WO1998011336A1 - Structure d'aspiration pour moteurs a combustion interne - Google Patents

Structure d'aspiration pour moteurs a combustion interne Download PDF

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Publication number
WO1998011336A1
WO1998011336A1 PCT/JP1996/002629 JP9602629W WO9811336A1 WO 1998011336 A1 WO1998011336 A1 WO 1998011336A1 JP 9602629 W JP9602629 W JP 9602629W WO 9811336 A1 WO9811336 A1 WO 9811336A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
intake
internal combustion
combustion engine
intake passage
Prior art date
Application number
PCT/JP1996/002629
Other languages
English (en)
Japanese (ja)
Inventor
Teruhiko Minegishi
Hiroyuki Nemoto
Mitsunori Nishimura
Original Assignee
Hitachi, Ltd.
Hitachi Car Engineering Co., Ltd.
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 Hitachi, Ltd., Hitachi Car Engineering Co., Ltd. filed Critical Hitachi, Ltd.
Priority to PCT/JP1996/002629 priority Critical patent/WO1998011336A1/fr
Priority to JP51346998A priority patent/JP3905560B2/ja
Priority to US09/254,857 priority patent/US6443114B2/en
Priority claimed from US09/254,857 external-priority patent/US6443114B2/en
Publication of WO1998011336A1 publication Critical patent/WO1998011336A1/fr

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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
    • F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
    • F02B27/02—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means
    • F02B27/0205—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means characterised by the charging effect
    • F02B27/021—Resonance charging
    • 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
    • F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
    • F02B27/02—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means
    • F02B27/0226—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means characterised by the means generating the charging effect
    • F02B27/0247—Plenum chambers; Resonance chambers or resonance pipes
    • F02B27/0252—Multiple plenum chambers or plenum chambers having inner separation walls, e.g. comprising valves for the same group of cylinders
    • 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
    • F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
    • F02B27/02—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means
    • F02B27/0226—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means characterised by the means generating the charging effect
    • F02B27/0268—Valves
    • F02B27/0273—Flap valves
    • 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
    • F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
    • F02B27/02—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means
    • F02B27/0294—Actuators or controllers therefor; Diagnosis; Calibration
    • 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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/08—Modifying distribution valve timing for charging purposes
    • F02B29/083—Cyclically operated valves disposed upstream of the cylinder intake valve, controlled by external means
    • 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 an intake device for an internal combustion engine, and more particularly, to an intake device using an intake inertia effect.
  • FIG. 2 of JP-A-60-224924 the position of the opening to the intake pipe is changed by rotating the substantially cylindrical surge tank, and the length of the intake pipe is changed.
  • the output torque of the internal combustion engine can be increased using the inertia effect.
  • an on-off valve is provided in the intake pipe, and the internal combustion engine rotates at a low speed.
  • the on-off valve is closed to increase the length of the intake pipe, thereby increasing the output torque during low-speed rotation.
  • Japanese Patent Application Laid-Open No. H08-170536 discloses that, of two intake pipes having different lengths, a cylindrical shut-off mechanism is provided in an intake passage at an intermediate portion of a shorter intake pipe. By opening and closing the shut-off mechanism according to the engine speed, it is possible to select whether to use only a long intake pipe or to increase the cross-sectional area of the flow path using both intake pipes. Is increasing.
  • the butterfly valve consists of a flat valve body and a rotating shaft, which are manufactured separately and connected with screws.
  • the rotating shaft is a long and narrow rod, and a plurality of butterfly valves are attached.
  • the butterfly A bearing is also provided between the valve and the butterfly valve.
  • the intake pipe In order to incorporate such a valve body and bearing in the middle of the intake pipe of the intake device, the intake pipe must be divided into two parts, which may reduce dimensional accuracy in assembly. .
  • the cylindrical one has an opening that penetrates in the radial direction of the cylinder, and the opening and the other part constitute a valve.
  • the rotation of the opening causes intermittent intake air flowing through it. Is done.
  • a hole for inserting a cylindrical on-off valve in the axial direction shall be manufactured integrally with a part of the intake pipe of the suction device, and an assembling method of inserting the cylindrical on-off valve into this hole shall be adopted. This eliminates the need to divide the intake pipe into two parts as in the case of a butterfly valve, and avoids a decrease in radial dimensional accuracy due to the assembly work.
  • the present invention provides an intake device for an internal combustion engine having an excellent on-off valve, which can solve the problems that cannot be solved by the above-mentioned conventional technology. That is, in the present invention, the connecting member for connecting the cylindrical on-off valve and the rotation mechanism is brought into contact with the cylindrical on-off valve via a ball-shaped member. As a result, even if there is an inclination between the direction of the rotation axis of the connecting member connecting the rotation mechanism for rotating the circular on-off valve and the cylindrical on-off valve and the direction of the rotation axis of the cylindrical on-off valve, Since the ball-shaped member is a kind of ball joint mechanism, the rotation can be transmitted smoothly. BRIEF DESCRIPTION OF THE FIGURES
  • FIG. 1 is a perspective view of an intake device for guiding intake air supplied to an internal combustion engine.
  • FIG. 2 is a sectional view taken along line aa of FIG.
  • FIG. 3 is a perspective view of a part of the on-off valve 8.
  • FIG. 4 is a sectional view taken along the line d--d in FIG.
  • FIG. 5 is an e-e sectional view of FIG.
  • FIG. 6 is an enlarged view of a part P in FIG.
  • FIG. 7 is a cross-sectional view of the valve body portion 801.
  • FIG. 8 is a cross-sectional view of the valve body portion 801.
  • FIG. 9 is a perspective view of a part of the on-off valve 8. FIG.
  • FIG. 10 is a sectional view taken along the line f-f in FIG.
  • FIG. 11 is a cross-sectional view showing a connection portion between the on-off valve 8 and the negative pressure module 9.
  • FIG. 12 is an enlarged view of a portion Q in FIG.
  • FIG. 13 is a perspective view of the input shaft 16.
  • FIG. 14 is a cross-sectional view showing a joint structure between the input shaft 16 and the ball portion 16 1.
  • FIG. 15 is a cross-sectional view showing a coupling structure between the input shaft 16 and the on-off valve 8.
  • FIG. 16 is a cross-sectional view showing an example of a bearing mechanism of the on-off valve 8.
  • FIG. 17 is a perspective view of the bearing member 21.
  • FIG. 18 is a sectional view showing another example of the same mechanism as in FIG.
  • FIG. 19 is a cross-sectional view showing another example of the same mechanism as in FIG.
  • FIG. 20 is a perspective view of the bearing member 30.
  • FIG. 21 is a sectional view taken along the line d--d of FIG. 3 similarly to FIG.
  • FIG. 22 is a sectional view taken along the line d--d of FIG. 3, similarly to FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • a spark ignition type internal combustion engine using fuel such as gasoline is used as an example, but the present invention can be applied to other types of internal combustion engines such as a self-ignition type internal combustion engine.
  • FIG. 1 is a perspective view of an intake device for guiding intake air supplied to an internal combustion engine (not shown), and FIG. 2 is a cross-sectional view taken along aa of FIG.
  • the intake device mainly comprises an intake pipe 2, which guides intake air to the internal combustion engine.
  • An injector 5 is attached to the intake pipe 2 to supply fuel to a combustion chamber 11 of a cylinder of the internal combustion engine shown in FIG.
  • a fuel pipe 4 is attached to the injector 5 to supply fuel.
  • the intake pipe 2 includes a collector 201 composed of i chambers, a branch 202 having the same number of intake passages as the number of cylinders of the internal combustion engine, and a throttle on-off valve (not shown) for adjusting the amount of intake air. 2 and a flange 204 for connecting to the internal combustion engine block 1 shown in FIG. 2, and these are integrally manufactured.
  • the branch 200 is further provided with a valve holder 206 and a common volume 207 (the common volume 207 is a single space that is long in a direction perpendicular to the plurality of branches 202).
  • the number of openings is the same as the number of the branches 202, and the openings are connected to the valve holders 206 corresponding to the respective branches 202.
  • the valve holders 206 are opened and closed. This is a hole-shaped chamber into which the valve 8 is inserted, and has a long space in the direction perpendicular to the plurality of branches 202. At a position corresponding to each of the branches 202, a common space is formed. It has an opening communicating the volume 207 and the branch 202.
  • the on-off valve 8 is inserted into the hole of the valve holder 206 and assembled to open and close the communication between the common volume 207 and the branch 202.
  • a negative pressure module 9 composed of a differential pressure actuator 901 and an electromagnetic valve 902 is connected.
  • the opening and closing valve 8 is driven by a negative pressure module 9.
  • Driving mechanisms such as diaphragm actuators that utilize the pressure difference between the negative pressure inside the intake pipe and the atmospheric pressure during operation of the internal combustion engine are widely used.
  • Negative pressure module 9 uses this as its operating principle A differential pressure actuator 901, which converts the differential pressure into motion, and a solenoid valve 902, which interrupts the pressure to the differential pressure actuator 901, to open and close the on-off valve 8, ie, 0 N — Control 0 F P '.
  • An air-fuel mixture consisting of fuel and suction is burned in a plurality of combustion chambers 11 of the internal combustion engine block 1 shown in FIG. 2, and the generated expansion pressure pushes down the piston 12 to obtain power.
  • the spark plug 3 ignites a spark in the air-fuel mixture, the intake valve 13 introduces intake air into the combustion chamber 11, and the exhaust valve 14 exhausts gas after combustion.
  • the intake air branches from the collector 201 into a plurality of branches 202 and is introduced into the combustion chamber 11 of the internal combustion engine.
  • the chamber of the common volume 207 communicates with the inside of the branch 202 via the on-off valve 8 and the inside of the same number of branch branches 6 10 as the branches 202.
  • the valve holder 206 is formed integrally with the branch 202 and the branch branch 61, and is made of a material capable of securing rigidity for the purpose of securing strength. For example, when a metal material such as steel or light metal alloy, or a resin material is used, a material containing a reinforcing material is used.
  • the on-off valve 8 can be manufactured by integral molding, it can be molded in one piece with a resin material, or forged or forged with a light metal alloy. Next, the effect of opening and closing the on-off valve 8 will be described.
  • the on-off valve 8 When the rotation speed of the internal combustion engine is low, the on-off valve 8 is closed. In this condition, the intake air passes through the chamber of the relatively long branch 202 [tl Inhaled. When the intake air passes through a relatively long pipe, the intake theory has a resonance point at a low frequency from the acoustic theory of the pipe. Therefore, the intake pipe is suitable when the rotation speed of the internal combustion engine is low.
  • the on-off valve 8 is kept open. In this state, since it is in a state of being spatially connected to the other branch 202 in the middle of the room of the branch 202, the length of the branch branch 6 10 having a relatively short length and the on-off valve 8 is combined. The inertia effect can be obtained by the number of times of the internal combustion engine corresponding to the resonance frequency of the pipeline. Therefore, the intake pipe is suitable for a region where the rotation speed of the internal combustion engine is small.
  • Third view is a perspective view of a part of the on-off valve 8.
  • the on-off valve 8 is arranged so as to intersect the direction of the passage of the branch branch 610.
  • the main configuration of the on-off valve 8 is a valve body portion 801 and a shaft portion 802, and the valve body portion 801 is flat.
  • the shaft portion 802 has a disk shape or a solid round rod shape in which the diameter of the shaft portion 802 is almost the same as the diameter of the valve body portion 801. . Since the shape of the valve body portion 800 and the shaft portion 802 is simple, they can be easily manufactured integrally.
  • the material may be integrally molded as a synthetic resin, or may be integrally molded or forged with a light alloy such as an aluminum alloy. Needless to say, the valve body portion 801 and the shaft portion 802 may be made of different materials.
  • FIG. 4 is a sectional view taken along the line d--d in FIG.
  • the outer diameter ⁇ d of the shaft portion 802 is set smaller than the inner diameter ⁇ D of the valve holder 206.
  • the inner diameter ⁇ D of the valve holder 206 is set to be larger than the height h of the internal passage of the branch branch 61 0.
  • the operating angle of the valve body portion 81 is represented by ⁇ shown in the figure, and it is understood that there is no need to rotate the valve portion 90 °.
  • seal ring 6 is provided with a split portion 61 to attach the seal ring 6 to the groove 803 of the on-off valve 8, this position must be changed to the common volume 200 as shown in Fig. 4. When installed on the side, even if there is leakage of intake air, the effect is small.
  • FIG. 5 is an e-e sectional view of FIG. 3, and FIG. 6 is an enlarged view of a portion P in FIG.
  • the thickness of the seal ring 6 is set smaller than the width of the groove 8 () 3 of the on-off valve 8, and is set so as to maintain the clearance in the axial direction of the on-off valve 8.
  • the outer diameter of the seal ring 6 in a free state where it is not inserted into the valve holder 206 is large enough not to be deformed from the inner diameter of the valve holder 206, and the shaft portion 802
  • the protrusion length is set so that it always protrudes outward from the outside diameter of.
  • the inner diameter of the seal ring 6 when inserted into the valve holder 20 ⁇ is set to be larger than the outer shape of the groove portion 803 of the on-off valve 8, thereby creating a radial clearance.
  • the gap in the axial direction of the on-off valve 8 is bent in the radial direction at the groove 803, and has a labyrinth structure with respect to the flow of intake air. Leakage can be minimized.
  • FIG. 7 is a cross-sectional view of the valve body portion 801 of the on-off valve 8, and shows a cross section d_d in FIG. 3 as in FIG.
  • An end portion 805 of the valve body portion 800 is inscribed in a circle having an outer diameter ⁇ d of the shaft portion 802.
  • the thickness of the valve body portion 801 is a rhombus-like shape that linearly increases from the end portion 805 toward the center. Such a shape can not only secure deformation strength unlike a flat plate having a constant thickness, but also can prevent a sudden increase in resistance to the flow of intake air.
  • FIG. 8 shows another example of the cross-sectional shape of the valve body 8 01 of the on-off valve 8.
  • the shape of the step surface of the valve body portion 801 is a spindle shape whose thickness increases in a curved manner from the end portion 805 toward the center. With such a cross-sectional shape, the same effect as that of FIG. 7 is obtained.
  • FIG. 9 shows another embodiment of the on-off valve 8, and is a perspective view of a part of the on-off valve 8 as in FIG.
  • FIG. 10 is the f-f section iS diagram of FIG.
  • a passage portion 806 having substantially the same cross-sectional shape as the branch branch 61 1 is formed in the opening / closing valve 8 to form an intake passage.
  • the opening and closing of the passage section 806 is performed by rotating the entire on-off valve 8 by the operating angle as shown in FIG. In the case of closing, the working angle ⁇ may be 90 degrees or less because the inside of the branching branch 6110 and the passage section 806 need only be shut off.
  • FIG. 11 shows the connection between the on-off valve 8 and the negative pressure module 9 in the section taken along the line c--c in FIG.
  • an opening / closing valve 8 is inserted into a valve holder 206 integral with a branch 202, and a negative pressure module 9 is attached to an end face thereof.
  • a fitting hole 807 is provided at an end of the on-off valve 8, and a ball part 161 provided on an end face of the input shaft 16 of the negative pressure module 9 is inserted.
  • the input shaft 16 is provided with a flange portion 162, which is in contact with the pin portion 80 so that when the flange portion 162 rotates, the pin portion 804 of the on-off valve 8 moves.
  • the input ⁇ 16 and the on-off valve 8 are pressed by a spring 20 via a spring receiver 19 in a direction in which both are separated in the axial direction.
  • a bearing section 15 is provided between the input shaft 16 and the negative pressure module 9, and supports the input shaft 16.
  • a lever 17 and a pin 18 are fixed on the opposite side of the input shaft 16 from the ball section 16 1 .When the input shaft 16 rotates, these also rotate the rotation shaft of the input shaft 16. Rotate as center.
  • the lever 17 has a function of stopping the rotation of the input shaft 16 at a predetermined angle.
  • the differential pressure actuator 90 1 of the negative pressure module 9 includes a rod 904, a cover 905, a spring 906, a diaphragm 907, a diaphragm receiver 908, and a diaphragm receiver 90. Consists of nine. The tip of the mouth 904 is in contact with the pin 18 so as to move the pin 18.
  • the diaphragm 907 is moved to the state shown in FIG.
  • the rod 904 moves upward, thereby moving the pin 18 and rotating the input shaft 16.
  • the flange portion 162 of the input shaft 16 rotates to move the pin portion 804 of the on-off valve 8, and the on-off valve 8 rotates.
  • FIG. 12 is an enlarged view of a portion Q in FIG.
  • the negative pressure module 9 When the negative pressure module 9 is mounted on the valve holder 206, it projects cylindrically into the negative pressure module 9 in order to absorb the misalignment that occurs between the on-off valve 8 and the input shaft 16.
  • a portion 903 is provided, and is configured to be fitted with a small clearance with the valve holder 206. The coaxiality can be adjusted by shifting the valve holder 206 and the negative pressure module 9 in the radial direction within the range of the minute gap.
  • FIG. 13 is a perspective view of the input shaft 16.
  • the spring receiver 19 and the spring 20 are mounted movably in the direction of the axis of the input shaft 16 between the ball portion 161 and the flange portion 162.
  • a notch 163 is provided in the flange 162. Either one or both of the ball part 16 1 and the flange part 16 2 of the input shaft 16 are manufactured separately from the input shaft, and attached to the input shaft 16.
  • FIG. 14 is a cross-sectional view showing the connection between the input shaft 16 and the ball portion 16 1.
  • the two parts may be joined by screws 16 4 or they may be joined by welding or pressing. No.
  • FIG. 15 is a cross-sectional view showing the connection between the human-powered shaft 16 and the on-off valve 8, and a part of the cross-section shown in FIG. 11 is extracted.
  • the spring 20 presses the spring receiver 1 9 against the on-off valve 8
  • the other end face of the on-off valve 8 described below is pressed against the valve holder 206 to determine the axial position of the on-off valve 8.
  • a dimensional error in the axial direction between the on-off valve 8 and the valve holder 206 and a dimensional difference due to thermal deformation or the like can be absorbed by the expansion and contraction of the spring 20.
  • the fitting hole 807 and the ball portion 161 function as a universal joint, and the inclination of the on-off valve 8 and the input shaft] .6 can be absorbed. Therefore, according to this configuration, a dimensional error between the on-off valve 8, the valve holder 206, and the negative pressure module 9 can be absorbed, and the on-off valve 8 can always be smoothly rotated.
  • FIG. 16 is a cross-sectional view showing an example of a bearing mechanism at the other end of the on-off valve 8, showing only a part of the cross section taken along the line c-c in FIG.
  • FIG. 7 is a perspective view of the bearing member 21.
  • FIG. A cap 22 is attached to the valve holder 206 by a screw 23, and an airtightness between the two is maintained by an O-ring 24. The cap 22 may be press-fitted or bonded to the valve holder 206 without using the () ring 24.
  • a metal shaft pin 25 is fixed to the cap 22 and rotatably inserted into the bearing member 21.
  • the shaft pin 25 must be made of metal in order to ensure the accuracy and strength of the bearing system.
  • the shaft pin 25 provided with a screw may be integrally molded with a resin cap 22, but not shown.
  • the nut having the pin 25 thermally welded and the nut provided with a female thread may be integrally molded, and the shaft pin 25 may be screwed in after that, or the cap 22 itself may be made of a metal having the shaft pin integrated. It may be made of metal.
  • the bearing member 2 1 is provided with a flange portion 2 11 1, and the shaft pin 25 is provided with a flange portion 2 51, which abuts to generate the spring 20 described in FIG. 15. Subject to axial forces.
  • FIG. 18 is a cross-sectional view of another example of the same mechanism as in FIG.
  • a protrusion 808 and a shaft hole 809 are provided at the end of the on-off valve 8 as in FIG. 16, and the bearing member 21 shown in FIG. 17 is fitted thereto. .
  • the end face of the valve holder 2 0 6 and the bearing pin 2 6 is attached, t The valve holder performs rotational sliding between the shaft pin portion 2 6 1 and the bearing member 2 1 bearing only pins 2 6
  • a thrust ring 27 is provided between 206 and the bearing member 21. The thrust ring 27 is brought into contact with the flange portion 2] 1 of the bearing member 21 to form the spring 20 as described with reference to FIG. Is generated in the axial direction.
  • the material of the bearing pin 26 is made of metal, similarly to the shaft pin 25 of FIG. I6, and the material of the thrust ring 27 is also made of metal.
  • FIG. 19 is a cross-sectional view of another example of the same mechanism as in FIG.
  • a bearing member 30 is fitted to the end of the on-off valve 8 as in FIG. 6, but the bearing member 30 differs from the bearing member 21 shown in FIG. 17 in that a hole is provided. Absent.
  • FIG. 20 is a perspective view of the bearing member 30.
  • FIG. 20 is a perspective view of the bearing member 30.
  • Rotational sliding is performed between the bearing pin 28 attached to the end face of the valve holder 206 and the bearing member 30.
  • a spring 29 is provided inside the bearing pin 28, and one end of the spring 29 abuts a thrust receiving surface 28 1 provided on the end face of the bearing pin 28, and the other end abuts the spring receiver 31.
  • the other surface of the spring receiver 31 slides in contact with the bearing member 30 fixed to the on-off valve 8.
  • Spring 29 has spring bearing 31 and bearing member 30 Push open / close valve 8 in the axial direction via.
  • the material of the bearing pin 28, the spring bearing 31 and the bearing member 30 is metal. The method of fixing the bearing pin 28 to the valve holder 206 is the same as that described with reference to FIG.
  • the spring 29 since the spring 29 generates a fixing force in the axial direction of the on-off valve 8, the spring 20 described with reference to FIGS. 13 to 15 can be omitted.
  • the opening / closing valve 8 needs to be fixed to the input shaft 16 so as not to come off from the valve holder 206.
  • FIGS. 21 and 22 show another embodiment of the seal ring 6 of the on-off valve 8 described in FIG. Each is a sectional view taken along the line d--d in FIG.
  • Fig. 4 illustrates the position of the split part 6 01 of the seal ring 6, but the material of the branch branch 6 10 and the valve holder 206 is made of high-strength material, and the on-off valve 8 is deformed by external force. If the seal ring 6 is made of a resilient material that is easily deformed, a defect may occur in the position shown in FIG. In Fig. 21, if each of them expands thermally in a high temperature atmosphere, the dimensional change in the direction perpendicular to the plane of the opening and closing valve 8 will be large, and the seal ring 6 will protrude into the intake passage. The outer diameter of split part 6 01 of ring 6 becomes larger than valve holder 2 ⁇ 6.
  • the position of the split portion 60 1 of the seal ring 6 be a portion of the wall other than the intake passage as shown in FIG.
  • a projection-like guide 208 is provided in a direction perpendicular to the plane of the paper to guide the split part 601, The split section 60 1 is prevented from rotating in the direction of the intake passage from the wall section. And since this guide 208 is configured so as to close the split portion 601, it is possible to reduce the leakage of intake air between the intake passages.
  • the present invention employs a configuration in which an input shaft, which is a connecting member for connecting a cylindrical on-off valve and a rotating mechanism, and a cylindrical on-off valve are brought into contact via a ball-shaped member.
  • a seal ring is provided on the on-off valve, and a split portion of the seal ring is provided on the wall of the valve holder into which the on-off valve is inserted, so that the seal ring does not return when the material expands and contracts due to thermal expansion. Failure can be prevented.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Biomedical Technology (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Abstract

La présente invention concerne une structure dans laquelle un arbre de commande constitue un élément permettant de relier une soupape de commutation cylindrique et un mécanisme rotatif. La soupape cylindrique de commutation entre en contact avec le mécanisme rotatif via un élément en forme de bille. Lorsqu'on utilise une telle structure, l'élément en forme de bille sert d'articulation à bille de sorte que le mouvement de rotation peut être transmis sans à coup, même quand il existe un angle d'inclinaison entre le sens de l'axe de rotation de l'arbre primaire par lequel le mécanisme rotatif fait tourner la soupape cylindrique de commutation et ladite soupape, lorsque ces éléments sont reliés, et le sens de l'axe de rotation de cette soupape de commutation.
PCT/JP1996/002629 1996-09-13 1996-09-13 Structure d'aspiration pour moteurs a combustion interne WO1998011336A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP1996/002629 WO1998011336A1 (fr) 1996-09-13 1996-09-13 Structure d'aspiration pour moteurs a combustion interne
JP51346998A JP3905560B2 (ja) 1996-09-13 1996-09-13 内燃機関の吸気装置
US09/254,857 US6443114B2 (en) 1996-09-13 1996-09-13 Suction structure for internal combustion engines

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/JP1996/002629 WO1998011336A1 (fr) 1996-09-13 1996-09-13 Structure d'aspiration pour moteurs a combustion interne
US09/254,857 US6443114B2 (en) 1996-09-13 1996-09-13 Suction structure for internal combustion engines

Related Child Applications (2)

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US09/254,857 A-371-Of-International US6443114B2 (en) 1996-09-13 1996-09-13 Suction structure for internal combustion engines
US10/091,471 Division US6598575B2 (en) 1999-03-15 2002-03-07 Air intake apparatus for an internal combustion engine

Publications (1)

Publication Number Publication Date
WO1998011336A1 true WO1998011336A1 (fr) 1998-03-19

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1304461A1 (fr) * 2001-10-17 2003-04-23 Hitachi, Ltd. Collecteur d'admission pour un moteur à combustion interne, et multiples et indépendants conduits d'admission
JP2008002296A (ja) * 2006-06-20 2008-01-10 Daikyo Nishikawa Kk ロータリバルブの軸受け構造
JP2022500598A (ja) * 2018-09-10 2022-01-04 ジー．ダブリュ．リスク カンパニー，インク． バルブアセンブリおよび方法

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JPS60549B2 (ja) * 1979-08-17 1985-01-08 バイエリツシエ モ−ト−レン ウエルケ アクチエンゲゼルシヤフト ４乃至６気筒直列内燃機関の吸気マニホ−ルド
JPS6157284U (fr) * 1984-09-20 1986-04-17
JPS61101620A (ja) * 1984-10-23 1986-05-20 フオード　モーター　カンパニー 多シリンダ内燃機関の吸気マニホルド
JPH01117919A (ja) * 1987-10-30 1989-05-10 Mazda Motor Corp エンジンの吸気装置
JPH0491242A (ja) * 1990-08-03 1992-03-24 Toray Ind Inc ファンシーヤーンの製造方法
JPH04143418A (ja) * 1990-10-04 1992-05-18 Toyota Motor Corp 内燃機関の吸気制御装置
JPH04219425A (ja) * 1990-02-26 1992-08-10 Vdo Adolf Schindling Ag スロットルバルブユニット
JPH0642356A (ja) * 1992-07-21 1994-02-15 Daihatsu Motor Co Ltd 内燃機関における吸気制御弁の構造
JPH0681735A (ja) * 1992-08-31 1994-03-22 Hitachi Ltd 内燃機関の吸気装置
JPH07158458A (ja) * 1993-12-10 1995-06-20 Mitsubishi Motors Corp 多気筒内燃エンジンの吸気制御装置
JPH08135472A (ja) * 1994-11-07 1996-05-28 Sanshin Ind Co Ltd 船外機の運転制御装置

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JPS60549B2 (ja) * 1979-08-17 1985-01-08 バイエリツシエ モ−ト−レン ウエルケ アクチエンゲゼルシヤフト ４乃至６気筒直列内燃機関の吸気マニホ−ルド
JPS6157284U (fr) * 1984-09-20 1986-04-17
JPS61101620A (ja) * 1984-10-23 1986-05-20 フオード　モーター　カンパニー 多シリンダ内燃機関の吸気マニホルド
JPH01117919A (ja) * 1987-10-30 1989-05-10 Mazda Motor Corp エンジンの吸気装置
JPH04219425A (ja) * 1990-02-26 1992-08-10 Vdo Adolf Schindling Ag スロットルバルブユニット
JPH0491242A (ja) * 1990-08-03 1992-03-24 Toray Ind Inc ファンシーヤーンの製造方法
JPH04143418A (ja) * 1990-10-04 1992-05-18 Toyota Motor Corp 内燃機関の吸気制御装置
JPH0642356A (ja) * 1992-07-21 1994-02-15 Daihatsu Motor Co Ltd 内燃機関における吸気制御弁の構造
JPH0681735A (ja) * 1992-08-31 1994-03-22 Hitachi Ltd 内燃機関の吸気装置
JPH07158458A (ja) * 1993-12-10 1995-06-20 Mitsubishi Motors Corp 多気筒内燃エンジンの吸気制御装置
JPH08135472A (ja) * 1994-11-07 1996-05-28 Sanshin Ind Co Ltd 船外機の運転制御装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1304461A1 (fr) * 2001-10-17 2003-04-23 Hitachi, Ltd. Collecteur d'admission pour un moteur à combustion interne, et multiples et indépendants conduits d'admission
JP2008002296A (ja) * 2006-06-20 2008-01-10 Daikyo Nishikawa Kk ロータリバルブの軸受け構造
JP2022500598A (ja) * 2018-09-10 2022-01-04 ジー．ダブリュ．リスク カンパニー，インク． バルブアセンブリおよび方法
US11598428B2 (en) 2018-09-10 2023-03-07 G.W. Lisk Company, Inc. Valve assembly and method
US11971106B2 (en) 2018-09-10 2024-04-30 G.W. Lisk Company, Inc. Valve assembly and method

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