US3712065A - Antipollution exhaust system for an internal combustion engine - Google Patents

Antipollution exhaust system for an internal combustion engine Download PDF

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Publication number
US3712065A
US3712065A US00095319A US3712065DA US3712065A US 3712065 A US3712065 A US 3712065A US 00095319 A US00095319 A US 00095319A US 3712065D A US3712065D A US 3712065DA US 3712065 A US3712065 A US 3712065A
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Prior art keywords
exhaust
gas
jet
internal combustion
passage
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US00095319A
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English (en)
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R Hurst
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Madison Management Group Inc
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Clevepak Corp
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Assigned to CITIBANK, N.A. AS AGENT FOR CITIBANK, N.A., THE BANK OF NEW YORK BANK OF MONTREAL, AND FIRST WISCONSIN NATIONAL BANK OF MILWAUKEE reassignment CITIBANK, N.A. AS AGENT FOR CITIBANK, N.A., THE BANK OF NEW YORK BANK OF MONTREAL, AND FIRST WISCONSIN NATIONAL BANK OF MILWAUKEE MORTGAGE (SEE DOCUMENT FOR DETAILS). Assignors: CLEVEPAK CORPORATION A DE CORP.
Assigned to CITIBANK, N.A., AS AGENT FOR ITSELF; BANK OF NEW YORK, THE; BANK OF MONTREAL AND FIRST WISCONSIN NATIONAL BANK OF MILWAUKEE reassignment CITIBANK, N.A., AS AGENT FOR ITSELF; BANK OF NEW YORK, THE; BANK OF MONTREAL AND FIRST WISCONSIN NATIONAL BANK OF MILWAUKEE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CLEVEPAK CORPORATION, A CORP.OF DE
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/30—Arrangements for supply of additional air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2700/00—Measures relating to the combustion process without indication of the kind of fuel or with more than one fuel
    • F02B2700/02—Four stroke engines
    • F02B2700/021—Four stroke engines with measures for removing exhaust gases from the cylinder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • ABSTRACT A system for reducing the back pressure on the exhaust valves of an internal combustion engine which includes, for instance, a source of compressed air, which may be powered by the internal combustion engine, and, in particular, a unique momentum transfer pump device which utilizes the high pressure compressed air output to create a suction or lower pressure at the exhaust manifold.
  • a diffuser may be connected at the output end of the momentum pump to further increase the efficiency of the momentum pump.
  • This invention relates to devices for increasing the operating efficiency of internal combustion engines and, more particularly, to devices which accomplish the above object by reducing the back pressure on the exhaust valves of an internal combustion engine.
  • one important method for improving internal combustion engine efficiency comprises the reduction of back pressure on the exhaust valves of the internal combustion engine. It is well known that in four stroke otto cycle" internal combustion engines, some of the power developed'during the power stroke, is required during the exhaust stroke to force the combustion products from the cylinder out through the exhaust valve and engine exhaust system. If the back pressure can be reduced therefor, engine efficiency will be improved. The reduction of back pressure on the exhaust line also allows an advantageous change in the design of the cylinders of an internal combustion engine.
  • the cylinder exhaust valves can be smaller which allows the cylinder intake valves to be larger.
  • larger intake valves are advantageous since they permit a greater rate of fuel-air mixture to be fed to the cylinder which in turn increases the cylinders efficiency.
  • an engine of less size, or overall weight could be used.
  • the above and other objects of this invention may be accomplished through the addition to the exhaust system of an internal combustion engine of a compressor unit, which may be powered by the fan belt of the internal combustion engine, for producing a desired volume of high pressure air, tubing connecting such source of high pressure air to a momentum pump, as more fully described hereafter, and means directing the high pressure air from the momentum pump into the exhaust line of an internal combustion engine.
  • the efficiency of the momentum pump may still further be increased through the use of a diffuser at the downstream end of the pump.
  • the air compressor may be replaced by another suitable source of compressed air, as, for instance, by a tap into the exhaust manifold or a rechargeable tank of compressed gas.
  • FIG. 1 is a schematic view of an internal combustion engines exhaust system in accordance with applicant's invention
  • FIG. 2 is a side sectional view of the momentum pump and diffuser utilized in the applicant 5 INTERNAL COMBUSTION ENGlNEs exhaust system;
  • FIG. 3 shows an end view, partly in section, of the momentum pump and diffuser utilized in the internal combustion engine's exhaust system according to applicants invention.
  • numeral 1 indicates a conventional internal combustion engine while numeral 2 indicates a conventional exhaust manifold connected to an internal combustion engine for collecting exhaust gases from the cylinders of the internal combustion engine. Also conventional is the radiator cooling fan 3 and the fan shaft 4 which are driven by the internal combustion engine through conventional means, ndt shown in detail.
  • An endless belt 5 is tightly wrapped around a pulley 6 which in turn is rigidly attached to the fan shaft 4. At its other end the endless belt 5 is tightly wrapped around the input shaft pulley 7 of air compressor 8 for powering air compressor when the internal combustion engine is operating.
  • the air compressor should be capable of developing at least about 20 p.s.i.g., and pressures up to about p.s.i.g., are presently considered to be the most useful pressure range for the compressed air source.
  • the made-up air for the compressor 8 may be supplied from a tap in the manifold upstream of the pump, as illustrated in FIG. I, by tap 41 and line 42.
  • the outlet line from the air compressor with optional control valve 9 is connected by standard tubing to the entrance for the compressed air storage tank 12.
  • the check valve 11 can be used to prevent the compressed air from seeking ambient conditions through line and the air compressor when the air compressor is not in operation.
  • the solenoid of solenoid valve 13 may be electrically connected to the ignition circuit 16 of the internal combustion engine in such a manner that valve 13 is opened when the ignition switch is closed and vice versa.
  • jet bores 17 and 17' have a very short dimension along their central axes and that their central axes make an angle in the range of 15 to 40 with respect to the central axis of passage 18 of the momentum pump. It is also noted that the downstream ends of the jet bores 17 and 17' point towards the downstream end of the momentum pump passage 18 and the high velocity air streams flowing therethrough thus impart a downstream force vector to the relatively slow moving exhaust gas stream flowing through pressure 18.
  • a diffuser 20 may be attached to the downstream end of the momentum pump in communication with passage 18.
  • the downstream end of diffuser 20 is connected to duct 21 which communicates with an exhaust gas treating such as the muffler or the exhaust gas purifying device 22.
  • the output of the exhaust gas purifying device 22 is then transmitted via tailpipe 23 to the atmosphere.
  • the upstream end 20a of the diffuser has essentially the same internal shape and cross-sectional area as the downstream end of passage 18, but the diffuser gradually increases in internal cross-sectional area until it reaches its downstream end 20b whose cross-sectional area exceeds the upstreams cross-sectional area within the range of about 1 to 4 times. Further, the angle of the ingested gas and the diameter of the ingested gas hole determine the distance that the opposite wall is from the hole from which the gas escapes; and further, the distance from the ingested hole to where the diffuser starts.
  • This compressed gas then exits through the short substantially circular jet bores 17 and 17' at effective sonic to supersonic velocities, entering the passage 18 still at such velocities.
  • the circular bores intersect the wall of passage 18, such that the exit holes of bores in the passage have a substantially elliptical shape. This shape is believe to have a contributing factor to the efficiency of the momentum pump.
  • this high velocity air stream On exiting from the jet bores, this high velocity air stream, vectorially directed from the device as described, creates a highly turbulent vortical flow of air. Some mixing of this air takes place with the exhaust gas due to shear between the laminar exhaust gas stream and the air jet vortices.
  • the very highly efficient transfer of the momentum from the high velocity airstream to the relatively slow moving exhaust gases in passage 18 is believed to largely take place by a more mechanical, screw-conveyor-like, action of the air jet vortices carrying the exhaust gas stream forward along the vector axis of said jets. Studies indicate that the exiting high velocity airstream from each jet establishes a pair of counter-vortical flow paths indicated by the numbers 24, in FIG. 3.
  • the momentum pump utilized in this invention constitutes, a means to transfer momentum from a relatively low volume flow of high speed gas to a large volume of relatively low speed gas, with the result that the velocity of the latter is greatly increased with remarkably high efficiencies as compared to conventional venturi tune devices.
  • jet bores are angled as described above, air introduced into the passage 18 has a vector of force pointing downstream in the axial direction.
  • the turbulent mixture of compressed air and exhaust gases is driven by the axial component of the compressed air input force towards the downstream end of the momentum pump.
  • the jet bores create helical vortices which greatly improve the mixing and momentum transfer between the compressed air and exhaust gas streams. While the vortical flow path might provide a smaller vector force component in the desired downstream direction than in laminar flow, the effect from the vigorous mixing which thus occurs is advantageous.
  • a diffuser may also be placed to further improve the momentum pump's efficiency.
  • Diffusers are normally used in subsonic fluid flow systems to reduce the velocity and increase the static pressure of a fluid passing therethrough.
  • the addition of the diffuser to a momentum pump as described above mayv result in a still further increase of at least about 25 percent in the pump's efficiency. This unexpected result, i.e., this increase in efficiency, appears to derive from the conversion of energy from the spinning tangentially directed energy of the air jet vortices, to a spinning axial directed energy.
  • the input jet of air imparts a violent tangential spin to the lamina flow of exhaust gases with the resulting storing of angular kinetic energy.
  • the diffuser by gradually expanding or opening up the cross sectional area, converts the stored kinetic energy, both tangential and axial, to the pressure energy, which is in a downstream direction, thereby increasing the efi'iciency of this pump.
  • the back pressure normally existing upstream at the exhaust parts or exhaust manifold of the engine is greatly reduced.
  • the flow volume of air introduced in the exhaust gas line is generally only a minor fraction of the flow volume of the exhaust gases treated, e.g., generally only about to about 50percent, preferably no more than percent, these beneficial effects are achieved.
  • the outputtherefrom is connected by conduit 21 to exhaust gas purifying device 22 and therefrom by tailpipe 23, to the atmosphere.
  • the air compressor is shown to be powered from the fan shaft, it could also be powered by other means associated with the internal combustion engine such as an electric motor energized by the engines generator or by means not associated with the engine.
  • the compressed air storage tank 12 and its associated valves and circuitry could be dispensed with and the output of the air compressing means connected directly to the supply chamber 15 of the momentum pump. In this event, of course, during start-up conditions an under-pressure flow of compressed gas would be received in supply chamber l5and thus the momentum pump would not be operating as efficiently.
  • This modification would have the advantage, in some cases however, of an automatic correlation between the flow rates of the air delivered to the air supply chamber 15 and the exhaust gases delivered to the passage 18 of the momentum pump.
  • the momentum pump is shown in the drawings and described above as located between the exhaust manifold and the purifying device, it may also be located downstream from the purifying device or muffler. Alternative locations include those adjacent the exhaust manifold. A plurality of such devices could be placed on each cylinder's exhaust line leading to the manifold itself, or one such pump may be placed upstream of the purifying device, and a second pump may be placed downstream of that device. In each instance, the operation will be essentially as described above.
  • a standard muffler could be utilized in addition to or in place of the exhaust gas purifying device described above.
  • the relative height of the passage should be maintained essentially as it is shown while the width of the passage should be increased in increments which are about one-half as wide as the passage shown and an additional bore, sized and angled as are the two bores shown, is positioned at the median line of each such additional width increment.
  • Passages 18 which are not substantially rectangular are also within the scope of applicants invention; for instance, the passage may be a circle (especially with single jet bore pumps), a hexagon or any other regular or irregular cross-sectional shape.
  • the important criterion for best results in a specific device is to suitably space the jet bores from each other such that maximum vortical action achieved (which means, in most cases, such that minimal vortical interferences and self-destroying energy losses are achieved).
  • one of the bores may be located at a position more upstream or downstream than the other two jet bores.
  • the size of the plenum chamber the internal shape of which is not critical
  • the air compressor 8 and storage tank 12 can be replaced with a tank of the compressed compress gas.
  • the capacity of the compressed air supply source must be sufficient to maintain the plenum chamber at the required pressure conditions.
  • said plenum chamber should be sufficiently large so as not to be depleted of such pressurized air during operation of the momentum pump.
  • the jet bores should be small enough that the pressurized gas issuing therefrom will exit at at least substantially super-sonic velocities, while the jet gas stream should have sufficient volume passing through said jet bores such that the stream in the passage is accelerated to the desired velocity, i.e., that the jet gas stream has sufficient mass as well as sufficient velocity to produce the desired momentum.
  • the jet bores will have a length which is at most about from one-half to 2 diameters of said bore for most efficient operation.
  • the practical limit on the length of the said bores is dictated by the requirement for sufficient surrounding wall thickness to define said bore and said passage.
  • the exit opening of the jet bore should be essentially flush with the adjacent wall of the passage way for it is through this structure that the momentum pump which is especially believed to contribute to the higher efficient transfer of energy from the high velocity jet gas stream to the relatively low velocity exhaust gas flow.
  • an apparatus for reducing the back pressure of said exhaust gases in said exhaust line comprising:
  • a plenum chamber located adjacent said exhaust line
  • jet bore means located between said exhaust line and plenum chamber said bore means permitting egress of at least one jet of said compressed gas from said plenum chamber into said exhaust line including at least one circular bore which creates an elliptically shaped aperture at its intersection with said wall which is flush with said wall to create turbulence downstream of said bore in said exhaust line,
  • said means for producing a supply of gas includes an air compressor driven by said internal combustion engine.
  • the apparatus as recited in claim 1 further including means located between said supplyof compressed gas and said plenum chamber for controlling the pressure of gas supplied to said plenum chamber.
  • the apparatus as recited in claim 1 further including flow directing means located downstream of the intersection of said exhaust line and said jet bore means for smoothing the turbulence induced in said exhaust gases and thereby increasing the efficiency of said apparatus.
  • said flow directing means comprises a diffuser which has a downstream cross section larger than its upstream cross section.
  • An anti-pollution exhaust system for an internal combustion engine which has an exhaust line surrounded by a wall for removing exhaust gases therefrom to the surrounding atmosphere comprising:
  • a plenum chamber located adjacent said each passage
  • a process for reducing the back pressure action upon an internal combustion engine having an exhaust line, with an axis including the steps of:
  • step of injecting includes the step of creating a pair of counter helical vortices by injecting a jet of said gas.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Toxicology (AREA)
  • Exhaust Gas After Treatment (AREA)
  • Jet Pumps And Other Pumps (AREA)
US00095319A 1970-12-04 1970-12-04 Antipollution exhaust system for an internal combustion engine Expired - Lifetime US3712065A (en)

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US9531970A 1970-12-04 1970-12-04

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US (1) US3712065A (de)
AU (1) AU3289971A (de)
BE (1) BE776143A (de)
CA (1) CA932543A (de)
CH (1) CH534299A (de)
DE (1) DE2159490A1 (de)
ES (2) ES390680A1 (de)
FR (1) FR2114970A5 (de)
GB (1) GB1351668A (de)
NL (1) NL7106385A (de)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4185604A (en) * 1977-04-12 1980-01-29 Nissan Motor Company, Limited Feedback control system for gas flow in internal combustion engine for purpose of exhaust gas purification
EP0053057A2 (de) * 1980-11-20 1982-06-02 Canadian Fram Limited Emissionssteuerungssystem und Verfahren zur Emissionssteuerung
US4356696A (en) * 1980-04-04 1982-11-02 The Garrett Corporation Turbocharger combustor system
US5286164A (en) * 1991-05-15 1994-02-15 Robert Bosch Gmbh Radial blower with blower wheel rotating in spiral housing
US5548955A (en) * 1994-10-19 1996-08-27 Briggs & Stratton Corporation Catalytic converter having a venturi formed from two stamped components
US5606768A (en) * 1995-06-19 1997-03-04 Esteam Manufacturing Ltd. Emissions collection and venting system for van-mounted cleaning apparatus
US5983632A (en) * 1997-08-07 1999-11-16 Honda Giken Kogyo Kabushiki Kaisha Exhaust emission control apparatus for a general-purpose internal combustion engine
GB2373197A (en) * 2001-03-15 2002-09-18 James Stuart Moray Edmiston Apparatus and method for treating exhaust emissions
US20030003030A1 (en) * 2001-06-27 2003-01-02 Glenn Knight Reverse flow catalytic muffler
US6622482B2 (en) 2001-06-27 2003-09-23 Environmental Control Corporation Combined catalytic muffler
US20030195071A1 (en) * 1999-10-06 2003-10-16 Sun Chen Automatic cooling mechanism for electrical device
US20040139740A1 (en) * 2003-01-13 2004-07-22 Reinhard Burk Exhaust gas flow circuit and decharge unit for an internal combustion engine
US20040221829A1 (en) * 2003-05-09 2004-11-11 Fults Steven P. System for improving motor vehicle performance
US20050183704A1 (en) * 2004-02-25 2005-08-25 Masayoshi Usui Supercharging system for internal combustion engine
US20070137190A1 (en) * 2005-12-19 2007-06-21 L.C. Eldridge Sales Co., Inc. Method and apparatus for manipulating and diluting internal combustion engine exhaust gases
WO2008017673A1 (en) * 2006-08-08 2008-02-14 Inergy Automotive Systems Research (Société Anonyme) System for storing an additive and injecting it into the exhaust gases of an engine
US20140352318A1 (en) * 2012-04-02 2014-12-04 Powerphase Llc Gas turbine efficiency and regulation speed improvements using supplementary air system continuous and storage systems and methods of using the same
WO2015147751A1 (en) * 2014-03-26 2015-10-01 Azen Manufacturing Pte Ltd Method and apparatus for handling exhaust gas
US10107199B2 (en) 2012-10-04 2018-10-23 Powerphase Llc Aero boost—gas turbine energy supplementing systems and efficient inlet cooling and heating, and methods of making and using the same
CN110685785A (zh) * 2019-10-22 2020-01-14 燕山大学 一种超声复合型二次空气喷射系统及其控制方法
US10995670B2 (en) 2012-10-26 2021-05-04 Powerphase International, Llc Gas turbine energy supplementing systems and heating systems, and methods of making and using the same

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DE3204952A1 (de) * 1981-02-13 1982-11-18 Fuji Jukogyo K.K., Tokyo Auspuffanordnung eines verbrennungsmotors
DE4430849A1 (de) * 1994-08-31 1996-03-14 Heinrich Dipl Ing Kesselmeyer System zur Verbesserung des Wirkungsgrades beim Kolbenmotor (Verdichtungsmotor) durch Abgasabsaugung
GB2350310A (en) * 1999-05-27 2000-11-29 Btr Industries Ltd Air dryer for use with an air delivery system for a vehicle exhaust.
DE102015005602A1 (de) * 2015-05-02 2016-11-03 Valentin Karl Mattis Die Abgas-Ventilator/Druckluft-Anlage
DE102015011409B3 (de) * 2015-08-29 2016-10-27 Audi Ag Antriebseinrichtung für ein Kraftfahrzeug
DE102016200329A1 (de) * 2016-01-14 2017-07-20 Bayerische Motoren Werke Aktiengesellschaft Abgasbehandlungsvorrichtung mit reduziertem Abgasgegendruck
CA3143975A1 (en) * 2019-07-19 2021-01-28 Arne V. Kobernik Gas jet deflection in pressurized systems

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US1903803A (en) * 1926-06-04 1933-04-18 Maurice E Barker Catalyst for oxidizing carbon monoxide in exhaust gases
US2308059A (en) * 1941-04-03 1943-01-12 Ammiel F Decker Exhaust device for internal combustion engines
US2667031A (en) * 1950-12-21 1954-01-26 Ryder William Exhaust auxiliary for internalcombustion engines
CA629100A (en) * 1961-10-17 M. Baxter James Exhaust gas diluting device
US3082597A (en) * 1961-06-26 1963-03-26 Universal Oil Prod Co Apparatus for injecting secondary air into engine exhaust gases and for other uses
GB933943A (en) * 1960-02-02 1963-08-14 Union Carbide Corp Improvements in the treatment of exhaust gases from engines
US3444584A (en) * 1966-07-11 1969-05-20 Philip J Cote Air ejector type device
US3525474A (en) * 1968-12-09 1970-08-25 Us Air Force Jet pump or thrust augmentor
US3599427A (en) * 1969-09-22 1971-08-17 Ford Motor Co Exhaust gas purification

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Publication number Priority date Publication date Assignee Title
CA629100A (en) * 1961-10-17 M. Baxter James Exhaust gas diluting device
US1903803A (en) * 1926-06-04 1933-04-18 Maurice E Barker Catalyst for oxidizing carbon monoxide in exhaust gases
US2308059A (en) * 1941-04-03 1943-01-12 Ammiel F Decker Exhaust device for internal combustion engines
US2667031A (en) * 1950-12-21 1954-01-26 Ryder William Exhaust auxiliary for internalcombustion engines
GB933943A (en) * 1960-02-02 1963-08-14 Union Carbide Corp Improvements in the treatment of exhaust gases from engines
US3082597A (en) * 1961-06-26 1963-03-26 Universal Oil Prod Co Apparatus for injecting secondary air into engine exhaust gases and for other uses
US3444584A (en) * 1966-07-11 1969-05-20 Philip J Cote Air ejector type device
US3525474A (en) * 1968-12-09 1970-08-25 Us Air Force Jet pump or thrust augmentor
US3599427A (en) * 1969-09-22 1971-08-17 Ford Motor Co Exhaust gas purification

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4185604A (en) * 1977-04-12 1980-01-29 Nissan Motor Company, Limited Feedback control system for gas flow in internal combustion engine for purpose of exhaust gas purification
US4356696A (en) * 1980-04-04 1982-11-02 The Garrett Corporation Turbocharger combustor system
EP0053057A2 (de) * 1980-11-20 1982-06-02 Canadian Fram Limited Emissionssteuerungssystem und Verfahren zur Emissionssteuerung
EP0053057A3 (de) * 1980-11-20 1983-02-23 Canadian Fram Limited Emissionssteuerungssystem und Verfahren zur Emissionssteuerung
US5286164A (en) * 1991-05-15 1994-02-15 Robert Bosch Gmbh Radial blower with blower wheel rotating in spiral housing
US5548955A (en) * 1994-10-19 1996-08-27 Briggs & Stratton Corporation Catalytic converter having a venturi formed from two stamped components
US5732555A (en) * 1994-10-19 1998-03-31 Briggs & Stratton Corporation Multi-pass catalytic converter
US5606768A (en) * 1995-06-19 1997-03-04 Esteam Manufacturing Ltd. Emissions collection and venting system for van-mounted cleaning apparatus
US5983632A (en) * 1997-08-07 1999-11-16 Honda Giken Kogyo Kabushiki Kaisha Exhaust emission control apparatus for a general-purpose internal combustion engine
US20030195071A1 (en) * 1999-10-06 2003-10-16 Sun Chen Automatic cooling mechanism for electrical device
US6638192B2 (en) * 1999-10-06 2003-10-28 Mustek Systems, Inc. Automatic cooling mechanism for electrical device
GB2373197A (en) * 2001-03-15 2002-09-18 James Stuart Moray Edmiston Apparatus and method for treating exhaust emissions
US20030003030A1 (en) * 2001-06-27 2003-01-02 Glenn Knight Reverse flow catalytic muffler
US6622482B2 (en) 2001-06-27 2003-09-23 Environmental Control Corporation Combined catalytic muffler
US7018590B2 (en) 2001-06-27 2006-03-28 Environmental Control Corporation Reverse flow catalytic muffler
US20040139740A1 (en) * 2003-01-13 2004-07-22 Reinhard Burk Exhaust gas flow circuit and decharge unit for an internal combustion engine
US20060180129A1 (en) * 2003-05-09 2006-08-17 Fults Steven P System for improving motor vehicle performance
US20040221829A1 (en) * 2003-05-09 2004-11-11 Fults Steven P. System for improving motor vehicle performance
US7107765B2 (en) * 2003-05-09 2006-09-19 Fults Steven P System for improving motor vehicle performance
US20070006853A1 (en) * 2003-05-09 2007-01-11 Fults Steven P System for improving motor vehicle performance
US7350513B2 (en) 2003-05-09 2008-04-01 Fults Steven P System for improving motor vehicle performance
US20050183704A1 (en) * 2004-02-25 2005-08-25 Masayoshi Usui Supercharging system for internal combustion engine
US7281530B2 (en) * 2004-02-25 2007-10-16 Usui Kokusai Sangyo Kabushiki Kaisha Supercharging system for internal combustion engine
US20070137190A1 (en) * 2005-12-19 2007-06-21 L.C. Eldridge Sales Co., Inc. Method and apparatus for manipulating and diluting internal combustion engine exhaust gases
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US20140352318A1 (en) * 2012-04-02 2014-12-04 Powerphase Llc Gas turbine efficiency and regulation speed improvements using supplementary air system continuous and storage systems and methods of using the same
US9695749B2 (en) 2012-04-02 2017-07-04 Powerphase Llc Compressed air injection system method and apparatus for gas turbine engines
US10145303B2 (en) * 2012-04-02 2018-12-04 Powerphase Llc Gas turbine efficiency and regulation speed improvements using supplementary air system continuous and storage systems and methods of using the same
US10107199B2 (en) 2012-10-04 2018-10-23 Powerphase Llc Aero boost—gas turbine energy supplementing systems and efficient inlet cooling and heating, and methods of making and using the same
US10995670B2 (en) 2012-10-26 2021-05-04 Powerphase International, Llc Gas turbine energy supplementing systems and heating systems, and methods of making and using the same
US11686250B2 (en) 2012-10-26 2023-06-27 Powerphase Llc Gas turbine energy supplementing systems and heating systems, and methods of making and using the same
WO2015147751A1 (en) * 2014-03-26 2015-10-01 Azen Manufacturing Pte Ltd Method and apparatus for handling exhaust gas
US20170284271A1 (en) * 2014-03-26 2017-10-05 Azen Manufacturing Pte Ltd Method and apparatus for handling exhaust gas
US10533482B2 (en) 2014-03-26 2020-01-14 Azen Manufacturing Pte Ltd Method and apparatus for handling exhaust gas
CN110685785A (zh) * 2019-10-22 2020-01-14 燕山大学 一种超声复合型二次空气喷射系统及其控制方法
CN110685785B (zh) * 2019-10-22 2021-08-20 燕山大学 一种超声复合型二次空气喷射系统及其控制方法

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BE776143A (fr) 1972-06-02
GB1351668A (en) 1974-05-01
NL7106385A (de) 1972-06-06
CA932543A (en) 1973-08-28
AU3289971A (en) 1973-03-08
FR2114970A5 (de) 1972-06-30
ES417597A1 (es) 1976-10-16
ES390680A1 (es) 1974-06-16
CH534299A (de) 1973-02-28
DE2159490A1 (de) 1972-07-20

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