METHOD FOR PREDICTING THE NOISE/COMFORT PERFORMANCE OF A VEHICLE TRAVELLING ON UNEVEN GROUND

• US 20120035894A1
• Filed: 04/28/2009
• Published: 02/09/2012
• Est. Priority Date: 04/30/2008
• Status: Active Grant

• Current Assignee: Compagnie générale des établissements Michelin
• Original Assignee: Michelin Recherche et Technique SA (Compagnie Generale DES Etablissements Michelin SCA), Societe De Technologie Michelin (Compagnie Generale DES Etablissements Michelin SCA)
• Inventors: Le Salver, Robert, Le Salver, Françoise, Le Salver, Clarisse, Le Salver, Annig, Le Salver, Vincent
• Granted Patent: US 8,731,878 B2
• Time in Patent Office: Days
• US Class Current: 703/2
• CPC Class Codes: G01M 17/0072 the wheels of the vehicle co-operating with rotatable rolls G01M17/022, G01M17/045, G01M17/065 take precedence
• CPC Class Codes: G01M 17/045 the vehicle wheels co-operating with rotatable rollers

Abstract

A method is presented for predicting a noise/comfort performance in a cabin of a vehicle with a body-shell and a suspension system linked to the body-shell by at least one point of attachment, with the vehicle rolling at a given speed on a rolling device with a macrorough rolling surface. The method includes: determining a global transfer function of the body-shell, determining a global admittance of the body-shell, determining an impedance of the suspension system, determining, while rolling on the macrorough rolling surface, lockup loads of the suspension system, and combining together the global transfer function of the body-shell, the global admittance of the body-shell, the impedance of the suspension system, and the lockup loads of the suspension system to obtain a prediction of noise/comfort performance (P) inside the cabin.

Claims

1-17. -17. (canceled)

18. A method for predicting noise/comfort performance corresponding to an acoustic and/or vibratory level in a cabin of a vehicle with a body-shell and a suspension system linked to the body-shell by at least one point of attachment, the vehicle rolling at a given speed V on a rolling device that includes on its rolling surface at least one irregularity of a predetermined dimension, the method comprising:

determining a global transfer function of the body-shell for a point of attachment to the cabin (T_body-shell);

determining a global admittance of the body-shell for a point of attachment of the suspension system to the body-shell (Y_body-shell);

determining a global impedance of the suspension system for the point of attachment to the body-shell (Z_S);

determining, while rolling, lockup loads of the suspension system at the point of attachment to the body-shell (F_S^b); and

combining together the global transfer function of the body-shell, the global admittance of the body-shell, the global impedance of the suspension system, and the lockup loads of the suspension system to obtain a prediction of a noise/comfort performance (P) inside the cabin.

19. The method according to claim 18, wherein the global transfer function of the body-shell (T_body-shell) and the global admittance of the body-shell (Y_body-shell) are determined when stationary.

20. The method according to claim 18, wherein, to determine the global transfer function of the body-shell, measurements are made on the body-shell when stationary by:

recording noise and vibration signals at m points previously determined in the cabin using recording devices placed inside the vehicle;

positioning the point of attachment of the suspension system with respect to the body-shell in a manner analogous to a position the suspension system would have on the vehicle;

the point of attachment at a level of the body-shell being free in displacement and rotation and being suspended using flexible elastic links;

applying excitations at the point of attachment of the suspension system using an excitation system, the excitation being applied in predetermined directions corresponding to excitations in directions of a reference frame of the vehicle;

obtaining a set of temporal data by, for each excitation, recording the noise and vibration signals in the cabin of the vehicle together with, at the level of the point of attachment, an excitation signal;

translating the set of temporal data to a frequency domain using computer software; and

obtaining the global transfer function of the body-shell by referring the noise and vibration signals of m various points of the cabin to a unit excitation in translation or rotation in a right-handed orthonormal reference frame.

21. The method according to claim 20, wherein, when the point of attachment is not accessible, excitations are applied at geometric points determined in relation to the point of attachment, and loads at the point of attachment are calculated using a geometric transformation based on loads at the geometric points.

22. The method according to claim 18, wherein, to determine the global admittance of the body-shell for the point of attachment of the suspension system to the body-shell, measurements are made on the body-shell when stationary by:

positioning the point of attachment of the suspension system with respect to the body-shell in a manner analogous to a position the suspension system would have on the vehicle;

the point of attachment at a level of the body-shell being free in displacement and rotation and being suspended using flexible elastic links;

equipping the point of attachment with vibration sensors for measuring a vibratory level of the point of attachment of the body-shell;

applying excitations to the point of attachment using an excitation system, the excitations being applied in predetermined directions corresponding to excitations in directions of a reference frame of the vehicle;

obtaining a set of temporal data by, for each excitation, recording an excitation signal at the level of the point of attachment and recording vibratory responses at the point of attachment;

translating the set of temporal data to a frequency domain using computer software; and

obtaining the global admittance of the body-shell at the level of the point of attachment by calculating a ratio between the vibratory responses in the directions of the reference frame of the vehicle at the point of attachment and the excitation signal at the level of the point of attachment.

23. The method according to claim 22, wherein translational and rotational vibratory responses of the point of attachment are recorded.

24. The method according to claim 22, wherein, when the point of attachment is not accessible, vibration sensors are fitted to and excitations are applied at geometric points determined in relation to the point of attachment, and vibratory levels and loads at the point of attachment are calculated using a geometric transformation based on loads at the geometric points.

25. The method according to claim 18, wherein, to determine the global impedance of the suspension system for the point of attachment to the body-shell, measurements are made on the suspension system by:

arranging the suspension system in place on a device equipped with a smooth cladding;

mechanically connecting the suspension system to a bench at the point of attachment by way of connections that are flexible in relation to a rigidity of the suspension system, the bench being equipped with sensors for measuring displacements and measuring forces and moments of the point of attachment of the suspension system, in such a way that the point of attachment is free to move in a direction of translation or rotation;

applying excitations at the point of attachment using an excitation system adapted for imposing kinematics at the point of attachment in a direction previously left free of motion;

obtaining a set of temporal data by, for each excitation at the point of attachment of the suspension system, measuring a displacement vector (translation and rotation) of the point of attachment, during excitation, and measuring a vector of resulting loads (forces and moments) at the point of attachment, for a set of degrees of freedom of the point of attachment;

translating the set of temporal data to a frequency domain using computer software; and

obtaining the global impedance of the suspension system by calculating a ratio between signals of forces and moments at the point of attachment and a vibratory level at the point of attachment for plural degrees of freedom of the point of attachment.

26. The method according to claim 25, wherein the suspension system, prior to the applying of the excitations, is arranged in place on the device equipped with the smooth cladding under rolling conditions similar to those experienced by the vehicle.

27. The method according to claim 25, wherein the excitation system is adapted for imposing the kinematics at the point of attachment in the direction previously left free of motion without exciting other degrees of freedom of the point of attachment.

28. The method according to claim 20, wherein the excitation system includes vibrating pots.

29. The method according to claim 18, wherein, to determine the lockup loads of the suspension system at the point of attachment, measurements are made on the suspension system by:

arranging the suspension system in place on a rolling device that includes on its rolling surface at least one irregularity of predetermined a dimension similar to used in on-vehicle trials;

rigidly fixing the suspension system on a bench at the point of attachment, the bench being equipped with a sensor for measuring forces and moments at the point of attachment;

stressing the suspension system on the rolling device under rolling conditions identical to those used in the on-vehicle trials;

obtaining a set of temporal data by recording, while rolling, signals of the forces and moments at the point of attachment; and

translating the set of temporal data to a frequency domain using computer software.

30. The method according to claim 18, wherein, to evaluate the noise/comfort performance of the vehicle equipped with the suspension system, a formula of:

P=T_body-shell*[I+Z_S*Y_body-shell]<sup>−

1</sup>*F_S^b

is calculated, in which, for each frequency studied;

P is a comfort performance of the vehicle in the cabin, and is a matrix of dimensions m, 1, with m being a number of measurement points in the cabin;

T_body-shell is the global transfer function of the body-shell, and is a matrix of dimensions m, n;

I is a unit matrix of dimensions n, n, n being a number of predetermined directions of excitation of the point of attachment;

Y_body-shell is the global admittance of the body-shell, and is a square matrix of dimensions n, n;

Z_S is the global impedance of the suspension system, and is a square matrix of dimensions n, n; and

F_S^b corresponds to the lockup loads of the suspension system, and is a matrix of dimensions n, 1.

33. The method according to claim 18, wherein the suspension system is a tire and wheel assembly.

35. The method according to claim 18, wherein the global transfer function of the body-shell, the global admittance of the body-shell, the global impedance of the suspension system, and the lockup loads of the suspension system are digital data derived from a simulation of an experimental characterization.

31. A method for predicting operational loads at a point of attachment of a vehicle that includes a body-shell and a suspension system linked to the body-shell by at least one point of attachment, the vehicle rolling at a given speed V on a rolling device that includes on its rolling surface at least one irregularity of a predetermined dimension, comprising:

determining an admittance of the body-shell for the point of attachment of the suspension system to the body-shell (Y_body-shell);

determining an impedance of the suspension system for the point of attachment (Z_S);

determining, while rolling, lockup loads of the suspension system at the point of attachment (F_S^b); and

combining together the admittance of the body-shell, the impedance of the suspension system, and the lockup loads of the suspension system.

32. The method according to claim 31, wherein, to evaluate the operational loads at the point of attachment of the vehicle equipped with the suspension system, a formula of:

F_S^op=[I+Z_S*Y_body-shell]<sup>−

1</sup>*F_S^b

is calculated, in which, for each frequency studied;

F_S^op corresponds to the operational loads at the point of attachment of the vehicle, and is a matrix of dimensions n, 1, n being a number of predetermined directions of excitation of the point of attachment of the vehicle;

I is a unit matrix of dimensions n, n;

Y_body-shell is the admittance of the body-shell, and is a square matrix of dimensions n, n;

Z_S is the impedance of the suspension system, and is a square matrix of dimensions n, n; and

F_S^b corresponds to the lockup loads of the suspension system, and is a matrix of dimensions n, 1.

34. The method according to claim 31, wherein the suspension system is a tire and wheel assembly.

36. The method according to claim 31, wherein the admittance of the body-shell, the impedance of the suspension system, and the lockup loads of the suspension system are digital data derived from a simulation of an experimental characterization.