CN106640252A - Axial mobile multimode hydraulic variable valve drive system - Google Patents

Abstract

The axial mobile multimode hydraulic variable valve drive system belongs to the field of the engine valve actuation. The system comprises a camshaft,a camshaft bushing,an axial movement mechanism, a valve control mechanism, a plunger type feed oiler and aoil reservoir and so on. The camshaft bushing is provided with a first cam and a second cam at least. Through the use of the axial movement mechanism a two-stroke engine drive mode, a four stroke a drive mode, a two-stroke braking mode a four stroke and so on a plurality kinds of mode conversion between braking mode can be realized. Comprehensively improve engine power performance, fuel economy, emissions and braking safety purposes and the best ventilation of the engine under different conditions can be achieved through the further use with valve control mechanism. The invention is the submitted to practical application. The system has the advantages of high reliability, compacted bodies, reducing the requirement of the system of institutions. The components are adopted more mature technology, so the system has high practical application potential in the short term and good application prospect.

Description

A kind of axial displacement multi-mode hydraulic variable valve drive system

Technical field

The present invention relates to a kind of axial displacement multi-mode hydraulic variable valve drive system, belongs to engine valve actuations Field.

Background technology

It is increasingly serious with the energy and environmental problem, and people are to the driving of vehicle and being absorbed in for security, not Carrying out engine needs on the premise of discharge index is met, to consider dynamic property, economy, emission performance and security.This is just Need driving and braking in the range of full working scope, optimize engine performance.And changeable air valve, the stroke changeable for receiving much concern at present The technologies such as number, cylinder deactivation, auxiliary braking, new combustion mode, variable compression ratio, variable EGR are mostly only in engine small range fortune Its performance is improved in row conditioned area.The drive in fixed punch number of passes engine is only applied to such as existing changeable air valve technology Start building under condition, and be mostly used for the inlet valve of gasoline engine reducing pumping loss.Stroke changeable number technology is at home and abroad still located In conceptual phase, and it is served only for driving under operating mode.The existing vehicle with cylinder stopping technique can only provide cylinder deactivation function, therefore, Low to consumption improvement degree, 7% or so oil consumption can only be obtained mostly to be reduced.On the other hand, with engine recoverable amount Sharply increase, vehicle safety is increasingly subject to people's attention, EBA is classified as vehicle by increasing country One of indispensable annex.But at present there is brake component and work long hours easily overheated, braking effect in EBA mostly Rate is quickly reduced, retardation efficiency controllable degree is low, braking when the easy sideslip of vehicle, brakes take limited vehicle space etc. Problem.In current engine auxiliary braking technology, preferably, it is in import/exhaust to the braking effect of the auxiliary braking technology that reduces pressure On the basis of door ruuning situation is constant, realize subtracting to open exhaust valve or pressure-reducing valve compared with small guide vane near Pressure braking effect, engine realizes a braking cycle per 720 ° of crank angles, belongs to the braking of four strokes, and its braking effect cannot Meet requirement when vehicle heavy load is braked.

For the problem in above-mentioned engine research field, Internal Combustion Engine institute burning seminar of Dalian University of Technology is based on The thought of partition zone optimizing engine performance in the range of full working scope is driven-braked, a kind of multimode engine is proposed, and provides each The application operating mode of the pattern of kind and the requirement to the valve keying moment：Under the driving operating mode of the big load of low speed, using two-stroke Drive pattern, to reach the purpose for improving power output；Under other engine driving operating modes, using four stroke drive patterns, To reduce the purpose of fuel consumption and emission formation；Under heavy load damped condition, using two-stroke braking mode, with Reach the purpose for improving braking power output；Under little load brake operating mode, using four stroke braking modes, according to deceleration loading Requirement, change braking mode number of stroke come adjust braking output, with reach improve vehicle safety purpose.

At present, practical Variabale valve actuation system remains valve cam mostly, mostly using mechanical mechanism, It is broadly divided into：1) camshaft phase modulation formula, the VVT systems of such as TOYOTA, the Vanos systems of BMW；2) changeable air valve liter stage by stage The VTEC systems of formula, such as Honda；3) the Valvetronic systems of continuously variable valve lift formula, such as BMW, Hyundai CVVL systems etc., this kind of system realizes keying timing and the maximum of each cylinder valve of engine by controlling intermediate transmission mechanism The synchronous adjustment of stroke three.

For relatively having cam Variabale valve actuation system, more flexible valve event is capable of achieving without camming, while Mechanism is complicated, cost intensive, and needs more to be stretched at aspects such as reliability, durability and valve temperature compensation controls The research for entering.This kind of system mainly includes electromagnetic type and the class of electric-liquid type two.Electromagnetic type system is in motion precise control, valve stroke The aspects such as adjustable degree are remained to be further improved.For electromagnetic type system, electric-liquid type system can with relatively higher valve The features such as adjusting flexibility ratio, higher power density, flexible arrangement, is Variabale valve actuation system most potential at present.This is System mainly includes common rail oil feeding type and the big class of cam oil feeding type two.

Common rail oil feeding type system eliminates valve cam, by driving oil in the open/close states and accumulator that control magnetic valve Pressure, adjust valve keying timing and range.Ford companies, Lucas companies etc. carried out research to this, and future is still The research that need to be stretched at system cost, response speed, the aspect such as take up room.With engine cylinder number, single cylinder valve number And the increase of rotating speed, the system is also present：A) common rail pipe is bulky, difficulty in arrangement problem；B) made in system The quantity of high-speed large-flow magnetic valve is excessive, and the magnetic valve cost determined by current magnetic valve material and processing technology It is higher, therefore, the holistic cost of the system is higher.These problems cause traditional common rail oil feeding type system automobile-usedization and are more stranded Difficulty, this kind of system is widely used on the exhaust valve of low powered two stroke engine.

By comprehensive mechanical formula and the advantage of common rail oil feeding type system, cam oil feeding type system receives researcher and Sheng Produce the extensive concern of manufacturer, the Multiair systems of such as FIAT, the VCM systems of ABB.This kind of system adopts cam-plunger type Oil feeder takes up room little replacing accumulator, be capable of achieving valve keying timing it is separately adjustable, open and close timing and determine row Journey.This kind of system remains a need for being improved at following two aspects：A) quantity of oil feeder needed for system and magnetic valve is more, is System holistic cost is higher；B) valve operation adjustable extent is limited by fuel feeding and control device, it is impossible to realize that valve is opened and closed just When and stroke three between it is separately adjustable, do not realize engine two-stroke drive pattern and two-stroke braking mode requirement yet 360 °C of A/ circulations valve running etc..

Because existing practical Variabale valve actuation system is mostly used for the engine of four stroke drive patterns, it is impossible to full The requirement of sufficient multimode engine, therefore develop a set of reliability height and meet the variable valve actuation of multimode engine requirement System is imperative.The braking of engine two-stroke drive pattern, four stroke drive patterns, two-stroke braking mode and four strokes Under pattern, be present greatly difference in import/exhaust door open frequency, unlatching timing and unlatching duration, which greatly increases The development difficulty of the Variabale valve actuation system that multimode engine is required.Such as due to two-stroke drive pattern or two-stroke system Dynamic model formula requires that import/exhaust door runs once per 360 ° of crank angles, and four stroke drive patterns and four stroke braking modes are required Import/exhaust door runs once per 720 ° of crank angles, therefore, this requirement needs to realize two-stroke driving/braking pattern and four punchings The multi-mode Variabale valve actuation system switched between journey driving/braking pattern must have realizes both valve running frequencies Between flexible switching function.Even under the constant driving of number of stroke and braking mode, import/exhaust door is opened timing and is opened Opening the duration yet suffers from very big difference.If using an actuated by cams, by using mechanical continuous variable valve Come if realizing the little unlatching duration, valve maximum lift is accordingly reduced, charging efficiency and pumping loss etc. refer to controlling organization Mark is more difficult while meeting.If realizing the little unlatching duration by draining using hydraulic valve controlling organization, at a high speed Lower hydraulic valve controlling organization will appear as well the problem that system cannot be fully oil-filled, and this will cause the system to apply at a high speed On engine.When switching between various patterns, the phase adjusted of very wide-angle, vane type vvt mechanism common at present are needed Requirement cannot be met, and the electronic vvt mechanism cost intensive of requirement can be met, short-term cannot be popularized on a large scale, accordingly, it would be desirable to The requirement of the adjustable range to valve opening timing is reduced as far as possible, to realize without VVT or using conventional minor adjustment model The purpose of the VVT for enclosing.Even under same pattern, it is different that working conditions of different engines remains that valve-driving system is provided The unlatching timing of import/exhaust door, maximum lift and open the duration.At the same time, various parts should be adopted as far as possible More mature technology, to improve system possibility practical in a short time good application prospect is finally obtained.At present not yet There is a Variabale valve actuation system can be while meet requirements above, therefore the exploitation of multi-mode Variabale valve actuation system is compeled In the eyebrows and eyelashes.

The content of the invention

It is an object of the invention to：By designing a kind of axial displacement multi-mode hydraulic variable valve drive system, use In realization：A () realizes engine two-stroke drive pattern, four stroke drive patterns, two punchings by using axial moving mechanism Conversion between the various modes such as journey braking mode, four stroke braking modes come meet engine in different modes to ventilation Requirement；B () in each mode, different operating points under each pattern is further optimized by using valve control machanism Generator operating conditions, reach the aspects such as comprehensive raising engine power performance, fuel economy, emission performance and braking safety The purpose of energy；C () arranges in pairs or groups hydraulic pressure or various different valve adjustments mechanisms such as mechanical to meet practical application to changeable air valve The requirement of the aspects such as degree of flexibility, cost, system arrangement, each mechanism is short to improve system as far as possible using more mature technology Practical possibility in phase, finally to obtain good application prospect.

The technical solution adopted in the present invention is：This axial displacement multi-mode hydraulic variable valve drive system, it Including valve actuating mechanism, camshaft, cam shaft sleeve, axial moving mechanism, valve control machanism, plunger type oil feeder, work Plug driver and oil conservator.The cam shaft puts the first cam of setting and the second cam.First cam adopts single-tab Cam lobes or biconvex cam lobes, the second cam is using single-tab cam lobes or biconvex cam lobes, biconvex Playing cam lobes adopts molded line identical and 180 ° of camshaft degrees of phase two projections.Plunger type oil feeder has post Plug input and fuel supply chamber.Piston actuator has driving chamber and piston output end.Valve control machanism includes oil-feeding control End, drive control end and oil storage control end.The axial location of axial moving mechanism adjustment cam axle axle sleeve, determines direct or logical It is the first cam or the second cam to cross transmission mechanism and drive the cam of plunger input.Fuel supply chamber is connected with oil-feeding control end, Driving chamber is connected with drive control end, and oil conservator is connected with oil storage control end.Piston output end is driven directly or by transmission mechanism Take offence door drive mechanism.

Cam shaft puts the 3rd cam of increase, and the 3rd cam is using single-tab cam lobes or biconvex cam lobe Piece.The axial location of axial moving mechanism adjustment cam axle axle sleeve, decision directs or through transmission mechanism and drives plunger input The cam at end is the first cam, the second cam, or the 3rd cam.

It increases a valve actuating mechanism, i.e. the first valve actuating mechanism and duaspiracle drive mechanism.Increase valve Drive axle.Piston output end is first last respectively directly or by driver by valve actuation bridge again directly or by transmission mechanism Structure drives the first valve actuating mechanism and duaspiracle drive mechanism.

It increases a valve actuating mechanism, a valve control machanism and plunger type oil feeder, a piston type Driver and an oil conservator, i.e., using the first valve actuating mechanism, the first valve control machanism, the first plunger type oil feeder, First piston formula driver, the first oil conservator, duaspiracle drive mechanism, duaspiracle controlling organization, the second plunger type fuel feeding Device, second piston formula driver and the second oil conservator.Increase valve actuation bridge.First plunger type oil feeder has the first plunger defeated Enter end and the first fuel supply chamber.First piston formula driver has the first driving chamber and first piston output end.First valve is controlled Mechanism includes the first oil-feeding control end, the first drive control end and the first oil storage control end.Second plunger type oil feeder has the Two plunger inputs and the second fuel supply chamber.Second piston formula driver has the second driving chamber and second piston output end.Second Valve control machanism includes the second oil-feeding control end, the second drive control end and the second oil storage control end.Cam is first direct or logical Cross transmission mechanism and drive the first plunger input and second directly or by transmission mechanism respectively by the way that valve actuation bridge is last again Plunger input.First fuel supply chamber is connected with the first oil-feeding control end, and the first driving chamber is connected with the first drive control end, and first Oil conservator is connected with the first oil storage control end.First piston output end drives the first valve actuation machine directly or by transmission mechanism Structure.Second fuel supply chamber is connected with the second oil-feeding control end, and the second driving chamber is connected with the second drive control end, the second oil conservator with Second oil storage control end is connected.Second piston output end drives duaspiracle drive mechanism directly or by transmission mechanism.

For two cam switchings, the cam shaft puts and is provided with two switching slot.The axial moving mechanism is adopted With two electromagnetic actuators.Or the axial moving mechanism is using two hydraulic actuating mechanisms and two hydraulic control machines Structure.

For three cam switchings, the cam shaft puts and is provided with two switching slot.The axial moving mechanism is adopted With three electromagnetic actuators.Or the axial moving mechanism is using three hydraulic actuating mechanisms and three hydraulic control machines Structure.

Valve control machanism has a two-way valve.Two-way valve has two-way valve first end and the end of two-way valve second.Fuel feeding Control end and drive control end are connected with two-way valve first end.Oil storage control end is connected with the end of two-way valve second.

Valve control machanism also has a check valve.Check valve has check valve oil inlet end and check valve oil outlet end.It is single It is connected with oil-feeding control end to valve oil inlet end.Check valve oil outlet end is connected with oil storage control end.

Valve control machanism has a two-way valve and two check valves, i.e. the first check valve and the second check valve.Two lead to Valve has two-way valve first end and the end of two-way valve second.There is first check valve the first check valve oil inlet end and the first check valve to go out Oily end.Second check valve has the second check valve oil inlet end and the second check valve oil outlet end.First check valve oil outlet end and second Check valve oil inlet end is connected with oil-feeding control end, the second check valve oil outlet end and two-way valve first end with drive control end phase Even, the first check valve oil inlet end and the end of two-way valve second are connected with oil storage control end.

Valve control machanism has a triple valve and a check valve.Triple valve has triple valve first end, triple valve Second end and the end of triple valve the 3rd.Check valve has check valve oil inlet end and check valve oil outlet end.Triple valve first end and unidirectional Valve oil outlet end is connected with oil-feeding control end, and the end of triple valve second is connected with drive control end, the end of triple valve the 3rd and check valve Oil inlet end is connected.

Valve control machanism also has a two-way valve.Two-way valve has two-way valve first end and the end of two-way valve second.Two Port valve first end is connected with drive control end, and the end of two-way valve second is connected with oil storage control end.

The transmission mechanism is slide block, push rod, rocking arm, swing arm, four-bar mechanism, or Hydraulic Main is from piston type mechanism.

The invention has the beneficial effects as follows：A () this axial displacement multi-mode hydraulic variable valve drive system is mainly wrapped Camshaft, cam shaft sleeve, axial moving mechanism, valve adjustments mechanism, valve control machanism etc. are included, cam shaft sleeve is at least wrapped The first cam and the second cam are included, by using axial moving mechanism, engine two-stroke drive pattern, four strokes is realized and is driven Conversion between the various modes such as dynamic model formula, two-stroke braking mode, four stroke braking modes, so as to meet engine not With the requirement under pattern to taking a breath；B () in each mode, by using valve control machanism, is realized under each pattern Different operating points generator operating conditions further optimization, engine power performance, fuel-economy are finally improve comprehensively Property, emission performance and braking safety；(c) present invention according to actual type, provide the user mechanical valve governor motion or Fluid pressure type valve adjustments mechanism, the former has preferable changeable air valve degree of flexibility and good reliability, and the latter has higher Changeable air valve degree of flexibility, suitable scheme is selected so as to allow user according to the actual conditions of oneself, in high performance-price ratio On the basis of, meet the requirement to import/exhaust door ruuning situation under the various operating conditions of engine；D () present invention is by closing Reason design, reliability is high, mechanism is compact, reduces the requirement to various parts, and each mechanism is improved using more mature technology System possibility practical in a short time, is finally obtained good application prospect.

Description of the drawings

Below in conjunction with the accompanying drawings the present invention is further described with embodiment.

Fig. 1 is the axial displacement of the dull section of the operation of the biconvex wheel drive list valve with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.

Fig. 2 is the axial displacement of the dull section of the operation of the biconvex wheel drive dual valve with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.

Fig. 3 is the double axial displacements for adjusting of the operation of the biconvex wheel drive dual valve with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.

Fig. 4 is the axial displacement of the dull section of the operation of the three actuated by cams list valves with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.

Fig. 5 is the axial movement of the dull section of biconvex wheel drive list valve operation of the double groups of cams with single camshaft axle sleeve The schematic diagram of formula multi-mode hydraulic variable valve drive system.

Fig. 6 is the axial direction of the dull section of the operation of the electromagnetic type biconvex wheel drive list valve with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.

Fig. 7 is the axial direction of the dull section of the operation of the actuated by cams list valve of electromagnetic type three with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.

Fig. 8 is the axial direction of the dull section of the operation of the fluid pressure type biconvex wheel drive list valve with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.

Fig. 9 is the axle of the dull section of fluid pressure type biconvex wheel drive list valve operation with two cam shaft sleeve single group cams To the schematic diagram of portable multi-mode hydraulic variable valve drive system.

Figure 10 is inlet valve cam schematic diagram under four stroke drive patterns.

Figure 11 is exhaust valve cam schematic diagram under four stroke drive patterns.

Figure 12 is inlet valve cam schematic diagram under four stroke braking modes.

Figure 13 is exhaust valve cam schematic diagram under four stroke braking modes.

Figure 14 is inlet valve cam schematic diagram under two-stroke drive pattern.

Figure 15 is exhaust valve cam schematic diagram under two-stroke drive pattern.

Figure 16 is inlet valve cam schematic diagram under two-stroke braking mode.

Figure 17 is exhaust valve cam schematic diagram under two-stroke braking mode.

Figure 18 is the schematic diagram of the valve control machanism using a two-way valve.

Figure 19 is the schematic diagram of the valve control machanism using a two-way valve and a check valve.

Figure 20 is the schematic diagram of the valve control machanism using a two-way valve and two check valves.

Figure 21 is the schematic diagram of the valve control machanism using a triple valve and a check valve.

Figure 22 is the schematic diagram of the valve control machanism using one triple valve of a two-way valve and a check valve.

In figure：1st, cylinder cap；2nd, valve actuating mechanism；201st, the first valve actuating mechanism；202nd, duaspiracle drive mechanism； 2A, left side valve actuating mechanism；2B, right side valve actuating mechanism；2-1, a valve actuating mechanism；2-2, No. two valve actuations Mechanism；3rd, camshaft；3-1, a camshaft；3-2, No. two camshafts；4th, cam shaft sleeve；401st, the first cam；402nd, Two cams；401A, the cam of left side first；402A, the cam of left side second；401B, the cam of right side first；402B, right side second are convex The 403, the 3rd cam of wheel；404th, the first switching slot；405th, the second switching slot；4-1, a cam shaft sleeve；401-1, No. one One cam；402-1, second cam；404-1, first switching slot；405-1, second switching slot；4-2, No. two Cam shaft sleeve；401-2, No. two first cams；402-2, No. two second cams；404-2, No. two first switching slot；405-2、 No. two second switching slot；5th, axial moving mechanism；501st, the first electromagnetic actuator；501b, the switching of the first electromagnetic actuator Pin；502nd, the second electromagnetic actuator；502b, the second electromagnetic actuator switching pin；503rd, the 3rd electromagnetic actuator； 503b, the 3rd electromagnetic actuator switching pin；511st, the first hydraulic actuating mechanism；511a, the first hydraulic actuating mechanism drive mouth； 511b, the first hydraulic actuating mechanism switching pin；511k, the first hydraulic actuating mechanism back-moving spring；512nd, the second hydraulic pressure performs machine Structure；512a, the second hydraulic actuating mechanism drive mouth；512b, the second hydraulic actuating mechanism switching pin；512k, the second hydraulic pressure are performed Reset spring；521st, the first hydraulic control；521a, the first hydraulic control drive mouth；521p, the first hydraulic pressure control Mechanism's high-pressure mouth processed；521t, the first hydraulic control low pressure port；522nd, the second hydraulic control；522a, the second hydraulic pressure control Mechanism processed drives mouth；522p, the second hydraulic control high-pressure mouth；522t, the second hydraulic control low pressure port；53rd, low pressure Source；54th, high-voltage power supply；511-1, first hydraulic actuating mechanism；511a-1, first hydraulic actuating mechanism drive mouth； 511b-1, a first hydraulic actuating mechanism switching pin；511k-1, a first hydraulic actuating mechanism back-moving spring；512-1、 Number second hydraulic actuating mechanism；512a-1, second hydraulic actuating mechanism drive mouth；512b-1, second hydraulic pressure are held Row mechanism switching pin；512k-1, a second hydraulic actuating mechanism back-moving spring；511-2, No. two first hydraulic actuating mechanisms； 511a-2, No. two first hydraulic actuating mechanisms drive mouth；511b-2, No. two first hydraulic actuating mechanism switching pins；511k-2, two Number the first hydraulic actuating mechanism back-moving spring；512-2, No. two second hydraulic actuating mechanisms；512a-2, No. two second hydraulic pressure are performed Mechanism drives mouth；512b-2, No. two second hydraulic actuating mechanism switching pins；512k-2, No. two second hydraulic actuating mechanisms reset Spring；55th, the first common rail chamber；56th, the second common rail chamber；6th, valve control machanism；6a, oil-feeding control end；6b, drive control end； 6c, oil storage control end；601st, the first valve control machanism；601a, the first oil-feeding control end；601b, the first drive control end； 601c, the first oil storage control end；602nd, duaspiracle controlling organization；602a, the second oil-feeding control end；602b, second drive control End processed；602c, the second oil storage control end；6-1, a valve control machanism；6-1a, an oil-feeding control end；6-1b, a drive Dynamic control end；6-1c, an oil storage control end；6-2, No. two valve control machanisms；6-2a, No. two oil-feeding control ends；6-2b, two Number drive control end；6-2c, No. two oil storage control ends；6A, left side valve control machanism；6Aa, left side oil-feeding control end；6Ab、 Left side drive control end；6Ac, left side oil storage control end；6B, right side valve control machanism；6Ba, right side oil-feeding control end；6Bb、 Right side drive control end；6Bc, right side oil storage control end；62V, two-way valve；62Va, two-way valve first end；62Vb, two-way valve Two ends；6CV, check valve；6CVa, check valve oil inlet end；6CVb, check valve oil outlet end；6CV1, the first check valve；6CV1a, One check valve oil inlet end；6CV1b, the first check valve oil outlet end；6CV2, the second check valve；6CV2a, the second check valve oil inlet end； 6CV2b, the second check valve oil outlet end；63V, triple valve；63Va, triple valve first end；63Vb, the end of triple valve second；63Vc, three The end of port valve the 3rd；7G, plunger type oil feeder；7Ga, plunger input；7Gb, fuel supply chamber；7Q, piston actuator；7Qa, driving Chamber；7Qb, piston output end；7T, oil conservator；701G, the first plunger type oil feeder；701Ga, the first plunger input；701Gb、 First fuel supply chamber；701Q, first piston formula driver；701Qa, the first driving chamber；701Qb, first piston output end；701T、 First oil conservator；702G, the second plunger type oil feeder；702Ga, the second plunger input；702Gb, the second fuel supply chamber；702Q、 Second piston formula driver；702Qa, the second driving chamber；702Qb, second piston output end；702T, the second oil conservator；7AG, a left side Lateral column plug oil feeder；7AGa, left side plunger input；7AGb, left side fuel supply chamber；7AQ, left hand piston formula driver；7AQa、 Left side driving chamber；7AQb, left hand piston output end；7AT, left side oil conservator；7BG, right side plunger type oil feeder；7BGa, right side Plunger input；7BGb, right side fuel supply chamber；7BQ, right hand piston formula driver；7BQa, right side driving chamber；7BQb, right hand piston Output end；7BT, right side oil conservator；7G-1, a plunger type oil feeder；7Ga-1, a plunger input；7Gb-1, a confession Oil pocket；7Q-1, a piston actuator；7Qa-1, a driving chamber；7Qb-1, a piston output end；7T-1, a storage Oily device；7G-2, No. two plunger type oil feeders；7Ga-2, No. two plunger inputs；7Gb-2, No. two fuel supply chambers；7Q-2, No. two work Plug driver；7Qa-2, No. two driving chambers；7Qb-2, No. two piston output ends；7T-2, No. two oil conservators；8th, valve actuation Bridge.

Specific embodiment

The present invention relates to a kind of axial displacement multi-mode hydraulic variable valve drive system.It includes valve actuating mechanism 2nd, camshaft 3, cam shaft sleeve 4, axial moving mechanism 5, valve control machanism 6, plunger type oil feeder 7G, piston actuator 7Q and oil conservator 7T.Fig. 1 is the axial direction of the dull section of the operation of the biconvex wheel drive list valve with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.It is convex that first cam 401 and second is set in cam shaft sleeve 4 Wheel 402.First cam 401 is using single-tab cam lobes or biconvex cam lobes, and the second cam 402 is convex using single-tab Impeller blade or biconvex cam lobes, biconvex cam lobes adopt molded line identical and 180 ° of camshaft degrees of phase Two projections.Plunger type oil feeder 7G has plunger input 7Ga and fuel supply chamber 7Gb.Piston actuator 7Q has driving Chamber 7Qa and piston output end 7Qb.Valve control machanism 6 includes oil-feeding control end 6a, drive control end 6b and oil storage control end 6c.The axial location of the adjustment cam axle axle sleeve 4 of axial moving mechanism 5, decision directs or through transmission mechanism and drives plunger defeated The cam for entering to hold 7Ga is the first cam 401 or the second cam 402.Fuel supply chamber 7Gb is connected with oil-feeding control end 6a, driving chamber 7Qa is connected with drive control end 6b, and oil conservator 7T is connected with oil storage control end 6c.Piston output end 7Qb is directly or by transmission Mechanism drives valve actuating mechanism 2.The transmission mechanism be slide block, push rod, rocking arm, swing arm, four-bar mechanism, or Hydraulic Main from Piston type mechanism.

Fig. 2 is the axial displacement of the dull section of the operation of the biconvex wheel drive dual valve with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.It increases a valve actuating mechanism 2, i.e. the first valve actuating mechanism 201 and duaspiracle drive mechanism 202.Increase valve actuation bridge 8.Piston output end 7Qb first directly or by transmission mechanism again The first valve actuating mechanism 201 and duaspiracle is driven to drive directly or by transmission mechanism respectively by the way that valve actuation bridge 8 is last Motivation structure 202.Realize the synchronous adjustment of the first valve actuating mechanism 201 and duaspiracle drive mechanism 202.

Fig. 3 is the double axial displacements for adjusting of the operation of the biconvex wheel drive dual valve with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.It increases by 2, valve control machanism 6 of a valve actuating mechanism With a plunger type oil feeder 7G, a piston actuator 7Q and an oil conservator 7T, i.e., using the first valve actuating mechanism 201st, the first valve control machanism 601, the first plunger type oil feeder 701G, first piston formula driver 701Q, the first oil conservator 701T, duaspiracle drive mechanism 202, duaspiracle controlling organization 602, the second plunger type oil feeder 702G, second piston formula Driver 702Q and the second oil conservator 702T.Increase valve actuation bridge 8.First plunger type oil feeder 701G has the first plunger defeated Enter to hold 701Ga and the first fuel supply chamber 701Gb.First piston formula driver 701Q has the first driving chamber 701Qa and first piston Output end 701Qb.First valve control machanism 601 includes the first oil-feeding control end 601a, the first drive control end 601b and the One oil storage control end 601c.Second plunger type oil feeder 702G has the second plunger input 702Ga and the second fuel supply chamber 702Gb.Second piston formula driver 702Q has the second driving chamber 702Qa and second piston output end 702Qb.Duaspiracle control Mechanism processed 602 includes the second oil-feeding control end 602a, the second drive control end 602b and the second oil storage control end 602c.Cam elder generation The input of the first plunger is driven directly or by transmission mechanism directly or by transmission mechanism respectively by the way that valve actuation bridge 8 is last again End 701Ga and the second plunger input 702Ga.First fuel supply chamber 701Gb is connected with the first oil-feeding control end 601a, and first drives Chamber 701Qa is connected with the first drive control end 601b, and the first oil conservator 701T is connected with the first oil storage control end 601c.First lives Plug output end 701Qb drives the first valve actuating mechanism 201 directly or by transmission mechanism.Second fuel supply chamber 702Gb and second Oil-feeding control end 602a is connected, and the second driving chamber 702Qa is connected with the second drive control end 602b, the second oil conservator 702T and the Two oil storage control ends 602c are connected.Second piston output end 702Qb drives duaspiracle driving machine directly or by transmission mechanism Structure 202.Realize the separately adjustable of the first valve actuating mechanism 201 and duaspiracle drive mechanism 202.

Fig. 4 is the axial displacement of the dull section of the operation of the three actuated by cams list valves with single camshaft axle sleeve single group cam The schematic diagram of multi-mode hydraulic variable valve drive system.Increase by the 3rd cam 403 in cam shaft sleeve 4, the 3rd cam 403 is adopted With single-tab cam lobes or biconvex cam lobes.The axial location of the adjustment cam axle axle sleeve 4 of axial moving mechanism 5, certainly Surely it is the first cam 401, the second cam 402, Huo Zhe to direct or through transmission mechanism and drive the cam of plunger input 7Ga Three cams 403.The situation for increasing more cams is similar, is not repeated.

Fig. 5 is the axial movement of the dull section of biconvex wheel drive list valve operation of the double groups of cams with single camshaft axle sleeve The schematic diagram of formula multi-mode hydraulic variable valve drive system.Cam shaft puts and is provided with two groups of cams, i.e., left side first is convex Wheel 401A, left side the second cam 402A, right side the first cam 401B and right side the second cam 402B.It increases a valve actuation 2, valve control machanism 6 of mechanism and plunger type oil feeder 7G, a piston actuator 7Q and an oil conservator 7T, Driven using left side valve actuating mechanism 2A, left side valve control machanism 6A, left side plunger type oil feeder 7AG, left hand piston formula Dynamic device 7AQ, left side oil conservator 7AT, right side valve actuating mechanism 2B, right side valve control machanism 6B, right side plunger type oil feeder 7BG, right hand piston formula driver 7BQ and right side oil conservator 7BT.Left side plunger type oil feeder 7AG has left side plunger input 7AGa and left side fuel supply chamber 7AGb.Left hand piston formula driver 7AQ has left side driving chamber 7AQa and left hand piston output end 7AQb.Left side valve control machanism 6A includes that left side oil-feeding control end 6Aa, left side drive control end 6Ab and left side oil storage are controlled End 6Ac.Right side plunger type oil feeder 7BG has right side plunger input 7BGa and right side fuel supply chamber 7BGb.Right hand piston formula is driven Dynamic device 7BQ has right side driving chamber 7BQa and right hand piston output end 7BQb.Right side valve control machanism 6B includes right side fuel feeding Control end 6Ba, right side drive control end 6Bb and right side oil storage control end 6Bc.Axial moving mechanism 5 determines cam shaft sleeve 4 Axial location, and then determine that it is left side first currently to drive the cam of left side plunger input 7AGa directly or by transmission mechanism The second cam 402A of cam 401A or left side, and determine currently to drive right side plunger input directly or by transmission mechanism The cam of 7BGa is right side the first cam 401B or right side the second cam 402B.Left side fuel supply chamber 7AGb and left side oil-feeding control End 6Aa is connected, and left side driving chamber 7AQa is connected with left side drive control end 6Ab, left side oil conservator 7AT and left side oil storage control end 6Ac is connected.Left hand piston output end 7AQb drives left side valve actuating mechanism 2A directly or by transmission mechanism.Right side fuel supply chamber 7BGb is connected with right side oil-feeding control end 6Ba, and right side driving chamber 7BQa is connected with right side drive control end 6Bb, right side oil conservator 7BT is connected with right side oil storage control end 6Bc.Right hand piston output end 7BQb drives right side valve to drive directly or by transmission mechanism Motivation structure 2B.

Fig. 6 is the axial direction of the dull section of the operation of the electromagnetic type biconvex wheel drive list valve with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.The first cam 401, second is provided with cam shaft sleeve 4 Cam 402, the first switching slot 404, the second switching slot 405, the first electromagnetic actuator 501 and the second electromagnetic actuator 502. First electromagnetic actuator 501 has the first electromagnetic actuator switching pin 501b.Second electromagnetic actuator 502 has second Electromagnetic actuator switching pin 502b.It is current to drive valve governor motion input 7a's to be the first cam 401, when the first electromagnetism Executing agency 501 is energized, when the second electromagnetic actuator 502 is not energized, under the first electromagnetic actuator switching pin 501b Go and stretch into the first switching slot 404, promote cam shaft sleeve 4 to be moved to the left, driving valve governor motion input 7a's is convex Wheel switches to the second cam 402 by the first cam 401.It is current to drive valve governor motion input 7a's to be the second cam 402, When the first electromagnetic actuator 501 is not energized, and the second electromagnetic actuator 502 is energized, the second electromagnetic actuator is cut Change pin 502b descending and stretch into the second switching slot 405, promote cam shaft sleeve 4 to move right.Drive valve governor motion defeated Enter to hold the cam of 7a to switch to the first cam 401 by the second cam 402.When the first electromagnetic actuator 501 and the second electromagnetism are held When row mechanism 502 is not energized, cam shaft sleeve 4 is not moved axially.First switching slot 404 and the second switching slot 405 It is kept completely separate.The right side changeover portion of first switching slot 404 and the left side changeover portion of the second switching slot 405 can also coincide.

Fig. 7 is the axial direction of the dull section of the operation of the actuated by cams list valve of electromagnetic type three with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.Increase by the 3rd cam 403 in cam shaft sleeve 4.Increase by the Three electromagnetic actuators 503.3rd electromagnetic actuator 503 has the 3rd electromagnetic actuator switching pin 503b.First switching The right side changeover portion of groove 404 and the left side changeover portion of the second switching slot 405 coincide.It is current to drive valve actuation governor motion input 7a's is the second cam 402, and when the first electromagnetic actuator 501 is energized, the second electromagnetic actuator 502 and the 3rd electromagnetism are held When row mechanism 503 is not energized, the first electromagnetic actuator drive pin 501b is descending and stretches into the first switching slot 404, Promote cam shaft sleeve 4 to be moved to the left, drive valve governor motion input 7a to switch to the 3rd cam by the second cam 402 403.It is current to drive valve governor motion input 7a to be the 3rd cam 403, when the first electromagnetic actuator 501 and the 3rd electromagnetism Executing agency 503 is not energized, when the second electromagnetic actuator 502 is energized, the second electromagnetic actuator drive pin 502b It is descending and stretch into the second switching slot 405, promote cam shaft sleeve 4 to move right, drive valve governor motion input 7a Second cam 402 is switched to by the 3rd cam 403.It is current to drive valve governor motion input 7a to be the second cam (402), when 3rd electromagnetic actuator 503 is energized, and the first electromagnetic actuator 501 and the second electromagnetic actuator 502 are not energized When, the 3rd electromagnetic actuator drive pin 503b is descending and stretches into the second switching slot 405, promotes cam shaft sleeve 4 to the right It is mobile, drive valve governor motion input 7a to switch to the first cam 401 by the second cam 402.It is current to drive valve adjustments Mechanism input 7a is the first cam 401, when the first electromagnetic actuator 501 and the 3rd electromagnetic actuator 503 are not swashed Encourage, when the second electromagnetic actuator 502 is energized, the second electromagnetic actuator drive pin 502b is descending and stretches into the first switching In groove 404, promote cam shaft sleeve 4 to be moved to the left, drive valve governor motion input 7a to be switched to by the first cam (401) Second cam 402.First electromagnetic actuator 501, the second electromagnetic actuator 502 and the 3rd electromagnetic actuator 503 are not When energized, cam shaft sleeve 4 is not moved axially.

Fig. 8 is the axial direction of the dull section of the operation of the fluid pressure type biconvex wheel drive list valve with single camshaft axle sleeve single group cam The schematic diagram of portable multi-mode hydraulic variable valve drive system.Fluid pressure type axial moving mechanism includes that two sets of hydraulic pressure perform machine Structure, two sets of hydraulic controls, high-voltage power supply 54 and low pressure sources 53.Hydraulic actuating mechanism adopts reciprocating-piston mechanism, including the One hydraulic actuating mechanism 511 and the second hydraulic actuating mechanism 512.First hydraulic actuating mechanism 511 includes that the first hydraulic pressure performs machine Structure drives mouth 511a, the first hydraulic actuating mechanism drive pin 511b and the first hydraulic actuating mechanism back-moving spring 511k.Second liquid Pressure actuator 512 includes that the second hydraulic actuating mechanism drives mouth 512a, the second hydraulic actuating mechanism drive pin 512b and second Hydraulic actuating mechanism back-moving spring 512k.Hydraulic control includes the first hydraulic control 521 and the second hydraulic control machine Structure 522.First hydraulic control 521 includes the first hydraulic control high-pressure mouth 521p, the first hydraulic control low pressure Mouth 521t and the first hydraulic control drive mouth 521a.Second hydraulic control 522 includes that the second hydraulic control is high Pressure mouth 522p, the second hydraulic control low pressure port 522t and the second hydraulic control drive mouth 522a.First hydraulic pressure is performed Mechanism drives mouth 511a to drive mouth 521a to be connected with the first hydraulic control.Second hydraulic actuating mechanism drives mouth 512a and the Two hydraulic controls drive mouth 522a to be connected.First hydraulic control high-pressure mouth 521p and the second hydraulic control high pressure Mouth 522p is connected with high-voltage power supply 54.First hydraulic control low pressure port 521t and the second hydraulic control low pressure port 522t It is connected with low pressure source 53.When first hydraulic control 521 is not energized, the first hydraulic control high-pressure mouth 521p is blocked Plug, the first hydraulic control low pressure port 521t drives mouth 521a to be connected with the first hydraulic control.First hydraulic control machine When structure 521 is energized, the first hydraulic control low pressure port 521t is blocked, the first hydraulic control high-pressure mouth 521p and the One hydraulic control drives mouth 521a to be connected.When second hydraulic control 522 is not energized, the second hydraulic control is high Pressure mouth 512p is blocked, and the second hydraulic control low pressure port 522t drives mouth 522a to be connected with the second hydraulic control.The When two hydraulic controls 522 are energized, the second hydraulic control low pressure port 522t is blocked, and the second hydraulic control is high Pressure mouth 512p drives mouth 522a to be connected with the second hydraulic control.It is current to drive valve governor motion input 7a's to be first Cam 401, and the first hydraulic control 521 is energized, when the second hydraulic control 522 is not energized, the first hydraulic pressure Executing agency drive pin 511b is descending and stretches into the first switching slot 404, promotes cam shaft sleeve 4 to be moved to the left, drive gas Door governor motion input 7a switches to the second cam 402 by the first cam 401.It is current to drive valve governor motion input 7a Be the second cam 402, the first hydraulic control 521 is not energized, when the second hydraulic control 522 is energized, second Hydraulic actuating mechanism drive pin 512b is descending and stretches into the second switching slot 405, promotes cam shaft sleeve 4 to move right, and drives A governor motion input 7a that takes offence switches to the first cam 401 by the second cam 402.First hydraulic control 521 and When two hydraulic controls 522 are not energized, cam shaft sleeve 4 is not moved axially.Fluid pressure type axial moving mechanism enters When the cam of row three switches, need to increase a hydraulic actuating mechanism and hydraulic control.It is not repeated herein.

Fig. 9 is the axle of the dull section of fluid pressure type biconvex wheel drive list valve operation with two cam shaft sleeve single group cams To the schematic diagram of portable multi-mode hydraulic variable valve drive system.Fluid pressure type axial moving mechanism includes that four sets of hydraulic pressure are performed Mechanism, two sets of hydraulic controls, high-voltage power supply 54 and low pressure sources 53.Hydraulic actuating mechanism includes first hydraulic actuating mechanism 511-1 and the second hydraulic actuating mechanism 512-1, No. two first hydraulic actuating mechanism 511-2 and No. two second hydraulic pressure are performed Mechanism 512-2.Number first hydraulic actuating mechanism 511-1 include first hydraulic actuating mechanism drive mouth 511a-1, No. one A first hydraulic actuating mechanism drive pin 511b-1 and first hydraulic actuating mechanism back-moving spring 511k-1.Number second hydraulic pressure Executing agency 512-1 includes that second hydraulic actuating mechanism drives mouth 512a-1, a second hydraulic actuating mechanism drive pin 512b-1 and second hydraulic actuating mechanism back-moving spring 512k-1.No. two first hydraulic actuating mechanism 511-2 include No. two First hydraulic actuating mechanism drives mouth 511a-2, No. two first hydraulic actuating mechanism drive pin 511b-2 and No. two first hydraulic pressure to hold Row reset spring 511k-2.No. two second hydraulic actuating mechanism 512-2 include that No. two second hydraulic actuating mechanisms drive mouth 512a-2, No. two second hydraulic actuating mechanism drive pin 512b-2 and No. two second hydraulic actuating mechanism back-moving spring 512k-2. Hydraulic control includes the first hydraulic control 521 and the second hydraulic control 522.Wherein, the first hydraulic control machine Structure 521 includes the first hydraulic control high-pressure mouth 521p, the first hydraulic control low pressure port 521t and the first hydraulic control Mechanism drives mouth 521a.Second hydraulic control 522 includes the second hydraulic control high-pressure mouth 522p, the second hydraulic control Mechanism low pressure port 522t and the second hydraulic control drive mouth 522a.Number first hydraulic actuating mechanism drive mouth 511a-1 and No. two first hydraulic actuating mechanisms drive mouth 511a-2 to direct or through the first common rail chamber 55 and the first hydraulic control Mouth 521a is driven to be connected.Number second hydraulic actuating mechanism drives mouth 512a-1 and No. two second hydraulic actuating mechanisms to drive mouth 512a-2 directs or through the second common rail chamber 56 and drives mouth 522a to be connected with the second hydraulic control.First hydraulic control Mechanism high-pressure mouth 521p and the second hydraulic control high-pressure mouth 522p are connected with high-voltage power supply 54.First hydraulic control is low Pressure mouth 521t and the second hydraulic control low pressure port 522t is connected with low pressure source 53.First hydraulic control 521 not by During excitation, the first hydraulic control high-pressure mouth 521p is blocked, the first hydraulic control low pressure port 521t and the first hydraulic pressure Controlling organization drives mouth 521a to be connected.When first hydraulic control 521 is energized, the first hydraulic control low pressure port 521t It is blocked, the first hydraulic control high-pressure mouth 521p drives mouth 521a to be connected with the first hydraulic control.Second hydraulic pressure control When mechanism processed 522 is not energized, the second hydraulic control high-pressure mouth 512p is blocked, the second hydraulic control low pressure port 522t drives mouth 522a to be connected with the second hydraulic control.When second hydraulic control 522 is energized, the second hydraulic control Mechanism low pressure port 522t is blocked, and the second hydraulic control high-pressure mouth 512p drives mouth 522a phases with the second hydraulic control Even.That current number valve adjustments mechanism input 7a-1 of driving is a first cam 401-1, drives No. two valve adjustments machines That structure input 7a-2 is No. two first cam 401-2, and the first hydraulic control 521 is energized, the second hydraulic control When mechanism 522 is not energized, a first hydraulic actuating mechanism drive pin 511b-1 is descending and stretches into first switching slot In 404-1, promote cam shaft sleeve 4-1 be moved to the left, drive a valve adjustments mechanism input 7a-1 cam by A number first cam 401-1 is switched to a second cam 402-1；Meanwhile, No. two first hydraulic actuating mechanism drive pin 511b- 2 is descending and stretch into No. two first switching slot 404-2, promotes No. two cam shaft sleeves 4-2 to be moved to the left, and drives No. two valves The cam of governor motion input 7a-2 is switched to No. two second cam 402-2 by No. two first cam 401-2.It is current to drive one That number valve adjustments mechanism input 7a-1 is a second cam 402-1, drives No. two valve adjustments mechanism input 7a-2 Be No. two second cam 402-2, and the first hydraulic control 521 is not energized, and the second hydraulic control 522 is swashed When encouraging, a second hydraulic actuating mechanism drive pin 512b-1 is descending and stretches into second switching slot 405-1, promotes one Number cam shaft sleeve 4-1 moves right, and drives the cam of a valve adjustments mechanism input 7a-1 by second cam 402-1 is switched to a first cam 401-1；Meanwhile, No. two second hydraulic actuating mechanism drive pin 512b-2 are descending and stretch Enter in No. two second switching slot 405-2, promote No. two cam shaft sleeves 4-2 to move right, drive No. two valve adjustments mechanisms defeated Enter to hold the cam of 7a-2 to be switched to No. two first cam 401-2 by No. two second cam 402-2.

For the system with multiple cam shaft sleeves 4, fluid pressure type axial moving mechanism needs a set of first hydraulic pressure Controlling organization 521 and a set of second hydraulic control 522, and need first hydraulic pressure equal with cam shaft sleeve quantity to hold Row mechanism 511, the driving mouth of these the first hydraulic actuating mechanisms 511 directs or through the first common rail chamber 55 and the first hydraulic pressure Controlling organization drives mouth 521a to be connected；Second hydraulic actuating mechanism 512 equal with cam shaft sleeve quantity is needed, these second The driving mouth of hydraulic actuating mechanism 512 directs or through the second common rail chamber 56 and the second hydraulic control drives mouth 522a It is connected.First hydraulic control 521 controls all of first hydraulic actuating mechanism 511 and runs simultaneously, and realizes all of cam The synchronization of axle axle sleeve 4 is moved to the left；Second hydraulic control 522 controls the synchronous fortune of all of second hydraulic actuating mechanism 512 OK, the synchronization for realizing all of cam shaft sleeve 4 moves right, and finally realizes the first cam in all of cam shaft sleeve 4 401 and second switching between cam 402.

For for the Variabale valve actuation system of multimode engine, based on the actual application requirements engine has Which pattern is selecting the type of cam lobes.Figure 10 is inlet valve cam schematic diagram under four stroke drive patterns.Figure 11 is four Exhaust valve cam schematic diagram under stroke drive pattern.Figure 12 is inlet valve cam schematic diagram under four stroke braking modes.Figure 13 is Exhaust valve cam schematic diagram under four stroke braking modes.Figure 14 is inlet valve cam schematic diagram under two-stroke drive pattern.Figure 15 It is exhaust valve cam schematic diagram under two-stroke drive pattern.Figure 16 is inlet valve cam schematic diagram under two-stroke braking mode.Figure 17 is exhaust valve cam schematic diagram under two-stroke braking mode.Such as can be adopted with meeting the vehicle based on low-speed big power output With four stroke drive patterns and two-stroke drive pattern, then, the cam of air inlet side selects Figure 10 and Figure 14, the cam of exhaust side Select Figure 11 and Figure 15.Such as four stroke drive patterns can be adopted to meet the vehicle based on the auxiliary braking security of heavy-duty vehicle With two-stroke braking mode, then, the cam of air inlet side selects the cam of Figure 10 and Figure 16, exhaust side to select Figure 11 and Figure 17. Such as with meet heavy-duty vehicle auxiliary braking security vehicle can also using four stroke drive patterns, four stroke braking modes and Two-stroke braking mode, then, the cam of air inlet side may be selected three cams, i.e. Figure 10, Figure 12 and Figure 16, the cam of exhaust side Three cams, i.e. Figure 11, Figure 13 and Figure 17 may be selected.Such as with while needing to meet low-speed big power output and meeting heavily loaded The vehicle of the auxiliary braking security of vehicle adopts four stroke drive patterns, two-stroke drive pattern and two-stroke braking mode, So, the cam of air inlet side may be selected three cams, i.e. Figure 10, Figure 14 and Figure 16, and the cam of exhaust side may be selected three cams, That is Figure 11, Figure 15 and Figure 17.Such as with while needing to meet low-speed big power output and meeting the auxiliary braking of heavy-duty vehicle The vehicle of security can also be using the braking of four stroke drive patterns, four stroke braking modes, two-stroke drive pattern and two-stroke Pattern, then, the cam of air inlet side may be selected four cams, i.e. Figure 10, Figure 12, Figure 14 and Figure 16, and the cam of exhaust side is optional Select three or four cams, i.e. Figure 11, Figure 13, Figure 15 and Figure 17.Due to number of stroke it is constant in the case of, import/exhaust door running frequency It is constant, then, import/exhaust door is possible with a cam to drive, by valve control machanism 6 individually or be arranged on Camshaft phase governor motion on camshaft is engaged and provides corresponding valve opening timing and unlatching for concrete operating point Duration.The constant situation of number of stroke, drive pattern and braking mode to the valve opening timing of import/exhaust door, open and continue There is very big difference in phase, the requirement of valve maximum lift, the difference of valve opening timing is bigger, it is desirable to camshaft phase The adjustable extent of position governor motion is bigger, once beyond conventional such as the adjustable range of vane type vvt mechanism, need expensive Electronic VVT；If using an actuated by cams, by realizing little opening using mechanical continuous variable valve control machanism Open if the duration, valve maximum lift can be reduced accordingly, in fact it could happen that cannot simultaneously meet different mode to opening the duration With the requirement of maximum lift, it is impossible to realize optimal ventilation.Under two-stroke drive pattern and two-stroke braking mode, or in four punchings Under journey drive pattern and four stroke braking modes, the unlatching timing of inlet valve and open the duration and be more or less the same, exhaust valve is opened Open timing and unlatching duration difference is larger.Therefore, the constant situation of number of stroke, using one or two cams root is also needed to Determine according to actual conditions.

For for the Variabale valve actuation system of single-mode engine, such as four stroke drive patterns, air inlet side Cam select Figure 10.Under different operating modes, two to three different cams are selected.Adopt such as under low speed and load operating mode and have The little cam for opening duration and little lift, using having big duration and the high-lift of opening under high speed high load capacity operating mode Cam.For another example, under low speed same cylinder two inlet valve asynchronous operations, i.e., one inlet valve is with big valve stroke and unlatching Duration is run, and another inlet valve is with little valve stroke and opens duration operation, can strengthen In Cylinder Flow, improves The performance of engine, therefore, can pass through using the such as structure of Fig. 5, left cam and right cam under the low speed have not Same cam profile, or left side valve control machanism 6A and right side valve control machanism 6B using the methods such as different controlled quentity controlled variables come Realize.

In order to meet requirement of the practical application to aspects such as changeable air valve degree of flexibility, cost, system arrangements, the present invention can Arrange in pairs or groups various different valve control machanisms.Figure 18 is the schematic diagram of the valve control machanism using a two-way valve.Valve control Mechanism processed 6 has a two-way valve 62V.Two-way valve 62V has two-way valve first end 62Va and the second end of two-way valve 62Vb.Fuel feeding Control end 6a and drive control end 6b are connected with two-way valve first end 62Va.Oil storage control end 6c and the second end of two-way valve 62Vb It is connected.Figure 19 is the schematic diagram of the valve control machanism using a two-way valve and a check valve.On the basis of Figure 18, gas Gate control mechanism 6 also has a check valve 6CV.Check valve 6CV has check valve oil inlet end 6CVa and check valve oil outlet end 6CVb.Check valve oil inlet end 6CVa is connected with oil-feeding control end 6a.Check valve oil outlet end 6CVb is connected with oil storage control end 6c.

Figure 20 is the schematic diagram of the valve control machanism using a two-way valve and two check valves.Valve control machanism 6 With a two-way valve 62V and two check valve 6CV, i.e. the first check valve 6CV1 and the second check valve 6CV2.Two-way valve 62V has There are two-way valve first end 62Va and the second end of two-way valve 62Vb.First check valve 6CV1 has the first check valve oil inlet end 6CV1a With the first check valve oil outlet end 6CV1b.There is second check valve 6CV2 the second check valve oil inlet end 6CV2a and the second check valve to go out Oily end 6CV2b.First check valve oil outlet end 6CV1b and the second check valve oil inlet end 6CV2a are connected with oil-feeding control end 6a, the Two check valve oil outlet end 6CV2b and two-way valve first end 62Va are connected with drive control end 6b, the first check valve oil inlet end 6CV1a and the second end of two-way valve 62Vb are connected with oil storage control end 6c.

Figure 21 is the schematic diagram of the valve control machanism using a triple valve and a check valve.Valve control machanism 6 With an a triple valve 63V and check valve 6CV.Triple valve 63V has triple valve first end 63Va, the end of triple valve second The 63Vb and end 63Vc of triple valve the 3rd.Check valve 6CV has check valve oil inlet end 6CVa and check valve oil outlet end 6CVb.Triple valve First end 63Va and check valve oil outlet end 6CVb are connected with oil-feeding control end 6a, triple valve the second end 63Vb and drive control end 6b is connected, and the end 63Vc of triple valve the 3rd is connected with check valve oil inlet end 6CVa.Figure 22 is using one triple valve of a two-way valve With the schematic diagram of the valve control machanism of a check valve.On the basis of Figure 21, valve control machanism 6 is also logical with one two Valve 62V.Two-way valve 62V has two-way valve first end 62Va and the second end of two-way valve 62Vb.Two-way valve first end 62Va and driving Control end 6b is connected, and two-way valve the second end 62Vb is connected with oil storage control end 6c.

Claims (9)

1. a kind of axial displacement multi-mode hydraulic variable valve drive system, it includes valve actuating mechanism (2), its feature It is：It also includes camshaft (3), cam shaft sleeve (4), axial moving mechanism (5), valve control machanism (6), plunger type fuel feeding Device (7G), piston actuator (7Q) and oil conservator (7T)；First cam (401) and are set on the cam shaft sleeve (4) Two cams (402)；First cam (401) is adopted using single-tab cam lobes or biconvex cam lobes, the second cam (402) With single-tab cam lobes or biconvex cam lobes, biconvex cam lobes are using molded line is identical and 180 ° of phase Two projections of camshaft degree；Plunger type oil feeder (7G) has plunger input (7Ga) and fuel supply chamber (7Gb)；Piston type Driver (7Q) has driving chamber (7Qa) and piston output end (7Qb)；Valve control machanism (6) including oil-feeding control end (6a), Drive control end (6b) and oil storage control end (6c)；The axial location of axial moving mechanism (5) adjustment cam axle axle sleeve (4), certainly Surely it is the first cam (401) or the second cam to direct or through transmission mechanism and drive the cam of plunger input (7Ga) (402)；Fuel supply chamber (7Gb) is connected with oil-feeding control end (6a), and driving chamber (7Qa) is connected with drive control end (6b), oil conservator (7T) it is connected with oil storage control end (6c)；Piston output end (7Qb) drives valve actuating mechanism directly or by transmission mechanism (2)。

2. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Institute The 3rd cam (403) of increase in cam shaft sleeve (4) is stated, the 3rd cam (403) is using single-tab cam lobes or biconvex Cam lobes；The axial location of axial moving mechanism (5) adjustment cam axle axle sleeve (4), decision directs or through transmission mechanism The cam for driving plunger input (7Ga) is the first cam (401), the second cam (402), or the 3rd cam (403).

3. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Increase Plus a valve actuating mechanism (2), i.e. the first valve actuating mechanism (201) and duaspiracle drive mechanism (202)；Increase valve Drive axle (8)；Piston output end (7Qb) is first finally direct respectively by valve actuation bridge (8) again directly or by transmission mechanism Or the first valve actuating mechanism (201) and duaspiracle drive mechanism (202) are driven by transmission mechanism.

4. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Increase Plus a valve actuating mechanism (2), a valve control machanism (6) and plunger type oil feeder (7G), a piston type drive Dynamic device (7Q) and an oil conservator (7T), i.e., using the first valve actuating mechanism (201), the first valve control machanism (601), One plunger type oil feeder (701G), first piston formula driver (701Q), the first oil conservator (701T), duaspiracle drive mechanism (202), duaspiracle controlling organization (602), the second plunger type oil feeder (702G), second piston formula driver (702Q) and Two oil conservators (702T)；Increase valve actuation bridge (8)；First plunger type oil feeder (701G) has the first plunger input (701Ga) with the first fuel supply chamber (701Gb)；First piston formula driver (701Q) has the first driving chamber (701Qa) and first Piston output end (701Qb)；First valve control machanism (601) includes the first oil-feeding control end (601a), the first drive control End (601b) and the first oil storage control end (601c)；Second plunger type oil feeder (702G) has the second plunger input (702Ga) with the second fuel supply chamber (702Gb)；Second piston formula driver (702Q) has the second driving chamber (702Qa) and second Piston output end (702Qb)；Duaspiracle controlling organization (602) includes the second oil-feeding control end (602a), the second drive control End (602b) and the second oil storage control end (602c)；Cam first passes through valve actuation bridge (8) most again directly or by transmission mechanism Afterwards respectively directly or by transmission mechanism the first plunger input (701Ga) of driving and the second plunger input (702Ga)；First Fuel supply chamber (701Gb) is connected with the first oil-feeding control end (601a), the first driving chamber (701Qa) and the first drive control end (601b) it is connected, the first oil conservator (701T) is connected with the first oil storage control end (601c)；First piston output end (701Qb) is straight Connect or the first valve actuating mechanism (201) is driven by transmission mechanism；Second fuel supply chamber (702Gb) and the second oil-feeding control end (602a) it is connected, the second driving chamber (702Qa) is connected with the second drive control end (602b), the second oil conservator (702T) and second Oil storage control end (602c) is connected；Second piston output end (702Qb) drives duaspiracle to drive directly or by transmission mechanism Mechanism (202).

5. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：It is right In two cam switchings, on the cam shaft sleeve (4) two switching slot are provided with；The axial moving mechanism (5) adopts two Individual electromagnetic actuator；Or the axial moving mechanism (5) is using two hydraulic actuating mechanisms and two hydraulic controls； For three cam switchings, on the cam shaft sleeve (4) two switching slot are provided with；The axial moving mechanism (5) adopts Three electromagnetic actuators；Or the axial moving mechanism (5) is using three hydraulic actuating mechanisms and three hydraulic control machines Structure.

6. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Institute Valve control machanism (6) is stated with a two-way valve (62V)；There is two-way valve (62V) two-way valve first end (62Va) and two to lead to The end of valve second (62Vb)；Oil-feeding control end (6a) and drive control end (6b) are connected with two-way valve first end (62Va)；Oil storage Control end (6c) is connected with the end of two-way valve second (62Vb)；Or the valve control machanism (6) also has a check valve (6CV)；Check valve (6CV) has check valve oil inlet end (6CVa) and check valve oil outlet end (6CVb)；Check valve oil inlet end (6CVa) it is connected with oil-feeding control end (6a)；Check valve oil outlet end (6CVb) is connected with oil storage control end (6c).

7. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Institute Valve control machanism (6) is stated with a two-way valve (62V) and two check valves (6CV), i.e. the first check valve (6CV1) and Two check valves (6CV2)；Two-way valve (62V) has two-way valve first end (62Va) and the end of two-way valve second (62Vb)；First is unidirectional Valve (6CV1) has the first check valve oil inlet end (6CV1a) and the first check valve oil outlet end (6CV1b)；Second check valve (6CV2) With the second check valve oil inlet end (6CV2a) and the second check valve oil outlet end (6CV2b)；First check valve oil outlet end (6CV1b) It is connected with oil-feeding control end (6a) with the second check valve oil inlet end (6CV2a), the second check valve oil outlet end (6CV2b) and two leads to Valve first end (62Va) is connected with drive control end (6b), the first check valve oil inlet end (6CV1a) and the end of two-way valve second (62Vb) it is connected with oil storage control end (6c).

8. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Institute Valve control machanism (6) is stated with a triple valve (63V) and a check valve (6CV)；Triple valve (63V) has triple valve the One end (63Va), the end of triple valve second (63Vb) and the end (63Vc) of triple valve the 3rd；Check valve (6CV) has check valve oil inlet end (6CVa) with check valve oil outlet end (6CVb)；Triple valve first end (63Va) and check valve oil outlet end (6CVb) are and oil-feeding control End (6a) is connected, and the end of triple valve second (63Vb) is connected with drive control end (6b), the end (63Vc) of triple valve the 3rd and check valve Oil inlet end (6CVa) is connected；Or the valve control machanism (6) also has a two-way valve (62V)；Two-way valve (62V) has Two-way valve first end (62Va) and the end of two-way valve second (62Vb)；Two-way valve first end (62Va) and drive control end (6b) phase Even, the end of two-way valve second (62Vb) is connected with oil storage control end (6c).

9. a kind of axial displacement multi-mode hydraulic variable valve drive system according to claim 1, is characterized in that：Institute It is slide block, push rod, rocking arm, swing arm, four-bar mechanism to state transmission mechanism, or Hydraulic Main is from piston type mechanism.