SU1513374A1 - Method of determining the mass of cargo in moving wheeled vehicle - Google Patents

Abstract

The invention relates to the field of weighing technology. To improve the accuracy of determining the mass of the cargo on the vehicle, the vertical oscillations of this vehicle are measured during its movement with the load without it, the resonant frequencies of these oscillations are selected, from which the mass is calculated taking into account the stiffness coefficient of the sprung parts, i.e. The weight of the cargo is judged by the difference between the mass of the sprung parts with the load and the known mass of the sprung parts of the vehicle. 2 Il.

Description

one

(21) 4267403 / 24-10

(22) 06.24.87

X46) 10/07/89. Bul Number 37

, (71) East-Siberian Branch of the Research Institute of Automobile Transport (72) B.М. Konstantinov, A.M. Borodich, A.M. Zlobin and V.A. Bushes i (53) 681.26 (088.8) (56) USSR Author's Certificate No. 802802, cl. G 01 G 3/16., 1981. USSR Copyright Certificate No. 678323, G 01 G 19 / OQ, 1975.

(54) METHOD FOR DETERMINING THE WEIGHT OF CARGO ON A MOVING WHEEL VEHICLE

(57) The invention relates to the field of weighing equipment. To vary the accuracy of determining the mass of the load on the vehicle, the vertical oscillations of this vehicle with its load and without it are measured, the resonant frequencies of these oscillations are calculated, and the mass is calculated using the rigidity coefficient of the sprung parts, i.e. The weight of the cargo is judged by the difference between the mass of the sprung parts with the load and the known mass of the sprung parts of the vehicle. 2 Il.

(L

The invention relates to weighing technology.

The aim of the invention is to improve the accuracy.

FIG. Figure 1 shows a diagram of the vertical oscillations of one of the axles of a wheeled vehicle, explaining the method; FIG. 2 is a block diagram of a device for implementing the method.

The design diagram of FIG. 1 includes the sprung parts coming to bridge 1; with mass M, elastic. element 2 with xapticpics yes: C is the coefficient of rigidity of the spressor.

,four

parts, K is the friction coefficient of the sprout of the unsprung parts of w, the sensor 4 is of the vertical unsprung parts of 5 s. characteristic stiffness of the non-part (tire), forcing the sides of the base 6.

Starting from the calculated dead-frequency characteristic accelerations of the correlated and unresolved ones have the form

Ai (W)

wlciiGi + KiHi},

SHY + (MS + tC- -MSy) U2 + SSTs 2+ SuK -MK-tK

parts, K - coefficient of hydraulic friction of the sprung parts, unsprung parts 3 with mass w, sensor 4 vertical vibrations, unsprung parts, elastic element 5 s. characteristic C, is the stiffness coefficient of the unsprung parts (tires), which forces the force from the base 6.

Starting from the design scheme, the amplitude-frequency characteristics of the vertical accelerations of the sprung and unsprung parts, respectively, are

SP

M

1st

(one)

GA GiLg, iC-2MCW2 + M2wVK2W2)

 j wj j МТЙ + СМС + тС + МСШ) W2 + cc 2 + C

e W 2if - angular frequency of vertical oscillations; f is the frequency of vertical oscillations; 2 - vertical oscillations Q

Podsoryorennyh parts. Differentiating with respect to W and equalizing the equations (1) and (2) to zero, i.e.

drAi (W) T2 dW

Q;

15

dlAji (W) dW

ABOUT,

we get

Yu

- (MmK) 2W. ,, -2 (MmG) 2Wp, + (2M2tSZ +

pz.

+ 2Mm2 sz + 2M2mC2. + 4 MtsSSt, K2 +

+ M C2K2-2MC K -2mC K) Wp2 +2 (-2MCC2K -2mC2C K2-2MC2C, K2). +2 (2S2 eg, K2 -MSZ Cgj-iriC Sc,) W, +

0; (3)

,

(MV + 2MZ tK2 -2M pS-2M tSC,) Wp, + +2 (M C + 2M5tC2 + 2m SSi-1-4MZ, - No. SZ-ш shSZ-5MZ S2 Sts, -6M2 tC2 C + 4№nCC K2 40.

When a wheeled vehicle is moving, t

“. Its sprung and non-resistive-2M3Cj, K-2M2mCj K2) Wpx +2 (ZM2SSts, K2-asteA, while the sensor 7, for example, an accelerometer (Fig. 2), produces a signal proportional to the amplitude of oscillations of unsprung parts, which enters the amplifier 8 and then through the analog-digital converter 9 to the microprocessor system 10, where first a fast Fourier transform is performed, which allows to determine the natural frequencies of the vertical oscillations of the sprung and unsprung parts, and then the mass transported cargo.

74M3CCS, + 2M2C K2-MC K -mC K-) WpK + + (8М2 СЗ Сц, + 8№СЗ Сщ-8МСС2 К С С -4МС2С К2-4тС2Сц, К2 + 2С2 „K) Wpx + +2 (2C2C2K2- MC Cy-mC Ci, -4MC C2) WJ, +

where w

ABOUT

W,

ft px

(four)

own corner

the frequencies of vertical oscillations, respectively, of the podressorny and unsprung parts.

45

Equations (3) and (4) are the basic ones in determining the mass transported by the wheeled vehicle of the load.

For the case of movement without load,. when M is MQ, where M is the mass of the sprung parts known pertaining to this bridge, equations (4) and (3) are reduced to

Claims (1)

Invention Formula The method of determining the mass of a load on a moving wheeled vehicle, which consists in measuring the vertical oscillations of the vehicle during its movement without a load and with a load, gives the resonant frequencies of these oscillations and calculates MKVP mKW JJ (2) SSh tfCWpx,); WITH ,). From the joint solution of these equations, the stiffness coefficient C of the wheeled vehicle is determined. For the case of movement with a load, equations (4) and (3) are reduced to C c, M (Wpx); m Q (Wp,). (7) (8) When solving these equations together, we substitute the value of the coefficient C found in the previous case and determine the mass of the sprung parts. Finally, we determine the mass of the cargo from the expiry. M, Have  M - M about thirty A device for implementing the method works as follows. Invention Formula The method of determining the mass of the load on a moving wheeled vehicle, which consists in measuring the vertical oscillations of the vehicle during its movement without a load and with a load, makes the resonant frequencies of these oscillations and calculate the mass of the cargo according to the obtained resonant frequencies and the known mass of the sprung parts of the vehicle, characterized in that, in order to improve accuracy, when driving without a load, the resonant vibration frequencies are determined separately for the sprung and unsprung parts of the vehicle, calculated from the obtained values of the resonant frequencies, the value of the stiffness coefficient of the sprung parts 513374. 6 and remember it, while moving around, the resonant frequencies of oscillations of the sprung and unsprung parts are also determined, from which the previously obtained stiffness coefficient determines the mass of the sprung parts with the load, and about the mass of the load is judged by the difference between the mass of the sprung parts with the load and the sheer mass of the sprung parts of the vehicle. ten Figg