WO2011065326A1 - 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
WO2011065326A1
WO2011065326A1 PCT/JP2010/070799 JP2010070799W WO2011065326A1 WO 2011065326 A1 WO2011065326 A1 WO 2011065326A1 JP 2010070799 W JP2010070799 W JP 2010070799W WO 2011065326 A1 WO2011065326 A1 WO 2011065326A1
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WO
WIPO (PCT)
Prior art keywords
cam
shaft
phase
internal combustion
combustion engine
Prior art date
Application number
PCT/JP2010/070799
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大輔 吉賀
村田　真一
Original Assignee
三菱自動車工業株式会社
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
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Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=44066431&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2011065326(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by 三菱自動車工業株式会社 filed Critical 三菱自動車工業株式会社
Priority to EP10833172.9A priority Critical patent/EP2505795B1/de
Priority to IN1666DEN2012 priority patent/IN2012DN01666A/en
Priority to KR1020127005150A priority patent/KR101169900B1/ko
Priority to RU2012107178/06A priority patent/RU2493376C1/ru
Priority to BR112012004601A priority patent/BR112012004601A2/pt
Priority to US13/392,460 priority patent/US20120145101A1/en
Priority to CN2010800386806A priority patent/CN103038458A/zh
Publication of WO2011065326A1 publication Critical patent/WO2011065326A1/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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • the present invention relates to a variable valve operating apparatus for an internal combustion engine in which the phase of one cam of a pair of cams driving a pair of intake valves or a pair of exhaust valves is changed with respect to the other cam by a cam phase changing mechanism.
  • variable valve gear In a reciprocating engine (internal combustion engine) mounted on an automobile, a variable valve gear is being mounted on a cylinder head in order to prevent engine exhaust gas and improve pumping loss.
  • the variable valve operating system has a structure in which a phase between the valves of a multi-valve (a pair of intake valves and a pair of exhaust valves) widely used in an engine is varied to change a period during which the multi-valve is open. .
  • a device that varies the phase of the other cam with respect to one cam has been proposed.
  • variable valve operating device is difficult to realize with a camshaft in which a cam is integrally formed with a normal shaft member.
  • the variable valve device uses a camshaft having an assembly cam structure in which a separate cam member (component) is rotatably assembled to the shaft member, thereby realizing a variable phase between the valves.
  • the first cam on the reference side is fixed on the outside of the shaft member driven by the crank output in accordance with the arrangement of the pair of intake valves or the pair of exhaust valves.
  • a second cam having the same cam width on the pair of movable sides is fitted so as to be displaceable in the circumferential direction, and the phase of the second cam is changed with reference to the phase of the first cam by a cam phase changing mechanism such as a movable vane mechanism.
  • a cam phase changing mechanism such as a movable vane mechanism.
  • the cam displacement of the first cam and the second cam is transmitted to each valve via a follower member of a tappet member (or a rocker member or the like), and a pair of intake valves or a pair of exhaust valves
  • the open period of is greatly changed.
  • the first cam and the second cam are substantially at the same valve lift and timing.
  • misalignment does not increase because the valve lift load acts equally on the cam journal width.
  • the valve lift load acts on the time difference between before and after in the cam journal width direction, resulting in misalignment.
  • the cam surfaces of the first cam and the second cam have a reduced contact area with the cam contact portion of the tappet or the rocker, resulting in a high load, and a good lubrication state cannot be maintained. It becomes a factor of wear.
  • the second cam used in the variable valve operating device is rotatable in the circumferential direction of the shaft member, unlike the structure formed integrally with the normal shaft member or the first cam fixed to the shaft member. For this reason, there is a minute clearance necessary to rotate the shaft member. Since this clearance promotes misalignment of the second cam, it causes a further increase in friction with the cam contact portions of the tappet and the rocker and causes uneven wear. In addition, the misalignment causes instability of the clearance, the offset load acting on the sliding surface of the second cam and the shaft member also increases, and the responsiveness is deteriorated due to the increased friction and wear of the part is also generated.
  • variable valve operating apparatus has a problem in that the variable performance varies when this occurs. From this, it is conceivable to employ misalignment processing, improve assembly accuracy, and use wear-resistant materials and surface treatment that can withstand misalignment, but both are expensive and require alternative technologies. .
  • An object of the present invention is to provide a variable valve operating apparatus for an internal combustion engine that has a simple structure and can increase the resistance against misalignment of a movable cam that varies the phase.
  • a variable valve operating apparatus for an internal combustion engine varies a phase between a pair of intake valves provided for one cylinder or a phase between a pair of exhaust valves.
  • a variable valve operating apparatus for an internal combustion engine comprising: a shaft member driven by a crank output of the internal combustion engine; and one of the pair of intake valves or one of the pair of exhaust valves provided outside the shaft member
  • a first cam having a cam surface for driving; a second cam having a cam surface for driving the other of the intake valve or the other of the exhaust valve, which is provided on the outer side of the shaft member so as to be displaceable in the circumferential direction;
  • a cam phase changing mechanism that changes the phase of the second cam with respect to the first cam, and the cam surface of the second cam has a cam width dimension larger than the cam width of the cam surface of the first cam. Characterized in that in consists formed.
  • the shaft member is configured such that an inner cam shaft is rotatably accommodated in an outer cam shaft formed of a pipe member.
  • a cam is provided on an outer peripheral portion of the outer cam shaft, and the second cam is provided so as to be rotatable around an axis of the outer cam shaft, and the relative displacement between the outer cam shaft and the inner cam shaft is provided.
  • the phase of the second cam is variable with respect to the first cam.
  • a variable valve operating apparatus for an internal combustion engine is the variable valve operating apparatus according to the first or second aspect, wherein the first cam is larger than a cam width of a camshaft including a cam integrated with a shaft member applied in the same type of internal combustion engine. It is characterized by being formed with a large cam width.
  • variable valve operating apparatus for an internal combustion engine of claim 1 the contact area with the cam contact portion of the tappet or the rocker due to misalignment of the cam surfaces of the first cam and the second cam is maintained, and a good lubricating state is maintained.
  • the increase in friction and uneven wear of the contact portion is suppressed, and the maximum value of the uneven load acting on the sliding surfaces of the second cam and the shaft member due to misalignment is reduced. Therefore, with a simple structure, it is possible to increase the tolerance against misalignment of the cam that performs phase change.
  • variable valve operating apparatus for an internal combustion engine since the outer cam shaft is formed by a pipe member having low bending rigidity, the outer cam is changed from the second cam using the second cam having a large cam width. The force applied to the shaft can be dispersed.
  • the first cam and the second cam have optimum cam widths, can effectively cope with misalignment associated with variable splitting, and deteriorate responsiveness due to increased friction. And uneven wear can be effectively suppressed.
  • FIG. 1 is a plan view of an internal combustion engine equipped with a variable valve gear according to a first embodiment of the present invention.
  • Sectional drawing of the variable valve apparatus which follows the II line
  • Sectional drawing which shows the cam shaft in which the cam was integrally formed.
  • the disassembled perspective view which shows the structure of each part of a variable valve apparatus.
  • the diagram which shows the variable characteristic of a variable valve apparatus.
  • the top view which shows the principal part of the 2nd Embodiment of this invention.
  • FIG. 1 shows a plan view of an internal combustion engine, for example, a multi-cylinder reciprocating engine (hereinafter simply referred to as an engine), and FIG. 2 shows a cross section taken along line II in FIG.
  • the cylinder block 2 is a cylinder head mounted on the head of the cylinder block 1.
  • the cylinder block 1 is formed with a plurality of cylinders 3 (only some cylinders are shown) along the longitudinal direction of the engine as shown in FIGS.
  • pistons 4 separated from a crankshaft (not shown) via connecting rods (not shown) are housed so as to be able to reciprocate.
  • a combustion chamber 5 is formed on the lower surface of the cylinder head 2 corresponding to each cylinder 3.
  • Each combustion chamber 5 has a pair of intake ports 7 (two) for performing intake and a pair of exhaust ports (not shown) for performing exhaust.
  • Each intake port 7 is provided with a pair of intake valves 10 (two) each having a bottomed cylindrical tappet 9 (driven member) attached to the stem end.
  • a spherical crowning (cam contact surface) formed on the top surface 9 a of each tappet 9 faces the upper portion of the cylinder head 2.
  • Each exhaust port (not shown) is similarly provided with a pair of exhaust valves (both not shown) with tappets.
  • the valve base end faces the upper part of the cylinder head 2.
  • the intake port 7 and the exhaust port (not shown) are opened and closed by the intake valve 10 and the exhaust valve (not shown).
  • each combustion chamber 5 is provided with a spark plug (not shown).
  • an intake side valve operating device 6a driven by a crankshaft shaft output
  • an exhaust side valve operating device 6b 4 cycles of intake stroke, compression stroke, expansion stroke, and exhaust stroke) are repeated.
  • the exhaust-side valve gear 6b has a structure using a normal camshaft 13 shown in FIG. 3, for example. Specifically, a camshaft formed integrally with an exhaust cam, specifically, a camshaft 13 formed by machining the exhaust cams 12 for a plurality of cylinders together with a shaft 13a (shaft member) is used.
  • the camshaft 13 is assembled so as to be rotatable in the direction in which the cylinders 3 are arranged, and the cam surface of each exhaust cam 12 is brought into contact with the crowning (not shown) of the top surface of the tappet. Thus, the cam displacement of each exhaust cam 12 is transmitted to an exhaust valve (not shown).
  • the intake-side valve gear 6a includes a camshaft constituted by assembling separate parts as shown in FIG. It is used.
  • the camshaft 14 is used to form a split type variable valve operating device 15 as shown in FIG.
  • the shaft member of the camshaft 14 is, for example, an inner camshaft 17b formed of a solid shaft member serving as a control member in an outer camshaft 17a formed of a pipe member as shown in FIGS. Is formed by a double shaft 17 (corresponding to the shaft member of the present application).
  • the double shaft 17 is also arranged along the direction in which the cylinders 3 are arranged, like the camshaft 13 on the exhaust side.
  • One end portion (one side) of the double shaft 17, that is, one end portion of the outer cam shaft 17 a is connected to one end of the cylinder head 2 via a bracket 37 attached to the end of the outer cam shaft 17 a. It is rotatably supported by a bearing portion 18a installed at the end (one side).
  • the intermediate portion of the outer cam shaft 17a is rotatably supported by an intermediate bearing portion 18b installed between the tappets 9,9.
  • both shafts 17a and 17b can rotate around the same axis.
  • the outer camshaft 17a and the inner camshaft 17b can be relatively displaced by a clearance.
  • the outer cam shaft 17a is provided with a pair (two) of intake cams 19 corresponding to the pair of intake valves 10 for each cylinder.
  • Each of the intake cams 19 is a combination of a fixed cam 20 (corresponding to the first cam of the present application) that defines a reference phase and a cam lobe 22 (movable cam, corresponding to the second cam of the present application) on the movable side.
  • the fixed cam 20 serving as the reference side is provided on an outer peripheral portion corresponding to a tappet on one side of the outer cam shaft 17a, for example, the tappet 9 on the left side in the drawing.
  • the fixed cam 20 is formed of a plate cam, and is fixed by being fitted to the outside of the outer cam shaft 17a, specifically, fixed by press-fitting.
  • the cam surface 20a formed on the outer peripheral surface of the fixed cam 20 abuts on the crowned top portion 9a of the left tappet 9, and the cam displacement of the fixed cam 20 is transmitted to the left intake valve 10b.
  • the cam lobe 22 has a cam nose 22a formed of a plate cam.
  • a portion for ensuring stability, that is, a hollow boss portion 22b is combined with the cam nose portion 22a to constitute the entire cam lobe.
  • the cam crest portion 22a and the boss portion 22b are fitted on the outer side of the outer cam shaft 17a so as to be freely rotatable (displaceable) in the circumferential direction, and the cam crest portion 22a is disposed immediately above the remaining right tappet 9.
  • a cam surface 22c formed on the outer peripheral surface of the cam peak portion 22a abuts on the crowned top portion 9a of the right tappet 9, and the cam displacement of the cam peak portion 22a is transmitted to the right intake valve 10a.
  • the boss portion 22b and the inner camshaft 17b are connected while allowing relative displacement of the inner and outer shafts 17a and 17b by a connecting member, for example, a press-fit pin 24 that is press-fitted so as to penetrate the diameter direction of the double shaft 17. ing.
  • a connecting member for example, a press-fit pin 24 that is press-fitted so as to penetrate the diameter direction of the double shaft 17.
  • the cam crest 22 a (cam lobe 22) can be displaced relative to the fixed cam 20. That is, as shown in FIG. 4, a hole for allowing the press-fit pin 24 to escape, for example, a pair of long holes 26 extending in the retarding direction, is formed in the peripheral wall portion of the outer cam shaft 17 a through which the press-fit pin 24 passes.
  • the inner cam shaft 17b can be displaced relative to the outer cam shaft 17a.
  • the cam crest portion 22a can be varied from the phase of the reference fixed cam 20 to a phase that is greatly retarded.
  • 14a indicates a press-fitting hole formed in the inner cam shaft 17b
  • 14b indicates a press-fitting hole formed in the peripheral wall portion of the boss portion 22b.
  • a cam phase changing mechanism 25 for relatively displacing the inner and outer shafts 17a and 17b is attached to one end of the double shaft 17 so that the cam phase of the cam lobe 22 can be changed based on the fixed cam 20.
  • the apparatus 15 is comprised.
  • the cam phase changing mechanism 25 includes a plurality of retarding chambers 30 radially extending from the outer peripheral portion of the shaft portion 32 in a cylindrical housing 31 having a circumferential direction.
  • a rotating vane structure is used in which the vane portion 34 from which the vane 33 protrudes is rotatably housed and the interior of each retarded angle chamber 30 is partitioned by each vane 33.
  • a timing sprocket 39 is provided on the outer peripheral portion of the housing 31.
  • the sprocket 39 is connected to a crankshaft (not shown) through a timing chain 40 together with a timing sprocket 13a attached to the end of the camshaft 13 on the exhaust side.
  • the housing 31 is connected to a bracket 37 (shown in FIG. 2) at the end of the outer cam shaft 17a by a fixing bolt 36, and the shaft portion 32 of the remaining vane portion 34 is connected to the shaft end of the inner cam shaft 17b by a fixing bolt 38.
  • the cam phase of the cam peak portion 22a is determined by the urging force of a return spring member 42 (shown only in FIG. 2) provided so as to pass between the housing 31 and the vane portion 34. Aligned to 20 cam phases.
  • Each retard chamber 30 is provided with an oil control valve 44 (hereinafter referred to as OCV 44) through various oil passages 43 (only part of which are shown in FIG. 2) formed in the housing 31, the bracket 37, and the bearing portion 18a.
  • the hydraulic pressure supply unit 45 is connected to a hydraulic pressure supply unit 45 (for example, a device having an oil pump for supplying oil). That is, in the camshaft 14 on the intake side, when oil is supplied into each retarding angle chamber 30, splitting is performed such that the cam peak portion 22a is displaced from the fixed cam 20 in the retarding direction.
  • the shaft output from the crankshaft is transmitted to the outer shaft 17 a via the timing chain 40, the timing sprocket 39, the housing 31, and the bracket 37, and the fixed cam 20 is driven to rotate, and the left side via the tappet 9.
  • the intake valve 10b is opened and closed.
  • the cam crest portion 22 a is coupled with the urging force of the return spring member 42 as shown in FIG. Since the cam phase of the fixed cam 20 is aligned as in the state A, the right intake valve 10a is opened and closed while maintaining the same phase as that of the left fixed cam 20.
  • the vane 33 When the hydraulic pressure of the hydraulic pressure supply unit 45 is supplied into the retard chamber 30 through the OCV 44, the vane 33 is displaced from the initial position to the retard side in the retard chamber 30 according to the hydraulic pressure output. At this time, for example, when the vane 33 is displaced halfway in the retard chamber 30 by hydraulic pressure output control, the inner cam shaft 17b is displaced in the retard direction to the midway position. The displacement at this time is transmitted to the cam lobe 22 through the press-fit pin 24, and the cam peak portion 22a is displaced in the retarding direction. Then, as shown in the state B in FIG. 5, the open / close timing of the left intake valve 10b as a reference remains unchanged, and only the open / close timing of the right intake valve 10a changes.
  • the right intake valve 10a is opened / closed according to the cam profile of the cam peak portion 22a from the middle of the opening / closing period of the left intake valve 10b.
  • the opening and closing timing of the left intake valve 10b remains unchanged as shown in the state C in FIG. 5, and the right intake valve 10a is left unchanged. Opens and closes at the most retarded time from the left intake valve 10b while maintaining a state in which the left intake valve 10b opens and closes. That is, the valve opening periods of the left and right intake valves 10 are varied within the range from the smallest valve opening period ⁇ to the largest valve opening period ⁇ (split variable) according to the state of the engine.
  • the variable valve operating device 15 that causes the cam lobe 22 to be phased with respect to the fixed cam 20 has a problem peculiar to the device 15 because the cam lobe 22 is rotatable. That is, unlike the fixed cam 20, the cam lobe 22 assembled to the double shaft 17 is required to be able to rotate the outer peripheral surface of the outer cam shaft 17a. Therefore, the cam lobe 22 is provided between the cam lobe 22 and the outer cam shaft 17a. There is a small clearance necessary to rotate. Moreover, since the clearance includes the component tolerance of the cam lobe 22 and the outer cam shaft 17a and the assembly tolerance when assembling both components, the cam crest 22a is easily displaced over a wide range, and the posture of the cam surface 22c is likely to vary ( Not constant). That is, as shown in FIG. 6A, the cam surface 22c is likely to be misaligned with respect to the center of the cam shaft.
  • the valve lift load works with a time lag, resulting in misalignment. That is, in a general cam shaft in which the cam is integrally fixed to the shaft, when the cam journal is provided between the first cam at the fixed cam position and the second cam at the cam lobe position, the first cam and the second cam Misalignment does not increase because the cams have substantially the same valve lift and timing and the valve lift load acts equally on the cam journal width.
  • the valve lift load acts on the cam journal 18b in the width direction, so that the valve lift load is large. Misalignment occurs.
  • the cam surface of the cam crest 22a that changes the phase as shown in FIGS. 1, 2, and 4 is not the idea that the cam width of the fixed cam 20 and the cam crest 22a that are paired is the same.
  • the cam width dimension of 22c was made larger than the cam width dimension b of the cam surface 20a of the fixed cam 20 to make the cam width dimension different. That is, the cam surface 22c of the cam nose 22a is formed with a larger cam width than the cam surface 20a of the fixed cam 20 (a> b). Then, as shown in FIG. 6B, even if misalignment occurs, contact between the crowned top surface 9a of the cam contact surface of the tappet 9 and the cam width end portion of the cam peak portion 22a can be avoided. .
  • the tolerance to misalignment of the cam that changes the phase is enhanced. Therefore, the camshaft 14 can be assembled to the cylinder head 2 in the same manner as the conventional cam (FIG. 2), and it is possible to suppress troublesome alignment work and improvement of the processing accuracy of each of the previous components (no processing accuracy is required). ). Furthermore, the maximum value of the unbalanced load acting on the sliding surfaces of the cam nose 22a (second cam) and the outer camshaft 17a (shaft member) due to misalignment is reduced, and the response and deterioration due to increased friction are also reduced. Can be suppressed.
  • the inclination of the cam nose 22a can be suppressed by increasing the cam width dimension, so the occurrence of friction and uneven wear due to the instability of the cam nose 22a can be suppressed, and good variable performance can be secured. can do.
  • the valve lift as designed is obtained, there is no performance degradation or NVH deterioration.
  • the outer cam shaft 17a is formed of a pipe member having low bending rigidity, if the cam width of the cam peak portion 22a is increased, the force transmitted from the cam peak portion 22a to the outer cam shaft 17a is dispersed, which is good. Variable performance is maintained.
  • the cam width dimension b of the fixed cam 20 is the cam width dimension of a camshaft that is used in the same type of engine and has a cam integral with a shaft member, for example, the shaft 13a shown in FIG.
  • the cam width dimension of the cam surface is larger (a> c, b> c), and the optimum cam width is set for each of the cam surfaces.
  • it can handle misalignment associated with variable split. Needless to say, such an effect can also be obtained when the crowning of the cam contact surface of the tappet 9 is provided on the cam surface 22c side.
  • FIG. 7 shows a second embodiment of the present invention.
  • a phase change device is provided at one end of a double shaft 17 (shaft member) in which a fixed cam 20 (first cam) and a cam lobe 22 (second cam) are assembled as in the first embodiment.
  • 25 is not a variable valve operating device 15 that varies the phase of the cam lobe 22 with respect to the fixed cam 20, but a variable valve operating device 50 that has a function of integrally changing the phase of the fixed cam 20 and the phase of the cam lobe 22.
  • the present invention is applied.
  • variable valve operating device 50 is attached to one end of the double shaft 17 (shaft member) in which the fixed cam 20 (first cam) and the cam lobe 22 (second cam) are assembled, for example, the end on the rear side of the engine.
  • a phase change mechanism 25 having the same structure as that of the first embodiment is connected, and a second phase change mechanism 51 formed by a rotary vane structure such as VVT is connected to the other engine front side end, and the outer
  • the phases of the fixed cam 20 and the cam lobe 22 are integrally variable based on the integral rotational displacement of the outer camshaft 17a and the inner camshaft 17b. It is made to be done.
  • variable valve operating apparatus 50 Even if the present invention is applied to the variable valve operating apparatus 50, the same effects as those of the first embodiment can be obtained.
  • FIG. 7 the same parts as those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • variable valve operating apparatus for an internal combustion engine according to the present invention
  • the present invention is not limited to the above embodiment.
  • the structure is described in which the valve is driven by receiving the cam displacement with the tappet.
  • the invention may be applied.
  • a configuration is conceivable in which one cam abutting surface is provided on the cam side of the rocker member, a bifurcated valve driving portion is provided on the valve side, and a plurality of valves are driven by one cam.
  • the present invention is not limited to the variable valve operating apparatus that relatively changes the phase of the pair of intake cams as in the above-described embodiment, but is not shown in the drawing, the variable movement that relatively changes the phase of the pair of exhaust cams.
  • You may apply to a valve apparatus.
  • the engine to be applied may be an engine having a valve operating system in which the variable valve operating device is combined with a structure for driving a valve using a camshaft in which a cam is integrally formed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
PCT/JP2010/070799 2009-11-25 2010-11-22 内燃機関の可変動弁装置 WO2011065326A1 (ja)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP10833172.9A EP2505795B1 (de) 2009-11-25 2010-11-22 Variable ventilvorrichtung für einen verbrennungsmotor
IN1666DEN2012 IN2012DN01666A (de) 2009-11-25 2010-11-22
KR1020127005150A KR101169900B1 (ko) 2009-11-25 2010-11-22 내연 기관의 가변 밸브 장치
RU2012107178/06A RU2493376C1 (ru) 2009-11-25 2010-11-22 Устройство регулируемых клапанов для двигателя внутреннего сгорания
BR112012004601A BR112012004601A2 (pt) 2009-11-25 2010-11-22 dispositivo de válvula variável para um motor de combustão interna
US13/392,460 US20120145101A1 (en) 2009-11-25 2010-11-22 Variable valve device for an internal combustion engine
CN2010800386806A CN103038458A (zh) 2009-11-25 2010-11-22 内燃机的可变气门装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-267506 2009-11-25
JP2009267506A JP4883330B2 (ja) 2009-11-25 2009-11-25 内燃機関の可変動弁装置

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WO2011065326A1 true WO2011065326A1 (ja) 2011-06-03

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Country Status (9)

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US (1) US20120145101A1 (de)
EP (1) EP2505795B1 (de)
JP (1) JP4883330B2 (de)
KR (1) KR101169900B1 (de)
CN (1) CN103038458A (de)
BR (1) BR112012004601A2 (de)
IN (1) IN2012DN01666A (de)
RU (1) RU2493376C1 (de)
WO (1) WO2011065326A1 (de)

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EP2920435B1 (de) 2012-11-13 2016-09-14 Mahle International GmbH Nockenwelle

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KR101222229B1 (ko) * 2009-12-07 2013-01-15 미쯔비시 지도샤 고교 가부시끼가이샤 내연 기관의 가변 밸브 장치
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EP2505795A1 (de) 2012-10-03
EP2505795B1 (de) 2014-06-11
KR101169900B1 (ko) 2012-07-31
JP2011111936A (ja) 2011-06-09
JP4883330B2 (ja) 2012-02-22
KR20120039741A (ko) 2012-04-25
IN2012DN01666A (de) 2015-06-05
BR112012004601A2 (pt) 2016-04-05
EP2505795A4 (de) 2013-04-24
US20120145101A1 (en) 2012-06-14
RU2493376C1 (ru) 2013-09-20
CN103038458A (zh) 2013-04-10

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