CN101988399A - Aerodynamic valve control device - Google Patents
Aerodynamic valve control device Download PDFInfo
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- CN101988399A CN101988399A CN2009101615816A CN200910161581A CN101988399A CN 101988399 A CN101988399 A CN 101988399A CN 2009101615816 A CN2009101615816 A CN 2009101615816A CN 200910161581 A CN200910161581 A CN 200910161581A CN 101988399 A CN101988399 A CN 101988399A
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Abstract
The invention provides a valve control device (13) used in an internal combustion engine, the engine comprises an engine valve (101) and a camshaft with a cam profile (117), and the cam profile (117) comprises a first lift curve. The valve control device comprises a first main body (201) and a second main body (203). The valve control device can be configured according to first configuration and second configuration. When the valve control device is in the first configuration, the relative motion between the first main body and the second main body caused when the first lift curve is in contact with the contact surface of a cam can prevent a valve operation connecting rod from operating the engine valve. The valve control device further comprises a mechanism, when the first lift curve is in contact with the contact surface of the cam under the situation that the valve control device is in the second configuration, the mechanism can prevent the relative motion between the first main body and the second main body so as to allow the valve operation connecting rod to operate the engine valve, wherein the mechanism is arranged to be capable of leading the force applied on the mechanism when the valve is operated is pressure when the valve control device is in the second configuration.
Description
Technical field
The present invention relates to be used in valve control apparatus in the internal-combustion engine, that be used for motion is delivered to from the nose molded lines of engine cam engine valve.
Background technique
As everyone knows, internal-combustion engine adopts a plurality of valves (intake valve and exhaust valve), is used for controlling air/fuel mixture and enters cylinder.Usually, the opening/shutting mode of these valves is controlled by the nose that rotates on engine cam.Each cam has basic circle and peach point, and mechanical linkage is connected to cam on the valve.When connecting rod moved with basic circle, it is motionless that valve keeps; But when connecting rod moved with nose, it made valve be open.Usually, along with connecting rod is back to basic circle from nose, valve is closed under the effect of spring.
Known single cam can have two nose molded lines, opens/close action in order to different valves to be provided.Variable valve-operating is well-known and allows mechanical linkage that the part of whole motion is passed to valve, otherwise this motion will all be transmitted.So, engine valve is opened and closed according to the different moment according to the required working order of motor.
A kind of such working order is an engine braking.With different according to typical burn cycle, if only allow internal-combustion engine at its cylinder compressed air and mustn't combustion fuel, then internal-combustion engine can be used as break.In case the air in the cylinder is compressed, then compressing the used energy of this air must be released, and this finishes by open engine exhaust port near the top dead center of compression stroke the time usually.Yet the power that produces on engine part in the engine compression brake process is greater than the power that produces in the normal operation process.In normal engine operation process, when in the cylinder pressure minimum being arranged, promptly piston is positioned at or contiguous lower dead center and will upwards shift to cylinder cap for exhaust stroke the time, exhaust valve often leaves.Yet, in the engine compression brake process, in cylinder material be compressed and thereby be in high pressure following time, exhaust valve is opened.Therefore, open exhaust valve in this case and need drive the cam of valve and the conventional bias voltage that connecting rod not only will overcome valve return springs, also will overcome and in cylinder, do in order to keep the reaction pressure of valve-closing.
Therefore, there are the needs that improve the mechanical type valve control apparatus, this valve control apparatus allows each cam to have one or more cam profiles, but this valve control apparatus is durable and simple, thus under the rugged environment of common vehicle motor unlikely breaking down.
Summary of the invention
According to a first aspect of the invention, a kind of valve control apparatus that is used in the internal-combustion engine is provided, motor comprises engine valve and has the camshaft of cam profile, cam profile comprises the first lift molded lines, valve control apparatus comprises first main body and second main body, and valve control apparatus can dispose according to first configuration and second, when valve control apparatus is in first configuration, when first lift molded lines contact cam contact surface, caused, relative movement between first and second main bodys stops valve operating link maneuvering engine valve, valve control apparatus comprises such mechanism, when valve control apparatus is in second configuration, when first lift molded lines contact cam contact surface, this mechanism stops relative movement between first and second main bodys to allow valve operating link maneuvering engine valve, wherein, when valve control apparatus was in second configuration, described mechanism arranged that so all basically power that promptly puts on this mechanism when valve is handled is compressive force.
Comprise also that with existing, the power in the mechanism that is used to stop relative movement of being applied to the device of shearing force and/or torsion component compares, this makes moderate progress.Pure compressive force than comprise shearing force and/or torsion make a concerted effort be easier to bear, so embodiments of the invention are more durable than known devices, especially when running into the high loading of engine braking action.
Description of drawings
Now, a plurality of embodiment of the present invention will be described with reference to the accompanying drawings, wherein:
Fig. 1 is relevant with cam, push rod, rocking arm and engine valve, according to the schematic representation of the valve tappet of first embodiment of the invention;
The more detailed view of the valve tappet of Fig. 2 presentation graphs 1;
Fig. 3 represents the exploded perspective view of valve tappet shown in Figure 2;
The partial sectional view of the valve tappet of Fig. 4 A presentation graphs 2;
Fig. 4 B shows partial sectional view partial view, valve tappet perpendicular to valve tappet shown in Fig. 4 A;
Fig. 5 is the skeleton diagram of another part of the valve tappet of presentation graphs 2;
Fig. 6 A is the skeleton diagram of a part of expression work cycle, has shown valve tappet responding engine brake cam peach point how when being in normal combustion mode;
Fig. 6 B shows the skeleton diagram of the part of work cycle, has shown how valve tappet responds the normal combustion nose when being in normal combustion mode;
Fig. 6 C shows another part of the work cycle shown in Fig. 7 B;
Fig. 7 is the skeleton diagram of the part of expression work cycle, has shown how valve tappet responds each nose when being in the engine braking pattern.
Fig. 8 shows the skeleton diagram that the valve according to second embodiment of the invention stops; With
Fig. 9 shows schematic representation relevant with cam, rocking arm and engine valve, valve tappet according to a second embodiment of the present invention;
That Figure 10 shows is relevant with cam, rocking arm and engine valve, according to the schematic representation of the valve tappet of third embodiment of the invention;
That Figure 11 a, Figure 11 b and Figure 11 c show is relevant with rocking arm, according to the schematic representation of the valve tappet of third embodiment of the invention;
Figure 11 d shows the decomposition view in rocking bar and control room;
Figure 12 a and Figure 12 b show the schematic representation according to the valve tappet of third embodiment of the invention;
That Figure 12 c shows is relevant with the rocking arm shown in the partly cut-away, according to the schematic representation of the valve tappet of third embodiment of the invention;
Figure 13 schematically illustrates the chart with respect to the valve rise of crankshaft rotation;
Figure 14 schematically illustrates according to the 3rd embodiment's tappet and the configuration of another operating mechanism.
Embodiment
Fig. 1 shows the layout of the component that internal-combustion engine (for clarity sake and not shown cylinder body) has usually.Engine valve 101 is installed in the opening of engine cylinder-body and is arranged to seal the opening of engine cylinder-body.Valve is remained on operating position by valve spring 103.Be provided with rocking arm 105, it is installed into and can puts 107 rotations around centerpivot, and an arm of rocking arm 105 contacts with the top of valve 101.The arm at pivoting point 107 opposite sides of rocking arm has overhanging element 109.Be provided with push rod 111, push rod at one end have with rocking arm on the bonding point that joins of overhanging element 109.The other end at push rod 111 is provided with second contact surface, is used for joining with valve tappet 113.Valve tappet 113 is on its top and push rod joins and have cam following face 115 at its base portion.The cam following face contacts with cam 117, and this cam is formed on the engine cam (not shown).
When cam 117 rotation (because of the camshaft that cam is housed on it is suitably driven by unshowned connecting rod from motor), cam following face 115 servo-actuateds of valve tappet 113 are in cam profile, and lifting when it crosses nose 121,123 protruding.Correspondingly, when the valve tappet lifting, it causes push rod together with moving up and down.The overhanging element 109 that this push rod promotes rocking arm 105 again moves up and down.Owing to be provided with pivot in the rocking arm 105, when being promoted by push rod 11, overhanging element 109 is around pivotal point 107 rotations, rather than vertical up-or-down movement.When overhanging element when pivotal point 107 turns clockwise (being that valve tappet and push rod move upward), described rocking arm also be forced to turn clockwise and be pressed in downwards on the valve 101 with valve 101 contacted arms, open position is provided the restoring force that this valve is overcome provide by valve spring 103.When valve tappet 113 and push rod 111 moved downward, rocking arm was rotated counterclockwise, and valve is got back to closed position by the restoring force of valve spring 103.
Be provided with oil supply system 125, together with control fuel tap 127, but their co-operation are come according to hereinafter described mode fuel feeding to valve tappet 113.Oil supply system can combine with the standard oil plant system of motor car engine, and perhaps it can be that a specialized designs is used for the independent self-loading type unit that fuel feeding is given valve tappet.Oil supply system 125 and control fuel tap 127 are electrically coupled on the control unit of engine 129 and the control of launched machine control unit.
Referring to figs. 2 to Fig. 5, the engine valve tappet according to first embodiment of the invention will be described now.As shown in Figures 2 and 3, valve tappet 113 comprises three major components: outer main body 201, interior main body 203 and empty moving portion 205.The layout of outer main body 201 will further be described with reference to figure 4A and Fig. 4 B.
Outer main body is solid column for 201 one-tenth substantially.In the bottom direction of main body 201 outward, this cylindrical wall is outwards opened and is formed base portion 207, and the bottom surface of this base portion is exactly a cam following face 115.The diameter of base portion 207 is greater than the remaining part of outer main body 201.As Fig. 4 A and the clearest the illustrating of Fig. 4 B, the end face 403 of vertical hole 401 along its longitudinal axis from outer main body 201 with constant cross section penetrates the base portion 207 of outside main body 201.Vertically hole 401 does not extend to base portion 207 from the end face 403 of outer main body 201 always, but extends near the mid point of outer main body shown in Fig. 4 A and Fig. 4 B.In midpoint, vertically hole 401 unexpected constrictions become the standpipe 405 that has less than vertical hole 401 diameters, thereby form annular surface 407.Standpipe 405 is further worn the base portion 207 of outside main body 201, up to the end that intersects vertically of it and transverse tube 409.Transverse tube 409 has the diameter that equates with standpipe 405, and outside above the portion of the opening section of base portion 207, penetrating into outside the main body 201.Standpipe 405 and transverse tube 409 constitutes a paths, oil can by this path from valve tappet 113, by lock pin 217,401 bottoms, vertical hole of main body 201 and the chamber that the bottom limited of interior main body 203 are discharged outside.
Be provided with two lock pins 217, each lock pin comprises little solid cylinder and has circular recess 219 at its base portion.These two lock pins 217 interconnect by Returnning spring 221, and each end of Returnning spring is arranged in the above-mentioned circular recess 219 of each lock pin 217.The assembly of being made up of lock pin 217 and Returnning spring 221 is inserted in the outer main body 201 by described two radially relative circular opens 213.The diameter of lock pin 217 is matched with two radially diameters of opening opposing 213.During main body 201, each lock pin 217 is arranged in vertical hole 401 with the part of its length outside being arranged in, remainder pass in the radially opening opposing 213 in the wall separately one arrive outside.Because radially opening opposing 213 is formed on annular notch 211 positions in the main body 201 outside, so that part of length of stretching to outer main body 201 outer surfaces of lock pin 217 is greatly to the external diameter that does not surpass part outer main body 201, ringless-type recess 211.
In this layout, when being applied to their outer surface effectively, each lock pin 217 can along perpendicular to outside the axis of movement of main body 201 longitudinal axis inwardly move towards another lock pin.Along with two lock pins 217 move relative to each other, Returnning spring 221 will be compressed.Stop pin 223 is arranged in vertical hole 401, between two lock pins 217.Stop pin 223 is used to limit the inside motion of lock pin 217, and promptly lock pin the time is forced to stop in the surface separately of face butt stop pin 223 in its back-end.When removing lock pin 217 suffered external force, Returnning spring 221 will stretch and attempt to promote lock pin 217 separately, and the elastic energy in Returnning spring 221 exhausts.At its uncompressed state, the Returnning spring long enough, thereby lock pin can be as described above the external outer surface of main body 201 location mutually.
Keep enclosing the outer surface arrangement of 225 (for clarity sake), thereby keep the top of circle 225 to be positioned in the annular groove 209 that is formed in the outer main body 201 around outer main body 201 not shown in Fig. 4 A and Fig. 4 B.Keep circle 225 to extend vertically downward, thereby it partly surround annular notch 211.Therefore can be easy to see, keep circle 225 to be used to stop that lock pin 217 leaves outer main body 201, although directly do not contact with the outer surface of lock pin 217.
With reference to figure 2, Fig. 3 and Fig. 5, interior main body 203 comprises the solid cylindrical portion 501 of central authorities, and it has the external diameter of the diameter in the vertical hole 401 that equals outer main body 201.At an end of the solid columnar protrusions 503 of central authorities, columnar protrusions 503 extends a bit of distance.The axis of columnar protrusions 503 is arranged with one heart with the solid cylindrical portion 501 of central authorities, but its diameter is less than the central part shown in Fig. 5 501.Become columnar protrusions 503 at diameter from central part 501, produced annular flange flange 515.Central part 501 transfers joint 505 in the termination extension in contrast to columnar protrusions 503.The diameter of joint 505 is less than the diameter of the solid cylindrical portion 501 of central authorities, but greater than the diameter of columnar protrusions 503.Diameter from central part 501 to joint 505 parts that change, produce annular flange flange 507.Finish with dome 509 the end away from central part 501 of joint 505.The dome 509 and the push rod 111 of joint 505 join.Annular groove 511 is positioned under the dome of joint 505.
In prolate shape concave surface 513 is formed on the surface of central part 501 of main body 203.The width of concave surface equals the diameter of the 3rd opening 215 in the outer main body 201, but its length is greater than described diameter.
As shown in Figures 2 and 3, interior main body 203 is positioned at vertical hole 401 of outer main body 201, and outer main body 201 with can be mutually internally the mode that reciprocatingly slides of main body 203 arrange.The 3rd opening 215 in the outer main body 201 is aimed at the prolate shape concave surface 513 of interior main body in some place along its length.Stopper pin 227 is inserted in the 3rd opening 215 of outer main body 201 like this, that is, the part of stopper pin 227 is arranged in the 3rd opening 215, and remainder is arranged in the prolate shape concave surface 513 of main body 203.Therefore, if the interior main body 203 that outer main body 201 is contained in vertical hole 401 is relatively upwards slided, then when stopper pin 227 (this pin keeps static with respect to outer main body) when running into the top of prolate shape concave surface 513, outer main body arrives extreme limit of travel, if and outer main body 201 is contained in interior main body 203 in vertical hole 401 relatively to lower slider, then when running into the bottom of prolate shape concave surface 513, outer main body arrives extreme limit of travel when stopper pin 227 (externally the main body maintenance is static mutually for this pin).
When the length of interior main body 203 allows when interior main body is positioned at outside main body 201 annular flange flange 507 and outside the end face 403 of main body 201 be in same level height, and the bottom surface 517 of columnar protrusions 503 is concordant with the end face of lock pin 217.The interval of the diameter of columnar protrusions 503 and lock pin 217 (when Returnning spring 219 is in relaxed state) is such, promptly do not have when stressed when lock pin 217 outer surfaces, the interval between the lock pin rear surface be enough to allow columnar protrusions 503 outside main body 201 between the rear surface, pass when interior main body 203 in vertical hole 401 moves upward around being contained in.When outer main body 203 when internally main body 203 continues to move upward mutually, in the upper surface of lock pin 217 is connected on the annular flange flange 515 at the place, bottom of main body 203, therefore the internal mutually main body 203 of the outer main body 201 of restriction is done and is anyly further moved upward.When this butt occurs in stopper pin 227 and gets at the upper end of prolate shape concave surface 511.
Refer again to Fig. 2 and Fig. 3, rounded tabs 229 is connected on outer main body 201 end faces 403.Be provided with opening 231 in rounded tabs 229, the joint 505 of interior main body 203 passes this opening.Opening 231 in the catch 229 is sized to the joint 505 that has only interior main body 203 and can passes, and catch 229 not only contacts with the end face 403 of outer main body 201, and depend on outer main body 201 ground, position of internal main body 203 mutually, also contact sometimes with the annular flange flange 507 of interior main body 201.Second circle 233 annular groove 511 that are arranged on the joint 505, " empty moving " spring 235 are around the protuberance of joint 505, and spring 235 is attached to respectively on each end and sheet circle 233 of rounded tabs 229 at its each end.It is noted that this sky of compression is moved spring 235 needed power must be less than overcoming valve spring 103 and and then promoting push rod 111 upwards to open valve 101 needed power.Correspondingly, the sky spring 235 of moving will be compressed before pushrod movement.
With reference to figure 6A, Fig. 6 B, Fig. 6 C and Fig. 7, present operation with more detailed description engine valve tappet.
When the cam on engine cam 117 rotation, cam following face 115 on the cam 117, will act on the outer main body 201 of valve tappet 113 successively corresponding to the peach point 121,123 of normal combustion mode and engine braking pattern.In normal combustion mode, the lock pin 217 of valve tappet 113 will be in the unlocked position as Fig. 6 A, Fig. 6 B and Fig. 6 C, that is, Returnning spring 219 is not compressed and lock pin 217 parts are arranged in vertical hole 401 and part is passed radially opening opposing 213.When on the cam 117 corresponding to the peach point 121 of brake operating when the base portion of valve tappet 113 turns over for 207 times, it will promote tappet 113 base portions 207 and upwards and therefore promote outer main body 201 and make progress.Because the empty spring 235 needed power of moving of compression are less than overcoming valve spring 103 needed power by handling the push rod 111 that joins with tappet joint 505, so the interior main body 203 of tappet 113 will keep static, and simultaneously outer main body 201 will move upward and compress the sky spring 235 of moving.Although lock pin 217 moves upward with outer main body 201, the scope deficiency that moves upward of the outer main body 201 that is caused by engine braking peach point 121 is so that lock pin 217 touches the annular flange flange 515 on interior main body 203 bottoms.Also have, stopper pin 227 only moves upward in prolate shape concave surface 513 and does not contact its end.Owing to have between the lock pin 217 at interval, so they are only in the both sides process of the columnar protrusions 503 of interior main body 203.
As shown in Figure 6A, the peak place that moves upward of main body 201 (the ultimate range A that the moving peach point 121 of the launched mechanism of promptly outer main body upwards promotes) outside:
The sky spring 235 of moving will be compressed identical distance A;
Stopper pin 227 distance A that will in prolate shape concave surface 513, move upward, but still can not contact the concave surface top; With
The upper surface of lock pin 217 is the annular flange flange 515 of the main body distance A (relatively, columnar protrusions 503 will move downward approximate distance A between lock pin 217) that moves upward inwardly.
But, interval 601 will be arranged between main body 201 and the interior main body 203 outside, correspondingly, interior main body 203 will can not rise with rising in response to the outer main body that engine braking peach point is caused.Equally, the push rod 111 that is connected on the interior main body 203 by joint 505 will can not handled.
With reference to figure 6B and Fig. 6 C, because normal combustion mode nose 123 ratio engine braking mode peaches point 121 height, so it causes outer main body climb greater than the climb that is caused by engine braking pattern peach point.Correspondingly, when engine braking pattern peach point 201 worked, outer main body 201 moved upward usually, thereby still had interval 601 when initial.But in this case, outer main body 201 continues to move upward, the result, even lock pin 217 still in the both sides process of the columnar protrusions 503 of interior main body 203, but lock pin 217 upper surfaces touch the annular flange flange 515 in interior main body 203 bottoms.In addition, in lock pin 217 contact annular flange flange 515, the top of the prolate shape concave surface 513 in stopper pin 217 arrives in the main body 203.This situation shown in Fig. 6 B, can see here that the distance of internal mutually main body 203 motions of outer main body 201 is greater than the distance (as shown in Figure 6A) under engine braking flange peach point 121 situations.In addition, Fig. 6 B shows and no longer includes interval 601 between outer main body 201 and the interior main body 203.From this moment, interior main body 203 is forced to rise with the speed identical with outer main body 201, so push control rod 111 and final maneuvering engine valves 101.When outer main body 201 rose, the power that makes progress was passed to interior main body by lock pin 217, therefore it is also moved up.The power of transmitting by lock pin 217 plays the compressed effect of lock pin that makes.
When normal combustion mode nose 123 turned over the center, valve tappet 113 will begin to fall.Both will one in front and one in back fall outer main body 201 and interior main body 203, be closed (that is, in the push rod 111 that does not have power to be connected from joint 505 is applied on main body 203 joints 505) until engine valve 101.In the 101 pent moment of engine valve, interior main body 203 will stop to fall, and outer main body 201 will be promoted and continue to fall by move spring 235 of sky, until getting back to the position of normal combustion mode nose 123 before working.
Therefore as can be seen, be at lock pin under the situation of initial unlocked position, the lifting that engine braking nose 121 is caused will can not be passed to engine valve 101, and the lifting that is caused by normal combustion mode nose 123 will be passed to engine valve.
When needs engine braking pattern, the control fuel tap is opened to allow the outer surface of high pressure oil contact lock pin 217.Thisly be applied to pressure on lock pin 217 outer surfaces by high pressure oil and promote them and inwardly draw close mutually.Lock pin 217 will inwardly be drawn close mutually, contacts with stop pin 223 and is in as shown in Figure 7 position until them.This is second locked position of coupler.
Scheme as an alternative, lock pin 217 can be assemblied in its radially opening opposing 213 separately like this, that is and, high pressure oil can be easy to flow through around lock pin 217, flows to chamber behind the lock pin 217 from the outer surface of valve tappet 113.In the case, the oil of the chamber behind the arrival lock pin will flow through the standpipe and the transverse tube (being respectively 405 and 409) of current drainage.In this configuration, the high pressure oil that needs are stable flows, and it maintains lock pin 217 on their the inside locked position of coupler by the high pressure oil that flows through lock pin.
When on the cam, corresponding to the peach point 121 of engine braking action when valve tappet turns over for 113 times, it will upwards promote the base portion of tappet 113 and therefore upwards promote outer main body 201.Yet, be at lock pin 217 under the situation of " locking " position, when outer main body 201 moves upward (being driven by nose 121), the columnar protrusions 503 of main body 203 in the upper surface of lock pin 217 presses, therefore interior main body 203 is forced to move on outer main body 201.When outer main body 201 rose, therefore main body 203 in the power that makes progress is passed to by lock pin 217 also moved upward it.The power of being transmitted by lock pin 217 plays their compressed effects that makes.In the case, do as a wholely when all moving upward when outer main body 201, interior main body 203 and the sky spring 235 of moving, outer main body 201 is not compressed the sky spring 235 of moving.Therefore, the rising of engine braking nose 121 is directly passed to push rod 111 (thereby finally pass to engine valve 101 self) by in fact hard valve tappet.In running locking pattern, valve tappet 113 will directly respond nose 121,123 caused liftings and lifting.The breaking force of passing to engine valve 101 by motor tappet 113, push rod 111 and rocking arm 115 by engine braking nose 121 is not enough to overcome the restoring force of valve spring 103, be applied to power on the base portion of engine valve 101 but be enough to overcome by the pressurized gas in the cylinder, these pressurized gas are compressed and play the effect that keeps engine valve 101 in the closed position in the engine braking action.
When no longer needing the engine braking pattern, the control fuel tap be closed and lock pin 217 outer surfaces on oil pressure be reduced.When outer oil pressure during less than the restoring force of Returnning spring 219 (spring is compressed when lock pin 217 is inwardly drawn close mutually), Returnning spring 219 will force two lock pins 217 outwards to get back to unlocked position apart from each other.Then, valve tappet 113 will carry out the action relevant with normal combustion mode once more as described above.
Therefore as can be seen, be at lock pin 217 under the situation of second locked position of coupler, all will be delivered to engine valve 101 by engine braking nose 121 and by the 123 caused risings of normal combustion mode nose.
Can also understand, no matter whether lock pin 217 upper surfaces contact columnar protrusions 503 or contact annular flange flange 515, by outer main body 201 by the lock pin transmission be used to make in the power that rises of main body 203 come down to pure pressure.At lock pin fully by outer main body 201 under the situation of their bottom supporting, therefore the surface of the interior main body 203 that contacts with lock pin 217 also so acts on the upper surface of lock pin 217, does not have shearing stress to be applied on the lock pin 217.Apply pure pressure and can obtain more durable layout to lock pin, thereby lost efficacy under the valve tappet 113 unlikely on-stream engine braking patterns, and in the engine braking pattern, owing to need extra power to overcome pressurized gas in the cylinder opening engine valve, so the situation of the power by the valve tappet transmission during greater than normal combustion.
Second embodiment
To describe second embodiment of engine valve tappet now, in the present embodiment, the configuration of engine part is different from first embodiment's part and is that motor comprises overhead camshaft, rather than camshaft and push rod.Setting type and running have a lot of similarities, and similar feature will be represented with similar reference character with reference to first embodiment's description.
With reference to figure 8, show valve tappet 113 '.In a second embodiment, interior main body 203 ' is placed in the hole of outer main body 201 ' like this, and promptly interior main body 203 ' can external mutually main body 201 ' reciprocatingly slide.But compare with first embodiment, the base portion of interior main body 203 ' does not have columnar protrusions, the substitute is, and this base portion is smooth.
Lock pin 217 ' is similar to the described lock pin of first embodiment, but the last angle that each lock pin 217 ' (promptly is positioned at the part of the farthest on the center direction of main body 201 outward) at their rear portions comprises the supercilium 801 of depression.Yet in first embodiment, the upper surface of lock pin 217 or contact with the columnar protrusions 503 of interior main body 203, or contact with annular flange flange 515, this depends on that lock pin 217 is in locked position of coupler (promptly being pushed to the central authorities of outer main body 201) or unlocked position.In a second embodiment, if lock pin 217 ' is in the unlocked position, the planar base portion of so interior main body 203 ' can moving up and down between the rear surface at lock pin 217 ' separately, and when being in locked position of coupler, the planar base portion of interior main body 203 ' partly is positioned on the depression supercilium 801 of lock pin 217 '.
Interior main body 203 in first embodiment is solid, and by contrast, interior main body 203 ' in a second embodiment is hollow and comprises pillared plunger 803 substantially.Pillared plunger 803 can back and forth slide up and down in interior main body 203 ' substantially.Column plunger 803 so is arranged in main body 203 ', promptly is formed for the hydraulic lash compensating part pressure oil cavity 805 of (the hydraulic lash compensating part is totally represented with 807) in Fig. 8 between the base portion of the base portion of column plunger 803 and hollow interior main body 203 '.Gap compensation/the regulating mechanism that is used for motor car engine is well-known, therefore is not described in further detail in this article.But briefly, column plunger 803 comprises reservoir compartment 809, and reservoir compartment 809 is communicated with pressure oil cavity 805 fluids by gap compensating part 807.Main body 203 ' is moved as a unit usually with plunger 803 in it will be apparent to those skilled in the art that.But in first embodiment, the topmost part of valve tappet is the topmost part of interior main body 203, and in a second embodiment, it is the top of plunger 803.Gap compensating part 807 can be operated, and is used to adjust the length that plunger 803 projects upwards from hollow interior main body 203 '.
Second embodiment's valve tappet is designed to and can works in having the motor that is different from the described part configuration of first embodiment (as shown in Figure 1).Fig. 9 shows second embodiment's valve tappet, and the motor that this valve tappet is arranged to be used for having overhead camshaft 901 is worked, and this is different from the camshaft shown in Figure 1 and the collocation form of push rod.In this configuration, the outer main body 201 ' of valve tappet 113 ' is fixedly installed in the motor body or passes through other mounting mechanism and install.Be provided with rocking arm 903, this rocking arm joins at the plunger 803 of first end and valve tappet, joins at the bar of its other end and engine poppet valve 905.The contacting point that joins with plunger 803 tops realizes that by the hemisphere nest 907 that is processed to be assemblied in around the circular top part of plunger 803 at rocking arm 903 first ends however, those skilled in the art will be readily understood that other the way of contact.With the contacting point that the bar of engine poppet valve 905 joins can be that the valve that is positioned at second end of rocking arm 903 contacts cushion block 907, in the case, the following side contacts valve stem top of valve contact cushion block 909, same, however, those skilled in the art will be readily understood that other the way of contact.Rocking arm 903 comprises rotatable cam follower 911, and this cam follower and valve are handled cam 913 contact (, valve handle cam 913 have basic circle portion 915 and lifting parts 917) here.
Engine poppet valve 905 upwards is biased into closed position by valve spring 919.Therefore the compression valve spring also causes engine poppet valve 905 to open sky that needed power is higher than compression valve tappet spring 235 ' the needed power of moving.
On-stream, second embodiment's valve tappet 113 ' can be used as the invalid mechanism of valve, thereby makes otherwise can be handled the motion that the lifting parts 917 of cam 913 passes to engine poppet valve 905 through rocking arm 903 by valve invalid.
When lock pin 217 ' was positioned at unlocked position, interior main body 203 ' (comprising plunger 803 and gap compensating part 807) moved up and down in the hole of main body 201 ' outside.When interior main body 203 ' outside in the hole of main body 201 ' during motion downwards, main body 203 ' was from passing between them in the interval between the lock pin 217 ' rear surface was enough to allow.Sky move spring 235 ' stop in main body 203 ' moving downward and playing interior main body 203 ' bias voltage in the main body 201 ' outside to its effect from outer main body 201 ' outstanding position farthest.When valve was handled lifting parts 917 rotations of cam 913, it pressed the rotatable cam follower 911 of rocking arm 903 gradually, causes rocking arm 903 displacements.Yet, because the required power of compression valve spring 919 is greater than the sky of the compression valve tappet required power of spring 235 ' of moving, thus rocking arm 903 pivots around the top of valve stem and the interior main body 203 ' that promotes valve tappet to the lower compression sky spring 235 ' of moving.Therefore, when lock pin 217 ' was in the unlocked position, the motion of rocking arm 903 made the interior main body 203 ' motion of valve tappet, rather than makes the valve stem motion, thereby engine poppet valve 905 keeps closing.
Yet if wish that handling the motion that the lifting parts 917 of cam 913 causes by valve is passed to engine poppet valve 905 as " valve event " (being that valve will be opened), lock pin 217 ' moves to locked position of coupler.Lock pin 217 (is high pressure oil is supplied to lock pin 217 ' by control fuel tap and suitable supply line a outer surface according to moving with the described identical mode of first embodiment between unlocked position and locked position of coupler, the high pressure oil pressure that lock pin 217 ' outer surface is exerted pressure promotes lock pin is drawn close compression reseting spring 221 ' in this process towards the central authorities of valve tappet).
When lock pin 217 ' was in locked position of coupler, interior main body 203 was stopped in motion downwards in the hole of outer main body 201 ', because the base portion of interior main body 203 ' has now leaned against on the depression shoulder 801 of lock pin 217 '.Therefore, the sky of valve tappet moving be cancelled and valve tappet as rigid element work.No longer include relative movement between interior main body 203 ' and the outer main body 201 '.
Interior main body 203 ' and outer main body 201 ' according to the blocked situation of this rigid arrangement under, main body 203/ plunger 803 moves downward required power greater than the required power (remaining in engine cylinder-body or other supporting structure because of the valve tappet rigidity) of compression valve spring 919 in making.Thereby when the lifting parts 917 of handling cam 913 by valve when rocking arm 903 was forced to move, rocking arm 903 pivoted around plunger 803, is pressed in downwards on the valve stem, resist thus valve spring 919 restoring force open engine poppet valve 905.
Because lock pin 217 ' part is positioned under the base portion of main body 203 ',, and on lock pin 217 ', there is not the shearing stress component so any power that is applied to plunger 803 tops (for example by rocking arm 803) and passes to lock pin 217 ' will be pure pressure.Because pressure ratio shearing stress is easier to bear, thus lock pin 217 ' and and then valve tappet do as a whole more durablely, be difficult for running into the inefficacy of material and/or part.
The 3rd embodiment
Figure 10 shows engine air door system 1000, comprises exhaust valve 1001, rocking arm 1002, push rod 1003 and cam 1004.Exhaust valve 1001 is arranged in the relief opening 1005 of engine cylinder-body 1006, and the valve spring 1007 that centers on the valve stem setting is arranged to bias voltage exhaust valve 1001 to close relief opening 1005.Rocking arm 1002 can be put 1008 around centerpivot and be provided with rotatably, and an end of rocking arm 1002 contacts with the upper end of the bar of valve 1001.Rocking arm 1002 is provided with integral housing 1002a at its other end, and this housing comprises valve control room 1009.One end in valve control room 1009 and an end of push rod 1003 join.
When camshaft (not shown) rotation and and then during cam 1004 rotations, push rod 1003 servo-actuateds are in the molded lines of this cam, and cross nose 1012 and lifting in 1013 o'clock at it.
Figure 11 a and Figure 11 b show and are in motor impeding shutdown configuration (Figure 11 a) and valve control room 1009 and the rocking arm 1002 of motor when interrupting open configuration (Figure 11 b).Be appreciated that at the rocking arm 1002 shown in this two secondary figure be translucent, so that observe other part.In order to contrast, Figure 11 c provides the view same with Figure 11 a, except rocking bar 1002 illustrates with opaque form.Figure 11 d shows the decomposition view in rocking bar 1002 and control room 1009.
Second main body 1015 comprises 1015a of first portion and second portion 1015b (not shown in Figure 11 d).Be similar to first main body 1014, the 1015a of first portion also is column (although it is than first main body, 1014 height) usually, the 1015a of first portion has the diameter similar to first main body 1014 and is supported among the housing 1002a, a shade below first main body 1014 and coaxial with first main body.
Away from an end of 1014, the 1015a of first portion comprises the protruding 1015d (seeing Figure 11 d) that the other parts diameter of the relative first parts 1015a reduces at it, and this projection is passed slightly and run through the hole that housing 1002a one end ground forms.Second portion 1015b (not shown in Figure 11 d) comprises diameter less than the cylinder of the first parts 1015a and have opening end and the closed end that is sleeved on the protruding 1015d, and this closed end forms the surface of contact that joins with push rod 1003.Retaining clip among the second portion 1015b (not shown, or other suitable holding device) second portion 1015b is firmly remained on the protruding 1015d.
Second main body 1015 is supported among the housing 1002a by any suitable device such as retaining clip 1015e, thereby second main body 1015 can (Figure 11 a) and rotation between the motor rotational position (11b) that interrupts opening at the rotational position of motor impeding shutdown around the longitudinal axis A-A of chamber 1009.
The 1015a of first portion of second main body 1015 comprises lever 1015c, the side surface extension that this lever is horizontally through the elongated cuts 1021 that runs through and partly centers on housing 1002a from first portion.Lever 1015c finishes with the pommel 1015d between planar driving member 1020.
When chamber 1009 and operating mechanism 1016 were in motor impeding shutdown position, lever 1015c was in first end of otch 1021.
For the ato unit interrupt mode, system's 1010 breakout pressure fluid source such as source of high pressure air, (Figure 11 a) moves to its forward facing position (Figure 11 b) from its retracted position to make piston.When piston 1018 moves, promote second end of lever 1015c from first end of otch 1021 to otch 1021 at rightmost driving member in Figure 11 a and Figure 11 b, this causes second main body 1015, and (Figure 11 a) rotates to motor and interrupts enable possition (Figure 11 b) from motor impeding shutdown position.
When the motor interrupt mode was lost efficacy subsequently, system did not work the pressure fluid supply source, and Returnning spring 1019 makes piston 1018 move to its retracted position from its forward facing position.When living base 1018 motions, in Figure 11 a and figure b, promote first end of lever 1015c, cause second main body 1015 to interrupt enable possition (Figure 11 b) and rotate to motor impeding shutdown position (Figure 11 a) from motor from second end of otch 1021 to otch 1021 at leftmost driving member.
Figure 12 a and Figure 12 b schematically illustrate and are in motor impeding shutdown position (Figure 12 a) and be in the chamber 1009 that motor interrupts enable possition (Figure 12 b).Figure 12 c represents rocking arm 1002 with the schematic representation of partly cut-away, and this moment, the chamber was in motor interruption enable possition.These figure show first main body 1014 that includes rounded ends 1014d and second main body 1015 that includes corresponding rounded ends 1015c together with Figure 11 d, and above-mentioned end is faced mutually.End 1014d and 1015c have sawtooth around its length strip, and each end comprises a series of recesses that replace and projection.On motor impeding shutdown position, therefore each crowning of end 1014d exists the gap to the respective notches of end 1015c in both.Interrupt on the enable possition at motor, each crowning of end 1014d is to the respective bump of end 1015c, and each recess of end 1014d is in the face of the respective notches of end 1015c.
In engine operation process, when 1001 rotations of the cam on the camshaft (not shown), peach point 1012 and 1013 is come push rod 1003 places successively.In normal combustion mode, this chamber is in the motor impeding shutdown configuration of Figure 12 a.When on the cam 1001, corresponding to the peach point 1012 of motor interrupt action during in 1003 times motions of push rod, its promotes push rod 1003 upwards, push rod and then promote second main body 1015 again upwards.When second main body 1015 moved upward, first main body, 1014 relative rocking bars 1002 were fixed and keep transfixion.When second main body 1015 moves upward, each projection of the end 1015c of band saw tooth is moved in the respective notches of facing of end 1014d of band saw tooth, and each recess of the end 1015c of band saw tooth moves on the respective bump of facing of end 1014 of band saw tooth.Yet, motor interrupt peach point 1015 caused second main bodys 1015 the scope deficiency that moves upward so that end 1014d and 1015c be in contact with one another.Two ends rise to the peak place in second main body 1015 and keep very small gap, thereby moving upward of push rod can not cause rocking arm 1002 pivots and open valve.When peach point 1012 rotated through the center, the push rod 1003 and second main body dropped to the position that peach point 1012 works and kept before.At the indoor sky spring 1015f (seeing Figure 11 d) that moves that is provided with, when second main body 1015 moved upward, the sky spring 1015d that moves was compressed, in case and peach point 1012 turn over the center, the sky spring 1015d that moves promotes second main body 1015 downwards.
When corresponding to the peach point 1013 of normal combustion action during in 1003 times rotations of push rod, it makes distance that second main body 1015 rises greater than the climb that is caused by peach point 1012, because it is higher peach point.Correspondingly, when 1012 work of engine braking peach point, second main body 1015 begins to move upward, but in this case, second main body 1015 continues to move upward, thereby cause the end 1014c engagement of the end 1015c of band saw tooth and band saw tooth, first main body 1014 and second main body 1015 are moved as integral piece, thereby moving upward of push rod 1003 causes rocking arm 1002 to pivot clockwise and cause valve 1001 to be opened.
When peach point 1013 turned over the center, the push rod 1003 and second main body 1015 descended, and valve 1001 is closed under spring 1007 effects, and rocking arm 1002 rotates counterclockwise.
When needs motor interrupt mode, the supply of control system 1010 primer fluid hydraulic fluid so that piston moves to forward facing position from retracted position, and makes second main body 1015 turn to the interrupt mode enable possition in the case.When motor interrupted peach point 1012 in 1003 times rotations of push rod, it promoted push rod upwards, and then promoted second main body 1015 upwards.In the interrupt mode enable possition, each crowning of the end 1014 of band saw tooth is to the corresponding projection of the end 1015c of band saw tooth, thereby when push rod rose, second main body 1015 did not have ability or may relative first main body 1014 move hardly.On the contrary, when forcing valve to be opened when rocking arm 1002 clockwise pivots, first main body 1014 is moved as integral unit along with the rising of push rod 1003 with second main body 1015, moves with rocking arm 1002 under the effect of push rod 1003 with being integral.
When peach point 1012 rotated through the center, valve was closed under spring action, and rocking arm 1002 pivots counterclockwise and push rod 1003 descends.
When peach point 1013 during in push rod 1003 times rotation, valve opens and closes in the same way, although because peach point 1013 is higher, so valve is opened greatlyyer than peach point 1012 when 1003 times rotations of push rod and the time is longer.
Figure 13 represents that the valve with crankshaft rotating (X-axis) contrast promotes the plotted curve of (Y-axis).Can find out from plotted curve that in normal combustion mode, each circulation that is caused by peach point 1013 is exhaust valve actuation once, wherein exhaust valve opens and cuts out at an EVC at an EVO.In the motor interrupt mode, in each circulation valve event is arranged twice, wherein just to arrive top dead center (TDC) when opening before when valve, cause valve event for the first time by peach point 1012, be used for pressurized gas is discharged (the motor interrupt action wherein promotes 1.6mm usually) in the cylinder, and (normal valve is moved when valve is opened at an EVO-B place and closed at an EVC-B place, wherein promote 10mm usually), cause valve event for the second time by peach point 1013." empty moving " that motion absorbed by second main body, 1015 relative first main bodys 1014 is shown in broken lines.For the purpose of complete, this plotted curve also shows the valve event of the corresponding engine intake valve of working together with exhaust valve.
The shape of described end is such, that is, in the valve event process, the power of being transmitted by their (and by whole chambers) is pure compressive force.If valve event is the valve interrupt action, then this is particularly advantageous, because relevant high chamber pressure causes corresponding high pressure to be applied on this chamber.Because the power of being transmitted by the rising end only is pressure,, this chamber is not easy to break down so comparing when comprising torsion/shearing force.
Figure 14 a (motor impeding shutdown configuration) and Figure 14 b (motor interruption open configuration) show alternate embodiment, in this embodiment, piston 1018 is not supported on the rocking arm 1002, but but to-and-fro motion be installed on the air supply pipe 1022, control system 1010 is interrupted the enable possition by this air supply pipe supply pressurized air so that piston 1018 moves to motor from motor impeding shutdown position.Still be provided with spring 1019, be used for pressurized air being supplied make when invalid piston 1018 get back to motor interrupting stop position in control system.
Modification
It will be understood to those of skill in the art that valve tappet 113 of the present invention also can be used as " directly " pushing device, rather than by push rod 111 and rocking arm 105 effects, in " directly " pushing device, joint 505 is attached to directly on the engine valve 101.
It will be understood to those of skill in the art that valve tappet, may be only carry out when cam is in basic circle portion handling, the compressive force on the valve tappet thereby be minimum in the locked position of coupler of lock pin and the conversion between the unlocked position for first or second embodiment.
Those skilled in the art will be understood that also the keying of the control fuel tap among first and second embodiments all can automatically perform by suitable control system, thereby its running can be by automation.
First and second embodiments' lock pin 217 is described pillared.But it will be understood to those of skill in the art that lock pin can have at its upper surface on the locked position of coupler is positioned under the main body and is subjected to the Any shape or the cross section of pure pressure.
Although second embodiment who has described only has single lifting parts about handling cam, but it will be understood to those of skill in the art that handling cam can have a plurality of lifting parts (in them can corresponding to as the valve opening action of the described engine compression brake of first embodiment).In the case, engine control/management unit or similar device can be controlled the fuel tap action, so that lock pin moves, thereby can selectedly pass to engine poppet valve corresponding to one or more valve events of handling a plurality of lift molded lines on the cam between locked position of coupler and unlocked position.
In order to be used in the motor that needs engine compression brake, to handle cam and can have first " burning " lift molded lines and second " engine braking " lift molded lines.When the motor plan is worked in normal combustion mode rather than under engine braking, control unit of engine will be handled control fuel tap (and then handling lock pin arrival locked position of coupler), thereby engine poppet valve is opened by " burning " lift molded lines.In case pass through " burning " lift molded lines and cam basic circle is rotated against cam follower, then control unit of engine will be handled control fuel tap (and then handling the lock pin position to unlocked position) before the lifting parts action corresponding to " engine braking action ".Therefore, when " engine braking " lifting parts was rotated against cam follower, engine poppet valve was not opened.In case " engine braking " lift molded lines passes through and cam rotates basic circle portion once more against cam follower, then control unit of engine will be handled the control fuel tap once more, make the lock pin position get back to locked position of coupler, being that " burning " lift molded lines is ready once more.This circulation will continue.
When motor planned work with the engine braking state, control unit of engine will be handled and control fuel tap (and then making the lock pin position come locked position of coupler) and all keep lock pin to be in locked position of coupler in two lifting parts of cam when cam follower rotates.Like this, engine poppet valve both can be opened by " burning " lift molded lines, can be opened by " engine braking " lift molded lines again.Lock pin all will be maintained at locked position of coupler when the needs engine braking.When being in " engine braking " pattern, the breaking force that puts on engine poppet valve 905 from the engine braking nose must not only be enough to overcome the restoring force of valve spring 919, also must overcome by the pressurized gas in the cylinder and be applied to power on the engine poppet valve 905, these pressurized gas are compressed and play the effect that keeps engine valve 905 in the closed position in the engine braking action.Although when valve tappet is rigidity (lock pin 217 is in locked position of coupler), can occur during just as " engine braking " pattern in being in running; rocking arm 905 only rotates around the top of plunger 803, but still the compressive component is delivered to the base portion of valve tappet downwards from rocking arm.In on-stream " engine braking " pattern, this power may quite reach, because in order to open engine valve 905, this driving force not only must overcome valve spring 919, open engine valve with also must being enough to resist the compressed-air actuated additional pressure of injection in cylinder.
The configuration of lock pin among second embodiment allows lock pin that compressive force is led away from rocking arm 903, as be applied on the lock pin 217 not with the pure compressive force of shear stress components, even if they be between main body 203 and the outer main body 201.Apply pure compressive force and can obtain more durable layout to the lock pin, thereby valve tappet is unlikely breaks down in the engine braking pattern of running.
In the 3rd embodiment, 1014 rotations of second main body, 1015 relative first main bodys change to motor impeding shutdown collocation form so that the configuration of chamber interrupts opening collocation form from motor, otherwise perhaps.It will be understood that, also can realize the relative movement except that rotation in other embodiments, for example transverse movement relatively.
Described a plurality of embodiment of the present invention in above specification in detail, those skilled in the art it is believed that from reading and understanding and understand multiple change and modification this specification.These all changes and modification are planned in the present invention involved, and they all fall into the scope of appending claims.
Claims (35)
1. valve control apparatus (113) that is used in the internal-combustion engine, this motor comprises engine valve (101) and has the camshaft of cam profile (117), this cam profile (117) comprises first lifting curve, this valve control apparatus comprises first main body (201) and second main body (203), wherein this valve control apparatus can dispose by first configuration and second, when this valve control apparatus is in first configuration, when first lifting curve contact cam contact surface, caused, relative movement between first main body and second main body stops the valve operating link to handle this engine valve, this valve control apparatus comprises mechanism, be at this valve control apparatus under the situation of second configuration, when first lifting curve contact cam contact surface, this mechanism stops the relative movement between first main body and second main body to handle this engine valve to allow this valve operating link, it is characterized in that, when this valve control apparatus was in second configuration, it was compressive force that this arrangement of mechanism becomes to make the power that puts on this mechanism when this valve is handled.
2. valve control apparatus according to claim 1, it is characterized in that, this mechanism comprises locking mechanism, this locking mechanism is configured to be in the release configuration when this valve control apparatus is in first configuration, dispose and when this valve control apparatus is in second configuration, be in locking, wherein when this locking mechanism is in blocking, this locking mechanism is arranged to contact first main body and/or second main body, and it is compressive force that described contact makes the nearly all power that puts on this locking mechanism when this valve is handled.
3. valve control apparatus according to claim 2, it is characterized in that, this locking mechanism (217) comprises first relative blocking element and second blocking element (217), first blocking element and second blocking element (217) can closely move to locked position of coupler from unlocked position mutually, so that this locking mechanism is configured to blocking, in blocking, the first relative blocking element and second blocking element contact between each contact surface of first main body and second main body and with each contact surface.
4. valve control apparatus according to claim 3 is characterized in that this locking mechanism comprises operating mechanism, is used to make first blocking element and second blocking element (217) to move to locked position of coupler from unlocked position.
5. valve control apparatus according to claim 4, it is characterized in that this operating mechanism comprises and is used for giving this locking mechanism so that first blocking element and second blocking element (217) move to the valve of locked position of coupler and are used to open and close the mechanism of this valve from unlocked position from fluid source supply pressure fluid.
6. valve control apparatus according to claim 5, it is characterized in that, this locking mechanism comprises the bias mechanism between first blocking element and second blocking element, and this bias mechanism is arranged to first blocking element and second blocking element from the locked position of coupler bias voltage to unlocked position.
7. according to each described valve control apparatus in the claim 3 to 6, it is characterized in that, second main body comprises projection at the one end, this projection limits the contact surface of second main body, second main body also limits around this protruding concave surface, wherein when this locking mechanism was in released state and between first main body and second main body relative movement is arranged, the motion of first blocking element and second blocking element was held by described concave surface.
8. according to each described valve control apparatus in the claim 3 to 6, it is characterized in that, the shoulder that each comfortable one end of first blocking element and second blocking element has depression, when this locking mechanism was in the locking configuration, the shoulder of this depression contacted the described contact surface of second main body.
9. according to each described valve control apparatus in the claim 2 to 8, it is characterized in that, first main body (201) comprises this cam contact surface, and when this locking mechanism (217) when being in released state, when the first lift molded lines contacted this cam contact surface, first main body (201) was handled this engine valve relative to the prevention valve operating link that moves of second main body (203).
10. valve control apparatus according to claim 9, it is characterized in that, when this locking mechanism is in blocking and this cam contact surface and contacts the first lift molded lines, this locking mechanism makes first main body and second main body as a unit motion, handles this engine valve to allow this valve operating link.
11. according to claim 9 or 10 described valve control apparatus, it is characterized in that, this cam profile comprises second lifting parts, when this locking mechanism is in released state and this cam contact surface and contacts second lifting parts, force first main body to move and touch second main body, first main body and second main body are handled this engine valve as a cell moving to allow this valve operating link subsequently.
12. valve control apparatus according to claim 11, it is characterized in that, when this locking mechanism was in blocking and this cam contact surface and contacts second lifting parts, this locking mechanism made first main body and second main body handle this engine valve as a cell moving to allow this valve operating link.
13., it is characterized in that this valve operating link comprises push rod (111) and rocking arm (105) according to each described valve control apparatus in the claim 9 to 11, second main body contacts this push rod, this push rod contacts this rocking arm, and this rocking arm contacts this valve.
14. according to one of claim 2 to 6 or the described valve control apparatus of claim 8, it is characterized in that, first main body is used for fixing and is installed on this motor, but be installed in this first main body to the second main body to-and-fro motion, when this locking mechanism is in blocking and this cam contact surface and contacts first lifting parts, this locking mechanism stops second main body to move in first main body, thereby allows this power management connecting rod to handle this engine valve.
15. valve control apparatus according to claim 14, it is characterized in that, when this locking mechanism was in released state and this cam contact surface and contacts first lifting parts, second main body moved to stop this valve operating link to handle this engine valve in first main body.
16. according to claim 14 or 15 described valve control apparatus, it is characterized in that, this valve operating link comprises rocking arm, and this rocking arm comprises first end and the cam follower that is used to contact second end of valve and comprises this cam contact surface that is used to contact second main body.
17., it is characterized in that the shape of this locking mechanism and second main body can make relative second main body motion when this locking mechanism is in released state of first main body according to each described valve control apparatus in the claim 2 to 16.
18., it is characterized in that first lifting parts (121) limits and is used to provide the valve of engine braking to promote the engine braking pattern molded lines that moves according to each described valve control apparatus (113) in the claim 2 to 17.
19. valve control apparatus according to claim 11 (113) is characterized in that, second lifting parts (123) limits and is used to provide the valve of burning to promote the normal engine combustion mode curve that moves.
20. according to the described valve control apparatus of one of one of claim 2 to 7 or claim 9 to 14 (113), it is characterized in that, first main body (201) also comprises annular retaining mechanism (225), is suitable for part and surrounds this locking mechanism and this locking mechanism is remained in first main body (201); Diameter is greater than the base portion of first main body (201), and this base portion (207) is suitable for contacting this cam profile (117).
21. according to the described valve control apparatus of one of one of claim 2 to 7 or claim 9 to 14 (113), it is characterized in that, first main body (201) comprises first opening (215), second main body (203) comprises second opening (513), this valve control apparatus (113) also comprises and is suitable for being assemblied in this opening (215,213) link in (227), this link (227) be arranged to allow on the direction that is parallel to this valve tappet (113) longitudinal axis between first main body and second main body (201,203) slide relative stops second main body (203) to be rotated relative to first main body (201) simultaneously.
22., it is characterized in that this valve control apparatus also comprises the sky spring (235) of moving according to each described valve control apparatus in the claim 2 to 21, this sky is moved and is compressed in the relative movement process of spring between first main body and second main body.
23. valve control apparatus according to claim 1, wherein, this mechanism comprises the end separately of first main body and second main body, and this end is configured to and allows described relative movement and stop described relative movement when this valve control apparatus is in first configuration when this valve control apparatus is in second configuration.
24. valve control apparatus according to claim 23, it is characterized in that, the described end of first main body comprises one or more first projection and one or more first concave surfaces, the described end of second main body comprises one or more second projection and one or more second concave surfaces, when this valve control apparatus is in first configuration, in described one or more first concave surface each is in the face of in described one or more second projectioies corresponding one, in described one or more second concave surface each is in the face of in described one or more first projectioies corresponding one, thereby can carry out described relative movement, when valve control apparatus is in second configuration, in described one or more first projection each is in the face of in described one or more second projectioies corresponding one, thereby stops described relative movement.
25. according to claim 23 or 24 described valve control apparatus, it is characterized in that, the configuration of this valve control apparatus by make second main body from primary importance move to the second place and from first configuration change be second the configuration.
26. valve control apparatus according to claim 25 is characterized in that, the configuration of this valve control apparatus by make second main body from primary importance rotate to the second place and from first configuration change be second the configuration, otherwise or.
27. according to each described valve control apparatus in the claim 23 to 26, it is characterized in that, this cam profile comprises the second lift molded lines higher than the first lift molded lines, when this valve control apparatus is in first configuration, contact under the situation of this cam contact surface at the second lift molded lines, the shape of described end allows the initial relative movement between first main body and second main body, described end is in contact with one another to stop relative movement, allows this valve operating link to handle this engine valve thus.
28. valve control apparatus according to claim 27, it is characterized in that, when valve control apparatus is in second configuration, contact under the situation of this cam contact surface at the second lift molded lines, the shape of described end stops the relative movement between first main body and second main body, allows this valve operating link to handle this engine valve thus.
29., it is characterized in that this valve operating link comprises rocking arm according to each described valve control apparatus in the claim 23 to 28, this valve control apparatus is encapsulated in first end of this rocking arm.
30. valve control apparatus according to claim 29, it is characterized in that, this valve operating link comprises push rod, this push rod comprises first end and second end, this cam action is on first end of this connecting rod, second end of this push rod acts on second main body, and second end of this rocking arm acts on the valve.
31., it is characterized in that first lifting parts limits motor interrupt mode molded lines according to each described valve control apparatus in the claim 23 to 31, be used to provide motor to interrupt valve and promote action.
32. valve control apparatus according to claim 27 is characterized in that, second lifting parts limits ordinary combustion pattern molded lines, is used to provide the burning valve to promote action.
33. according to claim 25 or 26 described valve control apparatus, it is characterized in that, on the contrary also comprise be used to make second main body from primary importance move to the second place or operating mechanism.
34. valve control apparatus according to claim 33 is characterized in that, this operating mechanism comprises that setting is used for the piston that is used on second main body.
35. valve control apparatus according to claim 34 is characterized in that, hydraulic fluid causes this piston to make second main body move to the second place from primary importance, and Returnning spring causes this piston to make second main body get back to primary importance from the second place.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910161581.6A CN101988399B (en) | 2009-08-04 | 2009-08-04 | Aerodynamic valve control device |
| EP10737594.1A EP2462321B1 (en) | 2009-08-04 | 2010-08-04 | Lost motion valve control apparatus |
| US13/389,176 US8573171B2 (en) | 2009-08-04 | 2010-08-04 | Lost motion valve control apparatus |
| PCT/EP2010/061358 WO2011015603A2 (en) | 2009-08-04 | 2010-08-04 | Lost motion valve control apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910161581.6A CN101988399B (en) | 2009-08-04 | 2009-08-04 | Aerodynamic valve control device |
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| Publication Number | Publication Date |
|---|---|
| CN101988399A true CN101988399A (en) | 2011-03-23 |
| CN101988399B CN101988399B (en) | 2014-08-20 |
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| CN200910161581.6A Active CN101988399B (en) | 2009-08-04 | 2009-08-04 | Aerodynamic valve control device |
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| CN106321181A (en) * | 2015-06-29 | 2017-01-11 | 上海高斯通船舶配件有限公司 | Hydraulic type valve lift adjusting and buffering device for internal combustion engine |
| CN106368754A (en) * | 2016-08-29 | 2017-02-01 | 潍柴动力股份有限公司 | Intake valve device, air distribution system and air distribution phase switching method |
| CN106545371A (en) * | 2017-01-23 | 2017-03-29 | 广西玉柴机器股份有限公司 | The exhaust cam of engine cam |
| CN108368752A (en) * | 2015-12-17 | 2018-08-03 | 康明斯公司 | The compression brake of internal combustion engine |
| CN111108280A (en) * | 2017-08-14 | 2020-05-05 | 伊顿智能动力有限公司 | Integrated engine brake configuration |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106321181A (en) * | 2015-06-29 | 2017-01-11 | 上海高斯通船舶配件有限公司 | Hydraulic type valve lift adjusting and buffering device for internal combustion engine |
| CN106321181B (en) * | 2015-06-29 | 2019-07-09 | 上海高斯通船舶配件有限公司 | Internal combustion engine fluid pressure type valve stroke adjusts buffer unit |
| CN108368752A (en) * | 2015-12-17 | 2018-08-03 | 康明斯公司 | The compression brake of internal combustion engine |
| CN108368752B (en) * | 2015-12-17 | 2021-01-01 | 康明斯公司 | Compression brake for internal combustion engine |
| CN106368754A (en) * | 2016-08-29 | 2017-02-01 | 潍柴动力股份有限公司 | Intake valve device, air distribution system and air distribution phase switching method |
| CN106368754B (en) * | 2016-08-29 | 2019-01-15 | 潍柴动力股份有限公司 | A kind of inlet valve means, air distribution system and port timing switching method |
| CN106545371A (en) * | 2017-01-23 | 2017-03-29 | 广西玉柴机器股份有限公司 | The exhaust cam of engine cam |
| CN111108280A (en) * | 2017-08-14 | 2020-05-05 | 伊顿智能动力有限公司 | Integrated engine brake configuration |
| CN111108280B (en) * | 2017-08-14 | 2023-01-17 | 伊顿智能动力有限公司 | Integrated engine brake configuration |
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| CN101988399B (en) | 2014-08-20 |
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