US3818841A - Railway car roll stabilizing bogie - Google Patents

Railway car roll stabilizing bogie Download PDF

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Publication number
US3818841A
US3818841A US00171608A US17160871A US3818841A US 3818841 A US3818841 A US 3818841A US 00171608 A US00171608 A US 00171608A US 17160871 A US17160871 A US 17160871A US 3818841 A US3818841 A US 3818841A
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United States
Prior art keywords
bolster
suspension system
lower frame
articulated
bogie
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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
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US00171608A
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English (en)
Inventor
M Julien
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Luxembourgeoise de Brevets et de Participations SA
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Luxembourgeoise de Brevets et de Participations SA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/04—Bolster supports or mountings
    • B61F5/06—Bolster supports or mountings incorporating metal springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F1/00—Underframes
    • B61F1/08—Details
    • B61F1/14—Attaching or supporting vehicle body-structure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/04—Bolster supports or mountings
    • B61F5/08—Bolster supports or mountings incorporating rubber springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/22—Guiding of the vehicle underframes with respect to the bogies
    • B61F5/24—Means for damping or minimising the canting, skewing, pitching, or plunging movements of the underframes

Definitions

  • a suspension for ahigh-speed railway vehicle comprises between the body and the bogie chassis a bolster platform which is connected to the body by a pivot allowing the free rotation of the bogie in the curves, in combination with springs.
  • the bolster platform is connected to a transom of the bogie chassis by an articulated trapezium, with springs ensuring the stability.
  • the body can thus orientate itself in the direction of the centrifugal force in the curves without loss of the stability.
  • the articulations of the trapezium are situated very low, which reduces to a minimum the dynamic transfers to the axles.
  • the insufficiency of cant has to be compensated by the rolling stock and, more especially since the wheels have to preserve contact with the rails by the suspended portion of thevehicles. It is accordingly sufficient to compel themedian plane of thebodies to have, in relation to thenormal to the transverse slope of the 2 "track, angles of tilt equal tothe angular insufficiency of cant and directed towards the inside of the curve.
  • the reliability of such systems is no longer, nowadays, debatable and their cost can be reduced to reasonable limits.
  • these solutions require the use of a large source of mechanical energy.
  • the insensitivity of the vertical suspension to the dynamic transfers of load due to longitudinal acceleration ordeceleration is a preferred embodiment, the insensitivity of the vertical suspension to the dynamic transfers of load due to longitudinal acceleration ordeceleration.
  • Thefirst relating to the attachment of the bogiesto thevehicle bodies, requires thatthe points of application to bogiechassis of thelongitudinal resultantsof inertia of the body (upon acceleration orupon braking) sion system, allowingthe aforesaid disadvantages to be be situated at a level as close as possible to that of the rails, so as to reduce to a minimum the dynamic transfers of vertical loads between axles of the bogie.
  • the invention consists, principally, in suspensions of vehicles of the type in question comprising, as is known, on each carriage or bogie whether or not provided with a relatively rigid primary suspension a bolster, which will also be referred to as, an intermediate element or a platform between the bogie chassis and vehicle body, and connected to these latter by connection systems, in arranging these systems-in such a way that the one interposed between bolster platform and body comprises, on the one hand, a kinematic connection suited to ensure only freedom of vertical translation and freedom of rotation about an axis for the displacement of the bogie and, on the other hand, a resilient connection for bearing the vertical loads, and that the connection system between platform and bogie chassis comprises, on the one hand, a kinematic connection arranged so as to allow the platform and the body to move in rotation, in relation to the chassis, in a transverse plane itself articulated about a median transverse axis of the chassis and situated at the base of this latter
  • the kinematic connection between platform and bogie chassis will be constituted essentially by an articulated trapezium system, with the large base on the chassis and the bogie small base on the platform, the lateral sides of the trapezium being articulated, at their base, on a median bottom traverse of the chassis, by articulations of the type with swivel joint or universal joint.
  • FIGS. 1 and 2 show diagrammatically and respectively in elevation and semi-section and in partial side view, a railway vehicle having bogies which may have a relatively stiff primary suspension, and provided with a suspension system in accordance with the invention
  • FIGS. 3 and 4 show similarly, respectively in plan view and in side view, portions being broken away, another embodiment of the invention.
  • FIG. 5 shows in plan a variant of the embodiment of FIG. 3
  • FIG. 6 shows in section, on a larger scale, a connection element of the assembly of FIG. 5;
  • FIGS. 7 and 8 show respectively and partially, in elevation and in side view, an assembly similar to that of FIGS. 1 and 2, but of another embodiment
  • FIG. 9 shows in partial elevation an assembly similar to that of FIGS. 3 or 5 and 4, but according to a further embodiment
  • FIG. 10 finally, shows diagrammatically a vehicle provided with suspensions in accordance with the invention, according to the embodiments of FIGS. 3, 4 and 5.
  • the drawings show suspensions between a body 1 of a railway vehicle, and one of its bogie trucks.
  • the bogie chassis also referred to as the lower frame includes side frames 2 and a connecting transom 11.
  • An intermediate movable element or bolster 3 which will also be called a platform, is connected to the body and the chassis respectively by two connection assemblies or connection stages, namely: the upper stage E, between body and platform, and the lower stage E, between platform and bogie chassis.
  • Each of the stages E, and E comprises, co-acting in parallel:
  • a kinematic connection device defining geometrically the relative mobilities of the elements in question
  • a resilient connection device controlling, through springs, the equilibrium of the stresses brought into play in accordance with at least one of the aforegoing relative mobilities.
  • connection stages have distinct main functions:
  • the upper stage E ensures the function of guided vertical suspension of the body and the pivotal freedom of the bogie
  • the lower stage E ensures the function of pendular transverse suspension of the body and the hunting of the bogie.
  • the two stages co-operate through their kinematic connections in the function of effecting longitudinal attachment between body and bogie.
  • the two stages perform the following functions:
  • the kinematic connection keeps the platform and the body parallel one to the other and allows between them only a freedom of vertical translation (suspension) and a freedom of rotation abouttheir common vertical median axis (bogie, pivoting),
  • the kinematic connection of the lower stage E allows the platform to move, in relation to the bogie chassis, in a transverse plane itself articulated about a median transverse axis situated at the bottom portion of the chassis, this latter mobility permitting hunting of the bogie.
  • the mobility in the transverse plane will be defined essentially, as shown in FIGS. 1 and 2, by the deformation of a trapezium having articulated rigid elements whose small base is formed by the platform 3, the large base formed by the bogie chassis, and whose sides are constituted by two connecting elements 6, comparable (in projection onto the plane of the movement) to two oblique connecting rods converging (in the state of rest and on a horizontal track) at a point such as I of the median plane of symmetry of the body, the altitude of which point is advantageously situated, as a result of suitable choice of the proportions of the articulated trapezium substantially at the level of half the height of the lateral surface of the body so as virtually to cancel any movement of rocking under the action of a thrust of lateral wind F,.. v
  • This mobility finds expression, for any transverse excursion GG of the center G of the platform3 in relation to its mean position, in a tilting of this platform and therefore of the body which is fastened to it about a longitudinal axis, a tilting whose angular value defines the angle of tilt y of the body.
  • FIGS. 3 to 6, as well as 9 and '10 and which eliminate sliding consists in connecting the platfomi 3, at its center in an articulated manner, to a vertical pivot 18 carried at 17 by the said platform and traversing a clevis or the like 19 integral with at least one arm 20 mounted in an oscillating manner on the body, at a suitable distance b from the median transverse axis of the bogie.
  • a triangular disposition may be used, comprising two arms of this type converging on the aforesaid pivot and articulated about axes 21a, 21b, which are also convergent, or else a bipod single assembly 20 such as that of FIG. 3 may be used with interpolation of resilient bushes at the articulations.
  • Such an articulated triangle assembly has the effect of keeping thepivotal axis 18 in the median body plane while allowing it as well as the platform 3 angular movement in relation to the bottom of the body 1, in the longitudinal median plane, very close to the vertical translation tangent to the position of equilibrium.
  • a variant, shown in FIGS. 5 and 6, consists in having recourse to a single arm 20, arranged in the vertical median plane of the body and articulated at 21, in combination with transverse stays 50 substantially horizontal in the mean position of rest and articulated at their ends respectively to the body 1 and to the central arm 20 with the aid of appropriate clevises 51, the said stays 50 being provided with a limited longitudinal extensibility obtained for example through the incorporation at their terminal articulations of elastic bushes such as 52 (FIG. 6).
  • this suspension having an oscillating arm advantageously includes an anti-roll device, arranged for example in the following manner (FIGS. 3 to 5 and 9).
  • clevises 24a and 24b are connected respectively to pivot pins 25a and 25b mounted at the ends of the platform 13 by substantially vertical connecting rods 26, articulated to the said clevises and pivot pins.
  • the resilient connection means of the upper stage E is constituted for example by vertical suspension springs 7 (FIG. I) inserted between body 1 and platform 3 and the choice of which is arbitrary (helical springs, pneumatic springs, etc.) as well as their arrangement (number, spacing, etc.).
  • vertical suspension springs 7 (FIG. I) inserted between body 1 and platform 3 and the choice of which is arbitrary (helical springs, pneumatic springs, etc.) as well as their arrangement (number, spacing, etc.).
  • arbitrary helical springs, pneumatic springs, etc.
  • their arrangement number, spacing, etc.
  • the lower stage comprises two identical inverted rigid traiangles 6 disposed symmetrically on either side of the longitudinal vertical median plane of equilibrium at rest of the bogie chassis and of the platform 3.
  • the triangles 6 are articulated at their upper base portions on two longitudinal pins 8 integral with the platform 3 and, by their lower apices, which carry universal joints 9 having a swivel joint, for example, on to cooperating support surfaces 10 for example cups integral with the bogie chassis and situated as low as possible for example at the ends, adjacent to the longerons, of a lower tranverse or transom 11 forming the large base of the transverse suspension trapezium.
  • the triangles 6 thus transmit to the bogie chassis the vertical loads of the body I and of the platform 3 under compression stresses.
  • the suspension in accordance with the invention gives rise to only small differences of adhesion load between the axles of the bogie under the effect of the braking.
  • the function of the universal joint is divided into two orthogonal rotations.
  • the lower traverse 11 instead of being integral with the bogie chassis, is connected to this latter, in the vicinity of the longerons, by two elastic articulations 13 capable of transmitting to the said longerons the vertical and transverse loads emanating from the body 1 and from the platform 3 but provided furthermore, about their common longitudinal axis (traverse to the bogie chassis) with angular elastic mobility to allow hunting of the bogie.
  • This embodiment offers the advantage of combining in a single subassembly all the elements of the transverse kinematic connection and of facilitating the mounting thereof, the articulation blocks 13 being able to be slipped easily between the longerons of the chassis 2 and held in position before fixing.
  • the resilient connection which the lower stage E, comprises is arranged, for example, in the following manner.
  • any system of springs such as that schematized at 12 in FIG. 1 acting in the plane of transverse suspension and bearing respectively on the chassis and on the platform 3 is capable when suitably dimensioned of applying to the said platform transverse forces opposing the negative restoring force due to the unbalancing torque due to gravity.
  • those spring devices will be chosen which, in addition to exerting the desired transverse restoration forces, are capable of exerting in a permanent manner, upward thrusts on the platform 3, whose values can thus diminish the gravitational loads'applied to the triangles 6 or cross-braced sidebeams 6,, and to their articulations.
  • FIGS. 7 and 8 In a first embodiment (FIGS. 7 and 8), applicable more especially to the case where the lower traverse 11 is endowed with freedom for pivotal movement, two pins 14a are mounted on either side of the central portion of this traverse, parallel to the end pins 14, and on these pins are articulated the lower ends of two pairs of telescopic sliding connecting rods 15, the upper ends of which are, in their turn, articulated on the pins 8 of the platform 3, between the articulations of the side beams 6,,. Each end of the sliding connecting rods 15 is provided with a plate 16.
  • a helical spring 12 is mounted on each rod between the two plates, the said spring being in a state of prestressed compression in the mean position of the system.
  • the connecting rods 16 therefore exert equal oblique thrusts on the pins 8.
  • the horizontal components of these thrusts on each side counter-balance one another but their components F in the direction of the planes of the side beams 6,, are directed upwardly against the loads exerted by gravity.
  • FIG. 9 Another embodiment of resilient restoration (shown in FIG. 9), effecting a reduction in the static loads applied to the triangles 6 or side beams 6 uses still in a symmetrical arrangement and in the transverse plane of suspension rubber or rubber-metal elements 27, of substantially prismatic shape, whose bearing surter-balancing the unbalancing torque due to gravity.
  • a suitable geometrical arrangement is preferably chosen whereby any tendency of the body 1 to incline forwards or rearwards under the action of a deceleration or of an acceleration is avoided.
  • elastomers could be used for the various articulations between rigid elements
  • a suspension system for supporting at least a por tion of a vehicle body on a bogie comprising:
  • a lower frame including side frames supported on wheel axles of the bogie and a transom extending from one side frame to the other and rigidly connected to said side frames,
  • first mechanic] connection means comprising an articulated system pivotally connected to the lower frame and the bolster, the instantaneous center of rotation of which articulated system is situated at a higher level than the level of the center of gravity of the body, such that tilting movement from an upright position of said bolster relative to said lower frame transversely of the vehicle frame lowers the center of gravity of the vehicle body,
  • first resilient means interconnecting said lower frame and said bolster for exerting on said bolster a resilient restoring force opposing instability of the body due to lowering of the center of gravity of the body during tilting movement of the body around said center of rotation away fram a vertical line through the centerof the lower frame
  • a second mechanical connection between said bolster and said body including means for limiting movement between said bolster and said body to relative vertical displacement and relative rotation about a substantially vertical axis
  • each side of the trapezium is arranged in the form of a triangle whose upper base is pivoted on the bolster and is parallel to the longitudinal vertical median plane of the vehicle body, while the lower apex is articulated on the transom of the lower frame.
  • a suspension system in which said second mechanical connection between said body and said bolster includes a vertical pivot pin cooperating with a sleeve carried by the bolster.
  • said second mechanical connection comprises at least one arm articulated at one end to the body and at the other end to the bolster by a pivot traversing this latter.
  • a suspension system according to claim 8 in which the arm is articulated on the body about a single axis, and is stayed by two symmetrical stays each articulated at one end to the body and at the other to the bolster and provided with slight longitudinal extensibility.
  • a suspension system according to claim 1 wherein the median transverse axis of the lower frame, about which the bolster can in effect pivotally tilt, is arranged below the axes of the wheels of the lower frame, in the vicinity of the track, so as to limit the size of the longitudinal rocking torque of the lower frame under the action of forces of acceleration or of deceleration.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Handcart (AREA)
US00171608A 1970-08-28 1971-08-13 Railway car roll stabilizing bogie Expired - Lifetime US3818841A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7031604A FR2102922A5 (sl) 1970-08-28 1970-08-28

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US3818841A true US3818841A (en) 1974-06-25

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US00171608A Expired - Lifetime US3818841A (en) 1970-08-28 1971-08-13 Railway car roll stabilizing bogie

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US (1) US3818841A (sl)
BE (1) BE771912A (sl)
CA (1) CA942587A (sl)
CH (1) CH543998A (sl)
DE (1) DE2142975C3 (sl)
FR (1) FR2102922A5 (sl)
GB (1) GB1365910A (sl)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3988992A (en) * 1973-07-25 1976-11-02 Wegman & Co. High speed railway truck
US4013016A (en) * 1975-06-12 1977-03-22 Willets Elwood H Railroad car truck suspension system
US4046080A (en) * 1973-06-08 1977-09-06 Wegmann & Co. Motorized swiveling streetcar trucks
US4324187A (en) * 1978-09-04 1982-04-13 Schweizerische Lokomotiv-Und Maschinenfabrik Rail vehicle having a roll support device
US4914019A (en) * 1989-02-06 1990-04-03 Chu Tung Y Multi-purpose learning device
US5081934A (en) * 1987-05-13 1992-01-21 S.A. Constructions Ferroviaires Et Metalliques Railway bogie with articulated side frames
US5222440A (en) * 1988-10-13 1993-06-29 Sig Schweizerisch Industrie-Gesellschaft Tilt compensator for high-speed vehicles, in particular rail vehicles
US5255611A (en) * 1988-10-13 1993-10-26 Sig Schweizerische Industrie-Gesellschaft Tilt compensator for high-speed vehicles, in particular rail vehicles
US6131520A (en) * 1997-04-07 2000-10-17 Siemens Aktiengesellschaft Rail vehicle
US6247413B1 (en) * 1996-12-19 2001-06-19 Siemans Sgp Verkehrstechnik Gmbh Truck frame for railway rolling stock
US20120137926A1 (en) * 2009-03-30 2012-06-07 Bombardier Transportation Gmbh Vehicle Having Rolling Compensation
CN105923007A (zh) * 2016-06-21 2016-09-07 中车唐山机车车辆有限公司 转向架的摇枕
CN106004913A (zh) * 2016-06-21 2016-10-12 中车唐山机车车辆有限公司 转向架
CZ308667B6 (cs) * 2019-06-26 2021-02-03 ŠKODA TRANSPORTATION a.s Dvojice tažně-tlačných tyčí pro přenos podélných sil mezi podvozkem a skříní kolejového vozidla

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4271765A (en) * 1979-06-21 1981-06-09 The Budd Company Railway car tilting stabilizing system
DE4040047C2 (de) * 1990-12-14 1996-06-27 Rexroth Mannesmann Gmbh Wagenkasten-Neigungssystem
FR2756241B1 (fr) * 1996-11-25 2003-11-14 Gec Alsthom Transport Sa Dispositif de pendulation a bielles et bogie a pendulation a bielles
DE102010000125A1 (de) 2010-01-19 2011-07-21 Claas, Benedikt, 37154 Aufhängevorrichtung für einen Eisenbahnwaggon

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US593153A (en) * 1897-11-02 Apparatus for transporting ships by railway
US2243493A (en) * 1937-12-10 1941-05-27 Symington Gould Corp Railway truck
US2402501A (en) * 1943-10-30 1946-06-18 Budd Edward G Mfg Co Railway truck
US2590033A (en) * 1945-09-04 1952-03-18 Transit Res Corp Springs for rail trucks
US2901240A (en) * 1955-12-12 1959-08-25 Tyman H Fikse Vehicle suspension system
US2973722A (en) * 1957-01-24 1961-03-07 Acf Ind Inc Vehicle with centering device
US2981207A (en) * 1957-06-18 1961-04-25 Luxembourg Brev Participations Railway trucks and similar carriages
FR1272175A (fr) * 1960-08-12 1961-09-22 Luxembourg Brev Participations Perfectionnements apportés aux systèmes élastiques de liaison
US3121402A (en) * 1960-05-24 1964-02-18 Usines Pautstra Soc Vehicles mounted on trucks
US3455252A (en) * 1967-02-20 1969-07-15 Gen Steel Ind Inc Railway truck roll stabilizer and draft link
US3628465A (en) * 1969-01-13 1971-12-21 Dominion Foundries & Steel Stabilizing high speed railway trucks
US3631810A (en) * 1968-05-29 1972-01-04 British Railways Board Laterally movable railway vehicle truck

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US593153A (en) * 1897-11-02 Apparatus for transporting ships by railway
US2243493A (en) * 1937-12-10 1941-05-27 Symington Gould Corp Railway truck
US2402501A (en) * 1943-10-30 1946-06-18 Budd Edward G Mfg Co Railway truck
US2590033A (en) * 1945-09-04 1952-03-18 Transit Res Corp Springs for rail trucks
US2901240A (en) * 1955-12-12 1959-08-25 Tyman H Fikse Vehicle suspension system
US2973722A (en) * 1957-01-24 1961-03-07 Acf Ind Inc Vehicle with centering device
US2981207A (en) * 1957-06-18 1961-04-25 Luxembourg Brev Participations Railway trucks and similar carriages
US3121402A (en) * 1960-05-24 1964-02-18 Usines Pautstra Soc Vehicles mounted on trucks
FR1272175A (fr) * 1960-08-12 1961-09-22 Luxembourg Brev Participations Perfectionnements apportés aux systèmes élastiques de liaison
US3455252A (en) * 1967-02-20 1969-07-15 Gen Steel Ind Inc Railway truck roll stabilizer and draft link
US3631810A (en) * 1968-05-29 1972-01-04 British Railways Board Laterally movable railway vehicle truck
US3628465A (en) * 1969-01-13 1971-12-21 Dominion Foundries & Steel Stabilizing high speed railway trucks

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4046080A (en) * 1973-06-08 1977-09-06 Wegmann & Co. Motorized swiveling streetcar trucks
US3988992A (en) * 1973-07-25 1976-11-02 Wegman & Co. High speed railway truck
US4013016A (en) * 1975-06-12 1977-03-22 Willets Elwood H Railroad car truck suspension system
US4324187A (en) * 1978-09-04 1982-04-13 Schweizerische Lokomotiv-Und Maschinenfabrik Rail vehicle having a roll support device
US5081934A (en) * 1987-05-13 1992-01-21 S.A. Constructions Ferroviaires Et Metalliques Railway bogie with articulated side frames
US5222440A (en) * 1988-10-13 1993-06-29 Sig Schweizerisch Industrie-Gesellschaft Tilt compensator for high-speed vehicles, in particular rail vehicles
US5255611A (en) * 1988-10-13 1993-10-26 Sig Schweizerische Industrie-Gesellschaft Tilt compensator for high-speed vehicles, in particular rail vehicles
US4914019A (en) * 1989-02-06 1990-04-03 Chu Tung Y Multi-purpose learning device
US6247413B1 (en) * 1996-12-19 2001-06-19 Siemans Sgp Verkehrstechnik Gmbh Truck frame for railway rolling stock
US6131520A (en) * 1997-04-07 2000-10-17 Siemens Aktiengesellschaft Rail vehicle
US20120137926A1 (en) * 2009-03-30 2012-06-07 Bombardier Transportation Gmbh Vehicle Having Rolling Compensation
US8356557B2 (en) * 2009-03-30 2013-01-22 Bombardier Transportation Gmbh Vehicle having rolling compensation
CN105923007A (zh) * 2016-06-21 2016-09-07 中车唐山机车车辆有限公司 转向架的摇枕
CN106004913A (zh) * 2016-06-21 2016-10-12 中车唐山机车车辆有限公司 转向架
CN106004913B (zh) * 2016-06-21 2019-03-19 中车唐山机车车辆有限公司 转向架
US10745036B2 (en) * 2016-06-21 2020-08-18 Crrc Tangshan Co., Ltd. Bogie
US11084510B2 (en) 2016-06-21 2021-08-10 Crrc Tangshan Co., Ltd. Bolster of bogie
CZ308667B6 (cs) * 2019-06-26 2021-02-03 ŠKODA TRANSPORTATION a.s Dvojice tažně-tlačných tyčí pro přenos podélných sil mezi podvozkem a skříní kolejového vozidla

Also Published As

Publication number Publication date
FR2102922A5 (sl) 1972-04-07
GB1365910A (en) 1974-09-04
DE2142975C3 (de) 1978-11-02
BE771912A (fr) 1972-02-28
DE2142975A1 (de) 1972-03-02
DE2142975B2 (de) 1978-02-23
CH543998A (fr) 1973-11-15
CA942587A (en) 1974-02-26

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