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This paper depicts the optimization of tractor trolley chassis to carry the maximum load using all design operating condition safely.
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A constant force of 2000 N was applied through the center of the ball and normal to the surface of the liner, with the load centered 23° away from the pole of the liner (Fig. 5), corresponding to the maximum load used in the hip simulator tests.
This paper analyses the redistribution of maximum loads using a system of load limiters on shores in which the limiters yield at a given load and thus reduce the maximum load absorbed by the shores.
In particular, we focus on the identification of minimum load to be removed using external MSAs, excess capacity of process MSAs, and maximum removable load using process MSAs.
For the positioning task, participants held a 30%% one-repetition maximum (1-RM) load using the index finger until volitional fatigue.
This result can be utilized as a conservative dimensioning strategy by designing biaxially loaded joints in terms of maximum peak resultant bearing load using uniaxial fatigue data.
The parameters measured during the experiment were peak load (Pmax), peak displacement hmax, contact area Ac, and stiffness S. The stiffness was calculated from the slope of the initial unloading curve; the region between 20 and 95% of the maximum load was used to determine the slope of the unloading curve.
Data provided by indentation tests at different maximum loads were used to estimate size-independent hardness and elastic modulus.
Instron machine (Instron 2716 010, maximum load 50kN) was used for the experiments with a loading rate of 10 N/min.
Numerically predicted and measured maximum reinforcement loads are compared to loads using the AASHTO reinforcement strength-based design approach (Simplified Method) and the Simplified Stiffness Method which is an empirical reinforcement stiffness-based method.
Maximum load was successfully evaluated using plastic section modulus and modified flow stress, in dependent to failure mode.
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