Patent Document

This application, which contains no new matter, is a CONTINUATION-IN-PART of application Ser. No. 12/290,748, filed 2008, Nov. 3, CIP of Ser. No. 11/441,320, filed 2006 May 24 by the present inventor. The subject matter therein is hereby incorporated by reference into this application. 
     CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is a CONTINUATION-IN-PART of application Ser. No. 12/290,748, filed 2008, Nov. 3, CIP of Ser. No. 11/441,320. 
    
    
     FEDERALLY SPONSORED RESEARCH 
     Not Applicable 
     SEQUENCE LISTING OR PROGRAM 
     Not Applicable 
     BACKGROUND OF THE INVENTION 
     Field of Invention 
     This invention relates to an exhaust apparatus and method of an ambient air intake cooling device with a rotating blade assembly which significantly reduces air pollution in the form of greenhouse gases, hydrocarbons, oxides of nitrogen emissions and other gases and pollutants not yet required to be tested, exhaust noise and temperature of the exhaust gases. It improves the efficiency, duration and fuel economy of the underlying electromotive driver, such as a diesel driven internal combustion engine. This unit can be used to produce a major increase in both the cooling of exhaust gases, and a major increase in obtainable vacuum. This invention also finds application in improving the cooling of the steam in the operation of steam power plants, chemical plants, oil refineries, electric generating stations and cooling towers. 
     Background of the Invention 
     The embodiment of this exhaust apparatus was first conceived and built by Donald M. Toney in 1938. It was first tested in 1939 on a 4-cylinder  1930  “Model A” Ford. With the exhaust apparatus installed into the exhaust system in place of the muffler, the car was able to attain the speed of over 79 miles per hour. Without the exhaust apparatus, approximately 60 miles per hour was as fast as could be attained. The car was able to go 19 miles per hour faster with the exhaust apparatus installed than without the exhaust apparatus. After the test the oil pan was removed to inspect the rod and main bearings. It was found, surprisingly, that there was no damage to any of the bearings in the scoop oil system. 
     In 1963 the device was re-designed and built a new exhaust apparatus of different metals to test the control of steam. It was discovered that the exhaust apparatus was able to change 500 degree live steam to liquid water with a temperature of 90 degrees in only 24 inches. 
     The device was installed an exhaust apparatus in a 4-cylinder Ford Pinto and was able to accelerate faster than a Ford V/8. 
     In 1978 the device was installed an exhaust apparatus in a 1972, 1800 cc Volkswagen and was able to skid the back tires for 20 feet in low gear, 10 feet in second gear, to speeds of approximately 70 mph in ⅓ of a mile. With the exhaust apparatus installed and the vacuum it created, the engine was so cooled that the number  3  cylinder was no longer a heat problem. 
     In 2000 and 2001 the device was redesigned, re-built and tested over a 15 month period, with a resulting new model of the exhaust apparatus. 
     Seven new blade arrangements for the device were made to find the most effective arrangement and the front housing was redesigned for more efficient cooling to the mixing chamber. The device was able to attain 1800 to 2000 RPM over the red line for the engine without any damage to the bearings. The oil temperature was about 93 degrees instead of 190 degrees, which would extend the life of the viscosity of the oil. The vacuum created by the exhaust apparatus cooled the metal of the engine by relieving the exhaust gas so rapidly that almost no carbon remained in the cylinder or valve ports. This vacuum relieved the exhaust so rapidly, that the back pressure was nearly nil and valve floating was overcome, letting the engine attain much higher RPM. With temperature lowered metal fatigue is greatly lessened. All this was accomplished with handmade parts. With perfect casting of extrusion of parts, the efficiency will be greatly increased. 
     Prior Art 
     U.S. Pat. No. 4,912,927 describes a prior air intake device and a rotary fan blade (rotating blade) assembly. Intake air contacts the exhaust gases in a counter-flow direction, that is, in a direction opposite to the direction of flow of exhaust gases. 
     The major differences between U.S. Pat. No. 4,912,927 (prior unit) and application Ser. No. 12/290,748 (this exhaust apparatus) are, this exhaust apparatus produces a major reduction in:
         (a) Greenhouse gases (CO and CO 2 ). (See  FIGS. 10-15 .)   (b) Hydrocarbon emissions (HC). (See  FIGS. 10-15 .)   (c) Oxides of nitrogen emissions (NO x ). (See  FIGS. 10-15 )
 
In addition this exhaust apparatus produces:
   (d) Virtually no unburnt fuel remaining in combustion chamber.   (e) A major increase in cooling of exhaust gases. (See  FIGS. 13 and 14 .)   (f) A major increase in engine vacuum compared to the prior art. (See  FIG. 13 .)   (g) The prior unit is driven from the front and must be driven by a belt-drive assembly, which limits its mounting location, and its ability to be mounted to modern engine&#39;s belt system. This exhaust apparatus is driven from the rear and is electrically driven and can be mounted almost anywhere.   (h) The prior unit contains a rotating mixing chamber, whereas in this embodiment of the exhaust apparatus the cooling chamber is stationary.   (i) This embodiment of the exhaust apparatus has fewer moving parts, is easier to manufacture and assemble.
 
This embodiment of the exhaust apparatus reduces the following engine performance parameters:
   (a) Back-pressure. (See  FIG. 13 .)   (b) Exhaust noise. (See  FIG. 14 .)   (c) Engine temperature. (See Background—Field of Invention.)   (d) Exhaust temperature. (See Background—Field of Invention.)   (e) Exhaust pollutants. (See  FIGS. 10-14 .)
 
Additionally this unit provides:
   (f) Extended engine life. (See Background—Field of Invention.)   (g) Extended oil life. (See Background—Field of Invention.)   (h) Relief of crystallization of engine parts. (See  FIGS. 10-14 )   (i) Increased power. (See Background—Field of Invention.)   (j) Greater engine efficiency. (See  FIGS. 13 and 14 .)   (k) Reduced fuel consumption. (See Background—Field of Invention.)       

     BRIEF SUMMARY OF THE INVENTION 
     This invention relates to an exhaust apparatus and method of an ambient air intake cooling device with a rotating blade assembly. The embodiment of the exhaust apparatus consists of three main sections, the front section which contains an air deflector and mixing chamber, a middle section contains a centrifuge and rotating blade assembly and a rear section which contains deflecting blades and drive mechanism. 
     The idea of the invention of this exhaust apparatus is to make a unit that can be mounted anywhere on a vehicle and work properly without a lot of alterations to the vehicle. 
     This embodiment of the exhaust apparatus would give greater fuel mileage and cool the engine, relieving the backpressure on the pistons by creating a high vacuum in the exhaust pipes to take away any unburnt fuel. This also relieves crystallization and carbonization of the engine&#39;s parts. 
     This allows the valves to work normally without a floating condition. Without unnecessary backpressure in the exhaust valve port area there is less pressure of the down stroke of the pistons on the rod bearings at the crankshaft, letting the engine run at higher revolutions per minute without any damage to the bearing surfaces. This also lengthens the life of the rod-bearings and the polished area of the crankshaft, thereby lengthening the life of the engine. 
     This embodiment of the exhaust apparatus also cools the engine, cutting down the high heat in the piston and valve port areas lessening the crystallization of the engine&#39;s metal, making the engine last much longer. Removing the hot, unburned fuel gases lets the piston ring springs maintain their expansion without becoming fouled. This allows the engine to run longer without the necessity of costly repairs. Cutting down wear of the engine&#39;s parts extends the engine&#39;s life by thousands of miles before overhaul of the engine is necessary. 
     Safer, cooler exhaust temperatures are accomplished by the vacuum created by the exhaust apparatus in the exhaust pipes from the engine to the exhaust apparatus. Normal temperature at the end of an exhaust tail pipe is approximately 750 to 1200 degrees Fahrenheit, whereas with the exhaust apparatus installed, the temperature becomes much cooler. The temperature at the engine&#39;s exhaust ports is approximately 500 degrees Fahrenheit. The exhaust apparatus drops the temperature so rapidly by its vacuum that in a short distance the temperature drops to approximately 100 to 150 degrees. The temperature of the discharging of the exhaust gases and chilled air from the turbine cools down to approximately 97 to 140 degrees. You may comfortably place your hand on the surface of the rear housing without discomfort from exhaust heat. See  FIG. 15 . 
     Since the exhaust apparatus has only one moving part, the simplicity of its design leaves very little to maintain and align, which should be able to be accomplished by any good automobile mechanic. Driven by an electric motor, the exhaust apparatus could be placed in place of the muffler system, making a clean installation where it would be very easy to service. 
     The exhaust apparatus can be placed anywhere in the exhaust system of any Otto cycle vehicle. This exhaust apparatus has the ability to replace the muffler system, resonator and tailpipes, since the exhaust pipes from each bank of the engine are fed directly into the exhaust apparatus for eliminating most of the harmful exhaust gases. See  FIG. 15 . 
     With the addition of the exhaust apparatus, the modern Otto cycle engine could be free-breathing again. It has the ability to eliminate most of the electronic controls of the smog equipment mounted on the engine. The catalytic burner could also be removed as the exhaust apparatus eliminates the need for this equipment. 
     By using an electric drive we are able to control the revolutions per minute desired for best performance. 
     The exhaust apparatus has the ability to clean and cool the exhaust system to the extent that the existing emissions become so low that they surpass the 2012 emission requirements. See  FIGS. 10-15 . With the exhaust apparatus in operation, the backpressure from the valve ports is relieved to give approximately an 1800-2000 increase in revolutions per minute without endangering engine parts. 
    
    
     
       BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS 
       Figures 
         FIG. 1  shows a partial cross-section and side elevation of the unit, with the placement of all the parts. 
         FIG. 2  shows a schematic representation of the ambient air, chilled air, chilled exhaust gas and gaseous mixture flows. (See  FIG. 13  showing Test Results for Engine Speed, Chilled Air Velocity, Temperature and Inches of Vacuum.) 
         FIGS. 3A and 3B  show a side view ( 3 A) and end view ( 3 B) of the front housing. 
         FIG. 4  shows a side view of the chilling air deflector, blades, mixing chamber, and exhaust gases intake pipe. 
         FIG. 5  shows a front view of the chilling air deflector, blades, mixing chamber and exhaust gas intake pipes. 
         FIG. 6  shows a top view of the rear housing, coupling screws and alignment bolts for blade assembly. 
         FIG. 7  shows an end view of the rear bearing housing, deflecting blades and rear bearing housing supports and drive shaft. 
         FIG. 8  shows the sample calculations for the percentage reduction and arithmetic difference in hydrocarbon emissions. 
         FIG. 9  shows the sample calculations for the percentage reduction and arithmetic difference in carbon monoxide emissions. 
         FIG. 10  shows the tabulated results for the percentage change and arithmetic difference calculations for exhaust gas emissions produced by a diesel powered engine, with and without the unit running. 
         FIG. 11  shows the tabulated results for the percentage change and arithmetic difference calculations for exhaust gas emissions produced by a diesel powered engine, with and without the unit running. 
         FIG. 12  shows a compilation of tabulated test results for the percent change in emissions for a series of four gas emission tests of a diesel powered engine. 
         FIG. 13  shows the test data and sample results for diesel engine speed, air velocity, temperature and vacuum with two different nose cones, tests performed on 2001 Aug. 26. 
         FIG. 14  shows the data sheet for centrifuge vacuum obtained with seven different centrifuge and blade configurations, at different RPM with and without nose cone collar, performed on 2001 Aug. 25 and 2001 Sep. 13. 
         FIG. 15  shows a visual picture of the arrangement of an engine, the exhaust pipes, exhaust apparatus and electrical drive motor. 
     
    
    
     DRAWINGS 
     Reference Numerals 
     
         
           20  exhaust apparatus 
           30  front housing 
           31  ambient air inlet port 
           32  outer wall of front housing 
           33  fastening screws ( 8 ) 
           34  ambient air 
           35  chilled air 
           36  chilling air deflector and mixing chamber 
           37  chilling, deflecting and supporting blades ( 4 ) 
           38  engine exhaust and embodiment of the exhaust apparatus entrance flanges 
           39  embodiment of the exhaust apparatus exhaust gas intake pipes 
           40  vacuum sampling ports 
           41  exhaust gas chilling and mixing chamber 
           42  centrifuge front deflector 
           43  exhaust gases 
           50  centrifuge and rotating blade assembly 
           51  centrifuge mixing chamber 
           52  deflecting collars 
           53  exhaust gas deflecting blades ( 18 ) 
           54  deflecting blade exhaust gas entry ports 
           55  deflecting blade exhaust gas exit ports 
           56  centrifuge rear deflector 
           57  clearance space between blade assembly and rear housing 
           58  chilled air and exhaust gas mixture 
           60  rear housing 
           61  uniform cross-sectional wall 
           62  rear bearing housing 
           63  deflecting blades and rear bearing housing supports 
           64  rear support adjusting screws ( 12 ) 
           65  chilled air and exhaust gas mixture discharge port 
           66  drive shaft 
           67  drive shaft coupling 
           68  drive shaft coupling bolts 
           69  electric motor drive shaft 
           70  electric motor 
           71  exhaust pipes 
           72  engine exhaust flange 
           73  engine 
       
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The embodiment of the exhaust apparatus  20  consists of three sections, a front section, a middle section assembly and a rear section. The front section consists of a front housing  30  which features a conically shaped outer wall  32 , an ambient air inlet port  31 . The front housing  30  is fastened to the rear housing  60  with eight fastening screws  33 . The centrifuge and rotating blade assembly  50 , draws ambient air  34  into the ambient air inlet port  31 . The ambient air  34  passes over the chilling air deflector and mixing chamber  36 . The ambient air  34  is chilled by the front housing  30 , chilling air deflector and mixing chamber  36 , and the four chilling, deflecting and supporting blades  37 . The chilled air  35  moves past chilling, deflecting and supporting blades  37  and moves over the exhaust gas intake pipes  39  and the exhaust gas chilling and mixing chamber  41 , chilling both items and fills the clearance space between blade assembly and rear housing  57  and passes over the exhaust gas deflector blades  53  of the centrifuge and rotating blade assembly  50 . 
     Engine exhaust gases  43  are drawn into the unit, passing through engine exhaust and exhaust apparatus entrance flanges  38  and exhaust apparatus exhaust gas intake pipes  39 , which each contain a vacuum sampling port  40 . The exhaust gases  43  continue into exhaust gas chilling and mixing chamber  41  and contact centrifuge front deflector  42 , which deflects the exhaust gases  43  into centrifuge and rotating blade assembly  50 . All of the items in the front section are made of aluminum, except the fastening screws  33  which are tempered-steel Allen head screws. 
     The middle section contains centrifuge and rotating blade assembly  50  which draws exhaust gases  43  into centrifuge mixing chamber  51 . The exhaust gases  43  are drawn past deflecting collars  52  and enter the exhaust gas deflector blades  53  by way of blade exhaust gas entry ports  54 , which are in the bottom of exhaust gas deflector blades  53 . Exhaust gases  43  then exit blades  53  via blade exhaust gas exit ports  55 . While in the mixing chamber  51 , exhaust gases  43  also strike centrifuge rear deflector  56 , which deflects the gases upwards and into the entry ports  54  and helps equalize and maintain the flow of exhaust gases  43 . Exhaust gases  43  mix with chilled air  35  in clearance space between blade assembly and rear housing  57  and in the region around and beyond the center blades of the centrifuge and blade assembly  50 . 
     The rear section consists of rear housing  60 , which contains a uniform cross-sectional wall  61 , rear bearing housing  62 , deflecting blades and rear bearing housing supports  63  which are fastened by rear support adjusting screws  64 . Rear support adjusting screws  64  permit motion of rear bearing housing supports  63  which permit adjustment of centrifuge and rotating blade assembly  50 . Rear bearing housing  62  holds the rear bearing, which is not shown, supporting drive shaft  66 , which is fastened to centrifuge and rotating blade assembly  50  with two machine screws, which are not shown, and drives the centrifuge and rotating blade assembly  50 , which draws the gases into the exhaust apparatus  20  invention. 
     Drive shaft coupling  67  is attached to drive shaft  66  by drive shaft coupling bolts  68 . An electric motor shaft  69  is inserted into outer end of drive shaft coupling  67  and drives drive shaft  66 . The chilled air and exhaust gas mixture  58  exits the unit through chilled air and exhaust gas discharge port  65 . 
       FIG. 2  shows the flow of ambient air  34 , chilled air  35 , exhaust gases  43  and the chilled air  35  and chilled air and exhaust gas mixture  58  at the various places in unit leaving the unit. This figure omits a view of the electric motor shaft. 
       FIG. 3  shows a side view ( 3 A) and end view ( 3 B) of the front housing  30 , eight tapped holes  33  for fastening the front housing to the rear housing and ambient air inlet port  31 . 
       FIG. 4  shows a top view of the chilling air deflector  36 , 3 of the 4 chilling, deflecting and supporting blades  37 , exhaust apparatus exhaust gas inlet pipes  39 , exhaust gas chilling and mixing chamber  41 , and centrifuge front deflector  42 . 
       FIG. 5  shows an end view of the chilling air deflector and mixing chamber  36 , four chilling, deflecting and supporting blades  37 , and exhaust apparatus exhaust gas intake pipes  39 . 
       FIG. 6  shows a top view of the rear housing  60 , fastening screws  33 , exhaust apparatus exhaust gas intake pipes  39 , uniform cross-sectional wall  61 , rear support adjusting screws  64 , and chilled air and exhaust gas mixture discharge port  65 . 
       FIG. 7  shows an end view of the rear bearing housing  62 , four deflecting blades and rear bearing housing supports  63  and drive shaft  66 . 
       FIG. 8  shows the sample calculations for the percentage reduction and arithmetic difference in hydrocarbon emissions. 
       FIG. 9  shows the sample calculations for the percentage reduction and arithmetic difference in carbon monoxide emissions. 
       FIG. 10  shows the tabulated results for the percentage change and arithmetic difference calculations for exhaust gas emissions produced by a diesel powered engine, with and without the unit running. 
       FIG. 11  shows the tabulated results for the percentage change and arithmetic difference calculations for exhaust gas emissions produced by a diesel powered engine, with and without the unit running. 
       FIG. 12  shows a compilation of tabulated test results for the percent change in emissions for tests  1 ,  2 ,  3 , and  4  of a four gas emission test of a diesel powered engine. 
       FIG. 13  shows the test data and sample results for diesel engine speed, air velocity, temperature and vacuum with two different nose cones, tests performed on 2001 Aug. 26. 
       FIG. 14  shows the data sheet for centrifuge vacuum obtained with seven different centrifuge and blade configurations, at different RPM with and without nose cone collar, performed on 2001 Aug. 25 and 2001 Sep. 13. 
       FIG. 15  shows a visual picture of the arrangement of an engine, the exhaust pipes, exhaust apparatus and electrical drive motor. 
     OPERATION OF THE INVENTION 
     Operation 
     FIG.  1   
     Electric motor shaft, which is not shown, is inserted into the drive shaft coupling  67 , is fastened with coupling bolts  68  and turns drive shaft  66 . The drive shaft  66  is fastened to centrifuge and rotating blade assembly  50  and drives the blade assembly  50  which creates a vacuum of 3.3 inches (Hg) and draws ambient air  34  and exhaust gases  43  into the unit. The blade assembly  50  creates a swirling and chilling effect for both the ambient air and exhaust gases. In addition ambient air  34  is drawn into each of the 4 quadrants of the front housing by the blades of chilling, deflecting and supporting blades  37 . Within each quadrant, the blades swirl and chill the ambient air  34  to become chilled air  35 . The chilled air  35  moves through the unit cooling interior parts and flows parallel to and mixes with the exhaust gases  43  in clearance space between blade assembly and rear housing  57  and in the region behind the first set of blades  52  and beyond those blades of the centrifuge and blade assembly  50 . Further mixing occurs in the space between deflecting blades and rear bearing housing supports  63 . The chilled air and exhaust gas mixture passes through the four quadrants enclosed by rear bearing housing supports  63  and exits the unit via the exhaust port  65 . The vacuum created by the rotating blades  60  also removes virtually all the unburned fuel in the combustion chamber. 
     Operation 
     FIG.  2   
     Ambient air  34  is drawn into the front housing  30  contacts the outer wall of the exhaust apparatus  32  chilling air deflector and mixing chamber and the chilling, deflecting and supporting blades and becoming chilled air  35  as a result. Exhaust gases  43  enter the unit and flow into exhaust gas chilling and mixing chamber  41 , pass into the centrifuge mixing chamber  51 , strike the deflecting collars  52  enter deflecting exhaust gas entry ports  54 , pass through the blades of centrifuge and blade assembly  50  and exit through deflecting blade exhaust exit ports  55 . Exhaust gas  42  mixes with chilled air  35  in clearance space between blade assembly and rear housing  57  and in the region behind the first set of blades  52  and beyond those blades of the centrifuge and blade assembly  50 . Further mixing occurs in the space between deflecting blades and rear bearing housing supports  63 . Chilled air  35  flows parallel to and mixes with the exhaust gases  43  and becomes chilled air and exhaust gas mixture  58 , which exits through the chilled air and exhaust gas discharge port  65 . 
     Operation 
     FIG.  15   
     A four cylinder engine is connected to the exhaust apparatus  20  by exhaust pipes which leave the engine and enter into the exhaust apparatus  20  where exhaust gases  43  become chilled and temperatures are lowered from approximately 464 degrees Fahrenheit at the engine to an exhaust temperature of approximately 120 degrees Fahrenheit at the rear of the exhaust apparatus. The surface temperature of the exhaust pipes leaving the engine exhaust flanges is approximately 464 degrees. In the short distance from the engine exhaust and turbine entrance flanges  38  connecting the exhaust pipes to the exhaust apparatus  20  the temperature drops to approximately 158 degrees, which is approximately a 300 degree temperature drop. Then in the short one inch distance from the connecting engine exhaust and turbine entrance flanges  38  to the outer surface of the exhaust apparatus  20  an astounding approximately 100 degrees change of temperature takes place. Therefore, from the engine to the outer surface of the exhaust apparatus  20  is a drop in temperature of approximately 360 degrees. Within the exhaust apparatus  20  itself, when it is in motion, a great change in temperature takes place. The exhaust gases  43  come out of the deflecting blade exhaust gas exit ports  55  and blend with the chilled air  35 , becoming the chilled air and exhaust mixture  58  at a temperature of approximately 120 degrees when expelled from the unit. The surface skin of the rear housing  60  of the exhaust apparatus  20  is approximately 97 degrees. See Operation— FIGS. 1 and 2 . See  FIG. 13  for detail of vacuum attained and air velocity flows and how the vacuum changes the temperatures of the exhaust system. 
     This embodiment of the exhaust apparatus  20  is not to be limited by the embodiment shown and described above but only in accordance with the scope of the appended claims. For example, it is believed that the embodiment of the exhaust apparatus  20  can control temperatures in conventional chemical and electricity producing plants including refineries. Result: surprisingly low exhaust temperatures of downstream products and by-products. Hence, unit designs can be maximized, say reducing the number of cooling towers and/or height or number of emission reducing stacks as well as allowing different fuel charge such as garbage. 
     ADVANTAGES 
     From the description, test data, calculations and tabulated results above, a number of advantages of this embodiment of the exhaust apparatus become evident: 
     (a) The unit can be used to create a vacuum at the exhaust valves of the engine which serves to remove virtually all the unburnt fuel in the combustion chamber, which significantly reduces greenhouse gases including (CO and CO 2 ), hydrocarbon emissions (HC), oxides of nitrogen emissions (NO x ) and other gases and pollutants not yet required to be tested. 
     (b) The unit can be used to produce a major increase in cooling of exhaust gases, and a major increase in obtainable vacuum. 
     (c) This unit is driven from the rear for ease of placement. 
     (d) This unit contains a rotating mixing chamber that allows the gases to be blended and separated more easily. 
     (e) This embodiment of the exhaust apparatus has few moving parts, making it easier to manufacture and assemble. This embodiment of the exhaust apparatus significantly reduces the following engine performance factors: 
     (f) Back-pressure 
     (g) Exhaust noise 
     (h) Exhaust temperature 
     (i) Exhaust pollutants 
     Although the description above contains many specificities, these should not be construed as limiting the scope of the embodiment but as merely providing illustrations of some of the presently preferred embodiments. 
     CONCLUSION, RAMIFICATION, AND SCOPE 
     Accordingly, the reader can see that this unit can be used to reduce pollution in the form of greenhouse gases (CO and CO 2 ), hydrocarbon emissions (HC), oxides of nitrogen emissions (NO x ) and other gases &amp; pollutants not yet required to be tested. In addition, this unit can be used to produce a major increase in both the cooling of exhaust gases, and a major increase in obtainable vacuum in the exhaust system. This unit has fewer moving parts, is easier to manufacture and assemble. Furthermore, the unit significantly reduces the following engine performance factors: back-pressure, exhaust noise, engine and exhaust temperatures, and exhaust pollutants. Also the unit can be used to extend engine life, extend oil life, relieve the crystallization of engine parts, increase power, provide greater engine efficiency, and increase gas mileage. 
     Although the description above discusses many specificities, these should not be construed as limiting the scope of the exhaust apparatus but merely providing some of the features of this exhaust apparatus. For example, the unit was primarily fabricated from aluminum, but the unit could be fabricated of ferrous or other non-ferrous alloys, metals, plastic, glass, chemical elements, phenolic resin, other resins or any other material that is suitable for this application. This unit was formed by machining but it could also be cast, extruded, molded, pressed, poured or any other forming process.

Technology Category: f