DE102015213618A1 - Test bench for rolling bearings - Google Patents

Abstract

Disclosed is a test stand (1) for a rolling bearing (2), in particular for a tapered roller bearing, with a first flange (10) and a second flange (12) between which the rolling bearing 2 is clamped, wherein the first flange (10) and the second flange (12) by means of a fastening means (14) are fixable to each other in its axial position, wherein at least on the first flange (10) in the direction of the second flange (12) axially displaceable piston (32) is arranged, with one the piston axially displaceable predetermined force can be acted upon, with which the force required for the examination of the rolling bearing can be applied to the rolling bearing, and a method for testing a rolling bearing (2) on such a test bed (1).

Description

The present invention relates to a test stand for a rolling bearing, in particular for a tapered roller bearing, according to the preamble of patent claim 1, and a method for testing a rolling bearing on such a test bed.

In order to check whether rolling bearings, in particular the rolling elements, meet the required loads, the rolling bearings are usually checked in a test bench for their capacity out. Since rolling bearings are often installed at critical points, it must be checked regularly whether the rolling bearings meet the required conditions. In particular, the rolling elements are of particular interest, since these are the weakest components in terms of pressure loading. The reason for this is that the rolling elements only ever along one line (conical, cylindrical rolling elements) or at one point (balls) must absorb the entire pressure acting on the bearing, which makes very great demands on the pressure load resistance of the rolling elements.

In order to check whether a rolling bearing has sufficient load values, the rolling bearings are usually clamped in a test stand, rotated and then so long with pressure, for example via an axial force, applied until a damage to the rolling bearing, in particular to the rolling elements to observe is. If the force required for the damage is above a threshold value which corresponds to the required loads, the rolling bearing has passed its test.

For this purpose, test stands are known from the prior art, which have a first and a second flange, between which the rolling bearing is clamped. The two flanges themselves can, in order to apply an axial force to the bearing, be delivered axially, for which fastening means, usually a bolt-nut system, is provided. In this case, usually a variety distributed over the circumference bolt and nut combinations are used to apply the appropriate forces can. In addition, in order to apply uniform forces as possible and not to tilt the flanges against each other, in each case the opposite screw-nut combinations are tightened, which is time-consuming and error prone to others.

In addition, it is disadvantageous that the rolling bearing can not be rotated continuously during the application of force, but the bearing braked for each additional Zustellprozess and the rotation must be restarted. However, this also means at the same time that when the forces applied via the flange system, the starting operation, especially at very high axial forces, requires a very high torque, so that a strong drive system for the bearing is needed. This is again very expensive.

Another disadvantage of the known test stands is that, although with a great deal of work, although on the bolt system very high forces can be applied to the bearings, a size of the forces is limited, however, is limited, since the colliding thread of the bolt nut -System itself bring a high friction with it, which is difficult to determine.

Object of the present invention is therefore to provide a test stand for a rolling bearing, which is easier to use and with a clearly measurable force can be applied to the rolling bearing to be tested.

This object is achieved by a test stand according to claim 1, and a method for testing a rolling bearing according to claim 9.

According to the invention, a test stand for a roller bearing, in particular for a tapered roller bearing is proposed which has a first flange and a second flange. Between the first flange and the second flange, the rolling bearing to be tested can be clamped. Furthermore, a fastening means is provided, by means of which the first flange and the second flange are fixable to one another in their axial position. This serves in particular for the attachment of the rolling bearing to be tested. In this case, the fastening means, as known from the prior art, in particular in a bolt-nut system, which is distributed circumferentially around the rolling bearing or the test stand. Alternatively, several hydraulic cylinders distributed over the circumference can be used as fastening means.

In contrast to the prior art, however, the fastening means no longer serve to apply the necessary force for testing the stability of the rolling bearing on the rolling bearing. For this purpose, it is provided according to the invention to arrange at least one piston, which is axially displaceable in the direction of the second flange, on the first flange. This piston in turn is designed to apply the force required for the stability test of the rolling bearing on the rolling bearing. In this case, it is particularly preferred to arrange the piston in the test stand such that the force required for the test can be applied to the rotating bearing ring.

Of course, it would also be possible to provide such a piston on the second flange, but since Actio equal Reactio applies, can be dispensed with such a piston on the second flange.

According to a further advantageous embodiment, at least one recess is provided on the first flange, which is designed to receive the at least one piston. In this case, the at least one recess may be formed as a groove or as a continuous opening. The shape of the recess is preferably adapted to the shape of the piston.

Thus, as an advantageous embodiment shows, the piston can be designed as a piston which can be acted upon by a fluid. It is particularly preferred to form the recess as a groove or blind bore in which the piston is received. In this embodiment, a pressure chamber is preferably formed between a recess bottom and the piston, which is designed to pressurize the piston with a pressure applied by a pressurized fluid. In this case, the pressure chamber may be formed directly from the recess, the piston and the piston in the recess sealingly leading sealing elements, but it is also possible to receive the pressurized fluid, for example, in a bellows or hose-like element which is arranged between Aussparungsgrund and piston.

Particularly advantageous is a piston designed as an annular piston, which is arranged in an annular groove. Since the annular piston applies a uniform force over the circumference of the clamped bearing, this can be applied equally force at all points. Alternatively, it would also be possible to form only one pressure side of the piston annular.

Of course, it is also possible to use several discrete pistons distributed over the circumference. These may also be operable with a pressurized fluid as described above, but it is also possible to perform them in continuous recesses through the flange and to actuate from outside the flange. In this case, the pistons can also be designed as a multiplicity of delivery pistons that can be actuated or connected to a central working piston. The working piston can be formed mechanically or hydraulically / pneumatically.

According to a further advantageous embodiment, the piston is axially displaceable with a predetermined force, wherein the predetermined force is provided, for example, via the adjustable pressure of the pressure fluid. Since the pressure of the pressure fluid acts directly on the piston and thus directly on the rolling bearing, the force which acts on the piston and thus on the rolling bearing can be determined via the easily determined magnitude of the pressure of the pressure fluid. An influence of friction, as in the prior art by the threads of the nut and bolt need not be considered. A friction applied by the seals is negligible. If, in addition, a bellows or tubular element is used as the pressure chamber, it is even possible to dispense with the seals rubbing in the recess. In addition, the use of pressurized fluids as pressurizing medium has the advantage that thus a constant and continuous application of force is possible. At the same time very large forces can be applied via pressure fluids. As a result, a test stand can be provided, in which the force actually acting on the rolling bearing can be clearly determined. This makes the measurements and the load values clearly definable.

• – Anordnen des Wälzlagers zwischen dem ersten Flansch und dem zweiten Flansch;
• – Befestigen des Wälzlagers in dem Prüfstand durch Zustellen der Flansche zueinander und Fixieren der beiden Flansche in ihrer Position mittels des Befestigungsmittels;
• – Drehen der Lagerringe relativ zueinander und damit Drehen des mindestens einen Wälzkörpers;
• – Aufbringen einer definierten Kraft auf zumindest einen Lagerring mittels des axial verstellbaren Kolbens.

A further aspect of the present invention relates to a method for testing a rolling bearing having an inner ring and an outer ring, between which at least one rolling element is arranged, on a test stand described above, the method having at least the following steps:

• - Arranging the rolling bearing between the first flange and the second flange;
• - Fixing of the rolling bearing in the test bed by advancing the flanges to each other and fixing the two flanges in position by means of the fastening means;
• - Rotate the bearing rings relative to each other and thus rotating the at least one rolling element;
• - Applying a defined force on at least one bearing ring by means of the axially adjustable piston.

In the test stand or the method according to the invention, it is particularly advantageous that a change in the size of the applied force during rotation of the bearing rings can take place. A stopping and re-tightening the bearing rings can thus be omitted.

According to a further advantageous embodiment, the force applied to the bearing ring is continuously increased. As a result, it is not only possible to determine stepwise, but exactly, in which force application damage to the bearing occurs.

Furthermore, it is advantageous if the force can be preset via a pressure fluid pressure. Since in particular pressure fluids can form very high forces, wherein the forces are also infinitely variable, it can be a particularly accurate test done.

Further advantages and advantageous embodiments are specified in the claims, the description and the drawings.

In the following, the invention will be explained in more detail with reference to an embodiment shown in the figure. In this case, the embodiment is purely exemplary in nature and should not determine the scope of the application. This is defined solely by the appended claims.

It shows:

1 a schematic sectional view through and a plan view of a test stand according to the invention.

1a shows a sectional view through a test stand 1 with arranged therein to be tested bearings 2 , The rolling bearing to be tested 2 is designed as a double row tapered roller bearing and includes two inner rings 20 . 22 and an outer ring 24 , between which rolling elements 26 . 28 are arranged. Because the rolling elements 26 . 28 the bearing rings 20 . 22 . 24 always contact only along a line L, along the line L, the force is particularly high. The inner rings 20 . 22 themselves are arranged at a distance from each other.

Furthermore is 1a to see that the test bench 1 even a first flange 10 and a second flange 12 that has the rolling bearing 2 between them. This is still a fastener 14 provided, in the illustrated embodiment, a threaded rod 16 and a mother screwed on her 18 includes. Like the supervision 1b can be seen, are the fasteners 14 around the flange 12 arranged. As known from the prior art, the conventional flanges can be used with their variety of bolt-nut combinations. Unlike in the prior art, however, serve the fasteners 14 not to put a force on the rolling bearing 2 exercise, but only to the two flanges 10 . 12 to be arranged axially relative to one another such that the rolling bearing 2 between the flanges 10 . 12 is fixed and the axial position of the flanges 10 . 12 does not change during the experiment. So that the flanges 10 . 12 not bending, is still a support 15 provided at the same time the voltage curve in the flanges 10 . 12 , improved and thus allows an application of particularly high forces.

Now to the axial force that is required for the test, on the rolling bearing 2 is still the first flange 10 with a recess 30 provided in an annular piston 32 is arranged, which is adapted to apply the rotating bearing ring with the force required for the test. In the in 1 illustrated embodiment, the annular piston contacted 32 doing so on its recess 30 opposite pressure side 34 the inner ring rotating during the test 20 of the rolling bearing 2 , The ring piston 32 is in the in 1 illustrated embodiment acted upon by a pressurized fluid, the pressure chamber 36 that between a recess floor 38 and the piston 32 is formed, can be fed. This also causes the piston 32 with one towards the second flange 12 and thus in the direction of rolling bearings 2 acting axial force acted upon. Because the two flanges 10 . 12 to each other via the fastener 14 axially fixed in position, the piston can 32 only in the direction of rolling bearings 2 move and bring over its print page 34 an axial force on the inner ring 20 on (see arrow 40 ). This in turn directs the axial force on the rolling elements 26 , over the outer bearing ring 24 , on the rolling elements 28 , and from there to the inner ring 22 (see also force line 42 ). It will be the piston 32 applied force transmitted directly to the rolling bearing and in particular to the rolling elements, whereby a stability test of the rolling bearing is feasible.

Since a pressurized fluid is used as a pressure-giving medium, on the one hand a continuous increase in force is possible, which on the other hand can also be measured directly or determined. Although in the prior art, the force that was necessary for further delivery of the nuts, could also be measured. However, since part of this force was lost due to the friction of the nut-bolt threads, it was not possible to determine exactly how much force actually acted on the bearing. In the test bench according to the invention 1 In contrast, the force is essentially lossless on the rolling bearing 2 transferred and is thus clearly determinable. As at the exam, in which 1 illustrated embodiment, in addition to the inner ring 20 also the ring piston 32 and the flanges 10 . 12 can rotate, one of sealing elements 44 caused friction in the recess 30 neglected. To even the low friction on the seals 44 To eliminate, can also be provided between Aussparungsboden 38 and pistons 32 to provide a bellows or hose-like element which is elastic, receives the pressurized fluid and is designed as a pressure chamber. The piston 32 can then be essentially frictionless in the recess 30 be stored. The pressure room 36 itself can be pressurized via one or more Druckfluidzuführstellen (not shown) with pressurized fluid.

The piston 32 can be designed as an annular piston, as shown, in an annular groove 30 However, it is also possible that several discretely distributed over the circumference of the piston 32 are provided.

At the same time is also possible, the piston 32 pressurized by a central working piston, inside or outside the flange 10 can be arranged. For example, a pressure on the rolling bearing 2 However, it is also possible to discretely form the pistons, the pressure side acting on the rolling bearing 34 of the piston 32 However, ring-shaped design.

Of course, it will be apparent to one skilled in the art that an embodiment of the invention is also included in the flange 10 continuous recesses are provided by the piston 32 to the bearing rings 20 of the rolling element 2 be guided, the pistons 32 can be actuated by a working piston arranged outside.

Furthermore, it is advantageous that with the test stand according to the invention, the applied force during the rotation of the bearing rings 20 . 22 . 24 relative to each other is changeable. Braking, re-adjusting and turning again is not necessary in the embodiment according to the invention. As a result, the drive device may be made weaker, since the initial torque must be overcome only with a small application of force.

Overall, a rolling bearing can be easily examined for stability with the test stand according to the invention. It is particularly advantageous that on the one hand a continuous and detectable force on the bearing is possible, and on the other hand, the introduction of force is variable even during a rotation of the bearing. As a result, a test of the stability values of the bearing can be carried out under real conditions.

LIST OF REFERENCE NUMBERS

1

 test bench

2

 roller bearing

20, 22

inner ring

24

outer ring

26, 28

rolling elements

L

 line load

10

first flange

12

second flange

14

fastener

15

support

16

threaded rod

18

mother

30

recess

32

piston

34

Pressure surface of the piston

36

pressure chamber

38

pocket bottom

40

Kraftbeaufschlagungsrichtung

42

power line

44

poetry

Claims (12)

Test bench ( 1 ) for a rolling bearing ( 2 ), in particular for a tapered roller bearing, with a first flange ( 10 ) and a second flange ( 12 ), between which the rolling bearing ( 2 ) is clamped, wherein the first flange ( 10 ) and the second flange ( 12 ) by means of a fastening means ( 14 ) are fixable to each other in their axial position; characterized in that at least at the first flange ( 10 ) in the direction of the second flange ( 12 ) axially displaceable piston ( 32 ) is arranged, which is acted upon by a piston axially displaceable predetermined force with which the force required for the examination of the rolling bearing can be applied to the rolling bearing. Test bench ( 1 ) according to claim 1, wherein the piston ( 32 ) with a piston ( 32 ) axially displaceable predetermined force can be acted upon, wherein preferably the applied force is exerted by a pressurized fluid. Test bench ( 1 ) according to one of claims 1 or 2, wherein the for the examination of the rolling bearing ( 2 ) required force can be applied to a rotating bearing ring. Test bench ( 1 ) according to any one of the preceding claims, wherein the piston ( 32 ) in at least one of the first flanges ( 10 ) formed recess ( 30 ) is arranged, wherein preferably at least one recess is formed as a groove or blind bore and / or as a continuous opening. Test bench ( 1 ) according to one of the preceding claims, wherein the at least one piston ( 32 ) is axially displaceable by means of a pressurized fluid, and the recess ( 30 ) is formed as a groove or blind bore, wherein between recess ( 30 ) and pistons ( 32 ) a pressure space is formed, which with a pressurized fluid for actuating the piston ( 32 ) can be acted upon. Test bench ( 1 ) according to one of the preceding claims, wherein at least one piston ( 32 ) is actuated via a working piston. Test bench ( 1 ) according to any one of the preceding claims, wherein the piston ( 32 ) is designed as an annular piston or an annular pressure surface ( 34 ) having.. Test bench ( 1 ) according to one of claims 1 to 6, wherein a plurality of pistons ( 32 ) are distributed discretely distributed over the circumference. Test bench ( 1 ) according to claim 8, wherein in the flange ( 10 ) continuous recesses ( 30 ) are provided, which are adapted to the plurality of pistons ( 32 ). Method for testing a roller bearing ( 1 ) with at least one between two rotatable relative to each other formed bearing rings ( 20 ; 22 ; 24 ) on a test bench ( 1 ) according to one of the preceding claims, characterized in that the method comprises at least the following steps: - arranging the rolling bearing ( 2 ) between the first flange ( 10 ) and the second flange ( 12 ); - fixing the rolling bearing ( 2 ) by advancing the first flange ( 10 ) and fixing the two flanges ( 10 ; 12 ) in position by the fastener ( 14 ); - turning the bearing rings ( 20 ; 22 ; 24 ) and the at least one rolling element ( 26 ; 28 ) relative to each other; - Applying a defined force on at least one bearing ring ( 20 ; 22 ; 24 ) by means of the axially adjustable piston ( 32 ). The method of claim 10, wherein the on the bearing ring ( 20 ; 22 ; 24 ) applied force is continuously increased. The method of claim 10 or 11, wherein the of the piston ( 32 ) applied force via a pressure fluid pressure is predetermined adjustable.

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