EP0542386B1 - Verfahren und Einrichtung zum Dämpfen der Schwingungen eines Schienenfahrzeuges - Google Patents

Verfahren und Einrichtung zum Dämpfen der Schwingungen eines Schienenfahrzeuges Download PDF

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Publication number
EP0542386B1
EP0542386B1 EP92250327A EP92250327A EP0542386B1 EP 0542386 B1 EP0542386 B1 EP 0542386B1 EP 92250327 A EP92250327 A EP 92250327A EP 92250327 A EP92250327 A EP 92250327A EP 0542386 B1 EP0542386 B1 EP 0542386B1
Authority
EP
European Patent Office
Prior art keywords
rail vehicle
cylinder
piston
rail
pressure
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
EP92250327A
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German (de)
English (en)
French (fr)
Other versions
EP0542386A1 (de
Inventor
Mahmud Keschwari Rasti
Peter Saffe
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.)
Vodafone GmbH
Original Assignee
Mannesmann AG
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 Mannesmann AG filed Critical Mannesmann AG
Publication of EP0542386A1 publication Critical patent/EP0542386A1/de
Application granted granted Critical
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Classifications

    • 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
    • B61F5/245—Means for damping or minimising the canting, skewing, pitching, or plunging movements of the underframes by active damping, i.e. with means to vary the damping characteristics in accordance with track or vehicle induced reactions, especially in high speed mode

Definitions

  • Such a device is also known from FR-A-2 593 455.
  • the known solution aims at the goal in the field of railways Connection occurring with ever higher vehicle speeds To counteract rolling movements.
  • a contemplated stake previous damper which are designed so that they the would dampen the vibration range of the roll movement, according to the expressed an excessive increase in the hardness of the Lead vehicle suspension. This would have a negative impact on the Shock and Vibration movements of the vehicle exercised.
  • the invention specified in claim 1 is based on the problem the spring stiffness of a wheel / rail system at low frequencies to increase the damping system and at high frequencies To reduce spring stiffness, i.e. the cheapest damping adjust. At the same time, the system of passive Leave lateral force control and through a system of active Shear force control to be replaced.
  • Another measure is that the pressure in the cylinder is on a setpoint calculated on the basis of a path signal is regulated and that when vibrations occur over the cylinder or over the piston Energy is fed back into a store. This can significantly increase Energy is saved and the print media source does not need more become.
  • a program-controlled device a decision is made as to which of the valves formed circuit branch, the regulation of the actual pressure takes place. This can advantageously result in an energy and flow technology favorable pressure medium presence in the cylinder can be achieved.
  • Another improvement is that the program-controlled Established an increase or decrease in the pressure level to influence the passive spring stiffness.
  • the device for damping vibrations between one Rail vehicle body and a rail chassis is based on one acting between the rail vehicle body and the rail chassis Piston-cylinder drive unit that can be acted on from both sides.
  • Such a device consists of a pneumatic or hydraulic piston-cylinder system with connected control device a displacement measuring device assigned to the piston and a System of control and non-return valves associated with pressure rooms.
  • a such a device per vehicle is not of great weight connected or a large space for accommodation is required.
  • the facility is further developed so that the system of Control and check valves in each pressure chamber in the cylinder allocated memory is connected. So both sides of the piston connectable to a memory.
  • brackets 5 and 6 stabilizers 7 and 8 articulated, which consist of hydraulic dampers.
  • These mechanical, hydraulic or pneumatic spring assemblies consisting of the coil springs 3 and 4, the stabilizers 7 and 8, catch in the transverse direction to the direction of travel 9 only partially arising vibrations.
  • These vibrations also lie different passive forces with different dynamics.
  • the Passive forces are vibrations generated by the rail vehicle itself, that cause the vehicle with its wheels or Wheel groups 10 and 11 back and forth between the rails of a track heart pendulums.
  • each rail chassis 2 In order to match active forces to the passive forces that occur, is between the rail vehicle body 1 and a rail chassis 2 each have at least one pneumatic or hydraulic cylinder 12 arranged and with its end 12a on a hinge 13 on the Rail chassis 2 attached via a bearing 2a. His piston rod 14 is accordingly with a joint 14a on the Rail vehicle body 1 attached or stored. On the Rail chassis 2 are also supports 15a and 15b elastic stops 16a and 16b for one between the two arranged guide rod 17, which on the rail vehicle body 1 is attached.
  • the piston 14a is double-sided in the cylinder 12 actable, the pressures p1 and p2 depending on Driving conditions are regulated by lower driving stiffness according to the dynamics and the level of active forces between Rail vehicle body and rail chassis are set.
  • a length measuring device 18 with a path converter 19 provided, the signals input into a microprocessor 20 in which the signals of pressures p1 and p2 as well as others Press p3 and p4 of a first pressure accumulator 21 and a second one, respectively Pressure accumulator 22 can be entered.
  • the microprocessor 20 outputs the calculated values in the form of signals to control or continuous valves V1, V2, V3 and V4 or V5 further, which are connected as shown.
  • the pressure accumulators 21 and 22 are here via check valves 23 and 24 and this connected to a pressure source 25.
  • the mode of operation of the device results from the flow master plan according to FIG. 4:
  • a path "s" from the length measuring device 18 and the path converter 19 is read into the microprocessor 20 from the pressures p1 and p2.
  • the setpoint is calculated, which is made available as a signal ramp. Accordingly, it is determined whether the target value is zero or greater than zero (cf. flow chart according to FIG. 4).
  • the pressures p1 and p2 are then calculated from the setpoints and actual values as paths in the corresponding pressure spaces and as signals to the valves V1 to V5 in a system with the pressure accumulators 21 and 22.
  • FIG. 3 a doubled arrangement is swapped with sides for Attachment of two cylinders 12 shown.
  • cylinder 12 In the drawing above lying cylinder 12 is the piston rod 14 and the joint 14a on the right, however in the case of the lower cylinder 12 on the left side.
  • the cylinder end 12a and the top cylinder 12 are located there Joint 13 on the left, however, in the lower cylinder 12 on the right side.
  • the invention can both with a piston-cylinder system or with several according to FIG. 3 and also with more than two Piston-cylinder systems depending on the masses to be damped be realized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)
  • Vibration Prevention Devices (AREA)
EP92250327A 1991-11-11 1992-11-09 Verfahren und Einrichtung zum Dämpfen der Schwingungen eines Schienenfahrzeuges Expired - Lifetime EP0542386B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4137869A DE4137869C1 (enExample) 1991-11-11 1991-11-11
DE4137869 1991-11-11

Publications (2)

Publication Number Publication Date
EP0542386A1 EP0542386A1 (de) 1993-05-19
EP0542386B1 true EP0542386B1 (de) 1999-01-13

Family

ID=6445032

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92250327A Expired - Lifetime EP0542386B1 (de) 1991-11-11 1992-11-09 Verfahren und Einrichtung zum Dämpfen der Schwingungen eines Schienenfahrzeuges

Country Status (3)

Country Link
EP (1) EP0542386B1 (enExample)
AT (1) ATE175635T1 (enExample)
DE (1) DE4137869C1 (enExample)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4420367C1 (de) * 1994-06-10 1995-08-17 Talbot Waggonfab Querfederung für ein Schienenfahrzeug und Verfahren zu deren Steuerung
DE4436137A1 (de) * 1994-10-10 1996-04-11 Talbot Waggonfab Verfahren zum Steuern der Querverschiebung eines Schienenfahrzeugs gegenüber seinem Fahrwerk
DE19501136C2 (de) * 1995-01-05 2001-08-02 Knorr Bremse Mrp Systeme Fuer Verfahren und Einrichtung zur Dämpfung von Fahrschwingungen bei Fahrzeugen
DE19512437A1 (de) * 1995-04-03 1996-10-10 Rexroth Mannesmann Gmbh Einrichtung zur Kompensation der auf ein Schienenfahrzeug wirkenden Querkraft
DE19606364C2 (de) * 1995-05-06 1998-01-29 Deutsche Bahn Ag Modale Abstützung der Fahrwerke und/oder Transportgefäße von Verkehrsfahrzeugen,vorzugsweise Schienenfahrzeugen
DE19806347C1 (de) 1998-02-12 1999-07-15 Mannesmann Ag Vorrichtung zur aktiven Querzentrierung und Schwingungsdämpfung bei Schienenfahrzeugen (AQZ-Zylinder)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT7470428A1 (it) * 1974-11-25 1976-05-25 Fabbriche Riunite Way Assauto S P A Ammortizzatore antirollio per veicoli
JPS61275053A (ja) * 1985-05-31 1986-12-05 財団法人鉄道総合技術研究所 車両の振動制御装置
DE3537325A1 (de) * 1985-10-19 1987-04-23 Messerschmitt Boelkow Blohm Aktives federungselement, insbesondere fuer schienengebundene hochgeschwindigkeitsfahrzeuge
JPH06104450B2 (ja) * 1986-01-29 1994-12-21 財団法人鉄道総合技術研究所 車両の振動制御装置
IT1216147B (it) * 1988-03-18 1990-02-22 Socimi Dispositivo per il controllo delle sollecitazioni dinamiche trasmesse dalla superficie di rotolamento alla cassa di un veicolo, in particolare un veicolo ferrotramviario.
DE3818179A1 (de) * 1988-05-28 1989-12-07 Messerschmitt Boelkow Blohm Aufhaengung fuer fahrzeuge
FR2632260B1 (fr) * 1988-06-03 1990-08-31 Durand Charles Procede et systeme d'amortissement des mouvements oscillatoires des vehicules ferroviaires
EP0390546B1 (en) * 1989-03-31 1996-12-27 Hitachi, Ltd. Railway rolling stock
GB9015109D0 (en) * 1990-07-09 1990-08-29 Gec Alsthom Ltd Damping arrangements

Also Published As

Publication number Publication date
EP0542386A1 (de) 1993-05-19
DE4137869C1 (enExample) 1993-04-01
ATE175635T1 (de) 1999-01-15

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