US3762639A - Gaseous fuel burner system - Google Patents

Gaseous fuel burner system Download PDF

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Publication number
US3762639A
US3762639A US00098246A US3762639DA US3762639A US 3762639 A US3762639 A US 3762639A US 00098246 A US00098246 A US 00098246A US 3762639D A US3762639D A US 3762639DA US 3762639 A US3762639 A US 3762639A
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Prior art keywords
flame
rate
burner
flow
gas
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US00098246A
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English (en)
Inventor
J Katchka
H Braucksiek
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Robertshaw Controls Co
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Robertshaw Controls Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/02—Systems for controlling combustion using devices responsive to thermal changes or to thermal expansion of a medium
    • F23N5/10—Systems for controlling combustion using devices responsive to thermal changes or to thermal expansion of a medium using thermocouples
    • F23N5/107—Systems for controlling combustion using devices responsive to thermal changes or to thermal expansion of a medium using thermocouples using mechanical means, e.g. safety valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • F23D14/04—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone induction type, e.g. Bunsen burner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/18—Groups of two or more valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/24—Valve details

Definitions

  • ABSTRACT A gaseous fuel burner system wherein a single burner is designed to operate at dual rates in accordance with the fuel flow supplied by a combination control device which is operated thermostatically and which includes the features of a manual on-off valving mechanism and a burner flame responsive safety valving mechanism. A single conduit between the control device and the burner supplies the fuel flow at both rates of flow to the burner that provides two flame patterns with each flame pattern impinging on the flame responsive element of the safety valving mechanism.
  • the present invention relates to a fuel burner system and, in particular, to such a system having burner apparatus supplied with fuel under the control of a thermostatic control device.
  • the fuel burning system includes burner apparatus having main outlet port means and auxiliary outlet port means, a source of fuel flow for the burner apparatus, a thermostatically operated control device controlling the rate of fuel flow to the burner apparatus, and a single flow path from the control device to the burner apparatus whereby the flame pattern issuing from the main outlet ports and the auxiliary outlet ports is established in accordance with the rate of fuel flow from the control device.
  • Another object of this invention is to construct a sin gle burner having a single inlet port and a plurality of outlet ports establishing a plurality of flame patterns.
  • This invention has another object in that a flame responsive element is carried by burner apparatus in such a manner that the various flame patterns of the burner apparatus always impinge on the flame responsive element.
  • Another object of this invention is to eliminate a separate bracket for mounting a pilot and/or thermocouple on burner apparatus.
  • the invention has another object in that only a single tubing or conduit supplies the burner apparatus with fuel and tne need for standby or pilot gas conduits is eliminated.
  • Still another object of this invention is to construct a thermostatic control device that has only a single outlet for feeding a flow of fuel to burner apparatus.
  • This invention has another object in that a fuel burning system is provided with a dual rate burner controlled by a thermostatically operated valve which varies the rate of flow to the burner apparatus.
  • the present invention has another object in that leakage past a thermostatically operated valve is not a critical factor since a dual rate burner is always operating at either its high or low flame pattern.
  • This invention has another er object in that the use of a dual rate burner minimizes the effect of throttling and/or graduating valves which control the rate of flow to the burner.
  • Another object of the present invention is to construct a thermostatically operated control device with a single outlet port for feeding burner apparatus at a plurality of rates of fuel flow.
  • a further object of this invention is to combine a manual on-off valving mechanism, a thermostatically operated valving mechanism and] a flame responsive safety shut-off valving mechanism into a unitary control device having a single inlet port and a single outlet port.
  • FIG. 1 is a schematic representation of a fuel burning system with parts broken away and parts in section embodying the present invention.
  • FIG. 2 is a partial top plan view of FIG. 1 showing the manual control knob in its off position.
  • FIG. 3 is a partial top plan view similar to FIG. 2 but showing the manual control knob in its pilot position.
  • FIG. 4 is partial top plan view :similar to FIG. 3 but showing the manual control knob in its on position.
  • FIG. 5 is a schematic representation similar to FIG. 1 but on a different scale with parts broken away and parts in section to illustrate the manual depression of the reset button with the manual control knob being positioned as shown in FIG. 3.
  • FIG. 6 is a schematic representationsimilar to FIG. 5 but correlated to the position of the manual control knob illustrated in FIG. 4.
  • FIG. 7 is a cross section of a modification of the burner apparatus of FIG. 1 and showing the burner apparatus operating under a low rate flame condition.
  • FIG. 8 is a cross section similar to FIG. 7 but on a smaller scale and showing the burner apparatus operating under a high rate flame condition.
  • FIG. 9 is a cross section through the burner ports taken along line 9-9 of FIG. 7.
  • FIG. I is a cross section of another modification of the burner apparatus of FIG. I. and showing such apparatus operating under a low rate flame condition.
  • FIG. II is a cross section similar to FIG. 10 but showing the burner apparatus operating under a high rate flame condition.
  • FIG. 12 is an isometric view of a detail of FIG. 10.
  • FIG. 13 is a top plan view of FIG. 12.
  • FIG. I4 is a cross section taken along line 14-14 of FIG. 13.
  • the present invention is embodied in a fuel burning system including fuel burner apparatus operatively connected to a control device which controls a flow of fuel to such apparatus.
  • the control device indicated generally at 10, has an inlet port 12 and an outlet port 14; the inlet port I2 is connected to any suitable fuel supply, such as gas. Adjacent the inlet port 12, the flow is controlled by an automatic safety mechanism, indicated generally at 16, which embodies structure that is conventionally known in the art.
  • the automatic safety device 16 is a flame responsive shut-off mechanism that includes a safety valve member 18 biased by a coil spring 20 towards a valve seat 22; the valve member 18 is held away from the seat 22 by an electromagnetic mechanism 24 which is electri cally connected to a thermocouple T by means of a thermocouple cable C.
  • the voltage generated by the thermocouple T is not sufficient to attract the armature to the magnet core of the electromangetic mechanism 24 but it is sufficient to hold such armature in its attracted position.
  • reset means to move the armature to its attracted position include a plunger 26 having one end extended through the valve seat 22 and its opposite end slidably extending through a wall of the casing and through a fixed sealing washer 28; a coil spring 30 surrounds the outer portion of the plunger 26 and is mounted in compression between a wall of the casing and a reset button 32 fixed to the outer end of the plunger 26.
  • the inner end of plunger 26 projects through a passage 34, one end of which is defined by the valve seat 22 and the opposite end of which is de fined by a valve seat 36.
  • a valve member 38 fixed to an intermediate portion of the plunger 26 cooperates with the valve seat 36 to control a fuel flow to a main passage 40.
  • Plug valve 42 Downstream of the valving elements 36 and 38, the main flow passage is intersected by a conical bore which defines a seat for a manually rotatable plug valve 42.
  • Plug valve 42 has a central axial bore, having inlet and outlet portions for registry with the main flow passage 40 to permit a main flow of fuel therethrough.
  • the rotatable plug valve 42 is retained in its conical valve seat by any suitable means such as a spring retaining washer 46 secured to the top wall of the control device casing.
  • a shaft 47 projecting from the valve plug 42 is keyed to a control knob 48 to permit manual rotation thereby.
  • the control knob 48 is provided with indicia representing the on, pilot and off positions of the plug valve 42.
  • a notched portion 50 in the periphery of the control knob 48 permits the reset button 32 to be depressed for ignition purposes. As is apparent from FIGS. 2 and 4, the reset button 32 cannot be depressed when the control knob 48 is in its off or on position.
  • the mechanism 52 Downstream of the plug valve 42, the main flow passage 40 is controlled by a thermostatically operated valve mechanism, indicated generally at 52.
  • the mechanism 52 includes an annular valve seat 54 which intersects the main flow passage 40, and a valve disc member 56 normally biased towards the valve seat 54 by a coil spring 58 mounted in compression between the valve member 56 and an internal wall surface of the control device casing.
  • the valve member 56 is attached to a valve stem 60 which slidably projects through a guide 62 formed in a rear wall of the control device casing; the free end of the valve stem 60 is engageable with actuating means 64.
  • the actuating means 64 includes a conventional snap mechanism in which clicker disc moves from an operative to an inoperative position through an overcenter position with a snap action in response to an applied force exerted by a lever assembly 66. Intermediate its ends the lever assembly 66 receives the end of a rod and tube type thermostat 68. The other end of the lever 66 is engaged by an adjusting shaft 70 which is rotated to a selected position by a temperature adjusting dial 72.
  • the above described structure of the thermostatically operated valving mechanism 52, the snap acting device 64, the lever assembly 66, the rod and tube thermostat 68, the adjusting shaft and temperature selection dial 70 and 72 are conventional structures well known in the art and for a more complete description of the structure and operation reference is made to U. S. Pat. No. 2,953,937.
  • the internal passage 34 communicates with an auxiliary flow passage 74.
  • the flow through the auxiliary passage 74 is at a smaller rate than that through the main passage and may be consistent with capacities usually associated with pilot burners. While the smaller flow passage 74 may completely bypass the manual plug valve 42, as an additional safety feature an exterior channel in the plug valve 42 may be utilized to intersect the auxiliary flow passage 74 and thus establish manual control of the auxiliary flow of fuel.
  • the auxiliary flow passage '74 Downstream of the manual plug valve 42, the auxiliary flow passage '74 is provided with an adjustable flow restrictor 75 to preset the flow rate through the auxiliary passage 74. Downstream of the adjustable flow restrictor '75, the auxiliary flow passage 74 intersects the main passageway at a position. adjacent the outlet I4 and downstream of the thermostatically operated valving mechanism 52.
  • any flow from the unitary control device 10 issues from the single outlet port 14 to a single conduit 76 extending between the outlet 14 and the burner apparatus, indicated generally at 78.
  • the burner apparatus 78 includes a cylindrical housing 80 having a single inlet port 82 and a plurality of circumferentially spaced outlet ports 84.
  • a second cylindrical housing 86 is generally concentrically arranged in the outer housing 80 and the hollow space between the two housings defines a generally cylindrical annular chamber 88 receiving a flow of gas from the inlet 82 which is located on the outer housing 80 adjacent the lower end thereof as viewed in FIGS. 5 and 6.
  • the two housings 80 and 86 have portions that are conical in cross-section constructed so that the annular chamber 88 is gradually reduced in cross-section toward its upper end.
  • FIG. 5 is in general alignment with one of the ports 84 to facilitate cleaning of the portDtl as by a wire inserted through such two ports.
  • the outer housing 80 has a top wall with a plurality of circumferentially spaced ports 92 and a centrally located annular collar 94 through which the thermocouple T is mounted.
  • a flow of gas from the single port 90 enters a mixing chamber 96 defined by the interior of housing 86; the spaced ports 92 also communicate with the mixing chamber 96 to define burner ports therefor.
  • An apertured plate 98 defines a common bottom wall for the two housings 80 and 86 as well as an air intake for the mixing chamber 96.
  • the top portion of outer housing 80 has an offset shoulder supporting the mounting collar 108 of a ring shaped flame spreader 110.
  • a plurality of circumferentially spaced apertures 112 in the flame spreader lit) encircle the mounting collar 108 for a purpose to be described more fully hereinafter; as is shown in FIG. 5, the outer periphery of the flame spreader 110 terminates in an upturned flange 114.
  • the apertures 1112 are formed by spokes connecting the mounting collar 1108 to the main portion of the spreader ll 10.
  • the apertures 84 are located in quadrants around the outer housing 80, and the above mentioned spokes are oriented so as to be positioned above the spaces formed between the quadrants whereby a low rate or standby flame does not impinge directly on the spokes.
  • a plurality of tabs I13 bent down from the spokes on the flame spreader llIO protect the low rate or standby flame from drafts; see FIG. 5.
  • a hollow cylindrical shield M6 is secured by any suitable means, such as welding, to the top surface of the flame spreader; the diameter of the shield 116 is of a larger dimension than the diameter defined by the ring of apertures 112 so as not to interfere with any flame extending through the apertures 11112.
  • a cover 1118 is spot welded on the top of the shield IE6 by means of a plurality of tabs I press fitted over the outer surface of the shield H6. The spaces between the downwardly directed tabs I20 define vents whereby the interior of the shield I16 is vented to the atmosphere.
  • FIGS. 1 and 2 represent the off position of the control device; i.e., in the off position of the control knob 48 (see FIG. 2), the inlet portion of the plug valve porting 44 is not in registry with the main flow passage 40 and the exterior channel of the plug valve 42 is not in registry with the auxiliary flow passage 74, so there is no flow through the control device 10.
  • the safety shutoff valve 18 is closed on the valve seat 22 so no flow can take effect until the ignition or reset mechanism is actuated.
  • control knob 48 is rotated counterclockwise from its position shown in FIG. 2 to its intermediate or pilot position 'as shown in FIG. 3.
  • the reset button 32 is in registry with the control knob slot 50, which permits the reset button 32 to be depressed.
  • plunger 26 and the valve 34 are moved downwardly to the positions illustrated in FIG. 5.
  • the safety shut-off valve 18 While the button 32 is depressed, the safety shut-off valve 18 is moved away from its valve seat 22 permitting a flow of fuel from the inlet 12 to the passage 34 and thence through the auxiliary flow passage 74 to the outlet I4 through the conduit 76, burner inlet 82, burner chamber 88 and burner outlet orifices 84 where it is ignited by any suitable means, such as a match. Since the flow of fuel through auxiliary flow passage 74 is at a low rate, the flame from burner orifices 84 has a pattern that resembles an umbrella so that such flame impinges directly thermocouple T. As soon as such flame sufflciently heats the thermocouple T, the electromagnetic mechanism 24 is energized whereupon the reset button 32 may be released and the safety shut-off valve 18 will be held in its open position.
  • the control knob 48 is then rotated counterclockwise from its pilot position in FIG. 3, to its on position in FIG. 4.
  • the internal passage 44 of the plug valve 42 is in registry with the main flow passage 40 which permits a flow of fuel having a path traced as follows: From the inlet 12 through the valve seat 22, the passage 34, the valve seat 36, the main flow passage 40, thence through the plug valve 42 and the thermostatically operated valving mechanism 52 which is in its open condition, the outlet 14, the conduit 76, the burner inlet 82, the inlet chamber 8%, the burner outlet orifices 84 whence the flame assumes a large annular shaped flame pattern adjacent the flange 114 of the flame spreader 110; at the same time, since the burner chamber 88 is supplied with the flow of fuel at a high rate, the pressure of such fuel causes fuel flow through the aperture 90 into the air-fuel mixing chamber 96 and thence through the burner orifices 92 where it formsa generally coneshaped flame pattern impinging on the thermo
  • umbrella shaped flame pattern of FIG. 5 serves to ignite the fuel from the ports 92 as well as the ports 84.
  • the snap mechanism 64 will return to its position as illustrated in FIG. ll whereby the thermostatically operated valving element 56 is closed on its valve seat 54.
  • the thermostatically operated valving mechanism 52 is again opened to provide a high rate of fuel flow to the burner 78.
  • the dual rate burner 78 will be thus cycled thermostatically between its high and low flames in accordance with the temperature demand as sensed by the thermostat 68. In the event the entire flame at the dual rate burner 78 should be extinguished for any reason,
  • thermocouple T will cool and the coil in the electromagnetic mechanism 24 will be deenergized causing the release of the safety shut-off valve 18 to its shut-off position.
  • the dual rate burner automatically changes between its high and low flame patterns in accordance with the high and low rates of fuel flow to the burner inlet 82. It should be noted that during both high and low flow rates, the flame impinges directly on the flame responsive element T; furthermore, contrary to con ventional burner apparatus, during low input conditions (FIG. the fuel flow exists from the main burner outlet orifices 84. Such an arrangement eliminates the necessity of a separate pilot burner or standby burner resulting in substantial cost reduction in manufacture and assembly.
  • the output of the burner apparatus 78 is approximately 45,000 BTU/HR during its high input rate and approximately 1,000 BTU/HR during its low input rate.
  • the burner apparatus may be design in accordance with the particular requirements of different types of installations.
  • the fuel is under relatively low pressure and will flow out the plurality of the burner outlet ports 84 and burn around the thermocouple T.
  • the flame pattern during the low flow rate is illustrated in FIG. 5 and the air intake openings into the chamber 96 permits a drawing in of air and out of the apertures 92 for good combustion characteristics.
  • the outlet pressure in the burner head is sufficient to force the fuel outward through the same burner ports 84 and along the underside of the flame spreader 110. Since the velocity of this fuel stream is too high to allow any gas to trickle upward from the burner outlet ports 84 and heat the thermocouple, the small aperture 90 in the wall of the inner housing 86 allows a small amount of fuel to flow upward along the side of the thermocouple T and burn upon exiting the apertures 92 to heat the thermocouple.
  • the pressure in the outlet manifold and burner head is very low (normally less than 0.1 inch w.c. above atmospheric pressure). At this low pressure the amount of gas exiting the small port 90 is insignificant compared to the amount exiting the larger and more numerous ports 84. This very small quantity of gas exiting at port 90 in the standby condition will be burned off in the standby flame.
  • the higher pressure causes a significant increase in the quantity of gas exiting port 90 so that it is now sufficient to heat the thermocouple to hold the electromagnetic safety valve open without the aid of the flame from ports 84.
  • control knob 48 is rotated clockwise from its position shown in FIG. 4 to its position shown in FIG. 2 whereby the manual plug valve 42 will cut off all fuel flow to the outlet 14.
  • the electromagnetic device 24 will be deenergized and the safety shut-off valve 18 will close on its valve seat 22 to provide 100% shut-off of any fuel flow from the inlet 12.
  • FIGS. 7-9 illustrate a second modification of the burner apparatus and only the structure which differs from that of FIGS. 5 and 6 is being described in detail. Accordingly, the same reference numerals are being utilized for those elements previously described in connection with FIGS. 1-6 and new reference numerals are being utilized for new elements.
  • the outer cylindrical housing has a plurality of circumferentially spaced outlet ports 284, each of which is set at an angle of approximately 30 from the vertical.
  • the inner housing 86 has an inwardly directed indentation formed by right angled wall portions with a single port 290 in the uppermost wall portion.
  • the indented wall portions are shown in FIG. 7 as having an L-shaped cross-section but any other suitable crosssectional configuration, such as conical, may be used; whatever cross-section is used, the port 290 is located in the uppermost part of the indentation so as to be angled upwardly and inwardly (about 30 from the vertical) to direct the fuel flow from the port 290 toward the outlet end of the mixing chamber 96.
  • the inner housing 86 has a top wall with plurality of circumferentially spaced ports 292 encircling an annular collar 294 through which the thermocouple T is received.
  • a flow of gases from the single port 290 enters the mixing chamber 96 defined by the interior of the housing 86; the spaced ports 292 define burner ports at the outlet end of the mixing chamber 96.
  • An annular collar 208 of a ring-shaped flame spreader 210 is secured to the housing 86 adjacent its upper end by being spot welded thereto.
  • the mounting collar 208 is off-set adjacent its lower end which cooperates with the upper end of the outer housing 80 to define wall portions of the outlet ports 284.
  • the mounting collar 208 has an annular portion disposed above the burner ports 292, which portion is provided with a plurality of circumferentially spaced apertures 212; as is apparent from FIG. 7, the lowrate flame pattern emanating from the burner ports 284 projects through the spaced apertures 212 to encircle the end of the thermocouple.
  • the flame spreader 210 Above the apertures 212, the flame spreader 210 has a flange dome-shaped configuration with its outer periphery terminating in an upturned flange 214.
  • a plurality of draft protection tabs 213 are carried by the flame spreader 210 by means of lugs 215 which project through suitable slots in the flame spreader and which are spot welded to the top surface of the flame spreader.
  • a condensation shield 216 in the form of an inverted cup-shaped member is attached to the top surface of the flame spreader as by spot welding the flange rim of the cup to the top surface of the flame spreader 210.
  • the condensation shield 216 defines a cover for the central portion of the flame spreader 210 and a plurality of vent openings 217 permits the interior of the shield 216 to be vented to the atmosphere.
  • FIG. 7 represents a low rate flame condition with the gas exiting from the burner outlet orifices 284.
  • the flame passes through the apertures 212 in the flame spreader and coalesces around the thermocouple in the normal manner.
  • FIG. 8 represents the flame pattern when the burner apparatus is being supplied with the gas flow at a high rate.
  • the high rate flame from the burner outlet orifices 284 spreads outwardly against the underside of the flame spreader 210.
  • the pressure of the gas causes flow through the aperture 290 into the mixing chamber 96 and thence through the bruner orifices 292 where it forms a generally cone-shaped flame pattern impinging on the thermocouple.
  • the other parts of the sequence of operation of the burner apparatus shown in FIGS. 7-9 are substantially the same as those described above in connection with the sequence of operation of FIGS. 1-7. and are not being repeated for the sake of brevity.
  • FIGS. 10-14 A third modification of the burner apparatus is illustrated in FIGS. 10-14 wherein only that structure and operation which differs from that of FIGS. 1-9, is being described below.
  • the indentation for the single port 290 in the housing 86 is disposed adjacent the thermocouple T; the burner port 290 in such indentation directs the gas flow upwardly toward the outlet of the mixing chamber 96.
  • a mounting collar 308 centrally located on a flame spreader 310 is attached to an offset shoulder adjacent the top portion of the outer housing 80 and is secured thereto as by being spot welded.
  • a plurality of openings or apertures 312 are formed in the flame spreader by spokes 31 it (see FIG. 13) connecting the mounting collar 308 to an outer ring member 309.
  • a tab 313 is bent down from each spoke 311 to protect the low rate or standby flame from drafts.
  • a plurality e.g., four of spaced struts 320 project downwardly and outwardly from the ring element 309 to support an integrally formed annulus 322 which is disposed in an inclined plane in such a manner as to present an annular surface on the top side of the flame spreader 310; as is illus trated in FIGS. 12 and 13, the annular surface is angularly disposed upwardly from a horizontal plane defined by the lowermost edges of the flame spreader assembly.
  • a plurality of fins 324 are bent downwardly from the outer periphery of the annular surface 322 and are utilized to dissipate heat from the flame spreader. y
  • FIGS. 10-11 illustrate burner apparatus where the high rate flame impinges on the top surface of the flame spreader whereas in the previous modifications the high rate flame impinged on the under surface of the flame spreader.
  • the particular design of the flame spreader shown in FIGS. 10-14 permits better control of the high rate flame characteristics and size due to the ability to control the angle of impingement of the gas hitting the angled surface 322.
  • the unitary multiple rate burner exhibits desired performance characteristics at two levels of operation, main flame and standby flame.
  • the significance of such performance becomes apparent when comparing the increase of the input rate of gas from the low rate maintaining the standby flame to the high rate maintaining the main flame.
  • pilot burners are conventionally identified according to their input rate, i.e., BTU per hour at a particular pressure generally measured in inches of a water column; the usual type of pilot burner would have an input rate of 750 to 1000 BTU per hour and such a pilot burner could be operated between two flame levels such as is shown in U. S. Pat. No. 3,405,999.
  • the increase in the BTU input rate is usually limited to a multiplier of approximately three.
  • a, conventional pilot burner could not be increased to operate at a BTU input rate necessary to sustain a main flame.
  • the present invention has the particular advantage of a single burner capable of operating at a standby flame level as well as at a main flame level.
  • the BTU input rate must be limited to a multiplier of at least five; i.e., the gas rate must be increased from its minimum flow associated with a standby flame having a 1000 BTU per hour input rate to a higher flow associated with a main flame having a 5000 BTU per hour input rate. It is this minimum multiplier of five which defines the minimum range of operation necessary to sustain both the standby flame and the main flame.
  • control valving means disposed between said burner apparatus and a source of gas, and being operative to deliver a gas flow at a high rate and a gas flow at a low rate
  • control valving means including a safety shut-off valving mechanism, flow restrictor means restricting the low rate gas flow, valve means movable between positions to change the gas flow rates, and a rod and tube thermostat assembly operatively connected to said valve means for moving the same between its positions in response to predetermined temperature conditions,
  • said burner apparatus including a housing having an inlet chamber, outlet port means from said inlet chamber and a single inlet port for said inlet chamber,
  • said burner housing having a second chamber, aperture means establishing communication between said inlet chamber and said second chamber, and outlet ports at an end of said second chamber whereby a flame is sustained at the outlet port means from said inlet chamber to define the high rate flame
  • said second chamber includes air intake means to define an air-gas mixing chamber upstream of the outlet ports of said second chamber.
  • a multiple rate burner having a single inlet adapted to be connected to a source of gas, ports in said burner being adapted to sustain a small compact standby flame when the gas is flowing in said inlet at a low rate and to project the gas to sustain a larger main flame when the gas in said inlet is increased to flow at a minimum rate at least 5 times greater than the low rate associated with the standby flame,
  • a gas flow control device operatively disposed between the gas source and said multiple rate burner
  • valve means in said control device movable between controlling positions to change the gas flow rates
  • a rod and tube thermostat assembly operatively connected to said valve means for moving the same between controlling positions in accordance with predetermined temperature conditions
  • restrictor means in said control device to restrict the low rate gas flow
  • a safety shut-off gas valve in said control device to control a gas flow from the gas source to said valve means and said restrictor means
  • a flame sensor positioned adjacent said multiple rate burner so that the standby flame is directed toward said flame sensor during low rate gas flow while a large portion of the main flame is projected away from said flame sensor with a small portion of the main flame being directed toward said flame sensor during high rate gas flow, and
  • a multiple rate gas burner and flame sensor combination comprising:
  • a multiple rate burner having a single inlet adapted to be connected to a source of gas, ports in said burner being adapted to sustain a small compact standby flame when the gas is flowing in said inlet at a low rate and to project the gas to sustain a larger main flame when the gas in said inlet is increased to flow at a minimum rate at least 5 times greater than the low rate associated with said standby flame,
  • wall means separates said first and second chambers, and aperture means in said wall means establishes communication between said first and second chambers.
  • control valving means disposed between said burner apparatus and a source of fuel, and being operative to deliver fuel flows at a high rate and low rate,
  • control valving means including a thermostatic control device movable between controlling positions to change the rate of fuel flow between its high and low rates, and a safety shut-off valving mechanism,
  • said burner apparatus including a burner housing having an inlet chamber, outlet port means from said inlet chamber and a single inlet port for said inlet chamber, single fuel conduit between said control valving means and the single inlet port for said inlet chamber whereby said burner housing produces a high rate flame or a low rate flame in accordance with the rate of fuel flow delivered by said thermostatic control device, said burner housing including a second chamber, ap-
  • erture means establishing communication between said inlet chamber and said second chamber, and outlet ports at an end of said second chamber whereby a flame is sustained at the outlet ports from said second chamber and at the outlet port means from said inlet chamber to define the high rate flame
  • flame responsive means positioned to respond to a flame from said burner housing and being operatively connected to said safety shut-off valving mechanism for maintaining the same in a flow permitting position as long as a flame exists at said burner housing.
  • the combination comprising burner apparatus operative at dual rates for alternately sustaining a high rate flame and a low rate flame,
  • control valving means disposed between said burner apparatus and a source of fuel, and being operative to deliver fuel flows at a high rate and low rate,
  • control valving means including a thermostatic control device movable between controlling positions to change the rate of fuel flow between its high and low rates, and a safety shut-off valving mechanism,
  • said burner apparatus including a burner housing having an inlet chamber, outlet port means from said inlet chamber and a single inlet port for said inlet chamber,
  • said burner housing including a second chamber, ap-
  • erture means establishing communication between said inlet chamber and said second chamber, and outlet ports at an end of said second chamber whereby a flame is sustained at the outlet ports from said second chamber and at the outlet port means from said inlet chamber to define the high rate flame
  • said flame responsive means including a thermocouple operatively carried by said burner housing so as to be disposed in the high rate flame and in the low rate flame.
  • the combination comprising gas flow control means adapted for connection to a gas source and being operative to deliver gas at a low rate of flow and at a high rate of flow,
  • a dual rate burner connected to receive gas from said gas flow control means and alternately sustaining a low rate flame and a high rate flame in accordance with the respective low and high rates of flow delivered by said gas flow control means
  • flame responsive means operatively associated with said gas flow control means for shutting off gas flow to said dual rate burner upon flame extinguishment thereat,
  • said flame responsive means inciuding a flame sensor carried by said dual rate burner so as to be impinged upon by a major portion of said low rate flame
  • outlet orifice means on said dual rate burner directing a major portion of said high rate flame away from said flame sensor and a minor portion of said high rate flame impinges on said flame sensor.
  • gas flow control means includes a. thermostatically operated valve device automatically changing the rate of gas flow between the low and high rates of flow.
  • a dual rate burner comprising a burner housing having first and second outlet orifice means, i
  • aperture means in said wall means establishing communication between said first and second cham bers
  • said aperture means defining a cross-sectional flow area substantially smaller than a cross-sectional flow area defined by said first. outlet orifice means whereby a low fuel pressure in said first chamber causes a fuel flow through said first outlet orifice means and whereby a high fuel pressure in said first chamber causes a fuel flow through said first outlet orifice means and through said aperture means and said second outlet orifice means, and
  • said burner housing having flame responsive means adapted to assure a fuel flow to said single inlet as long as a flame exists at said burner housing.
  • said flame responsive means includes an element being disposed in a flame issuing from said second outlet orifice means during a high flow rate of fuel and being disposed in a flame issuing from 'a low flow rate of fuel.
  • thermocouple 16. The invention as recited in claim 15 wherein the element of said flame responsive means comprises a thermocouple.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Control Of Combustion (AREA)
  • Gas Burners (AREA)
US00098246A 1970-12-15 1970-12-15 Gaseous fuel burner system Expired - Lifetime US3762639A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US9824670A 1970-12-15 1970-12-15

Publications (1)

Publication Number Publication Date
US3762639A true US3762639A (en) 1973-10-02

Family

ID=22268325

Family Applications (1)

Application Number Title Priority Date Filing Date
US00098246A Expired - Lifetime US3762639A (en) 1970-12-15 1970-12-15 Gaseous fuel burner system

Country Status (13)

Country Link
US (1) US3762639A (fr)
AU (3) AU451000B2 (fr)
BE (1) BE776669A (fr)
CA (1) CA959751A (fr)
DE (1) DE2162009A1 (fr)
DK (1) DK131954C (fr)
ES (1) ES397945A1 (fr)
FR (1) FR2118593A5 (fr)
GB (2) GB1380568A (fr)
IT (1) IT943931B (fr)
NL (1) NL7117100A (fr)
NO (1) NO131362C (fr)
SE (2) SE7410581L (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3846064A (en) * 1973-09-28 1974-11-05 Robertshaw Controls Co Flame spreader with stress relief for a burner
US3870458A (en) * 1973-09-26 1975-03-11 Robertshaw Controls Co Plural rate burner with deflection of high rate flame against flame sensing element
US4108370A (en) * 1977-02-23 1978-08-22 Robertshaw Controls Company Fuel control system having by-pass means and parts therefor and the like
US5275555A (en) * 1992-08-14 1994-01-04 Goodridge Mark S Holding and covering a gas pilot
US5281130A (en) * 1986-07-11 1994-01-25 Lebaigue Research Limited Domestic gas fires
US6322352B1 (en) * 1998-06-10 2001-11-27 Isphording Germany Gmbh Gas burner system
US20060138372A1 (en) * 2002-09-25 2006-06-29 Bsh Bosch Und Siemens Hausgerate Gmbh Gas tap comprising an electromagnetic safety valve and magnetic insert for an electromagnetic safety valve
US20090206168A1 (en) * 2008-02-11 2009-08-20 Alex Schwartzman Thermostatic control device
US20100252122A1 (en) * 2009-03-24 2010-10-07 Robertshaw Controls Company Unregulated Integrated Function Gas Valve for a Water Heater
US8931707B2 (en) 2008-02-11 2015-01-13 Marine Canada Acquisition Inc. Appliance with thermostatic controls
US9746176B2 (en) 2014-06-04 2017-08-29 Lochinvar, Llc Modulating burner with venturi damper
US20170350086A1 (en) * 2016-06-06 2017-12-07 Daniel Jensen Ground Thawing Device

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2915725A1 (de) * 1979-04-19 1980-10-30 Gok Gmbh & Co Kg Zuendbrennersicherung
GB8431029D0 (en) * 1984-12-07 1985-01-16 Kinder J M Combustion assemblies

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1881637A (en) * 1928-10-29 1932-10-11 Honeywell Regulator Co Fuel regulating device for gas ovens
US1917345A (en) * 1931-05-19 1933-07-11 Vedoe Peterson Co Oven regulator
US3559884A (en) * 1969-02-19 1971-02-02 Emerson Electric Co Gas valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1881637A (en) * 1928-10-29 1932-10-11 Honeywell Regulator Co Fuel regulating device for gas ovens
US1917345A (en) * 1931-05-19 1933-07-11 Vedoe Peterson Co Oven regulator
US3559884A (en) * 1969-02-19 1971-02-02 Emerson Electric Co Gas valve

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3870458A (en) * 1973-09-26 1975-03-11 Robertshaw Controls Co Plural rate burner with deflection of high rate flame against flame sensing element
US3846064A (en) * 1973-09-28 1974-11-05 Robertshaw Controls Co Flame spreader with stress relief for a burner
US4108370A (en) * 1977-02-23 1978-08-22 Robertshaw Controls Company Fuel control system having by-pass means and parts therefor and the like
US5281130A (en) * 1986-07-11 1994-01-25 Lebaigue Research Limited Domestic gas fires
US5275555A (en) * 1992-08-14 1994-01-04 Goodridge Mark S Holding and covering a gas pilot
AU751061B2 (en) * 1998-06-10 2002-08-08 Isphording Germany Gmbh Safety device for a gas burner
US6322352B1 (en) * 1998-06-10 2001-11-27 Isphording Germany Gmbh Gas burner system
US9140451B2 (en) * 2002-09-25 2015-09-22 Bsh Hausgeraete Gmbh Gas tap comprising an electromagnetic safety valve and magnetic insert for an electromagnetic safety valve
US20060138372A1 (en) * 2002-09-25 2006-06-29 Bsh Bosch Und Siemens Hausgerate Gmbh Gas tap comprising an electromagnetic safety valve and magnetic insert for an electromagnetic safety valve
US20090206168A1 (en) * 2008-02-11 2009-08-20 Alex Schwartzman Thermostatic control device
US20090208888A1 (en) * 2008-02-11 2009-08-20 Alex Schwartzman Method for controlling the temperature of an appliance
US8141788B2 (en) 2008-02-11 2012-03-27 Marine Canada Acquisition Inc. Thermostatic control device
US8141789B2 (en) 2008-02-11 2012-03-27 Marine Canada Acquisition Inc. Method for controlling the temperature of an appliance
US8931707B2 (en) 2008-02-11 2015-01-13 Marine Canada Acquisition Inc. Appliance with thermostatic controls
US20100252122A1 (en) * 2009-03-24 2010-10-07 Robertshaw Controls Company Unregulated Integrated Function Gas Valve for a Water Heater
US9423153B2 (en) * 2009-03-24 2016-08-23 Robertshaw Controls Company Unregulated integrated function gas valve for a water heater
US9746176B2 (en) 2014-06-04 2017-08-29 Lochinvar, Llc Modulating burner with venturi damper
US10161627B2 (en) 2014-06-04 2018-12-25 Lochinvar, Llc Modulating burner with venturi damper
US20170350086A1 (en) * 2016-06-06 2017-12-07 Daniel Jensen Ground Thawing Device
US10633816B2 (en) * 2016-06-06 2020-04-28 Daniel Jensen Ground thawing device

Also Published As

Publication number Publication date
AU3685671A (en) 1973-06-21
DE2162009A1 (de) 1972-07-13
BE776669A (fr) 1972-04-04
ES397945A1 (es) 1974-07-01
DK131954C (da) 1976-02-23
AU6967374A (en) 1974-08-15
NO131362C (fr) 1975-05-14
GB1380567A (en) 1975-01-15
AU6967474A (en) 1974-08-15
DK131954B (da) 1975-09-29
NL7117100A (fr) 1972-06-19
SE7410582L (fr) 1974-08-20
IT943931B (it) 1973-04-10
GB1380568A (en) 1975-01-15
AU469371B2 (en) 1974-08-15
AU451000B2 (en) 1974-07-25
SE7410581L (fr) 1974-08-20
NO131362B (fr) 1975-02-03
CA959751A (en) 1974-12-24
FR2118593A5 (fr) 1972-07-28

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Effective date: 19900730