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N1 = xFn sin a N2 = (1 + x ) Fn sin a in which Fn is the normal contact force, a is the pressure angle, and x is a dimension ratio The modeling of passive system parameters such as masses, moments of inertia, and spring stiffnesses is carried out in a standard way The choice for the value of the damping factor of 003 for structural damping and of 005 to 007 for well-lubricated machine components is considered reasonable Let us analyze the dynamic response of the complex eleven-degree-of freedom model to include some major sources of manufacturing errors This was accomplished by Kim and Newcomb (1981) to include system exibility with cam pro le variations due to errors or tolerances A computer simulation technique was applied for this analysis which indicated the stochastic nature of manufacturing as discussed in Chap 10 The cam-follower drive system was simulated to include elasticity and manufacturing with the following data: A cam rotates at 800 rpm with a dwell-rise-return dwell action The displacement is 0 to 30 , dwell; 30 to 180 , rise 0381 m with modi ed trapezoidal motion; 180 to 210 , dwell; and 210 to 360 , return with 4-5-6-7 polynomial motion The base circle radius of the cam is 0381 m and the follower roller radius is 009525 m The tolerance of the cam pro le equals 27 10-5 m and the tolerance of the roller follower equals 0254 10-5 m The v-result of the eves gation revealed that the assumed tolerances had very little in uence on the vibration of the cam-follower system Figure 1228 shows two whole revolutions of the cam and the transient behavior of follower acceleration It includes the combined effects of exibility in the system and the tolerances of the cam and follower For more on this subject see the original reference.

8:

Overload2 ob = new Overload2(); int i = 10; double d = 101; byte b = 99; short s = 10; float f = 115F;

The following table summarizes when to store the intelligence in a fact table and when it poses disadvantages:

obMyMeth(i); // calls obMyMeth(int) obMyMeth(d); // calls obMyMeth(double) obMyMeth(b); // calls obMyMeth(int) -- type conversion obMyMeth(s); // calls obMyMeth(int) -- type conversion obMyMeth(f); // calls obMyMeth(double) -- type conversion } }

.

The output from the program is shown here:

Relational Table Benefits Precalculated in the table, so fast, consistent response times Server-based, so consistent business definitions and minimal network traffic Relational Table Disadvantages Requires complex programming logic in the load routines Fixed table design may limit flexibility IT/DBA must implement Requires additional disk space Not suitable for ratios and percentages

Inside Inside Inside Inside Inside MyMeth(int): 10 MyMeth(double): 101 MyMeth(int): 99 MyMeth(int): 10 MyMeth(double): 115

We conclude the chapter with a summary of both theoretical and practical design considerations for high-speed cam-follower performance Vibrations in dynamic cam-follower systems are primarily due to the compliance in the system Vibration may also be the result of other practical factors, ie, errors in fabrication, wornout (old) machine parts, misalignment in assembled parts, and imbalance of parts Backlash should be minimized Preloaded bearings may sometimes be applied and lubrication systems should be selected carefully for optimum performance An elastic follower with a rigid camshaft in general can employ a single-degree-of freedom model with impunity The elastic follower with a rigid camshaft model presents the transient vibratory state for important primary and residual vibrations to be studied; see Chap 13 The elastic camshaft presents a more complicated mathematical nonlinear relationship The models of this cam-follower include the closed-track and open-track systems Choose the lubricant properly for compatability in the system Proper choice of cam curves (acceleration curve continuity) are the modi ed sine, modi ed trapezoidal, and polynomial curves These will minimize the effect of follower output, linear system, and cam drive nonlinear vibrations The inertia load of the closedtrack model produces vibrations that are twice the frequency of the modes of the opentrack Also, the elastic camshaft may produce vibratory resonant couple of the cam input and the follower system to produce dif culties Excessive noise may accompany vibrations in cam-follower systems This may be the result of a waviness error in the cam pro le fabrication For automotive camshaft (valve gear) optimization, performance proprietary software exists in all manufacturers In App D the designer will nd a comprehensive listing of available software for design, manufacturing, and engine performance Some of the camshaft studies are: cam pro le determination, cam surface hertzian stresses, and harmonic analysis for spring surge and valve bounce.