Massless bilinear hysteresis elements are often used to model frictional energy dissipation in dynamic systems. These quasi-static elements possess only two describing parameters, the damper stiffness and the force at which it slips. Bilinear hysteresis elements capture the qualitative nature of friction-damped forced response, but sometimes have difficulty with quantitative comparisons. This paper examines the performance of massless bilinear hysteresis elements as well as the role of damper mass in energy dissipation, and specifically evaluates its influence on the kinematic state of the damper (pure slip, stick-slip, pure stick). Differences between the massless and non-zero mass case are explored, as are the implications on both damper and system response. The results indicate that even small damper mass can have a qualitative effect on the system response, and provide advantages over the massless case. Further, we develop transition maps, describing damper response kinematics in the damper parameter space, which segment the space into two linear analysis regions (pure slip, pure stick) and one nonlinear analysis region (stick-slip). The results suggest non-zero mass dampers which are tuned as optimal vibration absorbers provide substantial resonance response attenuation and substantially reduce the size of the nonlinear analysis region in the damper parameter space.

1.
Iwan
,
W. D.
,
1967
, “
On a Class of Models for the Yielding Behavior of Continuous and Composite Systems
,”
ASME J. Appl. Mech.
,
34
, pp.
612
617
.
2.
Ferri, A. A., and Heck, B. S., 1995, “Vibration Analysis of Dry Friction Damped Turbine Blades Using Singular Perturbation Theory,” Proceedings of the ASME International Mechanical Engineering Congress and Exposition, AMD-Vol. 192, pp. 47–56.
3.
Berger
,
E. J.
,
Begley
,
M. R.
, and
Mahajani
,
M.
,
2000
, “
Structural Dynamic Effects on Interface Response-Formulation and Simulation Under Partial Slipping Conditions
,”
ASME J. Appl. Mech.
,
67
, pp.
785
792
.
4.
Den Hartog
,
J. P.
,
1931
, “
Forced Vibrations with Combined Coulomb and Viscous Damping
,”
ASME J. Appl. Mech.
,
APM-53-9
, pp.
107
115
.
5.
Griffin
,
J. H.
,
1980
, “
Friction Damping of Resonant Stresses in Gas Turbine Engine Airfoils
,”
ASME J. Eng. Power
,
102
, pp.
329
333
.
6.
Menq
,
C.-H.
,
Griffin
,
J. H.
, and
Bielak
,
J.
,
1986
, “
The Influence of a Variable Normal Load on the Forced Vibration of a Frictionally Damped Structure
,”
ASME J. Eng. Gas Turbines Power
,
108
, pp.
300
305
.
7.
Menq
,
C.-H.
, and
Griffin
,
J. H.
,
1985
, “
A Comparison of Transient and Steady State Finite Element Analyses of the Forced Response of a Frictionally Damped Beam
,”
ASME J. Vibr. Acoust.
,
107
, pp.
19
25
.
8.
Cameron, T. M., Griffin, J. H., Kielb, R. E., and Hoosac, T. M., 1987, “An Integrated Approach for Friction Damper Design,” ASME Design Booklet, The Role of Damping in Vibration and Noise Control, ASME DE-Vol. 5, pp. 205–211.
9.
Wang
,
J. H.
, and
Chen
,
W. K.
,
1993
, “
Investigation of the Vibration of a Blade With Friction Damper by HBM
,”
ASME J. Eng. Gas Turbines Power
,
115
, pp.
294
299
.
10.
Sanliturk
,
K. Y.
, and
Ewins
,
D. J.
,
1996
, “
Modelling Two-Dimensional Friction Contact and Its Application Using Harmonic Balance Method
,”
J. Sound Vib.
,
193
, pp.
511
523
.
11.
Sanliturk
,
K. Y.
,
Imregun
,
M.
, and
Ewins
,
D. J.
,
1997
, “
Harmonic Balance Vibration Analysis of Turbine Blades With Friction Dampers
,”
ASME J. Vibr. Acoust.
,
119
, pp.
96
103
.
12.
Szwedowicz, J., Kissel, M., Ravindra, B., and Kellerer, R., 2001, “Estimation of Contact Stiffness and Its Role in the Design of a Friction Damper,” Proceedings of ASME TURBO EXPO 2001, New Orleans, Louisiana.
13.
Pierre
,
C.
,
Ferri
,
A. A.
, and
Dowell
,
E. H.
,
1985
, “
Multi-Harmonic Analysis of Dry Friction Damped Systems Using an Incremental Harmonic Balance Method
,”
ASME J. Appl. Mech.
,
52
, pp.
958
964
.
You do not currently have access to this content.