【文章內(nèi)容簡介】 of equations: a system of nonlinear algebraic equations for calculation w and a bined system of linearised differential and algebraic equations for calculation wπ. If one considers that friction losses in the driving part are implicitly expressed already in the torquespeed characteristic of the drive and in the external static characteristic of the applied hydrodynamic torque converter and friction losses in the loading part are supposed as a bination of Coulomb and viscous friction, .:MT2=a+bω2,(16)then the nonlinear algebraic system has the form:(17)The bined system of the linearised differential and algebraic equations is(18)where for writing abbreviation it is denoted:(19)The solution process of both equation systems Figs. (17) and (18) is introduced in [8]. The system of nonlinear equations (17) was calculated for three parameter levels u (u=,,) that respond to 30%, 40%, and 60% of the maximal gas lever displacement. To each chosen parameter value u, a certain driving angular velocity interval responds. From Fig. 2 and from Eq. (2) it is evident that for a chosen value u the corresponding mean driving angular velocity value must lie in interval:ω1aω1ω1b,(20)where for border values of the interval it holds:(21)For the chosen parameter value u= and for different mean values Mz, the calculated mean values w (for the drive line with given drive and all the considered converter types) are introduced in diagrams in Fig. 4(a)–(d). Analogical mean values w of the same variables corresponding with the parameter u= are in Fig. 5(a)–(d). Finally, the calculated mean values w corresponding with parameter u= and identical torque converter types are depicted in Fig. 6(a)–(d). Here it is important to remind that xcoordinates in Fig. 4, Fig. 5 and Fig. 6 represent the mean angular velocity interval (20) gradually for parameters u=,, and the decimal fractions on this section denote only its decimal division. From the calculated mean values w in Fig. 4, Fig. 5 and Fig. 6 and from the introduced external static characteristics in Fig. 3a plete nine of the mean values w can be determined for any mean loading value Mz and estimated loss moment value MT2 in the loading part. When this plete nine w is known then it is possible, in the sense of the applied method, to construct all the constant coefficients of the bined differential and algebraic system (18) for calculation wπ. This system is already linear and may be solved by known classical methods. First of all, we take interest in stationary dynamic solution. In sense of the procedure one may express the centred periodic ponent of every dynamic variable in the form:wπ=Mza(Wccosνt+Wssinνt),(22)where notations Wc, Ws represent cosine and sine ponents of the dynamic factor (transmissibility) of corresponding dynamic variable. Detailed puting procedure is introduced in [8]. For transmissibility of the centred periodic ponent of every dynamic variable it holds:(23)As an example in Fig. 7, Fig. 8, Fig. 9, Fig. 10 and Fig. 11 there are successively introduced dynamic characteristics of the centred periodic ponents of dynamic variables: moment (M) and angular velocity of the drive (ω1), loading moment of the pump (M1), moment (M2) and angular velocity of the turbine (ω2) for the system with hydrodynamic converter and for chosen parameter value u=. Results are given in two forms of dynamic characteristics, namely as classic frequency response functions (upper parts) and as Nyquist diagrams (lower parts). Both types of dynamic characteristics are calculated for four values of the loading mechanism inertia moment: kgm2 and for supplementary gear ratio im=1. Equal sections of loading angular velocity Δν with value π corresponding to equal sections on frequency response function xcoordinates are in the Nyquist diagrams separated by bold points as well. In dynamic calculations, the Dieselengine time constant s, regulator time constant s and the regulator damping ratio ζ= were considered. The left parts of the dynamic characteristics in Fig. 7, Fig. 8, Fig. 9, Fig. 10 and Fig. 11 correspond to the dynamic regime with mean values: λ=, K=,i=, which are quantified by bold points on the left thin vertical in the external static characteristic in Fig. 3(a), when the converter works in socalled friction clutch regime. Mean values of dynamic variables, corresponding to this dynamic regime, are: M=, M2=, ω1=, ω2=, Mz=, z=. These values are also accentuated in Fig. 5(a) by bold points on thin vertical line. In this dynamic regime the converter works with mean transfer energy efficiency η≈. The right parts of the dynamic characteristics introduced in Fig. 7, Fig. 8, Fig. 9, Fig. 10 and Fig. 11 correspond to dynamic regime with mean values: λ=,K=, i=, represented by bold points on the right thin vertical on the external static characteristic in Fig. 3(a) when the converter works in socalled moment converter regime with mean energy transfer efficiency higher than . The mean values of dynamic variables corresponding to this dynamic state are: M=, M2=, ω1=, ω2=, Mz=, z= and are marked out in Fig. 5(a) as well on thin vertical line by bold points. Nondimensional friction losses at dynamic calculation were considered according to (16) as follows: , , where is dimensional relative moment standard value (13). Fig. 4.Mean values of the chosen dynamic variables w of the system with converters: , , , for optional parameter u=.Fig. 5.Mean values of the chosen dynamic variables w of the system with converters: , , , for optional parameter u=.Fig. 6.Mean values of the chosen dynamic variables w of the system with converters: , , , for optional parameter u=.Fig. 7.Dynamic factor (transmissibility) of the centred periodic ponent of