CN101046167B - Variable valve device for internal combustion engine - Google Patents
Variable valve device for internal combustion engine Download PDFInfo
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- CN101046167B CN101046167B CN200710093612XA CN200710093612A CN101046167B CN 101046167 B CN101046167 B CN 101046167B CN 200710093612X A CN200710093612X A CN 200710093612XA CN 200710093612 A CN200710093612 A CN 200710093612A CN 101046167 B CN101046167 B CN 101046167B
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- rocking arm
- rocker
- cam
- oil circuit
- intake cam
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Abstract
A variable valve device for an internal combustion engine comprises a first switching oil passage which is formed along an axial direction in one of a rocker shafts, the first rocker arm being switched to the first mode by applying oil pressure to a first rocker arm through the first switching oil passage, and a second switching oil passage which is formed along an axial direction in the other rocker shaft, a second rocker arm being switched to the first mode by applying oil pressure to the second rocker arm through the second switching oil passage. The first switching oil passage and the second switching oil passage are formed in a ladder shape in which the first switching oil passage and the second switching oil passage communicate via a plurality of relay oil passages.
Description
Quoting mutually of related application
The application is a preference based on also requiring No.2006-089144 of Japanese patent application formerly and No.2006-089415 with application on March 28th, 2006, and both contents are attached to herein by reference.
Technical field
The present invention relates to a kind of variable valve device for internal combustion engine, wherein, a pair of rocker is provided with at least a switching oil circuit, so that when the oil pressure of the switching oil circuit of a rocker is passed to the switching oil circuit of another rocker, switches the rocking arm that is positioned on the rocker simultaneously.
Background technique
The motor that has the variable valve device of rocking arm, when switching to fast mode or cylinder park mode (cylindersuspension mode) from common state, can balance improve the output characteristics of the Reciprocating engine of installing on the automobile (internal-combustion engine) and reduce the fuel consumption performance.When motor entered high engine speed range, motor switched to the fast mode that is applicable to high engine speed range.When motor entered the runnability that does not require big output, motor switched to the cylinder park mode that partial cylinders is suspended.
In the cylinder park mode, the frequent lifting (opening and closing) of suction valve in the cylinder and outlet valve is stopped to reduce pumping loss.Therefore, in most of variable valve devices, suction valve is subjected to the driving of hydraulic pressure rocking arm, this hydraulic pressure rocking arm can make suction valve switch in normal mode (low-speed mode), fast mode and cylinder park mode, outlet valve is subjected to the driving of hydraulic pressure rocking arm, this hydraulic pressure rocking arm can make outlet valve switch between normal mode (low-speed mode) and cylinder park mode, and above-mentioned rocking arm is by the different oil pressure system drive.For example, Japanese Patent Application Publication communique No.2005-90408 discloses this technology.
Specifically, as disclosed among the open communique No.2005-90408 of Japan Patent, in air inlet rocker and exhaust rocker (a pair of rocker), two kinds of switching oil circuits that are used for fast mode and cylinder park mode are formed in the air inlet side rocker vertically.The switching oil circuit that is used for the cylinder park mode is formed in the exhaust side rocker vertically.
Use two kinds of pressurized oil systems.A kind of pressurized oil system comprises the switching oil circuit of the cylinder park mode that is used for the exhaust side rocker and is used for the switching oil circuit of the cylinder park mode of air inlet side rocker.They are connected in series together.Another pressurized oil system is used for switching at a high speed.
In aforementioned two pressurized oil systems, when oil pressure was not applied to the switching oil circuit that is used for fast mode and exhaust side and switches on the oil circuit, air inlet side rocking arm and exhaust side rocking arm were all selected low-speed mode (cam selects to be applicable to normal operation).
When oil pressure only was applied on the switching oil circuit of air inlet side rocker, air inlet side rocking arm switched to fast mode (cam selects to be applicable to high speed operation).When oil pressure only was applied on the exhaust side switching oil circuit (being used for the cylinder park mode), air inlet side rocking arm and exhaust side rocking arm switched to cylinder park mode (lifting of suction valve and outlet valve is suspended), and wherein, cam does not move and is delivered on the valve.
In variable valve device, because mode of operation often switches according to the running state of motor (automobile), thus require all cylinders in the motor in the switching time of appointment, to have mode switching performance fast, i.e. performance of handoffs.
As disclosed among the open communique NO.2005-90408 of Japan Patent, in this system, oil pressure is delivered to another rocker from a rocker, only is arranged on the exhaust side rocker owing to be used for the exhaust side switching oil circuit of cylinder park mode, so can guarantee large-area passage.
Yet, the air inlet side switching oil circuit that is used for the cylinder park mode is arranged to parallel with the switching oil circuit of the air inlet side rocker that is used for fast mode, compare so switch the aisle spare of oil circuit with the exhaust side that is used for the cylinder park mode, the aisle spare of this structure diminishes.
Therefore, in Japanese Patent Application Publication communique No.2005-90408 in the disclosed structure, wherein, oil pressure sequentially switches oil circuit from the exhaust side that is used for the cylinder park mode and is delivered to the air inlet side switching oil circuit that is used for the cylinder park mode, though oil pressure is swiftly delivered to the exhaust side rocking arm, oil pressure is difficult for being delivered in the air inlet side rocking arm because of the difference of aisle spare.
So, air inlet side rocking arm, the operation that especially is positioned at the air inlet side rocking arm of pressurized oil system end lags behind exhaust side rocking arm (cylinder park mode switch when initial or at the end).
This hysteresis effect has reduced the performance of handoffs during the cylinder park mode.The switching fluctuation that is caused by hysteresis effect produces noise and vibration sometimes.In addition, hysteresis effect narrows down the scope of operation cylinder park mode in the motor.
Summary of the invention
An object of the present invention is to provide a kind of internal-combustion engine with making the improved variable valve device of its mode switching performance.
Variable valve device for internal combustion engine comprises according to the present invention: be arranged on the rotatable camshaft in the body of internal-combustion engine; The rocker that a pair of next-door neighbour's camshaft is provided with; Suction valve by the camshaft actuated of rotating; Outlet valve by the camshaft actuated of rotating; By freely the first hydraulic pressure rocking arm of shaking of a support in the rocker, and the described first hydraulic pressure rocking arm can be at least at drive condition usually be different from one the driving of switching between first pattern of described common drive condition in described suction valve and the described outlet valve; Shaken freely the second hydraulic pressure rocking arm by what another rocker supported, and the described second hydraulic pressure rocking arm can be at least at described common drive condition be different from another the driving of switching between described first pattern of described common drive condition in described suction valve and the described outlet valve; Be formed at first on the rocker vertically and switch oil circuit, oil pressure switches oil circuit via first and is applied on first rocking arm, makes first rocking arm switch to first pattern; And being formed at the switching of second on another rocker oil circuit vertically, oil pressure switches oil circuit via second and is applied on second rocking arm, makes second rocking arm switch to first pattern.The first switching oil circuit and the second switching oil circuit form trapezoidal, wherein are communicated with by a plurality of relaying oil circuits between the first switching oil circuit and the second switching oil circuit.
So by the transfer of relaying oil circuit, oil pressure is delivered to various piece in the switching oil circuit that is formed at another rocker rapidly from being formed at a switching oil circuit on the rocker.
Other purposes of the present invention and advantage will be described in the following description, and partial content is conspicuous in specification, maybe can know by implementing the present invention.Can realize objects and advantages of the present invention according to following pointed method.
Description of drawings
With the accompanying drawing that constitutes a part in the specification the specific embodiment of the present invention is described, and principle of the present invention is described with the detailed description of above-mentioned explanation and following mode of execution.
Fig. 1 is a perspective view, shows the V-type engine of being furnished with variable valve device according to an embodiment of the invention;
Figure 2 shows that the plan view of the variable valve system on the left side in the motor;
Fig. 3 is a plan view, shows the trapezoidal oil circuit in the variable valve device in the variable valve system;
Fig. 4 is a perspective view, shows the variable valve device that is used for a cylinder that is installed in left bank;
Fig. 5 is a perspective view, shows the state when rocker lid breaks away from variable valve device in it;
Fig. 6 is a plan view, shows the variable valve device of observing along the arrow A direction of Fig. 5;
Fig. 7 is a sectional drawing, shows along the rocker lid of the F-F line of Fig. 3;
Fig. 8 is a plan view, shows the layout of various cams in the camshaft;
Fig. 9 is the sectional drawing along B-B line shown in Figure 6, the air inlet side rocking arm (low speed) shown in the displayed map 6;
Figure 10 is the sectional drawing along C-C line shown in Figure 6, the air inlet side rocking arm (at a high speed) shown in the displayed map 6;
Figure 11 is the sectional drawing along D-D line shown in Figure 6, the exhaust side rocking arm shown in the displayed map 6;
Figure 12 is the sectional drawing along E-E line shown in Figure 5, the non-lift cam shown in the displayed map 6;
Figure 13 is a perspective view, shows the structure of air inlet side rocking arm;
Figure 14 is a perspective view, shows the state the when structure of air inlet side rocking arm is opened in it;
Figure 15 is a perspective view, shows the structure of exhaust side rocking arm;
Figure 16 is a perspective view, shows the state the when structure of exhaust side rocking arm is opened in it;
Figure 17 shows that the view of the operating mode of explanation variable valve device;
Figure 18 is a plan view, shows the variable valve device of observing along the arrow directions X of Fig. 4;
Figure 19 is a plan view, shows the state that only stays rocker; And
Figure 20 is a plan view, shows the main body of variable valve device second embodiment of the invention.
Embodiment
Be described with reference to Fig. 1～19 pair first embodiment of the present invention.
Figure 1 shows that the perspective view of motor when observing motor from behind (internal-combustion engine), for example, V-six Reciprocating engines (hereinafter to be referred as V-type engine).
Figure 2 shows that the plan view of V-type engine left bank, Figure 3 shows that the plan view when a part in rocker in the left bank and the rocker lid is left, Figure 4 shows that the perspective view of the variable valve device in the suction valve and outlet valve in the V-type engine, and Figure 5 shows that the rocker lid breaks away from the perspective view of variable valve device.
Figure 6 shows that the plan view of the variable valve device of observing along the arrow A direction of Fig. 5, Figure 7 shows that along the sectional drawing of the rocker lid of the F-F line of Fig. 3, and the plan view that Figure 8 shows that various cams in the variable valve device.The sectional drawing of the part the variable valve device that Fig. 9～12 are depicted as respectively arrow B～E from Fig. 6 when observing.Figure 13 shows that the perspective view of the structure of air inlet side rocking arm, Figure 14 shows that the perspective exploded view of the structure of air inlet side rocking arm, Figure 15 shows that the perspective view of the structure of exhaust side rocking arm, Figure 16 shows that the perspective exploded view of the structure of exhaust side rocking arm, and the view that Figure 17 shows that the valve characteristic that explanation is caused by variable valve device.In Fig. 1, alphabetical Fr represent V-type engine forwards to.
With reference to Fig. 1, the body in the numeral 1 expression V-type engine.Engine body 1 comprises cylinder in V-arrangement body 5 and cylinder head 6.Specifically, cylinder block 5 is included in the common crankshaft case part 2 of its underpart, and cylinder block 5 comprises V-type deck cylinder block part (deck cylinder portion) 4 at an upper portion thereof.Each V-type deck cylinder block part 4 all has three cylinders 3 (shown in Fig. 4～6).Cylinder head 6 is installed in respectively on the top of deck cylinder block part 4.
Little assembly such as top cover and food tray do not show in Fig. 1.The right 7a that protrudes with V-arrangement and among the 7b of the left side each are formed by deck cylinder block part 4 and cylinder head 6.Define the right and left of this row based on forward direction.As shown in Figure 4 and Figure 5, piston 8 is arranged in the cylinder 3 of respectively arranging 7a, 7b, and can be reciprocating.The bent axle (not shown) is combined in the crankcase part 2.
Yet row 7a and 7b have skew on fore-and-aft direction, so that arrange the connecting rod (not shown) of stretching out from piston 8, and make it axial alignment with bent axle.
As shown in Figure 4 and Figure 5, in the lower surface of cylinder head 6, firing chamber 11 is forming in the zone of cylinder 3.As shown in Figure 4 and Figure 5, in each firing chamber 11, two (a plurality of) suction port 12a and 12b and two (a plurality of) suction valve 13a and 13b are located at the inboard of row 7a and 7b.Suction valve 13a and 13b be opening and closing suction port 12a and 12b respectively.Two (a plurality of) relief opening 14a and 14b and two (a plurality of) outlet valve 15a and 15b are located at the outside of row 7a and 7b.Outlet valve 15a and 15b opening and closing relief opening 14a and 14b.So the row of combustion air from motor 1 inboard sucks, discharge in the row of gas of combustion from motor 1 the outside.
Be respectively applied among suction valve 13a and 13b and outlet valve 15a and the 15b to the biased structure of sealing all the time of closing direction with the valve spring (not shown).
On the cylinder head 6 on the right of single-top camshaft (single overhead camshaft) variable valve system 17 is located among 7a and the left side 7b.As shown in Figure 2, variable valve system 17a on the left bank 7a comprises a kind of (can three kinds of mode switching) intake rocker module 18 and a kind of (can two kinds of mode switching) exhaust rocker arm module 19.Usually (low speed) pattern, fast mode (being equivalent to second pattern among the present invention) and cylinder park mode (in order to suspend the pattern of cylinder: be equivalent to first pattern among the present invention) can switch in intake rocker module 18.Usually (low speed) pattern and cylinder park mode (in order to suspend the pattern of cylinder: be equivalent to first pattern among the present invention) can switch in exhaust rocker arm module 19.In the present invention variable valve system 17a is defined as variable valve device.
That variable valve system 17b on the right row 7b comprises is a kind of (can two kinds of mode switching) intake rocker module 20 and variable valve device 21.Usually (low speed) pattern and fast mode can switch in intake rocker module 20.Variable valve device 21 only has (low speed) pattern usually.
Fig. 4～6 are depicted as the structure of the single cylinder the variable valve system 17a that is installed on the left bank 7a when the motor back is observed.Figure 13 shows that the rocking arm module 18 when observing from the inboard.Figure 14 shows that the state when its inner rocker arm module 18 is opened.Figure 15 shows that the rocking arm module 19 when observing from the inboard.Figure 16 shows that the state when its inner rocker arm module 19 is opened.
Structure to single cylinder is described below.With reference to Fig. 4～6, rotatable camshaft 25 is along the centre of the tip position that vertically is arranged on firing chamber 11 of cylinder head 6.On the inboard of air inlet rocker 26 (corresponding in the rocker of the present invention) row of being fixed to and be arranged to substantially parallel with camshaft 25.On the outside of exhaust side rocker 27 (corresponding to another rocker among the present invention) row of being fixed to and be arranged to substantially parallel with camshaft 25.
Rocker 26 and rocker 27 are arranged on the top of camshaft 25 in couples.The oil circuit 27a (be equivalent to the present invention's second and switch oil circuit) that is used for the cylinder park mode is formed in the rocker 27 vertically.The oil circuit 26a (be equivalent to the present invention's first and switch oil circuit) that is used for the cylinder park mode is formed in the rocker 26 vertically, and the oil circuit 26b (be equivalent to the 3rd of the present invention and switch oil circuit) that is used for fast mode also is formed in the rocker 26 vertically.That is to say, different rockers 27, oil circuit 26a and oil circuit 26b and rocker 26 are provided with abreast.
As shown in Figure 7, rocker 26 and 27 is arranged on the upper surface of rib 6a.Cylinder 3 is between rib 6a, and rib 6a rises from the upper surface portion of cylinder head 6.Part in the rocker 26 and 27 is located between the rib 6a on the cylinder head 6 with rocker lid.
Specifically, shown in Fig. 2～5, rocker lid 130 comprises rocker lid 130a and rocker lid 130b.Rocker lid 130a is located between the cylinder 3 and rocker covers the row end that 130b is located at cylinder 3.
As Fig. 4, Fig. 5 and shown in Figure 7, rocker lid 130a and 130b all have this structure, and a plurality of cylindrical bolt insertion portions 133 of inserting bolt 132 are formed on the platy substrate part 131 of crossing rocker 26 and 27 in it.
So, as Fig. 5 and shown in Figure 7, base part 131 adapts in the groove 134 that is formed on rocker 26 and 27 top (side relative with rib 6a), and the bolt insertion portion 133 of bolt 132 from base part 131 is screwed among the rib 6a via the through hole 134a (as shown in Figure 5 and Figure 6) in rocker 26 and 27.In the method, rocker lid 130a and 130b are fixed on the cylinder head 6 with rocker 26 and 27.
In the fixed structure of rocker lid 130a and 130b, on rocker 26 1 sides, use single bolt 132, on rocker 27 1 sides, use two bolts 132.
As shown in Figure 3, the rocker lid 130b on being positioned at the motor end (owing to oil circuit 26a not being set), also on rocker lid 130a and 130b, form oil circuit 140 (being equivalent to the relaying oil circuit among the present invention) in this part.
As shown in Figure 7, each oil circuit 140 is formed by cylindrical part 143, and cylindrical part 143 is formed on the base part 131 along rocker 26 and 27.Cylindrical part 143 has bottom 142a in that one is distolateral, and has by stopper 142 sealed opening 142b at the other end.
Specifically, the bottom of cylindrical part 143 is located between two bolt insertion portions 133 and 133 on rocker 27 sides.Opening be located at the contiguous position of the bolt insertion portion 133 of rocker 26 sides on.So cylindrical part 143 is provided with obliquely.Thin passage in the cylindrical part 143 is as oil circuit 140.
As shown in Figure 7, through hole 143a that is communicated with the end of oil circuit 140 and 143b are manufactured on respectively as in the back of the base part 131 of an end of cylindrical part 143 and in the back as the base part 131 of cylindrical part 143 the other ends.
As shown in Figure 7, the through hole 143a on exhaust side rocker 27 1 sides is communicated with branched hole 144a (also as shown in Figure 5), and branched hole 144a makes the oil circuit 27a bifurcated in the rocker 27.Through hole 143b on air inlet side rocker 26 1 sides is communicated with branched hole 144b (also as shown in Figure 5), and branched hole 144b makes the oil circuit 26a bifurcated in the rocker 26.
Form the structure of a plurality of (for example, three) oil circuit, wherein whole oil circuit 26a is communicated with through a plurality of oil circuits 140 and whole oil circuit 27a in parallel.Trapezoidal oil circuit 146 is formed by this oil channel structures.
Low speed intake cam 33 has cam profile, and wherein open-close timing and valve-lift amount are arranged to be suitable for the low cruise of motor.High speed intake cam 30 has cam profile, and wherein open-close timing and valve-lift amount (being higher than Lower speed cam 33) are arranged to be suitable for the high speed operation of motor.Non-lift cam 31 has the cam profile that is only formed by the identical basic circle of radius, its Base radius greater than intake cam 30 and 33 and exhaust cam 32 in Base radius.Exhaust cam 32 has cam profile significantly, and wherein open-close timing and valve-lift amount are arranged to be suitable for the discharge of gas of combustion.
As Fig. 4～6, Figure 13 and shown in Figure 14, intake rocker module 18 has this structure, and wherein hydraulic rocking arm 18a is installed on the rocker 26.Rocking arm module 18 comprises that valve drives rocking arm 35 and a pair of low speed and the driven rocking arm 60 of High speed cam and 70.Valve drives rocking arm 35 and drives suction valve 13a and 13b, and the driven rocking arm 60 of cam and 70 is followed intake cam 30 and 33 motions respectively.
As Fig. 4, Fig. 5 and shown in Figure 14, valve drives rocking arm 35 and comprises cylindrical rocker supporting sleeve 36, a pair of rocking arm 37, adjusting screw (abutting part) 38 and mode switching operative section 40a and 40b.Rocking arm 37 extends (axle sleeve radially) from the two end portions of axle sleeve 36 to suction valve 13a and 13b.Adjusting screw 38 is connected to the fore-end of rocking arm 37.Mode switching operative section 40a and 40b are located on the base part of rocking arm 37.
As Fig. 4～shown in Figure 6, in the scope of the point that has intake cam 33 (being used for low speed), rocker 26 is rotatably installed on the axle sleeve 36 in the rocking arm 37 from the point that has intake cam 30 (being used at a high speed).In axle sleeve 36, the adjusting screw 38 on the fore-end of rocking arm 37 is positioned at the top (valve rod end) of suction valve 13a and 13b.
That is to say, when valve drives rocking arm 35 when rocker 26 shakes, drive suction valve 13a and 13b in abutting connection with the end portion of the adjusting screw 38 of valve rod end.
Shown in Figure 12～14, on the outer circumferential face of axle sleeve 36, slide block 41 protrudes towards the outer circumferential face of non-lift cam 31 in the zone towards non-lift cam 31 from axle sleeve 36.
The outstanding length of slide block 41 is arranged to a certain size, thereby when suction valve 13a and 13b close, the outer circumferential face that the fore-end of slide block 41 can the non-lift cam 31 of butt.When suction valve 13a and 13b closed, the reaction force by the valve spring among suction valve 13a and the 13b made the non-lift cam 31 of slide block 41 butts, thereby prevented that the accident that whole valve drives rocking arm 35 from moving.
The piston type handover operation partly is used as handover operation part 40a and the 40b on two end portion that are arranged on axle sleeve 36.Below the handover operation part 40a that is located on intake cam 33 (the being used for low speed) side is described.With reference to Fig. 9, Figure 13 and Figure 14, cylinder 43 is formed on the base part of rocking arm 37 of intake cam 33 sides.Cylinder 43 is longitudinally, along the radially extension of rocker 26.Operation window 44 is formed on the front (surfaces on camshaft 25 1 sides) in the bottom of cylinder 43.Make the through hole 45 (only among Fig. 9 show) of diameter less than cylinder 43, this through hole is from the internal surface 36a of the axle sleeve 36 of bottom below being located immediately at cylinder 43 of cylinder 43.
Be contained in the cylinder 43 as the piston 46 of receiving part pressure spring 47 (only in Fig. 9, showing) with the bottom of piston 46 being pressed to cylinder 43.Therefore, the operation window 44 of cylinder 43 is closed by the outer circumferential face of piston 46 bottoms usually, and when piston 46 rose, piston 46 returned with opening operation window 44 from operation window 44.
As shown in Figure 9, pin 48 is slidably disposed in the through hole 45, and the opening that is positioned at the lower end of through hole 45 is communicated with the branch's oil circuit 49 that makes oil circuit 26a bifurcated.So, shown in long double dot dash line staggered among Fig. 9, when oil pressure when oil circuit 26a is applied on the pin 48, piston 46 is driven along such direction, promptly moves the direction of returning from operation window 44 because of the rising of pin 48 along piston 46.That is to say that operation window 44 is opened.
As Figure 10, Figure 13 and shown in Figure 14, as handover operation part 40a, wherein cylinder 51 is formed at the handover operation part 40b that structure on the base part of rocking arm 37 is used to be located at intake cam 30 (being used at a high speed) side.Cylinder 51 extends to the internal surface of axle sleeve 36 to increase path increment.So the through hole 52 that is communicated with of connecting with cylinder 51 is manufactured on the rocker 26 that is located immediately at below the cylinder 51.
The diameter of through hole 52 is less than the diameter of cylinder 51.As shown in figure 10, be different from handover operation part 40a, operation window 50 is formed on the upper front surface of cylinder 51, and piston 53 is contained in the cylinder 51 with the pressure spring 54 that makes piston 53 push down cylinder 51 bottoms.
As piston 53, make piston 53 can be installed in the cylinder block part on the bottom of operation window 50 with thin contour (low-profile) piston.40a is opposite with the handover operation part, and the opening of operation window 50 is normally opened in the cylinder 51, and when piston 53 rose, this opening was closed by the outer circumferential face of piston 53.As shown in figure 10, pin 55 is slidably disposed in the through hole 52, and the end portion of through hole 52 is communicated with the part of oil circuit 26b, and crossing with oil circuit 26b.Shown in long double dot dash line staggered among Figure 10, when oil pressure when oil circuit 26b is applied on the pin 55, piston 53 is driven along such direction, promptly moves the direction of " locked in " operation window 50 because of the rising of pin 55 along piston 53.That is to say operation window 50 closures.
As shown in figure 14, notch portion 57 is formed on the opening edge on two end portion of axle sleeve 36.Notch portion 57 forms by cutting certain zone continuously, and this zone is from directly extending to base part (on the periphery wall of formation axle sleeve end) through the rocking arm 37 of axle sleeve 36 front portions (on a side relative with rocking arm 37) in cylinder 43 and part 51 below.
Shown in Fig. 2,4～6,10,13 and 14, the driven rocking arm 70 of high-speed side cam is arranged to the end next-door neighbour with the intake cam 30 of axle sleeve 36 (valve driving rocking arm) (being used at a high speed) side.
The driven rocking arm 70 of cam comprises cylindrical rocker support sleeve 71, a pair of Rollers supports (rolling yoke) 72, roller (rotation contact) 73 and abutting part 79 (abutment).Rocker 26 is rotatably installed on the axle sleeve 71.Roller bearings 72 is protruded to the tip position of intake cam 30 (being used at a high speed) linearly from two ends of axle sleeve 71.Roller 73 can be rotated to support between the fore-end of Rollers supports 72.Abutting part 79 is formed on the periphery wall of axle sleeve 71.
So the driven rocking arm 70 of cam has this structure, the driven rocking arm 70 of its cam at one end side has roller 73, simultaneously distolaterally has an abutting part 79 at another.Roller 73 rotates when the camming surface with intake cam 30 contacts.When camshaft 25 rotation, the driven rocking arm 70 of cam is moved following intake cam 30 when axle sleeve 71 shakes.
As shown in figure 14, notch portion 76 is formed on the end with axle sleeve 36 (valve driving rocking arm) next-door neighbour's axle sleeve 71, and notch portion 76 cuts to predetermined extent by the peripheral wall portions with the axle sleeve end and forms.Assign to form notch portion 76 by cutting circumferential part continuously, this circumferential section extends to the front portion (on the side relative with rocking arm 73) of axle sleeve 71 from the upper end of axle sleeve 71.
The edge part 36b that notch portion 57 on notch portion 76 on axle sleeve 71 ends and axle sleeve 36 ends is installed in axle sleeve 36 opening ends with complementing one another respectively go up and the edge part 71b of axle sleeve 71 opening ends on.
Assembling between above-mentioned part obviously allows the driven rocking arm 70 of cam to do essential motion.This assembling is along the edge part 71b on the end of edge part 36b on the end of the axial parcel axle sleeve 36 of the rocker in the outer circumferential face of rocker 26 26 and axle sleeve 71.
Abutting part 79 is arranged on the edge part 71b.Operation window 50, cylinder 51, piston 53 and pressure spring 54 are arranged on the edge part 36b.When edge part 36b and edge part 71b were wrapped, abutting part 79 and piston 53 were positioned to toward each other.So shown in Figure 13 and 14, the rocker 26 by edge part 71b, edge part 36b along the circumferential direction abreast-type arranges, the abutting part 79 of axle sleeve 71 and between the operation window on the axle sleeve 36 50 toward each other.
The Rollers supports 72 that contiguous axle sleeve 36 (inboard) is provided with is arranged to direct front at abutting part 79.The Rollers supports 72 of opposite side and abutting part 79 are arranged to be in line with operation window 50.
Shown in Figure 13 and 14, in the outer circumferential face of axle sleeve 71, flank part 74 is arranged in the scope of from abutting part 79 to inboard roller supporting element 72 (contiguous axle sleeve 36).Flank part 74 is by forming with the linear continuously rib 78 that links to each other of abutting part 79 and Rollers supports 72.
Abutting part 79 forms with such shape, and the horizontal wall energy in the fore-end of rib 78 passes in and out from operation window 50.Abutting part 79 is usually through operation window 50 turnover cylinders 51.When operation window 50 is sealed by piston 53, the piston 53 that abutting part 79 butts expose from operation window 50.
That is to say, be impinging air or butt piston 53 based on abutting part 79, and the mobile valve driving rocking arm 35 that whether passes to of high speed intake cam 30 being followed the driven rocking arm 70 of cam switches.Abutting part 79 and handover operation part 40a have constituted switching mechanism 79a.In the present invention switching mechanism 79a is defined as the air inlet switching unit.
As shown in figure 10, bearing 75 is formed on the front end of outboard roller supporting element 72 to bear the biasing force (making roller 73 push down the power of intake cam 30) among the pusher 70a that is combined in the rocker lid 130.
Shown in Fig. 2,4～6,9,13 and 14, the driven rocking arm 60 of low speed side cam is arranged to the end portion next-door neighbour on intake cam 30 (the being used for low speed) side with axle sleeve 36.The driven rocking arm 60 of cam has the symplex structure of the driven rocking arm 70 of high-speed side cam.
Because the driven rocking arm 60 of cam has the structure identical with the driven rocking arm of cam 70,, and omit explanation to it so the same section in the driven rocking arm 60 of cam is indicated the numeral 71～79 of indicating the part of the driven rocking arm 70 of cam with replacement with numeral 61～69.
Obviously, abutting part (abutment) 69 forms certain shape, and making wherein, abutting part 69 can pass in and out from operation window 44.As shown in Figure 9, for the driven rocking arm 60 of cam, the piston 46 of abutting part 9 common butt " locked in " operation windows 44.Operation window 44 is opened by piston 46 then, and abutting part 69 passes in and out from cylinder 43 through operation window 44.
That is to say, be impinging air or butt piston 46 based on abutting part 69, and the mobile valve driving rocking arm 35 that whether passes to of low speed intake cam 33 being followed the driven rocking arm 60 of cam switches.Abutting part 69 and piston 46 constitute switching mechanism 69a.In the present invention switching mechanism 69a is defined as the air inlet switching unit.
As Fig. 2, Fig. 4～6, Figure 11, Figure 15 and shown in Figure 16, exhaust rocker arm module 19 comprises branch open form rocking arm 18b, and branch open form rocking arm 18b is divided into the driven rocking arm 80 of cam and valve drives rocking arm 90.The driven rocking arm 80 of cam follows that exhaust cam 32 moves and valve drives rocking arm 90 and drives outlet valve 15a and 15b.In the present invention the driven rocking arm 80 of cam is defined as the driven rocking arm of outlet valve.In the present invention valve is driven rocking arm 90 and be defined as outlet valve driving rocking arm.
The driven rocking arm 80 of cam comprises cylindrical rocker support sleeve 81, U-shaped Rollers supports 82, roller 83 and flank part 84.Rocker 27 corresponding to exhaust cam 32 is rotatably installed on the axle sleeve 81.U-shaped Rollers supports 82 is outstanding linearly to the tip position of exhaust cam 32 from the two end portions of axle sleeve 81.Roller 83 can be rotated to support between the fore-end of Rollers supports 82.Flank part 84 is formed on the axle sleeve 81.
As Fig. 2, Fig. 4～6, Figure 11, Figure 15 and shown in Figure 16, valve drives rocking arm 90 and has this structure, and wherein door shape (gate-shaped) rocking arm 91 and mode switching operative section 98 are combined.Rocking arm 91 is arranged on (the driven rocking arm 80 of cam) on 81 two sides of axle sleeve.
A pair of cylindrical rocker support sleeve 92 is arranged on each end of rocking arm 91.Rocker 27 can be rotatably set in two axle sleeves 92 on the side, and its place's axle sleeve 81 (the driven rocking arm 80 of cam) is between axle sleeve 92.Arm 93 is arranged on the other end of rocking arm 91, and arm 93 from axle sleeve 92 respectively to outlet valve 15a and 15b linear extension.
Adjusting screw 94 is separately positioned on the fore-end of arm 93.Adjusting screw 94 is separately positioned on the upper end (valve stem end) of outlet valve 15a and 15b.Arm 93 is connected by tabular link arm 95 with the fore-end of 93 of arms.So it is shapes that valve drives rocking arm 90.
When valve drives rocking arm 90 when rocker 27 shakes, a plurality of outlet valve 15a and 15b are driven,
Shown in Figure 12,15 and 16, slide block 96 is arranged to protrude to the outer circumferential face of non-lift cam 31 from the outer circumferential face that is located at the axle sleeve 92 on non-lift cam 31 tip positions.The extrusion of slide block 96 is arranged to a certain size, thereby when outlet valve 15a and 15b close, the outer circumferential face that the fore-end of slide block 96 can the non-lift cam 31 of butt.
When outlet valve 15a and 15b closed, the reaction force by the valve spring among outlet valve 15a and the 15b made the non-lift cam 31 of slide block 96 butts, thereby the accident that prevents whole rocking arm 91 moves.
Shown in Figure 11,15 and 16, handover operation part 98 is located on the link arm 95.As shown in figure 11, use piston type handover operation part as handover operation part 98 shown in Figure 11.
Below handover operation part 98 is described.With reference to Figure 11, vertical escapement 99 is arranged to central protruding upward from link arm 95.Cylinder 99 tilts along the direction that cylinder 99 separates with rocker 27.Operation window 100 is formed on the front (surfaces on camshaft 25 1 sides) in the bottom of cylinder 99.In the bottom of cylinder 99 and be located immediately between the inboard of the arm below the cylinder 99 and make the through hole 101 of diameter less than cylinder 99.
The piston 102 that becomes receiving part is installed in the cylinder 99 with the pressure spring 103 of the bottom of piston 102 being pressed to cylinder 99.So the operation window 100 in the cylinder 99 is closed by the outer circumferential face of piston 102 usually, and when piston 102 rose, piston 102 returned with opening operation window 100 from operation window 100.
Pin 104 is slidably disposed in the through hole 101.As Fig. 6 and shown in Figure 11, the opening that is positioned on the lower end of through hole 101 is communicated with relaying oil circuit 105 on being formed on link arm 95.Relaying oil circuit 105 is opened in the internal surface of axle sleeve 92, passes the relaying oil circuit 106 that is formed on the arm 93.Relaying oil circuit 106 is communicated with the branch branch road 107 (only being presented among Figure 11) that makes oil circuit 27a bifurcated.Shown in long double dot dash line staggered among Figure 11, in the time of on oil pressure is applied to through the pin 104 of oil circuit 27a, piston 102 is driven in the direction, and wherein piston 102 moves from operation window 100 because of the rising of pin 104 and returns.That is to say that operation window 100 is opened.
Front end in the driven rocking arm 80 of cam is positioned at the front of operation window 100.As Figure 15 and shown in Figure 16, front end 89 forms this shape, and wherein front end 89 can pass in and out from operation window 100.
So, the piston 102 of front end 89 common butt " locked in " operation windows 100.When operation window 100 was opened, front end 89 passed in and out from cylinder 99 through operation window 100.
That is to say, be that sky hits air or butt piston 102 based on front end 89, and the mobile valve driving rocking arm 90 that whether passes to of exhaust cam 32 being followed the driven rocking arm 80 of cam switches.Front end 89 and handover operation part 98 have constituted switching mechanism 97.In the present invention, switching mechanism 97 is defined as the exhaust switching unit.Each cylinder 3 among the left bank 7a also uses this structure.
Figure 18 shows that the plan view of variable valve system 17a when observing by the arrow X among Fig. 4.As Fig. 4 and shown in Figure 180, in the rocker lid 130 that is provided with on the position of next-door neighbour rocking arm 18a and 18b, the rocker that the driven rocking arm 60 of low speed side cam and a plurality of pusher 60a and 80a are set in place on cylinder (two kinds) end covers among the 130b.Pusher 60a and 80a impose on the driven rocking arm 80 of exhaust side cams with pressure.
Because being arranged on rocker lid 130a between the cylinder and the driven rocking arm 70 of high-speed side cam in the adjacent cylinder 3 adjoins, so except pusher 60a and 80a, also on rocker lid 130a, the pusher 70a (three kinds of pushers) that pressure is imposed on the driven rocking arm 70 of cam is set.
Shown in Fig. 9～11, pusher 60a, 70a and 80a have such structure, and wherein, spring (resilient member) 140 combines with cylindrical stent 139, are attached with extruded member 131a at an end of cylindrical stent 139.
The elastic force of pusher 60a is set at a suitable load, makes driven rocking arm 60 extruding of idle cam live in gas cam 33 until the high engine speed range that enters motor.The elastic force load setting of pusher 70a and 80a is the elastic force load less than pusher 60a, and promptly the elastic force of pusher 70a and 80a is set for and made the idle driven rocking arm 70 of cam and 80 push down intake cam 33 until the high engine speed range that enters motor with valve spring.
As Fig. 4～6, Fig. 9 and shown in Figure 11, connect bearing 135 and be formed on the base part 131 to connect pusher 60a and the 80a on the rocker lid 130b (on the end of the cylinder that being arranged on embarks on journey arranges).Connect the top that bearing 135 is arranged to be located immediately at the top of the driven rocking arm 60 of low speed side cam respectively and is located immediately at the bearing 85 in the driven rocking arm 80 of exhaust side cams.Connect in the bearing 135 at each, support 131 is arranged so that extruder member 131a protrudes from the downside of rocker lid 130b.
The extruder member 131a that protrudes butt flexibly on bearing 65 and 85, thus elastic force is applied on the driven rocking arm 60 of cam.Elastic force makes the driven rocking arm 60 of cam press to low speed intake cam 33.Thereby elastic force is applied to and makes the driven rocking arm 80 of cam press to exhaust cam 32 on the driven rocking arm 80 of cam.
So in the pusher linkage structure, the driven rocking arm 60 of Lower speed cam is arranged on the outmost position, the driven rocking arm 80 of exhaust cam is arranged on the inboard.As shown in figure 18, among the pusher 60a and 80a on being connected in same rocker lid 130b, use the layout of pusher linkage structure and bearing 65 and 85, what pusher 60a was provided with more approaches the immovable point that rocker covers 131b than pusher 80a.In the case, the position of pusher 60a is approached the some O1 (L1＜L2) with the bolt on rocker 27 1 sides most.As shown in figure 18, alphabetical L1 represents the distance between the middle position of an O1 and pusher 60a.Letter L2 represents the distance between the middle position of an O1 and pusher 80a.
Similarly, shown in Fig. 4～6 and Fig. 9～11, connect bearing 135 and be formed on the base part 131 to connect pusher 60a, 70a and the 80a among the rocker lid 130a (being located between the cylinder).Connect bearing 135 and be arranged to be located immediately at the top of the bearing 65 in the driven rocking arm 60 of low speed side cam, the top that is located immediately at the top of the bearing 75 in the driven rocking arm 70 of high-speed side cam and is located immediately at the bearing 85 in the driven rocking arm 80 of exhaust side cams respectively.Connect in the bearing 135 at each, support 139 is arranged so that extruder member 131a protrudes from the downside of rocker lid 130b.
The extruder member 131a that protrudes butt flexibly on bearing 65, bearing 75 and bearing 85, thus elastic force is applied on the driven rocking arm 60 of cam.This elastic force makes the driven rocking arm 60 of cam press to low speed intake cam 33.Elastic force is applied on the driven rocking arm 70 of cam, thereby makes the driven rocking arm 70 of cam press to high speed intake cam 30.Elastic force is applied on the driven rocking arm 80 of cam, thereby makes the driven rocking arm 80 of cam press to exhaust cam 32.
So in the pusher linkage structure, driven rocking arm 60 of Lower speed cam and the driven rocking arm 70 of High speed cam are arranged on two sides, the driven rocking arm 80 of exhaust cam is arranged between driven rocking arm 60 of Lower speed cam and the driven rocking arm 70 of High speed cam.As shown in figure 18, among pusher 60a, the pusher 70a and pusher 80a on being connected in same rocker lid 130a, use the layout of pusher linkage structure and bearing 65, bearing 75 and bearing 85, what pusher 60a was provided with more approaches the immovable point that rocker covers 131a than pusher 70a and pusher 80a (the little of duty ratio pusher 60a is set).In the case, pusher 60a is arranged to approach most the some O2 (L3＜L4＜L5) with bolt.Letter L3 represents the distance between the middle position of an O2 and pusher 60a.Letter L4 represents the distance between the middle position of an O2 and pusher 70a.Letter L5 represents the distance between the middle position of an O2 and pusher 80a.This structure is applicable to each cylinder 3 among the left bank 7a.
Each rocking arm module 20 among the right row 7b among the variable valve system 17b has this structure, wherein removes member and the parts that actuating valve do not had contribution in the intake rocker module 18 from left bank 7a.
Though show that in structure, low speed side switching construction (mainly comprising the driven rocking arm 60 of handover operation part 40a and cam) is omitted, and valve drives rocking arm 35 always directly by 33 drivings of low speed intake cam.So,, between low-speed mode and fast mode, can carry out the switching of two stages though only kept the high speed switching construction.
Exhaust side has a kind of structure, and wherein, the exhaust rocker arm module from left bank 7a is removed the not member and the parts of actuating valve, that is, wherein unique valve drives the structure that rocking arm 90 is always directly driven by exhaust cam 32.
On the other hand, shown in Fig. 1～3, the oil control valve 120 (hereinafter to be referred as OCV 120) that is used for the cylinder park mode is arranged on the front end of left bank 7a.The oil control valve 121 (hereinafter to be referred as OCV 121) that is used for fast mode is arranged on the rear end of right row 7b.
As Fig. 3, Fig. 5 and shown in Figure 7, be used for the cylinder park mode OCV 120 discharge portion through path 153 and be formed on cylinder head 6 (left bank 7a) on rocker 27 in oil circuit 27a (exhaust side) be communicated with.
Oil circuit 26a in the rocker 26 is communicated with loop 153a on being formed on cylinder head 6.The discharge portion that is used for the OCV 121 of fast mode is communicated with oil circuit 26b (left side 7b) in the air inlet side rocker (not shown).As shown in Figure 3, the discharge portion among the OCV 121 is communicated with oil circuit 26b in the rocker 26 (air inlet side) through relay pipe member 155, and inlet 156a is formed on the cylinder head 6 among the left bank 7a, and path 156 is communicated with the 156a that enters the mouth.So, form two kinds of pressurized oil systems between " fast mode " and " cylinder park mode ", to switch.OCVs 120 and 121 as two kinds of oil pressure supply systems is connected on the control unit 122 (by forming as microcomputer).Control unit 122 is according to the predefined figure work of depending on engine operating state.According to its effect, in the desired speed scope (drive condition usually) of the normal operation of motor, OCVs 120 and 121 is " closing ", having OCV 121 only when surpassing the motor high engine speed range of desired speed scope " opens ", and when motor is in the cylinder suspension scope of the stable operation condition that satisfies little output, has OCV 120 only and " open ".
So air inlet side switching mechanism 69a and 79a and exhaust side switching mechanism 97 switch in these patterns according to engine operating status.Specifically, air inlet side switching mechanism 69a among the left bank 7a and 79a switch between low-speed mode, fast mode and cylinder park mode.In low-speed mode, moving through the driven rocking arm 60 of Lower speed cam (being used for air inlet) of low speed intake cam 33 is delivered to valve driving rocking arm 35 until the desired speed scope that reaches motor.In fast mode, high engine speed range from the motor that surpasses predetermined speed range, moving through the driven rocking arm 70 of High speed cam of high speed intake cam 30 is delivered on the valve driving rocking arm 35, and disconnects the transmission of the driven rocking arm 60 of Lower speed cam (being used for air inlet).In the cylinder park mode, not moving of cam is delivered on the valve driving rocking arm 35 from driven rocking arm 60 of Lower speed cam and the driven rocking arm 70 of High speed cam.Low-speed mode and fast mode are transfer mode.
Exhaust side switching mechanism 97 switches between transfer mode and cylinder park mode.In transfer mode, moving through the driven rocking arm 80 of cam (being used for exhaust) of exhaust cam 32 is delivered on the valve driving rocking arm 90 until the high engine speed range that reaches motor.In the cylinder park mode, disconnect the transmission of the driven rocking arm 80 of cam.
Obviously, the air inlet side switching mechanism (not shown) among the right row 7b is switched between low-speed mode and fast mode.In low-speed mode, suction valve by the mobile driving of low speed intake cam until the desired speed scope that reaches motor.In fast mode, from surpassing the motor high engine speed range of desired speed scope, suction valve is driven by the mobile of high speed intake cam.
Action with reference to Fig. 3, Fig. 7 and Fig. 9～12 pair variable valve system 17 is described.
Suppose that the order that will carry out low-speed mode according to the running state of motor offers 122.Then, OCVs 120 and 121 controlled unit 122 are closed.That is to say that the oil pressure supply system does not act on oil pressure on oil circuit 26a, 26b and the 27a.Operation window 44 among the handover operation part 40a (air inlet) among the left bank 7a is closed, and is promptly sealed by the piston shown in solid line among Fig. 9 46 (by the elastic force of pressure spring 47).
Shown in solid line among Figure 10, the operation window 50 among the handover operation part 40b (air inlet) be opened (elastic force that is compressed spring 54).As shown in figure 11, the operation window 100 in the handover operation part 98 (exhaust) among the left bank 7a is sealed by piston 102 (being compressed the elastic force of spring 103).
Then, in left bank 7a, cam follower rocking arm 70 (at a high speed) shakes, simultaneously impinging air.Because the driven rocking arm 70 of cam is pushed device 70a pushing.The driven rocking arm 80 of driven rocking arm 60 of air inlet side cam (low speed) and exhaust side cams shakes, and distinguishes butt piston 46 and 102 simultaneously.
The driven rocking arm 60 of cam and 80 is driven by the elastic force of valve spring and the elastic force of pusher 60a and 80a respectively, pushes down intake cam 30 and exhaust cam 32 simultaneously.
So in left bank 7a, moving through rocking arm 37 of intake cam 33 (low speed) drives the rod end that is delivered to suction valve 13a and 13b the rocking arm 35 from valve, to drive suction valve 13a and 13b.Moving through arm 93 of exhaust cam 32 drives the rod end that link arm 95 rocking arm 90 is delivered to outlet valve 15a and 15b from valve, to drive outlet valve 15a and 15b.
On the air inlet side of right side row 7b, as left bank 7a, the mobile of low speed intake cam that only will be delivered on the valve driving rocking arm is delivered on the suction valve, to drive suction valve.On exhaust side, moving through valve driving rocking arm (not shown) and arm (not shown) of exhaust cam (not shown) is directly delivered on the outlet valve (not shown), to drive outlet valve.
So motor promptly, in normal mode, is driven until the desired speed scope that reaches motor by Lower speed cam among Figure 17 and exhaust cam jointly with normal operation mode work.
When the speed range of motor because of the required operation of height output such as acceleration uprises so that when surpassing its desired speed scope, control unit 122 is only opened the OCV 121 that is used for fast mode.This makes the oil pressure can be on pipe component 155 is delivered to oil circuit 26a and the oil circuit in the air inlet side rocker among the right row 7b among the left bank 7a.
Oil pressure is applied on the pin 55 of the handover operation part 40b (air inlet side) among left bank 7a or the right row 7b.So piston 53 is driven upwards by pin 55, and piston 53 is shelved operation window 50 become shown in long double dot dash line staggered among Figure 10.
Then, shown in the staggered long double dot dash line among Fig. 9, the driven rocking arm 70 of air inlet side cam among left bank 7a and the right row 7b shakes, simultaneously butt piston 53.
Because the external shape greater than low speed intake cam 33 that the external shape of high speed intake cam 30 is set, so the moving from valve driving rocking arm 35 of intake cam 30 (being used at a high speed) that only is delivered in the driven rocking arm 70 of cam is delivered to suction valve 13a and 13b.That is to say that suction valve 13a and 13b are only driven by high speed intake cam 30.The driven rocking arm 60 of cam is pushed device 60a and presses to intake cam 60.
The moving of exhaust cam 32 is delivered to valve from the driven rocking arm 80 of cam and drives on the link arm 95 rocking arm 90, to drive the outlet valve 15a of left bank 7a continuously.Outlet valve among the right row 7b is with the move mode operation identical with above-mentioned low-speed mode.So motor switches to the fast mode that is produced by High speed cam among Figure 17 and exhaust cam acting in conjunction.
In the fast mode running, the big elastic force that does not need pusher 70a and 80a, this be because the reaction force of the valve spring among suction valve 13a and 13b and outlet valve 15a and the 15b as this power with pushing driven rocking arm 70 of High speed cam and the driven rocking arm 80 of exhaust cam.
On the other hand, during high engine speed range, the elastic force of pusher 60a is configured to high load, and this is because the driven rocking arm 60 of cam is only driven by the elastic force of pusher 60a.
So, normally, based on the structure that is easy to make and cost is low, sometimes make rocker lid 130a and 130b bending by the elastic force of setting pusher 60a, have on the rocker lid 130a and 130b that limits size thereby simply pusher 60a is arranged to this moment make abreast or obliquely pusher 60a to be arranged on pusher 70a and 80a.
Be located between the cylinder and rocker lid 130a is located in the terminal both of these case of cylinder at rocker lid 130a, compare with 80a with pusher 70a, the pusher 60a of the extruding driven rocking arm 60 of cam (low speed) is arranged to more to approach the immovable point among rocker lid 130a and the 130b, and promptly rocker lid 130a and 130b are fixed to some O1 and the some O2 on the cylinder head 6.
That is to say that pusher 60a is arranged to points of proximity O1 and some O2 as far as possible.When pusher 60a was arranged to approach an O1 and some O2, it was loaded greater than the load on pusher 70a and the 80a, and pusher 60a is bearing on the position of approaching the immovable point among rocker lid 130a and the 130b most, thereby it is bent hardly.
So in this simple structure, pusher 60a is arranged to approach immovable point, the pushing force of pusher 60a makes the driven rocking arm 60 of cam can suitably push down intake cam 33 and do not shake.
When motor enters the running state that fuel consumption reduces, i.e. middling speed operation area, control unit 122 is carried out cylinder park modes (in order to reduce the pattern of fuel consumption).That is to say, as shown in Figure 3, thereby control unit 122 control and only open the OCV 120 that is used for the cylinder park mode, so the oil pressure of introducing from OCV 120 is delivered to oil circuit 27a in the rocker 27 (exhaust side) through passage 153.Oil pressure among the oil circuit 27a is delivered to the oil circuit 26a in the rocker 26 (air inlet side) among the left bank 7a.
In oil circuit 26a, the area of path increases hardly, and this is because oil circuit 26a is formed on the rocker 26 with oil circuit 26b (less than oil circuit 27a).Therefore, in air inlet side rocking arm 18a, its handover operation obviously lags behind exhaust side rocking arm 18.
As shown in Figure 3, because oil circuit 27a communicates with each other with a plurality of parallel oil circuits 140 with oil circuit 26a, so the oil pressure that is delivered among the oil circuit 27a transmits along front portion, middle part and the rear portion of direction shown in Fig. 3 arrow in oil circuit 27a through a plurality of oil circuits 140.So oil pressure can be delivered to the various piece (the less area of passage with qualification) among the oil circuit 26a rapidly from oil circuit 27a.
So, operation window 44 among the air inlet side handover operation part 40a was opened by oil pressure (by the piston 46 that risen) with the essentially identical moment of exhaust side, promptly with exhaust side handover operation part 40b in essentially identical moment in the moment of being opened because of the rising of piston 104 of operation window 100.Operation window 50 does not act on handover operation part 40b be opened (Figure 10) because of oil pressure.As shown in figure 10, on exhaust side, the piston 104 in the handover operation part 98 is driven upwards by the pin 104 that rises.This can make the operation window 100 in the handover operation part 98 open.
In the essentially identical moment, the driven rocking arm 60 of the cam among the left bank 7a (air inlet: low speed) and the driven rocking arm 80 of cam (exhaust) switch to and shake drive pattern, driven rocking arm 60 of its cam and 80 impinging airs.The driving force that is used for actuating valve is not delivered to valve and drives rocking arm 35 and 90 (air inlet and exhaust).So, as shown in figure 12, because the slide block 41 and 96 that valve drives in the rocking arm 35 and 90 slides on the camming surface of non-lift cam 31 continuously, so suction valve 13a and 13b and outlet valve 15a and 15b keep closed condition (cylinder park mode).
At this moment, in the air inlet variable valve device 20 and exhaust variable control valve unit 21 in the row 7b of the right side, as with low-speed mode, moving of low speed intake cam is delivered on the suction valve continuously, moving of exhaust cam is delivered on the outlet valve continuously, thus the cylinder park mode that entering part cylinder (cylinder among the left bank 7a) is draped.
When motor when the cylinder park mode switches to low-speed mode or fast mode, driven rocking arm 60 of the cam among the left bank 7a and the driven rocking arm 80 of cam switched in the essentially identical moment.
Therefore, the use of trapezoidal oil circuit 146 has improved the hysteresis effect by the rocking arm 18a (air inlet side) of the control of the oil pressure among the oil circuit 26a, thereby improves the performance of handoffs of rocking arm 18a significantly.
So in the cylinder park mode, the initial point that is caused by the restriction of oil circuit 26a and the fluctuation of terminal point are suppressed, thereby the noise and the vibrations that produce because of this fluctuation also are suppressed.In addition, because of fluctuation is suppressed, so can enlarge the scope (second pattern) of cylinder park mode.
The oil circuit 26a and the 27a that are formed on rocker 26 and 27 communicate with each other in echelon through a plurality of oil circuits 140 (relaying oil circuit), and oil pressure promptly is delivered to the various piece among oil circuit 26a and the 27a, thereby makes rocking arm 18a and 18b be applied the oil pressure actuated on oily passage 26a and 27a and switch in the essentially identical moment.
So the hysteresis effect and the switching fluctuation of the switching reaction among the rocking arm 18a are suppressed.Especially, switch the improvement of reacting and prevent lasting reliability variation.Lasting reliability is variation with the increase of wearing and tearing in the switching part, and this is because of having been applied bigger load by valve stroke on the switching part that is under the incomplete switching state.
Because in the handoff procedure of the cylinder park mode that engine operating status lift cam generation therein greatly changes change greatly takes place, need to switch with control air fuel ratio and ignition timing synchronously.Cause under the less fluctuation in the switching reaction, can switch synchronously with control air fuel ratio and ignition timing.So in comprising the burning that misfires, bigger fluctuation is suppressed, thereby obtain low fuel consumption, this moment, the reduction or the waste gas of operability were suppressed.
In this structure, trapezoidal oil circuit 146 is formed by rocker lid 130a and 130b, therefore, produce and invest the structure on the cylinder block 6 respectively with assembly wherein or only compared by the structure that the technology in the cylinder head 6 forms with wherein all oil circuits, the cost of production of trapezoidal oil circuit 146 with this simple structure is lower.
With reference to Figure 20, second embodiment of the invention variable valve device is described.This mode of execution is an improved embodiment in first mode of execution.Pusher 60a is arranged in the layout between two immovable point O3 and the O4 (the 130a bolt is covered at its place fixedly rocker of air inlet rocker 26 and exhaust rocker) within it, pusher 60a is arranged to that (L8＜L6＜L7) more approaches (in the case, being the some O3 on rocker 27 sides) in these points than pusher 70a and 80a.In second mode of execution, also can obtain identical effect as first mode of execution.
Yet, in Figure 20, with assembly identical in first mode of execution with identical figure denote, and omit explanation.Letter L8 represents the distance between the middle position of an O3 and pusher 60a.Letter L6 represents the distance between the middle position of an O4 and pusher 70a.Letter L7 represents the distance between the middle position of an O3 and pusher 80a.
The invention is not restricted to above-mentioned mode of execution, and can in not departing from the scope of the present invention, carry out various improvement.In the above-described embodiment, the present invention is applied to V-type motor.Yet the present invention can be applied in the in line engine (in-line typeengine), and the layout of its inside cylinder is different from V-type motor and the DOHC h type engine h that rocker wherein is divided into air inlet rocker and exhaust rocker (not shown).
In the above-described embodiment, first mode initialization is the cylinder park mode.Alternatively, first pattern can also be set at fast mode.In the above-described embodiment, the present invention is applied to be furnished with on the air inlet side in the motor of three-mode variable valve device.Alternatively, the present invention can be applied to be furnished with on exhaust side in the motor of three-mode variable valve device or all be furnished with the motor of three-mode variable valve device on air inlet side and exhaust side.The present invention can also be applied to all be furnished with on air inlet side and exhaust side in the motor of two modes variable valve device.
For example, the rocker lid is fixed by fixed structure, and exhaust side is fixing by two bolt points in this structure, and the air inlet side is fixing by a bolt point.Be arranged to approach the said fixing point for the biased pusher of the driven rocking arm of Lower speed cam.The invention is not restricted to aforesaid way.Alternatively, pusher can be arranged to approach with the immovable point in the fixing rocker lid of another fixed structure or another fixed unit.
In mode of execution, Lower speed cam and High speed cam only are located on the air inlet side.Optionally, Lower speed cam and High speed cam only are arranged on the exhaust side or are located on air inlet side and the exhaust side, can be arranged to more approach immovable point than other pushers for the biased pusher of the driven rocking arm of Lower speed cam.
Other advantage and improvement are expected easily to the person skilled in the art.Therefore, the present invention is not limited to typical embodiment described herein and details with regard to the aspect of broad.Therefore, under the situation of aim that does not break away from the defined total inventive concept of appended claim and equivalents thereof and scope, can carry out various improvement.
Claims (6)
1. a variable valve device for internal combustion engine is characterized in that, comprising:
Camshaft is arranged in the body of internal-combustion engine rotationally;
A pair of rocker is close to described camshaft setting;
Suction valve is by the rotation driving of described camshaft;
Outlet valve is by the rotation driving of described camshaft;
The first hydraulic pressure rocking arm, can joltily support by one in the described rocker, and the described first hydraulic pressure rocking arm can be at least at drive condition usually be different from one the driving of switching between first pattern of described common drive condition in described suction valve and the described outlet valve;
The second hydraulic pressure rocking arm, can joltily support by in the described rocker another, and the described second hydraulic pressure rocking arm can be at least at described common drive condition be different from another the driving of switching between described first pattern of described common drive condition in described suction valve and the described outlet valve;
First switches oil circuit, is formed on vertically in the described rocker, and oil pressure switches oil circuit via described first and is applied on described first rocking arm, makes described first rocking arm switch to described first pattern; With
Second switches oil circuit, is formed on vertically in the described rocker another, and oil pressure switches oil circuit via described second and is applied on described second rocking arm, makes described second rocking arm switch to described first pattern,
A plurality of relaying oil circuits, be communicated with described first and switch oil circuit and the described second switching oil circuit, described first switches oil circuit, the described second switching oil circuit and described relaying oil circuit forms with scalariform, and described a plurality of relaying oil circuits are delivered to described first various piece of switching in the oil circuit rapidly with described second oil pressure that switches in the oil circuit.
2. variable valve device for internal combustion engine as claimed in claim 1 is characterized in that, each in the described a pair of rocker is fixed on the described internal-combustion engine by the rocker lid, and described rocker lid has the shape that described rocker is crossed in stretching, extension, and
Described relaying oil circuit is formed in the described rocker lid.
3. variable valve device for internal combustion engine as claimed in claim 1, it is characterized in that, also be included in the 3rd switching oil circuit that form at least one in the described rocker, the described first switching oil circuit of next-door neighbour, oil pressure switches oil circuit via the described the 3rd and is applied to described first rocking arm, make described first rocking arm switch to second pattern, described second pattern is different from described common drive condition and described first pattern.
4. variable valve device for internal combustion engine as claimed in claim 2, it is characterized in that, described camshaft is provided with intake cam and exhaust cam, described intake cam drives described suction valve with the described first rocking arm butt time, described exhaust cam drives described outlet valve with the described second rocking arm butt time, and
Cover at described rocker and to be provided with a plurality of pushers, described pusher utilizes elastic force that described first rocking arm and described second rocking arm are pressed on the described cam.
5. variable valve device for internal combustion engine as claimed in claim 4 is characterized in that, described intake cam comprises low speed intake cam and high speed intake cam,
Described first rocking arm comprises:
The suction valve that drives described suction valve drives rocking arm;
Follow the driven rocking arm of a pair of intake cam of described low speed intake cam and described high speed intake cam respectively; With
The air inlet switching unit that can between described common drive condition, second pattern and described first pattern, switch; Under described common drive condition, in the driven rocking arm of described intake cam one of moving of described low speed intake cam is delivered to described suction valve and drives on the rocking arm, until the desired speed scope that reaches described internal-combustion engine; Under described second pattern, surpass described desired speed scope from the high engine speed range of internal-combustion engine, disconnection is from one transmission in the driven rocking arm of described intake cam, and in the driven rocking arm of described intake cam another of moving of described high speed intake cam was delivered to described suction valve and drove rocking arm this moment; Under described first pattern, not moving of described cam is passed to described suction valve driving rocking arm from driven rocking arm of described low speed intake cam and the driven rocking arm of described high speed intake cam,
Described second rocking arm comprises:
The outlet valve that drives described outlet valve drives rocking arm;
Follow the driven rocking arm of a pair of exhaust cam of described exhaust cam; With
The exhaust switching unit that can between described common drive condition and described first pattern, switch; Under described common drive condition, moving through the driven rocking arm of described exhaust cam of described exhaust cam is delivered to described outlet valve driving rocking arm; Under described first pattern, disconnect the transmission that drives rocking arm from described outlet valve, and
Compare with the pusher of the driven rocking arm of the described exhaust cam of extruding, one the pusher that pushes in the driven rocking arm of described intake cam is arranged to more approach the immovable point that described rocker covers.
6. variable valve device for internal combustion engine as claimed in claim 5, it is characterized in that, be provided with a plurality of pushers in the described rocker lid, described pusher utilizes elastic force that another and the driven sub rocker arm don't push of described exhaust cam among one in the driven rocking arm of described intake cam, the driven rocking arm of described intake cam are pressed on described low speed intake cam, described high speed intake cam and the described exhaust cam, and
Compare with the described pusher of the driven rocking arm of described exhaust cam with the driven rocking arm of described another intake cam of extruding, one the described pusher that pushes in the driven rocking arm of described intake cam is configured to more approach the immovable point that described rocker covers.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006089144 | 2006-03-28 | ||
| JP2006089144A JP4556898B2 (en) | 2006-03-28 | 2006-03-28 | Variable valve operating device for internal combustion engine |
| JP2006-089145 | 2006-03-28 | ||
| JP2006-089144 | 2006-03-28 | ||
| JP2006089145 | 2006-03-28 | ||
| JP2006089145A JP4487964B2 (en) | 2006-03-28 | 2006-03-28 | Variable valve operating device for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101046167A CN101046167A (en) | 2007-10-03 |
| CN101046167B true CN101046167B (en) | 2010-05-26 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200710093612XA Expired - Fee Related CN101046167B (en) | 2006-03-28 | 2007-03-28 | Variable valve device for internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4556898B2 (en) |
| CN (1) | CN101046167B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5422181B2 (en) * | 2008-11-25 | 2014-02-19 | ヤマハ発動機株式会社 | Variable valve operating apparatus, engine apparatus equipped with the same |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4535732A (en) * | 1983-06-29 | 1985-08-20 | Honda Giken Kogyo Kabushiki Kaisha | Valve disabling device for internal combustion engines |
| CN1598253A (en) * | 2003-09-18 | 2005-03-23 | 三菱自动车工业株式会社 | Valve device with cylinder stop mechanism of ic engine |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2842062B2 (en) * | 1992-07-16 | 1998-12-24 | 三菱自動車工業株式会社 | In-vehicle structure of engine with cylinder-stop mechanism |
| JP3601837B2 (en) * | 1992-11-16 | 2004-12-15 | 三菱自動車工業株式会社 | Fuel control system for engine with cylinder-stop mechanism |
| JPH07180523A (en) * | 1993-11-10 | 1995-07-18 | Nissan Motor Co Ltd | Lubricating device for internal combustion engine |
| JPH06299807A (en) * | 1994-03-23 | 1994-10-25 | Mitsubishi Motors Corp | Structure of cylinder head |
| JP4143842B2 (en) * | 2003-09-18 | 2008-09-03 | 三菱自動車エンジニアリング株式会社 | Valve train with internal cylinder mechanism for internal combustion engine |
-
2006
- 2006-03-28 JP JP2006089144A patent/JP4556898B2/en not_active Expired - Fee Related
-
2007
- 2007-03-28 CN CN200710093612XA patent/CN101046167B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4535732A (en) * | 1983-06-29 | 1985-08-20 | Honda Giken Kogyo Kabushiki Kaisha | Valve disabling device for internal combustion engines |
| CN1598253A (en) * | 2003-09-18 | 2005-03-23 | 三菱自动车工业株式会社 | Valve device with cylinder stop mechanism of ic engine |
Non-Patent Citations (3)
| Title |
|---|
| JP特开2004-197588A 2004.07.15 |
| JP特开2005-105953A 2005.04.21 |
| JP特开2005-90408A 2005.04.07 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101046167A (en) | 2007-10-03 |
| JP2007262987A (en) | 2007-10-11 |
| JP4556898B2 (en) | 2010-10-06 |
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