DE102010060501A1 - Railway shaft testing stand has foundation, drive unit that is supported on foundation, where drive unit is stand in drive connection with test shaft - Google Patents

Abstract

The railway shaft testing stand has a foundation, a drive unit that is supported on the foundation, where the drive unit is stand in drive connection with a test shaft (2). Two bearing blocks are supported on the foundation, where the test shaft is mounted in the bearing blocks. Other two bearing blocks are arranged between the former bearing blocks. A controlling device is provided for controlling the drive unit and actuators.

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a railway shaft test rig, by means of which the behavior of a railway wave under dynamic load can be examined.

STATE OF THE ART

Railway shafts of a wheelset are subjected to high mechanical dynamic loads during driving. If there is a failure, for example, as a result of a crack in the railway shaft, this can cause considerable damage to the train equipped with the railway wave and the environment. In the worst case, a failure of a railway wave can lead to derailment of the train, which can result in serious injury to passengers. In July 2008, for example, it came to a break in one of the 32 axles of a high-speed train in a tight curve of Cologne Central Station. For the design of the railway shafts are on the requirement of lasting durability, even with the above-mentioned high dynamic stresses beyond narrow constraints: To reduce the so-called "unsprung masses" the railway shafts should have the lowest possible weight. Also, especially for driven railway shafts of the space in view of the directly attacking the railway shafts drive units space. This basically speaks for the smallest possible cross sections of the railway shaft, which, however, u. U. a conflict of objectives with the required fatigue strength is given at high loads. This conflict of objectives is increasingly solved by the use of a high-strength or high-strength steel. This has led increasingly to the use of chromium, nickel and molybdenum enriched tempering steel, in particular 34 CrNiMo 6. For the selection of materials and the structural design of the railway shafts, the dynamic forces acting during operation, the masses to be carried by the railway shafts and the technical regulations and standards (in particular EN 13261 . 13262 and 13104 "Wheelsets, bogies, wheelset product requirements"), which, however, do not contain any information on the permissible stresses with regard to the higher-strength steels. Only with regard to the higher notch sensitivity of the higher-strength steels should a higher safety impact be used.

A railway wave is exposed to about 300 load changes per kilometer. This should be "durable", which means that this 500 billion load cycles must survive without failure, which corresponds to a mileage of 15 million kilometers, which corresponds to a typical high-speed train a life of about 30 years. A particular stress on the railway waves results from during the ride of the train whirled up and hit against the railway waves stones, which can lead to defects in the surface of the railway waves, possibly with a then proceeding from the defect in the subsequent operation crack propagation. Other problems are corrosion nests as a result of damage to the protective coating, possibly due to the swirled stones and / or so-called turning depths, which has left a not perfect chip tool when turning off the shaft. There has been limited experience of the influence and evaluation of such additional stresses on railway shafts until relatively recently, with the fear that these additional stresses on railway shafts from the recently used high-strength steels will have very different effects than those for established ones Knows and has learned to master steel grades.

The problem outlined above has led, especially for railway shafts of high-speed trains, to an increased exchange rate of the railway shafts, which causes additional costs. While the "service booklet" stipulates an inspection every 300,000 km for these high-speed trains, the test interval after the Cologne failure of the railway shaft was shortened to 30,000 km. Performing an ultrasonic test on a so-called Hohlwellenprüfstand takes about 30 minutes for a single railway wave. From the foregoing problem, it can be seen that there is a great need for improved test rigs for testing railway shafts in order to gain further insight into the failure course and causes of failure of railway shafts as a result of the stress on their operation.

OBJECT OF THE INVENTION

• – einer tatsächlich in einem Laufsatz eingesetzten Laufsatzwelle und/oder
• – einer gesondert für Untersuchungen, unter Umständen mit veränderter Geometrie gegenüber der Laufsatzwelle erstellten Versuchswelle,

unter einer dynamischen Last, welche die tatsächlichen Beanspruchungen einer Eisenbahnwelle im Betrieb approximiert, ermöglicht.The invention has for its object to propose a railway shaft test bench, by means of which the examination of a railway shaft, in particular

• A moving set shaft actually used in a moving set and / or
• A test shaft separately prepared for examinations, possibly with an altered geometry in relation to the scroll set,

under a dynamic load which approximates the actual stresses of a railway shaft during operation.

SOLUTION

The object of the invention is achieved with a railway shaft test stand with the features of independent claim 1. Further embodiments of such a solution will become apparent according to the dependent claims 2 to 21.

DESCRIPTION OF THE INVENTION

While according to known from the prior art railway shaft test stands (see also 1 ) a railway shaft with only one impeller or spare impeller pressed thereon in an end region forms a T-shaped test structure in which the transverse leg of the T is formed with the impeller firmly clamped in the test bench and the railway shaft forms the vertical leg of the T, which is excited to bending vibrations in the end region opposite the impeller in the test bench, the present invention is based on the finding that such test stands are limited with regard to the stresses that can be applied to the railway shaft, in particular with regard to the applicable stress amplitudes and frequencies. In addition, the explained training known test stands leads to a of the excited end portion in the direction of the impeller firmly clamped end portion of the railway shaft linearly increasing bending moment, which differs substantially from the actually acting in operation of the railway shaft bending moment, so that brought about with such a test bed Trial results the reality u. U. only map locally.

Against this background, the solution according to the invention is designed to ensure a more realistic loading of the railway shaft with the bending moment compared to the test bench known from the prior art. For this purpose, the invention proposes a railway shaft test bench in which a drive unit supported on a foundation is in driving connection with the test shaft. Here, the coupling between the drive unit and test shaft can only serve to transmit the drive torque. Quite conceivable, however, is that, for example, via the said coupling and the test shaft is held axially.

In the railway shaft test stand according to the invention, two first bearing blocks are supported on the foundation. In these bearing blocks, the test shaft is supported, namely radially supported. Furthermore, two second bearing blocks are provided according to the invention. When looking in the direction of the longitudinal axis of the test shaft, the two aforementioned first bearing blocks are arranged between these second bearing blocks.

The second bearing blocks are not fixed (directly) to the foundation. Rather, the second bearing blocks are supported with the interposition of an actuator on the foundation that in the region of the second bearing blocks via the actuators each have a transverse force can be introduced into the test shaft. In this case, the admission of the two second bearing blocks via a single common actuator can take place. Preferably, however, in each case one actuator is used for each second bearing block, wherein this can also consist of two partial actuators on both sides of the bearing blocks (viewed in the direction transverse to the longitudinal axis of the test shaft).

Furthermore, the second bearing blocks have a degree of freedom in the direction of action of the actuator, so that the position of the bearing blocks can change depending on the actuation by the actuator in the direction of this degree of freedom.

According to the invention, a control device is provided, via which the drive unit and the actuators can be controlled in such a way that the test shaft can be subjected to a rotating four-point bending load for the rotating test shaft. This refinement is based on the finding that, for the actual operation of a railway shaft, the bending moment curve as a result of the introduction of transverse forces on the one hand in the region of the wheels and on the other hand in the region of the bearings between the railway shaft and the vehicle body corresponds to such a four-point bending stress. Thus, the stresses of the test shaft in actual operation of the railway shaft can be simulated with the railway shaft test stand according to the invention. In this case, the induced four-point bending stress represents a realistic load. Rather, the bending moment rotating in actual operation of the railway shaft can be simulated by the railway shaft test stand according to the invention. If the test shaft tested in the railway shaft test bench is a type of test shaft with a geometry that has changed compared to the actual track set shaft, the described four-point rotating bending stress has the advantage that in the test shaft between the first bearing blocks a bending moment characteristic that is substantially constant in the axial direction ( with rotating axis of action), so that there are defined conditions over an enlarged axial area of the test shaft.

It is entirely possible that in a railway shaft test bench according to the invention the distances of the bearing blocks are adapted to a predetermined geometry of the test shaft to be tested, these can then be given a firm design. In a further embodiment of the invention, however, the distance between adjacent bearing blocks is at least partially adjustable. In this case, an adjustment of the spacing of adjacent bearing blocks in a small frame may be possible to make a fine adjustment of the components, for example, to compensate for assembly or manufacturing inaccuracies. An adjustability of the distances of adjacent bearing blocks is also possible on a larger scale, if test shafts of different geometries are to be tested with the same test stand, for example, set sprockets for different series or even set of sprockets for different types of railways or trams u. ä. According to another idea of the invention, the adjustability of the distances between adjacent bearing blocks can also be used to test with the same test stand on the one hand "real" impeller shafts and on the other hand test shafts with fundamentally different geometry.

For the formation of the bearings of the test shaft in the bearing blocks can be any bearing, especially bearings in training as cylindrical roller bearings, use in any configuration as a fixed or floating bearing. In a preferred embodiment, the bearing of the test shaft is carried out in at least three bearing blocks with bearings in training as a floating bearing. If an axial fixation of the test shaft away from the bearing blocks, for example via the coupling of the drive unit, it is even proposed according to the invention that the bearing of the test shaft in all four bearing blocks with rolling bearings in training as a floating bearing. This embodiment is based on the recognition that on the one hand the considerable mechanical stress of the railway shafts in the test stand can lead to considerable heating of the railway shaft, which can be associated with a thermal change in length of the railway shaft. This change in length can be compensated via the formation of rolling bearings as a floating bearing, which then caused by a change in length longitudinal forces are avoided in the test shaft, which can distort the measurement result and / or have an axial distortion of the test shaft between the camps result, the increased Bearing friction can lead to further warming. U. U. can also be driven at higher speeds as a result of avoiding the lateral start-up of the camp, which can result in a time savings. On the other hand, the deflection of the test shaft can cause the axial distance between the support points of the bearing blocks or the bearing in the bearing blocks on the test shaft changes, which can also be compensated by the storage in training as a floating bearing. If such changes in length were blocked by fixed bearings, there would be an undesirable additional stress on the bearings of the railway shaft test bench. Above all, however, such additional axial loads on the test shafts would impair the test results in a manner which is difficult or impossible to grasp.

• – Sicherung eines Schmierzustandes eines Lagers,
• – Vermeidung von Verunreinigungen des Lagers von außen und/oder
• – Gewährleistung der Einbindung des Lagers in einen Schmiermittelkreislauf und/oder Kühlkreislauf

können aber auch Dichtungen vorgesehen sein. Eine besondere Ausgestaltung der Erfindung schlägt hier den Einsatz mindestens einer berührungslosen Dichtung vor, was den Vorteil hat, dass es nicht zu einer zusätzlichen unerwünschten Erwärmung der beteiligten Bauelemente und der Prüfwelle infolge eines Reibkontaktes der Dichtung kommen kann. Andererseits werden durch die berührungslose Dichtung unerwünschte Axialkräfte zwischen Prüfwelle und Lagerbock vermieden.It is possible that the bearings between test shaft and bearing block are not sealed. in particular to

• - securing a lubricating condition of a bearing,
• - Avoid contamination of the bearing from the outside and / or
• - Ensuring the integration of the bearing in a lubricant circuit and / or cooling circuit

But seals can also be provided. A particular embodiment of the invention proposes the use of at least one non-contact seal, which has the advantage that it can not come to an additional undesirable heating of the components involved and the test shaft due to a frictional contact of the seal. On the other hand, unwanted axial forces between the test shaft and the bearing block are avoided by the non-contact seal.

When using a non-contact seal, a gap, for example in a labyrinth seal, should be dimensioned so large that the absence of contact of the sealing elements is ensured even if length changes and / or bending of the test shaft occur. In a particular embodiment of the invention, at least one displacement sensor is used in the railway shaft test stand, via which a direct or indirect detection of the relative position of a connected to the test shaft sealing element of a seal against a connected to the housing of the bearing block sealing element of the seal. For example, can be detected by a laser, which is supported by the housing of a bearing block, the distance of a shifted with the change in length sealing element. If the value detected in this way exceeds a previously predetermined threshold value, a signal can be generated which, for example, is visually or acoustically brought to the knowledge of the operator of the railway shaft test bench or registered in a fault memory. It is also possible that an automatic termination of a test run occurs when the threshold value is exceeded.

In a further embodiment of the invention, the housing are rotatably mounted in all bearing blocks. Here, the housing in the bearing blocks have a degree of rotation about an axis which is oriented transversely to the longitudinal axis of the test shaft and transversely to the direction of action of the actuator. hereby should be avoided that in the support of the test shaft in the bearing blocks a bending moment is caused, which is opposite to the intended deflection of the test shaft and could affect the measurement result. The aforementioned embodiment of the bearing blocks with a twisting degree of freedom thus leads to an unimpeded deflection of the test shaft as a result of the action of the at least one actuator and exclusively or largely only by transverse forces.

It is possible that the specification of the application by the actuators by appropriate control of the actuator is carried out. In a preferred embodiment, however, the second bearing blocks (partially) supported by sensors on the foundation, which may be, for example, force transducer. The said sensors are thus integrated into a (partial) power flow between the bearing blocks and the foundation. By means of these sensors can then be carried out instead of a pure control monitoring or control of the action of the actuators.

In the context of the present invention, an actuator of any configuration, for example an electromagnetic actuator, a hydraulic actuator u. Ä. Find use, with a suitable transmission or reduction device such as a gearbox or a hydraulic converter can find use in the power flow. According to a particular proposal of the invention, the actuator is formed with a spindle drive in which a rotary drive of a spindle nut is performed by a drive unit and generating a large translation in the spindle drive a conversion of the rotational movement of the spindle nut in a transient movement of the spindle in the direction of action Actuator, ie transverse to the longitudinal axis of the test shaft, takes place. The use of such a spindle drive in an actuator has proven to be advantageous in terms of the most accurate adjustment of the force of the actuator and / or with respect to the generation of sufficiently large Aktuatorkräfte with reasonable effort in terms of performance of the actuator used in the actuator.

In a particular embodiment of this solution, the spindle drive is designed as a ball screw drive, which is characterized by high efficiency, ie low friction losses, and under certain circumstances a backlash.

In principle, the spindle drive can be driven via an arbitrary drive motor directly or with the interposition of a transmission or a transmission means such as a chain or a pulley. The invention proposes in a further embodiment that a drive of the spindle drive takes place via a servomotor. By means of such a servo motor, the required forces can be generated in finely dosed form, whereby the control and regulating measures and devices required for the control or regulation can also be designed relatively simply.

While in principle it is quite possible that a power transmission between the actuator and the second bearing blocks over largely rigid or articulated interconnected components, it has proved to be advantageous if the power flow from the foundation to the second bearing blocks via at least one spring element. In this spring element may be any spring element, a plurality of spring elements in series or parallel connection, at least pressure and / or tension spring, at least one elastomeric spring element u. act. On the one hand, such a spring element integrated into the power flow can simplify the assembly and compensate manufacturing inaccuracies or assembly inaccuracies. On the other hand, can be done by the spring element, a smoothing of force peaks or unwanted vibrations, which may arise with the rotation of the test threshold, superimposed bending vibrations, manufacturing inaccuracies and the like.

For a further railway wave test stand according to the invention, at least one second bearing block is supported on the foundation via at least one pendulum support. In the context of the present invention, a pendulum support is understood as a straight-line or curved support element which is subjected to transverse and longitudinal forces only in its end regions, but not with a bending moment. According to the invention, a first end portion of the pendulum support is rotatably supported on the housing of the second bearing block with a rotational degree of freedom about an axis which is oriented transversely to the longitudinal axis of the test shaft and transversely to the direction of action of the actuator. The other end portion of the pendulum support is rotatably supported on the actuator (or a coupling member connected to the actuator) with a rotational degree of freedom about an axis oriented parallel to the axis of rotational degree of articulation of the other end portion of the pendulum support. This configuration has the consequence that even in the event that the actuator is not aligned exactly in its direction of action to the connection point to the housing of the bearing block, no unwanted force component in the region of the bearing block is introduced into the test shaft. Rather, the pendulum support can perform a compensatory pivoting movement as a result of the aforementioned rotational degrees of freedom. This compensation movement can also be used for the occurring deflection of the test shaft.

As a result of the explained floating bearing of the bearings of the second bearing blocks, a generation of the lateral force by the actuators would result in a deflection of the test shaft to a force component, which would be aligned with a displacement of the second bearing block along the longitudinal axis of the test shaft. This effect can be counteracted according to a further proposal of the invention, according to which a distance of a second bearing block from an adjacent first bearing block in a direction parallel to the longitudinal axis of the test shaft by a spacer can be fixed predetermined. However, this spacer must ensure that a degree of freedom of the second bearing block in the direction of action of the actuator is not blocked, so as not to affect the stress generated by the actuator.

Here are different diverse configurations of the spacer conceivable. A particularly simple embodiment of the same is given if this is designed as a pendulum support. A first end portion of this pendulum support can then be rotatably hinged to the second bearing block with a degree of rotation about an axis which is oriented transversely to the longitudinal axis of the Prüfach and transverse to the direction of action of the actuator. By contrast, the other end portion of the pendulum support is rotatably articulated to the first bearing block with a degree of rotation about an axis which is oriented transversely to the longitudinal axis of the test shaft and transverse to the direction of action of the actuator. The distance between the two bearing blocks from each other is thus ensured that with a change in the distance the pendulum support would be applied in the longitudinal direction to pressure or train. On the other hand, the pendulum support can ensure the desired degree of freedom of the second bearing block in the direction of action of the actuator with a pivoting of the pendulum support to said rotational degrees of freedom.

The first bearing blocks are fixed relative to the foundation, which in principle can be done in a known per se, for example via a screw on nuts in grooves of the foundation u. Ä .. If a particularly sensitive adjustment for the specification of the distance of the first two bearing blocks in a direction parallel to the longitudinal axis of the test wave desired, a spindle drive can be provided which can specify the distance of the first bearing blocks. If a desired distance is then set via the spindle drive, the fixing of the bearing blocks can take place with respect to the foundation.

In a special embodiment, the test shaft tested in the test stand according to the invention is not (exclusively) a "real" impeller shaft, but rather a test shaft with a different geometry. In a central axial section, the test shaft carries an impeller installed in the test stand. Furthermore, the test shaft has two first axial sections, which are spaced on opposite sides in the axial direction of the test shaft from the central axial section, but preferably at an equal distance thereof. In the area of these first axial sections then the support of the test shaft in the first bearing blocks. Inside or adjacent to the opposite end portions of the test shaft second axial sections are respectively arranged, in the area where the loading of the test shaft via the second bearing blocks takes place. As a result of this embodiment, a constant rotating bending moment profile can be generated in the axial region of the test shaft between the two first axial sections, which also acts on the connecting region of the central axial section with the running wheel. Studies have shown that this central axial section and adjacent areas with changes in diameter are particularly at risk for failure. The test of the test shaft thus allows a targeted investigation occurring damage in the vicinity of the connection between the impeller and shaft. This would in principle also be possible for the test on the "real" spit set shaft, in which case, however, the access to the central axial section and immediately adjacent sections with varying diameter would possibly be impaired, since immediately adjacent to the connection of the impeller to the "real" spreader shaft the bearing surfaces are arranged. For the embodiment according to the invention with the use of a test shaft, the distance of the first axial sections from the central axial section can be selected such that examination instruments such as a visual observation of a progress of an applied crack or notch or other examination instruments can be brought directly into the surrounding area of the central axial section , A further advantage of the individual design of the test shaft with geometries different from the genuine movement set shaft is that also the distance of the first axial sections from the second axial sections can be made free, which can influence the required force of the actuator to produce a desired bending moment. by increasing the distance between the first and second axial sections, the force of the actuator required for the desired bending moment can be reduced as a result of the increased lever arm.

If the test shaft is to be a genuine sprocket shaft, it has two first axial sections in the region of which the sprocket shaft in the spinneret carries the wheel disks in an actual operation. In the railway shaft test bench but takes place in These two first Axialabschnitten the support of the Laufsatzwelle in the first bearing blocks. The second axial sections serve for the use of the sentence set shaft in the moving set in an actual operation of the storage relative to the vehicle body. In the railway shaft test bench, however, the action of the tower set shaft by the second bearing blocks takes place in the region of these second axial sections.

Finally, the use of a railway shaft test bench is also possible for a spreader shaft, in which in the moving set in actual operation, the storage relative to the vehicle body takes place internally of the wheel discs. In this case, the first axial sections, which in the railway shaft test bench serves to support the spool set in the first bearing blocks, for the actual use of the spool set in the moving set of the bearing of the tower set relative to the vehicle body, while in this case the second axial sections, the serve in the railway shaft test bench, the application of the set shaft through the second bearing blocks, serve in actual use of the movement set for supporting the wheel discs on the spreader shaft.

• – einer Versuchswelle mit gegenüber der Laufsatzwelle veränderter Geometrie,
• – einer Laufsatzwelle für einen Laufsatz, bei welchem die Lagerung der Laufsatzwelle gegenüber dem Fahrzeugaufbau außerhalb der Radscheiben angeordnet ist und
• – einer Laufsatzwelle in einem Laufsatz, bei welchem die Lagerung der Laufsatzwelle gegenüber dem Fahrzeugaufbau zwischen den Radscheiben erfolgt.

A multifunctional usability of a railway wave test stand is obtained if the distances between bearing blocks are changeable such that the railway shaft test bench can be used for the test

• A test shaft with geometry changed with respect to the moving set shaft,
• A spout set shaft for a spreader set, in which the bearing of the spreader shaft relative to the vehicle body is arranged outside the wheel discs, and
• - A movement set shaft in a moving set, in which the bearing of the movement set shaft relative to the vehicle body between the wheel discs.

An increased cooling requirement and / or need for lubrication can be inventively taken into account when arranged in the railway shaft test bench in the bearing blocks bearings are integrated into a lubrication and / or coolant cooling circuit.

In a further embodiment, at least one temperature sensor is provided, by means of which a monitoring of a temperature of a component of the railway shaft test stand, in particular a temperature of the test shaft, a seal, a bearing, an oil cooling circuit and / or a bearing block is possible. The output signal of the temperature sensor can be supplied to a control device, where this output signal is monitored and given the presence of a predetermined temperature gradient or exceeding a threshold value of the temperature information to the operator of the railway shaft test stand, an error occurs or a termination of a test run.

Advantageous developments of the invention will become apparent from the claims, the description and the drawings. The advantages of features and of combinations of several features mentioned in the introduction to the description are merely exemplary and can come into effect alternatively or cumulatively, without the advantages having to be achieved by embodiments according to the invention. Further features are the drawings - in particular the illustrated geometries and the relative dimensions of several components to each other and their relative arrangement and operative connection - refer. The combination of features of different embodiments of the invention or of features of different claims is also possible deviating from the chosen relationships of the claims and is hereby stimulated. This also applies to those features which are shown in separate drawings or are mentioned in their description. These features can also be combined with features of different claims. Likewise, in the claims listed features for further embodiments of the invention can be omitted.

BRIEF DESCRIPTION OF THE FIGURES

In the following the invention will be further explained and described with reference to preferred embodiments shown in the figures.

1 shows a railway shaft test stand according to the prior art.

2 shows a usable in a railway shaft test bench test shaft according to the invention in training as a moving set shaft, as this can be used in an actual operation of a rail vehicle use.

3 shows a usable in a railway shaft test bench test shaft according to the invention in training as a test shaft, as this can be used in an actual operation of a rail vehicle use.

4 shows a mechanical equivalent circuit diagram of a railway shaft test bench according to the invention.

5 shows in a three-dimensional view of a structural design of a railway shaft test bench according to the invention.

6 shows a detail of the railway shaft test bench according to 5 with partially dismantled foundation.

DESCRIPTION OF THE FIGURES

1 shows a railway wave test bench 1 according to the prior art, in which a test wave 2 in the 1 underlying end an impeller 3 or a spare wheel carries, whereby a part of a moving set is formed in the form of an inverted T. This forms the impeller 3 the transverse leg of the T, while the test shaft 2 forms the vertical leg of the T. The impeller 3 is via a clamping device 4 on a foundation 5 attached, which in a conventional manner for the purpose of vibration isolation via spring elements 6 is supported against the environment. In the end area of the test wave 2 , which is opposite to the end portion of the test shaft 2 which the impeller 3 carries, is arranged, acts on the test shaft 2 an actuator 7 which is a dynamic stress 8th generated on the test shaft 2 acts.

2 shows a test wave 2 in design as a walking set shaft 9 , The walk set shaft 9 is a moving set shaft, as it is actually used for a moving set in a rail vehicle, possibly with the materials and dimensions actually used. Preferably, a higher-strength steel or a high-strength steel, in particular according to the materials mentioned in the introduction, for the Laufsatzwelle 9 Commitment. The walk set shaft 9 has a middle section 10 with constant cross-sectional geometry. With an extension of the outer diameter goes the middle section 10 , for example via an undercut 11 , over into first axial sections 12 . 13 , The first axial sections 12 . 13 have a cylindrical surface. From the first axial sections 12 . 13 the diameter decreases in the direction of the end portions of the test shaft 2 , in particular via an undercut 14 , for example, back to the diameter of the middle section 10 in a section 15 , From this section 15 the test wave goes 2 about a jump 16 over into second axial sections 17 . 18 , with which the end portions of the test shaft 2 are formed and which have a cylindrical outer surface. It is understood that instead of a scroll set shaft 9 With the illustrated geometry, any other typesetting set can be used, as they can be used in the operation of moving sets in rail vehicles.

For a first embodiment, the movement set shaft 9 Use in a moving set, in which the storage of the moving set shaft 9 done inboard of the wheels. For such a configuration, the second axial sections carry 17 . 19 the wheels, while the first axial sections 12 . 13 for supporting the bearings between the spreader shaft 9 and vehicle construction serve.

For a second embodiment, the movement set shaft 9 Use for a running set, in which the storage of the movement set shaft 9 takes place opposite the vehicle body outside of the wheels. In this case, the first axial sections serve 12 . 13 the connection of the spreader shaft 9 with the wheels, while the second axial sections 17 . 18 the support of the bearings between sets of spouts 9 and vehicle construction serve.

3 shows a test wave 2 in design as a test shaft 19 , Also the test wave 19 has first axial sections 12 . 13 and second axial sections 17 . 18 which have sections 10 . 15 are separated from each other. Here are the sections 15 between the axial sections 17 . 12 respectively. 13 . 18 designed longer than for the Laufsatzwelle 9 according to 2 and the transition between the axial sections 17 . 12 respectively. 13 . 18 is formed on both sides by means of undercuts. The first axial sections 12 . 13 connecting middle section 10 is through a central axial section 20 divided into two parts 10-1 and 10-2 , The central axial section 20 has a cylindrical surface and goes over an undercut into the parts 10-1 and 10-2 of the middle section 10 , At the middle axial section 20 is when using the test shaft 19 as a test wave 2 in the railway wave test stand according to the invention 1 an impeller attached. The test waves 2 are each rotationally symmetrical to their longitudinal axis 21 educated.

4 shows a mechanical equivalent model of a railway shaft test bench according to the invention 1 , The railway wave test bench 1 can both with a test wave 2 in an embodiment as Laufsatzwelle 9 as well as with a test wave 2 in design as a test shaft 19 be used. In the first axial sections 12 . 13 is the test wave 2 over the area over camp 22 . 23 in first camp stands 24 . 25 supported at least in the radial direction, so that the bearings 22 . 23 can be designed as a floating bearing. But it is also possible that at least one of the bearings 22 . 23 a support of the test shaft 2 in the direction of its longitudinal axis 21 guaranteed.

• – einen Dreh-Freiheitsgrad der Prüfwelle 2 um ihre Längsachse zwecks Simulation einer Rotation der Prüfwelle 2 in dem Eisenbahnwellen-Prüfstand;
• – einen Dreh-Freiheitsgrad um eine Schwenkachse, welche vertikal zur Zeichenebene gemäß 4 orientiert ist, um eine Durchbiegung der Prüfwelle 2 ohne Behinderung der Durchbiegung durch die Abstützung der Prüfwelle 2 zu gewährleisten.

In the area of the second axial sections 17 . 18 support themselves over bearings 26 . 27 second bearing blocks 28 . 29 at the test shaft 2 from. About the second bearing blocks 28 . 29 In each case, a transverse force is introduced into the test shaft. It is possible that here are the bearings 26 . 27 are designed as a fixed bearing. To ensure that only a lateral force in the test shaft 2 is initiated without Axialkraftkomponente, are the bearings 26 . 27 designed as a floating bearing, as in 4 is shown schematically. The second bearing blocks 28 . 29 are rigid with joints 30 . 31 coupled to each one transverse to the longitudinal axis 21 the test wave 2 oriented pendulum support 32 . 33 is coupled while ensuring a rotational degree of freedom through the joints 30 . 31 around an axis, which is vertical to the plane according to 4 is oriented. The pendulum supports 32 . 33 have a structurally given elasticity, which by the mechanical rigidity of the pendulum supports 32 . 33 can be ensured or through in the pendulum supports 32 . 33 integrated spring elements 34 . 35 , In that the bearing blocks 28 . 29 opposite end areas have the pendulum supports 32 . 33 over joints 36 . 37 , to which, while ensuring a rotational degree of freedom about an axis, which is vertical to the plane according to 4 oriented, one actuator each 38 . 39 is coupled. By means of the actuators 38 . 39 each will be test personnel 40 . 41 generated by the joints 36 . 37 , the pendulum supports 32 . 33 with the spring elements 34 . 35 , the joints 30 . 31 , the second bearing blocks 28 . 29 and the camps 26 . 27 for generating a lateral force on the test shaft 2 act. Camps 26 . 27 or second bearing blocks 28 . 29 as well as the bearings 22 . 23 or first bearing blocks 24 . 25 ensure the following degrees of freedom:

• A rotation degree of freedom of the test shaft 2 about its longitudinal axis for the purpose of simulating a rotation of the test wave 2 in the railway shaft test bench;
• A rotational degree of freedom about a pivot axis which is vertical to the plane of the drawing 4 is oriented to a deflection of the test wave 2 without obstruction of the deflection due to the support of the test shaft 2 to ensure.

By supplementary constructive measures it is ensured that, as independent as possible of a possible deflection of the test wave 2 , the distance of the bearing block 28 from the bearing block 24 as well as the distance of the bearing block 29 from the bearing block 25 fixed or predetermined within predetermined limits. For the embodiments shown here, this is done in each case by using pendulum supports 42 . 43 parallel to the longitudinal axis 21 the test wave 2 are oriented. The pendulum supports 42 . 43 are in one end area over a joint 44 . 45 with a rotational degree of freedom about an axis that is vertical to the plane of the drawing 4 is oriented to the assigned first bearing blocks 24 . 25 coupled. In the other end area are the pendulum supports 42 . 43 over joints 46 . 47 , which ensure a corresponding rotational degree of freedom, on the second bearing blocks 28 . 29 coupled.

The result of a deflection of the test shaft 2 when loaded with test loads 40 . 41 resulting movements are exemplified for in 4 for the right part of the test wave 2 the corresponding applies. At deflection of the test shaft 2 as a result of exposure to the test personnel 40 . 41 this first rises to the test wave 2 acting bending moment between the axial sections 17 . 12 linear, while this between the first axial sections 12 . 13 (as far as possible) is constant. This results in a deflection of the test shaft 2 , As a result of the selected bearings has the bending line in the first axial section 12 . 13 a zero crossing - due to the explained rotational degree of freedom of the bearings 22 . 23 or bearing blocks 24 . 25 vertically to the drawing plane according to 4 But here the bending line goes through the bearings with a certain inclination. By contrast, results in the region of the second axial sections 17 a deflection of the test shaft 2 downward. Furthermore, results in the region of the second axial sections 17 . 18 a relation to the aforementioned inclination increased inclination of the bending line of the test shaft 2 passing through the chosen camp 26 . 27 or bearing blocks 28 . 29 is possible. With the aforementioned deflection of the second axial sections 17 . 18 moves, caused by the actuator 38 , the bearing buck 28 with joint 30 , Pendulum support 32 and spring element 34 downward. Due to the coupling of the pendulum support 42 to the bearing block 28 this can only move along a circular path, the center of which is the joint 44 forms. For sufficiently large dimensions of the pendulum support 42 in comparison to the deflection in the region of the second axial section 17 ensures the pendulum support 42 a movement of the bearing block 28 transverse to the longitudinal axis 21 the test wave 2 and an exact transmission of the test load 40 as a lateral force to the test shaft 2 with vanishing axial force component. About a clutch 48 and in particular a torsionally soft torsion bar 49 becomes the test wave 2 from a drive unit 50 driven.

In 5 is spatially a structural design of a railway shaft test bench according to the invention 1 shown. It can be seen that the bearing blocks 24 . 25 such as 28 . 29 each with a bearing housing 51 are formed, on which radially inside a rolling bearing is supported. So that the free deflection of the test shaft 2 is ensured, the bearing housings 51 each on both sides via pivot bearings 52 with aligned pivot axes that are vertical to the corresponding plane according to 4 are oriented, supported. This support is made for the first bearing blocks via vertical cheeks 53a . 53b who are rigid on a foundation 54 are supported and for the second bearing blocks 28 . 29 at the pendulum supports 32a . 32b . 331 . 33b , In 5 it can be seen that a support and guidance of the bearing housing 51 each on both sides of the test shaft 2 takes place, for example, two pendulum supports 42a . 42b respectively. 43a . 43b as well as two pendulum supports 32a . 32b such as 33a . 33b each in pairs.

For the in 5 illustrated embodiment is the test shaft 2 a test wave 19 , whose central axial section 20 an impeller 55 wearing. Since usually a failure of a movement set shaft 9 closely adjacent the interference fit between the impeller 55 and the walk set shaft 9 can be done by properly sizing the parts of the middle section 10-1 and 10-2 the test wave 19 a free space can be created, for example, an optical monitoring of crack development and crack propagation even when the test shaft is stressed 19 in the railway shaft test bench 1 can guarantee.

In the detail view according to 6 is first the integration of the spring element 34 , which is formed here with several coil springs, in the pendulum support 32 to recognize. In addition, the closer construction of the actuator 38 , which at the joint 36 the test load 40 generated to recognize. The actuator 38 has a drive unit 56 , In particular a servomotor, which a drive means, here a belt means 57 , in particular a belt or a chain, drives. The belt 57 in turn drives a spindle nut 58 on, which is rotatable about a vertical axis, but axially fixed. Through the spindle nut 58 through a spindle shaft extends 59 which is mounted secured against rotation, but axially displaceable in the vertical direction, which in a conventional manner, a spindle drive 60 is formed. Such generated and translated test loads 40 be over a crossbar 61 to the camp 36 transfer. In 6 is just the actuator 38a out of a total of four actuators 38a . 38b and 39a . 39b to recognize. In the pendulum supports 32 . 33 are each sensors 62 integrated, which are, for example, acceleration or load cell. About these sensors 62 can the test load 40 . 41 or in the test wave 2 introduced lateral force are detected, which then a control device for controlling or regulating the forces or speeds of the drive units 56 . 50 and / or a suitable evaluation device is supplied. Preferably, the spindle drive 60 as a ball screw drive 63 educated.

Continue in 6 to recognize is a spindle drive 64 whose spindle axis is parallel to the longitudinal axis of the test shaft 2 is oriented. Here is the spindle shaft 65 rotatable in one end, but fixed axially on the cheek 53 of the bearing block 25 stored while the spindle nut 66 on the cheek 53 of the bearing block 24 supported as shown. Will the connection of the cheeks 53 the bearing blocks 24 . 25 with the foundation 54 at least partially solved, can by pressing the spindle drive 64 the distance between the two bearing blocks 24 . 25 be adjusted sensitively. An actuation of the spindle drive 64 This can be done automatically, for example, electric motor or manually. For the illustrated embodiment are located on both sides of the test shaft 2 spindle drives 64a . 64b ,

LIST OF REFERENCE NUMBERS

1

Railway wave test

2

test shaft

3

Wheel

4

chuck

5

foundation

6

spring element

7

actuator

8th

demand

9

Run, full wave

10

middle section

11

Freeway

12

first axial section

13

first axial section

14

Freeway

15

section

16

step

17

second axial section

18

second axial section

19

experimental wave

20

middle axial section

21

longitudinal axis

22

camp

23

camp

24

first bearing block

25

first bearing block

26

camp

27

camp

28

second bearing block

29

second bearing block

30

joint

31

joint

32

Stabilizer

33

Stabilizer

34

spring element

35

spring element

36

joint

37

joint

38

actuator

39

actuator

40

test load

41

test load

42

Stabilizer

43

Stabilizer

44

joint

45

joint

46

joint

47

joint

48

clutch

49

torsion bar

50

power unit

51

bearing housing

52

pivot bearing

53

cheek

54

foundation

55

Wheel

56

power unit

57

endless

58

spindle nut

59

spindle shaft

60

spindle drive

61

crossmember

62

sensor

63

Ballscrew

64

spindle drive

65

spindle shaft

66

spindle nut

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited non-patent literature

• EN 13261 [0002]
• 13262 [0002]
• 13104 [0002]

Claims (21)

Railway shaft test bench ( 1 ) with a) a foundation ( 54 ), b) one at the foundation ( 54 ) supported drive unit ( 50 ), which with a test wave ( 2 ) is in driving connection, c) two on the foundation ( 54 ) supported first bearing blocks ( 24 . 25 ), in which the test wave ( 2 ), d) two second bearing blocks ( 28 . 29 ), da) between which the first bearing blocks ( 24 . 25 ) are arranged, db) with the interposition of an actuator ( 38 . 39 ) on the foundation ( 54 ) are supported, that in the area of the second bearing blocks ( 28 . 29 ) via the actuators ( 38 . 39 ) in each case a transverse force in the test wave ( 2 ), and dc) the one degree of freedom in the direction of action of the actuator ( 38 . 39 ), e) a control device via which the drive unit ( 50 ) and the actuators ( 38 . 39 ) are controllable such that for rotating test shaft ( 2 ) the test wave ( 2 ) is exposed to a rotating four-point bending stress. Railway shaft test bench ( 1 ) according to claim 1, characterized in that the distance between adjacent bearing blocks ( 28 . 24 ; 24 . 25 ; 25 . 29 ) is at least partially adjustable. Railway shaft test bench ( 1 ) according to claim 1 or 2, characterized in that the storage of the test wave ( 2 ) in at least three bearing blocks, in particular in all four bearing blocks ( 24 . 25 . 28 . 29 ), with rolling bearings in training as a floating bearing. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that in the bearing blocks ( 24 . 25 . 28 . 29 ) at least one non-contact seal between the test shaft ( 2 ) and a housing ( 51 ) of the bearing block ( 24 . 25 . 28 . 29 ) is arranged. Railway shaft test bench ( 1 ) according to claim 4, characterized in that a displacement sensor for direct or indirect detection of the relative position of one with the test wave ( 2 ) connected sealing element of a seal with respect to a with the housing ( 51 ) connected sealing element of the seal is present. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that in all bearing blocks ( 24 . 25 . 28 . 29 ) the housings ( 51 ) in pivot bearings ( 52 ) rotatable about an axis which transverse to the longitudinal axis ( 21 ) of the test wave ( 2 ) and transversely to the direction of action of the actuator ( 38 . 39 ), are stored. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that the second bearing blocks ( 28 . 29 ) via sensors ( 62 ) on the foundation ( 54 ) are supported. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that at least one actuator ( 38 . 39 ) with a spindle drive ( 60 ) is trained. Railway shaft test bench ( 1 ) according to claim 8, characterized in that the spindle drive ( 60 ) as a ball screw drive ( 63 ) is trained. Railway shaft test bench ( 1 ) according to claim 8 or 9, characterized in that the spindle drive ( 60 ) is driven by a servomotor. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that the flow of force from the foundation ( 54 ) to the second bearing blocks ( 28 . 29 ) via at least one spring element ( 34 . 35 ) runs. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that at least one second bearing block ( 28 . 29 ) via a pendulum support ( 32 . 33 ) on the foundation ( 54 ), wherein a) a first end portion of the pendulum support ( 32 . 33 ) with a bearing ( 30 . 52 ) rotatable on the housing ( 51 ) of the second bearing block ( 28 . 29 ) is supported with a rotational degree of freedom about an axis which is transverse to the longitudinal axis ( 21 ) of the test wave ( 2 ) and transversely to the direction of action of the actuator ( 38 . 39 ) and b) a second end region of the pendulum support with a bearing ( 36 ) rotatable on the actuator ( 38 . 39 ) or one with the actuator ( 38 . 39 ) is supported with a rotational degree of freedom about an axis transverse to the longitudinal axis ( 21 ) of the test wave ( 2 ) and transversely to the direction of action of the actuator ( 38 . 39 ) is oriented. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that a distance of a second bearing block ( 28 . 29 ) from an adjacent first bearing block ( 24 . 25 ) in a direction parallel to the longitudinal axis ( 21 ) of the test wave ( 2 ) is predetermined by a spacer, without thereby a degree of freedom of the second bearing block ( 28 . 29 ) in the direction of action of the actuator ( 38 . 39 ) is blocked. Railway shaft test bench ( 1 ) according to claim 13, characterized in that the spacer as pendulum support ( 42 ), wherein a) a first end region of the pendulum support ( 42 ) in a joint ( 46 ) rotatable on the second bearing block ( 28 . 29 ) is articulated with a rotary Degree of freedom about an axis transverse to the longitudinal axis ( 21 ) of the test wave ( 2 ) and transversely to the direction of action of the actuator ( 38 . 39 ) and b) a second end region of the pendulum support ( 42 ) in a joint ( 44 ) rotatable on the first bearing block ( 24 . 25 ) is articulated with a rotational degree of freedom about an axis which is transverse to the longitudinal axis ( 21 ) of the test wave ( 2 ) and transversely to the direction of action of the actuator ( 38 . 39 ) is oriented. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that the distance of the first bearing blocks ( 24 . 25 ) in a direction parallel to the longitudinal axis ( 21 ) of the test wave ( 2 ) via a spindle drive ( 64 ) is adjustable. Railway shaft test stand according to one of the preceding claims, characterized in that the test shaft ( 2 ) a test shaft ( 19 ) is with a) a central axial section ( 20 ), which is an impeller ( 55 b) two in the axial direction of the test shaft ( 19 ) spaced from the central axial section (FIG. 20 ) arranged first axial sections ( 12 . 13 ), in which the support of the test shaft ( 19 ) in the first bearing blocks ( 24 . 25 ), and c) two in opposite end regions of the test shaft (FIG. 19 ) arranged second axial sections ( 17 . 18 ), in the area which the impingement of the test shaft ( 19 ) over the second bearing blocks ( 28 . 29 ) he follows. Railway shaft test bench ( 1 ) according to one of claims 1 to 15, characterized in that the test wave ( 2 ) a moving set shaft ( 9 ) is with a) two first axial sections ( 12 . 13 ), in the area of which the Laufsatzwelle ( 9 ) in the moving set the wheel discs carries, but in the area of those in the railway shaft test bench ( 1 ) the support of the Laufsatzwelle ( 9 ) in the first bearing blocks ( 24 . 25 ), and b) two second axial sections ( 17 . 18 ), in the area of which the Laufsatzwelle ( 9 ) is mounted in the moving set opposite the vehicle body, but in the area of those in the railway shaft test bench ( 1 ) the application of the Laufsatzwelle ( 9 ) through the second bearing blocks ( 28 . 29 ) he follows. Railway shaft test bench ( 1 ) according to one of claims 1 to 15, characterized in that the test wave ( 2 ) a moving set shaft ( 9 ) is with a) two first axial sections ( 12 . 13 ), in the area of which the Laufsatzwelle ( 9 ) is mounted in the moving set opposite the vehicle body, but in the area of those in the railway shaft test bench ( 1 ) the support of the Laufsatzwelle ( 9 ) in the first bearing blocks ( 24 . 25 ), and b) two second axial sections ( 17 . 18 ), in the area of which the Laufsatzwelle ( 9 ) in the moving set the wheel discs carries, but in the area of those in the railway shaft test bench ( 1 ) the application of the Laufsatzwelle ( 9 ) through the second bearing blocks ( 28 . 29 ) he follows. Railway shaft test bench ( 1 ) according to one of claims 1 to 15, characterized in that distances of bearing blocks ( 24 . 25 . 28 . 29 ) are changeable such that the railway shaft test bench ( 1 ) can be used at least for two of the following embodiments: a) Railway shaft test stand according to claim 16 , b) Railway shaft test stand according to claim 17, c) railway shaft test stand according to claim 18. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that in the bearing blocks ( 24 . 25 . 28 . 29 ) arranged rolling bearings are integrated into a lubricant cooling circuit. Railway shaft test bench ( 1 ) according to one of the preceding claims, characterized in that at least one temperature sensor is provided for monitoring a temperature of the test shaft, a seal, a bearing, an oil cooling circuit and / or a bearing block.

Images