WO2015163252A1 - 内燃機関の可変動弁装置 - Google Patents

内燃機関の可変動弁装置 Download PDF

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Publication number
WO2015163252A1
WO2015163252A1 PCT/JP2015/061816 JP2015061816W WO2015163252A1 WO 2015163252 A1 WO2015163252 A1 WO 2015163252A1 JP 2015061816 W JP2015061816 W JP 2015061816W WO 2015163252 A1 WO2015163252 A1 WO 2015163252A1
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WO
WIPO (PCT)
Prior art keywords
cam
axial direction
switching
hydraulic chamber
carrier
Prior art date
Application number
PCT/JP2015/061816
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
宏 大澤
Original Assignee
スズキ株式会社
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 スズキ株式会社 filed Critical スズキ株式会社
Priority to CN201580001943.9A priority Critical patent/CN105579675B/zh
Priority to DE112015001969.3T priority patent/DE112015001969B4/de
Publication of WO2015163252A1 publication Critical patent/WO2015163252A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/105—Hydraulic motors

Definitions

  • the present invention relates to a variable valve operating apparatus for an internal combustion engine that moves a cam carrier having a plurality of cams having different valve operating characteristics in the axial direction of a cam shaft.
  • variable valve operating apparatus for an internal combustion engine
  • a variable valve operating apparatus that switches a cam for operating a valve by moving a cam carrier having a plurality of cams with different valve operating characteristics on the outer periphery in the axial direction of the cam shaft.
  • a cam carrier having a plurality of cams with different valve operating characteristics on the outer periphery in the axial direction of the cam shaft.
  • This variable valve operating apparatus moves the cam carrier in the axial direction by inserting and removing a switching pin provided so as to be able to reciprocate in the radial direction of the cam carrier into and out of a spiral guide groove formed on the outer periphery of the cam carrier. .
  • the switching pin is inserted into and removed from the spiral guide groove formed on the outer periphery of the cam carrier, so that the tip of the switching pin every time the switching pin is inserted into and removed from the guide groove. Slides against the side wall of the guide groove so as to strongly rub the side wall of the guide groove. For this reason, the wear of the switching pin and the side wall of the guide groove is increased, and the durability of the switching pin and the cam carrier may be deteriorated.
  • the present invention has been made paying attention to the above-mentioned problems, and prevents the switching pin and the side wall of the concave portion of the cam carrier from being worn out, and the durability of the switching pin and the cam carrier is deteriorated. It is an object of the present invention to provide a variable valve operating apparatus for an internal combustion engine that can prevent this.
  • a camshaft rotatably supported by a cylinder head is provided so as to be coaxial with the camshaft, rotates integrally with the camshaft, and is axial with respect to the camshaft.
  • a cam carrier having a first cam and a second cam installed adjacent to each other on the outer peripheral surface so that the valve operating characteristics are different from each other, and the cam carrier in the axial direction of the cam shaft.
  • a variable valve operating apparatus for an internal combustion engine comprising: a cam switching unit that switches between a first cam and a second cam that are moved to operate a valve, wherein the cam switching unit is formed on an outer peripheral surface of a cam carrier.
  • the cam switching portion includes a housing that extends along the axial direction of the cam shaft and is attached to the cylinder head, and is provided inside the housing and holds a base portion of the switching pin.
  • a piston that is movable in the axial direction of the cam shaft, a first hydraulic chamber and a second hydraulic chamber that are provided in the housing and are disposed in the axial direction of the cam shaft across the piston, and a first hydraulic pressure
  • an oil control valve that supplies a regulated hydraulic pressure to the second hydraulic chamber and a switching pin depending on a hydraulic pressure supplied from the oil control valve to the first hydraulic chamber and the second hydraulic chamber. May be moved in the axial direction of the cam shaft.
  • the piston has a first opening communicating with the first hydraulic chamber and a second opening communicating with the second hydraulic chamber, and the housing is in the axial direction of the cam shaft.
  • a first relief hole having a longer diameter than the first opening and a second relief hole extending along the axial direction of the cam shaft and having a longer diameter than the second opening,
  • the cam carrier is movable between a first position where the valve is operated by the first cam and a second position where the valve is operated by the second cam,
  • One of the pair of opposing side walls is a first switching cam that moves the cam carrier to the first position
  • the other of the pair of side walls is the second that moves the cam carrier to the second position.
  • the cam switching portion is formed on the outer peripheral surface of the cam carrier, and the pair of side walls are opposed to each other in the axial direction of the cam shaft so that the width changes in the axial direction of the cam shaft.
  • a switching pin having a tip portion inserted into the concave portion and movable in the axial direction of the cam shaft.
  • the cam carrier can be moved in the axial direction of the cam shaft by pressing the pair of side walls with the tip of the switching pin while the tip of the switching pin is inserted into the concave portion. Therefore, it is unnecessary to insert / remove the switching pin into / from the concave portion, and wear of the switching pin and the pair of side walls can be prevented. As a result, the durability of the switching pin and the cam carrier can be improved.
  • the switching pin is moved in the axial direction of the camshaft by the hydraulic pressure difference supplied from the oil control valve to the first hydraulic chamber and the second hydraulic chamber in the housing.
  • the cam carrier can be moved in the axial direction of the cam shaft by using hydraulic pressure, and the configuration of the cam switching portion that moves the cam carrier in the axial direction of the cam shaft can be simplified.
  • the housing extends along the axial direction of the cam shaft, it is possible to prevent the height of the cylinder head from being increased, and as a result, it is possible to prevent the height of the internal combustion engine from increasing.
  • the first opening and the first relief hole communicate with each other, and the second opening and the second relief hole communicate with each other.
  • the tip of the switching pin receives an excessive load in one of the axial directions of the cam shaft by the cam carrier, the hydraulic pressure of the first hydraulic chamber is supplied from the first opening through the first relief hole. Relieving can lower the hydraulic pressure of the first hydraulic chamber.
  • the tip of the switching pin receives an excessive load on the other of the camshafts in the axial direction by the cam carrier, the hydraulic pressure in the second hydraulic chamber is relieved from the second opening through the second relief hole.
  • the hydraulic pressure in the second hydraulic chamber can be lowered.
  • the impact received by the switching pin from the cam carrier can be reduced, and the switching pin can be protected.
  • the hydraulic pressure of the first hydraulic chamber can be lowered by relieving the hydraulic pressure of the first hydraulic chamber from the first opening through the first relief hole.
  • the hydraulic pressure in the second hydraulic chamber is changed to Relieving from the two openings through the second relief hole can reduce the hydraulic pressure of the second hydraulic chamber.
  • FIG. 1 is a sectional view of a cylinder head provided with a variable valve operating apparatus for an internal combustion engine according to an embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention.
  • FIG. 3 is an external perspective view of the cam carrier according to the embodiment of the present invention.
  • FIG. 4 is a side sectional view of the cam carrier and the cam shaft in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention.
  • FIG. 5 is a side cross-sectional view of the cam shaft, cam carrier, and valve switching unit in the variable valve operating apparatus for an internal combustion engine according to the embodiment of the present invention.
  • FIG. 6 is a diagram showing a hydraulic circuit in the variable valve operating apparatus for an internal combustion engine according to the embodiment of the present invention, and shows a state in which the oil control valve supplies hydraulic pressure to the first hydraulic chamber.
  • FIG. 7 is a diagram showing a hydraulic circuit in the variable valve operating apparatus for an internal combustion engine according to the embodiment of the present invention, and shows a state in which the oil control valve supplies hydraulic pressure to the second hydraulic chamber.
  • FIG. 8 is a front view showing a state in which the cam carrier in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention is installed at the first position (position where the high-speed cam is selected).
  • FIG. 9 is a front view showing a state when the switching pin is moved in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention.
  • FIG. 10 is a front view showing a state in which the cam carrier in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention starts moving toward the second position (position where the low speed cam is selected).
  • FIG. 11 is a front view showing a state where the cam carrier in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention is installed at the second position (position where the low-speed cam is selected).
  • FIG. 12 is a top view showing a state in which the switching pin is in contact with the side surface of the cam carrier in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention.
  • FIG. 13 is a side view showing a state where the switching pin is in contact with the side surface of the cam carrier in the variable valve operating apparatus for the internal combustion engine according to the embodiment of the present invention.
  • FIG. 14 is a perspective view of a cam carrier when the second cam in the variable valve operating apparatus for an internal combustion engine according to another embodiment of the present invention is a pause cam.
  • 1 to 14 are views showing a variable valve operating apparatus for an internal combustion engine according to an embodiment of the present invention.
  • variable valve operating apparatus for an internal combustion engine
  • a variable valve gear 2 for an internal combustion engine is built in a head 1 ⁇ / b> A provided opposite to the cylinder head 1 and the cylinder head 1.
  • the cylinder head 1 of this embodiment is comprised including the head cover 1A.
  • variable valve apparatus 2 includes a cam shaft 3, a cam carrier 4, and a cam switching unit 5 installed above the cam carrier 4, and the lift state of the intake valve 13 is changed. Switch cams to change.
  • the cylinder head 1 includes a camshaft 30 on the exhaust valve side, an exhaust cam 40, and the like.
  • the variable valve apparatus 2 of the present embodiment uses a rocker arm 11 of a type that swings as the cam carrier 4 rotates.
  • the rocker arm 11 is installed such that a recess formed on the lower surface of the arm base end portion 11C abuts on a pivot 12A of a hydraulic lash adjuster (HLA) 12.
  • HLA hydraulic lash adjuster
  • a pressed roller 11A is pivotally supported by a pin 11B.
  • the pressed roller 11A protrudes from the upper surface of the rocker arm 11 and abuts either the high speed cam 41 constituting the first cam of the cam carrier 4 or the low speed cam 42 constituting the second cam.
  • the high speed cam 41 constitutes the first cam of the present invention
  • the low speed cam 42 constitutes the second cam of the present invention.
  • the lower surface of the arm tip portion 11D on the other end side of the rocker arm 11 is in contact with the upper end of the intake valve 13.
  • the intake valve 13 is provided so as to be able to advance and retreat in the axial direction with respect to the cylinder head 1 and closes the intake port 15 and the combustion chamber 16 that are opened and closed by the valve spring 14, that is, the intake port 13. Is biased in the direction.
  • the camshaft 3 is rotatably supported by a lower cam housing 6 and an upper cam housing 7 that serve as bearings installed at the upper part of the cylinder head 1.
  • the camshaft 3 is provided with an interlocking portion so as to rotate in conjunction with a crankshaft (not shown) by a chain or belt (not shown).
  • the lower cam housing 6 and the upper cam housing 7 are covered with a head cover 1A and are built in the cylinder head 1.
  • the rotational speed of the camshaft 3 is set to be 1/2 of the rotational speed of the crankshaft.
  • the camshaft 3 is along the front-rear direction of the internal combustion engine having the cylinder head 1 constituting a part of the internal combustion engine (the left-right direction on the paper surface of FIGS. 2 and 4). It is installed to extend.
  • two intake valves 13 are provided for each combustion chamber 16 as a set of two.
  • the intake valves 13 are provided in four sets. Eight are provided.
  • spline external teeth 31 having a predetermined width dimension in the axial direction are formed around the outer peripheral surface of the predetermined region in the length direction of the cam shaft 3.
  • a positioning mechanism 32 is provided in a region adjacent to the axial direction of the region where the spline external teeth 31 are formed in the camshaft 3.
  • the storage recess 33 formed to be recessed along the radial direction with respect to the cam shaft 3, the spring 34 stored in the storage recess 33, and stored in the storage recess 33 so as to be separated from the surface of the cam shaft 3.
  • a ball 35 installed so that the portion protrudes.
  • the ball 35 is locked to a first positioning groove 46 and a second positioning groove 47 provided on the cam carrier 4 side described later.
  • the cam carrier 4 is formed in a cylindrical shape so as to surround the cam shaft 3, and a spline inner tooth 45 that meshes with the spline outer teeth 31 of the cam shaft 3 on the inner peripheral surface of the cam carrier 4. Is formed. For this reason, the cam shaft 3 and the cam carrier 4 rotate together, and the cam carrier 4 is movable in the axial direction with respect to the cam shaft 3.
  • first positioning groove 46 and a second positioning groove 47 are formed in a region adjacent to a region where the spline inner teeth 45 are formed on the inner peripheral surface of the cam carrier 4 ( (See FIG. 3).
  • the first positioning groove 46 and the second positioning groove 47 engage the cam carrier 4 with the first position by locking the ball 35 of the positioning mechanism 32 provided on the camshaft 3 side. Positioning is performed by a click operation between the second position.
  • the cam carrier 4 is integrally provided with a high-speed cam 41 and a low-speed cam 42 having different valve operating characteristics along the axial direction on the peripheral surface.
  • unit structure of the high speed cam 41 and the low speed cam 42 is installed in a pair at predetermined intervals.
  • each high-speed cam 41 When a pair of high-speed cams 41 is selected, each high-speed cam 41 is positioned above the rocker arm 11, and when a pair of low-speed cams 42 is selected, each low-speed cam 42 is above the rocker arm 11. Located in.
  • the cam carrier 4 is movable between a first position where the intake valve 13 is operated by the high speed cam 41 and a second position where the intake valve 13 is operated by the low speed cam 42.
  • the high-speed cam 41 includes a base circle portion 41 ⁇ / b> A that serves as a foundation, and a nose portion 41 ⁇ / b> B that protrudes radially outward from the base circle portion 41 ⁇ / b> A.
  • the low-speed cam 42 has a base circle portion 42A having the same radius as the base circle portion 41A of the high-speed cam 41 serving as a base, and a radial direction outward from the base circle portion 42A in the radial direction from the nose portion 41B of the high-speed cam 41. And a nose portion 42B formed with a low protruding dimension.
  • the cam nose of the nose portion 41B of the high speed cam 41 of the present embodiment is formed larger than the cam nose of the nose portion 42B of the low speed cam 42, and the protruding dimension of the nose portion 41B of the high speed cam 41 is It is larger than the protruding dimension of 42 nose part 42B.
  • the opening time of the intake valve 13 can be made longer than when the low-speed cam 42 opens the intake valve 13, and a large amount of intake air is drawn into the combustion chamber 16. I can inhale.
  • the cam carrier 4 is compared with the case where the low speed cam 42 is switched to the second position where the intake valve 13 is opened.
  • the operating characteristics of the intake valve 13 are changed so that the engine output increases.
  • the high-speed cam 41 and the low-speed cam 42 are installed adjacent to each other along the axial direction, and the base circular portions 41A and 42A are continuous surfaces formed flush with each other in the axial direction. ing.
  • the nose portions 41B and 42B of the high-speed cam 41 and the low-speed cam 42 are installed in directions that are substantially in phase.
  • the high-speed cam 41 and the low-speed cam 42 define the lift timing of the intake valve 13 that operates in accordance with the operation of a crankshaft (not shown) depending on the installation state with respect to the camshaft 3.
  • the guide groove 43 constituting the concave portion of the present invention is formed on the outer peripheral surface of the cam carrier 4 so as to circulate continuously.
  • a first switching cam 43A that moves the cam carrier 4 to the first position
  • the other of the pair of side walls is the cam carrier 4. It is the 2nd switching cam 43B moved to the 2nd position.
  • first switching cam 43A and the second switching cam 43B constitute a pair of side walls of the present invention, and the first switching cam 43A constitutes one of a pair of opposing side walls, The second switching cam 43B constitutes the other of the pair of opposing side walls.
  • the guide groove 43 includes a maximum groove width portion 43C that maximizes the groove width, a minimum groove width portion 43D that minimizes the groove width, and a maximum groove width.
  • a groove width changing portion 43E that communicates between the portion 43C and the minimum groove width portion 43D is provided.
  • the minimum groove width portion 43D is a groove width through which a distal end portion 51b of a switching pin 51 described later can pass.
  • the maximum groove width portion 43C is formed to have a groove width having a space through which the tip portion 51b of the switching pin 51 can pass on both outer sides in the groove width direction with the minimum groove width portion 43D as a center.
  • the guide groove 43 of the present embodiment is configured such that the width changes in the axial direction of the cam shaft 3.
  • the cam switching unit 5 extends along the axial direction of the cam shaft 3 and is attached to the head cover 1A.
  • the cam switching unit 5 is provided inside the housing 52 and is provided with a base 51a of the switching pin 51. And a piston 53 that is movable in the axial direction of the camshaft 3.
  • the tip 51b of the switching pin 51 is inserted into the guide groove 43, and both axial ends of the cam shaft 3 at the tip 51b of the switching pin 51 are the first switching cam 43A and the second switching cam. It faces 43B. For this reason, the switching pin 51 is movable in the axial direction of the camshaft 3, and can contact the first switching cam 43A and the second switching cam 43B.
  • the hydraulic chambers 54 and 55 are provided inside the housing 52, and the hydraulic chambers 54 and 55 are arranged in the axial direction of the camshaft 3 with the piston 53 interposed therebetween.
  • the hydraulic chamber 54 constitutes the first hydraulic chamber of the present invention
  • the hydraulic chamber 55 constitutes the second hydraulic chamber of the present invention.
  • the housing 52 is formed with oil holes 52A and 52B, and the oil holes 52A and 52B are located above the hydraulic chambers 54 and 55, respectively.
  • a coil spring 56 is accommodated in the hydraulic chamber 54, and the coil spring 56 biases the piston 53 toward the hydraulic chamber 55. For this reason, the switching pin 51 contacts the first switching cam 43A in a state where the urging force of the coil spring 56 acts.
  • An opening 53 a is formed in the piston 53, and the opening 53 a communicates with the hydraulic chamber 54.
  • An opening 53 b is formed in the piston 53, and the opening 53 b communicates with the hydraulic chamber 55.
  • the opening 53a constitutes the first opening of the present invention
  • the opening 53b constitutes the second opening of the present invention.
  • a relief hole 52C is formed in the housing 52, and the relief hole 52C extends along the axial direction of the cam shaft 3 and has a longer diameter than the opening 53a.
  • a relief hole 52D is formed in the housing 52. The relief hole 52D extends along the axial direction of the cam shaft 3 and has a longer diameter than the opening 53b.
  • the relief hole 52C communicates with the opening 53a when the piston 53 moves in the axial direction of the cam shaft 3, and the relief hole 52D communicates with the opening 53b when the piston 53 moves in the axial direction of the cam shaft 3. To do.
  • the cam carrier 4 is not positioned at the first position where the high-speed cam 41 operates the intake valve 13, and the cam carrier 4 operates the intake valve 13 using the low-speed cam 42.
  • the opening 53a and the relief hole 52C communicate with each other, and the opening 53b and the relief hole 52D communicate with each other.
  • the relief hole 52C constitutes a first relief hole of the present invention
  • the relief hole 52D constitutes a second relief hole.
  • the cam switching unit 5 includes a hydraulic circuit 57.
  • the hydraulic circuit 57 is formed in the head cover 1A and is formed in the head cover 1A through the oil hole 52A.
  • the oil passage 58 communicates with the hydraulic chamber 54 through the oil hole 52A.
  • An oil passage 59 communicating with the hydraulic chamber 55 is provided.
  • the oil passage 58 communicates with an oil passage (not shown) of the oil pump 66, and oil is supplied from the oil pump 66 to the oil passage 58.
  • the oil pump 66 may be a mechanical oil pump driven by rotation of the crankshaft or an electric pump.
  • the hydraulic circuit 57 includes an oil control valve (hereinafter simply referred to as OCV) 60, and the oil passage of the OCV 60 communicates with the oil passage 58 and the oil passage 59.
  • OCV 60 includes a four-port spool valve in which a spool 62 is provided inside a sleeve 61, and includes four ports 60a to 60d.
  • a coil spring 63 and an electromagnetic solenoid 64 are provided inside the sleeve 61 with a spool 62 interposed therebetween.
  • the OCV 60 presses the spool 62 in a direction in which the coil spring 63 is compressed against the urging force of the coil spring 63.
  • the spool 62 moves and the port 60a and the port 60c communicate with each other, and the port 60b and the port 60d communicate with each other.
  • the hydraulic circuit 57 of the cam switching unit 5 is formed in the head cover 1A and a relief passage 67 that communicates with the relief hole 52C, and a relief passage 68 that is formed in the head cover 1A and communicates with the relief hole 52D and the relief passage 67, respectively. have.
  • a drain passage 69 is formed in the head cover 1A, and the drain passage 69 communicates with the oil passage 59 and the relief passage 67.
  • the oil passage 58 is provided with a hydraulic pressure adjusting valve 65.
  • the hydraulic pressure adjusting valve 65 has an oil passage 65a inside the housing 65A, and a ball 65B and a coil spring 65C are installed in the oil passage 65a.
  • the coil spring 65C closes the valve seat 65b by urging the ball 65B toward the oil pump 66.
  • the hydraulic adjustment valve 65 separates the ball 65B from the valve seat 65b against the urging force of the coil spring 65C. As a result, oil is supplied from the oil pump 66 to the OCV 60.
  • the oil pressure adjusting valve 65 maintains the oil pressure in the oil passage 58 or the oil passage 59 at a high pressure by the ball 65B closing the valve seat 65b.
  • a hydraulic pressure adjusting valve 70 is provided in the drain passage 69.
  • the hydraulic pressure regulating valve 70 has an oil passage 70a inside the housing 70A, and a ball 70B and a coil spring 70C are installed in the oil passage 70a.
  • the coil spring 70C urges the ball 70B toward the housing 52 (upstream in the oil flow direction) to close the valve seat 70b.
  • the spring force of the coil spring 70C is applied to the valve seat 70b in a state where the pressure of the hydraulic chamber 54 or the hydraulic chamber 55 is equal to or higher than a certain pressure in a state where the hydraulic adjustment valve 65 blocks the communication between the oil pump 66 and the OCV 60. Set to the spring force to open.
  • the cam switching unit 5 of the present embodiment moves the switching pin 51 in the axial direction of the camshaft 3 due to the hydraulic pressure difference supplied from the OCV 60 to the hydraulic chambers 54 and 55 with the hydraulic pressure adjusting valve 70 closed. Can be made.
  • the hydraulic pressure regulating valves 65 and 70 and the OCV 60 of the present embodiment may be formed inside the head cover 1 ⁇ / b> A, or may be provided outside the cylinder head 1.
  • variable valve apparatus 2 the switching operation of the variable valve apparatus 2 according to the present embodiment to the high speed cam 41 and the low speed cam 42 will be described with reference to FIGS. 8 to 13, the direction of arrow R is the rotational direction of the camshaft 3.
  • the switching pin 51 moves to the left in the guide groove 43 and comes into contact with the first switching cam 43A of the guide groove 43, thereby moving the cam carrier 4 to the left and the base circle portion 41A of the high-speed cam 41.
  • the pressed roller 11A of the rocker arm 11 come into contact with each other. Accordingly, the intake valve 13 is driven to open and close by the high speed cam 41 after the start of the engine.
  • the cam carrier 4 includes a groove width changing portion 43E that communicates between the maximum groove width portion 43C and the minimum groove width portion 43D and bulges in the rotation direction of the cam carrier 4, the piston 53 is shown in FIG. In FIG. 8, when moving to the left, the tip 51b of the switching pin 51 comes into contact with the groove width changing portion 43E through the maximum groove width portion 43C of the first switching cam 43A and acts on the cam carrier 4 to the left in the axial direction. Works.
  • the cam carrier 4 moves to the first position when the first switching cam 43A is pressed leftward by the switching pin 51.
  • the base circle portion 42A of the low-speed cam 42 and the base circle portion 41A of the high-speed cam 41 slide smoothly with respect to the pressed roller 11A of the rocker arm 11, and the base circle portion of the high-speed cam 41 moves to the pressed roller 11A. 41A comes into contact.
  • the maximum groove width portion 43C of the cam carrier 4 is centered on the minimum groove width portion 43D, and the switching pin 51 is located on both outer sides (both outer sides in the axial direction of the cam carrier 4). It is formed in a groove width having a space through which the tip 51b can pass.
  • the cam carrier 4 moves to the first position when the tip 51b of the switching pin 51 contacts the groove width changing portion 43E as indicated by L3.
  • the tip 51b of the switching pin 51 reaches the minimum groove width 43D as indicated by L4, the movement of the cam carrier 4 to the first position is completed.
  • the tip 51b of the switching pin 51 comes into contact with the minimum groove width portion 43D from the maximum groove width portion 43C through the groove width changing portion 43E, and the cam carrier. 4 is moved to the first position.
  • the tip 51b of the switching pin 51 is not connected to the guide groove 43 until the switching to the low speed cam 42 is performed. It is installed so as to pass through the minimum groove width portion 43D.
  • the tip 51b of the switching pin 51 does not contact the first switching cam 43A and the second switching cam 43B, so that the position of the high speed cam 41 is maintained and the high speed cam 41 continues to operate.
  • the cam carrier 4 includes a groove width changing portion 43E that communicates between the maximum groove width portion 43C and the minimum groove width portion 43D and bulges in the rotation direction of the cam carrier 4, the piston 53 is moved to the right.
  • the distal end portion 51b of the switching pin 51 comes into contact with the groove width changing portion 43E through the maximum groove width portion 43C of the second switching cam 43B, and a right force in the axial direction acts on the cam carrier 4.
  • the cam carrier 4 moves to the second position through the state shown in FIG. At this time, the base circle portion 41A of the high-speed cam 41 and the base circle portion 42A of the low-speed cam 42 slide smoothly with respect to the pressed roller 11A of the rocker arm 11, and as shown in FIG. The base circle portion 42A of the cam 42 comes into contact.
  • the cam carrier 4 moves to the second position by the tip 51b of the switching pin 51 coming into contact with the groove width changing portion 43E as indicated by R3.
  • the tip 51b of the switching pin 51 reaches the minimum groove width 43D as indicated by R4, the movement of the cam carrier 4 to the second position is completed.
  • the tip 51b of the switching pin 51 comes into contact with the minimum groove width portion 43D from the maximum groove width portion 43C through the groove width changing portion 43E, and the cam carrier. 4 is moved to the second position.
  • the tip 51b of the switching pin 51 remains in the guide groove 43 until the switching to the high speed cam 41 is performed. It is installed so as to pass through the minimum groove width portion 43D. With such an installation, the tip 51b of the switching pin 51 does not contact the first switching cam 43A and the second switching cam 43B, so that the position of the low-speed cam 42 is maintained and the low-speed cam 42 continues to operate.
  • a hydraulic pressure adjusting valve 65 is provided between the OCV 60 and the oil pump 66.
  • the movement start timing of the switching pin 51 is controlled by the hydraulic control of the OCV 60. If it is not the movement start time (indicated by R1) that contacts 43C but the movement start time (indicated by R3) that contacts the groove width changing portion 43E, the tip 51b of the switching pin 51 is in the axial direction of the cam shaft 3. On the other hand, it comes into contact with the groove width changing portion 43E that is steeply inclined. In this state, an excessive load is received from the cam carrier 4 compared to when the tip 51b of the switching pin 51 comes into contact with the maximum groove width portion 43C substantially orthogonal to the axial direction of the cam shaft 3.
  • variable valve operating apparatus 2 of the present embodiment when the tip 51b of the switching pin 51 contacts the groove width changing portion 43E at the movement start timing, the hydraulic chamber 55 instantaneously becomes high pressure, and the oil in the hydraulic chamber 55 opens to the opening 53b. To the relief passage 68 through the relief hole 52D. Accordingly, the switching pin 51 can be protected by absorbing an excessive load received from the cam carrier 4 due to a decrease in the hydraulic pressure in the hydraulic chamber 55.
  • the opening 53b is closed by the piston 53, and the communication between the opening 53b and the relief hole 52D is blocked. Thereby, the hydraulic pressure of the hydraulic chamber 55 can be maintained at a high pressure.
  • variable valve operating apparatus 2 of the present embodiment is provided with the hydraulic pressure regulating valve 70 in the drain passage 69, the oil discharged to any of the oil passages 58 and 59 and the relief passages 67 and 68 is The oil is discharged to the drain passage 69 through the hydraulic adjustment valve 70.
  • the hydraulic pressure adjusting valve 70 opens to drain oil when the hydraulic pressure in the hydraulic circuit 57 rises above a predetermined hydraulic pressure, and closes the hydraulic circuit 57 when the hydraulic pressure in the hydraulic circuit 57 is less than the predetermined hydraulic pressure. Maintain high pressure. For this reason, in the state which the switching pin 51 operates normally and switches the cam carrier 4 between the first position and the second position, the work amount of the oil pump 66 can be reduced. As a result, the fuel efficiency of the engine can be improved and the oil pump 66 can be downsized.
  • the cam switching unit 5 is formed on the outer peripheral surface of the cam carrier 4, and the width of the cam shaft 3 changes in the axial direction of the cam shaft 3.
  • a switching pin 51 having a guide groove 43 having a first switching cam 43A and a second switching cam 43B facing each other and a tip 51b inserted into the guide groove 43 and movable in the axial direction of the cam shaft 3. It is comprised including.
  • the cam switching portion 5 extends along the axial direction of the cam shaft 3 and is mounted on the head cover 1A, and is provided inside the housing 52, and holds the base portion 51a of the switching pin 51.
  • the switching pin 51 is moved in the axial direction of the camshaft 3 due to a hydraulic pressure difference supplied from the OCV 60 to the hydraulic chambers 54 and 55.
  • the tip 51b of the switching pin 51 presses the first switching cam 43A and the second switching cam 43B in a state where the tip 51b of the switching pin 51 is inserted into the guide groove 43, so that the cam carrier 4 can be moved in the axial direction of the camshaft 3.
  • the cam switching unit 5 causes the switching pin 51 to move in the axial direction of the camshaft 3 due to the hydraulic pressure difference supplied from the OCV 60 to the hydraulic chambers 54 and 55 of the housing 52. Move.
  • the cam carrier 4 can be moved in the axial direction of the cam shaft 3 using hydraulic pressure, and the configuration of the cam switching portion 5 for moving the cam carrier 4 in the axial direction of the cam shaft 3 can be simplified.
  • the housing 52 extends along the axial direction of the camshaft 3, it is possible to prevent the height of the cylinder head 1 from being increased, and consequently to prevent the engine from being increased in height.
  • the piston 53 has the opening 53 a that communicates with the hydraulic chamber 54 and the opening 53 b that communicates with the hydraulic chamber 55, and the housing 52 is in the axial direction of the cam shaft 3. Extending along the axial direction of the camshaft 3 and the relief hole 52C having a longer diameter than the opening 53a, and having a relief hole 52D having a longer diameter than the opening 53b. When moving in the axial direction, the opening 53a and the relief hole 52C are communicated, and the opening 53b and the relief hole 52C are communicated.
  • the cam carrier 4 is movable between a first position where the intake valve 13 is operated by the high speed cam 41 and a second position where the intake valve 13 is operated by the low speed cam 42.
  • the cam carrier 4 is moved to the first position by the switching cam 43A, and the cam carrier 4 is moved to the second position by the second switching cam 43B.
  • the hydraulic chamber 55 The hydraulic pressure is relieved from the opening 53b through the relief hole 52D, and the hydraulic pressure in the hydraulic chamber 55 can be lowered. As a result, the impact received by the switching pin 51 from the cam carrier 4 can be reduced, and the switching pin 51 can be protected.
  • the present invention is not limited to this.
  • the present invention is applied to the two-stage variable valve operating device including the high speed cam 41 and the low speed cam 42.
  • the cam carrier 4A shown in FIG. If the pausing cam 48 has a peripheral surface, a valve pausing function can be realized. With such a configuration, the structure of the cam switching unit 5 can be simplified, and the intake valve 13 can be stopped.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
PCT/JP2015/061816 2014-04-23 2015-04-17 内燃機関の可変動弁装置 WO2015163252A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580001943.9A CN105579675B (zh) 2014-04-23 2015-04-17 内燃机的可变气门装置
DE112015001969.3T DE112015001969B4 (de) 2014-04-23 2015-04-17 Variable Ventiltriebvorrichtung für Verbrennungsmotoren

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JP2014088922A JP2015206341A (ja) 2014-04-23 2014-04-23 内燃機関の可変動弁装置
JP2014-088922 2014-04-23

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JP2019011705A (ja) * 2017-06-30 2019-01-24 本田技研工業株式会社 可変動弁装置
JP2019011706A (ja) * 2017-06-30 2019-01-24 本田技研工業株式会社 内燃機関
EP3434871A1 (de) * 2017-07-25 2019-01-30 MAN Truck & Bus AG Schiebenockensystem
US20190301317A1 (en) * 2018-03-29 2019-10-03 Honda Motor Co., Ltd. Oil passage structure for engine
DE102022209711A1 (de) 2022-09-15 2024-03-21 Mahle International Gmbh Baugruppe zum Betätigen von Ventilen einer Brennkraftmaschine

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JP2019011705A (ja) * 2017-06-30 2019-01-24 本田技研工業株式会社 可変動弁装置
JP2019011706A (ja) * 2017-06-30 2019-01-24 本田技研工業株式会社 内燃機関
CN109296419B (zh) * 2017-07-25 2022-03-11 曼卡车和巴士股份公司 滑动凸轮系统
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DE102022209711A1 (de) 2022-09-15 2024-03-21 Mahle International Gmbh Baugruppe zum Betätigen von Ventilen einer Brennkraftmaschine

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DE112015001969B4 (de) 2023-12-07
JP2015206341A (ja) 2015-11-19
CN105579675A (zh) 2016-05-11
CN105579675B (zh) 2018-04-13

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