CN101189413A - Variable valve apparatus - Google Patents
Variable valve apparatus Download PDFInfo
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- CN101189413A CN101189413A CNA200680020004XA CN200680020004A CN101189413A CN 101189413 A CN101189413 A CN 101189413A CN A200680020004X A CNA200680020004X A CN A200680020004XA CN 200680020004 A CN200680020004 A CN 200680020004A CN 101189413 A CN101189413 A CN 101189413A
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- 238000013019 agitation Methods 0.000 claims description 23
- 230000008859 change Effects 0.000 claims description 22
- 239000003607 modifier Substances 0.000 claims description 15
- 239000000446 fuel Substances 0.000 claims description 7
- 230000007246 mechanism Effects 0.000 abstract description 67
- 230000008878 coupling Effects 0.000 abstract description 2
- 238000010168 coupling process Methods 0.000 abstract description 2
- 238000005859 coupling reaction Methods 0.000 abstract description 2
- 230000033001 locomotion Effects 0.000 description 18
- 230000009977 dual effect Effects 0.000 description 12
- 230000000875 corresponding effect Effects 0.000 description 11
- 239000002360 explosive Substances 0.000 description 8
- 230000002093 peripheral effect Effects 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000010304 firing Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000009987 spinning Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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Abstract
An arm coupling mechanism 72 is provided as changing means for selectively switching double valve variable control and single valve variable control. The single valve variable control is achieved in a condition, in which a large lift arm 70 and a second rocking cam arm 40R are coupled together with a pin 76. The second rocking cam arm 40R for moving a second valve 16R includes a pin hole 80, in which the pin 76 is inserted, formed therein. The position of the pin hole 80 is set so that a pin switching operation can be executed when control is provided to achieve an operating angle, at which the single valve variable control is to be started for reduced NOx. A second driving cam 14 is adapted to have a cam height greater than a cam height of a first driving cam 12.
Description
Technical field
The present invention relates to a kind of variable valve gear, relate more specifically to a kind of variable valve gear that is used for the valve opening characteristic that can mechanically change valve of explosive motor.
Background technique
For example patent documentation 1 has disclosed the variable valve gear of the valve opening characteristic that can mechanically change valve that is used for explosive motor.On the single camshaft of this variable valve gear, be fixed with two rotating cams: first rotating cam and second rotating cam.Just be arranged at two intake valves in the single cylinder---first intake valve and second intake valve, first rotating cam drives opens or closes first intake valve, and second rotating cam drives opens or close second intake valve.The variable lift valve operating mechanism that comprises quadratic crank mechanism places between first rotating cam and first intake valve and between second rotating cam and second intake valve separately.
The quadratic crank mechanism of variable lift valve operating mechanism comprises four primary components: input arm, transmission arm, rocking arm and control arm.The input arm comprises the input part in abutting connection with rotating cam.Transmission arm is coupled to the input arm in the mode that can shake.When being coupled to transmission arm in the mode that can shake, rocking arm can also shake around the Spin Control axle, is delivered to the output of opening or closing intake valve with the driving force that will transmit the spinning cam.With driven while of the mode that can rotate, control arm can also be coupled to the input arm in the mode that can shake around the Spin Control axle.Can mechanically change the valve opening characteristic of intake valve by the pose of control quadratic crank mechanism, thereby change the position of rotating cam with respect to the input part.
Above-mentioned conventional variable valve gear also comprises selection mechanism, be used for controlling method with the valve opening characteristic of second intake valve from variable control break to fixing control, perhaps from fixing control break to variable control.More specifically, variable valve gear comprises and is coupled mechanism that the quadratic crank mechanism (first connecting rod mechanism) that it will be relevant with first intake valve is coupled to the quadratic crank mechanism (second connecting rod mechanism) relevant with second intake valve.Variable valve gear also comprises another mechanism, is used for pose with second connecting rod mechanism and remains on when being coupled when throwing off and make the operation angle of second intake valve become the pose of maximum value or minimum value.Be coupled interior through hole that extends of control arm and the pin that is coupled that is inserted in the through hole that mechanism is included in each quadratic crank mechanism.Be used for being coupled through hole and the above-mentioned pin that is coupled that the mechanism that keeps the pose of second connecting rod mechanism when throwing off is included in extension in the through hole that extends in the fixed plate, the control arm (second control arm) in second connecting rod mechanism.
Be coupled pin and always engage the interior through hole of second control arm.In the through hole that keeps engaging in second control arm, being coupled pin can be towards control arm (first control arm) side or the fixed plate side shifting of first connecting rod mechanism.When being coupled pin and shifting to the first control arm side and inject the through hole of first control arm, second control arm is coupled to first control arm by being coupled pin.When first and second control arms were coupled together, first connecting rod mechanism always presented identical pose with second connecting rod mechanism.Therefore, in this case, first and second valves can be controlled to be has identical valve opening characteristic.
On the other hand, when being coupled pin to the fixed plate side shifting and when injecting through hole in the fixed plate, second control arm is coupled to fixed plate by being coupled pin.When second control arm was coupled to fixed plate, second connecting rod mechanism was fixed to predetermined pose.In this case, the Pose Control of first connecting rod mechanism is for can change the pose of rotating cam with respect to the input part.This only allows mechanically to change the valve opening characteristic of first valve, and the valve opening characteristic of duaspiracle is fixed.
Particularly, according to above-mentioned variable valve gear, can optionally carry out in two kinds of different control modes any one, that is, first intake valve and second intake valve have the control mode (the variable control of single valve) that has the different air valve opening feature between the control mode (the variable control of dual valve) of identical valve opening characteristic or first intake valve and second intake valve.Therefore, change the valve opening characteristic between first intake valve and second intake valve, perhaps particularly, the lift that changes between two valves can make charge flow rate change.This produces swirling flow in the firing chamber, thus the indoor burning of smooth combustion.
The applicant learns that the following document that comprises above-mentioned document is as prior art of the present invention.
The open No.2004-100555 of [patent documentation 1] Japan Patent
Summary of the invention
According to the mechanism of prior art, it is configured to, and when the variable control of dual valve switched to the variable control of single valve, second connecting rod mechanism temporarily presented the maximum value of the operation angle that realizes second intake valve or the pose of minimum value via current operation angle.This method means that when control mode was switched, the operation angle that must control in the current operating range controlled to its maximum value or minimum value between variable control of dual valve and the variable control of single valve.In addition, select new control mode after, first intake valve of variable control is moved to produce charge flow rate between these intake valves has the required lift of heterodyne.
Like this, switch to the variable control of single valve from the variable control of dual valve and need a certain amount of time.In addition, when switching, also need control ignition timing and fuel injection amount to stand any unexpected change with the moment of torsion that prevents explosive motor.This makes the Economy variation of fuel.But, in the mechanism of prior art, do not consider shortening handover operation time aspect.Indented material also has the leeway of research.
Make the present invention to address the above problem, the purpose of this invention is to provide a kind of variable valve gear, it allows the valve opening characteristic of valve is controlled to fixing from variable control break, perhaps from fixing control break to variable control, and it can realize the rapid handover operation between two kinds of control modes.
Above-mentioned purpose realizes by a kind of variable valve gear, the control of the valve opening characteristic of at least one valve that will be switched in wherein a plurality of valves under from the control break under the variable control mode to fixing control mode control or from the control break under the fixing control mode to variable control mode under control.Described variable valve gear comprises agitation member, and it is arranged between main cam and the described valve, and described agitation member arrives described valve with the propagation of pressure of described main cam.Valve opening characteristic variset is provided, its be used for Pose Control with described agitation member in prespecified range to control the valve opening characteristic of the described valve that will be switched changeably.Valve opening characteristic fixing device also is provided, and it controls the valve opening characteristic of the described valve that will be switched with being used for fixing.Modifier also is provided, and it is used for that the control of the valve opening characteristic of the described valve that will be switched is switched to control under the described fixedly control mode or the control under the described fixedly control mode from the control under the described variable control mode and switches to control under the described variable control mode.Described modifier is arranged to, and the valve opening characteristic that allows the described valve that will be switched is under the pose relevant with the operating range of the valve opening characteristic that needs to switch the described valve that will be switched in described agitation member and changes.
In a second aspect of the present invention, the operating range of switching the valve opening characteristic of the described valve that will be switched according to the described needs of first aspect present invention comprises low engine speed range or the low-load range that is used to reduce NOx or improves fuel economy.
In a third aspect of the present invention, described valve opening characteristic variset comprises the control gear that is arranged at the intermediate member between described main cam and the described valve that will be switched and is used to change the position of described intermediate member.Described intermediate member is shared by the described a plurality of valves that comprise the described valve that will be switched.Second cam that separates with described main cam also is provided.Described valve opening characteristic fixing device comprises the input arm that the rotation homophase with described second cam shakes.Described modifier makes being coupled between the described agitation member be used for moving the described valve that will be switched and the described input arm engage or throws off.Described second cam is arranged to have the cam height bigger than described main cam.
In a fourth aspect of the present invention, described modifier is arranged so that, the operating range of valve opening characteristic of switching the described valve that will be switched when needs is in prespecified range the time, when being in, described agitation member realizes that the valve opening characteristic of the described valve that will be switched can be switched under the minimum operation angle and/or the situation of the pose of minimum lift of the described valve that will be switched in described prespecified range.
In a fifth aspect of the present invention, described modifier is arranged so that, the operating range of valve opening characteristic of switching the described valve that will be switched when needs is in prespecified range the time, when being in, described agitation member realizes that the valve opening characteristic of the described valve that will be switched can be switched under the maximum operation angle and/or the situation of the pose of maximum lift of the described valve that will be switched in described prespecified range.
In a sixth aspect of the present invention, described valve opening characteristic variset comprises the control gear that is arranged at the intermediate member between described main cam and the described valve that will be switched and is used to change the position of described intermediate member.Described intermediate member is shared by the described a plurality of valves that comprise the described valve that will be switched.Second cam that separates with described main cam also is provided.Described valve opening characteristic fixing device comprises the input arm that the rotation homophase with described second cam shakes.Described modifier comprises pin, and described modifier makes described pin being coupled between the described agitation member that is used for moving the described valve that will be switched and described input arm engage or throws off.The described agitation member or the described input arm that are used for the mobile described valve that will be switched comprise pin-and-hole, and described pin inserts in the described pin-and-hole.The intake section of described pin-and-hole comprises guiding surface, and described guiding surface forms and is used to guide the described pin that inserts or shift out described pin-and-hole.
In a seventh aspect of the present invention, described guiding surface has the tilt angle with respect to the axis of described pin-and-hole, and described tilt angle diminishes towards the intake section of described pin-and-hole.
In a eighth aspect of the present invention, the profile of described second cam is arranged so that the phase place of the described valve that will be switched that described second cam is realized is different from the valve-control that is realized by described main cam.
According to first aspect present invention, compare with the situation that switch at maximum value in the valve opening characteristic variable range of the valve that will be switched or minimum value place, shortened the required time of handover operation effectively.
The operating range of switching the valve opening characteristic of the described valve that will be switched when needs is in order to reduce NOx or to improve the low engine speed range of fuel economy or during low-load range, if switch at maximum value or minimum value place in the variable range of the valve opening characteristic of the valve that will be switched, then the required time of handover operation will be longer.According to second aspect present invention, this operating time can be shortened effectively.
If intermediate member is shared by a plurality of valves that comprise the valve that will be switched, and if select main cam as driving cam, then main cam drives these valves so that identical valve opening characteristic to be provided.In this case, suppose to attempt under agitation member is in the pose of operating range of the valve opening characteristic that needs to switch the valve that will be switched, to switch the valve opening characteristic of the valve that will be switched.If second cam has the cam height the same with main cam in this case, then can not control to value by the lift of the second cam-actuated valve that will be switched greater than the lift of other valve that drives by main cam.On the other hand, according to third aspect present invention, the existence of intermediate member does not influence the CLV ceiling limit value by the lift of the valve that will be switched of second cam control.Then, be under the pose that is used for the action required scope, can switch the valve opening characteristic of the valve that will be switched in agitation member.
According to third aspect present invention, after finishing handover operation, the lift of the valve that be switched can change to big lift immediately.In addition, according to fourth aspect present invention, the operating time that is used for after finishing handover operation other valve of variable control being controlled to enough little lift can be shortened further.
According to fifth aspect present invention, whenever, other valve except that the valve that will be switched can be compared in the small range in the operation angle of operation angle or lift and the valve that will switch in the prespecified range according to fifth aspect present invention or lift and change after the valve opening characteristic of the valve that will be switched has changed to fixing control.This has prevented to produce the gap between second cam and input arm.Therefore, during lift operation, can prevent between second cam and input arm, to produce noise or impact load.
According to sixth aspect present invention, even pin axially aligns with pin-and-hole, owing to pin is guided by guiding surface, so the rotation of agitation member is axially aligned pin and pin-and-hole.This has realized being coupled of pin.Therefore, can shorten the operating time of handover operation effectively according to the present invention.
According to seventh aspect present invention, can reduce the speed that agitation member moves when being coupled of pin thrown off.Therefore, can prevent the noise or the impact load that produces by the contact between the member during the disengagement that be coupled of shotpin according to the present invention.
According to eighth aspect present invention, do not use any mechanism that is used to change valve-control, can change the valve opening phase place of other valve that drives by the valve opening phase place of the second cam-actuated valve that will be switched with by main cam.
Description of drawings
Fig. 1 is used to illustrate be arranged on according to the driving cam of the variable valve gear of first embodiment of the invention and the view of the mechanism between the valve.
Fig. 2 illustrates the view that the variable valve actuator for air shown in Fig. 1 is seen from the axial direction of camshaft.
Fig. 3 illustrates the variable valve actuator for air shown in Fig. 1 and the fixing exploded perspective view of valve mechanism.
Fig. 4 A and 4B are the views that is used to illustrate the set positions of the inner pinhole of variable valve gear shown in Fig. 1.
Fig. 5 is the view that is used to illustrate according to the layout of the variable valve gear of second embodiment of the invention.
Fig. 6 is the plotted curve that the valve opening characteristic of the valve of being realized by variable valve gear is shown.
Fig. 7 is the view that is used to illustrate according to the modified example of the layout of the variable valve gear of second embodiment of the invention.
Fig. 8 is the plotted curve that the valve opening characteristic of the valve of being realized by variable valve gear is shown.
Fig. 9 illustrates the torque curve figure that is used for being illustrated in according to the variable valve gear of the third embodiment of the invention operating range when the variable control of fill order's valve.
Figure 10 A and 10B are the views of the problem that occurs when carrying out the pin handover operation of the little operation angle side that is used to be illustrated in the scope of the variable control of fill order's valve.
Figure 11 A and 11B are the views that is used to illustrate according to the operation when making the setting of pin handover operation of third embodiment of the invention.
Figure 12 is the view that is used to illustrate according to the layout of the variable valve gear of four embodiment of the invention.
Figure 13 is used to illustrate the sectional view that is coupled the layout of mechanism at the arm of four embodiment of the invention.
Figure 14 A and 14B illustrate the zoomed-in view of the part A of Figure 13.
Figure 15 A and 15B are the views that is used to illustrate the pin handover operation of four embodiment of the invention.
Figure 16 is the view that is used to illustrate the operation of the second oscillating cam arm during the pin handover operation.
Figure 17 is the zoomed-in view that the part A of Figure 13 is shown.
Embodiment
First mode of execution
[structure of variable valve gear]
Fig. 1 is used to illustrate be arranged on according to the driving cam of the variable valve gear 1 of first embodiment of the invention and the view of the mechanism between the valve.Here each cylinder of supposing explosive motor has two intake valves and two exhaust valves.Layout shown in Fig. 1 is as driving two intake valves being arranged in the single cylinder or the mechanism of two exhaust valves.
With reference to Fig. 1, the camshaft 10 of variable valve gear 1 provides two driving cams 12,14 for each cylinder.Two valves---the first valve 16L and duaspiracle 16R---are symmetrical arranged about one in two driving cams (first driving cam) 12.Each variable valve actuator for air 20L, 20R are arranged between first driving cam 12 and each valve 16L, the 16R.Variable valve actuator for air 20L, 20R are coupled to the lift motion of each valve 16L, 16R the rotational motion of first driving cam 12 in operation.
Another (second driving cam 14) in two driving cams is arranged so that duaspiracle 16R is interposed between first driving cam 12 and second driving cam 14.Fixedly valve mechanism 30 places between second driving cam 14 and the duaspiracle 16R.Fixedly valve mechanism 30 is coupled to the lift motion of duaspiracle 16R the rotational motion of second driving cam 14 in operation.Variable valve gear 1 is arranged so that can be at variable valve actuator for air 20R and the element of fixedly selecting the lift motion of duaspiracle 16R to be coupled between the valve mechanism 30.
(1) detailed construction of variable valve actuator for air
At first, in detail the layout of variable valve actuator for air 20L, 20R will be described with reference to Fig. 2.Fig. 2 illustrates the view that the variable valve actuator for air 20 shown in Fig. 1 is seen from the axial direction of camshaft 10.Because left and right variable valve actuator for air 20L, 20R are basically about first driving cam, 12 symmetries, so will describe left and right variable valve actuator for air 20L, 20R without distinction here.In this specification and accompanying drawing thereof, when not distinguishing left variable valve actuator for air 20L and right variable valve actuator for air 20R, this mechanism will abbreviate variable valve actuator for air 20 as.Similarly, unless be necessary to distinguish left side and right-hand side assembly, otherwise each parts of variable valve actuator for air 20L, 20R and comprise that the symmetrically arranged component of valve 16L, 16R will be called for short in the mode of subsidiary symbol L or R.
With reference to Fig. 2, in variable valve gear 1, support rocking arm 32 by valve 16.Variable valve actuator for air 20 is arranged between first driving cam 12 and the rocking arm 32, and the operation that changes continuously between the swing movement of the rotational motion of first driving cam 12 and rocking arm 32 is coupled situation.
As described in below inciting somebody to action, variable valve actuator for air 20 comprises Control Shaft 34, control arm 36, link arm 38, oscillating cam arm 40, first roller 42 and second roller 44 as its critical piece.Control Shaft 34 is set to be parallel to camshaft 10 and extends.The angle of rotation of Control Shaft 34 can control to arbitrary value by not shown mechanism (for example motor etc.).
The oscillating cam arm 40 that is supported on the Control Shaft 34 in the mode that can shake is arranged so that the upstream side of its front end towards first driving cam, 12 sense of rotation.Oscillating cam arm 40 comprises the slidingsurface 50 that is formed on the side relative with first driving cam 12.Slidingsurface 50 contacts second roller 44.Slidingsurface 50 forms curved surface, make when second roller 44 from the forward end of oscillating cam arm 40 when move in the axle center of Control Shaft 34, the spacing of distance first driving cam 12 diminishes gradually.On the side relative that oscillating cam surface 52 is formed on oscillating cam arm 40 with slidingsurface 50.Oscillating cam surface 52 comprises not operation face 52a and fore side 52b.Not operation face 52a forms apart from the constant distance at the center of shaking of oscillating cam arm 40 constant.Fore side 52b form make along with fore side 52b away from not operation face 52a, fore side 52b becomes big gradually apart from the distance in the axle center of Control Shaft 34.
The not shown sky spring of moving is hooked on the oscillating cam arm 40.The sky spring of moving is a pressure spring.Move the power forced to move of spring as allowing slidingsurface 50 second rollers 44 forced to move and making first roller 42 press the power forced to move of first driving cam 12 from sky.Therefore, first roller 42 and second roller 44 are by inserting and putting and correctly be positioned between the peripheral surface of the slidingsurface 50 and first driving cam 12 from both sides.The sky spring of moving is not limited to pressure spring; On the contrary, this spring for example can be a torsion spring.
Above-mentioned rocking arm 32 is arranged on the below of oscillating cam arm 40.Rocking arm 32 comprises is arranged to relative with oscillating cam surface 52 roller 56 that shakes.Shake roller 56 is installed in rocking arm 32 in the mode that can rotate middle part.Rocking arm 32 has first end by valve stem 58 supports of valve 16.Rocking arm 32 also has second end that is supported in the mode that can rotate by hydraulic lash adjuster 60.In lift operation, valve stem 58---is promptly upwards promoted the direction of rocking arm 32---along closing direction by not shown valve spring forced to move.In addition, by this power forced to move and hydraulic lash adjuster 60, shake the oscillating cam surface 52 that roller 56 presses oscillating cam arm 40.
According to the layout of variable valve actuator for air 20, when 12 rotations of first driving cam, the pressure of first driving cam 12 is delivered to slidingsurface 50 by first roller 42 and second roller 44.Therefore, oscillating cam surface 52 and the point of contact that shakes between the roller 56 move to fore side 52b from not operation face 52a, and then promote rocking arm 32 downwards, open valve 16.
In addition, according to the layout of variable valve actuator for air 20, the angle of swing that changes Control Shaft 34 can change second position of roller 44 on slidingsurface 50.This has changed the swing range of oscillating cam arm 40 in the lift operation.More specifically, as shown in Figure 2 when Control Shaft 34 rotates counterclockwise, second roller 44 on the slidingsurface 50 moves towards the forward end of oscillating cam arm 40.Along with the angle of the counter clockwise direction rotation of Control Shaft 34 as shown in Figure 2 increases, oscillating cam arm 40 is becoming big from oscillating cam arm 40 because the pressure of first driving cam 12 that is transmitted begins to act on the angle that needs to rotate in a period of time that rocking arm 32 ends when beginning its swing movement to actual pressure.Particularly, according to variable valve actuator for air 20, when in Fig. 2, observing, be rotated counterclockwise Control Shaft 34 operation angle of valve 16 and lift are diminished.On the other hand, when observing in Fig. 2, the Control Shaft 34 that turns clockwise makes the operation angle of valve 16 and lift become big.
(2) the fixing detailed construction of valve mechanism
Describe fixedly valve mechanism 30 in detail with reference to Fig. 1 and 3 below.
With reference to Fig. 1, fixedly valve mechanism 30 is arranged between second driving cam 14 and the second oscillating cam arm 40R.Fixedly valve mechanism 30 is coupled to the swing movement of the second oscillating cam arm 40R rotational motion of second driving cam 14 in operation.Fixedly valve mechanism 30 comprises that high-lift arm 70 and arm are coupled mechanism 72 (referring to Fig. 3).High-lift arm 70 drives by second driving cam 14.Arm is coupled mechanism 72 high-lift arm 70 is coupled to the second oscillating cam arm 40R.
The high-lift arm 70 and the second oscillating cam arm 40R are arranged side by side on Control Shaft 34.High-lift arm 70 can be independent of second oscillating cam arm 40R rotation.Input roller 74 is supported on the high-lift arm 70 in the mode that can rotate.The peripheral surface of input roller 74 contacts second driving cam 14.The not shown sky spring of moving is hooked on the high-lift arm 70.Sky is moved the spring force of spring as upwards urging input roller 74 with the power forced to move against the peripheral surface of second driving cam 14.
Fig. 3 illustrates the variable valve actuator for air 20 shown in Fig. 1 and the fixing exploded perspective view of valve mechanism 30.With reference to Fig. 3, high-lift arm 70 comprises and can advance and from the pin 76 of second oscillating cam arm 40R withdrawal towards the second oscillating cam arm 40R.High-lift arm 70 also comprises the hydraulic chamber 78 that is formed at wherein.Hydraulic chamber 78 has opening in the second oscillating cam arm 40R side.Pin 76 fits into hydraulic chamber 78.Hydraulic oil supplies to hydraulic chamber 78 by not shown hydraulic path.When hydraulic pressure in the hydraulic chamber 78 was increased, pin 76 was designed to by hydraulic pressure outside the second oscillating cam arm 40R releases hydraulic chamber 78.
On the other hand, the second oscillating cam arm 40R comprises the pin-and-hole 80 that is formed at wherein.Pin-and-hole 80 has opening in high-lift arm 70 sides.Pin 76 and pin-and-hole 80 are arranged on the identical circular arc of Control Shaft 34.This arranges and produces following result.Particularly, when the second oscillating cam arm 40R was positioned at predetermined angle of rotation with respect to high-lift arm 70, pin-and-hole 80 alignd with pin 76.Returnning spring 82 and piston 84 along from after forward order place in the pin-and-hole 80.
According to aforementioned arrangement, when pin-and-hole 80 aligns with pin 76, sell 76 butt pistons 84.If the hydraulic coupling of pushing pins 76 is then sold 76 and advanced in the pin-and-hole 80 greater than the power of Returnning spring 82 promotion pistons 84 in the hydraulic chamber 78 at this moment, piston 84 is advanced in the pin-and-holes 80 as pin 76.When pin 76 injected pin-and-hole 80, the second oscillating cam 40R and high-lift arm 70 were coupled to together by pin 76.Particularly, pin 76, the hydraulic chamber 78 that is supplied with hydraulic oil, pin-and-hole 80, Returnning spring 82 and piston 84 formation arms are coupled mechanism 72.
Be arranged in variable valve gear 1 when the second oscillating cam arm 40R is positioned at predetermined angle of rotation with respect to the arm 70 that rises higher, pin 76 and pin-and-hole 80 align mutually.When pin 76 correctly alignd with pin-and-hole 80, pin 76 injected pin-and-hole 80, makes the high-lift arm 70 and the second oscillating cam arm 40R be coupled.In variable valve gear 1, by using arm to be coupled mechanism 72 high-lift arm 70 is coupled to the second oscillating cam arm 40R, the element that is coupled with the lift motion of duaspiracle 16R in operation can switch to fixedly valve mechanism 30 from variable valve actuator for air 20R.On the contrary, be coupled being coupled between the high-lift arm 70 that mechanism 72 realizes and the second oscillating cam arm 40R by throwing off by arm, the element that is coupled with the lift motion of duaspiracle 16R in operation switches to variable valve actuator for air 20R from fixing valve mechanism 30.
When high-lift arm 70 and the second oscillating cam arm 40R were not coupled together, the rotational motion of camshaft 10 was delivered to each slidingsurface 50 of the first oscillating cam arm 40L and the second oscillating cam arm 40R via first roller 42 and second roller 44 from first driving cam 12.Therefore, in this case,, can provide control to make the operation angle of the valve 16L that wins have identical characteristic (the variable control of dual valve) with operation angle and the lift of duaspiracle 16R with lift by in operation, being coupled to the rotation of Control Shaft 34.
On the other hand, when high-lift arm 70 and the second oscillating cam arm 40R were coupled together, the rotational motion of camshaft 10 was delivered to the second oscillating cam arm 40R via high-lift arm 70 from second driving cam 14.Be coupled together under the situation of the position of describing with reference to Fig. 4 below the high-lift arm 70 and the second oscillating cam arm 40R move in Control Shaft 34 rotations and with the second roller 44R on the slidingsurface 50R.Therefore, the valve opening characteristic of duaspiracle 16R limits by shape and the position relation machinery of second driving cam 14, high-lift arm 70 and the second oscillating cam arm 40R.Thereby no matter the angle of rotation of Control Shaft 34 how, the valve opening characteristic of duaspiracle 16R is fixed and is constant.On the other hand, the rotational motion of camshaft 10 is delivered to the first oscillating cam arm 40L via first roller 42 and the second roller 44L from first driving cam 12.Therefore, in this case, identical mode when not being coupled together with the high-lift arm 70 and the second oscillating cam arm 40R, the valve opening characteristic of the first valve 16L changes with the angle of rotation of Control Shaft 34.
As previously mentioned, according to variable valve gear 1,, can only control the valve opening characteristic (the variable control of single valve) of the first valve 16L changeably when high-lift arm 70 and the second oscillating cam arm 40R are coupled to a time-out.Variable valve gear 1 allows the lift of valve 16 and operation angle both to change continuously as described above.Run through the part below this specification, unless otherwise indicated, " lift and the operation angle " of valve 16 may abbreviate " operation angle " or " lift " of valve 16 as.The setting of pin-and-hole position and cam profile in (3) first mode of executions
Fig. 4 A and 4B are the views that is used to illustrate the set positions of 1 inner pinhole 80 of variable valve gear shown in Fig. 1.More specifically, Fig. 4 A is the view that the set positions of variable valve gear A inner pinhole is shown, and variable valve gear A is called the contrast structure according to the variable valve gear 1 of first embodiment of the invention.Fig. 4 B is the view that illustrates according to the set positions of variable valve gear 1 inner pinhole 80 of first embodiment of the invention.Suppose that except the cam height of the pin-and-hole set positions and second driving cam variable valve gear A that is used to contrast has and the layout identical according to the variable valve gear 1 of first embodiment of the invention.Here the point of contact that claims to shake between the roller 56 and the second oscillating cam arm 40R is " roller point of contact X ", claims the not operation face 52a of the second oscillating cam arm 40R and the boundary point between the fore side 52b to be " lift starting point Y ".In addition, at the rotating center P that connects the second oscillating cam arm 40R with shake the angle that forms between straight line and the straight line that is connected rotating center P and lift starting point Y of rotating center Q of roller 56 and will be called " arm angle θ ".
Be provided with the angle of productivity of the camshaft 10 of first driving cam 12 and second driving cam 14 from production, be preferably first driving cam 12 and have identical cam profile with second driving cam 14.In the variable valve gear A shown in Fig. 4 A, first driving cam is arranged to have identical cam profile with second driving cam.In variable valve gear A, no matter control mode is variable control of dual valve or the variable control of single valve, second roller of the second oscillating cam arm side is attempted the propagation of pressure of first driving cam slidingsurface to the second oscillating cam arm.Therefore, be arranged to have under the situation of identical cam height at first driving cam and second driving cam, if the pin-and-hole set positions become to make the lift that is realized by fixing valve mechanism less than the maximum lift that is realized changeably by variable valve actuator for air, then after reaching maximum lift, will further drive by variable valve actuator for air by the valve of variable valve actuator for air driving.Therefore, make that the variable control of single valve is unavailable.
Therefore, operation angle for the duaspiracle of controlling fixed side independently, realizing simultaneously the maximum variable scope of operation angle in the variable control of single valve by variable valve actuator for air, must be to make the pose of the second oscillating cam arm can realize the maximum operation angle of the variable range that obtained by variable valve actuator for air or bigger with the pin-and-hole set positions.Variable valve gear A shown in Fig. 4 A represents to consider the setting of the pin-and-hole position of above-mentioned item.
More specifically, Fig. 4 A pressure that driving cam is shown does not act on the situation on the second oscillating cam arm.Thereby Fig. 4 A also illustrates the situation that the pose of controlling the second oscillating cam arm by Control Shaft reaches maximum operation angle.In variable valve gear A, the set positions of the second oscillating cam arm inner pinhole becomes when the second oscillating cam arm presents above-mentioned pose, and pin aligns with pin-and-hole.Arm angle θ in this case is called θ 1.Set the pin-and-hole position by the way, because the lift that has fully enlarged between two valves is poor, so allow to form more effective swirling flow.
On the other hand, in variable valve gear 1 according to first embodiment of the invention, the item below having considered when determining the position of pin-and-hole 80.Particularly, in explosive motor, in order in the firing chamber, to produce effective swirling flow, and so that---operation angle at this scope valve 16 is about 100 to 200 ° of CA---reducing the NOx discharge amount is final purpose, can send the request that is used for the variable control of single valve in for example low-load operation scope or low engine speed range.Similarly, in explosive motor, in low-load operation scope or low engine speed range, be final purpose for example to improve fuel economy, can send the request that is used for the variable control of single valve.After receiving this request, in explosive motor, be index to reduce NOx or to improve fuel economy, the scope that the variable control of dual valve switches to the variable control of single valve is set to predetermined low engine speed range or low-load operation scope.
In the variable valve gear 1 according to first embodiment of the invention, the set positions that the second oscillating cam arm 40R goes up pin-and-hole 80 becomes to satisfy following situation.Particularly, with reference to Fig. 4 B, under arm angle θ is situation greater than the angle θ 2 of above-mentioned angle θ 1, perhaps in other words, make by Control Shaft 34 controls that at the pose of the second oscillating cam arm 40R arm angle θ is that pin 76 should align with pin-and-hole 80 under the situation of the operation angle in the middle of the variable range of the valve 16 realized of variable valve actuator for air 20.In other words, the set positions of pin-and-hole 80 becomes when the second oscillating cam arm 40R is in realization from the pose of the operation angle of variable handover operation (back abbreviates " pin handover operation " sometimes as) the action required scope that controls to the variable control of single valve of dual valve, can carry out this and sell handover operation.
More specifically, according to first embodiment of the invention, the set positions of pin-and-hole 80 becomes to make when operation angle is controlled in the scope of about 100 to 200 ° of CA, promptly, when operation angle is controlled as when being used to begin the variable control of single valve with the operation angle of the purpose that reduces NOx or be used to be correlated with, can carry out the pin handover operation.In addition, the set positions of pin-and-hole 80 in the scope of needs pin handover operation (for example becomes to make, make operation angle fall into the scope in about 100 to 200 ° of CA) minimum operation angle side (situation below is when the pose that presents as the second oscillating cam arm 40R produces the operation angle of 100 ° of CA) can carry out the pin handover operation.
In the variable valve gear 1 according to first embodiment of the invention, the profile of first driving cam 12 and second driving cam 14 is set for and is made the cam height of second driving cam 14 greater than the cam height of first driving cam 12, shown in Fig. 4 B.Particularly, the cam height of second driving cam 14 is arranged so that the operation angle of duaspiracle 16R when pin is coupled becomes the peaked value of operation angle that is equal to or greater than the first valve 16L that is driven by variable valve actuator for air 20.
Carry out above-mentioned pin handover operation to follow step given below.Particularly, need operating time T1, during operating time T1, Control Shaft 34 is driven, and is used for the operation angle pose of the second oscillating cam arm 40R under the explosive motor current operation status changed to the operation angle pose that allows pin-and-hole 80 alignment pins 76.When finishing the pin handover operation and the second oscillating cam arm 40R and be coupled to high-lift arm 70, the motion of the lift of duaspiracle 16R switches to immediately by the fixedly operation of valve mechanism 30 execution.Yet,, need operating time T2 later on finishing the pin handover operation for the first valve 16L that drives by variable valve actuator for air 20.During T2 during this period of time, the first oscillating cam arm 40L moves to realize producing the little operation angle pose of required swirling flow.
According to the layout of the variable valve gear 1 of first embodiment of the invention, when the second oscillating cam arm 40R is the operation angle pose of the aforementioned pin handover operation of needs, carry out the pin handover operation.Therefore, with the pin-and-hole set positions to comparing according to the operating time among the peaked variable valve gear A (being shown among Fig. 4 A) of the operation angle variable range of variable valve actuator for air 20, can shorten operating time T1.In variable valve gear 1, be arranged so that second driving cam 14 has the cam height greater than the cam height of first driving cam 12.This allows to be actuated in the variable control of single valve realize that often the operation angle of the duaspiracle 16R of value is configured to be equal to, or greater than the maximum lift that is realized by variable valve actuator for air 20.In addition, first preferred implementation according to the present invention takes method to change cam height between first driving cam 12 and second driving cam 14, thereby realizes the characteristic of above-mentioned duaspiracle 16R.This allows the operation angle of duaspiracle 16R to change to required big operation angle immediately after the pin handover operation is finished.
As previously mentioned, need operating time T2 after pin is coupled in position, during time T 2, the first oscillating cam arm 40L moves to the little operation angle pose that can produce required swirling flow from the operation angle pose that the execution pin is coupled operation.Become peaked variable valve gear A (being shown among Fig. 4 A) to compare with the pin-and-hole set positions, can shorten this operating time T2 according to the variable valve gear 1 of first embodiment of the invention according to the operation angle variable range of variable valve actuator for air 20.
Produce enough swirling flows, it is effective making lift difference between the first valve 16L and the duaspiracle 16R bigger.Therefore, be controlled to be coupled the back and realize that the operation angle pose of the first oscillating cam arm 40L of this required swirling flow is less basically at pin.In the variable valve gear 1 according to first embodiment of the invention, as mentioned above, the set positions of pin-and-hole 80 becomes to allow to carry out the pin handover operation at the place, minimum operation angle of the scope of needs pin handover operation.Therefore, can promptly the operation angle pose of the first oscillating cam arm 40L be changed to the enough little operation angle pose of target.Particularly, can more effectively shorten operating time T2.
Corresponding as described below between the element of first mode of execution of the present invention and the element of others of the present invention.Particularly, respectively, the first valve 16L in first mode of execution is corresponding to " valve that will be switched " in the first aspect present invention; Oscillating cam arm 40 in first mode of execution is corresponding to " agitation member " of first aspect present invention; Control Shaft 34 in first mode of execution, control arm 36, link arm 38, first roller 42, second roller 44 and slidingsurface 50 are corresponding to " the valve opening characteristic variset " of first aspect present invention; High-lift arm 70 in first mode of execution is corresponding to " valve opening characteristic fixing device " in the first aspect present invention; Arm in first mode of execution is coupled " modifier " of device 72 corresponding to first aspect present invention.
Similarly, respectively, first roller 42 in first mode of execution and second roller 44 are corresponding to " intermediate member " in a third aspect of the present invention; Control Shaft 34 in first mode of execution, control arm 36 and link arm 38 are corresponding to " control gear " of third aspect present invention; Second driving cam 14 in first mode of execution is corresponding to " second cam " of third aspect present invention; And first high-lift arm 70 in the mode of execution corresponding to " the input arm " of a third aspect of the present invention.
Second mode of execution
With reference to Fig. 5 to 8 second mode of execution of the present invention is described below.
Fig. 5 is the view that is used to illustrate according to the layout of the variable valve gear 90 of second embodiment of the invention.Except that the layout of camshaft 92, have as the layout identical according to the variable valve gear 1 of first embodiment of the invention according to the variable valve gear 90 of second embodiment of the invention.Particularly, in variable valve gear 90, the position of pin-and-hole 80 also is arranged so that when the second oscillating cam arm 40R is in the pose that is used to realize from the operation angle of the required operating range of the variable handover operation (pin handover operation) that controls to the variable control of single valve of dual valve, can carries out the pin handover operation.
With reference to Fig. 5, variable valve gear 90 has the layout identical with the variable valve gear of first mode of execution, and wherein the cam height of second driving cam 96 is greater than the cam height of first driving cam 94.In addition, first driving cam 94 is installed on the camshaft 92 in the angle on the camshaft 92 to be different from second driving cam 96.Particularly, second driving cam 96 with respect to the fixed-site of the advance side deflection predetermined angle of first driving cam 94 to camshaft 92.
Fig. 6 is the plotted curve that the valve opening characteristic of the valve of realizing by variable valve gear 90 16 is shown.Layout according to above-mentioned variable valve gear 90, therefore the valve-opening time of the duaspiracle 16R that is driven by second driving cam 96 can realize given valve opening characteristic at the variable control period of single valve by the high-lift arm 70 and the second oscillating cam arm 40R with respect to the variable control valve-opening time of the first valve 16L in advance.According to this setting that is used for camshaft 92, at first in cylinder, produce after the vacuum by opening duaspiracle 16R, can open the controlled first valve 16L that little operation angle is provided.The flow velocity that this has increased the air inlet when the first valve 16L of little operation angle side opens allows to produce effective swirling flow.Under the situation of not using the mechanism's (vvt mechanism) that changes valve 16 phase places, can realize this effect.
According to second embodiment of the invention, be arranged to: second driving cam 96 arrives camshaft 92 in the fixed-site with respect to first driving cam, 94 advance side deflection predetermined angle.The technology with the phase place that changes two cams of being used is not limited to the technology among the present invention.Fig. 7 is the view that is used to illustrate the layout of this improvement example.In variable valve gear shown in Figure 7 100, be different from variable valve gear 90, the first driving cams 102 shown in Fig. 5 and be fixed on position with respect to second driving cam, 104 advance side deflection predetermined angle β.
Fig. 8 is the view that the valve opening characteristic of the valve of being realized by variable valve gear 100 16 is shown.Layout according to above-mentioned variable valve gear 100, at the variable control period of single valve, can be in advance by the valve-opening time of the first valve 16L of variable valve actuator for air 20 variable controls with respect to the valve-opening time of the duaspiracle 16R that drives by fixing valve mechanism 30.According to this setting that is used for camshaft 106, can reduce pumping loss effectively by at first opening the first valve 16L before the generation vacuum in cylinder.Under the situation of not using the mechanism's (vvt mechanism) that changes valve 16 phase places, can realize this effect.
The 3rd mode of execution
To 11A and 11B the 3rd mode of execution of the present invention is described with reference to Fig. 9 below.
Except following 2, have and the layout identical according to the variable valve gear 1 of first embodiment of the invention according to the variable valve gear 110 of third embodiment of the invention.Particularly, when carrying out from the variable handover operation (pin handover operation) that controls to the variable control of single valve of dual valve, the pose difference of the second oscillating cam arm 40R.In addition, second driving cam 114 is different with the height of first driving cam 112.
Fig. 9 is illustrated in the torque curve figure according to the operating range of the variable control of fill order's valve in the variable valve gear 110 of third embodiment of the invention.With reference to Fig. 9, under heavy load, high speed range, carry out two valves and all be set to the variable control of dual valve that realizes big operation angle.Scope beyond heavy load, high speed range is carried out and is only changed the first valve 16L so that the variable control of single valve of little operation angle to be provided.In aforesaid first mode of execution, the minimum operation angle side that is arranged in the scope of carrying out the variable control of this single valve is carried out the pin handover operation.On the other hand, be characterised in that, carry out the pin handover operation in the maximum operation angle side of the scope of carrying out the variable control of this single valve according to the variable valve gear 110 of third embodiment of the invention.
Figure 10 A and 10B are the views that is used to illustrate when the problem that occurs when the little operation angle side of the scope of the variable control of fill order's valve is carried out the pin handover operation.Figure 10 A illustrates the forward end that second roller 44 that contacts oscillating cam arm 40 is positioned at oscillating cam arm 40, that is, and and the view of the situation of little operation angle state of a control.Figure 10 B be illustrated under the situation shown in Figure 10 A carry out the pin handover operation with set the variable state of a control of single valve and then Spin Control axle 34 be the view of the situation of big operation angle state of a control to move second roller 44 towards the axle center of Control Shaft 34.Under the situation shown in Figure 10 B, between second driving cam 14 of fixing operation angle side and input roller 74, produce gapped.This is owing to following reason.Particularly, the second oscillating cam arm 40R and high-lift arm 70 use pin 76 to be coupled together under situation shown in Figure 10 A; Second roller 44 moves changing the pose of the second oscillating cam arm 40R then, thereby causes the pose of high-lift arm 70 to change.Therefore the gap that results between second driving cam 14 and the input roller 74 makes second driving cam 14 contact input roller 74 repeatedly in each lift motion.Therefore when contact, produce noise and impact load.
Figure 11 A and 11B are the views that is used to illustrate the operation of carrying out when making the setting that is used for according to the pin handover operation of third embodiment of the invention.Figure 11 A illustrates the view of situation of position that second roller 44 is positioned at the maximum operation angle of the scope that produces the variable control of single valve.According to third embodiment of the invention, the second oscillating cam arm 40R comprises the pin-and-hole 116 that is placed in one, thereby can carry out the pin handover operation under above-mentioned situation.Figure 11 B be illustrated under the situation shown in Figure 11 A carry out the pin handover operation with set the variable state of a control of single valve and then Spin Control axle 34 to move second roller 44 with the forward end towards oscillating cam arm 40 be the view of the situation of little operation angle state of a control.Under the situation shown in Figure 11 B, the first oscillating cam arm 40L of variable operation angle side keeps in touch second roller 44; But, when second roller 44 moves along the direction of leaving Control Shaft 34, between the second oscillating cam arm 40R of fixing operation angle side and second roller 44, produce the gap.
As previously mentioned, according to the setting of being done in the third embodiment of the invention, always in the variable control of operation angle side fill order valve less than the operation angle of carrying out the pin handover operation.Therefore, at the variable control period of single valve, between the second oscillating cam arm 40R and second roller 44, produce the gap; But, since very close to each other between second driving cam 14 and the input roller 74, so, do not produce noise or impact load between moving period in lift unlike the layout shown in Figure 10 A and the 10B.
The 4th mode of execution
With reference to Figure 12 to 17 the 4th mode of execution of the present invention is described below.
Figure 12 is the view that is used to illustrate according to the layout of the variable valve gear 120 of four embodiment of the invention.With reference to Figure 12, except that these points, have and the identical layout of layout according to the variable valve gear 1 of first embodiment of the invention according to the variable valve gear 120 of four embodiment of the invention.Particularly, first driving cam 12 that is used for moving first roller 42 have with the profile phase of second driving cam 122 that is used for moving input roller 74 with profile.In addition, arm is coupled mechanism 124 and has the layout that is different from the first embodiment of the invention equity part.
More specifically, be coupled in the mechanism 124 axis of pin 76 and the axial alignment of pin-and-hole 128 when the second oscillating cam arm 126R becomes the pose of realizing maximum operation angle at arm according to four embodiment of the invention.Figure 12 illustrates the second oscillating cam arm 126R and is in realization with respect to the situation of the pose of the maximum operation angle of pin-and-hole 128 few predetermined values of arranging as mentioned above.Particularly, Figure 12 illustrates the situation that pin 76 and pin-and-hole 128 are not axially aligned.The 4th mode of execution of the present invention is characterised in that allowing arm to be coupled mechanism 124 carries out the pin handover operation under situation shown in Figure 12.
Figure 13 is used to illustrate the sectional view that is coupled the layout of mechanism 124 at the arm according to four embodiment of the invention.Although hydraulic chamber 78 is arranged on high-lift arm 70 sides in layout shown in Figure 3, in the 4th mode of execution, supposes that hydraulic path 132 and hydraulic chamber 134 are not arranged on high-lift arm 130 sides, and be arranged on the second oscillating cam arm 126R side.Further supposition, high-lift arm 130 sides comprise the pin-and-hole 128 that holds piston 136 and Returnning spring 138.Arm according to four embodiment of the invention is coupled the shape that mechanism 124 is characterised in that the part that marks with " A " in the pin-and-hole 128 in the high-lift arm 130 among Figure 13.
Figure 14 A and 14B are the zoomed-in views that the part A of Figure 13 is shown.More specifically, Figure 14 A is the view that the pin-and-hole of seeing from hydraulic chamber 134 sides 128 is shown.Figure 14 B is the view that the cross section of part A is shown.With reference to Figure 14 A and 14B, be formed with the guiding surface 128a that is used for guide finger 76 in the ingress of pin-and-hole 128.Guiding surface 128a forms and makes and be formed with recessed biglyyer radius at the second oscillating cam arm 126R shift-in with the part place of the side (right side of Figure 14 B) that is used for the pin handover operation, thereby guarantees that pin 76 more easily injects pin-and-hole 128.Guiding surface 128a forms inlet radius towards pin-and-hole 128 and becomes big radial gradually.More specifically, guiding surface 128a forms the tilt angle that makes with respect to the axis of pin-and-hole 128 and diminishes gradually towards the inlet of pin-and-hole 128.Even be arranged in the layout of high-lift arm 70 sides (layout shown in Fig. 3),, can realize similarly that also arm is coupled these layouts of mechanism 124 if be similar to the guiding surface of guiding surface 128a in the second oscillating cam arm 40R side setting at hydraulic chamber 78.
Figure 15 A and 15B are the views that is used for illustrating the pin handover operation of four embodiment of the invention.Figure 15 A is the view that the situation that pin 76 and pin-and-hole 128 do not axially align is shown.Arm according to four embodiment of the invention is coupled mechanism 124, even when pin 76 and pin-and-hole 128 are not axially aligned, the pin 76 that is applied with hydraulic pressure also can be guided guiding surface 128a, and it rotates the second oscillating cam arm 126R so that sell shown in 76 Figure 15 B and axially align with pin-and-hole 128.This allows pin 76 to inject pin-and-hole 128.
Figure 16 is the view that is used to illustrate the operation of the second oscillating cam arm 126R during the pin handover operation.Figure 12 of top reference is relevant with the situation of Figure 15 A.Arm according to four embodiment of the invention is coupled mechanism 124, even when pin 76 is not axially aligned with pin-and-hole 128 as shown in Figure 12, also can carry out the pin handover operation.Figure 16 is illustrated in and attempts to carry out the pin handover operation is finished the pin handover operation afterwards owing to the rotation of the second oscillating cam arm 126R shown in Figure 15 B situation under the situation shown in Figure 12.Particularly, by this pin handover operation, when pin 76 injects pin-and-holes 128, before beginning, the pin handover operation rotates to the position shown in Figure 16 with the second oscillating cam arm 126R that the first oscillating cam arm 40L is in identical pose.
As previously mentioned, the layout in the 4th mode of execution of the present invention does not need drive controlling axle 34 the second oscillating cam arm 126R is moved to the operation angle pose that pin 76 and pin-and-hole 128 are axially aligned, and is used for carrying out the pin handover operation.Particularly, when the variable control of needs list valve, the operating time that is used for the second oscillating cam arm 126R is moved to the operation angle pose that can carry out the pin handover operation is reduced.In addition, according to the layout of being done in the four embodiment of the invention, the second oscillating cam arm 126R itself rotates to the position that causes the maximum operation angle that pin 76 is coupled.This does not need like that the cam height of second driving cam 122 to be arranged in first and second mode of executions as described above the cam height greater than first driving cam 12.But in the layout that should be noted that in four embodiment of the invention to be done, second driving cam 122 also can be arranged to have the cam height of the cam height that is different from first driving cam 12.
Be coupled in the layout of mechanism 124 at above-mentioned arm, guiding surface 128a forms radial that inlet radius towards pin-and-hole 128 increases gradually.Therefore, when the variable control of single valve switches to the variable control of dual valve, that is, and when pin 76 shifts out pin-and-hole 128, the effect of the shape by the 128a of guiding surface shown in Figure 17, the second oscillating cam arm 126R that has pin 76 can little by little reduce towards the speed of little operation angle side shifting.Therefore, when being coupled of pin 76 discharges the back second oscillating cam arm 126R and contacts second roller 44 again, contact mitigations that can become, thereby the noise or the impact load of generation when helping reducing to contact.
At the 4th mode of execution of the present invention, the guiding surface 128a in the pin-and-hole 128 forms radial.Shape according to guiding surface of the present invention is not limited to radial.For example, guiding surface can be cut sth. askew into a plurality of steps, makes that the tilt angle about the axis of pin-and-hole diminishes towards the inlet of pin-and-hole.
According to the guiding surface 128a of four embodiment of the invention " guiding surface " corresponding to sixth aspect present invention.
Claims (8)
1. variable valve gear, the control of the valve opening characteristic of at least one valve that will be switched in wherein a plurality of valves under from the control break under the variable control mode to fixing control mode control or from the control break under the fixing control mode to variable control mode under control, described variable valve gear comprises:
Agitation member, it is arranged between main cam and the described valve, and described agitation member arrives described valve with the propagation of pressure of described main cam;
Valve opening characteristic variset, its be used for Pose Control with described agitation member in prespecified range to control the valve opening characteristic of the described valve that will be switched changeably;
Valve opening characteristic fixing device, it controls the valve opening characteristic of the described valve that will be switched with being used for fixing; And
Modifier, it is used for that the control of the valve opening characteristic of the described valve that will be switched is switched to control under the described fixedly control mode or the control under the described fixedly control mode from the control under the described variable control mode and switches to control under the described variable control mode;
Wherein said modifier is arranged to, and the valve opening characteristic that allows the described valve that will be switched is under the pose relevant with the operating range of the valve opening characteristic that needs to switch the described valve that will be switched in described agitation member and changes.
2. variable valve gear as claimed in claim 1,
The wherein said operating range of the valve opening characteristic of the described valve that will be switched of switching that needs comprises low engine speed range or the low-load range that is used to reduce NOx or improves fuel economy.
3. variable valve gear as claimed in claim 1 or 2,
Wherein said valve opening characteristic variset comprises the control gear that is arranged at the intermediate member between described main cam and the described valve that will be switched and is used to change the position of described intermediate member;
Wherein said intermediate member is shared by the described a plurality of valves that comprise the described valve that will be switched;
Comprise second cam that separates with described main cam;
Wherein said valve opening characteristic fixing device comprises the input arm that the rotation homophase with described second cam shakes;
Wherein said modifier makes being coupled between the described agitation member be used for moving the described valve that will be switched and the described input arm engage or throws off;
Wherein said second cam is arranged to have the cam height bigger than described main cam.
4. variable valve gear as claimed in claim 3,
Wherein said modifier is arranged so that, the operating range of valve opening characteristic of switching the described valve that will be switched when needs is in prespecified range the time, when being in, described agitation member realizes that the valve opening characteristic of the described valve that will be switched can be switched under the minimum operation angle and/or the situation of the pose of minimum lift of the described valve that will be switched in described prespecified range.
5. variable valve gear as claimed in claim 3,
Wherein said modifier is arranged so that, the operating range of valve opening characteristic of switching the described valve that will be switched when needs is in prespecified range the time, when being in, described agitation member realizes that the valve opening characteristic of the described valve that will be switched can be switched under the maximum operation angle and/or the situation of the pose of maximum lift of the described valve that will be switched in described prespecified range.
6. variable valve gear as claimed in claim 1 or 2,
Wherein said valve opening characteristic variset comprises the control gear that is arranged at the intermediate member between described main cam and the described valve that will be switched and is used to change the position of described intermediate member;
Wherein said intermediate member is shared by the described a plurality of valves that comprise the described valve that will be switched;
Comprise second cam that separates with described main cam;
Wherein said valve opening characteristic fixing device comprises the input arm that the rotation homophase with described second cam shakes;
Wherein said modifier comprises pin, and described modifier makes described pin being coupled between the described agitation member that is used for moving the described valve that will be switched and described input arm engage or throws off;
The described agitation member or the described input arm that wherein are used for the mobile described valve that will be switched comprise pin-and-hole, and described pin inserts in the described pin-and-hole; And
The intake section of wherein said pin-and-hole comprises guiding surface, and described guiding surface forms and is used to guide the described pin that inserts or shift out described pin-and-hole.
7. variable valve gear as claimed in claim 6,
Wherein said guiding surface has the tilt angle with respect to the axis of described pin-and-hole, and described tilt angle diminishes towards the intake section of described pin-and-hole.
8. as each described variable valve gear in the claim 1 to 7,
The profile of wherein said second cam is arranged so that the phase place of the described valve that will be switched that described second cam is realized is different from the valve-control that is realized by described main cam.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP165312/2005 | 2005-06-06 | ||
| JP2005165312 | 2005-06-06 | ||
| JP255250/2005 | 2005-09-02 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101189413A true CN101189413A (en) | 2008-05-28 |
Family
ID=39481118
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200680020004XA Pending CN101189413A (en) | 2005-06-06 | 2006-05-10 | Variable valve apparatus |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101189413A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101802351A (en) * | 2008-11-05 | 2010-08-11 | 丰田自动车株式会社 | Valve gear for internal combustion engine |
| CN104696033A (en) * | 2013-12-06 | 2015-06-10 | 上海汽车集团股份有限公司 | Engine valve driving mechanism and engine valve driving device |
| CN111670295A (en) * | 2017-12-08 | 2020-09-15 | 伊顿智能动力有限公司 | Device for actuating a latching device |
-
2006
- 2006-05-10 CN CNA200680020004XA patent/CN101189413A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101802351A (en) * | 2008-11-05 | 2010-08-11 | 丰田自动车株式会社 | Valve gear for internal combustion engine |
| CN101802351B (en) * | 2008-11-05 | 2013-06-19 | 丰田自动车株式会社 | Valve gear for internal combustion engine |
| CN104696033A (en) * | 2013-12-06 | 2015-06-10 | 上海汽车集团股份有限公司 | Engine valve driving mechanism and engine valve driving device |
| CN104696033B (en) * | 2013-12-06 | 2017-02-15 | 上海汽车集团股份有限公司 | Engine valve driving mechanism and engine valve driving device |
| CN111670295A (en) * | 2017-12-08 | 2020-09-15 | 伊顿智能动力有限公司 | Device for actuating a latching device |
| CN111670295B (en) * | 2017-12-08 | 2022-02-08 | 伊顿智能动力有限公司 | Device for actuating a latching device |
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Application publication date: 20080528 |