CA1313042C - Drying apparatus - Google Patents

Abstract

ABSTRACT OF THE DISCLOSURE

A drying apparatus including a pulse combustor coupled to a processing tube for flowing material to be processed therethrough, the processing tube being coupled to a pair of cyclone collectors for receiving the material flowing therefrom. An optional recycling section is coupled to the cyclone collectors for flowing vapor from the cyclone collectors back to the upstream end of the processing tube.
The pulse combustor includes a rotary valve, a combustion chamber, an inner tail pipe and an outer tail pipe. The combustion chamber and inner tail pipe are conical and tubular sections mounted in longitudinal compression, and the compressive forces are transmitted externally across the junction of the combustion chamber and tail pipe by a strongback assembly. The rotary valve includes first, second, and third closely adjacent cylinders defining an interior air chamber. The cylinders have radially oriented substantially aligned apertures which define an air intake.
Air passing from the air chamber into the combustion chamber passes through an annular passage which impedes air flow from the combustion chamber toward the air chamber to a greater extent than air flow from the air chamber to the combustion chamber. Control systems regulate the product feed rate, the system firing rate, the system flow rate, and the operating frequency of the pulse combustor.

Description

1 30~2 DRYING APPARATUS

This application is divided from Canadian Patent Application Serial Number 534,822, ~iled April 15, 1987.
This invention relates to a method and system for directing and combusting fuel in a combustion chamber of a pulse combustor~ The method and system of the present invention finds particular application in drying equipment and processes, and i9 particularly suitable for use in a novel drying apparatus and proces~ in which the material to b~ dried is atomiz~d and dried by the pulsating flow of a stream of hot gases.
~ he general process known as combustion drying has been in use for many years. The process has been widely used to remove moisture to obtain or recover a solid material which has been in suspension or solution in a fluid. Typically, the fluid i~ atomized and the resultant spray is subjected to a flow of hot gases from a combustion process such as that available from an air heater or a pulse combustor to evaporate the moisture from the spray. The solid particles are then carried from the drying chamber by the flow o~ the drying gas and ~re removed from the gas by means such as a cyclone separator.
There are two types of pulse combustors. The first is the valved type pulse combustor of which the Y-l "Buzz Bomb" engine is the best known Pxample. ~he second is the air valved pulse combustor which uses the pulse energy to pump its combustion air. The best known example of this type is the air valve engine developed by Mr. Raymond Lockwood and disclosed in many of his patents such as U.S.
Patent No~3,462,955.
An air valved pulse combustbr consists of a combustion chamber where the ~uel i~ introduced, a combu~tion chamber inlet which is a short tube, and a combustion chamber tail pipe which i8 longer than the combustion chamber inletO Fuel is pre~sure atomized in the ; combustion chamber, and when the proper explosive mixture is 13~3Q~

fuel and air explode and burning gas expands out both the inlet tube and the outlet tube. The energy released in the explosion provides thrust or power when the two shock waves exit from the combustion chamber. One shock wave will exit from the short inlet tube of the chambex before the second shock wave can exit from the tail pipe.
The momentum of the combustion products cau~es a partial vacuum to develop in the combustion chamber, causing a reverse flow in both the inlet and tail pipe. Thi reverse flow brings a new air charge into the combustion chamber where the air mixes with a new fuel charge and with the hot gas which reversed its flow in the tail pipe. The momentum of the reverse flow causes a slight compres~ion to develop in the combustion chamber and a very vigorous mixing of the fuel, air, and hot combustion products results.
Spontaneous ignition of the mixture takes place and the process repeats it self about lOO times per second.
Most pulse combustion systems today use the air valve engine because it is simple to make and has no mechanical moving parts. Howeverl the air valve system uses a substantial percentage of the energy from the combustion process to pump the combustion air required for the succeeding fuel detonation~. Even though this system can be made into an efficient thrust producing ensine through the addition of thrust augmenters, the energy consumed in pumping the combu tion air detracts from the total energy available for the process and reduces the overall system efficiency.
The valved type pulse combustor uses the same combustion principle except that it has a mechanical (reed, flapper, or primitive rotary type) valve on the combustion chamber inlet side which prevents any back flow of co~bustion products out of the inlet tube. The valve is closed during the final phase of fuel/air mixing and during the explosion, so all of the combustion products exit through the tail pipe, preceded by the shock wave. ~owever, these valved type systems have experienced limited valve life in the hot environment of the engine inlet since the ` -- 13130~2 valve must open and close with each combustion cycle, which can be over 100 times per second.
A furthar problem with engine life which affects both types of pulse combustors is caused by the corrosive effects of the hot combustion gases. Parts of the system which experience the hottest temperatures deteriorate ~uickly, necessitating frequent expensive repair and replacement of those parts. Attempts to fabricate such parts from corrosion resi~tant material, such as high quality stainless steel or inconel, have been unsuccessful because the parts have failed due to mechanical and thermal stresses in the systemO Attempts to fabricate such parts from ceramics have failed becauRe of the prohibitive costs associated with existing technology. A major reason for the prohibitive costs of ceramic construction is that the components must be cast as thick walled sections which must then be machined to form flanges, apertures, etc. This process wastes expen~ive ceramic material and requires extensive labour and the use of sophisticated tooling and cutting techniques.
The effectiveness of a pulse combustion energy system depends a great deal on its operating char-acteristics~ For example, the operating frequency affects the rate of flow through the system (and hence drying time) of material to be dried, and the amplitude, or pressure, of the sonic shock wave must be appropriate for a given material since too much pressuxe over dries or destroys the material while too little pressure provides inadequate drying.
Present systems operate only at the natural frequency of the pulse combustor which is set by the length of the exhaust tubes. Accordingly, the operating frequency, and hence drying rate, cannot be altered without the ubstantial expenditures resulting from system reconstxuction. This often results in systems which will only achieve their maximum efficiency when used to dry a specific type of material. Furthermore, since the natural frequency of the pulse combustor also depends on the speed of sound, variations in temperature in the combust4r will change the natural frequency. As the natural frequency deviates from the frequency of optimal performance of the pulse combustor, the amplitude of the pressure wave diminishes, increasing the drying time of some products above acceptable levels. The result is lack of uniformity and effectiveness in drying.
Another disadvantage of present systems resides in the inability to meet OSHA standards. External noise has been a major reason for industry to discount pulse combustion as a viable alternative energy source since ambient noise can exceed 120 dB.
Finally, a risk of explosion is often present because of overheating during operationl excessive fuel buildup during start-up, or combustion of the dried product when there is excessive oxygen in the drying gas stream.
The present invention is a drying apparatus which, as one of its functions, recovers a solid material which has been in sl1spension or solution in a fluid.
Accordingly, the present invention provides a drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the ~ combustion chamber for emitting high temperature pulses;
- 25 a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse com'bustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign ma-terial to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means, in fluid communication with the doSwnstream end of the processing tube, for xeceiving the foreign material flowing therefrom;
means for flowing a separate fluid into the processing tube proximate the upstream end thereof, s :.

~"` 1 3 1 3042 means for detecting a prescribed differential pressure through the processing tube; and means, responsive to the pressure detecting means for modulating the flow of fluid into the upstream end of the processing tube.
In a further aspect, the present invention provides a drying apparatu~ comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperat~re pulses;
a processing tube for flowing a foreign material to be proce~sed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
: means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means, in fluid communication with the downstre~m end of the processing tube, for receiving the foreign material flowing therefrom;
a conduit in fluid communication with the receiving means for receiving vapor flowing therefrom and extending proximate to the upstream end of the processing tube; and wherein the processing tube has an aperture for directing the vapor from the conduit into the processing tube~
: 30 The present invention also provides a drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
means for selectively modulating the emission of pulse~ ~rom the pulse combustor;
the pulse modulating means comprising:

:

means for detecting a prescribed temperature in the receiving means; and means responsive to the temperature detecting means for selectively modulating the smission of pulses from the pulse combustor;
a processing tube for flowin~ a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being; in fluid colmmunication with the outlet of the pulse co~bustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be : processed into the high temperature pulses flowing through the upstream end of the processing tube; and means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing there~rom.
In a still further aspect, the present invention provides a drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the ~: combustion chamber for emitting high temperature pulses;
means for ~electively modulating the emission of pulses from the pulse combustor, the pulse modulating means comprising:
means for detecting a prescribed fxequency of high temperature pulses; and means responsive to the frequency detecting mean~
for modulating the emission of pulses from the pulse combustor;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream : end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
mean~ for introducing the foreign material to be _ 7 _ 1 3~ 3 0~2 processed into the high temperature pulses flowing through the upstream end of the processing tube; and means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom.
In a further aspect, the present invention provides a drying apparatus comprising:
a pulse combustor having a com~ustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be proce~sed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means for modulating the flow into the processing tube of foreign material to be processed, the flow modulating means comprising:
means for detecting a prescribed temperature in the receiving means; and means respon ive to the temperature detecting means for modulating the flow into the processing tube of foreign material to be processed; and means, in fluid communications with the downstream end of the processing tube~ for receiving the foreign material flowing therefrom.
In a still further aspect, the present invention provides a drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream and being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefromî
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream and of the processing tube;
means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;
means for modulating the flow rate through the processing tube of foreign material to be processed therein, the flow rate modulating means comprising:
means for detecting a prescribed pressure in the receiving means: and a fan in fluid communication with the processing tube for ~electively drawing vapor from the processing tube in response to the pressure detecting means.
Operating flexibility and safety of the present invention are enhanced by control systems which regulate the product feed rate, the system firing rate, the system ~low rate, and the operating frequency of the pulse combustor.
During normal operation the fuel nozzles in the system may be set to fire on air-atomized oil which further enhances safety by ensuring that detonation occurs on time due to the initial combustion that takes place between the oil and the atomizing air as the mixture is discharged into the hot combustion chamber. Finally, noise suppression equipment enhances safety by suppressing external noise to a level which exceed OSEA s~andards.
In a final aspect, the present invention provides a drying apparatus compri ing:
a pul~e combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber emittin~ high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the 1 3 1 30~2 g pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;
means for modulating the flow rate through the processing tube of foreign material to be processed therein~
the flow rate modulating means comprising a conduit in fluid communication with the receiving means for receiving vapor flowing therefrom, the condui~ extending proximate to the upstream end of the processing tube, and wherein the processing tube ha~ an aperture for directing the vapor from the conduit into the processing tuhe.
The invention is illustrated in the drawings, in which:
Fig. 1 is a side cross sectional view illustrating a preferred embodiment of the drying apparatus of the present invention.
Fig. 2A is a side cross sectional view of the pulse combustion engine of Fig. 1.
Fig. 2B is an alternative embodiment of the pulse combustion engine of Fig. 2A.
Fiy. 3A is a side cross sectional view of the ~rotary valve used in the pulse combustion engin~ of Fig. 2A.
; Fig. 3B is a side cross-sectional exploded view of the outer, intermediate, and inner sleeves of the rotary valve used in the pulse combustion engine of Fig. 2A.
Fig. 4, on the third sheet, is a detailed view of the coupling mechanism for the combustion chamber and inner tail pipe of Fig. 2A.
Fig. 5 is a schematic diagram of the flame safety system used in the preferred embodiment of the invention.
Fig. 6 is a schematic diagram of the operating control system used in the drying apparatus.

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~ 10 --Fig. 7 is a side cross-sectional view illustrating an alternative embodiment of the inv~ntion.
Overview Fig. 1 shows a novel drying apparatus of the present invention generally designated as 4. Drying apparatus 4 includes a processing section 8 and a receiving section 12. A product feed system 16 is coupled to processing section 8 for introducing material to be processed into processing section 8, and an air pump assembly 18 having a combustion air control damper 17 provides combustion air to the system by drawing air through an air inlet filter silencer 19.
Processing section 8 includes an outer shell 20 which is lined with sound absorbing materials to reduce the external system noise level. Disposed within outer shell 20 is combustor mounting cell 24 within which is mounted a pul~e combustor 28. The puls~ combustor is the subject of our United States Patent NoO 4 ~ 992 ~ 039 ~
Also disposed within outer shell 20 and coupled to pulse combustor 28 is a processing tube 32 having an upstream section 33 and a discharge section 34. Discharge section 34 has a constriction 36 so that the sonic pulse from pulse combustor 28 is partially reflected back, establishing in part a pattern of standing waves. Upstream of constriction 36 is an adjustable wave tuner 40 having a pi ton 44 which may be adjusted from the exterior of outer shell 20. Adjustable piston 44 allows the operator to set the amplitude of the standing waves rom a maximum value down to a point where the reflected waves are fully dampened and no standing waves are produced.
Downstream of constriction 36 is a baffle assembly 46 which is designed to suppress the high intensity sound before the vapor and processed particles flowing through processing tube 32 enter receiving section 12. Baffle assembly 46 comprises a baffle housins 45 having a plurality of movable sound partitions 47 therein which define a plurality of sound suppression chambers 48. Sound partitions 47 may be axially adjusted to alter the volume of sound suppression chambers 48 for a particular application.
A variable length upper portion 51 of each sound partition 47 further alters the volume of sound suppression chambers 48. At the bottom of each partition 47 is a deflector 49 which is shaped to effect a prescribed constriction and rate of opening for each sound suppression chamber 48. A lower surface 50 of each deflector 49 is shaped to ensure that the particles 10wing through processing tube 32 are deflected away from the entrance to each chamber 48.
Coupled to the discharge section 34 of processing tube 32 is receiving section 12 including a first cyclone collector 52 which, in turn, is coupled through a silencer 54 to a second cyclone collector 56 having a bag house 60 including fabric bags 61 disposed on the top thereof.
Cyclone collectors 52 and 56 are fully insulated to reducs the noise on their exterior. At the bottom of each cyclone collector 52, 56 are star valves 62, 63, respectively, for the discharge of a processed product to a processed product conveying system 64. Disposed on the top of second cyclone collector 56 is a blowback fan 66 for intermittently blowing air counterflow through fabric bags 61.
Coupled to an outlet 68 of second cyclone collector 56 is an induced draft fan 69 designed to pull the vaporized moisture and combustion products through receiving section 12 and then push them through an exhaust silencer 70 and through a stack 71. Also coupled to outlet 68 is an optional recycling section 72 having conduits 73 and 74, a recycle air fePd tube 75, and a recycle fan 76 for recycling the vapor stream flowing through second cyclone collector 56 to upstream section 33 of processing tube 32 when the pulse combustion energy ~ystem is used in an application where the load varies and maximum turndown is required. Recycling section 72 may be optionally coupled to the outlet of first cyclone collector 52 if desired.
Rotary Valve As shown in Fig. 2A pulse combustor 28 generally comprises a rotary valve 78, a combustion chamber sleeve 80 whose interior defines a combustion chamber 81, an inner tail pipe 84 and an outer tail pipe 86. The valve of Figure 2A is the subject of our co-pending patent application serial number 534,822 filed April 15, 1987.
As shown in Figs. 3A and 3~, rotary valve 78 has an outer sleeve 96 having a plurality e.g. four apertures 100 of a prescribed geometry which are equally spaced or disposed in any manner around the perimeter thereof which results in a balanced structure. Outer sleeve 96 is affixed to a face plate 102 of a valve motor 104. Disposed coaxially within outer sleeve 96 is a valve rotor defined by a drive plate 108 and an intermediate sleeve 109 attached thereto. Drive plate 108 is coupled to valve motor 104 through a motor shaft 110 and shaft nut 111. Intermediate sleeve 109 has a plurality e.g. four apertures 116 of a pxescribed geometry which are equally spaced or disposed in any manner around the perimeter thereof which results in a balanced structure. Apertures 116 generally align with outer sleeve apertures 100 when intermediate sleeve 109 is in a prescribed rotational position. As used herein and throughout the specification and claims, apertures generally align whenever they form a common opening of any shape or size.
Disposed coaxially within intermediate sleeve 25 109 is an inner sleeve 120 having a plurality, e.g. four apertures 122 of a prescribed geometry equally spaced or disposed in any manner around the perimeter thereof which results in a balanced structure. Inner sleeve 120 usually has the same number of apertures as outer sleeve 96, and apertures 1~0 in outer sleeve 96 are generally aligned with them. In some cases it may be advantageous to advance or retard apertures 100 in relation to the apertures 122 in inner sleeve 120 to obtain optimum performance. Apertures 100, 116 and 122 defins an air intake 124 for valve 78 as shown in Fig. 3A~
Apertures 100 are also designed to be modified as necessary to allow the valve capacity coefficient Cv of rotary valve 78 to vary predictably as the air intske 124 opens and closes to match the engine performance needs.

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They may be shaped, as shown by dotted lines 125 in Fig~ 3B, to allow a greater or lesser air flow as air intake 124 initially opens, or they may be shaped to ailow a greater or lesser air flow just as air intake 124 closes. In other words, apertures 100 have the necessary shape to provide the engine with the desired air intake flow rate and char-acteristics. The apertures in intermediate sleeve 109 or inner sleeve 120 likewise may be shaped to adjust the engine breathing rate as shown by dotted lines 126 and 127, respectively~
Ad~acent to drive plate 108 and coupled to inner sleeve 120 is a backplate 128 for preventing the back pressure from combustion chamber 81 from pressurizing drive plate 108. This protects motor shaft 110 and shaft nut 111 while preventing any thrust loading of valve motor 104.
As ~hown in Fig. 3A, located adjacent to outer sleeve 96, intermediate sleeve 109, and inner sleeve 120, opposite motor 104, is a valve outlet section 132 comprising an outer portion 136, coupled to combustion chamber sleeve 80 and inner sleeve 120, and an inner portion 140 disposed coaxially within and radially spaced from outer portion 136.
Inner portion 140 is coupled to backplate 128 at one end and to a flame stabilizer 142 at the other end. Flame stabilizer 142 is preferably constructed of ceramics.
An outer surface 144 of inner portion 140, an outer surface 148 of backplatP 128, and an inner surface 152 of innPr sleeve 120 together define an annular air chamber 156 in fluid communication with an annular "air diode" 160 formed by an inner surface 164 of outer portion 136 and an outer surface 168 of inner portion 140. The shape of annular air diode 160 is such that it will impede the flow of gas from combustion chamber 81 toward air chamber 156 to a greater extent than the flow of gas from air chamber 156 toward combustion chamber 81. This is accomplished by scalloping surface 164 and by forming surface 168 as a series of waves as shown in Fig. 3A.
Annular air chamber 156 is designed to minimize the air volume between the combustion chamber 81 and the air .
' `'' .

-intake. This reduces any cushioning effects this volume might have on the shock waves which are reflected towards the valve 78 during the detonation phase of the pulse combustor cycle.
Disposed within inner portion 140 i8 a cooling chamber 170 having a cooling inlet 174 and a cooling outlek 178 so that a cooling medium flowing through cooling chamber 170 helps cool the rotary valve/combustion chamber junction during operation.
To provide further cooling an air inlet 182 i5 provided to supply air to the junction of drive plate 108 and face plate 102. The air flows toward and through the annulus defined by the inner ~urface of outer sleeve 96 and the outer surface of intermediate sleeve 109 and ultimately passes through apertures 116 and 122 in intermediate sleeve 109 and inner sleeve 120, respectively, and into air ~hamber 156.
As shown in Fig. 1, rotary valve 78 is mounted to the front of the pulse combustor 28 and located in the combustor mounting cell 24. The rotary valve motor 104 is also mounted inside the combu~tor mounting cell 24, but an expansion joint 184 provides an airtight seal between the motor 104 and the inside of the pul e combustor mounting cell 24. Expansion joint 184 al~o takes up any expansion due to heat buildup in the combustor during operation.
Pulse Combustor Fig. 2A illustrates the remaining sections of pulse combustor 28. Located adjacent to valve outlet section 132 is combustion chamber sleeve 80 the interior of which defines combustion chamber 81. Combustion chamber 81 is in fluid communication with the annular air diode 160 of valve outlet section 132. Four fuel nozzles 186 and two igniters 187, mounted adjacent to two of the fuel nozzles 186~ are disposed circumferentially on valve outlet section 132 for supplying fuel and ignition energy to combustion chamber 81. Combustion chamber sleeve 80 terminates in a tapered combustion chamber exit 188. Adjacent combustion chamber exit 188 is inner tail pipe 84 and outer tail pipe 86, respectively. A radiation shield 189 is disposed cir-cumferentially around combustion chamber sleeve B0 and inner tail pipe 84 to protect combustor mounting cell 24 against the extreme temperatures generated by these sections.
During normal operation, incoming air is heated by radiation shield 189 as the air flows toward rotary valve 78, and the heated air recycles the combustor 28 surface heat losses back to the pulse combustion process for increased efficiency.
The combustion chamber sleeve 80, the flame stabilizer 142, and the inner tail pipe section 84 of the pulse combustor 28 are subjected to the highest temperatures in the systemO All flanges, apertures and other rough features have been eliminated from these sections to reduce thermal stress concentrations which can lead to a cracking of the parts, which renders them useless. Combustion chamber sleeve 80 and inner tail pipe 84 may then be constructed as smooth conical and tubular sections. This makes it commercially feasible to use high temperature ceramic materials to fabricate these parts, since the need for thick wall casting and extensive machining is eliminated. The ceramic parts significantly improve the life of this pulse combustor over others presently known.
Accordingly, there are three different ways of fabricating these parts listed in the order of preference A. They may be fabricated entirely out of high temperature ceramic materials such as Silicon Nitride, Silicon Carbide, Alumina Oxide, or Mullite-type ceramics.
Different engine sections in the same engine assembly may be made from different ceramics. It is also possible to ~ metallize the inside surface of the ceramic parts with ; catalytic metals such as platinum (or other metals) which improve the combustion process and reduce pollution.
B. They may be fabricated or cast as thin walled sections made from Inconel* or hiqh temperature stainless steel and lined with thin walled ceramic segments which are attached to the inside surfaces of the metal shells~ The same type of ceramics as described in A, above~ may be used *Trade-mark ., -.

--'` 1 31 3042 with this ~abrication method. This system is preferable when the engine parts are larger than the equipment available to manufacture the individual ceramic ~ections.
Again, the inside surface of the ceramic inserts may be metallized with catalytic metals such as platinum to improve the combustion process.
C. They may be fabricated or cast as thick walled sections made from Inconel* or high temperature stainless steel and coated with high temperature 2irconia based coatings. The zirconia coating is about 10-15 thousandths of an inch thick and will reduce the metal surface temperature by more than 200F.
In addition to eliminating thermal stresses by fabricating the components without stress-producing lS features, the mounting system must substantially eliminate all bending moments on these sections in order to reduce the probability of failure of the parts due to mechanical stresses. The mounting system illustrated in Figs 2A, 3A
and 4 achieves this result.
As shown in Fig. 3A, a bracket 204 applies pressure to a flange 205 radially extending from outer portion 136 of outlet section 132. Flange 205 is coupled to combustion chamber sleeve 80 through a ring 206 and a wedge 207, and the assembly is secured by bolts 208. As shown in Fig. 2A, bracket 204 longitudinally compresses combustion chamber sleeve 80 and inner tail pipe B against a flange 210 of outer tail pipe 86. Bracket 204 is secured by compression bolts 212 which thread into a flange 213 and are secured by nuts 214 and expansion springs 215. Expansion springs 215 allow for thermal expansion of pulse combustor 28 during operation.
To avoid bending moments at combustion cham~er exit 188, a stronsback assembly 218, illustrated in Fig. 4, transmits externally the force which compresses combustion chamber sleeve 80 and inner tail pipe 84 towards each other.
Strongback assembly 218 comprises stainless steel rings 219, 220, which clamp stainless steel wedges 221, 222 respectively to combustion chamber sleeve 80 and inner tail *Trade-mark - 17 - l 3 1 3 04 2 pipe 84, respectively. A ~trongback ring 2~4 i~ disposed betwe en wedge 8 2 21 and 2 2 2 .
Strongback a~embly 218 i~ ~ecured to a bracket 232 by bolts 234 pas~ing through bolt hole~ in ring 219 and wedge 221 and extending into ~trongbaclc ring 224.
Strongbac}c a~sembly 218 is eecured to a bracket 236 in a ~imilar fashion. A pin 238 extend~ ~lidingly through brackets 232, 236 and ~ support bracket 240. Pin 238 allowa the midRection of pul~e combustor 28 to be supported while accommodating any thermal expansion during operation.
Longitudinal compre~sion of combu~tion chamber ~leeve 80 i3 thu~ transmitted ~xternally to wedge 221 and along strongback ring 224 to wedge 22~ which in turn direct~ the longitudinal compression to inner tail pipe 84.
The outer tail pipe 86 will operate under different condition~ than the other pulse combustor ~ection~. It i~ subjected to much higher thermal stress loadings because the material to be proces~ed enters the tail pipa through a plurality of nozzles 246 extending through a plurality of apertures 248 as ~hown in Fig. 2A.
As a result, thi~ ~ection i~ not u~ually made from ceramic material~. The proces~ed material i~ at much lower temperature~ than the gas Btream BO the tail pipe ~urface mu~t accommodate hîgh temperature differentials. It i8 preferably made of Inc~nel*or high temperature stainles3 steel~ and may be coated with high temperature Zirconia. It i8 within the ~cope of the pre~ent invention to di~pose the nozzle~ 246 externally of tail pipe 86, as ~hown i~ Fig. 2B, and flow the material to be proces~ed generally parallel to tail pipe 86. Thi~ arrangement i~ preferable in ~ystem~
used to dry matexial, ~uch as tomatoes, whexein a component of the material, ~uch as ~ugar ~ tends to accumulate at the nozzle openings when the nozzles ar~ di~po~ed i~ the tail pipe. ~liminating apertures 248 in thi~ embodLment allows outer tail pipe 86 to be fabricated from ceramic Materials.
It i~ al~o wi~hin the ~cope of the pre~ent invention to u~e only one nozzle 246 when desirable.
*Trademark , J;

1 3 1 30~2 As shown in Fig. 2A, combustor mounting cell 24 mounts to processing tube 32 so that outer tail pipe 86 is coaxially disposed within and radially spaced from the inner surface of processing tube 32.
Part of the upstream section 33 of processing tube 3 is disposed coaxially within and radially spaced from a recycle air sleeve 250 ~orming an annular air passage 254.
Coupled to recycle air sleeve 250 and in fluid communication with annular air passage 254 is recycle air feed tube 75 which receives recycled vapor from receiving section 12.
The recycled vapor flows from annular air passage 254 and into processing tube 32 through a plurality of slots 255 circumfer~ntially disposed on the surface of processing tube 3~
Since the natural frequency of a pulse combustor depends in part on the length of the tail pipe, it is desirable in some cases to ensure that processing tube 32 does not have the eff~ct of bein~ an extension of outer tail pipe 86. To accomplish this, a plurality of apertures 256 are circumferentially disposed on the surface of processing tube 32 for forming a decoupler between outer tail pipe 86 and processing tube 32. Apertures 256 may be selectively : covered with plates (not shown) to vary the decoupling effect.
Flame Safety System The pulse combustion energy system is started, operated and shut down under the supervision of a flame ~afety system illustrated in Fig. 5. The flame safety system is controlled by a programmable microprocessor or a relay logic system located in a logic cabinet 500. Logic cabinet 500 receives signals from a plurality of ~ensors, : and thes~ signals are used to control the fuel, fuel drain, combugtlon aLr. and atc~ a~ ~ ~ye~:~a~e d~a~-~ ~ed h^~
A ~ id fue7 supply ~D2~ p~efera~ly ~o, 2 2D fuel 3!i oil, is coupled to a fuel llne 504 which is monitored by a low oil press~re switch 506 and hi~'n oi~ press~re switch $08. Disposed in fuel lin~ 504 is a safety shut-off valve 510 which is controlled by a safety shut-of~ solenoid 512.

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Fuel line 504 passes through shut-off valves 514, controlled by shut-off solenoids 516, and then to nozzles 18Ç.
A natural gas supply 520 is coupled to fuel line 522 which is moni*ored by high gas pre~sure switch 524 and low gas pressure switch 526. Disposed in fuel line 522 are safety shut-off valves 528, 530, and vent valve 532 which are controlled by safety shut-off solenoids 534, 536, and vent solenoid 538, respectively. Fuel line 522 passes through shut-off valves 540, controlled by shut-off solenoids 542, on its way to nozzles 186.
An atomizing air source 550 is coupled to an atomizing air line 552 which is monitored by a low atomizing ai~ pressure switch 554. Atomizing air line 552 passes through shut-off valves 556, controlled by shut-off solenoids 558, and proceeds to nozzles 186.
A low combustion air pressure switch 560 for monitoring combustion air pressure is coupled to air intake assembly 18 below combustion air control damper 17, and a system high temperature switch 562 is coupled to the proces ing tube to detect overheating in the system.
The flame safety system also has a flame indicator 570 for detecting the combustion process. In a pulse combustion system, flame indicator 570 may be either an optical scanner for detecting the ultraviolet or infrared light waves radiating from the flame, or a pressure sensor for measuring a positive pressure pulse which is produced by the detonation of fuel in the combustion chamber~ The pressure sensor is calibrated so that it will detect pressures in excess of the supply pressure of the combustion air blower so that it will only measure the component of the total pressure supplied by the burning of the fuel.
The flame safety system will shut off fuel to the pulse combustor under the following conditions: low or high fuel pressure, low combustion or atomizing air pressure, flame out, or high system temperature. When oil is being used, safety shut-off solenoid 512 will close safety shut-off valve 510, and if gas is being used, safety shut-off solenoids 534 and 536 will close safety shut-off valves 528 ; ~,, ~ . . ' `
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and 530, respectively, and vent solenoid 538 will open vent valve 532.
The flame safety system also controls the comhustion chamber fuel drain system~ The pulse combustion system has a special drain valve 580 mounted on outer portion 136 of rotary valve 78, which is coupled to a solenoid 582. The pulse combustor drain valve 580 is opened by the flame safety system whenever there is an attempt to ignite oil either during start-up or during fuel changeover.
When flame indicator 570 detects the ignition of the fuel oil, the flame safety logic closes the combustion chamber drain valve 580 and any excess fuel will have been removed from the chamber.
Process Control System As shown in Fig. 6, the Pulse Combustion Energy System has process controls which allow for automatic control of the system. These controls are designed to check process set points and adjust the operating parameters to maintain the set points. ~he operating set points are adjusted depending on the product to be processed through the system, the rate at which it is processed, etc.
One control loop sets the speed of the rotary valve 78 to vary the operating frequency o~ the pulse combustor 28. A frequency sensor 600 is used to measure the combustion pulse rate which in turn transmits a signal to a controller 602 where the operating frequency set point can be adjusted. Frequency sensor 600 may alternatively be used to measure the rate of air pulses entering combustion chamber 81r The controller 602 sends a signal to a motor control unit 604 to adjust the valve speed and receives a ` feedback signal from a valve motor tachometer 606 to verify the actual valve RPM. Controller 602 and/or contxol unit 604 may be an integral part of rotary valve 78. The adjustment at controller 602 allows the rotary valve 78 ~peed to be set at the natural frequency of pulse combustor 28 or slightly off frequency, depending upon the product being processed. This feature is included because, as the rotary valve 78 speed approaches the natural frequency of the pulse combustor 28, the sonic pressure wave is enhanced, which may increase the processing speed of some products above acceptable levels and cause the processed particle tempera~ure to increase. Products which are more difficult to dry would require the maximum sonic pressure wave ~nd rotary valve 78 is operated at a rate which matches the natural frequency of the engine to achieve this result.
A separate control loop is used to establish the product feed ratP and adjust the feed rate according to the moisture content. When the pulse combustion s~stem is operating, it is necessary to keep the baghouse 60 temperature above the dew point (approximately 2120F in dewatering applications) so that condensing water will not cause the fine particles caught on the bag surface to become wet and stick to the bags. Since the system heat input is set by the desired production rate and it is difficult to know at any instant what the moisture content of the feed will be, a temperature sensor 610 is mounted in the discharge of the baghouse 60. From the sensor 610, a temperature transmitter 612 sends a signal to a temperature controller 614 which sets the baghouse 60 discharge temperature about lOQF above the dew point. The controller 614, in turn, sends a signal to the variable speed motor controller 616 which operates the product feed system 16, setting the speed at which the product is fed to the pul~e combustion system. If the product has less moisture, the feed rate is increased. If the product has more moisture, the feed rate is reduced so that the water to be removed from the product by the system is not greater than the heat which is available to evaporate the water.
A control loop is also provided to allow the operator to set the system firing rate and protect the system from overheating if the product feed should be temporarily interrupted. A temperature sensor 620 measures the temperature at the discharge of the first cyclone collector 52. From the sensor 620 a temperature transmitter 622 sends a temperature signal to a temperature controller 624 where the operator can either establish a control set , - 22 - l 3 1 3042 point or set the system firing rate by hand. The signal from controller 624 sets the position of a fuel control valve 626 and the combustion air control valve 17. The valves both have positioners to tell controller 624 what percentage the valves have opened or closed. This system may also be used to set the pulse combustion system firing rate if the equipment i5 to be operated at less than full capacity. Also, if ~ particular product is hard to dewater or takes longer to dewater, this control loop cuts back the firing rate when the first cyclone collector 52 temperature becomes too high. It also cuts back the firing rate if the product feed is interrupted resulting in an increase in temperature. Xf this control loop cannot cut firing rate sufficiently to maintain the cyclone temperature below a prescribed level, then the flame safety system shuts down the system when the system high temperature switch 562, shown in Fig. 5, activates.
A control loop is al80 provided to control the pressure in processing tube 32. The pressure must be controlled to insure that the proper system pressures are maintained downstream of the pulse combuætor 28 and in receiving section 12. This in turn insures that the flow rate through the collectors is within limits for optimum system performance. The control loop consists of a pressure indicator 630 which is located at the discharge section 34 o~ proceæsing tube 32 and which senses the system pressure.
The signal from the pressure indicator 630 goes to a pressure transmitter 632 and on to a pressure controller 634 which is set to maintain the pressure at the end of processing tube 32. The controller 634 then sends a signal to a power unit 636 that drives an inlet vane control damper 638 on the induced draft fan 69.
If the pulse combustion system i8 used in an application where the load varies and maximum turndown is required, an additional control loop maintains the vapor velocities in the processing tube 32 at the reduced system firing rates. The control loop has a differential pressure transmitter 640 which senses the pressure drop through the processing tube which in turn reflects the proper velocity.
The transmitter 640 sends a signal to a differential pressure controller 642 where the operator can adjust the differential pressure set point according to the desired processing tube velocity. The differential pressure controller 642 sends a signal to a power unit 644 which adjusts the setting of an inlet vane control damper 646 on the recycle fan 76~ At the regular firing rate, the velocity in the processing tube 32 would be higher than the set point so the inlet vane control damper 646 is normally closed. As the firing rate is reduced, the processing tube 32 velocity falls until the set point i5 reach~d. Then the controller 642 starts to open the inlet vane control damper 646 to add recycle air to the processing tube 32 so that the minimum conveying velocity is maintained. The recycle stream is made up of vaporized water and products of combustion which are 10 degrees above the dew point. This means that the recycle stream will not reduce the system ther~oodynamic efficiency nor will it add oxygen to the system which might degrade the particles in the processing tube or create a risk of explosion by mixing added oxygen with unburned combustion fuel or with the fine particles of a combustible product being processed.
Operation The pulse combustion energy system is started, operated, and shut down under the supervision of the flame safety system. This syst~m has the logic to control the light-off sequence timing, to check all permissive limit switches and open the appropriate fuel valves in the proper order during the system start-up. During the system operation, the flame safety system constantly checks that the combustion process is functioning normally and ensures that all the fuel, combustion air and other required services are within acceptable limits to support the combustion process. The system is also used to properly sequence the shut down of the pulse combustor both in the event an emergency situation develops or in the ~ormal process of terminating the system operation.

- 2~ -The pulse combustion energy system operation begins with energizing the flame safety system at cabinet 257. Then air pump assembly 18, the rotary valve 78, the induced draft fan 69, the recycle fan 76 and the other motors in the system are started. The flame safety system then checks and verifies that all the limit switches ~how that the system~s ser~ices are within design specifications.
With all the permissives set, the flame safety system drives combuætion air control damper 17, inlet vane control damper 638 and inlet vane control damper 646 to the full open position prior to the start of the engine purge. At this point, the engine purge timing begins. The purge timer starts, and the rotary valve 78 speed is set to the proper frequency for initial engîne ignition at low fire~ Air pump assembly 18 draws outsid~ air through air inlet filter silencer 19 and into air pump assembly 18 where its pressure is increased by up to-6 PSI. From the airpump assembly 18 the air flows into combustor mounting cell 24 where it passes inside the radiation shield 189. The combustion air then enters the rotary valve 78 on its way to the combustion chamber 81. The combustion chamber receives a minimum of five complete air charges during the purge cycle.
When purging is complete, the flame safety system drive~ combustion air control damper 17, inlet vane control damper 638 and inlet vane control damper 646 to the ignition position. When the d~mpers are proven to be in the ignition position, the flame safety system energizes the two (or more) igniters 187 and opens the gas safety shut-off valves 528, 530 while closing the vent valve 532. The system also opens the gas solenoid valve 540 that supplies gas to the two (or more) fuel nozzles 186 which are adjacent to the two (or more) igniters 187. At this point the ignition tLmer starts and holds the safety shut-off valves 528, 530 open for the 10 second trial for ignition.
The pulse combustion cycle starts when an air pulse from the rotary valve 78 mixes with gas from the two nozzles 186 and the mixture explodes due to the ignition energy from igniters 187. When the fuel and air detonate, ~ 31 3042 the pressure in the combustion chamber 81 increases, causing a back flow of the air in the chamber towards the closed rotary valve 78. As the back flow of air flows through air diode 160, surface 168 in air diode 160 causes the air flowing there along to reverse direction and flow transversely toward surface 164. ~he combination of the reverse momentum of this flow with the scalloped shape o~
surface 164 creates an artificial vena contracta which has the effect of constricting the flow through air diode 160 and reducing the back pressure on the closed rotary valve 78.
I~ the flame safety system detects the proper ignition of fuel with flame indicator 570, it leaves the safety valves open and allows the operator to open the ga~
solenoid valve 540 to the remaining fuel nozzles. On the other hand, if the flame indicator 570 fails to pick up a positive flame signal-within the 10 second trial for ignition, the safety valves 528; 530 are closed and the system returns to its prepurge point in the system start-up program.
When all fuel nozzles 186 are operating and the flame safety system detects a normal fl~me, the system releases dampers 17, 638 and 646 to the combustion control system where the process controls set the pulse combustion firing rate.
The ~lame safety system also contains the logic and control~ to allow a changeover from one fuel to another.
Fuel nozzles 186 are designed to inject gas or liquid fuels or both. During normal operation the nozzles are set to fire on air atomized oil. Air atomized oil is preferable over prior art systems which use pressure-atomized mechanically injected fuel oil because the air atomized oil produces smaller oil drops which vaporize faster. This also ensures that detonation occurs on time due to the initial combu~tion that takes place between the oil and the atomiæing air as the mixture is discharged into the hot combustion chamber.

~ 3~ 3042 Th0 fuel changeover starts by firing all fuel nozzles 186 on natural ~as. The flame safety system checks the oil and atomizing air limit switches to ensure they fit within specifications and then opens the combustion chamber drain valve 5800 The operator opens shut-off valve 514 to allow oil to flow to two (or more) of the nozzles 186 which are firing natural gas. The natural gas atomizes the oil and the mixture immediately ignites. Within 10 seconds the combustion chamber drain valve 580 closes and the operator opens atomizer air valve 556 and closes shut-off valvss 540 on the natural gas system. The atomizin~ air blows the remaining gas out of the fuel nozzles 186 and takes over the function of atomizing the fuel oil. The operator repeats the process and chan~es the remaining two ~or more) nozzles 186 over to firing oil.
This ability to burn two fuels on the same nozzles gives the pulse combustion system additional flexibility over prior art systems in selecting fuels and firing modes.
The new system can be set up to operate as follows:
A) ALL NOZZLES FIRING AIR ATOMIZED OIL
B) ALL N02ZLES FIRING GAS ATOMIZED OI~
C) ~ALF NOZZLES FIRING AIR ATOMIZED OI~ ~ND
HALF NOZZ~ES FIRING GAS ATOMIZED OIL
D) HALF NOZZLES FIRING AIR ATOMIZ~D OIL AND
HALF NOZZLES FIRING GAS
E) H~LF NOZZLES FIRING GAS ATOMIZED OIL AND
H~I,F NOZ2LES FIRING GAS
F) ALL NOZZLES FIRING GAS
The combustion fuel is supplied to the combustion cha~ber 81 at low pressure (below 15 PSIG) so that its flow will be interrupted by the peak combustion pressures in the combustion chamber 81. This means that fuel flow is automatically timed to the pulse frequency of the co~bustion chamber 81 and the fuel system does not need a special valve which is imed to open and close in sync with the variable speed rotary valve 78.
The initial detonation releases heat and creates a preæsure wave. The heat starts to heat up combustion chamber sleeve 80, inner kail pipe 84, and outer tail pipe 86 while the pressure wave stops the flow of the fuel gas and sends a pressure pulse down initial and outer tail pipes 84 and 86, respectively. The momentum of the combustion products moving down the tailpipes with the wave generates a partial vacuum in the combustion chamber that is in sync with the opening of the rotary valve 78. This draws additional charges of air and gas from the val~e and the fuel nozzles 186 which mix rapidly. At this instant the rotary valve 78 closes and the mixture comes in contact with combustion products remaining from the previous cycle which, along with the hot combustion chamber walls, causes the ignition of the new fuel charge. The pulse combustor 28 typically cycles and detonates between 100 and 200 timesper second. Each pulse sends a pressure wave, followed by a partial vacuum, down tail pipes 84 and 86.
During the unit start up and during uel changeover, the temperature in the combustor is likely to ~hi~t. ~his will change the operating frequency. Here the variable speed rotary valve 78 on the combustion air system can be set to follow the frequency change. This improves the safety as well as the reliability of the system.
Once the ~ystem is started up, a slurry, which can consist of up to 99% moisture, is sprayed into the outer tail pipe 86 where it comes into contact with the heat and sonic energy from the pulse combustion process. Nozzles 246 are oriented to effect a prescribed spray configuration so that the slurry is expo ed to the hot gas pulses in a manner which maximizes drying effectiveness. As the mixture flows through processing tube 32, the water is mechanically driven or stripped off the solid particles in the feed by the sonic shock waves and, at the same time, the heat evaporates the moisture, thus completing the drying process in fractions of a second.
The processed particle~ then enter first cyclone collector 52 from which they are discharged through star valve 62 and into the dry product conveying system 64. ~he vapor, with a small percentage of the initial particulate .

' loading, passes out of the first cyclone collector 52 and through silencer 54 into second cyclone collector 56.
Second cyclone collec~or 56 further reduces the dust load in the vapor stream. Most of the remaining dust particles will drop to the bottom of second cyclone collector 56 from which they are discharged through star valve 63 and into the dry product conveying system 64.
At the top part of the second cyclone collector 56 is a baghouse 60 which has fabric bags 61 designed to remove the final and ~mallest particle~ from the vapor stream. The vapor stream moves up second cyclone collector 56 and through the fabric bags 61. The dust particles are deposited on the outside of the fabric bags 61 and the cleaned vapor stream is exhausted through the stack 71. To maintain the porosity of fabric bags 61, in revers~ of the filtering action by blowback fan 66. The dust which has accumulated on fabric-bags 61 is dislodged and falls to ~he bottom of the second cyclone collector 56 where it i9 discharged through star valve 63 and into the dry product conveying system 64.
A~ the system operates, the control system maintains proper valve speed, product feed rate, system firing rate, and vapor velocities to insure optim~m per~ormanceO
The flame safety system is used to shut down the system if the combustion flame goes out, if the operating temperatures approach dangerous levels, or during normal shut down. A normal shu~ down starts with running all the ~eed material out of the slurry feed system. Then the pulse combustion engine 28 is set to low fire and the safety shut-; off valves 510 and/or 528 are closed. All the system motors would be secured with the exception of air pump assembly 18, rotary valve 78 and the induced draft fan 690 If the system is firing oil, the atomizing air system would be left on until the atomizing air can be used to purge out the fuel nozzles 186 by opening valves 556. The airflow would burn out any remaining fuel and cool down the hot pulse combustion engine parts. After a short period the flame - 29 - 1 3 1 30~2 safety system would also secure the remaining motors and the system would be completely shut down.
Conclusion And Alternative Embodiments While the above is a complete description of a preferred embodiment of the present invention, the rapid and efficient dewatering capabilities of the drying apparatus also may be used to process a wide range of products if the sy~tem configuration is modified to meet specific needs of a product. The horizontal configuration shown in Fig~ 1 of the application would normally be used for slurry type products with small particle sizes. In this configuration, the exhaust from the pulse combustor and the steam released in the drying process is used to convey the particles through the system.
If, however, a large particle must be processed which cannot be conveyed through the processing tube by the pulse combustor exhaust, then a vertical and counter flow model of the system may be used. This system is shown in Fig. 7. In this case the feed is introduced at the upper end of the vertical section of the processing tube 32 opposite the pulse combustor 28~ The product feed is drawn towards the pulse combustor by gravity while the sonic energy and heat passes up towards the top of the processing tube 32.
~5 As the product passes through the sonic waves and heat, the moisture turns to steam which increa~es the gas velocity in the processing tube. This velocity change does not affect the larger particles which continue to fall to the bottom of the processing tube from which they are recovered by the large particle recovery system 300, comprising star valve 304 and the large particle conveying system 308. The dust or smaller particles which may be in the feed, or which may.be detached from the large particles during the drying process, are picked up by the exhaust and steam and are conveyed through the baffle assembly 46 and on to the receiving section 12 for recovery.
The vertical configuration may also operate as a parallel flow unit if a slurry is introduc~d into the pulse - 30 ~ 1 3 1 3042 combustor exhaust by nozzles extending through outer tail pipe 86 as shown for the horizontal configuration of the system in Fig. 1.
The vertical configuration also has an optional recycling section 72, similar in theory and construction to the recycling section for the horizontal unit, and a control loop, similar to the one shown in Fig~ 6, to establish the exhaust and steam velocity in the processing ~ube. This velocity may be altered in order to establish a di~tribution of particles which either fall to the bottom of the processing tube or are carried over to the receiving section 12, i.e., this control loop acts as a primitive separator.
Also, this control loop determines product stay time in the processing tube which establishes the dryness of the final product.
The remainder of the vertical system is identical in function to the horizontal confi~uration of the system.
The pulse combustion energy system may be used for many different applications such as firing boilers, calcining minerals, vaporizing products for distillation, and other chemical processes. In these applications, the pul~e combustor may operate with a liquid oxidizer, instead of a gaseous oxidizer such as air, flowing into rotary valve 78. In fact, it i8 within the scope of the preæent invention to use rotary valve 78 and pulse combustor 28 with any oxidizing agent - that is, any substance which oxidizes by takin~ up electrons to form a new molecule and in the process releases energy in the foxm of heat and pressure.
Depending on the application, the puls~ combustor may operate oxidizer rich, ætoichiometrically, or in a redu~ing mode by varying the setting of combu~tion air control damper 17 in response to a gas analyzer (not shown) which samples the combustion products emitted from outer tail pipe 86.
The systems described herein are for dewatering, so the collection systems shown are specifically designed for dewatering applications. If the pulse combustion energy ~ystem were to be applied to another process then the downstream equipment would be selected accordingly.

- 31 - I 3 ~ 3042 Consequently, the foregoing description should not be used to limit the scope of the invention which is properly set out in the claims.

'~

,. :~.

.

Claims

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means, in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;
means for flowing a separate fluid into the processing tube proximate the upstream end thereof;
means for detecting a prescribed differential pressure through the processing tube; and means, responsive to the pressure detecting means for modulating the flow of fluid into the upstream end of the processing tube.

2 A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means, in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;
a conduit in fluid communication with the receiving means for receiving vapor flowing therefrom and extending proximate to the upstream end of the processing tube; and wherein the processing tube has an aperture for directing the vapor from the conduit into the processing tube.
3. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
and means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means, in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;
means for flowing a separate fluid into the processing tube proximate the upstream end thereof;
wherein the receiving means comprises a first cyclone collector having an inlet and an outlet, the inlet being in fluid communication with the downstream end of the processing tube;
wherein the fluid flowing means further comprises a conduit in fluid communication with the outlet of the first cyclone collector for receiving vapor flowing therefrom, the conduit extending to the upstream end of the processing tube; and wherein the processing tube has an aperture proximate the upstream end in fluid communication with the conduit for directing the vapor into the processing tube.

4. A drying apparatus as in claim 3 further comprising means, disposed at the outlet of the first cyclone collector, for suppressing sound.

5. A drying apparatus as in claim 3 further comprising a second cyclone collector having an inlet and an outlet, the inlet of the second cyclone collector being in fluid communication with the outlet of the first cyclone collector.
6. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means, in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;

wherein the receiving means comprises:
a first cyclone collector having an inlet and an outlet, the inlet being in fluid communication with the downstream end of the processing tube; and a second cyclone collector having an inlet and an outlet, the inlet of the second cyclone collector being in fluid communication with the outlet of the first cyclone collector; and wherein the fluid flowing means further comprises a conduit in fluid communication with the outlet of the second cyclone collector for receiving vapor flowing therefrom, the conduit extending to the upstream end of the processing tube, and wherein the processing tube has an aperture proximate the upstream end in fluid communication with the conduit for directing the vapor into the processing tube; and means for flowing a separate fluid into the processing tube proximate the upstream end thereof.

7. A drying apparatus as in claim 6 further comprising means, disposed at the outlet of the second cyclone collector, for filtering particles in the high temperature pulses passing therethrough.

8. A drying apparatus as in claim 5 further comprising means, disposed at the outlet of the second cyclone collector, for suppressing sound.
9. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
means for selectively modulating the emission of pulses from the pulse combustor;
the pulse modulating means comprising:
means for detecting a prescribed temperature in the receiving means; and means responsive to the temperature detecting means for selectively modulating the emission of pulses from the pulse combustor;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being; in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube; and means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom.

10. A drying apparatus as in claim 9 wherein the pulse modulating means comprises means for modulating the flow of fuel into the pulse combustor.

11. The drying apparatus according to claim 10 wherein the fuel flow modulating mans comprises means for selectively setting a fuel valve to one of a plurality of positions between a fully open and fully closed position.
12. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
means for selectively modulating the emission of pulses from the pulse combustor, the pulse modulating means comprising:
means for detecting a prescribed frequency of high temperature pulses; and means responsive to the frequency detecting means for modulating the emission of pulses from the pulse combustor;

a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube; and means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom.

13. A drying apparatus in claim 12 wherein the pulse modulating means further comprises means for modulating the flow of oxidizer into the pulse combustor.
14. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means for modulating the flow into the processing tube of foreign material to be processed, the flow modulating means comprising:
means for detecting a prescribed temperature in the receiving means; and means responsive to the temperature detecting means for modulating the flow into the processing tube of foreign material to be processed; and means, in fluid communications with the downstream end of the processing tube, for receiving the foreign material flowing therefrom.
15. A drying apparatus as in claim 14 wherein the prescribed temperature is greater than or equal to 212° F.
16. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber for emitting high temperature pulses;
a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream and being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream and of the processing tube;
means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom;
means for modulating the flow rate through the processing tube of foreign material to be processed therein, the flow rate modulating means comprising:
means for detecting a prescribed pressure in the receiving means: and a fan in fluid communication with the processing tube for selectively drawing vapor from the processing tube in response to the pressure detecting means.
17. A drying apparatus comprising:
a pulse combustor having a combustion chamber and a generally tubular outlet in fluid communication with the combustion chamber emitting high temperature pulses;

a processing tube for flowing a foreign material to be processed therethrough, the processing tube having an axis including upstream and downstream ends, the upstream end being in fluid communication with the outlet of the pulse combustor for receiving the high temperature pulses emitted therefrom;
means for introducing the foreign material to be processed into the high temperature pulses flowing through the upstream end of the processing tube;
means in fluid communication with the downstream end of the processing tube, for receiving the foreign material flowing therefrom, means for modulating the flow rate through the processing tube of foreign material to be processed therein, the flow rate modulating means comprising a conduit in fluid communication with the receiving means for receiving vapor flowing therefrom, the conduit extending proximate to the upstream end of the processing tube, and wherein the processing tube has an aperture for directing the vapor from the conduit into the processing tube.

18. A drying apparatus as in claim 17 wherein the flow rate modulating mean further comprises:
means for detecting a prescribed differential pressure through the processing tube; and means responsive to the pressure detecting means, for modulating the flow of vapor from the conduit into the upstream end of the processing tube.
19. A drying apparatus comprising:
an elongated combustion tube having an upstream end and a downstream end;
an oxidizer intake valve at the upstream end in fluid communication with the tube for supplying the oxidizer to the tube in the form of discrete oxidizer pulses, the valve including:

first and second coaxially mounted valve members in close proximity and adapted to rotate relative to each other, each member having an aperture for the flow of oxidizer therethrough and which are arranged so the apertures move into and out of registration during relative rotation of the members;
means defining an oxidizer inlet chamber on a side of one of the members;
unidirectional fluid flow means in fluid communication with the chamber, disposed between the oxidizer inlet chamber and the combustion tube, and defining an outlet from the oxidizer inlet chamber for promoting the flow of fluid from the oxidizer inlet chamber, through the outlet and into the combustion tube, and for inhibiting the flow of fluid from the combustion tube, through the outlet and into the oxidizer inlet chamber;
means for adding fuel to the oxidizer pulses proximate the upstream end of the combustion tube so that the fuel cam be combusted to generate hot gas pulses which propagate through and exit from the combustion tube at the downstream end;
a processing tube for flowing a material to be processed therethrough, the processing tube having upstream and downstream ends, the upstream end being fluid communication with the downstream end of the combustion tube for receiving the hot gas pulses emitted therefrom;
means for flowing material to be processed into the upstream end of the processing tube; and means coupled to the downstream end of the processing tube, for receiving the material flowing therefrom.

20. A drying apparatus as in claim 19 further comprising means for modulating the emission of pulses from the pulse combustor.

21. A drying apparatus as in claim 20 wherein the pulse modulating means comprises means for modulating the flow of oxidizer into the pulse combustor.

22. A drying apparatus as in claim 21 wherein the oxidizer flow modulating means includes means for selectively varying the relative rotational speed of the valve members.

23. A drying apparatus as in claim 22 wherein the pulse modulating means further comprises means for detecting a prescribed frequency of pulses emitted from the combustion tube, and wherein the oxidizer flow modulating means varies the relative rotational speed of the valve members in response to the frequency detecting means.