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radio mailbox do its magic. You may have to adjust the proper audio level to prevent distorted audio from reaching the radio mailbox; this might take a few tries to get right. Operation begins with your radio buddies sending the proper touch-tone sequence to your radio. Once the proper tone sequence is received and decoded, the STAMP 2 takes the output at pin 12 to a low state, which propagates a low through the exclusive OR gate at U4, thus triggering the ISD2590 to begin recording the first message. After the voice message has been recorded, the radio operator sends the digits #9 (pound-nine) to reset the tone decoder. Once the decoder is reset, it waits for the proper tone sequence. A number of recorded messages can be recorded by different radio friends, and, on returning to your radio, you can elect to listen to all the recorded messages by simply toggling S3 to the play position. When you have listened to all the recorded messages, just return S3 to the standby position. This project has many possibilities, and it can be expanded with many more features if desired. Just enter the magic code *1234567# and the radio mailbox is ready to serve you!

where TP = pinion torque in inch-pounds (in lb) and d = pinion operating pitch diameter in inches. If the duty cycle is not uniform but does not vary substantially, then the maximum anticipated load should be used. Similarly, if the gear set is to operate at a combination of very high and very low loads, it should be evaluated at the maximum load. If, however, the loading varies over a well-defined range, then the cumulative fatigue damage for the loading cycle should be evaluated by using Miner s rule. For a good explanation, see Ref. [10.2]. Application Factors Ca and Ka. The application factor makes the allowances for externally applied loads of unknown nature which are in excess of the nominal tangential load. Such factors can be defined only after considerable field experience has been established. In a new design, this consideration places the designer squarely on the horns of a dilemma, since new presupposes limited, if any, experience. The values shown in Table 10.3 may be used as a guide if no other basis is available.

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The application factor should never be set equal to unity except where clear experimental evidence indicates that the loading will be absolutely uniform. Wherever possible, the actual loading to be applied to the system should be defined. One of the most common mistakes made by gear system designers is assuming that the motor (or engine, etc.) nameplate rating is also the gear unit rating point. Dynamic Factors Cv and K v . These factors account for internally generated tooth loads which are induced by nonconjugate meshing action.This discontinuous motion occurs as a result of various tooth errors (such as spacing, profile, and runout) and system effects (such as deflections). Other effects, such as system torsional resonances and gear blank resonant responses, may also contribute to the overall dynamic loading experienced by the teeth. The latter effects must, however, be separately evaluated. The effect of tooth accuracy may be determined from Fig. 10.4, which is based on both pitch line velocity and gear quality Qn as specified in Ref. [10.3]. The pitch line velocity of a gear is vt = 0.2618nD (10.20)

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All data in a SQLite database is stored in a single cross-platform file on disk. To work with a SQLite database, you first have to open a connection and specify the database file. When done working with the database, you should close that connection. You ll add two functions to do this:

FIGURE 10.4 Dynamic factors C and K . (From Ref. [10.1].)

U1 U2 U3 U4 U5 U6 R1, R5 R2, R13, R14 R3 R4 R6, R7 CM8880 touch-tone decoder chip BASIC STAMP 2 (original) ISD2590 voice recorder chip LM7486 exclusive OR gate TLC2471I audio amplifier chip LM7805 5-V regulator IC 10-k 100-k 390-k 3.3-k 47-k

vt = pitch line velocity, feet per minute (ft/min) n = gear speed, revolutions per minute (r/min) D = gear pitch diameter, in

Effective and Net Face Widths FE and FN The net minimum face width of the narrowest member should always be used for FN In cases where one member has a substantially larger face width than its mate, some advantage may be taken of this fact in the bending stress calculations, but it is unlikely that a very narrow tooth will fully transfer its tooth load across the face width of a much wider gear At best, the effective face width of a larger-face-width gear mating with a smaller-face-width gear is limited to the minimum face of the smaller member plus some allowance for the extra support provided by the wide face Figure 105 illustrates the definition of net and effective face widths for various cases Rim Thickness Factor Kb.

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