This paper proposes a new, flexible, and accurate method for predicting the vibroacoustic environment, which is a driving load case in the development of panel-mounted spacecraft units. This method accounts for the physical parameters that intervene in the dynamically coupled response of units and panels to the impingement of the sound radiated by the rocket engines. Accordingly, it can simplify the costly overdevelopment imposed by testing standards relying on simple mass formulas and significant safety factors. It quickly provides acceleration and force levels for vibration tests, can be applied during any project phase, and allows for the coupling of models with different levels of maturity, while still avoiding the lengthy processing imposed by finite and boundary element tools. It uses impedance/ mobility for dynamically condensing panels and units in a compact and modular way. The acoustic load experienced by a panel is characterized by means of physical reasoning based on acoustic diffraction and joint acceptance between the mode shapes and diffuse field. Predicted levels are presented for an actual spacecraft panel coupled with several units, and are compared to detailed vibroacoustic analysis using finite and boundary element methods, test results, and ESA and NASA standards. Nomenclature A = integrating range of the panel a = circular plate radius, m C F f = force dynamic coupling between panel and units C U1 f = acceleration dynamic coupling between panel and units c = speed of sound, m=s f = frequency, Hz f co = cutoff frequency, Hz G r f = scaling factor of power spectral density of impinging acoustic field G res = static residual of panel compliance at interface to units, m=N g = acceleration of gravity, 9:81 m=s 2 H n f = modal frequency response H nF f = force modal frequency response j = imaginary unit j 2 nn f = joint-acceptance function k = wave number L = largest side length of a rectangular plate or diameter of a circular plate, m m = mass, kg p = acoustic pressure p 1 = far-field acoustic pressure Sf = structural response power spectral density, g 2 =Hz for acceleration and N 2 =Hz for force S r f = acoustic loading power spectral density, Pa 2 =Hz S a f = spectrum of sound pressure level specified to mission, Pa 2 =Hz y = coordinate in panel U 1 f = acceleration frequency response function Y f f = flexible part of modal mobility matrix Z e f = impedance matrix of units at the interface points exn f = generalized modal force applied to panel y 1 ; y 2 ; f = cross-correlation coefficient of acoustic diffuse field n y 1 = spatial distribution of mode shape of panel fn = matrix of flexible mode shapes of panel Subscripts F = force U1 = acceleration Superscripts T = transpose = complex conjugate