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Decimal and Metric EquivalentsConversion of Small Inch MeasurementsConversion of Small Metric MeasurementsAmerican / Metric Gear EquivalentsFunctions of NumbersTrigonometric Functions & EquationsValues of Trigonometric FunctionsSolution of TrianglesProperties of the circleCircumferences and AreasDimensions of Circular SegmentsFormulas of: Energy, Inertia, Torque, Power & WorkInertia of Round DiscsConversion of SI UnitsMultipliers for SI Units

Hardness Conversion ChartsFastenersStandards for Inch Size ThreadsStandards for Metric ThreadsScrew Head DimensionsStrength of FastenersStrength of Screws and PinsNon-Metallic FastenersHub Fasteners

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θ = Center Angleι = Length of Arc

c = Length of Chordh = Height of segmenta = Area of Segmentr = Radius of Circle

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any components such as clutches, brakes, couplings, drive belts, etc. are used in applicatiohere starting, stopping or reversing of a load is involved. Factors and formulas needed totablish the power requirements are given here.

netic Energy of Relationarting from basic equation

= mV² .........ft lb (1)2

here

is mass = W in slugs i.e. lb/sec²G ft

is velocity in ftsec

W = weight in lbs.G = gravitational acceleration in ft/sec²

(G = 32.2 ft/sec² = 386 in/sec²)

we assume that the entire mass is concentrated at the radius of gyration k then we canbstitute

= 2kπN .... ft where N is in RPM; k is in feet60 sec

ubstituting values for V and G in the basic equation we obtain

= Wk² . N² = Wk²N² ..............ft lb (2)G 182.5 5878

nertia

simple terms, Inertia is the property of a body at rest to stay at rest, or in motion to remaotion.

xpression = Wk² =IG is known as mass moment of Inertia and is given in ft. lb. sec².

G

ften, expression Wk² = I in lb. ft² is used as "moment of inertia in weight units”. It isoportional to IG and its proportionality factor G = 32.2 is often lumped with other constants

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able below tabulates the values of Wk² for commonly used cross sections.

able compiled based on References 1 and 2.

omographs on subsequent pages facilitate conversion of different units of inertia. A table sh

tual inertia values for discs of different diameters.

quivalent Inertiaust be considered when inertia has to be reflected to a shaft which rotates at a different spe

orquea body of inertia IG is accelerated at a constant angular acceleration θ radians/sec² the

ecessary constant torque isT = IG · θ.......... lb.ft (3)

the acceleration speeds up the load ∆ N RPM within t seconds then the angular acceleratione expressed as:

here ∆ω is the change of angular velocity in radians/sec.ubstitution into (3) yields

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ork and Powerork is the product of the magnitude of a force and the distance moved in the direction of thrce Power is the time rate at which the work is performed Unit of power is

nce torque T = P· r. The following table can be constructed. (Note that 1 HP = 745.7 watts.

he functional relationships between power, torque and speed can be illustratively expressedaphs or nomograms as shown on the following pages.

EFERENCES:"The Significance of WK² and How to Calculate it", Product Engineering June 27, 1960 pag

9.ASME Handbook, Engineering Tables, McGraw Hill Co., 1956.Calculating Mass Moments of Inertia" Product Engineering, Jan. 1956 p. 215

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o determine WR² of a shaft or disc multiply numbers given in this table by the length of shaickness of disc in inches.

or hollow shafts or rings, subtract WR² of the I.D. from the WR² of the O.D. and then multipy length or thickness in inches.

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FOR RUBBER AND PLASTICS

CONVERSION ARE APPROXIMATEVALUES DEPENDENT ON GRADES AND CONDITIONS OF MATERIALS INVOLVED

ourtesy of Shore Mfg. Co. New York

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he fasteners most frequently used by machinery designers are screws, nuts, retaining rings rious types of pins because of the basic role that they play In the assembly of all mechanis

here are many instances where these fasteners have been improved by patented innovationnd are familiar to most designers.

Our staff of experienced engineers after careful consideration, compiled in this catalog aoup of fasteners which are most often used by designers of all types of machine devices. Tchnical section on fasteners consists of a number of useful design tables and are presentede following order:

1. ScrewsTable 1. Stress Areas of Unified Screw Threads, UNC and UNF

2. Standards For Inch Size Fasteners3. Standards For Metric Threads4. Screw Head Dimensions5. Max. Torque Values For Fasteners of Different Materials6. Max. Tightening Torques For Hex Socket Head Screw Products7. Torsional Holding Power (in-lbs) For Cup-Point Set Screws

2. PinsTable 8. Shear Strength For Solid Pins

3. Non-Metallic FastenersTable 9. Properties of Zytel and PVC

10. Nylon Thread Rod and Screw Torque Data11. Nylon Nut Torque Data

4. Hub FastenersTable 12. Correlation of Bores and Sot Screw Sizes

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H = 0.86603Ph3 = 0.61343P

H1 = 0.54127P

r = H = 0.14434P

6d2 = d - 0.64953P (Effective-Pitch-Diameter)

D1 = d - 2H1 (Minor Diameter - Internal)

d3 = d - 2h3 (Minor Diameter - External)

D = (Major Diameter)

NOTE:Above limits are based on DIN 13 Sheet 13 for medium tolerance class. Fexternal threads: For internal threads:M1 - Tolerance 6hM1.6 and up - Tolerance 6g

M1 - Tolerance 5HM1.6 and up - Tolerance 6H

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Table 4

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TABLE 5 SUGGESTED MAXIMUM TORQUE VALUES FOR FASTENERS OF DIFFERENTMATERIALS (SCREW STRENGTH)

TABLE 6 SUGGESTED MAXIMUM TIGHTENING TORQUES FOR HEX SOCKET SCREPRODUCTS (SOCKET HEAD STRENGTH)

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he holding ability of an alloy steel setscrew bearing down directly on the shaft is given in Tabarring of the shaft has to be anticipated due to the cup point of the screw.

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TABLE 7 TORSIONAL HOLDING POWER (IN- LBS ) FOR CUP-POINT SETSCREWS

nsnning is a reliable and positive fastening method. The pin can be designed to shear underverload conditions. Straight pins require precision because of their interference fit, whereaspered pins avoid reaming to critical diameter dimensions. The strain on the shaft caused by

ghtly driven taper pin can cause shaft bowing. Roll pins and Spirol pins present an economiclution.The allowable shearing force and torque is given in the following table. It has to be note

at if recommended shaft size is used the shaft strength will be the limiting factor rather thae pin.

TABLE 8 SHEAR STRENGTHS FOR SOLID PINS

his table is calculated based on C1212 and S.S. 18-8 shearing strength of 65,000 psi, and0,000 psi, respectively.

Shear torque values should be divided by a safety factor of 8 to yield recommended workingrques.

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) Nylonylon offers good insulating properties plus resistance to heat, shock, vibration and chemicallvents Also nylon possesses lightness elasticity and superior torque strength Nylon 6/6 is ur 80 or 9O% of all nylon fastener applications. Nylon 6/10 is used for ultraviolet applicationhere high temperatures are Involved Nylon should not be used in mineral acids Also, nylonould be carefully considered for use in direct sunlight application because It has a tendency

xidize and embrittle.

) PVCsed for outdoor weathering, and applications where there are high concentrations of mineraids The prime reason PVC fasteners are used in industry is because of their corrosionsistance to acids.

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Hubs are usually fastened to shafts by means of setscrews, pins or special fasteners.henever the size of hub permits there are 2 setscrews supplied usually 90 apart. The diamethe setscrew used is dependent on the bore size and the configuration of the hub.

The usual correlation of bores and setscrews is shown on Table 12.

Inch SizeSetscrew

Shaft Size MetricSetscrew SizeInch Metric

4-40 .125 3 M2

4-40, 6-32, 6-40 .187 4 M2.5

6-32, 6-40, 8-32 .250 6 M3

8-32, 10-32 .312 8 M4

10-32 .375 10 M5

1/4-20 .500 12 M6

The hub outside diameter should be designed large enough to accommodate a setscrewhich has a length approximately 15 times its diameter. It is a minimum requirement that thtscrew engagement with the hub must be at least as long as the outside diameter of thetscrew.

A patented FAIRLOC® hub fastener is available if phasing, positioning or overload protectrequired. This clamping feature is based on the following principle:

wo slots are machined into the hub, one oriented radially, the other angularly, to create aansverse wedge which remains attached to the solid portion of the hub on one side. Thesultant cantilevered clamping section has a tapped hole to accept a cap screw which passes

rough a clearance hole in the solid portion of the hub, and into a threaded hole in theansverse wedge section. As the screw is tightened the cantilevered section clamps the shaftcurely. The screw can be tightened and released repeatedly without marring the shaft orfecting its torque transmitting abilities.

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