CN202596828U - Drive device, internal combustion engine having the drive device and vehicle having the internal combustion engine - Google Patents
Drive device, internal combustion engine having the drive device and vehicle having the internal combustion engine Download PDFInfo
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- CN202596828U CN202596828U CN 201120517909 CN201120517909U CN202596828U CN 202596828 U CN202596828 U CN 202596828U CN 201120517909 CN201120517909 CN 201120517909 CN 201120517909 U CN201120517909 U CN 201120517909U CN 202596828 U CN202596828 U CN 202596828U
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Abstract
The utility model provides a drive device, which comprises a cam (1) and a rocking arm (3) with a central part hinged and supported on a rocking arm shaft (5). The drive device further comprises an adjusting mechanism (2) supported between the cam (1) and the rocking arm (3). The rocking arm (3) comprises first working curved faces (9) and second working curved faces (19) connected with the first working curved faces. The first working curved faces (9) and the second working curved faces (19) are applied for adjusting the maximum lifts of driven objects such as a cylinder valve (14), etc. By having a function for adjusting the maximum lifts of driven objects through the adjusting mechanism (2) added, the drive device achieves a continuously changeable lift of the cylinder valve (14). In particular, the drive device can perform significant adjustment on the maximum lifts of driven objects due to the fact that the second working curved faces (19) can perform significant correction on the transmitted cam (1) motion rule.
Description
Technical field
The utility model relates to a kind of drive unit, particularly a kind of drive unit that is used to regulate the air inlet valve and air outlet valve of internal combustion engine open and close.
Background technique
European patent communique EP 1 672 183 A1 disclose a kind of rocking arm that is used to force the control valve device.Wherein, an end of rocking arm is connected with a regulating device, thereby the part of this regulating device can the protruding position of adjusting this end of rocking arm.Be provided with a rocker-arm roller at the middle part of rocking arm, the axle of this roller is connected with the supporting axle of roller on being coated on the cam excircle through a link.But this pressure control gear is restricted for the adjustment of the opening travel of valve, promptly can not significantly adjust the stroke of valve.Simultaneously, this device can not be adjusted the switching phase place of valve.
A kind of device that is used for the controlling combustion engine air inlet and exhaust valve is disclosed among the japanese kokai publication hei 5-98913.Comprising a rocking arm, an end of rocking arm links to each other with an end of air inlet and exhaust valve push rod, and the other end is connected with a hydraulic tappet.The middle part of rocking arm is provided with a roller.The deficiency of this device is that the variation that its adjusting to air inlet and exhaust valve switching phase place and stroke can only be passed through the radius of curvature of each point on the cam external peripheral surface realizes, causes the amplitude of accommodation to be restricted thus.
A kind of device that is used for the controlling combustion engine air inlet and exhaust valve is disclosed among the japanese kokai publication hei 9-21305.Wherein also be to have adopted rocking arm and roller has been set at the middle part of rocking arm.But the shortcoming of this device is the same with above-mentioned shortcoming of the prior art, all is to do bigger adjustment to the switching phase place and the stroke of air inlet and exhaust valve, can not adjust accurately it.
The model utility content
The purpose of the utility model is to provide a kind of drive unit, so that the lift characteristics of internal-combustion engine cylinder valve is adjusted.This drive unit generally is applicable to various internal-combustion engines.Be particularly useful for being arranged in the space of the narrow and small valve cages of compact internal combustion engine such as motorcycle, the adjustment means be provided the switching phase place and the maximum lift characteristic of its inlet and outlet valve.In addition, particularly can in the coaxial mounted distribution device of inlet and outlet camshaft, realize regulating continuously the function that opens and closes phase place and maximum lift to the inlet and outlet valve respectively, more can carry out control separately the cylinder valve of internal-combustion engine with multi-cylinders.
For realizing above-mentioned model utility purpose; According to the utility model a kind of drive unit is provided; Comprise that cam and intermediate portion are hinged on the rocking arm on the pitman arm shaft; Wherein, said drive unit also comprises the controlling mechanism that is bearing between said rocking arm and the said cam, and said controlling mechanism comprises setting section and do-part; And said rocking arm comprises at least one first working curved surface; Said first working curved surface is used to support the do-part of said controlling mechanism, and the said setting section of said controlling mechanism can be set in said do-part on the assigned position of said first working curved surface.
Because the drive unit according to the utility model has increased the adjusting to internal-combustion engine cylinder valve maximum lift through controlling mechanism is set, therefore with in the existing technology there is not the drive unit of controlling mechanism to compare regulating power with countercylinder valve lift; The influence of the lever ratio (L2/L1) that receives owing to the lift of cylinder valve to be formed by the lift of cam and the structural parameter of rocking arm etc. is so can reach the purpose of the lift characteristics that changes driven object such as valve through adjustment cam lifting curve parameter, rocker structure parameter etc.
A technological scheme according to the utility model; The shape of said first working curved surface satisfies following condition: when the said setting section of said controlling mechanism made said do-part move along said first working curved surface, said do-part was resisted against on the basic circle of said cam all the time and the rotation angle of keeping said rocking arm is zero state.
Even, can not change the primary clearance of valve system because the shape of first working curved surface of rocking arm can guarantee to have changed the initial position of controlling mechanism in the drive unit of the utility model yet.
A technological scheme according to the utility model; The said setting section of said controlling mechanism is a live axle and be fixedly connected or be articulated and connected crank on said live axle; The said do-part of said controlling mechanism comprises connecting rod; One end of said connecting rod is bearing on said first working curved surface movably; The other end of said connecting rod and the other end of said crank are hinged, and said live axle can be set in the assigned position on said first working curved surface with the end by said first working curved surface supporting of said connecting rod through said crank.Preferably, said pitman arm shaft is also used as said live axle.
A technological scheme according to the utility model; The said setting section of said controlling mechanism is an eccentric shaft; The said do-part of said controlling mechanism comprises connecting rod; One end of said connecting rod is bearing on said first working curved surface movably, and the other end of said connecting rod and said eccentric shaft are hinged, and said eccentric shaft can be set in the assigned position on said first working curved surface with the end by said first working curved surface supporting of said connecting rod.
Because the drive unit of the utility model has compared with prior art only increased by cover live axle and connecting rod or an eccentric shaft and a linkage mechanism; So can continue to use the existing structure of internal-combustion engine when using the utility model basically, less to the structural modification of internal-combustion engine.Therefore, the development cost of cost is less when utilizing the utility model that internal-combustion engine is transformed, and can realize the continuous variable of the maximum lift of driven object with simple structure and less cost that is:.Therefore, use the utility model, can continue to use basically cylinder of internal combustion engine valve system, cam shaft system and correct time the train existing structure design parameter, thereby can practice thrift development cost greatly.
A technological scheme according to the utility model; Said connecting rod comprises the 3rd working curved surface of at least one circular arc and the 4th working curved surface of at least one circular arc; Wherein, Said the 3rd working curved surface is bearing on said first working curved surface movably, and said the 4th working curved surface is resisted against on the working curved surface of said cam movably.
Because the connecting rod of the controlling mechanism in the drive unit of the utility model comprises the 3rd working curved surface of circular arc and the 4th working curved surface of circular arc; So the end by the supporting of first working curved surface of controlling mechanism is able between rocking arm and cam, move swimmingly.
A technological scheme according to the utility model; End between said rocking arm and said cam of said connecting rod is provided with roller; Said roller wheel bearing is on said first working curved surface; And said roller is resisted against on the working curved surface of said cam, and said first working curved surface is an arc surface, and the radius of curvature of this arc surface is substantially equal to the diameter sum of the Base radius and the said roller of said cam.
Because the connecting rod of the controlling mechanism in the drive unit of the utility model is provided with at least one roller; So can partly replace between cam and the controlling mechanism and the slip between controlling mechanism and the rocking arm at least to roll; Make that the motion of whole drive unit is smooth and easy more flexibly, thereby improved the functional reliability and the stability of device, can reduce friction loss; Improve transmission efficiency, increase the service life.
A technological scheme according to the utility model; End between said rocking arm and said cam of said connecting rod is provided with at least one first roller and at least one second roller; Wherein, Said first roller is resisted against on the basic circle of said cam; Said second roller wheel bearing is at said first working curved surface, and said first working curved surface is arc surface, and the radius of curvature of this arc surface is substantially equal to Base radius and the radius of said first roller and the radius sum of said second roller of said cam.
Because the connecting rod of the controlling mechanism in the drive unit of the utility model is provided with at least one first roller and at least one second roller; First roller is resisted against on the basic circle of cam, and second roller wheel bearing is on first working curved surface, and first working curved surface is an arc surface; The radius of curvature of this arc surface is substantially equal to Base radius and the radius of first roller and the radius sum of second roller of cam; So, can replace between cam and the controlling mechanism and the slip between controlling mechanism and the rocking arm to roll, make that the motion of whole drive unit is smooth and easy more flexibly; Thereby the functional reliability and the stability of device have further been improved; Can further reduce friction loss, improve transmission efficiency, increase the service life.
According to a technological scheme of the utility model, said rocking arm also comprises at least one and second working curved surface that said first working curved surface links to each other, and said second working curved surface is used to support the do-part of said controlling mechanism.
According to a technological scheme of the utility model, the shape of said second working curved surface satisfies following condition: cooperate with said first working curved surface and the transfer law of said cam is revised.
Owing to comprise second working curved surface that links to each other with said first working curved surface in the drive unit of the utility model; And this second working curved surface cooperates with first working curved surface and the transfer law of cam is revised; So; Through second working curved surface is carried out suitable design, can strengthen the regulation range and the amplitude of accommodation according to the actual conditions of internal-combustion engine to the maximum lift of driven object.
According to a technological scheme of the utility model, be provided with the spring that auxiliary said connecting rod resets in the said controlling mechanism.
Because the controlling mechanism in the drive unit of the utility model is provided with auxiliary its spring that resets, so can guarantee better that controlling mechanism resets.
Internal-combustion engine with the drive unit described in above-mentioned any technological scheme is provided according to the utility model.
Because the internal-combustion engine of the utility model has the drive unit of the utility model, so the cylinder of internal combustion engine valve of the utility model can be realized the continuous variable of maximum lift.
The vehicle that uses above-mentioned internal-combustion engine is provided according to the utility model.
Because the vehicle of the utility model has used the internal-combustion engine of the utility model, so, can through regulating the maximum lift of cylinder of internal combustion engine valve, reach the reduction oil consumption according to the needs of operating mode, and reduce discharging, improve the effect of combustion efficiency.
Because the organization plan of the utility model is with respect to the existing structure of this type internal-combustion engine; Only increased and be used for controlling mechanism that the transfer law of cam is revised; Therefore do not need too much to increase structure space, can not cause structure huge yet, so the utility model generally is applicable to various internal-combustion engines; Especially can be applicable to the compact internal combustion engine that only has smaller internal-combustion engine space, like the internal-combustion engine of motorcycle and minicar.
Because it is few to participate in the to-and-fro motion of valve system and number of components that camshaft rotatablely moves in the controlling mechanism that the utility model increases; Therefore can not increase considerably the movement inertia of valve system and the rotary inertia of cam shaft system; Like this; Even increased native system, also being difficult for the movement inertia of causes valve door system and the rotary inertia of cam shaft system too much increases, and can not increase train burden in correct time.Therefore, use the utility model, can continue to use internal combustion engine valve door system, cam shaft system and the existing design parameter of train in correct time, thereby can practice thrift development cost.
In addition; Owing to the utility model fundamentally is to revise and reach the effect of regulating cylinder valve maximum lift transmitting the cam rule, can carry out independent control to single cam respectively so both have, also can carry out the characteristics of unified control to a plurality of cams; Therefore; Compare with the gas distribution system control technique of existing control camshaft, have high flexibility, its advantage with respect to existing technology is also very obvious.
Description of drawings
Fig. 1 is the stereogram that schematically shows the utility model first embodiment's drive unit.
Fig. 2 is the plan view that schematically shows the utility model first embodiment's drive unit.
Fig. 3 is near the partial enlarged drawing the adjusting member in the utility model first embodiment's the drive unit, is the schematic representation that is used to explain the adjustment process of this adjusting member countercylinder valve maximum lift, and wherein, adjusting member is set at first limit position.
Fig. 4 is near the partial enlarged drawing the adjusting member in the utility model first embodiment's the drive unit, is the schematic representation that is used to explain the adjustment process of this adjusting member countercylinder valve maximum lift, and wherein, adjusting member is set at the neutral position.
Fig. 5 is near the partial enlarged drawing the adjusting member in the utility model first embodiment's the drive unit, is the schematic representation that is used to explain the adjustment process of this adjusting member countercylinder valve maximum lift, and wherein, adjusting member is set at second limit position.
Fig. 6 is the figure that schematically shows cylinder valve lifting curve among the utility model first embodiment.
Fig. 7 is the plan view that schematically shows the utility model second embodiment's drive unit.
Fig. 8 is the figure that schematically shows the utility model second embodiment's drive unit, and Fig. 8 (a) is a plan view, and Fig. 8 (b) is the A-A sectional view of Fig. 8 (a).
Fig. 9 is the cross-section profile that schematically shows the utility model first embodiment's adjusting member variation.
Figure 10 is the stereogram that schematically shows another variation of the utility model first embodiment.
Figure 11 is near the enlarged front view of second working curved surface that schematically shows other variation of the utility model first embodiment.
Figure 12 is the figure that schematically shows the utility model the 3rd embodiment's a variation, and Figure 12 (a) is a plan view, and Figure 12 (b) is the B-B sectional view of Figure 12 (a).
Figure 13 is the plan view that schematically shows the utility model the 3rd embodiment's a variation.
Figure 14 is the plan view that schematically shows another variation of the utility model the 3rd embodiment.
Embodiment
First embodiment
Fig. 1 is the stereogram that schematically shows according to the utility model first embodiment's drive unit.Fig. 2 is the plan view that schematically shows according to the utility model first embodiment's drive unit.This drive unit is particularly useful for driving unlatching, the closing movement of cylinder of internal combustion engine valve.To combine accompanying drawing below, describe the embodiment of the utility model in detail.
One, constitutes
As depicted in figs. 1 and 2, in the present embodiment, drive unit has a cam 1 and a rocking arm 3.Cam 1 is installed on the camshaft 13.Through other power plant drive cam shaft 13 that do not illustrate among the figure, rotate thereby drive cam 1.Rocking arm 3 at the middle part hinged support on pitman arm shaft 5.
Drive unit also has and controlling mechanism cam 1 cooperating, that represent with drawing reference numeral 2 on the whole.
In traditional driving device, camshaft drives cam rotation, and cam is realized the inlet and outlet of cylinder through giving the driven cylinder of internal combustion engine valve of the pitman arm shaft the other end against rocking arm above that with its power and transmission of movement.
Compare with such traditional driving device, present embodiment has added controlling mechanism 2 between cam 1 and rocking arm 3, and on rocking arm 3, is provided with first working curved surface 9 and second working curved surface 19.Below with reference to Fig. 2, the part that mainly is different from existing technology with regard to present embodiment is elaborated.
At first, rocking arm 3 is a member of growing crosswise in Fig. 2.As shown in Figure 2; the middle part hinged support of rocking arm 3 is on pitman arm shaft 5; end of a side (among Fig. 2 for left end) is resisted against driven member; the upper end portion of cylinder of internal combustion engine valve 14 for example, the end side (being right-hand end among Fig. 2) at rocking arm 3 is provided with first working curved surface 9 and second working curved surface 19.Detailed description about this first working curved surface 9 and second working curved surface 19 will be carried out hereinafter.
Next controlling mechanism 2 is described.As shown in Figure 2, in the present embodiment, controlling mechanism 2 mainly comprises setting section 21 and do-part 22.Particularly, controlling mechanism 2 comprises live axle 12 as setting section 21, crank 4 and as the connecting rod 6 of do-part 22, and this controlling mechanism 2 can be passing to the rocking arm 3 with controlling mechanism 2 cooperatings from the power of cam 1 together with its motion.
Specify the concrete formation of the controlling mechanism 2 of present embodiment below.One end of connecting rod 6 (being left upper end among Fig. 2) is hinged through bearing pin 16 and crank 4; The other end of crank 4 is fixedly connected with Control Shaft 12 as the setting section 21 of controlling mechanism 2, and the motor that does not illustrate among Control Shaft 12 and the figure, hydraulic mechanism, reducing gear etc. provide the device of power to be connected.Certainly, also can be as required, the motor that does not illustrate in making crank 4 and scheming, hydraulic mechanism, reducing gear etc. provide the device of power to be connected.The other end of connecting rod 6 (being bottom righthand side among Fig. 2) is provided with the adjusting member 61 with Control Shaft 12 and bearing pin 16 almost parallels; This adjusting member 61 is between cam 1 and rocking arm 3; On this adjusting member 61, be provided with the 3rd working curved surface 611 and the 4th working curved surface 612; Connecting rod 6 is bearing on first working curved surface 9 of rocking arm 3 through the 3rd working curved surface 611, is resisted against through the 4th working curved surface 612 on the working curved surface 10 of cam 1.The 3rd working curved surface 611 is and first working curved surface 9 of rocking arm 3 arc surface of inscribe roughly; The 4th working curved surface 612 is the arc surface roughly circumscribed with the basic circle of cam 1; And the 3rd working curved surface 611 is identical with the axle center of the 4th working curved surface 612; The radius of curvature of the two can be the same or different, and under the identical situation of the two radius of curvature, adjusting member 61 also can form the cylndrical surface.Under the drive of the unshowned in the drawings device that power is provided; Control Shaft 12 drives the crank 4 that is fixedly connected with it and rotates; Connecting rod 6 is moved, thereby the end by rocking arm 3 supporting that will be positioned at connecting rod 6 is set in the assigned position on first working curved surface 9 of rocking arm 3.
Turn back to rocking arm 3.First working curved surface 9 of rocking arm 3 is an arc surface; Its radius of curvature designs according to following mode: when the 3rd working curved surface 611 of the adjusting member 61 of connecting rod 6 is resisted against on first working surface 9 of rocking arm 3 and the 4th working curved surface 612 of this adjusting member 61 is resisted against 102 last times of base circle portion of the working curved surface 10 of cam 1; This first working curved surface 9 is roughly concentric with the basic circle of cam 1, and the radius of curvature of this first working curved surface 9 is substantially equal to Base radius and the radius of curvature of the 3rd working curved surface 611 and the radius of curvature sum of the 4th working curved surface 612 of cam 1.
In other words; the profile of rocking arm 3, adjusting member 61 and cam 1 and position relation satisfies following condition: between the base circle portion 102 of cam 1 and rocking arm 3, form the passage 7 that passes through of confession adjusting member 61 just, the radius of curvature sum of the radius of curvature of the 3rd working curved surface 611 of adjusting member 61 and the 4th working curved surface 612 is substantially equal to the width of this passage 7.Under such condition; When adjusting member 61 is driven by live axle 12 and moves and change in the process of its initial position along first working curved surface 9 of rocking arm 3; Adjusting member 61 can move swimmingly in this passage 7 and can the zero lift characteristic of valve mechanism do not impacted; That is: the setting of 12 pairs of adjusting member 61 of live axle neither can make this adjusting member 61 break away from cam 1 and the constraint of rocking arm 3 to it, can not promote rocking arm 3 again and rotate around pitman arm shaft 5.
As stated; First working curved surface 9 of the 3rd working curved surface 611 and rocking arm 3 is inscribe roughly; The 4th working curved surface 612 is roughly circumscribed with the basic circle of cam 1; And the 3rd working curved surface 611 is identical with the axle center of the 4th working curved surface 612, and the radius of curvature sum of the radius of curvature of the 3rd working curved surface 611 and the 4th working curved surface 612 is substantially equal to the width of passage 7.
Second working curved surface 19 and first working curved surface 9 of rocking arm 3 are circumscribed, and with the bump of avoiding cam 1 and other component in the valve mechanism are caused, and second working curved surface 19 is that axle center with bearing pin 16 is the part on the arc surface in axle center.
As stated, left end is resisted against driven member among Fig. 2 of rocking arm 3, the upper end portion of cylinder of internal combustion engine valve 14 for example, and right-hand end is provided with first working curved surface 9 and second working curved surface 19 among Fig. 2 of rocking arm 3.Like this,, can rocking arm 3 be pressed to the 3rd working curved surface 611 of controlling mechanism 2, make the 4th working curved surface 612 of controlling mechanism 2 can be resisted against on the cam 1 through the Returnning spring 15 of cylinder of internal combustion engine valve 14.Thus; Make cam 1 compress each other and the motion of transmission of drive force and cam 1 through controlling mechanism 2 and rocking arm 3; Promptly when cam 1 rotates; The working curved surface 10 of cam 1 withstands the 4th working curved surface 612 of controlling mechanism 2; The 3rd working curved surface 611 of controlling mechanism 2 withstands first working curved surface 9 or second working curved surface 19 on the rocking arm 3 makes rocking arm 3 follow the rotation of cam 1 and rotate around pitman arm shaft 5, opens, closes thereby the left end of rocking arm 3 drives cylinder valve 14, realizes the inlet and outlet of internal-combustion engine.
In order to guarantee resetting of adjusting member 61 better, can be between connecting rod 6 and crank 4 or live axle 12 and other possibly parts be provided for the spring (not shown) that auxiliary adjustment member 61 resets.The stop portion 33 of adjusting member 61 can also be set at the end of second working curved surface 19 of rocking arm 3 in addition.
Above-mentioned only is a concrete embodiment by means of Fig. 2 to the specific descriptions that controlling mechanism of the utility model 2 and rocking arm 3 carry out, and the controlling mechanism 2 of the utility model is not limited to this embodiment, as long as can realize its function, can carry out various changes.
For example, present embodiment schematically illustrates the position of Control Shaft 12, this Control Shaft 12 can be installed in that cylinder of internal combustion engine covers or other positions of being convenient to install of internal-combustion engine on.
In addition, should be appreciated that when not needing to regulate the maximum lift of cylinder valve 14 significantly, second working curved surface 19 is not set on rocking arm 3, the effect that first working curved surface 9 can reach the maximum lift continuous variable that makes cylinder valve 14 equally only is set.
Two, the adjusting of cylinder valve maximum lift
Drive unit with the utility model first embodiment illustrated in figures 1 and 2 is an example below, describes the maximum lift of how to regulate cylinder valve 14 according to the drive unit of the utility model in detail with reference to Fig. 3 to Fig. 6.
Fig. 3 to Fig. 5 is according near the partial enlarged drawing the adjusting member in the utility model first embodiment's the drive unit; It is the schematic representation that is used to explain the adjustment process of this adjusting member countercylinder valve maximum lift; Wherein, Adjusting member is set at first limit position in Fig. 3, and adjusting member is set at the neutral position in Fig. 4, and adjusting member is set at second limit position in Fig. 5.Fig. 6 is the figure that schematically shows according to cylinder valve lifting curve among the utility model first embodiment.
The adjusting of the maximum lift of the drive unit countercylinder valve 14 of the utility model mainly is to realize through the initial position of do-part 22 on first working curved surface 9 of rocking arm 3 that changes controlling mechanism 2.Be specially: the do-part 22 of controlling mechanism 2 is set on first working curved surface 9 of rocking arm 3; It is moved along first working curved surface 9 and second working curved surface 19 at cam 1 duration of work, pass to cylinder valve 14 after the characteristics of motion of cam 1 is revised.
As stated, an end of connecting rod 6 (being left upper end among Fig. 3) is hinged through bearing pin 16 and crank 4, and the other end of crank 4 is fixedly connected with Control Shaft 12, Control Shaft 12 with scheme in the motor that do not illustrate etc. provide the device of power to be connected.
Device by power is provided provides power, and the action that Control Shaft 12 is set in connecting rod 6 and the adjusting member 61 by the end of rocking arm 3 supporting that is positioned at connecting rod 6 through crank 4 diverse location on first working curved surface 9 of rocking arm 3 is called the adjusting of the maximum lift of countercylinder valve 14.Notice that though in the present embodiment, such adjusting action is to carry out with adjusting member 61 period of contact in the base circle portion 102 of cam 1; But this just for the ease of explanation does; In practical application, can carry out at any time, or even when internal-combustion engine is idle, also can carry out.
Adjusting member 61 is resisted against on first working curved surface 9 of rocking arm 3 and can be become control band by the zone that Control Shaft 12 freely is provided with, and the left-most position with control band in following explanation is called the first limit position PL
1, the right-most position of control band is called the second limit position PL
2, with the first limit position PL
1With the second limit position PL
2Between the position be called neutral position P
MThe position that adjusting member 61 is provided with by Control Shaft 12 is called the initial position of adjusting member 61.
At first, to the initial position of adjusting member 61 at the first limit position PL
1The time situation describe.Fig. 3 is that the drive unit of expression the utility model is set in the first limit position PL at controlling mechanism 2 by Control Shaft 12
1The time cam 1, adjusting member 61, rocking arm 3 and cylinder valve 14 moving situation.Shown in Fig. 3 (a), under the driving of unshowned power plant, adjusting member 61 is set the first limit position PL of the leftmost side of first working curved surface 9 in the drawings in the drawings
1
Begin from this initial position, cam 1 clockwise direction in camshaft 13 driving lower edge Fig. 3 (a) rotates.The base circle portion 102 of the working curved surface 10 of cam 1 contact with the 4th working curved surface 612 on the adjusting member 61 move during; Because the radius of curvature of first working curved surface 9 is substantially equal to radius of curvature and the radius of curvature sum of the 4th working curved surface 612 of the 3rd working curved surface 611 of Base radius and the adjusting member 61 of cam 1; So rocking arm 3 keeps state of rest; Corresponding with it, cylinder valve 14 state that keeps shut.
Under this state, cam 1 continues to rotate along clockwise direction.When shown in Fig. 3 (b); The starting point M of the lift portion 101 of the working curved surface 10 of cam 1 begin with adjusting member 61 on the 4th working curved surface 612 when contacting; The 4th working curved surface 612 begins to receive the promotion of this lift portion 101 to its top in figure; So; Adjusting member 61 while keep the 3rd working curved surface 611 to contact with first working curved surface 9 of rocking arm 3 and working curved surface 10 state of contact of the 4th working curved surface 612 and cam 1 mobile above to Fig. 3 (b) in; Simultaneously the power of cam 1 and the characteristics of motion thereof pass to rocking arm 3 through the 4th working curved surface 612, the 3rd working curved surface 611 and first working curved surface 9; The loading force that makes rocking arm 3 overcome to pass over through cylinder valve 14 at the Returnning spring 15 of the cylinder valve 14 of the other end and the inertial force of cylinder valve parts begin around pitman arm shaft 5 along counterclockwise rotating among Fig. 3, and corresponding with it, cylinder valve 14 is activated and begins to open.
Under this state, cam 1 continues to rotate along clockwise direction.When shown in Fig. 3 (c), the peach sharp apex H of the lift portion 101 of cam 1 is resisted against the 612 last times of the 4th working curved surface of adjusting member 61, and the 3rd working curved surface 611 of rocking arm 3 roughly is positioned at the second limit position PL
2In other words, reach at cam 1 till the maximum lift amount of itself, adjusting member 61 all is on first working curved surface 9 of rocking arm 3, to move.After this; When cam 1 continues to rotate along clockwise direction; The peach sharp apex H of its lift portion 101 is with after the 4th working curved surface 612 of adjusting member 61 separates; Adjusting member 61 turns back to initial position along first working curved surface 9 of rocking arm 3, i.e. the first limit position PL under the booster action of the main effect of the Returnning spring 15 of cylinder valve 14 and not shown Returnning spring
1Therefore, be set at the first limit position PL when adjusting member 61
1The time, identical with the situation of the conventional ADS driving device that controlling mechanism 2 is not set, adjusting member 61 is not regulated the maximum lift amount of cam 1, and the lifting capacity of cam 1 has passed to rocking arm 3 fully.The cylinder valve lifting curve of this moment is schematically illustrated as the l among Fig. 6
1
Secondly, to the initial position of adjusting member 61 in the neutral position P
MThe time situation describe.Fig. 4 is that the drive unit of expression the utility model is placed neutral position P at controlling mechanism 2 by Control Shaft 12
MThe time cam 1, adjusting member 61, rocking arm 3 and cylinder valve 14 moving situation.Shown in Fig. 4 (a), according to the needs of operating mode, in the drawings under the driving of unshowned power plant, adjusting member 61 is set in the drawings the first limit position PL on first working curved surface 9
1With the second limit position PL
2Between neutral position P
M1
Begin from this initial position, cam 1 clockwise direction in camshaft 13 driving lower edge Fig. 4 (a) rotates.With initial position at the first limit position PL
1The time situation identical; The 4th working curved surface 612 period of contact on the base circle portion 102 of the working curved surface 10 of cam 1 and adjusting member 61; Because the radius of curvature of first working curved surface 9 is substantially equal to radius of curvature and the radius of curvature sum of the 4th working curved surface 612 of the 3rd working curved surface 611 of Base radius and the adjusting member 61 of cam 1; So rocking arm 3 keeps state of rest, and is corresponding with it, cylinder valve 14 state that keeps shut.
Under this state, cam 1 continues to rotate along clockwise direction.When shown in Fig. 4 (b); The starting point M of the lift portion 101 of the working curved surface 10 of cam 1 begin with adjusting member 61 on the 4th working curved surface 612 when contacting; The 4th working curved surface 612 begins to receive the promotion of this lift portion 101 to its top in figure; So; Adjusting member 61 while keep the 3rd working curved surface 611 to contact with first working curved surface 9 of rocking arm 3 and working curved surface 10 state of contact of the 4th working curved surface 612 and cam 1 mobile above to Fig. 4 (b) in; Simultaneously the power of cam 1 and the characteristics of motion thereof pass to rocking arm 3 through the 4th working curved surface 612, the 3rd working curved surface 611 and first working curved surface 9; Make rocking arm 3 overcome loading force that the Returnning spring 15 at the cylinder valve 14 of the other end passes over through cylinder valve 14 and begin around pitman arm shaft 5 that corresponding with it, cylinder valve 14 is activated and begins to open along counterclockwise rotating among Fig. 4.So just can under the prerequisite of the zero-bit that does not change cylinder valve 14 lifting capacitys,, can change the switch phase of cylinder valve 14 through changing the initial position of adjusting member 61; Through changing the initial position of the joint member 61 that modifies tone; Can change the driving arm of force L2 that cam 1 drives rocking arm 3; Variation has taken place in the lever ratio (L2/L1) (referring to Fig. 2) that causes valve system to drive rocking arm 3, thereby has realized the switch phase of internal-combustion engine cylinder valve 14 and the adjusting of maximum lift.
Under this state; Cam 1 continues to rotate along clockwise direction; When shown in Fig. 4 (c), when the starting point M that is positioned at the lift portion 101 of cam 1 contacts with the 4th working curved surface 612 of adjusting member 61, cross the second limit position PL along the adjusting member 61 that first working curved surface 9 of rocking arm 3 moves
2, promptly the 3rd working curved surface 611 of adjusting member 61 is crossed the second limit position PL with the point of contact of first working curved surface 9 of rocking arm 3
2, promptly adjusting member 61 becomes the state that is bearing on second working curved surface 19 from the state that is bearing on first working curved surface 9.
In the present embodiment; Owing to second working curved surface 19 is to be that purpose designs with the transmission that more effectively reduces cam 1 lift; Be that an axle center with bearing pin 16 is the arc surface in axle center; So, when the 3rd working curved surface 611 and the point of contact of first working curved surface 9 of rocking arm 3 are crossed the second limit position PL
2After, along with cam 1 continues to rotate along clockwise direction, the starting point M on the lift portion 101 of cam 1 partly begins partly to be offset by second working curved surface 19 of rocking arm 3 to the cam lift between the peach sharp apex H.After this; When cam 1 continues to rotate along clockwise direction; Its peach sharp apex H is with after the 4th working curved surface 612 of adjusting member 61 separates; Adjusting member 61 turns back to initial position along second working curved surface 19 of rocking arm 3, i.e. neutral position P under the booster action of the main effect of the Returnning spring 15 of cylinder valve 14 and not shown Returnning spring
MTherefore, though cam 1 the maximum lift amount of itself is brought into play, but the rocking arm 3 and not exclusively maximum lift amount of cam 1 is passed to the cylinder valve 14 of rocking arm 3 the other ends like this, is set at the first limit position PL with adjusting member 61
1The time situation compare, the maximum lift of cylinder valve 14 diminishes.In other words; Because second working curved surface 19 is the curves that deviate from the basic circle of cam 1 gradually; So the lifting capacity of cam 1 is partly offset by the part that this deviates from, the maximum lift that makes cylinder valve 14 open reduces, thereby has realized the adjusting of countercylinder valve maximum lift.The cylinder valve lifting curve of this moment is schematically illustrated as the l among Fig. 6
M1
In order more clearly to represent the regulating effect of adjusting member 61 countercylinder valves 14 maximum lift, schematically show initial position among Fig. 6 and be set at neutral position P
MThe neutral position P in left side
M2Neutral position P with the right side
M3The time cylinder valve lifting curve l
M2And l
M3
Be not difficult to find out from Fig. 6, along with the initial position of adjusting member 61 gradually away from the first limit position PL
1And near the second limit position PL
2, the maximum lift of cylinder valve 14 diminishes gradually.
Next, the initial position to adjusting member 61 is set at the second limit position PL
2The time situation describe.Fig. 5 is that the drive unit of expression the utility model is placed the second limit position PL at controlling mechanism 2 by Control Shaft 12
2The time cam 1, adjusting member 61, rocking arm 3 and cylinder valve 14 moving situation.Shown in Fig. 5 (a), according to the needs of operating mode, not shown power plant are set in the second limit position PL on first working curved surface 9 with adjusting member 61
2
Begin from this initial position, cam 1 clockwise direction in camshaft 13 driving lower edge Fig. 5 (a) rotates.With initial position at the first limit position PL
1The time situation identical; The 4th working curved surface 612 period of contact on the base circle portion 102 of the working curved surface 10 of cam 1 and adjusting member 61; Because the radius of curvature of first working curved surface 611 is substantially equal to radius of curvature and the radius of curvature sum of the 4th working curved surface 612 of the 3rd working curved surface 611 of Base radius and the adjusting member 61 of cam 1; So rocking arm 3 keeps state of rest, and is corresponding with it, cylinder valve 14 state that keeps shut.
Under this state, cam 1 continues to rotate along clockwise direction.When shown in Fig. 5 (b), the starting point M of the lift portion 101 of the working curved surface 10 of cam 1 begin with adjusting member 61 on the 4th working curved surface 612 when contacting, the 4th working curved surface 612 begins to receive the promotion of this lift portion 101 to its top in figure.Because this second limit position PL
2Be first working curved surface 9 of rocking arm 3 and the turning point of second working curved surface 19; The two is circumscribed in this position; And the axis coinciding of the axle center of second working curved surface 19 and bearing pin 16, so, even receive the promotion of cam 1; Adjusting member 61 also just moves and does not promote rocking arm 3 along the tangent direction of second working curved surface 19 and rotates around pitman arm shaft 5; Like this, just realized not motion with cam 1 to the purpose that rocking arm 3 transmits, also just reached make the member that comprises rocking arm 3 and driven by rocking arm 3 for example cylinder valve 14 be in the purpose of closed condition always.Therefore, adjusting member 61 is set at the second limit position PL
2Situation be that a kind of lift that makes cylinder valve 14 is zero situation.The cylinder valve lifting curve of this moment is actually zero, but for the ease of being set at the first limit position PL with initial position
1Or the situation of neutral position PM compares, and schematically the initial position of this adjusting member 61 is set at the second limit position PL among Fig. 6
2The lifting curve of situation is expressed as a l
2
This shows; As long as the physical dimension of length, shape and rocking arm 3, controlling mechanism 2 and the cam 1 of first working curved surface 9 and second working curved surface 19 and configuration relation thereof etc. are carried out suitable design; Through changing the initial position of adjusting member 61; Transmission of movement rule to cam 1 is revised, and the lift that just can realize cylinder valve 14 is continuous variable on a large scale, comprises that lift is zero state.Like this, can regulate the maximum lift of cylinder of internal combustion engine valve, improve combustion efficiency, reduce oil consumption and discharging and realize engine braking brake function efficiently according to the needs of internal-combustion engine under different operating modes.
Second embodiment
Below with reference to the drive unit of Fig. 7 explanation according to the utility model second embodiment.
Fig. 7 is the plan view that schematically shows according to the utility model second embodiment's drive unit.As shown in Figure 7, the present embodiment and first embodiment's formation is basic identical, and its difference only is to have realized with a roller 62 function of the adjusting member 61 among first embodiment.Below, only the present embodiment and first embodiment's difference is described and omit being repeated in this description other parts.
One end of connecting rod 6 (being left upper end among Fig. 7) is hinged through bearing pin 16 and crank 4, and the other end of crank 4 is fixedly connected with Control Shaft 12, Control Shaft 12 with scheme in the motor, hydraulic mechanism, reducing gear etc. that do not illustrate provide the device of power to be connected.Certainly, also can be as required, the motor that does not illustrate in making crank 4 and scheming, hydraulic mechanism, reducing gear etc. provide the device of power to be connected.The other end of connecting rod 6 (being bottom righthand side among Fig. 7) is provided with the roller shaft 63 with Control Shaft 12 and bearing pin 16 almost parallels, and this roller shaft 63 is provided with roller 62, and this roller 62 is bearing on first working curved surface 9 of rocking arm 3, and is resisted against on the working curved surface 10 of cam 1.In the present embodiment, the radius of curvature of first working curved surface 9 of rocking arm 3 is substantially equal to the diameter sum of the Base radius and the roller 62 of cam 1.
Like this; Under the driving of the unshowned in the drawings device that power is provided; Control Shaft 12 drives the crank 4 that is fixedly connected with it and rotates, and connecting rod 6 is moved, thereby the roller 62 by the end of rocking arm 3 supportings that will be positioned at connecting rod 6 is set in the assigned position on first working curved surface 9 of rocking arm 3.
Through roller 62 is set, the motion between adjusting member 61 among first embodiment and rocking arm 3 and the cam 1 is become rolling by slip, reduced because of the transmission loss of friction and the wearing and tearing of component.
The 3rd embodiment
Below with reference to the drive unit of Fig. 8 explanation according to the utility model the 3rd embodiment.
Fig. 8 is the figure that schematically shows according to the utility model second embodiment's drive unit, and Fig. 8 (a) is a plan view, and Fig. 8 (b) is the A-A sectional view of Fig. 8 (a).As shown in Figure 8, the present embodiment and first embodiment's formation is basic identical, and its difference mainly is to have realized with a roller 65 and a pair roller 66,66 function of the adjusting member 61 among first embodiment.Below, only the present embodiment and first embodiment's difference is described and omit being repeated in this description other parts.
One end of connecting rod 6 (being left upper end among Fig. 8) is hinged through bearing pin 16 and crank 4, and the other end of crank 4 is fixedly connected with Control Shaft 12, Control Shaft 12 with scheme in the motor, hydraulic mechanism, reducing gear etc. that do not illustrate provide the device of power to be connected.Certainly, also can be as required, the motor that does not illustrate in making crank 4 and scheming, hydraulic mechanism, reducing gear etc. provide the device of power to be connected.The other end of connecting rod 6 (being bottom righthand side among Fig. 8) is provided with the roller shaft 63 with Control Shaft 12 and bearing pin 16 almost parallels; This roller shaft 63 is provided with roller 65 and is separated with the pair roller 66,66 that suitable distance is provided with in these roller 65 both sides and this roller 65; Wherein, the diameter of roller 65 is greater than the diameter of roller 66,66.Correspondingly, on rocking arm 3, offer the groove 31 that cross section is roughly rectangle with roller 65 corresponding parts, the degree of depth of groove 31 is poor greater than the radius of the radius of roller 65 and roller 66, and the width of groove 31 is wideer than the thickness of roller 65.In the present embodiment; Two curved surfaces of the cell wall both sides of groove 31 are first working curved surfaces 9 of rocking arm 3; The outer circumferential face of roller 65 is corresponding to the 4th working curved surface 612 among first embodiment, and the outer circumferential face of roller 66 is corresponding to the 3rd working curved surface 611 among first embodiment.Like this, roller 65 is resisted against on the working curved surface 10 of cam 1, and a pair roller 66,66 is bearing in respectively on two first working curved surfaces 9 simultaneously.In addition, in the present embodiment, the radius of curvature of first working curved surface 9 of rocking arm 3 is substantially equal to Base radius and the radius of roller 65 and the radius sum of roller 66 of cam 1.
Like this; Under the driving of the unshowned in the drawings device that power is provided; Control Shaft 12 drives the crank 4 that is fixedly connected with it and rotates; Connecting rod 6 is moved, thereby the roller 66,66 by the end of rocking arm 3 supporting that will be positioned at connecting rod 6 is set in the assigned position on two first working curved surfaces 9 of rocking arm 3.
Through a roller 65 and a pair roller 66,66 are set; Motion between adjusting member 61 among first embodiment and rocking arm 3 and the cam 1 is become rolling and the rolling between roller 66,66 and the rocking arm 3 between roller 65 and the cam 1 respectively by sliding, compare further the reduction with second embodiment because of the transmission loss that rubs and the wearing and tearing of component.
Various variation
First embodiment's variation
In above-mentioned first embodiment, adjusting member 61 is made into integration with connecting rod 6.Also can with adjusting member 61 be fixedly connected after connecting rod 6 is separately made, or connect rotatably after being separately made.
In addition, adjusting member 61 can as a whole member, also can be a member with the 3rd working curved surface 611 and member with the 4th working curved surface 612 are fixed together composition with coaxial and relative mode composite body structure.Schematically show the shape of transverse section of several kinds of variation of the utility model first embodiment's adjusting member among Fig. 9.
In addition, Figure 10 is the stereogram that schematically shows another variation of the utility model first embodiment.Shown in figure 10, controlling mechanism 2 also can comprise pair of links 6, and this pair of links 6 is hinged with bearing pin 16 in parallel to each other, that is, pair of links 6 is hinged on the bearing pin 16, and rocking arm 3 is clipped in therebetween.In this occasion, adjusting member 61 is between the other end of pair of links 6.Likewise, adjusting member 61 both can be made into integration with pair of links 6, also can be separately made the back and be fixedly connected, or connect rotatably after being separately made.
In addition; In first embodiment; second working curved surface 19 and first working curved surface 9 of rocking arm 3 are circumscribed; and be that axle center with bearing pin 16 is the part on the arc surface in axle center, but this is that purpose designs with the transmission that reduces cam 1 lift just, the shape of this second working curved surface 19 can design arbitrarily as required.For example, when the maximum lift that the maximum lift that obtains when hope itself can provide than cam 1 is also big, can second working curved surface 19 be designed to shown in figure 11 and shapes first working curved surface, 9 inscribes according to the amount of hoping its lifting.Reference as a comparison shows the elongation line of first working curved surface with double dot dash line among Figure 11, be shown in broken lines second working curved surface that reduces lift transmission usefulness.
In addition, in first embodiment, also can crank 4 be hinged on the live axle 12, and provide the device of power to drive crank 4 by the motor that does not illustrate among the figure, hydraulic mechanism, reducing gear etc.In addition; Also live axle 12 can be set, and crank 4 is fixedly connected on the pitman arm shaft 5, and provide the device of power to be connected the motor that does not illustrate among pitman arm shaft 5 or crank 4 and the figure, hydraulic mechanism, reducing gear etc.; In other words, replacing 12 pairs of cranks 4 of live axle with pitman arm shaft 5 drives.Have again, can also crank 4 be hinged on the pitman arm shaft 5, and provide the device of power to drive crank 4 by the motor that does not illustrate among the figure, hydraulic mechanism, reducing gear etc.
The 3rd embodiment's variation
Figure 12 is the figure that schematically shows the utility model the 3rd embodiment's a variation, and Figure 12 (a) is a plan view, and Figure 12 (b) is the B-B sectional view of Figure 12 (a).
In above-mentioned the 3rd embodiment, the diameter of roller 65 correspondingly, is offered groove 31 with roller 65 corresponding parts greater than the diameter of roller 66,66 on rocking arm 3.But this is a concrete embodiment only, also can be shown in figure 12, roller 66 ', 66 ' diameter greater than roller 65 ' diameter, correspondingly, on rocking arm 3, the convexity 32 that cross section is roughly rectangle is set with roller 65 ' corresponding part.In this case, protruding 32 is first working curved surface 9 of rocking arm 3, roller 65 ' outer circumferential face corresponding to the 3rd working curved surface 611 among first embodiment, roller 66 ' outer circumferential face corresponding to the 4th working curved surface 612 among first embodiment.Like this, roller 65 ' be bearing on first working curved surface 9, simultaneously a pair roller 66 ', 66 ' be resisted against on the working curved surface 10 of cam 1.In this variation, same with the 3rd embodiment, the radius of curvature of first working curved surface 9 of rocking arm 3 be substantially equal to Base radius and the roller 65 of cam 1 ' radius and roller 66 ' the radius sum.
Convexity or groove perhaps are not set on rocking arm 3, and projection or groove are arranged on the working curved surface 10 of cam 1, correspondingly arrange each roller, they are resisted against respectively on rocking arm 3 and the cam 1.Here, though diagram not be appreciated that under the situation that rocking arm or cam enough approach, need not to be provided with above that dodge with they in the opposing party against the groove used of roller can realize that each roller leans with them respectively separately.Notice that no matter in which kind of scheme, the radius of curvature of first working curved surface 9 of rocking arm 3 all is substantially equal to the radius sum of the Base radius of cam 1 and two rollers that contact with cam 1 with rocking arm 3 respectively.
In addition, Figure 13 is the plan view that schematically shows the utility model the 3rd embodiment's a variation.In the 3rd embodiment, a roller 65 and a pair roller 66,66 are set on the same roller shaft 63.But, also can be shown in figure 13, roller 65 " with roller 66 " is separately positioned on the roller shaft 63,64 of two almost parallels, and this roller shaft 63,64 all is arranged on the connecting rod 6.Wherein, " be bearing on first working curved surface 9 of rocking arm 3, roller 66 " is resisted against on the working curved surface 10 of cam 1 roller 65.In this case, the shape of first working curved surface 9 of rocking arm 3 can design according to following mode.When the initial position of the roller 65 that makes controlling mechanism 2 through live axle 12 " along first working curved surface 9 of rocking arm 3 move change this roller 65 ", can guarantee roller 66 and " be resisted against on the basic circle of cam 1 and can guarantee that again rocking arm 3 can not rotate around pitman arm shaft 5.The shape that in other words, should make this first working curved surface 9 is with drive the formed envelope of motion that bottom rollers 66 " are resisted against roller 65 when moving on the basic circle of cam 1 " at live axle 12 consistent.Because this envelope is to confirm according to actual conditionses such as the size that respectively constitutes element of controlling mechanism 2 and configuration relations thereof, so the shape of first working curved surface 9 is not unique.In addition, " to be resisted against on the working curved surface 10 of cam 1 roller 66 " and to be bearing in the situation on first working curved surface 9 of rocking arm 3 also be same to roller 65.And the number of each roller and layout thereof also can be provided with arbitrarily as required.
Other variation
In each embodiment of the utility model of above-mentioned explanation, adopted the structure of crank 4, but this is a kind of concrete embodiment.According to the utility model; Also can adopt eccentric shaft shown in figure 14 20 to substitute the function of live axle 12 and crank 4; In this case; Under the driving of the drive part 201 of eccentric shaft 20, eccentric part 202 drivening rods 6 that are equivalent to the eccentric shaft 20 of the crank 4 among first embodiment move.Likewise, eccentric shaft 20 can be installed in that cylinder of internal combustion engine covers or other positions of being convenient to install of internal-combustion engine on.The preferred employing is arranged on eccentric shaft 20 on the pitman arm shaft 5.
In addition; In each embodiment of the utility model of above-mentioned explanation; second working curved surface 19 of rocking arm 3 is arc surfaces mutually circumscribed with first working curved surface 9, but the utility model is not limited to this structure, and second working curved surface 19 also can carry out various deformation designs as required.Second working curved surface 19 also can be according to the arbitrary surface that designs of the maximum lift characteristic curve of the cylinder valve 14 of hoping to obtain, said here arbitrary surface comprises various curved surfaces and plane.
Abovely be illustrated with reference to several kinds of embodiments of accompanying drawing to the utility model; Those skilled in the art are to be understood that; The drive unit of second embodiment of the utility model, the 3rd embodiment and various variation also can be realized the continuous variable of the maximum lift of driven object equally with first embodiment; And under not afoul situation, each embodiment's of the utility model technical characteristics can be bonded to each other; All in the protection domain of the utility model, this paper enumerates no longer one by one in the change that is produced thus.
In sum; Be used for controlling mechanism that the transfer law of cam is revised because the organization plan of the utility model with respect to the existing structure of this type internal-combustion engine, has only increased, therefore do not need too much to increase structure space; Can not cause structure huge yet; So the utility model generally is applicable to various internal-combustion engines, especially can be applicable to the compact internal combustion engine that only has smaller internal-combustion engine space, like the internal-combustion engine of motorcycle and minicar.
And; Because it is few to participate in the to-and-fro motion of valve system and number of components that camshaft rotatablely moves in the controlling mechanism that the utility model increases; Therefore can not increase considerably the movement inertia of valve system and the rotary inertia of cam shaft system, and can not increase the burden of train in correct time.Therefore, use the utility model, can continue to use internal combustion engine valve door system, cam shaft system and the existing design parameter of train in correct time, thereby can practice thrift development cost.
In addition; Owing to the utility model fundamentally is to revise and reach the effect of regulating cylinder valve maximum lift transmitting the cam rule, can carry out independent control to single cam respectively so both have, also can carry out the characteristics of unified control to a plurality of cams; Therefore; Compare with the gas distribution system control technique of existing control camshaft, have high flexibility, it is also very obvious with respect to existing technical advantage.
Claims (27)
1. a drive unit comprises that cam (1) and intermediate portion are hinged on the rocking arm (3) on the pitman arm shaft (5), it is characterized by,
Said drive unit also comprises the controlling mechanism (2) that is bearing between said rocking arm (3) and the said cam (1), and said controlling mechanism (2) comprises setting section (21) and do-part (22);
And said rocking arm (3) comprises at least one first working curved surface (9),
The said setting section (21) of said controlling mechanism (2) can be set in said do-part (22) on the assigned position of said first working curved surface (9),
The said do-part (22) of said controlling mechanism (2) is bearing in said rocking arm (3) and goes up and be resisted against on the said cam (1).
2. drive unit according to claim 1 is characterized by,
The shape of said first working curved surface (9) satisfies following condition: when the said setting section (21) of said controlling mechanism (2) made said do-part (22) move along said first working curved surface (9), said do-part (22) was resisted against on the basic circle of said cam (1) all the time and the rotation angle of keeping said rocking arm (3) is zero state.
3. drive unit according to claim 1 is characterized by,
The said setting section (21) of said controlling mechanism (2) for live axle (12) be fixedly connected or be articulated and connected crank (4) on said live axle (12),
The said do-part (22) of said controlling mechanism (2) comprises connecting rod (6), and an end of said connecting rod (6) is bearing on said first working curved surface (9) movably, and the other end of the other end of said connecting rod (6) and said crank (4) is hinged,
And said live axle (12) can be set in the assigned position on said first working curved surface (9) with the end by said first working curved surface (9) supporting of said connecting rod (6) through said crank (4).
4. drive unit according to claim 3 is characterized by,
Said pitman arm shaft (5) is also used as said live axle (12).
5. drive unit according to claim 1 is characterized by,
The said setting section (21) of said controlling mechanism (2) is eccentric shaft (20),
The said do-part (22) of said controlling mechanism (2) comprises connecting rod (6), and an end of said connecting rod (6) is bearing on said first working curved surface (9) movably, and the other end of said connecting rod (6) and said eccentric shaft (20) are hinged,
And said eccentric shaft (20) can be set in the assigned position on said first working curved surface (9) with the end by said first working curved surface (9) supporting of said connecting rod (6).
6. according to any described drive unit in the claim 3 to 5, it is characterized by,
Said connecting rod (6) comprises the 3rd working curved surface (611) of at least one circular arc and the 4th working curved surface (612) of at least one circular arc; Wherein, Said the 3rd working curved surface (611) is bearing on said first working curved surface (9) movably, and said the 4th working curved surface (612) is resisted against on the working curved surface (10) of said cam (1) movably.
7. according to any described drive unit in the claim 3 to 5, it is characterized by,
An end that is positioned between said rocking arm (3) and the said cam (1) of said connecting rod (6) is provided with roller (62), and said roller (62) is bearing on said first working curved surface (9), and said roller (62) is resisted against on the working curved surface (10) of said cam (1),
Said first working curved surface (9) is an arc surface, and the radius of curvature of this arc surface is substantially equal to the diameter sum of the Base radius and the said roller (62) of said cam (1).
8. according to any described drive unit in the claim 3 to 5, it is characterized by,
The end between said rocking arm (3) and the said cam (1) of being positioned at of said connecting rod (6) is provided with at least one first roller (65,65 ', 66,66 ') and at least one second roller (65,65 ', 66,66 '); Wherein, Said first roller (65,65 ', 66,66 ') is resisted against on the basic circle of said cam (1); Said second roller (65,65 ', 66,66 ') is bearing in said first working curved surface (9)
And said first working curved surface (9) is an arc surface, and the radius of curvature of this arc surface is substantially equal to the radius sum of radius and said second roller (65,65 ', 66,66 ') of Base radius and said first roller (65,65 ', 66,66 ') of said cam (1).
9. according to any described drive unit in the claim 1 to 5, it is characterized by,
Said rocking arm (3) also comprises second working curved surface (19) that at least one links to each other with said first working curved surface (9), and said second working curved surface (19) is used to support the do-part (22) of said controlling mechanism (2).
10. drive unit according to claim 9 is characterized by,
The shape of said second working curved surface satisfies following condition: cooperate with said first working curved surface (9) and the transfer law of said cam (1) motion is revised.
11. drive unit according to claim 6 is characterized by,
Said rocking arm (3) also comprises second working curved surface (19) that at least one links to each other with said first working curved surface (9), and said second working curved surface (19) is used to support the do-part (22) of said controlling mechanism (2).
12. drive unit according to claim 11 is characterized by,
The shape of said second working curved surface satisfies following condition: cooperate with said first working curved surface (9) and the transfer law of said cam (1) motion is revised.
13. drive unit according to claim 7 is characterized by,
Said rocking arm (3) also comprises second working curved surface (19) that at least one links to each other with said first working curved surface (9), and said second working curved surface (19) is used to support the do-part (22) of said controlling mechanism (2).
14. drive unit according to claim 13 is characterized by,
The shape of said second working curved surface satisfies following condition: cooperate with said first working curved surface (9) and the transfer law of said cam (1) motion is revised.
15. drive unit according to claim 8 is characterized by,
Said rocking arm (3) also comprises second working curved surface (19) that at least one links to each other with said first working curved surface (9), and said second working curved surface (19) is used to support the do-part (22) of said controlling mechanism (2).
16. drive unit according to claim 15 is characterized by,
The shape of said second working curved surface satisfies following condition: cooperate with said first working curved surface (9) and the transfer law of said cam (1) motion is revised.
17. according to any described drive unit in the claim 3 to 5, it is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
18. drive unit according to claim 6 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
19. drive unit according to claim 7 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
20. drive unit according to claim 8 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
21. drive unit according to claim 9 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
22. drive unit according to claim 10 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
23. drive unit according to claim 11 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
24. drive unit according to claim 12 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
25. drive unit according to claim 13 is characterized by,
Be provided with the spring that auxiliary said connecting rod (6) resets in the said controlling mechanism (2).
26. an internal-combustion engine is characterized by,
It has any described drive unit in the claim 1 to 25.
27. a vehicle is characterized by,
It uses the described internal-combustion engine of claim 26.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201120517909 CN202596828U (en) | 2011-12-13 | 2011-12-13 | Drive device, internal combustion engine having the drive device and vehicle having the internal combustion engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201120517909 CN202596828U (en) | 2011-12-13 | 2011-12-13 | Drive device, internal combustion engine having the drive device and vehicle having the internal combustion engine |
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| Publication Number | Publication Date |
|---|---|
| CN202596828U true CN202596828U (en) | 2012-12-12 |
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| CN 201120517909 Expired - Fee Related CN202596828U (en) | 2011-12-13 | 2011-12-13 | Drive device, internal combustion engine having the drive device and vehicle having the internal combustion engine |
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| CN (1) | CN202596828U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103161543A (en) * | 2011-12-13 | 2013-06-19 | 常州嵘驰发动机技术有限公司 | Driving device, combustion motor with the same and vehicle using the combustion motor |
-
2011
- 2011-12-13 CN CN 201120517909 patent/CN202596828U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103161543A (en) * | 2011-12-13 | 2013-06-19 | 常州嵘驰发动机技术有限公司 | Driving device, combustion motor with the same and vehicle using the combustion motor |
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