CN102061957B - Variable valve operating system for internal combustion engine - Google Patents

Variable valve operating system for internal combustion engine Download PDF

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Publication number
CN102061957B
CN102061957B CN2010105556311A CN201010555631A CN102061957B CN 102061957 B CN102061957 B CN 102061957B CN 2010105556311 A CN2010105556311 A CN 2010105556311A CN 201010555631 A CN201010555631 A CN 201010555631A CN 102061957 B CN102061957 B CN 102061957B
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China
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cam
valve
control shaft
external gear
engine valve
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CN102061957A (en
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大泽宏
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Suzuki Motor Corp
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Suzuki Motor Corp
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015Modifications 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
    • F01L13/0021Modifications 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
    • F01L13/0026Modifications 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015Modifications 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
    • F01L13/0063Modifications 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

The variable valve-operating system that is used for internal-combustion engine
Technical field
The present invention relates to a kind of variable valve-operating system for internal-combustion engine, particularly a kind of variable valve-operating system that is used for internal-combustion engine that changes continuously the lifting characteristic of engine valve.
Background technique
In routine techniques, change continuously lifting capacity and the operation angle of engine valve for the operating condition according to internal-combustion engine, a kind of vehicle internal combustion engine that comprises variable valve-operating system is provided.This variable valve-operating system is the swinging in the cross rest cam unsteadily, this swing cam promotes the engine valve on Control Shaft, the cam follower that will be swung and swing swing cam by evolution mechanism by the rotating cam of camshaft be connected to rocking cam, and change rocking cam by evolution mechanism and change the lifting characteristic of engine valve with respect to the relative position relation of cam follower.
For example, according to patent document 1(Japan Patent No.3799944) the vario valve operating device and the intake-air quantity control apparatus that are used for internal-combustion engine, the input part of middle driving mechanism and the relative phase difference of output are changed.That is to say, be used for the rocking arm from cam to the Control Shaft input that is different from camshaft and change for the joint of the phase difference between the swing cam that outputs to roller rocking arm (roller rocker arm) by spiral helicine spline.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, namely, phase place is by the control that moves axially of Control Shaft, thereby the error that the valve between 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 are all assembly or the parts of vario valve operating device, thereby the length that causes due to temperature variation changes between cylinder head and Control Shaft different.
Say further, make spiral helicine spline more difficult, 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 for internal-combustion engine, can eliminate the variation of the lifting characteristic of each engine valve that causes due to the thermal expansion difference between construction package or parts, and improve the manufacturability of internal-combustion engine.
The above and other purpose can obtain according to the present invention, one preferred aspect, the invention provides a kind of variable valve-operating system 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 swings this swing cam; With
Evolution mechanism, this evolution mechanism make cam follower connect with swing cam, and this evolution mechanism construction is used for changing swing cam with respect to the relative position relation of 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 eccentric shaft portion, and this eccentric shaft portion is as rotatingshaft; And internal gear, this internal gear is formed on swing cam, and Control Shaft is as rotatingshaft, in order to 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 movement by the anastomosis part of internal gear of the position of cam follower.
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 rotating cam periphery along rotating cam, and the movement of swing cam causes the change of the lifting capacity of engine valve, and when Control Shaft rotated along the direction of the lifting capacity that reduces described engine valve, the point of contact between cam follower and rotating cam moved along the direction with the direction of rotation of this rotating cam.
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 hollow space.
According to the present invention of above-mentioned feature, can effectively eliminate the variation of the lifting characteristic of each engine valve that causes due to the thermal expansion difference between construction package or parts, 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 used for the stereogram of 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 the 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 the 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 operational condition, and Fig. 4 B is illustrated in the engine valve operation under little lifting and operational condition;
Fig. 5 illustrates the operation of engine valve, and comprises: Fig. 5 A is illustrated in large lifting and the not operation of the engine valve under operational condition, and Fig. 5 B is illustrated in the engine valve operation under large lifting and operational condition; With
Fig. 6 means the lifting capacity of engine valve according to an embodiment of the invention and opens/close the chart of the relation between 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 ", 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 for opening and closing the suction port be communicated with the firing chamber of cylinder head and 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 cylinder head, in order to move vertically.
Engine valve 2 comprises a side engine valve 2A who is arranged in the front side and the opposite side engine valve 2B that is arranged in rear side, and a side engine valve 2A and opposite side engine valve 2B are juxtaposed to each other.
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 continuously a side valve lid 3A.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 continuously opposite side valve gap 3B.
Say further, a side valve lid 3A and opposite side valve gap 3B consist of valve gap 3, one side valve bar 4A and opposite side valve rod 4B formation valve rod 4.
Internal-combustion engine 1 further comprise roller refer to driven member (roller finger follower RFF: rocking arm) 5, this roller refers to that driven member 5 is according to its axial (up/down) mobile engine valve 2 that opens and closes.
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 side arm 6A of section of along continuous straight runs and left/right direction orientation, be supported on a side roll shaft 7A of the central part of a side arm 6A of section; 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 side arm 6A of section; Be formed on a side regulator supporting portion 10A of the right end portion of a side arm 6A of section.This side regulator supporting portion 10A is supported on a side hydraulic shock regulator 11A of section.
In a similar manner, the opposite side roller refers to that driven member 5B comprises: be arranged to the opposite side arm 6B of along continuous straight runs and left/right direction 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 regulator 11B of section.
In this illustrated structure, a side arm 6A of section and opposite side arm 6B consist of arm 6.One side roll shaft 7A and opposite side roll shaft 7B consist of roll shaft 7.One side roller 8A and opposite side roller 8B consist of roller 8.One side regulator supporting portion 10A and opposite side regulator supporting portion 10B consist of regulator and support 10.The one side hydraulic shock regulator 11A of section and the opposite side hydraulic shock regulator 11B of section consist of 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 with the crankshaft-synchronous of internal-combustion engine 1, thereby drives engine valve 2.
Rotating cam 13 integrally is arranged on 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.
As shown in Fig. 1 to 3, variable valve-operating system 16 comprises the Control Shaft parallel with camshaft 12 17 that longitudinally is arranged between engine valve 2 and camshaft 12.Control Shaft 17 drives and controls by the actuator 18 that comprises motor.Actuator 18 drives and controls by control unit 19.
As 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 opposite side shaft portion 21, the diameter of the eccentric shaft portion 22 of tubular is larger 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 the eccentric predetermined offset of opposite side shaft portion 21 (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 as the eccentric offset " e " radially 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, in order to can promote engine valve 2.
Swing cam 23 comprises a side oscillation cam member 23A who is attached to a side shaft part 20 and the opposite side swing cam member 23B that is attached to opposite side shaft portion 21.
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 and cause the side cam portion 25A that a side engine valve 2A is raised from a side group circular portion 24A.
As shown in Figure 2, a side hollow space 26A with internal diameter larger 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 further note, align 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 pressed or a mobile side roller refers 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 radially gives prominence to and causes 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 larger 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 further note, align 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 pressed 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 consist of the base circle portion 24 of swing cam 23.One side cam portion 25A and opposite side cam portion 25B consist of the cam portion 25 of swing cam 23.One side hollow space 26A and opposite side hollow space 26B consist of the hollow space 26 of swing cam 23.One side internal gear piece 27A and opposite side internal gear piece 27B consist of 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 swings and causes that swing cam 23 is swung by the rotating cam 13 of camshaft 12.
Cam follower 31 comprises: have the tubular body 33 of shaft through-hole 32, the eccentric shaft portion 22 of Control Shaft 17 is fitted in this shaft through-hole 32; In the axial centre position of tubular body 33 towards the outstanding pair of rolls supporting part 34 and 34 of camshaft side; Be supported in the roller pin 35 of pair of rolls supporting part 34 and 34; With at the roller 36 that is supported in rotationally between pair of rolls supporting part 34 and 34 on roller pin 35.
Cam follower 31 can unsteadily be supported on eccentric shaft portion 22.
As 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 consist of the external gear 37 of cam follower 31.
Say 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 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 changes the lifting characteristic of a side engine valve 2A and opposite side engine valve 2B by changing a side and opposite side swing cam member 23A and 23B with respect to the relative position relation of cam follower 31.
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 in the number of teeth of each in a side and opposite side internal gear piece 27A and 27B and a side and opposite side external gear piece 37A and 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 respectively fore-end and the rear end part of the tubular body 33 of cam follower 31.Therefore, two valve 2A and 2B can be driven by a cam follower 31.
Have such structure according to the variable valve-operating system 16 of the present embodiment, wherein Control Shaft 17, cam follower 31 and swing cam 23 refer to additionally be arranged between driven member 5 conventional roller oscillatory valve guidance system at camshaft 12 and roller.
As shown in Figure 4 and 5, the lifting capacity of engine valve 2 (β) is changed for the rotational angle (α) of Control Shaft 17 continuously by the angle of nip (nip angle) that changes between cam follower 31 and swing cam 23.
Say further, as shown in Figure 3, variable valve-operating system 16 refers to driven member 5 operate engine valves 2 by making swing cam 23 press with mobile roller, can replace to be suitable for various valve guidance systems with analogs such as tappets (tappet) but roller refers to driven member 5.
The following operation of variable valve-operating system 16.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 changed with respect to the movement 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 structure as above, the impact of the relatively hot differential expansion between the uncontrolled axle 17 of the lifting characteristic of engine valve 2 and internal-combustion engine 1.
In addition, evolution mechanism 30 consists of 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 consisting of, thereby simplifies the structure and improved the productivity of variable valve-operating system 16.
Say further, when Control Shaft 17 rotated, cam follower 31 moved, so that the point of contact of itself and rotating cam 13 moves along the periphery of rotating cam 13, and the movement of the lifting capacity of engine valve 2 by swing cam 23 is changed.When Control Shaft 17 was rotated along the direction of the lifting capacity that reduces engine valve 2, the point of contact between cam follower 31 and rotating cam 13 was along mobile with the direction (towards advance side (advanceangle side)) of the direction of rotation of rotating cam 13.According to this movement, 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 damage.
Next, the lifting operation of variable valve-operating system 16 is described with reference to Figure 4 and 5.
As 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 swing cam 23 is reduced to β 1, and the contact position between rotating cam 13 and cam follower 31 is moved to γ 1 along the advance angle direction.At this moment, even the cam portion of rotating cam 13 15 touch rolls 36 are to wave swing cam 23, as shown in Figure 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 in Fig. 6).
Simultaneously, as shown in Fig. 5 A, in order to increase lifting capacity when engine valve 2 inoperation, Control Shaft 17 clockwise directions rotate, until change to angle [alpha] 2 with respect to the angle of reference position from angle [alpha] 1.Then, external gear 37 rotates around the axle center O2 clockwise direction of eccentric shaft portion 22.Then, cause that as the evolution mechanism 30 of cycloid mechanism operation cam follower 31 slides (shown in the arrow M in Fig. 5 A) to the right, until the contact position between rotating cam 13 and cam follower 31 changes to γ 2 from γ l.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, until 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 as shown in Fig. 5 B, when engine valve 2 operation, swing cam 23 and roller refer to that between driven member 5, the contact range by cam portion 25 increases.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 large lifting situation) (seeing R2 in Fig. 6).
Say 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 less, and more move along the advance angle direction 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 rotating cam 13 is along mobile with the direction (advance angle direction) of 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 damage, and improve fuel consumption efficiency.
In addition, be different from conventional system, because do not need the axial control of Control Shaft, even also can obtain stable precision or performance in little lifting situation, and be not subject to consisting of the impact of the material thermal expansion coefficient of the parts of motor or assembly due to temperature variation.
In the present embodiment, evolution mechanism 30 provides following advantages as the use of cycloid mechanism.
According to the minimizing principle of cycloid mechanism, drift angle (deflection angle) α〉drift angle β.More particularly, according to the rotation of Control Shaft 17 and the rotation of swing cam 23, obtain formula (α 2-α 1)〉(β 2-β 1), thus can obtain big retarding, simultaneously, according to torque transfer, insensitive in 17 pairs of change in torque of Control Shaft of acceleration side.In other words, this causes the improvement for the reliability of the actuator 18 that drives Control Shaft 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 internal gear, can guarantee large contact gear ratio (flank of tooth contact gear ratio) and can reduce slip ratio, thereby advantageously improving 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 carry out many other changes and improvements in the situation that do not deviate from the scope of the claim of enclosing.
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 arrange 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 etc.
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 comprises the camshaft of engine valve and the described engine valve of operation, and described variable valve-operating system comprises:
Rotating cam, described rotating cam integrally are arranged on described camshaft;
Swing cam, described swing cam promotes described engine valve, and described swing cam can unsteadily be supported on Control Shaft;
Cam follower, described cam follower swings described swing cam; With
Evolution mechanism, described evolution mechanism makes described cam follower connect with described swing cam, described evolution mechanism construction is used for changing described swing cam with respect to the relative position relation of 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; The external gear that is divided into rotatingshaft with described eccentric axial portion, described external gear are formed on the described cam follower that can unsteadily be supported on described eccentric shaft portion; With the internal gear take described Control Shaft as rotatingshaft, described internal gear is formed on described swing cam, in order to 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 movement by the described anastomosis part of described internal gear of the position of described cam follower.
2. the variable valve-operating system for internal-combustion engine as claimed in claim 1, it is characterized in that, when Control Shaft is rotated, described cam follower moves, make with the point of contact of the described rotating cam periphery along rotating cam and move, and the movement of described swing cam causes the change of the lifting capacity of described engine valve, and when described Control Shaft rotated along the direction of the lifting capacity that reduces described engine valve, the point of contact between described cam follower and described rotating cam moved along the direction with the direction of rotation of described rotating cam.
3. the variable valve-operating system 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 described hollow space.
CN2010105556311A 2009-11-12 2010-11-12 Variable valve operating system for internal combustion engine Expired - Fee Related CN102061957B (en)

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Families Citing this family (14)

* Cited by examiner, † Cited by third party
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
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
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
KR102371229B1 (en) 2016-12-14 2022-03-04 현대자동차 주식회사 Continuous variable vavle timing apparatus and engine provided with the same

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6041746A (en) * 1997-12-09 2000-03-28 Nissan Motor Co., Ltd. Variable valve actuation apparatus
DE10211969A1 (en) * 2002-03-19 2003-10-02 Bayerische Motoren Werke Ag Valve gear for reciprocating piston engine has connecting element in frictional contact with first operating element and form-locking on driven spindle, and with roller between first operating element and connecting element
EP1619362A2 (en) * 2004-07-20 2006-01-25 Bayerische Motoren Werke Aktiengesellschaft Valve train for an internal combustion engine

Family Cites Families (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59111559U (en) * 1983-01-19 1984-07-27 富士機工株式会社 reclining seat device
US7155222B1 (en) * 2000-01-10 2006-12-26 Qualcomm, Inc. Method for performing RR-level registration in a wireless communication system
JP3799944B2 (en) * 2000-03-21 2006-07-19 トヨタ自動車株式会社 Variable valve mechanism and intake air amount control device for internal combustion engine
JP4165446B2 (en) * 2004-05-10 2008-10-15 トヨタ自動車株式会社 Variable valve mechanism for multi-cylinder internal combustion engine
DE102005018956A1 (en) * 2005-04-23 2006-11-23 Schaeffler Kg Device for adjusting the camshaft of an internal combustion engine
JP2007071174A (en) * 2005-09-09 2007-03-22 Toyota Motor Corp Control device for internal combustion engine
JP4297189B2 (en) * 2005-09-27 2009-07-15 トヨタ自動車株式会社 Variable valve operating apparatus and valve opening adjustment method
JP4718979B2 (en) * 2005-12-02 2011-07-06 トヨタ自動車株式会社 Variable valve timing device
JP4924922B2 (en) * 2006-01-16 2012-04-25 株式会社デンソー Valve timing adjustment device
JP4600326B2 (en) * 2006-03-27 2010-12-15 トヨタ自動車株式会社 Variable valve timing device
US8151750B2 (en) * 2007-03-16 2012-04-10 Nissan Motor Co., Ltd. Valve operating device for internal combustion engine
JP2008291744A (en) * 2007-05-24 2008-12-04 Toyota Motor Corp Control device for internal combustion engine
JP4871310B2 (en) * 2008-02-15 2012-02-08 株式会社オティックス Variable valve mechanism for internal combustion engine
US20090241873A1 (en) * 2008-03-27 2009-10-01 Tomoyuki Muraoka Variable valve-operating system for internal combustion engine
JP4348564B2 (en) * 2008-03-28 2009-10-21 三菱自動車工業株式会社 Variable valve operating device for internal combustion engine
KR100986355B1 (en) * 2008-07-23 2010-10-08 현대자동차주식회사 Slide type continuous variable valve lift device
JP5028355B2 (en) * 2008-08-01 2012-09-19 株式会社オティックス Variable valve mechanism
US20100059005A1 (en) * 2008-09-08 2010-03-11 Stone Albert C Method and apparatus for adjusting variable valve lift
JP5313644B2 (en) * 2008-11-26 2013-10-09 株式会社オティックス Variable valve mechanism
KR101080796B1 (en) * 2008-12-04 2011-11-07 기아자동차주식회사 Continuous variable valve lift apparatus
US8291874B2 (en) * 2008-12-05 2012-10-23 Hyundai Motor Company Apparatus for adjusting deviation of engine and continuously variable valve lift device including the same
JP2010138737A (en) * 2008-12-10 2010-06-24 Hitachi Automotive Systems Ltd Variable valve gear for internal combustion engine and controller of the same
JP5115747B2 (en) * 2009-02-13 2013-01-09 スズキ株式会社 Variable valve operating device for internal combustion engine
US8408172B2 (en) * 2009-09-14 2013-04-02 Delphi Technologies, Inc. High efficiency lift profiler for an internal combustion engine
JP2012036864A (en) * 2010-08-10 2012-02-23 Hitachi Automotive Systems Ltd Variably operated valve apparatus for internal combustion engine, start system for internal combustion engine, and start control apparatus for internal combustion engine
JP5561480B2 (en) * 2010-11-08 2014-07-30 スズキ株式会社 Variable valve operating device for internal combustion engine
JP2012117376A (en) * 2010-11-29 2012-06-21 Hitachi Automotive Systems Ltd Valve actuation apparatus of internal combustion engine and rockable cam to be used in the same
US8640660B2 (en) * 2011-03-10 2014-02-04 Jesper Frickmann Continuously variable valve actuation apparatus for an internal combustion engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6041746A (en) * 1997-12-09 2000-03-28 Nissan Motor Co., Ltd. Variable valve actuation apparatus
DE10211969A1 (en) * 2002-03-19 2003-10-02 Bayerische Motoren Werke Ag Valve gear for reciprocating piston engine has connecting element in frictional contact with first operating element and form-locking on driven spindle, and with roller between first operating element and connecting element
EP1619362A2 (en) * 2004-07-20 2006-01-25 Bayerische Motoren Werke Aktiengesellschaft Valve train for an internal combustion engine

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
JP特开2001-263015A 2001.09.26
JP特开2007-71174A 2007.03.22

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US20110107989A1 (en) 2011-05-12
JP5294156B2 (en) 2013-09-18

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