CN102061957A - Variable valve operating system for internal combustion engine - Google Patents
Variable valve operating system for internal combustion engine Download PDFInfo
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- CN102061957A CN102061957A CN2010105556311A CN201010555631A CN102061957A CN 102061957 A CN102061957 A CN 102061957A CN 2010105556311 A CN2010105556311 A CN 2010105556311A CN 201010555631 A CN201010555631 A CN 201010555631A CN 102061957 A CN102061957 A CN 102061957A
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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
- F01L13/0021—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 by modification of rocker arm ratio
- F01L13/0026—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 by modification of rocker arm ratio by means of an eccentric
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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
- F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A variable valve operating system includes a position changing mechanism, which is configured by a circular eccentric portion provided for a control shaft of a engine valve in a manner decentered from an axis of the control shaft, an external gear formed on a cam follower swingably supported on the eccentric shaft portion, and an internal gear formed on a rocking cam so as to be engaged with the external gear. The control shaft is rotated when opening/closing characteristics of the engine valve are changed, the external gear is revolved by the eccentric shaft portion around the axis of the control shaft, an engaged portion of the internal gear with the external gear is moved in a circumferential direction of the internal gear by the revolution of the external gear, and the position of the rocking cam with respect to the cam follower is changed by the movement of the engaged portion of the internal gear.
Description
Technical field
The present invention relates to a kind of variable valve-operating system that is used for internal-combustion engine, particularly a kind of variable valve-operating system that is used for internal-combustion engine that changes the lifting characteristic of engine valve continuously.
Background technique
In routine techniques,, provide a kind of vehicle internal combustion engine that comprises variable valve-operating system for the operating condition according to internal-combustion engine changes the lifting capacity and the operation angle of engine valve continuously.This variable valve-operating system is the swinging in the cross rest cam unsteadily, this swing cam promotes the engine valve on the Control Shaft, to be connected to rocking cam by the rotating cam swing of camshaft and the cam follower of swing swing cam by evolution mechanism, and change rocking cam changes engine valve with respect to the relative position relation of cam follower lifting characteristic by evolution mechanism.
For example, according to the vario valve operating device and the intake-air quantity control apparatus that are used for internal-combustion engine of patent document 1 (Japan Patent No.3799944), the input part of middle driving mechanism and the relative phase difference of output are changed.That is to say, be used for from cam to the rocking arm of the Control Shaft input that is different from camshaft and the joint of phase difference by spiral helicine spline that is used to output between the swing cam of roller rocking arm (roller rocker arm) change.At this moment, Control Shaft moves axially the change that realizes and obtained the joint of spiral helicine spline.
Yet, in the structure such as above-mentioned patent document 1 disclosed routine, the vario valve operating device that is used for internal-combustion engine proposes a problem to be solved, promptly, phase place is by the control that moves axially of Control Shaft, thereby the error that the valve between the cylinder promotes is along with the temperature difference increase of internal-combustion engine.This is that Control Shaft is fabricated from iron because cylinder head is made of aluminum, and cylinder head and Control Shaft all are the assembly or the parts of vario valve operating device, thereby because the length that temperature variation causes changes between cylinder head and Control Shaft different.
Say further, make difficulty of spiral helicine spline, cause that cost increases, thus inconvenient and bad.
In addition, in the variable valve-operating system of above-mentioned structure, although the valve lifting capacity is variable valuably, the cam timing that is used for operate engine valves is fixed, and this may cause the unfavorable of aspect of performance.
Summary of the invention
The present invention considers that just above-mentioned situation makes, one object of the present invention is to provide a kind of variable valve-operating system that is used for internal-combustion engine, can eliminate the variation of the lifting characteristic of each engine valve that causes owing to the thermal expansion difference between construction package or the parts, and improve the manufacturability of internal-combustion engine.
Above-mentioned and other purposes can obtain according to the present invention, one preferred aspect, the invention provides a kind of variable valve-operating system that is used for internal-combustion engine, comprise the camshaft of engine valve and operate engine valves, this variable valve-operating system comprises:
Swing cam, described swing cam promotes engine valve, and this swing cam is supported to Control Shaft waving;
Cam follower, described cam follower is swung this swing cam; With
Evolution mechanism, this evolution mechanism makes cam follower connect with swing cam, this evolution mechanism structure is used for changing the relative position relation of swing cam with respect to cam follower, thereby changes the lifting characteristic of engine valve,
This evolution mechanism comprises: the eccentric shaft portion of tubular, and this eccentric shaft portion is formed into Control Shaft in the mode from the eccentric axis of Control Shaft; External gear, this external gear are formed on the cam follower that can unsteadily be supported on the eccentric shaft portion, and this eccentric shaft portion is as rotatingshaft; And internal gear, this internal gear is formed on the swing cam, and Control Shaft is as rotatingshaft, so that engage with external gear,
Wherein, when the opening/closing characteristic changing of engine valve, Control Shaft is rotated, external gear is by the axis rotation of eccentric shaft portion around Control Shaft, the rotation of the anastomosis part of internal gear and external gear by external gear moved along the circumferencial direction of internal gear, and swing cam is changed with respect to the position of cam follower the mobile of anastomosis part by internal gear.
In the preferred embodiment aspect above-mentioned of the present invention, what want is when Control Shaft rotates, cam follower moves, thereby move with the point of contact of the cam that rotates periphery along the cam that rotates, and the mobile change that causes the lifting capacity of engine valve of swing cam, and when Control Shaft when the direction of the lifting capacity that reduces described engine valve is rotated, the point of contact between the cam of cam follower and rotation moves along the direction with the direction of rotation of the cam of this rotation.
What also want is, swing cam comprises base circle portion and cam portion, this base circle portion prevents that described engine valve is raised, this cam portion is radially outstanding from base circle portion, hollow space was formed on the interior week of base circle portion, internal gear is formed on the interior perimeter surface of hollow space, and external gear and eccentric shaft portion are arranged in the hollow space.
According to the present invention of above-mentioned feature, can eliminate effectively because the variation of the lifting characteristic of each engine valve that the thermal expansion difference between construction package or the parts causes, and improve the manufacturability of internal-combustion engine, from but effective and useful.
Performance of the present invention and further feature will become clearer by the following description that the reference accompanying drawing is made.
Description of drawings
In the accompanying drawings:
Fig. 1 is the stereogram that is used for the variable valve-operating system of internal-combustion engine according to an embodiment of the invention;
Fig. 2 is the exploded view according to the variable valve-operating system that is used for internal-combustion engine of present embodiment;
Fig. 3 is the sectional view along the line III-III of Fig. 1 according to the variable valve-operating system that is used for internal-combustion engine of present embodiment;
Fig. 4 illustrates the operation of engine valve, and comprises: Fig. 4 A is illustrated in little lifting and the not operation of the engine valve under the operational condition, and Fig. 4 B is illustrated in the engine valve operation under little lifting and the operational condition;
Fig. 5 illustrates the operation of engine valve, and comprises: Fig. 5 A is illustrated in big lifting and the not operation of the engine valve under the operational condition, and Fig. 5 B is illustrated in the engine valve operation under big lifting and the operational condition; With
Fig. 6 is the chart of representing the lifting capacity of engine valve according to an embodiment of the invention and opening/close the relation between the timing.
Embodiment
The variable valve-operating system that is used for internal-combustion engine according to preferred embodiment of the present invention is described hereinafter with reference to the accompanying drawings, to reach the purpose of mentioning hereinbefore.
Say further, it should be noted that, in describing hereinafter, with reference to illustrated embodiment, the crank of internal-combustion engine 1 (bent axle) axially (Fig. 3) is called as " front and back (vertically) direction ", and cylinder axis is to being called as " vertical direction ", and perpendicular to crankshaft to cylinder axis to direction be called as " horizontal direction ", in addition, should be noted that term " on ", D score, " right side ", " left side " and similar terms be here with reference to illustrated embodiment and use under the actual arrangement state of internal-combustion engine.
Referring to figs. 1 through 3, internal-combustion engine 1 comprises engine valve 2, and this engine valve 2 has and is used to open and close the suction port that is communicated with the firing chamber of cylinder head and the suction valve and the outlet valve of relief opening.As shown in Figure 3, in plan view, engine valve 2 has axis C, and axis C tilts at a predetermined angle and is supported on the cylinder head, so that move vertically.
One side (front side) engine valve 2A comprises that a side (front side) valve gap 3A and this side valve bar 4A, a side (front side) valve gap 3A have end portion and connecting end opening removably, and this side valve bar 4A has the end side that is connected to side valve lid 3A continuously.Opposite side (rear side) engine valve 2B comprises opposite side (rear side) valve gap 3B and opposite side valve rod 4B, opposite side (rear side) valve gap 3B has the end portion that is detachably connected to end opening, and opposite side valve rod 4B has the end side that is connected to opposite side valve gap 3B continuously.
Say that further side valve lid 3A and opposite side valve gap 3B constitute valve gap 3, one side valve bar 4A and opposite side valve rod 4B constitutes valve rod 4.
Internal-combustion engine 1 further comprise roller refer to driven member (roller finger follower RFF: rocking arm) 5, this roller refer to driven member 5 according to its axially (up/down) move and open and close engine valve 2.
Roller refers to that driven member 5 comprises that a side roller corresponding to a side engine valve 2A refers to driven member 5A and refers to driven member 5B corresponding to the opposite side roller of opposite side engine valve 2B.
One side roller refers to that driven member 5A comprises: be arranged to a 6A of side arm portion of an along continuous straight runs and a left side/right orientation, be supported on a side roll shaft 7A of the central part of a 6A of side arm portion; Be installed to a side roll shaft 7A so that a rotating side roller 8A; Be formed on a side valve adjacent portion 9A of the left part of a 6A of side arm portion; Be formed on a side regulator supporting portion 10A of the right end portion of a 6A of side arm portion.This side regulator supporting portion 10A is supported on the side hydraulic shock conditioner section 11A.
In a similar manner, the opposite side roller refers to that driven member 5B comprises: be arranged to the opposite side arm 6B of an along continuous straight runs and a left side/right orientation, be supported on the opposite side roll shaft 7B of the central part of opposite side arm 6B; Be installed to opposite side roll shaft 7B so that rotating opposite side roller 8B; Be formed on another side valve adjacent portion 9B of the left part of opposite side arm 6B; Be formed on the opposite side regulator supporting portion 10B of the right end portion of opposite side arm 6B.This opposite side regulator supporting portion 10B is supported on the opposite side hydraulic shock conditioner section 11B.
In this illustrated structure, a 6A of side arm portion and opposite side arm 6B constitute arm 6.One side roll shaft 7A and opposite side roll shaft 7B constitute roll shaft 7.One side roller 8A and opposite side roller 8B constitute roller 8.One side regulator supporting portion 10A and opposite side regulator supporting portion 10B constitute regulator and support 10.One side hydraulic shock conditioner section 11A and opposite side hydraulic shock conditioner section 11B constitute hydraulic shock regulator 11.
Camshaft 12 is arranged to along fore-and-aft direction and is supported on the cylinder head of internal-combustion engine 1, and can rotate synchronously with the bent axle of internal-combustion engine 1, thereby drives engine valve 2.
Rotating cam 13 integrally is installed on the camshaft 12, and rotating cam 13 comprises base circle portion 14 and from the radially outstanding cam portion 15 of base circle portion 14.
Internal-combustion engine 1 further comprises the variable valve-operating system 16 of the lifting characteristic that changes engine valve 2.
Shown in Fig. 1 to 3, variable valve-operating system 16 comprises the Control Shaft 17 parallel with camshaft 12 that longitudinally is arranged between engine valve 2 and the camshaft 12.Control Shaft 17 drives and control by the actuator 18 that comprises motor.Actuator 18 drives and control by control unit 19.
Shown in Fig. 2 and 3, Control Shaft 17 comprises: a side shaft part 20 that has predetermined diameter at its fore-end; Part has the opposite side shaft portion 21 of the diameter identical with the diameter of a side shaft part 20 in its back-end; And be arranged in the eccentric shaft portion 22 of the tubular between a side shaft part 20 and the opposite side shaft portion 21, the diameter of the eccentric shaft portion 22 of tubular is bigger than the diameter of a side shaft part 20 and opposite side shaft portion 21, and its axle center is from a side shaft part 20 and opposite side shaft portion 21 eccentric predetermined offsets (moving distance) " e ".The eccentric shaft portion 22 of one side shaft part 20, opposite side shaft portion 21 and tubular connects as one.
More particularly, the axle center O2 of eccentric shaft portion 22 is set at the radially eccentric offset " e " from the axle center O1 of a side shaft part 20 and opposite side shaft portion 21 prejudicially, and eccentric shaft portion 22 is rotated prejudicially around the axle center O1 of a side shaft part 20 and opposite side shaft portion 21.
Control Shaft 17 is equipped with swing cam 23 in swingable mode, so that can promote engine valve 2.
One side oscillation cam member 23A comprises a side group circular portion 24A who prevents that a side engine valve 2A is raised; With radially outstanding from a side group circular portion 24A and cause the side cam portion 25A that a side engine valve 2A is raised.
As shown in Figure 2, side hollow space 26A with internal diameter bigger than the diameter of a side shaft part 20 is formed on the interior perimeter surface of a side group circular portion 24A, and a side internal gear piece 27A is formed on the inner circumferential surface of a side hollow space 26A as spur wheel (spur gear).Align coaxially with the center of a side shaft part 20 in the center of one side group circular portion 24A.
In addition, the side supporting part 29A with a side shaft hole 28A axially gives prominence to and is connected to continuously the outer end portion of a side group circular portion 24A, and a side shaft part 20 is passed a side shaft hole 28A.More particularly, one side oscillation cam member 23A comprises a side group circular portion 24A and a side cam portion 25A, one side group circular portion 24A prevents that the lifting of cam portion 15 of the rotating cam 13 of camshaft 12 is transferred to a side roller and refers to driven member 5A, and a side cam portion 25A causes that the lifting of cam portion 15 of the rotating cam 13 of camshaft 12 is transferred to a side roller and refers to driven member 5A.
Should notice further aliging coaxially with a side shaft part 20 of Control Shaft 17 in the center of a side group circular portion 24A.Therefore, when Control Shaft 17 was rotated, Control Shaft 17 can not be pushed or move a side roller and refer to driven member 5A.
Opposite side swing cam member 23B comprises opposite side base circle portion 24B and opposite side cam portion 25B, opposite side base circle portion 24B prevents that opposite side engine valve 2B is raised, and opposite side cam portion 25B is radially outstanding and cause that opposite side engine valve 2B is raised from opposite side base circle portion 24B.
As shown in Figure 2, opposite side hollow space 26B with internal diameter bigger than the diameter of opposite side shaft portion 21 is formed on the interior perimeter surface of opposite side base circle portion 24B, and opposite side internal gear piece 27B is formed on the inner circumferential surface of opposite side hollow space 26B as spur wheel.Align coaxially with the center of opposite side shaft portion 21 in the center of opposite side base circle portion 24B.
In addition, the opposite side supporting part 29B with opposite side axis hole 28B radially gives prominence to and is connected to continuously the outer end portion of opposite side base circle portion 24B to ground, and opposite side shaft portion 21 passes opposite side axis hole 28B.
More particularly, opposite side swing cam member 23B comprises opposite side base circle portion 24B and opposite side cam portion 25B, opposite side base circle portion 24B prevents that the lifting of cam portion 15 of the rotating cam 13 of camshaft 12 is transferred to the opposite side roller and refers to driven member 5B, and opposite side cam portion 25B causes that the lifting of cam portion 15 of the rotating cam 13 of camshaft 12 is transferred to the opposite side roller and refers to driven member 5B.
Should notice further aliging coaxially with the opposite side shaft portion 21 of Control Shaft 17 in the center of opposite side base circle portion 24B.Therefore, when Control Shaft 17 rotated, Control Shaft 17 can not be pushed or mobile opposite side roller refers to driven member 5B.
In said structure, a side group circular portion 24A and opposite side base circle portion 24B constitute the base circle portion 24 of swing cam 23.One side cam portion 25A and opposite side cam portion 25B constitute the cam portion 25 of swing cam 23.One side hollow space 26A and opposite side hollow space 26B constitute the hollow space 26 of swing cam 23.One side internal gear piece 27A and opposite side internal gear piece 27B constitute the internal gear piece 27 of swing cam 23.
Cam follower (rocking arm) 31 is connected to swing cam 23 by evolution mechanism 30.Cam follower 31 is swung by the rotating cam 13 of camshaft 12 and is caused that swing cam 23 is swung.
Shown in Fig. 2 and 3, tubular body 33 comprises a side external gear piece 37A and opposite side external gear piece 37B, one side external gear piece 37A is formed on its fore-end as the spur wheel that engages with the side internal gear piece 27A of a side oscillation cam member 23A, and eccentric shaft portion 22 is as rotatingshaft, opposite side external gear piece 37B is formed on its rear end part, as the spur wheel that engages with the opposite side internal gear piece 27B of opposite side swing cam 23B, and eccentric shaft portion 22 is as rotatingshaft.
One side external gear piece 37A and opposite side external gear piece 37B constitute the external gear 37 of cam follower 31.
Say that further a side external gear piece 37A, opposite side external gear piece 37B and eccentric shaft portion 22 are arranged in the inside of a side hollow space 26A and opposite side hollow space 26B.Thereby the axial length of eccentric shaft portion 22 can be shortened, and can improve the installability of variable valve-operating system 16 on internal-combustion engine 1.
As shown in Figure 3, the axial centre of the axle of a side external gear piece 37A and opposite side external gear piece 37B is alignd coaxially with the oscillation center of cam follower 31.Say that further the axial centre of the axle of a side internal gear piece 27A and opposite side internal gear piece 27B is alignd coaxially with the oscillation center of swing cam 23.Thereby a side internal gear piece 27A and opposite side internal gear piece 27B engage with a side external gear piece 37A and the opposite side external gear piece 37B of skew offset " e ".
In the present embodiment, evolution mechanism 30 is constructed to comprise the cycloid mechanism (cycloidmechanism) of eccentric shaft portion 22, a side internal gear piece 27A, opposite side internal gear piece 27B, a side external gear piece 37A and opposite side external gear piece 37B.Evolution mechanism 30 is by changing a side and opposite side swing cam member 23A and 23B change a side engine valve 2A and opposite side engine valve 2B with respect to the relative position relation of cam follower 31 lifting characteristic.
As shown in Figure 3, the side of a side and opposite side swing cam member 23A and 23B and opposite side internal gear piece 27A and 27B engage with one of the tubular body 33 of cam follower 31 and opposite side external gear piece 37A and 37B respectively on the eccentric direction of eccentric shaft portion 22.Thereby each quantity among the number of teeth of each among a side and opposite side internal gear piece 27A and the 27B and a side and opposite side external gear piece 37A and the 37B is determined by offset " e " respectively.
Say further, should be noted that a side oscillation cam member 23A and opposite side swing cam member 23B attach to the fore-end and the rear end part of the tubular body 33 of cam follower 31 respectively.Therefore, two valve 2A and 2B can be driven by a cam follower 31.
Variable valve-operating system 16 according to present embodiment has such structure, and wherein Control Shaft 17, cam follower 31 and swing cam 23 refer to additionally be arranged between the driven member 5 conventional roller oscillatory valve guidance system at camshaft 12 and roller.
Shown in Figure 4 and 5, the lifting capacity of engine valve 2 (β) is changed for the rotational angle (d) of Control Shaft 17 continuously by the angle of nip (nip angle) that changes between cam follower 31 and the swing cam 23.
Say that further as shown in Figure 3, variable valve-operating system 16 can be replaced to be suitable for various valve guidance systems with tappet analogs such as (tappet) but roller refers to driven member 5 by making swing cam 23 push and mobile roller refers to driven member 5 operate engine valves 2.
Variable valve-operating system 16 following operations.When the opening/closing characteristic of engine valve 2 is changed, thereby Control Shaft 17 rotates by eccentric shaft portion 22 and makes external gear 37 around the rotation of the axial centre of Control Shaft.This spinning movement of external gear 37 causes that internal gear 27 moves on the circumferencial direction of internal gear 27 with respect to the bonding point " G " (seeing Figure 4 and 5) of external gear 37, and swing cam 23 is with respect to mobile being changed by the bonding point " G " of internal gear 27 of the position of cam follower 31.
As mentioned above, evolution mechanism 30 constitutes the cycloid mechanism of the internal gear 27 of the external gear 37 of the eccentric shaft portion 22 that comprises Control Shaft 17, cam follower 31 and swing cam 23, and evolution mechanism 30 operation is so that swing cam 23 is changed with respect to the rotation by Control Shaft 17 of the position of cam follower 31, thereby changes the lifting characteristic of engine valve 2.According to the evolution mechanism 30 of aforesaid structure, the influence of the relatively hot differential expansion between uncontrolled axle 17 of the lifting characteristic of engine valve 2 and the internal-combustion engine 1.
In addition, evolution mechanism 30 constitutes by external gear 37 and the internal gear 27 of comparing the spur wheel that can easily be made with the spiral helicine spline of routine and constituting, thereby simplifies the structure and improved the productivity of variable valve-operating system 16.
Say that further when Control Shaft 17 rotated, cam follower 31 moved, so that it moves with the point of contact of rotating cam 13 periphery along the cam 13 of rotation, and the lifting capacity of engine valve 2 is changed by the mobile of swing cam 23.When Control Shaft 17 by when the direction of the lifting capacity that reduces engine valve 2 is rotated, the point of contact between cam follower 31 and the cam 13 that rotates moves along the direction (towards advance side (advance angle side)) with the direction of rotation of the cam 13 that rotates.Move according to this, along with the lifting capacity of engine valve 2 is lowered, the cam timing of the valve 2 that can kill engine in advance and can reduce pump and decrease.
Next, the lifting operation of variable valve-operating system 16 will be described with reference to Figure 4 and 5.
Shown in Fig. 4 A, in order to reduce lifting capacity when engine valve 2 inoperation, Control Shaft 17 counterclockwise rotates.At this moment, the Control Shaft 17 of rotation is assumed to α 1 with respect to the angle of reference position.More particularly, the rotation of eccentric shaft portion 22 causes that external gear 37 counterclockwise rotates around the axle center O1 of a side lever part 20 and another side lever part 21.Then, the angle of nip between cam follower 31 and the swing cam 23 is reduced to β 1, and the contact position between rotating cam 13 and the cam follower 31 is moved to γ 1 along the advance angle direction.At this moment, though the cam portion of rotating cam 13 15 touch rolls 36 to wave swing cam 23, shown in Fig. 4 B, swing cam 23 and roller refer to that the roller 8 of driven member 5 contacts with each other by base circle portion 24.Therefore engine valve 2 promotes hardly, and lifting capacity is minimized (little lifting situation) (seeing R1 among Fig. 6).
Simultaneously, shown in Fig. 5 A, in order to increase lifting capacity when engine valve 2 inoperation, Control Shaft 17 clockwise directions rotate, and change to angle [alpha] 2 up to the angle with respect to the reference position from angle [alpha] 1.Then, external gear 37 rotates around the axle center O2 clockwise direction of eccentric shaft portion 22.Then, the evolution mechanism 30 of operating as cycloid mechanism causes that cam follower 31 slides (shown in the arrow M among Fig. 5 A) to the right, and the contact position between rotating cam 13 and cam follower 31 changes to γ 2 from γ 1.Thereby the valve timing slows down.Simultaneously, swing cam 23 rotates (opening direction along valve) around the axle center O1 clockwise direction of a side and another side lever part 20 and 21, and the angle of nip between cam follower 31 and swing cam 23 is increased to β 2 from β 1.
At this moment, angle of nip is β 2＞β 1 and shown in Fig. 5 B, and when engine valve 2 operations, swing cam 23 and roller refer to that the contact range by cam portion 25 increases between the driven member 5.Thereby roller refers to that driven member 5 greatly waves around the spherical part at the top of hydraulic shock regulator 11, and engine valve 2 is by greatly operation (being big lifting situation) (seeing R2 among Fig. 6).
Say that further as shown in Figure 6, in the lifting capacity and the relation between the opening/closing timing of engine valve 2, lifting capacity is more little, move along the advance angle direction more at maximum lift position (top of lifting curve).
This is because when the lifting capacity of engine valve 2 reduces, contact position between cam follower 31 and the rotating cam 13 moves along the direction (advance angle direction) with the direction of rotation of rotating cam 13, thereby the opening/closing timing of engine valve 2 is accelerated.Correspondingly, when engine valve 2 was in little lifting situation, engine valve 2 can be controlled as and promptly being closed, thereby, reduce pump and decrease, and improve fuel consumption efficiency.
In addition, be different from conventional system, because do not need the axial control of Control Shaft, even under little lifting situation, also can obtain stabilized accuracy or performance, and not because temperature variation is subjected to constituting the influence of the material thermal expansion coefficient of the parts of motor or assembly.
In the present embodiment, evolution mechanism 30 provides following advantage as the use of cycloid mechanism.
According to the minimizing principle of cycloid mechanism, drift angle (deflection angle) α＞drift angle β.More particularly,, obtain formula (α 2-α 1)＞(β 2-β 1), thereby can obtain big retarding according to the rotation of Control Shaft 17 and the rotation of swing cam 23, simultaneously,, insensitive in 17 pairs of change in torque of Control Shaft of acceleration side according to torque transfer.In other words, this causes being used for the improvement of reliability of the actuator 18 of drive controlling axle 17.
In addition, the internal gear 27 of swing cam 23 and the external gear 37 of cam follower 31 are the relations between a kind of external gear and the internal gear, can guarantee big contact gear ratio (flank of tooth contact gear ratio) and can reduce slip ratio, thereby advantageously improve the reliability of the flank of tooth.
Further again, because the offset " e " of the rotatingshaft of internal gear 27 and external gear 37 is generally very little, even when rotating cam 13 is operated, two gears all have very little slippage, thereby advantageously improve the reliability of the flank of tooth.
Further, please note that the present invention is not limited to described embodiment, can under the situation of the scope that does not deviate from the claim of enclosing, carry out many other changes and improvements.
For example, in described embodiment, although two external gears attach to a cam follower and two valves are driven by a cam portion, the present invention can be configured to be provided with two cam portions and two cam followers.
In addition, in described embodiment, although use roller to refer to that the valve guidance system of driven member (RFF) is used as example, the present invention can be applied to use the direct-acting valve guidance system (direct acting valve train system) of tappet or the like.
Can be used to the internal-combustion engine of various vehicles according to variable valve-operating system of the present invention.
Claims (3)
1. variable valve-operating system that is used for internal-combustion engine, described valve-operating system comprise the camshaft of engine valve and the described engine valve of operation, and described variable valve-operating system comprises:
Swing cam, described swing cam promotes described engine valve, and described swing cam can unsteadily be supported on the Control Shaft;
Cam follower, described cam follower is swung described swing cam; With
Evolution mechanism, described evolution mechanism makes described cam follower connect with described swing cam, described evolution mechanism structure is used for changing the relative position relation of described swing cam with respect to described cam follower, to change the lifting characteristic of described engine valve
Described evolution mechanism comprises: the eccentric shaft portion of tubular, and described eccentric shaft portion is formed into described Control Shaft in the mode from the eccentric axis of described Control Shaft; Be divided into the external gear of rotatingshaft with described eccentric axial portion, described external gear is formed on the described cam follower that can unsteadily be supported on the described eccentric shaft portion; Be the internal gear of rotatingshaft with described Control Shaft, described internal gear is formed on the described swing cam so that engage with described external gear,
Wherein, when the opening/closing characteristic changing of described engine valve, described Control Shaft is rotated, described external gear is by the axis rotation of described eccentric shaft portion around described Control Shaft, the rotation of the anastomosis part of described internal gear and described external gear by described external gear moved along the circumferencial direction of described internal gear, and described swing cam is changed with respect to the position of described cam follower the mobile of described anastomosis part by described internal gear.
2. the variable valve-operating system that is used for internal-combustion engine as claimed in claim 1, it is characterized in that, when Control Shaft is rotated, described cam follower moves, make and to move with the point of contact of the cam of described rotation periphery along the cam that rotates, and the mobile change that causes the lifting capacity of described engine valve of described swing cam, and when described Control Shaft when the direction of the lifting capacity that reduces described engine valve is rotated, the point of contact between the cam of described cam follower and described rotation moves along the direction with the direction of rotation of the cam of described rotation.
3. the variable valve-operating system that is used for internal-combustion engine as claimed in claim 1, it is characterized in that, described swing cam comprises base circle portion and cam portion, described base circle portion prevents that described engine valve is raised, described cam portion is radially outstanding from described base circle portion, hollow space was formed on the interior week of described base circle portion, and described internal gear is formed on the interior perimeter surface of described hollow space, and described external gear and described eccentric shaft portion are arranged in the described hollow space.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009-258991 | 2009-11-12 | ||
| JP2009258991A JP5294156B2 (en) | 2009-11-12 | 2009-11-12 | Variable valve operating device for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102061957A true CN102061957A (en) | 2011-05-18 |
| CN102061957B CN102061957B (en) | 2013-05-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010105556311A Expired - Fee Related CN102061957B (en) | 2009-11-12 | 2010-11-12 | Variable valve operating system for internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20110107989A1 (en) |
| EP (1) | EP2322771B1 (en) |
| JP (1) | JP5294156B2 (en) |
| CN (1) | CN102061957B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011014744B4 (en) * | 2011-03-22 | 2015-04-30 | Kolbenschmidt Pierburg Innovations Gmbh | Mechanically controllable valve drive and mechanically controllable valve train arrangement |
| JP5862161B2 (en) | 2011-09-27 | 2016-02-16 | スズキ株式会社 | Internal combustion engine |
| CN103016091B (en) * | 2012-12-31 | 2015-02-04 | 长城汽车股份有限公司 | Adjusting device of variable valve lift mechanism and variable valve lift mechanism |
| US9133735B2 (en) | 2013-03-15 | 2015-09-15 | Kohler Co. | Variable valve timing apparatus and internal combustion engine incorporating the same |
| JP2016035252A (en) * | 2014-08-04 | 2016-03-17 | トヨタ自動車株式会社 | Internal combustion engine valve gear device |
| KR101637296B1 (en) | 2014-12-09 | 2016-07-07 | 현대자동차 주식회사 | Continuous varible vavle duration apparatus and engine provided with the same |
| KR101628102B1 (en) | 2014-12-09 | 2016-06-08 | 현대자동차 주식회사 | Continuous varible vavle duration apparatus and engine provided with the same |
| KR101619389B1 (en) | 2014-12-10 | 2016-05-18 | 현대자동차 주식회사 | Continuous varible vavle duration apparatus and engine provided with the same |
| KR101655170B1 (en) | 2015-06-19 | 2016-09-07 | 현대자동차 주식회사 | Continuous variable vavle duration apparatus and engine provided with the same |
| KR101786708B1 (en) | 2016-03-31 | 2017-10-18 | 현대자동차 주식회사 | Continuous variable vavle duration apparatus and engine provided with the same |
| KR101755512B1 (en) | 2016-03-31 | 2017-07-07 | 현대자동차 주식회사 | Continuous variable vavle duration apparatus and engine provided with the same |
| KR101734235B1 (en) | 2016-03-31 | 2017-05-11 | 현대자동차 주식회사 | Continuous variable vavle timing apparatus and engine provided with the same |
| US10138764B2 (en) | 2016-03-31 | 2018-11-27 | Hyundai Motor Company | Continuous variable valve duration apparatus and engine provided with the continuous variable valve duration apparatus |
| KR102371229B1 (en) | 2016-12-14 | 2022-03-04 | 현대자동차 주식회사 | Continuous variable vavle timing apparatus and engine provided with the same |
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2009
- 2009-11-12 JP JP2009258991A patent/JP5294156B2/en active Active
-
2010
- 2010-11-08 US US12/941,618 patent/US20110107989A1/en not_active Abandoned
- 2010-11-10 EP EP10190636A patent/EP2322771B1/en not_active Not-in-force
- 2010-11-12 CN CN2010105556311A patent/CN102061957B/en not_active Expired - Fee Related
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| JP2001263015A (en) * | 2000-03-21 | 2001-09-26 | Toyota Motor Corp | Variable valve system for internl combustion engine and intake amount control device |
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| EP1619362A2 (en) * | 2004-07-20 | 2006-01-25 | Bayerische Motoren Werke Aktiengesellschaft | Valve train for an internal combustion engine |
| JP2007071174A (en) * | 2005-09-09 | 2007-03-22 | Toyota Motor Corp | Control device for internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102061957B (en) | 2013-05-08 |
| US20110107989A1 (en) | 2011-05-12 |
| EP2322771B1 (en) | 2012-06-27 |
| JP5294156B2 (en) | 2013-09-18 |
| EP2322771A1 (en) | 2011-05-18 |
| JP2011106279A (en) | 2011-06-02 |
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