$70 
 
 NRLF 
 
 B M S3D MSS 
 
GIFT OF 
 Arthur E. Moncaster 
 
 
 
 
e 
 
 Westinghouse-Parsons 
 Steam Turbine 
 
 A description, 
 
 with suggestions and instructions 
 for its 
 
 INSTALLATION 
 
 CARE AND 
 
 OPERATION 
 
 ENGINEER'S REFERENCE BOOK 
 
 Please keep this book where your engineer can refer 
 
 to it readily 
 
Instruction Book WM 103 
 
 The West i n 2h ouse 
 
 TFe 
 
 Westinghouse-Parsons 
 Steam Turbine 
 
 A description, 
 
 with suggestions and instructions 
 for its 
 
 INSTALLATION 
 
 CARE AND 
 
 OPERATION 
 
 EAST PJTTSBUR.O,I>A. 
 
\i J 
 
TABLE OF CONTENTS 
 
 iHHH 
 
 I. 
 
 INTRODUCTION. 
 
 II. 
 THE FUNDAMENTAL PRINCIPLES OF A STEAM TURBINE. 
 
 III. 
 THE WESTINGHOUSE-PARSONS STEAM TURBINE: 
 
 ROTOR 
 
 CYLINDER 
 
 THRUST BEARING 
 
 MAIN BEARINGS 
 
 GLANDS 
 
 GOVERNOR 
 
 VALVE GEAR 
 
 OILING SYSTEM 
 
 AUTOMATIC SAFETY STOP 
 
 AUTOMATIC THROTTLE VALVE 
 
 COUPLING 
 
 IV. 
 
 OPERATING SUGGESTIONS. 
 
 V. 
 
 CONDENSERS. 
 
 VI. 
 
 OILS. 
 
 VII. 
 
 METHODS OF CONNECTING UP GLANDS AND OIL COOLING 
 
 COILS. 
 
 VIII. 
 FOUNDATIONS. 
 
 726306 
 
INTRODUCTION 
 
 While the turbine is simple in design and construction, 
 and does not require constant tinkering and adjustment of 
 valve gears, or taking up of wear in the running parts, it is 
 like any other piece of fine machinery, in that it should receive 
 intelligent and careful attention from the operator by inspection 
 of the working parts that are not at all times in plain view. 
 Any piece of machinery, no matter how simple and durable, if 
 neglected or abused, will in time come to grief, and the higher 
 the class of the machine, the more is this true. 
 
 The experienced engineer understands, in a general 
 way, the principles and operation of almost any piece of 
 apparatus that he may come across in the power house. At 
 the same time there are points about any new machine that he 
 has to learn, either from his own experience or the previous 
 experience of others, and the latter supplemented and confirmed 
 by the former, is perhaps apt to be the least costly. In the 
 case of the ordinary large size reciprocating engine, where it is 
 almost never run and sometimes not even assembled in the 
 shop, the operating engineer can often tell the builders more 
 about the care and operation of the engine than they are able 
 to tell him; but in the case of the turbine, which is not only 
 assembled but is thoroughly tested and operated for some time 
 in the shop, the builders have had continued and varied 
 experience under all sorts of conditions, and are, therefore, in a 
 position to give advice in regard to its operation and mainte- 
 nance. 
 
 The object of this pamphlet is to cover in a general 
 manner the principal features of construction and methods of 
 operation common to all Westinghouse turbines, the details 
 occasionally met with in special types being described in a 
 separate pamphlet covering each particular case. 
 
 5 
 
II. 
 
 Fundamental Principles of a Steam Turbine. 
 
 Any steam turbine depends for its operation upon the 
 effect of steaui being caused to expand through suitably formed 
 passages, thereby attaining a velocity. The steam then 
 impinging upon suitable buckets gives up the energy due to 
 velocity and thus gives motion to the rotating element of the 
 turbine. In some cases the steam expands through passages 
 which are themselves capable of movement, in which case the 
 effect of velocity is to give motion to the rotating element by 
 reason of reaction. 
 
 In the Westinghouse-Parsons turbine use is made of 
 each of the two effects. A general idea of the turbine blades 
 may be gathered from the diagram, Fig. i, in which both 
 stationary and moving blades are shown in their respective 
 location to one another. 
 
 ELEMENT A 
 
 ELEMENT B 
 
 NARY BLADES 
 
 MOVING BLADES 
 
 J) J) J) J) J) J )) D )) 
 
 BLADES 
 BLADES 
 
 Fig. 1 
 
 The steam in passing through row i, falls from pressure 
 P to pressure P^ In thus expanding it does work upon 
 itself and attains a velocity, the energy of which is given upon 
 the moving blades, row 2. Again, in the passage of steam 
 through the blades of row 2, the pressure falls from P : to P 2 . 
 This expansion again produces a velocity, but this time its 
 effect is to react on row 2. This cycle is repeated a number of 
 times until exhaust pressure is reached. 
 
III. 
 
 The Westinghouse-Parsons Steam Turbine. 
 
 Figure 2 is a sectional view showing the construction 
 of the Westinghouse-Parsons straight parallel flow steam 
 turbine. While the different types vary somewhat in minor 
 details, the principle of operation remains the same. Steam 
 enters through the strainer S, passes through the main 
 admission valve, into the turbine at A. After expanding 
 through the cylinders R x , R 2 , R 3 , it passes down the exhaust 
 chamber D to the condenser. The admission of steam is 
 regulated by the valve V actuated by the governor G, driven 
 by the worm wheel at the end of turbine rotor. 
 
 There are two distinct types of steam turbines built by 
 the Westinghouse Machine Company the straight parallel 
 flow Westinghouse-Parsons steam turbine as shown in Figure 2, 
 and the Double Flow Westinghouse steam turbine, Figure 3. 
 As the latter is a development of the former, especially suited 
 for handling large volumes of steam, but having the same 
 elements of construction such as rotor, cylinder, governor, etc., 
 and is operated in practically the same manner, it is treated as 
 a special case and the details of design such as direction and 
 regulation of flow of steam are discussed in a separate 
 pamphlet. 
 
 The principal elements of construction are taken up as 
 follows : 
 
 Rotor: 
 
 This is shown at R, P, Figure 2. The parts R x , R 2 , 
 R 3 , consist of steel drums mounted upon a spindle, in which 
 are inserted rows of blades or vanes, by means of which the 
 rotative effort imparted by the steam is received and transmitted 
 to the rotor. On the opposite end of the spindle and corre- 
 sponding to each diameter, R, are balance pistons Pj, P 2 , P 3 , 
 of such diameter as to exactly balance the axial pressure on the 
 drums R 1? R 2 , R 3 , the different pressures at either end of the 
 respective drum diameter being communicated to the corre- 
 
10 
 
spending piston faces by means of the passages EI, E 2 , Es, 
 as shown. These balance pistons have a number of grooves 
 cut in their faces, into which mesh corresponding collars in the 
 cylinder, thereby effectively preventing leakage, although they 
 run without actual metallic contact. 
 
 Cylinder: 
 
 The rotor revolves in the stator or stationary cylinder, 
 which has rows of guide blades corresponding to those in the 
 spindle, but set in reverse position. (See Fig. i.) Also placed 
 in the cylinder, at the section occupied by the balance piston, 
 are collars or strips, which fit into the grooves in the balance 
 pistons on the spindle as referred to above. By means of 
 aligning bearings, T T , T 2 , Figure 2, the spindle is held in 
 such a position that the sides of the grooves in the balance 
 piston are close to the strips in the cylinder, but not close 
 enough to touch them, thus preventing the passage of any 
 appreciable amount of steam without rubbing contact between 
 the adjacent surfaces. 
 
 Referring again to Figure 2, which represents the 
 typical Westinghouse-Parsons turbine in sizes from 300 to 
 3000 Kw., it will be noticed that there are three large changes 
 in the diameter of the working portions of the spindle and 
 cylinder. These are commonly referred to as the different 
 cylinders of the turbine, being respectively the high pressure, 
 the intermediate pressure and the low pressure cylinders, 
 starting with the smallest diameter at RI, R_> being the inter- 
 mediate and R 3 the low pressure cylinder. It will be noticed 
 that each cylinder is further divided into small steps, each one 
 of these latter having blade rows of the same height. Each of 
 these steps is known as a barrel, there being usually three to 
 five of these in each of the cylinders, and anywhere from one 
 to twenty rows in each of these barrels. In the event of any 
 correspondence relating to blading, it is customary to refer to 
 any particular row of blades as the ist, 2d, 3d, or otherwise 
 row in the ist, 2d, 3d or otherwise barrel in the high pressure, 
 intermediate or low pressure cylinder of the spindle or cylinder, 
 as the case may be, counting from the high pressure end. 
 
 11 
 
12 
 
Thrust Bearing: 
 
 The aligning or thrust bearing is made up of two parts 
 T!, T>, each consisting of a cast iron body in which are placed 
 brass collars. (See Fig. 4.) These collars fit in grooves C, cut 
 in the shaft as shown. The halves of the block are brought 
 into position by means of screws Si, S 2 , acting on levers Li> 
 1,2, mounted in the bearing pedestal and cover. It will be 
 seen that, by turning the screw inwards, the half of the block 
 that it acts on is moved in the opposite direction, and that 
 the spindle cannot move beyond that point. 
 
 The screws are provided with graduated heads, which 
 permit the position of the respective halves of the thrust bear- 
 ing to be set to one-thousandth of an inch. The arrangement 
 of each screw is similar to the familiar micrometer. 
 
 The upper screw S 2 , is set so that when the rotor exerts 
 a light pressure against it, the grooves in the balance pistons 
 just escape coming in contact with the strips in the cylinder. 
 The lower screw Si, is adjusted to permit about eight one- 
 thousandths to ten one-thousandths of an inch freedom for the 
 collars C, between the thrust bearings. 
 
 The alignment bearings are carefully adjusted before 
 the machine leaves the shop and, to prevent either accidental 
 or unauthorized changes of their adjustment, the adjusting 
 screw heads are locked by the method shown in Figure 4. It 
 will be observed that the screw cannot be revolved without 
 sliding back the latch L 3 . To do this the pin P 4 , must be 
 withdrawn, for which purpose the bearing cover must be 
 removed. 
 
 In general, this adjustment should not be changed 
 except in some special case where there has been wear of the 
 collars in the alignment bearings. Nevertheless, it is a wise 
 precaution to go over the adjustment at intervals. The method 
 of doing this is usually as follows: The machine should have 
 been in operation for some time so as to be well and evenly 
 heated and should be run at a reduced speed, say 10% of the 
 normal speed, during the actual operation of making the adjust- 
 ment. Adjust the screw, which, if tightened, would push the 
 
 13 
 
spindle away from the thrust bearing towards the exhaust. 
 This, in some type of machines might be the upper screw and 
 in others the lower screw; as shown in Figure 4 it is the upper 
 screw. Find a position for this, such that, when the lower 
 screw is tightened, thus drawing the spindle towards the 
 governor end, the balance pistons can just be heard coming in 
 contact, and such that the least change of position inwards of 
 the upper screw will cause the contact to cease by forcing the 
 spindle towards the exhaust end as evident from Figure 2. 
 To hear if the balance pistons are in contact, a short piece of 
 hard wood should be placed against the cylinder casing near 
 the balance pistons. If one's ear is applied to the other end of 
 the piece of wood, the balance pistons can be heard when in 
 contact with the strips in the cylinder. The lower screw 
 should then be loosened and the upper screw advanced six one- 
 thousandths, at which position the latter may be considered to 
 be set. The lower screw should then be advanced until one- 
 half of the thrust pushes the rotor against the other half of the 
 thrust bearing, and from this position it should be slacked 
 back ten one-thousandths to give freedom for the rotor between 
 the thrusts and locked. 
 
 Great care must be exercised in this operation, in 
 determining when the collars of the balance pistons are just in 
 contact. Gentle pressures only must be exerted in adjusting 
 these screws or the parts will be strained, giving an erroneous 
 setting. This contact should be only momentary, and the 
 screw should be released just as soon as the rubbing is heard. 
 
 The above mentioned dimensions of clearance apply 
 only to turbines up to 1000 Kw. Special settings are generally 
 used in larger sizes. 
 
 The object in view is to have the grooves of the balance 
 pistons running as close as possible to the collars in the 
 cylinder, but without danger of their coming in actual contact 
 and to allow as little freedom as possible in the thrust bearing 
 itself, but enough to be sure that it will not heat. The tur- 
 bine rotor itself has scarcely any end thrust, so that all the 
 thrust bearing has to do is to maintain the above described 
 adjustment. 
 
 14 
 
Some machines are provided with a thrust-bearing, 
 having both adjusting screws on the upper cap, facilitating the 
 operation of adjusting the thrust blocks. However, the 
 same precautions and directions given in connection with 
 Figure 4, apply to this bearing, as it differs only in arrange- 
 ment of details. 
 
 The principal feature wherein it differs from Figure 4 is 
 the position of lever for adjusting the lower half of the bear- 
 ing. Instead of engaging in the bottom of the bearing and 
 requiring adjustment in the lower part of the pedestal, the 
 lever consists of two arms which span the upper bearing and 
 engage in recesses at the side of the lower bearing so that it is 
 adjusted from above. The two adjustment screws are so 
 located that both may be conveniently regulated at the same 
 time, by adjusting one with either hand. In most cases the 
 inner adjustment screw, that is the one nearer to the turbine 
 casing, controls the upper thrust block, while the outer regu- 
 lates the lower block. 
 
 The lock slide (L 3 ) is held in place by a screw which 
 in turn is prevented from becoming loose by being drilled to 
 receive two cotter pins, one on each side of the slide. 
 
 Main Bearings: 
 
 The bearings which support the rotor of the smaller 
 machines running at 3,600 r. p. m. are shown at B, B, Fig. 2, 
 and in detail in Fig. 5. The bearing proper consists of a brass 
 tube, B, Fig. 5, with suitable oil grooves. It has a dowel arm 
 L, which fits into a corresponding recess in the bearing cover, 
 to prevent the bearing from turning. Around this tube are 
 three concentric tubes, C, D, E, each one fitting over the other 
 with some clearance, so that the bearing itself is free to move 
 slightly in any direction. These tubes are held in place by 
 the nut F, and this nut in turn is held by the small set screw 
 G. The bearing with the surrounding tubes is placed inside 
 of the cast iron shell A, which rests in the bearing pedestal on 
 the blocks and liners H. The packing ring M, prevents the 
 leakage of oil past the bearing. Oil enters the chamber at one 
 
 15 
 
16 
 
end of the bearing and passes through the oil grooves lubri- 
 cating the journal, and then out into the reservoir under the 
 bearing. The oil also fills the clearance between the tubes 
 and forms a cushion which dampens any slight vibra- 
 tions. The bearings, therefore, absorb any vibration that 
 might occur. 
 
 In some cases the bronze tube B is lined with babbitt, 
 giving a babbitt bearing surface, while the rest of the bearing 
 parts remain the same. 
 
 This type of bearing with its nest of tubes is required 
 only in high speed machines where the bodies revolve above 
 the critical speed, the tubes permitting the revolving element 
 to tend to revolve about its gravity axis rather than about its 
 geometric axis. The results are the same as were obtained 
 later by Dr. De Laval by means of his flexible shaft. 
 
 In the larger machines running at 1,800 r. p. m. or less, 
 a babbitted bearing is usually employed. This type of bearing 
 is shown in Fig. 6, being divided longitudinally in the 
 usual manner. It is also self-aligning, and is supplied with 
 oil at the center through suitable passages, discharging at 
 each end. 
 
 This bearing consists of two cast iron shells, A and B, 
 Fig. 6, lined with babbitt and held together by the bolts C C 
 and supported by the blocks and liners H. H. The babbitt is 
 bored out slightly larger than the shaft, and further bored 
 along the sides so that the horizontal dimension of the bore is 
 somewhat greater than the vertical, thus giving close contact 
 along only about two-thirds of the bottom half of the circum- 
 ference, allowing ample room for oil to produce perfect lubri- 
 cation. The oil enters at the point D and passes around the 
 passages E, E, coming into the bearing at F. 
 
 The outer shells of both types of bearings are provided 
 with four recesses, in which are fitted keys, as shown at H, upon 
 which the bearing is carried in the pedestal. These keys have 
 a number of sheet metal liners behind them by means of which 
 accurate adjustment may be made of the bearings to give any 
 desired adjustment of the revolving part with reference to the 
 
 17 
 
Fig. 6 
 
 18 
 
stationary part. These liners are arranged in combinations to 
 permit adjustments to be made in increments of five one- 
 thousandths of an inch. 
 
 Glands: 
 
 On either end of the turbine spindle at W W, Fig. 2, 
 are located the water sealed glands to prevent air leaking into 
 the turbine when running condensing and to prevent steam 
 blowing out when operating with atmospheric or greater press- 
 ure at the exhaust. 
 
 Referring to Fig. 7, the sealing water is supplied to the 
 glands through passage A in the turbine casing to chamber 
 B, in which the runner C revolves with the turbine shaft. 
 This runner is designed to be capable of pumping to a pressure 
 of about thirty-five pounds if it were furnished with water at 
 its inner radius, so that when water is supplied to its periphery 
 at twenty pounds absolute, or say twenty pounds greater than 
 the pressure within the turbine, this water is unable to flow 
 into the turbine by reason of the pumping effect of the gland 
 runner in the opposite direction. Thus there is maintained at 
 the outer edge a solid annulus of water of a pressure greater 
 than the pressure the gland has to pack against, producing a 
 hermetic seal entirely precluding the passage of air. 
 
 The spindle gland sleeve E, which is shrunk on the 
 shaft and doweled at H, consists of a bronze ring provided with 
 grooves. This gland sleeve has a running clearance between 
 it and the casing F, and acts as a labyrinth packing to prevent 
 excessive leakage along the shaft while the turbine is operat- 
 ing slowly. What slight leakage there may be is taken care 
 of by the drain pipe K. This should be a free drain, and at 
 all times maintained clear, otherwise water may leak through 
 the oil ring into the bearing chamber, and contaminate the 
 oiling system. 
 
 A pipe G is provided at the inner side of the gland for 
 the purpose of draining away any leakage to the exhaust pipe 
 and preventing it from splashing on the revolving rings of the 
 turbine. 
 
 19 
 
20 
 
The outer flange is to prevent any leakage from the 
 shaft being thrown off into the engine room. 
 
 A gauge at D indicates the pressure at the outer edge 
 of the glands, so that it may be known whether or not the 
 water supply is being properly maintained. 
 
 Suggestions regarding various methods of connecting 
 the water supply to these glands are given in the latter part of 
 this pamphlet. 
 
 In the case of low pressure turbines where it is neces- 
 sary to obtain a vacuum before the spindle is revolved, a special 
 type of gland is furnished, as described elsewhere, in connec- 
 tion with low pressure turbines. 
 
 Governor : 
 
 Fig. 8 shows a section of the Westinghouse-Parsons 
 flyball type of governor used in conjunction with poppet valves 
 and steam relay mechanism for controlling the admission of 
 steam. 
 
 Keyed on the end of the turbine shaft is a steel worm 
 driving the bronze worm wheel A. This gear A drives the oil 
 pump crank C and transmits its motion by means of a bevel 
 gear and pinion to the governor spindle, D. On this spindle 
 is keyed the governor arm which carries the balls W W, the 
 levers N N being mounted on knife edge pins. On the ends 
 of these levers are rollers which support a roller ring and ball 
 race upon which the governor spring S acts. The object of 
 this arrangement is to allow adjustment of the governor while 
 the turbine is running; by lightly grasping the sleeve locking 
 plate G, the tension sleeve, spring and spindle sleeve collar 
 are brought to rest, and the governor balls are still free to 
 revolve on the above mentioned ball thrust bearing. 
 
 Therefore, to vary the speed of the turbine, hold the 
 tension sleeve nut G with one hand, and with the other loosen 
 the locknut K a sufficient amount to disengage the pin in the 
 locking plate from slot in G. Then adjust the sleeve nut until 
 the speed has been changed the desired amount. In this 
 manner adjustments of speed are made without interfering 
 
 21 
 
GOV. SPINDLE CAP 
 
 QOV.TENSION SLEEVE 
 
 GOV. TENSION SLEEVE LOCK NUT 
 
 GOV.TENSION SLEEVE LOCKING PLATE 
 
 QOV.TENSION SLEEVE NUT 
 
 GOV. CASE 
 GOV. BALL LEVER 
 
 GOV.CASE STAND 
 GOV.CLUTCH SLEEVE RING, UPPER 
 
 GOV.ROCKER ARM 
 GOV.ROCK SHAFT BRACKET CAP 
 
 GOV.CLUTCH LEVER LINK 
 
 GOV.CLUTCH DISTANCE PIECE 
 
 GOV.CLUTCH SLEEVE RING. LOWER 
 
 GOV.ROCK SHAFT BRACKET 
 
 GOV.CLUTCH SLEEVE NUT 
 
 GOV.STARTING TRIGGER 
 
 GOV.STARTING TRIGGER BRACKET 
 
 GOV.SPINDLE BUSHING.UPPER 
 
 GOV. SPINDLE 
 GOV.THRUST BEARING RING.UPP 
 
 " INTERMEDIATE 
 .. LOWER 
 
 GOV. SPINDLE BUSHING, LOWER 
 GOV. BEVEL PINION 
 
 GOV.SPINDLE WASHER 
 
 GOV.WORM WHEEL SHAFT CAP 
 
 GOV.WORM WHEEL SHAFT BUSHING, SMALL 
 
 GOV. BEVEL GEAR 
 
 SECONDARY LEVER 
 
 GOV.SPRING 
 
 GOV.SPINDLE SLEEVE 
 
 GOV.SPINDLE SLEEVE COLLAR 
 
 GOV. BALL RETAINER RING 
 
 GOV. ROLLER RING 
 GOV. KNIFE EDGE PIN I BLOCK 
 
 GOV.ARM 
 GOV.ROLLER E. PIN 
 
 GOV. CONNECTING LINK 
 
 GOV.CLUTCH SLEEVE 
 GOV.DASH POT LEVER 
 GOV.DASH POT CLUTCH 
 
 GOV.CLUTCH 
 .VIBRATOR ROD LINK 
 GOV.CLUTCH LEVER 
 GOV.VIBRATOR ROD GUIDE 
 
 GOV.YOKE 
 COV.VIBRATOR ROD BUSHING, UPPER 
 
 IV.VIBRATOR ROD 
 GOV.VIBRATOR SPRING 
 QOV.VIBRATOR SPRING SLEEVE 
 GOV.VIBRATOR ROD BUSHING, LOWER 
 GOV.GEAR CASE 
 OV.VIBRATOR ROLLER 
 GOV.VIBRATOR ROLLER BUSHING 
 GOV.VIBRATOR ROLLER PIN 
 
 WHEEL SHAFT BUSHING, LARGE 
 
 GOV.VIBRATOR CAM 
 OV.WORM WHEEL SHAFT 
 
 L PUMP CRANK 
 -GOV.WORM WHEEL 
 GOV.WORM 
 
 Fig. 8 
 
 22 
 
with the operation of the turbine. This spring adjustment 
 may be used if desired for bringing one machine into syn- 
 chronism with another or for transferring the load to or from 
 other turbines operating in parallel. 
 
 Of course the spring tension may be changed while the 
 turbine is at rest, but it cannot be set at any definite speed 
 unless the nuts have been previously marked for certain 
 settings. 
 
 The oscillatory motion of the valves is derived from a 
 cam or eccentric on the worm wheel shaft operating the vibra- 
 tor rod which in turn actuates the clutch lever F, which is 
 pivoted on the governor clutch. This clutch is free to travel 
 on the spindle in response to different positions of the governor 
 balls and levers. The effect of a change in the position of the 
 governor weights is merely to change the plane of oscillation 
 of the clutch lever, since the amplitude of the oscillations 
 remains constant. The clutch lever is connected by means of 
 suitable arms to the relay plunger which, while constantly 
 oscillating, changes its mean position in accordance with 
 changes in the position of the governor balls, or in other 
 words, in accordance with the demands of the load. The oper- 
 ation of this relay plunger and manner in which it regulates 
 the inlet of steam is explained on page 27 and following. 
 
 The motion of the clutch is dampened by means of a 
 dash pot connected by levers pivoted at I. 
 
 The starting trigger M holds the lever in the position 
 corresponding to normal speed, so that the relay plunger will 
 allow the primary valve to open. It should fall out of place 
 as soon as the turbine attains normal speed and the governor 
 weights regulate the position of the valve mechanism. 
 
 Fig. 9 shows a sectional view of another type of gover- 
 nor. 
 
 The governor spindle F is driven directly from the 
 worm S on the end of the turbine shaft, meshing with the 
 worm wheel V. This spindle carries the governor arm on 
 which the weights, two cast iron blocks of rectangular cross 
 section, are supported by means of levers and parallel guide 
 
 23 
 
WEIGHTS 
 
 GOV. SPRING RETAINER 
 
 OOV. WEIGHT GUIDE LINK 
 GOV. ARM 
 
 CLUTCH LEVER BALL B*RG 
 
 (c 
 
 VIBRATOR ROD 
 GOV WOR 
 
 VIBRATOR CAM GEAR 
 
 r- GOV. SPRING ADJUSTING SCREW 
 
 NUT 
 
 GOV. WEIGHT LEVERS 
 
 SPINDLE THRUST BEARING RINGS 
 
 OIL INLET TO SPINDLE 
 OV. CLUTCH 
 
 LEVER 
 
 CLUTCH LEVERBRACKET 
 
 DASH POT 
 
 E^Sf-OOV. SPINDLE BEARING 
 
 ^ ff 
 
 ~|p--OOV. SPINDLE 
 
 ^SPINDLE BUSHING 
 
 tN 1 "?.-; 
 
 V. WORM WHEEL 
 
 VIBRATOR CAM PINION 
 
 Fig. 9 
 
 24 
 
links T. When the turbine is at rest the weights are in their 
 innermost position and the clutch A at its lowest position, and 
 therefore the relay plunger is raised to such a position as to 
 admit steam to the turbine, as explained in the discussion of 
 the valve setting. As the turbine is brought up to speed the 
 centrifugal force of the weights is resisted by the spring R 
 directly opposing this force through the axis, and thus no 
 stresses are transmitted through the governor levers. 
 
 The lower end of the governor spindle carries a pinion, 
 meshing into a larger gear C, which operates the oil pump 
 below. The upper surface of this gear carries a cam, operating 
 the vibrator rod, which is maintained against the face of the 
 cam by means of the spring shown in the illustration. 
 
 The tension of the governor spring may be adjusted by 
 means of the adjusting screw K, which acts on the spring 
 shackles, the latter being constructed so that a number of coils 
 of the spring may be thrown in, or out of action as desired. 
 Thus, the speed at which the governor will regulate may be 
 adjusted by the adjusting screws, and if it is desired to increase 
 the speed variation between different loads, the spring may be 
 shackled up, cutting coils out of action, or vice versa, to make 
 the speed variation less with changes of load more coils may 
 be thrown into action. Such adjustments, however, are always 
 made at the time the turbines are tested, and no further adjust- 
 ment should be necessary. 
 
 This governor differs from the one previously described 
 in that the spring cannot be adjusted while the turbine is in 
 operation, and hence, an auxiliary spring is required. The 
 combined adjustment of the springs should permit the speed 
 of the turbine to be lowered, say 5%, by means of the auxiliary 
 spring, or enough so that the turbine may always be syn- 
 chronized when being started up. Therefore, the main gover- 
 nor spring should have an adjustment such that with the 
 machine shut down and the weights in their innermost posi- 
 tion, the auxiliary spring having substantially no tension, 
 the turbine will run with no load, and be under control of the 
 governor at 5% below speed. Then, by means of the auxiliary 
 
 25 
 
26 
 
spring, the speed may be brought up to normal, when the tur- 
 bine should have a speed variation between no load and normal 
 load, in] [accordance with the requirements of the particular 
 service to which it is applied. 
 
 With this, as much as with any governor, it is always 
 essential that the main valve shall come to its closed position 
 before the governor weights are in their outermost position. 
 
 It is to be noted that oil from the main oiling system is 
 admitted between the two spindle bushings, from which point 
 suitable passages lead it to every part of the governor requir- 
 ing lubrication. The weight of the governor is carried on the 
 thrust bearing rings M. These rings receive a liberal supply 
 of oil from the spindle bushing, the surplus passing on to the 
 surface of the clutch A. Oil also passes to the interior of the 
 spindle and out through the tubes P, lubricating the joints of 
 the governor weight levers. 
 
 One feature of this governor is that the clutch sleeve 
 revolves, being driven by the governor weight levers. It 
 revolves, however, on a stationary portion, thus rendering it 
 frictionless, in so far as any vertical sliding motion is concerned. 
 
 Valve Gear: 
 
 Figure 10 shows a section through the valve chamber 
 of a Westinghouse-Parsons steam turbine fitted with its valves 
 and relay plungers for governing the admission of steam. 
 
 By means of a rockshaft and system of levers connected 
 to the governor clutch lever, an oscillatory motion is com- 
 municated to the relay plungers F and P, which operate the 
 primary and secondary admission valves Vi and V 2 , Figure 2. 
 The primary valve regulates between no load and slightly over 
 full load, and then the secondary valve automatically comes 
 into operation enabling the turbine to carry high overload with 
 normal operating conditions, or full load without a vacuum. 
 
 The action of these relay plungers is shown in detail in 
 Figure] 10. If the throttle valve be opened with the relay 
 plunger F in the position shown, steam will pass up through 
 the small port A to the space beneath the piston C, the 
 
 27 
 
amount of steam being regulated by the needle valve B. As 
 the exhaust through the port E is closed by the relay plunger 
 and the upper side of the piston C is subjected to atmospheric 
 pressure only, the steam pressure beneath raises the piston 
 compressing the spring H, thus lifting the valve from its seat, 
 and admitting steam to the turbine at V. While the plunger 
 is oscillating in this position, the oscillations are not great 
 enough to uncover the port E. However, the outward motion 
 of the governor weights will cause the plunger to move to a 
 lower mean position such that the oscillations will uncover the 
 port E and exhaust more or less of the steam from below the 
 piston, and the valve will be closed correspondingly by the 
 spring H. Violent closing of the valve is prevented by the 
 dash pot piston. 
 
 While the plunger is oscillating with a constant ampli- 
 tude the opening of the port E varies in accordance with the 
 position of the governor. At light loads, no more pressure 
 accumulates beneath the piston than is sufficient to just raise 
 the valve Vi off its seat at each oscillation. As the load in- 
 creases the valve will have an increasing lift, admitting steam 
 to the turbine in puffs, until at maximum load these puffs 
 merge into a continuous blast, and the valve is practically sta- 
 tionary in its wide open position. 
 
 There are several advantages arising from the use of 
 this puff system of steam admission, 
 
 ist. Inasmuch as the valve is continually moving it 
 never can become stuck in one position, any tendency to 
 sticking will be apparent at once and may be rectified. 
 
 2nd. In effect this valve wiredraws the steam, and if it 
 were in a fixed position the seats would cut out rapidly during 
 times of light load. This wire drawing effect is practically 
 eliminated because at reasonably fractional loads the valve 
 virtually opens wide at its up stroke, when there is no wiredraw- 
 ing, and reaches its seat and is closed on the down position. 
 It might be approximately said that at light loads the valve is 
 closed the greater part of the time of an oscillation and open but 
 a small part. At heavier loads it is open the greater part of the 
 
 28 
 
time and closed but a small portion. Hence the wiredrawing is 
 much, less than if the valve were in a fixed position. 
 
 3rd. Inasmuch as the valve admits puffs of high pres- 
 sure steam, the walls of the cylinder assume temperatures cor- 
 responding to the higher pressures, so an increase of load 
 practically merely increasing the duration of the puffs will af- 
 fect the temperature condition of the turbine cylinder less than 
 if the increase of load required an increase of steam pressure as 
 in the case of a wiredrawing method of steam admission. 
 
 It will be seen that the secondary valve is slightly dif- 
 ferent in its action. As this valve is in operation only when 
 there is an overload on the turbine, it may not be brought into 
 action for comparatively long periods. In order that the relay 
 mechanism may not consume steam during such periods, it is 
 so constructed that the relay plunger does not begin to exhaust 
 steam until such time as the operation of the secondary valve 
 is required. Steam is admitted to both sides of the piston N 
 through the needle valves M M, and when on account of in- 
 creased load the mean position of the relay plunger P is raised 
 sufficiently by the governor, the port O is opened, exhausting 
 the steam from the upper side of the piston, and the valve 
 lifts by reason of the greater pressure beneath the piston N. 
 The port O may be permanently closed by the hand valve Q, 
 on the side of the secondary relay steam chest, thus cutting 
 the secondary valve entirely out of action. The spring R acts 
 in a similar way to PI in the main valve. The end of the sec- 
 ondary valve stem shows in the gauge glass S, so that it can 
 be readily seen whether or not the valve is operating properly, 
 or that it remains shut all of the time when its operation is 
 not required. 
 
 There are two needle valves for the purpose of regulat- 
 ing the action of the primary poppet valve. The one on the 
 dash pot is merely for the purpose of checking the drop of the 
 valve and needs no comment. The lower one, B, on the relay 
 steam cylinder controls the inlet of the steam to the bottom of 
 the piston. If this valve is not opened to pass sufficient steam, 
 the result will be that the main valve will not be raised to its 
 
 29 
 
extreme lift and the machine will be unable to carry maximum 
 load. If too wide open, the valve will operate with unneces- 
 sary violence, and if opened to admit an inordinate amount of 
 steam, the valve will fail to close effectively when it is called 
 upon to do so, because the volume of the steam will be so 
 great that it cannot be completely exhausted by the relay 
 plunger F. 
 
 The functions of the needle valves M, M, on the second- 
 ary valve are somewhat different. The lower needle valve 
 admits steam below and the upper one above the operating 
 piston. The effect of the relay plunger is to release the pres- 
 sure above the piston when the valve is required to open. The 
 lower needle valve should be opened no wider than is just 
 necessary to allow the secondary valve to open freely when 
 the relay plunger releases the pressure above the piston. 
 The upper needle valve should be open sufficiently to prevent 
 the valve from being lifted from its seat at full load or less, by 
 the puffs of steam within the turbine. At the same time this 
 needle valve must not be opened too much, or steam will not 
 be released freely enough by the relay plunger to permit the 
 poppet valve to open when it is called upon to do so. The 
 upper valve should not, however, be opened very much wider 
 than the lower valve, as when the pressure drops with each 
 impulse of steam admitted by the primary valve, the pressure 
 on top of the piston will decrease faster than below, on account 
 of the freer communication with the interior of the turbine, 
 causing the valve to lift slightly. The bobbing of the valves 
 on light loads may, therefore, usually be remedied by changing 
 the relative opening of the two valves ; and as a rule the upper 
 valve should never be open more than a half turn to a turn 
 more than the lower valve. In all the recent turbines the 
 upper needle valve is supplied with steam at pressure in Vi by 
 a pipe tapped into the primary valve chamber, thus overcom- 
 ing a tendency of the valves to operate at light loads. The 
 secondary valve should begin to open when the pressure below 
 the primary valve, that is the inlet pressure of the turbine, 
 is within a few pounds of the throttle pressure. 
 
 30 
 
The proper setting of the valves is not a difficult matter, 
 as there may be quite a wide variation in adjustment without 
 seriously affecting the economy of the machine. There are 
 two things, however, which must be carefully looked out for. 
 First, that when the governor is in its highest position the 
 primary poppet valve will stop oscillating and remain solidly 
 in its seat. Second, that the machine can readily carry the 
 maximum load for which it will be called upon. The following 
 adjustments should therefore be carefully made: 
 
 With the governor clutch resting on the starting trigger, 
 or the mid-position of its travel, the turbine should be revolved 
 with just enough steam pressure to keep the turbine at a 
 sufficiently low speed to prevent the governor lifting off the 
 trigger. The primary relay plunger should then be set so 
 that the primary poppet valve tends to stay as far open as the 
 steam pressure can keep it except when the plunger reaches 
 its very lowest position, when the poppet valve should show a 
 tendency to drop slightly. If the plunger were raised one- 
 eighth of a turn in the plunger head, the primary valve would 
 then tend to stay as wide open as possible during the complete 
 oscillation of the plunger. The plunger, however, should be 
 left in the first position so that whenever the turbine is started 
 up it can be readily noticed that the valve setting is correct by 
 the poppet valve having a slight tendency to drop when the 
 plunger reaches its lowest position and the governor has not 
 yet lifted off the trigger. 
 
 In the case of a turbine equipped with a governor of the 
 type shown in Figure 9, which is not provided with a trigger, 
 the preliminary setting is made when the turbine is tested, by 
 blocking the governor weights to bring the levers in the posi- 
 tion of mid-travel. After the turbine has attained speed, any 
 further adjustment necessary may be made on the relay 
 plungers in the manner described above. 
 
 Having made this adjustment of the primary relay 
 plunger, the turbine should then be brought up to its full 
 speed and in order to check up the setting the governor clutch 
 should be deliberately forced into its highest position when the 
 
 31 
 
32 
 
primary poppet valve should stop beating and remain tight 
 shut. 
 
 The secondary relay plunger is adjusted so that the 
 secondary poppet valve will admit steam to the intermediate 
 cylinder of the turbine when the average pressure below the 
 primary valve has reached nearly the pressure at the throttle. 
 This is of course the point when the turbine is doing all the 
 work possible with the primary valve open, and any further 
 opening of the primary valve alone could not admit any more 
 steam to the machine. The secondary valve should open soon 
 enough so that there will not be too great a drop in speed 
 before it comes into play, the allowable drop, of course, depend- 
 ing entirely on the nature of the service. Care should be 
 taken in this setting to prevent the valve from opening too 
 soon as the economy of the machine will be impaired if this 
 valve comes into operation before the turbine is carrying the 
 maximum load possible with the primary valve alone. 
 
 Figure 1 1 shows a section of another steam chest having 
 the same principle of operation as the arrangement shown in 
 Figure 10, but differing in the following details: 
 
 The relay cylinder and dash pot pistons instead of being 
 solid with split packing rings are made up of self-aligning 
 sleeves accurately turned to the bore of the cylinder and pro- 
 vided with small grooves to form a labyrinth packing. By 
 referring to the cut it w r ill be seen that on either side of this 
 sleeve or ring are two centering pieces called the upper and 
 lower dash pot pistons, fitted on the valve stem, so as to allow 
 a small clearance vertically as well as sidewise, thus avoiding 
 the liability of valves sticking or binding should the stem be 
 slightly out of true, due to carelessness in assembling. 
 
 Self-aligning packing is also provided for bushing the 
 valve stem both below the relay cylinder and at the bottom of 
 the poppet valve cage. This bushing is made up of two pieces, 
 the lower one fitting the valve stem with no more than work- 
 ing clearance, and held against a ground bevel seat on the 
 upper section by means of two springs. This provides very 
 nicely for a steam tight seal and still permits of a slight mis- 
 
 33 
 
alignment of the valve stem, without resultant binding or stick- 
 ing of the valves. 
 
 The needle valves in place of having the seats bored in 
 the relay cylinder casting are provided with bronze bushings 
 having less tendency to cut from wiredrawing and may be 
 easily renewed if cut by wet steam. 
 
 The poppet valve is provided with a removable upper 
 disc and the upper valve seat is also a solid removable ring 
 instead of being made in halves as formerly. To avoid any 
 chance of the primary valve spinning, a block with a pin 
 extending down between the webs of the valve is clamped on 
 the valve stem. 
 
 There is a pipe leading from the chamber beneath the 
 relay piston of the primary valve to the automatic stop governor 
 valve. This is an additional overspeed safety device sup- 
 plementing the automatic throttle valve, as whenever the stop 
 governor operates, the chamber below the relay piston is 
 opened to the atmosphere regardless of the position of the 
 relay plunger, and whether the automatic throttle drops or not. 
 In this manner the pressure is relieved from below the piston 
 and the valve returned to its seat by the spring. It will be 
 noted that there is a check valve in this exhaust pipe which 
 should be kept tight so that line pressure steam may not get 
 back to interfere with the regulation of the valve. 
 
 The relay steam chest cylinders are extended and pro- 
 vided with a port connecting the relay plunger bushing on 
 either side of its working ports, so that any slight leakage 
 may be entrapped and drained away rather than bubble over 
 the steam chest. 
 
 Oiling System: 
 
 Mounted on the end of the bedplate is the oil pump con- 
 nected to the turbine as previously explained. Around the 
 bedplate are located the oil cooling coil, the oil strainer, the 
 oil reservoir and the oil piping to the bearings, etc. 
 
 In some machines of the older types the oil pump draws 
 
 34 
 
the oil from the reservoir, sending it through the strainer, and 
 thence through the oil cooling coil located on the side of the 
 bedplate. It will be noted that there is a by-pass between the 
 pipes leading to and from the strainer, and there are valves in 
 these pipes so arranged that the strainer may be cut out of the 
 system and taken apart and cleaned while the turbine is 
 running A spring-loaded check valve in the by-pass auto- 
 matically cuts out the strainer, in case it should clog up to 
 such an extent is to interfere with the free circulation of the 
 oil. The strainer itself consists of a cast iron case containing 
 screens of varying fineness of mesh, the oil passing through 
 the coarsest first. 
 
 In later type machines the strainer is located in one 
 end of the reservoir. The oil returning from the bearings 
 flows through this strainer into the reservoir and is then redis- 
 tributed, as above. To clean this strainer while the turbine is 
 running, it is only necessary to remove the cover plate above 
 it and lift out the several portions. 
 
 From the cooling coil the oil enters the bearing supply 
 pipes, whence it is led by branch pipes to the several bearings. 
 The governor gear case acts as a reservoir to maintain the oil 
 at a static head of from one to two feet. This is the only 
 pressure under which the oil is supplied to the bearings. After 
 the oil passes through the bearings it flows into small reser- 
 voirs immediately under them, and thence back to the main 
 reservoir under the bedplate. The oil is thus used constantly 
 over and over again and the only loss is by deterioration with 
 time, and the very small loss due to leakage and spilling. A 
 gauge glass is usually located in the governor gear case to 
 indicate the level of the oil. In certain types of turbines a 
 rotary pump is used in place of a plunger pump and the requi- 
 site pressure is maintained on the bearings without any oil 
 reservoir in the governor gear case. 
 
 The oiling system is somewhat different in cases where 
 an oil relay governor system is employed for operating the 
 valve gear. In these cases the main oil pump is arranged to 
 pump to a higher pressure and it delivers oil directly to the 
 
36 
 
valve operating gear whence it passes to the oil cooler. A 
 spring loaded valve is provided which allows the oil not 
 required by the governor to pass direct to the cooler; this valve 
 at the same time maintains the pressure necessary for operat- 
 ing the governor gear. 
 
 In the larger machines an auxiliary oil pump is fur- 
 nished. This pump is only for the purpose of establishing a 
 circulation through the bearings with the turbine at rest, and 
 should be cut out of service as soon as the turbine has reached 
 speed and the main oil pump is maintaining the necessary oil 
 pressure. After steam is shut off the turbine and the speed 
 decreases, the auxiliary pump should be started to keep up the 
 oil supply to the bearings until the turbine comes to rest. 
 
 This pump should be located lower than the turbine so 
 that the oil can run to it by gravity. Its throttle valve should 
 be within easy reach of the operator starting or stopping the 
 turbine. 
 
 The oiling systems in different types of machines vary 
 in their detailed arrangements, but the general principles are 
 as set forth above. 
 
 Automatic Safety Stop: 
 
 All turbines now built are equipped with automatic 
 safety stop valves to shut down the turbine in case the normal 
 speed is exceeded by a predetermined amount. This auto- 
 matic stop valve is operated by a small valve actuated by an 
 automatic stop governor. The general type of governor and 
 governor valve is shown in Figure 12. 
 
 When the speed of the turbine for any reason rises 
 above normal and reaches a predetermined limit, the governor 
 weight is thrown out by centrifugal force. This limit is of 
 course fixed or adjusted by the compression put on the gov- 
 ernor spring. The weight on flying out comes in contact with- 
 a trigger cam, causing the trigger to disengage from the gov- 
 ernor valve lever, relieving the compression on the governor 
 valve spring, and allowing the governor valve to open freely. 
 This exhausts the steam from the lower side of a differential 
 
 37 
 

 38 
 
piston on the automatic throttle stem, causing the throttle to 
 close, and shut off the steam from the turbine. 
 
 It should also be noted that the governor trigger may 
 be disengaged by hand, and the turbine shut down when 
 desired, by means of the automatic stop valve. 
 
 It is expected that the main turbine governor and inlet 
 valve will be kept in such condition that the governor will 
 control the speed at no load under all conditions of steam 
 pressure and vacuum. Nevertheless, the automatic stop gov- 
 ernor and throttle valve should be tested at frequent intervals 
 to insure their always being operative. Where a reliable 
 tachometer or frequency meter is used, it is well to shut down 
 occasionally by raising the turbine speed 8% or 10% above 
 normal, when the automatic stop governor should come into 
 operation. 
 
 Automatic Throttle Valve : 
 
 Figure 13 shows a section of an automatic throttle 
 valve, which is placed in the steam line, on the boiler side of 
 the main throttle valve, and which is controlled by the auto- 
 matic stop governor, just referred to. 
 
 Steam is shut off by the piston D, which is shown in 
 the figure as being in the closed position. Steam from the 
 main line passes up through the valve D, and freely enters the 
 chamber M, above the operating piston, by means of the 
 passage J. It also leaks in limited quantities past the piston 
 and through the bushing around the stem F, and if prevented 
 from escaping, accumulates a pressure under the piston E. 
 The stem K passes up through the automatic throttle valve 
 cylinder cap, and serves as an indicator to show the position of 
 the valve. There is no packing at this point, so that the pres- 
 sure at P always corresponds to that of the atmosphere. The 
 opening C is connected to the automatic stop governor valve, 
 which, when closed, causes the steam pressure to build up 
 under the piston E, and the piston rises and opens the valve. 
 Should the valve connected with C be released, steam will be 
 exhausted from below the piston, and the pressure in the 
 chamber M will force the valve to the closed position. 
 
 39 
 
40 
 
There are some packing rings on the small diameter of 
 the operating piston. These are only useful when the valve 
 is operating, or is in the closed position. When the valve is 
 open, which is its normal position, these packing rings are of 
 no value, as the steam-tightness of the parts is maintained by 
 the ground seat on the piston N fitting against the ground 
 seat Q. To ensure against leakage of steam, it is well to see 
 that the piston has a steam tight ground fit against the 
 shoulder of the valve stem. 
 
 The main valve D is provided with two packing rings, 
 and in assembling, care should be taken that these packing 
 rings are not caught in the ports of the valves. There is a 
 projection on the valve cover to prevent the piston from re- 
 volving and getting the joints of the packing rings in an im- 
 proper position. At G there is a dowel, the function of which 
 is to prevent the valve from being assembled in such a manner 
 that the steam may be cut off from the port J. 
 
 Sometimes, instead of the automatic throttle valve just 
 described, a combination automatic and hand throttle, of the 
 type shown in Figure 14, is employed. Steam is admitted at 
 the upper side of the valve disc, filling the space above the 
 valve. By reason of leakage past the balance-piston, immedi- 
 ately above the valve disc, the full pressure is established at S, 
 in the balance cylinder, which so long as it is maintained, 
 tends to hold the valve disc on its seat. On the pilot valve A 
 being opened, the pressure in S is relieved, and the valve disc 
 then becomes approximately balanced. The high pressure 
 steam entering the valve, freely passes into the space L above 
 the operating piston, through the ports Q and W. It also 
 passes in limited quantities to the space T below the piston, 
 both by leakage past the piston, and leakage around the stem 
 R, so should there be no outlet for the steam at J, full pressure 
 will be established at T, causing the valve to open as the 
 hand wheel is raised, inasmuch as the upper portion of the 
 operating piston, where it enters the dashpot, is exposed to 
 atmospheric pressure only. On the other hand, should the 
 pressure be relieved from T, the valve will be closed in a 
 manner similar to the automatic throttle valve previously 
 
 41 
 
42 
 
described, the port J, as in the other case, being connected 
 to the automatic stop governor. 
 
 On the upper portion of the valve are the dashpot and 
 piston, for preventing the valve from slamming violently on its 
 seat. There is also a valve position indicator, to show the po- 
 sition of the valve with reference to its seat. 
 
 At P is a metallic packing with a connection to the 
 atmosphere, to carry away any leakage. 
 
 Provision is made for locking the valve disc when it is 
 in its wide open position, so that it may not vibrate or rattle in 
 the steam current. There is also a device to prevent the sud- 
 den opening of the valve after it has automatically closed, 
 should the operator reset the automatic stop governor, without 
 first closing down the throttle valve hand wheel. It is thus 
 possible to readmit steam to the turbine with proper judgment, 
 instead of instantaneously turning on the full head of steam. 
 It is, of course, presupposed that there is some derangement of 
 the governing gear, which has caused the turbine to speed up, 
 and trip the safety stop mechanism, so that in starting the 
 turbine again care must be taken to see that the governor is in 
 proper control. Hence the desirability of speeding up the tur- 
 bine somewhat slowly and not exposing it instantaneously to 
 the full head of steam. 
 
 This is accomplished by holes through the operating 
 piston at G, and a spring loaded valve called the cylinder 
 exhaust valve, located in the upper portion of the operating 
 piston. The lower side of this valve is exposed to the full 
 pressure, which, however, is insufficient to compress the spring. 
 On the valve being opened, the valve disc fetches up against 
 the body head. The upper stem, however, has a little further 
 to travel before the head on the lower end of it is stopped 
 against the bushing on the upper pcrtion of the dashpot. 
 This permits the cylinder exhaust valve spring to expand a 
 trifle, but still not sufficient for the steam pressure to force 
 open the valve D; this feature of the valve disc, being held by 
 the operating piston tightly against the valve body head, is 
 what prevents the valve Jfrom rattling in the current of steam. 
 
 43 
 
44 
 
Should the valve close automatically, the operating piston with 
 the cylinder exhaust valve, will descend leaving the upper 
 throttle valve stem, when the spring will be entirely released, 
 and the valve D will be free to open. Then, should the auto- 
 matic stop governor valve be closed at this time, thus prevent- 
 ing egress of steam at J, it will be impossible for the steam 
 pressure to build up at T, because the steam will be free to 
 escape through the holes G, the valve D, and the sight hole N. 
 Hence the valve will be unable to open until the hand wheel 
 has been screwed down, forcing the cylinder exhaust valve D 
 to the seat. 
 
 In opening the valve, the upper valve stem on being 
 raised, permits the operating piston to first open the pilot 
 valve A, relieving the steam in S, thus practically balancing 
 the throttle valve itself, after which the operating piston is 
 capable of opening the main valve in the manner before 
 described. 
 
 Coupling: 
 
 The coupling between the turbine rotor and the gener- 
 ator field shaft is either of the sleeve type or of the claw type. 
 
 The former is used on turbines of small capacity and 
 high speed. In this case the coupling ends of the turbine and 
 generator shafts are machined square, and the coupling is a 
 steel cylinder slotted out to fit with sufficient clearance to allow 
 it to slide freely on the squares. This coupling should be free 
 to slide easily on the shafts, both when turbine is cold and 
 when it is heated to operating conditions. 
 
 The claw coupling employed on the larger machines is 
 shown in Figs. 15 and 16. The sleeves are pressed on the ends 
 of the shafts, and secured by the keys K K. They are then 
 turned true, a narrow shoulder being left near the fingers on 
 which the coupling head fits freely with a slight clearance. 
 The smaller diameter at the ends of sleeves C C allows some 
 flexibility. 
 
 Oil grooves H are cut in the driving faces of the fingers 
 on the coupling head and are supplied with oil thrown off the 
 
 45 
 
shaft and caught in the retaining ring D. This is a split oil 
 ring held on the head by bolts T and has oil holes which reg- 
 ister with the grooves on the coupling fingers. On assembling, 
 care should be taken that the rings are placed so that the oil 
 holes correspond to the grooves in the fingers, and that they 
 are free from foreign matter that might restrict the oil passages. 
 The retainer rings also serve to restrict the end motion 
 of the revolving field and prevent the shoulders on the shaft 
 from coming in contact with the ends of the bearings. 
 
 46 
 
IV. 
 Operating Suggestions. 
 
 Before putting the turbine into operation for trie first 
 time, it should be completely dismantled and the spindle re- 
 moved so that an inspection may be made of all of the parts, 
 to insure that they have suffered no injury in transit. The 
 bearings, valve gear and governor parts should be carefully 
 inspected and cleaned. The oil tanks and pedestal reservoirs 
 should be thoroughly cleaned, and particular care should be 
 taken that the gland overflow drain is clear, as should this 
 become clogged, any water that might leak through the glands 
 would pass into the oiling system. The pilot valves should be 
 removed and the bushings cleaned. 
 
 After the turbine has been reassembled, the oiling sys- 
 tem should be filled either by pouring the oil into the governor 
 gear case G, Fig. 2 if this type of governor is used or by 
 means of the pipe and funnel provided in connection with 
 the oil reservoir. Bnough oil should be provided so that when 
 the turbine is running at full speed, the suction to the pump 
 is covered, and no air is drawn into the system. Although 
 there is a strainer in the oiling system, it is well, as a matter 
 of precaution, to strain the oil either before putting it into the 
 turbine, or to pour it into the reservoir through a fine mesh 
 screen or cloth. 
 
 Before connecting the steam line to the turbine inlet, 
 the whole line clear back to the boilers should be blown out 
 with live steam to remove all scale from the pipe, as well as 
 any other foreign matter that might have been left in the pip- 
 ing during erection. There is a steam strainer in the inlet at 
 S, Fig. 2, but fine sand and particles of gasket might pass 
 through and choke up the first row of blades, restricting the 
 steam passage to some extent. 
 
 Care and judgment must be exercised in the warming 
 up of the turbine before starting, as it is quite possible to over 
 do it, particularly where steam is superheated. If it were 
 
possible to warm the turbine evenly all over, it could not 
 become overheated before starting, but so long as the turbine 
 is standing still, this is impossible. With small quantities of 
 steam passing through the turbine, the hottest steam will 
 remain above, falling to the lower portion as it is cooled, with 
 the natural resiilt that neither the spindle nor the cylinder will 
 be straight, the former running out of true as soon as it is 
 revolved. It is, therefore, the better practice to warm the 
 turbine only moderately and get it revolving as quickly as 
 possible, and really do the latter part of the warming up after 
 the machine is in motion. The higher the superheat the more 
 important it is that the machine be not allowed to stand for a 
 long time with steam blowing through it. 
 
 The turbine should be started up non-condensing and 
 not subjected to vacuum until it has attained sufficient speed to 
 allow the water glands to effectively seal. The reason for this 
 precaution is that if a vacuum were established in the condenser 
 or even the air pump operated with the turbine at rest, or 
 before the glands were packed, a certain amount of air would 
 be drawn into the casing at both ends of the spindle, which 
 would result in some distortion of the spindle, causing it to 
 run out of true until such time as it had become evenly heated 
 throughout its length. When there is no gate valve between 
 the turbine and condenser, some means of forced injection 
 must be provided so that the turbine can be started non-con- 
 densing and the vacuum established afterwards. 
 
 This general rule, of course, does not apply to low 
 pressure turbines, which are treated of in a special pamphlet. 
 
 After the turbine is up to speed and under control of 
 the governor, it is well to make sure that the speed is correct, 
 either by counting the strokes of the governor vibrator, or by 
 noting the tachometer, if there is one, as it is possible that the 
 adjustment of the governor may have been interfered with 
 while the machine was standing idle. It is also well at this 
 time, while there is no load on the turbine, to be sure that the 
 governor controls the machine with a high vacuum and the 
 throttle wide open. It might be that the main poppet valve 
 
 48 
 
was leaking or that it had sustained some injury not evident 
 when the inspection was made. The action of the valve and 
 the control of the governor should be noted each time the 
 turbine is started or shut down, and should there be any such 
 defect, steps should be taken to regrind the valve to its seat at 
 the first opportunity, as a small leak will rapidly become seri- 
 ous through wiredrawing the steam. 
 
 Where conditions will permit, it is better to build up the 
 load gradually so that there may be no sudden heavy demand 
 upon the boilers with the possibility of water being drawn over 
 into the turbine. While there is 110 danger of the serious 
 results that are almost certain to occur in a reciprocating 
 engine, a slug of water is by no means desirable, as it will 
 cause the turbine speed to decrease considerably and impose 
 undue strains on the machine. Care should be taken both in 
 the arrangement of the piping and in the method of operation 
 to avoid any sudden rush of water to the turbine, especially in 
 case superheated steam is used. 
 
 It should hardly be necessary to state that while the 
 turbine is running it should be given the same careful and 
 systematic attention demanded by any high class engine. That 
 is, at regular intervals the engineer should inspect and note 
 the temperature of bearings and oiling system, the water 
 pressure on the glands, pressure of steam and action of governor 
 and valves. Should any irregularity be detected, such as 
 loss of gland water or insufficient oil supply, he should im- 
 mediately locate the cause and correct it. 
 
 No alarm should be felt if the turbine bearings are very 
 warm, as there is no danger as long as the hand can be borne 
 on them even momentarily. However, should a bearing show 
 signs of distress, as evidenced b}^ smoke or burning oil, the 
 trouble should be investigated immediately without attempt- 
 ing to nurse it back into condition. These bearings are subject 
 to a continuous circulation of oil, and should give no trouble, 
 and if a bearing starts to burn, there is some definite cause for 
 it, such as a stoppage of oil supply, foreign matter in the oil, 
 or a tight bearing cap, and the cause should be removed with- 
 
 49 
 
out delay. In case superheated steam is used, the thermome- 
 ter should be read at intervals in order to make sure that the 
 turbine is not being subjected to excessive variations of tem- 
 perature. 
 
 While accidents to blading are of infrequent occnrrence 
 and not to be expected tinder normal operating conditions, 
 should any sound of rubbing or grinding be detected, the tur- 
 bine shonld be shut down immediately, and the trouble located 
 and rectified before any serious damage results. The engineer 
 should not be misled by thinking any nnusual sound too 
 trivial to warrant investigation. Every irregularity should be 
 looked into at once and in* this way serious results may be 
 averted. It is possible that after inspection, the bearing align- 
 ment may have been changed inadvertently, and the blade 
 clearance decreased. Should any blades be damaged, and 
 should there be insufficient, time to make a proper repair, the 
 turbine may be put back into service if the damaged blades are 
 removed. If any considerable portion of any blade row is 
 damaged, the entire row should be removed. As the blade 
 rows are in pairs one stationary and one moving not only 
 must the damaged row be removed, but also the correspond- 
 ing moving or stationary row that in connection with the 
 damaged row makes a complete pair unless a complete pair 
 of rows is removed, the end thrust of the rotor will be unbal- 
 anced. The turbine will operate at some small sacrifice of 
 economy until such time as it is convenient to make a proper 
 repair. 
 
 When a turbine is first put into service the oil strainers 
 should be removed after a few hours' run and cleaned of any 
 foreign matter that may have found its way into the oiling 
 system. After the first few days' run, when the oil circulation 
 has washed out the system, as it were, such frequent cleanings 
 of this strainer should not be necessary, and the amount of 
 dirt found will indicate how often it is advisable to take care of 
 it. The strainer may be removed while the turbine is in opera- 
 tion, as explained in the description of the oiling system. 
 
 50 
 
Frequent and sudden changes from condensing to non- 
 condensing operation with the turbine under load should be 
 avoided. Should it be necessary to cut out the condenser, the 
 vacuum should be reduced as slowly as the existing conditions 
 will allow, so that no stresses may be set up in the turbine 
 casing, by reason of sudden changes of temperature in the 
 exhaust end. 
 
 In shutting down the turbine, the vacuum should be 
 broken as soon as the turbine throttle is closed so that as 
 the turbine comes to rest, cold air will not be drawn in through 
 the glands on the heated spindle. Also do not leave the gland 
 water running, as it may leak over into the bearing and 
 pedestal reservoirs. 
 
 As is customary with engines of any type, the turbine 
 should be completely dismantled and inspected every year. 
 The word dismantled is used in its fullest sense, and means 
 that the rotor, valves, bearings, oil cooling coil, etc., should all 
 be removed. If the valves show any sign of cutting they 
 should be ground to their seats. The cooling coil may show 
 a deposit from the oil on one side or water on the other side, 
 thus interfering with the circulation of the oil and effectiveness 
 of the cooling surface. If the bearings or coils show an exces- 
 sive oil deposit, the brand of oil should be looked into, as in 
 time the piping may become clogged up, imperiling the safety 
 of bearings by restricting the oil supply. 
 
 The governor should be cleaned and inspected and the 
 knife edge pins examined to make sure that no grit has found 
 its way to them, causing wear which would injuriously affect 
 the sensitive action of the governor. 
 
 The glands and balance pistons should be examined for 
 any deposit of lime from hard water, as discussed later in the 
 explanation of the several methods of gland piping. Also the 
 blading should be carefully inspected, and in case there is any 
 deposit of mud or scale from the boilers, it should be cleaned 
 out and steps taken to prevent a renewal of this condition. 
 
 During an inspection it is always desirable to check up 
 the clearance over the tips of the blades. This is accomplished 
 
 51 
 
by removing liners one by one from behind the keys on the 
 under side of the main bearings, (see H, Fig. 6.) This allows 
 the spindle to be lowered in the cylinder, a distance equal to 
 the thickness of the liners removed. Several trials should be 
 made, removing additional liners at each trial, and revolving 
 the spindle by hand until the tips of the blades just begin to 
 rub. As the liners are of known thickness expressed in 
 thousandths of an inch, the clearance can be obtained with 
 great exactness. 
 
 In a similar manner the spindle may be raised above its 
 original position, and the top clearance determined; it may 
 then be moved sidewise in either direction and the side clear- 
 ances measured. 
 
 From the measurement of liner thicknesses, the spindle 
 may readily be set in any desired position in the cylinder. It 
 is customary to set it some few thousandths above the central 
 position, the exact amount differing somewhat according to the 
 size and type of the machine. It is always desirable to have 
 the clearances such that the spindle blades will rub on the 
 walls of the cylinder before the cylinder blades rub on the sur- 
 faces of the spindle, as in the event of blades striking while 
 the turbine is running the rubbing is less harmful. 
 
 52 
 
V. 
 Condensers. 
 
 While the choice of the condenser is a matter of special 
 engineering and hardly within the province of this pamphlet, 
 the economy of the tnrbine is so dependent on the condenser 
 performance, that a few remarks on this snbject will not be 
 out of place. 
 
 So far as the turbine is concerned, one type of conden- 
 ser is as good as another. The condenser which will give the 
 best performance, regarded from the standpoint of condenser 
 performance only, is the best one to use. The condenser 
 should be such that it will carry the highest vacuum con- 
 sistent with the temperature and volume of cooling water 
 available, and the choice of type depends largely upon the 
 individual conditions of the plant. 
 
 Where a condenser capable of giving the highest 
 vacuum is installed, the need of utilizing this capability to the 
 utmost, can hardly be emphasized too strongly. A high 
 vacuum will, of course, entail special care and attention and 
 constant guarding against air leaks in the exhaust piping, but 
 it will result in the most economical operation of the turbine. 
 It must not be inferred that a high vacuum is essential to suc- 
 cessful operation of the turbine, for most satisfactory results 
 are obtained with low vacuum and even without any at all. 
 However, as it is a well known fact that the steam economy of 
 a turbine with high vacuum increases in greater proportion 
 than that of a reciprocating engine, the condenser should be 
 kept at its highest efficiency, in order that full advantage may 
 be taken of this feature. 
 
 53 
 
VI. 
 Oils. 
 
 There are several oils on the market that are suitable 
 for use in the turbine oiling system, but great care must be 
 taken to select a proper one. In the first place, the oil must 
 be pure mineral, unadulterated with either animal or vegetable 
 oils, and must have been washed free from acid. Certain 
 brands of oil require the use of sulphuric acid in their manu- 
 facture and are apt to contain varying degrees of free acid in 
 the finished product. A sample from one lot may have almost 
 no acid, while one from another lot may contain a dangerous 
 amount. 
 
 Mineral oils that have been adulterated will, when 
 heated up, partially decompose, forming acid. These oils may 
 be very good lubricants when first put into use, but after a 
 while they lose all their good qualities and become harmful 
 to the machine by corroding the journals in which they are 
 used. These oils must be very carefully avoided in the 
 turbine, as the cheapness of their first cost will in no way pay 
 for the damage they may do. A very good and simple way to 
 test for such adulterations is to shake up a quantity of the 
 oil in a test tube with a solution of borax and water. If there 
 is any animal or vegetable adulterant present it will appear as 
 a white, milk-like emulsion, which will not separate out when 
 allowed to stand. The pure mineral oil will appear at the top 
 as a clear liquid, and the excess of the borax solution at the 
 bottom, the emulsion being in between. A number of oils also 
 contain a considerable amount of paraffine which is deposited 
 in the oil cooling coil, preventing the oil from being cooled 
 properly, and in the pipes and bearings, choking the oil 
 passages and preventing the proper circulation of the oil and 
 the cushioning effect in the bearing tubes. This is not entirely 
 a prohibitive drawback, the chief objection being that it neces- 
 sitates an unduly frequent cleaning of the cooling coil, oil 
 piping and bearings. 
 
 54 
 
Some high class mineral oils of high viscosity are 
 inclined to emulsify with water, the emulsion appearing as a 
 jelly-like substance. It might be added that oils having a 
 high viscosity are not the most suitable for turbine use. 
 
 Since the consumption of oil in a turbine is so very 
 small, being practically only that due to leakage or spilling, 
 the price paid for it should be of secondary importance; the 
 prime consideration should be its suitability for the purpose. 
 
 In some cases a central gravity system will be employed, 
 instead of the oil system furnished with the turbine, which, of 
 course, will be a special consideration . 
 
 For large installations a central gravity oiling system 
 has much to recommend it, but as it performs such an impor- 
 tant function in the power plant and its failure would be the 
 cause of so much damage, every detail in connection with it 
 should be most carefully thought out, and designed with a 
 view that under no combination of circumstances would it be 
 possible for the system to become inoperative. One of the 
 great advantages of such a system is that it can be designed to 
 contain very large quantities of oil in the settling tanks, and 
 the oil will thus have quite a long rest between the times of 
 its being used in the turbine, a circumstance which seems to 
 be very helpful in extending the life of the oil. We further- 
 more believe that where the oil can have a long rest for set- 
 tling, an inferior grade of oil may be used, providing, however, 
 that it is absolutely free from acid. 
 
 We will at all times be glad to co-operate with engin- 
 eers installing our turbines and consult with them as to the 
 design of oiling systems. 
 
 55 
 

 
 JL,& 
 
 A -. & 
 
 fl^iSH 
 
 
 * &, 
 
 
 METHOD OF 
 MAKING WATER 
 CONNECTIONS TO 
 GLANDS AND 
 OIL COOLING 
 COILS. 
 
 Fig. 17 
 
 56 
 
VII. 
 Methods of Connecting up Glands and Oil Cooling Coils. 
 
 Theue are several satisfactory plans of connecting the 
 water supply to the glands and oil cooler, the choice of any 
 certain one depending upon the particular conditions existing 
 in the power house. 
 
 The temperature of the water for the gland supply must 
 be lower than the temperature of the steam, due to the vacuum 
 in the turbine, or it will evaporate rapidly and find its way 
 into the turbine in the form of steam. 
 
 In any case, a small amount of the sealing water will 
 pass by the gland collars into the turbine so that, if the con- 
 densed steam be returned to the boilers, the water used in the 
 glands must be of such character that it will not be injurious 
 to the boilers. Whether the water so used is returned to the 
 boilers or not, it should never contain an excessive amount of 
 lime or solid matter, as some evaporation is continually going 
 on in the glands which will cause the deposit of scale, and 
 necessitate frequent disassembling for cleaning. If the scale 
 is allowed to form, it will be deposited on the back of the 
 balance piston, throwing the machine out of balance. There 
 is also danger of its filling up the space in which the gland 
 runners work to such an extent as to cause mechanical contact 
 which may produce serious vibrations. 
 
 In the following pages are described various plans for 
 supplying water to the glands and oil cooler, and it is believed 
 these cover all of the conditions that are ordinarily met with. 
 
 First: 
 
 Where there is a cheap supply of good pure water, the 
 same water that is used in cooling the oil may be utilized for 
 the glands. The discharge from the cooling chamber is run 
 to a stand pipe with a height of 10 feet above the axis of the 
 glands and the supply to the glands is taken through a T just 
 
 57 
 
outside of the cooling chamber, as shown diagrammatically at 
 A, Figure 17. This is the method generally employed. 
 
 The quantity of water required for the oil cooler is 
 always more than sufficient for the glands. 
 
 Second: 
 
 Where there is a limited supply of proper water for the 
 glands and a large and cheap supply of poorer water which 
 may be readily used in the oil cooling chamber, the cooling 
 chamber and the glands will be piped up separately, each to 
 its own supply, the oil cooling supply discharging through the 
 cooler, direct into the sewer or similar waste. The glands 
 will then be supplied from a pure water supply, this supply 
 pipe having a branch to the glands and being led to a stand 
 pipe, the overflow from which discharges into the hot well> 
 serving, if desired, for "make up feed," as in B, Figure 17. 
 In this case it is possible to take the water for the glands from 
 the feed line at a point between the pump and the feed heater, 
 and discharge it from the gland overflow into the tank to 
 which the suction of the feed pumps is connected. 
 
 Third: 
 
 When the only available supply of pure water is that 
 for the boiler feed and the condensed steam is pumped directly 
 back to the boiler, as is shown at C, Fig. 17, then the delivery 
 from the condensed water pump may deliver to an elevation 
 10 feet above the axis of the glands, where a tank should be 
 furnished of sufficient capacity that the water may have time 
 to cool considerably before being delivered to the glands. 
 
 In most of these cases, if desired, the oil cooling water 
 may come from the circulating pump for the condenser, pro- 
 viding there is sufficient pressure to produce circulation. 
 
 Fourth: 
 
 The arrangement B may be somewhat costly if the 
 water fed to the glands has to be brought from the city water 
 mains and cannot, after service in the glands, be made good 
 use of, as opening the supply too wide will allow most of the 
 
water to go into the overflow which, in some cases, may exceed 
 the quantity necessary for make-up boiler feed, and is, there- 
 fore, liable to be wasted. The arrangement shown diagram- 
 matically at D admits just enough and no more water than is 
 necessary for sealing the glands. This method is probably the 
 one which is the most economical of water. One tank can obvi- 
 ously furnish required water pressure to any number of tanks in 
 the same station. This type of tank is one which can be bought 
 in plumbers' stores, and is such as is used for toilet rooms, etc. 
 
 Fifth: 
 
 In certain cases the turbine is required to exhaust 
 against a back pressure of one or two pounds, when a slightly 
 different arrangement of piping must be made. The sealing 
 water in this case must be allowed to circulate through the 
 glands in order to keep the temperature that is within, below 
 212 degrees Fahrenheit. If this is not done the water in the 
 glands will become heated from the main castings of the 
 machine and will evaporate. This evaporation will make the 
 glands appear as though they were leaking badly. In reality 
 it is nothing more than the boiling of water in the glands, but 
 it is, nevertheless, equally objectionable. 
 
 E, Fig. 17, illustrates a method of overcoming this 
 objectionable feature where the general arrangement may be 
 the same as any one of the se'/eral methods proposed, except 
 that two connections and valves are furnished at M and N, 
 which drain away to any suitable tank or sewer. These valves 
 are open just enough to keep sufficient circulation to keep the 
 temperature of the gland water below the boiling point, boiling 
 being evidenced by steam coming out of the glands as though 
 they w~ere leaking. 
 
 In case the turbine is operating against back pressure 
 the water pressure on the glands must be raised above the 
 standard of five pounds by the amount that the back pressure 
 exceeds the pressure of the atmosphere. That is to say, in 
 case a back pressure of five pounds gauge is maintained, a 
 gland pressure of ten pounds or a standpipe about twenty feet 
 above the axis would be required. 
 
<9H 
 
 & i 
 
 
VIII. 
 Foundations. 
 
 The foundations should be built in accordance with the 
 requirements called for in the official foundation plans. 
 
 These drawings, however, are not intended to give the 
 actual design of the foundation, as this must be made to suit the 
 particular conditions of the individual power house. Its design 
 is not limited like that for a reciprocating engine, and hence 
 can be made in many ways, to suit the arrangement of con- 
 densers and auxiliary apparatus in the basement, as well as 
 any peculiarities of building, etc. As the motion of the tur- 
 bine is rotary, it is not necessary to provide heavy foundations 
 or any foundation bolts, but at the same time it is necessary to 
 provide a foundation such that any part of it will support its 
 share of the weight of the turbine and generator without sink- 
 ing, and consequently disturbing the alignment of the machine. 
 In designing the foundation, provision should be made 
 for the necessary air ducts for ventilating the generator, and 
 one inch of grout should always be allowed for on top of the 
 foundation. 
 
 While concrete is to be preferred wherever practicable 
 it is often convenient to install the turbine on a structural 
 steel floor because of the greater amount of space left in the 
 basement for auxiliary apparatus. In order that such a floor 
 may be sufficiently rigid, and to avoid the location of beams in 
 positions where they would interfere with proper access to the 
 turbine, we show on our foundation plan a desirable arrange- 
 ment of beams. We also specify the size of beams required 
 for various spans in order that the deflection may be kept 
 down to .020, which is considered to be as great a deflection 
 as should be allowed. In using a structural steel floor, it is 
 very convenient to run in one-half to one inch of lead between 
 the turbine bedplate and the steel work, so that the turbine 
 may be properly leveled with the weight evenly distributed on 
 
 61 
 
all beams, as there is liable to be some slight misalignment in 
 the steel work. This lead pad also tends to absorb any slight 
 vibration that may exist. With either a structural steel or 
 concrete foundation the final leveling should not be done until 
 the entire weight of the turbine and generator is in place, after 
 which the lead or grout may be poured. 
 
 As before stated the concrete foundation is more desir- 
 able, as any vibration tends to be intensified if the turbine is 
 mounted on structural steel, and especially is this the case if 
 any members form a harmonic with the turbine vibration. 
 A desirable and convenient form of foundation is shown in 
 Fig. 18. 
 
The Westinghouse Machine Co. 
 
 General Offices and Works 
 
 East Pittsburg, Pa. 
 
 New York 
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 Boston 
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 SALES OFFICES 
 
 165 Broadway 
 
 Candler Building 
 
 131 State Street 
 
 171 La Salle Street 
 
 1102 Traction Building 
 
 New England Building 
 
 Hunt, Mirk & Co., 141 Second Street 
 
 512 McPhee Building 
 
 Westinghouse Building 
 
 1003 North American Building 
 
 Chemical Building 
 
 - G. and O. Braniff & Co. 
 
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 WILL BE ASSESSED FOR FAILURE TO RETURN 
 THIS BOOK ON THE DATE DUE. THE PENALTY 
 WILL INCREASE TO SO CENTS ON THE FOURTH 
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 UNIVERSITY OF CALIFORNIA LIBRARY