SU1312430A1 - Installation for testing the bearings - Google Patents

Abstract

This invention relates to a testing technique. The purpose of the invention is to approximate the test conditions of the sliding bearings to the operational ones by creating normalized axial and radial loads on the tested bearing and a certain stress state thereof. The installation comprises a housing 1, supports 2 and 3 for a drive shaft 4, a holder 5 for accommodating sleeve 7 with a test bearing 6 therein. Radial; The load on the bearing 6 is set by the mechanism 8 and controlled by a dynamometer 9. The rotational speed of the bearing 6 is controlled by the sensor 10, - and the drive shaft 4 - by the sensor 11, the electromagnetic friction half coupling 12 is fixed on the shaft 4 by screw 14, and the half coupling 13 moves along the shaft 4 relative to the guide 15 and provides the necessary, pressing the bearing 6 to the coupling half 12 by means of electromagnets 16 and 17, the current collector 18, the rheostat 19 and the current source 20. When the shaft 4 rotates due to the selection of forces and the inner diameter of the sleeve 1, it is possible to ensure the possibility of testing the bearing 6 in the modes of pure rolling, sliding with sliding and pure sliding, 1 hp f-ly, 2 ill. C & L "TYUZ. x 12 D 11 Fi.

Description

The invention relates to a solid technique and can be used for testing sliding bearings,

The purpose of the invention is to approximate the condition of the test of the Ir-slip slip to the operational,

FIG. 1 shows a schematic diagram of bearings for bearing testing: FIG. 2 is a section of FIG.

The installation contains a drive shaft 4, supported on supports 2 and 3, a holder 5, placed between the holder 5 and the test subtype NIKOM 6, a replaceable sleeve 7 with a diameter that provides a certain bearing condition of the bearing dynamometer 9 for radial loading of the sensor 10 speed of rotation bearing: - n: a 6, sensor 11 of the speed of rotation of the drive room 4, friction coupling half 12 and 13, zgptt; 14 fastening the coupling half 12 to E-alu 4., the guide 15 for the axial bearing; neither the coupling half 13, electromagnets 16 and 17, the current collector 18, - the rheostat 19 and the current source 20.

Installation works cJ IedyiOi i i way.

In the initial state, isytuem bearing 6 is placed; in the sleeve 7 with an internal diameter, the circumference of which is a stress state a trifricyopa-under-layer, corresponding to the operating conditions Install the bearing 6 with 7 on the drive shaft 4 gz cage 5. When tested, a current is supplied to -tromugs 16 and 17 and compress the bearing 6 axed; force of the coupling half 12 and 13, using the mechanism 8 load podshpgp .; 6 radial force and set the rotation of the drive shaft 4 "

Due to the friction half couplings 12 and 13 with under: 11, chg N} PhnO--: 6; and t is also due to the friction in the contacts of the shaft 4 with the bearing 6 and the bearing 6 with the sleeve 7, podiipn-n 6 makes a complex move- rolling over the shaft 4 with relative slip around it, acting as a force on the bearing & in kachemi mode with slippage is shown in FIG. 2,

The cjieriyio force is applied to the bearing 6: load R., equalizer shaft reaction; mutually balanced two axial forces Oh press to the ends of the friction nolufuf 12 and 13 ..ie

shown); ci-ina friction F.p, with shaft 4, r ip-1-shozhenna on the shoulder equal to the inner diameter,;. bearing R, rolling friction force F of bearing 6 on replaceable sleeve 7,. irr false on the ple

-ij 5. „,., ... ,,. | .r, p ends of the friction half couplings 12 and 13, applied on the average radius of the bearing 6.

"" "-: -5 Friction forces .p to G r are moving and for bearing 6, TR is la resistance. Under the action of these three forces, the bearing 6 is located in a diag- ragical diversity, i.e. is constant with a constant angular velocity of 1 3, |

together with the key; - 4 (rolls over uajiy 4) HC - / g: yu13o -1 oO speed, j slips relative to the shaft 4o On —-.- (l) -Iu.i, j- SO, where f.) - angular velocity of rotation of shaft 4,

The sum of the moments k.: Ex sn relative to the axis of rotation of the bearing 6 is n-uppo.

 F, p, R, O

or

five

- friction friction coefficient in the shaft; shaft 4 - bearing -5:

f is the coefficient of friction slip at the contact ends of the fricciology 1.; olumuf 5 2 and 13 - the end face: 1;

K - coefficient of rolling in contact LOGEPNIK 6 sleeve 7,

In the presence of Ti, a grease housing 1, the level of which allows Macjjy to come in contact with, -1, G1Ipnik 6 with v.7.4 45 friction mode of the explosive 4 and bearing 6 hydrodynamic-D or half-hollow, fusion, for 3TMis friction. - 0.001-0 / 005,

For steel -: oh fundamentals of the bearing 5 and cast-iron with; a sleeve / coefficient of friction of rolling; 0.12,

The slip coefficient f, in contact with the frontal coupling of the frkki.ionnyh half couplings 12 and 13 (J tori.and subpattern 6 depends on the material of the working surfaces {semi-semi-shells -2 y 13, So,

3 .. 1 steel ends of the coupling halves 1-2 and 13 and the steel base of the bearing 6, the coefficient of friction is in the range of f 0.14-0.18. Thus, taking the average values of the coefficients of friction for the bearing 6, having R 2.5 cm

b

and R 4 cm, we get the required ordered

the force of pressure to press Q friction coupling halves 12 and 13 to the ends of the test bearing 6, adjustable by a rheostat 19.

0.0025-P 2.5 + 0.16Q-3, 25 - - 0.12 - | ABOUT

After simplification, we get Q 0.218 P

The angular velocity of the cJ bearing 6 on the shaft 4 and the angular velocity 0.1, the rotation of the shaft 4 is recorded by the sensors 10 and 11.

An increase in the friction force F causes an increase in the rolling speed i) and a decrease in the velocity of the friction | end of the friction half couplings 12 and 13 and, therefore, the test mode

When placed in the holder 5, the sleeves 7 with an inner diameter that provide a tight fit over the outer diameter of the bearing 6, and at F 0 receive a clean slip mode.

In the case of rigid coupling of the friction half hugs 12 and 13 with the test bearing 6 slip

04

bearing 6 relative to the shaft 4 will not, which corresponds to the mode of pure rolling.

In addition, by changing the internal diameter of the sleeve 7 by replacing it, they provide a bearing of the fifth, the fifth state of the stress state of the antifriction layer, most of all corresponding to the opposite state of the real design of the slide bearing.

Claims (2)

1. Installation for testing bearings, comprising a housing, a drive shaft mounted on supports on it to accommodate a test bearing on it, a housing for placing there is a bearing in it, a cage radial loading mechanism, a rotational speed sensor of the drive shaft mounted on supports, and a rotational speed sensor of the test bearing, fixed in the cage, characterized in that. that, in order to approximate the test conditions of the sliding bearings to the operational one, it is equipped with two friction coupling halves located on the shaft with both sides of the holder, one of which is rigidly fixed on the shaft, and the other is mounted on it with the possibility of axial movement, and a sleeve placed between the holder and the test bearing. 2. Installation under item 1, characterized in that the coupling halves are made electromagnetic. Editor A, Sabo Compiled by E. Kharitonov Tehred L. Oliynyk Proofreader C, Cherni Order 1964/40 Circulation 777 Subscription BHWilTH USSR State Committee for inventions and discoveries 113035, Moscow, Zh-35, Raushsk nab., 4/5 Production and printing company, Uzhgorod, Projecto st., 4 FIG. 2