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`Page 1 of 33
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`

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`Twenty-Eighth Edition
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`Page 2 of 33
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`Page 2 of 33
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`

`

`A REFERENCE BOOK
`FOR THE MECHANICAL ENGINEER, DESIGNER,
`MANUFACTURING ENGINEER, DRAFTSMAN,
`TOOLMAKER, AND MACHINIST
`
`Machinery's
`Handbook
`28' Edition
`
`By ERIK OBERG, FRANKLIN D. JONES,
`HOLBROOK L. HORTON, AND HENRYH. RYFFEL
`
`CHRISTOPHERJ. MCCAULEY, SENIOR EDITOR
`RICCARDOM. HEALD, ASSOCIATE EDITOR
`MUHAMMED IQBAL HUSSAIN, ASSOCIATE EDITOR
`
`2008
`
`INDUSTRIAL PRESS
`
`NEWYORK
`
`Page 3 of 33
`
`
`
`Page 3 of 33
`
`

`

`
`
`Fe
`
`COPYRIGHT
`
`—==
`
`COPYRIGHT© 1914, 1924, 1928, 1930, 1931, 1934, 1936, 1937, 1939, 1940, 1941, 1942,
`1943, 1944, 1945, 1946, 1948, 1950, 1951, 1952, 1953, 1954, 1955, 1956, 1957, 1959,
`1962, 1964, 1966, 1968. 1971. 1974, 1975, 1977, 1979, 1984, 1988, 1992, 1996, 1997.
`1998, 2000, 2004, © 2008 by Industrial Press Inc., New York, NY.
`
`Library of Congress Cataloging-in-Publication Data
`
`Oberg, Erik, 1881—1951
`Machinery's Handbook,
`2704 p.
`Includes index,
`
`mmmammm
`
`ee
`
`[, Mechanical engineering—Handbook, manuals, etc.
`[. Jones, Franklin Day, 1879-1967
`II. Horton, Holbrook Lynedon, 1907-2001
`Il. Ryffel, Henry H.1920-_IV. Title.
`TJ151.0245
`2008
`621.8'0212
`72-622276
`
`ISBN 978-0-83 1 1-2800-5 (Toolbox ThumbIndexed 11.7x 17,8cm)
`ISBN 978-0-8311-2801-2 (Large Print Thumb Indexed 17.8 x 25.4 cm)
`ISBN 978-0-8311-2888-3 (CD-ROM)
`
`ISBN 978-0-8311-2828-9 (Toolbox Thumb Indexed /CD-ROM Combo 11.7x 17.8cm)
`ISBN 978-0-831 1-2838-8 (Large Print Thumb Indexed / CD-ROM Combo 17.8 x 25.4cm)
`LC card number 7?-622276
`
`INDUSTRIAL PRESS, INC.
`989 Avenue of the Americas
`New York, New York 10018
`
`MACHINERY'S HANDBOOK
`28™EDITION
`Third Printing
`
`Printed and bound by Thomson Press
`All rights reserved. This book orparts thereof may not be reproduced, stored ina
`retrieval system, or transmitted ing ny§ ay Without permission of the publishers.
`Page 4'of 33
`
`Page 4 of 33
`
`

`

`SHAFT ALIGNMENT
`
`SHAFT ALIGNMENT
`
`Introduction
`Shaft alignmentis the positioning of the rotational centers oftwo or more shaftssothat
`the shafts are co-linear when the machinesare operating. The purpose of shaft alignmentis
`to increase the operating life span of rotatingmachinery and to achieve high motor effi-
`ciency. It is not easy to detect misalignment when machinesare running, but secondary
`effects of misalignment can be observed,:such as excessive radial and axial vibration; high
`temperature in casings, bearings, or lubricant, loose, broken or missing coupling bolts or
`foundation bolts; cracks in shafts;.and excessive amounts of Jubricant leakage.
`There are no universally accepted specifications for shaft alignment, however, there are
`defined limits for shaft-to-shaft alignment of coupled machines. Thelimits are defined in
`terms of two measures of misalignment, angularity and offset.
`—_
`Angular Misalignment.—Angular misalignmentis the difference in the slope of one
`shaft, as. compared to slope of the other shaft. The units are expressed as rise/run.Rise is
`measured in mils (1 mil = 0.001 inch), and the run (distance along shaft) ismeasured in
`inches. Theprocess of correcting this type of alignment problem is sometimescalled gap
`or face alignment.
`ae
`.
`
`Fig. 1. Shafts in Angular MisalignedPosition
`Offset Misalignment.—Offset misalignmentis the distance between the shaft centers of
`rotation measuredatthe plane ofpower transmission or coupling center. The units of mea-
`
`
`surementare mils.
`
` 2526
`
`
`
`Fig. 2. Shafts in Offset Misaligned Position -
`There are fouralignmentparameters to be measured andcorrected; vertical angularity,
`vertical offset, horizontal angularity, and horizontal offset.Values in Table.1 may be used
`as a general guide for acceptable limits of misalignment.:Proper shaft alignmentisespe-
`cially critical when shafts are running at high speeds, thus the allowablelimits ofmisalign-
`mentdecrease-asshaft speeds increase.
`—
`a
`-
`a
`
`| _ Table 1. Misalignment Tolerance Guide
`L
`Offset Misalignment (Mils)
`- Angular Misalignment(mils/inch)
`
`“RPM |
`Excellent
`© | Acceptable
`~ Excellent
`- Acceptable
`|;
`“600
`42.00 “| , . +4.00
`“0.80
`"1,25
`900°
`£1.50 °
`+3.00 0.700
`1.00
`1200 |. #1.25
`2.00 |.
`050 |... 0.80.
`1800 |... 41.0 -.
`Ff
`41.50.
`|
`°030
`...
`0.50
`+£0.50
`.
`40.75
`>. 0.20.
`~ 0.30»
`- 3600-|
`..
`
`© 40.50.
`|
`£0.75 -- 2 0.10:
`0.25
`>4000..;
`
`
`
`
`
`
`
`Page 5 of 33
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`Page 5 of 33
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`

`

`SHAFT ALIGNMENT
`
`2327
`
`Whenthe shafts of two machines require alignment, the process generallycalls for one of
`the machines to be permanently mountedandthe other one to be movable. Thefixedunit ts
`usually the driven machinery, such as the pumpin a pump-motorpair. The second machine
`(usually the motor) is moved into approximate alignment (by eye andstraight edge, tor
`example) in preparation for measurements that will determine the magnitude anddirection
`of moves required to put it in final alignment with the fixed machine. It is the movable
`machine whose shaft will be aligned withthe shaft of the fixed machinery, The position of
`the movable machinets adjusted vertically by adding and/or removing shims from under
`its feet, and horizontally by making small lateral moves as requireduntil satisfactoryfinal
`alignment is obtained.
`
`Shaft Alignment with Dial Indicators
`
`The material that follows describes the process ofshaft alignment when dial indicators
`are used to measure the alignment data.
`Instruments and Methods.—Numbers of instruments are available for making shaft
`measurements and calculating moves. but the most important requirement for anyshaft
`alignment systemis repeatability of the readings. Dial indicators and lasers are two choice
`Measuring systems.
`Dial indicaters provide accurate and reliable measurement of shaft alignment. Theyare
`the most useful because they can be used to measure bearing alignment. shaft runout. and
`sift foot directly. Measurement accuracy downto 0.001 inch (1 mul) may be achieved if
`care is taken in mounting and reading the indicators correctly. and controlling or account-
`ing for such variables as indicator sag, axial endplay in the shaft, and vibration from out-
`side sources. The data obtained from properly installed dial indicators is converted by
`equations described later in this section into the vertical and horizontal movements
`requiredto bring the movable unit into alignment with the fixed unit.
`Laser measurement systems are another popular choice for shaft alignment werk,
`although the cost of such systems is much greater thandial indicators, Accuracy of 0.0001]
`inchor greater 1s possible, and setup and operationts generally faster and simpler than with
`dial indicators. Many laser systems can performsomeor all ofthe calculations required to
`obtain the horizontal and vertical moves. Lasers maynot be safe for use in explosive envi-
`ronments.
`
`Runout Check.—<Arunout test of either or both couplings is important onlyif there 1s a
`runout problem. Seldom will the runout of a pump or motor coupling be enough to detect
`with the eye alone, Standardpractice is to position a rim and faceindicator setup on the
`uncoupled couplings (one at a time) androll said couplings through several 360° turns
`while monitoring the indicators. The indicator bracket shouldbe firmly attached toa static
`object close to the pump or motor coupling being checked. Usually a magnetic base
`designed to hold indicators is used for this purpose if the two couplings involved are more
`than five or six inches apart. For an ordinary pump and motor, however, it
`is frequently
`convenient to mount the indicatorjig to the motorto check the runout on the pumpandthen
`vice-versa for the motor.
`
`Fig. 3 shows aprofile viewon the left and a motor- or pump-eye view(night) ofa lypical
`runout check setup involving the use ofindicators attached to. a magnetic base, Assumethe
`rim indicator to have been adjusted to zero, the coupling being checked is rotated several
`full turns. Repeatedturns deliver repeated readings of a maximumminus of -O.XXX inch
`al one extreme, and a maximum plus of 0.XXX inchat the other extreme, Assuming there
`IS no paint orrust, etc. involved, ut least three possibilities exist.
`L) the coupling was boredoff-center.
`2) the shaft is bent.
`3) a combination ofthe above two conditions.
`
`Page 6 of 33
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`Page 6 of 33
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`

`

`
`
`
`Fig.3. Indicators setup for arunoutcheck.Infield applications, mountthe face
`dial as nearas possible to the rim indicator. The face indicator is drawn atthe6
`o’clock position in both views for clarity.
`Concerning Item 3) in the previous list, it is possible (however unlikely) for a coupling
`that was bored off center and would have shown upas coupling runout with a rim indicator
`test exceptthat a slight bend in the shaft has canceled out what would normally have been
`evidentdueto the off-center bored coupling. This odd situation can cause vibration even
`when a standardtest provesthere isno misalignment. Coupling runout can also be caused
`by too large a coupling bore, with the slack being taken up by set screws.
`Interpreting the Indicators: The actual amount of runoutregistered by the rim indicator
`is halfofthe difference between the plus andminus reading extremes.
`.
`wnin Fig. 3 and set on zero. Then, several full
`Example: A rim indicatoris mounted as sho
`f 0.006 inch and a maximum plus of +0.012
`turns of the shaft reveals a maximum minus©
`nch and half of 0.018 is 0.009. Thus,the
`inch on the indicator. Thetotal variation is 0.018 i
`or 0.018 inch TIR (total indicator
`result of Items 1), 2), or 3) is 0.009 inch of eccentricity,
`unout than is described aboveis
`reading)of coupling runout. Note: Muchless coupling r
`usually expected.
`If the faceindicator showszero at all points around a coupling while the rim indicator
`moves between +0.XXX inch and-0.XXXinch, itis probable that the coupling was bored.
`off-center.If the rim indicator shows practically zero movement while the face indicator
`moves between —0.XXX inch and 40.XXXinch,the cause could be Item 2), or 3) above,
`or the coupling wasboredessentially centered, but at an angle other than perpendicularto
`the face of the coupling,as is shownin Fig.4.
`
`
`
`|
`
`Fig. 4. Coupling Bore Centered but not Perpendicular to Coupling Face
`~ Race Indicator Shown, Rim Indicator Not Shown
`In Fig. 4, both the indicators shown will alternate from plus to minus and back again‘as
`the coupling being checked 1s rotated. Even if the shaft centerline goes through the center
`ofthe coupling,itwill do so atan angle other thanperpendicularto the face ofthe coupling.
`Theresultis serious couplingrunouton the face indicator andless serious runouton therim
`Face runout can easily showup when thereis none. Ifa machinehassleeve bearings and
`if the shaft is not axially restrained by a thrust bearing during the runouttest, severe face
`runout will likely be indicated whenlittle, if any, exists.
`Note: Unacceptable runoutof either or both couplings should beoflittle concern in the
`
`alignment process. The extendedcenterlines of the two shafts can be aligned even when
`
`indicator. re =.
`
`
`
`
`
`
`
`
`Page 7 of 33
`
`Page 7 of 33
`
`

`

`Soft Legs.—Oneof the most often overlooked precautions relevant to motoralignment is
`the firming upofthe soft legs. For the motorin Fig. 5, one leg (D) is 4inch short, In align-
`ment jargon,the short leg is said to be soft. Itis also clear that if a 4 inch shim were placed
`under the short leg, all four motor feet would firmly support the motor. On the other hand,
`if the motor were tightened down without the use of proper shims, its support would be
`very spongyand would produce non-repeatable indicator readings.
`
`1/2" GAP MOTOR BASE
`
`(a)
`
`fb)
`
`SHAFT ALIGNMENT
`
`ao2o
`
`there is serious coupling runout. A runout check is mainly to have recorded informationif
`excessive Vibration occurs.
`
`Page 8 of 33
`
`Fig. 5. Profile (a) and Overhead(b) Views of Motor with Soft Foot
`Onan ordinaryelectric motor any ofthe four motor feet maybe either raised or lowered
`via the placement or removal of shims, as applicable, to render the motor equally supported
`byall four feet. Geometry may allow a certain freedom ofchoice, so it is practical to be
`very selective about which motorfoot or feet will receive additional shims during the firm-
`ing up ofthe motor.
`Whenasoft leg involves only a few thousandths ofan inch, it is much less obvious than
`in Fig. §. By using what is known to some mechanics as the rock-a-bye method, it is possi-
`ble to deteeta slight amount ofinstability in the motor supports. With the bolts inserted, but
`only partly threaded in, alternately apply heel-of-the-hands pressure on or above two
`motor feet at a diagonal. If no rock-a-bye is evident when heel-of-the-hands pressure is
`alternately applied above feet A and D,switch to B and C.If rock-a-bye is found, remove
`applicable shims if possible or add shims under one or bothofthe unstable feet.
`For the inch gap shownin Fig. 5, downward heel-of-the-hands pressure at points A and
`D would yield more movement than the indicators could handle. On moresubtle soft feet,
`it takes an experienced feel to detect only a few mils of rock-a-bye at a motorfoot. When
`feel becomes toolittle to be certain,it is time to applyindicators.
`On units where 0.010 inch or more of movement is evident, a tapered wedge gauge can be
`inserted under the motor foot as the motoris gently rocked. When the motor will no longer
`rock, the approximate thickness of the wedge gauge under the motor foot will be the
`amount ofshim material to insert underthat foot. Ifa single foot requires more shim thick-
`ness than is desirable, put halfthe thickness under the soft foot andthe other half under the
`opposite diagonal foot; then, a second slight amount ofshim placed under one of the two
`feet should remove any unwanted slack. During the rock-a-byetest, trial and error shim-
`ming will eliminate any obvious soft feet in a fewtries. The careful step-by-step elimina-
`tion of unwanted slack in the support feet of a motor or other movable unit should result in
`averystable movable unit.
`On larger motors, leverage proportional to resistance should be used, involving anything
`froma small pry-bar to hydraulics. When the rock-a-bye method gets so involved,it is
`advisable to have dial indicators mounted at the applicable motor feet and/orat the motor
`coupling, with the indicator button on top of the pump coupling or comparable static
`object, to register any movement.
`
`Page 8 of 33
`
`

`

`SHAFT ALIGNMENT
`
`A heavy duty version of the rock-a-bye methodisto haveall the hold down bolts tight and
`then loosen them one ata time while monitoring the indicators.
`
`Profile
`
`
`
`
`
`Tt .
`
`
`
`
`
`
`
`Overhead
`. View
`
` 2530
`
`Fig. 6. Rim Indicator Mountedto Test for Soft Feet
`Fig. 6 showsa profile view (left) and overhead view (right) of the motor previously
`shown.In this figure, the indicatorillustrated is mounted exactly as the rim indicatorwill
`later be mountedfor checking alignment, andanysoft leg activity will register the same as
`in the line-up process. Once a motorgets a cleanbill of health from this soft foot check,it
`is safe to proceed with the normalproceduresof motor alignment. Mountthe indicatorsin
`the most convenient mannerthat will apply to the problem at hand andselect the proper
`formula as discussed in the material that follows. Besure all the bolts are tight before mak-
`ing thefirst (vertical) indicator reading
`Other Mounting Issues: Any combinationof the mounting conditionsillustrated in Fig. 7
`will produce soft motor feet, even-if the motor feet are machined properly, The motor,
`base, or shimswill need alterations to circumventtheillustrated problems. Depending on
`the magnitudeofthe angle in a problem ofthis sort, wedge-shaped shimsor machine work
`on the motororthe base may berequired.
`-
`BC
`Sometimeson relatively unimportant equipment,it is permissible to simply fold shims in
`various thicknessesto take up the slack.This methodshould not be used as common prac-
`tice; but as an emergency measure,it is very effective.
`.
`Co
`
` Dee
`
`.
`Fig. 7. Mounting Conditions ThatProduce SoftMotor Feet. /
`-
`Mounting Dial Indicators, Perpendicular vs. Otherwise—When indicators are
`mountedto get a rim reading on a coupling,the indicator stem should besetto aim straight
`through the centerof the shaft, and at a perpendicular to the.axis of the shaft. This center
`shotat a perpendicular does not haveto be absolutely perfect, butit should be close enough
`so that a closer than casual visual inspection can find no flaw. Thisis close enoughfor prac-
`tical purposes, re
`
`A C
`
`Fig. 8. Indicator Stem Orientation, Correct at A and B, Incorrectat CandD:.-
`
`Page 9 of 33
`
`Page 9 of 33
`
`

`

`
`
`253]
`SHAFT ALIGNMENT
`
`
`In Fig. 8 observethe rim indicator settings at positions A, B,C, and D. Indicators at posi-
`tions A andB are set correctly, indicators at C and D are not. A slight tltin the mounting of
`the indicators will maketoolittle difference to matter. but any tilt over a few degrees
`should be avoided.
`Just as important, the face indicator should be set perpendicularto the coupling face with
`the centerline ofthe indicator stem parallelto the axis ofthe fixed unit coupling shaft.
`Fig. 9a showsa setup with rim and face indicators set at odd angles that will cause incor-
`rect readings. Note the difference between the arrangement ofFig. ga, and the correct one
`shown in Fig. gb.
`
`
`
`ee bh}
`
`Fig. 9a. Incorrect Positioning of Dial Indicators
`Fig. 9b, Correct Positioning ofDial Indicators
`Preparations.—Before starting anal ignmentprocess several importantfactors need to be
`considered, among them the following.Is temperature rise in the coupled machinery acon-
`sideration? Whatis the indicator sag ofthe dial indicators in use? Is coupling runout acon-
`sideration? Are there improperly supported or“soft feet” in the movable machine? Are the
`motor feet, jack bolts, and shims clean? Can the movable unit be moved laterally far
`enough to permit alignment, or is movementrestricted bybolts (“balt bound”) or nearby
`obstructions?Is the driving unit powered off and locked out?
`Thermal Effects: Metals increase in length as temperature increases, and decreasein
`length as temperature decreases, Rotatin£ equipmentat rest slowlyattains the temperature
`of the surrounding environment, the ambient or room temperature. In service, machinery
`suchas electric motors and fuel-burning engines generate heat and increase in temperature
`during operation; other machinerysuch as pumps may warmor cool during operation.
`If initial alignment adjustments are made when machinesare al ambient or room temper-
`ature, thermal movementwill occur in various parts of the machines as they reach operat-
`ing temperature. The various dimensions will not increase or decrease uniformly. In a
`motor-pump combination, for example, the motor shaft height above the base may
`increase while the pumpshaft height may decrease.
`The amount of thermal expansion canbe estimated by the formula Ae = HAT:
`where 4e = changein height ofshaft
`ff =Vvertical height or distance between shaft centerline and shims
`= expansioncoefficient of materials in Uin/inch-°F (forstainless steel= 7.4, mild
`steel= 6.3. cast iron = 5.9, bronze=10, and aluminum=12.6)
`AT =the difference between operating temperature and ambient(initial measure-
`ment) temperature
`Example Ia):A pumpis to beinstalled andal igned with a motor, The cast iron pump
`delivers fresh water at 34 °F andis at present at 75 °F. The pump shaft centerline is 12
`inches above the baseline of the pump. The carbon steel motoris also at 75 °F and is
`expected to rise to 140 °F whenin operation. The motor shaft centerline js | 2 inches above
`the base ofthe motor. At operating temperature, compare the expected thermal growthof
`the pump and motorshaft centerlines.
`For the pump, the change in shaft height:
`Ae = aHAT = 0,0000059 x 12 x (34 — 75) = —0,002903 inch
`
`eee
`
`Page 10 of 33
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`Page 10 of 33
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`

`

`
`
`
`
`EESOo
`
`2532
`
`SHAFT ALIGNMENT
`
`For the motor, the changein shaft heightis:
`Ae = aHAT = 0.0000063 x 12 x (140-75) = 0.004914 inch
`These calculationsindicate that the pump and motorshafts, if they were in alignmentat
`ambient temperature, would be misaligned at operating temperature by approximately
`0.0078 inch difference in elevation.
`Indicator Bracket Sag: Indicator sag,indicator bracketsag, or jig sag are all terms com-
`monly usedto describe the effect on indicator readingsofthe weightofthe dial indicator(s)
`in combination with the length, weight, and orientation of the indicator bracket. Dial indi-
`cators are designedto be usedin the vertical position and indicator bracketsag is especially
`significant in measurements that are made whenthe dial indicatoris inverted in the vertical
`plane. Considera rim indicator and bracket mounted on a shaft with the indicator zeroed at
`the 12 o'clock position; when the shaft andfixture are rotated to put the dial indicatorin the
`6 o'clock position, the reading will indicate a non-zero negative value, whichiis the indica-
`tor fixture sag factor.
`Indicator bracket sag is dependent on the mounting arrangementofthe indicators, andis
`difficult to measure accurately on equipmentthat is being aligned becausetheeffect of
`shaft misalignment will combine with the indicator bracket sag to produce incorrect
`results.
`To measure indicator fixture sag, set up the indicator and mounting components on the
`machinery to be aligned exactly as if doing alignment, and tighten everything down.Then,
`removethe bracketandindicator from the machine and remountin exactly the same man-
`ner on a rigid fixture, such as a piece of pipe supported by V-blocks. Zero the indicatorat
`the 12 o’clock (reference) position, then without changing the setup carefully rotate the
`fixture and read the indicatorat the 6 o’clock (reading) position. At the reading position,
`the indicator displays the total indicator reading (TIR) and this valueis the total sagfactor.
`The actual sag in the indicator bracket is equal to one half of the total indicator reading,
`Whenthe indicator bracket sag has been determined,it can be accounted for in measure-
`ments taken during the alignment procedure. One procedureis to add the indicator bracket
`sag factor to the indicator value whenthe indicatoris “zeroed”at the reference position, so
`that the sag factor is accounted for throughout subsequentcalculations. For example, if an
`indicator is zeroedat the 12 o’clock position and reads 0.006inchat the 6 o’ clock position,
`set the indicatorto positive 0.006 at the 12 o’clock referenceposition to accountforthe sag
`factor in further measurements.If the reference position used for checking indicatorsagis
`the 6 o’clock position (indicator zeroedat 6 o’clock position), the positive reading foundat
`the 12 o’clock position is the sag factorthat must be subtracted from indicator value when
`the indicator is zeroed at the 6 o’clock (reference) position.
`Alignment Procedures for Machinery.— Thefaceand rim method and the reverse dial
`indicator method are the techniques most commonly used for aligning machinery shafts.
`The usual shaft alignment procedureis to establish one machineasfixed, and the other as
`the movable machine. The driven machinery is usually the fixed unit. The shaft of the mov-
`able unit is positioned, as required,to align with the shaft of the fixed unit. Mostaligning
`specialists recommend vertical alignmentfirst, and then horizontal alignment. It is impor-
`tant to verify in advancethat the movable unit has sufficient horizontal clearanceand free-
`dom of movementto obtain the required horizontal position before starting on the vertical
`alignment.
`Vertical Moves: Vertical adjustments are accomplished by adding or removing shims
`from underthe.machinefeet. Use as few shimsas possible. Too many shims undera foot
`may causeit to actlike a soft foot by creating a spring effect; usually a maximum offour
`shims are allowed. Shims should be measured by micrometerbefore placing. If possible,
`apply a single shim thatis the total thickness required under the foot. Insert the shimsall the
`way in until the shim slot bottoms out on the bolt, then pull the shim back about a quarter
`inch before tightening thebolts. If alignmentis not possible with four shims,then use fewer,
`
`Page 11 of 33
`
`Page 11 of 33
`
`

`

`SHAFT ALIGNMENT
`
`amounting to the required thickness. Tighten bolts to their prescribed torque each time after
`placing the shims to avoid any movement when working on the other side of the machine.
`Neverloosen all hold down bolts at the same time. A maximumoftwo bolts are allowed
`to be loosened at a time. Loosening all hold down bolts will lose the entire alignment.
`Loosen the bolts from either the left or right side of the machine. Then, raise that side just
`enough to make the shim change. Raising the machine too high can bendthe foot. Once the
`machine is lifted. remove all shims and add or subtract the number of shims required to
`make the necessary vertical move. Be very cautious al this point not to get confused among
`alot of loose shims.
`
`2533
`
`Page 12 of 33
`
`Hortzontal Moves: | is preferable to utilize a base plate with jackbolts for horizontal
`moves. Ifjack bolts are not available, a small hydraulic jack, pipe clamps, or pony clamps
`can be used. The most accurate method for measuring the horizontal moveis to place dial
`indicators around the machineat convenient locations, such as at machinefeet. The indica-
`tors can be located anywhere convenient as long as the dimensions used in the alignment
`calculationsreflect the actual position at which measurements are made. When the indica-
`tors are mounted, adjust the dials to zero, and move the unit the distance and direction indi-
`cated by the calculations. Once the horizontal move has been completed, a final set of
`readings should be takento verify both vertical and horizontal alignment.
`Safety: Shaft alignment should not be performed when machines are running. Before
`shaft alignment, all sources of powerto the machine should be off and verified. Energy
`sources must be locked out byelectrical controls; steam valves, gas main valve, and fuel oil
`valve must be shut down before shaft alignment.
`Rim and Face Alignment Procedure.—Figs. 10 and 11 showdial indicator arrange-
`ments forrim and face alignment that are typical of those used in the remainder ofthis sec-
`tion. Fig. 10 illustrates a chain indicatorjig, but it could be of any type. The arrangement in
`Fig. 11 represents an equivalent setup. In each figure, two dial indicators are shown, one
`for the rim reading and the otherfor the face reading. Darkened squares, trianglesor circles
`are simply to indicate attachment points.
`
`
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`Fig. V1
`Fig. 10.
`Starting on page 2537. a number ofdifferent indicator arrangements are il/ustrated in
`Figs. 1athrough 16a. Each arrangement 1s associated with a specific equation and a chart
`that facilitates understanding the dial and face readings and the corresponding tasks of
`determining where shims need to be added or removed and what horizontal moves are
`required, To use this system, the mechanic needs to set up the rim and face indicators in the
`most Convenient manner, then turnto the figure of the matching indicator arrangement and
`use the formulas provided.
`Example Aligning a Motor with a Pump by the Rim and Face Method: A \0-horsepower
`electric motor needs to be precision aligned to a specific pump. Both the pump and motor
`are to be mounted on a base that when finished will look similar to Fig. 12. Not shown are
`the intake and discharge piping. electrical fixtures, and other incidentals including shims
`under the motorfeet.
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`Page 12 of 33
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`2534
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`SHAFT ALIGNMENT
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`The shimsare omitted to visually explain why the miotorwillusually havealittle less dis-
`tance from the motor shaft centerline to the base than the pumphas.Thisset up is desirable
`because with the motor shafta little lower than the pumpshaft, the motor can be shimmed
`
`up until both shafts share a common elevation.If the motorshaft is higher than the pump
`
`shaft, it can be very difficult to alter the position of the pumpbecauseof the rigidly con-
`
`nected piping.
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`Spool Piece
`
`Fig. 12. Pump and Motorare to be Aligned
`The motorin Fig. 12 isin its approximate finished position about8 inches from thepump.
`The spool piece shownin Fig. 12 is to be bolted between the motor and pumpcouplings
`after the alignmentis complete. The spool piece (not shownin Fig. 13) 1s 8 inches long and
`there's an 8inch space between the pump and motor couplings.
`Fig. 13 showsa viable mounting of dial indicators in the process of procuring readings
`from the zerosetting at 12 o’clock (broken lines) to the 6 o’clock position (solid lines).
`Somecalibrated eyeballing, a scale measure and some straight edging are usedto align the
`motorinitially to the pump.
`oo
`.
`face
`indicator
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`iM gts
`indicator
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`Fig. 13. Alignment Setup for Pump and Motor
`There are many ways to mountand adjust dial indicators to measure the remaining mis-
`alignmentbetween the two units. Several are correct and only a few are optimum. The
`mounting of the pair of dial indicators between the:motorand pump showninFig.13 is as
`good as any and commonly used. Many other-arrangements are shownstarting on
`page 2537.
`.
`Althoughthere seem tobefour dial indicators inFig. 13, there are only two. The two indi-
`cators with broken lines are drawnat theinitial 12 o’clock position where they are zeroed
`with about half the indicator stems exposed, (both indicator pointers are shownat 12
`o’clock). Then the motor and pump shafts are both turnéd 180°. to the 6 o’clockposition
`(those indicators are drawn with solid lines, and the pointers are shownsetto the 3 o'clock
`and 9 o’clockpositions in Fig. 13). Inreallife alignments, the pointers mightbe aimed any-
`where on the dial face, but the dial face will rotate 360°, so the zero can be manually
`adjusted to align with the pointer no matter which direction the needlepoints.
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`Page 13 of 33
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`Page 13 of 33
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`SHAFT ALIGNMENT
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`2535
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`Solution for Vertical Alignment: Once a motorhas been aligned with straight edges and
`such, it is probably close enough to use dial indicators, The dials most often used have a
`stem range ofjust over 0.200 inch (roughly inch), These dial indicators (usually two) are
`positioned with the buttonsofthe indicators against the rim and face of the pump coupling
`respectively, as shown in Fig. 13. The seasoned millwright/mechamic will adjust the indi-
`cator jig/bracket in such mannerthat the stem on eachof the indicators has freedomto
`travel inward or outward about 0.100 inch. This adjustment is made at the 12 o'clock posi-
`tion, shown by broken lines in Fig. 13.
`A good arrangement is for the rimindicatorin Fig, 13 to register a minus rreading at the
`6 o'clock position and theface indicatorto register a plusfreading (see bottomright ofFig.
`ib on page 2538). Readings on both indicators showthat the motor needs to be raised,
`involving the simple task of determining how much shimmaterial to add undereachfoot.
`For the indicator arrangementin Fig. 13, the required shim thickness can be determined by
`using the equations below,
`
`I+
`pa it , 2f* B
`RI
`A
`
`ba
`
`ry
`+ I+a7
`+=
`!
`ba
`
`bie
`
`and
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`R=
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`Page 14 of 33
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`where F = tchange in shimthickness needed under the front feet
`A =+changein shimthickness needed under the rear feet
`r=plus or minus rim indicator reading
`f=plus or minus faceindicator reading
`A =diameterofface indicator path on coupling
`#8 =distancefrom rimindicator path tofront feet
`C =distance from rimindicator path to rear feet
`The equations use the gathered data to calculate the correct shim placement. With either
`equation, a positive solution indicates that shims equal to the calculated value are added,
`and a negative solution indicates that shims equal to the calculated value are removed.
`The rim and face indicator setup depicted in Fig. 13 is one of the sixteen arrangements
`describedin the material that follows. Each ofthese formats has its own similar bul unique
`formula; just plug the variables into the formulas that matches the current indicator formal
`and calculate the shims required.
`Solution for Horizontal Alignment: Fig, 14 showsatop viewofthe motor in Fig. 13, with
`indicators in the reading positions for horizontal alignment. Therim and face indicators are
`zeroedat the position 180° opposed to that shownin Fig. 14.
`The directions corresponding to horizontal movement ofthe motorin Fig. 14 are indi-
`cated by east and west arrows. Magnetic-mount dial indicators (not shown) may be set up
`to monitor the horizontal movements. The dimensions 8 and Crepresent the distances
`from the rimindicator path to the locations of the