Patent Application
20100313827
The present invention relates to a boiler that forms part of hot water supply or heating system of a building, and more specifically, the present invention relates to a gas-fired condensing boiler providing improved heat transfer and ultra-high thermal and operating efficiencies.
A typical boiler for use in providing a supply of hot water, or other so-called working fluid, for heating a relatively large-sized commercial or industrial building, for instance, a school, apartment building, office building, or the like, includes an enclosed furnace where a fuel is combusted to produce heat. A tank or pipes filled with water or other fluid extend within an enclosure through or adjacent the furnace so that heat is transferred to the water/working fluid. Typically, the water/working fluid flows through a loop external of the boiler and is returned to the boiler as “return” water/working fluid at a predetermined return water/fluid temperature, is heated as it flows through the boiler enclosure, and leaves the boiler as “supply” water/working fluid to the loop at an elevated temperature. Combustion gases exit the furnace and are exhausted via a flue to ambient atmosphere.
The size or capacity of a boiler is typically expressed in terms of BTUs (British Thermal Units) or BTUH (BTUs per hour). This can also be expressed in terms of MBH (thousands of BTUs per hour). One particular contemplated embodiment of the present invention is primarily directed to boilers producing about 3,000 MBH or smaller, such as within the range of 3,000 MBH to 2,000 MBH. However, it should be understood that the boiler of the present invention is not limited to such range and that such range is provided merely for purpose of example.
The thermal efficiency of a boiler relates to its ability to maximize heat transfer. Thus, it is expressed in terms of percentage and provides an indication of the percentage of heat generated within the furnace that is actually transferred to the water/working fluid as opposed to being lost “up the flue” to ambient atmosphere.
Many boilers compromise thermal efficiency by discharging flue gas at a predetermined temperature above its dew point. The advantage of this is that condensation is prevented from being formed within the heat exchanging portion of the boiler and the collection and discharge of condensate is not required. However, thermal efficiency is greatly compromised.
Another type of boiler known to have fairly high thermal efficiency is so-called “condensing” boilers. A condensing boiler uses heat generated by combusting gas or like fuel within a boiler enclosure to directly heat circulating water and re-absorbs condensed latent heat in exhaust gas to improve thermal efficiency. The boiler converts the latent heat of condensation into useful energy instead of expelling it with exhaust gases.
Water droplets form on the walls and tubes of heat exchangers of condensing boilers. As an example of the amount of condensation produced within a condensing boiler, a typical condensing boiler generating about 100 MBH of heat for one hour will produce about one to two gallons of liquid condensate. This condensed water is required to be collected and discharged from the boiler. The condensation is slightly acidic, typically having a pH of about 3.5 to 4.5, and some jurisdictions require the condensation to be neutralized before disposal.
Although known condensing boilers may be satisfactory for their intended purpose, there is a need for an energy efficient condensing boiler having improvements with respect to maximizing heat transfer and thermal and operating efficiencies thereby reducing energy costs while also meeting air quality requirements with low NOx combustion. Preferably, such a boiler should be able to provide about 3,000 MBH to about 2,000 MBH or other amount of heat for purposes of heating commercial and industrial buildings as well as residential buildings.
According to the present invention, a high-efficiency hot-water boiler for a heating system of a building is provided. The boiler includes a sealed boiler enclosure that contains a furnace area compartment within an insulated sealed casing, a first watertube compartment within a sealed casing, a second watertube compartment within a sealed casing, and an air-to-air preheat exchanger within a sealed casing. A plurality of separate, closely-spaced watertubes extend within each of the furnace area, first watertube and second watertube compartments and provide paths for working fluid to flow through the compartments for purposes of transferring heat to the working fluid. A burner is located within the furnace area compartment for combusting an air/gas mixture and producing products of combustion. The casings include openings for directing the passage of the products of combustion through the enclosure to a flue. The openings extend between the furnace area compartment and the first watertube compartment, the first watertube compartment and the second watertube compartment, and the second watertube compartment and the air-to-air preheat exchanger and are positioned to enable the products of combustion to make a first pass through the furnace area compartment, a second pass through the first watertube compartment and a third pass through the second watertube compartment and then through the air-to-air preheat exchanger to preheat fresh combustion air before being exhausted from the enclosure via the flue.
According to another aspect of the present invention, a burner for a high-efficiency hot-water boiler is provided. The burner includes a hollow, cylindrical, elongate metal fiber burner head having a distal end and a proximal end and an air/gas mixer located adjacent a proximal end of the burner head for uniformly distributing an air/gas fuel mixture within the burner head. The mixer has a central hub and hollow spokes extending radially therefrom. The central hub is adapted to receive a supply of gas and direct it into the hollow spokes, and the mixer defines channels between the spokes through which a supply of combustion air flows transversely through the mixer into the burner head. The spokes have gas outlets in the sides thereof that discharge gas into the flow of combustion air such that the gas is discharged in a direction substantially perpendicular to the flow of combustion air.
According to an additional aspect of the present invention, a two-stage ignition system and method for igniting a burner is provided. The two-stage ignition system uses an ignition flame to ignite a main gas pilot flame which, in turn, ignites said burner. The two-stage ignition system includes an electrically-operated pilot ignition gas valve for providing gas to an ignition tube for creating the ignition flame with a spark igniter. The two-stage ignition system further includes a separate electrically-operated main pilot gas valve for separately providing gas to a main pilot gas divider that exists on only a small portion of the metal fiber burner. During a first period, the ignition flame fueled by the electrically-operated pilot ignition gas valve ignites the main gas pilot flame at the main pilot gas divider which is fueled by the separate electrically-operated main pilot gas valve, and after the main gas pilot flame is ignited, the system automatically de-energizes the electrically-operated pilot ignition gas valve to extinguish the ignition flame. During a second period, gas is introduced into the burner head via a main gas burner supply line, and the burner is fully ignited by the main gas pilot flame. After the burner is ignited, the system automatically de-energizes the electrically-operated main pilot gas valve to extinguish the main gas pilot flame.
The features and advantages of the present invention should become apparent from the following description when taken in conjunction with the accompanying drawings, in which:
A boiler 10 according to the present invention includes an enclosure, or cabinet, 12 best illustrated in FIGS. 1 and 2A-2D. Typically, the boiler 10 is connecting to a loop (not shown) in which water or like fluid is continuously, continually, or intermittently circulated. For example, the loop can include pipes, radiators or the like through which heated water circulates to heat various areas of a building. The loop also includes pipes or the like to return water to the boiler for reheating and recirculation through the loop. Accordingly, the enclosure 12 includes a return inlet 14 and a supply outlet 16 for the re-circulating water.
As shown in the drawings, the enclosure 12 can have a compact, relatively-rectangular configuration, although other configurations are possible. Simply for purposes of example and to provide an explanation of the relative size of one contemplated embodiment of the boiler 10, and not be way of limitation, the enclosure 12 may have a footprint of approximately 12 feet by 3 feet and a height of about 6 feet, and the boiler 10 may weight about 4,000 to 5,000 lbs. Of course, the boiler can be made to greater or lesser dimensions and weight depending upon its intended end use.
Preferably, the enclosure 12 is formed by numerous readily removable access panels 18 to make the interior of the boiler 10 accessible for service and inspection. The modular construction of the boiler also makes it easy to expand or reduce the size of the boiler, as specifically desired by the end user. The furnace area access panels of the boiler 10 are preferably constructed of heavy gauge stainless steel having about two inch thick high-temperature ceramic fiber insulation and are bolted and tightly sealed to the boiler frame. The outer steel surface of the enclosure 12 is preferably made with sixteen gauge and a powder coated finish.
In the illustrated embodiment, a supply nozzle 20 through which heated water is supplied to an exterior loop of a heating system of a building is located at the top of the front 22 of the enclosure 12 adjacent a control panel/display 24 of the boiler 10. Oppositely, a return nozzle 26 through which return water is fed to the boiler 10 is located at the bottom of the rear 28 of the enclosure 12. A drain connection 30 also extends through the rear 28 of the enclosure 12 directly underneath the return nozzle 26 and provides a path for discharging working fluid from the boiler 10, such as required during watertube replacement and/or other boiler maintenance service. A flue connection 32 for venting exhaust combustion gases is located on a top wall 34 of the enclosure 12 and is located adjacent the rear 28 of the enclosure 12. A combustion air inlet 36 for providing ambient air to be ultimately mixed with natural gas or propane and combusted in a burner located within the furnace of the boiler 10 is also located on the top wall 34 of the enclosure 12 adjacent the front 22 of the enclosure 12. A hot water relief valve 38 also extends through the top wall 34 of the enclosure 12. Finally, the side wall 40 of the enclosure 12 includes a flame observation port 42 through which the flame of the burner extending within furnace area of the boiler 10 can be readily viewed.
The inner workings of the boiler 10 are best illustrated in
Turning first to the water or like re-circulating working fluid of the boiler, it is provided as return water at a predetermined temperature via return inlet 14 into a base header 48. The base header 48 is a relative large diameter pipe or manifold that extends substantially horizontally from the rear 28 of the enclosure 12 along the bottom of the boiler toward the front 22 of the enclosure. The base header 48 extends under the furnace area 46 of the boiler and terminates shortly in front of the furnace area 46 adjacent the front 22 of the enclosure.
A plurality of closely-spaced, upstanding watertubes 50 interconnects to the base header 48 and provides a path for the working fluid of the boiler to an upper header 52. The upper header 52 is similar in size and function to the base header 48, except that it extends substantially horizontally along the top of the enclosure 12 and extends through the front 22 of the enclosure 12 to the supply outlet 16.
In the embodiment illustrated in
An example of one of the watertubes 50 located in the furnace area compartment 54 is shown in
The watertubes in compartments 56 and 58 are similar to that illustrated in
For purposes merely of example, the watertube 50 can be made of 316L stainless steel, weigh about fifty pounds or more, and have a constant outer diameter of about 1.5 inch and a constant inner diameter of about 1.25 inch thereby providing a tube wall thickness of about 0.125 inch. Of course, other dimensions can be utilized. The undulating design of the watertube 50 provides the watertube 50 with a needed amount of flexibility to prevent damage from thermal shock and by stresses caused by uneven internal circulation. Thus, an advantage of the above referenced watertube design is that it can be used with forced hot water heating systems designed for higher working fluid temperatures and greater temperature drops.
Preferably, each watertube is individually replaceable, and replacement can be accomplished without welding or rolling. Also, preferably the ends, 60 and 62, of the watertubes 50 are formed (i.e. not provided by way of separately-manufactured fitments welded to the ends of the tube) with circumferential flanges 68 and a reduced outer-diameter throat section 70 adjacent the flanges 68 so that the watertubes can be closely-spaced where they are connected to the headers, 48 and 52. For instance the outer-diameter of the circumferential flange 68 can be equal to or less than the outer-diameter of the intermediate section 64 of the watertube. This enables the intermediate undulating sections 64 to be closely spaced together within the compartments, 54, 56 and 58, further enhancing heat transfer and operating efficiency.
As stated above, fresh combustion air and the products of combustion also follow a path through the boiler 10. Fresh combustion air is initially drawn into the enclosure 12 through the combustion air inlet 36 via the action of an adjustable speed air blower 72. As best illustrated in
The purpose of the combustion air preheat exchanger 76 is to further preheat the combustion air via heat exchange with the spent hot flue combustion products just before the combustion products are exhausted from the boiler 10 up the flue. Accordingly, as the fresh combustion air passes through the combustion air preheat exchanger 76 from the inlet 74 to an outlet 78 of the exchanger 76, the temperature of the fresh combustion air is further increased. This preheating of the fresh combustion air takes place entirely within the confines of the enclosure 12 of the boiler 10.
The preheated fresh combustion air passes through the outlet 78 of the exchanger 76 into an air duct 80 that extends adjacent the top of the boiler over the compartments 54, 56 and 58 to a burner box 82. At this point, the preheated fresh combustion air is mixed with natural gas or propane from a main gas supply line 84 via a gas/air mixer 86. This gaseous fuel mixture is provided into a burner combustion head 88 and is burned to generate heat. As shown in
The furnace area compartment 54 has an opening 90 adjacent the base of the compartment 54 that provides a path for the combustion products to flow into the adjacent compartment 56. Thus, after making one pass through the furnace area compartment, the combustion products make one pass through compartment 56. In compartment 56, the combustion products flow in a generally upward direction through the close array of watertubes 50 extending within compartment 56 transferring heat to the working fluid within the watertubes 50 which thereby further reduces the heat of the combustion products.
The compartment 56 has an opening 92 adjacent the top of the compartment 56 that provides a path for the combustion products to flow into the adjacent compartment 58. Thus, after making a pass through compartment 56, the combustion products make a pass through compartment 58. In compartment 58, the combustion products flow generally downward through the close array of watertubes 50 extending within compartment 56 transferring heat to the working fluid within the watertubes 50 which thereby further reduces the heat of the combustion products.
The compartment 58 has an opening 94 adjacent the base of the compartment 58 that provides a path for the combustion products to flow into the combustion air preheat exchanger 76. Thus, after making a pass through compartment 58, the combustion products make a pass through the combustion air preheat exchanger 76 where heat is transferred from the combustion products to the fresh combustion air as discussed previously. This further reduces the temperature of the combustion products which are then directed up the flue to ambient atmosphere.
Thus, in summary, fresh combustion air travels the length of the enclosure 12 twice (from air inlet 36 to blower 72; then through exchanger 76 and duct 80 to burner box 82) so that it can be preheated to a desired temperature before being mixed with natural gas or propane. After combustion of the air/gas fuel mixture, the products of combustion make one pass through the furnace area compartment 54, one pass through watertube compartment 56, and one pass through watertube compartment 58 before passing through the combustion air preheat exchanger and then up the flue.
The above described arrangement of watertubes, watertube compartments, preheating of combustion air, and combustion products flow through the boiler permits the boiler to be of high efficiency. For example, the boiler 10 can achieve a minimum of 90% thermal efficiency at standard loop operating temperatures in which the return water enters the boiler at 160° F. and leaves the boiler at 180° F. Such a boiler can reach 98% thermal efficiency with lower return temperature systems.
Also, by way of example, the fresh combustion air preheating arrangement described above for the boiler 10 can raise the temperature of fresh combustion air at ambient temperatures to about 200° F. to 250° F., and the temperature of combustion products exhausted from the boiler 10 up the flue can be at a temperature of about 130° F. to 180° F.
The dew point for flue gas is 132° F. The flue gas will be reduced to this temperature when working fluid within the boiler is lower than 132° F. In this case, condensation forms only on the exterior surfaces of the watertubes 50 where the film temperature becomes less than the dew point of the flue gas. The boiler 12 includes condensate pans below each compartment to collect the condensate and a condensate drain to provide a path for drainage of the condensate from the boiler.
When the boiler 12 is operated at boiler water temperatures greater than the dew point of the flue gas, condensation will continue to condense in the air-to-air exchanger 76 where the fresh combustion air temperature is below the dew point of the flue gas. The condensation within the air-to-air exchanger 76 enables high thermal efficiencies to be achieved by the boiler 12 despite boiler water temperatures being greater than dew point of the flue gases.
Another novel aspect of the present invention relates to a flame ignited gas pilot ignition assembly which provides a two stage pilot ignition system. The gas pilot ignition assembly is shown in
During a “trial for ignition” period, the electrically operated pilot ignition gas valve 102, a spark igniter 106, and the electrically operated main pilot gas valve 104 are electrically energized. Thus, gas is permitted to flow through piping from the electrically operated main pilot gas valve 104 to a main pilot channel divider 108 (see
The electrically operated pilot ignition gas valve 102 and the spark igniter are de-energized after the first half of the “trial for ignition” period. This extinguishes ignition flame 114 and leaves main gas pilot flame 116 on for the second half of the “trial for ignition” period.
After the “trial for ignition” period, the “main burner trial” period begins. This period begins when gas is introduced into the main gas burner 44 via a main gas burner supply line 84. This supply of gas is ignited within the burner combustion head 88 with the main gas pilot flame 116.
After the first half of the “main burner trial” period, the electrically operated main pilot gas valve 104 is de-energized and thereby extinguishes the main gas pilot flame 116. After the second half of the “main burner trial” period, the burner 44 is released for normal operation during the run period of the burner 44. The air/gas mixture burns on the surface of the metal fiber burner combustion head 88.
Another aspect of the boiler of the present invention is the design of the air/gas mixer 86 of the burner 44. As best illustrated in
The portion of one of the spokes 122 shown broken away in
Accordingly, the present invention provides an ultra high-efficiency gas-fired forced-draft condensing hot water boiler having an improved watertube arrangement, improved combustion air preheating, improved flame ignited pilot assembly, and improved air/gas mixer. The combustion products make three distinct passes through sealed-casing watertube compartments and an additional pass through an air-to-air heat recovery exchanger before being directed up the flue. The air-to-air heat recovery exchanger is contained entirely within the enclosure of the boiler. The watertube assembly can include a single base header, a single upper header and a plurality (such as thirty-nine) of closely-spaced, flexible, bent (i.e. undulating) watertubes extending therebetween. Condensation is permitted to form on the outer surfaces of the watertubes and is collected and discharged. Finally, the burner can safely be ignited via a unique two-stage pilot ignition system, and combustion air and gas (i.e., natural gas or propane) can be uniformly distributed within the burner head by a unique wagon-wheel mixer.
While a preferred boiler and components and systems thereof have been described in detail, various modifications, alterations, and changes may be made to the present invention without departing from the spirit and scope of the present invention as defined in the appended claims.
