WO2009028802A2 - Turbo charger - Google Patents

Turbo charger Download PDF

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Publication number
WO2009028802A2
WO2009028802A2 PCT/KR2008/004433 KR2008004433W WO2009028802A2 WO 2009028802 A2 WO2009028802 A2 WO 2009028802A2 KR 2008004433 W KR2008004433 W KR 2008004433W WO 2009028802 A2 WO2009028802 A2 WO 2009028802A2
Authority
WO
WIPO (PCT)
Prior art keywords
air
turbocharger
tube
guide portion
compressor
Prior art date
Application number
PCT/KR2008/004433
Other languages
French (fr)
Other versions
WO2009028802A3 (en
Inventor
Seong-Wan Kim
Original Assignee
Xyvec Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Xyvec Inc. filed Critical Xyvec Inc.
Publication of WO2009028802A2 publication Critical patent/WO2009028802A2/en
Publication of WO2009028802A3 publication Critical patent/WO2009028802A3/en

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Classifications

    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/20—Control of the pumps by increasing exhaust energy, e.g. using combustion chamber by after-burning
    • 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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • 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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/07—Mixed pressure loops, i.e. wherein recirculated exhaust gas is either taken out upstream of the turbine and reintroduced upstream of the compressor, or is taken out downstream of the turbine and reintroduced downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/19—Means for improving the mixing of air and recirculated exhaust gases, e.g. venturis or multiple openings to the intake system
    • 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

  • the present invention relates to a turbocharger. More particularly, the present invention relates to a turbocharger that is designed to improve efficiency of an internal combustion engine by increasing an amount of air supplied to the internal combustion engine.
  • An internal combustion engine is designed to suck mixing air or air using negative pressure that is generated in a cylinder during a down-stroke of a piston. That is, in the down-stroke of the piston, inner pressure of the cylinder is reduced to be lower than the atmospheric pressure. Therefore, mixing air under the atmospheric pressure is sucked into the cylinder by a difference between the inner pressure of the cylinder and the atmospheric pressure. This is referred to as natural aspiration or normal aspiration.
  • the mixing air that will be sucked by the engine is kept under the atmospheric pressure and an amount of fuel that can be combusted in the cylinder is determined by an amount of the mixing air supplied into the cylinder. If it is possible to supply more mixing air into the cylinder, the amount of the fuel supplied to the cylinder can increase in proportional to the amount of the mixing air supplied into the cylinder. Therefore, the engine can generate higher power with the same engine displacement. As described above, when the amount of the mixing air supplied into the cylinder increases, the pressure increases and the output of the engine can be improved during an expansion stroke.
  • the air is compressed by an air compressor connected to a crankshaft of an engine by a belt pulley.
  • the supercharger method has a limitation in that there is an engine output loss since the air compressor is driven by engine toque. Further, since the air compressor receives power from the crankshaft of the engine, power is always consumed during idling or in a high RPM range, thereby increasing fuel consumption.
  • a supercharger is designed to compress the air using a separate driving unit.
  • turbocharger method a turbine wheel installed on a turbocharger rotates using engine exhaust and a compressor wheel installed on the turbocharger compresses and supplies the air.
  • the turbocharger method is ineffective in a low RPM range.
  • the RPM of the turbocharger is quickly reduced upon releasing an accelerator.
  • a turbo lag phenomenon occurs and thus starting force of a vehicle is deteriorated when starting to move the vehicle.
  • the present invention has been made in an effort to provide a turbocharger having advantages of not only generating no load at a high output, but also of supplying air into an internal combustion engine without retarding the increase of output.
  • the present invention has been also made in an effort to provide a turbocharger having advantages of sufficiently supplying air to an internal combustion engine without having a separate cooler.
  • An exemplary embodiment of the present invention provides a turbocharger including a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine, a driving shaft rotatably connected to the turbine wheel, a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel, an air charger that is connected to the compressor to amplify air introduced into the compressor, and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger.
  • the air charger is formed in a tube shape, and includes a convex portion protruding toward a central axis of the air charger and an amplification portion having a passage communicating the gas supply tube with the inside of the convex portion.
  • a boundary portion between the amplification portion and a surface of the convex portion, which is formed at an air discharge side, may be rounded.
  • the convex portion may be highest at a portion connected to the amplification portion.
  • the gas supply tube may be connected to an air inflow tube of the compressor.
  • the convex portion may include an inflow guide portion having an inner diameter that is gradually reduced in an airflow direction and a discharge guide portion that is spaced apart from the inflow guide portion and having an inner diameter that is gradually increased in the airflow direction.
  • the amplification portion may include an intake hole that is connected to the gas supply tube to introduce the exhaust gases, a dispensing passage that is connected to the intake hole and extends in a circumferential direction of the convex portion, and a guide passage connecting the dispensing passage to the inside of the convex portion.
  • the air charger may include: an outer body including a tube-shaped inflow guide portion for guiding introduction of the air, a tube-shaped receiving portion connected to the inflow guide portion, and an intake hole that is connected to the gas supply tube to introduce the exhaust gases; and a tube-shaped inner body inserted in the receiving portion and provided at an outer circumference thereof with a dispensing passage having a stepped portion having an outer diameter of less than an inner diameter of the receiving portion and extending along a circumferential direction of the convex portion, and a guide passage that is defined by a gap in an axial direction between the inner body and the outer body to connect the dispensing passage to the inside of the convex portion.
  • the inflow guide portion has an inner circumference that protrudes toward a central axis thereof.
  • a turbocharger including a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine, a driving shaft rotatably connected to the turbine wheel, a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel, an air charger that is connected to the compressor to amplify air introduced into the compressor, and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger.
  • the air charger includes an inflow guide portion for guiding introduction of the air, a tube-shaped discharge guide portion communicating with the inflow guide portion, and an amplification portion that is installed between the inflow guide portion and the discharge guide portion, the amplification portion including an intake hole that is connected to the gas supply tube to introduce the exhaust gases, a dispensing passage that is connected to the intake hole and extends in a circumferential direction of the discharge guide portion, and at least one guide passage connecting the dispensing passage to the inside of the discharge guide portion, the amplification portion introducing the air from the inflow guide portion as the gas introduced from the intake hole is directed to the discharge guide portion.
  • the air charger may further include an outer body including the inflow guide portion and a tube-shaped receiving portion connected to the inflow guide portion, and a tube-shaped inner body inserted in the receiving portion and provided at an outer circumference thereof with the dispensing passage having a stepped portion having an outer diameter of less than an inner diameter of the receiving portion, and the guide passage that is defined by a gap defined between the inner body and the outer body in an axial direction.
  • the air charger may further include a plurality of protrusions that are provided in the gap defined between the inner body and the outer body in the axial direction to form a plurality of the guide passages.
  • the plurality of guide passage may be spaced apart from each other along an inner circumference of the receiving portion.
  • the plurality of protrusions may be oriented toward a central axis of the receiving portion.
  • the plurality of protrusions may be inclined in a rotational direction of the compression wheel relative to a direction toward a central axis of the receiving portion.
  • the protrusions may be formed on the outer body.
  • the protrusions may be formed on a front end surface of the inner body.
  • the protrusions may be formed to protrude from an inner circumference of a separate ring-shaped spacing member.
  • the thickness of the spacing member may be 0.03-0.15 mm.
  • the outer body may have a first surface and the inner body may have a second surface that faces the first surface with the guide passage interposed between the first and second surfaces in the receiving portion of the outer body.
  • the first surface may be perpendicularly formed with respect to a central axis of the receiving portion, and the second surface has a rounded surface curved toward the discharge guide portion.
  • the discharge guide portion may have an inner diameter that is gradually increased in an airflow direction.
  • the turbocharger since the turbocharger does not generate air resistance even at a high RPM, it can sufficiently supply air to the internal combustion engine at the high RPM. Therefore, output of the internal combustion engine can be improved.
  • a prior art turbocharger has a limitation in that it generates exhaust fumes when a turbo lag phenomenon occurs since a large amount of fuel is supplied while the air is not sufficiently supplied.
  • the turbocharger since the turbocharger sufficiently supplies the air to the compressor upon starting, the generation of the exhaust fumes can be reduced.
  • turbocharger of the exemplary embodiments introduces the air at 25 times the amount of exhaust gases supplied, there is no need to use an intercooler for reducing the air temperature. Further, since the exhaust gases can be diluted, the performance of the internal combustion engine can be improved.
  • turbocharger of the exemplary embodiments amplifies a supplying amount of the air upon starting the internal combustion engine and operates in response to an amount of exhaust gas, an air shortage problem can be solved even when output increases.
  • turbocharger of the exemplary embodiments recovers a part of the exhaust gas and supplies the recovered exhaust gas to an inlet side and the exhaust gas enhances the introduction of the mixing air, output can be increased and the amount of harmful ingredients such as SOx, NOx, CO, and the like contained in the exhaust gases can be reduced.
  • turbocharger of the exemplary embodiments is provided with the dispensing passage and the inflow passage to uniformly supply the exhaust gases, output of the internal combustion engine can be improved.
  • turbocharger of the exemplary embodiments is provided with a spiral protrusion, the exhaust gas and air can be effectively mixed with each other and thus the output of the internal combustion engine can be improved.
  • turbocharger of the exemplary embodiments is designed to have protrusions inclined with respect to an axial direction in the air charger, a swirl flow can be generated in advance by the air applied to the compressor wheel by force of the injected exhaust gas.
  • the rotational direction of the swirl flow coincide with the rotational direction of the compressor wheel, the power of the compressor, which is required to compress the introduced air, can be reduced. Accordingly, the compression of the introduced air can be effectively realized even when the power transferred from the turbine wheel in initial starting where an amount of the exhaust gas is relatively small.
  • the turbo lag can be shortened and the output increases.
  • exhaust fumes can be reduced.
  • FIG. 1 is a schematic diagram of an air charging system for an internal combustion engine having a turbocharger according to a first exemplary embodiment of the present invention.
  • FIG. 2 is a partly cut-away perspective view of the turbocharger of Fig. 1.
  • FIG. 3 is a cross-sectional view of an air charger of the turbocharger of FIG. 2.
  • FIG. 4 is a schematic view of a modified example of the air charging system of
  • FIG. 5 is a cross-sectional view of a modified example of the air charger of FIG. 3.
  • FIG. 6 is a partially cut-away exploded perspective view of the air charger of FIG. 5.
  • FIGs. 7 and 8 are perspective views of modified examples of a tube fitting depicted in FIG. 6.
  • FIG. 9 is an exploded perspective view of an air charger applied to a turbocharger according to a second exemplary embodiment of the present invention.
  • FIG. 10 is a partially cut-away perspective view of the air charger of FIG. 9.
  • FIG. 11 is a cross-sectional view taken in an axial direction of FIG. 10.
  • FIG. 12 is a top plan view of a spacing member depicted in FIG. 9.
  • FIG. 13 is a top plan view of a modified example of the spacing member of FIG. 12.
  • FIG. 14 is an exploded perspective view of an air charger applied to a turbocharger according to a third exemplary embodiment of the present invention.
  • FIG. 15 is an exploded perspective view of an air charger applied to a turbocharger according to a fourth exemplary embodiment of the present invention.
  • FIG. 1 is a schematic diagram of an air charging system for an internal combustion engine having a turbocharger according to a first exemplary embodiment of the present invention.
  • FIG. 1 shows an internal combustion engine having a cylinder structure
  • the present invention is not limited to this.
  • the present invention can be applied to all of internal combustion engines that perform intake/exhaust through an inlet and an outlet.
  • a turbocharger system includes an intake tube 152 supplying air to an internal combustion engine 150, an exhaust tube 151 that is connected to the internal combustion engine 150 to discharge exhaust gases to an external side, and a turbocharger 100 that is connected to the intake and exhaust tubes
  • the internal combustion engine 150 typically includes a cylinder, an intake valve, and an exhaust valve.
  • the intake tube 152 directs the air to the intake valve and the exhaust tube 151 discharges the exhaust gases generated in the engine to the external side.
  • the turbocharger 100 includes a turbine 102 that is connected to the exhaust tube 151 to provide rotational force using the exhaust gases, a driving shaft 105 rotatably installed on the turbine 102, a compressor 103 that is connected to the driving shaft 105 to rotate by the rotational force generated by the turbine 102 and is connected to the intake tube 152 to enhance the inflow of the air, and an air charger 120 that is installed near an air inlet of the compressor 103 to enhance the inflow of the air to the compressor 103.
  • FIG. 2 is a partly cut-away perspective view of the turbocharger 100 of Fig. 1. The following will describe the turbocharger 100 with reference to FIG. 2.
  • the turbine 102 includes a turbine housing 116 defining an external shape thereof, and a turbine wheel 104 that is rotatably disposed in the turbine housing 116.
  • the turbine wheel 104 is fixed on the driving shaft 105.
  • the turbine 102 is provided at a circumference thereof with a scroll passage 113 communicating with a gas inflow tube 112.
  • the exhaust gases discharged from the internal combustion engine 150 are directed from a turbine inlet 107 into the scroll passage 113 along the gas inflow tube 112.
  • the exhaust gases introduced into the scroll passage 113 are injected toward the turbine wheel 104 to rotate the turbine wheel 104, and are subsequently discharged through a turbine outlet 108.
  • the compressor 103 includes a compressor housing 117 defining an outer shape thereof, a compressor wheel 109 that is rotatably installed in the compressor housing 117, and an air intake tube 1 14 supplying air to the compressor 103.
  • the compressor 103 is provided at a circumference thereof with a scroll passage 1 15 communicating with a compressor outlet 106.
  • the air introduced through the air intake tube 114 is forcedly compressed by the compression wheel 109 to be directed to the scroll passage 115.
  • the air directed to the scroll passage 115 is supplied to the internal combustion engine 150 through the compressor outlet 106.
  • the air charger 120 is installed on the air intake tube 1 14 of the compressor 103.
  • a gas supply tube 130 is installed on the air charger 120 to connect the gas inflow tube 1 12 to the air charger 120. Pressure of the exhaust gases is maximized at a portion near the turbine inlet 107. Therefore, when the gas inflow tube 112 is installed on the turbine inlet 107, the exhaust gases can be supplied to the air charger 120 under a higher pressure.
  • the present invention is not limited to the above configuration. That is, as shown in FIG. 4, the gas supply tube 140 may be installed near an outlet of the turbine 102. Since the exhaust gases discharged by the operation of the turbine 102 have considerable pressure, the exhaust gases can be supplied to the air charger 120 under a high pressure.
  • the air charger 120 functions to amplify the air introduced into the compressor 103 by injecting the compressed exhaust gases supplied through the gas supply tube 130 into the air charger 120.
  • FIG. 3 is a cross-sectional view of the air charger of FIG. 2.
  • the air charger 120 is formed in a tube shape.
  • the air charger 120 includes a convex portion 125 protruding toward a central axis and an amplifying portion 129 providing a passage communicating the gas supply tube 130 with an inner circumference of the convex portion 125.
  • the convex portion 125 includes an inflow guide portion 121 having an inner diameter that is gradually reduced in an air flow direction, and a discharge guide portion 123 having an inner diameter that increases in the airflow direction.
  • the amplifying portion 129 includes an intake hole 127 that communicates with an outer circumference to introduce the exhaust gases, a dispensing passage 128 that is connected to the intake hole to enable the exhaust gases to flow in a circumferential direction, and a guide passage 126 that connects the dispensing passage 128 to the inside of the amplifying portion 129 and is disposed between the inflow guide portion 121 and the discharge guide portion 123.
  • the entire air charger 120 of this exemplary embodiment is formed in one body, and has a tube structure with a hollow portion formed therein.
  • the inflow guide portion 121 has an inner circumference that gradually protrudes toward a central axis thereof as it goes in the airflow direction so that the airflow area can be gradually reduced. Therefore, the flow rate of air passing through the inflow guide portion 121 gradually increases while the pressure of the air is gradually reduced.
  • the discharge guide portion 123 has the smallest inner diameter at a portion near the inflow guide portion 121. A distance from an inner circumference of the discharge guide portion 123 to a central axis thereof gradually increases as it goes in the airflow direction. Therefore, the inner diameter of the air charger 120 is gradually reduced at the inflow guide portion 121 and gradually increased at the discharge guide portion 121.
  • the dispensing passage 128 is formed in a circular shape extending in a circumferential direction in the air charger 120 and is connected to the intake hole
  • the intake hole 127 extends to an outer surface of the air charger to communicate with the gas supply tube 130. Therefore, the exhaust gases introduced through the intake hole 127 flow in the circumferential direction of the air charger 120 through the dispensing passage 128. Meanwhile, the dispensing passage 128 is connected to the inside of the air charger 120 through the guide passage 126.
  • the guide passage 126 forms a gap spaced in an axial direction between the inflow guide portion 121 and the discharge guide portion 123, thereby being formed along the inner circumference of the air charger 120.
  • a boundary portion between the guide passage 126 and the discharge guide portion 123 is rounded.
  • the exhaust gases introduced through the intake hole 127 flow in the circumferential direction of the air charger 120 along the dispensing passage 128, in the course of which the exhaust gases are introduced into the air charger 120 through the guide passage 126.
  • the guide passage 126 is formed along the inner circumference of the air charger 120 so that the exhaust gases can be uniformly supplied into the air charger 120.
  • the gas introduced under the high pressure flows toward the discharge guide portion 123 along the rounded boundary portion. At this point, the gas quickly flowing under the high pressure enhances the introduction of the air, thereby supplying a large amount of air into the internal combustion engine.
  • the internal combustion engine into which a relatively large amount of mixing air is supplied generates high pressure during an expansion stroke to increase an output thereof, thereby generating power greater than that generated by a natural intake internal combustion engine by 35-60%.
  • FIG. 5 is a cross-sectional view of a modified example of the air charger of FIG. 3, and FIG. 6 is a partially cut-way exploded perspective view of the air charger of FIG. 5.
  • an air charger includes a gas supply tube 130 connected to an intake hole 127. That is, the gas supply tube 130 is connected to the intake hole 127 by a tube fitting 160.
  • the tube fitting 160 is formed in a T-shape, and includes a gas inflow port 162 connected to the gas supply tube 130 and a gas discharge port 168 linearly connected to the gas inflow port 162.
  • a cleaning agent inflow port 164 is perpendicularly formed between the gas inflow port 162 and the gas discharge port 168.
  • a sealing cap 166 is installed on the cleaning agent inflow port 164.
  • the tube fitting 160 not only connects the gas supply tube 130 to the intake hole 127, but also provides the cleansing agent inflow port 164 through which a cleaning agent can be injected into the air charger 120.
  • the cleaning agent inflow port 164 is normally closed by the sealing cap 166. When there is a need to inject the cleaning agent to remove a pollutant material accumulated in the air charger 120, the sealing cap 166 is separated from the cleaning agent inflow port 164 and the cleaning agent is injected into the air charger 120 through the cleaning agent inflow port 164.
  • FIGs. 7 and 8 are perspective views of modified examples of the tube fitting of FIG. 6.
  • a tube fitting 170 includes a cleaning agent inflow port 174 with a sealing cap 176, a gas inflow port 172 linearly connected to the cleaning agent inflow port 174, and a gas discharge port 178 perpendicularly connected between the cleaning agent inflow port 174 and the gas inflow port 172, and is provided in the form of a branch tee shape.
  • FIG. 7 includes a cleaning agent inflow port 174 with a sealing cap 176, a gas inflow port 172 linearly connected to the cleaning agent inflow port 174, and a gas discharge port 178 perpendicularly connected between the cleaning agent inflow port 174 and the gas inflow port 172, and is provided in the form of a branch tee shape.
  • a tube fitting 180 includes a gas discharge port 188, a cleaning agent inflow port 184 linearly connected to the gas discharge port 188 and having a sealing cap 186, and a gas inflow port 182 perpendicularly connected between the gas discharge port 188 and the cleaning agent inflow port 184, and is provided in the form of a run tee shape.
  • FIG. 9 is an exploded perspective view of an air charger applied to a turbocharger according to a second exemplary embodiment of the present invention.
  • an air charger in accordance with a second exemplary embodiment is installed near a compressed air inlet of a turbocharger.
  • a turbocharger of the present exemplary embodiment is the same as that of the first exemplary embodiment except for a structure of an air charger 200. Therefore, a description of like elements will be omitted.
  • the air charger 200 includes an outer body 210 having an inflow guide portion
  • FIG. 10 is a partially cut-away perspective view of the air charger of FIG. 9, and FIG. 1 1 is a cross-sectional view taken in an axial direction of FIG. 10.
  • the outer body 210 is formed in a cylindrical tube structure, including the inflow guide portion 212 disposed at a front portion thereof and the receiving portion 214 disposed at a rear portion thereof.
  • the inflow guide portion 212 has an inner diameter that is gradually reduced as it goes in the airflow direction (the y-axis direction in FIG. 10) from a front end thereof.
  • an inner circumference 212a of the inflow guide portion 212 is curved to be convex toward a central axis thereof. Accordingly, the flow rate of air passing through the inflow guide portion 212 is increased and pressure thereof is reduced.
  • the inner circumference 212a of the inflow guide portion 212 is connected to a supporting surface 212b that connects the inner circumference 212a to the receiving portion 214 and is perpendicularly formed with respect to a central axis of the receiving portion 214.
  • the receiving portion 214 is formed in a cylindrical tube structure having a hollow portion in which the inner body 220 is fitted.
  • the intake hole 216 is located at a front portion of the receiving portion 214 and opened to the outer circumference to introduce the gas. At this point, the gas introduced through the intake hole 216 is compressed air having a higher pressure than atmospheric pressure.
  • the intake hole 216 functions as a passage that is connected to the gas supply tube 270 to supply the exhaust gases into the receiving portion 214.
  • the inner body 220 is formed in a cylindrical tube structure that is fitted in the receiving portion 214.
  • the stepped portion 221 is formed at a front portion of the inner body 220.
  • the stepped portion 221 has an outer diameter of less than an inner diameter of the receiving portion 214 and extends along the outer circumference of the inner body 220. Therefore, as shown in FIG. 9, a space is defined between the stepped portion 221 and the receiving portion 214.
  • the space is referred to as a dispensing passage 225.
  • the dispensing passage 225 is connected to the intake hole 216 so that the gas introduced through the intake hole 216 can flow along the outer circumference of the inner body 220.
  • the protrusions 234 are located between the outer and inner bodies 210 and 220 to space the outer and inner bodies 210 and 220 in an axial direction from each other.
  • the protrusions 234 are formed to protrude from an inner circumference of a ring-shaped spacing member 230.
  • the spacing member 230 includes a ring-shaped support 232.
  • the protrusions 234 extend from an inner circumference of the ring-shaped support 232 toward a center C and are spaced apart from each other along the inner circumference.
  • the ring-shaped support 232 is spaced apart from the inner body 220 and contacts an inner surface of the receiving portion 214. A front end of the inner body 220 contacts the protrusions 234.
  • gaps between adjacent protrusions 234 define guide passages 227.
  • the guide passages 227 are spaced apart from each other along the front end of the inner body 220. The gas is introduced into a discharge guide portion 223 through the guide passages 227.
  • the protrusions 234 are disposed to be spaced apart from each other and the gas are supplied to the gaps defined between the protrusions. Therefore, the gas can be uniformly divided and supplied into the air charger 200.
  • a thickness of the spacing member 230 may be 0.03-0.15 mm.
  • the thickness of the spacing member 230 is less than 0.03 mm, an amount of the exhaust gases introduced into the air charger 200 is too small to be effectively injected.
  • the thickness of the spacing member 230 is greater than 0.15 mm, since the sectional area of the guide passages 227 is too big, the injection speed is reduced.
  • the spacing member 230 may have a thickness of 0.05-0.08 mm.
  • first and second surfaces surfaces of the outer and inner bodies 210 and 220, which face each other with the guide passages 227 interposed therebetween in the receiving portion 214 of the outer body 210, are referred to as first and second surfaces, respectively, the first surface is perpendicularly formed with respect to the central axis of the receiving portion 214 and the second surface is formed to have a rounded portion 226 curved toward the discharge guide portion 223.
  • the second surface is first curved so as to direct the introduced gas toward the discharge guide portion 223 (see a circled portion in FIG. 11).
  • the tube-shaped discharge guide portion 223 is formed at a downstream side of the rounded portion 226.
  • the discharge guide portion 223 has an inner diameter that is gradually increased in the airflow direction (the y-axis direction of FIG. 11) from the rounded portion 226.
  • the smallest inner diameter of the rounded portion 226 may be same as the smallest inner diameter of the discharge guide portion 223. Therefore, the air introduced along the inflow guide portion 212 can be stably discharged along the discharge guide portion 223.
  • the exhaust gases introduced into the inner body 220 flow toward the discharge guide portion 223 along the rounded portion 226 by the Coanda effect.
  • the Coanda effect is the tendency of a fluid to flow in a direction where the smallest energy is consumed. When there is a curved surface at a front portion with respect to a flow direction of the fluid, the fluid flows along the curved surface. In accordance with the Coanda effect, it becomes possible to predict the flow direction of the fluid in advance.
  • the exhaust gases can be effectively directed toward the discharge guide portion 223.
  • the air charger 200 in accordance with the present exemplary embodiment is formed of a material having excellent durability, such as stainless steel or engineering plastic, which can withstand a high temperature and has excellent corrosion-resistance.
  • the outer and inner bodies 210 and 220 may be coupled to each other in a shrink-fitting manner or by welding in a state where the inner body 220 is fitted in the outer body 210.
  • the outer and inner bodies 210 and 220 may be screw-coupled to each other by forming a female screw portion on the inner circumference of the receiving portion 214 of the outer body 210 and a male screw portion on the outer circumference of the inner body 220.
  • the gas can be supplied into the air charger 200 via the intake hole 216, dispensing passage 225, and guide passages 227.
  • a vacuum space V is formed behind the guide passages 227.
  • the vacuum space V amplifies the introduction of the mixing air. That is, an amount of air of 25 times that of the gas introduced through the intake hole 216 can be introduced into the air charger 200.
  • the internal combustion engine charged with the mixing air generates high pressure during the expansion stroke to enhance the output thereof.
  • the temperature of the air is not increased even when the air is compressed, there is no need to install an intercooler.
  • the gas introduced through the intake hole 216 is mixed with a large amount of air, the temperature is reduced and the concentration is diluted. Therefore, the internal combustion engine is not overloaded.
  • FIG. 12 is a top plan view of the spacing member depicted in FIG. 9, and FIG. 13 is a top plan view of a modified example of the spacing member of FIG. 12.
  • the spacing member 230 includes the ring-shaped support
  • the protrusions 234 are oriented toward the center C of the ring-shaped support 232.
  • the protrusions 234 define the guide passages 227 of the air charger 200 in accordance with the present exemplary embodiment.
  • the guide passages 227 function to inject the gas introduced through the intake hole 216 toward the central axis at a high speed.
  • a spacing member 330 includes a ring-shaped support 332 and a plurality of protrusions 334 protruding from an inner circumference of the ring-shaped support 332.
  • the protrusions 334 are oriented in a direction away from the center of the ring-shaped support 332. That is, the protrusions 334 extend from the inner circumference of the support 332 at a predetermined inclined angle ⁇ of less than 90 ° .
  • the protrusions 334 may be inclined in a rotational direction of the compressor wheel 109 depicted in FIG. 2 relative to a direction toward a center of the support 332. In this case, since the gas that rotates while passing through the air charger can pass through the compressor wheel 109 while maintaining the same rotational direction, the air can be sufficiently supplied to the internal combustion engine while minimizing a loss of kinetic energy.
  • the gas When the gas is injected through the guide passages defined between the protrusions 334, the gas generates an eddy current in the rotational direction of the compressor wheel 109 and flows toward the central axis of the receiving portion 214.
  • the exhaust gases and the mixing air can be more effectively mixed with each other and air-resistance acting on the compressor wheel is reduced. That is, by making the rotational direction of the eddy current identical to the rotational direction of the compressor wheel 109 as described above, power consumption of the compressor, which is required to compress the introduced air, can be reduced and thus the compression of the introduced air can be effectively realized even when power transferred from the turbine wheel in an initial starting operation where an amount of the exhaust gases is relatively small is low. As a result, the turbo lag is shortened and the output increases. Furthermore, exhaust fumes can be reduced.
  • FIG. 14 is an exploded perspective view of an air charger applied to a turbocharger according to a third exemplary embodiment of the present invention.
  • an air charger 400 in accordance with a third exemplary embodiment is installed near an air inlet of the compressor to amplify air introduced into the compressor.
  • a turbocharger of the present exemplary embodiment is the same as that of the first exemplary embodiment except for a structure of the air charger 400. Therefore, a description of like elements will be omitted.
  • the air charger 400 includes an outer body 410 having an inflow guide portion 412 having an inner sectional area that is gradually reduced in an airflow direction and a receiving portion 414 connected to the inflow guide portion 412 and provided with an intake hole 416, and an inner body 420 inserted in the receiving portion 414 and provided at an inner circumference thereof with a stepped portion 421 and at a front end surface with a plurality of protrusions 425.
  • the outer body 410 is formed in a cylindrical tube structure.
  • the inflow guide portion 412 has an inner surface that gradually protrudes toward a central axis as it goes toward the receiving portion. Therefore, an inner diameter of the outer body 410 is gradually reduced as it goes toward the receiving portion 414.
  • the inner body 420 includes the stepped portion 421 formed on an outer circumference thereof and a discharge guide portion 423 formed in a tube structure.
  • the stepped portion 421 defines a space between the receiving portion 414 and the inner body 420.
  • the discharge guide portion 423 has an inner diameter that is gradually increased in the airflow direction.
  • the protrusions 425 are formed on the front surface (i.e., a surface facing the outer body) of the inner body 420.
  • the protrusions 425 are spaced apart from each other in a circumferential direction by a predetermined distance.
  • the inner and outer bodies 420 and 410 are spaced apart from each other by the protrusions 425 and thus passages are formed between the protrusions 425.
  • the exhaust gases are introduced into the discharge guide portion 423 through the passages.
  • the manufacturing process can be simplified.
  • FIG. 15 is an exploded perspective view of an air charger applied to a turbocharger according to a fourth exemplary embodiment of the present invention.
  • an air charger 500 in accordance with a third exemplary embodiment is installed near an air inlet of the compressor to amplify air introduced into the compressor.
  • a turbocharger of the present exemplary embodiment is the same as that of the first exemplary embodiment except for a structure of the air charger 500. Therefore, a description of like elements will be omitted.
  • the air charger 500 in according with the fourth exemplary embodiment includes an outer body 510 having an inflow guide portion 512 having an inner sectional area that is gradually reduced in an airflow direction and a receiving portion 514 connected to the inflow guide portion 512 and provided with an intake hole 516, and an inner body 520 that is inserted in the receiving portion 514 and has a stepped portion 521 formed on a front end thereof and a discharge guide portion 523 communicating with the inflow guide portion 512.
  • the outer body 510 is formed in a cylindrical tube structure.
  • the inflow guide portion 512 has an inner surface that gradually protrudes toward a central axis as it goes toward the receiving portion. Therefore, an inner diameter of the outer body 510 is gradually reduced as it goes toward the receiving portion 514.
  • the inflow guide portion 512 has an arc-shaped section, including a guide surface 512a guiding the inflow of the air and a supporting surface 512b connecting the guide surface 512a to the receiving portion 514 and perpendicularly formed with respect to the receiving portion 514.
  • the supporting surface 512b contacts the front end of the inner body 520 when the inner body 520 is fitted in the receiving portion 514.
  • the supporting surface 512b is provided with a plurality of protrusions 515.
  • the protrusions 515 are spaced apart from each other along an inner circumference of the receiving portion 514 by a predetermined distance.
  • the inner body 520 and the supporting surface 512b are spaced apart from each other by the protrusions 515 and thus passages are formed between the protrusions 515.
  • the exhaust gases are directed to the discharge guide portion 523 through the passages formed between the protrusions 515.
  • the manufacturing process can be simplified.

Abstract

A turbocharger that can enhance output by increasing an intake amount of air is provided. The turbocharger includes a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine, a driving shaft rotatably connected to the turbine wheel, a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel, an air charger that is connected to the compressor to amplify air introduced into the compressor, and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger. The air charger is formed in a tube shape and includes a convex portion protruding toward a central axis of the air charger and an amplification portion having a passage communicating the gas supply tube with an inside of the convex portion.

Description

[DESCRIPTION] [Invention Title]
TURBO CHARGER [Technical Field] The present invention relates to a turbocharger. More particularly, the present invention relates to a turbocharger that is designed to improve efficiency of an internal combustion engine by increasing an amount of air supplied to the internal combustion engine. [Background Art] An internal combustion engine is designed to suck mixing air or air using negative pressure that is generated in a cylinder during a down-stroke of a piston. That is, in the down-stroke of the piston, inner pressure of the cylinder is reduced to be lower than the atmospheric pressure. Therefore, mixing air under the atmospheric pressure is sucked into the cylinder by a difference between the inner pressure of the cylinder and the atmospheric pressure. This is referred to as natural aspiration or normal aspiration.
As described above, the mixing air that will be sucked by the engine is kept under the atmospheric pressure and an amount of fuel that can be combusted in the cylinder is determined by an amount of the mixing air supplied into the cylinder. If it is possible to supply more mixing air into the cylinder, the amount of the fuel supplied to the cylinder can increase in proportional to the amount of the mixing air supplied into the cylinder. Therefore, the engine can generate higher power with the same engine displacement. As described above, when the amount of the mixing air supplied into the cylinder increases, the pressure increases and the output of the engine can be improved during an expansion stroke.
However, the greater the amount of mixing air introduced along an intake line, the greater the pressure drop in the intake line. Therefore, it is difficult to sufficiently introduce the mixing air and thus the mixing air cannot be sufficiently supplied into the cylinder.
In order to solve the above limitation, a supercharger or turbocharger method has been applied. In the supercharger method, the air is compressed by an air compressor connected to a crankshaft of an engine by a belt pulley.
However, the supercharger method has a limitation in that there is an engine output loss since the air compressor is driven by engine toque. Further, since the air compressor receives power from the crankshaft of the engine, power is always consumed during idling or in a high RPM range, thereby increasing fuel consumption.
In addition, a supercharger is designed to compress the air using a separate driving unit.
Therefore, when an output increases above a predetermined level, it becomes difficult to sufficiently supply the air. That is, this design only disturbs the increase of the output.
Meanwhile, in the turbocharger method, a turbine wheel installed on a turbocharger rotates using engine exhaust and a compressor wheel installed on the turbocharger compresses and supplies the air. However, the turbocharger method is ineffective in a low RPM range. In addition, the RPM of the turbocharger is quickly reduced upon releasing an accelerator. Further, since a predetermined time is required to compress the air, a turbo lag phenomenon occurs and thus starting force of a vehicle is deteriorated when starting to move the vehicle.
[Disclosure] [Technical Problem]
The present invention has been made in an effort to provide a turbocharger having advantages of not only generating no load at a high output, but also of supplying air into an internal combustion engine without retarding the increase of output. The present invention has been also made in an effort to provide a turbocharger having advantages of sufficiently supplying air to an internal combustion engine without having a separate cooler. [Technical Solution]
An exemplary embodiment of the present invention provides a turbocharger including a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine, a driving shaft rotatably connected to the turbine wheel, a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel, an air charger that is connected to the compressor to amplify air introduced into the compressor, and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger. The air charger is formed in a tube shape, and includes a convex portion protruding toward a central axis of the air charger and an amplification portion having a passage communicating the gas supply tube with the inside of the convex portion. A boundary portion between the amplification portion and a surface of the convex portion, which is formed at an air discharge side, may be rounded. The convex portion may be highest at a portion connected to the amplification portion.
The gas supply tube may be connected to an air inflow tube of the compressor. The convex portion may include an inflow guide portion having an inner diameter that is gradually reduced in an airflow direction and a discharge guide portion that is spaced apart from the inflow guide portion and having an inner diameter that is gradually increased in the airflow direction. The amplification portion may include an intake hole that is connected to the gas supply tube to introduce the exhaust gases, a dispensing passage that is connected to the intake hole and extends in a circumferential direction of the convex portion, and a guide passage connecting the dispensing passage to the inside of the convex portion.
The air charger may include: an outer body including a tube-shaped inflow guide portion for guiding introduction of the air, a tube-shaped receiving portion connected to the inflow guide portion, and an intake hole that is connected to the gas supply tube to introduce the exhaust gases; and a tube-shaped inner body inserted in the receiving portion and provided at an outer circumference thereof with a dispensing passage having a stepped portion having an outer diameter of less than an inner diameter of the receiving portion and extending along a circumferential direction of the convex portion, and a guide passage that is defined by a gap in an axial direction between the inner body and the outer body to connect the dispensing passage to the inside of the convex portion. The inflow guide portion has an inner circumference that protrudes toward a central axis thereof. Another exemplary embodiment of the present invention provides a turbocharger including a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine, a driving shaft rotatably connected to the turbine wheel, a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel, an air charger that is connected to the compressor to amplify air introduced into the compressor, and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger. The air charger includes an inflow guide portion for guiding introduction of the air, a tube-shaped discharge guide portion communicating with the inflow guide portion, and an amplification portion that is installed between the inflow guide portion and the discharge guide portion, the amplification portion including an intake hole that is connected to the gas supply tube to introduce the exhaust gases, a dispensing passage that is connected to the intake hole and extends in a circumferential direction of the discharge guide portion, and at least one guide passage connecting the dispensing passage to the inside of the discharge guide portion, the amplification portion introducing the air from the inflow guide portion as the gas introduced from the intake hole is directed to the discharge guide portion.
The air charger may further include an outer body including the inflow guide portion and a tube-shaped receiving portion connected to the inflow guide portion, and a tube-shaped inner body inserted in the receiving portion and provided at an outer circumference thereof with the dispensing passage having a stepped portion having an outer diameter of less than an inner diameter of the receiving portion, and the guide passage that is defined by a gap defined between the inner body and the outer body in an axial direction.
The air charger may further include a plurality of protrusions that are provided in the gap defined between the inner body and the outer body in the axial direction to form a plurality of the guide passages. The plurality of guide passage may be spaced apart from each other along an inner circumference of the receiving portion. The plurality of protrusions may be oriented toward a central axis of the receiving portion. Alternatively, the plurality of protrusions may be inclined in a rotational direction of the compression wheel relative to a direction toward a central axis of the receiving portion. The protrusions may be formed on the outer body. Alternatively, the protrusions may be formed on a front end surface of the inner body. Alternatively, the protrusions may be formed to protrude from an inner circumference of a separate ring-shaped spacing member. The thickness of the spacing member may be 0.03-0.15 mm. The outer body may have a first surface and the inner body may have a second surface that faces the first surface with the guide passage interposed between the first and second surfaces in the receiving portion of the outer body. At this point, the first surface may be perpendicularly formed with respect to a central axis of the receiving portion, and the second surface has a rounded surface curved toward the discharge guide portion.
The discharge guide portion may have an inner diameter that is gradually increased in an airflow direction. [Advantageous Effects]
According to the exemplary embodiments, since the turbocharger does not generate air resistance even at a high RPM, it can sufficiently supply air to the internal combustion engine at the high RPM. Therefore, output of the internal combustion engine can be improved.
In addition, a prior art turbocharger has a limitation in that it generates exhaust fumes when a turbo lag phenomenon occurs since a large amount of fuel is supplied while the air is not sufficiently supplied. However, according to the exemplary embodiments, since the turbocharger sufficiently supplies the air to the compressor upon starting, the generation of the exhaust fumes can be reduced.
Further, since the turbocharger of the exemplary embodiments introduces the air at 25 times the amount of exhaust gases supplied, there is no need to use an intercooler for reducing the air temperature. Further, since the exhaust gases can be diluted, the performance of the internal combustion engine can be improved.
In addition, since the turbocharger of the exemplary embodiments amplifies a supplying amount of the air upon starting the internal combustion engine and operates in response to an amount of exhaust gas, an air shortage problem can be solved even when output increases.
Further, since the turbocharger of the exemplary embodiments recovers a part of the exhaust gas and supplies the recovered exhaust gas to an inlet side and the exhaust gas enhances the introduction of the mixing air, output can be increased and the amount of harmful ingredients such as SOx, NOx, CO, and the like contained in the exhaust gases can be reduced.
In addition, since the turbocharger of the exemplary embodiments is provided with the dispensing passage and the inflow passage to uniformly supply the exhaust gases, output of the internal combustion engine can be improved. In addition, since the turbocharger of the exemplary embodiments is provided with a spiral protrusion, the exhaust gas and air can be effectively mixed with each other and thus the output of the internal combustion engine can be improved.
Further, since the turbocharger of the exemplary embodiments is designed to have protrusions inclined with respect to an axial direction in the air charger, a swirl flow can be generated in advance by the air applied to the compressor wheel by force of the injected exhaust gas. By making the rotational direction of the swirl flow coincide with the rotational direction of the compressor wheel, the power of the compressor, which is required to compress the introduced air, can be reduced. Accordingly, the compression of the introduced air can be effectively realized even when the power transferred from the turbine wheel in initial starting where an amount of the exhaust gas is relatively small. As a result, the turbo lag can be shortened and the output increases. In addition, exhaust fumes can be reduced.
[Description of Drawings] FIG. 1 is a schematic diagram of an air charging system for an internal combustion engine having a turbocharger according to a first exemplary embodiment of the present invention.
FIG. 2 is a partly cut-away perspective view of the turbocharger of Fig. 1. FIG. 3 is a cross-sectional view of an air charger of the turbocharger of FIG. 2. FIG. 4 is a schematic view of a modified example of the air charging system of
FIG. 1.
FIG. 5 is a cross-sectional view of a modified example of the air charger of FIG. 3.
FIG. 6 is a partially cut-away exploded perspective view of the air charger of FIG. 5.
FIGs. 7 and 8 are perspective views of modified examples of a tube fitting depicted in FIG. 6.
FIG. 9 is an exploded perspective view of an air charger applied to a turbocharger according to a second exemplary embodiment of the present invention. FIG. 10 is a partially cut-away perspective view of the air charger of FIG. 9.
FIG. 11 is a cross-sectional view taken in an axial direction of FIG. 10.
FIG. 12 is a top plan view of a spacing member depicted in FIG. 9.
FIG. 13 is a top plan view of a modified example of the spacing member of FIG. 12.
FIG. 14 is an exploded perspective view of an air charger applied to a turbocharger according to a third exemplary embodiment of the present invention.
FIG. 15 is an exploded perspective view of an air charger applied to a turbocharger according to a fourth exemplary embodiment of the present invention. [Mode for Invention]
The present invention will be described more fully hereinafter with reference to the accompanying drawings, in which exemplary embodiments of the invention are shown. As those skilled in the art would realize, the described embodiments may be modified in various different ways, all without departing from the spirit or scope of the present invention. In order to more clearly describe the present invention, a description of elements that are not related to the present invention will be omitted. Like reference numerals denote like elements throughout the drawings.
In the following exemplary embodiments, a term "compressed air" means gas having pressure that is higher than atmospheric pressure. FIG. 1 is a schematic diagram of an air charging system for an internal combustion engine having a turbocharger according to a first exemplary embodiment of the present invention.
Although FIG. 1 shows an internal combustion engine having a cylinder structure, the present invention is not limited to this. The present invention can be applied to all of internal combustion engines that perform intake/exhaust through an inlet and an outlet.
Referring to FIG. 1, a turbocharger system includes an intake tube 152 supplying air to an internal combustion engine 150, an exhaust tube 151 that is connected to the internal combustion engine 150 to discharge exhaust gases to an external side, and a turbocharger 100 that is connected to the intake and exhaust tubes
152 and 151 to enhance the inflow of the air.
The internal combustion engine 150 typically includes a cylinder, an intake valve, and an exhaust valve. The intake tube 152 directs the air to the intake valve and the exhaust tube 151 discharges the exhaust gases generated in the engine to the external side.
The turbocharger 100 includes a turbine 102 that is connected to the exhaust tube 151 to provide rotational force using the exhaust gases, a driving shaft 105 rotatably installed on the turbine 102, a compressor 103 that is connected to the driving shaft 105 to rotate by the rotational force generated by the turbine 102 and is connected to the intake tube 152 to enhance the inflow of the air, and an air charger 120 that is installed near an air inlet of the compressor 103 to enhance the inflow of the air to the compressor 103.
FIG. 2 is a partly cut-away perspective view of the turbocharger 100 of Fig. 1. The following will describe the turbocharger 100 with reference to FIG. 2.
The turbine 102 includes a turbine housing 116 defining an external shape thereof, and a turbine wheel 104 that is rotatably disposed in the turbine housing 116. The turbine wheel 104 is fixed on the driving shaft 105. The turbine 102 is provided at a circumference thereof with a scroll passage 113 communicating with a gas inflow tube 112. The exhaust gases discharged from the internal combustion engine 150 are directed from a turbine inlet 107 into the scroll passage 113 along the gas inflow tube 112. The exhaust gases introduced into the scroll passage 113 are injected toward the turbine wheel 104 to rotate the turbine wheel 104, and are subsequently discharged through a turbine outlet 108.
Meanwhile, the compressor 103 includes a compressor housing 117 defining an outer shape thereof, a compressor wheel 109 that is rotatably installed in the compressor housing 117, and an air intake tube 1 14 supplying air to the compressor 103. The compressor 103 is provided at a circumference thereof with a scroll passage 1 15 communicating with a compressor outlet 106. The air introduced through the air intake tube 114 is forcedly compressed by the compression wheel 109 to be directed to the scroll passage 115. The air directed to the scroll passage 115 is supplied to the internal combustion engine 150 through the compressor outlet 106.
In addition, the air charger 120 is installed on the air intake tube 1 14 of the compressor 103. A gas supply tube 130 is installed on the air charger 120 to connect the gas inflow tube 1 12 to the air charger 120. Pressure of the exhaust gases is maximized at a portion near the turbine inlet 107. Therefore, when the gas inflow tube 112 is installed on the turbine inlet 107, the exhaust gases can be supplied to the air charger 120 under a higher pressure. However, the present invention is not limited to the above configuration. That is, as shown in FIG. 4, the gas supply tube 140 may be installed near an outlet of the turbine 102. Since the exhaust gases discharged by the operation of the turbine 102 have considerable pressure, the exhaust gases can be supplied to the air charger 120 under a high pressure. The air charger 120 functions to amplify the air introduced into the compressor 103 by injecting the compressed exhaust gases supplied through the gas supply tube 130 into the air charger 120.
FIG. 3 is a cross-sectional view of the air charger of FIG. 2. Referring to FIG. 3, the air charger 120 is formed in a tube shape. The air charger 120 includes a convex portion 125 protruding toward a central axis and an amplifying portion 129 providing a passage communicating the gas supply tube 130 with an inner circumference of the convex portion 125.
The convex portion 125 includes an inflow guide portion 121 having an inner diameter that is gradually reduced in an air flow direction, and a discharge guide portion 123 having an inner diameter that increases in the airflow direction.
The amplifying portion 129 includes an intake hole 127 that communicates with an outer circumference to introduce the exhaust gases, a dispensing passage 128 that is connected to the intake hole to enable the exhaust gases to flow in a circumferential direction, and a guide passage 126 that connects the dispensing passage 128 to the inside of the amplifying portion 129 and is disposed between the inflow guide portion 121 and the discharge guide portion 123.
The entire air charger 120 of this exemplary embodiment is formed in one body, and has a tube structure with a hollow portion formed therein. The inflow guide portion 121 has an inner circumference that gradually protrudes toward a central axis thereof as it goes in the airflow direction so that the airflow area can be gradually reduced. Therefore, the flow rate of air passing through the inflow guide portion 121 gradually increases while the pressure of the air is gradually reduced. The discharge guide portion 123 has the smallest inner diameter at a portion near the inflow guide portion 121. A distance from an inner circumference of the discharge guide portion 123 to a central axis thereof gradually increases as it goes in the airflow direction. Therefore, the inner diameter of the air charger 120 is gradually reduced at the inflow guide portion 121 and gradually increased at the discharge guide portion 121.
Meanwhile, the dispensing passage 128 is formed in a circular shape extending in a circumferential direction in the air charger 120 and is connected to the intake hole
127. The intake hole 127 extends to an outer surface of the air charger to communicate with the gas supply tube 130. Therefore, the exhaust gases introduced through the intake hole 127 flow in the circumferential direction of the air charger 120 through the dispensing passage 128. Meanwhile, the dispensing passage 128 is connected to the inside of the air charger 120 through the guide passage 126. The guide passage 126 forms a gap spaced in an axial direction between the inflow guide portion 121 and the discharge guide portion 123, thereby being formed along the inner circumference of the air charger 120.
A boundary portion between the guide passage 126 and the discharge guide portion 123 is rounded.
Therefore, the exhaust gases introduced through the intake hole 127 flow in the circumferential direction of the air charger 120 along the dispensing passage 128, in the course of which the exhaust gases are introduced into the air charger 120 through the guide passage 126. The guide passage 126 is formed along the inner circumference of the air charger 120 so that the exhaust gases can be uniformly supplied into the air charger 120. The gas introduced under the high pressure flows toward the discharge guide portion 123 along the rounded boundary portion. At this point, the gas quickly flowing under the high pressure enhances the introduction of the air, thereby supplying a large amount of air into the internal combustion engine. As described above, the internal combustion engine into which a relatively large amount of mixing air is supplied generates high pressure during an expansion stroke to increase an output thereof, thereby generating power greater than that generated by a natural intake internal combustion engine by 35-60%.
FIG. 5 is a cross-sectional view of a modified example of the air charger of FIG. 3, and FIG. 6 is a partially cut-way exploded perspective view of the air charger of FIG. 5.
Referring to FIGs. 5 and 6, an air charger includes a gas supply tube 130 connected to an intake hole 127. That is, the gas supply tube 130 is connected to the intake hole 127 by a tube fitting 160. The tube fitting 160 is formed in a T-shape, and includes a gas inflow port 162 connected to the gas supply tube 130 and a gas discharge port 168 linearly connected to the gas inflow port 162. A cleaning agent inflow port 164 is perpendicularly formed between the gas inflow port 162 and the gas discharge port 168. A sealing cap 166 is installed on the cleaning agent inflow port 164. The tube fitting 160 not only connects the gas supply tube 130 to the intake hole 127, but also provides the cleansing agent inflow port 164 through which a cleaning agent can be injected into the air charger 120. The cleaning agent inflow port 164 is normally closed by the sealing cap 166. When there is a need to inject the cleaning agent to remove a pollutant material accumulated in the air charger 120, the sealing cap 166 is separated from the cleaning agent inflow port 164 and the cleaning agent is injected into the air charger 120 through the cleaning agent inflow port 164.
FIGs. 7 and 8 are perspective views of modified examples of the tube fitting of FIG. 6. As shown in FIG. 7, a tube fitting 170 includes a cleaning agent inflow port 174 with a sealing cap 176, a gas inflow port 172 linearly connected to the cleaning agent inflow port 174, and a gas discharge port 178 perpendicularly connected between the cleaning agent inflow port 174 and the gas inflow port 172, and is provided in the form of a branch tee shape. As shown in FIG. 8, a tube fitting 180 includes a gas discharge port 188, a cleaning agent inflow port 184 linearly connected to the gas discharge port 188 and having a sealing cap 186, and a gas inflow port 182 perpendicularly connected between the gas discharge port 188 and the cleaning agent inflow port 184, and is provided in the form of a run tee shape.
FIG. 9 is an exploded perspective view of an air charger applied to a turbocharger according to a second exemplary embodiment of the present invention. Referring to FIG. 9, an air charger in accordance with a second exemplary embodiment is installed near a compressed air inlet of a turbocharger. A turbocharger of the present exemplary embodiment is the same as that of the first exemplary embodiment except for a structure of an air charger 200. Therefore, a description of like elements will be omitted. The air charger 200 includes an outer body 210 having an inflow guide portion
212 having an inner sectional area that is gradually reduced in an airflow direction (a y-axis direction in FIG. 9) and a receiving portion 214 provided with an intake hole 216 that is connected to the inflow guide portion 212 to introduce gas, an inner body 220 inserted in the receiving portion 214 and provided at an inner circumference with a stepped portion 221, and a plurality of protrusions 234 installed between the outer and inner bodies 210 and 220.
FIG. 10 is a partially cut-away perspective view of the air charger of FIG. 9, and FIG. 1 1 is a cross-sectional view taken in an axial direction of FIG. 10. Referring to FIGS. 10 and 1 1, the outer body 210 is formed in a cylindrical tube structure, including the inflow guide portion 212 disposed at a front portion thereof and the receiving portion 214 disposed at a rear portion thereof.
The inflow guide portion 212 has an inner diameter that is gradually reduced as it goes in the airflow direction (the y-axis direction in FIG. 10) from a front end thereof. For example, an inner circumference 212a of the inflow guide portion 212 is curved to be convex toward a central axis thereof. Accordingly, the flow rate of air passing through the inflow guide portion 212 is increased and pressure thereof is reduced.
The inner circumference 212a of the inflow guide portion 212 is connected to a supporting surface 212b that connects the inner circumference 212a to the receiving portion 214 and is perpendicularly formed with respect to a central axis of the receiving portion 214.
The receiving portion 214 is formed in a cylindrical tube structure having a hollow portion in which the inner body 220 is fitted. The intake hole 216 is located at a front portion of the receiving portion 214 and opened to the outer circumference to introduce the gas. At this point, the gas introduced through the intake hole 216 is compressed air having a higher pressure than atmospheric pressure. In addition, the intake hole 216 functions as a passage that is connected to the gas supply tube 270 to supply the exhaust gases into the receiving portion 214.
The inner body 220 is formed in a cylindrical tube structure that is fitted in the receiving portion 214. As shown in FIG. 9, the stepped portion 221 is formed at a front portion of the inner body 220. The stepped portion 221 has an outer diameter of less than an inner diameter of the receiving portion 214 and extends along the outer circumference of the inner body 220. Therefore, as shown in FIG. 9, a space is defined between the stepped portion 221 and the receiving portion 214. The space is referred to as a dispensing passage 225. The dispensing passage 225 is connected to the intake hole 216 so that the gas introduced through the intake hole 216 can flow along the outer circumference of the inner body 220.
As shown in FIG. 9, the protrusions 234 are located between the outer and inner bodies 210 and 220 to space the outer and inner bodies 210 and 220 in an axial direction from each other. The protrusions 234 are formed to protrude from an inner circumference of a ring-shaped spacing member 230.
That is, the spacing member 230 includes a ring-shaped support 232. The protrusions 234 extend from an inner circumference of the ring-shaped support 232 toward a center C and are spaced apart from each other along the inner circumference. The ring-shaped support 232 is spaced apart from the inner body 220 and contacts an inner surface of the receiving portion 214. A front end of the inner body 220 contacts the protrusions 234.
As shown in FIG. 10, when the outer and inner bodies 210 and 220 are spaced apart from each other by the protrusions 234, gaps between adjacent protrusions 234 define guide passages 227. The guide passages 227 are spaced apart from each other along the front end of the inner body 220. The gas is introduced into a discharge guide portion 223 through the guide passages 227.
As described above, according to the present exemplary embodiment, the protrusions 234 are disposed to be spaced apart from each other and the gas are supplied to the gaps defined between the protrusions. Therefore, the gas can be uniformly divided and supplied into the air charger 200.
Meanwhile, a thickness of the spacing member 230 may be 0.03-0.15 mm. When the thickness of the spacing member 230 is less than 0.03 mm, an amount of the exhaust gases introduced into the air charger 200 is too small to be effectively injected. Meanwhile, when the thickness of the spacing member 230 is greater than 0.15 mm, since the sectional area of the guide passages 227 is too big, the injection speed is reduced. Preferably, the spacing member 230 may have a thickness of 0.05-0.08 mm. By setting the thickness of the spacing member 230 as described above, the outer body 210 can be properly spaced apart from the inner body 220 and the guide passages 227 can be properly formed.
Meanwhile, when surfaces of the outer and inner bodies 210 and 220, which face each other with the guide passages 227 interposed therebetween in the receiving portion 214 of the outer body 210, are referred to as first and second surfaces, respectively, the first surface is perpendicularly formed with respect to the central axis of the receiving portion 214 and the second surface is formed to have a rounded portion 226 curved toward the discharge guide portion 223. At this point, as the first and second surfaces extend toward the central axis while maintaining a uniform gap therebetween, the second surface is first curved so as to direct the introduced gas toward the discharge guide portion 223 (see a circled portion in FIG. 11).
The tube-shaped discharge guide portion 223 is formed at a downstream side of the rounded portion 226. The discharge guide portion 223 has an inner diameter that is gradually increased in the airflow direction (the y-axis direction of FIG. 11) from the rounded portion 226. The smallest inner diameter of the rounded portion 226 may be same as the smallest inner diameter of the discharge guide portion 223. Therefore, the air introduced along the inflow guide portion 212 can be stably discharged along the discharge guide portion 223. The exhaust gases introduced into the inner body 220 flow toward the discharge guide portion 223 along the rounded portion 226 by the Coanda effect. The Coanda effect is the tendency of a fluid to flow in a direction where the smallest energy is consumed. When there is a curved surface at a front portion with respect to a flow direction of the fluid, the fluid flows along the curved surface. In accordance with the Coanda effect, it becomes possible to predict the flow direction of the fluid in advance.
As described above, when the rounded portion is formed at a boundary portion between the guide passages 227 and the discharge guide portion 223, the exhaust gases can be effectively directed toward the discharge guide portion 223.
The air charger 200 in accordance with the present exemplary embodiment is formed of a material having excellent durability, such as stainless steel or engineering plastic, which can withstand a high temperature and has excellent corrosion-resistance.
Meanwhile, the outer and inner bodies 210 and 220 may be coupled to each other in a shrink-fitting manner or by welding in a state where the inner body 220 is fitted in the outer body 210. Alternatively, the outer and inner bodies 210 and 220 may be screw-coupled to each other by forming a female screw portion on the inner circumference of the receiving portion 214 of the outer body 210 and a male screw portion on the outer circumference of the inner body 220.
By the above-described structure, the gas can be supplied into the air charger 200 via the intake hole 216, dispensing passage 225, and guide passages 227. In addition, when gas having high pressure is introduced into the air charger 200, a vacuum space V is formed behind the guide passages 227. The vacuum space V amplifies the introduction of the mixing air. That is, an amount of air of 25 times that of the gas introduced through the intake hole 216 can be introduced into the air charger 200.
As described above, the internal combustion engine charged with the mixing air generates high pressure during the expansion stroke to enhance the output thereof. In addition, since the temperature of the air is not increased even when the air is compressed, there is no need to install an intercooler. Further, since the gas introduced through the intake hole 216 is mixed with a large amount of air, the temperature is reduced and the concentration is diluted. Therefore, the internal combustion engine is not overloaded.
FIG. 12 is a top plan view of the spacing member depicted in FIG. 9, and FIG. 13 is a top plan view of a modified example of the spacing member of FIG. 12. Referring to FIG. 12, the spacing member 230 includes the ring-shaped support
232 and the plurality of the protrusions 234 extending from the inner circumference of the ring-shaped support 232. The protrusions 234 are oriented toward the center C of the ring-shaped support 232. The protrusions 234 define the guide passages 227 of the air charger 200 in accordance with the present exemplary embodiment. The guide passages 227 function to inject the gas introduced through the intake hole 216 toward the central axis at a high speed.
Referring to FIG. 13, a spacing member 330 includes a ring-shaped support 332 and a plurality of protrusions 334 protruding from an inner circumference of the ring-shaped support 332. According to this modified example, the protrusions 334 are oriented in a direction away from the center of the ring-shaped support 332. That is, the protrusions 334 extend from the inner circumference of the support 332 at a predetermined inclined angle α of less than 90° . At this point, the protrusions 334 may be inclined in a rotational direction of the compressor wheel 109 depicted in FIG. 2 relative to a direction toward a center of the support 332. In this case, since the gas that rotates while passing through the air charger can pass through the compressor wheel 109 while maintaining the same rotational direction, the air can be sufficiently supplied to the internal combustion engine while minimizing a loss of kinetic energy.
When the gas is injected through the guide passages defined between the protrusions 334, the gas generates an eddy current in the rotational direction of the compressor wheel 109 and flows toward the central axis of the receiving portion 214.
When the exhaust gases generate the eddy current, the exhaust gases and the mixing air can be more effectively mixed with each other and air-resistance acting on the compressor wheel is reduced. That is, by making the rotational direction of the eddy current identical to the rotational direction of the compressor wheel 109 as described above, power consumption of the compressor, which is required to compress the introduced air, can be reduced and thus the compression of the introduced air can be effectively realized even when power transferred from the turbine wheel in an initial starting operation where an amount of the exhaust gases is relatively small is low. As a result, the turbo lag is shortened and the output increases. Furthermore, exhaust fumes can be reduced.
FIG. 14 is an exploded perspective view of an air charger applied to a turbocharger according to a third exemplary embodiment of the present invention.
Referring to FIG. 14, an air charger 400 in accordance with a third exemplary embodiment is installed near an air inlet of the compressor to amplify air introduced into the compressor.
A turbocharger of the present exemplary embodiment is the same as that of the first exemplary embodiment except for a structure of the air charger 400. Therefore, a description of like elements will be omitted.
The air charger 400 includes an outer body 410 having an inflow guide portion 412 having an inner sectional area that is gradually reduced in an airflow direction and a receiving portion 414 connected to the inflow guide portion 412 and provided with an intake hole 416, and an inner body 420 inserted in the receiving portion 414 and provided at an inner circumference thereof with a stepped portion 421 and at a front end surface with a plurality of protrusions 425.
The outer body 410 is formed in a cylindrical tube structure. The inflow guide portion 412 has an inner surface that gradually protrudes toward a central axis as it goes toward the receiving portion. Therefore, an inner diameter of the outer body 410 is gradually reduced as it goes toward the receiving portion 414. The receiving portion
414 is formed in a tube structure communicating with the inflow guide portion 412.
The inner body 420 includes the stepped portion 421 formed on an outer circumference thereof and a discharge guide portion 423 formed in a tube structure.
The stepped portion 421 defines a space between the receiving portion 414 and the inner body 420. The discharge guide portion 423 has an inner diameter that is gradually increased in the airflow direction.
Meanwhile, the protrusions 425 are formed on the front surface (i.e., a surface facing the outer body) of the inner body 420. The protrusions 425 are spaced apart from each other in a circumferential direction by a predetermined distance. The inner and outer bodies 420 and 410 are spaced apart from each other by the protrusions 425 and thus passages are formed between the protrusions 425. The exhaust gases are introduced into the discharge guide portion 423 through the passages.
As described above, according to the present exemplary embodiment, since the protrusions 425 are formed on the front end surface of the inner body 420, there is no need to install a separate spacing member. Therefore, the manufacturing process can be simplified.
FIG. 15 is an exploded perspective view of an air charger applied to a turbocharger according to a fourth exemplary embodiment of the present invention. Referring to FIG. 15, an air charger 500 in accordance with a third exemplary embodiment is installed near an air inlet of the compressor to amplify air introduced into the compressor.
A turbocharger of the present exemplary embodiment is the same as that of the first exemplary embodiment except for a structure of the air charger 500. Therefore, a description of like elements will be omitted.
The air charger 500 in according with the fourth exemplary embodiment includes an outer body 510 having an inflow guide portion 512 having an inner sectional area that is gradually reduced in an airflow direction and a receiving portion 514 connected to the inflow guide portion 512 and provided with an intake hole 516, and an inner body 520 that is inserted in the receiving portion 514 and has a stepped portion 521 formed on a front end thereof and a discharge guide portion 523 communicating with the inflow guide portion 512.
The outer body 510 is formed in a cylindrical tube structure. The inflow guide portion 512 has an inner surface that gradually protrudes toward a central axis as it goes toward the receiving portion. Therefore, an inner diameter of the outer body 510 is gradually reduced as it goes toward the receiving portion 514. In addition, the inflow guide portion 512 has an arc-shaped section, including a guide surface 512a guiding the inflow of the air and a supporting surface 512b connecting the guide surface 512a to the receiving portion 514 and perpendicularly formed with respect to the receiving portion 514.
The supporting surface 512b contacts the front end of the inner body 520 when the inner body 520 is fitted in the receiving portion 514. The supporting surface 512b is provided with a plurality of protrusions 515. The protrusions 515 are spaced apart from each other along an inner circumference of the receiving portion 514 by a predetermined distance.
Therefore, when the inner body 520 is inserted in the receiving portion 514, the inner body 520 and the supporting surface 512b are spaced apart from each other by the protrusions 515 and thus passages are formed between the protrusions 515. The exhaust gases are directed to the discharge guide portion 523 through the passages formed between the protrusions 515.
As described above, according to the present exemplary embodiment, since the protrusions 515 are formed on the supporting surface 512b of the outer body 510, there is no need to install a separate spacing member. Therefore, the manufacturing process can be simplified.
While this invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.

Claims

[CLAIMS] [Claim 1 ]
A turbocharger comprising: a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine; a driving shaft rotatably connected to the turbine wheel; a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel; an air charger that is connected to the compressor to amplify air introduced into the compressor; and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger, wherein the air charger is formed in a tube shape and includes a convex portion protruding toward a central axis of the air charger and an amplification portion having a passage communicating the gas supply tube with the inside of the convex portion.
[Claim 2]
The turbocharger of claim 1, wherein a boundary portion between the amplification portion and a surface of the convex portion, which is formed at an air discharge side, is rounded.
[Claim 3] The turbocharger of claim 1 , wherein the convex portion is highest at a portion connected to the amplification portion.
[Claim 4] The turbocharger of claim 1 , wherein the gas supply tube is connected to an air inflow tube of the compressor.
[Claim 5]
The turbocharger of claim 1 , wherein the convex portion comprises an inflow guide portion having an inner diameter that is gradually reduced in an airflow direction and a discharge guide portion that is spaced apart from the inflow guide portion and having an inner diameter that is gradually increased in the airflow direction.
[Claim 6] The turbocharger of claim 1 , wherein the amplification portion comprises: an intake hole that is connected to the gas supply tube to introduce the exhaust gases; a dispensing passage that is connected to the intake hole and extends in a circumferential direction of the convex portion; and a guide passage connecting the dispensing passage to the inside of the convex portion.
[Claim 7] The turbocharger of claim 1, wherein the air charger comprises: an outer body comprising a tube-shaped inflow guide portion for guiding introduction of the air, a tube-shaped receiving portion connected to the inflow guide portion, and an intake hole that is connected to the gas supply tube to introduce the exhaust gases; and a tube-shaped inner body inserted in the receiving portion and provided at an outer circumference thereof with a dispensing passage having a stepped portion having an outer diameter of less than an inner diameter of the receiving portion and extending along a circumferential direction of the convex portion, and a guide passage that is defined by a gap in an axial direction between the inner body and the outer body to connect the dispensing passage to the inside of the convex portion.
[Claim 8]
The turbocharger of claim 1 , wherein the gas supply tube is connected to the amplification portion with a tube fitting provided with a cleaning agent inflow port and interposed between the gas supply tube and the amplification portion.
[Claim 9]
A turbocharger comprising: a turbine having a turbine wheel rotating by exhaust gases from an internal combustion engine; a driving shaft rotatably connected to the turbine wheel; a compressor connected to the driving shaft and having a compressor wheel rotating by rotational force of the turbine wheel; an air charger that is connected to the compressor to amplify air introduced into the compressor; and a gas supply tube having a first end connected to the air charger and a second end that is installed near a turbine inlet or a turbine outlet to supply the exhaust gases to the air charger, wherein the air charger comprises: an inflow guide portion for guiding introduction of the air; a tube-shaped discharge guide portion communicating with the inflow guide portion; and an amplification portion that is installed between the inflow guide portion and the discharge guide portion, the amplification portion comprising an intake hole that is connected to the gas supply tube to introduce the exhaust gases, a dispensing passage that is connected to the intake hole and extends in a circumferential direction of the discharge guide portion, and at least one guide passage connecting the dispensing passage to the inside of the discharge guide portion, the amplification portion introducing the air from the inflow guide portion as the gas introduced from the intake hole is directed to the discharge guide portion.
[Claim 10]
The turbocharger of claim 9, the air charger further comprises: an outer body comprising the inflow guide portion and a tube-shaped receiving portion connected to the inflow guide portion; and a tube-shaped inner body inserted in the receiving portion and provided at an outer circumference thereof with the dispensing passage having a stepped portion having an outer diameter of less than an inner diameter of the receiving portion, and the guide passage that is defined by a gap defined between the inner body and the outer body in an axial direction.
[Claim 1 1 ]
The turbocharger of claim 10, wherein the air charger further comprises a plurality of protrusions that are provided in the gap defined between the inner body and the outer body in the axial direction to form a plurality of the guide passages.
[Claim 12]
The turbocharger of claim 1 1 , wherein the plurality of guide passage are spaced apart from each other along an inner circumference of the receiving portion.
[Claim 13]
The turbocharger of claim 11 , wherein the plurality of protrusions are oriented toward a central axis of the receiving portion.
[Claim 14] The turbocharger of claim 11 , wherein the plurality of protrusions are inclined in a rotational direction of the compression wheel relative to a direction toward a central axis of the receiving portion.
[Claim 15]
The turbocharger of claim 1 1 , wherein the protrusions are formed on the outer body.
[Claim 16]
The turbocharger of claim 11 , wherein the protrusions are formed on a front end surface of the inner body.
[Claim 17] The turbocharger of claim 11, wherein the protrusions are formed protruding from an inner circumference of a separate ring-shaped spacing member.
[Claim 18]
The turbocharger of claim 9, wherein the gas supply tube is connected to the intake hole by a tube fitting provided with a cleaning agent inflow port.
[Claim 19]
The turbocharger of claim 10, wherein the outer body has a first surface and the inner body has a second surface that faces the first surface with the guide passage interposed between the first and second surfaces in the receiving portion of the outer body; and the first surface is perpendicularly formed with respect to a central axis of the receiving portion and the second surface has a rounded surface curved toward the discharge guide portion.
[Claim 20]
The turbocharger of claim 19, wherein the discharge guide portion has an inner diameter that is gradually increased in an airflow direction.
PCT/KR2008/004433 2007-08-28 2008-07-30 Turbo charger WO2009028802A2 (en)

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KR1020070086731A KR100963278B1 (en) 2007-08-28 2007-08-28 Turbo charger

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011106293A (en) * 2009-11-12 2011-06-02 Mitsubishi Motors Corp Exhaust gas recirculation device
DE102011110285A1 (en) * 2011-06-21 2012-12-27 Mtu Friedrichshafen Gmbh Intake pipe element and compressor assembly thereof
DE102011117360A1 (en) * 2011-10-29 2013-05-02 Volkswagen Ag Gas supply system i.e. exhaust gas recirculation system, for guiding gas to flow of another gas in internal combustion engine of e.g. lorry, has pipeline connected with another pipeline by inlet that is realized by annular gap
JP2014136977A (en) * 2013-01-15 2014-07-28 Isuzu Motors Ltd Internal combustion engine and egr gas mixing device
AT525743B1 (en) * 2022-04-29 2023-07-15 Avl List Gmbh COMBUSTION ENGINE

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101429848B1 (en) * 2013-02-13 2014-08-12 한승주 Air Expander driven by Rotating Magnetic Field
KR101427387B1 (en) * 2014-01-29 2014-08-07 주식회사 그린테크 Turbo charger for automobile

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5591722A (en) * 1978-12-29 1980-07-11 O M T:Kk Washing method and device for supercharger turbine
US4461150A (en) * 1981-02-21 1984-07-24 Daimler-Benz Aktiengesellschaft Exhaust gas return pipe connection for an internal combustion engine
JPH01159134U (en) * 1988-04-26 1989-11-02
JPH0474577A (en) * 1990-07-16 1992-03-09 Mitsubishi Heavy Ind Ltd Jet washing apparatus
US5402938A (en) * 1993-09-17 1995-04-04 Exair Corporation Fluid amplifier with improved operating range using tapered shim
JPH10131742A (en) * 1996-10-29 1998-05-19 Yanmar Diesel Engine Co Ltd Exhaust gas recirculating type gas engine
JP2001165002A (en) * 1999-11-09 2001-06-19 Caterpillar Inc Intake venturi for exhaust gas circulating system in internal combustion engine
JP2002155751A (en) * 2000-09-21 2002-05-31 Caterpillar Inc Turbo-charger with exhaust gas recirculation
JP2003003910A (en) * 2001-06-05 2003-01-08 Holset Eng Co Ltd Device and method for mixing flow of fluid
JP2007092592A (en) * 2005-09-28 2007-04-12 Hino Motors Ltd Egr gas mixing device

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5591722A (en) * 1978-12-29 1980-07-11 O M T:Kk Washing method and device for supercharger turbine
US4461150A (en) * 1981-02-21 1984-07-24 Daimler-Benz Aktiengesellschaft Exhaust gas return pipe connection for an internal combustion engine
JPH01159134U (en) * 1988-04-26 1989-11-02
JPH0474577A (en) * 1990-07-16 1992-03-09 Mitsubishi Heavy Ind Ltd Jet washing apparatus
US5402938A (en) * 1993-09-17 1995-04-04 Exair Corporation Fluid amplifier with improved operating range using tapered shim
JPH10131742A (en) * 1996-10-29 1998-05-19 Yanmar Diesel Engine Co Ltd Exhaust gas recirculating type gas engine
JP2001165002A (en) * 1999-11-09 2001-06-19 Caterpillar Inc Intake venturi for exhaust gas circulating system in internal combustion engine
JP2002155751A (en) * 2000-09-21 2002-05-31 Caterpillar Inc Turbo-charger with exhaust gas recirculation
JP2003003910A (en) * 2001-06-05 2003-01-08 Holset Eng Co Ltd Device and method for mixing flow of fluid
JP2007092592A (en) * 2005-09-28 2007-04-12 Hino Motors Ltd Egr gas mixing device

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011106293A (en) * 2009-11-12 2011-06-02 Mitsubishi Motors Corp Exhaust gas recirculation device
DE102011110285A1 (en) * 2011-06-21 2012-12-27 Mtu Friedrichshafen Gmbh Intake pipe element and compressor assembly thereof
DE102011110285B4 (en) * 2011-06-21 2013-05-29 Mtu Friedrichshafen Gmbh Intake pipe element and compressor assembly thereof
US9217444B2 (en) 2011-06-21 2015-12-22 Mtu Friedrichshafen Gmbh Intake conduit element and compressor arrangement therefrom
DE102011117360A1 (en) * 2011-10-29 2013-05-02 Volkswagen Ag Gas supply system i.e. exhaust gas recirculation system, for guiding gas to flow of another gas in internal combustion engine of e.g. lorry, has pipeline connected with another pipeline by inlet that is realized by annular gap
JP2014136977A (en) * 2013-01-15 2014-07-28 Isuzu Motors Ltd Internal combustion engine and egr gas mixing device
AT525743B1 (en) * 2022-04-29 2023-07-15 Avl List Gmbh COMBUSTION ENGINE
AT525743A4 (en) * 2022-04-29 2023-07-15 Avl List Gmbh COMBUSTION ENGINE

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