CA1240609A - Pulsing combustion - Google Patents
Pulsing combustionInfo
- Publication number
- CA1240609A CA1240609A CA000494113A CA494113A CA1240609A CA 1240609 A CA1240609 A CA 1240609A CA 000494113 A CA000494113 A CA 000494113A CA 494113 A CA494113 A CA 494113A CA 1240609 A CA1240609 A CA 1240609A
- Authority
- CA
- Canada
- Prior art keywords
- combustion
- chamber
- combustible mixture
- pulsing
- pressurized
- 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.)
- Expired
Links
Landscapes
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
- Portable Nailing Machines And Staplers (AREA)
Abstract
Abstract of the Disclosure A pulsing combustion device including a combustion chamber having an inlet for combustible mixture and an unvavled outlet open to the atmosphere for combustion gases, a floating valve member mounted in reciprocation relation in the wall of the combustion chamber, the reciprocation of the floating valve closing and opening communication through ports between the supply of combustible mixture and the combustion chamber.
The pulsing combustion device may be used as an air heater by providing an exhaust manifold passing the combustion gases through a closed heat exchanger over which treatment air is passed through an air treatment duct. The pulsing combustion device may be provided with a pressurized combustion air flow regulator providing higher pressure combustion air to a lower pressure combustible mixing chamber to which fuel gas is added.
The pulsing combustion device may be used as an air heater by providing an exhaust manifold passing the combustion gases through a closed heat exchanger over which treatment air is passed through an air treatment duct. The pulsing combustion device may be provided with a pressurized combustion air flow regulator providing higher pressure combustion air to a lower pressure combustible mixing chamber to which fuel gas is added.
Description
124q;~6Q~t BACKGROUND OF THE INVENTION
Field of the Invention The invention disclosed herein pertains generally to improvements in combustors or burners and more particularly relates to gas and fuel mixing for such combustors and hot air furnaces having an improved pulsing combustor.
Descri tion of the Prior Art p A vast number of burner arrangements are known for a virtually limitless number of specific uses. Typically, combustion takes place in an open combustion zone with the combustion gases then passed through a heat exchanger to heat a fluid such as air or water. Conventional combustion devices are unsatisfactory since oftentimes combustion is incomplete producing various pollutants and furthermore because the efficiency obtainable from such combustion devices is relatively poor.
The known burners or combustors used for heating liquids such as water are generally quite massive and consume large amounts of fuel (usually oil or gas). Most presently used burners rely on a continuous flow of the fuel, thus perhaps wasting some of the fuel due to incomplete combustion.
Combustion devices having an intermittent flow of fuel are known, for example, as in a conventional ARK-105-Can -2-~Z4(~6~)9 piston engine or in a pulsing combustor. Perhaps one of the first pulsing combustors was the pulse-jet engine utilized in the German V-l rocket or buzz bomb which is described on pages 2 and 3 of the book Rocke' Propulsion Elements by George P.
Sutton (John Wiley & Sons, 1949.).
Another known pulsing combustor is disclosed in United States Patent ~o. 2,857,332 to Ténney et al and is utilized in a machine for producing dispersions of liquid in air or other gases. In the Tenney et al device, a fuel-air mixture is supplied through an inlet portion of a combustor with combustion air passing sequentially through a throat of an air inlet passage and over a sloping step in a fuel injection tube. Fuel is discharged as a spray and is metered in proportion to the incoming air. The fuel-air mixture is forced through a plurality of diverging passages into a combustion zone of the combustor. The passages each have a port at the combustion chamber end of each passage. Each port is covered by a finger-like portion of a metal valve preferably made of a flexible steel. The finger-like portions of the valve are sufficiently flexible to be deflected against a backing plate by the inrush of the air-fuel mixture when the burner is operating.
ARK-105-Can -3-12g~6~
Initially, the starting air-fuel mixture is introduced into the burner chamber and is ignited by a spark plug. The resulting explosion causes the finger-like portions of the valve to close against the intake ports leaving an exhaust tube as the only path of exit for the combustion zone gases. The mass of gases in the exhaust tube is then driven forceably at extremely high velocity outwardly of an open end of the exhaust tube by the expanding combustion gases produced by the explosion in the combustion zone. The rush of gases out of the exhaust tube causes a low pressure area in the combustion zone. The low pressure area induces a fresh charge of combustible air-fuel mixture through the ports and into the combustion zone. Fuel is fed to the combustion zone through a plurality of fuel ports and the air used is atmospheric air. The burner depends on the low pressure zone existing in the combustion chamber after exhaustion of the hot combustion products to induce a further flow of the air-fuel mixture into the combustion zone.
A resonant intermittent combustion heater system using a pulsing combustion arrangement similar to the pulsing combustor disclosed in United States Pat~nt No. 2,857,332 is also known in , .
ARK-105-Can -4-~z~U6~9 the prior art and is disclosed in United States Patent No. 2,715,390, issued to Tenney et al.
A different pulsing combustion arrangement having a burner is disclosed in United States Patent No. 2,959,214 issued to Durr et al.
During ignition of the burner in the Durr et al device, a spark plug is activated along with a pump to supply air through a conduit under pressure to a tightly closed fuel tank. The air streaming through the tube vaporizes an amount of fuel at a diaphragm and this mixture flows into a mixing tube. The mixing tube mixes the fuel-air mixture with a further supply of air and the resulting mixture then is ignited by the spark. The burning does not provide a complete combustion of the fuel-air mixture and therefore unburned combustible components circulate within a cyclone-form combustion tube before reaching an exhaust tube.
As the burner continues to operate, a part of the cyclone-form combustion tube becomes hot and the unburned combustible components which enter the cyclone combustion tube are ignited. An explosion takes place within the combustion tube and the explosion provides a sudden blast of exhaust gases through the exhaust tube. These explosions follow each other uniformly and a resonant intermittent ARK-105-Can -5-lZ4~61~9 combustion takes place providing an automatic suction of fuel and air.
A spraying device having a different pulsing combustor with an oscillating burner resonator fed by a carburetor is disclosed in United States Patent No. 3,758,036 issued to Bauder et al. A blower is set into operation so that a fuel whirling chamber is pressurized via a starting air pipe and fuel is supplied to the fuel whirling chamber by a tank through a nozzle. The fuel-air mixture is then supplied through a tube to the burner and an ignition device in the burner ignites the fuel-air mixture. During subsequent operation, air is drawn into a valve chamber through a suction valve provided on a front side of the carburetor and is mixed with fuel from the fuel nozzle. On a side wall of the carburetor is a lid which carries an adjusting device for the oscillating burner resonator. The adjusting device includes an air evacuating valve associated with the fuel whirling chamber and a pressure space enclosed by the lid.
A diaphragm is sealed at its edges to an outside of the lid with a middle area of the diaphragm being connected to a valve closing part of the air evacuating valve.
The Bauder et al patent also discloses a portable spraying apparatus having a hand held gun.
ARK-105-Can -6-lZ4~16~-9 The burner in the ~auder et al patent is cooled by air in a surrounding cooling cover which obtains the air from a blower through a pipe. An oscillating tube, also surrounded by the cooling cover, conducts the hot combustion products away from the burner toward a front section of the cooling cover. A liquid agent is introduced oy the nozzle into the oscillating pipe so that the hot combustion products of the burner will turn the liquid into a steam or mist which will be expelled through a widened end section of the gun.
A known recirculating burner is disclosed in Patent No. 3,366,154 issued to Walsh et al which shows a compact portable burner useful in flame cultivation of crops. Some of the products of combustion are recirculated from a discharge end of the burner to a position between the discharge end and a venturi throat and just forward of an oil nozzle for the purpose of providing a clean flame and more efficient burning of the fuel. A
recirculation jacket surrounds a central portion of the burner and has a top wall, a bottom wall and a pair of similar symmetrically disposed side walls in a predetermined outwardly spaced relation to top, bottom and side walls of the burner. The front ends of the jacket wall and the burner wall are joined together by a front shoulder.
ARK-105-Can -7-~Z~16~`~9 Similarly, the rear end of the jacket wall and the burner wall are joined together by a rear shoulder.
A plurality of openings is provided in the burner walls adjacent and slightly rearwardly of the front shoulder and a similar plurality of openings is provided adjacent and slightly forwardly of the rear shoulder. Hot combustion gas enters the plurality of front shoulder openings and is récirculated to the rear and reenters the burner by venturi action at the rear shoulder openings to provide a more efficient burning of the fuel as well as improved vaporization of the fuel which is preferably fuel oil.
Other patents and publications which disclose combustor arrangements of interest to the present invention include: U.S. Patent No.
Field of the Invention The invention disclosed herein pertains generally to improvements in combustors or burners and more particularly relates to gas and fuel mixing for such combustors and hot air furnaces having an improved pulsing combustor.
Descri tion of the Prior Art p A vast number of burner arrangements are known for a virtually limitless number of specific uses. Typically, combustion takes place in an open combustion zone with the combustion gases then passed through a heat exchanger to heat a fluid such as air or water. Conventional combustion devices are unsatisfactory since oftentimes combustion is incomplete producing various pollutants and furthermore because the efficiency obtainable from such combustion devices is relatively poor.
The known burners or combustors used for heating liquids such as water are generally quite massive and consume large amounts of fuel (usually oil or gas). Most presently used burners rely on a continuous flow of the fuel, thus perhaps wasting some of the fuel due to incomplete combustion.
Combustion devices having an intermittent flow of fuel are known, for example, as in a conventional ARK-105-Can -2-~Z4(~6~)9 piston engine or in a pulsing combustor. Perhaps one of the first pulsing combustors was the pulse-jet engine utilized in the German V-l rocket or buzz bomb which is described on pages 2 and 3 of the book Rocke' Propulsion Elements by George P.
Sutton (John Wiley & Sons, 1949.).
Another known pulsing combustor is disclosed in United States Patent ~o. 2,857,332 to Ténney et al and is utilized in a machine for producing dispersions of liquid in air or other gases. In the Tenney et al device, a fuel-air mixture is supplied through an inlet portion of a combustor with combustion air passing sequentially through a throat of an air inlet passage and over a sloping step in a fuel injection tube. Fuel is discharged as a spray and is metered in proportion to the incoming air. The fuel-air mixture is forced through a plurality of diverging passages into a combustion zone of the combustor. The passages each have a port at the combustion chamber end of each passage. Each port is covered by a finger-like portion of a metal valve preferably made of a flexible steel. The finger-like portions of the valve are sufficiently flexible to be deflected against a backing plate by the inrush of the air-fuel mixture when the burner is operating.
ARK-105-Can -3-12g~6~
Initially, the starting air-fuel mixture is introduced into the burner chamber and is ignited by a spark plug. The resulting explosion causes the finger-like portions of the valve to close against the intake ports leaving an exhaust tube as the only path of exit for the combustion zone gases. The mass of gases in the exhaust tube is then driven forceably at extremely high velocity outwardly of an open end of the exhaust tube by the expanding combustion gases produced by the explosion in the combustion zone. The rush of gases out of the exhaust tube causes a low pressure area in the combustion zone. The low pressure area induces a fresh charge of combustible air-fuel mixture through the ports and into the combustion zone. Fuel is fed to the combustion zone through a plurality of fuel ports and the air used is atmospheric air. The burner depends on the low pressure zone existing in the combustion chamber after exhaustion of the hot combustion products to induce a further flow of the air-fuel mixture into the combustion zone.
A resonant intermittent combustion heater system using a pulsing combustion arrangement similar to the pulsing combustor disclosed in United States Pat~nt No. 2,857,332 is also known in , .
ARK-105-Can -4-~z~U6~9 the prior art and is disclosed in United States Patent No. 2,715,390, issued to Tenney et al.
A different pulsing combustion arrangement having a burner is disclosed in United States Patent No. 2,959,214 issued to Durr et al.
During ignition of the burner in the Durr et al device, a spark plug is activated along with a pump to supply air through a conduit under pressure to a tightly closed fuel tank. The air streaming through the tube vaporizes an amount of fuel at a diaphragm and this mixture flows into a mixing tube. The mixing tube mixes the fuel-air mixture with a further supply of air and the resulting mixture then is ignited by the spark. The burning does not provide a complete combustion of the fuel-air mixture and therefore unburned combustible components circulate within a cyclone-form combustion tube before reaching an exhaust tube.
As the burner continues to operate, a part of the cyclone-form combustion tube becomes hot and the unburned combustible components which enter the cyclone combustion tube are ignited. An explosion takes place within the combustion tube and the explosion provides a sudden blast of exhaust gases through the exhaust tube. These explosions follow each other uniformly and a resonant intermittent ARK-105-Can -5-lZ4~61~9 combustion takes place providing an automatic suction of fuel and air.
A spraying device having a different pulsing combustor with an oscillating burner resonator fed by a carburetor is disclosed in United States Patent No. 3,758,036 issued to Bauder et al. A blower is set into operation so that a fuel whirling chamber is pressurized via a starting air pipe and fuel is supplied to the fuel whirling chamber by a tank through a nozzle. The fuel-air mixture is then supplied through a tube to the burner and an ignition device in the burner ignites the fuel-air mixture. During subsequent operation, air is drawn into a valve chamber through a suction valve provided on a front side of the carburetor and is mixed with fuel from the fuel nozzle. On a side wall of the carburetor is a lid which carries an adjusting device for the oscillating burner resonator. The adjusting device includes an air evacuating valve associated with the fuel whirling chamber and a pressure space enclosed by the lid.
A diaphragm is sealed at its edges to an outside of the lid with a middle area of the diaphragm being connected to a valve closing part of the air evacuating valve.
The Bauder et al patent also discloses a portable spraying apparatus having a hand held gun.
ARK-105-Can -6-lZ4~16~-9 The burner in the ~auder et al patent is cooled by air in a surrounding cooling cover which obtains the air from a blower through a pipe. An oscillating tube, also surrounded by the cooling cover, conducts the hot combustion products away from the burner toward a front section of the cooling cover. A liquid agent is introduced oy the nozzle into the oscillating pipe so that the hot combustion products of the burner will turn the liquid into a steam or mist which will be expelled through a widened end section of the gun.
A known recirculating burner is disclosed in Patent No. 3,366,154 issued to Walsh et al which shows a compact portable burner useful in flame cultivation of crops. Some of the products of combustion are recirculated from a discharge end of the burner to a position between the discharge end and a venturi throat and just forward of an oil nozzle for the purpose of providing a clean flame and more efficient burning of the fuel. A
recirculation jacket surrounds a central portion of the burner and has a top wall, a bottom wall and a pair of similar symmetrically disposed side walls in a predetermined outwardly spaced relation to top, bottom and side walls of the burner. The front ends of the jacket wall and the burner wall are joined together by a front shoulder.
ARK-105-Can -7-~Z~16~`~9 Similarly, the rear end of the jacket wall and the burner wall are joined together by a rear shoulder.
A plurality of openings is provided in the burner walls adjacent and slightly rearwardly of the front shoulder and a similar plurality of openings is provided adjacent and slightly forwardly of the rear shoulder. Hot combustion gas enters the plurality of front shoulder openings and is récirculated to the rear and reenters the burner by venturi action at the rear shoulder openings to provide a more efficient burning of the fuel as well as improved vaporization of the fuel which is preferably fuel oil.
Other patents and publications which disclose combustor arrangements of interest to the present invention include: U.S. Patent No.
2,634,804 of Erickson; U.S. Patent No. 2,589,566 of Neth et al; U.S. Patent No. 2,077,323 of Hendrix;
U.S. Patent No. 2,411,675 of Alexander; U.S. Patent No. 1,719,015 of Lewis; U.S. Patent No. 1,885,040 of Arnold; U.S. Patent No. 4,259,928 of Huber;
British Patent No. 166,455; French Patent No.
1,366,565; and, "Pulsating Combustion: An Old Idea May Give Tomorrow's Boiler's a New Lookn, Power pp. 88-91, August 1954.
Accordingly, the need exists for an lmproved burner which provides an efficient and A~K-105-Can -8-lZ4~63D~
economical use of fuel. Such an improved burner would have particular utility in steam generation devices and in home heating equipment especially where a fluid is to be heated by the combustion.
SUMMARY OF THE INVENTION
It is therefore an object of the present invention to provide an improved co~bustion device having a floating valve member mounted in the wall of a combustion chamber of the combustion device which reciprocates in a floating manner to regulate a supply of a combustible mixture to the combustion chamber.
It is therefore another object of the present invention to provide a pulsing combustion device which provides an efficient and economical use of fuel and which overcomes the disadvantages of known combustion devices.
Yet another object of the present invention is to provide a heating device having a pulsing combustion device wherein the co~bustion gases heat either a liquid or a gas, which liquid or gas cools the shell of the burner.
The combustor of the present invention is especially useful in any type of a fluid heating system, such as a home heating or hot water heating system. Present home heating systems are often large and expensive as well as being ARK-105-Can -9-124106{~9 energy-inefficient because much of the heating value of the fuel is wasted. It would be advantageous to provide a building heating system in which a simple and compact pulsing combustion device is used to heat the fluid medium by which the home is heated. This would provide a more effi~ient use of heating fuels, since in many of today's home heating systems a large percentage of the heat generated is lost through the chimney.
The need therefore remains for a building heating system which efficiently utilizes heat energy contained in the combustion gases produced by the burner.
It is therefore still another object of the present invention to provide an efficient and low cost heating system for a building wherein the fluid medium which heats the home is itself heated by a compact pulsing combustion device.
It is therefore yet still another object of the present invention to provide a heating system in which the spent gases of combustion are utilized to improve the efficiency of the system.
A pulsing combustion device according to the present invention comprises a combustion chamber with an inlet for a combustible mixture and an unvalved outlet to the atmosphere for combustion gases. A pressurized combustlble mixture is ARR-105-Can -10-lZ4~)609 supplied to a floating valve with through ports providing controlled communication between the supply of the combustible mixture and the combustion chamber. Reciprocation of the floating valve member increases and decreases the flow of combustible mixture into the combustion chamber.
The combustible mixture is ignited and burned in the combustion chamber. The floating valve is reciprocated in its mounting in the wall of the combustion chamber by the pressure of the pressurized combustible mixture and the pressure of the combustion gases to regulate the flow of the combustible mixture into the combustion chamber.
My earlier filed Canadian Patent Application, Serial No. 392,910, filed December 22, 1981, teaches and claims specific embodiments of my pulsing combustion device and process and specific embodiments of a fluid heating device incorporating my pulsing combustion device. My Canadian Patent Application, Serial No. 479,890, filed April 24, 1985, teaches and claims further improvements to my pulsing combustion device and its use in water heating applications. This application teaches new methods for feeding combustible mixtures to my pulsing combustion device and its use in hot air heating applications.
ARK-105-Can -11-124(~6~9 Heating devices for a wide variety of purposes according to the present invention may use a pulsing combustion device as described having a flow of gas encircling the combustion chamber so that the gas is heated. 8eat exchange may be enhanced by placement of baffles in and/or downstream of the combustion zone and combustion products may be passed through a wide variety of coil and/or finned heat exchangers. Likewise, the gas to be heated may be passed through coil and/or finned heat exchangers. A particularly suitable combustible mixture supply means and system is described.
BRIEF DESCRIPTION OF THE DRAWINGS
Preferred embodiments of a pulsing combustion device and preferred embodiments of heating devices including the pulsing combustion device, according to the present invention are described with reference to the accompanying drawings wherein like members bear like reference numerals and wherein:
Fig. 1 is a cross-sectional view of one embodiment of a pulsing combustion device according the present invention;
' Fig. 2 is a view through the line 2-2 of Fig. 1;
ARK-105-Can -12-1~4~6V9 Fig. 3 is a perspective view of a hot air heater utilizing a pulsing combustion device according to this invention;
Fig. 4 is a perspective view of another embodiment of a hot air heater utilizing a pulsing combustion device according to this invention;
Fig. 5 is a sectional view of the combustible gas mixing and feeding portion of the apparatus; and - Fig. 6 is a sectional side view of , another embodiment of the floating valve of a pulsing combustion device of this invention.
; DESCRIPTION OF THE PREFERRED EMBODIMENTS
With reference to Fig. 1, one embodiment , - of a pulsing combustion device 10, includes an elongate combustion chamber shell or burner shell 14 which defines a combustion chamber 15. The combustion chamber shell 14 is generally tubular with a length that is considerably greater than its width. The combustion chamber shell is preferably circular in cross section, but may of course be square, rectangular or of any other suitable configuration. The combustion chamber 15 is closed except for the outlet for combustion gases and the I inlet for admitting the combustible mixture. The j combustible mixture may be supplied by a line 40 through a ball valve chamber 34 by way of a ARK-105-Can -13-1%~6~9 reciprocating floating valve 20. The ball valve chamber 34 is provided within an end cap 17 disposed at an inlet end of the combustor shell 14.
The end cap 17 together with the combustor shell 14 define a path of reciprocation for the floating valve 20. After combustion, the combustion gases exit through an open exhaust tube 50 disposed at an exhaust end 18 of the combustor shell 14.
If desired, the ball valve chamber may be deleted or replaced by a suitable conventional check valve. The ball valve chamber 34 or the check valve 507 may serve to prevent a flashback of the combustible mixture. Any suitable flame arrestor may be used.
As shown in Fig. 1, ball valve chamber 34 and unvalved exhaust tube 50 have diameters which are considerably smaller than the cross-sectional diameter of the burner shell 14. Thus, the burner shell 14 is substantially closed on each end and has two restricted passageways: the ball valve chamber 34 at the inlet to the combustion chamber 15 and the exhaust tube 50 disposed at the exhaust end 18 of the burner shell 14. The burner shell 14, the ball valve chamber 34 and the exhaust tube 50 are all preferably made of a temperature resistant steel or other material which can tolerate the high temperatures generated in the ARK-105-Can -14-lZ~ 9 combustion chamber while the combustible mixture is burning~
A flange 76 is secured, for example, by welding, to the end cap 17 to facilitate the asse~bly of the end cap 17 with the shell 14. A
plurality of bolts 74 extend through openings in the flange and are threadably received by corresponding nuts 72 which are secured, as by welding, to the shell 14. The end cap 17 is thereby detachably secured to the shell 14 by the nuts 72 and the bolts 74. A sealing gasket 78, preferably of neoprene or another gasket material suitable for high temperature use may be preferably disposed between the end cap 17 and a lower end wall of the burner shell 14.
The floating poppet valve 20 disposed for reciprocal movement in the burner or combustor shell 14 may be generally mushroom-shaped with an open interior or bore 26, as shown in Figs. 1 and 2. The floating valve 20 is of integral construction and includes a base 27 having a first diameter and a tube 23 having a reduced diameter with the bore extending through the tube and through a portion of the base. A small clearance is provided between a side wall 25 of the base of the floating valve and a side wall 19 of a base portion of the burner shell 14 to allow the A~K-105-Can -15-~Z4~6V9 combustible mixture to flow therethrough. The side wall 19 of the burner shell 14 is disposed between an annular shoulder portion 16 and the end cap 17 of the burner shell 14. The floating valve 20 is preferably made of a temperature resistant metal or other suitable material for high temperature use.
The floating valve 20 is disposed within the combustor shell 14 for reciprocation between the annular shoulder 16 provided on a lower portion of the combustor shell 14 and the cap 17 of the combustor shell 14. A corresponding annular shoulder 22 on the base portion of the poppet valve 20 limits movement of the floating valve 20 toward the combustion chamber when the shoulder 22 of the poppet valve contacts the shoulder 16 of the burner shell 14. Movement of the valve 20 away from the combustion chamber is limited by contact of a rear surface 21 of the floating valve 20 with an inside surface 11 of the cap 17 of the combustor shell 14.
A plurality of ports 24 are disposed around the floating valve 20 beneath the shoulder 22 of the floating valve 20 and provides communication between the bore of the valve and the small clearance between the valve side wall X5 and the side wall 19. The ports 24 are preferably arranged substantially parallel to the rear surface 21 of the valve 20 and extend radially from the bore.
ARK-105-Can -16-~Z4Q16~9 A spark plug 60 extends into the combustion chamber through a threaded bore in the combustor chamber shell 14. The spark plug 60 is provided to initially ignite the combustion gases in the shell 14. The spark plug 60 is preferably threaded into the combustion chamber shell 14 so as to provide a seal between the spark plug 60 and the combustor shell 14. The spark plug 60 is disposed near the floating valve 20 but far enough from the inlet end of the combustion chamber 25 to not interfere with the reciprocation of the floating valve 20.
The ball check valve provided in the combustible mixture supply line 40, as shown in Fig. 1, includes a smooth ball 30 arranged to reciprocate toward and away from a rear seat 32 of the ball valve chamber 34. The ball 30 is preferably maintained in contact with the rear surface 21 of the floating valve 20. Furthermore, the extent of reciprocation of the valve 20 is preferably small with respect to the diameter of the ball 30, so that the ball 30 is held within the chamber 34 by the floating valve 20 during reciprocation. Still further, it is preferred that the valve seat snugly against the ball 30 when the ball is received on the rear seat 32 so that the valve 20 may maintain a sealing relationship for ARK-105-Can -17-~24~6~9 the ball and seat 32 when the valve is in contact with the end cap 17. Alternatively, various arrangements may be provided at a front end of the ball valve 34 such as fingers or a lattice to retain the ball 30 in the ball valve chamber 34.
The ball check valve during reciprocation assists in the regulation of the flow of combustible mixture into the combustion chamber 15 along with the floating valve 20.
The ball valve 30 also prevents backfire through the supply line 40 by preventing a flame in the combustion chamber 15 from spreading backwardly into the combustible mixture supply line 40. If desired, additional or different backfire prevention devices, such as a suitable conventional check valve or other type of flame arrestor, could be provided in supply line 40 upstream of the ball valve 34 or instead of the ball valve 34.
The exhaust tube 50 at the exhaust end 18 of the burner shell 14 has a first end 51 disposed inside the burner shell 14 and a second end 52 disposed outside the burner shell 14. The exhaust tube 50 is relatively small in cross-sectional diameter with respect to the burner shell 14. The burner shell 14 preferably has a sloping or curving exnaust end surface 12 which slopes inwardly toward the exhaust tube 50 and with the tube 50 preferably A~K-105-Can - -18-lZ4~6~39 ending at, or perhaps extending only slightly through, a central portion of the end surface 12.
If the inner end of the exhaust tube 50 protrudes too far into the combustion chamber 15, the efficient operation of the chamber may be interrupted. It is preferable, however, to have the end surface 12 curved or sloping to provide a tornadic action which is believed to cause intense héat and compIete combustion of the combustible mixture and therefore a more efficient use of the fuel within the pulsing combustor.
It is to be noted that the exhaust tube 50 may have to be adjusted in size and location to "tune" the exhaust flow from the combustion chamber shell or burner shell 14. By "tuning" the exhaust tube 50, the desired operating characteristics of the burner namely, the number of pulses per minute, the pressure in the combustion chamber 15, the velocity of the gas exhausted and other such factors may be optimized. For example, if the tube diameter is too large, the combustion of the gases may not produce a sufficient pressure to reciprocate the floating valve 20.
Generally it can be stated that the burner shell 14 is considerably larger in diameter than the exhaust tube 50. The appropriately sized exhaust tube 50 is rigidly secured to the ARK-105-Can -19-lZ~4~6~9 combustion chamber 14, preferably by welding. The appropriate relative dimensions for the shell 14, the exhaust tube 50 and the floating valve 20 will be readily determined experimentally by one skilled in the art upon reading the present specification.
Specifically, in each embodiment, it is recommended that values for all but one of the variables be preselected with the remaining variable sized according to the preferred operation of the device.
During operation, a pressurized combustible mixture is supplied to the bottom of the floating valve through the combustible mixture supply line 40 by way of the ball valve chamber 34.
The combustible mixture is preferably an air and gas combination with the gas preferably being either natural gas or propane although pure ethane, pure methane or other combustible gases would also suffice. Gas and air are mixed through a suitable conventional valving system, from an air compressor, and a source of fuel gas, not illustrated, in a suitable, conventional manner to form the combustible mixture which is supplied to the combustible mixture supply line 40.
The pressurized combustible mixture initially lifts the ball valve 30 from its seat 32 in the ball valve chamber and since the ball is in contact with the rear surface 21 of the floating ARK-105-Can -20-12~1U6~9 valve 20, the floating valve 20 is also lifted so that the combustible mixture can flow around the ball valve 30 into the small clearance between the valve side wall 25 and the side wall l9 of the shell 14. The combustible mixture may then flow through the ports 24 into the combustion chamber by way of the bore 26 of the floating valve. The combustible mixture exerts a force against the entire rear surface 21 of the floating valve 20 as soon as it is lifted and thereby lifts the floating valve 20 quickly away from the end cap 17 of the burner shell 14. With continued force against the rear surface 21, floating valve 20 continues upwardly being restricted by the shoulder 22 of the floating valve 20 contacting the shoulder 16 of the burner shell 14.
Since the valve 20 floats on a cushion of the combustible mixture, no lubrication of the floating valve is needed and the valve is cooled by the incoming combustible mixture. Note also that unlike the normal poppet valve which is either cam operated or spring loaded, the valve of the present invention is reciprocated by the pressure differential between a pressure in the combustion chamber 15 and a pressure in the combustible mixture supply line 40 and may have the assistance of a spring in some embodiments.
ARK-105-Can -21-1;~45~6~9 The combustible mixture then flows between the side wall 19 of the burner shell 14 and the side wall 25 of the floating valve 20. The mixture flows around and through the ports 24 in the floating valve 20 and into the open interior 26 thereof. Note that because the shoulder 22 of the valve 20 is close to or in contact witb the shoulder 16 of the burner 14, the combustible mixture is constrained to flow through the ports 24 in the valve 20. The combustible mixture then flows out a front bore 26 in the floating valve 20 and flows into a main portion of the burner shell 14.
After the combustible mixture has first entered the combustion chamber 15, the spark plug 60 is fired to initially ignite the mixture. Once the spark plug 60 has initially ignited the combustible mixture the spark plug 60 is no longer utilized. Instead, further ignition oE the combustion mixture occurs due to the continuing flame or heat still retained in the combustion chamber 15. When a new charge of combustible mixture is admitted into the combustion chamber 15, the continuing flame ignite the fresh combustion mixture. Thus the combustion, charging and ignition process continues automatically.
ARK-105-Can -22-12~ 9 Combustion thereupon takes place of the combustible mixture which increases the pressure within the combustion chamber and thereby forces the floating valve 20 toward the inner surface 11 of the cap 17 of the burner shell 14. At the same time, the ball valve 30 is forced to séat itself on the ball valve seat 32 of the ball valve chamber 34. With the ball 30 seated and the floating valve 20 also seated, a double seal is provided to prevent the combustible mixture from backfiring by flowing into the combustion mixture supply line 40.
As the burned combustible mixture is exhausted from the combustion chamber 15 through the exhaust tube 50, the pressure in the combustion chamber 15 decreases. When the pressure in the combustion chamber 15 has decreased sufficiently, for example, to an effective pressure below the effective pressure of the combustible mixture in the combustible mixture supply line 40~ the pressure of the combustible mixture forces the floating valve 20 upwardly from the cap 17 of the burner shell 14 to repeat the process. With the pressurized mixture pushing against the rear surface 21 of the floating valve 20 ancl the hot exhaust products pushing on an inside rear surface 28 of the floating valve 20, the valve acts like a differential piston. When the floating valve is in ~RK-105-Can -23-- ~2~
its lowermost position, the cross-sectional area of the floating valve 27 upon which the exhaust products force acts, is significantly ~arger than the area upon which the combustible mixture force acts, only the cross-sectional area of the supply line 40. Thus a lower pressure than the pressure in the combustible mixture supply line 40 is required in the combustion chamber 15 before the fioating valve 20 is lifted from engagement with the end cap 17 of the burner shell 14. The length of reciprocation of the floating valve 20 is desirably smaller than the diameter of the ball valve 30 to ensure that the ball valve 30 stays in the ball valve chamber 34.
In this way, it should be noted that the pressure of the mixture in the line 40 acts on the exposed lower surface of the ball 30 when the ball is seated in the chamber 34 whereas the pressure of the combustion gases effectively acts on the entire cross-sectional area of the floating valve. Thus a significantly lower pressure in the combustion chamber than in the supply line will keep the ball seated in the ball check valve. Once the pressure within the combustion chamber 15 has dropped sufficiently, the ball is unseated, the pressuri~ed combustion gases rapidly begin to act on the entire lower surface of the floating valve 20 with the ARK-105-Can -24-124~6~9 result that the valve is quickly driven upwardly toward the shoulder 16. As soon as contact is made between the valve shoulder 22 and the shoulder 16 of the burner shell 14, the effective area of the floating valve on which the combustion gases act is reduced to the cross-sectional area of the combustion chamber.
After the combustion gases have expanded sufficiently, the force on the floatiny valve upper surface will be sufficient to urge the floating valve downwardly away from the surface 16. At that point, the effective surface area of the floating valve, as seen by the combust-ion gases, increases with the result that the floating valve is more easily urged downwardly. Furthermore, once the ball 30 seats in the ball check valve, the effective surface area of the floating valve as seen by the combustion mixture is significantly reduced to the cross-sectional area of the supply line 40. Thus the combustion gases may now more easily keep the valve 20 and the ball 30 seated in the lowermost position.
Because the effective areas of the floating valve upon which the combustible mixture and combustion gases act are quickly changing during the reciprocation of the floating valve, the speed at which the valve travels is increased AP~K-105-Can -25- -lZ~6~9 significantly. That is, the valve moves quickly between its uppermost and lowermost positions because a slight movement of the valve immediately results in a significant increase in the effective area of the dominant force. Thus, the varying surface area helps maintain the floating valve in the uppermost and lowermost positions and helps to quickly move the floating valve between the positions.
The valve 20, as shown in Figs. 1 and 2, has a passageway provided in the front face whereas the rear surface 21 is completely closed. An upper section of the valve 20 including the bore 26 is defined by an annular portion or tube 23 which is reduced in size with respect to the base portion 27 of the valve. The valve is preferably machined from a solid piece of metal. The bore 26 extends completely through the upper section and only partially through the base portion 27 of the valve 20. The plurality of ports 24, which are arranged radially communicate with the bore 26. The ports 24 extend into the bore 26 to provide a path of flow for the combustible mixture. The size and the number of the ports 24 in the poppet valve 20 depends upon the type of fuel used and the pressure at which the combustible mixture is supplied.
ARK-105-Can -26-1 Z4~'61~9 The combustible mixture preferably enters the combustion chamber only through the ports 24 and thus, the valve 20 may serve as a flame holder or flame tube to contain the flame generated by the burning of the combustible mixture.
Floating valve 20 may suitably reciprocate at up to about 3500 times per minute in the pulse combustion device. The frequency of reciprocation may vary and depends upon the relative size of the combustor shell and the exhaust tube 50, the rate of flow of the fuel and air mixture through the floating valve, and the pressure at which the combustible gases are supplied. While variation of physical characteristics and conditions may vary the pulsing rate, generally, for most purposes the frequency of reciprocation of the floating valve will be about 3200 to about 3400 cycles per minute. ~owever, for some purposes it may be desired to have the frequency of reciprocation as low as 800 to 900 cycles per minute.
- One preferred embodiment of the present invention has a burner shell which is about 25 centimeters (ten inches) long with a diameter of about 2.5 centimeters (one inch) (i.e., a 10:1 ratio). The floating valve is about l centimeter (three-eighths of an inch) in length and A~K-105-Can -27-~;~4~6~9 reciprocates through a length of approximately 0.5 centimeter ~three-sixteenths of an inch). The combustible mixture is pressurized to approximately 2.5-3.5 kg/cm (40-50 psi) with an air to propane mixture ratio of about 25 to l. An interior temperature of approximately 925C was very ~uickly developed in the combustion chamber 15 after ignition of the combustible mixture.
As taught in my earlier filed application, a pumping mechanism may provide the combustible mixture as a series of discrete pressurized pulses at the desired rate of cycling of the floating valve. To facilitate use of lower pressure combustible mixture a spring may be provided in a chamber beneath the floating valve to urge the floating valve toward the open position.
Suitable for use in all embodiments previously described in my patents and in this disclosure are advantageous embodiments wherein the floating valve, preferably the flat plate floating valve, as shown in Fig~ 6 is in the form of annular floating valve 628 having through holes 624 and the combustible gas inlet is in the form of a plurality of inlets 641 supplied by gas manifold 6~2 around a corresponding annular area in the end cap 676. The annular structure of the end cap may have a hollow cylindrical portion 677 extending into the K-105-Can -28-~2~t~6~
combustion chamber with a solid end a short dlstance into the combustion chamber from the limit of travel of the floating valve and having the ignition means 660 extending therethrough. For example, a spark plug or other ignitor may be placed through the solid end of the cylindrical portion of the end cap extending into the combustion chamber. This location for the ignitor provides ignition more evenly to the hollow flame.
The pulse combustor of this invention is particularly well suited for use in air heating systems. Fig. 3 schematically shows one embodiment of a pulse combustor of this invention used in an air heating system. Fig. 3, in simplified schematic form, shows air heater 900 wherein an air treatment passage is defined by air treatment duct 930 with cold air entering as shown by arrows 901 and leaving as heated air shown by arrows 902. The air to be heated, usually return air from an enclosed volume, such as a room, is driven through treatment duct 930 by an upstream blower, not shown, and first passed over heat exchanger 903 and then passed in direct contact with pulse combustor chamber 906 and pulse combustor exhaust manifold 904 and through treatment unit 931 comprising any desired humidification means and filtering means.
The treatment air blower means, filtering means and ARK-105-Can -29-~24~6~9 humidification means are not shown, but are any such suitable means as conventionally used in warm air furnaces as known to the art. Although shown in a horizontal air passage configuration, the entire assembly may be rotated 90 and operated in either a down-pass or up-pass mode. The pulse combustor will operate in any of these positions.
As shown in Fig. 3, combustion air is provided through air intake 941 of combustion air blower 940 where it is pressurized to about 3-1j2 to about 7 inches of water, preferably about 4 to about 6 inches of water. The combustion air pressure and flow rate is maintained and regulated by combustion air flow regulator shown generally as 924 in Fig. 3. Referring also to Fig. 5, combustion air flow regulator 924 has rod 925 with tapered head 927 which fittingly engages tapered inlet 928. Combustion air flow regulator rod 925 is preferably threaded and is readily adjustable through a threaded bore in the T-shaped end of combustion air pressurized conduit 942. Suitably, lock nut 926 is provided to lock combustion air flow regulator rod 925 in desired position and if desired, bearing means may be provided within combustion air pressurized conduit 942 to assure centering of tapered head 927 within tapered inlet 928. It is readily seen that as tapered head 927 ARK-105-~an -30-lZ4~6~
is advanced into tapered inlet 928 the flow of pressurized combustion air is decreased and its pressure, assumïng a constant speed combustion air blower 940, is increased.
Combustible fuel gas, such as natural gas, is introduced through gas supply line 921 into a mixing chamber downstream from combustion air flow regulator 924. Not shown in the drawing in gas supply line 921 is a suitable gas pressure controller, as is well known to the art, to provide fuel gas at a pressure of about 2 inches to 3-1/2 inches of water and preferably about 3 inches to
U.S. Patent No. 2,411,675 of Alexander; U.S. Patent No. 1,719,015 of Lewis; U.S. Patent No. 1,885,040 of Arnold; U.S. Patent No. 4,259,928 of Huber;
British Patent No. 166,455; French Patent No.
1,366,565; and, "Pulsating Combustion: An Old Idea May Give Tomorrow's Boiler's a New Lookn, Power pp. 88-91, August 1954.
Accordingly, the need exists for an lmproved burner which provides an efficient and A~K-105-Can -8-lZ4~63D~
economical use of fuel. Such an improved burner would have particular utility in steam generation devices and in home heating equipment especially where a fluid is to be heated by the combustion.
SUMMARY OF THE INVENTION
It is therefore an object of the present invention to provide an improved co~bustion device having a floating valve member mounted in the wall of a combustion chamber of the combustion device which reciprocates in a floating manner to regulate a supply of a combustible mixture to the combustion chamber.
It is therefore another object of the present invention to provide a pulsing combustion device which provides an efficient and economical use of fuel and which overcomes the disadvantages of known combustion devices.
Yet another object of the present invention is to provide a heating device having a pulsing combustion device wherein the co~bustion gases heat either a liquid or a gas, which liquid or gas cools the shell of the burner.
The combustor of the present invention is especially useful in any type of a fluid heating system, such as a home heating or hot water heating system. Present home heating systems are often large and expensive as well as being ARK-105-Can -9-124106{~9 energy-inefficient because much of the heating value of the fuel is wasted. It would be advantageous to provide a building heating system in which a simple and compact pulsing combustion device is used to heat the fluid medium by which the home is heated. This would provide a more effi~ient use of heating fuels, since in many of today's home heating systems a large percentage of the heat generated is lost through the chimney.
The need therefore remains for a building heating system which efficiently utilizes heat energy contained in the combustion gases produced by the burner.
It is therefore still another object of the present invention to provide an efficient and low cost heating system for a building wherein the fluid medium which heats the home is itself heated by a compact pulsing combustion device.
It is therefore yet still another object of the present invention to provide a heating system in which the spent gases of combustion are utilized to improve the efficiency of the system.
A pulsing combustion device according to the present invention comprises a combustion chamber with an inlet for a combustible mixture and an unvalved outlet to the atmosphere for combustion gases. A pressurized combustlble mixture is ARR-105-Can -10-lZ4~)609 supplied to a floating valve with through ports providing controlled communication between the supply of the combustible mixture and the combustion chamber. Reciprocation of the floating valve member increases and decreases the flow of combustible mixture into the combustion chamber.
The combustible mixture is ignited and burned in the combustion chamber. The floating valve is reciprocated in its mounting in the wall of the combustion chamber by the pressure of the pressurized combustible mixture and the pressure of the combustion gases to regulate the flow of the combustible mixture into the combustion chamber.
My earlier filed Canadian Patent Application, Serial No. 392,910, filed December 22, 1981, teaches and claims specific embodiments of my pulsing combustion device and process and specific embodiments of a fluid heating device incorporating my pulsing combustion device. My Canadian Patent Application, Serial No. 479,890, filed April 24, 1985, teaches and claims further improvements to my pulsing combustion device and its use in water heating applications. This application teaches new methods for feeding combustible mixtures to my pulsing combustion device and its use in hot air heating applications.
ARK-105-Can -11-124(~6~9 Heating devices for a wide variety of purposes according to the present invention may use a pulsing combustion device as described having a flow of gas encircling the combustion chamber so that the gas is heated. 8eat exchange may be enhanced by placement of baffles in and/or downstream of the combustion zone and combustion products may be passed through a wide variety of coil and/or finned heat exchangers. Likewise, the gas to be heated may be passed through coil and/or finned heat exchangers. A particularly suitable combustible mixture supply means and system is described.
BRIEF DESCRIPTION OF THE DRAWINGS
Preferred embodiments of a pulsing combustion device and preferred embodiments of heating devices including the pulsing combustion device, according to the present invention are described with reference to the accompanying drawings wherein like members bear like reference numerals and wherein:
Fig. 1 is a cross-sectional view of one embodiment of a pulsing combustion device according the present invention;
' Fig. 2 is a view through the line 2-2 of Fig. 1;
ARK-105-Can -12-1~4~6V9 Fig. 3 is a perspective view of a hot air heater utilizing a pulsing combustion device according to this invention;
Fig. 4 is a perspective view of another embodiment of a hot air heater utilizing a pulsing combustion device according to this invention;
Fig. 5 is a sectional view of the combustible gas mixing and feeding portion of the apparatus; and - Fig. 6 is a sectional side view of , another embodiment of the floating valve of a pulsing combustion device of this invention.
; DESCRIPTION OF THE PREFERRED EMBODIMENTS
With reference to Fig. 1, one embodiment , - of a pulsing combustion device 10, includes an elongate combustion chamber shell or burner shell 14 which defines a combustion chamber 15. The combustion chamber shell 14 is generally tubular with a length that is considerably greater than its width. The combustion chamber shell is preferably circular in cross section, but may of course be square, rectangular or of any other suitable configuration. The combustion chamber 15 is closed except for the outlet for combustion gases and the I inlet for admitting the combustible mixture. The j combustible mixture may be supplied by a line 40 through a ball valve chamber 34 by way of a ARK-105-Can -13-1%~6~9 reciprocating floating valve 20. The ball valve chamber 34 is provided within an end cap 17 disposed at an inlet end of the combustor shell 14.
The end cap 17 together with the combustor shell 14 define a path of reciprocation for the floating valve 20. After combustion, the combustion gases exit through an open exhaust tube 50 disposed at an exhaust end 18 of the combustor shell 14.
If desired, the ball valve chamber may be deleted or replaced by a suitable conventional check valve. The ball valve chamber 34 or the check valve 507 may serve to prevent a flashback of the combustible mixture. Any suitable flame arrestor may be used.
As shown in Fig. 1, ball valve chamber 34 and unvalved exhaust tube 50 have diameters which are considerably smaller than the cross-sectional diameter of the burner shell 14. Thus, the burner shell 14 is substantially closed on each end and has two restricted passageways: the ball valve chamber 34 at the inlet to the combustion chamber 15 and the exhaust tube 50 disposed at the exhaust end 18 of the burner shell 14. The burner shell 14, the ball valve chamber 34 and the exhaust tube 50 are all preferably made of a temperature resistant steel or other material which can tolerate the high temperatures generated in the ARK-105-Can -14-lZ~ 9 combustion chamber while the combustible mixture is burning~
A flange 76 is secured, for example, by welding, to the end cap 17 to facilitate the asse~bly of the end cap 17 with the shell 14. A
plurality of bolts 74 extend through openings in the flange and are threadably received by corresponding nuts 72 which are secured, as by welding, to the shell 14. The end cap 17 is thereby detachably secured to the shell 14 by the nuts 72 and the bolts 74. A sealing gasket 78, preferably of neoprene or another gasket material suitable for high temperature use may be preferably disposed between the end cap 17 and a lower end wall of the burner shell 14.
The floating poppet valve 20 disposed for reciprocal movement in the burner or combustor shell 14 may be generally mushroom-shaped with an open interior or bore 26, as shown in Figs. 1 and 2. The floating valve 20 is of integral construction and includes a base 27 having a first diameter and a tube 23 having a reduced diameter with the bore extending through the tube and through a portion of the base. A small clearance is provided between a side wall 25 of the base of the floating valve and a side wall 19 of a base portion of the burner shell 14 to allow the A~K-105-Can -15-~Z4~6V9 combustible mixture to flow therethrough. The side wall 19 of the burner shell 14 is disposed between an annular shoulder portion 16 and the end cap 17 of the burner shell 14. The floating valve 20 is preferably made of a temperature resistant metal or other suitable material for high temperature use.
The floating valve 20 is disposed within the combustor shell 14 for reciprocation between the annular shoulder 16 provided on a lower portion of the combustor shell 14 and the cap 17 of the combustor shell 14. A corresponding annular shoulder 22 on the base portion of the poppet valve 20 limits movement of the floating valve 20 toward the combustion chamber when the shoulder 22 of the poppet valve contacts the shoulder 16 of the burner shell 14. Movement of the valve 20 away from the combustion chamber is limited by contact of a rear surface 21 of the floating valve 20 with an inside surface 11 of the cap 17 of the combustor shell 14.
A plurality of ports 24 are disposed around the floating valve 20 beneath the shoulder 22 of the floating valve 20 and provides communication between the bore of the valve and the small clearance between the valve side wall X5 and the side wall 19. The ports 24 are preferably arranged substantially parallel to the rear surface 21 of the valve 20 and extend radially from the bore.
ARK-105-Can -16-~Z4Q16~9 A spark plug 60 extends into the combustion chamber through a threaded bore in the combustor chamber shell 14. The spark plug 60 is provided to initially ignite the combustion gases in the shell 14. The spark plug 60 is preferably threaded into the combustion chamber shell 14 so as to provide a seal between the spark plug 60 and the combustor shell 14. The spark plug 60 is disposed near the floating valve 20 but far enough from the inlet end of the combustion chamber 25 to not interfere with the reciprocation of the floating valve 20.
The ball check valve provided in the combustible mixture supply line 40, as shown in Fig. 1, includes a smooth ball 30 arranged to reciprocate toward and away from a rear seat 32 of the ball valve chamber 34. The ball 30 is preferably maintained in contact with the rear surface 21 of the floating valve 20. Furthermore, the extent of reciprocation of the valve 20 is preferably small with respect to the diameter of the ball 30, so that the ball 30 is held within the chamber 34 by the floating valve 20 during reciprocation. Still further, it is preferred that the valve seat snugly against the ball 30 when the ball is received on the rear seat 32 so that the valve 20 may maintain a sealing relationship for ARK-105-Can -17-~24~6~9 the ball and seat 32 when the valve is in contact with the end cap 17. Alternatively, various arrangements may be provided at a front end of the ball valve 34 such as fingers or a lattice to retain the ball 30 in the ball valve chamber 34.
The ball check valve during reciprocation assists in the regulation of the flow of combustible mixture into the combustion chamber 15 along with the floating valve 20.
The ball valve 30 also prevents backfire through the supply line 40 by preventing a flame in the combustion chamber 15 from spreading backwardly into the combustible mixture supply line 40. If desired, additional or different backfire prevention devices, such as a suitable conventional check valve or other type of flame arrestor, could be provided in supply line 40 upstream of the ball valve 34 or instead of the ball valve 34.
The exhaust tube 50 at the exhaust end 18 of the burner shell 14 has a first end 51 disposed inside the burner shell 14 and a second end 52 disposed outside the burner shell 14. The exhaust tube 50 is relatively small in cross-sectional diameter with respect to the burner shell 14. The burner shell 14 preferably has a sloping or curving exnaust end surface 12 which slopes inwardly toward the exhaust tube 50 and with the tube 50 preferably A~K-105-Can - -18-lZ4~6~39 ending at, or perhaps extending only slightly through, a central portion of the end surface 12.
If the inner end of the exhaust tube 50 protrudes too far into the combustion chamber 15, the efficient operation of the chamber may be interrupted. It is preferable, however, to have the end surface 12 curved or sloping to provide a tornadic action which is believed to cause intense héat and compIete combustion of the combustible mixture and therefore a more efficient use of the fuel within the pulsing combustor.
It is to be noted that the exhaust tube 50 may have to be adjusted in size and location to "tune" the exhaust flow from the combustion chamber shell or burner shell 14. By "tuning" the exhaust tube 50, the desired operating characteristics of the burner namely, the number of pulses per minute, the pressure in the combustion chamber 15, the velocity of the gas exhausted and other such factors may be optimized. For example, if the tube diameter is too large, the combustion of the gases may not produce a sufficient pressure to reciprocate the floating valve 20.
Generally it can be stated that the burner shell 14 is considerably larger in diameter than the exhaust tube 50. The appropriately sized exhaust tube 50 is rigidly secured to the ARK-105-Can -19-lZ~4~6~9 combustion chamber 14, preferably by welding. The appropriate relative dimensions for the shell 14, the exhaust tube 50 and the floating valve 20 will be readily determined experimentally by one skilled in the art upon reading the present specification.
Specifically, in each embodiment, it is recommended that values for all but one of the variables be preselected with the remaining variable sized according to the preferred operation of the device.
During operation, a pressurized combustible mixture is supplied to the bottom of the floating valve through the combustible mixture supply line 40 by way of the ball valve chamber 34.
The combustible mixture is preferably an air and gas combination with the gas preferably being either natural gas or propane although pure ethane, pure methane or other combustible gases would also suffice. Gas and air are mixed through a suitable conventional valving system, from an air compressor, and a source of fuel gas, not illustrated, in a suitable, conventional manner to form the combustible mixture which is supplied to the combustible mixture supply line 40.
The pressurized combustible mixture initially lifts the ball valve 30 from its seat 32 in the ball valve chamber and since the ball is in contact with the rear surface 21 of the floating ARK-105-Can -20-12~1U6~9 valve 20, the floating valve 20 is also lifted so that the combustible mixture can flow around the ball valve 30 into the small clearance between the valve side wall 25 and the side wall l9 of the shell 14. The combustible mixture may then flow through the ports 24 into the combustion chamber by way of the bore 26 of the floating valve. The combustible mixture exerts a force against the entire rear surface 21 of the floating valve 20 as soon as it is lifted and thereby lifts the floating valve 20 quickly away from the end cap 17 of the burner shell 14. With continued force against the rear surface 21, floating valve 20 continues upwardly being restricted by the shoulder 22 of the floating valve 20 contacting the shoulder 16 of the burner shell 14.
Since the valve 20 floats on a cushion of the combustible mixture, no lubrication of the floating valve is needed and the valve is cooled by the incoming combustible mixture. Note also that unlike the normal poppet valve which is either cam operated or spring loaded, the valve of the present invention is reciprocated by the pressure differential between a pressure in the combustion chamber 15 and a pressure in the combustible mixture supply line 40 and may have the assistance of a spring in some embodiments.
ARK-105-Can -21-1;~45~6~9 The combustible mixture then flows between the side wall 19 of the burner shell 14 and the side wall 25 of the floating valve 20. The mixture flows around and through the ports 24 in the floating valve 20 and into the open interior 26 thereof. Note that because the shoulder 22 of the valve 20 is close to or in contact witb the shoulder 16 of the burner 14, the combustible mixture is constrained to flow through the ports 24 in the valve 20. The combustible mixture then flows out a front bore 26 in the floating valve 20 and flows into a main portion of the burner shell 14.
After the combustible mixture has first entered the combustion chamber 15, the spark plug 60 is fired to initially ignite the mixture. Once the spark plug 60 has initially ignited the combustible mixture the spark plug 60 is no longer utilized. Instead, further ignition oE the combustion mixture occurs due to the continuing flame or heat still retained in the combustion chamber 15. When a new charge of combustible mixture is admitted into the combustion chamber 15, the continuing flame ignite the fresh combustion mixture. Thus the combustion, charging and ignition process continues automatically.
ARK-105-Can -22-12~ 9 Combustion thereupon takes place of the combustible mixture which increases the pressure within the combustion chamber and thereby forces the floating valve 20 toward the inner surface 11 of the cap 17 of the burner shell 14. At the same time, the ball valve 30 is forced to séat itself on the ball valve seat 32 of the ball valve chamber 34. With the ball 30 seated and the floating valve 20 also seated, a double seal is provided to prevent the combustible mixture from backfiring by flowing into the combustion mixture supply line 40.
As the burned combustible mixture is exhausted from the combustion chamber 15 through the exhaust tube 50, the pressure in the combustion chamber 15 decreases. When the pressure in the combustion chamber 15 has decreased sufficiently, for example, to an effective pressure below the effective pressure of the combustible mixture in the combustible mixture supply line 40~ the pressure of the combustible mixture forces the floating valve 20 upwardly from the cap 17 of the burner shell 14 to repeat the process. With the pressurized mixture pushing against the rear surface 21 of the floating valve 20 ancl the hot exhaust products pushing on an inside rear surface 28 of the floating valve 20, the valve acts like a differential piston. When the floating valve is in ~RK-105-Can -23-- ~2~
its lowermost position, the cross-sectional area of the floating valve 27 upon which the exhaust products force acts, is significantly ~arger than the area upon which the combustible mixture force acts, only the cross-sectional area of the supply line 40. Thus a lower pressure than the pressure in the combustible mixture supply line 40 is required in the combustion chamber 15 before the fioating valve 20 is lifted from engagement with the end cap 17 of the burner shell 14. The length of reciprocation of the floating valve 20 is desirably smaller than the diameter of the ball valve 30 to ensure that the ball valve 30 stays in the ball valve chamber 34.
In this way, it should be noted that the pressure of the mixture in the line 40 acts on the exposed lower surface of the ball 30 when the ball is seated in the chamber 34 whereas the pressure of the combustion gases effectively acts on the entire cross-sectional area of the floating valve. Thus a significantly lower pressure in the combustion chamber than in the supply line will keep the ball seated in the ball check valve. Once the pressure within the combustion chamber 15 has dropped sufficiently, the ball is unseated, the pressuri~ed combustion gases rapidly begin to act on the entire lower surface of the floating valve 20 with the ARK-105-Can -24-124~6~9 result that the valve is quickly driven upwardly toward the shoulder 16. As soon as contact is made between the valve shoulder 22 and the shoulder 16 of the burner shell 14, the effective area of the floating valve on which the combustion gases act is reduced to the cross-sectional area of the combustion chamber.
After the combustion gases have expanded sufficiently, the force on the floatiny valve upper surface will be sufficient to urge the floating valve downwardly away from the surface 16. At that point, the effective surface area of the floating valve, as seen by the combust-ion gases, increases with the result that the floating valve is more easily urged downwardly. Furthermore, once the ball 30 seats in the ball check valve, the effective surface area of the floating valve as seen by the combustion mixture is significantly reduced to the cross-sectional area of the supply line 40. Thus the combustion gases may now more easily keep the valve 20 and the ball 30 seated in the lowermost position.
Because the effective areas of the floating valve upon which the combustible mixture and combustion gases act are quickly changing during the reciprocation of the floating valve, the speed at which the valve travels is increased AP~K-105-Can -25- -lZ~6~9 significantly. That is, the valve moves quickly between its uppermost and lowermost positions because a slight movement of the valve immediately results in a significant increase in the effective area of the dominant force. Thus, the varying surface area helps maintain the floating valve in the uppermost and lowermost positions and helps to quickly move the floating valve between the positions.
The valve 20, as shown in Figs. 1 and 2, has a passageway provided in the front face whereas the rear surface 21 is completely closed. An upper section of the valve 20 including the bore 26 is defined by an annular portion or tube 23 which is reduced in size with respect to the base portion 27 of the valve. The valve is preferably machined from a solid piece of metal. The bore 26 extends completely through the upper section and only partially through the base portion 27 of the valve 20. The plurality of ports 24, which are arranged radially communicate with the bore 26. The ports 24 extend into the bore 26 to provide a path of flow for the combustible mixture. The size and the number of the ports 24 in the poppet valve 20 depends upon the type of fuel used and the pressure at which the combustible mixture is supplied.
ARK-105-Can -26-1 Z4~'61~9 The combustible mixture preferably enters the combustion chamber only through the ports 24 and thus, the valve 20 may serve as a flame holder or flame tube to contain the flame generated by the burning of the combustible mixture.
Floating valve 20 may suitably reciprocate at up to about 3500 times per minute in the pulse combustion device. The frequency of reciprocation may vary and depends upon the relative size of the combustor shell and the exhaust tube 50, the rate of flow of the fuel and air mixture through the floating valve, and the pressure at which the combustible gases are supplied. While variation of physical characteristics and conditions may vary the pulsing rate, generally, for most purposes the frequency of reciprocation of the floating valve will be about 3200 to about 3400 cycles per minute. ~owever, for some purposes it may be desired to have the frequency of reciprocation as low as 800 to 900 cycles per minute.
- One preferred embodiment of the present invention has a burner shell which is about 25 centimeters (ten inches) long with a diameter of about 2.5 centimeters (one inch) (i.e., a 10:1 ratio). The floating valve is about l centimeter (three-eighths of an inch) in length and A~K-105-Can -27-~;~4~6~9 reciprocates through a length of approximately 0.5 centimeter ~three-sixteenths of an inch). The combustible mixture is pressurized to approximately 2.5-3.5 kg/cm (40-50 psi) with an air to propane mixture ratio of about 25 to l. An interior temperature of approximately 925C was very ~uickly developed in the combustion chamber 15 after ignition of the combustible mixture.
As taught in my earlier filed application, a pumping mechanism may provide the combustible mixture as a series of discrete pressurized pulses at the desired rate of cycling of the floating valve. To facilitate use of lower pressure combustible mixture a spring may be provided in a chamber beneath the floating valve to urge the floating valve toward the open position.
Suitable for use in all embodiments previously described in my patents and in this disclosure are advantageous embodiments wherein the floating valve, preferably the flat plate floating valve, as shown in Fig~ 6 is in the form of annular floating valve 628 having through holes 624 and the combustible gas inlet is in the form of a plurality of inlets 641 supplied by gas manifold 6~2 around a corresponding annular area in the end cap 676. The annular structure of the end cap may have a hollow cylindrical portion 677 extending into the K-105-Can -28-~2~t~6~
combustion chamber with a solid end a short dlstance into the combustion chamber from the limit of travel of the floating valve and having the ignition means 660 extending therethrough. For example, a spark plug or other ignitor may be placed through the solid end of the cylindrical portion of the end cap extending into the combustion chamber. This location for the ignitor provides ignition more evenly to the hollow flame.
The pulse combustor of this invention is particularly well suited for use in air heating systems. Fig. 3 schematically shows one embodiment of a pulse combustor of this invention used in an air heating system. Fig. 3, in simplified schematic form, shows air heater 900 wherein an air treatment passage is defined by air treatment duct 930 with cold air entering as shown by arrows 901 and leaving as heated air shown by arrows 902. The air to be heated, usually return air from an enclosed volume, such as a room, is driven through treatment duct 930 by an upstream blower, not shown, and first passed over heat exchanger 903 and then passed in direct contact with pulse combustor chamber 906 and pulse combustor exhaust manifold 904 and through treatment unit 931 comprising any desired humidification means and filtering means.
The treatment air blower means, filtering means and ARK-105-Can -29-~24~6~9 humidification means are not shown, but are any such suitable means as conventionally used in warm air furnaces as known to the art. Although shown in a horizontal air passage configuration, the entire assembly may be rotated 90 and operated in either a down-pass or up-pass mode. The pulse combustor will operate in any of these positions.
As shown in Fig. 3, combustion air is provided through air intake 941 of combustion air blower 940 where it is pressurized to about 3-1j2 to about 7 inches of water, preferably about 4 to about 6 inches of water. The combustion air pressure and flow rate is maintained and regulated by combustion air flow regulator shown generally as 924 in Fig. 3. Referring also to Fig. 5, combustion air flow regulator 924 has rod 925 with tapered head 927 which fittingly engages tapered inlet 928. Combustion air flow regulator rod 925 is preferably threaded and is readily adjustable through a threaded bore in the T-shaped end of combustion air pressurized conduit 942. Suitably, lock nut 926 is provided to lock combustion air flow regulator rod 925 in desired position and if desired, bearing means may be provided within combustion air pressurized conduit 942 to assure centering of tapered head 927 within tapered inlet 928. It is readily seen that as tapered head 927 ARK-105-~an -30-lZ4~6~
is advanced into tapered inlet 928 the flow of pressurized combustion air is decreased and its pressure, assumïng a constant speed combustion air blower 940, is increased.
Combustible fuel gas, such as natural gas, is introduced through gas supply line 921 into a mixing chamber downstream from combustion air flow regulator 924. Not shown in the drawing in gas supply line 921 is a suitable gas pressure controller, as is well known to the art, to provide fuel gas at a pressure of about 2 inches to 3-1/2 inches of water and preferably about 3 inches to
3-1/2 inches of water. High pressure air gas tap 923 is provided to monitor the pressure of combustion air prior to passage through tàpered inlet 928 and may be provided with a safety switch which allows a gas valve in gas supply line 921 to open only after desired pressure is reached in combustion air pressurized conduit 942. Low pressure combustible mixture tap 922 is provided in combustible gaseous mixture supply line 920 for control purposes. I have found that using the high pressure combustion air supply as described in conjunction with pulse combustor that there has been no tendency for flashback, however, safety codes may require that a spark arrestor be placed in combustible gaseous mixture supply line 920.
. .
ARK-105-Can -31-~:Z4q~6V9 Due to the low pressure combustible gaseous mixture supplied to floating valv~ 915, I
have found it desirable to provide an enlarged combustible gas inlet chamber 912 to provide a greater force upon the combustible gas supply line side of floating valve 915. As shown in Fig. 5, floating valve 915 has combustible gas feed bores 916 in communication from valve chamber 913 to pulse combustor chamber 906 wherein combustible gas feed director flange 917 directs the combustible gas along the periphery of pulse combustor chamber 906. Valve chamber 913 is defined by pulse combustor removable end piece 907 which is provided with holding flange 908 for secure fastening to pulse combustor chamber 906 by assembly bolts passing through pulse combustor holding flange 909 and tightened with assembly nuts 911. Provision of the removable combustor end piece 907 facilitates changing of dimensions of combustible gas inlet chamber 912 and valve chamber 913 to accommodate different types of floating valves 915 as have been described herein before. The pulse combustor operates in the same fashion as previously described herein. The pulse combustion is initiated by ignitor 960 and takes place within pulse combustor chamber 906 with combustion gases passing through pulse combustor exhaust 905 and ARK-105-Can -32-lZ4~6~39 into exhaust manifold 904 feeding tubes passing through heat exchanger 903 and through an unvalved opening (not shown) to the atmosphere. The air heater as shown in Fig. 3 incorporating the pulse combustor and passing the air stream being treated in sequence over the finned heat exchanger through which combustion exhaust gases are passed in closed relationship and over the pulse combustion chamber 906 and pulse combustion exhaust manifold 904 provides high efficiency heating of the air stream to be treated.
Fig. 4 schematically shows another embodiment of an air heater according to the present invention, wherein the cold ai{ to be treated 901 is passed downwardly in sequence through heat exchanger 903 and finned pulse combustion chamber 950 and finned exhaust manifold 951 to exit as heated air shown by arrows 902. The embodiment shown in Fig. 4 operates in the same fashion as the embodiment shown in Fig. 3 except that the pulse combustor chamber and the combustion exhaust manifold is provided with expanded heat exchange surfaces.
In all of the pulse combustors of this invention, while reference has been made to pulsed combustion it should be understood that the flame is a continual flame generally attached to the ARK-105-Can -33-lZ~L~6~9 upper side of the floating valve which serves as a flame holder limiting combustion to a combustion zone adjacent the floating valve. Likewise, the action of the floating valve during combustion is generally a modulating action of increasing and decreasing the flow of combustible gas by movement of the floating valve. The combustion obtained by the pulsed combustor of this invention results in a high temperature, 2000 to over 2500F clean burn blue flame. The fuel efficiency in the combustor of this invention may be in excess of 95 percent and preferably in excess of 96.5 percent. The small size and geometry of the combustor unit and the hollow flame together with the scrubbing action of the flame and gases along heat transfer surfaces provides exceptionally high heat transfer through the combustor walls. The pulsed combustor of this invention provides a clean, cool combustion product stream which may be vented through a small tube without the need for a conventional chimney.
During experimental operation of various models of the present invention, noise levels observed were from blowers and accessory equipment, the combustor itself contributed very little to the overall noise level. Condensation formed in the exhaust was only slightly acidic and the device ARK-105-Can -34-1246~ 9 could readily be adjusted so as to provide no unburned hydrocarbons in the exhaust.
While some specific dimensions have been set forth, a wide variety of sizes of combustors according to this invention for various applications have been operated, for example, having combusti on chambers up to 8 inches in diameter and 48 inches in length with combustible gas inputs of up to 412,000 Btu per hour. Higher gas inputs are feasible in larger units.
The pulse combustor of this invention may be used to provide the advantages of high efficiency energy utilization, both in increased fuel efficiency in combustion and in thermal transfer of heat from the combustion products.
These high efficiencies result in small physical size combustors suitable for a wide variety of heating applications, such as for heating gases, liquids or solids such as industrial or home space heating, industrial or home hot water boilers and hot water heaters, chemical process heating, deep fat fryers, cooking griddles and other heating appliances and processes.
ARK-105-Can -35-
. .
ARK-105-Can -31-~:Z4q~6V9 Due to the low pressure combustible gaseous mixture supplied to floating valv~ 915, I
have found it desirable to provide an enlarged combustible gas inlet chamber 912 to provide a greater force upon the combustible gas supply line side of floating valve 915. As shown in Fig. 5, floating valve 915 has combustible gas feed bores 916 in communication from valve chamber 913 to pulse combustor chamber 906 wherein combustible gas feed director flange 917 directs the combustible gas along the periphery of pulse combustor chamber 906. Valve chamber 913 is defined by pulse combustor removable end piece 907 which is provided with holding flange 908 for secure fastening to pulse combustor chamber 906 by assembly bolts passing through pulse combustor holding flange 909 and tightened with assembly nuts 911. Provision of the removable combustor end piece 907 facilitates changing of dimensions of combustible gas inlet chamber 912 and valve chamber 913 to accommodate different types of floating valves 915 as have been described herein before. The pulse combustor operates in the same fashion as previously described herein. The pulse combustion is initiated by ignitor 960 and takes place within pulse combustor chamber 906 with combustion gases passing through pulse combustor exhaust 905 and ARK-105-Can -32-lZ4~6~39 into exhaust manifold 904 feeding tubes passing through heat exchanger 903 and through an unvalved opening (not shown) to the atmosphere. The air heater as shown in Fig. 3 incorporating the pulse combustor and passing the air stream being treated in sequence over the finned heat exchanger through which combustion exhaust gases are passed in closed relationship and over the pulse combustion chamber 906 and pulse combustion exhaust manifold 904 provides high efficiency heating of the air stream to be treated.
Fig. 4 schematically shows another embodiment of an air heater according to the present invention, wherein the cold ai{ to be treated 901 is passed downwardly in sequence through heat exchanger 903 and finned pulse combustion chamber 950 and finned exhaust manifold 951 to exit as heated air shown by arrows 902. The embodiment shown in Fig. 4 operates in the same fashion as the embodiment shown in Fig. 3 except that the pulse combustor chamber and the combustion exhaust manifold is provided with expanded heat exchange surfaces.
In all of the pulse combustors of this invention, while reference has been made to pulsed combustion it should be understood that the flame is a continual flame generally attached to the ARK-105-Can -33-lZ~L~6~9 upper side of the floating valve which serves as a flame holder limiting combustion to a combustion zone adjacent the floating valve. Likewise, the action of the floating valve during combustion is generally a modulating action of increasing and decreasing the flow of combustible gas by movement of the floating valve. The combustion obtained by the pulsed combustor of this invention results in a high temperature, 2000 to over 2500F clean burn blue flame. The fuel efficiency in the combustor of this invention may be in excess of 95 percent and preferably in excess of 96.5 percent. The small size and geometry of the combustor unit and the hollow flame together with the scrubbing action of the flame and gases along heat transfer surfaces provides exceptionally high heat transfer through the combustor walls. The pulsed combustor of this invention provides a clean, cool combustion product stream which may be vented through a small tube without the need for a conventional chimney.
During experimental operation of various models of the present invention, noise levels observed were from blowers and accessory equipment, the combustor itself contributed very little to the overall noise level. Condensation formed in the exhaust was only slightly acidic and the device ARK-105-Can -34-1246~ 9 could readily be adjusted so as to provide no unburned hydrocarbons in the exhaust.
While some specific dimensions have been set forth, a wide variety of sizes of combustors according to this invention for various applications have been operated, for example, having combusti on chambers up to 8 inches in diameter and 48 inches in length with combustible gas inputs of up to 412,000 Btu per hour. Higher gas inputs are feasible in larger units.
The pulse combustor of this invention may be used to provide the advantages of high efficiency energy utilization, both in increased fuel efficiency in combustion and in thermal transfer of heat from the combustion products.
These high efficiencies result in small physical size combustors suitable for a wide variety of heating applications, such as for heating gases, liquids or solids such as industrial or home space heating, industrial or home hot water boilers and hot water heaters, chemical process heating, deep fat fryers, cooking griddles and other heating appliances and processes.
ARK-105-Can -35-
Claims (12)
1. A pulsing combustion device comprising:
means for defining an elongate combustion chamber having an inlet for a combustible mixture and an unvalved outlet open to the atmosphere for combustion gases;
a floating valve member mounted in reciprocation relation in a wall of said combustion chamber, said valve member having a first side in communication with said combustion chamber and a second side in communication with a supply of a pressurized combustible mixture and having a plurality of ports through said valve member, means for directing said combustible mixture along the periphery of said combustion chamber; said reciprocation of said floating valve member in said wall closing and opening communication through said ports between said supply of combustible mixture and said combustion chamber;
means for supplying a pressurized combustible mixture to said second side of said floating valve member;
means for igniting and combusting said combustible mixture in said combustion chamber to produce pressurized combustion gases, said floating valve member being reciprocated by said pressurized combustible mixture in communication with said second side and said pressurized combustion gases in communication with said first side to regulate the flow of said combustible mixture into said combustion chamber.
means for defining an elongate combustion chamber having an inlet for a combustible mixture and an unvalved outlet open to the atmosphere for combustion gases;
a floating valve member mounted in reciprocation relation in a wall of said combustion chamber, said valve member having a first side in communication with said combustion chamber and a second side in communication with a supply of a pressurized combustible mixture and having a plurality of ports through said valve member, means for directing said combustible mixture along the periphery of said combustion chamber; said reciprocation of said floating valve member in said wall closing and opening communication through said ports between said supply of combustible mixture and said combustion chamber;
means for supplying a pressurized combustible mixture to said second side of said floating valve member;
means for igniting and combusting said combustible mixture in said combustion chamber to produce pressurized combustion gases, said floating valve member being reciprocated by said pressurized combustible mixture in communication with said second side and said pressurized combustion gases in communication with said first side to regulate the flow of said combustible mixture into said combustion chamber.
2. A pulsing combustion device of Claim 1 mounted within an air treatment duct and having said unvalved outlet leading into an exhaust manifold means in gas flow communication with one end of a closed heat exchanger means, the other end of said closed heat exchanger means open to said atmosphere, all situated within said air treatment duct; blower means for passage of cold air to be heated in sequence through said air treatment duct and in thermal exchange with said heat exchange means and said combustion chamber and exhaust manifold, providing heated air.
3. A pulsing combustion device of Claim 2 wherein said combustion chamber and said exhaust manifold have extending fins providing higher heat exchange.
4. A pulsing combustion device of Claim 2 further comprising combustion air blower means to a pressurized combustion air conduit at about 3-1/2 to about 7 inches water, a combustion air flow regulator means at one end of said pressurized combustion air conduit controlling combustion air flow to a combustible mixture mixing chamber, means for supplying fuel gas at a pressure of about 2 inches to about 3-1/2 inches water to said mixing chamber, and combustible gaseous mixture supply line means for supplying pressurized combustible mixture from said mixing chamber to said second side of said floating valve member.
5. A pulsing combustion device of Claim 4 having a high pressure tap in said pressurized combustion air conduit, A low pressure tap in said combustible mixture supply line, and control means opening said means for supplying fuel gas only after said pressure is reached in said pressurized combustion air conduit.
6. A pulsing combustion device of Claim 4 wherein said combustion air flow regulator is adjustable.
7. A pulsing combustion device of Claim 2 further comprising combustion air blower means to a pressurized combustion air conduit at about 4 to about 6 inches water, a combustion air flow regulator means at one end of said pressurized combustion air conduit controlling combustion air flow to a combustible mixture mixing chamber, means for supplying fuel gas at a pressure of about 3 inches to about 3-1/2 inches water to said mixing chamber, and combustible gaseous mixture supply line means for supplying pressurized combustible mixture from said mixing chamber to said second side of said floating valve member.
8. A pulsing combustion device of Claim 2 wherein an end of said combustion chamber comprising said inlet for a combustible mixture is removably attached to said elongate combustion chamber.
9. A pulsing combustion device of Claim 8 wherein said end and said combustor chamber are provided with holding flanges extending radially therebeyond with through bores which may be aligned providing passage and securement for assembly bolts.
10. A pulsing combustion device of Claim 8 wherein the inner side of said combustion chamber end defines an enlarged combustible gas inlet chamber.
11. A pulsing combustion device of Claim 1 further comprising combustion air blower means to a pressurized combustion air conduit at about 3-1/2 to about 7 inches water, a combustion air flow regulator means at one end of said pressurized combustion air conduit controlling combustion air flow to a combustible mixture mixing chamber, means for supplying fuel gas at a pressure of about 2 inches to about 3-1/2 inches water to said mixing chamber, and combustible gaseous mixture supply line means for supplying pressurized combustible mixture from said mixing chamber to said second side of said floating valve member.
12. A pulsing combustion device of Claim 11 wherein said combustion air flow regulator is adjustable.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/666,458 US4569310A (en) | 1980-12-22 | 1984-10-30 | Pulsing combustion |
| US666,458 | 1984-10-30 | ||
| US785,433 | 1985-10-11 | ||
| US06/785,433 US4637792A (en) | 1980-12-22 | 1985-10-11 | Pulsing combustion |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1240609A true CA1240609A (en) | 1988-08-16 |
Family
ID=27099468
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000494113A Expired CA1240609A (en) | 1984-10-30 | 1985-10-29 | Pulsing combustion |
Country Status (3)
| Country | Link |
|---|---|
| AU (1) | AU593532B2 (en) |
| CA (1) | CA1240609A (en) |
| DE (1) | DE3584224D1 (en) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4479484A (en) * | 1980-12-22 | 1984-10-30 | Arkansas Patents, Inc. | Pulsing combustion |
-
1985
- 1985-10-24 DE DE8585307691T patent/DE3584224D1/en not_active Expired - Fee Related
- 1985-10-29 CA CA000494113A patent/CA1240609A/en not_active Expired
- 1985-10-29 AU AU49170/85A patent/AU593532B2/en not_active Ceased
Also Published As
| Publication number | Publication date |
|---|---|
| AU593532B2 (en) | 1990-02-15 |
| DE3584224D1 (en) | 1991-10-31 |
| AU4917085A (en) | 1986-05-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4651712A (en) | Pulsing combustion | |
| US4637792A (en) | Pulsing combustion | |
| US4569310A (en) | Pulsing combustion | |
| US4480985A (en) | Pulsing combustion | |
| US4479484A (en) | Pulsing combustion | |
| US4759312A (en) | Furnace system | |
| US4640674A (en) | Pulse combustion apparatus | |
| US4780076A (en) | Power burner | |
| ES2004106A6 (en) | Power gas burner for wood stove | |
| US2715436A (en) | Resonant pulse jet combustion heating device | |
| US5927961A (en) | Multifuel burner with pressurized fuel-holding tank | |
| CN101344249B (en) | Valveless gas fluctuation combustor | |
| US4671056A (en) | Pulse-sonic jet nozzle | |
| RU2293253C1 (en) | Pulse burning boiler | |
| US6161506A (en) | Pulsed air combustion high capacity boiler | |
| US5666944A (en) | Water heating apparatus with passive flue gas recirculation | |
| US4926798A (en) | Process for pulse combustion | |
| US5395230A (en) | High ratio modulation combustion system and method of operation | |
| CA1240609A (en) | Pulsing combustion | |
| CA1240608A (en) | Pulsing combustion | |
| KR100267884B1 (en) | Device for burning waste oil for burner | |
| JPS6287708A (en) | Pulse combustion apparatus | |
| RU2201553C2 (en) | Burner for liquid-fuel combustion apparatuses | |
| RU2808886C1 (en) | Method of liquid fuel burning | |
| KR100268389B1 (en) | A boiler |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |