CN87101609A

CN87101609A - Cam mechanism

Info

Publication number: CN87101609A
Application number: CN198787101609A
Authority: CN
Inventors: 弗雷德里克·迈克尔·斯蒂沃西
Original assignee: Individual
Current assignee: Individual
Priority date: 1986-02-04
Filing date: 1987-02-03
Publication date: 1987-10-21
Also published as: GB2186337A; WO1987004757A1; GB8602716D0; GB8702367D0; AU6932987A; EP0262159A1

Abstract

The short cam mechanism that continues of a kind of air valve variation lift profile and high lift adopts the ring cam set (5) concentric with axis (2).(5) around the axis adjustable angle with location cam ring profile (6) different eccentric segments.Output encircles the box piece (13) of (16), slider (12) but is contained in to-and-fro motion in the district of camshaft rectangular cross-section, by being loaded on lever (18) displacement that camshaft can change around pivotal line (2a).Lever have with the follower (22) of cam profile bridle joint and with the operator of box piece mating face (13a) bridle joint.In another embodiment, the short cam areas that continues of high lift is made of the changeed lift cam of being carried by ring cam set and rotate synchronously with camshaft.

Description

Cam mechanism

The invention relates to cam mechanism, especially for converting straight-line mechanism to rotatablely moving, the camshaft of internal-combustion engine is the particular application of this mechanism.

By convention, camshaft has solid cam, and this solid cam is with the camshaft rotation and have external cam profile molded lines.The rotatablely moving of this cam utilized the straight line motion that converts reciprocating type valve gear such as the rocking arm of installing pivotably that keeps in touch with this cam profile to.

Solid cam has various shortcomings, such as the action that can not provide high lift to lack the endurance, and has a unmodifiable working profile molded lines.

An object of the present invention is to provide a kind of universal cam mechanism, it has eliminated or has reduced at least some shortcoming at least of known solid cam mechanism.

According to one aspect of the present invention, provide a kind of being used for to convert straight-line mechanism to rotatablely moving, this mechanism comprises a running shaft, an axis that has with this running shaft is the cam of a kind of cam profile molded lines at center, yet one non-rotatably is placed on the running shaft but the slider that can do to slide with an axial direction that is transverse to this running shaft limitedly on this running shaft, be used for the device that between running shaft and cam, produces relative rotation, and the contact device that during this relatively rotates, keeps in touch and straight line motion is passed to slider according to an eccentric section of cam profile molded lines with the cam profile molded lines, contact device in this mechanism comprises a rocking arm that is installed in pivotably on the running shaft, and this rocking arm has an actuating arm that approximal surface keeps in touch of an idle rod that keeps in touch with the cam profile molded lines and and slider.

On the other hand, the invention provides a kind of cam mechanism, it comprises that one has with the running shaft that to be the cam of cam profile molded lines at center and one do the follow-up unit that keeps in touch with the cam profile molded lines during relatively rotating at cam and follow-up unit around running shaft, at the eccentric section of this mechanism's cam profile molded lines is that a cam face by lift cam parts that carried by cam limits, so that be synchronized with the movement with relatively rotating of cam and follow-up unit.

Again on the one hand, the invention provides a kind of being used for converts straight-line mechanism to rotatablely moving, it comprises a running shaft, an axis that has with running shaft is the cam of the cam profile molded lines at center, one non-rotatably is placed on the running shaft but can does the slider that slides on running shaft with a direction that is transverse to the axis of running shaft limitedly, be used for the device that between running shaft and cam, produces relative rotation, and the contact device that during this relatively rotates, keeps in touch and straight line motion is passed to slider by an eccentric section of cam profile molded lines with the cam profile molded lines, a cam face that at the eccentric section of this mechanism's cam profile molded lines is lift cam parts being carried by cam limits, so that around axle rotation that is parallel to rotating shaft axis, and provide be used for running shaft and cam between relatively rotate the device that rotates these lift cam parts mutually in phase.

For ease of understanding the present invention, embodiments of the invention are described with reference to the following drawings:

Fig. 1 is the simple sectional view according to first embodiment of camshaft mechanism of the present invention;

Fig. 2 is a simple sectional view according to second embodiment of camshaft mechanism of the present invention to Fig. 4, and it represents three continuous states of this mechanism during the camshaft rotation;

Fig. 5 is the schematic drawing according to the 3rd embodiment of cam mechanism of the present invention;

Fig. 6 represents a kind of improvement of the 3rd embodiment, and it provides a kind of different lifting values;

Fig. 7 represents the 3rd embodiment's further improvement to Fig. 9, and they provide different separately lifting values;

Figure 10 shows the 4th embodiment according to camshaft mechanism of the present invention to Figure 14;

Figure 15 shows the 5th embodiment according to camshaft mechanism of the present invention to Figure 17;

Figure 18 shows the 6th embodiment according to camshaft mechanism of the present invention to Figure 19;

Figure 20 shows the 7th embodiment according to camshaft mechanism of the present invention;

Figure 21 is the sketch according to another camshaft mechanism of the present invention;

Figure 22 and Figure 23 are the sketches that embodies camshaft mechanism advantage of the present invention.

Corresponding components in each embodiment of each accompanying drawing is represented with identical reference number.

At first with reference to Fig. 1, according to first embodiment of camshaft mechanism of the present invention comprise one can be around the camshaft 1 of an axis 2 rotations, this camshaft has the part in the cross section of an expression pair of parallel guide face 3 and 4.This camshaft can rotate in a hollow cam 5 of annular prejudicially, cam 5 has cam ring profile molded lines 6, molded lines 6 has the first eccentric section 7 and the second eccentric section 8, section 8 is by also can limit with the lift cam part 9 of driving shaft 11 rotations in the opening 10 that is installed on the cam 5, and driving shaft 11 can be around an axis rotation that is parallel to the spin axis 2 of camshaft 1.

A slider 12 comprises the box parts 13 of a U-shaped, and it is contained in slidably on the camshaft 1 and by support 14 and 15 and links on the output ring 16.Parts 13 non-rotatably are placed on the camshaft 1, so that slider rotates with camshaft.Yet box shape assembly 13 can slide on the guide surface 3 and 4 of camshaft, slides thereby make slider 12 can be transverse to axis 2.Box shape assembly 13 is made of a follow-up unit 17, and follow-up unit 17 meshes itself and cam profile molded lines 6 by the valve spring of being exported ring 16 effects or the spring (not shown) biasing that provides separately.

Ring cam set 5 can be adjusted on angle around axis 2 in 360 ° of scopes, and can be locked on the position of having set up.Such adjustment, for example can utilize one that form around the periphery of cam 5 and with one can carry out around the worm gear of the worm meshing of 2 the axle rotation of paralleling to the axis, this mechanism has a locking lead angle (for example 10 °), therefore can make the worm gear rotation by rotary worm, but worm gear can not make the worm screw rotation.Go up in the position shown in the figure 1, the eccentric section 7 of cam profile molded lines 6 is on an effective position, during camshaft 1 rotation when follow-up unit 17 is run into the section 7 of molded lines, thereby this position makes slider displacement operated valve downwards, the eccentric section 8 of cam profile molded lines 6 then is on a non-effective position, when follow-up unit 17 was run into section 8, this position made slider 12 upward displacements during the camshaft rotation.The

section

7 and 8 of molded lines respectively has 3.80 millimeters entad eccentricity.

The eccentric section 7 of cam profile molded lines provides the normal breakdown action of valve, and the continuity scope of this valve event for example is 120 ° of camshaft rotations, and maximum displacement or lift L are 9 millimeters.

Ring cam set 5 ° can make the section 7 of molded lines move on to non-effective position from position Rotate 180 shown in Figure 1, and the section 8 of molded lines then moves on to active position, makes valve opening at this position upper curtate 8.On lift cam 9, profile molded lines section 8 provides the valve opening action that has high lift L, lacks the endurance.In this example, the continuity scope of this breakdown action only is 40 ° of camshaft rotations, yet has but obtained 9 millimeters maximum lift.In order to obtain this result, the rotation of the rotation of driving shaft 11 and camshaft 2 (in the R direction) will cooperatively interact, and the ratio that therefore drives driving shaft 11 should be: camshaft 1 whenever circles clockwise, and driving shaft will change for 3 weeks counterclockwise.This can finish by the so any suitable device of direct gears such as two axles of 1: 3 ratio.When follow-up unit 17 has rotated 160 ° and axle 11 when counterclockwise having rotated 480 ° in the direction of the clock from its present position, the follow-up unit 17 among Fig. 1 and the relative position of lift cam 9 have promptly reached and can produce the desired degree that is arranged in a straight line.Like this, 20 ° of camshaft rotations and during 60 ° of lift cam 9 rotations, follow-up unit 17 is at first run into the guiding edge of face 8 at position 17a, move on to the position of maximum lift 17b then.Camshaft is further rotated 20 ° and lift cam 9 is correspondingly rotated 60 ° again, and this makes follow-up unit turn back to the contacted position 17c of this off-centre section with molded lines 6.

Like this, described mechanism just can provide two or more selectable valve opening actions with various durations and/or maximum lift, a possibility in these actions is exactly short endurance high lift action, and this situation is that the known camshaft mechanism with solid cam can not reach satisfactorily.Mechanism shown in Figure 1 can provide the valve opening action of short endurance high lift, the lift that wherein will reach 9 millimeters only needs 20 ° of camshaft rotations, can also be so that lift be similarly apart from finishing this action therewith, therefore whole valve event is only required 40 ° of camshaft rotations.In addition, the synchronous rotation of lift cam part 9 makes follow-up unit 17 can cross the desired precipitous unlatching inclined-plane of cam section 8 easily.

Camshaft 1 can be driven by the driving shaft 11 that promotes valve, and perhaps driving shaft 11 is driven by camshaft 1, and perhaps two axles can be driven respectively.

The use such as the lift cam of cam 9 that constitutes the eccentric section of cam profile molded lines 6 provides sizable scope for having any valve event in cycle that requires.By selecting the correct crossing radius between follow-up unit and the lift cam and calculating the number of degrees that overlap by two rotations that parts produced of all rotating, can determine to reach the rotation ratio of two axles that intersect synchronously simply.

Fig. 2 has illustrated second embodiment of the present invention to Fig. 4, and it has provided the another kind of method that does not rely on lift cam as shown in Figure 1 and obtain short endurance high lift valve opening action.

In the embodiment of Fig. 4, camshaft 1 is around axis 2 rotations in the ring cam set 5 by adjustable angle of cam profile molded lines 6 at center, in the R direction having with axis 2 at Fig. 2.Molded lines 6 has the first eccentric section 7 and the second eccentric section 8.

A slider 12 is placed on the camshaft 1 slidably, and slider 12 comprises the box parts 13 of U-shaped, and parts 13 are placed on the camshaft 1 and by support 14 and 15 and are connected on the output ring 16.Rocking arm 18 is installed on the camshaft 1 pivotably by the 2 pivot 2a that extend that parallel to the axis, thereby makes arm 18 with camshaft 1 rotation.Rocking arm 18 comprises the idle rod 21 that is made of follow-up unit 22, and follow-up unit 22 keeps in touch with the cam profile molded lines.Rocking arm 18 also comprises an actuating arm 19 that has actuator 20, and actuator 20 keeps sliding contact with the approximal surface 13a that bottom interior surface by box parts 13 constitutes.

Fig. 2 is illustrated in a camshaft in the rotational position, and wherein the follow-up unit 22 of idle rod 21 is the starting ends at second short cam section.Camshaft to position shown in Figure 3, makes follow-up unit 22 cross over 14.5 ° of angles that the unlatching inclined-plane 23 by cam section 8 occupies from 54 ° of the position of Fig. 2 rotations.Camshaft rotation makes rocking arm 18 forward the position of Fig. 3 pivotably downwards to from the position of Fig. 2 for 54 °, thus make U-shaped parts 13 on camshaft 1 to lower slider (as shown in the figure).Thereby this will make output ring 16 have corresponding displacement to open a coupled valve (not shown).Suppose that output ring 16 contacts with the valve spring device, and Fig. 3 and situation shown in Figure 4 will take place so.Like this, if the peak dot of cam section 8 is peaks of entad eccentricity and without any the stop factor, then reach summit in a flash at this, there is not the maintenance factor that makes follow-up unit 22 maintain summit, even so camshaft is not further rotated, this follow-up unit also can be got back to its home position under the influence of the return spring of valve.In fact, the closed inclined-plane 24 of cam section 8 requires a kind ofly can make return load that the profile molded lines that slows down can take place enough, and therefore the total angle size of this action can increase slightly, greater than 54 °.

The ratio of supposing arm 19 and arm 21 is as shown in the figure, and cam section 8 is 3.80 millimeters in the entad eccentricity of its peak dot, and then the output ring will be shifted 13.5 millimeters, thus the magnification ratio that rocking arm 18 was had 3.5526316: 1.

The pivot spinning movement of rocking arm 18 can be crossed the precipitous unlatching inclined-plane of cam section 8 easily, therefore can obtain the high lift valve event of short endurance.

With regard to air door operation, in Fig. 4, cam section 8 is indicated on active position at Fig. 2, and cam section 7 is represented as non-active position.Yet cam section 7 will still will cause the to-and-fro motion of slider 12, but slider 12 this to-and-fro motion are away from this valve.

Fig. 5 has illustrated the 3rd embodiment of the cam mechanism of the present invention that uses eccentric rocking arm 18 by pivot deflection to Fig. 9.

Fig. 5 comprises a rocking arm 18 that is installed in pivotably on the pivot 2a, and in fact pivot 2a may be a crank section of camshaft 1.This camshaft 1 has an eccentric rectangular area 1a who settles, and lays slider 12 slidably.Contact with cam profile molded lines 6 at the follow-up unit 22 of idle rod 21 ends by the ring cam set 5 of adjustable angle, actuator 20 is linked on the output ring 16 by support 14 with the approximal surface 13a sliding contact that is connected to the U-shaped parts 13 of exporting ring 16 by support 14, U-shaped parts 13.It is cam section 8 and the cam section 7 that the continuity scope is the long duration of camshaft rotation hexagonal angle of the short endurance at 29.75 ° of angles of camshaft rotation that there is a continuity scope in this ring cam set.

When camshaft 1 when the R direction is rotated, follow-up unit 22 sails on the unlatching slope of cam section 8 causing actuator to the moving of slider 12, thereby output ring 16 is moved on to by the position 16a at maximum displacement point place shown in the dotted line, makes valve opening thus.The return spring of valve is with valve-closing and make slider get back to its home position.For instance, this cam section can have 2 millimeters entad eccentricity at its peak dot, and the size of determining lever arm makes the reduction factor that is provided by this lever arm increase to 4.5, thereby the maximum that makes relevant valve is opened or lift L is 9 millimeters, and this appears at camshaft after position shown in Figure 5 has rotated 9.5 ° of angles.

Interest be, the length of idle rod 21 has been determined the rotating range of this unlatching sequence just, so lever arm is short more, it is just rapid more to be opened to maximum lift.For the short arm 21 of compensating pole, can prolong actuator arm 19, thereby the size that needn't increase cam section 8 just can be kept maximum lift.

Cam section 7 than long duration can provide desired any lift, but it has 9.0 millimeters identical maximum lift abilities as shown in the figure.

Fig. 6, Fig. 7 and Fig. 8 have omitted slider 12, camshaft zone 1a and output ring 16.The lift that reaches at each situation lower edge axis x-x is regarded as maximum lift L.

Fig. 6 has illustrated that two respectively have 5 millimeters

entad cam sections

7 and 8 of eccentricity.The leverage of rocking arm 18 increases to 12.5 millimeters maximum lift L to it at relevant valve upper edge axis x-x.The maximum opening point that obtains is the place that has rotated 52 ° of angles at camshaft from position shown in Figure 6.

What Fig. 7 represented is the mechanism of a kind of Fig. 6 of being similar to, but

cam

7 and 8 has only 2 millimeters entad eccentricity, is 10 millimeters along the maximum lift of axis x-x.

Fig. 8 entad represents to have that eccentricity is a kind of mechanism of 2 millimeters cam section, and cam 8 provides peak dot when 33.75 ° of angles of camshaft rotation, and cam 7 provides peak dot when 83.75 ° of angles of camshaft rotation.The feature that should be borne in mind that rocking arm will be reflected in

cam

8 and 7 on both.

Fig. 9 is illustrated in all has 2 millimeters entad a kind of mechanisms of eccentricity on

cam section

7 and 8, also express the output ring 16 on the 16a of its mobile position.The total lift that is provided is 12 millimeters.With regard to cam section 8, in 21 ° of angles of camshaft rotation, reach peak dot.

Though at Fig. 6 not shown actuator in Fig. 9, the effect of actuator is different with the interior approximal surface 13a of U-shaped parts 13 certainly.It should be noted that in all embodiments approximal surface itself also can have its profile molded lines so that change the character of the leverage of rocking arm 18 by certain desired mode.

Figure 10 has the 4th embodiment of the present invention of special compact nature to Figure 14 explanation.

In mechanism shown in Figure 14, rocking arm 18 comprises that a regional 1a who is rotatably installed in camshaft 1 goes up and has mutually a cylindrical body of the circular cross section of the follow-up unit 21 of configuration and actuating arm 19 at an angle of 90 at Figure 10.Idle rod 21 and profile molded lines 6 bridle joints by the ring cam set of adjustable angle, box parts 13 and output ring 16 have formed a monolithic construction, by the approximal surface bridle joint of this form with actuating arm 19 and slider 12.

Ring cam set 5 comprises a camshaft rotating range that occupies 28 ° of angles, and has the cam section 8 of the short endurance of high lift of a peak dot in the time of 14 °, and the cam section 7 than long duration that occupies hexagonal angle camshaft rotating range.Two cams all provide 8.0 millimeters peak lift L.Figure 14 represents that output ring 16 does not have displacement, and Figure 13 represents along the maximum displacement of output ring on axis X-directions X.Two cams are 2.05 millimeters in the entad eccentricity of peak dot.In general, actuating arm 19 fixes by the approximal surface 13a that the effect that pushes the valve spring (not shown) of exporting ring 16 heads on slider as shown in figure 14.When camshaft 1 rotates to eccentric section 8 with cam profile molded lines bridle joint, cause rocking arm 18 to rotate around its axle, make actuating arm 19 leave position shown in Figure 14 and move to position shown in Figure 13, promptly passed through 90 ° of angles.This causes slider 12 and output thereof to encircle the 16 effect displacements against valve spring, thereby desired 8.0 millimeters valve lift L are provided.Rocking arm 18 reaches peak dot by the reaction force of the return spring of valve and then gets back to home position as Figure 11 and shown in Figure 14 it later on.Figure 10 makes to the short rocker arm 18 among Figure 14 only needs the action of valve opening very rapidly at 14 ° of angles of camshaft rotation to realize.

Figure 15 represents the 5th embodiment of the present invention to Figure 17, it is different from previous described embodiment, it does not rely on employed general return spring mechanism in poppet valve, embodies the return spring of valve of in-house necessity of the present invention yet it but has to pack into.This feasible output ring can be opened and can closed used special valve.Figure 15 represents that to Figure 17 valve is on its closed position.

Be similar to Figure 10 to rocking arm shown in Figure 14 at Figure 15 employed rocking arm 18 in the embodiment of Figure 17, it is rotatably installed on the rectangle part zone 1a of camshaft 1, and box parts 13 and output ring 16 constitute all-in-one-piece slider 12.One end of the return spring 30 of valve is placed in the dimple 31 on the 1a of camshaft zone, and its other end then abuts against on the interior prevent surface 32 of slider 12.Valve 33 is included in 34 li of valve lifting devices, and device 34 has a pair of

clamp

35 and 36, and when output ring 16 kept constant the contact with clamp, output ring 16 was rotatable in

clamp

35 and 36.

When camshaft rotates, follow-up unit 21 rolls across the cam profile molded lines by the ring cam set 5 of adjustable angle, when it runs into the effective cam section of of cam profile molded lines, the approximal surface 13a that causes actuator 19 pushing sliders 12, thereby make output ring 16 axis shift along spring 30, this spring of extruding thus, this motion of output ring make lifting device 34-36 move (if this ring cam set is to be similar to situation shown in Figure 11 a kind of) on downward direction and make this valve opening.Then, the spring 30 initial position valve that makes rocking arm 18 get back to it operating position of then getting back to it.

Also comprise the firm parts 37 of idle running, it is a simple mechanism that can guarantee the linear reciprocating motion of lifting device.

Referring now to Figure 18 and Figure 19, a kind of combined type cam mechanism that constitutes the 6th embodiment of the present invention comprises two by the ring cam set 5 of adjustable angle and 5a and two rocking arms 18 and 18a.Two ring cam sets 5 and 5a differ from one another, and wherein the unlatching cycle of the relevant valve of first cam 5 controls, second cam then provides the closed cycle for this valve.Two ring cam sets are coupled in single parts 38, and parts 38 rotatable 360 ° of angles also can be locked on any desired position.

If opening cam 5 is considered to be similar to Figure 10 and cam shown in Figure 11, and closing cam 5a is opposite fully with it, then by follow-up unit 21 and the 21a with these two cams 5 and 5a bridle joint is provided respectively, make the rotation of camshaft 1 cause rocking arm 18 half-twist angles, thereby by actuator 19, move output ring 16 to open valve from position 16a, when arriving the closed inclined-plane of this special cam, follow-up unit 21a promptly begins to contact with this closing cam.The closed inclined-plane of opening cam 5 is arranged to the unlatching inclined-plane of closing cam 5a overlaps mutually.This will cause two rocking

arms

18 and 18a by antipodal phase place half-twist angle, thereby make 16 to-and-fro motion of output ring.Output ring 16 is clamped in as between two

clamp

35 and 36 of Figure 15 in the device shown in Figure 17, will cause valve 33 by desired such unlatching and closure (33a) thus.

For keeping the required precision in the accessible limit,

actuator

21,21a and slider 12 and and camshaft 1 between surface of contact can have the light spring (not shown), so that between two lever systems, produce a limited elasticity, thereby can reduce wearing and tearing and can reduce tolerance during manufacture.In the embodiment of Figure 19, the lever arm of rocking

arm

18 and 18a is described to comprise 90 ° angle at Figure 10.Yet, can use any suitable angle, noticeable being to use greater than 90 ° angle can provide return preferably characteristic later on obtaining peak lift.

Figure 20 has illustrated that principle of the present invention has the application in the mechanism of outer surface cam in use.

As shown in figure 20, camshaft 1 has a Rocker arm 40 of installing pivotably thereon, and Rocker arm 40 is around an axle 2b rotation perpendicular to the spin axis 2 of camshaft.Rocker arm 40 has an idle rod 41, arm 41 has a taper roller 42, roller 42 can move around an axle 42a rotation and with an inclination outer cam surface 43, surface 43 axis with camshaft are provided by the center and by an oblique cam 44, tiltedly the position of cam 44 can utilize the combination of worm screw 45 and worm gear 46 to come spin axis adjustment around camshaft, and worm gear 46 can pass around the axle journal 53 of camshaft 1 and carries cam 44 and move with a sleeve 52 of its rotation with one.

Rocker arm 40 has an actuating arm 47, arm 47 have one with an approximal surface 49 of a slider 50 that the passes camshaft therein roller 48 of bridle joint mutually.Slider 50 can rotate with camshaft as previous embodiment, and the axis that meanwhile can be transverse to camshaft moves linearly.Spring piston of this slider and a reciprocating type valve (not shown) or follower 51 be bridle joint mutually.

When camshaft 1 rotation, the camming surface 43 of the oblique cam 44 of roller follower 42 crosscuts, and any fluctuation all is repeated to generate as the to-and-fro motion of slider 50.Approximal surface 49 is illustrated as a kind of beveled profile molded lines that has along on 2 the axial direction of paralleling to the axis.This not only provides bigger lift ability but also is a kind of selectable characteristic.

Figure 20 has illustrated a kind of by second the surface cam 44a of opposite direction in the face of first face cam 44, and cam 44a is positioned in the another side of axle journal 53 so that utilize another rocking arm (not shown) that is similar to Rocker arm 40 to handle the valve that another does not illustrate in the drawings.Cam 44a is attached on the sleeve 52 equally.

Referring now to Figure 21, for example it should be noted that employed rocking arm 18 can have the profile of an expansion in mechanism shown in Figure 6, thereby can make single ring cam set remove to handle a plurality of output rings.This can respectively have each follow-up unit 22 of its oneself crank 22a to realize that crank 22a is fixed on the countershaft 60 or on the part of countershaft 60 by providing.The actuating arm 20 of rocking arm 18 is fixed on the countershaft 60 or on the part of countershaft 60 equally, but will be along separating certain distance with follow-up unit 22 on the direction of countershaft 60, and this distance is determined by the interval of valve.Actuator 20 is represented as the crank 20a with it, and contacts with an interior approximal surface 16a who forms in being used to handle the output ring 16 of a relevant valve (not shown).Each countershaft is all carried by main camshaft, and for instance, if be provided with two cylinders of the online engine of four cylinders on any one side of ring cam set 5, two countershafts 60 will extend to the right of cam so, and other two countershafts 60 will extend to the left side of cam, so, just the valve on any one side is all provided and driven operation.Need two long countershafts 60 and two short countershafts 60, follow-up unit 22 will be pressed the spaced apart of 90 ° of angles around main camshaft.

Though the embodiment of the invention described above has used rotatable camshaft and non-rotatable cam, be noted that and use fixing camshaft and rotatable cam.

Figure 22 and Figure 23 have illustrated the advantage with respect to common cam provided by the invention.

In all general four-stroke ic petrol engine designs, for instance, during the four-stroke cycle, require intake valve only to open once; Camshaft rotates with half crankshaft speed.Yet for making suction valve in suitable moment action, intake cam is divided into 90 ° cycle, and one of them such section outwards radially extends out from this center so that produce a projection.This degree of radially extending has been determined the lifting capacity that produces on valve, and the straightness of peak dot has determined the stop period of this valve.

The general solid cam of external frame molded lines can not provide high lift for minimum camshaft rotating amount, because tangential restriction must produce very big ramp angles, and wear and tear, noise and speed all is enough to stop the external form cam to obtain than 90 ° of much lower valve events.External cam also has the profile molded lines usually, and valve event just can all have one-period on each limit at its oneself appointed 90 ° of angles like this.Usually the situation of appearance is exactly really for the valve event of closure/opened/closed, and the rotation of camshaft will occupy hexagonal angle, and the rotation of bent axle occupies 240 ° of angles.In each is equivalent to 180 ° the single-stroke of crankshaft rotating scope, can see the overlapping that has 60 ° of angles by this.

Embody ring cam set of the present invention mechanism greater flexibility is arranged, this be because, different with external cam, cam ring can provide more than a kind of working profile molded lines, and just can realize the operation of another working profile molded lines by ring part being rotated to different active positions.In addition, the adjustment of same rotation can change any one the profile molded lines that is determined whole effect in their each valve event.

Figure 22 represents a ring cam set that two

eccentric cam sections

7 and 8 are arranged.When this cam and a reciprocating type follow-up unit 17,22 use together, can obtain 10 millimeters displacement, this displacement amount or occur or occur as long pulse as short burst.In addition, the shape of each pulse all can be determined by the shape of specific profile molded

lines

7,8.

If the output of supposition from reciprocating type follow-up unit to valve is downward, position so shown in the figure, 45 ° cam section 8 is effective sections, 120 ° cam section then produces non-effective displacement upwards.But, by being locked on this position, just having become 120 ° valve event with regard to this valve effective contour molded lines cam 5 Rotate 180s ° and it, 45 ° valve event has then become invalid now.It is unessential that non-effective profile molded lines also will make reciprocating member produce this situation of to-and-fro motion.

If between two

sections

7 and 8, selected a position, then still can make reciprocating type follow-up unit produce two kinds of to-and-fro motion, but will not any influence be arranged, like this valve, if necessary, just can allow a relevant cylinder of motor be in idle state.

For use with Figure 22 in employed similar and intercomparable predicate illustrate with the exceedingly difficult situation of the valve event of the closure/opened/closed of the similar 45 of solid cam realization of a known external frame molded lines, now attention is turned to Figure 23.

Can see that in order to obtain the lasting scope of the 45 from valve closure to valve closure, the profile molded lines 71 of external cam 70 has become extreme shape, therefore must have very big shortcoming from the conversion that rotates to linear motion.

When between the present invention and external cam, comparing, further consider the centrifugal force effect.Under the external cam situation, centrifugal force trends towards making reciprocating type follow-up unit to maintain peak dot, as if thereby make external cam below follow-up unit " disappearances ", consequently the follow-up unit under extreme external cam situation as shown in figure 23 may also not touch closed inclined-plane and just returns.Yet, under the ring cam set situation, trend towards helping that expectation takes place between follow-up unit and the cam contacts at the centrifugal force on the reciprocating type follow-up unit of rotation.Be clear that equally, just can not comprise profile molded lines if there is positive effect to act on external cam on the follow-up unit, but ring cam set may comprise the profile molded lines more than more than one.Like this, just can obtain an effective profile molded lines by the rotary annular cam, make other all profile molded lines all invalid simultaneously, perhaps, also can obtain the state of a void in whole if necessary.Such selectivity is impossible fully for general external cam, and each complete single revolution of camshaft all will cause one or more profile molded lines to remove to influence valve.

Under the motor car engine manufacturer requires to have situation more than a kind of air door operation state, for example, a kind of is the general valve event of 120 ° or other numerical value and another kind of valve event for short endurance with maximum lift and for example 28 °/30 ° of angles, embodying the answer that mechanism of the present invention provides is that this mechanism can not only provide the complete adjustable profile molded lines of two kinds (or multiple), but also can on parts they be provided.In addition, mechanism described here if necessary can make and in large quantities without any need for special manufacturing process.

Claims

1, a kind of being used for converts straight-line mechanism to rotatablely moving, comprise a running shaft, an axis that has with this running shaft is the cam of a kind of cam profile molded lines at center, yet one non-rotatably is placed on the running shaft but the slider that can slide with a direction that is transverse to the axis of running shaft limitedly on running shaft, be used for the device that between running shaft and cam, produces relative rotation, and the contact device that during this relatively rotating, keeps in touch and straight line motion is passed to slider according to an eccentric section of cam profile molded lines with this cam profile molded lines, contact device comprises a rocking arm that is installed in pivotably on the running shaft in this mechanism, and this rocking arm has an actuating arm that approximal surface keeps in touch of an idle rod that keeps in touch with the cam profile molded lines and and slider.

2, a kind of mechanism as claimed in claim 1, rocking arm wherein is with rotating so that center on an axle that is transverse to the axis of running shaft that the mode of pivot is installed.

3, a kind of mechanism as claimed in claim 1, cam wherein is that a kind of axis that has with running shaft is the hollow cam of the cam ring profile molded lines at center, and rocking arm is rotating so that center on an axle that is parallel to the axis of running shaft of pivotally installing.

4, as any one a kind of mechanism in the claim 1 to 3, wherein, the idle rod of rocking arm and actuating arm can be separated out around the countershaft direction of this pivot rotation along one.

5, as a kind of mechanism of above-mentioned any one claim, contact device wherein comprises a plurality of rocking arms of opening by angular separation around running shaft, and each rocking arm all is installed on the running shaft pivotably so that the pivot that centers on separately rotates.

6, as a kind of device of above-mentioned any one claim, wherein running shaft passes an opening on slider and extends, and the sectional shape of running shaft and slider wants to make slider to be non-rotatable with respect to running shaft but can to move linearly transverse to the axis of running shaft.

7, a kind of mechanism as claimed in claim 6 wherein provides elastic device so that work between slider and running shaft, thereby makes idle rod be partial to and contact with the cam profile molded lines.

8, a kind of cam mechanism, comprise that an axle that has with a rotation is the cam of the cam profile molded lines at center, and follow-up unit of doing around the axle of this rotation to keep in touch with the cam profile molded lines during relatively rotating at cam and follow-up unit, eccentric section at this mechanism's cam profile molded lines is to be determined by a cam face of lift cam parts, these lift cam parts are carried by cam, so that move with relatively rotating synchronously of cam and follow-up unit.

9, a kind of being used for converts straight-line mechanism to rotatablely moving, comprise a running shaft, an axis that has with running shaft is the cam of the cam profile molded lines at center, one non-rotatably is placed on the running shaft but can does the slider of limited slip with an axial direction that is transverse to running shaft on running shaft, be used between running shaft and cam, producing the device that relatively moves, and the contact device that during this relatively rotates, keeps in touch and straight line motion is passed to slider according to an eccentric section of cam profile molded lines with the cam profile molded lines, in this mechanism, the eccentric section of cam profile molded lines is to be determined by a cam face of lift cam parts, these lift cam parts are carried by cam so that around an axle rotation that is parallel to the axis of running shaft, and provide the device of rotary lifting cam part in phase that relatively rotates mutually that is used for between running shaft and cam.

10, as a kind of mechanism of claim 8 or 9, cam wherein is that a kind of axis that has with running shaft is the hollow cam of a kind of cam ring profile molded lines at center.

11, as a kind of mechanism of above-mentioned any one claim, cam wherein is adjustable around the angular orientation of rotating shaft axis.

12, as a kind of mechanism of claim 11, the angular orientation of cam wherein can utilize the combination of the worm and worm wheel with locking lead angle to adjust.

13, as a kind of mechanism of above-mentioned any one claim, running shaft wherein is a camshaft, reciprocating valve spare of this camshaft actuated.

14, a kind of internal-combustion engine that comprises as the valve operating mechanism of claim 13.

15, a kind ofly convert straight-line mechanism with reference to accompanying drawing described being used for to rotatablely moving in fact as mentioned.

16, the combination of described here any new feature or new feature.