EP1247716B1 - Tampon à deux phases - Google Patents

Tampon à deux phases Download PDF

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Publication number
EP1247716B1
EP1247716B1 EP20020252068 EP02252068A EP1247716B1 EP 1247716 B1 EP1247716 B1 EP 1247716B1 EP 20020252068 EP20020252068 EP 20020252068 EP 02252068 A EP02252068 A EP 02252068A EP 1247716 B1 EP1247716 B1 EP 1247716B1
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EP
European Patent Office
Prior art keywords
buffer
tube
deformable
deforming member
taper
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 - Lifetime
Application number
EP20020252068
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German (de)
English (en)
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EP1247716A1 (fr
Inventor
Klaus Mombour
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.)
Oleo International Ltd
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Oleo International Ltd
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Filing date
Publication date
Application filed by Oleo International Ltd filed Critical Oleo International Ltd
Publication of EP1247716A1 publication Critical patent/EP1247716A1/fr
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Publication of EP1247716B1 publication Critical patent/EP1247716B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61G—COUPLINGS; DRAUGHT AND BUFFING APPLIANCES
    • B61G11/00—Buffers
    • B61G11/16—Buffers absorbing shocks by permanent deformation of buffer element

Definitions

  • This invention relates to a two stage buffer suitable for use on heavy vehicles such as railway locomotives, trams, "light rail” cars, ore trains and some earth moving machines.
  • the primary application of two stage buffers is in impact protection for vehicles that travel on permanent way, especially conventional railways.
  • Two known kinds of such buffers are single stage hydraulic buffers; and single stage ring spring buffers.
  • the various kinds of single stage buffer mentioned have differing force absorption characteristics.
  • a common feature of the buffers is that they are only effective to absorb impacts of heavy vehicles at shunting speeds that typically are less then 15 km/h.
  • a two stage buffer as defined in Claim 1.
  • the arrangement is particularly good at absorbing side impacts, that may be defined as oblique impacts acting at an angle of up to 8° from the longitudinal axis of the buffer (although of course the buffer of the invention absorbs side impacts at other angles).
  • the two stage buffer of the invention may conveniently be arranged to be virtually any length, simply by choosing the dimensions of the components employed. It is as a result comparatively easy to devise a two stage buffer that in operation does not interfere with operation of anti-climb equipment fitted to a railway vehicle.
  • the characteristics of the buffer may be readily varied.
  • the choice of the diameter of the hollow tube and the deforming member therein may give rise to variations in the characteristics of the buffer.
  • buffer of the invention is that all components thereof, with the exception of the plastically deformable hollow tube, may be re-used following impact.
  • the buffer is easy to assemble and dismantle when it is needed to replace the hollow tube.
  • the locating member is compressively engaged with the deforming member.
  • the hollow tube is longitudinally tapered and of circular cross section;
  • the deforming member is of complementary external cross section; and
  • the locating member includes a slit ring force transmittingly interconnecting the deforming member and the tube in the vicinity of the said tapers.
  • the slit ring includes multiple slits, but the buffer of the invention will function even if the slit ring has only a single slit.
  • the primary function of the or each slit in the ring is to permit variation of the diameter of the ring. This in turn permits ready assembly of the ring into the (double) tapered tube.
  • the buffer start force (ie. the force needed to initiate plastic deformation of the deformable tube) is controlled by the geometry of the taper of the deformable hollow tube, and the thickness of the material of the tube in this region.
  • the start force also includes a frictional force component that results from shrink fitting of the slit ring onto the deforming member and is determined by how tightly the slit ring is so shrink fitted. In any event, from a knowledge of the tapers and of the tightness of the shrink fitting the start force is predictable.
  • the exterior of the deforming member tapers generally parallel to a taper of the interior of the tube; and the inner cross section of the slit ring tapers in a fashion complementary to the external taper of the deforming member.
  • the aforesaid geometry advantageously ensures that the slit ring is compressed into the tapers of the deformable tube, and the deforming member, whereby the buffer accommodates buff forces.
  • the deforming member includes a further hollow cylinder having an open end that is closed by a thrust plate having a part inserted into the open end and lying within the deformable tube, the thrust plate and the further, hollow cylinder being secured to one another by a tightenable fastener, tightening of the fastener causing expansion of the slit ring to increase the pressure of contact between the deforming member, the slit ring and the deformable tube.
  • the tightenability of the thrust plate into the end of the further, hollow cylinder gives rise to a known deformation start force. It is also ensures location of the slit ring relative to the plastically deformable hollow tube by virtue of positive engagement of the mutually divergent tapers of the slit ring defined hereinabove with the mutually divergent tapers formed in the interior wall of the plastically deformable, hollow tube.
  • the shrink fitting of the slit ring onto the deforming member prevents relative rotation between the components when (as in the preferred embodiment) the hollow tube and deforming member are both of circular cross-section.
  • a buffer according to the broad aspect of the invention, wherein the deforming member includes engaged therewith a locating member that acts on the deformable member interiorly of the tube; wherein the internal taper of the tube narrows with increasing distance from the buffering element and the exterior of the locating member includes the said external taper; and wherein the buffer includes, at a location remote from the said external taper, at least two surfaces formed respectively on the deformable tube and the deforming member that are capable of transmitting forces acting between the deformable tube and the deforming member in a direction other than that in which the external taper of the deforming member transmits forces to the deformable tube.
  • the locating member can if desired be solid or at least continuous.
  • the locating member abuts the deforming member, such that engagement of the external taper of the locating member with the internal taper of the tube urges the locating member against the deforming member.
  • This advantageously retains the locating member relative to the deforming member.
  • the buffer preferably also includes one or more dowels (or a functionally equivalent arrangement) linking the deforming member and the locating member together.
  • the deforming member including, at a location remote from the locating member, a first shoulder that faces away from the internal taper of the deformable member; and the deforming member includes a further shoulder that faces towards the first said shoulder such that the transmission of forces between the said shoulders retains the deforming member within the hollow tube.
  • the buffer includes a force transmitting member that force-transmittingly interconnects the first and further shoulders.
  • the buffering element acts directly on the deforming member.
  • the buffering element acts on, and moves, the plastically deformable, hollow tube that engages a stationary deforming member.
  • the deformable element includes extending therefrom a hollow housing, containing the buffering element, including co-operating constraint members for constraining movement of a moveable part of the buffer in the hollow housing.
  • This feature advantageously prevents rotation of the buffering element and other components connected thereto during an impact.
  • the housing is integral with the deforming member.
  • the force transmitting member includes an annulus defining a pair of mutually spaced, annular abutment surfaces that respectively engage the first and further shoulders; and a hollow cylinder extends from the said annulus externally of the hollow tube to define the said hollow housing.
  • the arrangement advantageously combines the functions of a force transmitting member and a hollow guide housing in a single component.
  • a moveable member of the buffer has secured thereto a buffer head, in order to provide a complete, two stage buffer.
  • the constraint members include a key secured on the said moveable part by one or more fasteners; and a keyway formed in the hollow housing and constraining movement of the key and hence the said moveable part, the said constraint members preventing detachment of the buffer head and the buffering element from one another.
  • the key that moves in the keyway also secures the buffer head relative to the buffering element in an advantageously compact arrangement.
  • the solid plate and hollow housing are held within the deformable member against the hollow cylinder by a retaining ring which is secured to the deformable member by tightenable fasteners. This locates the thrust plate relative to the plastically deformable hollow tube by virtue of positive engagement of the external taper of the thrust plate against the internal taper of the deformable member.
  • the buffering element may optionally be or include an hydraulic buffer capsule; a ring spring; or a polymeric or rubber buffer.
  • the principles of the two stage buffer of the invention are effective regardless of the precise type of buffering element chosen.
  • FIG. 1 and 2 there is shown a two stage buffer 10 according to the invention.
  • Buffer 10 includes a buffering element in the form of a per se known, hydraulic buffer capsule 12 the large diameter end 12a of which is in series, force transmitting contact with a deformable element 11 constituting the second stage of the buffer 10.
  • deformable element 11 The components of deformable element 11 are shown in detail in Figure 2.
  • Capsule 12 forms a first stage (or primary element) of the buffer and deformable element 11 the second stage (or secondary element).
  • the arrangement between hydraulic capsule 12 and the components of deformable element 11 is such that impacts experienced by capsule 12 are transmissible to deformable element 11, by virtue of contact of end 12a with a component 24 (described in more detail below) of the deformable element 11, as best shown in Figure 2.
  • the deformable element 11 includes a plastically deformable, hollow cylindrical tube 14 having an internal taper 13.
  • Taper 13 reduces in diameter with increased distance from capsule 12.
  • Deforming member 15 has an external taper 20 located at its end remote from capsule 12.
  • the angle and direction of taper 20 are substantially the same as the angle and direction of taper 13, but the dimensions of taper 20 are such as to permit member 15 to lie within taper 13.
  • the taper of the deforming member 15 is capable of transmitting force to the taper 13 of the deformable cylinder 14 by virtue of the presence of a slit ring 16 interposed between taper 20 and taper 13.
  • the slit ring may be regarded as the operative part of the deforming member; with the tube 15 (and thrust plate 18 described below) acting to support the slit ring 16.
  • Slit ring 16 is in the embodiment shown an annulus having a cross section, described in more detail below, that occupies the space between tapers 13 and 20.
  • the slit ring includes at least one slit, as indicated at 16a, whereby its diameter is adjustable.
  • slit ring 16 is elastically deformable to permit assembly of the buffer 10, by compression of ring 16 to permit it to pass into tube 14.
  • slit ring 16 may include a plurality of slits preferably spaced at equal intervals about the circumference of annulus defined by slit ring 16.
  • the slit ring may be constituted by an annulus of discrete ring segments.
  • tube 14 In addition to taper 13, that diminishes in diameter with increasing distance from capsule 12, tube 14 also includes, extending from taper 13 towards capsule 12 from taper 13, a second taper 19.
  • the exterior cross section of slit ring 16 similarly includes mutually divergent, contiguous tapers 21,22 that are complementary in angle and direction respectively to tapers 13 and 19 of plastically deformable tube 14.
  • the inner circumference of the annulus defined by slit ring 16 includes a further taper 23 of generally complementary shape to the taper 20 defined on the exterior of the free end of deforming member 15.
  • slit ring 16 is capable of transmitting forces from deforming member 15 to the taper 19 of deformable tube 14. This prevents the member 15 from being withdrawn from the tube 14.
  • the slit ring 16 is positively located, relative to tube 14, in both the buff and draft directions.
  • the taper 19 serves in particular to support the buffer head under the aforementioned side loading.
  • the section of tube 14 between the taper 19 and the mouth of the tube adjacent the buffer/buffer head is a guiding zone. Since it is essential to use ductile material for the deforming tube, this section has a thick end wall to compensate for the low yield point of the material and provide enough stiffness as is necessary for the guiding effect. In a pre-used condition the section of the tube 14 above the taper 19 and 13 is not cold hardened. When the deforming element actuates and starts to stroke the deformed area is work hardened. The work hardening assists the guiding action. However the element has to be capable of withstanding significant side load in a stage where the deforming element has not been actuated, hence the thickened wall portion.
  • the free end thereof adjacent slit ring 16 is formed as an open-ended, hollow cylinder that is closed by a thrust plate 18 formed as a parallel sided, hollow cylinder having a peripheral flange 18a at one end thereof, such that flange 18a overlies the wall of deforming member 15 at the free end thereof.
  • deforming member 15 is formed as a solid plate spanning the hollow cylindrical interior of deforming plate 24.
  • Thrust plate 18 is perforated in at least two locations as shown by throughgoing apertures 26,27 that extend parallel to the longitudinal axis of deforming member 15.
  • Plate 24 is perforated by further, threaded apertures 28,29 that are aligned with the respective apertures 26,27.
  • a plurality of screws 17 are inserted through the apertures 26,27 and threadedly engaged in apertures 28,29 to provide a retaining force for retaining the thrust plate 18 inserted into the open end of the hollow cylindrical portion of deforming member 15.
  • the screws 17 constitute a tightenable fastener for securing the thrust plate and the hollow cylinder forming part of deforming member 15 together.
  • Figure 2 shows the condition in which the screws 17 are not fully tightened.
  • the free end 20a of deforming member 15 adjacent taper 20
  • the free end 20a and the flange 18a are drawn closer together in the direction of the longitudinal axis of the buffer 10, with the result that the slit ring 16 expands in the space between the tapers 20 and 13.
  • the pressure of contact between taper 20, taper 13 and slit ring 16 increases such that the slit ring is shrink fitted on to the exterior of tube 15.
  • This arrangement conveniently and simply permits pre-setting of the start force of the secondary element of the buffer 10, whereby the secondary element 11 only operates when the impact force experienced by the buffer exceeds a predetermined value.
  • the start force is determined by both the force necessary to initiate plastic deformation of tube 14; and friction forces resulting from the shrink fitting of slit ring 16.
  • the solid plate 24 performs a secondary function, in acting as a reaction member for the large diameter end 12a of hydraulic buffer capsule 12, that rests, and consequently acts, directly thereon.
  • the capsule 12 could lie the other way round, ie. so that its small diameter end 12b engages the plate 24.
  • the hollow cylinder defining deforming member 15 extends beyond solid plate 24 as a hollow, cylindrical housing 32 ( Figure 1) that encircles capsule 12.
  • Housing 32 includes co-operating constraint members for constraining movement of a moveable part of the buffer 10 within the hollow housing 32, in the form of a slot 33 extending longitudinally along part of the length of housing 32 to define a keyway; and a key 34 that is slidably constrained to move longitudinally in slot 33.
  • Key 34 is secured by further screws 36 to the cylindrical parts of a buffer head 37 that may be of per se known design.
  • the portion 37a of buffer head 37 that terminates the interior of the hollow, cylindrical part thereof is in force-transmitting engagement with the free end of the piston 12b of capsule 12.
  • the deforming member 15 includes a hollow cylinder that is open at either end and is received within the hollow interior of tube 14.
  • the open end 15a of deforming member 15 that is remote from capsule 12 is closed by a locating member 51 formed as a parallel sided, solid cylinder having at its free end an external taper 52 which decreases in diameter in the direction away from buffer capsule 12.
  • Tube 14 includes an internal taper 53 that is of complementary shape to external taper 52. Engagement of the tapers 52, 53 tends to retain locating member 51 relative to deforming member 15.
  • locating member 51 and deforming member 15 are secured together by a plurality of dowels 43 inserted into mutually aligned bores 54 formed respectively in end 15a of deforming member 15 and the adjacent, rear face of locating member 51.
  • the bores 54 extend parallel to the longitudinal axis of deforming member 15.
  • the surface 56 is defined in the end of member 15 remote from taper 52, as an annular shoulder that results from the presence of a reduced diameter end portion 15b of member 15. As a result, surface 56 faces capsule 12.
  • Juxtaposed surface 57 is defined by a radially inwardly extending flange ring 59 that is secured to the open end of tube 14 (in which member 15 is received) by a series of fasteners such as the screws 61 shown threadedly received in associated bores; or by equivalent means.
  • a force transmitting member in the form of hollow cylinder 58 interconnects the surfaces 56, 57 so as to transmit the aforesaid forces therebetween.
  • Cylinder 58 has a free end that engages surface 56; and an upstanding shoulder 58a that engages surface 57.
  • the shoulder 58a terminates in a cylindrical wall of lesser diameter than cylinder 58. This wall protrudes externally of the tube 14 to define a housing 32 that is functionally similar to housing 32 visible in Figure 1.
  • the diameters of the various cylindrical components in the vicinity of surfaces 56, 57 and flange ring 59 are such as to cause retention of cylinder 58 and deforming member 15 within tube 14 while permitting movement of deforming member 15 along tube 14 when required.
  • deforming member 15 is closed by a solid plate 24.
  • the solid plate 24 acts as a reaction member for the large diameter end 12a of hydraulic buffer capsule 12 that rests, and consequently acts, directly thereon.
  • the capsule 12 lies the other way round, so that its small diameter end 12b engages the plate 24.
  • the flange ring 59 constitutes a tightenable fastener for securing the hollow cylinder 58, solid plate 24, and deforming member 15 within tube 24. This arrangement prevents the deforming member 15 from being withdrawn from the tube 14.
  • the locating member 51 is positively located relative to tube 14 in both the buff and draft directions.
  • Housing 32 encircles capsule 12. Housing 32 extends in a direction parallel to deformable member 15 towards the buffer head 37.
  • capsule 12 includes an hydraulic circuit that damps the impact energy according to a known force - stroke curve.
  • the hydraulic capsule 12 also typically contains an energy converter in the form of a volume of compressible gas, that restores the capsule 12 to its pre-impact length after occurrence of an impact.
  • the resistive force of the hydraulic buffer capsule 12 is dependant upon the internal static forces controlled by the gas inflation of the buffer plus the dynamic element of oil forced through an orifice.
  • the deformable member 14 moves at such a velocity that the effective velocity of the plunger relative to the cylinder would generate eg. a 1200kN load across the hydraulic buffer. It is thus likely that the hydraulic and deforming stages of the buffer would operate concurrently.
  • deforming member 15 By virtue of the rigid construction of deforming member 15, impact forces experienced by solid plate 24 are transmitted via taper 20 and slit ring 16 (in the Figure 1 embodiment); or member 51 (in the Figure 4 embodiment) to taper 13 or taper 53 (as appropriate) of deformable tube 14.
  • deforming member 15 travels along deformable tube 14 effectively ironing the walls thereof in the region to the right of taper 13 as shown in Figures 1 and 2, with the result that the taper 13 "moves" along the length of the tube 14.
  • deformable element 11 gives rise to a peak force component 41 that is greater than the start force 39 necessary to initiate plastic deformation at the start of the stroke.
  • the buffer 10 of the invention includes an inherent assurance that plastic deformation of the tube 14 does not commence unless the impact force exceeds a predetermined threshold value that in the embodiment plotted in Figure 3 is approximately 1400 kN.
  • the constant force characteristic of the secondary element 11 of the buffer is substantially a straight, horizontal line whereby the area under the plotted line of Figure 3 is maximised. It follows from this that energy absorption in the secondary element 11 also is a maximum.
  • Figure 3 plots a dynamic force component. Similar results can of course be plotted for a static force.
  • the static force is typically 5% higher than the dynamic (impact) force.
  • Figure 3 shows the force/stroke characteristic of a buffer 10 according to the invention in which the constant force (represented by portion 42 of the plot) is designed to be 1200kN.
  • the constant force represented by portion 42 of the plot
  • FIG. 3 shows the force/stroke characteristic of a buffer 10 according to the invention in which the constant force (represented by portion 42 of the plot) is designed to be 1200kN.
  • the buffer of the invention is highly effective at buffering side loads applied obliquely to the buffer head at angles of up to 8° to the longitudinal axis of the buffer.
  • the primary buffering element may of course be replaced by other energy absorbing apparatuses including, but not limited to, ring springs.
  • the choices of material of the slit ring 16 and deformable tube 14 assure the correct constant force 42.
  • the slit ring 16 is manufactured from hardened steel BS970 708 M40t-condition (min hardness 266 VH), in order to ensure that it does not deform as it deforms tube 14.
  • slit ring 16 could be manufactured from other materials of known hardness.
  • Tube 14 is manufactured from annealed, cold drawn steel tube.
  • Deforming member 15 can be manufactured from eg. a general construction steel (such as BSEN10025:1993:S355J2G3) that is normalised to permit safe plastic deformation.
  • a general construction steel such as BSEN10025:1993:S355J2G3
  • a further advantage of the apparatus of Figures 1 and 2 is that the slit ring 16 causes localised brinelling of tube 14 during operation to absorb impact energy. Since the direction of movement of slit ring 16 in tube 14 is parallel to the longitudinal axis of tube 14, such brinelling effectively keys slit ring 16 in the tube 14 and further prevents rotation of deforming member 15 relative to tube 14 during working of the secondary element 11.
  • the buffer Since the force characteristic of the buffer 10 is accurately controllable (as evidenced by the plot constituting Figure 3), the buffer operates so as not to interfere with anti-climb apparatus that may be secured to eg a railway vehicle.
  • the length of tube 14 may be selected at the option of the buffer designer.
  • a unit intended for installation on a locomotive headstock might have a maximum stroke (ie effective length of tube 14) of 600 mm; whereas a railway carriage might have a maximum stroke of 150 mm.
  • the choice of the length of tube 14 also permits manufacture of a device having a minimal risk of interfering with anti-climb apparatus.
  • two keyways lie directly opposite one another on the outer surface of locating member 51.
  • the keyways key themselves onto the deformable member. This effect further prevents rotation of deforming member 15 relative to tube 14 during working of the secondary element 11.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Dampers (AREA)

Claims (21)

  1. Amortisseur à deux niveaux (10) comprenant un élément d'amortissement (12) et un élément déformable (11) raccordé en série de telle manière que des forces soient transmissibles de l'élément d'amortissement (12) à l'élément déformable (11), l'élément d'amortissement (12) étant en prise à transmission de force avec l'élément déformable (11),
       de telle manière que les forces subies par l'amortisseur (12) qui sont insuffisantes pour provoquer la déformation plastique du tube (14) soient amorties par l'élément d'amortissement (12) ;
       l'amortisseur à deux niveaux (10) étant caractérisé en ce que :
    l'élément déformable (11) comprend :
    un tube creux plastiquement déformable (14) ayant une conicité interne (13) ; et
    un élément déformant (15) de section transversale externe généralement complémentaire à l'intérieur du tube (14) et ayant une conicité externe (20), l'élément déformant (15) étant inséré dans le tube (14) pour que la conicité (20) de l'élément déformant (15) soit capable de transmettre des forces à la conicité interne (13) du cylindre (14) et vice versa ;
       et dans lequel des forces plus grandes transmises de la conicité (20) de l'élément déformant (15) à la conicité (13) du tube (14) provoquent une déformation plastique de celle-ci ;
       l'élément déformant (15) comprend, en prise avec lui, un élément de contact (16) qui agit sur l'élément déformable (11) à l'intérieur du tube (14) ;
       le tube (14) comprend deux conicités mutuellement divergentes (13,19) ; et
       dans lequel la section transversale extérieure de l'élément de contact (16) s'effile dans deux directions mutuellement divergentes (21, 22) d'une manière complémentaire à la forme effilée du tube (14), moyennant quoi l'élément de contact (16) est positivement situé par rapport à l'élément déformable (11).
  2. Amortisseur (10) selon la revendication 1 dans lequel l'élément de contact (16) est en prise de manière compressive avec l'élément déformant (15).
  3. Amortisseur (10) selon la revendication 1, dans lequel le tube (14) est longitudinalement effilé et de section transversale circulaire ; l'élément déformant (15) a une section transversale externe complémentaire ; et l'élément de contact (16) comprend un anneau fendu (16) interconnectant l'élément déformant (15) et le tube (14) dans le voisinage desdites conicités (20, 23) en transmettant un effort.
  4. Amortisseur (10) selon l'une quelconque des revendications 2 ou 3 dans lequel l'extérieur de l'élément déformant (15) s'effile d'une manière généralement parallèle à une conicité (13) de l'intérieur du tube (14) ; et dans lequel la section transversale intérieure de l'élément de contact (16) s'effile d'une manière complémentaire à la conicité extérieure (20) de l'élément déformant (15).
  5. Amortisseur (10) selon la revendication 2 ou l'une quelconque des revendications précédentes dépendant de celle-ci dans lequel l'élément déformant (15) comprend un autre cylindre creux ayant une extrémité ouverte qui est fermée par une plaque de poussée (18) ayant une partie insérée dans l'extrémité ouverte et se trouvant à l'intérieur du tube déformable (14), la plaque de poussée (18) et l'autre cylindre creux étant fixés l'une à l'autre par un élément de fixation.
  6. Amortisseur (10) selon la revendication 1 dans lequel l'élément déformant (15) comprend, en prise avec celui-ci, un élément de contact (51) qui agit sur l'élément déformable (11) à l'intérieur du tube (14) ; dans lequel la conicité interne du tube (53) se rétrécit à mesure que la distance vers l'élément d'amortissement (12) augmente et l'extérieur de l'élément de contact (51) comprend ladite conicité externe (52) ; et dans lequel l'amortisseur (10) comprend, dans un endroit éloigné de ladite conicité externe (52), au moins deux surfaces (57, 56) formées respectivement sur le tube déformable (14) et l'élément déformant (15) qui sont capables de transmettre des forces agissant entre le tube déformable (14) et l'élément déformant (15) dans une direction autre que celle dans laquelle la conicité externe (52) de l'élément déformant (15) transmet des forces au tube déformable (14).
  7. Amortisseur selon la revendication 6 dans lequel l'élément de contact (51) bute contre l'élément déformant (15), de sorte que l'entrée en prise de la conicité externe (52) de l'élément de contact (51) avec la conicité interne (53) du tube (14) pousse l'élément de contact (51) contre l'élément déformant (15).
  8. Amortisseur (10) selon la revendication 7 comprenant une ou plusieurs chevilles (43) reliant l'élément déformant (15) et l'élément de contact (51).
  9. Amortisseur (10) selon l'une quelconque des revendications 6 à 8 dans lequel l'élément déformant (15) comprend, dans un endroit éloigné de l'élément de contact (51) un premier épaulement (56) qui est orienté à l'écart de la conicité interne (53) de l'élément déformable (11); et l'élément déformant (15) comprend un autre épaulement (57) qui est orienté vers le premier épaulement (56) de sorte que la transmission des forces entre lesdits épaulements (56, 57) maintient l'élément déformant (15) à l'intérieur du tube creux (14).
  10. Amortisseur (10 selon la revendication 9 comprenant un élément de transmission de force (58) qui interconnecte le premier (56) et l'autre (57) épaulement en transmettant une force.
  11. Amortisseur (10) selon l'une quelconque des revendications 6 à 10 comprenant un élément de bride annulaire (59) qui est fixé à l'extrémité ouverte du tube (14) pour définir ledit autre épaulement (57).
  12. Amortisseur (10) selon l'une quelconque des revendications précédentes dans lequel l'élément d'amortissement (12) agit directement sur l'élément déformant (15).
  13. Amortisseur (10) selon l'une quelconque des revendications précédentes dans lequel l'élément déformable (11) comprend un logement creux (32) s'étendant à partir de là et contenant l'élément d'amortissement (12) et comprenant des éléments de contrainte coopérants (33, 34) pour contraindre le mouvement d'une pièce mobile de l'amortisseur (12) dans le logement creux (32).
  14. Amortisseur (10) selon la revendication 13 dans lequel le logement (32) fait partie intégrante de l'élément déformant (15).
  15. Amortisseur (10) selon la revendication 13 lorsqu'elle dépend de la revendication 10, dans lequel l'élément de transmission de force (38) comprend une paire de surfaces de butées annulaires espacées entre elles et définissant un anneau, qui entrent respectivement en prise avec les premier (56) et autre (57) épaulements ; et dans lequel un cylindre creux s'étend à partir dudit anneau à l'extérieur du tube creux pour définir ledit logement creux (32).
  16. Amortisseur (10) selon l'une quelconque des revendications précédentes dans lequel un élément mobile de l'amortisseur (10) a une tête d'amortisseur (37) fixée sur celui-ci.
  17. Amortisseur selon la revendication 16 lorsqu'elle dépend de la revendication 13, dans lequel les éléments de contrainte comprennent une clavette (34) fixée sur ladite pièce mobile par un ou plusieurs éléments de fixation (36) ; et
       un logement de clavette (33) formé dans le logement creux (32) et contraignant le mouvement de la clavette (34) et donc de ladite pièce mobile, lesdits éléments de contrainte (33, 34) empêchant le détachement de la tête d'amortisseur (37) et de l'élément d'amortissement (12) l'un de l'autre.
  18. Amortisseur (10) selon l'une quelconque des revendications précédentes dans lequel le tube creux déformable (14) comprend une région épaissie que le travail durcit pendant la déformation dudit tube (51).
  19. Amortisseur selon l'une quelconque des revendications précédentes, dans lequel l'élément d'amortissement (12) est ou comprend une capsule d'amortissement hydraulique.
  20. Amortisseur (10) selon l'une quelconque des revendications 1 à 18 dans lequel l'élément d'amortissement (12) est ou comprend une bague élastique.
  21. Amortisseur (10) selon l'une quelconque des revendications 1 à 18 dans lequel l'élément d'amortissement est ou comprend un élément d'amortissement en polymère ou en caoutchouc.
EP20020252068 2001-04-04 2002-03-22 Tampon à deux phases Expired - Lifetime EP1247716B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0108413A GB0108413D0 (en) 2001-04-04 2001-04-04 A two stage buffer
GB0108413 2001-04-04

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EP1247716A1 EP1247716A1 (fr) 2002-10-09
EP1247716B1 true EP1247716B1 (fr) 2004-09-08

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EP (1) EP1247716B1 (fr)
DE (1) DE60201141T2 (fr)
GB (1) GB0108413D0 (fr)

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CN101674969B (zh) * 2007-05-08 2012-01-11 沃依特专利有限责任公司 用于多节车辆的能量消耗装置
KR20180076379A (ko) * 2016-12-27 2018-07-06 한국철도기술연구원 철도차량 연결기용 충격흡수장치
US10988149B2 (en) 2015-11-30 2021-04-27 Dellner Dampers Ab Energy absorption device and method

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SE526663C2 (sv) * 2004-02-04 2005-10-18 Dellner Couplers Ab Draginrättning för tågkoppel samt deformationsrör härför
EP1740435B1 (fr) * 2004-04-27 2008-04-23 Sieghard Schneider Tampon a boisseau
DE102004045600A1 (de) * 2004-09-17 2006-04-06 Keystone Bahntechnik Gmbh Puffersystem
PL1752353T3 (pl) * 2005-08-10 2008-05-30 Voith Turbo Scharfenberg Gmbh & Co Kg Urządzenie rozpraszające energię o podwyższonej sile zadziałania
DE202006014402U1 (de) * 2006-09-15 2006-11-30 Fahrzeugtechnik Dessau Ag Railroad Technologies Schienenfahrzeug mit Crashausrüstung
ATE533683T1 (de) * 2007-09-11 2011-12-15 Voith Patent Gmbh STOßSICHERUNG
KR100916597B1 (ko) 2007-12-06 2009-09-11 한국철도기술연구원 철도차량 튜브완충기용 스테빌라이저 및 스테빌라이저부가형성된 철도차량용 튜브완충기
EP2227410A4 (fr) * 2007-12-06 2013-03-13 Korea Railroad Res Inst Tampon tubulaire pour véhicules ferroviaires
KR100916595B1 (ko) 2007-12-06 2009-09-11 한국철도기술연구원 철도차량용 복합식 튜브 완충기
DE502007004212D1 (de) * 2007-12-17 2010-08-05 Voith Patent Gmbh Energieverzehrvorrichtung für einen Wagenkasten eines mehrgliedrigen Fahrzeuges
US8051995B2 (en) 2007-12-17 2011-11-08 Voith Patent Gmbh Energy dissipation device for a car body of a multi-member rail vehicle
CN102514588A (zh) 2011-12-16 2012-06-27 唐山轨道客车有限责任公司 排障吸能装置及动车组头车
EP2687416B1 (fr) * 2012-07-16 2014-09-03 Voith Patent GmbH Sécurité anti-chocs, en particulier sous forme d'un tampon de crash
JP6247471B2 (ja) * 2013-07-31 2017-12-13 川崎重工業株式会社 鉄道車両用衝突エネルギー吸収装置および鉄道車両
GB2517970B (en) 2013-09-06 2016-02-10 T A Savery & Co Ltd A buffer
EP2949539B3 (fr) 2014-05-28 2021-04-14 Dellner Couplers AB Dispositif de dissipation d'énergie et appareil de connexion comprenant un tel dispositif
DE102015204008A1 (de) * 2015-03-05 2016-09-08 Bombardier Transportation Gmbh Drehgelenk zum drehgelenkigen Verbinden von Schienenfahrzeugen
CN105292164B (zh) * 2015-10-16 2017-11-14 中南大学 伸缩式轨道车辆碰撞吸能装置
DE102016107399A1 (de) * 2016-04-21 2017-10-26 Festo Ag & Co. Kg Pneumatikzylinder
PL233589B1 (pl) 2017-08-29 2019-11-29 Axtone Spolka Akcyjna Aparat pochlaniajacy

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DE364072C (de) * 1922-11-16 Ernst Kreissig Eisenbahnpuffer
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NL134701C (fr) * 1965-11-12
DE1912049C3 (de) * 1969-03-07 1981-08-13 Scharfenbergkupplung Gmbh, 3320 Salzgitter Vorrichtung zur Aufnahme übergroßer Stöße
BE756205A (fr) * 1969-09-22 1971-03-01 Bergische Stahlindustrie Dispositif destine a absorber des forces se manifestant par saccades
FR2775240B1 (fr) * 1998-02-25 2000-12-22 Nantes Ecole Centrale Perfectionnement aux tampons amortisseurs d'accostage pour vehicules ferroviaires

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101674969B (zh) * 2007-05-08 2012-01-11 沃依特专利有限责任公司 用于多节车辆的能量消耗装置
US10988149B2 (en) 2015-11-30 2021-04-27 Dellner Dampers Ab Energy absorption device and method
KR20180076379A (ko) * 2016-12-27 2018-07-06 한국철도기술연구원 철도차량 연결기용 충격흡수장치
KR101898097B1 (ko) 2016-12-27 2018-09-13 한국철도기술연구원 철도차량 연결기용 충격흡수장치

Also Published As

Publication number Publication date
GB0108413D0 (en) 2001-05-23
DE60201141T2 (de) 2005-10-13
EP1247716A1 (fr) 2002-10-09
DE60201141D1 (de) 2004-10-14

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