachfolgend anhand von Zeichnungen näher erläutert. Dabei zeigt:

  • Fig. 1 einen Längsschnitt durch einen überwiegend schematisch dargestellten Puffer;
  • Fig. 2 einen Querschnitt durch den Puffer entlang der Linie A-A in Fig. 1.
A preferred embodiment of the invention will be explained in more detail with reference to drawings. Showing:
  • Fig. 1 a longitudinal section through a buffer shown mainly schematically;
  • Fig. 2 a cross section through the buffer along the line AA in Fig. 1 ,

In der Fig. 1 ist im Längsschnitt ein Puffer für Schienenfahrzeuge dargestellt, der mit einer erfindungsgemäss ausgebildeten Dämpfungsvorrichtung versehen ist. Der im unbelasteten Ruhezustand gezeigte Puffer weist eine am Schienenfahrzeug (nicht dargestellt) zu befestigende Hülse 1 sowie einen relativ dazu verschiebbaren Stössel 2 auf. Auf der Vorderseite des Stössels 2 ist ein Pufferteller 3 angeschweisst. Sowohl die Hülse 1 wie auch der Stössel 2 sind im wesentlichen hohlzylindrisch ausgebildet.In the Fig. 1 is shown in longitudinal section a buffer for rail vehicles, which is provided with an inventively designed damping device. The buffer shown in the unloaded resting state has a sleeve 1 (not shown) to be fastened to the rail vehicle and a slide 2 that is displaceable relative thereto. On the front of the plunger 2 a buffer plate 3 is welded. Both the sleeve 1 and the plunger 2 are formed substantially hollow cylindrical.

Im Innern des Puffers ist die Dämpfungsvorrichtung angeordnet. Die Dämpfungsvorrichtung umfasst eine elastomerische Dämpfungseinrichtung in Form einer Federanordnung 4 sowie eine gashydraulische Dämpfungseinrichtung 5. Obwohl die beiden Dämpfungseinrichtungen 4, 5 physisch hintereinander angeordnet sind, wirken sie in funktioneller Hinsicht parallel zueinander und dienen zusammen dem federnden Abstützen des Stössels 2 an der Hülse 1. Die elastomerische Federanordnung 4 besteht aus einer Vielzahl von Elastomerelementen 4a, welche mittels Scheiben 4b voneinander getrennt sind. Die einzelnen Federelemente 4a sind hintereinander auf einem Kolben 7 aufgereiht, der am fahrzeugseitigen Ende an der Hülse 1 abgestützt ist. Der Kolben 7 besitzt die Form eines Bolzens, der einstückig ausgebildet ist und vorzugsweise auf seiner ganzen Länge einen konstanten Aussendurchmesser sowie eine glatte Mantelfläche besitzt. Das vordere Ende des Kolbens 7 ist mit einer Abschrägung in Form einer umlaufenden Phase versehen.In the interior of the buffer, the damping device is arranged. The damping device comprises an elastomeric damping device in the form of a spring assembly 4 and a gas-hydraulic damping device 5. Although the two damping devices 4, 5 are physically arranged one behind the other, they function parallel to each other in functional terms and together serve the resilient support of the plunger 2 on the sleeve first The elastomeric spring assembly 4 consists of a plurality of elastomeric elements 4a, which are separated from each other by means of discs 4b. The individual spring elements 4a are lined up in succession on a piston 7, which is supported on the sleeve 1 at the vehicle end. The piston 7 has the shape of a bolt, which is integrally formed and preferably has a constant outer diameter and a smooth outer surface over its entire length. The front end of the piston 7 is provided with a chamfer in the form of a circumferential phase.

Sowohl die Elastomerelemente 4a wie auch die Scheiben 4b sind mit je einer Bohrung versehen, deren Durchmesser auf den Aussendurchmesser des Kolbens 7 abgestimmt ist, so dass der Kolben 7 gleichzeitig dem Positionieren und Abstützen der Elastomerelemente 4a dient. Die Scheiben 4b werden durch die Elastomerelemente 4a derart gehalten, dass sie nicht mit dem Kolben 7 in Kontakt kommen und dessen Oberfläche beschädigen können.Both the elastomer elements 4a as well as the discs 4b are each provided with a bore whose diameter is matched to the outer diameter of the piston 7, so that the piston 7 simultaneously serves to position and support the elastomeric elements 4a. The discs 4b are held by the elastomeric members 4a so that they can not come into contact with the piston 7 and damage its surface.

Die gashydraulische Dämpfungseinrichtung 5 umfasst ein Zylinderelement 6, das an der Rückseite des Puffertellers 3 fixiert ist. Um die korrekte Lage des Zylinderelements 6 gegenüber dem Stössel 2 sicherzustellen, sind Zentrierstifte 20 vorgesehen. Um bei einer Schrägstellung des Puffertellers 3, beispielsweise ausgelöst durch exzentrisch auf den Pufferteller 3 einwirkende Druckkräfte, ein Auslenken bzw. Abrollen des Zylinderelements 6 gegenüber dem Pufferteller 3 zu ermöglichen, besteht eine kugelförmige Auflage zwischen dem Zylinderelement 6 und dem Pufferteller 3. Namentlich ist das Zylinderelement 6 auf der dem Pufferteller 3 zugewandten Seite mit einer kugelförmig ausgebildten Oberfläche 31 versehen.The gas-hydraulic damping device 5 comprises a cylinder element 6, which is fixed to the rear side of the buffer plate 3. In order to ensure the correct position of the cylinder member 6 relative to the plunger 2, centering pins 20 are provided. In order to allow at an inclination of the buffer plate 3, for example, triggered by eccentrically acting on the buffer plate 3 compressive forces, a deflection or rolling of the cylinder member 6 relative to the buffer plate 3, there is a spherical support between the cylinder member 6 and the buffer plate 3. In particular Cylinder element 6 on the buffer plate 3 facing side provided with a spherical surface 31.

Das Zylinderelement 6 ist mit einer zentralen Druckkammer 9 sowie einer koaxial dazu angeordneten, die Druckkammer 9 koaxial umfassenden Aufnahmekammer 10 in Form eines Ringraums versehen. Auf der Aussenseite des Zylinderelements 6 ist ein ringförmiger Deckel 8 angebracht, der die Aufnahmekammer 10 nach aussen begrenzt und abdichtet. Die Druckkammer 9 ist über ca. 90% ihrer Länge zylindrisch ausgebildet, wobei die Druckkammer 9 in dem der Eintauchseite des Kolbens 7 gegenüberliegenden Endbereich, d.h. im Bereich ihres Bodens 18, mit einem sich im Durchmesser konisch erweiternden Abschnitt 9a versehen ist.The cylinder element 6 is provided with a central pressure chamber 9 and a coaxially arranged, the pressure chamber 9 coaxially comprehensive receiving chamber 10 in the form of an annular space. On the outside of the cylinder element 6, an annular cover 8 is attached, which limits the receiving chamber 10 to the outside and seals. The pressure chamber 9 is cylindrical over about 90% of its length, the pressure chamber 9 in the opposite end of the immersion side of the piston 7, i. is provided in the region of its bottom 18, with a conically widening in diameter section 9a.

Die Druckkammer 9 ist vollständig mit einem Hydraulikmedium wie beispielsweise Hydrauliköl gefüllt, während die Aufnahmekammer 10 im hier dargestellten Ruhezustand mehrheitlich mit Hydraulikmedium und einem unter Überdruck stehenden Gas gefüllt ist. Die zwischen dem Zylinderelement 6 und der Aufnahmekammer 10 verlaufende Zylinderwand ist mit dem Bezugszeichen 6a versehen. Die Wandstärke der Zylinderwand 6a nimmt zu dem Pufferteller 3 hin zu. Dadurch wird die höhere Elastizität in der Mitte des Zylinders überkompensiert und stellt sicher, dass die Ringspaltfläche zwischen Kolben und Zylinderwand über den Hub abnimmt. Dadurch soll erreicht werden, dass beim dynamischen Einfedern des Stössels 2 der Druck in der Druckkammer 9, trotz kontinuierlich abnehmender Eintauchgeschwindigkeit des Kolbens 7, über einen weiten Hubbereich weitgehend konstant ist.The pressure chamber 9 is completely filled with a hydraulic medium such as hydraulic oil, while the receiving chamber 10 is filled in the idle state shown here in majority with hydraulic medium and a gas under pressure. The extending between the cylinder element 6 and the receiving chamber 10 cylinder wall is provided with the reference numeral 6a. The wall thickness of the cylinder wall 6a increases toward the buffer plate 3. This overcompensates for the higher elasticity in the center of the cylinder and ensures that the annular gap area between the piston and the cylinder wall decreases over the stroke. This is intended to ensure that the pressure in the pressure chamber 9, despite a continuously decreasing immersion speed of the piston 7, is largely constant over a wide stroke range during dynamic compression of the plunger 2.

Die in das Zylinderelement 6 eingelassene Druckkammer 9 ist auf der dem Pufferteller 3 abgewandten Seite offen, wobei der Kolben 7 über diese Öffnung in die Druckkammer 9 hineingeführt ist. Auf der der Öffnung gegenüberliegenden Seite wird die Druckkammer 9 von dem Zylinderboden 18 begrenzt. In die Zylinderwand 6a des Zylinderelements 6 sind in dem dem Fahrzeug zuzuwendenden Endbereich zwei den Kolben 7 umfassende Dichtringe 11 eingelassen. Zwischen dem Kolben 7 und der die Druckkammer 9 umfassenden Zylinderwand 6a besteht ein Durchlass in Form eines Ringspalts 15, der aus dieser Darstellung nicht ersichtlich ist. Die Grösse dieses Ringspalts 15 kann den Anforderungen entsprechend gewählt werden, wobei er sich vorzugsweise im Bereich von einigen tausendstel Millimetern bis hin zu wenigen hundertstel Millimetern bewegt. Im weiteren ist in die Zylinderwand 6a des Zylinderelements 6 ein Ringkanal 13 eingelassen, der mit dem Ringspalt 15 in Verbindung steht. Von diesem Ringkanal 13 führt ein Kanal in Form einer Bohrung 14 nach unten in die Aufnahmekammer 10. Zwischen dem Ringkanal 13 und den Dichtringen 11 ist ein Entlastungsringkanal 16 in die Zylinderwand 6a des Zylinderelements 6 eingelassen, der über einer radiale Entlastungsbohrung 17 ebenfalls mit der Aufnahmekammer 10 in Verbindung steht. Im Bereich des Zylinderbodens 18 ist das Zylinderelement 6 mit einem Rückschlagventil 19 versehen, das die Aufnahmekammer 10 mit der Druckkammer 9 verbindet und ein Zurückströmen von Hydraulikmedium von der Aufnahmekammer 10 in die Druckkammer 9 ermöglicht, wenn sich der Kolben 7 beim Ausfedern des Puffers aus der Druckkammer 9 zurückzieht. Ein derartiges Rückschlagventil 19 wird vorzugsweise auf der Unterseite in die Zylinderwand 6a eingelassen, damit beim Ausfedern des Kolbens 7 Hydraulikmedium in die Druckkammer 9 gespeist wird.The recessed into the cylinder element 6 pressure chamber 9 is open on the side facing away from the buffer plate 3, wherein the piston 7 is guided into the pressure chamber 9 via this opening. On the opposite side of the opening, the pressure chamber 9 is bounded by the cylinder bottom 18. In the cylinder wall 6a of the cylinder member 6, two sealing rings 11 surrounding the piston 7 are embedded in the end region facing the vehicle. Between the piston 7 and the pressure chamber 9 comprehensive cylinder wall 6a is a passage in the form of an annular gap 15, which is not apparent from this illustration. The size of this annular gap 15 can be selected according to the requirements, wherein it preferably moves in the range of a few thousandths of a millimeter to a few hundredths of a millimeter. In addition, in the cylinder wall 6a of the cylinder member 6, an annular channel 13 is inserted, which is in communication with the annular gap 15. From this annular channel 13, a channel in the form of a bore 14 leads down into the receiving chamber 10. Between the annular channel 13 and the sealing rings 11 is a relief annular channel 16 in the cylinder wall 6a of the cylinder member 6 is inserted, which also has a radial relief hole 17 with the receiving chamber 10 communicates. In the region of the cylinder bottom 18, the cylinder member 6 is provided with a check valve 19 which connects the receiving chamber 10 with the pressure chamber 9 and allows backflow of hydraulic medium from the receiving chamber 10 into the pressure chamber 9, when the piston 7 during rebound of the buffer from the Retracts pressure chamber 9. Such a check valve 19 is preferably embedded on the underside in the cylinder wall 6a, 7 hydraulic medium is fed into the pressure chamber 9 during rebound of the piston.

Mit zunehmender Einfederung des Puffers -Einschieben des Stössels 2- verkleinert sich die Druckkammer 9 durch den in sie eintauchenden Kolben 7. Damit der Kolben 7 weiter in die Druckkammer 9 eintauchen kann, muss Hydraulikmedium aus der Druckkammer 9 verdrängt werden. Das Hydraulikmedium strömt dabei über den ringförmigen Spalt 15 zwischen dem Kolben 7 und der Zylinderwand 6a in den Ringkanal 13, von wo es über den radial nach unten führenden Kanal 14 in die Druckkammer 10 gelangt. Zusätzlich oder anstelle eines Ringkanals 15 könnte auch ein Überströmkanal vorgesehen werden, über den das Hydraulikmedium am Kolben 7 vorbei in den Ringkanal 13 einströmen kann. Ein solcher Überströmkanal wird vorzugsweise auf der Oberseite in die Zylinderwand 6a eingelassen, damit beim Einfedern des Kolbens 7 zuerst das Gas verdrängt wird und sich die Druckkammer 9 automatisch entlüftet.With increasing deflection of the buffer -Einschieben the plunger 2-, the pressure chamber 9 is reduced by the plunging into them piston 7. So that the piston 7 can continue to dive into the pressure chamber 9, hydraulic medium must be displaced from the pressure chamber 9. The hydraulic medium flows through the annular gap 15 between the piston 7 and the cylinder wall 6a in the annular channel 13, from where it passes via the radially downwardly leading channel 14 into the pressure chamber 10. In addition or instead of an annular channel 15, an overflow channel could also be provided, via which the hydraulic medium can flow past the piston 7 into the annular channel 13. Such an overflow channel is preferably introduced on the upper side into the cylinder wall 6a, so that upon compression of the piston 7, the gas is first displaced and the pressure chamber 9 automatically vented.

Die gezeigte Ausführung, bei der der Kolben 7 von der dem Pufferteller 3 abgewandten Seite in die Druckkammer 9 hineingeführt ist, hat den weiteren Vorteil, dass sich das Hydraulikmedium aufgrund der Massenträgheit bei einem Auflaufstoss beim Zylinderboden 18 sammelt, während kleine Gasmengen, die ungewollt in die Druckkammer 9 gelangen können, sich bei der Stirnseite des Kolbens 7 sammeln. Damit ist sichergestellt, dass sich die Druckkammer 9 bei jedem Auflaufstoss selbständig entlüftet, da zuerst das Gas aus der Druckkammer 9 verdrängt wird, was insbesondere bei mehreren aufeinanderfolgenden Auflaufstössen von grosser Bedeutung ist. Bei umgekehrter Anordnung nämlich würde die kleinen Gasmengen in der Druckkammer 9 verbleiben und sich bei mehreren aufeinanderfolgenden Auflaufstössen ständig vermehren, was einen grossen Verlust an Energieaufnahme- und Dämpfungsvermögen der Dämpfungsvorrichtung und damit des ganzen Puffers bedeuten würde.The embodiment shown, in which the piston 7 is guided from the side facing away from the buffer plate 3 in the pressure chamber 9, has the further advantage that the hydraulic medium due to the inertia in a casserole at the cylinder bottom 18 collects, while small amounts of gas inadvertently in the pressure chamber 9 can get to collect at the end face of the piston 7. This ensures that the pressure chamber 9 vented independently at each impulse, since first the gas is displaced from the pressure chamber 9, which is particularly important for several successive casseroles of great importance. With a reverse arrangement, namely, the small amounts of gas would remain in the pressure chamber 9 and constantly multiply at several successive bumps, which would mean a large loss of energy absorption and damping capacity of the damping device and thus the whole buffer.

Da der Kolben 7 einen konstanten Aussendurchmesser sowie eine glatte Mantelfläche aufweist, erhöht sich mit zunehmender Einfederung des Stössels 2 der Drosselwiderstand in dem den Kolben 7 ringförmig umgebenden Spalt 15, wodurch eine Kraftzunahme über den Einschubweg erreicht wird. Diese Kraftzunahme wird jedoch nicht nur über den statischen Querschnitt des Ringspalts 15 bestimmt, sondern ggf. auch über eine elastische Ausdehnung des Zylinderelements 6, dessen Zylinderwand 6a insbesondere bei einem Auflaufstoss die Tendenz hat, sich in radialer Richtung materialelastisch nach aussen zu wölben, womit sich gleichzeitig auch der Ringspalt 15 vergrössern würde. Diese materialelastische Ausdehnung des Zylinderelements 6 wird über die Steifigkeit bzw. Wandstärke der Zylinderwand 6a beeinflusst, zumal die Wandstärke der Zylinderwand 6a entlang der Druckkammer 9 varüert. Da die Zylinderwand 6a durch den Zylinderboden 18 zum Ende hin sehr steif wird und kaum mehr radial auslenkbar ist, ist die Druckkammer 9 in diesem Endbereich mit dem sich konisch erweiternden Abschnitt 9a versehen. Dieser Abschnitt 9a soll sicherstellen, dass im extremen Belastungsfall auch gegen das Hubende hin genügend Hydrauliköl am Kolben 7 vorbeiströmen kann.Since the piston 7 has a constant outer diameter and a smooth lateral surface, increases with increasing deflection of the plunger 2 of the throttle resistance in the piston 7 annular surrounding gap 15, whereby an increase in force is achieved via the insertion path. However, this increase in force is not only determined by the static cross section of the annular gap 15, but possibly also via an elastic extension of the cylinder member 6, the cylinder wall 6a has a tendency especially in a casserole to bulge material elastic in the radial direction to the outside, bringing itself at the same time the annular gap 15 would increase. This material-elastic expansion of the cylinder element 6 is influenced by the rigidity or wall thickness of the cylinder wall 6a, especially since the wall thickness of the cylinder wall 6a varies along the pressure chamber 9. Since the cylinder wall 6a is very stiff through the bottom of the cylinder 18 towards the end and is hardly any more radially deflectable, the pressure chamber 9 is provided in this end with the conically widening portion 9a. This section 9a is to ensure that in the extreme load case even against the stroke end sufficient hydraulic oil can flow past the piston 7.

Somit wird das Federverhalten der gashydraulischen Dämpfungseinrichtung 5, und damit des ganzen Puffers, in Abhängigkeit der durch den Puffer zu verzögernden Masse und/oder der Einschubgeschwindigkeit des Stössels 2 verändert.Thus, the spring behavior of the gas-hydraulic damping device 5, and thus the entire buffer, depending on the mass to be delayed by the buffer and / or the insertion speed of the plunger 2 is changed.

Der Kolben 7 stützt sich auf seiner Rückseite nicht direkt an der Hülse 1 ab, sondern über einen ringförmigen Einsatz 22. Während die Hülse 1 vorzugsweise aus Gusseisen besteht, wird der Einsatz 22 vorzugsweise aus einem hochvergüteten Stahl gefertigt. Der ringförmige Einsatz 22 ist mit einer schrägen Druckfläche 25 versehen, die an einer korrespondierenden Ringfläche an der Rückwand 21 der Hülse 1 aufliegt. Der Einsatz 22 weist zudem einen Fortsatz 23 auf, der eine kugelförmige Oberfläche sowie eine zentrale Durchgangsbohrung 24 besitzt. An dieser kugelförmigen Oberfläche stützt sich der Kolben 7 mit einer korrespondierenden Druckfläche auf seiner Rückseite ab. Der Kolben 7 ist auf seiner Rückseite ausserdem mit einem Kolbenfortsatz 26 versehen, der in die in den Einsatz 22 eingelassene Bohrung 24 hineinragt. Der Aussendurchmesser des Kolbenfortsatzes 26 ist etwas kleiner als der Durchmesser der in den Einsatz 22 eingelassenen Bohrung 24, so dass der Kolben 7 geringfügig um die eine Art Gelenk bildende kugelförmige Oberfläche des Einsatzes 22 in radialer Richtung ausgelenkt werden kann, was im Falle von radial auf den Pufferteller 3 bzw. Stössel 2 einwirkenden Reibkräften von Vorteil ist. Am Ende des Kolbenfortsatzes 26 ist eine Verschlussanordnung 27 vorgesehen, welche dem Verschliessen eines in Längsrichtung durch den Kolben 7 führenden Kanals 28 dient. Die Verschlussanordnung 27 ist durch nicht näher bezeichnete Mittel gesichert, welche in der Bohrung 24 des Einsatzes 22 angeordnet sind. Über den Kanal 28 kann der Puffer nach dem Zusammenbau mit einem Gas und einer Hydraulikflüssigkeit gefüllt werden.The piston 7 is supported on its rear side not directly on the sleeve 1, but via an annular insert 22. While the sleeve 1 is preferably made of cast iron, the insert 22 is preferably made of a high-tempered steel. The annular insert 22 is provided with an oblique pressure surface 25 which at a corresponding annular surface on the rear wall 21 of the sleeve 1 rests. The insert 22 also has an extension 23 which has a spherical surface and a central through-bore 24. At this spherical surface, the piston 7 is supported with a corresponding pressure surface on its back. The piston 7 is also provided on its back with a piston extension 26 which projects into the recessed into the insert 22 bore 24. The outer diameter of the piston extension 26 is slightly smaller than the diameter of the inserted into the insert 22 bore 24, so that the piston 7 can be slightly deflected about the type of joint forming spherical surface of the insert 22 in the radial direction, which in the case of radially on the buffer plate 3 or ram 2 acting frictional forces is advantageous. At the end of the piston extension 26, a closure arrangement 27 is provided, which serves to close off a channel 28 leading through the piston 7 in the longitudinal direction. The closure assembly 27 is secured by unspecified means which are arranged in the bore 24 of the insert 22. Via the channel 28, the buffer can be filled after assembly with a gas and a hydraulic fluid.

Die Fig. 2 zeigt einen Querschnitt durch den Puffer entlang der Linie A-A in Fig. 1. Aus dieser Darstellung ist insbesondere der ringförmige Spalt 15 zwischen dem Kolben 7 und dem Zylinderelement 6 ersichtlich, der in dieser Darstellung zwecks besserer Erkennbarkeit jedoch übertrieben gross dargestellt ist. Im weiteren ist eine in die Hülse 1 eingelassene Nut 29 ersichtlich, in welche ein am Stössel 2 angeordneter Führungskeil 30 eingreift, um die Lage der Hülse 1 gegenüber dem Stössel 2 in Umfangsrichtung zu definieren und ein Verdrehen des Stössels 2 gegenüber der Hülse 1 zu verhindern. Schliesslich sind vier in die Rückwand 21 eingelassene Befestigungsbohrungen ersichtlich, mittels welchen die Hülse 1 an einem Schienenfahrzeug befestigt werden kann.The Fig. 2 shows a cross section through the buffer along the line AA in Fig. 1 , From this representation, in particular, the annular gap 15 between the piston 7 and the cylinder member 6 can be seen, which is shown exaggerated in this representation, however, for better visibility. In addition, a recessed into the sleeve 1 groove 29 can be seen, in which a arranged on the plunger 2 guide wedge 30 engages to define the position of the sleeve 1 relative to the plunger 2 in the circumferential direction and to prevent rotation of the plunger 2 relative to the sleeve 1 , Finally, four recessed in the rear wall 21 mounting holes can be seen, by means of which the sleeve 1 can be attached to a rail vehicle.

Beim einem langsamen Einfedern des Puffers ergibt sich eine Federkennlinie, die weitgehend mit derjenigen der elastomerischen Federanordnung 4 übereinstimmt, während beim dynamischen Einfedern zusätzlich das dynamische Verhalten der gashydraulischen Dämpfungseinrichtung 5 zum Tragen kommt, indem die Kraft bezogen auf den Einfederweg schneller ansteigt und insgesamt auf einem höheren Niveau verharrt. Durch die Grösse des Ringspalts 15, der Steifigkeit der Zylinderwand 6a und/oder des allenfalls vorhandenen Überströmkanals zusammen mit dem Ringkanal 13 und der in die Aufnahmekammer führenden Bohrung 14 kann das dynamische Verhalten beeinflusst werden. Jedenfalls befindet sich der den Kolben 7 umgebende Ringkanal 14 im Ruhezustand des Puffers hinter der Stirnfläche des Kolbens 7, d.h. er wird von Kolben 7 überdeckt, so dass von Beginn des Einfedervorgangs an die gashydraulische Dämpfungseinrichtung 5 aktiv ist, indem das aus der Druckkammer 9 verdrängte Hydraulikmedium nur über den Ringspalt 15 in den Ringkanal 13 bzw. den Kanal 14 einströmen kann, was mit einer entsprechende Drosselwirkung verbunden ist.When a slow compression of the buffer results in a spring characteristic, which largely coincides with that of the elastomeric spring assembly 4, while dynamic compression additionally the dynamic behavior of the gas-hydraulic damping device 5 comes into play by the force increases faster in relation to the compression travel and a total higher level remains. Due to the size of the annular gap 15, the rigidity of the cylinder wall 6a and / or the possibly existing overflow channel together with the annular channel 13 and the bore 14 leading into the receiving chamber, the dynamic behavior can be influenced. In any case, the annular channel 14 surrounding the piston 7 is in the resting state of the buffer behind the end face of the piston 7, ie it is covered by the piston 7, so that from the beginning of the Einfedervorgangs to the gas-hydraulic damping device 5 is active by the displaced from the pressure chamber 9 hydraulic medium can flow only through the annular gap 15 in the annular channel 13 and the channel 14, which is associated with a corresponding throttling action.

Die Vorteile des beschriebenen Puffers liegen insbesondere darin, dass er aus wenigen Teilen besteht, einfach aufgebaut ist und kostengünstig hergestellt werden kann. Diesbezüglich sei beispielsweise der Kolben 7 erwähnt, der einstückig ausgebildet ist und auf seiner ganzen Länge einen konstanten Aussendurchmesser besitzt. Es versteht sich, dass sich ein solcher Kolben 7 vergleichsweise kostengünstig fertigen lässt. Anstelle oder zusätzlich zu einer aus Elastomerelementen bestehenden Federanordnung könnten natürlich auch andere Federanordnungen wie beispielsweise mechanische Federanordnungen oder Reibungsfederanordnungen zum Einsatz kommen.The advantages of the described buffer are, in particular, that it consists of a few parts, has a simple structure and can be produced inexpensively. In this regard, for example, the piston 7 may be mentioned, which is integrally formed and has a constant outer diameter over its entire length. It is understood that such a piston 7 can be manufactured comparatively inexpensively. Of course, instead of or in addition to a spring arrangement consisting of elastomer elements, other spring arrangements such as, for example, mechanical spring arrangements or friction spring arrangements could also be used.

Neben dem Einsatz in Puffern eignen sich erfindungsgemäss gestaltete Dämpfungsvorrichtungen beispielsweise auch für den Einsatz in Kupplungen an Schienenfahrzeugen.In addition to the use in buffers designed according to the invention damping devices, for example, for use in clutches on rail vehicles.

Claims (16)

  1. Damping apparatus for pulling devices and/or shock absorption devices on rail vehicles, having a sleeve (1) and having a plunger (2) which can be moved relatively thereto, having an elastomeric and/or mechanical damping device (4) and having a gas-hydraulic damping device (5) for sprung assistance to the plunger (2) on the sleeve (1), with the gas-hydraulic damping device (5) being provided with a cylindrical pressure chamber (9) and a receiving chamber (10) which is connected thereto via at least one channel (14) and with the pressure chamber (9) being reduced in size by a piston (7) which enters it when loaded in the shock direction, and with at least one passage being formed between the piston (7) and a cylinder wall (6a) which bounds the pressure chamber (9), which passage is connected to the at least one channel (14) which leads into the receiving chamber (10), characterized in that the majority of that part of the piston (7) which can enter the pressure chamber (9) is cylindrical and has a continuously constant external diameter, and in that the piston (7) is at the same time intended for positioning of and assistance to the elastomeric and/or mechanical damping device (5).
  2. Damping apparatus according to Claim 1, characterized in that at least that part of the piston (7) which can enter the pressure chamber (9) is provided with a smooth casing surface.
  3. Damping apparatus according to Claim 1 or 2, characterized in that the pressure chamber (9) is provided in the end area opposite the end where the piston (7) enters with a section (9a) in which the diameter widens or increases.
  4. Damping apparatus according to Claim 3, characterized in that the section (9a) in which the diameter widens or increases has an axial length which corresponds to a maximum of 25% of the piston diameter.
  5. Damping apparatus according to one of the preceding claims, characterized in that the pressure chamber (9) is cylindrical over at least 75% of its length.
  6. Damping apparatus according to one of the preceding claims, characterized in that the cylinder wall (6a) which bounds the pressure chamber (9) can be deflected elastically outwards in the radial direction as a function of the speed of the piston (7) as it enters the pressure area (9) in such a way that the cross section of the at least one passage between the piston (7) and the cylinder wall (6a) which bounds the pressure chamber (9) is enlarged.
  7. Damping apparatus according to one of the preceding claims, characterized in that the wall thickness of the cylinder wall (6a) which bounds the pressure chamber (9) varies at least along the cylindrical section such that, when the plunger (2) springs in dynamically, the pressure in the pressure chamber (9) is largely constant over a wide stroke range, despite the speed at which the piston (7) enters it decreasing continuously.
  8. Damping apparatus according to one of the preceding claims, characterized in that the passage between the piston (7) and the cylinder wall (6a) which bounds the pressure chamber (9) is in the form of an annular gap (15) and/or an overflow channel which are/is connected to the at least one channel (14) which leads into the receiving chamber (10).
  9. Damping apparatus according to one of the preceding claims, characterized in that the at least one channel (14) is connected to an annular channel (13) which radially surrounds the piston (7).
  10. Damping apparatus according to one of the preceding claims, characterized in that the piston (7) is in the form of a bolt, is formed integrally and has a constant external diameter over its entire length.
  11. Damping apparatus according to one of the preceding claims, characterized in that at least one sealing element (11) which surrounds the piston (7) is incorporated in the cylinder wall (6a) which bounds the pressure chamber (9), and in that a further relief channel (16), which radially surrounds the piston (7), is arranged between the sealing element (11) and the annular channel (13) which radially surrounds the piston (7), and this relief channel (16) is connected to the receiving chamber (10) by a bore (17).
  12. Damping apparatus according to one of the preceding claims, characterized in that the piston (7) is supported on the rear face facing the vehicle on an insert (22) which is provided with a spherical surface (23), such that it can be pivoted in the radial direction along the spherical surface (23).
  13. Damping apparatus according to Claim 9, characterized in that the cylinder element (6) is fixed on the rear face of the buffer head (3) and in that the mechanical and/or elastomeric damper arrangement (4) is clamped in between the insert (22) in the end face of the cylinder element (6).
  14. Damping apparatus according to Claim 13, characterized in that the pressure chamber (9) which is incorporated in the cylinder element (6) is open on the side facing away from the buffer head (3) and the piston (7) is inserted into the pressure chamber (9) via the opening formed in this way.
  15. Damping apparatus according to Claim 14, characterized in that the annular channel (13) which radially surrounds the piston (7) is arranged behind the end surface of the piston (7) when the buffer is in the rest state, and is covered by the piston (7).
  16. Damping apparatus according to one of the preceding claims, characterized in that a non-return valve (19) is arranged between the pressure chamber (9) and the receiving chamber (10) and allows hydraulic fluid to flow back from the receiving chamber (10) into the pressure chamber (9) while the piston (7) is moving out of the pressure chamber (9).
EP06405264A 2005-06-30 2006-06-21 Damping device for drawing and/or buffing devices of railway vehicles Not-in-force EP1738985B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH11052005 2005-06-30

Publications (2)

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EP1738985A1 EP1738985A1 (en) 2007-01-03
EP1738985B1 true EP1738985B1 (en) 2008-11-19

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EP06405264A Not-in-force EP1738985B1 (en) 2005-06-30 2006-06-21 Damping device for drawing and/or buffing devices of railway vehicles

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EP (1) EP1738985B1 (en)
AT (1) ATE414644T1 (en)
DE (1) DE502006002099D1 (en)
ES (1) ES2317478T3 (en)

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Publication number Priority date Publication date Assignee Title
CN114407962B (en) * 2021-11-29 2023-03-31 宁波吉威熔模铸造有限公司 Multistage buffering formula railway carriage connector

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2703530A1 (en) * 1977-01-28 1978-08-03 Rheinmetall Gmbh HYDRAULIC DAMPER LYING IN A RAILWAY SLEEVE BUFFER
IT7953498V0 (en) * 1979-08-01 1979-08-01 Riv Officine Di Villar Perosa IMPROVEMENT OF THE DAMPERS FOR AUTOMATIC COUPLING DEVICES BETWEEN RAIL VEHICLES
DE4011439C2 (en) 1990-04-09 1994-01-20 Fischer Ag Georg Buffer with a hydraulic damper
DE19619214A1 (en) 1996-05-13 1997-11-20 Eisenbahntech Halberstadt Gmbh Shock absorbers for rail vehicles and industrial applications

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ATE414644T1 (en) 2008-12-15
DE502006002099D1 (en) 2009-01-02
ES2317478T3 (en) 2009-04-16
EP1738985A1 (en) 2007-01-03

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