CONVECTOR HEATING APPARATUS

Abstract: Heating apparatus for heating an environment, which apparatus comprises one or more heat exchange conduits (A, B, C, D, E, F, 6, 8) for location in the path of a flow of heat (F1 - F2), and air flow inducing means (4) for inducing a flow of air in the or each said conduit, the or each said conduit being adapted to carry air into, through and out of a said heat flow path to a said environment (2), the arrangement being such that, in use, air within the or each said conduit progresses from a cooler to a hotter part of a said heat flow path; where preferably said heat exchange conduits take the form of parallel banks of tubes.

Description: CONVECTOR HEATING APPARATUS This invention relates to convector heating apparatus, particularly of the type which makes use of heat from existing heating or cooking apparatus. Open fires, closed fires, boilers, cookers (solid fuel, oil or gas), ceiling mounted radiant gas heaters and etc, loose valuable heat to the outside atmosphere without the benefit of all the heat generated having contributed to the inside atmosphere of the home or workplace. Heat is transmitted by three means; Radiation, Convection and Conduction. Most of the heat transmitted to the room from an open fire is by radiation. No convected heat emits from an open fire - it cannot. All the convected heat and most of the conducted heat - which conducted heat in turn transfers to convected heat in the main as air passing over the fire surrounds draws on that heat and takes it away up the flue - is lost up the flue and in turn to the outside atmosphere. All fires - unless supplied with air for combustion in a sealed ducted source from the exterior - actually lower room temperature for some time after starting up. An open fire on an exterior wall is at best 10% efficient, on an interior wall is at best 20% efficient. A free standing closed solid fuel fire is at best 30% efficient. Solid fuel, oil or gas cookers are at best 53% efficient. Ceiling mounted radiant gas heaters are at best 30% efficient, and wall mounted rad iant/convector gas heaters are at best 50% efficient. Solid fuel, oi l or gas boilers are in the 50% - 60% efficiency range with the most efficient being a very low output gas boiler in the region of ' 7k% efficiency. These figures take into account all the heat generated which actually finds its way first to the interior including that which bleeds through the linings and structure of the flue to the interior. The remaining percentage is the heat energy which is lost to the outside atmosphere without benefit to the purpose for the heating system - this is the heat lost up the flue in the form of the convected heat generated in the s-ystem, and in turn a part of that convected heat which is converted to conducted heat and lost through the exterior lining and structure of the flue. An object of this invention is to provide ^ apparatus which makes use of the otherwise wasted heat and put it back to the interior. According to a first aspect of the present invention there is provided a convector heating apparatus for heating an environment, which apparatus comprises one or more heat exchange conduits for location in the path of a flow of heat, and air flow- inducing means for inducing a low of air in the or each said conduit, the or each said conduit being adapted to carry air into, through and out of a said heat flow path to a said environment, the arrangement being such that, in use, air within the or each said conduit progresses from a cooler to a hotter part of a said heat flow path. Preferably said one or more heat exchange conduits comprises one or more first banks of parallel tubes extending into a said heat flow path, the inlets of said tubes being operatively connected to said air f 1ow- induc ing means, and one or more second banks of parallel tubes connected directly or indirectly to the outlets of said first tubes and extending out of said heat low path. Preferably said one or more heat exchange conduits comprises a plurality of parallel tube elements which provide a sinuous flow path for air. Preferably the or each heat exchange conduit is in the form of a continuous tube. According to a second aspect of the present invention there is provided a convector heating apparatus comprising a plurality of banks of tubes for parallel spaced location in the path of a flow of heat each bank being in i nte ' rcorrrnunicat ion with the or each end adjacent bank by passage means and so disposed that the bank nearest the heat source is upstream of the heat flow and the bank remote or remotest from the heat source is downstream of the or each other bank, and air 1ow- induc ing means for inducing a flow of air into the bank or banks of tubes at the downstream end of the heat flow, to pass the air through successive banks, provided to the upstream bank or banks nearest the heat source from which the air exits into a room or other enclosed area, the air as it enters the downstream bank or banks of tubes being relatively cool and being gradually heated as it passes through successive banks of tubes to exit at the upstream bank or banks of tubes at a higher temperature. Preferably, where more than two banks of tubes are provided, the spacing between adjacent banks decreases towards the downstream bank. Preferably the banks of tubes are formed as a unit and are located in a containment member mounted on, in or around the heat flow. Preferably the air inlet or inlets to the or the most downstream bank" or banks of tubes, being operatively connected to said air flow-inducing means, and the air outlet or outlets from the or the most upstream bank or banks of tubes communicate with a corrmon room or other enclosed area whereby cool air is withdrawn therefrom into the banks of tubes and heated air is returned thereto. Preferably said tubes in banks downstream of the two most upstream banks progressively reduce in wall thickness from two said upstream banks. - - Embodiments of the present invention will now be described, by way of example, with reference to the accompanying drawings, in which: - Figure 1 is a front view of a convector heating apparatus according to a first embodiment: Figures 2 and 3 are an exploded view of the apparatus shown in Figure I; Figures , 5 and 6 are exploded views of the apparatus according to a further embodiment. Figures 7, 8 and 9 are diagraπmat ic views showing the flow of heat from existing heating or cooking apparatus and the flow of air in the banks of tubes of the apparatus according to the invention. Figure 10 is a schematic elevation of a third embod iment : Figure 11 is an end elevation of Figure 10; Figure 12 is a partial cross section of Figure 10 to a smal ler scale; Figure 13 is a plan view of Figure 10; Figure 1 is a schematic elevation of part of the apparatus shown in Figures 10 to 13; Figure 15 is an end elevation of Figure 1 ; Figures 16 a-nd 17 show further illustrations of heat flow past the banks of tubes and air flow in the tubes ; Figure 18 is a schematic elevation of Figures 16 and 17 illustrating a fourth embodiment of the invent ion; Figure 19 is a schematic cross section of a fourth embodiment of the invention; and Figure 20 is a plan view of a chimney breast for location therein of the apparatus of the fourth embodiment . Referring firstly to Figures 1 to 6, the room air flowing into the system to be heated is 1 and the heated air returning is 2. Figure 1 is an open fire burning coal, wood, peat, gas (artificial logs or coal), and etc., with the unit Figure 3, fitted to the top of the open surround by a containment 19 and 20 - - figure 2 as if a drawer in its slider to a cabinet. Figure 4 shows a unit fitted to the after flue pipe of a closed fire. Figure 5 shows a unit fitted to the after flue pipe of a solid fuel, oil or gas fired cooker/boi ler . Figure 6 shows a unit fitted to the flue pipe in the chimney breast above an open fire. Other applications of the system may be; above a ceiling mounted radiant gas heater in a factory or warehouse. A unit with the inlet 1 and the outlet 2 on the opposite side of the wall to the heat source - e.g. in Figure 6, and the inlet 1 and the outlet 2 may be on opposite sides of the wall to each other, e.g. where emission is required in an adjoining room or hallway or into an adjacent cupboard for use as an airing cupboard. A unit may or may not have a supply of ducted fresh air from the exterior supplied to the inlet 1 and a unit may or may not have air from outlet 2 ducted away to some distant use. Ail applications of the system dependant on the requirements of the user. The working principles of the system are shown from Figure 7 and Figure 8 which shows banks of tubes A, B, C, D, E, F, through which may be forced air say from the room. The flow of the air through the unit is in the form of from the room 1 through the upper banks of tubes 6 down through the coπmun icat ing chamber 7 and back along the lower banks of tubes 8 and return to the room 2. 25 is a seperating membrane. Flue gases from the heat source (fire etc.) rise up through the array of tubes at Fl and exit at F2. As the flue gases travel through the banks of tubes they heat up these tubes which in turn pass their heat on to the air passing through the tubes , Figure . The passage of air through the tubes is in overall effect in reverse order to that of the passage of the flue gases. Cool room air entering the system meets cooled flue gases leaving the system in the upper banks of tubes. This room air is gradually heated as it passes through the system, the reverse being the case for the flue gases, and meets the hotter flue gases entering the system in the lower banks of tubes as it - the room air - then leaves this harmonious system. Figures 10, 11, 12, and 13 depict a unit in schematic elevation, end view, partial cross section and plan view, which unit may be fitted to the upper part of the opening to an open fire (as depicted in Figures 1 and 3) with the containment unit depicted in Figure 14 and 15 (as depicted in Figure 2). Air is shown entering from the room 1 through a probable filter 3 and into the unit through the fan or fans 4, along a coπmunicat ion duct 5 and into the banks of tubes 6 (Figure 12, one tube drawn for clarity) and into the corrmun icat ing duct 7 and down and back along the banks of tubes 8 (Figure 12, one tube drawn for clarity) and exiting into the room 2. - & - In the typical system with banks of tubes A, B, C, D, E, F, there may be a unit spacing horizontally between tubes of d for diameter, and a spacing between F and E which is less than the spacing between E and D which is less than the spacing between D and C which is less than the spacing between C and B which is less than the spacing between B and A. The net effect of this is that the spacing X between tubes from one bank to another and through which passes flue gases from Fl to F2, this spacing X is gradually reduced as the flue gases approach the upper banks of tubes. The flue gases enter the system Fl and pass through the spacing X between banks B and A and heat is given up to the tubes contacted (Figure 9). The flue gases - now reduced in temperature - travel on to spacing X between banks C and B which is smaller than that at B and A and which squeezes the flue gases and increases the flue gas pressure at this point, above that which it would have been had the flue gases met a spacing X between banks C and B the same as the spacing X between banks B and A. From gas law P.V/T is a constant this increase in flue gas pressure has the effect of raising the flue gas temperature as it passes through spacing X, and by the raising of the flue gas temperature at that point effecting an increase In the heat exchange between the flue gases flowing round the tubes and the air flowing through the tubes. As the volume of flue gases remains a constant the flue velocity through spacing X is thereby increased. This process is repeated again and again through each spacing X at each juncture of banks of tubes until the flue gases leave the system F2 much reduced in temperature, and more so - reduced in temperature - than had the flue gases merely passed through a system with the spacings X a constant, and with this overal l effective throat system having increased flue velocity to such an extent as to negate the possibility of back puff into the heat source. The gauge thickness of the tube wall (Figure 9) 26, in the two lower banks A and B are of equal gauge and of such thickness as to minimize their destruction from heat contact. The system may be further enhanced by the tubes in the upper banks above A and B being constructed of a gauge wall thickness lighter than that of tubes A and B and reducing in gauge wall thickness to the lightest being in the uppermost bank. This would have the effect of maximizing the rate of transfer of heat to the room air passing through the tubes which room air is quenching the inner wall of the tube of the heat conducted through the tube wall thickness.. The net effect of this being maximum heat gain in the room air and maximum heat loss in the flue gases, i.e. maximum efficiency in the system. A unit may comprise any number of tubes from two upwards depending on the system required for a particular application. Figures 16 and 17 are further interpretations of the previously stated system whereby flue gases enter at Fl and exit at F2 through a greater number of tubes than depicted in Figure 7, with room air entering at 1 and flowing through tubes 6 into and down communicating duct 7 and through tubes 8 and down communicating duct 9 and through tubes 10 and down conrmunicat ing duct 11 and through tubes 12 and exiting into the room 2. Figure 18 is a schematic elevation of Figures 16 and 17 with flue gases entering Fl and exiting F2 with room air entering at 1 and exiting at 2, for a possible installation to a chimney breast as depicted in Figure 6 with a plan view of the containment depicted in Figure 20, as 19, having flange 20 for bolting the unit in a gas proof seal, with the unit taking heat from the gases in a standard wall flue 21. Further adaptations of this unit are as previously stated - into an airing cupboard and/or another room and etc. Figure 19 is a schematic cross section of a possible system to a boiler or cooker or free standing heater as depicted in Figure 4 and 5 with further banks of tubes to previously stated, - through tubes 12 - and down- communicating duct 13 and through tubes 14 and down communicating duct 15 and through tubes 16 and exiting into the room 2. The containment here is an open sided box 17 with flange 20 for gas proof seal and flue connector 18 at either end of the box for connection to after flue pipe of the heat source. A further adaptation may be as in Figure 1 where the fans housings 22 may be fitted at the bottoms of legs - as conrmunicat ing ducts, vertically to and with duct 5, immediately in front of 23 - and thereby allowing the open fire to be increased in size forward of its original surround 23 and with a larger grate fitted forward of the original at 24. The unit Is removable from its containment structure thereby providing accessibility for the cleaning of the flue and also the unit itself which may be immersed, e.g. in a bath of liquids capable of dissolving any solid matter adhering to the unit. The unit could be constructed of materials such as stainless steel for appearance and freedom of maintenance and, e.g. zinc galvanized or electroplated steel tubes etc, and which unit by its removability may be maintained by redipping etc, if required. Central heating is generally represented by radiators supplied with hot water from a boiler system through pipes, and over which radiators - should be referred to as convectors as radiation does not take place without a 200degC temperature difference between the radiator and the radiated - flows room air convectirrg away the heat to room furniture and etc, and generally raising room temperature. With the unit fitted to an ordinary open fire, central heating is achieved without the cost and space of an installation of boiler, pipes or radiators. Air flowing through the unit at temperatures well in excess of lOOdegC from a fan rated at say 100 CFM (cubic feet per minute) will be taken through or under doors, through Building Regulation required room ventilators and/or by other means - as depicted - to all parts of a standard sized home, and in a short space of time drastically improve the temperature of that home. e.g. providing forced air convection from an open fire with 100 CFM air at lOOdegC to a 1200 sq ft home with an 8 ft stud height could increase the average air temperature to 25degC (77degF) from OdegC in ' 1 lOOdegC X 100 CF per Min X 60 Min/Hr 25degC 1200 X 8 CF Given no losses. = 0.4 Hrs. / 24 Mins. The cost of running a 100 CFM fan is 1 unit of electricity (6.38pence) per 40 Hrs, with a life expectancy of the fan between 25,000 - 30,000 Hrs (1250 days) continuous running. The apparatus as hereinbefore described provides filtered particle free air and heated (depending on the fire built up) to temperatures well in excess of . LOOdegC, which intensely heated air within the unit provides a bacterium and virus destruct - the vast majority of these being destroyed at 121degC - environment, further benefiting the interior environment of the home or workplace in providing all round warmth from an open fire - whereas without the apparatus ones front was warm and ones back was cold - and in providing a de-humidified (condensation loss), and well ventilated atmosphere. Although in the embodiments described the heating apparatus of this invention operates in counter current fashion by moving air from a cooler more distant region of the heat flow path to a hotter region of the heat flow path nearer to the source of heat, it is to be understood that in other embodiments the apparatus may be arranged to utilize a temperature gradient existing across a heat flow path. It is also to be understood that it is not neccessary for the heat exchange conduits to be in the form of banks of tubes. It could for example be in the form of a single generally rectangular cross section duct, traversing the heat flow path and, for example, provided with bores therethrough to allow passage of flue gases. - - I 3 Testing a unit of four banks of parallel spaced tubes in an open fire of dimensions 24 Inches wide by 18 Inches deep and using one fan of 100 CFM rating gave the following results in outputs: " est Output Eff iciency 1, 220 deg C 78% 2, 66 deg C 83% 3, 102 deg C 83% 44,, 118855 ddeegg CC 84% 5, 104 deg C 82% The unit generally performed in the region of 80% efficiency, with the slight discrepancies in the test results due to the fluctuation of flame strength resulting from the burning of wood only, for the results obtained in all tests. Further tests were performed for actual output readings, and with Test 6 of the unit fitted into the top of an open fire of average burn; actual output from the unit registered 538,000 BTU. During testing it was recorded that temperature some 40 feet distant from the unit, and seperated from the open fire by partitions, reached 0.8 deg C higher than at positions 4 Feet either side of the unit. It was also recorded that during all tests the unit remained cool to the touch, with Test 4 recording only 32 deg C on top of the unit.

Claims: CLA IMS i Heating apparatus for heating an environment, which apparatus comprises one or more heat exchange conduits (A, B, C, D, E, F, 6, 8) for location in the path of a flow of heat (Fl - F2), and air flow- inducing means (4) for inducing a flow of air in the or each said conduit, the or each said conduit being adapted to carry air into, through and out of a said heat flow path to a said environment (2), -the arrangement being such that, in use, air within the or each said conduit progresses from a cooler to a hotter part of a said heat flow path. 2 Apparatus according ,to Claim 1, wherein said one or more heat exchange conduits comprises one or more first banks of parallel tubes (6) extending into a said heat flow path, the inlets of said tubes being operatively connected to said air flow-i-nducing means (4), and one or more second banks of parallel tubes (8) connected directly or indirectly to the outlets of said first tubes and extending out of said heat flow path (Fl - F2) . 3 Apparatus according to claim 2, in which there is provided a single said first bank of tubes (6) and a single said second bank of tubes (8). 4 Apparatus according to claim 2, in which there is provided two said first banks of tubes (6, 10) and two said second banks of tubes (8, 12). 5 Apparatus according to claim 2, in which there is provided three said first banks of tubes (6, 10, 14), and three said second banks of tubes (8, 12, 16). 6 Apparatus according to claim 1, wherein said one or more heat exchange conduits comprise a plurality of parallel tube elements (6, 8, 10, 12, 14, 16) which provide a sinuous flow path (1 - 2) for air. 7 Apparatus according to claim 6, in which the flow of air is arranged to change its direction two or more t imes . 8 Apparatus according to any one of the preceeding claims, in which the or each heat exchange conduit is in the form of a continuous tube. 9 Apparatus according to any one of claims 1 to 7, in which the or each conduit is in the form of serial tubing elements (6, 8, 10, 12, 14, 16) connected via one or more plenum chambers (-7,- 9,- 11). 10 Apparatus according to any one of the preceeding claims, which is adapted to subject gases in the heat flow path (Fl - F2) to compression, thereby to increase their temperature and hence increase the heat exchange between the gases and the or each condui t . 11 Apparatus according to claim 10, which is adapted to subject a given volume of said gases to greater compression in a downstream part of the heat flow path (Fl - F2) than they in an upstream part of the heat flow path (Fl - F2) . 12 Apparatus according to any one of the preceeding claims, in which the wall thickness of the or each said heat exchange conduit is less in a downstream part of said heat flow path (Fl - F2) than is said wall thickness in an upstream part of said heat flow path (Fl - F2). 13 Apparatus according to any one of the preceeding claims wherein the or each heat exchange conduit comprises a plurality of tube elements (6, 8, 10, 12, 14, 16), the spacing (E - F)(D - E) between adjacent tubes being less in a downstream part of the heat flow path than that (C - D)(B - C) between adjacent tubes in an upstream part of the heat flow path. 14 Apparatus according to any one of the preceeding claims, wherein said air flow- indueing means comprises a compressor or fan (4). 15 Apparatus according to any one of the preceeding claims, wherein said air f low-Inducing means includes a filter (3) for filtering air entering the apparatus. 16 Apparatus according to any one of the preceeding claims, which is adapted to take in air from a room environment (1) and to return heated air to the same room environment (2). 17 Apparatus according to any one of claims 1 to 15, which is adapted to take in air from one environment a ' nd to deliver heated air to another envi ronmen . 18 Apparatus according to any one of the preceeding claims, which includes a housing or containment member (17, 19) for containing components of said apparatus.

Inventors: WARWICK DEAN MABIN, WARWICK, DEAN, MABIN
Applicants: WARWICK DEAN MABIN, WARWICK, DEAN, MABIN
Application year: 1987
Main classification: F24B7
IPC codes: F24B1, F24B7, F24H3, F28D21