{1995年}Bearing Dynamic Coefficients of Flexible-Pad Journal Bearings
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=
vibration amplitudes
= pivot diameter = pivot housing diameter = bearing eccentricity, distance from Ob to Oj
= impedance notation, Z = K
+ jwC
= fluid film impedance matrix containing the fixed
Eq. [131
= damping = bearing radial clearance, assembled clearance
=
pad radial clearance, machined clearance
= fixed global coordinates = vibrations in (x,y) coordinates
-
= dynamic flexibility notation ( A = K - ' ) = reduced pad dynamic flexibility matrix, defined in
.
"
= pad center of curvature without movement = journal radius = distance from pad to O o p = bearing static load = static load on the individual pad
Bearing Dynamic Coefficients of Flexible-Pad Journal Bearingso
WEN JENG CHEN Ingersoll-Rand Company Centrifugal Compressor Division Mayfield, Kentucky 42066
pad coefficients
= reduced effective impedance matrix, Z* = ( I ZA;)-'Z
= pad eccentricity, distance from Op g's modulus = energy per cycle of motion = fluid film force = pivot film thickness = pad inertia =
+
(5,q)
= local coordinate system for each pad, journal
h~ IP
4
i
I ~ I R ~
= identity matrix
= web cross-sectional properties, A = area,
AE, El
j K
I = moment of inertia
KEY WORDS
Fluid Film Bearings, Hydrodynamic Bearings, TiltingPad Bearings, Rotor Bearing Dynamics
= indices
= static equilibrium = pad = displacement directions
= bearing geometric center
Oi OP
= pad center of curvature
= journal equilibrium center
P
253
x,y,y,S,q
Wen Jeng Chen
a a
Centrifugal Compressor Division , Ingersoll-Rand Company , Mayfield, Kentucky, 42066 Published online: 25 Mar 2008.
To cite this article: Wen Jeng Chen (1995) Bearing Dynamic Coefficients of Flexible-Pad Journal Bearings, Tribology Transactions, 38:2, 253-260, DOI: 10.1080/10402009508983402 To link to this article: /10.1080/10402009508983402
This article was downloaded by: [Princeton University] On: 06 January 2014, At: 03:40 Publisher: Taylor & Francis Informa Ltd Registered in England and Wales Registered Number: 1072954 Registered office: Mortimer House, 37-41 Mortimer Street, London W1T 3JH, UK
= dynamic stiffness notation, K= K - 0 2 m = pivot axial length for line-contact tilting-pad
bearing, web length
= mass
SUBSCRIPTS
b (i9j) o
= bearing
= pad mass
Downloaded by [Princeton University] at 03:40 06 January 2014
The application of flexible-pad journal bearings for high-speed rotating machinery has recently gained attention from equipment manufacturers for its simplicity of one-piece design which can elim-
Tribology Transactions
Publication details, including instructions for authors and subscription information: /loi/utrb20
Bearing Dynamic Coefficients of Flexible-Pad Journal Bearings
Presented as a Soclety of Tribologists and Lubrication Engineers paper at the ASMEISTLE Triboiogy Conference in Lahalna, Hawaii, October 16-20, 1994 Final manuscript approved June 20, 1994
PLEASE SCROLL DOWN FOR ARTICLE Taylor & Francis makes every effort to ensure the accuracy of all the information (the “Content”) contained in the publications on our platform. However, Taylor & Francis, our agents, and our licensors make no representations or warranties whatsoever as to the accuracy, completeness, or suitability for any purpose of the Content. Any opinions and views expressed in this publication are the opinions and views of the authors, and are not the views of or endorsed by Taylor & Francis. The accuracy of the Content should not be relied upon and should be independently verified with primary sources of information. Taylor and Francis shall not be liable for any losses, actions, claims, proceedings, demands, costs, expenses, damages, and other liabilities whatsoever or howsoever caused arising directly or indirectly in connection with, in relation to or arising out of the use of the Content. This article may be used for research, teaching, and private study purposes. Any substantial or systematic reproduction, redistribution, reselling, loan, sub-licensing, systematic supply, or distribution in any form to anyone is expressly forbidden. Terms & Conditions of access and use can be found at http:// /page/terms-and-conditions
=vT
= stiffness = pivot stiffness
K~ K L
m
m~
06
displacements ({op,qop) = displacements of pad center of curvature (Sp,qp,yp) = pad displacements, two translations and one rotation $6 = attitude a n d e o = frequency 0 = phase angle v = Poisson's ratio $P = pivot angular location measured from x to 6 in the direction of rotation
inate the manufacturing tolerance stack-up and possible lowerfrictional power loss. This paper presents a general method for the calculation of bearing dynamic coefficients of flexible-pad journal bearings. These coefficients are critical to the rotor dynamics study. The flexibility of the support web and mu~slinertiaeffects are included in this approach. The bearing coefficients of a conventional tiltinppad journal bear in^ can also be obtained from this method ..,. . by adjwting the reduced pad dynamic flexibility matrix. The numerial results are in good correlation with the laboratory expm'ments.
vibration amplitudes
= pivot diameter = pivot housing diameter = bearing eccentricity, distance from Ob to Oj
= impedance notation, Z = K
+ jwC
= fluid film impedance matrix containing the fixed
Eq. [131
= damping = bearing radial clearance, assembled clearance
=
pad radial clearance, machined clearance
= fixed global coordinates = vibrations in (x,y) coordinates
-
= dynamic flexibility notation ( A = K - ' ) = reduced pad dynamic flexibility matrix, defined in
.
"
= pad center of curvature without movement = journal radius = distance from pad to O o p = bearing static load = static load on the individual pad
Bearing Dynamic Coefficients of Flexible-Pad Journal Bearingso
WEN JENG CHEN Ingersoll-Rand Company Centrifugal Compressor Division Mayfield, Kentucky 42066
pad coefficients
= reduced effective impedance matrix, Z* = ( I ZA;)-'Z
= pad eccentricity, distance from Op g's modulus = energy per cycle of motion = fluid film force = pivot film thickness = pad inertia =
+
(5,q)
= local coordinate system for each pad, journal
h~ IP
4
i
I ~ I R ~
= identity matrix
= web cross-sectional properties, A = area,
AE, El
j K
I = moment of inertia
KEY WORDS
Fluid Film Bearings, Hydrodynamic Bearings, TiltingPad Bearings, Rotor Bearing Dynamics
= indices
= static equilibrium = pad = displacement directions
= bearing geometric center
Oi OP
= pad center of curvature
= journal equilibrium center
P
253
x,y,y,S,q
Wen Jeng Chen
a a
Centrifugal Compressor Division , Ingersoll-Rand Company , Mayfield, Kentucky, 42066 Published online: 25 Mar 2008.
To cite this article: Wen Jeng Chen (1995) Bearing Dynamic Coefficients of Flexible-Pad Journal Bearings, Tribology Transactions, 38:2, 253-260, DOI: 10.1080/10402009508983402 To link to this article: /10.1080/10402009508983402
This article was downloaded by: [Princeton University] On: 06 January 2014, At: 03:40 Publisher: Taylor & Francis Informa Ltd Registered in England and Wales Registered Number: 1072954 Registered office: Mortimer House, 37-41 Mortimer Street, London W1T 3JH, UK
= dynamic stiffness notation, K= K - 0 2 m = pivot axial length for line-contact tilting-pad
bearing, web length
= mass
SUBSCRIPTS
b (i9j) o
= bearing
= pad mass
Downloaded by [Princeton University] at 03:40 06 January 2014
The application of flexible-pad journal bearings for high-speed rotating machinery has recently gained attention from equipment manufacturers for its simplicity of one-piece design which can elim-
Tribology Transactions
Publication details, including instructions for authors and subscription information: /loi/utrb20
Bearing Dynamic Coefficients of Flexible-Pad Journal Bearings
Presented as a Soclety of Tribologists and Lubrication Engineers paper at the ASMEISTLE Triboiogy Conference in Lahalna, Hawaii, October 16-20, 1994 Final manuscript approved June 20, 1994
PLEASE SCROLL DOWN FOR ARTICLE Taylor & Francis makes every effort to ensure the accuracy of all the information (the “Content”) contained in the publications on our platform. However, Taylor & Francis, our agents, and our licensors make no representations or warranties whatsoever as to the accuracy, completeness, or suitability for any purpose of the Content. Any opinions and views expressed in this publication are the opinions and views of the authors, and are not the views of or endorsed by Taylor & Francis. The accuracy of the Content should not be relied upon and should be independently verified with primary sources of information. Taylor and Francis shall not be liable for any losses, actions, claims, proceedings, demands, costs, expenses, damages, and other liabilities whatsoever or howsoever caused arising directly or indirectly in connection with, in relation to or arising out of the use of the Content. This article may be used for research, teaching, and private study purposes. Any substantial or systematic reproduction, redistribution, reselling, loan, sub-licensing, systematic supply, or distribution in any form to anyone is expressly forbidden. Terms & Conditions of access and use can be found at http:// /page/terms-and-conditions
=vT
= stiffness = pivot stiffness
K~ K L
m
m~
06
displacements ({op,qop) = displacements of pad center of curvature (Sp,qp,yp) = pad displacements, two translations and one rotation $6 = attitude a n d e o = frequency 0 = phase angle v = Poisson's ratio $P = pivot angular location measured from x to 6 in the direction of rotation
inate the manufacturing tolerance stack-up and possible lowerfrictional power loss. This paper presents a general method for the calculation of bearing dynamic coefficients of flexible-pad journal bearings. These coefficients are critical to the rotor dynamics study. The flexibility of the support web and mu~slinertiaeffects are included in this approach. The bearing coefficients of a conventional tiltinppad journal bear in^ can also be obtained from this method ..,. . by adjwting the reduced pad dynamic flexibility matrix. The numerial results are in good correlation with the laboratory expm'ments.