WO2002010555A1 - Bloc-cylindres de machine a vapeur, machine a vapeur et alimentation en vapeur - Google Patents

Bloc-cylindres de machine a vapeur, machine a vapeur et alimentation en vapeur Download PDF

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Publication number
WO2002010555A1
WO2002010555A1 PCT/GB2001/003382 GB0103382W WO0210555A1 WO 2002010555 A1 WO2002010555 A1 WO 2002010555A1 GB 0103382 W GB0103382 W GB 0103382W WO 0210555 A1 WO0210555 A1 WO 0210555A1
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WO
WIPO (PCT)
Prior art keywords
steam
cylinder block
engine
supply
steam engine
Prior art date
Application number
PCT/GB2001/003382
Other languages
English (en)
Inventor
David Langley Walker
Original Assignee
David Langley Walker
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by David Langley Walker filed Critical David Langley Walker
Priority to AU2001276467A priority Critical patent/AU2001276467A1/en
Publication of WO2002010555A1 publication Critical patent/WO2002010555A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02—Engines
    • F01B17/04—Steam engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
    • F16J10/02—Cylinders designed to receive moving pistons or plungers

Definitions

  • the present invention is concerned with steam engines.
  • the invention concerns a steam engine cylinder block, a steam engine as such and a steam supply.
  • Compound steam engines are well known.
  • boiler steam is led via a valve to a high pressure (HP) cylinder.
  • Steam exhausted from the HP cylinder again under the control of the valve and at reduced pressure but still carrying usable energy, is passed via a transfer conduit and a further valve chest to a low pressure (LP) cylinder.
  • LP low pressure
  • the LP cylinder may have a larger cross section than the HP cylinder or may be one of a set of LP cylinders such as to make up a total LP cylinder cross section greater than that of the HP cylinder.
  • the steam does useful work in both HP and LP cylinders.
  • the expansion ratio of the steam is increased (as compared with a non-compounded engine) and compound engines consequently offer potentially higher efficiency.
  • a steam jacket receives a supply of steam from the boiler and serves to transfer heat to the cylinders, and in some cases also to the valve chests. By keeping the components through which steam is passed at a sufficiently high temperature, steam jacketing alleviates or altogether overcomes condensation problems.
  • FIGs la and lb illustrate a known, and in its day successful, cylinder block for a steam jacketed compound engine. This was in fact designed by Charles Burrell & Co., in about 1900 -1910.
  • the high pressure cylinder is marked HP
  • the low pressure cylinder is marked LP
  • cavities within the block supplied with boiler steam, to perform the jacketing function are marked S.
  • steam heating of the cylinder block is achieved by having core holes in the casting supplied with boiler steam.
  • the block was cast in grey iron and only sufficient jacketing was provided to enable the engine to run dry - i.e. without condensation.
  • the intention of steam jacketing has in the past been simply to prevent liquid water from being present in the exhaust. Such water can be condensation on the engine parts - eg. cylinder walls - and can take the form of a mist of droplets in the steam.
  • the inventor has recognised that in such engines there was little possibility of re-heating of steam between HP and LP cylinders.
  • An object of Hie present invention is to make possible a steam engine of improved energy efficiency.
  • a steam engine cylinder block comprising a higher pressure cylinder, a lower pressure cylinder and a transfer conduit through which steam exhausted from the higher pressure cylinder is led to drive the lower pressure cylinder, the cylinders being steam jacketed and the transfer conduit being steam jacketed such that the exhausted steam is re-heated during passage through the transfer conduit.
  • the cylinder block is such as to maintain the steam at or near boiler steam temperature throughout its cycle in normal operation. Heat input to the steam during its cycle, due to the steam jacketing, largely offsets the drop in temperature due to expansion in the cylinders.
  • T- where ⁇ is efficiency and T in and T out are the input and exhaust temperatures of the working fluid (in this case, the steam).
  • Camot's equation is derived on the basis that expansion of the working fluid is adiabatic.
  • the input of heat to the steam during its cycle, as a result of the steam jacketing, means that the working cycle is non-adiabatic so that Camot's equation does not apply.
  • Thermal efficiency is consequently not limited by the above equation.
  • the steam engine according to the present invention is preferably adapted to run on high pressure input steam. Raising working pressure allows T in to be increased without extra losses and tests show that efficiency is consequently increased.
  • the steam jacketing is provided by means of a hollow steam chest around the cylinders and transfer conduit, means being provided for connection of the interior of the steam chest to a source of steam.
  • a hollow steam chest around the cylinders and transfer conduit, means being provided for connection of the interior of the steam chest to a source of steam.
  • steam can flow freely around exterior surfaces of the transfer conduit and the cylinders.
  • the transfer conduit comprises a pipe whose exterior is exposed to steam within the steam chest.
  • substantially the entire exterior of the pipe is exposed to the steam.
  • valves which are steam jacketed.
  • steam jacketing is achieved by disposing the valve chests in the steam chest. Exteriors of the valve chests are preferably exposed to steam in the steam chest. This again facilitates heat transfer.
  • steam supply and exhaust conduits leading to and from the valve chests are formed as pipes extending through the steam chest and having exteriors exposed to steam in the steam chest. This again promotes heat transfer.
  • the pipes can be wide and flat to maximise exposed area.
  • the transfer conduit comprises a cruciform arrangement having a central passage for receiving steam exhausted from the higher pressure cylinder and outputs to the lower pressure cylinders at its extremities.
  • the cruciform transfer conduit is again preferably formed by pipes whose exteriors are exposed to steam in the steam chest.
  • the cylinder arrangement preferably has the higher pressure cylinder disposed between two lower pressure cylinders.
  • the steam chest is preferably formed as a box-like enclosure.
  • the cylinder block is thermally insulated from other structural components of the steam engine to reduce conduction of heat from the cylinder block.
  • all components of the cylinder block are steam jacketed.
  • the steam jacket is preferably provided with a drain for receiving condensate from the steam jacket, the drain being led to the cylinder steam input path such that the condensate is evaporated and re-circulated.
  • the cylinder block according to the present invention is preferably coupled to the crank case of a steam engine through a thermally insulating mounting.
  • a steam engine comprising a cylinder block mounted upon a crank case through a mounting structure which separates the cylinder block from the crank case.
  • the mounting structure preferably comprises one or more mounting limbs bridging a space between the crank case and the cylinder block.
  • the inventor has recognised that important heat loss - and consequent thermal inefficiency - arises in many known engines through heat flow from the cylinder block to the crank case. By separating the two, this heat loss can be reduced.
  • the mounting limbs are provided with thermal insulation to impede heat flow to the crank case. Heat loss by this route is thereby further reduced.
  • the reduced heat flow to the crank case results in a lower operating temperature in the crank case, making it unnecessary to use a specialist high temperature lubricant.
  • piston rods and/or valve rods preferably extend across the separation between the crank case and the cylinder block. Where the piston and/or valve rods emerge from the cylinder block they are preferably provided with sealing glands.
  • the separation of the cylinder block from the crank case enables easy access to and maintenance of the glands, which require occasional adjustment. Due again to the separation of the crank case from the cylinder block, only light duty glands are required where the piston and/or valve rods pass into the crank case. These glands prevent ingress of water which would otherwise cause the lubrication system to deteriorate.
  • the cylinder block of the steam engine is constructed according to the first aspect of the present invention.
  • Steam engines according to the present invention can be of up to 10,000 horsepower or more.
  • the engine is for running on superheated steam.
  • a steam supply comprising an accumulator in the form of a pressure vessel which is part filled with water in use, a boiler, means defining a path through which water from the accumulator is input to the boiler, means defining a path through which steam output from the boiler is led into the water in the accumulator, and a steam take-off through which steam can escape the accumulator to supply an engine.
  • An accumulator in this manner has several advantages. Particularly important is the fact that it becomes unnecessary to use a bulky conventional shell boiler.
  • a boiler can be used whose output is a frothy mixture of water and steam. In the accumulator, this is separated - steam in the space above the water is taken off to drive the engine, while water remains in the accumulator and is eventually recirculated to the boiler.
  • the accumulator contains the mass of water required to make the system stable and controllable.
  • the accumulator is provided with thermal insulation and with cut off valves at its input and output. In this manner the heat energy in the water can be stored (with a large accumulator, heat can be retained for several days) giving rapid starting of the plant when required.
  • the boiler is preferably a flash boiler.
  • the boiler comprises water conduits arranged to form a water walled combustion chamber.
  • a particularly preferred boiler for use in the steam supply according to the present invention has a set of upright fin tubes each connected between a lower manifold and an upper manifold, the boiler having a water input through the lower manifold and a steam take off to the accumulator from the upper manifold.
  • the fin tubes may be arranged along a loop effectively forming a water- walled combustion chamber.
  • This format of boiler encourages controlled, fast circulation. It is ideal for a high pressure environment and provides excellent heat transfer characteristics. A further advantage where water quality is less than optimum is that given sufficiently fast circulation the tubes can be self cleaning.
  • an economizer is fitted in an upper region of the boiler.
  • Economisers are known to those skilled in the art and serve to pre-heat feed water, using radiant heat and a proportion of the convective heat in combustion exhaust gases. Thermal efficiency is thus improved.
  • the steam supply according to the third aspect of the present invention be connected to a steam engine according to the second aspect of the present invention or a steam engine having a cylinder block according to the first aspect of the present invention.
  • the steam supply is well suited to driving such a high efficiency engine and the resulting arrangement can be both thermally efficient and compact.
  • the steam supply is preferably adapted to supply high pressure steam. This is an important factor in achieving high thermal efficiency and the steam supply according to the present invention allows high pressure steam to be generated without the problems - and dangers - involved in running shell boilers at high pressures.
  • Figs, la and lb are respectively vertical and horizontal sections through a cylinder block of known design
  • Figs 2 and 3 illustrate, in perspective and from respective different angles, a cylinder block assembly and part of a crank case of a steam engine embodying the invention, a steam chest of the engine being shown cut-away;
  • Fig.4 corresponds to Fig.3 except that the steam chest is not cut-away in this drawing and consequently the cylinder block cannot be seen
  • Fig. 5 corresponds to Fig. 3 except that in this drawing a cylinder and a valve chest are cut away to reveal their interiors;
  • Fig. 6 is a schematic illustration, from the side, of a steam supply arrangement according to an aspect of the present invention.
  • Fig. 7 is a schematic illustration of a boiler used in the same steam supply arrangement, viewed from above;
  • Fig. 8 is a simplified view of the cylinder block in plan showing the general layout of the cylinders and valve chests.
  • Fig. 9 is a corresponding simplified side view of the cylinder block showing the arrangement of a transfer conduit.
  • Figs. 2 to 5 it can be seen that the cylinder block 2 and associated parts are housed in a generally box-like hollow steam chest 4 formed by walls 6.
  • a steam chest input pipe 8 Leading into the steam chest from above is a steam chest input pipe 8 which supplies steam from the boiler to the interior of the steam chest.
  • a steam chest drain seen emerging from the steam chest at 10, receives any condensate.
  • Seen in Figs. 2 - 5 is a row of three cylinder covers at the steam chest exterior corresponding to three cylinders within the steam chest.
  • Middle cylinder cover 12 corresponds to the middle, high pressure (HP) cylinder while the two outer covers 16 correspond to outer, low pressure (LP) cylinders.
  • HP high pressure
  • LP low pressure
  • FIG. 8 only one of the LP cylinders themselves, labelled 18, can be seen. However, the layout of the cylinders is made clear by the simplified plan view of Fig. 8 in which the outer, LP cylinders are again labelled 18 and the middle, HP cylinder is labelled 20.
  • Fig. 8 also makes most clear the layout of three valve chests. These are arranged in a row, correspondingly to the three cylinders.
  • the middle of the three valve chests, labelled 22, controls high pressure steam to and exhaust from the HP cylinder 20.
  • the two outer valve chests, labelled 24, control lower pressure steam input to and exhaust from the respective low pressure cylinders 18.
  • the other pistons although not seen, are similarly formed.
  • Descending from and securely coupled to each of the pistons is a respective piston rod 28.
  • each piston rod 28 exits the steam chest downwardly through a respective sealing gland 30 and passes into a crank case 32. Inside the crank case the piston rods 28 drive a crank.
  • the crank mechanism is of well known type and is not itself illustrated herein.
  • Steam to drive the engine is input through a pair of high pressure boiler steam input pipes 34, 36. These are arranged in the middle of the steam chest one above the other, to supply steam via the middle, HP valve chest 22 to the HP cylinder 20.
  • the input pipes are in the illustrated embodiment circular in section, although pipes of other sections could be used. Inside the steam chest 4, exteriors of the steam input pipes 34, 36 are exposed to steam in the chest.
  • the transfer conduit 38 receives steam from a single, middle, exhaust (labelled 40 in Fig. 9) from the HP valve chest 22 and transfers it to respective upper and lower inputs of the LP valve chests 24. To achieve this the transfer conduit 38 has a diagonal cruciform configuration.
  • the transfer conduit 38 is formed by pipe work whose exterior is exposed to steam within the steam chest.
  • valves are piston valves each having a pair of valve pistons 42, 44 mounted upon a valve rod 46 and running in a valve chest cylinder bore 48.
  • Annular upper and lower valve inlet ports 50, 52 are formed around the bore 48, being open toward the bore and in flow communication with respective limbs of the cruciform transfer conduit 38 to supply low pressure steam to upper and lower regions of the valve bore 48.
  • annular valve exhaust port 54 communicating with an exhaust pipe 56.
  • upper and lower annular supply ports communicating respectively with upper and lower steam passages 58, 60 through which steam is supplied to and exhausted from upper and lower regions of the LP cylinder 18.
  • valve rods and pistons 42, 44, 46 are reciprocally driven while the engine is running and by closing/opening the valve ports in the course of this reciprocal motion control input and exhaust of the low pressure steam to drive the piston 26 in a double acting manner (i.e. the piston is driven in both directions, by steam input to alternate sides of the piston).
  • each of the valve rods 46 exits the steam chest 4 downwardly through a respective sealing gland 62 and passes into the crank case 32.
  • the mechanism for reciprocally driving the valve rods is contained in the crank case.
  • suitable known mechanisms e.g. utilising an eccentric driven from the crank shaft, and these parts are not illustrated.
  • a second LP exhaust pipe, labelled 64, is associated with the other LP valve. Exhaust from the middle, HP, valve is into the HP exhaust 40, as has been mentioned above.
  • valve chests 22, 24, the input pipes 34, 36, the transfer conduit 38, the supply passages 58, 60 and the exhaust pipes 56, 64 are all designed to provide large surface areas exposed to the steam which circulates freely in the steam chest 4.
  • the valve chests have ridges (an example is labelled 66 in Fig. 2) to accommodate the valve ports and supply passages, these ridges providing a large surface area for exchange of heat between the valve chest steam and the working steam.
  • ridges an example is labelled 66 in Fig. 2
  • Substantially the entire exteriors of both cylinders 18, 20 and valve chests 22, 24 are also exposed to steam in the chest to promote heat transfer.
  • the inventor has calculated that the illustrated design provides fifteen times more surface area exposed to jacket steam than known jacketed engines.
  • the assembly comprising the cylinders, valves and the steam chest 4 is mounted to the engine's crank case 32 through a pair of limbs formed as mounting legs 68, thereby providing a gap between the steam chest 4 and the crank case 32.
  • a layer of thermal insulation may be incorporated e.g. between mounting lugs 70 of the legs and the crank case 32 to which they are bolted.
  • a starter input 72 which communicates with the transfer conduit 38 and which is connectable via a cut off valve (not illustrated) to boiler steam. On starting of the engine, boiler steam is admitted through the starter input 72 directly to the LP valve chests 24/cylinders 18.
  • the LP cylinders are driven by high pressure boiler steam. Not only does this make large torque temporarily available (due to the large total cross section of the LP cylinders) but since all three cylinders are driven upon starting it can be ensured that at least one cylinder is always away from top or bottom dead centre and so can provide initial motion.
  • the steam chest drain 10 can be seen to be connected to the starter input pipe 72 so that condensate in the chest is evaporated and passed as steam to the LP cylinders 18. Hence the condensate's heat energy is used rather than being lost, as it would if the condensate were vented to the exterior.
  • the steam supply will now be described with reference to Figs. 6 and 7.
  • the major components of the steam supply are a boiler 100 and an accumulator 102.
  • the boiler 100 is formed in the illustrated embodiment from tubes.
  • a lower manifold 104 of the boiler is formed as a loop (a square loop in the embodiment depicted although it could for example be a circular loop) of tubing and has a water inlet 106.
  • An upper manifold 108 is formed as a corresponding loop and has a steam take-off or outlet 110.
  • Between the upper and lower manifolds 104, 108 is a set of upright fin tubes 112. Each fin tube communicates (at its upper and lower ends respectively) with the upper and lower manifolds 104, 108.
  • the fin tubes are provided around the full perimeter of the manifolds thereby forming a combustion chamber. A wall is thus formed around the combustion chamber which is filled with water/steam. The arrangement proves highly thermally efficient.
  • the boiler 100 can be referred to as a flash boiler. Water input to the lower manifold 104 is rapidly evaporated and ejected as steam from the upper manifold 108.
  • the boiler's output is a frothy combination of steam and hot water. Before being led to the engine itself, this output is let to the accumulator 102.
  • the accumulator comprises a hollow pressure vessel 114 having a steam inlet 116 and a supply outlet 118. In use the accumulator is part filled with water. The water level is marked 120 in Fig. 6. Steam entering through the steam inlet 116 is directed below the water level by a steam conduit 122 and escapes through stub outlets 124, which are directed downwardly, into the water.
  • the supply outlet 118 is above the water level and so delivers only steam to the engine.
  • the accumulator also has a water outlet 107 through which water, already warmed by the steam from the boiler, is supplied from the accumulator to the water inlet 106 of the boiler.
  • the combustion chamber of the boiler can be fitted, at the bottom, with a grate for solid fuel or with an arrangement for burning liquid or gaseous fuels including ecologically acceptable renewable fuels.
  • the combustion chamber is provided in an upper region with an economiser which uses radiant heat and heat carried convectively by the exhaust gases to pre-heat feed water thereby increasing efficiency.
  • the gases emerging from the economiser are exhausted via any ecologically desirable screen, scrubber or filter mechanism to either a stack or an exhaust steam device to produce the necessary draught.
  • the low impedance of flow in the combustion chamber means the necessary draught is low. This in turn means that environmental control devices can be fitted to the exhaust without affecting the performance of the engine.
  • the steam accumulator 102 is (optionally) fitted with valves to isolate the accumulator so pressure can be retained with the combustion chamber shut down.
  • safety valve and fusible plug protection is fitted to the top manifold 108.
  • the relative height of the accumulator and top of combustion chamber should be set so that the combustion chamber is flooded at all times. Otherwise an auxiliary circulating pump can be provided to circulate the water.
  • the steam supply is well suited to provision of high pressure steam to the engine, an important factor for high thermal efficiency.
  • Output steam pressures are not expected to exceed 350 psi (2400 kPa).
  • a typical working pressure could be 250 psi (1700 kPa).
  • the illustrated cylinder block is not for a superheated engine but the present invention could be applied to superheated engines.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention concerne un bloc-cylindres de machine à vapeur comprenant un cylindre haute pression, un ou des cylindres à pression plus faible, et un conduit de transfert par lequel la vapeur rejetée par le cylindre à pression élevée est dirigée afin d'entraîner le cylindre à pression plus faible, les cylindres présentant une chemise de vapeur et le conduit de transfert présentant une chemise de vapeur de sorte que le vapeur émise est à nouveau chauffée durant son passage par le conduit de transfert. Le bloc-cylindres forme une partie de la machine à vapeur et est monté sur un carter par l'intermédiaire d'une structure de montage qui sépare le bloc-cylindres du carter. La machine à vapeur présente une alimentation en vapeur comprenant un accumulateur se présentant sous la forme d'une cuve pressurisée qui est partiellement remplie d'eau lors de l'utilisation, une chaudière, des éléments définissant une trajectoire par laquelle l'eau de l'accumulateur est introduite dans la chaudière, des éléments définissant une trajectoire par laquelle la vapeur sortant de la chaudière est introduite dans l'eau de l'accumulateur, et un dispositif de prise de vapeur par lequel la vapeur peut sortir de l'accumulateur pour alimenter la machine.
PCT/GB2001/003382 2000-07-28 2001-07-26 Bloc-cylindres de machine a vapeur, machine a vapeur et alimentation en vapeur WO2002010555A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001276467A AU2001276467A1 (en) 2000-07-28 2001-07-26 Steam engine cylinder block, steam engine and steam supply

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0018419.2 2000-07-28
GB0018419A GB2365076A (en) 2000-07-28 2000-07-28 Steam engine having a cylinder block steam jacket, accumulator and upright tubed boiler

Publications (1)

Publication Number Publication Date
WO2002010555A1 true WO2002010555A1 (fr) 2002-02-07

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Application Number Title Priority Date Filing Date
PCT/GB2001/003382 WO2002010555A1 (fr) 2000-07-28 2001-07-26 Bloc-cylindres de machine a vapeur, machine a vapeur et alimentation en vapeur

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AU (1) AU2001276467A1 (fr)
GB (1) GB2365076A (fr)
WO (1) WO2002010555A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101649752B (zh) * 2008-08-11 2011-06-15 姜忠扬 燃汽动力机
EP2562351A1 (fr) * 2011-08-22 2013-02-27 Voith Patent GmbH Moteur à vapeur

Citations (7)

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US719530A (en) * 1902-01-09 1903-02-03 William Sutcliffe Steam-engine.
US734720A (en) * 1901-12-06 1903-07-28 Henry K Lee Steam-engine.
US813301A (en) * 1903-09-09 1906-02-20 Frank S Hyde Steam-engine.
US870585A (en) * 1901-04-24 1907-11-12 Charles F Brown Method of utilizing working fluid in jacketed engines.
US1044392A (en) * 1912-02-24 1912-11-12 Robert Jung Compound engine.
US4395885A (en) * 1981-10-08 1983-08-02 Cozby Enterprises, Inc. Unitary steam engine
US5010852A (en) * 1989-04-14 1991-04-30 Milisavljevic Milorad S Heat engine

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GB223303A (en) * 1923-07-17 1924-10-17 Stephen Evans Alley Improvements in or relating to fluid-pressure-operated engines
US1753925A (en) * 1927-12-07 1930-04-08 Spinner Engine Company Steam engine
GB328852A (en) * 1929-06-25 1930-05-08 Bamag Meguin Ag Process for the utilisation of the quenching vapours periodically resulting from the quenching of glowing coke in a pressure vessel
GB404870A (en) * 1932-12-23 1934-01-25 Sulzer Ag Improvements in or relating to electrically heated steam generating installations
GB565081A (en) * 1943-06-25 1944-10-25 Arthur Abbey Improvements in quadruple expansion steam engines
US3893426A (en) * 1974-03-25 1975-07-08 Foster Wheeler Corp Heat exchanger utilizing adjoining fluidized beds
JPS58158304A (ja) * 1982-03-15 1983-09-20 Nippon Kokan Kk <Nkk> 蒸汽アキユムレ−タによる蓄熱方法および装置
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Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US870585A (en) * 1901-04-24 1907-11-12 Charles F Brown Method of utilizing working fluid in jacketed engines.
US734720A (en) * 1901-12-06 1903-07-28 Henry K Lee Steam-engine.
US719530A (en) * 1902-01-09 1903-02-03 William Sutcliffe Steam-engine.
US813301A (en) * 1903-09-09 1906-02-20 Frank S Hyde Steam-engine.
US1044392A (en) * 1912-02-24 1912-11-12 Robert Jung Compound engine.
US4395885A (en) * 1981-10-08 1983-08-02 Cozby Enterprises, Inc. Unitary steam engine
US5010852A (en) * 1989-04-14 1991-04-30 Milisavljevic Milorad S Heat engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101649752B (zh) * 2008-08-11 2011-06-15 姜忠扬 燃汽动力机
EP2562351A1 (fr) * 2011-08-22 2013-02-27 Voith Patent GmbH Moteur à vapeur

Also Published As

Publication number Publication date
AU2001276467A1 (en) 2002-02-13
GB0018419D0 (en) 2000-09-13
GB2365076A (en) 2002-02-13

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