US20070148605A1 - Splitter valve - Google Patents

Splitter valve Download PDF

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Publication number
US20070148605A1
US20070148605A1 US10/546,848 US54684804A US2007148605A1 US 20070148605 A1 US20070148605 A1 US 20070148605A1 US 54684804 A US54684804 A US 54684804A US 2007148605 A1 US2007148605 A1 US 2007148605A1
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US
United States
Prior art keywords
valve
burner
flow
vane
splitter
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.)
Abandoned
Application number
US10/546,848
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English (en)
Inventor
James Lowrie
Stephen Hasko
Anthony Owens
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.)
Koninklijke Philips NV
Microgen Engine Corp Holding BV
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to MICROGEN ENERGY LIMITED reassignment MICROGEN ENERGY LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HASKO, STEPHEN MICHAEL, OWENS, ANTHONY PETER MICHAEL, LOWRIE, JAMES ROBERT
Assigned to KONINKLIJKE PHILIPS ELECTRONICS N.V. reassignment KONINKLIJKE PHILIPS ELECTRONICS N.V. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WANG, LING
Publication of US20070148605A1 publication Critical patent/US20070148605A1/en
Assigned to MICROGEN ENGINE CORPORATION HOLDING B.V. reassignment MICROGEN ENGINE CORPORATION HOLDING B.V. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SUNPOWER INC.
Assigned to SUNPOWER INC. reassignment SUNPOWER INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MICROGEN ENERGY LIMITED
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/08—Regulating fuel supply conjointly with another medium, e.g. boiler water
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/04—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
    • F16K11/052—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves with pivoted closure members, e.g. butterfly valves
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K2203/00—Feeding arrangements
    • F23K2203/10—Supply line fittings
    • F23K2203/105—Flow splitting devices to feed a plurality of burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2237/00—Controlling
    • F23N2237/02—Controlling two or more burners

Definitions

  • the present invention relates to a splitter valve for splitting a single fluid stream into two streams.
  • valves are known in the art and are primarily used to handle powders, dry solids and slurries, although some types are available that can handle liquids or gases.
  • splitter valves There are two main types of splitter valves. One is a Y line diverter, which contains a poppet whose position is adjustable to proportion incoming flow between two outlets. The second type of splitter is primarily used for liquid. Instead of using moving parts, the flow stream is altered by pneumatic pressure differential pumping.
  • U.S. Pat. No. 4,169,354 discloses an air/gas diverter. This uses a butterfly valve to vary the proportion of flow that is directed through two parallel ducts.
  • U.S. Pat. No. 3,905,193 describes a diaphragm valve diverting air flow away from an exhaust system, with the proportion of flow directed to each outlet duct controlled by an exhaust manifold vacuum.
  • U.S. Pat. No. 5,184,592 discloses a diverter valve for a premix flow providing variable flow to two outlet streams.
  • the application is for internal combustion engines, with an atmospheric air intake to the valve.
  • the splitter valve is used to vary the proportion of the incoming charge sent through the preheater after mixing.
  • the degree of preheating is used to vary the density of the fuel: air charge and therefore torque.
  • the arrangement is designed to be a replacement for a conventional throttle. The actual detail of the valve design is not disclosed.
  • the present invention is primarily intended for use in a gas-fired domestic appliance, and more particularly, a domestic combined heat and power system using a linear free piston Stirling engine.
  • the Stirling engine can provide a certain amount of heat.
  • a supplementary burner is required. Both the Stirling engine burner and the supplementary burner require a supply of fuel and air. The two supplies can be independent. However, this introduces complexity also problems with hot gases from one burner being drawn back through an inactive burner. Therefore, preferably, the two burners are supplied with air from a single fan which is then split by a splitter valve into separate streams.
  • a splitter valve for splitting a single fluid stream into two streams, the valve comprising a vane rotatable through a range of positions across an orifice to vary the ratio of the single fluid stream diverted to the two streams, wherein the orifice is profiled such that there is a substantially linear relationship between the angular position of the vane and the ratio of the fluid diverted to the two streams.
  • a splitter valve of this type can cause significant turbulence in the fluid passing through the valve. This can be overcome by design modifications tailored to match the nature of the flow path. Once such modification involves the addition of a ramp extending along the inner surface of either flow passageway downstream of the valve reducing the flow area and then increasing it again, positioned so as to direct the flow and minimise turbulence. In an alternative design a laminarising device is provided in each of the two streams downstream of the splitter valve.
  • the laminarising device is preferably a plate with a plurality of apertures, but may also be a device with a significant dimension in the direction of flow which effectively provides a plurality of tubes through which the fluid flows.
  • the second aspect of the invention may be broadly defined as a heating appliance comprising first and second burners, a supply of air, a splitter valve for splitting the supply of air into a stream feeding the first burner and a stream feeding the second burner, means for feeding combustible fuel to mix with the air, a controller for controlling the combustible fuel flow and a proportion of the air fed to each burner dependent on the appliance requirements, and a laminarising device for each of the stream feeding the first burner and the stream feeding the second burner positioned downstream of the splitter valve.
  • the laminarising device is preferably a plate with a plurality of apertures, but may also be a device with a significant dimension in the direction of flow which effectively provides a plurality of tubes through which the fluid flows.
  • FIG. 1 is a perspective view of the valve casting with top plate removed
  • FIG. 2 is a cross-section through line A-A in FIG. 1 showing the profiled orifice
  • FIG. 3 is a cross-section through line Y-Y in FIG. 1 ;
  • FIG. 4 is a cross-section through line X-X in FIG. 1 ;
  • FIG. 5 is a graphical representation of the flow characteristics of a uniform orifice
  • FIG. 6 is a similar representation of the flow characteristics of a profiled orifice
  • FIG. 7 is a control map of the vane angle and fan speed characteristics for a dual burner.
  • FIG. 8 is a schematic diagram of the air and gas supply to a dual burner system.
  • the valve casting of FIG. 1 has an air inlet port 1 having a curved shape as shown in FIG. 3 .
  • Two outlet ports 2 , 3 lead from the valve casting. The first of these is provided with a perforate plate 14 . Ducting for the outlet port is provided on the bottom plate and ducting for the outlet parts is provided on the top plate (not shown).
  • a splitter valve comprising a vane 5 which is rotatable about the spindle 6 under the control of a servo motor (not shown).
  • Two valve seats 7 , 8 are provided in the casting to seat the vane 5 at the two extremities of its travel.
  • a profiled plate 9 Located upstream of the vane 5 is a profiled plate 9 , the downstream face of which has an arcuate shape to accommodate the movement of the vane 5 .
  • the profile plate is best illustrated in FIG. 2 .
  • the orifice 10 is symmetrical about a centre line 11 . When the vane 5 is positioned on this centre line, equal flow is diverted to the two outlet ducts 2 , 3 .
  • the orifice 10 is profiled such that the general flow tends to be concentrated towards the centre line 11 .
  • the exact profile of the orifice is determined functionally in accordance with the considerations set out below.
  • FIG. 5 shows the flow characteristics which will be obtained by a rectangular (letter box-shaped) orifice. In other words, this would be the profile if no profiled plate 9 were present in the valve shown in FIGS. 1 and 2 .
  • the X axis shows the vane angle from a centre line shown as 0° in the centre of the graph, while the Y axis shows the percentage of flow out of the two outlet ports.
  • Line 30 shows the flow to one outlet, while line 31 shows the flow to the other outlet. It is immediately apparent that moving the vane through a considerable angle away from the centre line has little or no impact in the flow to the two outlets. No control of the flows is therefore available in this range of movement. It is only once the valve gets relatively close to its closed position on either side that any significant change in flow is noticed.
  • FIG. 6 shows the impact of the profiled orifice.
  • Line 40 represents the flow to one outlet, while line 41 represents the flow to the other.
  • Both lines are approximately linear, as compared to corresponding lines in FIG. 5 .
  • true linearity is impossible to achieve in practice.
  • FIG. 6 what is apparent from FIG. 6 is that any variation in vane angle will result in a noticeable variation in the flow to the two ports. Therefore, the flow is now controllable to a far more accurate extent across the full range of vane angles. This allows more accurate control of both burners, with a resulting increase in the accuracy of control to the power and heat output.
  • FIG. 7 shows the control map derived using experimental data with the valve of FIGS. 1 and 2 .
  • the required output from one burner is shown in a set of curves from left to right in FIG. 7 , while the required output for the other is shown by the curves from right to left.
  • the required fan speed and vane position are obtained at the cross-over point of the two curves.
  • the exact change in fan speed with a vane angle for all combinations of burner flows has been derived experimentally, as the downstream gas path design will have significant impact on the flows involved.
  • splitter valve could have applications beyond the current use in a twin-burner gas-fired appliance. Any dual burner system could incorporate such a valve. Potential applications include ventilation systems or industrial processes.
  • the vane 5 does not provide an airtight seal when it is seated. For the gas-fired domestic appliance for which the valve is designed, this is not a problem and can even be beneficial that it always provides a positive purge air flow to an unused burner. Indeed, a small hole may be provided through the vane to ensure that a purge flow is present.
  • Airflow along the two separate outlet ducts is dependent on the speed of the fan and the relative flow resistance of each duct.
  • the latter is dominated by the respective cross-sectional areas (immediately following the fan outlet) at which the airflow is divided.
  • a further condition is that the total pressure drop in each arm, i.e., burner loss plus splitter valve loss, must be equal.
  • the open area for airflow down each tract is directly and linearly related to the angle of the vane.
  • the gas train for a heating appliance is shown in FIG. 6 .
  • the splitter valve 5 is as shown in FIG. 1 .
  • Air is fed to the splitter valve by a variable speed DC fan 60 from an inlet 61 , controlled by a control signal 62 .
  • This flow is split as previously described under the control of control signal 63 .
  • the split flow is then passed through laminarising devices 4 . These may take the form of perforated plates (one of which is shown in FIG. 1 ) or a set of channels, effectively providing a “honeycomb”. arrangement.
  • the open area of these devices is maximised in order to minimise the pressure drop caused by the devices.
  • FIG. 1 An alternative laminarising device is shown in FIG. 1 in the line to the outlet 3 .
  • the lower wall of outlet 3 is also ramped as shown at 14 to help smooth the flow.
  • Each laminarised stream then passes into a venturi 65 in which it is mixed with combustible gas 66 under the control of a governor valve 67 before being supplied to either the engine burner 68 or supplementary burner 69 .
  • dP is sum of pressure drops experienced by the flow in traversing the tract.
  • K is a geometric factor reflecting shape, texture and sectional area of the tract.
  • volumetric output from a blower or fan Q f ( dP,v,N )
  • dP pressure rise across fan
  • v is kinematic viscosity
  • N is speed of the rotor.
  • Q fan is the flow induced by a blower, arranged as per FIG. 8 , labelled 61 ;
  • Q 1 is the flow exiting tract 1 , labelled 2 on FIG. 8 ;
  • Q 2 is the flow exiting tract 2 , labelled 3 on FIG. 8 .
  • dP 1 ⁇ ( ⁇ P 1v +dP 1F ) (4a)
  • dP 2 ⁇ ( ⁇ P 2v +dP 2F ) (pb 4 b
  • ⁇ P 1v is the variable pressure drop created by the variable inlet area to tract 1 afforded by the splitter valve
  • ⁇ P 2v is the variable pressure drop created by the variable inlet area to tract 1 afforded by the splitter valve
  • dP 1F is the sum of the fixed pressure drops, which occur along tract 1 ;
  • dP 2F is the sum of the fixed pressure drops, which occur along tract 2 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Gas Burners (AREA)
  • Flow Control (AREA)
  • Multiple-Way Valves (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Lift Valve (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
US10/546,848 2003-03-11 2004-03-10 Splitter valve Abandoned US20070148605A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GBGB0305566.2A GB0305566D0 (en) 2003-03-11 2003-03-11 A splitter valve
GB0305566.2 2003-03-11
PCT/GB2004/000985 WO2004081362A2 (fr) 2003-03-11 2004-03-10 Soupape de separation

Publications (1)

Publication Number Publication Date
US20070148605A1 true US20070148605A1 (en) 2007-06-28

Family

ID=9954561

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/546,848 Abandoned US20070148605A1 (en) 2003-03-11 2004-03-10 Splitter valve

Country Status (12)

Country Link
US (1) US20070148605A1 (fr)
EP (1) EP1601896B1 (fr)
JP (1) JP2006525478A (fr)
KR (1) KR20050107616A (fr)
CN (1) CN100402902C (fr)
AT (1) ATE415599T1 (fr)
BR (1) BRPI0408190A (fr)
CA (1) CA2516707A1 (fr)
DE (1) DE602004017965D1 (fr)
GB (1) GB0305566D0 (fr)
RU (1) RU2005131431A (fr)
WO (1) WO2004081362A2 (fr)

Cited By (1)

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US20090230204A1 (en) * 2004-12-08 2009-09-17 Poehner Michael Fuel-powered vehicle heating

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GB0624945D0 (en) * 2006-12-14 2007-01-24 Microgen Energy Ltd A heating system
US8359868B2 (en) * 2008-09-11 2013-01-29 General Electric Company Low BTU fuel flow ratio duct burner for heating and heat recovery systems
JP2011058426A (ja) * 2009-09-10 2011-03-24 Ihi Corp 調整バルブ及び過給装置
DE102009053011C5 (de) 2009-11-16 2014-03-27 Viessmann Werke Gmbh & Co Kg Heizungsanlage und Verfahren zum Betrieb dieser Anlage

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US738115A (en) * 1903-02-24 1903-09-01 Chester E H Lincoln Locomotive-valve.
US743714A (en) * 1903-07-23 1903-11-10 George A Fox Valve for vapor-stoves.
US1143409A (en) * 1914-09-30 1915-06-15 George S Kyle Boiler-flue-cleaning apparatus.
US1425642A (en) * 1918-08-01 1922-08-15 Cleveland Pneumatic Tool Co Fitting for air lines and the like
US1932016A (en) * 1930-01-10 1933-10-24 Philip S Harper Air shutter for double gas range burners
US2447423A (en) * 1945-02-27 1948-08-17 George L Nies Rotary fuel distributing valve
US2641280A (en) * 1948-06-23 1953-06-09 Henry G Fleischhauer Automatic control valve for branch pipe lines
US2655929A (en) * 1950-01-11 1953-10-20 Barry Wehmiller Mach Co Apparatus for cleansing bottles
US3005467A (en) * 1958-01-24 1961-10-24 Bernard P Suchoza Multi-port valve
US3115926A (en) * 1958-07-15 1963-12-31 Gen Controls Co System and safety device for multiple furnaces
US3208719A (en) * 1962-08-28 1965-09-28 Drilling Tools Inc Rotary sleeve valves
US3443793A (en) * 1966-12-23 1969-05-13 Eldon E Hulsey Variable area orifice,rotary control valve
US3605811A (en) * 1968-11-14 1971-09-20 United Aircraft Corp Controlled impedance diverter valve
US3752439A (en) * 1971-11-15 1973-08-14 American Air Filter Co Damper arrangement
US3905193A (en) * 1974-02-25 1975-09-16 Gen Motors Corp Air diverter valve and controlling means therefor
US3946685A (en) * 1974-07-11 1976-03-30 The United States Of America As Represented By The Secretary Of The Navy Hover control valve for submarine hovering system
US4169354A (en) * 1976-12-27 1979-10-02 Cummins Engine Company, Inc. Exhaust gas and turbine compressor system
US4635567A (en) * 1984-01-25 1987-01-13 Babcock Power Limited Monitoring of burner operation
US4894368A (en) * 1986-07-23 1990-01-16 American Cyanamid Company Certain triphenylphosphinimide derivatives
US5184592A (en) * 1991-01-28 1993-02-09 Durbin Enoch J Method and apparatus for force or torque control of a combustion engine
US5242150A (en) * 1992-09-30 1993-09-07 The United States Of America As Represented By The Secretary Of The Navy Rotary hydraulic servo or throttle valve
US5343893A (en) * 1993-03-12 1994-09-06 Irvin Industries Canada Ltd. Distribution valve
US6056001A (en) * 1994-03-14 2000-05-02 Texaco Inc. Methods for positively assuring the equal distribution of liquid and vapor at piping junctions in two phase flow by intermittent flow interruption
US5517800A (en) * 1994-06-21 1996-05-21 Brenner; Joseph H. Conveyor with intermittent fluid supply
US5524822A (en) * 1995-03-13 1996-06-11 Simmons; Thomas R. Apparatus for producing variable-play fountain sprays
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US5931163A (en) * 1996-10-23 1999-08-03 Dragerwerk Ag Valve for setting the flow of a flow medium
US6250916B1 (en) * 1997-04-15 2001-06-26 American Air Liquide, Inc. Heat recovery apparatus and methods of use
US6158465A (en) * 1998-05-12 2000-12-12 Lambert; Steven Rotary valve assembly for engines and other applications
US6357463B1 (en) * 1998-08-07 2002-03-19 Resmed Limited Control member for a valve and method for determining fluid flow rate through a valve
US6185757B1 (en) * 1999-06-24 2001-02-13 Saratoga Spa & Bath Co., Inc. Manual control of water delivery through ports of tub, spa or shower
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WO2004081362A3 (fr) 2005-01-20
GB0305566D0 (en) 2003-04-16
JP2006525478A (ja) 2006-11-09
CA2516707A1 (fr) 2004-09-23
EP1601896B1 (fr) 2008-11-26
ATE415599T1 (de) 2008-12-15
DE602004017965D1 (de) 2009-01-08
RU2005131431A (ru) 2006-01-27
BRPI0408190A (pt) 2006-03-21
KR20050107616A (ko) 2005-11-14
CN1759266A (zh) 2006-04-12
WO2004081362A2 (fr) 2004-09-23
CN100402902C (zh) 2008-07-16
EP1601896A2 (fr) 2005-12-07

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