BACKGROUND OF THE INVENTION

The present invention relates to a method and apparatus for heating a fluid stream and more particularly to a unique and novel method and apparatus for heating a gas or a liquid with compressed combustible fuel gas and compressed gas for supporting the efficient combustion of such fuel gas.

It long has been known to conduct and inject into a combustion burner a fluid combustible fuel through the chamber of a central conduit and to conduct and inject therewith a combustion supporting fluid into the burner through an annular passage defined by another conduit spaced from and surrounding the central conduit. In this regard, attention is directed to long expired U. S. Patent No. 405,391, issued to P. L. Bear on June 18, 1889, which patent broadly teaches such an arrangement for an oil burner and to long expired U. S. Patent No. 622,146, issued to G. Heysel on March 28, 1899, which patent broadly teaches another such arrangement for a hydrocarbon burner. Further attention is directed to unexpired U. S. Patent No. 3,902,840, issued to Paul Baguet on September 2, 1975, which also teaches two coaxial injectors for a fuel gas and combustion supporting gas, this patent further teaching a combustion chamber having a narrowing outlet. In this regard, attention is further directed to expired U. S. Patent No. 2,652,890, issued to C. . Morck, Jr., et al on September 22, 1953 and to U. S. Patent No. 3,424,541, issued to R. Wang, et al on January 28, 1969, both of which teach such a refractory lined combustion chamber, attention being further directed to the coaxial injection apparatus disclosed by the Wang patent. Finally, attention is directed to the coiled heat exchange arrangement of unexpired U. S. Patent No. 4,161,391, issued to Herbert W. Parker on July 17, 1979 and to the reduced heat exchange tubes taught by expired Patent No. 2,182,218, issued to J. C. Woodson on December 5, 1939 and by unexpired Patent No. 4,218,211, issued to Stanley Z. Caplan on August 19, 1980. A number of other patents noted as of possible interest relating to the mixing of gases for burning are as follows: Patents No. 993,687, issued to B. F. Jackson on May 30, 1911; No. 1,921,059, issued to J.

M. Weil, et al on August 8, 1933; No. 2,340,120, issued to H. L. Grupp on January 25, 1944; No. 2,526,748, issued to N. E. Hill on October 24, 1950; No. 2,838,105, issued to D. Eastman, et al on June 10, 1958; and No. 3,074,469, issued to R. P. Babbitt, et al on January 2, 1963.

Although a number of these several aforementioned patents might each broadly and separately have suggested coaxial injection apparatus, refractory lined combustion chamber apparatus narrowing at the outlet end thereof, coiled heat exchange tubes and heat exchange change tubes narrowing at the outlet thereof, none of these aforementioned patents, either alone or in combination with each other, recognizes or teaches a solution of the problems recognized and resolved by the inventive method and apparatus as is disclosed in this application. The present invention recognizing past limitations in manufacture, assembly, installation and performance of prior furnace assemblies and in methods for heating gases and liquids, teaches a nfew and unexpected method and apparatus which considerably surmounts past limitations in the heat exchange art, providing a readily and economically manufactured, assembled, installed, maintained and repaired or replaced heat exchange system and parts thereof, the inventive system being capable of producing high and efficient performance over a broad range of turn-up and turn-down operating conditions. More specifically, the present invention provides a highly efficient, very compact heat exchange system which allows for operation at comparatively higher velocities and pressures to entrain and purge the system of corrosive condensation and other combustion outfalls, the arrangement of the present invention providing extremely high heat transfer efficiencies in a comparatively and considerably smaller equipment space with minimum standby losses. Further, the present invention provides a novel furnace assembly and method of operation which obtains a high ignition rate of reaction with a comparatively inexpensive venting system that reduces construction and insulation costs, avoids roll out of flame or gas, avoids undesirable chimney effects and minimizes standby losses. In addition, the method and apparatus of the present invention is readily adaptable to a large range of construction and processing environments with a capability of

operating efficiently and quietly in a minimum of space and with a minimum of safety hazards due to a sealed pressure vessel combustion chamber arrangement.

Various other features of the present invention will become obvious to one skilled in the art upon reading the disclosure set forth herein.

SUMMARY OF THE INVENTION More particularly, the present invention provides an improved process for heating fluids comprising: compressing a combustible fuel gas to a preselected pressure level in a first compression zone; compressing a combustion supporting gas to a preselected pressure level in a second compression zone; passing the compressed gases from the first and second compression zones through an injection and mixing zone having entrance and exit sections in a preselected manner to thoroughly mix the compressed gases; passing the mixture of compressed gases through a combustion zone having entrance and exit sections, igniting the mixture while therein; passing the products of combustion from the combustion zone through a heat exchange zone wherein the products are progressively contracted from inlet to outlet to increase the velocity thereof; passing a fluid to be heated thereby through the heat exchange zone in heat exchange relation therewith; and, exhausting the contracted products of combustion from the heat exchange zone. In addition, the present invention provides an improved structural arrangement for heating fluids comprising: a first compressor means having the suction side thereof in communication with a combustible fuel gas source; a second compressor means having the suction side thereof in communication with a combustion supporting gas source; a fluid heating assembly including an injection and mixing chamber having an entrance and exit section and a combustion chamber having an entrance and exit section, the entrance section of the injection and mixing chamber communicating with the first and second compressor means to receive combustible fuel gas and combustion supporting gas respectively therefrom under pressure and thoroughly mix the gases and the entrance section of the combustion chamber communicating with the exit section of the injection and mixing chamber to receive the thoroughly mixed gases therefrom; an ignition means disposed in

the combustion chamber to ignite the mixed fuels; and, a heat exchanger conduit having the inlet end thereof communicating with the exit end of the combustion chamber to receive the products of combustion therefrom and the outlet end exhausting the products, the heat exchanger conduit narrowing progressively in cross-sectional area from inlet to outlet end thereof to contract and increase the velocity of the heated products of combustion passing therethrough. In addition, the present invention provides a novel arrangement for injection and mixing two fluids; a novel combustion arrangement along with a fluid reversing arrangement; and, a novel heat exchanger arrangement.

It is to be understood that various changes can be made by one skilled in the art in one or more of the several parts of the apparatus disclosed herein and in one or more of the several steps of the method disclosed herein without departing from the scope or spirit of this invention.

BRIEF DESCRIPTION OF THE DRAWINGS Referring to the drawings which disclose an advantageous embodiment of the present invention: Figure 1 is a flow diagram of the invention method and apparatus, disclosing schematically one possible arrangement of the several parts of the invention;

Figure 2 is a greatly enlarged cross-sectional view of the novel injection and mixing arrangement which can be used to carry out the present invention;

Figure 3, when compared with Figure 2, is a somewhat reduced cross-sectional view of the novel combustion chamber arrangement which can be used to carry out the present invention;

Figure 4 is a cross-sectional side view of the novel combustion chamber and heat exchanger arrangement used in carrying out the present invention; and,

Figure 5 is an end view of the combustion chamber and heat exchanger of Figure 4 taken in a plane through 5-5 of Figure 4, disclosing one manner such heat exchanger and-combustion chamber can be incorporated in a housing in heat exchange relation with a fluid stream to be heated.

Referring to Figure 1 of the drawings, the broad schematic arrangement 2 is disclosed as including a combustible fuel gas source 3 and a separate combustion supporting gas source 4. Advantageously, fuel gas source 3 can be natural gas taken at the usual established 0.25 psig pressure from a conventional natural gas line used in everyday commercial, industrial and domestic practices. Combustion supporting gas 4 can be ambient air which can advantageously, if desired, be enriched with oxygen to enhance combustion. Any one of several known arrangements can be utilized for oxygen enrichment of air and details of such oxygen enrichment are not disclosed herein. Natural gas source 3 is connected to compressor 6 through conduit 7 and the combustion supporting air source 4 is connected to compressor 8 through conduit 9. Compressors 6 and 8 can be any one of a number of suitable, commercially available gas compressors and, advantageously, it has been found desirable to use commercially available hermetically sealed refrigerant compressors of a similar type for both the natural gas and the combustion supporting air.

Positioned downstream from each compressor 6 and 8 in lines 7 and 9 respectively is one of a pair of pressure regulators 11, 12, each pressure regulator being provided upstream thereof with an appropriate lubricator extractor 11' , 12' having an appropriate recirculation line 13, 14 respectively to recirculate to the compressors lost lubricant. From the compressors 6 and 8, lines 7 and 9 lead to a novel injection and mixing chamber arrangement broadly referred to be reference numeral 16 in Figure 1, such chamber serving to inject and mix gases for combustion prior to their introduction into a combustion chamber.

Referring to Figure 2 of the drawings, injection and mixing chamber 16 includes a main tubular conduit 17. Conduit 17 can be of a suitable material, such as a copper alloy or brass material and serves to define main tubular plenum chamber 18. The main tubular conduit includes an upstream entrance section, the lineal extent of which is indicated by bracket 19 and a downstream exit section, the lineal extent of which is indicated by bracket 21. A coaxial, centrally disposed tubular conduit 22 of smaller cross-sectional area than main tubular conduit 17 and advantageously of equal cross-section to the aforedescribed conduit 7 to which it

is connected, or which, if desired, can be a continuation of conduit 7, is centrally positioned in the entrance section of main plenum chamber 18 to extend along substantially the entirety of entrande section 19 in spaced relation to main tubular conduit 17. Conduit 22 also can be formed from a suitable material such as copper alloy or brass material. With the spacing between conduit 17 and conduit 22 extending therein, the main plenum chamber 18 defined in accordance with usage of the subchambers and the mixing results desired. Referring particularly to Figure 3 of the drawings, combustion chamber 33, which can be formed from a suitable material, such as a mild steel material and appropriately lined with a compatible refractory material, also includes an upstream entrance section, the lineal extent of which is indicated by bracket 34 and a downstream exit section, the lineal extent of which is indicated by bracket 36- Combustion chamber 33 can be tubular in cross-section throughout from inlet end 37 of entrance section 34 to outlet end 38 of exit section 36. Exit section 36 advantageously is of frustum form to progressively narrow in cross-sectional diameter, approximately fifty (50) percent from upstream to the outlet of the exit section. Further, it is to be noted that the central lineal axis of exit section 36 comprises approximately fifty (50) percent of the overall central lineal axis of combustion chamber 33. Inlet end 37, which is connected to the outlet end of the mixing section 32 of injection and mixing chamber 16, advantageously has proximately positioned thereto a suitable igniter, such as a spark plug igniter 39 mounted in the back plate 41 of combustion chamber 33. As is generally known in the art, spark plug igniter 39 can be connected by wires to a suitable source of electrical energy (not disclosed) .

As can also be seen in Figure 3 of the drawings, suitably spaced annular fin members 42 can be integral with or appropriately fastened, such as by welding along the entirety of the outer periphery of tubular combustion chamber 33 on both entrance section 34 and exit section 36 to conduct heat from the combustion chamber and to augment heat exchange with a fluid stream, particularly when the novel heat exchanger coil described hereinafter is proximately spaced from the chamber 33. >

As can be seen in Figure 3, a suitable U-shaped or semi-circular tube 43 can be sized to be connected at one end to outlet end 38 of combustion chamber 33. The outlet end 44 of tube 43 which progressively narrows in tapered fashion can be connected to a coiled heat exchanger 46 by a suitable connecting union 47. The U-tube 43 serves to reverse the flow path of the products of combustion emanating at increased velocities from combustion chamber 33 due to the narrowing of exit section 36. This reversal of the flow path can be approximately 180° to place both combustion chamber 33 and heat exchanger coil or conduit 46 in heat exchange relation with fluids to be heated (Figures 1, 4 and 5).

As can be seen more fully in Figures 4 and 5 of the drawings, heat exchange coil 46 can be formed in the geometric configuration of a helix. The heat exchanger coil 46 can be of a suitable heat conductive material, such as steel alloys, aluminum or ceramic materials and in accordance with one feature of the present invention, progressively narrows in diameter and thus cross-section from inlet 48 to outlet -49 with the cross-sectional area reduction from inlet to -outlet being as much or even more than ninety (90) percent. It is to be noted that both combustion chamber 33 and heat exchanger coil 46 can be readily disposed in a flow-through housing 51 containing a suitable circulation blower 52 upstream thereof to move a gas stream, such as air, through and around heat exchange coil 46 and around the finned combustion chamber 33 and thus raise the gas stream temperature to a preselected and controlled level. In this regard, it is to be understood that, instead of a flow-through housing 51, the sealed combustor 33 and coil 46 or just the coil 46 can be disposed in a totally submerged condition in a flow through liquid chamber, such as a water boiler or a chemical distillation chamber, to raise the heat of liquid fluid therein with two or more units being usable because of compactness to provide rapid heat to the liquid fluid.

As above described, one of the unique features of the present invention is the compactness of the several parts of the inventive arrangement and the adaptability to usage of parts which are commercially available. For example, as above discussed, the compressors 6 and 8 can be of the hermetically sealed refrigerant type, with capabilities of raising combustion gas pressures such as

natural gas from a conventional 0.25 psig and ambient air from a conventional 15 psia to as high or even higher than sixty (60) psig. The conduits in the system, such as conduits 7 and 9, can be of a conventional material, such as a copper-type alloy, with external diameters in the range of one-quarter (1/4) inch to one-half (1/2) of an inch. The pressure regulators, such as regulators 11 and 12, can be any one of several types of regulators known in the art, as can be the lubricant separators 11 ^r , 12' to separate lubricant for recirculation back to the compressors through by-pass conduits 13 and 14.

In the fluid heater assembly, the novel injection and mixing chamber 16 can be formed from conventional material, such as metal or ceramic tubing, with a surprisingly and comparatively small overall main chamber conduit 17 length of less than three (3) inches, advantageously two and eleven-sixteenths (2 11/16) inches, with an inner diameter of main plenum chamber 18 being eleven-sixteenths (11/16) of an inch along the upstream entrance section 19 and nine-sixteenths (9/16) of an inch along the downstream exit or mixing section 21. The tubular conduit 22 which c n extend within main conduit 17 for approximately two and one-quarter (2-1/4) inches of its length can have an outer diameter of one-quarter (1/4) of an inch, flared at its outlet end to a five-sixteenths (5/16) outer diameter. The T-section joining conduit 9 with main conduit 17 can be five-sixteenths (5/16) of an inch at the inlet opening to a bell shape of nine-sixteenths of an inch and further flaring to join main conduit 17.

The tubular combustion chamber 33 which as above noted can be formed from mild steel, can be of less than eight (8) inches in length with the entrance section 34 having an approximate four (4) inch length and an internal diameter of three and one-half (3-1/2) inches therealong. The exit section, which can be approximately three and one-half (3-1/2) inches in length narrows from a three and one-half (3-1/2) inch inlet diameter to a one and one-fourth (1-1/4) inches outlet diameter to connect with U-tube 43 of similar one and one-fourth (1-1/4) inch diameter at such connecting end. The U-tube which is turned 180° on a twelve (12) inch outer diameter radius has the last two inches tapering from one and one-fourth (1-1/4) inch diameter to a five-eighths (5/8) inch

diameter to connect with helix-like heat exchanger coil 46. Coil 46 can narrow from an internal diameter of five-eighths (5/8) of an inch at the inlet down to three-sixteenths (3/16) of an inch at its outlet within a fifteen (15) inch diameter housing 51 and even further thereafter. The tapering can be progressively continuous or in steps of five-eighths (5/8) inch tubing of two turns in a row, four-eighths (4/8) inch tubing of six turns in a row and three-eighths (3/8) inch tubing with five turns in a row with the three-eighths (3/8) inch tubing row being the most proximate to circulation blower 52 outlet. The exit tubing from the housing can be two-eighths (2/8) inch tubing and can be further coiled in the center of the helix to further enhance heat exchange.

In carrying out the inventive method taught herein, a combustible fuel gas such as natural gas at an initial pressure of approximately 0.25 pound per square inch gauge (psig) having a firing rate in the approximate range of ten thousand (10,000) to sixty thousand (60,000) BTUH and a flow rate of ten (10) cubic feet -per hour to sixty (60) cubic feet per hour can be introduced into a hermetically sealed compression zone wherein the pressure of the gas is raised to an approximate pressure rate of ten (10) to sixty (60) pounds per square inch gauge (psig). At the same time, a sufficient air volume to allow stoichiometric combustion can be introduced into another hermetically sealed compression zone wherein the pressure of the air is raised to an approximate similar range of ten (10) to sixty (60) pounds per square inch. If desired, ten percent or greater excess air at an approximate velocity range of one hundred ten (110) cubic feet per hour to six hundred sixty (660) cubic feet per hour can also be employed above stoichiometric combustion, but is has been found that the efficiency effects of such excess air have been nominal. Further, if desired, the air can be oxyg'en enriched by some suitable arrangement (not disclosed) prior to compression to enhance efficiency. The compressed gas and air from the combustion zones can be regulated through pressure regulation zones with an advantageous turn-down, turn-up ratio of three (3) to one (1). Advantageously, the firing rate can be in the turn-down, turn-up range of ten thousand (10,000) to thirty thousand (30,000) BTUH and preferably held at approximately twenty thousand (20,000) BTUH. It is to be understood, however, that both the operational

range and the turn-down, turn-up ranges above described can be both below and above those stated, depending upon required demands and the concomitant size and capacity of equipment employed. In accordance with the present invention, when the compressed gases are regulated in the pressure regulation zones, the lubricants in the gases are separated therefrom and recirculated to the compression zones.

From the pressure regulating zones, the regulated compressed gases having a heat release ability in the approximate range of four hundred thousand (400,000) to two million five hundred thousand (2,500,000) BTUH/cu.ft. are then passed to an injection and mixing zone having entrance and exit sections to flow in separate coaxial linear streams along the entrance section of the zone with the compressed combustion supporting air stream annularly surrounding the compressed natural fuel gas stream until reaching the exit section of the zone wherein the compressed fuel gas is expanded with velocities in the approximate range of ten and one-half (10.5) to sixty three and four-tenths (63.4) feet per second and the combustion supported air stream is contracted to increase the velocity thereof with velocities in the approximate range of thirty-one and nine-tenths (31.9) to one hundred and ninety-one and four-tenths (191.4) feet per second with the mixed gases having a velocity in the approximate range of forty two and four-tenths (42.4) feet per second to two hundred seventy-four (274) feet per second and a pressure in the approximate range of seven (7) to twenty-three (23) psig.

The mixed gases are subsequently passed to a compression zone having entrance and exit, sections with flow rates being in the approximate range of 0.0305 to 0.183 cubic feet per second wherein the mixture of compressed gases is ignited upstream the entrance section of the combustion zone before passing as products of combustion to the exit section of the combustion zone, the gases being contracted approximately fifty (50) percent between the upstream and downstream extremities of the exit section of the combustion zone. The direction of flow of the products of combustion emanating from the exit section of the combustion zone can then be reversed in a reversing zone to pass proximate the combustion zone to improve greater heat exchange relation with the

accompaniment of the combustion zone. The products of combustion are passed from the reversing zone to a heat exchange zone proximate the combustion zone at least in part with the flow passage following the path of a helix and with the products of combustion in the heat exchange zone being progressively contracted in excess of at least ninety (90) percent from inlet to outlet of the heat exchange zone to thus increase the velocity of these products of combustion and to further entrain liquid condensations therefrom. In the heat exchange zone, a fluid-gas or liquid is passed in heat exchange relation with the products of combustions which are then exhausted, along with entrained condensations to ambient.

The velocities of the products in the entrance section of the combustion zone have been calculated to be in the approximate range for stoichiometric air input of 10,000 BTUH to be 0.536 feet per sec. to 3.21 feet per sec. for stoichiometric air input of 60,000 BTUH. Gas velocity calculations for stoichiometric air measured in the input range of 10,000 BTUH to 60,000 BTUH and with the cross-sectional area diminishing in the last four inches of the contracting exit section of a combustion zone are as set forth in Tables "A ^M and "B" below:

TABLE A

Stoichiometric - 10,000 BTUH input

Distance From Chamber Inlet End Velocity

4.5 inches 0.6277 feet per sec. 5.0 inches 0.7574 feet per sec.

5.5 inches 0.9290 feet per sec.

6.0 inches 1.1680 feet per sec.

6.5 inches 1.1530 feet per sec.

7.0 inches 2.0370 feet per sec. 7.5 inches 2.8900 feet per sec.

8.0 inches 4.4150 feet per sec.

TABLE B

Stoichiometric - 60,000 BTUH input

Distance From Chamber Inlet End Velocity

4.5 inches 3.766 feet per sec. 5.0 inches 4.538 feet per sec.

5.5 inches 5.574 feet per sec.

6.0 inches 7.009 feet per sec.

6.5 inches 9.080 feet per sec.

7.0 inches 12.226 feet per sec. 7.5 inches 17.340 feet per sec.

8.0 inches 26.491 feet per sec.

The addition, gas velocity calculations for air with stoichiometric input ranges of 12,980; 21,845; and 30,130 BTUH, calculated for nineteen selected substantially equally spaced positions extending sequentially from inlet end to outlet end along the approximately thirty-five (35) linear foot lengths of the narrowing heat exchange zone are as set forth in Table "C" below:

TABLE C

From the above Table "C", given a few aberrant calculating results, it can readily be seen that as the heat exchange zone narrows and as the BTUH input increases, the velocity of the products of combustion flowing through the heat exchange zone increases substantially in applicants' inventive arrangement, assuring the carrying away of condensation and undesirable contaminants.

Thus, a highly efficient, compact heat exchange system operating at high velocities and pressures is provided by the inventive arrangement described above.