RECIPROCATING HEAT EXCHANGER

Abstract: A heat exchanger for reclaiming energy from an exhaust airstream (H) includes a porous metal element (20) suitable for absorbing heat from the exhaust airstream (H), means for reciprocally moving the porous element (20) back and forth transversely to the exhaust airstream (H), an inlet duct (8) for receiving the exhaust airstream (H) and directing it through the porous element (20) to an outlet duct (10), and reclaiming air blower means (34) for delivering two heat-reclaiming airstreams (R) through the porous metal element (20), one on either side of the exhaust airstream (H) for drawing said airstream (R) through said porous element (20).

Description: The invention relates to an air-to-air heat exchanger according to the first part of claim 1 . Such air-to-air heat exchangers reclaim energy from, e.g. the air exhausted from heated or cooled buildings. The exhaust from a typical combustion furnace or other heating unit may contain of the order of one third of the energy supplied to the furnace; thus, tremendous losses of energy occur unless energy is reclaimed from the exhaust airstream. Similarly, in airtight buildings where it is desired to exhaust foul air to the ambient and pump fresh air into the building, there is a need for a more effective air-to-air heat exchanger, to reclaim more of the energy from the exhaust air. Efforts have been made to reclaim energy from exhaust airstreams. A heat recovery wheel has been known since the 1970s from Energy Conservation Through Heat Recovery (NORTHERN NATURAL GAS CO.), passing the exhaust airstream through one half of said porous heat-absorbing wheel; incoming air is passed through the other half; the wheel slowly turns, transferring heat from the exhaust airstream to the incoming air. Such wheels tend to be very large in size and are typically used in balanced systems where the incoming air stream has the same volumetric flow rate as the exhaust airstream (e.g. the airtight building example). When the exhaust airstream contains undesirable gases such as products of combustion, the undesirable gases have been purged from the heat recovery wheel to prevent them from being blown back into the building with the incoming air. A pie-shaped purging section at the boundary between the exhaust airstream and the incoming airstream has been employed, in combination with pie-shaped compartments in the wheel, to redirect back through the heat recovery wheel and into the outgoing exhaust incoming air that flows into the pie-shaped section. A heat exchanger according to the first part of claim 1 is described in GB -A- 220 867 (PERRY) (of 1924 ), namely a regenerator which is particularly applicable for the pre-heating of air to be used in the combustion of fuel in furnaces, the pre-heating of the air being effected by the waste heat from the furnace in which the pre-heated air is employed. The regenerator has an inlet for hot air from a furnace and which exits through an outlet. An inlet is provided for air to be heated which passes into an outlet. The hot air and air to be heated both pass through hollow rectangular casings, which are divided into a plurality of vertical compartments by partitions which are parallel to the direction of flow of the air and heating medium. The vertical compartments are filled with heat absorbing material, such as corrugated metal plates or sheets that extend from top to bottom of the casings and are placed parallel to the partitions. Additional rectangular casings are provided which are jarred or shaped by the movement of the casing so that any soot that has settled on any filling is taken off and falls into a receiver, the casings being open at their upper and lower parts for this purpose. At certain points where there is a possibility of leakage between the airduct and the ducts for the heating medium, packaging (such as a metal brush) is used. The technical p r o b l e m of the invention regarding this prior art is mainly to insure the separation of first airstream and reclaiming streaming air along the movement of the heat absorbing means so that mixing of the two different airs is prevented. The s o l u t i o n to this problem is accomplished by the characterizing part of claim 1 . The subclaims go further in specifying the invention. Preferred embodiments include those having any or all of the following features: (a) By the partitions of the porous element the purging airstream may be isolated from the reclaiming airstream. (b) The purging airstream is ambient air. (c) The purging airstream is a portion of the reclaiming airstream. The invention provides improved energy recovery in a compact, easily manufactured, easily serviced device. The improvements make energy recovery from exhaust gases suitable for applications for which prior exhaust gas reclaimers were impractical, e. g. on the exhaust of overhead heaters in industrial buildings, and on home furnaces. Alignment and balancing difficulties that can result with the heat recovery wheel are avoided. The heat exchanger according to the invention can be installed in any orientation (although power is minimized if the support rods are horizontal); by contrast, the heat recovery wheel is installed in a vertical orientation. The heat exchanger according to the invention also provides better uniformity of airflow through the porous element because the compartments can be rectangular; in the heat recovery wheel, the compartments are pie shaped, and flow is limited through the narrow portions of the compartments near the axis of rotation. The invention has application in summer as well as winter; energy can be reclaimed from cooled air exhausted from air conditioned buildings. The invention also has application to exhaust airstreams from hospital environments where it is necessary to purge bacteria from the exhaust. A plurality of ways of carrying out the invention is described in detail below with reference to d r a w i n g s , namely: Fig. 1 is a perspective view of the preferred embodiment of the invention, Fig. 2 is a cross-sectional view, somewhat diagrammatic, taken horizontally through Fig. 1. Figs. 3A, 3B, 3C are three diagrammatic views of three positions of the continuous chain drive and cam-follower used to reciprocate the porous metal element. Figures 4A, 4B, 4C and 4D show diagrammatically four stages within one full cycle of the reciprocating porous metal assembly. Shown in the figures is a reciprocating energy reclaimer with exhaust inlet duct 8 (6" (15 cm) diameter) for receiving heated exhaust gases from a gas furnace or other clean-burning heating unit. The exhaust gases pass through porous metal member 20 supported in surrounding frame, which is divided into twelve identical compartments 24 by metal partitions 25; each compartment is 1.5" (3.8 cm) wide, 2 7/8" (7.3 cm) deep, and filled with 1.5 oz. (42 g) of a heat-absorbing, porous metal mesh. The mesh is 2.5" (6.4 cm) wide tubular, knitted aluminium, crimped at a 45° angle (available from ACS Industries, Woonsocket, R.I., U.S.A.), and folded in serpentine fashion inside each compartment. The exhaust gases transfer their heat to the porous metal member 20, and exit through outlet duct 10 in which there is located exhaust fan 22 driven by motor 23. The porous metal member 20 and frame are supported for reciprocating motion by four linear ball bearing assembles 12, two at each end (only two of four show in Figure 1), that ride on linear rods 14. Movement of the porous member 20 is controlled by gear-drive motor 16, which drives continuous chain 17 around sprockets 18, 19 (Figures 1 and 3A-3C). Cam-follower 30, which is attached to chain 17, drives U channel 32, which is securely fastened to porous metal member 20. As the cam-follower 30 attached to continuous chain 17 is driven away from the gear motor, the porous metal member 20 is moved to one extremity of its traverse (Figure 3A). When the cam-follower reaches the extremity of its travel on the chain 17, the cam-follower repositions itself in the U channel to drive the porous member 20 in the opposite direction (Figures 3B and 3C). Reclaiming air blowers 34 direct reclaiming air through ducts 36 (3.5" (8.9 cm) wide) into the porous metal member. The reclaiming air ducts 36 are separated from the exhaust outlet duct 10 by a plate 38 (1.0" (2.5 cm) wide) in the plane of the cross section of Figure 2). Another plate 28 (1.75" (4.4 cm) wide) in the plane of the cross section of Figure 2) positioned on the opposite side of the porous member 20 acts as an air barrier, and in conjunction with plate 38 accomplishes purging of combustion gases from each compartment prior to energy reclaim. The reciprocating member is divided into twelve compartment 24 so that each compartment, as it passes from the exhaust airstream into a reclaim airstream, temporarily occupies the position shown at 26 in Figure 2. One side of the compartment straddles the discharge of the reclaim blower and the exhaust duct, while the other side of the compartment is sealed off by air barrier 28. As a result, residual combustion gases in this compartment are quickly and positively expelled by purge air P moving from the reclaim blower through the compartment to the exhaust. High temperature silicone seals are installed around the porous metal member to prevent leakage between the member and walls 28, 38. Exhaust fan 22 simultaneously draws hot exhaust gases into the metal mesh 20 and draws low temperature toxic fumes out the exhaust flue. Figures 4A to 4D illustrate the reciprocating movement of the porous metal member 20. In Figure 4A the left-most four compartments 24a-24d are being heated by exhaust gases H. In Figure 4B these compartments have moved out of the path of the exhaust gases H; compartments 24a has already fully passed once through the reclaiming airstream R, compartments 24b and 24c are in the reclaiming airstream, and compartment 24d is in the purging position. In Figure 4C all four of compartments 24a-24d have made one pass through the reclaiming airstream. In Figure 4D the same four compartments are making their second pass through the reclaiming airstream. All of the compartments, except the middle two, 24f, 24g, make two complete passes through a reclaiming airstream R for each pass through the heated exhaust gases H. The middle compartments 24f, 24g make a single pass, but they pause while exposed to the reclaiming air when the porous member 20 reversed direction, thus lengthening their exposure to the reclaiming air. Home and industrial combustion heating units typically exhaust to the atmosphere approximately one third of all input energy (BTUs or kJ) fed the heating unit. That lost energy is recovered by passing reciprocating porous metal member 20 through the heated exhaust airstream H, and reclaiming the heat from the porous metal member by passing reclaiming air R through the member. A positive exhaust fan 22 is positioned on the discharge side of the exhaust airstream (200 cfm (6.0 m/min) for a 100,000 BTU/hour (29 KW) furnace). The front portions of the porous metal member 20 (i.e. the portions nearest the feed of heated gases) will absorb virtually all the exhaust heat, and reach a temperature equal to the temperature of the exhaust gases, as the reciprocating porous metal member 20 passes through the exhaust airstream. The metal member is then subjected to a high volume-high velocity (465 cfm or 13 m/min) r eclaim blower forcing reclaiming air R through the porous member. The reclaiming air causes the temperature of the porous member on the exhaust side to be maintained equal to the temperature of the air discharged by the reclaim blower (typically room temperature). The greater the volumetric flow rate of the reclaim air (as compared to the exhaust), the smaller the porous member 20 needs to be. It is preferred that the reclaim airflow for each reclaim airstream be from 1 to 4 times the exhaust airflow, and most preferably 2 to 2.50 times. Because the majority of compartments 24 are exposed twice to reclaim air for each pass through the exhaust airstream, the ratio of total reclaim airflow to exhaust airflow for these compartments is twice the numbers just given, i.e. preferably from 2 to 8 or most preferably 4 to 5. The invention allows up to 95% of the exhaust energy (BTUs or kJ) to be reclaimed from any hot exhaust stack. Installation requires removing a small section of the exhaust duct and securely fastening the remaining ducts to the inlet and outlet ducts 8, 10 of the heat exchanging apparatus. As the hot exhaust gases rise into inlet duct 8, they are positively drawn through the porous metal member 20 by exhaust fan 22. This fan has the capacity to always cause a slight negative pressure in the hot exhaust inlet duct 8. As the hot exhaust gas contacts the porous metal member 20, the heat in the exhaust air dissipates into the metal member. The metal member is of such porosity as to not hinder the exhaust fan from maintaining a negative pressure at the inlet duct 8. The porous metal member is preferably constructed of mesh of such weight and density that the area and thickness of the mesh directly in front of inlet 8 has the capacity to absorb all exhaust heat rising into it. Both reclaim blowers should have a capacity of counterflowing sufficient air (460 cfm or 13 m/min) to reduce the metal mesh temperature to the reclaim blower discharge temperature. The porous metal member is preferably cycled at 13 cycles per minute. This frequency is based on tests which have shown that 10 cycles/minute should occur for every 50,000 BTU/hour (5.3 × 10⁴ kJ/h) of energy in the exhaust airstream. For a 200,000 BTU/hour (2.1 x 10⁵ kJ/h) furnace, which sends one third of its energy up the exhaust flue, the frequency is 13 cycles/minute. The total weight of the porous metal mesh traversing through the hot gaseous airstream in any given period should equal at least the weight of the air passing through the metal mesh for the same period. To produce maximum heat reclaim, it is preferable that the weight of the porous mesh traversing through the hot gaseous exhaust airstream be from one to four times (most preferably two to four times) the weight of the hot gaseous exhaust airstream flow for any given period of time. In operation, the reclaiming apparatus remains inactivated until an on/off heat sensor 50 located in the hot air feed duct 8 is heated to 210°F to 240°F (99° to 116°C) by the furnace turning on (the sensor would preferably be located closer to the furnace than shown in the drawing). When this sensor detects a temperature of 210°F to 240°F (99° to 116°C), it automatically starts motors 16, 23 and both reclaim blowers 34, thus initiating reciprocating movement of porous metal member 20, and positive pumping of the exhaust airstream through porous metal element 20. At the same time, a normally-closed thermal time-delay relay in the circuit to the furnace gas valve is activated, giving the apparatus approximately twenty seconds in which to raise the pressure in the exhaust duct 10, and thereby close the normally-open contacts of a pressure switch 52 connected in series with the gas valve. If the exhaust is not functioning properly (e.g. because fan 22 or motor 23 are not functioning, or flow through porous element 23 is blocked), the circuit to the gas valve would be opened resulting in shutdown of the fur nace as well as the reclaiming apparatus. If gear motor 16 or the reclaim blowers 34 fail, the resulting high temperatures in the ordinarily cold exhaust duct 10 will trip a thermal protection switch (located in the duct and set to trip at 200°F or 93°C), shutting off electrical power to the furnace gas valve and the reciprocating energy reclaiming apparatus. The thermal protection switch 54 is of the automatic reset (at 160°F or 71°C) type. As a safety backup if the thermal protection switch fails, there is a thermal switch in exhaust motor 23 that will also trip and shut off exhaust motor 23, resulting in shut off or both the gas valve and the reclaiming apparatus. Should any electrical component have a fault, an electrical fuse built into the reciprocating energy reclaiming apparatus would blow, shutting off the gas valve and apparatus. The safety features can be summarised as follows: Should any of the three fans or the reciprocating gear motor fail to function properly, safety controls will automatically shut off the main gas valve to the gas furnace. Should the exhaust fan 22 fail to function, a pressure switch on the discharge of the fan would lose pressure, resulting in the main gas valve circuit being interrupted. If the reciprocating gear motor 16 fails to function, there would be no heat exchange, resulting in the exhaust hot air passing straight through the mesh heating up the temperature switch located in discharge duct 10. This switch which is normally closed, will open the circuit to the gas valve resulting in the gas being shut off. Should either of the reclaim fans fail, this will result in high temperature air passing into the exhaust duct, and will also trip the high temperature limit switch. This automatic reset limit switch will trip at 200°F or 93°C. If the on/off temperature control fails to function, again the high temperature air would enter the exhaust duct and trip the high temperature limit switch. A second safety feature on the on/off control is the fact that there would be no pressure to the exhaust pressure switch, and once twenty seconds have past the gas valve would be shut off. The described reciprocating energy reclaiming apparatus is simple to fabricate (e.g. it can be made with 18 or 20 gauge sheet metal and electric spotwelding). The porous metal member 20 can be quickly removed for access and cleaning; two horseshoe clips on either end of the dual traverse rods 14 are removed, and the rods pulled out through the linear bearings and framework; allowing the porous metal member 20 to drop out easily. Cleaning of member 20 should ordinarily not be necessary except at multi-year intervals because of the continuous exposure of the member to counterflowing air currents H, R. As reclaiming apparatus of the invention operates only when the combustion chamber is fired (the sensors automatically turn it on and off), the monetary savings achievable by installing the unit is between ten to fifteen times the expense of electricity to operate the unit (primarily to operate the reclaim blowers 34). Other porous, heat-absorbing materials than the disclosed metal mesh could be used.

Claims: Air-to-air h e a t e x c h a n g e r for reclaiming energy from a first airstream (H) by transfer to reclaiming streaming air (R), comprising heat absorbing means for absorbing heat from said first airstream (H), being compartmentalized into compartments by partitions and reciprocally movable transversely to said first airstream (H); and an inlet duct (8) for receiving said first airstream (H) and directing it through said heat absorbing means to an outlet duct (10); characterized by a porous element (20) forming said heat absorbing means, an air exhaust fan (22, Fig. 2) positioned in the path of said first airstream (H) for drawing it through said porous element (20), reclaiming air blower means (34) for delivering said reclaiming streaming air (R), said first airstream (H) and said reclaiming streaming air (R) being sufficiently separated along the direction of movement of said porous element (20) so that airflow between said first airstream (H) and said reclaiming streaming air (R) is prevented. Heat exchanger of claim 1, characterized by said reclaiming streaming air (R) is so located and said reciprocal movement of said porous element (20) is sufficiently long that most of said porous element (20) passes twice through said reclaiming streaming air (R) for each single pass through said first airstream (H). Heat exchanger of claim 1 or 2, characterized by said porous element (20) movement is along a straight line. Heat exchanger of any of preceding claims, characterized by said reclaiming streaming air (R) flows counter to said first airstream (H). Heat exchanger of any of preceding claims, characterized by means for reciprocally moving said porous element (20) comprising one or more rods (14) extending along the direction of said reciprocal movement, and linear bearing means (12) supporting said porous element (20) on said rods (14) and providing low-friction, long-wearing support for said porous element (20). Heat exchanger of any of preceding claims, characterized in that said porous element comprises metal mesh (20) sufficiently porous to pass said first airstream (H). Heat exchanger of any of preceding claims, characterized by said reclaiming streaming air (R) is so located and said reciprocal movement of said porous element (20) is sufficiently long that, in each cycle of said porous element (20), most of said porous element (20) has a longer residence time in said reclaiming streaming air (R) than in said first airstream (H). Heat exchanger of any of preceding claims, wherein said first airstream (H) contains contaminated gases such as combustion gases from a combustion heating unit, characterized by purging means (25,28,38, Fig. 2) for directing a purging airstream (P) through portions of said porous element (20) emerging from said exhaust airstream so that said contaminated gases will not enter said reclaiming streaming air (R). Heat exchanger of claim 8, characterized by said purging means (25,28,38, Fig. 2) comprises means for directing said purging airstream (P) uncontaminated along a flow path extending through said emerging portions of said porous element (20) and exiting in said first airstream (H) at the exhaust side of said porous element (20). Heat exchanger of any of claims 6 - 9, characterized in that the total weight of said porous metal mesh (20) traversing through said first airstream (H) is equal to or greater, preferably two to four times, than the weight of said first airstream (H) for the same period.

Inventors: ASTLE, WILLIAM B. JR.
Applicants: ASTLE, WILLIAM B. JR.
Application year: 1987
Main classification: F28D19
IPC codes: F23L15, F28D1, F28D19