CN103397922A

CN103397922A - Engine and actuating mechanism of variable valve lift device of engine

Info

Publication number: CN103397922A
Application number: CN2013103260881A
Authority: CN
Inventors: 崔亚彬; 胡佳明; 饶良武
Original assignee: Great Wall Motor Co Ltd
Current assignee: Honeycomb Power System Jiangsu Co ltd
Priority date: 2013-07-30
Filing date: 2013-07-30
Publication date: 2013-11-20
Anticipated expiration: 2033-07-30
Also published as: CN103397922B

Abstract

The invention discloses an engine and an actuating mechanism of a variable valve lift device of the engine. The actuating mechanism comprises a hydraulic valve block, a first piston, a second piston, a first driving rod, a second driving rod, an oil supply and return mechanism, an elastic reset device and an elastic piece, wherein a first cavity and a second cavity are formed in the hydraulic valve block; the first piston is movably arranged in the first cavity and the first cavity is divided into a first valve cavity and a second valve cavity through the first piston; the second piston is movably arranged in the second cavity, the second cavity is divided into a third valve cavity and a fourth valve cavity through the second piston, the third valve cavity and the first valve cavity are identical in shape and are mutually communicated; the first driving rod is connected with the first piston; the second driving rod is connected with the second piston; the oil supply and return mechanism is communicated with the second valve cavity; the elastic reset device is arranged in the fourth valve cavity; the elastic piece is suitable for abutting against and pressing the portion between a first cam and a second cam in an elastic mode. The actuating mechanism is simple in structure, reliable in control and high in accuracy.

Description

The actuating mechanism of motor and variable air valve lift apparatus thereof

Technical field

The present invention relates to the automobile construction technical field, especially relate to a kind of actuating mechanism of the variable air valve lift apparatus for motor.

Background technique

The valve actuating mechanism of conventional engines, its port timing, generally based on the local optimum of a certain narrow and small condition range of motor and determine, immobilize in the course of the work, and the valve motion rule are determined by cam profile fully.But the conventional gasoline engin cam profile is single, can not adjust air inflow according to engine load conditions.The valve Operational Limits of conventional engines distribution device is also changeless, the operating point of determining to depend on design of parameter.

Existing non-continuously variable valve lift structure lift mode is single, can not realize most of operating mode of motor, and oil-saving effect is not obvious.And existing continuously variable valve lift technology component cost is high, and complex structure is high to the reliability requirement of each component, the difficulty of engine cylinder cover design is larger, particularly the structure of actuating mechanism is more complicated, and its adjustment process is wayward, and degree of regulation is poor.

Summary of the invention

The present invention is intended to solve at least to a certain extent one of above-mentioned technical problem of the prior art.

For this reason, one object of the present invention is to propose a kind of actuating mechanism of the variable air valve lift apparatus for motor, and this actuating mechanism is simple in structure, control is convenient.

Another object of the present invention is to propose a kind of motor, and this motor comprises the actuating mechanism of the above-mentioned variable air valve lift apparatus that is used for motor.

According to an aspect of the present invention, a kind of actuating mechanism of the variable air valve lift apparatus for motor has been proposed, described variable air valve lift apparatus comprises camshaft mechanism, described camshaft mechanism comprises camshaft, the first cam and the second cam, described actuating mechanism comprises: hydraulic valve block has the first chamber and the second chamber in described hydraulic valve block; First piston, described first piston are located at movably in described the first chamber and described the first chamber isolation are become the first valve pocket independent of each other and the second valve pocket; The second piston, described the second piston is located at movably in described the second chamber and described the second chamber isolation is become the 3rd valve pocket independent of each other and the 4th valve pocket, wherein said the 3rd valve pocket is identical with described the first valve pocket shape and communicate with each other, and is full of liquid in described the 3rd valve pocket and described the first valve pocket; The first driveshaft, described the first driveshaft is connected with described first piston and with described first piston, moves, and is provided with the first shift fork on described the first driveshaft; The second driveshaft, described the second driveshaft is connected with described the second piston and with described the second piston, moves, and is provided with the second shift fork on described the second driveshaft; The fuel feeding oil return mechanism, described fuel feeding oil return mechanism is communicated with described the second valve pocket; And elasticity reset device, described elasticity reset device is located in described the 4th valve pocket and is suitable for flexibly compressing described the second piston; And elastic component, described elastic component is suitable for flexibly being pressed between described the first cam and described the second cam.

Can be used in variable air valve lift apparatus according to the actuating mechanism of the embodiment of the present invention, the first cam in the driving cam axis mechanism and the second cam action, realize the continuous variable of valve lift, simple in structure, compact, convenient integrated being arranged in cylinder head, and this actuating mechanism can be arranged on the residing height of camshaft, can additionally not increase the height of cylinder head.And this actuating mechanism adopts hydraulic control, and the driving process is more reliable and precision is high thereby make.

In addition, the actuating mechanism according to the variable air valve lift apparatus for motor of the present invention can also have following additional technical feature:

According to one embodiment of present invention, described hydraulic valve block hollow and inside are provided with spacing block, described spacing block is isolated into described the first chamber and the second chamber with the inner space of described hydraulic valve block, the free-ended end face of described spacing block is spaced apart with the internal face of, a sidewall that free end end face described hydraulic valve block and this spacing block is relative, to be communicated with described the first valve pocket and described the 3rd valve pocket.

According to one embodiment of present invention,

One end of described the first driveshaft inwardly extend in described the second valve pocket with on a side that is fixed on described first piston from a sidewall of described the second valve pocket;

One end of described the second driveshaft inwardly extend in described the 4th valve pocket with on a side that is fixed on described the second piston from a sidewall of described the 4th valve pocket.

According to one embodiment of present invention, described elasticity reset device is spring, on the part of described spring housing in described the 4th valve pocket of stretching into of described the second driveshaft.

According to one embodiment of present invention, be provided with the leakage hole that is communicated with described the 4th valve pocket on described hydraulic valve block.

According to one embodiment of present invention, each in described first piston and described the second piston all forms cuboid shape or the square bodily form.

According to one embodiment of present invention, described fuel feeding oil return mechanism comprises:

Be connected by being communicated with oil duct between engine oil pressure chamber, described engine oil pressure chamber and described the second valve pocket; And

Be used to open or close the control valve of the entrance point in described engine oil pressure chamber.

According to one embodiment of present invention, described actuating mechanism also comprises be used to the pressure-detecting device of measuring described engine oil pressure intraluminal fluid force feed pressure.

According to one embodiment of present invention, described actuating mechanism also comprises clutch shaft bearing, described clutch shaft bearing be suitable for being enclosed within on described camshaft and lay respectively at described the first cam and described the first shift fork and described the second cam and described the second shift fork between.

According to a further aspect in the invention, proposed a kind of motor, this motor comprises the actuating mechanism of the above-mentioned variable air valve lift apparatus that is used for motor.

Description of drawings

Fig. 1 is that variable air valve lift apparatus is assemblied in the interior schematic diagram of cylinder head according to an embodiment of the invention;

Fig. 2 is the plan view of variable air valve lift apparatus according to an embodiment of the invention;

Fig. 3-Fig. 4 is the schematic diagram of variable air valve lift apparatus when valve lift is zero lift according to an embodiment of the invention;

Fig. 5-Fig. 6 is the schematic diagram of variable air valve lift apparatus when valve lift is little lift according to an embodiment of the invention;

Fig. 7-Fig. 8 is the schematic diagram of variable air valve lift apparatus when valve lift is high-lift according to an embodiment of the invention;

Fig. 9 is the schematic diagram of actuating mechanism and camshaft mechanism according to an embodiment of the invention;

Figure 10 is the schematic diagram of actuating mechanism and camshaft mechanism in accordance with another embodiment of the present invention;

Figure 11 is the actuating mechanism of another embodiment according to the present invention and the partial schematic diagram of camshaft mechanism;

Figure 12 is the schematic diagram of actuating mechanism, wherein not shown fuel feeding oil return mechanism according to an embodiment of the invention;

Figure 13 is the partial enlarged drawing of the 4th valve pocket of actuating mechanism according to an embodiment of the invention;

Figure 14 is the schematic diagram of the fuel feeding oil return mechanism of actuating mechanism according to an embodiment of the invention;

Figure 15 is the sectional view of the hydraulic valve block of actuating mechanism according to an embodiment of the invention;

Figure 16 is the plan view of the hydraulic valve block of actuating mechanism according to an embodiment of the invention;

Figure 17 is the plan view of platen according to an embodiment of the invention;

Figure 18 is the sectional view of platen according to an embodiment of the invention;

Figure 19 is the sectional view of camshaft mechanism according to an embodiment of the invention;

Figure 20 is the stereogram of the first cam or the second cam according to an embodiment of the invention;

Figure 21 is the sectional view of the first cam or the second cam according to an embodiment of the invention;

Figure 22 is the plan view of rocker arm body according to an embodiment of the invention;

Figure 23 is the side view of rocker arm body according to an embodiment of the invention;

Figure 24 is the sectional view of roller according to an embodiment of the invention.

Embodiment

Below describe embodiments of the invention in detail, described embodiment's example is shown in the drawings, and wherein same or similar label represents same or similar element or the element with identical or similar functions from start to finish.Be exemplary below by the embodiment who is described with reference to the drawings, be intended to for explaining the present invention, and can not be interpreted as limitation of the present invention.

in description of the invention, it will be appreciated that, term " " center ", " vertically ", " laterally ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", orientation or the position relationship of indications such as " counterclockwise " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, rather than device or the element of indication or hint indication must have specific orientation, with specific orientation structure and operation, therefore can not be interpreted as limitation of the present invention.

In addition, term " first ", " second " only are used for describing purpose, and can not be interpreted as indication or hint relative importance or the implicit quantity that indicates indicated technical characteristics.Thus, one or more these features can be expressed or impliedly be comprised to the feature that is limited with " first ", " second ".In description of the invention, the implication of " a plurality of " is two or more, unless otherwise expressly limited specifically.

In the present invention, unless otherwise clearly defined and limited, broad understanding should be done in the terms such as term " installation ", " being connected ", " connection ", " fixing ", for example, can be to be fixedly connected with, and can be also to removably connect, or be integral; Can be mechanical connection, can be also to be electrically connected to; Can be directly to be connected, also can indirectly be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, can understand as the case may be above-mentioned term concrete meaning in the present invention.

In the present invention, unless otherwise clearly defined and limited, First Characteristic Second Characteristic it " on " or D score can comprise that the first and second features directly contact, can comprise that also the first and second features are not directly contacts but by the other feature contact between them.And, First Characteristic Second Characteristic " on ", " top " and " above " comprise First Characteristic directly over Second Characteristic and oblique upper, or only represent that the First Characteristic level height is higher than Second Characteristic.First Characteristic Second Characteristic " under ", " below " and " below " comprise First Characteristic under Second Characteristic and tiltedly, or only represent that the First Characteristic level height is less than Second Characteristic.

The engine body group is the support of motor, is the matrix of connecting rod, distribution device and the assembling of each system.The body group mainly is comprised of cylinder block, cylinder head, cylinder head gasket and oil sump etc., oil sump generally is located at the bottom of cylinder block, cylinder head is located at the top of cylinder block, and cylinder head gasket is located between the bottom surface of the end face of cylinder block and cylinder head, is used for the gap between sealing both.

Cylinder head forms firing chamber together with piston head and cylinder, the top of firing chamber has suction port and relief opening, and valve mechanism is located in cylinder head and sealing suction port and relief opening.For existing general motor, adopt two valve mechanisms that advance scene 2 more, minority also has the valve mechanism that adopts one-in-and-one-out or three to advance scene 2.

For same motor, generally all has multiple different operating mode, such as low speed small load condition, high speed high load working condition etc., when motor is under the low speed small load condition, the power of motor and the output of moment of torsion are relatively low, and the air that therefore enters in firing chamber can be relatively less, and at motor, be under the high speed high load working condition, the power of motor is relative with the output of moment of torsion higher, therefore needs more air to enter in firing chamber and more oil inflame.

Variable air valve lift apparatus of the present invention can be realized the continuous variable of particularly air inlet side of valve lift valve lift, thereby can different operating modes residing according to motor carry out intelligent adjusting valve lift, guarantee that air and fuel oil in firing chamber fully burn, and improve power performance and the fuel economy of motor.

Below with reference to the variable air valve lift apparatus 1000 that be used for motor of Fig. 1-Figure 24 detailed description according to the embodiment of the present invention.

Variable air valve lift apparatus 1000 comprises valve mechanism 100, camshaft mechanism 200, rocker arm body 300 and actuating mechanism 400 according to an embodiment of the invention.

Wherein, as Fig. 3-shown in Figure 8, valve mechanism 100 has been prior art, and be well known for ordinary skill in the art, for example valve mechanism 100 can comprise the gentle door of valve head bar section, valve mechanism 100 can move up and down to open or close along the center line of valve mechanism 100 suction port or the relief opening of firing chamber in valve guide bushing, for these, can adopt the part of identical or close design with prior art, is not described in detail here.

Camshaft mechanism 200 is located at the top of valve mechanism 100, camshaft mechanism 200 comprises camshaft 201, the first cam 203 and the second cam 207, with reference to shown in Figure 2, the first cam 203 is set on camshaft 201 and with camshaft 201 and rotates and can move axially, that is to say, but the first cam 203 is with the central axis synchronous rotary of camshaft 201 around camshaft 201, and the first cam 203 camshaft 201 axially on camshaft 201 is removable relatively.For example, camshaft 201 can be splined shaft or with the singly-bound axle of keyway, the keyway that the first cam 203 has and camshaft 201 axially coordinates.That is, by the first cam 203, with the keyway between camshaft 201, coordinate, can realize the first cam 203 with camshaft 201 synchronous rotaries on the one hand, can also realize that on the other hand the first relative camshaft 201 of cam 203 moves axially.

Similarly, the second cam 207 is set on camshaft 201 and with camshaft 201 and rotates and can move axially, that is to say, but the second cam 207 is with the central axis synchronous rotary of camshaft 201 around camshaft 201, and the second cam 207 camshaft 201 axially on camshaft 201 is removable relatively.For example, camshaft 201 can be splined shaft or with the singly-bound axle of keyway, the keyway that the second cam 207 has and camshaft 201 axially coordinates.That is, by the second cam 207, with the keyway between camshaft 201, coordinate, can realize the second cam 207 with camshaft 201 synchronous rotaries on the one hand, can also realize that on the other hand the second relative camshaft 201 of cam 207 moves axially.

With reference to Fig. 2-shown in Figure 8, the first cam 203 and the second cam 207 are contiguous arranges to form the pair of cams group, and this pair of cams group is used for driving rocker arm body 300.Wherein, the shape of the first cam 203 and the second cam 207 is the mirror image symmetry preferably, and after the first cam 203, the second cam 207 are completed with camshaft 201 assemblings, the first cam 203 and the second cam 207 are also the mirror image symmetries, in other words, will overlap fully with the second cam 207 after 180 ° of the first cam 203 counter-rotatings.

With reference to Fig. 2, Figure 19 and shown in Figure 21, be configured with the first drive surface 205 on the first cam 203, be configured with the second drive surface 209 on the second cam 207, the first drive surface 205 and the second drive surface 209 camshaft 201 axially on toward each other, namely the first drive surface 205 and the second drive surface 209 are also the mirror image symmetries.The first drive surface 205 and the second drive surface 209 all are configured to be suitable for obtaining required valve lift, because the first drive surface 205 and the second drive surface 209 are also the mirror image symmetric relations, therefore here only take the first drive surface 205 as the example explanation.

for example, this first drive surface 205 can precompute according to the different operating modes of motor the line style of this first drive surface 205, particularly, the line style of this first drive surface 205 can draw by the anti-mode that pushes away, as the valve lift curve that according to valve mechanism 100 different air valve lifts, should have and consider roller 301 and the first cam 203(and the second cam 207) position that contacts obtains corresponding the first drive surface 205(and the second drive surface 209) the shape line, obtained by numerous cam-shaped line scanning again, this for the ordinary skill in the art, all that appearance is intelligible.

Like this, when this motor turns round with a certain operating mode, have on the first drive surface 205 be suitable for this operating mode under be suitable for driving the line style part of the roller 301 of rocker arm body 300 most, thus by the roller 301 of change rocker arm body 300 and the cooperation position that contacts of this first drive surface 205, thereby make the lift amount of valve mechanism 100 suitable, guarantee in firing chamber to enter sufficient and suitable air quantity,, in order to fuel oil, fully burn, improve power output and the fuel economy of motor.

More specifically, as Figure 19 and shown in Figure 20, the first drive surface 205 and the second drive surface 209 all can comprise chamfered portion and planar section, when roller 301 coordinates with chamfered portion, the lift amount of valve mechanism 100 is less, particularly, roller 301 contacts the position of cooperation the closer to planar section with inclined-plane, lift amount is larger, roller 301 contacts the position and the planar section that coordinate with inclined-plane far away, to such an extent as to the less lift amount of lift amount is zero, roller 301 contacts with planar section while coordinating, and lift amount is maximum.Certainly, be understandable that, the present invention is not limited to this, in other embodiments of the present invention, the first drive surface 205 and the second drive surface 209 also can be inclined-plane or arc shaped surface or other profile, as long as the first drive surface 205 and the second drive surface 209 can be configured to be suitable for obtaining required valve lift, this is all that appearance is intelligible for the ordinary skill in the art.

As Fig. 3-shown in Figure 8, rocker arm body 300 is located between valve mechanism 100 and camshaft mechanism 200, and rocker arm body 300 comprises roller 301, and roller 301 is suitable for respectively coordinating with the first drive surface 205 and the second drive surface 209.Namely, when camshaft 201 rotation, the first drive surface 205 and the second drive surface 209 can press down the non-zero lift situation of roller 301(), thus rocker arm body 300 is back and forth moved up and down around the central axis of valve mechanism 100 to drive valve mechanism 100 as fulcrum integral body to lower swing take fulcrum structure 341.

As shown in Figure 2, actuating mechanism 400 is used for driving the cooperation position that contacts that the first cam 203 is synchronized with the movement in opposite directions with the second cam 207 or is synchronized with the movement dorsad to change roller 301 and the first drive surface 205 and the second drive surface 209, regulate the lift of valve mechanism 100 with continuous variable ground, that is to say, actuating mechanism 400 drives the first cam 203 and the second cam 207 mirror movementses, thereby change the cooperation position that contacts of roller 301 and the first drive surface 205 and the second drive surface 209, thereby realize the purpose of adjusting valve lift amount.

Being understood that of value, above-mentioned " the first cam 203 and the second cam 207 are synchronized with the movement in opposite directions " can be understood as: the movement velocity equal and opposite in direction when the first cam 203 and the second cam 207 motion close to each other and the first cam 203 and the second cam 207 close motion.Above-mentioned " the first cam 203 and the second cam 207 are synchronized with the movement dorsad " can be understood as: the first cam 203 and the second cam 207 move and the first cam 203 and the second cam 207 movement velocity equal and opposite in direction during away from motion away from each other.In brief, the first cam 203 and the second cam 207 mirror movementses.

Like this, due to the first cam 203 and the second cam 207 mirror movementses, therefore roller 301 is that (mirror image) is relative with the first drive surface 205 and roller 301 with the cooperation position that contacts of the second drive surface 209, that is to say, suppose to remove this moment any one in the first cam 203 and the second cam 207, only by one of them driven roller 301, the lift amount of valve mechanism 100 and two drive surface simultaneously during driven roller 301 lift amount of valve mechanism 100 be the same, this is obviously that appearance is intelligible for the ordinary skill in the art.

In addition, need to prove, in description of the invention, as there is no specified otherwise, preferably, take valve mechanism 100 as air inlet side valve mechanism 100 as example, as shown in Figure 1 in reference, in this embodiment, valve mechanism 100 is the valve mechanism 100 of air inlet side, and the valve mechanism 100 of exhaust side does not arrange variable air valve lift apparatus 1000 according to an embodiment of the invention.Certainly, be understandable that, this valve mechanism 100 also can be exhaust valve, i.e. this variable air valve lift apparatus 1000 lift of also can be applicable to regulate exhaust valve.

Variable air valve lift apparatus 1000 according to the embodiment of the present invention, solved well motor in the requirement to distribution of high speed high load working condition and low speed small load condition, reduce pumping loss, also realized simultaneously the continuous variable of valve lift, greatly improve the power performance and the economy performance of motor, reduced the discharging of the harmful gases such as HC, CO, CO2, NOx.

Below with reference to Fig. 1-Figure 24 detailed description actuating mechanism 400 according to some embodiments of the invention.

Actuating mechanism 400 can comprise hydraulic valve block 401, first piston 411, the second piston 431, the first driveshaft 412, the second driveshaft 432, fuel feeding oil return mechanism, elasticity reset device 441 and elastic component 421 according to an embodiment of the invention.

As shown in figure 15, have the first chamber 402 and the second chamber 403 in hydraulic valve block 401, hydraulic valve block 401 can removably be located on cylinder head by bolt, certainly also can directly be welded on cylinder cap.As shown in Fig. 9-Figure 10,12, first piston 411 is located at movably in the first chamber 402 and the first chamber 402 is isolated into the first valve pocket 404 independent of each other and the second valve pocket 405, that is to say, the first valve pocket 404 and the second valve pocket 405 are disconnected mutually independently of one another, and the liquid in the first valve pocket 404 for example hydraulic oil in hydraulic oil and the second valve pocket 405 can not circulate by the internal face of first piston 411 and the first chamber 402.

Namely, thereby first piston 411 is engaged in hermetically in the first chamber 402 this first chamber 402 is isolated into the first valve pocket 404 and the second valve pocket 405, first piston 411 can be in the first interior movement of chamber 402, therefore the volume of the first valve pocket 404 and the second valve pocket 405 is variable, for example with reference to Fig. 9, Figure 10 and shown in Figure 12, when first piston 411 is moved to the left, the compressed and smaller volume of the first valve pocket 404, the volume phase strain of the second valve pocket 405 is large.

Equally, the second piston 431 is located at movably in the second chamber 403 and the second chamber 403 is isolated into the 3rd valve pocket 406 independent of each other and the 4th valve pocket 407, that is to say, the 3rd valve pocket 406 and the 4th valve pocket 407 are disconnected mutually independently of one another, and the liquid in the 3rd valve pocket 406 for example hydraulic oil in hydraulic oil and the 4th valve pocket 407 can not circulate by the internal face of the second piston 431 and the second chamber 403.

Namely, thereby the second piston 431 is engaged in hermetically in the second chamber 403 this second chamber 403 is isolated into the 3rd valve pocket 406 and the 4th valve pocket 407, the second piston 431 can be in the second interior movement of chamber 403, therefore the volume of the 3rd valve pocket 406 and the 4th valve pocket 407 is variable, for example with reference to Fig. 9, Figure 10 and shown in Figure 12, when the second piston 431 is moved to the left, the compressed and smaller volume of the 3rd valve pocket 406, the volume phase strain of the 4th valve pocket 407 is large.

Wherein, the 3rd valve pocket 406 is identical with the first valve pocket 404 shapes and communicate with each other, in other words, the 3rd valve pocket 406 is identical with the length of the first valve pocket 404, shape of cross section is identical and sectional area equates, that is to say, while being full of liquid such as hydraulic oil in the 3rd valve pocket 406 and the first valve pocket 404, the volume of this liquid equates.With reference to Fig. 9, Figure 10 and shown in Figure 12, the first valve pocket 404 be arranged in parallel with the 3rd valve pocket 406 and the first valve pocket 404 is communicated with an end (as the left end in Fig. 9, Figure 10 and Figure 12) of the 3rd valve pocket 406.

The 3rd valve pocket 406 and the first valve pocket 404 communicate with each other, and the liquid of these two valve pockets such as hydraulic oil can flow mutually like this.With reference to Fig. 9 and shown in Figure 10, be full of liquid in the 3rd valve pocket 406 and the first valve pocket 404, preferably, this liquid can be hydraulic oil.

The first driveshaft 412 is connected with first piston 411 and with first piston 411, moves, for example a side of an end of the first driveshaft 412 (left end in Fig. 9 and Figure 10) and first piston 411 (right flank in Fig. 9 and Figure 10) is connected, being provided with the first shift fork 413, the first shift forks 413 on the first driveshaft 412 is suitable for by the following clutch shaft bearing that will mention 221 pushing the first cams 203 to the motion of the direction near the second cam 207.As shown in Figure 9 and Figure 10, the first shift fork 413 can be connected to the other end (right-hand member in Fig. 9 and Figure 10) of the first driveshaft 412, and the first shift fork 413 and the first driveshaft 412 can be one-body molded.

The second driveshaft 432 is connected with the second piston 431 and with the second piston 431, moves, for example a side of an end of the second driveshaft 432 (left end in Fig. 9 and Figure 10) and the second piston 431 (right flank in Fig. 9 and Figure 10) is connected, being provided with the second shift fork 433, the second shift forks 433 on the second driveshaft 432 is suitable for by the following clutch shaft bearing that will mention 221 pushing the second cams 207 to the motion of the direction near the first cam 203.As shown in Figure 9 and Figure 10, the second shift fork 433 can be connected to the other end (right-hand member in Fig. 9 and Figure 10) of the second driveshaft 432, and the second shift fork 433 and the second driveshaft 432 can be one-body molded.

With reference to Fig. 9-shown in Figure 11, the first shift fork 413 and the second shift fork 433 lay respectively at the outside of the first cam 203 and the second cam 207, and the first shift fork 413 and the second shift fork 433 are respectively used to promote the first cam 203 and the second cam 207 to the direction synchronizing moving near each other.With reference to Fig. 9 and shown in Figure 10, the length of the first driveshaft 412 and the second driveshaft 432 does not wait, and can avoid like this interfering between the first shift fork 413 and the second shift fork 433.

Fuel feeding oil return mechanism (can comprise control valve 461 and engine oil pressure chamber 465) is communicated with the second valve pocket 405, and the fuel feeding oil return mechanism is used for to the second interior output hydraulic pressure oil of valve pocket 405 or receives the hydraulic oil that refluxes from the second valve pocket 405.Elasticity reset device 441 is located in the 4th valve pocket 407 and is suitable for flexibly compressing the second piston 431, and elastic component 421 is suitable for flexibly being pressed between the first cam 203 and the second cam 207.Elastic component 421 is compressed when the first cam 203 and the second cam 207 close motion, the deposit elastic potential energy, elastic component 421 can discharge the elastic potential energy of deposit when the first cam 203 and the second cam 207 need to deviate from motion, drives the first cam 203 and the second cam 207 and deviates from motion.

When initial equilibrium conditions, the elastic force of the first valve pocket 404, the second valve pocket 405 and the 3rd valve pocket 406 internal pressures and elasticity reset device 441, the elastic force of elastic component 421 form balance, this moment, first piston 411 and the second piston 431 stress balances and relative position were constant, for example with reference to Fig. 9 and shown in Figure 10, it is initial rest position that first piston 411 in Fig. 9 and Figure 10 and the position of the second piston 431 can be understood as, but, be appreciated that and the present invention includes but be not limited to this.

When needs are regulated the lift amount of valve mechanism 100, the first cam 203 and the second cam 207 are made mirror movements, be synchronous relative motion or synchronously motion dorsad, when synchronous relative motion, by the first shift fork 413 and the second shift fork 433 promote the first cams 203 and the second cam 207 close to each other, when synchronously moving dorsad, elastic component 421 promotes the first cam 203 and the second cam 207 deviates from motion.

Particularly, when the first cam 203 and the second cam 207 close motion, the fuel feeding oil return mechanism is to the second interior output hydraulic pressure oil of valve pocket 405, along with constantly entering of hydraulic oil, pressure in the second valve pocket 405 increases gradually, thereby destroys previous balance, makes the direction motion of first piston 411 to compression the first valve pocket 404, for example in the example of Fig. 9 and Figure 10, first piston 411 is to left movement.

After the first valve pocket 404 is compressed, liquid in the first valve pocket 404 can flow to by the connected part of the first valve pocket 404 and the 3rd valve pocket 406 the 3rd valve pocket 406, the volumetric expansion of the 3rd valve pocket 406 thus, thereby promote the second piston 431 to the direction motion opposite with first piston 411, for example in the example of Fig. 9 and Figure 10, the second piston 431 moves right.

Because the first valve pocket 404 is identical with the 3rd valve pocket 406 shapes, therefore the first valve pocket 404 due to the compressed volume that reduces with the 3rd valve pocket 406 because the volume that expansion increases is identical, the moving direction of first piston 411 and the second piston 431 is opposite and move distance equal thus.

Take the actuating mechanism 400 shown in Fig. 9 and Figure 10 as example, be transported to the second valve pocket 405 when interior at hydraulic oil from the fuel feeding oil return mechanism, first piston 411 move distance left is L, the second piston 431 moves right distance and also is L, the second piston 431 moves right meeting pressure elasticity resetting means 441, thereby makes 441 accumulation of energys of contracting elasticity reset device.When the fuel feeding oil return mechanism stops to the second valve pocket 405 interior supply hydraulic fluid, pressure and the elastic force of elasticity reset device 441, the elastic force of elastic component 421 in the first valve pocket 404, the second valve pocket 405 and the 3rd valve pocket 406 will reach balance again.

In this process, first piston 411 moves to left drive the first driveshaft 412 and the first shift fork 413 is moved to the left, the first shift fork 413 will promote the first cam 203 and be moved to the left, equally, the second piston 431 moves to right drive the second driveshaft 432 and the second shift fork 433 is moved right, the second shift fork 433 will promote the second cam 207 and move right, i.e. the first cam 203 and the second cam 207 synchronous relative motions.In the first cam 203 and the second close movement process of cam 207, elastic component 421 is with compressed, thus the deposit elastic potential energy.

and when the first cam 203 and the second cam 207 deviate from motion, part hydraulic oil in the second valve pocket 405 can be back to the fuel feeding oil return mechanism, thereby the oil pressure in the second valve pocket 405 reduces, balance before is destroyed, first piston 411 reversing motions (with moving direction is opposite before), the first valve pocket 404 volumes increase, thereby the liquid in the 3rd valve pocket 406 flows in the first valve pocket 404 again from connectivity part, thereby the volume of the 3rd valve pocket 406 reduces, and then second piston 431 reversing motion under the elastic force effect of elasticity reset device 441 (with moving direction is opposite before).

For example, take the actuating mechanism 400 shown in Fig. 9 and Figure 10 as example, at hydraulic oil when being partly refluxed to the fuel feeding oil return mechanism in the second valve pocket 405, first piston 411 will move right, the second piston 431 is to left movement, and displacement equal and opposite in direction both, opposite direction, until the elastic force of the elastic force of the pressure in the first valve pocket 404, the second valve pocket 405 and the 3rd valve pocket 406 and elasticity reset device 441, elastic component 421 will reach new balance again,

first piston

411 and 431, the second piston no longer move.In this process, because the first shift fork 413 and the second shift fork 433 deviate from motion, thereby under elastic component 421 elastic force effects, elastic component 421 will promote the first cam 203 and the second cam 207 synchronously deviates from motion.

Can be used in variable air valve lift apparatus according to the actuating mechanism 400 of the embodiment of the present invention, the first cam 203 in driving cam axis mechanism 200 and the second cam 207 actions, realize the continuous variable of valve lift, simple in structure, compact, convenient integrated being arranged in cylinder head, and this actuating mechanism 400 can be arranged on the residing height of camshaft, can additionally not increase the height of cylinder head.And this actuating mechanism 400 adopts hydraulic control, and the driving process is more reliable and precision is high thereby make.

according to one embodiment of present invention, as shown in figure 15, hydraulic valve block 401 hollows and inside are provided with spacing block 408, spacing block 408 is isolated into the first chamber 402 and the second chamber 403 with the inner space of hydraulic valve block 401, the free-ended end face of spacing block 408 (left side in Figure 15) with, the internal face of a sidewall relative with free end end face spacing block 408 hydraulic valve block 401 is spaced apart, in other words, the free-ended end face of spacing block 408 is spaced apart with the internal face of a sidewall of the hydraulic valve block 401 relative with it, thereby form communicating passage to be communicated with the first valve pocket 404 and the 3rd valve pocket 406.

With reference to Fig. 9 and shown in Figure 10, an end of the first driveshaft 412 inwardly extend in the second valve pocket 405 with on a side that is fixed on first piston 411 from a sidewall of the second valve pocket 405.For example, with reference to Fig. 9 and shown in Figure 10, the left end of the first driveshaft 412 inwardly extend in the second valve pocket 405 from the right side wall of the second valve pocket 405, and the left end of this first driveshaft 412 is connected with the right flank of first piston 411.

Equally, an end of the second driveshaft 432 inwardly extend in the 4th valve pocket 407 with on a side that is fixed on the second piston 431 from a sidewall of the 4th valve pocket 407.For example, with reference to Fig. 9 and shown in Figure 10, the left end of the second driveshaft 432 inwardly extend in the 4th valve pocket 407 from the right side wall of the 4th valve pocket 407, and the left end of this second driveshaft 432 is connected with the right flank of the second piston 431.

Further, as shown in Figure 9 and Figure 10, elasticity reset device 441 springs, spring housing stretches on part in the 4th valve pocket 407 the second driveshaft 432, such the second driveshaft 432 can be realized location to spring, avoid spring to move freely, reverse in the 4th valve pocket 407, improve the stability of actuating mechanism 400.

Wherein, the joint of the second driveshaft 432 and the second piston 431 is preferably placed at the central position of the second piston 431, and spring housing can, better to second piston 431 application of forces, make the second stressed balance more of piston 431 on the second driveshaft 432 like this.Certainly, be understandable that, the present invention is not limited to this, in other embodiments of the present invention, also independent spring stack can be set in the 4th valve pocket 407, spring stack can be set directly on the internal face of the 4th valve pocket 407, can certainly be arranged on a side that is positioned at the 4th valve pocket 407 of the second piston 431, spring can be enclosed within on spring stack, thereby by spring stack, is positioned, and avoids spring to move freely.

Preferably,, with reference to Figure 13 and shown in Figure 16, be provided with the leakage hole 462 that is communicated with the 4th valve pocket 407 on hydraulic valve block 401.By leakage hole 462 is set, when the second piston 431 moves to the direction of compression the 4th valve pocket 407, can avoid in the 4th valve pocket 407 because sealing causes the air in the 4th valve pocket 407 compressed, can improve the operation precision of actuating mechanism 400 thus, avoid the air in the 4th valve pocket 407 to be caused first piston 411 and the second piston 431 to drive difficulty by excessive compression.Leakage hole 462 can be one, and the shape of leakage hole 462 does not have specific (special) requirements, and it can be opened in the bottom of the 4th valve pocket 407, can certainly be opened in the sidepiece of the 4th valve pocket 407.

Around the first driveshaft 412 rotations, the situation that the first shift fork 413 separates with the first cam 203 appears for fear of the first shift fork 413, preferably, the first shift fork 413 should be limited rotary freedom, and namely the first shift fork 413 moves axially with the first driveshaft 412 only and can not rotate together.in view of this, preferably, according to one embodiment of present invention, first piston 411 is cuboid shape or the square bodily form, and the inner peripheral surface of the first chamber 402 is the shape adaptive with first piston 411 outer circumferential faces, take first piston 411 as example as square body, the cross section of the inner peripheral surface of the first chamber 402 is also square, first piston 411 not only can make the first valve pocket 404 and the second valve pocket 405 keep apart when the first interior slip of chamber 402 like this, and first chamber 402 can also the rotary freedom of first piston 411 be limited, avoid first piston 411 to rotate, and then limited the rotary freedom of the first driveshaft 412 and the first shift fork 413.

based on same reason, the second piston 431 is cuboid shape or the square bodily form, and the inner peripheral surface of the second chamber 403 is the shape adaptive with the outer circumferential face of the second piston 431, take the second piston 431 as square body as example, the cross section of the inner peripheral surface of the second chamber 403 is also square, such the second piston 431 not only can make the 3rd valve pocket 406 and the 4th valve pocket 407 keep apart when the second interior slip of chamber 403, and second chamber 403 can also the rotary freedom of the second piston 431 be limited, avoid the second piston 431 to rotate, and then limited the rotary freedom of the second driveshaft 432 and the second shift fork 433.

Thus, realized the restriction to the first shift fork 413 and the second shift fork 433 rotary freedoms, avoided freely rotating with the second shift fork 433 due to the first shift fork 413 and the generation of the situation of with respective cams, separating, guaranteed that actuating mechanism 400 is reliable.

Wherein, be understandable that, above-mentioned is only schematically to illustrate as the square bodily form as example take first piston 411 and the second piston 431, can not be interpreted as it is to a kind of restriction of the present invention.

But, the present invention is not limited to this, in other embodiments of the present invention, actuating mechanism 400 also can arrange independent positioning part structure, be used for the location of realization to the first driveshaft 412 and the second driveshaft 432, prevent that the first driveshaft 412 and the second driveshaft 432 from freely rotating, thereby prevent that the first shift fork 413 and the second shift fork 433 from freely rotating.

For example, on the first driveshaft 412 and the second driveshaft 432, projection can be set, the positioning part structure can be the long strip groove adaptive with projection, projection can be moved along the length direction of the first driveshaft 412 or the second driveshaft 432 in groove, but, due to the mating reaction of projection with groove, can prevent that the first driveshaft 412 and the second driveshaft 432 from freely rotating.

According to a preferred embodiment of the present invention, as Fig. 9-Figure 10, shown in Figure 14, the fuel feeding oil return mechanism comprises engine oil pressure chamber 465 and control valve 461, be connected by being communicated with oil duct 467 between engine oil pressure chamber 465 and the second valve pocket 405, namely the hydraulic oil in the second valve pocket 405 can enter in the fuel feeding oil return mechanism by being communicated with oil duct 467, and perhaps the hydraulic oil in the fuel feeding oil return mechanism can be communicated with oil duct 467 by this and enters in the second valve pocket 405.Engine oil pressure chamber 465 has entrance point, the external hydraulic pipeline can be communicated with entrance point, thereby the outer liquid force feed can enter in engine oil pressure chamber 465 by this entrance point, perhaps the hydraulic oil in engine oil pressure chamber 465 can flow out by entrance point, control valve 461 can be located in engine oil pressure chamber 465 and be positioned at the entrance point place, control valve 461 is used to open or close engine oil pressure chamber 465, thereby with engine oil pressure chamber 465 and external hydraulic pipeline connection or disconnection.

Preferably, according to one embodiment of present invention, control valve 461 can be two-position three way magnetic valve.Certainly, easily be understood that, control valve 461 of the present invention comprises two-position three way magnetic valve but is not limited to this, for other, can realize opening/closing machine oil pressure chamber 465 and be easy to be arranged in interior control valve 461 structures in engine oil pressure chamber 465, all is applicable to the present invention.

According to some embodiments of the present invention, as shown in figure 10, actuating mechanism 400 also comprises displacement measuring device 463, the displacement that this displacement measuring device 463 is used for measuring the first driveshaft 412 and/or the second driveshaft 432.For example, preferably, because the first driveshaft 412 and the second driveshaft 432 are made mirror movements, the displacement that therefore by a displacement measuring device 463 is set, is used for measuring one of the first driveshaft 412 and second driveshaft 432, just can obtain the displacement of another driveshaft indirectly.

by displacement measuring device 463 is set, can accurately obtain the displacement of the first driveshaft 412 and the second driveshaft 432, thereby obtain the information such as the moving direction of the first driveshaft 412 and the second driveshaft 432 and displacement distance, and then convenient controller by vehicle such as ECU control hydraulic oil and enter the total amount of the 4th valve pocket 407, realize the accurate control of the first driveshaft 412 and the second driveshaft 432 displacements, also can revise according to the result that displacement measuring device 463 records the position of the first driveshaft 412 and the second driveshaft 432 simultaneously, make the position of the first driveshaft 412 and the second driveshaft 432 more accurate, thereby obtain the valve lift amount of required the best, improve engine combustion efficiency and power output.

Wherein, be understandable that, displacement measuring device 463 has been prior art, and is well known for ordinary skill in the art, can be position transducer etc. such as displacement measuring device 463, not make specified otherwise for concrete structure and the working principle of displacement measuring device 463 here.

But the present invention is not limited to this, and in another embodiment of the present invention, as shown in Figure 9, actuating mechanism 400 also comprises pressure-detecting device 466, and this pressure-detecting device 466 is used for the pressure of measuring machine oil pressure chamber 465 interior hydraulic oil.Thus, the pressure in the engine oil pressure chamber 465 that records by pressure-detecting device 466, thus can indirectly calculate the position of first piston 411 and the second piston 431, thus the position information of the first driveshaft 412 and the second driveshaft 432 obtained.Need to prove, the particular location that the pressure informations in the engine oil pressure chamber 465 that records by pressure-detecting device 466 calculate first piston 411 and the second piston 431 for the ordinary skill in the art, is all understandable.

According to a preferred embodiment of the present invention, as shown in figure 11, the free end of the first shift fork 413 is provided with the first roller 471, the first rollers 471 and rollably pushes against the first cam 203, as shown in Figure 11 in reference, the outer circumferential face of the first roller 471 is the outside of rolling surface pushing and pressing the first cam 203.The free end of the second shift fork 433 is provided with the second roller 472, the second rollers 472 and rollably pushes against the second cam 207, and is as shown in Figure 11 in reference, and the outer circumferential face of the second roller 472 is the outside of rolling surface pushing and pressing the second cam 207.

By the first roller 471 and the second roller 472 being set to drive respective cams near motion, can reduce the wearing and tearing of roller and cam, make driving more reliable, increase the life-span of actuating mechanism 400.

Be appreciated that the first roller 471 and the second roller 472 can directly be pressed on respectively on the outer side surface of the first cam 203 and the second cam 207.Certainly, for the wearing and tearing that reduce the first cam 203 and the second cam 207, preferably, as shown in figure 11, the outside of the first cam 203 and the second cam 207 can be respectively arranged with platen 464, platen 464 is fixed on the outside of the first cam 203 or the second cam 207 and with respective cams, rotates, the first roller 471 and the second roller 472 compress respectively the platen 464 of respective side accordingly, and not directly compress respective cams, can avoid like this roller directly to contact with respective cams and cause respective cams wearing and tearing aggravation, affecting the life-span of cam.

According to other embodiments of the present invention, as shown in figure 19, actuating mechanism 400 also comprises clutch shaft bearing 221, clutch shaft bearing 221 be suitable for being enclosed within on camshaft 201 and lay respectively at the first cam 203 and the first shift fork 413 and the second cam 207 and the second shift fork 433 between.That is to say, variable air valve lift apparatus comprises two clutch shaft bearings 221 according to an embodiment of the invention, one of them clutch shaft bearing 221 is located between the first cam 203 and the first shift fork 413, and another clutch shaft bearing 221 is located between the second cam 207 and the second shift fork 433.

By between shift fork and cam (the first cam 203 and the second cam 207), clutch shaft bearing 221 being set, move vertically thereby be convenient to the shift fork driving cam, avoid between shift fork and cam directly contact friction to affect the life-span of cam.In brief, this embodiment is by clutch shaft bearing 221 is set, thereby with above-described embodiment, compares, and platen 464 and the first roller 471 and the second roller 472 in above-described embodiment can be set.

Alternatively, as shown in figure 19, clutch shaft bearing 221 comprises inner ring 223 and outer ring 225, inner ring 223 is provided with roll structure 227 between inner ring 223 and outer ring 225 so that can rotate relatively with outer ring 225, inner ring 223 and the first cam 203 or the second cam 207 preferably fit tightly together, and outer ring 225 and the first shift fork 413 or the second shift fork 433 preferably fit tightly together.

As shown in figure 19, the relative inner of the first cam 203 and the second cam 207 all is formed with the locating slot 221 that is suitable for locating elastic component 421, in other words, the first cam 203 is provided with locating slot 221 towards a side of the second cam 207, the second cam 207 also is formed with locating slot 221 towards a side of the first cam 203, and these two locating slots 221 are used for installing location elastic component 421 as spring.

Certainly, be understandable that, elastic component 421 also can directly be positioned on camshaft 201, for example according to one embodiment of present invention, variable air valve lift apparatus can also comprise locating piece (scheming not shown), this locating piece is used for elastic component 421 is fixed on bent axle as spring, and for example this locating piece can be screw or buckle structure, and its fixed position can be positioned at the axial centre of elastic component 421.

Below with reference to Fig. 1-Figure 24, the course of action of actuating mechanism 400 is according to an embodiment of the invention described.

With reference to shown in Figure 10, the position of the first driveshaft 412 shown in Figure 10 and the second driveshaft 432 can be the initial position of the first driveshaft 412 and the second driveshaft 432, this moment, the first driveshaft 412 was concordant with being connected the end that the left end of driveshaft 432 namely is connected with respective pistons, and the right-hand member of the first driveshaft 412 and the second driveshaft 432 can stagger.But, should be appreciated that the present invention is not limited to this.

When needs are regulated the lift amount of valve mechanism, for example increase the lift amount of valve mechanism, this moment, the first cam 203 and the second cam 207 needed near the motion certain distance.

as shown in figure 10, this moment, control valve 461 was opened, hydraulic oil in the external hydraulic pipeline can enter in engine oil pressure chamber 465 by control valve 461, the interior oil pressure in engine oil pressure chamber 465 increases, thereby hydraulic oil enters into the second valve pocket 405 by being communicated with oil duct 467, the second interior oil pressure of valve pocket 405 increases, thereby first piston 411 is moved to the left, first piston 411 be moved to the left can compression the first valve pocket 404 volume so that the liquid part in the first valve pocket 404 enter in the 3rd valve pocket 406 from connectivity part, the 3rd interior fluid pressure of valve pocket 406 increases, thereby the second piston 431 is moved right, the second piston 431 moves right and can push elasticity reset device 441, make elasticity reset device 441 accumulation of energys.

in this process, the first driveshaft 412 and the first shift fork 413 are moved to the left under the driving of first piston 411, the first shift fork 413 promotes the first cam 203 to left movement by its free-ended first roller 471, meanwhile, the second driveshaft 432 and the second shift fork 433 move right under the driving of the second piston 431, the second shift fork 433 promotes the second cam 207 by its free-ended second roller 472 and moves right, particularly, because first piston 411 is opposite with the second piston 431 moving direction and speed is identical, therefore the first cam 203 is also identical near the speed of motion with the second cam 207, the first cam 203 and the second cam 207 mirror movements relations.

on this basis, when the lift amount of needs change valve mechanism for example reduces lift amount, control valve 461 can be opened so that the part hydraulic oil in engine oil pressure chamber 465 releases, the cause of releasing due to the hydraulic oil in engine oil pressure chamber 465, oil pressure in the second valve pocket 405 that makes engine oil pressure chamber 465 and with it, be communicated with all descends, this moment, first piston 411 and the second piston 431 were in nonequilibrium state, the elastic potential energy of deposit before elasticity reset device 441 can discharge, promote the second piston 431 to left movement (with moving direction is opposite before), the second piston 431 compresses the 3rd valve pocket 406 conversely, liquid in the 3rd valve pocket 406 comes back in the first valve pocket 404 by connected part, volume in the first valve pocket 404 will increase, thereby make first piston 411 move right (with moving direction is opposite before) under the promotion of liquid, first piston 411 moves right and can compress the second valve pocket 405, thereby the hydraulic oil in the second valve pocket 405 is leaked in engine oil pressure chamber 465, and finally reach new balance.

In this process, the elastic potential energy of deposit before elastic component 421 will discharge, drive the first cam 203 and the second cam 207 moves dorsad, during motion the first cam 203 constantly (can by platen 464) compress the first roller 471, the second cam 207 (can by platen 464) constantly compresses the second roller 472, until first piston 411 and the second piston 431 reach new state of equilibrium again.

in the process of regulating, the controller of vehicle such as ECU can select suitable valve lift amount according to the motor current working, first piston 411 and the 431 pairs of valve lift amount that should select of the second piston have a specific activation point, enter the accurate control of the total amount realization of the hydraulic oil in the second valve pocket 405 to first piston 411 and the second piston 431 positions by control, wherein displacement transducer can feed back the concrete displacement information of the first driveshaft 412 and the second driveshaft 432, ECU can adjust and/or revise with Indirect method and/or revise the position of the first driveshaft 412 and the second driveshaft 432 particular location of first piston 411 and the second piston 431 according to this displacement information, thereby improve the accuracy of controlling.

Wherein, in above-mentioned course of action, enter in engine oil pressure chamber 465 with hydraulic oil in external hydraulic pipeline that engine oil pressure chamber 465 is communicated with or the hydraulic oil in engine oil pressure chamber 465 flows out and can realize by the oil pump that is arranged on the external hydraulic pipeline, this obviously easily understands and is easy to realize for the ordinary skill in the art.

1-Figure 24 describes cam rocker arm assembly according to some embodiments of the invention in detail with reference to the accompanying drawings.

According to one embodiment of present invention, the cam rocker arm assembly comprises above-mentioned camshaft mechanism 200 and rocker arm body 300.

With reference to Figure 22-shown in Figure 24, rocker arm body 300 also comprise

air valve bridge

311 and 321, two fixed plates 321 of two fixed plates parallel and be located at relative to one another on air valve bridge 311, roller 301 is folded between two fixed plates 321 pivotly.

Air valve bridge 311 and two fixed plates 321 are preferably integrally formed, and for example, but air valve bridge 311 and fixed plate 321 one moulding by casting facilitate air valve bridge 311 and the whole manufacturing of fixed plate 321, simplified manufacturing technique like this.With reference to Fig. 4, Fig. 6 and shown in Figure 8, one side of air valve bridge 311 can be provided with fulcrum structure 341, the opposite side of air valve bridge 311 coordinates with valve mechanism 100, particularly, the top of valve mechanism 100 is connected or is close to the opposite side (i.e. a side far away apart from fulcrum structure 341) of air valve bridge 311, cam (the first cam 203 and the second cam 207) press-on roller 301 like this, roller 301 drives whole rocker arm bodies 300 and swings around fulcrum structure 341, thereby drives valve mechanism 100 actions.Therefore be understandable that, fulcrum structure 341 has been prior art, and is well known for ordinary skill in the art, and does not explain for concrete structure and the working principle of fulcrum structure 341 here.

Due to the cause that is provided with air valve bridge 311, so the bottom of each air valve bridge 311 can be provided with a plurality of valve mechanisms 100, and namely an air valve bridge 311 can drive a plurality of valve mechanisms 100 and moves simultaneously.In related domain, the intake and exhaust structures that many employings at present go with each other all the time, therefore preferably, each air valve bridge 311 preferably drives two valve mechanisms 100, more specifically, the valve mechanism 100 of two air inlet sides of each air valve bridge 311 preferred driving.

Like this, can simplify the structure of variable air valve lift apparatus 1000, facilitate variable air valve lift apparatus 1000 to be arranged in cylinder cap 2000, and improve drive efficiency.Certainly, alternatively, an air valve bridge 311 also can only drive a valve mechanism 100, and perhaps an air valve bridge 311 drives three or more valve mechanisms 100, and these technological schemes all fall within the scope of protection of the present invention.

According to one embodiment of present invention, roller 301 is folded between two fixed plates 321 pivotly by the bearing pin 331 that passes two fixed plates 321.Preferably, be provided with the second bearing (scheming not shown) between roller 301 and bearing pin 331, can reduce like this friction between roller 301 and bearing pin 331, improve the life-span of roller 301.

In another embodiment of the present invention, roller 301 is folded between two fixed plates 321 pivotly by the bearing pin 331 that passes two fixed plates 321, roller 301 is integrally formed with bearing pin 331, preferably, can be provided with the 3rd bearing between bearing pin 331 and fixed plate 321.

Preferably, be provided with limit structure (scheming not shown) on bearing pin 331, this limit structure be used for bearing pin 331 axially on restriction roller 301, prevent that roller 301 from moving axially, limit structure can be spacing preiection.

With reference to shown in Figure 22, two transverse sides and two fixed plates 321 of roller 301 are spaced apart respectively.Be understandable that, this laterally is the thickness direction of roller 301.Thus, roller 301 is spaced apart with fixed plate 321, rubs between can avoiding both, affects the life-span of roller 301.

According to one embodiment of present invention, be provided with the reinforcement structure on air valve bridge 311, this reinforcement structure can be stiffening rib, and this stiffening rib can be a plurality of and be evenly distributed on air valve bridge 311, to increase better the intensity of air valve bridge 311.Stiffening rib and air valve bridge 311 can be the one cast moldings, certainly, are understandable that, stiffening rib also can be welded on air valve bridge 311.

, with reference to Figure 22 and shown in Figure 24, be configured with the first roller cambered surface 303 adaptive with the first drive surface 205 on roller 301, and also be configured with the second roller cambered surface 305 adaptive with the second drive surface 209 on roller 301.Like this, coordinate with the chamfered portion of the first drive surface 205 in the first roller cambered surface 303 and the second roller cambered surface 305 while with the chamfered portion of the second drive surface 209, coordinating, this moment, cam (the first cam 203 and the second cam 207) contacted for the line line with roller 301 in theory.Can be provided with arc surface 307 between the first roller cambered surface 303 and the second roller cambered surface 305, when this arc surface 307 coordinated with the planar section of the first drive surface 205 and the second drive surface 209, the lift amount of valve mechanism 100 was maximum.Certainly, the present invention is not limited to this, in other embodiments of the invention, on roller 301 with the first drive surface 205 and the second drive surface 209 adaptive also can be inclined-plane or other profile.

The working procedure of variable air valve lift apparatus 1000 is in accordance with a preferred embodiment of the present invention described below with reference to Fig. 1-Figure 24.

At first with reference to Fig. 3 and Fig. 4, it is the zero lift position that the first cam 203 in these two figure, the second cam 207 contact with roller 301 that the position that coordinates can be understood as, this moment, camshaft 201 drive the first cams 203 and the second cam 207 rotated, the first cam 203 and the second cam 207 can press-on roller 301, be that rocker arm body 300 can wholely not swing around fulcrum structure 341, therefore the lift amount of valve mechanism 100 is zero at this moment, be the suction port of valve mechanism 100 airtight firing chambers, realize intelligent cylinder deactivation.

secondly, with reference to Fig. 5 and shown in Figure 6, after engine operating condition changes, for example engine speed improves, this moment, motor needed less air inflow, hydraulic oil enters in engine oil pressure chamber 465 by control valve 461, and then enter in the second valve pocket 405, directly to drive first piston 411, the first driveshaft 412 and the first shift fork 413 actions, indirectly drive simultaneously the second piston 431, the second driveshaft 432 and the second shift fork 433 actions (process that specifically drives is referring to above-mentioned description for actuating mechanism 400 course of action), so that the first shift fork 411 can certainly be a clutch shaft bearing 221 by a platen 464() pushing the first cam 203, the second shift fork 442 can certainly be another clutch shaft bearing 221 by another platen 464() pushing the second cam 207, make these two cams close, thereby change the cooperation position that contacts of roller 301 and the first drive surface 205 and the second drive surface 209.

With reference to Fig. 5 and shown in Figure 6, it is little lift location that the first cam 203 in these two figure, the second cam 207 can be understood as with the position that contacts cooperation of roller 301, this moment, camshaft 201 drive the first cams 203 and the second cam 207 rotated, the first cam 203 and the second cam 207 are with press-on roller 301, make rocker arm body 300 integral body swing by a small margin around fulcrum structure 341, thereby drive valve mechanism 100 and open suction port, therefore the lift amount of valve mechanism 100 is less at this moment, is suitable for the low engine speed small load condition.

finally, with reference to shown in Figure 7 and Figure 8, after engine operating condition further changes, for example the rotating speed of motor further improves, this moment, motor needed larger air inflow, more hydraulic oil enters in engine oil pressure chamber 465 by control valve 461, and then enter in the second valve pocket 405, directly to drive first piston 411, the first driveshaft 412 and the first shift fork 413 actions, indirectly drive simultaneously the second piston 431, the second driveshaft 432 and the second shift fork 433 actions (concrete driving principle is with above-mentioned consistent), so that the first shift fork 411 can certainly be a clutch shaft bearing 221 by a platen 464() further push the first cam 203, the second shift fork 442 can certainly be another clutch shaft bearing 221 by another platen 464() further push the second cam 207, make these two cams more close, thereby change the cooperation position that contacts of roller 301 and the first drive surface 205 and the second drive surface 209.

With reference to shown in Figure 7 and Figure 8, it is the high-lift position that the first cam 203 in these two figure, the second cam 207 can be understood as with the position that contacts cooperation of roller 301, this moment, camshaft 201 drive the first cams 203 and the second cam 207 rotated, the first cam 203 and the second cam 207 are with press-on roller 301, make rocker arm body 300 integral body around fulcrum structure 341 amplitude swings, thereby drive valve mechanism 100 and open suction port, therefore the lift amount of valve mechanism 100 is larger at this moment, is suitable for the high engine speeds high load working condition.

In this process, roller 301 can coordinate with the planar section of the first drive surface 205 and the planar section of the second drive surface 209, certainly, be understandable that, the invention is not restricted to this, the first drive surface 205 and the second drive surface 209 also can be inclined-plane, and in above-mentioned whole adjustment process, roller 301 all contacts cooperation with inclined-plane (the first drive surface 205 and the second drive surface 209).

when the operating mode of motor becomes low speed or small load condition again again, hydraulic oil in the second valve pocket 405 can part flow in the external hydraulic oil circuit by engine oil pressure chamber 465 and control valve 461, this moment is under the elastic force effect of elastic component 421 as spring, the first cam 203 and the second cam 207 will move dorsad, increase distance both, thereby what change roller 301 and the first drive surface 205 and the second drive surface 209 contacts cooperation position (for example becoming above-mentioned little lift location again), and then the lift of reduction valve mechanism 100, make valve lift corresponding with the operating mode of motor.

In brief, according to a preferred embodiment of the present invention, enter or flow out the oil mass of the hydraulic oil in the second valve pocket 405 by control, can realize the first cam 203 and the second cam 207 near or away from (coordinate with elastic component 421), the first cam 203 and the second cam 207 near or away from rear, roller 301 changes with the cooperation position that contacts of the second drive surface 209 with the first drive surface 205 on the second cam 207 with the first cam 203, thereby can obtain valve lift amount required and that adapt with the motor current working.

For the first drive surface 205 on the first cam 203, the second drive surface 209 and the first roller cambered surface 303 on roller 301, the second roller cambered surface 305 and arc surface 307 on the second cam 207, can carry out its line style of adaptability design according to different motors, thereby at motor, be under different operating modes, by the contact cooperation position of change roller 301 with the first cam 203 and the second cam 207, realize the adaptability adjusting of valve lift, to meet the motor current working, this is obviously that appearance is intelligible for the ordinary skill in the art.

In addition, need to prove, in description of the invention, above-mentioned with a camshaft 201 take and on first cam 203 and the second cam 207 as example is only schematically to illustrate, can not be interpreted as it is to a kind of restriction of the present invention.Two air inlet side valve mechanisms 100 of an above-mentioned camshaft 201, first cam 203 and second cam 207 preferred corresponding cylinders, those of ordinary skill in the art is on the basis of having read the above-mentioned disclosure of specification, conventional techniques means and common practise in conjunction with related domain, many groups the first cam 203 and the second cam 207 obviously can be set on a camshaft 201, for example, take the motor of four-cylinder as example, four pairs of the first cams 203 and the second cam 207(obviously can be set as shown in Figure 2).

Generally speaking, be used for according to an embodiment of the invention the variable air valve lift apparatus 1000 of motor, can have following advantage:

1) variable air valve lift apparatus 1000 of the embodiment of the present invention can be realized the continuous variable of valve lift;

2) variable air valve lift apparatus 1000 of the embodiment of the present invention can be regulated valve opening duration and switching according to engine operating condition constantly, makes charging efficiency the best under each operating mode of motor, is of value to power character, Economy and the discharging of motor;

3) variable air valve lift apparatus 1000 of the embodiment of the present invention is applicable to petrol engine and the diesel engine of any camshaft actuated valve mechanism 100, and is applied widely, is beneficial to Negative valve overlap, emptying supercharging, cylinder stopping technique and the HCCI technology of realizing;

4) variable air valve lift apparatus 1000 of the embodiment of the present invention coordinates the VVT use can realize port timing and the full variable technique of valve lift;

5, the compact structure of the variable air valve lift apparatus 1000 of the embodiment of the present invention, do not increase the motor height, is convenient to arrange, cost is low.

Below the simple motor of describing according to the embodiment of the present invention.

Motor comprises according to the actuating mechanism 400 of describing in the above embodiment of the present invention according to an embodiment of the invention.

The motor of the embodiment of the present invention, due to the cause of the actuating mechanism 100 that adopts above-mentioned variable air valve lift apparatus 1000, therefore has the advantages such as power character is strong, fuel economy is good.

Need to prove, be all prior art according to other configuration example of the motor of the embodiment of the present invention such as body group, connecting rod, cooling system, lubrication system etc., and be well known for ordinary skill in the art, can adopt the part identical or close with prior art for these, describe in detail no longer one by one herein.

Below the simple vehicle of describing according to the embodiment of the present invention.

Vehicle comprises motor according to the above embodiment of the present invention according to an embodiment of the invention.

According to the vehicle of the embodiment of the present invention due to the cause that adopts above-mentioned motor, so good dynamic property, fuel economy is good, discharges low.

Need to prove, be all prior art according to other configuration example of the vehicle of the embodiment of the present invention such as speed changer, braking system, transmission system, vehicle body etc., and be well known for ordinary skill in the art, can adopt the part identical or close with prior art for these, describe in detail no longer one by one herein.

In the description of this specification, the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to be contained at least one embodiment of the present invention or example in conjunction with specific features, structure, material or the characteristics of this embodiment or example description.In this manual, to the schematic statement of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or characteristics can be with suitable mode combinations in any one or more embodiments or example.In addition, those skilled in the art can engage different embodiments or the example described in this specification and make up.

Although the above has illustrated and has described embodiments of the invention, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, modification, replacement and modification.

Claims

1. actuating mechanism that is used for the variable air valve lift apparatus of motor, described variable air valve lift apparatus comprises camshaft mechanism, and described camshaft mechanism comprises camshaft, the first cam and the second cam, it is characterized in that, and described actuating mechanism comprises:

Hydraulic valve block, have the first chamber and the second chamber in described hydraulic valve block;

First piston, described first piston are located at movably in described the first chamber and described the first chamber isolation are become the first valve pocket independent of each other and the second valve pocket;

The second piston, described the second piston is located at movably in described the second chamber and described the second chamber isolation is become the 3rd valve pocket independent of each other and the 4th valve pocket, wherein said the 3rd valve pocket is identical with described the first valve pocket shape and communicate with each other, and is full of liquid in described the 3rd valve pocket and described the first valve pocket;

The first driveshaft, described the first driveshaft is connected with described first piston and with described first piston, moves, and is provided with the first shift fork on described the first driveshaft;

The second driveshaft, described the second driveshaft is connected with described the second piston and with described the second piston, moves, and is provided with the second shift fork on described the second driveshaft;

The fuel feeding oil return mechanism, described fuel feeding oil return mechanism is communicated with described the second valve pocket; And

Elasticity reset device, described elasticity reset device are located in described the 4th valve pocket and are suitable for flexibly compressing described the second piston; And

Elastic component, described elastic component are suitable for flexibly being pressed between described the first cam and described the second cam.

2. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 1, it is characterized in that, described hydraulic valve block hollow and inside are provided with spacing block, described spacing block is isolated into described the first chamber and the second chamber with the inner space of described hydraulic valve block, the free-ended end face of described spacing block is spaced apart with the internal face of, a sidewall that free end end face described hydraulic valve block and this spacing block is relative, to be communicated with described the first valve pocket and described the 3rd valve pocket.

3. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 1, is characterized in that,

One end of described the first driveshaft inwardly extend in described the second valve pocket and is fixed on a side of described first piston from a sidewall of described the second valve pocket;

One end of described the second driveshaft inwardly extend in described the 4th valve pocket and is fixed on a side of described the second piston from a sidewall of described the 4th valve pocket.

4. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 3, is characterized in that, described elasticity reset device is spring, on the part of described spring housing in described the 4th valve pocket of stretching into of described the second driveshaft.

5. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 1, is characterized in that, is provided with the leakage hole that is communicated with described the 4th valve pocket on described hydraulic valve block.

6. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 1, is characterized in that, each in described first piston and described the second piston all forms cuboid shape or the square bodily form.

7. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 1, is characterized in that, described fuel feeding oil return mechanism comprises:

Be used to open or close the control valve in described engine oil pressure chamber.

8. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 7, is characterized in that, also comprises be used to the pressure-detecting device of measuring described engine oil pressure intraluminal fluid force feed pressure.

9. the actuating mechanism of the variable air valve lift apparatus for motor according to claim 1, it is characterized in that, also comprise clutch shaft bearing, described clutch shaft bearing be suitable for being enclosed within on described camshaft and lay respectively at described the first cam and described the first shift fork and described the second cam and described the second shift fork between.

10. a motor, is characterized in that, comprises the actuating mechanism of the described variable air valve lift apparatus for motor of any one according to claim 1-9.