EP2861476A1 - Fahrzeug mit einer federeinrichtung mit vorgebbarer querfedercharakteristik - Google Patents
Fahrzeug mit einer federeinrichtung mit vorgebbarer querfedercharakteristikInfo
- Publication number
- EP2861476A1 EP2861476A1 EP13730553.8A EP13730553A EP2861476A1 EP 2861476 A1 EP2861476 A1 EP 2861476A1 EP 13730553 A EP13730553 A EP 13730553A EP 2861476 A1 EP2861476 A1 EP 2861476A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spring
- vehicle
- contact element
- car body
- unit
- 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.)
- Granted
Links
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- 238000009530 blood pressure measurement Methods 0.000 claims description 3
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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
-
- 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
- B61F5/14—Side bearings
-
- 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
Definitions
- the present invention relates to a vehicle, in particular a rail vehicle, with a car body and a chassis unit, wherein the car body is supported on at least one spring device in a vehicle height direction on the chassis unit.
- the present invention further relates to a corresponding spring device of such a vehicle according to the invention.
- Transverse accelerations which act, for example, when traveling in a transverse direction (ie transversely to the direction of travel or transverse to a vehicle longitudinal axis), in such vehicles usually cause a transverse deflection of the car body with respect to the wheel units, which must be absorbed by the spring devices.
- Spring devices can achieve a desired transverse spring characteristic (ie, a desired course of the resistance of the spring device against the transverse deflection of the car body) only with comparatively complex means.
- the transverse spring characteristic is both in terms of ride comfort for the passengers but also with regard to the driving safety of the vehicle, for example, its derailment, from
- Vehicle height direction usually leaves little room for a simple
- EP 1 029 764 A2 and EP 1 264 750 A1 disclose hydropneumatic or
- Hydromechanical spring devices known in which the recording of the supporting force between the car body and wheel unit via a hydraulic unit whose working space is connected via a hydraulic line with another working space of a hydropneumatic or hydromechanical spring unit in conjunction, which the spring action for
- the present invention is therefore based on the object to provide a vehicle or a spring device of the aforementioned type, which or which does not have the disadvantages mentioned above or at least to a lesser extent and in particular in a simple and space-saving manner an adaptation of the
- Cross spring characteristic allows for a desired course.
- the present invention solves this problem starting from a vehicle according to the preamble of claim 1 by the characterizing part of claim 1
- the present invention is based on the technical teaching that allows a simple and space-saving way to adapt the transverse spring characteristic to a desired course, when the spring device comprises a first contact element, a second contact element and at least one spring unit, the kinematically in series between the car body and the chassis unit are arranged, that the first contact element at a deflection of the car body in a vehicle transverse direction, the second contact element at different contact points at least one
- Chassis unit can be realized, which converts a transverse movement of the car body relative to the chassis unit in a deflection of the spring unit in its main direction of action, in which it acts to support the car body in the vehicle height direction.
- the main direction of action is understood to be the direction in which the spring unit is primarily intended to achieve its spring action.
- this is the direction of the spring axis (that is, the center axis of the cylinder).
- Vehicle height direction but it can also be inclined to the vehicle height direction.
- the adaptation of the transverse spring characteristic to a desired course can, with a given spring characteristic of the spring device in the vehicle height direction or a predetermined spring characteristic of the spring unit in its main direction of action, be simply determined by the movement ratio between the transverse movement of the car body and the deflection of the spring unit in the main body as defined by the course of the contact point curve Main direction of effect done. In other words it is about the adaptation of
- the motion translation realized via the first and second contact elements can be realized in any suitable manner, so that a sliding movement between the first and second contact elements along the contact point curve can be provided. Furthermore, the first and second contact element for movement translation at least partially perform purely translational movements.
- Movement translation at least partially performs a rotational movement.
- a rolling movement or at least one rolling movement between the two contact elements can be realized, which is not least from a wear point of advantage.
- the present invention therefore relates to a vehicle, in particular a rail vehicle, with a car body and a chassis unit, wherein the car body via at least one spring device in a
- the spring device comprises a first contact element, a second contact element and at least one
- Spring unit wherein the first contact element, the second contact element and the at least one spring unit are arranged kinematically in series between the car body and the chassis unit.
- the first contact element is arranged and assigned to the second contact element such that the first contact element in a
- Contact element is pivotally mounted about a pivot axis and the second
- Contact element is assigned such that the first contact element at a
- Pivoting movement about the pivot axis contacts the second contact element at different contact points of the at least one contact point curve.
- an arbitrary profile of the transverse spring characteristic of the spring device can be realized via the at least one contact point curve, which is adapted to the specific application, for example the vehicle type and / or the rated operating speed of the vehicle.
- the spring device without much effort for any vehicle. So it can be easily adapted for a vehicle in the passenger transport with comparatively low nominal operating speeds (for example, a tram or subway) as well as for vehicles in regional, intercity or high-speed traffic, which then always higher
- constant and / or linear and / or progressive and / or declining courses of the resistance of the spring device can be adjusted against the transverse deflection of the car body, at least in sections.
- the at least one contact point curve defines a Querfederungscharaktstik the spring device.
- the at least one contact point curve is formed in certain variants of the invention such that the spring device at least in an adjacent to the neutral position Querlenklenkungsmitten Trial and / or at least in a distance from the neutral position outer
- Querlenkungsmitten Episode exerts a force acting in the vehicle transverse direction restoring force on the car body, which is caused by the force acting on the car body weight and which up to a maximum during operation of the vehicle
- Rail superelevation is sufficient to the car body at least in the vicinity of the neutral position, preferably return substantially to the neutral position.
- Contact point curve can be realized with progressive resistance to the transverse deflection.
- Contact point curve is formed such that the spring device, at least in a spaced from the neutral position outer Quunterslenkungs Scheme a progressive transverse deflection resistance to the Querauslenkung with at least
- Sectionally degressive characteristic opposes. This makes it possible, for example, to even support the further transverse deflection in certain areas.
- tilt systems which set a tilt angle or a roll angle of the car body about a parallel to the vehicle longitudinal roll axis to the passengers of the vehicle perceived as disturbing lateral acceleration (as it acts, for example, when cornering).
- tilt systems which set a tilt angle or a roll angle of the car body about a parallel to the vehicle longitudinal roll axis to the passengers of the vehicle perceived as disturbing lateral acceleration (as it acts, for example, when cornering).
- Tilting systems in which the adjustment of the roll angle takes place at least partially via actuators, this is advantageous because the actuators then have to apply less force and thus can be designed smaller and lighter.
- the at least one contact point curve may additionally or alternatively be designed such that the spring device, at least in sections, opposes a substantially constant resistance to a progressive transverse deflection. Again, this may be desired or advantageous depending on the particular application.
- the course of the resistance to the transverse deflections can basically be set arbitrarily.
- at least sections of any desired curved (rising or falling) curves of the resistance curve can be adjusted via the design of the contact point curve.
- the at least one contact point curve is designed such that the spring device, at least in sections, opposes a substantially linear (rising or falling) resistance running a progressive transverse deflection.
- the sequence of the two contact elements and the spring unit in the kinematic chain between the car body and the chassis unit can basically be chosen arbitrarily.
- the available space can play a crucial role here.
- the at least one spring unit is serially connected in a kinematic chain between the first contact element and the car body or between the first contact element and the chassis unit, wherein the first contact element is then displaceably mounted along a main direction of action of the spring unit.
- the first contact element can in this case be displaceably arranged in space in any direction.
- Vehicle height direction runs.
- the first contact element is then mounted displaceably in the vehicle height direction.
- the at least one spring unit is additionally connected (i.e., when a plurality of spring units are provided) or, alternatively, in a kinematic chain, serially between the second contact element and the carbody or between the second contact element and the chassis unit.
- the second one is additionally connected (i.e., when a plurality of spring units are provided) or, alternatively, in a kinematic chain, serially between the second contact element and the carbody or between the second contact element and the chassis unit.
- Car body and the suspension unit provided.
- a plurality of spring devices are provided, which may optionally take on additional functions.
- spaced-apart spring devices can absorb particular moments about certain axes of rotation.
- the car body is supported by at least one further spring device in the vehicle height direction on the chassis unit, which is in particular formed substantially identical to the spring device.
- the two spring devices are in one
- Vehicle longitudinal direction arranged offset by a longitudinal distance from each other, so that they can optionally accommodate a pitching moment about a running in the vehicle transverse direction pitch axis.
- the two spring devices in particular substantially equidistant, on both sides of a fulcrum of the
- the car body is additionally or alternatively via at least one further spring device in the vehicle height direction on the
- Chassis unit supported, in particular, substantially identical to the
- Spring device is formed. The two spring devices are in one
- the two spring devices in addition or alternatively, in particular substantially equidistant. on both sides of a fulcrum of the
- the two spring devices can also be designed such that they can not generate or absorb any pitching moments about such a pitch axis and / or no rolling moments about such a roll axis. In this way, it can be avoided that such pitching moments or rolling moments possibly have a negative effect on the derailment safety of the vehicle.
- This can be realized by a purely passive coupling of the two spring devices, in which, for example, there is a correspondingly opposite (in particular fluidly communicating) coupling of the two spring devices.
- an active control of the two spring devices is possible, which is tuned such that no such pitching moments or Wankmomente be generated or recorded.
- an active solution may be selected, in which the two spring means by a control device be actively controlled to a certain predetermined pitching moment and / or
- At least one size can be detected on the vehicle, which allows conclusions about the current derailment safety of the chassis unit. Depending on the currently detected value of this at least one size, the current derailment safety can then be evaluated and, if appropriate, a corresponding counter-reaction can be initiated via the two spring devices. Where appropriate, both for the assessment of dismissal security and for the
- Determining the backlash at least one previously determined for the vehicle model can be used.
- the spring units can in principle be designed as simple passive units.
- the spring units of the two spring devices are active, by a
- Control device controlled spring units formed.
- the suspension properties (in particular the rigidity) and / or the damping properties of the spring unit can be set active in an advantageous manner.
- Incline anti roll stabilizers or roll stabilizers in the spring devices are Incline anti roll stabilizers or roll stabilizers in the spring devices.
- Control device can then be designed to control the active spring units for active roll stabilization of the car body.
- the spring units can basically be designed in any suitable manner. So can simple conventional steel springs, rubber springs or air springs individually or in any combination are used. Particularly advantageous configurations result when the two spring devices each have a hydraulic spring unit (that is, for example, a hydropneumatic, a hydromechanical or
- Electro-hydraulic spring unit since this particularly space-saving or
- Austelkieen between the car body and the chassis unit can be taken in principle by the spring device in any suitable manner.
- the contact surface of at least one of the two contact elements can be designed so that even with such a boring movement, the contact between the contact surfaces of the two contact elements is maintained.
- the two contact elements may in particular be designed so that even such a boring movement between the car body and the chassis unit on the course of the contact point curve (analogous to the resistance to a Querauslenkung described above) a Auscardwiderstand with any course (on the
- the resistance to the transverse deflection in dependence on the Ausfwinkel the car body with respect to the chassis unit has an arbitrarily predetermined course.
- the profile of the transverse deflection resistance curve that is, the course of the
- Transverse deflection resistance across the transverse deflection regardless of the Turnout angle remains the same, so for example when cornering essentially the same cross spring characteristic results as when driving on a straight line.
- a design can be realized in which when cornering a deviating to any specifications from driving on a straight track cross spring characteristic is achieved.
- Cross spring characteristic of the spring system for a particular suspension unit mainly or even exclusively of a part of the spring means, in particular a single spring means defined, while another part of the spring means for this suspension unit for this purpose provides a lesser contribution or possibly even no contribution. This makes it possible, among other things, a desired
- Vehicle transverse direction exerts on the car body.
- the first contact element for at least partial compensation of Ausfierien between the car body and the chassis is pivotally mounted about the vehicle height direction.
- the second contact element for at least partial compensation of Ausfierien between the car body and the chassis to be mounted pivotably about the vehicle height direction.
- the contact surfaces between the first and second contact elements can in principle be designed in any suitable manner in order to realize the at least one contact point curve.
- the first contact element typically has a first contact surface
- the second contact element has a second contact surface which contacts the first contact surface in the at least one contact point.
- the first contact surface and the second contact surface are such
- Vehicle transverse direction can be achieved in any suitable manner.
- the first contact surface and the second contact surface are formed so as to substantially over two in a vehicle transverse direction
- first contact surface and / or the second contact surface is formed from a material. which comprises a plastic, preferably an elastomer, more preferably polyurethane. This can be in terms of wear characteristics and in particular the damping properties (for example, the attenuation of structure-borne noise) achieve particularly favorable configurations.
- the use of a plastic material also has the advantage that relative movements of the two contact elements parallel to the surface of the current contact zone (between the two contact surfaces) can be absorbed by an elastic shear deformation of the plastic material in the direction of relative movement, so there is no slippage between the two contact elements comes.
- Vehicle longitudinal direction acting longitudinal forces between the car body and the chassis unit can basically be done in any suitable manner.
- a conventional entrainment via a corresponding hinge between the car body and the chassis unit, for example, a pivot may be provided.
- this function of longitudinal driving is also at least partially integrated in the spring device.
- for the transmission of forces in a vehicle longitudinal direction between the first contact element and the second contact element may be provided two arranged in a vehicle longitudinal direction on both sides of the first contact element and the second contact element stop elements.
- the spring unit for transmitting forces in a vehicle longitudinal direction at least one to take in
- the guide means formed in the vehicle longitudinal direction comprise. In the case of a hydraulic design of the spring device, this may be a piston guide of this spring device.
- the spring unit can, as mentioned, basically be designed arbitrarily.
- the spring unit comprises a hydraulic spring element, in particular a
- hydropneumatic or electrohydraulic spring element In active variants of the spring unit this can preferably be supplied by an active hydraulic unit.
- the hydraulic unit can basically be arranged at any point in the vehicle. Preferably, it is arranged on the chassis. However, it is also understood that the hydraulic unit can also be integrated in the suspension device.
- the spring unit may comprise a passive emergency spring element in certain variants of the invention.
- the emergency spring element is kinematically arranged in series with another, in particular active, spring element of the spring unit, so that a particularly simple and compact design is achieved.
- the emergency spring element can basically be designed in any suitable manner. In particularly simple and robust designs, the emergency spring element comprises at least one rubber spring.
- Contact element comprise a passive emergency spring element.
- this emergency spring element may in turn comprise at least one rubber spring.
- the spring unit is designed as an active, actuated by a control device spring unit, wherein the control device is then designed in particular to the spring unit for modifying a
- control device may also be designed to control the spring unit for level control of the spring unit and thus also of the car body.
- the spring unit may comprise at least one passive damper device and / or at least one active damper device, whereby the degree of functional integration and thus the space savings can be further promoted.
- a damper device can be easily via one or more passive and / or active
- control device can then is adapted to the active damper device for modifying a
- the spring unit may for example comprise a measuring device of the detection device, in particular for
- Height measurement (thus, therefore, to measure the height level of the car body) and / or pressure measurement on the spring unit can serve.
- Detection means connected control means may be provided which processes the signals of the detection means and the spring unit in response to the signals of the detection means. This can be a leveling and / or a
- Roll compensation, and / or an active suspension and / or active damping can be realized as well as an active increase in the derailment safety, in particular an active increase in derailment safety by applying a pitching moment, which counteracts a wheel relief.
- a rolling support device is provided which
- Wank onlyinides is arranged kinematically parallel to the spring unit and counteracts in a conventional and well-known manner rolling movements of the car body to a vehicle longitudinal direction parallel to the roll axis.
- the anti-roll device may comprise two pendulum elements, which
- the transverse spring characteristic can then be matched to the position of the instantaneous pole via the design of the contact point curve, in order to achieve a specific rolling behavior (in particular a specific course of the tilting or roll angle) of the carbody at one
- Actuator provided, which is adapted to be driven by a
- Control device to generate a transverse deflection of the car body with respect to the chassis in a vehicle transverse direction can then be matched to the design and performance of the actuator via the design of the contact point curve.
- the resistance to a transverse deflection of the car body can be adjusted so that a comparatively small actuator device is sufficient to a desired transverse deflection
- the present invention can be used in conjunction with any vehicles for any purpose.
- the vehicle is for one
- the present invention further relates to a spring device for a vehicle, in particular a rail vehicle, which the above in connection with the
- FIG. 1 shows a schematic sectional view of a preferred embodiment of the vehicle according to the invention in neutral position with a preferred embodiment of the spring device according to the invention; a schematic sectional view of a part of the vehicle of Figure 1 in the region of the spring means; a further schematic sectional view of a part of the vehicle of Figure 1 in the region of the spring means (in the sectional plane of Figure 2 and along line III-III of Figure 4); a schematic sectional view taken along line IV-IV of Figure 3; a schematic representation of the course of the contact surfaces, the contact point curve and the Querauslenkungswiderstands the spring device of Figure 1;
- Figure 6 is a schematic sectional view of another preferred embodiment of the vehicle according to the invention in neutral position with a further preferred embodiment of the spring device according to the invention;
- Figure 7 is a schematic representation of the course of the contact surfaces, the
- Figure 8 is a schematic representation of the course of the contact surfaces
- a first preferred exemplary embodiment of the vehicle according to the invention in the form of a rail vehicle 101 will be described below with reference to FIGS. 1 to 5.
- the vehicle 101 is designed for high-speed traffic with a nominal operating speed above 250 km / h, in particular above 350 km / h.
- FIG. 1 shows a schematic sectional view of the vehicle 101 in a sectional plane perpendicular to the vehicle's longitudinal axis.
- the vehicle 101 comprises a body 102, which in the region of its first end on a chassis unit in the form of a
- Bogie 104 is supported and is supported in the region of its second end on another chassis in the form of another bogie.
- the bogie 104 and the further bogie are designed identically, so that only the features of the bogie 104 will be discussed below. It should be understood, however, that the present invention may be used in conjunction with other configurations that utilize other chassis designs, or that the body is supported on a different number of chassis, for example, a single chassis. Furthermore, two car bodies can be supported on a chassis unit, as this
- Jacob bogies is the case.
- a coordinate system x (predetermined by the wheel contact level of the bogie 104) is shown in the figures . , y, z, in which the x-coordinate is the longitudinal direction of the rail vehicle 101, the y-coordinate is the transverse direction of the rail vehicle 101 and the z-coordinate is the
- Height direction of the rail vehicle 101 denote.
- the bogie 104 conventionally comprises two wheel units in the form of wheelsets 04, on each of which a primary suspension 103.1 Bogie frame 104.2 is supported.
- the car body 102 is in turn supported by the secondary suspension 103.2 on the bogie frame 104.2.
- the primary suspension 103. 1 is simplified in FIG. 1 by coil springs. It will be understood, however, that primary spring 103.1 may be any suitable one
- the vehicle 101 further comprises in the region of the bogie 104 a
- Roll compensation device 105 acts kinematically parallel to the secondary suspension 103.2 between the swivel frame 104.2 and the car body 102 in the manner described in more detail below.
- the roll compensation device 105 comprises a sufficiently well-known roll support 106, which is connected on the one hand to the bogie frame 104.2 and on the other hand to the wagon body 102.
- the roll support 106 comprises a torsion arm in the form of a first lever 106.1 and a second torsion arm in the form of a second lever 106.2.
- the two levers 106.1 and 106.2 sit on both sides of the longitudinal center plane (xz-plane) of the vehicle 101 in each case rotationally fixed on the ends of a torsion shaft 106.3 of the roll support 106.
- the torsion 106.3 extends into
- Transverse direction (y-direction) of the vehicle and is rotatably mounted in bearing blocks 106.4, which in turn are fixedly connected to the bogie frame 104.2.
- a first link 106.5 is articulated, while at the free end of the second lever 106.2, a second link 106.6 is articulated.
- the roll support 106 is pivotally connected to the car body 102.
- the two arms 106.5, 106.6 extend in the drawing plane of Figure 1 (yz plane) in the present example so inclined to the vertical axis (z-axis) of the vehicle 101 that their upper (articulated to the car body 102) ends are offset towards the vehicle center and their longitudinal axes intersect at a point MP in the drawing plane of Figure 1 (yz plane) in the present example so inclined to the vertical axis (z-axis) of the vehicle 101 that their upper (articulated to the car body 102) ends are offset towards the vehicle center and their longitudinal axes intersect at a point MP in the
- 106.6 forms the instantaneous pole of a roll movement of the car body 102 about this roll axis.
- the roll support 106 allows a well-known on both sides of the vehicle synchronous compression of the secondary suspension 103.2, while preventing a pure rolling motion about the roll axis or the instantaneous pole MP. Furthermore, due to the inclination of the handlebars 106.5, 106.6 by the roll support 106 a
- the centrifugal force F acting on the bogie frame 104.2 in the center of gravity SP of the vehicle body 102 causes a bowing movement that results from a greater compression of the primary suspension 103.1 on the outside of the bow.
- the described design of the roll support 106 causes at a curved travel of the vehicle 101 in the region of the secondary suspension 103.2 a compensation movement, which counteracts the rolling movement of the car body 102 to the outside, as indicated in Figure 1 by the dashed contour 102.1.
- centrifugal force F causes or supports.
- the instantaneous pole MP is placed close to the center of gravity SP, possibly even coincides with this.
- the centrifugal force F provides only a small contribution or even no contribution to the deflection of the
- Roll compensation device 105 are applied, between the
- Bogie frame 104.2 and the car body 102 acts.
- the pitch comfort for the passengers of the vehicle 101 is increased because the passengers (in their frame system set by the car body 102) actually form part of the ground reference frame (x, y, z) acting lateral acceleration a p or centrifugal force F p only as an increased acceleration component a zp or Force effect F zp perceive in the direction of the bottom of the car body 102, which is generally perceived as less disturbing or unpleasant.
- Transverse acceleration component a yp or centrifugal force component F yp is thus reduced in an advantageous manner.
- the maximum permissible values for the lateral acceleration a yp max acting in the reference system (x p , y p , z p ) of the passengers are generally specified by the operators of the vehicle 101. Evidence of this is provided by national and international standards (such as EN 12299).
- Deflection in the vehicle transverse direction represents an important factor for the roll behavior of the car body.
- the actuator 107 for a desired adjustment of the roll angle of the car body around the instantaneous pole MP must apply the higher the higher the resistance to this transverse deflection ,
- the secondary suspension is usually one
- the secondary suspension 103.2 comprises two identically designed
- Car body 102 and the bogie 104 defined about the vehicle vertical axis.
- each spring device 108 comprises a first contact element 109 with a first contact surface 109.1, a second contact element 110 with a second contact surface 110.1 and a spring unit 11, which is kinematically connected in series between the vehicle body 102 and the chassis unit 104 are arranged.
- FIG. 2 shows a section through a plane of symmetry of the spring device 108.
- the spring unit 1 1 1 sits with one end on the bogie frame 104.2, while the other end supports a substantially U-shaped support 1 12.
- the carrier 1 12 sits reversed on the spring unit 1 1 1, so that there is a nested arrangement in which a part of the spring unit 1 1 1 between the two legs 1 2.1 of the carrier 1 12 extends and is connected to its base 1 12.2.
- the first contact element 109 is articulated via a respective pivot joint 1 13.
- the common pivot axis 1 13.1 of the two pivot joints 1 13 extends in the
- the first contact element 109 is also designed substantially U-shaped, wherein in each case a pivot joint 1 13 engages the free end of the respective leg 109.2 of the first contact element 109.
- the first contact element 109 and the carrier 1 12 are also arranged nested, wherein the first contact element 09, the carrier 108.4 in its interior (via the pivot area provided in normal operation) freely about the pivot axis 1 13.1 pivotally receives, so that overall results in a particularly compact design ,
- the first contact element 109 In the region of its base 109.3, the first contact element 109 (on the side facing away from the carrier 1 12), the first contact surface 109.1, via which the first contact element 109, a second contact surface 1 10.1 of the second contact element 1 10 in at least one contact point 1 14.1 a contact point curve 1 14 contacted.
- both the first contact surface 109.1 and the second contact surface 1 are 10.1 as at most simply curved surfaces with parallel
- the first contact surface is as in
- a certain surface contact results. It is understood, however, that in other variants of the invention, at least one of the two contact surfaces may be formed as a multi-curved surface. In this way, for example, a pitching mobility can be introduced into the secondary suspension 103.2, which pitching movements (about a pitch axis parallel to the vehicle transverse direction)
- pitch mobility optionally also elsewhere in the secondary suspension 103.2 (for example in the area of the bearing 1 13 and / or the connection of the second contact element 1 10 on the car body 102 and / or the connection of the spring unit 1 1 1 am Bogie frame 104.2) can be realized.
- the pitch mobility can also be realized via a corresponding elasticity of at least one of the contact elements (for example in the area of the contact surface).
- the second contact element 1 10 is attached to the underside of the car body 102, so that the kinematic chain or the power flow in supporting the car body 102 of the car body 102 via the second contact element 1 10, then the first contact element, then the carrier 112 and finally the Spring unit 1 1 1 runs in the bogie frame 104.2.
- Order of components between the car body 102 and the bogie 104 may be provided.
- the spring unit 1 1 1 between the car body 102 and the second contact element 1 10 may be arranged, in which case the carrier 1 12, for example, on the emergency spring 1 1 1 .1 sits.
- first contact surface 109.1 and the second contact surface 1 10.1 are provided with a toothing 16 (not shown in FIG. 2 for reasons of clarity) in order to avoid slipping in the vehicle transverse direction between the first contact element 109 and the second contact element 110 ,
- the toothing comprises a first groove 16.1 extending parallel to the pivoting plane of the first contact element 109 and into which a first projection 16.2 of the second contact element 109 engages.
- first groove 1 16.1 is centrally (in the vehicle transverse direction), a radial second projection
- first contact element 109 1 16.3 of the first contact element 109 is formed.
- the second projection 1 16.3 engages in an axial (in the vehicle transverse direction) axial second groove 16.4 in the first projection 1 16.2, wherein in the present example a slight play (in the
- Vehicle transverse direction is present, so that the second projection 1 16.3, the first projection 116.2 in a state with standing in a straight flat track vehicle 101 ideally initially does not touch. Accordingly, the first contact surface 109.1 and the second contact surface 1 10.1 can also roll unimpeded to one another in this respect.
- Boundary wall of the second groove 1 16.4 engaged and prevented by the resulting in the vehicle transverse direction positive locking such slip.
- the second projection 1 16.3 is provided in the pivoting plane for this purpose with a correspondingly curved surface contour, while the
- Boundary walls of the second groove 1 16.4 designed as a simple flat walls.
- 1 16.4 are preferably matched to one another in such a way that the positive locking in the vehicle transverse direction serving for preventing slippage is achieved in each swivel position, while in the vehicle height direction preferably no such positive connection is formed, so that the first projection 1 16.2 and the second projection 1 16.3 are not substantially involved in the transmission of the supporting force in the vehicle height direction.
- the design of the second projection 1 16.3 and the associated boundary walls of the second groove 1 16.4 continue such that the second projection 1 16.3 to be expected over the entire during operation of the vehicle
- Vehicle transverse direction spaced slip prevention pairings from a respective second projection 1 16.3 and an associated second groove 1 16.4 can be provided. These slip prevention pairings are at least arranged so that at any time or in any operating condition of the vehicle at least one of
- Slip prevention pairings takes over the function of slip prevention.
- the two contact surfaces can also be provided, in the case of which a slip of this kind can be prevented in the transverse direction of the vehicle by means of an otherwise positive fit.
- the two contact surfaces can be substantially completely provided with a corresponding toothing.
- Vehicle transverse direction between the two contact surfaces may also be missing, so therefore can be given in the vehicle transverse direction pure frictional engagement between the two contact surfaces.
- the spring unit 1 1 1 comprises a hydraulic part and a mechanical part.
- the hydraulic part comprises a hydropneumatic spring 1 15, while the mechanical part comprises an emergency spring 1 1 1.1.
- the emergency spring 1 1 1.1 is in the power flow between the
- the emergency spring 1 1 1 .1 is in the present example in a conventional manner as
- Rubber layer spring formed This has particular advantages in terms of damping of structure-borne noise. However, it is understood that in principle any other types of springs can be used for the emergency spring.
- the hydropneumatic spring 15 comprises a hydraulic power transmission part 1 15.1 connected in the power flow between the emergency spring 1 1 1 .1 and the bogie frame 104. 2 and a hydraulically coupled hydropneumatic spring part 1 15. 2 which provides the actual spring action of the hydropneumatic spring 115.
- the power transmission part 1 15.1 comprises a piston-cylinder arrangement with a cylinder 1 15.3, which is connected to the base 1 12.2 of the carrier 1 12.
- a cylinder 1 15.3 is sealingly on the emergency spring 1 1 1 .1 supported piston 115.4, so that the cylinder 1 15.3 and the piston 1 15.4 define a first working space 1 15.5.
- a reverse arrangement may be provided, in which the piston is connected to the base of the carrier 1 12 and the cylinder is supported on the emergency spring 1 1 1 .1.
- the spatial arrangement of cylinder 1 15.3 and piston 1 15.4 is selected so that the power transmission and thus the main direction of action of the spring unit 108 is parallel to the vehicle height direction. It is understood, however, that in other variants of the invention, a different orientation of the main direction of action of the spring unit can be provided.
- the working space 1 15.5 is filled with a hydraulic medium and connected via a hydraulic line 1 15.6 with the hydropneumatic spring part 1 15.2, which is arranged on the bogie frame 104 in the present example. It goes without saying, however, that the hydropneumatic spring part 1 15.2 can in principle also be arranged at any other point in the vehicle 101 thanks to the simple coupling via the hydraulic line 1 15.6.
- the hydropneumatic spring part 1 15.2 comprises in a conventional manner a hydraulic second working space into which the hydraulic line 1 15.6 opens.
- the second working space is connected via at least one sealed movable force-transmitting element with a pneumatic third working space in operative connection, which receives a closed acting as a gas spring gas volume.
- the compressibility of the gas thus provides the actual spring action in the present example.
- any other springs can be used, in particular purely mechanical springs, active or passive electromechanical springs, magnetic springs or the like can be used.
- FIG. 5 shows a schematic representation of the profile of the contact surfaces 109.1 and 110.1 resulting in the sectional plane of FIG. It should be noted at this point that the contact surfaces 109.1 and 10.1 in Figure 5 for the sake of
- the first contact surface 109.1 has a cylindrical shape
- the second contact surface 110.1 has a shape (prismatic in the vehicle longitudinal direction) with curvatures which vary in sections in FIG
- a transition into a convex configuration takes place, which then prevails in an outer area 1 17.3.
- Rolling device 105 predetermined compensating movement about the instantaneous pole MP, so the car body 102 is deflected, inter alia, in the vehicle transverse direction (y-direction) with respect to the bogie 104.
- the design of the two contact surfaces 109.1, 1 10.1 requires that the center of gravity SP of the car body 102 via the second contact element 1 10 by an amount dz is moved, more precisely, is lifted upwards (thus therefore the contact point 1 14.1 on the contact point curve 1 14 wanders).
- FIG. 5 furthermore shows a schematic representation of the profile of the deflection of the center of gravity SP of the car body 102 in the vehicle height direction, which results in the sectional plane of FIG. H. the function dz (y), depending on the
- FIG. 5 shows the profile of the transverse deflection resistance Wy
- Spring device 08 as a function of the transverse deflection y.
- Car body 102 continues to be easy. so that a section-wise degressive, then almost linear but only slight increase of the transverse deflection resistance Wy results.
- the transverse deflection resistance Wy depends on the deflection dz of the car body 102 and the inclination of the contact force K to the vehicle height direction. The larger these are, the greater is the transverse deflection resistance Wy.
- Nominal operating speed of the vehicle 101 is adjusted.
- the adaptation of the transverse spring characteristic to a desired course can be achieved with an (arbitrarily) predetermined spring characteristic of the spring device 108 in FIG.
- Vehicle height direction take place.
- High-speed traffic is the contact point curve 1 14 formed on the one hand in the adjacent to the neutral position transverse deflection center region 1 17.1 so that there is a progressive characteristic of the Querlenkungswiderstands Wy. This is chosen so that the spring unit 108 alone by acting on the car body weight force 102 a Querauslenkungswiderstand Wy and thus one in the
- Vehicle transverse direction acting restoring force on the car body 102 exerts.
- the restoring force on the car body 102 is dimensioned so large that it is sufficient even at a maximum during operation of the vehicle track cant to reset the car body at least in the vicinity of the neutral position, preferably substantially in the neutral position.
- the hereby achieved self-centering effect of the secondary suspension 103.2 is advantageous insofar as hereby in case of failure of the actuator 107 in the event that the vehicle comes to a point of the traveled route with such a maximum track overshoot stops, ensures that the limiting profile of the route not hurt.
- the actuator 107 must apply ever less additional force in order to achieve a desired roll angle of the vehicle body 102 to adjust.
- the actuator 07 used can then be made smaller and lighter. This is particularly advantageous for cases in which the instantaneous pole MP is close to the center of gravity SP, so that the centrifugal force can not make a significant contribution to the setting of the roll angle.
- Such configurations with low and thus close to the center of gravity SP instantaneous pole MP may be particularly desirable when comparatively large roll angle (for example, up to 8 ° to 10 °) to be set without violating the boundary profile of the track by large transverse deflections.
- the spring unit 1 1 1 1 can basically be designed as a simple passive unit. In particularly advantageous variants of the invention with a high degree of functional integration, the spring unit 1 1 1 is actively designed insofar as a control device 122 is provided which, optionally in response to the signals of a corresponding sensor
- Throttle device for adjusting the damping
- the supply device 124 on the one hand be designed so that it modifies the pressure in the gas spring and thus their characteristics. This can be done for example via an immediate adjustment of the pressure in the gas spring. Additionally or alternatively, the supply device 124, the filling of the hydraulic part of the
- hydropneumatic spring part 1 15.2 vary with the hydraulic medium. This makes it possible, inter alia, to raise or lower the car body 102 or to keep it independent of loading at a certain level.
- the second contact element 1 10 could be mounted correspondingly displaceable in the longitudinal direction of the car body. This is also possible without any problems. Additionally or alternatively, this compensation in the longitudinal direction of the car body but possibly also via an elastic shear deformation of at least one of the contact elements 109, 1 0 done.
- Vehicle longitudinal direction on both sides contact directly via sliding elements 126 and so realize the longitudinal entrainment of the car body 102.
- the first contact surface 109.1 and the second contact surface 110.1 are made of a plastic.
- This is preferably an elastomer, such as polyurethane. This is one with regard to wear and the
- Damping of structure-borne noise in the spring device 108 achieved particularly favorable design.
- a separate emergency spring 1 1.1 is provided, on which the power transmission part 1 5.1 of the spring unit 1 1 1 sits.
- the emergency spring can be arranged in other variants of the invention also elsewhere.
- the emergency spring for example, between the second contact element 1 10 and the car body 102 may be arranged.
- the emergency spring in the spring unit 1 1 1.
- a correspondingly elastic part of the carrier 1 12 and / or the bearing 1 13 and / or the first contact element 109 form at least a part of such emergency spring.
- vehicle 201 corresponds in its basic design and operation of the vehicle 101 of Figure 1 to 5, so that only the differences should be discussed here.
- the vehicle 201 is a regional vehicle or subway vehicle, which is a nominal operating speed in the low or medium speed range between 60 km / h and 160 km / h. This is reflected in the design of the roll support 206 and the design of the second contact element 210.
- FIG. 7 shows a schematic representation of the profile of the contact surfaces 209.1 and 210.1 resulting in the sectional plane of FIG. It should be noted at this point that the contact surfaces 209.1 and 210.1 in Figure 7 are again shown for reasons of clarity with a greater curvature than in reality.
- the first contact surface 209.1 has a cylindrical shape
- the second contact surface 210.1 has a (in FIG. 7
- Vehicle longitudinal direction prismatic has shape with sections of alternating curvature in the sectional plane shown.
- a point 217.2 is a
- Transverse deflection resistance Wy In a further transverse deflection of the car body 202, the deflection dz of the car body 102 increases continuously, with a sectionwise progressive, then linear or further progressive increase in the
- Transverse deflection resistance Wy results, as it would be achieved in a conventional transverse buffer.
- dash-dotted lines 227 in other variants of the invention it can be provided that the two spring devices in the vehicle transverse direction, in particular substantially equidistant, on both sides of a pivot point of the car body 102 with respect to the chassis 104 the
- Vehicle height direction in particular on both sides of a (not shown)
- Pivot are arranged.
- the two spring devices 227 can absorb a rolling moment about a rolling axis running in the vehicle longitudinal direction.
- the spring devices are then preferably not directly supported on the underside of the car body 102, but on a crossbar 228, on which is supported by sliding elements 229 of the car body 102. This can be ensured in a simple manner that a boring movement between
- Car body 102 and chassis 104 can be easily taken over a sliding movement in the area of the sliding elements 229, so that the spring devices for this purpose do not have to provide any significant contribution and simplifies their design so far.
- an arrangement of more than two spring means, in particular three spring means may be provided, which can accommodate in particular (for example by not lying on a line arrangement of the spring devices) both pitching moments and rolling moments ,
- FIG. 8 shows, for a further exemplary embodiment of the vehicle 301 according to the invention, a schematic representation of the profile of the contact surfaces 109.1 and 310.1 which results in a sectional plane similar to FIG.
- the vehicle 301 corresponds in its basic design and operation of the vehicle 101 of Figure 1 to 5, so that only the differences should be discussed here.
- identical components are provided with the identical reference numerals, while similar components are provided with reference numerals increased by the value 200.
- the vehicle 301 differs from the vehicle 101 only in the design of the second contact surface 310.1. It should be noted at this point that the
- the second contact surface 310. 1 has a (in FIG. 8
- the deflection dz of the car body 102 increases again, again resulting in an initially progressive, then linear or further progressive increase in the transverse deflection resistance Wy.
- transverse spring characteristic described in connection with the first embodiment can be supplemented with the self-centering in the transverse center region to an outer movement limit, as in conventional vehicles
- Transverse deflection resistance Wy results, as indicated in Figure 8 by the dash-dotted contour 319. In other words, it may even be possible to achieve a drop in the transverse deflection resistance Wy in sections.
- Spring devices such as electromechanical, electromagnetic or electro-hydraulic elements with a correspondingly high control bandwidth, is provided.
- the present invention has been described above by way of example only, in which the hydropneumatic spring means are used in isolation from each other. It is understood, however, that in other variants of the invention, an optionally actively controllable coupling between the spring devices may be provided to avoid, for example, roll and / or pitch stiffness or adapt to certain requirements or driving situations.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
- Springs (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012105310A DE102012105310A1 (de) | 2012-06-19 | 2012-06-19 | Fahrzeug mit einer Federeinrichtung mit vorgebbarer Querfedercharakteristik |
PCT/EP2013/062773 WO2013189999A1 (de) | 2012-06-19 | 2013-06-19 | Fahrzeug mit einer federeinrichtung mit vorgebbarer querfedercharakteristik |
Publications (2)
Publication Number | Publication Date |
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EP2861476A1 true EP2861476A1 (de) | 2015-04-22 |
EP2861476B1 EP2861476B1 (de) | 2022-08-03 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP13730553.8A Active EP2861476B1 (de) | 2012-06-19 | 2013-06-19 | Fahrzeug mit einer federeinrichtung mit vorgebbarer querfedercharakteristik |
Country Status (5)
Country | Link |
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EP (1) | EP2861476B1 (de) |
DE (1) | DE102012105310A1 (de) |
ES (1) | ES2929307T3 (de) |
HU (1) | HUE060066T2 (de) |
WO (1) | WO2013189999A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102014117047B4 (de) | 2014-11-21 | 2017-12-14 | Lothar Thoni | Traverse für Schienenfahrzeuge zur Anlenkung eines Wagenkastens eines Schienenfahrzeugs an dessenDrehgestell |
DE102015205085B3 (de) * | 2015-03-20 | 2016-06-23 | Bombardier Transportation Gmbh | Drehgestell für Schienenfahrzeug |
DE102015205531B3 (de) * | 2015-03-26 | 2016-07-21 | Siemens Aktiengesellschaft | Wiegendrehgestell für ein Schienenfahrzeug und Schienenfahrzeug |
DE102020109599A1 (de) | 2020-04-07 | 2021-10-07 | Liebherr-Transportation Systems Gmbh & Co Kg | Hydropneumatische Federung für ein Fahrzeug |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4444540B4 (de) * | 1994-06-16 | 2015-08-06 | Josef Nusser | Schienenfahrzeug mit Drehvorrichtung |
AT407032B (de) | 1999-02-19 | 2000-11-27 | Siemens Sgp Verkehrstech Gmbh | Federung für ein schienenfahrzeug |
JP2002104183A (ja) * | 2000-09-26 | 2002-04-10 | Hitachi Ltd | 鉄道車両 |
DE10128003A1 (de) | 2001-06-08 | 2002-12-12 | Alstom Lhb Gmbh | Sekundärfedersystem für Fahrwerke an Niederflurfahrzeugen |
DE10316497A1 (de) * | 2003-04-09 | 2005-01-05 | Bombardier Transportation Gmbh | Fahrwerk für ein Schienenfahrzeug mit verbesserter Querfederung |
JP2005132127A (ja) * | 2003-10-28 | 2005-05-26 | Hitachi Ltd | 鉄道車両および鉄道車両用台車 |
WO2010113045A2 (de) * | 2009-03-30 | 2010-10-07 | Bombardier Transportation Gmbh | Fahrzeug mit wankkompensation |
GB2473502A (en) * | 2009-09-15 | 2011-03-16 | Bombardier Transp Gmbh | Rail vehicle suspension system with malfunction sensor |
DE102010000125A1 (de) * | 2010-01-19 | 2011-07-21 | Claas, Benedikt, 37154 | Aufhängevorrichtung für einen Eisenbahnwaggon |
DE102010011211A1 (de) * | 2010-03-08 | 2011-09-08 | Siemens Aktiengesellschaft | Vorrichtung zum Begrenzen einer Nickbewegung bei Schienenfahrzeugen |
-
2012
- 2012-06-19 DE DE102012105310A patent/DE102012105310A1/de active Pending
-
2013
- 2013-06-19 WO PCT/EP2013/062773 patent/WO2013189999A1/de active Application Filing
- 2013-06-19 HU HUE13730553A patent/HUE060066T2/hu unknown
- 2013-06-19 EP EP13730553.8A patent/EP2861476B1/de active Active
- 2013-06-19 ES ES13730553T patent/ES2929307T3/es active Active
Non-Patent Citations (2)
Title |
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None * |
See also references of WO2013189999A1 * |
Also Published As
Publication number | Publication date |
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EP2861476B1 (de) | 2022-08-03 |
HUE060066T2 (hu) | 2023-01-28 |
WO2013189999A1 (de) | 2013-12-27 |
ES2929307T3 (es) | 2022-11-28 |
DE102012105310A1 (de) | 2013-12-19 |
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