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STEAM ENGINE

Online Encyclopedia
Originally appearing in Volume V25, Page 833 of the 1911 Encyclopedia Britannica.
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STEAM ENGINE. 1. A steam engine is a machine for the conversion of heat into mechanical work, in which the working substance is water and water vapour. The working substance may be regarded from two points of view. Thermodynamically it is the vehicle by which heat is conveyed to and through the engine from the hot source (the furnace and boiler). Part of this heat suffers a transformation into work as it passes through, and the remainder is rejected, still in the form of heat. Mechanically the working substance is a medium capable of exerting pressure, which effects this transformation in doing work by means of the changes of volume which it undergoes it the operation of the machine. Regarded as a thermodynamic device, the function of the engine is to get as much work as possible from a given quantity of heat or, to go a step further back, from the combustion of a given quantity of fuel. Accordingly, a question of primary importance is what is called the efficiency of the engine, which is the ratio of the work done to the heat supplied. Before, however, proceeding to discuss the steam engine in this aspect, or treating of the mechanics of its modern forms, it maybe useful to give a brief historical sketch of its early development as an industrial appliance. In any such sketch the chief share of attention must necessarily be given to the work of James Watt. But a process of evolution had been going on before the time of Watt which prepared the steam engine for the immense improvements it received at his hands. His labours stand in natural sequence to those of Thomas Newcomen, and Newcomen's to those of Denis Papin and Thomas Savery. Savery's engine in its turn was the reduction to practical form of a contrivance which had long before been known as a scientific toy. The most modern type of all, the steam turbine of C. A. Parsons, is a new departure which has but little to connect it directly with the past; but even the steam turbine not only profits by the inventions of Watt, but in its characteristic feature finds crude prototypes in <( I apparatus which employed ~Sl the kinetic energy of jets of steam. 2. One of these, indeed, is mentioned amongst the ear- Hero, 130 liest notices we have of any heat engine. In the Pneumatics of Hero of Alexandria (c. 130 B.C.) there is described the aeolipile, which is a primitive steam reaction tur- bine, consisting of a spherical vessel pivoted on a central axis and supplied with steam through one of the pivots. The steam escapes by bent pipes facing tangentially in opposite directions, at opposite ends of a diameter perpendicular to the axis. The globe revolves by reaction from the escaping steam just as a Barker's mill is driven by escaping water. Another apparatus described by Hero (fig. 1)1 is interesting as the prototype of a class of engines which long afterwards became practically important. A hollow altar containing air is heated by a fire kindled on it; the air in expanding drives some of the water contained in a spherical vessel beneath the altar into a bucket, which descends. and opens the temple doors above by pulling round a pair of vertical posts to which the doors are fixed. When the fire is extinguished the air cools, the water leaves the bucket, •andthe doors close. In another device a jet of water driven out by expanding air is turned to account as a fountain. 3. From the time of Hero to the 17th century there is no progress to record, though here and there we find evidence that appliances like those described by Hero were used for trivial purposes, such as organ-blowing and the Der6oltarPa a' turning of spits. The next distinct step was the publication in . 16or of a treatise on pneumatics by Giovanni Battista della Porta, in which he shows an apparatus similar to Hero's fountain, but with steam instead of air as the displacing fluid. Steam generated in a separate vessel passes into a closed chamber containing water, from which a ' pipe (open under the water) leads out. He also points out that the condensation of steam in the closed chamber may be used to pro-duce a vacuum and suck up water from a lower level. In fact, his suggestions anticipate very fully the engine which a century later became in the hands of Savery the earliest commercially successful steam engine. In 1615 Solomon de Caus gives a plan of forcing up water by a steam fountain which differs from Della Porta's only in having one vessel serve both as boiler and as displacement-chamber, the hot water being itself raised. 4. Another line of invention was taken by Giovanni Branca (1629), who designed an engine shaped like a water-wheel, to be driven by the impact of a jet of steam on its vanes, and in its turn to drive other mechanism for various useful purposes. But Branca's suggestion was for the time unproductive, and we find the course of invention reverting to the line followed by Della Porta and De Caus. 5. The next contributor is one whose place is not easily assigned. To Edward Somerset, second marquis of Worcester, appears to be due the credit of proposing, if not Ma, u1s of making, the first useful steam engine. Its object worcestet, was to raise water, and it worked probably like 1663. Della Porta's model, but with a pair of displacement-chambers, from each of which alternately water was forced by steam from an independent boiler, or perhaps by applying heat to the chamber itself, while the other vessel was allowed to refill. Lord Worcester's description of the engine in art. 68 of his Century of Inventions (1663) is obscure, and no drawings are extant. It is, therefore, difficult to say whether there were any distinctly novel features except the double action; in particular, it is. not clear whether the suction of . a vacuum was used to raise water as well as the direct pressure of steam. 6. The steam engine first became commercially successful in the hands of Thomas Savery,2 who, in 1698, obtained a patent for a water-raising engine, shown in fig. 2. Steam is admitted to one of the oval vessels A, displacing water, which it drives up through the check-valve r69s. B. When the vessel A is emptied of water the supply of steam is stopped, and the steam already there is condensed by allowing a jet of cold water from a cistern above to stream over the outer surface of the vessel. This produces a vacuum and causes water to be sucked up through the pipe C and the valve D. Meanwhile steam has been displacing water ' From Greenwood's translation of Hero's Pneumatica. 2 Savery was born probably" in 165o and died in 1715. See Sir E. Duelling Lawrence's presidential address to the Royal Institution of Cornwall (Journ. of the Roy. Inst. of Cornwall, No. li.), republished with a reprint of Savery's Miner's Friend of 1702, in which he discusses the originality of Savery's invention and dismisses. the claims put forward for Lord Worcester. the safety-valve as an adjunct to his " digester," suggested that the condensation of steam should be employed to make a vacuum under a piston previously raised by the expansion of the steam. Papin's was the earliest cylinder and piston steam engine, and his plan of using was that which afterwards took practical shape in the spheric engine of Newcomen. But his scheme was unworkable by the fact that he proposed to use but one vessel as both boiler and cylinder. A small quantity of water was placed at the bottom of a cylinder and heat was applied. When the piston had risen the fire was removed, the steam was allowed to cool, and the piston did work in its down-stroke under the pressure of the atmosphere. After hearing of Savery's engine in 1705 Papin turned his attention to improving it, and devised a modified form, shown in fig. 3, in which the displacement- from the other vessel, and is ready to be condensed there. The valves B and D open only upwards. The supplementary boiler and furnace E are for feeding water to the main boiler; E is filled while cold and a fire is lighted under it; it then acts like the vessel of De Gaus in forcing a supply of feed- water into the main boiler F. The gauge cocks G, G are an inter- esting feature in detail. Another form of Savery's engine had only one dis- placement-chamber and worked intermittently. In the use of artificial means to condense the steam, and in the appli- cation of the vacuum so formed to raise water by suction from a level lower than that of the engine, Savery's engine was probably an improvement on Worcester's; in any case it found what Worcester's engine had failed to find—considerable employment in pumping mines And in raising water to supply houses and towns, and even to drive water-wheels. A serious difficulty which prevented its general use in mines was the fact that the height through which it would lift water was limited by the pressure the boiler and vessels could bear. Pressures as high as 8 or to atmospheres were employed—and that, too, without a safety-valve—but Savery found it no easy matter to deal with high-pressure steam; he complains that it melted his common solder, and forced him, as Desaguliers tells us, " to be at the pains and charge to have all his joints soldered with spelter." Apart from this drawback, the waste of fuel was enormous, from the condensation of steam which took place on the surface of the water and on the sides of the displacement-chamber at each stroke; the consumption of coal was, in proportion to the work done, some twenty times greater than in a good modern steam engine. In a tract called The Miner's Friend Savery alludes thus to the alternate heating and cooling of the water-vessel: " On the outside of the vessel you may see how the water goes out as well as if the vessel were transparent, for so far as the steam continues within the vessel so far is the vessel dry without and so very hot as scarce to endure the least touch of the hand. But as far as the water is, the said vessel will be cold and wet where any water has fallen on it; which cold and moisture vanishes as fast as the steam in its descent takes the place of the water." Before Savery's engine was entirely displaced by its successor, Newcomen's, it was improved by J. T. Desaguliers, who applied to it the safety valve (invented by Papin), and substituted condensation by a jet of cold water within the vessel for the surface condensation used by Savery. To Savery is ascribed the first use of the term " horse power " as a measure of the performance of an engine. 7. So early as 1678 the use of a piston and cylinder (long before known as applied to pumps) in a heat-engine had been cylinder suggested by Jean de Hautefeuille, who proposed and to use the explosion of gun-powder either to raise a Piston piston or to force up water, or to produce, by the sub- engine, sequent cooling of the gases, a partial vacuum into which water might be sucked up. Two years later Christian Huygens described an engine in which the explosion of gun-powder in a cylinder expelled part of the gaseous contents, after which the cooling of the remainder caused a piston to descend under atmospheric pressure, and the piston in descending did work by raising a weight. 8. In 1690 Denis Papin, who ten years before had inventedNewcomen's success by separating the boiler from the cylinder Atmospheric and by using (as Savery had done) artificial means Engine, to condense the steam. This was Thomas New- 1705' comen, who in 1705, with his assistant, John Cawley, gave the steam engine the form shown in fig. 4. Steam admitted from the boiler to the cylinder allowed the piston to be raised by a heavy counterpoise on the other side of the beam. Then the steam valve was shut and a jet of cold water entered the cylinder and condensed the steam. The piston was consequently forced down by the pressure of the atmosphere and did work on the pump. The next entry of steam expelled the condensed FIG. 4.-Newcomen's Atmospheric water from the cylinder Engine, 1705. ' For an account of Papin's inventions see his Life and Correspondence, by Dr E. Gerland (Berlin, 1881). ing Engine, 1698. Papin. steam atmomade chamber A was a cylinder, with a floating diaphragm or piston on the top of the water to keep the water and steam from direct contact with one another. The water was delivered into a closed air-vessel B, from which it issued in a continuous stream, against the vanes of a water-wheel. After the steam had done its work in the displacement-chamber it was allowed to escape by the stop-cock C instead of being condensed. Papin's engine was, in fact, a non-condensing single-acting steam pump, with steam cylinder and pump cylinder in one. A curious feature of it was the heater D, a hot mass of metal placed in the diaphragm for the purpose of keeping the steam dry. Among the many inventions of Papin was a boiler with an internal fire-box—the earliest example of a construction that is now almost universal.' 9. While Papin was thus going back from his first notion of a piston engine to Savery's cruder type, a new inventor had appeared who made the piston engine a practical through an escape valve. The piston was kept tight by a layer of water on its upper surface. Condensation was at first effected by cooling the outside of the cylinder, but the accidental leakage of the packing water past the piston showed the advantage of condensing by a jet of injection water, and this plan took the place of surface condensation. The engine used steam whose pressure was little if at all greater than that of the atmosphere; sometimes, indeed, it was worked with the manhole lid off the boiler. to. About 1711 Newcomen's engine began to be introduced for pumping mines. It is doubtful whether the action was originally automatic, or depended on the periodical self-acting turning of taps by an attendant. The common story , Y is that in 1713 a boy named Humphrey Potter, whose duty it was to open and shut the valves of an engine he attended, made the engine self-acting by causing the beam itself to open and close the valves by suitable cords and catches. This device was simplified in 1718 by Henry Beighton, who suspended from the beam a rod called the plug-tree, which worked the valves by means of tappets. By 1725 the engine was in common use in collieries, and it held its place without material change for about three-quarters of a century in all. Near the close of its career the atmospheric engine was much improved in its mechanical details by John Smeaton, who built many large engines of this type about the year 1970, just after the great step which was to make Newcomen's engine obsolete had been taken by James Watt. Compared with Savery's engine, Newcomen's had (as a pumping engine) the great advantage that the intensity of pressure in the pumps was not in any way limited by the pressure of the steam. It shared with Savery's, in a scarcely less degree, the defect already pointed out, that steam was wasted by the alternate heating and cooling of the vessel into which it was led. Though obviously capable of more extended uses, it was in fact almost exclusively employed to raise water—in some instances for the purpose of turning water-wheels to drive other machinery. Even contemporary writers complain of its vast " consumption of fuel," which appears to have been scarcely smaller than that of the engine of Savery. 11. In 1763 James Watt, an instrument maker in Glasgow, while engaged by the university in repairing a model of New- comen's engine, was struck with the waste of steam watt' 1764 to which the alternate chilling and heating of the . cylinder gave rise. He saw that the remedy, in his own words, would lie in keeping the cylinder as hot as the steam that entered it. With this view he added to the engine a new organ—an empty vessel separate from the cylinder, into which the steam should be allowed to escape from the cylinder, to be condensed there by the application of cold water either outside or as a jet. To preserve the vacuum in his condenser he added a pump called the air-pump, whose function was to pump from it the condensed steam and water of con- densation, as well as the air which would otherwise accumulate by leak- age or by being brought in with the steam or with the injection 'water. Then, as the cylinder was no longer used as a condenser, he was able to keep it hot by clothing it with non- conducting bodies, and in particular by the use of a steam jacket, or layer of hot steam between the cylinder and an external casing. Further, and still with the same object, he covered in the top of the cylinder, taking the piston- rod out through a steam-tight stuffing-box, and allowed steam instead of air to press upon the piston's upper surface. The idea of using a separate condenser had no sooner occurred to Watt than he put it to the test by constructing the apparatus shown in fig. 5. There A is the cylinder, B a surface condenser, and C the air-pump. The cylinder was filled with steam above the piston, and a vacuum was formed in the surface condenser B. On opening the stop-cock D the steam rushed over from the cylinder and was condensed, while the piston rose and lifted a weight. After several trials Watt patented his improvements in 1769; they are described in his specification in the following words, which, apart from their immense historical interest, deserve careful study as a statement of principles which to this day guide the scientific development of the steam engine: " My method of lessening the consumption of steam, and consequently fuel, in fire-engines, consists of the following principles: " First, That vessel in which the powers of steam are to be employed to work the engine, which is called the cylinder in common fire-engines, and which I call the steam-vessel, must, during the whole time the engine is at work, be kept as hot as the steam that enters it; first by enclosing it in a case of wood, or any other materials that transmit heat slowly; secondly, by surrounding it with steam or other heated bodies; and, thirdly, by suffering neither water nor any other substance colder than the steam to enter or touch it during that time. " Secondly, In engines that are to be worked wholly or partially by condensation of steam, the steam is to be condensed in vessels distinct from the steam-vessels or cylinders, although occasionally communicating with them; these vessels I call condensers; and, whilst the engines are working, these condensers ought at least to be kept as cold as the air in the neighbourhood of the engines, by application of water or other cold bodies. Thirdly, Whatever air or other elastic vapour is not condensed by the cold of the condenser, and may impede the working of the engine, is to be drawn out of the steam-vessels or condensers byi means of pumps, wrought by the engines themselves, or other-wise. " Fourthly, I intend in many cases to employ the expansive force of steam to press on the pistons, or whatever may be used instead of them, in the same manner in which the pressure of the atmosphere is now employed in common fire-engines. In cases where cold water cannot be had in plenty, the engines may be wrought by this force of steam only, by discharging the steam into the air after it has done its office. . " Sixthly, I intend in some cases to apply a degree of cold not capable of reducing the steam to water, but of contracting it considerably, so that the engines shall be worked by the alternate expansion and contraction of the steam. Lastly, Instead of using water to render the pistons and other parts of the engine air and steam tight, I employ oils, wax, resinous bodies, fat of animals, quicksilver and other metals in their fluid state." The fifth claim was for a rotary engine, and need not be quoted here. The " common fire engine " alluded to was the steam engine, or, as it was more generally called, the " atmospheric " engine of Newcomen. Enormously important as Watt's first patent was, it resulted for a time in the production of nothing more than a greatly improved engine of the Newcomen type, much less wasteful of fuel, able to make faster strokes, but still only suitable for pumping, still single-acting, with steam admitted during the whole stroke, the piston, as before, pulling the beam by a chain working on a circular arc. The condenser was generally worked by injection, but Watt has left a model of a surface condenser made up of small tubes, in every essential respect like the condensers now used in marine engines .l 12. Fig. 6 is an example of the Watt pumping engine of this period. It should be noticed that, although the top of the cylinder is closed and steam has access to the upper side of the WatPs piston, this is done only to keep the cylinder and piston pamplag warm. The engine is still single-acting; the steam in Engiene the upper side merely plays the part which was played 1769. in Newcomen's engine by the atmosphere; and it is the lower end of the cylinder alone that is ever put in communication with the condenser. There are three valves: the " steam " valve a, the " equilibrium " valve b, and the " exhaust " valve c. At the beginning of the down-stroke c is opened to produce a vacuum below the piston and a is opened to admit steam above it. At the end of the down-stroke a and c are shut and b is opened. This puts the two sides in equilibrium and allows the piston to be pulled up by the pump-rod P, which is heavy enough to serve as a counterpoise. C is the condenser, and A the air-pump, which discharges into the hot well H, whence the supply of the feed-pump F is drawn. 13. In a second patent (1781) Watt describes the " sun-andplanet" wheels and other methods of making the engine give 1 An interesting detailed narrative of the steps leading to his invention was written by Watt as a note to the article " Steam Engine " in Robison's System of Mechanical Philosophy (1822). See Ewing, The Steam Engine and other Heat Engines, pp. 15-19. mental Apparatus. continuous revolving motion to a shaft provided with a flywheel. He had invented the crank and connecting-rod for this purpose, but it had meanwhile been patented Rotative by one Pickard, and Watt, rather than make terms Engine. with Pickard, whom he regarded as a plagiarist of his own ideas, made use of his sun-and-planet motion until the patent on the crank expired. The reciprocating motion of earlier forms had served only for pumping; by this invention Watt opened up for the steam engine a thousand other channels of usefulness. The engine was still single-acting; the connecting-rod was attached to the far end of the beam, and that carried a counterpoise which served to raise the piston when steam was admitted below it. 14. In 1782 Watt patented two further improvements of the first importance, both of which he had invented some years other before. One was the use of double action, that is Inventions to say, the application of steam and vacuum to "watt. each side of the piston alternately. The other (invented as early as 1769) was the use of steam expansively, in other words the plan (now used in all engines that aim at economy of fuel) of stopping the admission of steam when the piston had made only a part of its stroke, and allowing the rest of the stroke to be performed by the expansion of the steam already in the cylinder. To let the piston push as well as pull the end of the beam Watt devised his so-called parallel motion, an arrangement of links connecting the piston-rod head with the beam in such a way as to guide the rod to move in a very nearly straight line. He further added the throttle valve, for regulating the rate of admission of steam, and the centrifugal governor, a double conical pendulum, which controlled the speed by acting on the throttle-valve. The stage of development reached at this time is illustrated by the engine of fig. 7 (from Stuart's History of the Steam Engine), which shows the parallel motion pp, the governor g, the throttle-valve t, and a pair of steam and exhaust valves at each end of the cylinder. Among other inventions of Watt were the " indicator," by which diagrams showing the relation of the steam pressure in the cylinder to the movement of the piston are automatically drawn; a steam tilt-hammer; and also a steam locomotive for ordinary roads—but this invention was not prosecuted. In partnership with Matthew Boulton, Watt carried on in Birmingham the manufacture and sale of his engines with the utmost success, and held the field against all rivals in spite of severe assaults on the validity of his patents. Notwithstanding his accurate knowledge of the advantage to be gained by using steam expansively, he continued to employ only low pressures—seldom more than 7 lb per sq. in. over that of the atmosphere. His boilers were fed, as Newcomen's had been, through an open pipe which rose high enough to let the column of water in it balance the pressure of the steam. He gave a definite numerical significance to the term " horse-power" (q.v.) as a mode of rating engines, defining it as the rate at which work is done when 33,000 lb are raised one foot in one minute. 15. In the fourth claim in Watt's first patent the second sentence describes a non-condensing engine, which would have required steam of a higher pressure. This, how- Non_ ever, was a line of invention which Watt did not condensing follow up, perhaps because so early as 1725 a engine. non-condensing engine had been described by Jacob Leupold in his Theatrum machinarum. Leupold's proposed engine is shown in fig. 8, which makes its action sufficiently clear. Watt's aversion to high - pressure steam was strong, and its influence on steam engine practice long survived the expiry of his patents. So much indeed was this the case that the terms " high-pressure " and " non-condensing " were for many years synonymous in contradistinction to the " low-pressure " or condensing engines of Watt. This nomenclature no longer holds; in modern practice many condensing engines use as high pressures as non-condensing engines, and by doing so are able to take advantage of Watt's great invention of expansive working to a degree which was impossible in his own practice. 16. The introduction of the non-condensing and, at that time, relatively high-pressure engine was effected in England by Richard Trevithick and in • America by Oliver High-Evans about 1800. Both Evans and Trevithick pressure applied their engines to propel carriages on roads, Steam. and both used for boiler a cylindrical vessel with a cylindrical flue inside—the construction now known as the Cornish boiler. In partnership with William Bull,. Trevithick had previously made direct acting pumping-engines, with an inverted cylinder set over and in line with the pump-rod, thus dispensing with the beam that had been a feature in all earlier forms. But in these " Bull " engines, as they were called, a condenser was used, or, rather, the steam was condensed by a jet of cold water in the exhaust-pipe, and Boulton and Watt successfully opposed them as infringing Watt's patents. To Trevithick belongs the distinguished honour of being the first to use a steam carriage on a railway; in 1804 he built a locomotive in the modern sense, to run on what had formerly been a horse-tramway, in Wales, and it is noteworthy that th6' Engine, 1782. exhaust steam was discharged into the funnel to force the furnace draught, a device which, twenty-five years later; in the hands of George Stephenson, went far to make the locomotive what it is to-day. In this connexion it may be added that as early as 1769 a steam carriage for roads had been built in France by Nicolas Joseph Cugnot, who used a pair of single-acting high-pressure cylinders to turn a driving axle step by step by means of pawls and ratchet-wheels. To the initiative of Evans may be ascribed the early general use of high-pressure steam in the United States, a feature which for many years distinguished American from English practice. 17. Amongst the contemporaries of Watt one name deserves special mention. In 1781 Jonathan Carter Hornblower constructed and patented what would now be called Compound engine. a compound engine, with two cylinders of different sizes. Steam was first admitted into the smaller cylinder, and then passed over into the larger, doing work against a piston in each. In Hornblower's engine the two cylinders were placed side by side, and both pistons worked on the same end of a beam overhead. This was an instance of the use of steam expansively, and as such was earlier than the patent, though not earlier than the invention, of expansive working by Watt. Hornblower was crushed by the Birmingham firm for infringing their patent in the use of a separate condenser and air-pump. The compound engine was revived in 1804 by Arthur Woolf, with whose name it is often associated. Using steam of fairly high pressure, and cutting off the supply before the end of the stroke in the small cylinder, Woolf expanded the steam to several times its original volume. Mechanically the double-cylinder compound engine has this advantage over an engine in which the same amount of expansion is performed in a single cylinder, that the sum of the forces exerted by the two pistons in the compound engine varies less throughout the action than the force exerted by the. piston of the single-cylinder engine. This advantage may have been clear to Hornblower and Woolf and to other early users of compound expansion. But another and probably a more important merit of the system lies in a fact of which neither they nor for many years their followers in the use of compound engines were aware —the fact that by dividing the whole range of expansion into two parts the cylinders in which these are separately performed are subject to a reduced range of fluctuation in their temperature. This, as will be seen later, limits to a great extent a source of waste which is present in all steam engines, the waste which results from the heating and cooling of the metal by its alternate contact with hot and cooler steam. The system of compound expansion is now used in nearly all large engines that pretend to economy. Its introduction forms the most outstanding improvement which steam engines of the piston and cylinder type have undergone since the time of Watt; and we are ,able to recognize it as a very important step in the direction set forth in his " first principle " that the cylinder should be kept as hot as the steam that enters it. 18. Woolf introduced the compound engine somewhat widely about 1814 as a pumping engine in the mines of Cornwall. But here it met a .strong competitor in the. high- Cornish Engine. Pressure single-cylinder engine hnder en ine of Trevithick, which had the advantage of greater simplicity in construction. Woolf's engine fell into comparative disuse, and the single-cylinder type took a form which, under the name of the Cornish pumping engine, was for many years famous for its great economy of fuel. In this engine the cylinder was set under one end of a beam, from the other end of which hung a heavy rod which operated a pump at the foot of the shaft. Steam was admitted above the piston for a short portion of the stroke, thereby raising the pump-rod, and was allowed to expand for the remainder. Then an equilibrium valve, connecting the space above and below the piston, as in fig. 6, was opened,. and the pump-rod descended, doing work in the pump and raising the engine piston. The large mass which had to be started and stopped at each stroke served by its inertia to counter-balance the unequal pressure of, the steam, for the ascending ENGINE rods stored up energy of motion in the early part of the stroke, when the steam pressure was greatest, and gave out energy in the later part, when expansion had greatly lowered the pressure. The frequency of the stroke was controlled by a device called a cataract, consisting of a small plunger pump, in which the plunger, raised at each stroke by the engine, was allowed to descend more or less slowly by theescape .of fluid below it through an. adjustable orifice, and in its descent liberated catches which held the steam and exhaust valves from opening. A similar device controlled the equilibrium valve, and could be set to give a pause at the end of the piston's down-stroke, so that the pump-cylinder might have time to become completely filled. The Cornish engine is interesting as the earliest form which achieved an efficiency comparable with that of good modern engines. For many years monthly reports were published of the " duty " of these engines, the " duty " being the number of foot-pounds of work done per bushel or (in some cases) per cwt. of coal. The average duty of engines in the Cornwall district rose from about 18 millions of foot-pounds per cwt. of coal in 1813 to 68 millions in 1844; after which less effort seems to have been made to maintain a high efficiency (Prot. Inst. C.E., 1863, vol. 23). In individual cases much higher results were reported, as in the Fowey Consols engine, which in 1835 was stated to have a duty of 125 millions. This (to use a more modern mode of reckoning) is equivalent to the consumption of only a little more than 14 lb of coal per horse-power per hour—a result surpassed by very few engines in even the best recent practice. It is difficult to credit figures which, even in exceptional instances, place the Cornish engine of that period on a level with the most efficient modern engines—in which compound expansion and higher pressure combine to make a much more perfect thermodynamic machine; and apart from this there is room to question the accuracy of the Cornish reports. They played, however, a useful part in the process of steam engine development by directing attention to the question of efficiency, and by demonstrating the advantage to. be gained by high pressure and expansive working, at a time when the theory of the steam engine had not yet taken shape. 19. The final revival of the compound engine did not occur until about the middle of the 19th century, and then several agencies combined to effect it. In 1845 M'Naught introduced a plan of improving beam engines of the Bcnompound glne, original Watt type, by adding a high-pressure cylinder whose piston acted on the beam between the centre and the flywheel end. Steam of higher pressure than had formerly been used, after doing work in the new cylinder, passed into the old or low-pressure cylinder, where it was. further expandea. Many engines whose power was proving insufficient for the extended machinery they had to drive were " MNaughted " in this way, and after conversion were found not only to yield more power but to show a marked economy of fuel. The compound form was selected by William Pole for the pumping engines of Lambeth and other waterworks about 185o; in 1854 John Elder began to use it in marine engines; in 1857 E. A. Cowper added a steam-jacketed intermediate reservoir for steam between the high and low pressure cylinders, which made it unnecessary for the low-pressure piston to be just beginning when the other piston was just ending its stroke. As facilities increased for the : use of high-pressure steam, compound expansion came into more general use, its advantage becoming more conspicuous with every increase in boiler pressure —until now there are few large land engines and scarcely any marine engines that do not employ it. In marine practice, where economy of fuel is a much more important; factor in determining the design than it is on land, the principle of compound expansion has been greatly extended by the nitroduction of triple and even quadruple expansion engines, in which the steam is made to expand successively in three or in four cylinders. In locomotive engines, where other considerations are of more moment than the saving of coal, compound expansion has found some application, but its use there is comparatively rare. 2o. The adaptation of the steam engine to railways, begun by been for the new possibilities which the introduction of the Trevithick, became a success in the hands of George Stephen- Application son, whose engine, the " Rocket," when tried along to Loco- with others, in 1829, not only distanced its colnmotfres• petitors but settled once and for all the question tion for the first time to commercial success. 22. With improvements in the details of design and construction it gradually became practicable to use higher steam pressures Rise In and higher piston speeds, and consequently to steam obtain not only greater efficiency, but also a greater Pressure amount of power from engines of given bulk. In and in 1872 Sir F. J. Bramwell, describing the typical Piston Speed. marine practice of that time, gave a list of engines, all compound, in which the boiler pressure ranged from 45 to 6o lb, the mean piston speed was 350 ft. per minute, and the consumption of coal 2 to 22 lb per 'hour per indicated horse-power. In 1881 F. C. Marshall gave a similar list, in which the boiler pressure was 77 lb, the speed 46o ft. per minute, and the consumption a trifle under 2 lb. These were compound engines with expansion in two stages. The triple expansion engine, introduced by Dr A. C. Kirk Triple and in 1874, did not come into general use until after Quadruple 188r. It became the normal type of marine engine, Expansion. with pressures ranging, as a rule, from 15o to 200 lb, piston speeds generally of 500 or 600 ft. per minute, but sometimes as high as 900 or 1000, and coal consumption of about 11 lb per hour per indicated horse-power. In some instances quadruple expansion has been preferred, with some-what higher pressures, but it can scarcely be said to be established that the advantage of adding a fourth stage clearly compensates for the extra complication. Some particulars of the dimensions reached in modern practice will be given later. Several of the vessels engaged 'in the Transatlantic passenger service, and also a few armoured cruisers, have engines in which the twin sets together have an indicated horse-power exceeding 30,000. But even these figures are eclipsed in ships which are driven by turbine engines. The cruisers of the " Invincible " class have turbine engines of 41,000 horse-power, and the turbines of the great Cunarders "Lusitania" and "Mauretania" (1907) develop about 70,o00 h.p. in propelling these ships at a speed of 25 knots. It may be questioned whether such gigantic concentrations of power for the propulsion of a ship would have been practicable' had' it notsteam turbine has opened up. 23. The invention of the steam turbine has in fact revolutionized marine engine practice, so far as fast vessels are concerned, and has supplied a formidable rival to the Intro. reciprocating engine for use on land. The steam ductlon turbine has been brought to a degree of efficiency of the which places it, in respect of economy in steam steam and coal consumption, on a somewhat higher level Turbine. than the best engines of the older type in cases where a large amount of power is to be generated. Its greater simplicity, compactness and freedom from vibration are merits which have already gone far to secure for it a preference, notwithstanding the short time that has passed since it became known as a practicable engine. The largest demands for power 'occur in fast passenger vessels, in war-ships and in stations from which electric energy is distributed for traction or other uses; in all these cases the steam turbine is now taking the leading place. It is to the inventive genius of the Hon. C. A. Parsons that we owe not only the main idea of the modern steam turbine, but also the working out of many novel mechanical details which have been essential to success, as well as the adaptation of the turbine to marine propulsion. 24. In the steam turbine, as in the water turbine (for which see HYDRAULICS), the force directly operative to do useful work is derived from the kinetic energy of the operative fluid, either by the impulse of a jet or jets sliding over movable blades, or by the reaction of orifices or guides from which the jets issue. The pressure, instead of being exerted on a piston, is employed in the first instance to set the fluid itself in motion. There is a conversion of pressure-energy into velocity-energy as a preliminary step towards obtaining the effective work of the machine. But in a steam turbine this implies velocities which are immensely greater than those with which water turbines have to deal, in consequence of the much smaller density of steam as the moving fluid. Attempts to design a steam turbine were made by numerous inventors, but fell short of practical success mainly because of the difficulty of arranging for a sufficiently high velocity in the working parts to utilize a -reasonably large fraction of the kinetic energy of the steam, the principle involved being' that for good efficiency the velocity of the blades should approximate to half the velocity of the jets which strike them. There is a further difficulty in getting the energy of the steam into a suitable kinetic form, namely, to get the stream of issuing particles to take a single direction, without undue dispersion, when steam is allowed to expand through an orifice from a chamber at high pressure into a space where the pressure is greatly less. In 1889 Dr Gustaf de Laval introduced a form of steam turbine in which both of these difficulties were to a great extent over-come, partly by the special form of the nozzle used to produce the steam jet and partly by features of design which allowed an exceptionally high speed to be reached in the wheel carrying the vanes against which the steam impinged. This simple type of turbine, which will be described in a later section of this article, has met with considerable success, especially in comparatively small sizes, as an engine for driving electric generators. Its efficiency is fairly good, but it is not well adapted for work on a large scale, and it has not been applied to the propulsion of ships. Parsons attacked the problem at an earlier date, in an entirely different way in the invention of his " compound " turbine. By dividing the whole expansion of the steam into a great number of successive and separate steps he limited the velocity acquired at each step to such an extent as to make it comparatively easy to extract the greater part of the kinetic energy, as work done upon the moving blades, without making the velocity of these blades inconveniently high. Moreover, in Parsons's compound turbine the range of pressure through which the steam expands in each separate step is too small to give rise to any difficulty in the formation of the jets. The guide blades, which form the jets, are distributed round the whole whether horse traction or steam traction was to be used on railways. The principal features of the " Rocket " were an improved steam-blast for urging the combustion of coal and a boiler (suggested by Booth) in which a large heating surface was given by the use of many small tubes through which the hot gases passed. Further, the cylinders, instead of being vertical as in earlier locomotives, were set in at a slope, which was afterwards altered to a position more nearly horizontal. To these features there was added later the " link motion," a contrivance which enabled the engine to be easily reversed and the amount of expansion to be readily varied. In the hands of George Stephenson and his son Robert the locomotive took a form which has been in all essentials maintained by the far heavier locomotives of to-day. 21. The first practical steamboat was the tug " Charlotte Dundas," built by William Symington, and tried in the Forth Appikafoe and Clyde Canal in 1802. A Watt double-acting to steam- condensing engine, placed horizontally, acted directly boats. by a connecting-rod on the crank of a shaft at the stern, which carried a revolving paddle-wheel. The trial was successful, but steam towing was abandoned for fear of injuring the banks of the canal. Ten years later Henry Bell built the " Comet," with side paddle-wheels, which ran as a passenger steamer on the Clyde; but an earlier inventor to follow up Symington's success was the American, Robert Fulton, who, after unsuccessful experiments on the Seine, fitted a steamer on the Hudson in 1807 with engines made to his designs by Boulton and Watt, and brought steam naviga- circumference of the revolving wheel, and all the revolving blades are consequently in action at once. The steam streams from end to end through an annular space between a revolving drum and the casing which surrounds it. Parallel rings of fixed guide blades project inwards from the casing at suitable distances, and between these are rings of moving blades which project out-wards from the drum and revolve with it. At each step in the expansion the steam streams through a ring of fixed guide blades, and the streams so formed impinge on the next ring of moving blades, and so on. The construction, which is of great simplicity, will be described later; it lends itself well to the generation of power on a large scale, especially in cases where a fairly high speed of rotation is wanted. The more powerful the turbine the less important do various inevitable sources of loss become; and hence, though the small turbines which were first built were less economical than reciprocating engines, the advantage is the other way where large powers are concerned. 25. Parsons introduced his compound steam turbine in 1884. For some years it was made in small sizes only, and the steam was discharged to the atmosphere without condensation. So long, however, as this was done the steam turbine was sacrificing one of its most important advantages, namely, its exceptional capacity for utilizing the energy of low-pressure steam down to the lowest vacuum obtainable in a condenser. In 1891 it was first fitted with a condenser, and it then began to be used in electric supply stations. Its efficiency at that date was found, in tests made by the present writer, to be comparable with that of good reciprocating compound engines, but the figures then obtained were much improved on later in turbines of larger size and modified design. The first application to marine propulsion was in the " Turbinia," in 1897. The success of this little experimental vessel of loo tons, which with its horse-power of 2100 made a record in speed for a ship of any size, was soon followed by the application of the turbine to various war-ships and other steamers. In war-ships the use of steam turbines has a special advantage in enabling the machinery to be kept at a low level, beneath the protective deck, in addition to the general advantages of reduced bulk, reduced vibration, reduced liability to break-down, and reduced consumption of coal and of oil which are common to vessels of all classes. The successful trials of the cruiser " Amethyst " in 1904 demonstrated these advantages so conclusively that all new war-ships for the British navy, from battleships to torpedo-boats are being fitted with steam turbines. It is also used in many cross-channel packets, as well as in the largest ocean-going passenger vessels. The turbine-driven steamers " Lusitania and " Mauretania " (1907) are the most powerful and the fastest ocean-going vessels afloat. The rapid development of the marine steam turbine makes it probable that it will displace the reciprocating engine in all large and fast ships. For slow-going cargo-boats it is at a disadvantage, unless gearing is resorted to, on account of the difficulty of securing a sufficiently high peripheral velocity in the turbine drums without making the turbines unduly bulky, and the leakage losses (due to steam passing through the clearance spaces over the tips of the blades) unduly large. Experiments by Parsons (Trans. Inst. Nay. Arch., 1910) on a ship in which a slow-running propeller is driven through reducing-gear from a high-speed turbine, have given highly promising results. Enough has been said to show that the invention of the steam turbine is the most important step in steam engineering since the time of Watt. It is the first solution of the problem of using steam efficiently in an engine without reciprocating parts. The object in most steam engines is to deliver power to revolving machinery, and much ingenuity has been expended in attempts to devise engines which will produce rotation directly, instead of by conversion of reciprocating motion. No rotary engine, however, was permanently successful until the steam turbine took a practical form. 26. In the early development of the steam engine inventors had little in the way of theory to guide them. Watt had the advantage, which he acknowledges, of a knowledge of Joseph Black's doctrine of latent heat; but there was no philosophy of the relation of work to heat until long after the inventions of Watt were complete. The theory of the steam Theory of engine as a heat engine dates from 1824, when steam N. L. Sadi Carnot published his Rlflexions sur Engine. la puissance motrice du feu, and showed that heat does work only by being let down from a higher to a lower temperature. But Carnot had no idea that any of the heat disappears in the process, and it was not until the doctrine of the conservation of energy was established in 1843 by the experiments of J. P. Joule that the theory of heat engines began a vigorous growth. From 1849 onwards the science of thermodynamics was developed with extraordinary rapidity by R. J. M. Clausius, W. J. Macquorn Rankine and William Thomson (Lord Kelvin) and was applied, especially by Rankine, to practical problems in the use of steam. The publication in 1859 of Rankine's Manual of the Steam Engine formed an epoch in the history of the subject by giving inventors a new basis, outside of mere empiricism, from which they could push on the development of the steam engine. Unfortunately, however, it was assumed that the cylinder and piston might be treated as behaving to the steam like non-conducting bodies—that the transfer of heat between the steam and the metal was negligibly small. Rankine's calculations of steam consumption, work and thermodynamic efficiency involve this assumption, except in the case of steam-jacketed cylinders, where he estimates that the steam in its passage through the cylinder takes just enough heat from the jacket to prevent a small amount of condensation which would otherwise occur as the process of expansion goes on. If the transfer of heat from steam to metal could be overlooked, the steam which enters the cylinder would remain during admission as dry as it was before it entered, and the volume of steam consumed per stroke would correspond with the volume of the cylinder up to the point of cut-off. It is here that the actual behaviour of steam in the cylinder diverges most widely from the behaviour which the theory assumes. When steam enters the cylinder it finds the metal chilled by the previous exhaust, and a portion of it is at once condensed. This has the effect of increasing, often very largely, the volume of boiler steam required per stroke. As expansion goes on the water that was condensed during admission begins to be re-evaporated from the sides of the cylinder, and this action is often prolonged into the exhaust. It is now recognized that any theory which fails to take account of these exchanges of heat between the steam and its metal envelope fails also to yield even comparatively correct results in calculating the relative efficiency of various steam pressures or various ranges of expansion. But the exchanges of heat are so complex that there seems little prospect of submitting them to any comprehensive theoretical treatment, and information is rather to be sought from the scientific analysis of experiments with actual machines. 27. Formation of Steam under Constant Pressure.—In attempting a brief sketch of steam engine theory it is necessary to begin by giving some account of the properties of steam, so far as they are relevant. The properties of steam are most conveniently stated by referring in the first instance to what happens when steam is formed under constant pressure. This is substantially the process which occurs in the boiler of a steam engine when the engine is at work. To fix the ideas we may suppose that the vessel in which steam is to be formed is a long upright cylinder fitted with a piston which may be loaded so that it exerts a constant pressure on the fluid below. Let there be, to begin with, at the foot of the cylinder a quantity of water (which for convenience of numerical statement we shall take as 1 Ib), at any temperature to; and let the piston press on the surface of the water with a force of p lb per square foot. Let heat now be applied to the bottom of the cylinder. As it enters the water it will produce the following effects in three stages r. The temperature of the water rises until a certain temperature t is reached, at which steam begins to be formed. The value of t depends on the particular pressure p which the piston exerts. Until the temperature t is reached there is nothing but water below the piston. 2. Steam is formed, more heat being taken in. The piston (which is supposed to exert a constant pressure) rises. No further increase of temperature occurs during this stage, which continues until all the water is converted into steam. During this stage the steam which is formed is said to be saturated. The volume which the piston encloses at the end of this stage-the volume, namely, of 1 lb of saturated steam at pressure p (and temperature t)-will be denoted by v in cubic feet. 3. If after all the water is converted into steam more heat be allowed to enter, the volume will increase and the temperature will rise. The steam is then said to be superheated. The difference between saturated and superheated steam may be expressed by saying that if water (at the temperature of the steam) be mixed with steam some of the water will be evaporated if the steam is superheated, but none if the steam is saturated. Any vapour in contact with its liquid and in thermal equilibrium is necessarily saturated. When saturated its properties differ considerably, as a rule, from those of a perfect gas, especially at high pressures, but when superheated they approach those of a perfect gas more and more closely the further the process of superheating is carried, that is to say, the more the temperature is raised above t, the temperature of saturation corresponding to the given pressure p. 28. Relation of Pressure and Temperature in Saturated Steam.-The temperature t at which steam is formed depends on the value of p. Their relation was determined with great care by Regnault (Mem. Inst. France, vol. xxi.). The pressure of saturated steam rises with the temperature at a rate which increases rapidly in the upper regions of the scale. This will be apparent from the first and second columns of the following table. The first column gives the temperature on the Centigrade scale; the second gives the corresponding pressure in pounds per square inch. 29. Relation of Volume and Temperature.-The same table shows the volume v in cubic feet occupied by lb of saturated steam at each temperature. This is based on the investigations of H. L. Callendar who has shown (see THERMODYNAMICS and VAPORIZATION) that an equation of the form v= -r+b-c is applicable to water vapour, whether saturated or superheated, within the limits of experimental error throughout the range of pressure that is important in engineering practice. In this equation r is the absolute temperature, R and b are constants and c is a term varying inversely as a certain power of the temperature. By aid of this equation, in conjunction with the results of various experiments on the latent heat and other properties of steam, Callendar has shown that it is possible to frame expressions from which numerical values of all the important properties of steam may be derived throughout a range of saturation temperatures extending from o° C. to 200° C. or so. The values so obtained are thermodynamically consistent with one another, and are in good agreement with the most authoritative experimental results. They are accordingly to be accepted in lieu of those given in earlier steam tables which depended on measurements by Regnault, and are now known to be in some particulars erroneous. R. Mollier has applied Callendar's method with great completeness to the calculation of steam tables, and the figures given here are adapted from his results.' In addition to the relation of temperature, pressure and volume, the table shows other properties of steam which will be explained as we proceed. 30. Supply of Heat in Formation of Steam under Constant Pressure.-We have next to consider the supply of heat in the imaginary experiment of § 27. During the first stage, until the temperature rises from its initial value to to t, the temperature at which steam begins to form under the given pressure, heat is required only to warm the water. Since the specific heat of water is nearly constant, the amount of heat taken in during the first stage is approximately 1-to thermal units, or J (t-to) foot-pounds, J being Joule's equivalent, and this expression for it will generally serve with sufficient accuracy in practical calculations. More exactly, however, the heat taken in is somewhat greater than this at high temperatures, for Regnault's experiments show that the specific heat of water increases slightly as the temperature rises. In stating the amount of heat required for this first stage, to must be taken as a known temperature; for convenience in numerical statement the temperature o° C. is usually chosen as an arbitrary starting-point from which the reception of heat is to be reckoned. We shall employ the symbol h to designate the heat required to raise I lb of water from o° C. to the temperature t at which steam begins to form. During the first stage, sensibly all the heat supplied goes to increase the stock of internal energy which the fluid possesses, the amount of external work which is done by the expansion of the fluid being negligible. The heat taken. in during the second stage is what is called the latent heat of steam, and is denoted by L. Of it a part is spent in doing external work, namely, p multiplied by the excess of the volume of the steam v over the volume of the water w, and the remainder is the difference of internal energy between 1 lb of steam at-i and i lb of water at t. 31. Total Heat of Steam.-Adding together the heat taken in during the first and second stages, we have a quantity designated ' R. Moilier, Neue Tabellen and Diagramnie fur Wasserdampf (Berlin, 1906). See also Ewing's Steam Engine (3rd ed., 1910). Tempera- Pressure Volume Total Heat. Entropy. ture. It, per cub. ft. - --- - - Centigrade. sq. in. per Its. Of Water. Of Steam. Of Water. Of Steam. o 0.089 3283 0 594'7 0 2'178 g 0'127 2354' 5'0 597'1 o.o18 2.148 10 0.178 1708• 10.0 599'4 0.036 2.119 15 0 246 1253 ' 15.0 601.8 0.054 2.091 20 0.336 931 ' 20 *0 6041 0 '071 2.064 25 0'455 699'5 25'0 606.5 0.088 2.039 30 0.610 530'7 30.0 6o8 8 0104 2.015 35 o•8o9 406'8 35.0 611.1 0.121 1.991 40 1.062 314.8 40.1 613.5 0'137 1'969 45 1'381 245'8 45'1 615 '8 0.153 1'947 50 I.78 1937 50.1 618 •o 0.169 1 '927 55 227 153'9 55'I 6203 0.184 1.907 6o 2.88 123.3 6o • f 622.6 0.199 1.888 65 3 61 995 652 6248 0-214 I.870 70 4'51 80.9 70.2 6270 0.229 1.852 75 5'58 6624 75.3 629'2 0'244 1.835 8o 6.86 54.6o 8o •3 6313 0 .258 1.819 85 8'38 45'29 85'3 633.5 0.272 1.803 90 10.16 3779 90.4 6356 0286 1.788 95 1226 3.1'71 95'5 637'6 0.300 1.773 100 14.70 26.75 100'5 639'7 0'314 1.759 105 17.52 22.69 105.6 641 '7 0.327 I.745 110 20.79 19'34 110'7 643.6 0'340 1732 115 2455 1656 1158 6455 0.354 1'719 120 28.83 14.25 120.9 647'4 0'367 1.706 125 33'72 12.30 1260 6492 0.379 1.694 130 3926 10 .67 131 •I 651 •o 0.392 1682 135 45'51 9.29 136.2 652.8 0.405 I.671 140 52.56 8.12 141.3 654.5 0.417 I.66o 145 6o'42 7'13 146'4 656'1 0'430 1.649 I 150. 69'24 6'274 151.6 657.8 0.442 1.638 155 79'04 5'542 1567 6593 0'454 1.628 16o 89.93 4'910 161.9 66o.8 0.466 1.618 165 101.98 4.363 167.1 662.3 0.478 I.6o8 170 115 27 3.891 172 2 663'7 0'489 1.599 175 129.9 3'478 1774 665 •o o •501 1.589 18o 145.9 3'116 1826 6663 0512 I.580 185 1634 2 "800 187.9 667.6 0.524 1571 190 182.6 2.523 193.1 668.8 0.535 1.563 195 203.4 2.279 198.3 670.0 0.546 I '554 200 226.0 2.063 203.6 671.1 0.557 I'546 205 250 5 1.874 208.9 672.2 0.568 1.538 210 277.2 1703 214.1 673 2 0.579 1 '530 215 306.8 1.546 2194 674'1 0.590 1.522 by H which-may be called the heat of formation of I lb of saturated steam :- H=h+L. The heat of formation of I lb of steam, when formed under constant pressure from water at any temperature to, is H-ho, where ho corresponds to to. It has been pointed out by Moilier that for the purpose of calculations in technical thermodynamics it is convenient to add to the heat of formation the quantity pw/J, which represents the thermal equivalent of the work spent in introducing the water under the piston, against the constant pressure p, before the operation of heating imagined in § 27 begins, w being the volume of the water. We thus obtain a quantity which in its numerical values differs only very slightly from H, namely I=H+pw/J• We shall call this the total heat of saturated steam. Values of I are stated in the table. Since the volume of i lb of water is only Properties of Saturated Steam. 0016 cub. ft. the term pw/J is numerically insignificant except at the highest pressures. Similarly, in reckoning the total heat of water Ia we add pw/J to h, and this quantity is also given in the table. The latent heat L is to be found from the table by subtracting I,s, the total heat of water, from the total heat of steam. We shall use the centigrade scale of temperature throughout this article, and accordingly the total heats are expressed in terms of a unit involving the centigrade degree, namely, the quantity of heat required to raise the temperature of unit mass of water through I° C. at 15° C. With this unit of heat the mechanical equivalent is 1400 foot-pounds when the unit of mass is the lb, and is 427 ilogram-metres when the unit of mass is the kilogramme. 32. Internal Energy.-Of the heat of steam the part pv/J is spent in doing external work. The remainder has gone to increase the stock of internal energy which the substance possesses. In dealing with the heat required to produce steam we adopted the state of water at o°C. as an arbitrary starting-point from which to reckon the reception of heat. In the same way it is convenient This formula is easily applied to the construction of, the adiabatic curve when the initial pressure and the pressure after expansion are given, the corresponding values r and L being found from the table. 37. Ideal Action. of Heat Engine.—According to the principles of thermodynamics (q.v.), the action of a heat engine depends on its receiving heat at a temperature higher than that at which it is capable of rejecting heat to surrounding objects. The working substance in the engine must necessarily pass from an upper temperature, at which it takes in heat, to a lower temperature, at which it rejects heat, the difference. between the heat taken in and the heat rejected being the thermal equivalent of the work done. It may readily. be shown. that when the conditions are such as to make this difference as great as possible--in other words, to make the efficiency reach its ideal limit—the ratio of the heat taken in to the heat rejected depends only on the temperature at which reception and rejection of heat occur. Calling Ti and r.2 the absolute temperatures at which heat is taken in and rejected respectively, and Ql and Q2 the quantities of heat taken in and rejected, the limit of efficiency is reached when Qi/Qz = 2. The efficiency then has the value to use this arbitrary starting-point in reckoning what may be called the internal energy of the substance, which is the excess of the heat taken in over the external work done by the substance during its reception of heat. Thus the internal energy E of i lb of saturated steam at pressure p is equal to the total heat I, less that part of the total heat which is spent in doing external work, or E = I •—pv/J. The notion of internal energy is useful in calculating the heat taken in or rejected by steam during any stage of its expansion or compression in an engine., When a working substance passes from one condition to another its gain or loss of heat is determined by the equation Heat taken in = increase of internal energy +external work. Any of the terms of this equation may be negative ; the last term is negative when work is done, not by but upon the substance. 33. Wet Steam.—In calculations which relate to the action of steam in engines we have often to deal, not with dry saturated steam, but with wet steam, or steam which either carries in suspension, or is otherwise mixed with, a greater or less proportion of water. In any such mixture, assuming it to be in equilibrium, the steam and water have the same temperature, and the steam is saturated. The dryness of wet steam is measured by the proportion q of dry steam in each pound of the mixed substance. When that is known it is easy to determine the other physical constants: thus Latent heat of i lb of wet steam = qL; Total heat of 1 lb of wet steam = la,-1 L; Volume of i lb of wet steam = qv+(i -O., = qv very nearly, unless the steam is so wet as to consist mainly of water. 34. Superheated Steam.—Steam is superheated when its temperature is raised, in any manner, above the temperature corresponding to saturation at the actual pressure. When considerably super-heated, steam approximates in behaviour to a perfect gas. The specific heat during superheating is nearly constant at low pressures, its value being approximately o•48; at high pressures it is higher, especially when the amount of superheating is slight: Callendar's equations enable it to be calculated for any assigned conditions of temperature and pressure. They also allow a direct determination to be made of the total heat of superheated steam of given temperature and pressure, and from this. by comparison. with the total heat of saturated steam at the same pressure, the mean specific heat over any stated range of superheating,may be found. Calling I, the total heat of steam in the saturated condition, when the temperature is t, K the mean specific heat in superheating at constant pressure to a higher temperature t' and I' the total heat in the superheated state, we have I' = Ia + K(t' — t). The following are values of K: Temperature of Temperature of Saturation tin °C. Superheatt'in°C. 80° 120° 160° I800 200° 100° 0.49 150° 0.49 0'51 200° 0.49 0.51 0.54 0.57 25o° 0.48 0.50 0.53 0.56 0.59 300° 0.48 0.50 0.52 0.54 0.57 35o° 0.48 0.49 0.51 0.5,3 0.56 4000 0.48 0.49 0.51 0.52 0-55 450° 0.48 0.49 0.51 0.52 0.54 35. Isothermal Expansion of Steam.—The expansion of volume which occurs during the conversion of water into steam under constant pressure is isothermal. From what has been already said it is obvious that steam, or any other saturated vapour, can be expanded or compressed isothermally only when wet, and that evaporation (in the one case) or condensation (in the other) must accompany the process. Isothermal lines for a working substance which consists of a liquid and its vapour are straight lines of uniform pressure. 36. Adiabatic Expansion of Steam.—If steam initially dry be allowed to expand adiabatically (namely, without taking in or giving out any heat) it becomes wet. A part of the steam is condensed by the process of adiabatic expansion, at first in the form of minute particles suspended throughout the mass. The temperature and pressure fall; and, as that part of the substance which remains uncondensed is saturated, the relation of pressure to temperature throughout the expansion is that which holds for saturated steam. Before expansion let the initial dryness of the steam be ql and its absolute temperature T. Then, if it expand adiabatically until its temperature falls to T, its dryness after expansion may be shown to be 1l q=r, +loge T/ L, and L are the latent heats (in thermal units) of r lb of steam before and after expansion respectively. When the steam is dry to begin with, qi = 1. (Ql-Q2)IQl = (Ti ` T2)/T1 and W, the work done, is QW(TI-Try)/ri. In the ideal engine imagined by Carnot the action is of this simple character. The working substance is brought by adiabatic compression from 'the lower to the upper extreme of temperature. It then takes in heat, without changing in temperature. Next, it expands adiabatically until its temperature falls to' the lower extreme and finally at that temperature it rejects enough heat to restore it to its initial state, thereby completing a cycle of operations. 38. Carnot's Cycle with Steam for Working Substance.—We are now in a position to study the action of a heat engine employing steam as the working substance. To simplify the first consideration as far as possible, let it be supposed that we have a long cylinder composed of non-conducting material except at the base, and fitted with a. non-conducting piston; also a source of heat A at some temperaturerl; a receiver of heat, or, as we may now call it, a con-denser C, at a lower temperature Ti; and'a non-conducting cover B. Then we can perform as follows the ideal reversible cycle of operations first described by Carnot, which gives the highest possible efficiency attainable in any heat engine. To fix the ideas, suppose that there is lib of water in the cylinder to begin with, at the temperature Ti :- f. Apply A, and allow the piston to rise. The water will take in heat and be converted into steam, expanding isothermally at constant pressure pi. This part of the operation is shown by the line ab in fig. 9. 2. Remove A and apply B. Allow the expansion to continue adiabatically (bc) with falling pressure, until the temperature falls to ,T{,2. The pressure will then be C2, namely, the pressure given in the table corresponding to T2. 3. Remove B, apply C, and compress. Steam is condensed by rejecting heat to C. The action is isothermal, and the pressure remains p2. Let this be continued until a certain point d is reached, after which adiabatic compression will complete the cycle. 4. Remove C and apply B. Continue the compression, which is now adiabatic. If the point d has been rightly chosen, this will complete the cycle by restoring the working fluid to the state of water at temperature Ti. The " indicator diagram " or diagram exhibiting the relation of pressure to volume for such a cycle is given in fig. 9. Since the process is reversible, and since heat is taken in only at Ti and rejected only at Ti, the ideal conditions for perfect efficiency are satisfied, and accordingly the efficiency is (Ti —T2/Ti. The heat taken in per lb of the fluid is Li, and the work done is Ll(Ti-T2)/Ti, a result which may be used to check the calculation of the diagram. 39. Efficiency of a Perfect Steam Engine: Limits of Temperature.—If the action here described could be realized in practice, we should have a thermodynamically perfect steam engine using saturated steam. The fraction of the heat supplied to it which such an engine would convert into work would depend simply on the temperature, and therefore on the pressure, at which the steam was produced and condensed. The temperature of, condensation is limited by the consideration that there must be an abundant supply of some substance to absorb the rejected heat; water is actually used for this purpose, so that T2 has for its lower limit the temperature of the available water-supply. To' the higher temperature r, a practical limit is set by the mechanical difficulties, with regard to strength and to lubrication, which attend the use of high-pressure steam. In engines of ordinary construction the pressure is rarely so much as 250 lb per sq. in. It must not be supposed that the efficiency (ri—r2)/rl is actually determined by Regnault, between the limits of rl and r2. On this` attained, or is even attainable. Many causes conspire to prevent steam engines from being thermodynamically perfect, and some of the causes of imperfection cannot be removed. 4o. Engine with Separate Organs.—In the ideal engine represented in fig. to the functions of boiler, cylinder and condenser are combined in a single vessel; but, provided the working substance passes through the same cycle of operations, it is indifferent whether these are performed in several vessels or in one. To approach a little more closely the conditions that hold in practice, we may think of the engine as consisting of a boiler A (fig. to) kept at rl, a nonconducting cylinder and piston B, a surface con-denser C kept at T2, and a feed-pump D which restores the condensed water to the boiler. When the several organs of the engine are separated in this way we can still carry out the first three stages of the cyclic process described in § 38. The first stage of that cycle FIG. io.—Organs of a Steam Engine. cofrresp m n dsfto the themission ler into the cylinder. Then the point known as the point of cut-off is reached, at which admission ceases, and the steam already in the cylinder is allowed to expand, exerting a diminishing pressure on the piston. This is the second stage, or the stage of expansion. The process of expansion may be carried on until the pressure falls to that of the condenser, in which case the expansion is said to be complete. ,At the end of the expansion release takes place, that is to say, communication is opened with the con-denser. Then the return stroke begins, and a period termed the exhaust occurs, that is to say, steam passes out of the cylinder, into the condenser, where it is condensed at the pressure in the condenser, which is felt as a back pressure opposing the return of the piston. So far, all has been essentially reversible and identical with the corresponding parts of Carnet's cycle. But we cannot complete the cycle as Carnet's cycle was completed. The existence of a separate condenser makes the fourth stage, that of adiabatic compression, impracticable, and the best we can do is to continue the exhaust until condensation is complete, and then return the condensed water to the boiler. 41. Rankine Cycle.—It follows that the ideal cycle of Carnot is not an appropriate standard with which to compare the action of a. real steam engine. Instead of it we have, in the engine with separated organs, a cycle which is commonly called• the Rankine cycle, which differs from the Carnet cycle only in this, that the stage of adiabatic compression, is wanting and its place is taken by a direct return of the condensed water to the boiler, a process which makes the water receive heat at various temperatures, ranging from the temperature of the condenser up to that of the boiler. The chief part of the heat which the working substance receives is still taken in at the upper limit of temperature, during the process of changing from water to steam. But a small part is taken in at lower temperatures, namely, in the heating of the feed water in its transfer to the boiler. Any heat so taken in has less availability for conversion into work than if it were taken in at the top of the range, and consequently the ideal efficiency of the cycle falls somewhat short of this ideal reached in the cycle of Carnot. But the principle still applies that with respect to each portion of the heat that is taken in, the fraction convertible into work under ideally favourable conditions is measured by (T —r2)/r, where r is the absolute temperature at which that portion of heat is received, and r2 is the temperature at which heat is rejected. Accordingly, we may investigate as follows the ideal performance of an engine following the Rankine cycle. Let SQ represent that portion of the whole heat which is taken in at any temperature T. Then the greatest amount of work obtainable from that portion of heat is SQ(r-T2)/T, and the whole amount of work ideally obtainable in the complete process is found by calculating,XSQ(r-r2)/T where the summation includes all the heat that is taken in. In a steam engine using saturated steam the principal item in this sum is the latent heat L1, which is taken in at constant temperature el, during the change of state from water to steam. But there is, in addition, the heat taken in by the feed-water before it reaches the temperature at which steam is formed, and this may be represented as the sum of a series of elements aSr taken in at varying temperatures r, where a is the specific heat of water. Thus if W represents the thermal equivalent of the work theoretically obtainable per lb of steam, under ideally favourable conditions, W—zaST(T—T2) + LI(T,—T2. T TI The experiments of Regnault show that a, within the limits of temperature that obtain in boilers, is a nearly constant quantity, and no serious error will be introduced in this integration by treating it as a constant, with a value equal to the mean value, as basis `V = u(TI—T2) —aT2 logs TI LLl(Tl—T2). T2 Tl It is usual to take a as practically equal to 1, which makes W = (TI—T2) l t + I I) —es logs'L - \\ T1/t T2 This expresses the greatest amount of work which each pound of steam can yield when the temperature rl at which it reaches the engine and the temperature T2 at which it leaves the engine are assigned. It consequently serves as a standard with which the actual performance may usefully be compared. The actual yield per lb of steam is always considerably less, chiefly because the ideal condition of adiabatic expansion from the higher to the lower extreme of temperature is never satisfied. A more simple expression for the work theoretically obtainable per lb of steam when expanded adiabatically under the conditions of the Rankine cycle, is 11—12y where Ii is the total heat of the working substance in the initial state, before the adiabatic expansion, and I2 is its total heat after that expansion. For it may readily be proved that, in an adiabatic process, I1— I2 =if 92 vdp, and this integral is the area of the indicator diagram when the substance is taken in at pl, expanded to P2 and discharged at p2. This expression applies whether the steam is initially superheated or not. I2 will in general be the total heat of a wet mixture, and to calculate it we must know the condition as to wetness which results from the expansion. This is most easily found, especially when there has been initial superheat, by making use of the entropy-temperature diagram to be presently described, or by other graphic methods, for an account of which the reader should refer to the paper by Mollier already cited, or to J. A. Ewing's The Steam Engine and other Heat Engines (3rd ed.). 42. Entropy.—The study of steam-engine problems is greatly assisted by introducing the idea of entropy and making use of diagrams in which the two co-ordinates are entropy and temperature. Entropy is a condition of the working substance defined by the statement that when any quantity of heat SQ is received by, or generated in, or rejected by the substance, when its absolute temperature is r, the substance gains or loses entropy by the amount SQ/r. Thus SQ/r measures the whole change of entropy in a process which involves the taking in or rejection of heat at more than one temperature. We shall denote entropy by 0, and consider it as reckoned per unit of mass of the substance. Since by definition of entropy Sq,=SQ/r, TS¢=SQ, and hence if a curve be drawn with r and ' for ordinates to exhibit the action of a working substance, the area under the curve, or J rd¢, being equal to ESQ, measures the heat which the substance has received or rejected during the operation which the curve represents. In a reversible cycle of operations Carnet's principle shows that ESQ/T=o, and it is obvious in such a case that the entropy returns at the end of the cycle to its primitive value. The same result may be extended to a cycle which includes any non-reversible step, by taking account of the heat generated within the substance by such a step, as if it were heat communicated from outside, in the reckoning of entropy. Thus, for example, if at one stage in the cycle the sub-stance passes through a throttle-valve, which lowers its pressure without letting it do work, the action is equivalent in effect to an adiabatic expansion, together with the communication to the sub-stance, as heat, of the work which is lost in consequence of the irreversible expansion through the throttle-valve taking the place of adiabatic expansion against a piston. If this heat be included in the reckoning ZSQ/T=o for the complete cycle. The entropy-temperature diagram for any complete cyclic process is a closed curve, and the area it encloses, being the excess of the heat received over the heat rejected, measures the work done. The entropy-temperature diagram shares this useful characteristic with the pressure-volume diagram, and in addition it shows directly the heat received and the heat rejected by the areas under the forward and backward limbs of the curve. To draw the entropy-temperature diagram for the ideal steam engine (namely, the engine following the Rankine cycle), we have to reckon first the entropy which water acquires in being heated, and next the entropy Li/ri which is acquired when the conversion into steam has taken place. Reckoning from any standard temperature To, in the heating of the feed-water up to any temperature r, the entropy acquired is _ (T adr 4'w Jr0 T ' and taking a as sensibly constant, sis,,, = a(logsT— logeTO)' During evaporation at Ti a quantity of heat L1 is taken in at temperature r1, and hence the entropy of the steam ska = 44w+LI/ri = a (logsri — logero) +LI/T1• e n rntrnpq p Values of the entropy of water and steam are given in the table. The entropy-temperature diagram for a Rankine cycle is illustrated o in fig. ii, where ab, a logarithmic curve, repre- sents the process of heat- ing the feed-water, and bc the passage from the state of water into that of steam. The diagram is drawn to scale for a case in which steam is formed at a pressure of 180 lb per sq. in., and E condensed at a pressure of I lb per sq. in. After the formation of the steam, the next step in the ideal process is adiabatic expansion from the higher to the lower limit of temperature, which is represented by cd, an adiabatic process being also isentropic. Finally, the cycle is completed by da, which re-presents the condensation of the steam after its temperature has been reduced by adiabatic expansion to the lower limit of temperature. The area abcd represents the work done, and its value per lb of steam is identical with W as reckoned above. The area mabcp is the whole heat taken in, and the area made is the heat rejected. Let a curve cf be drawn to show the values of the entropy of steam for various temperatures of saturation: then if ad be produced to meet the curve in f, the ratio fd/fa represents the fraction of the steam which was condensed during adiabatic expansion. For the point f represents the state of 1 lb of saturated steam, and in the condensation of 1 lb of saturated steam the heat given out would be the area under fa, whereas the heat actually given out in the condensation from d was the area under &I,. Thus the state at d is that of a wet mixture in which da/fa represents the fraction present as steam, and fd/f a the fraction present as water. It obviously follows that by drawing horizontal lines at intermediate temperatures the development of wetness in the expanding steam can be readily traced. Again, if the steam is not dry when-expansion begins, its state may be represented by making the expansion line begin at a point in the line bc, such that the segments into which the line is divided are proportional to the constituents of the wet mixture. In this way the ideal process may be exhibited for steam with any assumed degree of initial wetness. Further, the entropy-temperature diagram admits of ready application to the case of incomplete expansion. Suppose, for example, that after adiabatic expansion from c to c' (fig. 12) the steam is directly cooled to the lower-limit b temperature by the application of cooling water instead of by continued expansion. This process is represented by the line c'ed, which is a curve of constant volume. Its form is determined by the consideration that at any point e the proportion of steam still uncondensed, or le/lk, is such that the mixture fills the same volume as was filled at c'. 43. Entropy-Temperature Diagrams extended to the Case of Super-heated Steam.—In the diagrams which have been sketched, it has r been assumed that the steam is supplied to the engine in a saturated state. To extend the same treatment to the case of super-heated steam, we have to take account of the supplementary supply of heat which the steam receives after the point c is reached, and before expansion be-sins. When superheating is resorted to, as is now often the case in practice, the superheat is given at constant pressure. If K represent as before the mean specific heat of steam at constant pressure, the addition of entropy during the process of superheating from r1 to r' is K(r'—rl). The value of K may be treated as approximately constant, and the addition to the entropy may then be written as K(log r'—log 'el). This gives a line such as cr on the entropy diagram (fig. 13), and increases the value of W by the amount (r'Kdr (r -72) Jr1 r which is represented on the diagram by the area dcrs. During adiabatic expansion from r the steam remains superheated until it reaches the state t, when it is just saturated, and further expansion results in the condition of wetness indicated by s. The extra work dcrs is done at the expense of the extra supply of heat ecru, and an inspection of the diagram suffices to show that the efficiency of the ideal cycle is only very slightly increased by even a large amount of superheating. In practice, however, superheating does much to promote efficiency, because it materially reduces the amount by which the actual performance of an engine falls short of the ideal performance by keeping the steam comparatively dry in its passage through the engine, and thereby reducing exchanges of heat between the steam and the metal. 44. Entropy of Wet Steam.—The entropy of wet steam is readily calculated by considering that the change of entropy in the conversion from water to steam will be qL/r if the steam is wet, q being the dryness. Accordingly the entropy of wet steam at any temperature r is e(loger—logero)+gL/r. Further, since cr for water is practically equal to unity this expression may be written 41= logo-- logero+gL/r. We may apply this expression to trace the development of wetness in steam when it expands adiabatically. In adiabatic expansion = constant. Using the suffix 1 to distinguish the initial state, we therefore have at any stage in the expansion loge- - logero+gL/r = logErl — lore 0+giLi /Tl, from which the dryness at that stage is found, namely, q =L (-1-F log4T') . The expression is not applicable to steam which is initially super-heated. In either case the graphic method of tracing the change of condition during adiabatic expansion is available. 45. Actual Performance.—Trials of engines using saturated steam show that in the most favourable cases from 6o to 65 % of the ideally possible amount of work is realized as " indicated " work. One of the causes of loss is that the expansion is incomplete. In practice the steam is allowed to escape to the condenser, while its pressure is still considerably higher than the pressure at which condensation' is to take place. When the pressure of steam in the cylinder has been so far reduced by expansion that it can only overcome the friction of the piston, there is no advantage in going on further; the indicated work due to any additional expansion would add nothing to the output of the engine, when allowance is made for the work spent on friction within the mechanism itself. Considerations of bulk often lead to an even earlier release of the expanding steam ; and another consideration which points the same way is that when expansion is carried very far, the losses due to exchange of heat between the cylinder and the steam, referred to below, tend to increase. Again, since experience shows that the most efficient engines are those in which the process of expansion is divided into two, three or more stages by the use of compounded cylinders, a certain amount of loss is to be ascribed to the drops in pressure which are liable to occur through unresisted expansion in the transfer of steam from one vessel to another. But the chief cause of loss is to be found in the exchanges of heat which take place between the steam and the metal. In each cylinder there is a process of alternate condensation and re-evaporation--condensation during the period of admission, when the steam finds itself brought into contact with metal which has been.chilled by evaporation during the preceding exhaust stroke, and then evaporation, when the pressure has fallen sufficiently, during the later stage of expansion, as well as during exhaust. The consequence is that the steam, though supplied in a dry 696 state, may contain some 20 - or 30 % of moisture when b C' C complete, and the entropy diagram for the real process of expansion takes a form such as is indicated by the line c'c" in fig. 14. The heat a, supplied is still measured by the area under abc. The condensation from c to c' occurs by contact with the walls of the cylinder; and though part of the heat thus abstracted is restored before release occurs at c", the general result is to make a large reduction in the area of the diagram. 46. Exchanges of Heat between the Steam and the Metal.-The exchanges of heat between steam and metal in the engine cylinder have been made the subject of an elaborate experimental examination admission to the cylinder is yii~~/ by Professors Callender and Nicolson (Prot. Inst. C.E. It should be added that these figures are exceptional. A consumpcxxxi. 147), who studied the cyclic variations of temperature tion of 13 or 14 lb of steam per horse-power-hour is much more usual throughout the metal by means of thermo-electric junctions set even in large and well-designed triple-expansion engines; and with at various depths. They found that the range of temperature two-cylinder compound engines, using steam with an absolute through which the surface of the metal fluctuates is much less than pressure of 100 or 120 lb per sq. in., anything from 14 to 15 lb the range of temperature passed through by the steam; the may be reckoned a good performance. processes of condensation and re-evaporation are slow, and the time 48. Superheated Steam.—The advantage of superheated steam, is too short to bring the surface of the metal into anything like which arises mainly from its influence in reducing the exchange of equilibrium with the steam. The amount of condensation up to heat between the steam and cylinder walls, was demonstrated by the point of cut-off, as inferred from the heat which the metal takes the experiments of Hirn, and as early as 1860 it was not unusual to up, may be much less than the " missing quantity " or difference supply superheaters with marine engines. But the practice of between the steam supplied per stroke and the dry steam then present. superheating was soon abandoned, chiefly on account of difficulties According to their experiments, this discrepancy is accounted for in regard to lubrication. By the introduction of heavy mineral oils by leakage of steam past the valve, direct from the steam chest to this objection has been removed, and a revival in the use of super-the exhaust, and they suggest that this source of error may have heating has taken place, with striking effect on the thermodynamic been present in many estimates of initial condensation based on economy of engines. Experiments made in 1892 by the Alsatian determinations of the missing quantity. This may explain cases Society of Steam Users on a large number of engines showed that in which the initial condensation has apparently been excessive, superheating effected an average saving in coal to the extent of but large amounts of initial condensation certainly do occur, and about 20 %, when the superheater was simply placed in the boiler constitute the most potent factor in making the real performance flue, so that it utilized what would otherwise be waste heat, and of the engine fall short of the ideal standard.' about 12 % when the superheater was separately fired. In those In the alternate condensation and re-evaporation of steam in the cases the steam was superheated only about 30° to 45° C. above the cylinder more heat is given to the metal by each pound of steam that temperature of saturation, but in more recent practice much greater is condensed than is taken from the metal by each pound of steam amounts of superheat have been successfully applied. Professor that is re-evaporated, the temperature of condensation being higher Schroter has tested a factory engine of Iwo h.p., using steam super-than that of re-evaporation. The quantity H1-H2, namely, the heated by some 50° C., and has shown that this amount of super-difference in the heat of formation at the two temperatures, repre- heat is not sufficient to prevent some of the steam from becoming sents this excess of heat. Unless this is in some way abstracted condensed on the walls during admission to the cylinder (Zeitschrift from the metal, the process cannot occur. Hence the action of the des Vereins deutsche?. Ingenieure, vol. xl., 1896). It follows that still cylinder walls in causing alternate condensation and re-evaporation larger amounts of superheat will be thermodynamically advantageous. to occur may be limited by imposing conditions which prevent or That this is the case has been demonstrated by the remarkable results reduce the abstraction of heat. By the use of a steam jacket the which have been obtained with highly superheated steam by W. metal may be prevented from losing heat externally, and may even Schmidt in stationary engines and locomotives. Using a somewhat be made to take up heat. Under these conditions the action special design, Schmidt has shown that it is perfectly practicable to depends on the fact that more water is re-evaporated than is con- employ steam superheated to a temperature of 400° C., and that an densed. To some extent this is a necessary result of the work done efficiency not attainable from steam in any other way is thereby during expansion, which (in an adiabatic process) would make the reached. In several authentic trials of Schmidt engines the consumpsteam become wetter as expansion proceeds, and would therefore tion of steam has been considerably less than so lb per indicated leave more water to be evaporated than is initially condensed by horse-power-hour--a figure which, after allowance is made for the the action of the cylinder walls. But it is important to notice that heat taken up during the process of superheating, represents a better any water which is introduced into the cylinder along with the steam performance than that of the best engines using saturated or slightly will be an important factor in supplying the means by which this superheated steam. It has been found that the consumption of thermal balance is maintained. With steam that is perfectly dry coal, in the boiler and superheater together, need not exceed i t lb before admission the action of the walls takes its limit from the per indicated horse-power even with engines of small power. To condensation which expansion brings about; with steam that is attain this remarkable result it is of course necessary that, after the wet before admission no such limit applies. Hence the importance hot gases from the furnace have passed the superheater, a further of having steam that is initially dry. To secure this, no method extraction of heat from them should take place. This is done by an is so certain as to give some initial superheat to the steam, and economizer or feed-water heater of peculiar form, consisting of a long hence arises the practical advantage which even a small amount of coil of small pipes which maintain a circulation of hot distilled water superheating is found to bring about. through a closed system containing an external coil, which forms the 47. Influence of the Slide-Valve.—To a considerable extent the heater of a tank through which the feed-water passes on its way to slide-valve itself promotes initial condensation, for it requires that the boiler. Somg of the Schmidt engines adopt the principle of the hot steam shall enter the cylinder through a passage which, single action, to & cape the necessity of having a piston-rod and gland immediately before, was chilled by being used for the escape of on the side which is exposed to contact with high-temperature steam ; exhaust steam. The use of entirely distinct admission and exhaust but it is found that this precaution is not essential, and that with ports and valves tends towards economy of steam, partly for this glands of suitable design a double-acting piston may be used without reason and partly because it allows the clearance spaces to be inconvenience, and without risk of undue wear. In some instances reduced. Accordingly, we find that many of the best recorded Schmidt transfers to the partially expanded steam in the intermeresults of tests relate to engines in which each cylinder has four diate receiver a portion of the heat which is conveyed to the engine separate valves of the Corliss or of the drop type. By using hori- by the highly superheated steam; and when this is done, the steam zontal cylinders with admission valves on the top and exhaust may properly receive a still higher degree of initial superheat. valves below, the further advantage of drainage through the exhaust Accordingly, though the initial temperature of the steam may b.e valves is secured. Water which is present at release has then the 4000 C. or more, this is reduced to about 320° by transfer to steam in chance of escaping without being re-evaporated, a circumstance the superheater before the high-pressure steam is admitted to the which contributes largely to reduce the exchange of heat between cylinder. In tests by the present writer of a Schmidt plant indicathe working substance and the metal. Thus a horizontal triple- tang 18o h.p., in which this device was employed, the steam expansion engine with drop valves, by Messrs Sulzer, using saturated was superheated to 3970 C. and 10.4 lb were used per horse-powersteam at an absolute pressure of 16o lb per sq. in., and indicat- hour. In this trial the temperature of the chimney gases was ing not much more than 200 h.p., is reported, in a test by reduced, by the use of Schmidt's feed-water heater, to 175° C., and Professor Stodola, to have used only II.52 lb of steam per indicated the consumption of coal was 1.31 lb per indicated horse-power-hour. horse-power-hour (see Engineer, July i, 1898; also summary of In another trial, of a larger engine with steam superheated to 425° C., trials by B. Donkin, ibid., Oct. 13, 1899). The performance in this the consumption of steam per horse-power-hour was only 9.0 lb. test is equivalent to nearly 69 % of the ideal, an exceptionally high 49. The Indicator.—The actual behaviour of steam in the cylinder figure. In one or two trials of larger engines even this performance of a steam engine is studied by means of the indicator, which serves has been surpassed, 11.2 and 11.3 lb per horse-power-hour having not only to measure the work done but to examine the operation been recorded. In other particularly favourable records of trials of the valves and generally to give much useful information regarding the consumption of steam with triple-expansion engines has been the action of the engine. The indicator, which was invented by found to lie between 12 and 13 lb per horse-power-hour. Some of Watt, and improved by Richards, is a device for automatically the best results relate to slow-running pumping engines fitted with drawing a diagram showing the pressure at all points of the piston's steam jackets on the barrels and on the covers of the cylinders, and stroke. In its most usual form it consists of a small steam cylinder may be taken as showing how influential, in a long-period engine, fitted with a piston which slides easily within it and is pressed the jacket may prove in reducing the evils of initial condensation. down by a spiral spring of steel wire. The cylinder of the indicator In the mean of several apparently authoritative trials by different is connected by a pipe below this piston to one or other end of the observers on different engines the consumption of steam was 12.2 lb cylinder of the engine, so that the piston of the indicator rises and per horse-power-hour, at an absolute pressure of about 140 lb per falls in response to the fluctuations of pressure which occur in the sq. in., which corresponds to 66 % of the ideal performance. engine cylinder. The indicator piston actuates a pencil, which rises and falls with it and traces the diagram on a sheet of paper i See also " Report of Steam Engine Research Committee," Inst. fixed to a drum that is caused to rotate back and forth through a Mech. Eng. (1905). certain arc, in unison with the motion of the engine piston. In M'Naught's indicator the pencil is directly attached to the indicator piston, in Richards's the pencil is moved by means of a system of links so that it copies the motion of the piston on a magnified scale. This has the advantage that an equally large diagram is drawn with much less movement of the piston, and errors which are caused by the piston's inertia are consequently reduced. In high-speed engines especially it is important to minimize the inertia of the indicator piston and the parts connected with it. In Richards's indicator the linkage employed to multiply the piston's motion is an arrangement similar to the parallel motion introduced by Watt as a means of guiding the piston-rod in beam engines. In several recent forms of indicator lighter linkages are adopted, and other changes have been made with the object of fitting the instrument better for high-speed work. One of. these modified forms of Richards's indicator (the Crosby) is shown in fig. 15. The pressure of steam in the engine cylinder raises the piston P, compressing the spring S and causing the pencil Q to rise in a nearly straight line through a distance proportional, on a magnified scale, to the compression of the spring and therefore to the pressure of the steam. At the same time the drum D, which carries the paper, receives motion through the cord C from the crosshead of the engine. Inside this drum there is a spiral spring which becomes wound up when the cord is pulled, and serves to turn the drum in the reverse direction during the back stroke. The cap of the indicator cylinder has holes in it which admit air freely to the top of the piston, and the piston has room to descend, extending the spring S, when the pressure of the steam is less than that of the atmosphere. The spring is easily taken out and replaced by a more or less stiff one when higher or lower pressures have to be dealt with. 50. Errors in Indicator Diagrams.—To register correctly, an indicator must satisfy two conditions: (I) the motion of the piston must be proportional to the change of steam pressure in the engine cylinder: and (2) the motion of the drum must be proportional to that of the engine piston. The first of these requires that the pipe which connects the indicator with the cylinder should be short and of sufficient bore, and that it should open in the cylinder at a place where the pressure in it will not be affected by the kinetic action of the inrushing steam. Frequently pipes are led from both ends of the cylinder to a central position where the indicator is set, so that diagrams may be taken from either end without shifting the instrument ; better results are obtained, especially when the cylinder is long, by using a pair of indicators, each fixed with the shortest possible connecting pipe. The general effect of an insufficiently free connexion between the indicator and the engine cylinder is to make the diagram too small. The first condition is also invalidated to some extent by the friction of the indicator piston, of the joints in the linkage, and of the pencil on the paper. The piston must slide very freely; nothing of the nature of packing is permissible, and any steam that leaks past it must have a free exit through the cover. The pencil pressure must not exceed the minimum which is necessary for clear marking. Another source of disturbance is the inertia of the moving parts, which tends to set them into oscillation whenever the indicator piston suffers a comparatively sudden displacement. These oscillations, superposed upon the legitimate motions of the piston, give a wavy outline to parts of the diagram, especially when the speed is great. When they appear on the diagram a continuous curve should be drawn midway between the crests and hollows of the undulations. To keep them within reasonable compass in high-speed work a stiff spring must be used and an indicator with light parts should be selected. Care must be taken that the spring isgraduated to suit the temperature (about too° C.) to which it is exposed when in use;. its stiffness at this temperature is about 3 % less than when cold. 51. Measurement of Horse-.Power.—To determine the indicated. horse-power, the mean effective pressure is found by dividing the area of the diagram by the length of its base. This gives a mean height, which, interpreted on the scale of pressures, is the mean effective pressure in pounds per square inch.. This has to be multi-plied by the effective area of the piston in square inches and by the length of the piston stroke in feet to find the work done per stroke in foot-pounds on that side of the piston to which the diagram refers. Let Ai be the area of the piston on one side and A2 on the other; pi and p2 the mean effective pressures on the two sides respectively; L the length of the stroke in feet; and n the number of complete double strokes or revolutions per minute. Then the indicated horse-power I.H.P. nL(p1Ai +p2A2) 33000 In finding the mean pressure the area of the diagram may be conveniently measured by . a planimeter. A less accurate plan, frequently followed, is to divide the diagram by lines drawn at the middle of strips of equal width and toy take the mean pressure as the average height of these lines. 52. Tests of Efciency.—In testing the actual efficiency of an engine the work done as determined by the indicator is compared with the supply of heat, which is calculated from the amount of steam passing through the engine. We may find the amount of steam passing through either by measuring the feed-water or,' when a surface condenser is used, by collecting the condensed water from the air-pump discharge and measuring that, adding the water drained from jackets if any are used. In some trials both of these measurements have been made, and it has been found that in general the amount of feed-water exceeds the amount of steam discharged from air-pump and jackets by something like 3 or 4 %, a discrepancy due to leakages in the boiler and the engine. The results of tests are generally stated by giving the number of pounds of steam used per horse-power-hour, or by giving the work done by each pound of steam, a quantity which is directly comparable with the amount of work ideally obtainable, if the engine followed the perfect Rankine cycle already discussed.' To make a complete engine trial the engine is caused to work not only at full power, but at various fractions of its greatest load. The results are very conveniently represented (in a manner due to P. W. Willans) by drawing a curve, the co-ordinates of which are the horsepower and the total consumption of steam per hour. This " Willans Line,". as it is called, is iii most cases straight or nearly straight. Another useful curve is drawn by plotting the steam used per horse-power-hour in relation to the horse-power. 53. Determination of the "Missing Quantity."—When the amount of steam passing through the engine is known, the indicator diagram enables the degree of wetness of the steam to be estimated at various stages in the expansion from cut-off to release, provided there is no direct passage from steam-chest to exhaust, such as has been referred to above in connexion with Messrs Callendar and Nicolson's researches. For this purpose we must first calculate the quantity of the working substance present in the cylinder. It is made up of two parts, namely, the amount supplied per stroke, plus the amount retained by being shut up in the clearance space. If we assume, as may generally be done without serious error, that at the beginning of compression the steam present. in the cylinder is dry, it is an easy matter to deduce from the diagram, knowing the pressure and the volume, how much steam is. shut up in the clearance. Adding that to the supply per stroke, we get the whole quantity that is present from cut-off to release. The volume which this would occupy at each pressure, if saturated, is found from the steam table, The volume actually occupied at each pressure is found from the diagram, and by comparing the two it is easy to infer how much of the substance exists as water and how much as steam. The ratio of the two volumes measures with sufficient accuracy the dryness of the steam. Any direct leakage from the steam side to the. exhaust side of the valve will invalidate this calculation, which proceeds, bra the basis that all the steam' passing through the engine passes through the cylinder. 54. Compound Engines.—In the original form of compound engine, invented by Hornblower and revived by Woolf, steam passed directly from the first to the second cylinder; the exhaust from the first and admission to the second went on together throughout the whole of the back stroke. This arrangement is possible only when the high and low pressure pistons begin and end their strokes together, as in engines of the " tandem type, whose high and low pressure cylinders are in one line, with one piston-rod common to both pistons. Engines in which the high and low pressure cylinders are placed side by side, and act either on the same crank or on cranks set at 180° apart, may also discharge steam directly from one to the other cylinder; the same remark applies to beam engines, whether of the class in which both pistons act on one end of the beam, or of the class introduced by AV Naught, in which the high and low pressure cylinders stand on opposite sides of the centre. By Et convenient usage which is now pretty general the name " Woolf engine " is restricted to those compound engines which discharge steam directly from the high to the low pressure cylinders without the use of an intermediate receiver. 55. Receiver Engine.—An intermediate receiver becomes necessary when the phases of the pistons in a compound engine do not agree With two cranks at right angles, for example, a portion of the discharge from the high-pressure cylinder occurs at a time when the low-pressure cylinder cannot properly receive steam. The receiver is in some cases an entirely independent vessel connected to the cylinders by pipes; very often, however, a sufficient amount of receiver volume is afforded by the valve casings and the steam pipe which connects the cylinders. The receiver, when it is a distinct vessel, is frequently jacketed. A receiver is frequently applied with advantage to beam and tandem compound engines Communication need not then be maintained between the high and low pressure cylinders during the whole of the stroke, admission to the low-pressure cylinder is stopped before the stroke is completed; the steam already admitted is allowed to expand independently; and the remainder of the discharge from the high-pressure cylinder is compressed into the intermediate receiver. Each cylinder has then a definite point of cut-off, and by varying these points the distribution of work between the two cylinders may be adjusted at will. In general it is desirable to make both cylinders of a compound engine contribute equal quantities of work. If they act on separate cranks this has the effect of giving the same value to the mean twisting moment of both cranks. 56. Compound Diagrams.—Wherever a receiver is used, care should be taken that there should not be a wasteful amount of unresisted expansion into it; in other words, the pressure in the receiver should be not greatly less than that in the high-pressure cylinder at the moment of release. If the receiver pressure is less there will be what is termed " drop " in the steam pressure between the high-pressure cylinder and the receiver, which will show itself in an indicator diagram by a sudden fall at the end of the high-pressure expansion. This " drop " is, from the thermodynamic point of view, irreversible, and therefore wasteful. It can be avoided by selecting a proper point of cut-off in the low-pressure cylinder. When there is no " drop the expansion that occurs in a compound engine has precisely the same effect in doing work as the same amount of expansion in a simple engine would have, provided the law of expansion be the same in both and the waste of energy which occurs by the friction of ports and passages in the transfer of steam from one to the other cylinder be negligible. The work done in either case depends merely on the relation of pressure to volume throughout the process; and so long as that relation is unchang :d it is a matter of indifference whether the expansion be performed in one vessel or in more than one. In general a compound engine has a thermodynamic advantage over a simple engine using the same pressure and the same expansion, inasmuch as it reduces the exchange of heat between the working substance and the cylinder walls and so makes the process of expansion more nearly adiabatic. The compound engine has also a mechanical advantage which will be presently described. The ultimate ratio of expansion in any compound engine is the ratio of the volume of the low-pressure cylinder to the volume of steam admitted to the high-pressure cylinder. Fig. 16 illustrates the combined action of the two cylinders in a hypothetical compound engine of the Woolf type, in which for simplicity the effect of clearance is neglected and also the loss of pressure which the steam undergoes in transfer from one to the other cylinder. ABCD is the indicator diagram of the high-pressure cylinder. The exhaust line CD shows a falling pressure in consequence of the increase of volume which the steam is then undergoing through the advance of the low-pressure piston. EFGH is the diagram of the low-pressure cylinder drawn alongside of the other for convenience in the construction which follows. It has no point of cut-off; its admission line is the continuous curve of expansion EF, which is the same as the high-pressure exhaust line CD, but drawn to a different scale of volumes. At any point K, the actual volume of the steam is Kt. + MN. By drawing OP equal to KL + MN, so that OP represents the whole volume, and repeating the same construction ,, at other points of the diagram, we may set out the curve QPR, the upper part of which is identical with BC, and so complete a single diagram which exhibits the equivalent expan- sion in a single cylinder. In a tandem compound engine of the receiver type the diagrams resemble ' - those shown in fig. 17. During CD Receiver type. is taking place into the large or low- grams: pressure cylinder. D and G mark the point of cut-off in the large cylinder, after which GH shows theindependent expansion of the steam now shut within the large cylinder, and DE shows the compression of steam by continued discharge from the small cylinder into the receiver. At the end of the stroke the receiver pressure is OE, and if there is to be no " drop " this must be the same as the pressure at C. Diagrams of a similar kind may be sketched without difficulty for the case of a receiver engine with any assigned phase relation between the pistons. 57. Adjustment of Work and " Drop."—By making the cut-off take place earlier in the large cylinder we increase the mean pressure in the receiver; the work done in the small cylinder is consequently diminished. The work done in the large cylinder is correspondingly increased, for the total work (depending as it does on the initial pressure and the total ratio of expansion) is unaffected by the change. The same adjustment serves, in case there is " drop," to lessen it.' By selecting a suitable ratio of cylinder volumes to one another and to the volume of the receiver, and also by choosing a proper point for the low-pressure cut-off, it is possible to divide the work suitably between the cylinders and at the same time prevent the amount of drop from being greater than is practically convenient. 58. Uniformity of Effort in a Compound Engine.-An important mechanical advantage belongs to the compound engine in the fact that it avoids the extreme'thrust and pull which would have to be borne by the piston-rod of a single-cylinder engine working at the same power with the same initial pressure and the same ratio of expansion. If all the expansion took place in the low-pressure cylinder, the piston at the beginning of the stroke would be exposed to a thrust much greater than the sum of the thrusts on the two pistons of a compound engine in which a fair proportion of the expansion is performed in the small cylinder. The mean thrust throughout the stroke in a tandem engine is of course not affected by compounding; only the range of variation in the thrust is reduced. The effort on the crank-pin is consequently made more uniform, the strength of the parts may be reduced, and the friction at slides and journals is lessened. The advantage in this respect is obviously much greater when the cylinders are placed side by side, instead of tandem, and work on cranks at right angles. As a set-off to its advantage in giving a more uniform effort, the compound engine has the drawback of requiring more working parts than a simple engine with one cylinder. But in many instances—as in marine engines—two or more cranks are almost indispensable- to give a tolerably uniform effort' and to get over the dead points ; and the comparison should then be made between a pair of simple cylinders and a pair of compounded cylinders. Another point in favour of the compound engine is that, although the whole ratio of expansion is great, there need not be a very early cut-off in either cylinder; hence the common slide-valve, which is unsuited to give an early cut-off, may be used in place of a more complex arrangement. The mechanical advantage of the compound engine has long been recognized, and had much to do with its adoption in the early days of high-pressure steam. Its subsequent development has been due in part to this, and in part to the thermodynamic advantage which has been discussed above. 59. Ratio of Cylinder Volumes.—In a two-cylinder compound engine, using steam at 8o to Ioo lb pressure, the large cylinder has 3 or 4 times the volume of the small cylinder. In triple engines the pressure is rarely less than 15o lb; the low-pressure cylinder has generally 6 or 7 times, and the intermediate cylinder 21 to 24 times the volume of the high-pressure cylinder. In naval practice the ratios are about I : 24 : 5 for a pressure of 160 lb and I : 2.6 : 7 for a pressure of 250 lb. In the mercantile marine the engines are normally working at full power, whereas in the navy most of the working is at greatly reduced powers, the cruising speed requiring very much less than the full output. Consequently, for the same boiler pressure, the cylinder ratio is made less in war-ships to adapt the engines for economical working under cruising conditions. 6o. The Distribution of Steam.—In early steam engines the distribution of steam was effected by means of conical valves, worked by tappets from a rod which hung from the beam. The slide-valve, the invention of which in the form now known as the long D-slide showing Slide-valve. is credited to Murdock, an assistant of Watt, came into general use with the introduction of locomotives, and is now employed, in one or other of many forms, in the great majority of engines. The common slide-valve is illustrated in fig. 18, which also shows the cylinder and the ports and passages leading to its ends. The seat, or surface on which the valve slides, is a plane surface formed on or fixed to the side of the cylinder, with three ports or openings which extend across the greater part of the cylinder's width. The central opening is the exhaust port through which the steam escapes; the others, or steam ports, which are narrower, lead to the two ends of the cylinder respectively. The valve is a box-shaped cover which slides over the seat, and the whole is enclosed in a chamber called the valve-chest, to which steam from the boiler is admitted. When the valve moves a sufficient distance to either Fide of the central position, steam enters one end of the cylinder from the valve-chest and escapes from the other end of the cylinder through the cavity of the valve into the exhaust port. The valve is generally moved by an eccentric on the engine shaft, which is mechanically equivalent to a crank whose radius is equal to the eccentricity, or distance from the centre of the shaft to the centre of the eccentric sheave. The eccentric rod is generally so long that the motion of the valve is sensibly the same as that which it would receive were the rod infinitely long. Thus if a circle (fig. 19) be drawn to represent the path of the eccentric centre during a revolution of the engine, and a perpendicular PM be drawn a from any point P on a diameter AB, the distance CM is the displacement of the valve from its middle position at the time when the eccentric centre is at P. AB is the whole travel of the valve. 61. Lap and Lead.—If the valve when in its middle position did not overlap the steam ports (fig. 20), any movement to the right or the left would admit steam, and the admission would continue until the valve had returned to its middle position, or, in other words, for half a revolution of the engine. Such a valve would not serve for expansive working, and as regards the relative position of the crank and eccentric it would have to be set so that its middle position coincided with the extreme position of the piston; in other words, without Lap. the eccentric radius would make a right angle with the crank. Expansive working, however, becomes possible when we give the valve what is called " lap," by making it project over the edges of the steam ports, as in fig. 21, where o is the " outside lap " and i is the " inside lap." Admission of steam (to either side) then begins only when the displacement of the valve from its middle position exceeds the amount of the outside lap, and continues only until the varve has returned to the same distance from its middle position. Further, exhaust begins only when the valve has moved past the middle by a distance equal to i, and continues until the valve has again returned to a distance i from its middle position. Thus on the diagram of the eccentric's travel (fig. 22) we find, by setting off o and i on the two sides of the centre, the positions a, b, c and d of the eccentric radius at which the four events of admission, cut-off, release and compression occur for one side of the piston. As to the other side of the piston, it is only necessary to set off o to the right and i to the left of the centre, but for the sake of clearness we may confine our attention to one of the two sides. Of the whole revolution, the part from a to b is the arc of steam admission, from b to c is the are of expansion, from c to d the arc of exhaust, and from d to a the arc of compression. The relation of these, however, to the piston's motion is still undefined. If the eccentric were set in advance of the crank by an angle equal to ACa, the opening of the valve would be coincident with the beginning of the piston's stroke. It is, however, desirable, in order to allow the steam free entry, that the valve be already some way open when the piston stroke begins, and thus the eccentric may be set to have a position Ca' at the beginning of the stroke. In that case the valve is open at the beginning of the stroke to the extent mm', which is called the " lead." The amount by which the angle between Ca' (the eccentric) and CA (the crank) exceeds a right angle is called the angular advance, this being the angle by which the eccentric is set in advance of the position it would occupy if the primitive arrangement without lap were adopted. The quantities lap, lead and angular advance (0) are connected by the equation outside lap+lead = half travel X cos B. An effect of lead is to cause preadmission, that is to say, admis-ENGINE sion before the end of the back stroke, which, together with the compression of steam left in the cylinder when the exhaust port closes, produces the mechanical effect of " cushioning," to which reference has already been made. To examine the distribution of steam throughout the piston's stroke, we may now draw a circle to represent the path of the crank pin (fig. 23, where the dotted lines have been added to show the assumed configuration of piston, connecting-rod and crank) and transfer to it from the former diagram the angular positions a, b, c and d at which the four events occur. To facilitate this transfer the diagrams of eccentric path and of crank-pin path may by a suitable choice of scales be drawn of the same actual size. Then by projecting these points on a diameter which represents the piston's path, by circular arcs drawn with a radius equal to the length of the connecting-rod, we find p, the position of the piston at which admis- sion occurs during the back stroke, Qy also q and r, the position at cut-off ea. and release, during the stroke which t: takes place in the direction of the arrow, and s, the point at which compression begins. It is obviously unnecessary to draw the two circles of figs. 22 and 23 separately; the single diagram (fig. 24) contains the solution of the steam distribution with a slide-valve whose laps, travel and angular advance are known, the same circle serving, on two scales, to show the motion of the crank and of the eccentric. Zeuner's Diagram.—The graphic construction most usually employed in slide-valve investigations is the ingenious diagram published by Dr G. Zeuner in the Civilingenieur in 1856.1 On the Line AB (fig. 25), which represents the travel of the valve, let a pair of circles (called valve-circles) be drawn, each with diameter equal to the half travel. A radius vector CP, drawn in the direction of the eccentric at any instant, is cut by one of the circles at Q, so that CQ re-presents the corresponding displacement of the valve from its middle position. That this is so will be seen by drawing PM (as in fig. 19) and joining QB, when it is obvious that CQ=CM, which is the displacement of the valve. The line AB with the circle on it may now be turned back through an angle of 90°+0 (0 being the angular advance), so that the valve-circles take the position shown to a larger scale in fig. 26. This makes the direction of CQ (the eccentric) coincide on the paper with the simultaneous direction of 1 Zeuner, Treatise on Valve Gears, trans. by M. Muller (1868). .—s with Lap. sh.f silos the crank, and hence to find the displacement of the valve at any at rest, and then re-engaging the gear. The eccentric sheave, position of the crank we have only to draw CQ in fig. 26 parallel to the crank, when CQ represents the displacement of the valve to the scale on which the diameter of each valve circle represents the half-travel of the valve. CQ0 is the valve displacement at the beginning of the stroke shown by the arrow. Draw circular arcs ab and cd with C as centre and with radii equal to the outside lap o and the inside lap i respectively. Ca is the position of the crank at which pre-admission occurs. The lead is aoQo. The greatest steam opening is a1B. the direction Cb. Cc is the position of the crank at release, and Cd marks the end of the exhaust. 63. In this diagram radii drawn from C mark the angular positions of the crank, and their intercepts by the valve circles determine the corresponding displacement of the valve. It remains to find the corresponding displacement of the piston. For this Zeuner employs a supplementary graphic construction, shown in fig. 27. Here ab or a'b represents the connecting rod, and be or b'c the crank. With centre c and radius ac a circle ap is drawn, and with centre b and radius ab another circle aq. Then for any position of the crank, as cb', the intercept pq between the circles is easily seen to be equal to aa', and is therefore the distance by which the piston has moved from its extreme position at the beginning of the stroke. In practice this diagram is combined with that of fig. 26, by drawing both about the same centre and using different scales for valve and piston travel. A radius vector drawn from the centre parallel to the crank in any position then shows the valve's displacement from the valve's middle position by the intercept CQ of fig. 26, and the piston's displacement from the beginning of the piston's motion by the intercept pq of fig. 27. 64. In the figures which have been sketched the events refer to the front end of the cylinder, that is, the end nearest to the crank (see fig. 23). To determine the events of steam distribution at the back end, the lap circles shown by dotted lines in fig. 26 must also be drawn, Ca' being the outside lap for the back end, and Cc' the inside lap. These laps are not necessarily equal to those at the other end of the valve. From the diagrams it will be seen that, especially with a short connecting-rod, the cut-off and release occur earlier and the compression later at the front than at the back end if the laps are equal, and a more symmetrical steam distribution can be produced by making the inside lap greater and the outside lap less on the side which leads to the front end of the cylinder. On the other hand, an unsymmetrical distribution may be desirable, as in a vertical engine, where the weight of the piston assists the steam during the down-stroke and resists it during the up-stroke, and this may be secured by a suitable inequality in the laps. 65. By varying the ratio of the laps o and i to the travel of the valve, we produce effects on the steam distribution which are readily traced by means of the diagram. Reduction of travel (which is equivalent to increase of both o and i) gives later pre-admission, earlier cut-off, later release and earlier compression; the ratios of expansion and of compression are both increased. Increase of angular advance accelerates all the events and causes a slight increase in the ratio of expansion. 66. In designing a slide-valve the breadth of the steam ports in the direction of the valve's motion- is determined with reference to the volume of the exhaust steam to be discharged in a given time, the area of the ports being generally such that the mean velocity of the steam during discharge is less than too ft. per second. The travel is made great enough to keep the cylinder port fully open during the greater part of the exhaust; for this purpose it is 22 or 3 times the breadth of the steam port. To facilitate the exit of steam the inside lap is always small, and is often wanting or even negative. During admission the steam port is rarely quite uncovered, especially if the outside lap is large and the travel moderate. Large travel has the advantage of giving freer ingress and egress of steam, with more sharply-defined cut-off, compression and release, but this advantage is secured at the cost of more work spent in moving the valve and more wear of the faces. To lessen the necessary travel without reducing the area of steam ports, double-ported valves are often used. An example is shown below in fig. 39. 67. Reversal of Motion with Slide-Valve.—The eccentric must stand in advance of the crank by the angle 9o°+0, as in fig. 28, where CK is the crank, and CE the corresponding y' / position of the eccentric when the engine is running —! in the direction of the arrow a. To set the engine in gear to run in the opposite direction (b) it is only necessary to shift the eccentric into the position crank. In the older engines this reversal was effected by temporarily disengaging the eccentric-rod from the valve-rod, working the valve by hand until the crank turned back through an angle equal to ECE', the eccentric meanwhile remaining
End of Article: STEAM ENGINE
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