The oil pressure distribution modifications due to the effect of unaligned shaft.
The Reynolds equation was analytically solved and pressure distribution is presented as a function of principal parameters for the case of unaligned journal bearings.
A study of the local minimum dimensionless film thickness expression is made. (Baskharone et al., 1991)
In the end of the article, some drawings, representative for the pressure distribution modifications, due to the effect of unaligned shaft, in stationary case, are presented. (Kanemory & Iwatsubo, 1992)
B--width of bearing;
[bar.B]--dimensionless width of bearing, B/D;
d--diameter of journal;
D--diameter of bearing;
e--journal lateral eccentricity;
h--dimensionless film thickness, 2h/J;
[[bar.h]sub.m] ([bar.z])--function of the minimum dimensionless film thickness;
[([[bar.h].sub.m]).sub.aligned]--minimum dimensionless film thickness for aligned case;
[([[bar.h].sub.m]).sub.max]--maximum value of function [bar.h]sub.m] ([bar.z]);
[([[bar.h].sub.m]).sub.min]--minimum value of function [bar.h]sub.m] ([bar.z]);
J--diametral clearance, D-d;
[bar.p]--dimensionless pressure, p x [PSI].sup.2]/(3[pi] x n[eta]);
x, y, z- cartesian co-ordinates (fixed xOyz--frame);
[x.sub.b], [y.sub.b]-co-ordinates of point [M.sub.b] on the bearing contour;
[x.sub.s], [y.sub.s]-co-ordinates of point [M.sub.s] on the shaft contour;
[bar.z]--dimensionless axial co-ordinate, 2z/B;
[??]--dimensionless axial co-ordinate corresponding to [([[bar.h].sub.m]).sub.max]
X,Y,Z- cartesian co-ordinates (rotatedXOYZ-frame);
[alpha], [beta]--angular displacements;
[??], [??]--angular velocities;
[[??].sup.*], [[??].sup.*]-dimensionless angular velocities, ([??], [??]/([pi], n);
[epsilon]--eccentricity ratio, 2e/J;
[PSI]--dimensionless clearance, J/D;
[theta]--angular co-ordinate. (Someya, 1989)
3. THE PRESSURE DISTRIBUTION LAW
Using a new mathematical model of a short length bearing where the shaft has a conical motion, the oil film thickness was calculated: (Suciu & Parausanu, 1996)
[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (1)
h [congruent to] J/2 + e cos [theta]-z [alpha] cos [theta] + z[beta] sin [theta] (2)
or in dimensionless form:
[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (3)
where: [bar.z] = 2 x z/B; [bar.B] = B/D and [PSI] = J/D . For each fixed [bar.z], the local minimum dimensionless film thickness expression is:
[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (4)
Considering the relation of [[bar.h].sub.m]([bar.z]), it is obvious that at the central plane the same minimum film thickness is obtained as in the aligned journal bearing case:
[[bar.h].sub.m]([bar.z] = 0)= 1 - [epsilon] = [([[bar.h].sub.m]).sub.aligned] (5)
Additionally, it can be demonstrated that in the point
[??] = [alpha] x [epsilon] x [PSI]/[bar.B] x ([[alpha].sup.2] + [[beta].sup.2]) (6)
the functions have a maximum value higher than the aligned journal bearing minimum thickness:
[([[bar.h].sub.m]).sub.max] = 1 - [epsilon] x [beta]/[square root of [[alpha].sup.2] + [[beta].sup.2] [greater than or equal to] 1 - [epsilon] (7)
Finally, the minimum value of the function [[bar.h].sub.m]([bar.z]) is reached at the left bearing end, namely:
[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (8)
this is lower than the minimum film thickness of the aligned case. (San Andres, 1993)
When the Reynolds equation is integrated twice along the axial co-ordinate z under boundary conditions, the pressure distribution has the form:
[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (9)
where [MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII]. In dimensionless form the pressure distribution is given by equation (10).
[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (10)
4. NUMERICAL RESULTS
In Figure 1 four sketches of dimensionless pressure (p/[p.sub.m]) versus angular co-ordinate ([theta] [member of] [0;2[pi]]) and axial co-ordinate (z [member of] [- B/2;B/2]), are considered, the main parameters having values presented in Table 1.
These drawings are representative for the pressure distribution modifications due to the effect of unaligned shaft, in stationary case (when there are important angular displacements [alpha] and [beta]).
Thus, Figure 1a is a plot of the reference case, namely the aligned narrow journal bearing case. Pressure distribution occurs as a single symmetric "mountain" regarding the axial co-ordinate, being placed approximately in [0;[pi]] [theta] domain.
Figures 1b, 1c and 1d are dedicated to the stationary case when angular displacement [alpha] is with an order greater then [beta]. The differences between these cases and the reference case are very significant. For the lowest eccentricity ([epsilon] = 0) two "pressure mountains" occur which have approximately the same peak. The "mountain" placed in [[pi];2[pi]] [theta] domain decreases with the increasing of eccentricity until it disappears at [epsilon] = 0.2, the pressure distribution becoming strongly non-symmetric, with a higher peak of pressure. So, it is obvious that this pressure distribution produces not only a load capacity, but a moment, too.
This work occurs as a hydrodynamic analysis regarding the problem of an unaligned narrow journal bearing.
The stationary unaligned narrow journal bearing case appears as a particular case of the non-steady case, when [??] = [??] = 0.
The pressure distribution is much different in comparison with the aligned case, becoming strongly non-symmetric, so it is obvious that this pressure produces not only a load capacity, but a moment too.
Although, in the central plane the same minimum film thickness as in the aligned case is obtained, the minimum oil film thickness is inferior to that corresponding in the aligned case.
The relative difference of the attitude angle is between 25 ... 35% in normal working conditions, and this important variation can badly affect the oil supplying of the journal bearing.
[FIGURE 1a OMITTED]
[FIGURE 1b OMITTED]
[FIGURE 1c OMITTED]
[FIGURE 1d OMITTED]
It was observed the angular displacements and velocities produce strong effects on the moment attitude angle.
As a consequence of the non-symmetric pressure distribution, a torque occurs. This must be taken into account when calculating the stiffness and the damping coefficients of unaligned journal bearings. This work is just a preliminary announcement of some results regarding these calculations.
Baskharone, E.A. & Hensel, S.J. (1991). "Interrelated Rotordynamic Effects of Cylindrical and Conical Whirl of Annular Seal Rotor"s, ASME, Journal of Tribology, vol. 113, pp. 470-480
Kanemory, Y., Iwatsubo, T. (1992). "Experimental Study of Dynamic Fluid Forces and Moments of a Long Annular Seal", Journal of Tribology, vol. 114, 2, pp. 773-778.
San Andres, L.A. (1993). "Dynamic Force and Moments for Short Length Annular Seals", ASME, Journal of Tribology, vol. 115, pp. 61-70
Someya, T. (1989). "Journal Bearing Databook", Springer Verlag, Berlin
Suciu, C.V. & Parausanu, I. (1996). "A Complet Investigation of unaligned narrow", Journal Bearing, Mecanique appliquee, Vol. 41, pp. 99-120
Tab. 1. The main parameters values [PSI] Figure [bar.[beta]] [per thousand] [epsilon] 1a 0.5 1 0.1 1b 0.5 1 0 1c 0.5 1 0.05 1d 0.5 1 0.2 [alpha] [beta] [(p/[p.sub.m]). Figure [rad] [rad] sub.max] 1a 0 0 0.4924 1b [10.sup.-3] [10.sup.-4] 0.5282 1c [10.sup.-3] [10.sup.-4] 0.8048 1d [10.sup.-3] [10.sup.-4] 2.2479
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|Author:||Parausanu, Ioan; Gheorghiu, Horia; Tudose, Virgil; Visan, Dana Codruta|
|Publication:||Annals of DAAAM & Proceedings|
|Date:||Jan 1, 2010|
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