US3760778A - Vapor generators - Google Patents

Vapor generators Download PDF

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Publication number
US3760778A
US3760778A US00200445A US3760778DA US3760778A US 3760778 A US3760778 A US 3760778A US 00200445 A US00200445 A US 00200445A US 3760778D A US3760778D A US 3760778DA US 3760778 A US3760778 A US 3760778A
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liquid
reservoir
chamber
inlet duct
release valve
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US00200445A
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C May
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/22—Methods of steam generation characterised by form of heating method using combustion under pressure substantially exceeding atmospheric pressure
    • F22B1/26—Steam boilers of submerged-flame type, i.e. the flame being surrounded by, or impinging on, the water to be vaporised, e.g. water in sprays
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/30—Technologies for a more efficient combustion or heat usage

Definitions

  • ABSTRACT Apparatus for the generation of liquid vapor under pressure, by means of heat from the combustion products of an internal combustion engine comprises a reservoir for the liquid to be vaporized having an inlet duct for the combustion products which communicates with the lower part of the interior of the reservoir.
  • the combustion products pass from the inlet duct into the reservoir by way of a screen formed with a large number of small holes providing free passage for gas or liq-' uid and this screen is preferably formed by an extension of the duct lying within the reservoir and formed with the small holes round its periphery.
  • the combustion product may bubble upwardly through liquid in the reservoir so as to transfer heat directly to the liquid with a high rate of heat transfer.
  • An outlet from the reservoir is preferably so constructed as to reduce the amount of liquid carried over with the vapor and the outlet line may pass through at least one further closed vessel in order to trap any residual liquid.
  • the internal combustion engine supplying the combustion products is preferably of the freepiston type and includes an arrangement for avoiding excessive heating of a release valve and its seat.
  • a duct is provided to supply liquid to a chamber in contact with the heated portion of the cylinder head and this chamber includes a portion adjacent the seat of the release valve'which includes narrow outlets opening into the inlet duct in the region of reduced pressure immediately following the valve opening. In this way liquid is drawn into the inlet duct leading to appreciable cooling of the release valve and its seat.
  • SHEET 3 (IF 4 Inventor Attorney PATENTED SEPZS I973 SHEET 0F 4 I rwenlor A Home y VAPOR GENERATORS
  • This invention relates to apparatus for the generation of liquid vapour at high temperature and pressure for utilisation in driving prime movers. It is particularly applicable to the generation of steam for such purposes although in'sorn'e circumstances other liquids may be used. Aparticularly suitable source of heat for the generation of 'liquidvapour is'the combustion'products of an internal combustion engine which are fed to a reservoir partly filled with liquid to be vaporised.
  • the reservoir has an inlet duct for the combustion products which communicates with the lower part of the interior ofthe'reservoir by way of a'screenfo'rmed with a large number of smallholes providing free passage for gas or liquid whereby the combustion product may bubble upwardly through liquid in the reservoir so'as to transfer heat'directly to the liquid.
  • the screen is preferably constituted by an extension of the inlet duct lying within the reservoir and formed with the small'holes round its periphery.
  • the reservoir is'prefe'rably cylindrical and is divided into axial compartments by circular baffle plates formed with openings for the passage of liquid and pressure fluid.
  • the provision of these baffles avoids splashing and liquid surging during movement of the equipment while the presence of the openings permits free but controlled flow of both liquid and pressure fluid.
  • the baffle plates may for example divide the reservoir along its length into compartments having a length of about 65 percent of the diameter.
  • the outlet pipe may comprise a pipe which extends upwardly towards the top of the reservoir where its end is obstructed, the walls of the pipe close to the end being formed with openings for the passage of pressure fluid and the upper portion of the pipe, including the openings, being surrounded by a cup-shaped shield formed with drainage openings at the bottom.
  • Pressure fluid can pass freely over the top of the shield and out through the openings in the pipe, but any liquid which tends to be splashed over the top of the shield is unlikely to enter the pipe and merely flows outwardly through the drainage openings.
  • the drainage openings in the cup may themselves be protected from splash by a down-turned skirt.
  • Each chamber includes a portion adjacent the seatof the respective release valve and also includes narrow outlets opening into the inlet duct in the region of reduced pressure immediately following the valve opening. In this way liquid is drawn into the inlet duct, thus leading to a circulation of liquid from the reservoir, through the chamber, into contact with the metal adjacent the seat of the release valve and then through.
  • Each chamber into which the liquid flows may include an' annular portion separatedfrom the region of reduced pressure by an annular diaphragm having a free inner edge bearing against the wall of the annular portion of the chamber adjacent the valve seat, the narrow openings being formed between this edge of the diaphragm and the wall.
  • the diaphragm thus divides the chamber from the duct by which the combustion products are supplied to the reservoir and additionally forms a sealing gasket against the high pressure of the pressure fluid.
  • FIG. 1 is a vertical section through the end of a reservoir and of an internal combustion engine supplying products of combustion to the reservoir;
  • FIG. 2 is a sectional view of the reservoir as seen from the right hand side of FIG. 1;
  • FIG. 3 is an end view, partly in section, of the internal combustion engine seen from the left in FIG. 1;
  • FIG. 4 is a sectional view to a reduced scale corresponding to FIG. 2 and showing subsequent details of an outlet line;
  • FIG. 5 is a detailed view showing part of a diaphragm seen in FIG. 1;
  • FIG. 6 is a sectional view to an enlarged scale showing part of a release valve and seat seen in FIG. 1 and also including the edge of the diaphragm seen in FIG. 5.
  • FIG. 1 the release or outlet end of an internal combustion engine is indicated generally as l and from it the products of combustion pass along a line 2 and thence via an inlet duct 3 to the interior of a cylindrical reservoir indicated generally as 4 and of which only the left hand end is shown in FIG. 1.
  • the inlet duct 3 continues downwardly at 5 towards the bottom of the reservoir 4 where it turns through a right angle at 6 and leads to a perforated horizontal extension 7 formed with a large number of small holes 8 through which the products of combustion bubble upwardly through liquid in the reservoir 4.
  • the level of the liquid is indicated by two horizontal lines 9 which represent the upper and lower levels which may be assumed by the liquid during operation. For most purposes the liquid in the reservoir will be water and will be described as such, but under some circumstances other liquids may be used.
  • the perforated extension 7 forms a screen through which passage of the combustion products transfers heat directly to the water within the reservoir.
  • the arrangement of holes 8 around the extension 7 is best seen from FIG. 2, but this arrangement is by no means critical. The arrangement is such that a large number of small bubbles is created so that the ratio of surface area to volume is very high and consequently a high rate of heat transfer is achieved.
  • a suitable size of hole is of approximately 0.75 mm diameter which causes the gas bubbles to be above a critical size in which the temperature of the trapped gas is still above that of the water when each bubble breaks through thesurface. This provides super heat to the steam and in this way an extremely efficient vapour generator is provided.
  • baffle plates 12 of which only one is seen in FIG. 2 are provided at intervals along the length of the reservoir. Each plate 12 is formed with openings 13 seen in FIG. 2 which permits free but con trolled flow of both liquid and steam while avoiding splashing and the surging movement of the water.
  • the baffle plates 12 are arranged to divide the reservoir 4 into compartments each having a length of about 65 percent of the diameter.
  • Outlet of pressure fluid from the reservoir 4 is controlled by the requirements of the motor to be driven or other apparatus to be supplied with the pressure fluid.
  • An outlet pipe 15 extends from the top of the reservoir 4 and passes outwardly through the wall at 16 in the lower half of the reservoir. It is important to avoid liquid being carried over with the pressure fluid into the pipe 15 and for this purpose the pipe is formed close to its end (which is obstructed by the presence of the wall of the reservoir) with small openings 17, and the upper end of the pipe is surrounded by a cup-shaped shield 20 formed with drainage openings 21 close to its bottom and lying on a line at right angles to that of the openings 17.
  • reservoirs 24 and 34 (shown in FIG. 4) similar to the reservoir 4 are provided in series with the outlet from the reservoir 4.
  • pressure fluid from the reservoir 4 together with any entrained liquid passes firstly to the reservoir 24, the outlet from which is arranged in a similar way to that from the reservoir 4 and the components of which are indicated by the same reference numerals.
  • the outlet from the reservoir 24 then passes to the reservoir 34 where again the outlet arrangement is similar, in any convenient direction and from there the pressure fluid passes onwardly to its point of application. By the time the pressure fluid leaves the reservoir 34 any entrained liquid is quite negligible.
  • the heat from and with the products of combustion of the engine 1 is converted with high efficiency into a pressure fluid which can be withdrawn as required.
  • a pressure fluid which can be withdrawn as required.
  • the pressure in the reservoir 4 builds up, it applies back pressure to the engine 1 and this, in combination with the high temperatures involved tends to cause the release valve of the engine to overheat, leading to erosion of the valve and its seat.
  • a free-piston engine is particularly suitable for this purpose and it is an engine of this type which is shown in the drawings.
  • the piston and cylinder are shown as 35 and 36 respectively and the release valve and its seat as 38 and 39 respectively.
  • the release valve carries a sparking plug 40 at its center and is controlled by four loading springs 41 of the leaf pack type. Two of these are seen at the right hand side of FIG. 3, the left hand half of this Figure being in section.
  • the valve 38 opens automatically when the pressure in the combustion chamber shown as 42 exceeds that exerted by the springs 41 and the combustion products then pass to the reservoir 4.
  • the free-piston engine illustrated will, of course, have two opposed cylinders, but in principle an engine having any number of cylinders may be used. These will all have similar release valve arrangements so that a description of the single cylinder shown in the drawing will suffice.
  • the line 2, inlet duct 3,5 and right angle piece 6, are repeated in mirror fashion at the opposite end of the reservoir 4, where the products of combustion enter the horizontal extension 7 from the opposite end.
  • these may either be arranged to manifold into the existing lines 2, 3 or may use an additional reservoir 4a shown in dotted lines in FIG. 4 which, in turn, feeds into the reservoir 24.
  • a cooling arrangement is provided which (as illustrated) is supplied with liquid from the reservoir 4 by a further line not shown in detail but indicated diagrammatically by the dotted line 45.
  • this line may be supplied from a separate source to replace lost water.
  • valve 38 As the valve 38 opens to the full the coefficient will improve and the orifice 46 will enlarge. Whereas in a conventional engine, ignition in the closed chamber would cause a pressure rise of some five times the compression pressure, this does not occur in a free-piston engine as illustrated in which the pressure rise is limited to about half that which would otherwise be expected. Nevertheless, by the time the release valve 38 is again seated which is about 1 millisecond later, some 80 percent of the combustion products will have escaped and most of the energy necessary for cycling will have been imparted to the piston assembly. At this stage the inward movement of the piston will have led to an increase of volume of the combustion space 42 of about 60 percent.
  • the improvement results from three main factors. Since the free-piston engine operates substantially at one set load and frequency, it is possible to adjust both the air/fuel ratio and the ignition timing to their optimum settings. The total amount of heat for subsequent transfer to the working fluid in the reservoir 4 is removed from the combustion space 42 at the outer end of the working stroke of the piston and, as already described, only the small proportion of burned gas required for cycling loses heat to the cylinder walls. Moreover, the relatively much lower pressure of gas during this stroke results in less friction due to inflation of the piston rings. Finally, as a result of thecooling system about to be described, the unavoidable heat transfer through the walls of the combustion chamber 42 is absorbed by the cooling liquid and passes with it and the products of combustion into the pressure fluid in the reservoir 4.
  • the liquid from the reservoir 4 passes through a fitting (not shown in the drawings) screwed into the outer head 51 at 52. From there the liquid passes to a substantially annular chamber 53.
  • the holes 54 and 55 thus pass through an outer portion of the diaphragm 62 which is annular in shape and has a free inner edge 65 which bears against the inner head 61 which constitutes the wall of the chamber 60.
  • the inner edge 65 of the diaphragm 62 is shown to an enlarged scale in FIG. 6 for which it can be seen that the edge locates in an annular recess indicated generally as 67 in the inner head 61.
  • This recess 67 has a square-cut corner 68 and the edge 65 is chamfered at 70-so as to leave an annular passage 71 of triangular section between the edge of the diaphragm 62 and the recess 67.
  • edge 65 of the diaphragm 62 is shaped as shown in FIG. 5.
  • the right hand side of the diaphragm as seen in FIG 6, that is to say the side in communication with the chamber 60, is formed with a series of approximately radial slots 73, which decrease in depth from the edge 65 so as to form a triangular configuration as seen in FIG. 5.
  • These slots are equally spaced and alternate with a series of generally axial slots 74 best seen in FIG. 5.1m one of whichcan be seen in FIG. 6.
  • the combination of the slots 73, the annular passage 71 and the axial slots 74 provides a series of narrow openings connecting the liquid in the chamber 60 to the chamber 63.
  • liquid is able to pass in a generally radial direction along one of the slots 73, from there in a circumferential direction along the passage 71 and thence in an axial direction along one of the slots 74 into the chamber 63.
  • the diaphragm 62 effectively forms a sealing gasket between the liquid in the chamber 60 and the high pressure of the combustion products in the chamber 63 against leakage to the exterior of the head.
  • FIG. 6 The large scale view of FIG. 6, in addition to showing the relationship between the diaphragm 62 and the inner head 61, also shows further details of the release valve 38 and the seat 39. Both these parts are subject to erosion due to the high temperatures involved since excess heat absorbed by the valve 38 will tend to flow to the seat 39 during the considerable portion of each cycle when the valve is seated.
  • each is shown as provided with an insert 80 and 81 respectively of metal resistant to high temperature gas erosion and thermal shock.
  • a particularly suitable metal for this purpose is a cobalt base alloy such as that available under the Trade Mark Stellite 6.
  • the valve 38 slides in a guide bore indicated as 83 and the provision of an adequate pressure seal between the valve 38 and the bore 83 is of considerable importance.
  • the wall of the bore is extended at 85 to form a relatively thin, sharp-angled lip which, during the initial manufacture is deformed inwardly as shown in dotted lines at 86 so as to form an interference fit with the valve 38.
  • this interference fit maintains an adequate seal, but even after long periods of running when both the surface of the valve 38 and of the lip 85 have been subjected to wear, the seal is maintained since the pressure in the chamber 63 develops a hoop-stress in the lip 85 which will keep the lip in close contact with the sides of the valve 38, thus providing an efficient seal with little friction and negligible wear.
  • Apparatus for the generation of liquid vapour under pressure by means of heat from the combustion products of an internal combustion engine comprising an internal combustion engine having at least one release valve having a seat and an outlet, a reservoir for the liquid to be vapourised, an inlet duct to said reservoir for said combustion products, and a connection between said outlet of said release valve and said inlet duct for the combustion products, said duct communicating with the lower part of the interior of the reservoir, and a screen formed with a large number of small holes providing free passage for gas or liquid, said screen being arranged between said duct and the interior of said reservoir whereby the combustion products may bubble upwardly through liquid in the reservoir so as to transfer heat directly to the liquid, and said engine including at least one cylinder head and structure defining at least one chamber in contact with said cylinder head, and a second duct connected to supply liquid from said reservoir to said chamber, said chamber including a portion adjacent said seat of said release valve, said portion including narrow outlets opening into a region in said inlet duct immediately following said valve, whereby liquid is drawn
  • said chamber includes an annular diaphragm mounted to separate said annular portion from said region in said inlet duct, said annular diaphragm having a free inner edge bearing against said cylinder head adjacent said valve seat, said narrow openings being formed between said inner edge of said diaphragm and said cylinder head.
  • Apparatus according to claim 1 including a guide bore in which said release valve works, said bore having a wall which is extended to form a relatively thin, narrow-angled lip bearing against the side of said release valve to maintain an effective seal.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
US00200445A 1970-12-04 1971-11-19 Vapor generators Expired - Lifetime US3760778A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB5780970A GB1364456A (en) 1970-12-04 1970-12-04 Vapour generators

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US3760778A true US3760778A (en) 1973-09-25

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US00200445A Expired - Lifetime US3760778A (en) 1970-12-04 1971-11-19 Vapor generators

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US (1) US3760778A (fr)
AR (1) AR194214A1 (fr)
AT (1) AT315208B (fr)
AU (1) AU452911B2 (fr)
BE (1) BE776217A (fr)
CA (1) CA940397A (fr)
CH (1) CH540460A (fr)
DE (1) DE2159771A1 (fr)
DK (1) DK137201B (fr)
ES (1) ES397646A1 (fr)
FR (1) FR2117144A5 (fr)
GB (1) GB1364456A (fr)
IT (1) IT945215B (fr)
NL (1) NL7116595A (fr)
SE (1) SE366817B (fr)
ZA (1) ZA717643B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4030456A (en) * 1975-11-05 1977-06-21 Corpus Daniel J M Vapor injector for internal combustion engines
US5113806A (en) * 1991-03-04 1992-05-19 Rodart George H Bicatalytic igniter converter and processor for internal combustion engines
ES2068149A2 (es) * 1993-06-09 1995-04-01 Ergos S A Caldera con aprovechamiento termico, en especial de los gases de combustion de motores.
US5735235A (en) * 1996-04-16 1998-04-07 Li; Weicheng Method and system for heating a liquid
US6666433B1 (en) 2000-06-27 2003-12-23 Dresser-Rand Company Grooved valve seat with inlay
US7255067B1 (en) 2006-04-10 2007-08-14 Thorpe Douglas G Evaporative in-cylinder cooling
US20070234977A1 (en) * 2006-04-10 2007-10-11 Thorpe Douglas G Evaporative in-cylinder cooling

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112317308B (zh) * 2020-11-05 2022-06-21 山东润昇新型建筑材料有限公司 一种石子生产用筛选装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US671236A (en) * 1900-02-26 1901-04-02 Louis Renault Steam-generating explosion-engine.
US706781A (en) * 1901-07-09 1902-08-12 William H Reynolds Steam-trap.
FR551533A (fr) * 1921-05-17 1923-04-07 Chaudière à vapeur
US1775263A (en) * 1927-09-29 1930-09-09 Martin W Wiegand Auxiliary vapor-supplying appliance for gas engines
GB360382A (fr) * 1929-05-23 1931-11-02 Hugo Junkers
US1873119A (en) * 1927-07-20 1932-08-23 Doherty Res Co Air cooled valve and valve seat
US2136690A (en) * 1930-08-12 1938-11-15 Eaton Mfg Co Internal combustion engine valve and seat
US3450116A (en) * 1967-08-28 1969-06-17 Alton D Knight Vapor charging system for internal combustion engines

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US671236A (en) * 1900-02-26 1901-04-02 Louis Renault Steam-generating explosion-engine.
US706781A (en) * 1901-07-09 1902-08-12 William H Reynolds Steam-trap.
FR551533A (fr) * 1921-05-17 1923-04-07 Chaudière à vapeur
US1873119A (en) * 1927-07-20 1932-08-23 Doherty Res Co Air cooled valve and valve seat
US1775263A (en) * 1927-09-29 1930-09-09 Martin W Wiegand Auxiliary vapor-supplying appliance for gas engines
GB360382A (fr) * 1929-05-23 1931-11-02 Hugo Junkers
US2136690A (en) * 1930-08-12 1938-11-15 Eaton Mfg Co Internal combustion engine valve and seat
US3450116A (en) * 1967-08-28 1969-06-17 Alton D Knight Vapor charging system for internal combustion engines

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4030456A (en) * 1975-11-05 1977-06-21 Corpus Daniel J M Vapor injector for internal combustion engines
US5113806A (en) * 1991-03-04 1992-05-19 Rodart George H Bicatalytic igniter converter and processor for internal combustion engines
ES2068149A2 (es) * 1993-06-09 1995-04-01 Ergos S A Caldera con aprovechamiento termico, en especial de los gases de combustion de motores.
US5735235A (en) * 1996-04-16 1998-04-07 Li; Weicheng Method and system for heating a liquid
US6666433B1 (en) 2000-06-27 2003-12-23 Dresser-Rand Company Grooved valve seat with inlay
US6817594B2 (en) 2000-06-27 2004-11-16 Dresser-Rand Company Grooved valve seat with inlay
US7255067B1 (en) 2006-04-10 2007-08-14 Thorpe Douglas G Evaporative in-cylinder cooling
US20070234977A1 (en) * 2006-04-10 2007-10-11 Thorpe Douglas G Evaporative in-cylinder cooling
US7299770B2 (en) 2006-04-10 2007-11-27 Thorpe Douglas G Evaporative in-cylinder cooling

Also Published As

Publication number Publication date
BE776217A (fr) 1972-06-05
FR2117144A5 (fr) 1972-07-21
AR194214A1 (es) 1973-06-29
ZA717643B (en) 1972-08-30
AU452911B2 (en) 1974-08-20
DK137201B (da) 1978-01-30
AT315208B (de) 1974-05-10
ES397646A1 (es) 1974-04-16
DK137201C (fr) 1978-07-03
GB1364456A (en) 1974-08-21
SE366817B (fr) 1974-05-06
DE2159771A1 (de) 1972-07-06
CH540460A (fr) 1973-08-15
NL7116595A (fr) 1972-06-06
IT945215B (it) 1973-05-10
CA940397A (en) 1974-01-22
AU3605471A (en) 1973-05-31

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