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WO2008010998A2 - Vanne de séparation dans un moteur thermique à régénération - Google Patents

Vanne de séparation dans un moteur thermique à régénération Download PDF

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Publication number
WO2008010998A2
WO2008010998A2 PCT/US2007/016149 US2007016149W WO2008010998A2 WO 2008010998 A2 WO2008010998 A2 WO 2008010998A2 US 2007016149 W US2007016149 W US 2007016149W WO 2008010998 A2 WO2008010998 A2 WO 2008010998A2
Authority
WO
WIPO (PCT)
Prior art keywords
steam
flow
multiple branch
outlets
lines
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/US2007/016149
Other languages
English (en)
Other versions
WO2008010998A3 (fr
Inventor
Harry Schoell
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
CYCLONE POWER TECHNOLOGIES Inc
Original Assignee
CYCLONE POWER TECHNOLOGIES Inc
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
Priority claimed from US11/489,335 external-priority patent/US7856822B2/en
Application filed by CYCLONE POWER TECHNOLOGIES Inc filed Critical CYCLONE POWER TECHNOLOGIES Inc
Publication of WO2008010998A2 publication Critical patent/WO2008010998A2/fr
Publication of WO2008010998A3 publication Critical patent/WO2008010998A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers

Definitions

  • This invention relates to directing flow of fluid and steam from a single line into multiple lines and, more particularly, to a splitter valve at the juncture of a feeder line and multiple branch lines for equalizing flow and pressure of fluid and steam among the multiple branch lines.
  • splitting a feeder tube (i.e. feeder line) into multiple branch tubes (i.e. branch lines) having a combined cross-sectional area equal to the feeder tube would effectively and significantly increase the tube surface area within the same volume of space.
  • the efficiency of heat transfer is greatly improved.
  • the smaller tube diameter allows the tube to withstand higher pressures. While such equalization of volumes and capacities between a single feeder line and multiple branch lines of reduced size would be balanced under static conditions, under the dynamic conditions of super critical high temperatures and high pressures, comparative flow among the smaller branch lines can become unbalanced. This can lead to potential overheating and possible wall failure in the pipe that has lower flow volume (i.e. a lower amount of water and steam flowing therethrough).
  • the present invention solves this problem by equalizing flow and pressure in the multiple branch lines, even at high temperatures and pressure levels.
  • valve device at the juncture of a single feeder line and multiple branch lines in a steam engine for equalizing flow and pressure of fluid and steam among the multiple branch lines.
  • the present invention is directed to splitter valve for use in a heat regenerative engine that uses water as both the working fluid and the lubricant.
  • water is pumped through a single line of a coil that wraps around a cylinder exhaust port, causing the water to be preheated by steam exhausted from the cylinder.
  • the preheated water is then directed through multiple branch lines in a steam generator to produce high pressure super heated steam.
  • the splitter valve is located at the juncture of the single line and multiple branch lines to equalize the flow among the multiple branch lines.
  • a "Y" junction within the splitter valve minimizes turbulence as the flow of water and steam is directed into the multiple branch lines.
  • Flow control restrictors in the splitter valve allow unimpeded flow of fluid towards the steam generator through each of the branch lines, while allowing any incremental over-pressure in any one branch line to "bleed" back to a branch line(s) bearing a lesser amount of pressure, thereby equalizing flow through the multiple branch lines.
  • Figure 1 is a general diagram illustrating air flow through the engine
  • Figure 2 is a general diagram illustrating water and steam flow through the engine
  • Figure 3 is a side elevational view, shown in cross-section, illustrating the principal components of the engine
  • Figure 4 is a top plan view, in partial cross-section, taken along the plane of the line 4-4 in figure 3;
  • Figure 5 is a top plan view of the splitter valve of the present invention
  • Figure 6 is a cross-sectional view of the splitter valve taken along line 6-6 in figure 5 and illustrating a flow control valve within the splitter valve.
  • the present invention is directed to a splitter valve 26 for use in a steam engine 10.
  • the engine 10 includes a steam generator 20, a condenser 30 and a main engine section 50 comprising cylinders 52, valves 53, pistons 54, push-rods 74, crank cam 61 and a crankshaft 60 extending axially through a center of the engine section.
  • ambient air is introduced into the condenser 30 by intake blowers 38.
  • the air temperature is increased in two phases before entering a cyclone furnace 22 (referred to hereafter as "combustion chamber").
  • the condenser 30 is a flat plate dynamic condenser with a stacked arrangement of flat plates 31 surrounding an inner core.
  • This structural design of the dynamic condenser 30 allows for multiple passes of steam to enhance the condensing function.
  • air enters the condenser 30 from the blowers 38 and is circulated over the condenser plates 31 to cool the outer surfaces of the plates and condense the exhaust steam circulating within the plates.
  • vapor exiting the exhaust ports of the cylinders 52 passes over the pre-heating coils surrounding the cylinders.
  • the vapor drops into the core of the condenser where centrifugal force from rotation of the crankshaft drives the vapor into the inner cavities of the condenser plates 31.
  • the vapor changes phase into a liquid, it enters sealed ports on the periphery of the condenser plates.
  • the condensed liquid drops through collection shafts and into the sump 34 at the base of the condenser.
  • a high pressure pump 90 returns the liquid from the condenser sump 34 to the coils in the combustion chamber, completing the fluid cycle of the engine.
  • the stacked arrangement of the condenser plates 31 presents a large surface area for maximizing heat transfer within a relatively compact volume.
  • the centrifugal force of the crankshaft impeller that repeatedly drives the condensing vapor into the cooling plates 31, combined with the stacked plate design, provides a multi-pass system that is far more effective than conventional condensers of single-pass design.
  • the engine shrouding 12 is an insulated cover that encloses the combustion chamber and piston assembly.
  • the shroud 12 incorporates air transfer ducts 32 that channel air from the condenser 30, where it has been preheated, to the intake portion of air-to-air heat exchangers 42, where the air is further heated. Exiting the heat exchangers 42, this heated intake air enters the atomizer/ igniter assemblies in the burner 40 where it is combusted in the combustion chamber.
  • the shroud also includes return ducts that capture the combustion exhaust gases at the top center of the combustion chamber, and leads these gases back through the exhaust portion of the air-to-air heat exchangers 42.
  • the engine shrouding adds to the efficiency and compactness of the engine by conserving heat with its insulation, providing necessary ductwork for the airflow of the engine, and incorporating heat exchangers that harvest exhaust has heat.
  • Water in its delivery path from the condenser sump pump 90 to the combustion chamber 22 is pumped through one or more main steam supply lines 21 for each cylinder.
  • the main steam line 21 passes through a pre-heating coil 23 that is wound around each cylinder skirt adjacent to that cylinder's exhaust ports (see figure 2).
  • the vapor exiting the exhaust ports of cylinders 52 gives up heat to this coil, which raises the temperature of the water being directed through the coil 23 toward the combustion chamber 22.
  • the exhaust vapor begins the process of cooling on its path through these coils preparatory to entering the condenser.
  • the positioning of these coils 23 adjacent to the cylinder exhaust ports scavenges heat that would otherwise be lost to the system, thereby contributing to the overall efficiency of the engine.
  • the air is directed through heat exchangers 42 where the air is heated prior to entering the steam generator 20 (see figures 2 and 3).
  • the preheated air is mixed with fuel from a fuel atomizer 41 (See Figure 4).
  • An igniter 43 burns the atomized fuel in a centrifuge, causing the heavy fuel elements to move towards the outer sides of the combustion chamber 22 where they are consumed.
  • the combustion chamber 22 is arranged in the form of a cylinder which encloses a circularly wound coil of densely bundled tubes 24 (see figure 3) forming a portion of the steam supply lines leading to the respective cylinders.
  • the bundled tubes 24 are heated by the burning fuel of the combustion nozzle burner assembly 40 comprising the air blowers 38, fuel atomizer 41, and the igniter 43 (see figure 4).
  • the burners 40 are mounted on opposed sides of the circular combustion chamber wall and are aligned to direct their flames in a spiral direction. By spinning the flame front around the combustion
  • the coil of tubes 24 is repetitively "washed' by the heat of this combustion gas which circulates in a motion to the center of the tube bundle 24. Temperatures in the tube bundle 24 are maintained at approximately 1,200 degrees Fahrenheit.
  • the tube bundle 24 carries the steam and is exposed to the high temperatures of combustion, where the steam is superheated and maintained at a pressure of approximately 3,200 psi.
  • the hot gas exits through an aperture located at the top center of the round roof of the cylindrical combustion chamber.
  • the centrifugal motion of the combustion gases causes the heavier, unburned particles suspended in the gases to accumulate on the outer wall of the combustion chamber where they are incinerated, contributing to a cleaner exhaust. This cyclonic circulation of combustion gases within the combustion chamber creates higher efficiency in the engine.
  • multiple passes of the coil of tubes 24 allows for promoting greater heat saturation relative to the amount of fuel expended.
  • the shape of the circularly wound bundle of tubes permits greater lengths of tube to be enclosed within a combustion chamber of limited dimensions than within that of a conventional boiler.
  • a greater tube surface area is exposed to the combustion gases, promoting greater heat transfer so that the fluid can be heated to higher temperatures and pressures which further improves the efficiency of the engine.
  • the splitter valve 26 located at the juncture of the single line 21 to the multiple lines 28 (see figure 3), equalizes the flow between the branch lines (see figures 3, 15 and 6).
  • the splitter valve includes a main body 100 with an inlet 102 for connection to the single feeder line 21 and a plurality of outlets 104 for connection to each of the branch lines 28.
  • a juncture 29 within the splitter valve 26 minimizes turbulence by forming not a right angle T' intersection, but a ⁇ ' intersection with a narrow apex 106.
  • Flow control valves or restrictors include ball check valves 27 between the juncture 29 and outlets 104 that allow unimpeded flow of fluid towards the steam generator 20 through each of the branch lines 28.
  • the ball check valves 27 prevent back-flow into the feeder line 21. Instead, any incremental over-pressure in one line is caused to Taleed' back to an U

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un moteur thermique à régénération qui utilise de l'eau tant comme fluide de travail que comme lubrifiant. L'eau est pompée dans un circuit unique d'un serpentin qui entoure l'orifice d'échappement d'un cylindre et entraîne le préchauffage de l'eau par la vapeur évacuée du cylindre. L'eau préchauffée est alors dirigée à travers de multiples circuits ramifiés pour atteindre un générateur de vapeur pour produire une vapeur surchauffée haute pression. Une vanne de séparation à la jonction du circuit unique et des multiples circuits ramifiés égalise l'écoulement dans les multiples circuits ramifiés. Une jonction en « Y » dans la vanne de séparation minimise la turbulence au fur et à mesure que le flux d'eau et de vapeur est dirigé dans les multiples circuits ramifiés. Dans la vanne de séparation, des réducteurs de contrôle de débit permettent un écoulement libre de fluide et de vapeur vers le générateur de vapeurs à travers chacun des circuits ramifiés tout en permettant une augmentation de la surpression dans tous les circuits ramifiés pour 'purger' un ou plusieurs circuits ramifiés et faire diminuer la pression et de ce fait égaliser le flux dans ces circuits.
PCT/US2007/016149 2006-07-19 2007-07-17 Vanne de séparation dans un moteur thermique à régénération Ceased WO2008010998A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US11/489,335 US7856822B2 (en) 2004-09-14 2006-07-19 Heat regenerative engine
US11/489,335 2006-07-19
US11/509,202 2006-08-24
US11/509,202 US20070056287A1 (en) 2005-09-13 2006-08-24 Splitter valve in a heat regenerative engine

Publications (2)

Publication Number Publication Date
WO2008010998A2 true WO2008010998A2 (fr) 2008-01-24
WO2008010998A3 WO2008010998A3 (fr) 2008-05-08

Family

ID=38957308

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2007/016149 Ceased WO2008010998A2 (fr) 2006-07-19 2007-07-17 Vanne de séparation dans un moteur thermique à régénération

Country Status (2)

Country Link
US (1) US20070056287A1 (fr)
WO (1) WO2008010998A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8344528B2 (en) 2009-07-01 2013-01-01 Terry Edgar Bassett Waste oil electrical generation systems
US9540960B2 (en) 2012-03-29 2017-01-10 Lenr Cars Sarl Low energy nuclear thermoelectric system
US10475980B2 (en) 2012-03-29 2019-11-12 Lenr Cars Sa Thermoelectric vehicle system

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010030864A2 (fr) * 2008-09-11 2010-03-18 Will Weldon Mathews Moteurs hybrides à conversion de l’énergie de combustion
JP6376492B2 (ja) * 2013-09-10 2018-08-22 パナソニックＩｐマネジメント株式会社 空冷ユニット

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3881513A (en) * 1974-01-25 1975-05-06 Sun Oil Co Pennsylvania Three-coordinate fluid manifold
US4301832A (en) * 1980-05-19 1981-11-24 Smith Dale R Pressure converter valve
DE3279179D1 (en) * 1982-06-15 1988-12-08 Jonas Sundberg Valve device for controlling the delivery of pressurized liquid to two separate hydrostatic motors from a common source of pressurized liquid
US4543990A (en) * 1983-07-05 1985-10-01 Aqua Control, Inc. Irrigation valve
DE4311672A1 (de) * 1993-04-08 1994-10-13 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
US20050199293A1 (en) * 2004-02-12 2005-09-15 Fulcher Robert A. Manifold for selectively dispersing multiple fluid streams

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8344528B2 (en) 2009-07-01 2013-01-01 Terry Edgar Bassett Waste oil electrical generation systems
US9540960B2 (en) 2012-03-29 2017-01-10 Lenr Cars Sarl Low energy nuclear thermoelectric system
US10475980B2 (en) 2012-03-29 2019-11-12 Lenr Cars Sa Thermoelectric vehicle system

Also Published As

Publication number Publication date
WO2008010998A3 (fr) 2008-05-08
US20070056287A1 (en) 2007-03-15

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