WO2014006476A2 - Shock absorbing trolley of a railway wagon - Google Patents

Shock absorbing trolley of a railway wagon Download PDF

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Publication number
WO2014006476A2
WO2014006476A2 PCT/IB2013/001411 IB2013001411W WO2014006476A2 WO 2014006476 A2 WO2014006476 A2 WO 2014006476A2 IB 2013001411 W IB2013001411 W IB 2013001411W WO 2014006476 A2 WO2014006476 A2 WO 2014006476A2
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WO
WIPO (PCT)
Prior art keywords
kinetic energy
rotor
shock absorbing
differentiated
energy
Prior art date
Application number
PCT/IB2013/001411
Other languages
French (fr)
Other versions
WO2014006476A3 (en
Inventor
Stanislaw Gumula
Jaroslaw KASINOWSKI
Przemyslaw Lagiewka
Original Assignee
Epar Sp. Z O. O.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Epar Sp. Z O. O. filed Critical Epar Sp. Z O. O.
Publication of WO2014006476A2 publication Critical patent/WO2014006476A2/en
Publication of WO2014006476A3 publication Critical patent/WO2014006476A3/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G5/00—Resilient suspensions for a set of tandem wheels or axles having interrelated movements
    • B60G5/005—Resilient suspensions for a set of tandem wheels or axles having interrelated movements the wheels being fixed on a non-pivotal structure, e.g. a sliding mount
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1022—Vibration-dampers; Shock-absorbers using inertia effect the linear oscillation movement being converted into a rotational movement of the inertia member, e.g. using a pivoted mass
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/20—Type of damper
    • B60G2202/22—Rotary Damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/30—Spring/Damper and/or actuator Units
    • B60G2202/32—The spring being in series with the damper and/or actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/17—Mounting of bogies, e.g. for trailers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/419—Gears
    • B60G2204/4192—Gears rack and pinion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/423—Rails, tubes, or the like, for guiding the movement of suspension elements
    • B60G2204/4232—Sliding mounts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
    • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
    • B60G2206/011—Modular constructions
    • B60G2206/0112—Bogies for heavy vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2300/00—Indexing codes relating to the type of vehicle
    • B60G2300/10—Railway vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
    • B60G2600/02—Retarders, delaying means, dead zones, threshold values, cut-off frequency, timer interruption
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2232/00—Nature of movement
    • F16F2232/06—Translation-to-rotary conversion

Definitions

  • the present invention relates to a shock absorbing trolley of a railway wagon decreasing transferring vibrations and shocks from wheels to a railway wagon body, thus increasing passenger travelling comfort.
  • European patent application EP0621 161 discloses a trolley of a rail-vehicle 5 comprising dual arrangement of shock absorbing means.
  • the first arrangement of shock absorbing means in this known solution comprises suspension springs by means of which a trolley chassis is disposed on wheels, whereas the second arrangement of shock absorbing means comprises suspension means by means of which the chassis supports an equalizer beam or directly a chassis of the rail-vehicle T O body.
  • the equalizer beam or the rail-vehicle body chassis are connected to the chassis of the trolley by medium of a set of shock-absorbers damping vertical movements and swinging movements and by medium of a set of stabilizers.
  • Patent application U84032829 discloses a shock absorbing arrangement for installing between the rail-vehicle body and wheels, in which a part of energy of 15 trolley vibrations is converted into electrical energy by a rack power transmission system with fly-wheels.
  • the toothed bar drives a rotor by means of a toothed wheel, wherein the rotor cooperates with a moveable weights.
  • the moveable weights are maintained in appropriate distance from a rotation axis by means of springs.
  • German patent application DE3141024 discloses a device for generation of energy by using its own vibrations or vibrations of other devices. The vibrations are converted in this known solution into kinetic energy of a rotational movement. Torque generated in this manner is transferred by medium of a toothed gear, with employment of fly-wheels, and also by hydraulic arrangements in order to be used for driving other electrical or mechanical devices.
  • the object of the present invention is to provide better efficiency of absorption and dissipation of energy of vibrations of different random amplitude, existing between a trolley chassis and a railway wagon body.
  • a shock absorbing trolley of a railway wagon comprising a first-stage shock absorbing means by means of which the chassis of the trolley is coupled with wheels, and a second-stage shock absorbing means which connect the chassis with an equalizer beam of the rail- vehicle, wherein the second-stage shock absorbing means comprise at least one energy absorbing element in a form of a kinetic energy absorption rotor arrangement in which kinetic energy of progressive movement is transformed into kinetic energy of rotational movement, and wherein the arrangement comprises a top plate and a bottom plate between which are arranged racks interengaged with toothed wheels driving the kinetic energy rotor accumulators of a given moment of inertia.
  • the solution according to the present invention is characterized in that the kinetic energy absorption rotor arrangement installed under the equalizer beam of the rail-vehicle comprises at least two racks interengaged with toothed wheels of the kinetic energy rotor accumulators of differentiated capabilities of energy accumulation, wherein the racks are installed between the bottom plate and the top plate defining differentiated gaps providing differentiated idle stroke between them and these plates.
  • the kinetic energy rotor accumulators installed between the bottom plate and the top plate of the kinetic energy absorption rotor arrangement preferably have differentiated moments of inertia.
  • the kinetic energy rotor accumulators are preferably driven by means of toothed gears of differentiated transmission ratios increasing rotational velocities.
  • the idle stroke of the rack driving the toothed wheel of the kinetic energy rotor accumulator having a capability of accumulation of higher energy, defined between the bottom plate and the top plate is greater than the idle stroke of the rack driving the toothed wheel of the kinetic energy rotor accumulator having a capability of accumulation of lower energy also defined between the bottom plate and the top plate.
  • an increase of energy absorption capability of vibrations between the trolley chassis and the rail-vehicle body chassis is achieved by inducing rotational movement of consecutive kinetic energy rotor accumulators of increasing moments of inertia or by inducing rotational movement of consecutive kinetic energy rotor accumulators which are gained with increasing rotational velocities by employment of gears of increasing transmission ratios that increase rotational velocities.
  • the shock absorbing trolley according to the present invention is suitable for absorbing energy in case of vibrations of small amplitude and low kinetic energy as well as in a case of vibrations of big amplitude and high kinetic energy.
  • the device according to the present invention provides an efficient and very smooth shock absorption of vibrations, as an absorption of kinetic energy of progressive movement takes place with using kinetic energy rotor accumulators of the smallest moment of inertia.
  • the device according to the present invention also provides appropriately efficient and smooth shock absorption of vibrations, as kinetic energy absorption takes place with using several rotor accumulators of increasing energy absorption capabilities.
  • Fig. 1 presents a side view of a shock absorbing trolley of a railway car depicting schematically shock absorbing means
  • Fig. 2 presents an enlarged fragment of the device according to the present invention visualising a second-stage shock absorbing means only generally identified in Fig. 1 ,
  • Fig. 3 shows a side view of the kinetic energy absorption rotor arrangement with rotor kinetic energy accumulators of the same moment of inertia with employment of toothed gears of different transmission ratios
  • Fig. 4 presents a side view of the kinetic energy absorption rotor arrangement with rotor kinetic energy accumulators of different moments of inertia with employment of toothed gears of different transmission ratios.
  • a second-stage shock absorbing means in a shock absorbing trolley comprises kinetic energy absorption rotor arrangement 1 , in which three racks 2 separated from each other are slidably mounted which by medium of toothed wheels 3 drive three kinetic energy rotor accumulators 4, 5, 6 of differentiated moments of inertia. Between the bottom plate 12 and particular racks 2 are formed gaps 7, 8, 9 defining an idle stroke of the bottom plate 12 relative to the racks 2.
  • the gap 9 between the top plate 12 and the rack 2 driving the toothed wheel 3 of the kinetic energy rotor accumulator 6 efficient for accumulating the biggest energy is larger than the gap 8 between the bottom plate 12 and the rack 2 driving the toothed wheel 3 of the kinetic energy rotor accumulator 5 efficient for accumulating medium energy, whereas the gap 7 between the bottom plate 12 and the rack 2 driving the toothed wheel 3 of the kinetic energy rotor accumulator 4 efficient for accumulating the smaller energy is the smallest.
  • elastic shock absorbing elements in forms of springs 10.
  • the kinetic energy absorption rotor arrangement 1 contacts by medium of the top plate 13 with the block 15 the plug 16 of which is embedded in the equalizer beam 17 of the railway wagon body which is not shown in the drawing.
  • the toothed wheel 3 and the kinetic energy rotor accumulators 4 are rotatively installed in the body plate 1 1 , wherein the racks 2 are slidably guided through the guides 14.
  • kinetic energy rotor accumulators 6 of the same moments of inertia.
  • a differentiation of capability of vibration kinetic energy accumulation is in this embodiment obtained by employment of toothed gears of differentiated transmission ratio.
  • a given transmission ratio is determined by the effective diameter of the toothed wheel 3a, 3b and 3c that cooperates with rack 2, and thus in the presented embodiments the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3a of the biggest effective diameter has the lowest kinetic energy absorption capability, the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3b of the medium effective diameter has the higher kinetic energy absorption capability, and the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3c of the smallest effective diameter has the highest kinetic energy absorption capability.
  • the toothed wheel 3a of the biggest diameter has the effective diameter two-fold bigger than corresponding diameter of the toothed wheel 3c of the smallest diameter
  • the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3c of the smallest effective diameter shall gain angular velocity two-fold greater than corresponding velocity of the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3a of the greatest effective diameter, thus it shall feature four-fold greater capability of rotational movement kinetic energy accumulation.
  • the embodiment presented in Fig. 4 comprises kinetic energy rotor accumulators 4, 5 and 6 of differentiated moments of inertia and toothed gears of differentiated transmission ratios resulting from differentiated effective diameters of the employed driving toothed wheels 3a, 3b, 3c.
  • the kinetic energy rotor accumulator 6 of the biggest moment of inertia is driven by means of the toothed wheel 3a of the greatest effective diameter
  • the kinetic energy rotor accumulator 4 of the smallest moment of inertia is driven by means of the toothed wheel 3c of the smallest moment of inertia.
  • Such a construction provides a possibility of defining a smooth characteristic of a capability of vibration kinetic energy of the device according to the present invention.
  • unidirectional couplings are also employed, though not presented on the drawing, and arranged between the toothed wheels 3 and kinetic energy accumulators 4, 5, 6.
  • the function of these unidirectional couplings is transferring a torque onto kinetic energy rotor accumulators, and after absorption of energy, when angular velocity of the toothed wheel 3 shall be smaller than angular velocity of corresponding kinetic energy rotor accumulator 4, 5, 6, the unidirectional coupling is disconnecting thus it enables for unrestricted rotation of the kinetic energy rotor accumulator 4, 5, 6.
  • all kinetic energy rotor accumulators 4, 5, 6 shall be driven, wherein the kinetic energy rotor accumulator 4 of the smallest moment of inertia shall gain in such a case the highest angular velocity, the kinetic energy rotor accumulator 5 of the medium moment of inertia shall gain a medium angular velocity, and the kinetic energy rotor accumulator 6 of the greatest moment of inertia shall gain the smallest angular velocity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vibration Dampers (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

A shock absorbing trolley of a railway wagon, comprising a first-stage shock absorbing means by means of which the chassis (18) of the trolley is coupled with wheels (20), and a second-stage shock absorbing means which connect the chassis (18) with an equalizer beam of the rail-vehicle, wherein the second-stage shock absorbing means comprise at least one energy absorbing element in a form of a kinetic energy absorption rotor arrangement (1) in which kinetic energy of progressive movement is transformed into kinetic energy of rotational movement, and wherein the arrangement comprises a top plate and a bottom plate between which are arranged racks interengaged with toothed wheels driving the kinetic energy rotor accumulators of a given moment of inertia, characterized in that the kinetic energy absorption rotor arrangement (1) installed under the equalizer beam (17) of the rail-vehicle comprises at least two racks (2) interengaged with toothed wheels (3, 3a, 3b, 3c) of the kinetic energy rotor accumulators (4, 5, 6) of differentiated capabilities of energy accumulation, wherein the racks (2) are installed between the bottom plate (12) and the top plate (13) defining differentiated gaps (7, 8, 9) providing differentiated idle stroke between them and these plates (12, 13)

Description

SHOCK ABSORBING TROLLEY OF A RAILWAY WAGON
The present invention relates to a shock absorbing trolley of a railway wagon decreasing transferring vibrations and shocks from wheels to a railway wagon body, thus increasing passenger travelling comfort.
European patent application EP0621 161 discloses a trolley of a rail-vehicle 5 comprising dual arrangement of shock absorbing means. The first arrangement of shock absorbing means in this known solution comprises suspension springs by means of which a trolley chassis is disposed on wheels, whereas the second arrangement of shock absorbing means comprises suspension means by means of which the chassis supports an equalizer beam or directly a chassis of the rail-vehicle T O body. Moreover, the equalizer beam or the rail-vehicle body chassis are connected to the chassis of the trolley by medium of a set of shock-absorbers damping vertical movements and swinging movements and by medium of a set of stabilizers.
Patent application U84032829 discloses a shock absorbing arrangement for installing between the rail-vehicle body and wheels, in which a part of energy of 15 trolley vibrations is converted into electrical energy by a rack power transmission system with fly-wheels.
International patent application WO2004028864 discloses a device for absorbing energy, in which kinetic energy is converted into kinetic energy of rotating masses. In this known solution an element that absorbs energy is connected with two toothed
20 bars which by medium of toothed wheels drive kinetic energy rotor accumulators in forms of rods with moveable weights slidably mounted on the rods. An appropriate progressiveness of energy absorption is obtained in this known solution by employment of the moveable weights located as close to the rotation axis of the rotor with the rods as possible in order that a moment of inertia of the rotor in the initial
25 phase of energy absorption be as small as possible. In further movement phase while the rotor starts to rotate, the weights start to translocate under influence of centrifugal force and move away from the rotation axis along the rod axis, until they reach the rod end limiters and in such weight positions the biggest moment of inertia of the rotor is achieved that enables for absorption of the increased kinetic energy. International application WO2005121593 discloses a device for absorbing energy comprising a beater element cooperating with an energy dissipation arrangement comprising a toothed bar inducing rotation of rotating masses, thus causing a conversion of progressive movement kinetic energy resulted form an impact into kinetic energy of a rotational movement. In one of disclosed embodiments of this known solution, the toothed bar drives a rotor by means of a toothed wheel, wherein the rotor cooperates with a moveable weights. In order to provide a progressive change of a moment of inertia of the rotor during a process of energy absorption, the moveable weights are maintained in appropriate distance from a rotation axis by means of springs.
German patent application DE3141024 discloses a device for generation of energy by using its own vibrations or vibrations of other devices. The vibrations are converted in this known solution into kinetic energy of a rotational movement. Torque generated in this manner is transferred by medium of a toothed gear, with employment of fly-wheels, and also by hydraulic arrangements in order to be used for driving other electrical or mechanical devices.
The known solutions do not provide effective absorption of energy of vibrations of differentiated amplitude originating from trolleys. Therefore the object of the present invention is to provide better efficiency of absorption and dissipation of energy of vibrations of different random amplitude, existing between a trolley chassis and a railway wagon body.
According to the present invention there is provided a shock absorbing trolley of a railway wagon, comprising a first-stage shock absorbing means by means of which the chassis of the trolley is coupled with wheels, and a second-stage shock absorbing means which connect the chassis with an equalizer beam of the rail- vehicle, wherein the second-stage shock absorbing means comprise at least one energy absorbing element in a form of a kinetic energy absorption rotor arrangement in which kinetic energy of progressive movement is transformed into kinetic energy of rotational movement, and wherein the arrangement comprises a top plate and a bottom plate between which are arranged racks interengaged with toothed wheels driving the kinetic energy rotor accumulators of a given moment of inertia. The solution according to the present invention is characterized in that the kinetic energy absorption rotor arrangement installed under the equalizer beam of the rail-vehicle comprises at least two racks interengaged with toothed wheels of the kinetic energy rotor accumulators of differentiated capabilities of energy accumulation, wherein the racks are installed between the bottom plate and the top plate defining differentiated gaps providing differentiated idle stroke between them and these plates.
The kinetic energy rotor accumulators installed between the bottom plate and the top plate of the kinetic energy absorption rotor arrangement preferably have differentiated moments of inertia.
The kinetic energy rotor accumulators are preferably driven by means of toothed gears of differentiated transmission ratios increasing rotational velocities.
In preferred embodiments of the present invention, the idle stroke of the rack driving the toothed wheel of the kinetic energy rotor accumulator having a capability of accumulation of higher energy, defined between the bottom plate and the top plate is greater than the idle stroke of the rack driving the toothed wheel of the kinetic energy rotor accumulator having a capability of accumulation of lower energy also defined between the bottom plate and the top plate.
In the trolley according to the present invention an increase of energy absorption capability of vibrations between the trolley chassis and the rail-vehicle body chassis is achieved by inducing rotational movement of consecutive kinetic energy rotor accumulators of increasing moments of inertia or by inducing rotational movement of consecutive kinetic energy rotor accumulators which are gained with increasing rotational velocities by employment of gears of increasing transmission ratios that increase rotational velocities.
The shock absorbing trolley according to the present invention is suitable for absorbing energy in case of vibrations of small amplitude and low kinetic energy as well as in a case of vibrations of big amplitude and high kinetic energy. In the first instance the device according to the present invention provides an efficient and very smooth shock absorption of vibrations, as an absorption of kinetic energy of progressive movement takes place with using kinetic energy rotor accumulators of the smallest moment of inertia. In the second instance, the device according to the present invention also provides appropriately efficient and smooth shock absorption of vibrations, as kinetic energy absorption takes place with using several rotor accumulators of increasing energy absorption capabilities.
In case of vibrations of greater energy an additional effect occurs consisting in that vibrations kinetic energy is in a great part accumulated in the rotor accumulators featuring lower energy absorption capability before the rotor accumulators featuring higher energy absorption capability are actuated. Such a sequence of energy absorption provides smoother operation of the device according to the present invention during actuation of alternate rotor accumulators, even those of the greatest capability of energy absorption featuring the biggest moment of inertia. The exemplary embodiments of the present invention are presented below in connection with the attached drawings on which:
Fig. 1 presents a side view of a shock absorbing trolley of a railway car depicting schematically shock absorbing means,
Fig. 2 presents an enlarged fragment of the device according to the present invention visualising a second-stage shock absorbing means only generally identified in Fig. 1 ,
Fig. 3 shows a side view of the kinetic energy absorption rotor arrangement with rotor kinetic energy accumulators of the same moment of inertia with employment of toothed gears of different transmission ratios, and
Fig. 4 presents a side view of the kinetic energy absorption rotor arrangement with rotor kinetic energy accumulators of different moments of inertia with employment of toothed gears of different transmission ratios.
As presented in the embodiment of Fig. 1 and Fig. 2, a second-stage shock absorbing means in a shock absorbing trolley according to the present invention comprises kinetic energy absorption rotor arrangement 1 , in which three racks 2 separated from each other are slidably mounted which by medium of toothed wheels 3 drive three kinetic energy rotor accumulators 4, 5, 6 of differentiated moments of inertia. Between the bottom plate 12 and particular racks 2 are formed gaps 7, 8, 9 defining an idle stroke of the bottom plate 12 relative to the racks 2. The gap 9 between the top plate 12 and the rack 2 driving the toothed wheel 3 of the kinetic energy rotor accumulator 6 efficient for accumulating the biggest energy is larger than the gap 8 between the bottom plate 12 and the rack 2 driving the toothed wheel 3 of the kinetic energy rotor accumulator 5 efficient for accumulating medium energy, whereas the gap 7 between the bottom plate 12 and the rack 2 driving the toothed wheel 3 of the kinetic energy rotor accumulator 4 efficient for accumulating the smaller energy is the smallest. In order to decrease impact in the initial stage, during contacting the bottom plate 12 with particular racks 2, between the bottom plate 12 and each rack 2 are arranged elastic shock absorbing elements in forms of springs 10. The kinetic energy absorption rotor arrangement 1 contacts by medium of the top plate 13 with the block 15 the plug 16 of which is embedded in the equalizer beam 17 of the railway wagon body which is not shown in the drawing. The toothed wheel 3 and the kinetic energy rotor accumulators 4 are rotatively installed in the body plate 1 1 , wherein the racks 2 are slidably guided through the guides 14.
Between the bearing construction of the railway wagon body and the trolley chassis are installed another stabilizing and shock absorbing arrangements. As shown in the embodiment of Fig. 3 in the kinetic energy absorption rotor arrangement 1 are employed kinetic energy rotor accumulators 6 of the same moments of inertia. A differentiation of capability of vibration kinetic energy accumulation is in this embodiment obtained by employment of toothed gears of differentiated transmission ratio. In a case of toothed gear employment, a given transmission ratio is determined by the effective diameter of the toothed wheel 3a, 3b and 3c that cooperates with rack 2, and thus in the presented embodiments the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3a of the biggest effective diameter has the lowest kinetic energy absorption capability, the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3b of the medium effective diameter has the higher kinetic energy absorption capability, and the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3c of the smallest effective diameter has the highest kinetic energy absorption capability.
In the embodiment presented in Fig. 3, the toothed wheel 3a of the biggest diameter has the effective diameter two-fold bigger than corresponding diameter of the toothed wheel 3c of the smallest diameter, what in case of the same velocities of translocation of racks 2 and usage of kinetic energy rotor accumulators of the same moment of inertia results in that the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3c of the smallest effective diameter shall gain angular velocity two-fold greater than corresponding velocity of the kinetic energy rotor accumulator 6 driven by means of the toothed wheel 3a of the greatest effective diameter, thus it shall feature four-fold greater capability of rotational movement kinetic energy accumulation.
The embodiment presented in Fig. 4 comprises kinetic energy rotor accumulators 4, 5 and 6 of differentiated moments of inertia and toothed gears of differentiated transmission ratios resulting from differentiated effective diameters of the employed driving toothed wheels 3a, 3b, 3c. The kinetic energy rotor accumulator 6 of the biggest moment of inertia is driven by means of the toothed wheel 3a of the greatest effective diameter, and the kinetic energy rotor accumulator 4 of the smallest moment of inertia is driven by means of the toothed wheel 3c of the smallest moment of inertia. Such a construction provides a possibility of defining a smooth characteristic of a capability of vibration kinetic energy of the device according to the present invention.
In an alternative embodiment which is not illustrated on the drawing, where for driving the kinetic energy rotor accumulator of the greatest moment of inertia is employed a toothed gear with a toothed wheel of the smallest effective diameter, and for driving the kinetic energy rotor accumulator of the smallest moment of inertia is employed a gear with a toothed wheel of the greatest effective diameter, the biggest progressiveness of vibration energy absorption shall be obtained.
In the described embodiments unidirectional couplings are also employed, though not presented on the drawing, and arranged between the toothed wheels 3 and kinetic energy accumulators 4, 5, 6. The function of these unidirectional couplings is transferring a torque onto kinetic energy rotor accumulators, and after absorption of energy, when angular velocity of the toothed wheel 3 shall be smaller than angular velocity of corresponding kinetic energy rotor accumulator 4, 5, 6, the unidirectional coupling is disconnecting thus it enables for unrestricted rotation of the kinetic energy rotor accumulator 4, 5, 6. In a result of a differentiation of widths of the gaps 7, 8, 9 the kinetic energy rotor accumulators 4, 5, 6 are actuated successively beginning with the kinetic energy rotor accumulator 4 of the smallest moment of inertia, and ending with the kinetic energy rotor accumulator 6 of the biggest moment of inertia. In a case of a bigger amplitude of vibrations transferred to equalizer beam 17 of the railway wagon body, all kinetic energy rotor accumulators 4, 5, 6 shall be driven, wherein the kinetic energy rotor accumulator 4 of the smallest moment of inertia shall gain in such a case the highest angular velocity, the kinetic energy rotor accumulator 5 of the medium moment of inertia shall gain a medium angular velocity, and the kinetic energy rotor accumulator 6 of the greatest moment of inertia shall gain the smallest angular velocity.

Claims

Patent Claims:
1 . A shock absorbing trolley of a railway wagon, comprising a first-stage shock absorbing means by means of which the chassis (18) of the trolley is coupled with wheels (20), and a second-stage shock absorbing means which connect the chassis (18) with an equalizer beam of the rail-vehicle, wherein the second- stage shock absorbing means comprise at least one energy absorbing element in a form of a kinetic energy absorption rotor arrangement (1) in which kinetic energy of progressive movement is transformed into kinetic energy of rotational movement, and wherein the arrangement comprises a top plate and a bottom plate between which are arranged racks interengaged with toothed wheels driving the kinetic energy rotor accumulators of a given moment of inertia, characterized in that the kinetic energy absorption rotor arrangement (1) installed under the equalizer beam (17) of the rail-vehicle comprises at least two racks (2) interengaged with toothed wheels (3, 3a, 3b, 3c) of the kinetic energy rotor accumulators (4, 5, 6) of differentiated capabilities of energy accumulation, wherein the racks
(2) are installed between the bottom plate (12) and the top plate (13) defining differentiated gaps (7, 8, 9) providing differentiated idle stroke between them and these plates (12, 13).
A shock absorbing trolley according to Claim 1 , characterized in that the kinetic energy rotor accumulators (4, 5, 6) installed between the bottom plate (12) and the top plate (13) of the kinetic energy absorption rotor arrangement (1) have differentiated moments of inertia.
3. A shock absorbing trolley according to Claim 1 or 2, characterized in that the kinetic energy rotor accumulators (4, 5, 6) are driven by means of toothed gears of differentiated transmission ratios that increase rotational velocities.
4. A shock absorbing trolley according to Claim 1 or 2 or 3, characterized in that the idle stroke of the rack (2) driving the toothed wheel (3) of the kinetic energy rotor accumulator (5, 6) having a capability of accumulation of higher energy, defined between the bottom plate (12) and the top plate (13) is greater than the idle stroke of the rack (2) driving the toothed wheel (3) of the kinetic energy rotor accumulator (4) having a capability of accumulation of lower energy also defined between the bottom plate (12) and the top plate (13).
PCT/IB2013/001411 2012-07-03 2013-07-02 Shock absorbing trolley of a railway wagon WO2014006476A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PLP.399778 2012-07-03
PL399778A PL399778A1 (en) 2012-07-03 2012-07-03 Shock absorbing trolley of a railway wagon

Publications (2)

Publication Number Publication Date
WO2014006476A2 true WO2014006476A2 (en) 2014-01-09
WO2014006476A3 WO2014006476A3 (en) 2014-03-06

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DE3141024A1 (en) 1981-10-15 1983-04-28 Horst 6651 Altenkirchen Böhnlein Method and device for converting the energy generated by oscillation of a mass into a continuously rotating drive force, especially for the operation of a motor vehicle
EP0621161A1 (en) 1993-04-22 1994-10-26 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Determination method of the overrun force of a trailer
WO2004028864A1 (en) 2002-09-24 2004-04-08 Lucjan Lagiewka Method and device for vehicle protection
WO2005121593A1 (en) 2004-06-11 2005-12-22 Georg Piontek Device for transforming kinetic energy

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US4032829A (en) 1975-08-22 1977-06-28 Schenavar Harold E Road shock energy converter for charging vehicle batteries
DE3141024A1 (en) 1981-10-15 1983-04-28 Horst 6651 Altenkirchen Böhnlein Method and device for converting the energy generated by oscillation of a mass into a continuously rotating drive force, especially for the operation of a motor vehicle
EP0621161A1 (en) 1993-04-22 1994-10-26 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Determination method of the overrun force of a trailer
WO2004028864A1 (en) 2002-09-24 2004-04-08 Lucjan Lagiewka Method and device for vehicle protection
WO2005121593A1 (en) 2004-06-11 2005-12-22 Georg Piontek Device for transforming kinetic energy

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