CN106368754A - Intake valve device, air distribution system and air distribution phase switching method - Google Patents
Intake valve device, air distribution system and air distribution phase switching method Download PDFInfo
- Publication number
- CN106368754A CN106368754A CN201610752707.7A CN201610752707A CN106368754A CN 106368754 A CN106368754 A CN 106368754A CN 201610752707 A CN201610752707 A CN 201610752707A CN 106368754 A CN106368754 A CN 106368754A
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- Prior art keywords
- valve
- face
- guide rod
- control valve
- inlet
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention relates to the technical field of engine equipment, in particular to an intake valve device, an air distribution system and an air distribution phase switching method. The intake valve device comprises a cam, an air valve transmission mechanism and an intake valve which are connected in sequence, wherein the cam rotates to push the air valve transmission mechanism to move so as to control opening and closing of the intake valve; a contour line of the cam comprises multiple molded lines with different lifts, and the air valve transmission mechanism is enabled to drive the intake valve to realize multiple air distribution phases; a hydraulic control mechanism is arranged on the air valve transmission mechanism and used for controlling the intake valve to be switched among the various air distribution phases. The intake valve device can meet the requirement of at least two different working conditions for the air distribution phases, especially can meet the performance and dynamic requirements for a Miller lift and an ordinary normal lift of the intake valve simultaneously and can realize flexible switching of different air distribution phases, and the accuracy of a switching process is high, so that optimal performance and emission target of an engine are achieved in a mobile manner.
Description
Technical field
The present invention relates to engine apparatus technical field, more particularly, to a kind of inlet valve means, air distribution system and distribution phase
Position changing method.
Background technology
Deterioration with environment and the impact of greenhouse effect, while people pay close attention to conventional diesel Pollution from the engine exhaust,
Also increasingly close the discharge of carbon dioxide injection, this is accomplished by diesel technology route escalation process, need to more variables
Realize controlled, valve actuating mechanism as the main device of diesel engine air inlet system, its to air inflow, the flexible control of port timing with
The no performance being related to diesel engine and discharge index.
Wherein, valve actuating mechanism is the important component part of electromotor, and its main function is the job order according to electromotor
With the requirement of cycle of operation, time opening and the inlet and exhaust valve closing each cylinder, new gas is made to enter cylinder, waste gas is discharged from cylinder.
Valve type distribution device is mainly made up of valve group and valve transmission group two parts.
Port timing, also known as valve timing, is to be opened and closed the moment with the inlet and exhaust valve that crank angle represents and its open lasting
Time.Different electromotors, due to the difference of structure and rotating speed, its valve timing also differs, even same electromotor,
Its valve timing also should change with the change of rotating speed, and most of electromotors adopt constant valve timing at present, and it is only suitable for
In a certain normal revolution of electromotor.
Using fixing port timing present diesel engine, that is, the port timing under full load full working scope is unique more
, so it is unfavorable for realizing the flexible control to gas handling system, and be unfavorable for realizing optimum diesel engine performance under full working scope.
Content of the invention
(1) technical problem to be solved
The technical problem to be solved in the present invention there is provided a kind of inlet valve means, air distribution system and port timing switching side
Method, this device can meet Miller lift and the commonly performance of normal lift and the demanding kinetics of valve simultaneously, to realize valve
The flexibly controlled switching of lift, so that this air distribution system can realize the optimum shape of performance and discharge under different operating modes
State.
(2) technical scheme
In order to solve above-mentioned technical problem, the invention provides a kind of inlet valve means, including the cam being sequentially connected with, gas
Door drive mechanism and inlet valve, described cam rotation promotes valve actuating gear motion, with control described inlet valve unlatching and
Close；The contour line of described cam includes the molded line that multistage is respectively provided with different lifts, so that described valve actuating gear can carry
Dynamic inlet valve realizes multiple port timings respectively；It is provided with hydraulic control, described hydraulic pressure control on described valve actuating gear
Mechanism processed is used for controlling inlet valve to switch between various port timings.
Further, the contour line of described cam includes basic circle, the first molded line and the second molded line, and described first molded line passes through
Second molded line is connected with basic circle, and the lift of described first molded line is more than the lift of described second molded line.
Further, the two ends of described first molded line are connected with basic circle by described second molded line respectively.
Further, described valve actuating gear includes tappet guide rod group, rocker arm shaft and drives piston, described rocker arm shaft
One end is connected with cam by tappet guide rod group, and is provided with guide rod gap between described rocker arm shaft and tappet guide rod group；Described shake
The other end of arm axle passes through to drive piston to be connected with inlet valve, is provided with plunger shaft between described rocker arm shaft and driving piston, described
The height of plunger shaft is valve clearance；Described hydraulic control is arranged between described rocker arm shaft and plunger shaft.
Further, described hydraulic control includes:
Main oil gallery；
Spool control valve, slidably sealing is arranged in described rocker arm shaft, described spool control valve be respectively arranged at two ends with the
End face and second end face, described first end face and second end face are connected with described main oil gallery respectively, the face of described first end face
The long-pending area more than second end face, described second end face top is provided with slide valve spring；
Control valve, is arranged between the first end face of described spool control valve and described main oil gallery, for controlling described control
Guiding valve slide handover between the first state and a second state；
Check valve, is arranged between oil inlet end and the oil outlet end of described plunger shaft, the oil inlet end of described plunger shaft and control
The second end face of guiding valve remains connection；Described spool control valve between the first state and a second state slide handover when, institute
State and connect between the oil outlet end of plunger shaft and the second end face of spool control valve or disconnect.
Further, described control valve is closed, and described spool control valve slides into first in the presence of described slide valve spring
During state, the oil inlet end of described plunger shaft and oil outlet end are connected respectively between the second end face of described spool control valve；Described control
When guiding valve processed slides into the second state, described control valve is opened, the oil inlet end of described plunger shaft and the second end face of spool control valve
Between connect, the oil outlet end of described plunger shaft is separated with the second end face of spool control valve.
Further, it is provided with the regulation spiral shell for adjusting described guide rod gap between described rocker arm shaft and tappet guide rod group
Bolt.
Present invention also offers a kind of air distribution system, including inlet valve means as above.
Present invention also offers a kind of port timing changing method, comprise the steps:
Gap adjustment: guide rod gap, the width in described guide rod gap are set between one end of rocker arm shaft and tappet guide rod group
Degree is matched with the lift of the second molded line of cam, in the other end of described rocker arm shaft and drives piston using described guide rod gap
Between piston intracavity setting valve clearance；
Inlet valve is switched to the first port timing: close electromagnetic valve so that the spool control valve of hydraulic control exists
First state is slid into, now the first end face of described spool control valve is in communication with the outside, described control in the presence of slide valve spring
The second end face of guiding valve is connected with the oil outlet end of main oil gallery, the oil inlet end of plunger shaft and plunger shaft simultaneously, so that described convex
Wheel rotate when, the lift of described second molded line is offset by guide rod gap, now the open and-shut mode of described inlet valve only with described
The lift of the first molded line of cam matches；
Described inlet valve is switched to second port timing: open electromagnetic valve, now the first end of described spool control valve
Face is connected with main oil gallery so that described spool control valve slides into second in the presence of both ends of the surface pressure differential respectively with second end face
State, now the first end face of described spool control valve connect with main oil gallery respectively with second end face, described second end face and piston
The oil inlet end connection in chamber, and disconnect with the oil outlet end of described plunger shaft, so that during described cam rotation, described valve clearance
Interior full of hydraulic oil, now the open and-shut mode of described inlet valve and the lift of the monolithic wheel profile of described cam match.
Further, between described one end in rocker arm shaft and tappet guide rod group, guide rod gap is set, further includes:
In the liner driving setting one between piston and inlet valve to have preset height, described preset height is equal to described convex
The lift of the second molded line of wheel；
Make to fit between described rocker arm shaft and tappet guide rod group by regulating bolt；
Take out described liner, so that having described guide rod gap between described rocker arm shaft and tappet guide rod group.
(3) beneficial effect
The technique scheme of the present invention has the advantages that what the inlet valve means of the present invention included being sequentially connected with
Cam, valve actuating gear and inlet valve, cam rotation promotes valve actuating gear motion, to control unlatching and the pass of inlet valve
Close；The contour line of cam includes the molded line that multistage is respectively provided with different lifts, so that valve actuating gear can drive inlet valve to divide
Do not realize multiple port timings；Hydraulic control is provided with valve actuating gear, hydraulic control is used for controlling air inlet
Door switches between various port timings.This inlet valve means arranges multistage on the contour line of same cam and is respectively provided with difference
The molded line of lift, so that this inlet valve means can take into account at least two different requirements to port timing for the operating mode, particularly can
Meet Miller lift and the commonly performance of normal lift and the demanding kinetics of valve simultaneously, and realized by hydraulic control
The flexible switching of different port timings, thus optimal performance and the emissions object of realizing electromotor of mobility；This hydraulic control
The compact conformation of mechanism, to engine body change less, and be directly used the lubricating oil on electromotor as pressure source it is not necessary to
Increase extra auxiliary device, it is rapid, accurate to respond in the handoff procedure of port timing, is capable of different air valve lift
Flexibly, accurately switch.
Brief description
Fig. 1 is the installation diagram of the inlet valve means of the embodiment of the present invention；
Fig. 2 is the cross section structure schematic diagram of the cam of the embodiment of the present invention；
Fig. 3 is that the spool control valve of the embodiment of the present invention is in structural representation during first state；
Fig. 4 is that the spool control valve of the embodiment of the present invention is in structural representation during the second state；
Fig. 5 is that the valve clearance of the plunger shaft of the embodiment of the present invention adjusts schematic diagram；
Fig. 6 is the valve lift diagram of the inlet valve of the embodiment of the present invention.
Wherein, 1, cam；110th, the first molded line；120th, the second molded line；130th, the first curve；140th, the second curve；2nd, very
Post guide rod group；3rd, control valve；4th, rocker arm shaft；5th, regulating bolt；51st, guide rod gap；52nd, primary importance；53rd, the second position；6、
Main oil gallery；61st, the first oil duct；62nd, the second oil duct；63rd, the 3rd oil duct；64th, the 4th oil duct；7th, check valve screw；71st, piston
Chamber；72nd, check valve；8th, drive piston；9th, spool control valve；A, first end face；B, second end face；10th, sealing bolt；11st, air inlet
Door.
Specific embodiment
With reference to the accompanying drawings and examples embodiments of the present invention are described in further detail.Following examples are used for
The present invention is described, but can not be used for limiting the scope of the present invention.
In describing the invention, unless otherwise stated, " multiple " are meant that two or more.Term " on ",
The orientation of instruction such as D score, "left", "right", " interior ", " outward ", " front end ", " rear end ", " head ", " afterbody " or position relationship are
Based on orientation shown in the drawings or position relationship, it is for only for ease of the description present invention and simplifies description, rather than instruction or dark
Show the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore it is not intended that right
The restriction of the present invention.Additionally, term " first ", " second " etc. are only used for describing purpose, and it is not intended that indicating or hint phase
To importance.
As shown in figure 1, the inlet valve means that the present embodiment provides include being sequentially connected with cam 1, valve actuating gear and
Inlet valve 11, cam 1 rotates and promotes valve actuating gear motion, to control the opening and closing of inlet valve 11；Cam 1 wheel
Profile includes the molded line that multistage is respectively provided with different lifts so that valve actuating gear that inlet valve 11 can be driven to realize respectively is multiple
Port timing, such that it is able to take into account at least two different requirements to port timing for the operating mode, particularly can meet valve simultaneously
Miller lift and the commonly performance of normal lift and demanding kinetics；Hydraulic control, liquid are provided with valve actuating gear
Pressure controlling organization is used for controlling inlet valve 11 to switch between various port timings, because the structure of this hydraulic control is tight
Gather, engine body is changed less, and be directly used the lubricating oil on electromotor as pressure source it is not necessary to increase is extra auxiliary
Help device, it is rapid, accurate to respond in the handoff procedure of port timing, is capable of the flexible, accurate of different air valve lift
Switching.
Ensure that and realize different valve strokes, to meet the working condition requirement of the different port timings of electromotor,
In the present embodiment, the contour line of cam 1 includes basic circle, the first molded line 110 and the second molded line 120, and the first molded line 110 passes through second
Molded line 120 is connected with basic circle, and the lift of the first molded line 110 is more than the lift of the second molded line 120.
As shown in Fig. 2 the frequency that can be opened and closed according to inlet valve 11, appropriate design the first molded line 110 and second
The layout of molded line 120, in the present embodiment, the two ends of the preferably first molded line 110 are connected with basic circle by the second molded line 120 respectively.
In order to further ensure that effectively opening and effectively closing of inlet valve 11, in the contour line of preferred cam 1, the first type
Line 110 has ascent stage and descending branch, so that having a wave crest point between ascent stage and descending branch, to pass by valve enough
Dynamic mechanism urges inlet valve 11 is opened.
In the present embodiment, valve actuating gear includes tappet guide rod group 2, rocker arm shaft 4 and drives piston 8, and the one of rocker arm shaft 4
End is connected with cam 1 by tappet guide rod group 2, and is provided with guide rod gap 51 between rocker arm shaft 4 and tappet guide rod group 2；Rocker arm shaft 4
The other end pass through drive piston 8 be connected with inlet valve 11, rocker arm shaft 4 and driving piston 8 between be provided with plunger shaft 71, plunger shaft
71 height is valve clearance, and preferably valve clearance is equal with the width in guide rod gap 51, and available guide rod gap 51 is arranged
And the size of valve gap adjustment, so that it is guaranteed that the reliability switching between different port timings；Preferably rocker arm shaft 4 and tappet are led
It is provided with the regulating bolt 5 for adjusting guide rod gap 51 between bar group 2.
Hydraulic control is arranged between rocker arm shaft 4 and plunger shaft 71, and the lubricating oil being carried by the use of electromotor is as pressure
Power source controls the pressure in plunger shaft 71, thus controlling the working condition driving piston 8, so that the opening and closing of inlet valve 11 and air inlet
State meets the working condition requirement of different port timings.
Specifically, when rotating, the molded line of the multistage difference lift being provided with using it promotes tappet to the cam 1 of the present embodiment
Guide rod group 2 vertically moves back and forth, and is swung by one end that tappet guide rod group 2 promotes rocker arm shaft 4, meanwhile, according to lever swing
Principle, drives piston 8 equally vertically to be moved back and forth in the other end of rocker arm shaft 4, drives piston 8 to control by valve spring
The switch of inlet valve 11 and air inlet.
In order to ensure that inlet valve 11 realizes the reliability switching of different port timings, preferably hydraulic control includes: main
Oil duct 6, spool control valve 9, control valve 3 and check valve 72.
Main oil gallery 6 is preferably the lubricating oil duct of electromotor；Spool control valve 9 slidably seals and is arranged in rocker arm shaft 4,
Control the switching of the port timing of inlet valve 11 by the slip of spool control valve 9 it can be ensured that switching action quick and precisely,
Preferably spool control valve 9 is sealed in rocker arm shaft 4 by sealing bolt 10；Spool control valve 9 be respectively arranged at two ends with first end face a and
Second end face b, first end face a and second end face b connect main oil gallery 6 respectively, and the area of first end face a is more than second end face b
Area, is provided with slide valve spring on second end face b top, and the elastic force using slide valve spring acts on it is ensured that the state of spool control valve 9 is cut
Change accurately, be especially to ensure that spool control valve 9, under the elastic force of slide valve spring acts on, can switch back into the first shape by the second state
State；Control valve 3 is arranged between first end face a of spool control valve 9 and main oil gallery 6, for controlling above-mentioned spool control valve 9
Slide handover between one state and the second state；Check valve 72 is arranged between oil inlet end and the oil outlet end of plunger shaft 71, piston
The oil inlet end in chamber 71 is remained with second end face b of spool control valve 9 and connects, using check valve 72 make inside plunger shaft 71
Can have sufficiently large pressure if necessary, thus ensureing to provide enough pressure to open inlet valve 11；Spool control valve 9 is first
Between state and the second state during slide handover, connect between the oil outlet end of plunger shaft 71 and second end face b of spool control valve 9 or
Disconnect.
Preferably rocker arm shaft 4 is provided with check valve screw 7, check valve screw 7 and driving piston with the one end driving piston 8 to be connected
Plunger shaft 71 is set between 8, check valve 72 is fixed by check valve screw 7, in order to the installation of check valve 72, adjustment and more
Change.
In the present embodiment, hydraulic control by the use of the lubricating oil of electromotor as pressure source, using control valve 3 to control
The change of the pressure differential of two end faces up and down of guiding valve 9 is controlled, and controls the trend of lubricating oil using check valve 72, thus will
Three flexibly combines to promote spool control valve 9 to slide, and then controls the pressure change in plunger shaft 71, according in plunger shaft 71
Pressure change, the elastic force effect of cooperation valve spring is so that inlet valve 11 switches to by a kind of port timing reliability and accurately
Another kind of port timing.
Specifically, preferably first end face a of spool control valve 9 and second end face b are provided with the second oil respectively and main oil gallery 6 between
Road 62 and the first oil duct 61, control valve 3 is installed on the first oil duct 61, the oil inlet end of plunger shaft 71 and oil outlet end respectively with control
It is provided with the 3rd oil duct 63 and the 4th oil duct 64 between second end face b of guiding valve 9.
When needing inlet valve 11 to realize the first port timing, inlet valve 11 is such as needed to realize the distribution phase of common lift
Position, then as shown in figure 3, making spool control valve 9 slide into first state, now control valve 3 is closed, second end face b of spool control valve 9
Connected with main oil gallery 6 by the first oil duct 61, and first end face a of spool control valve 9 then passes through the direct and external world of the second oil duct 62
Communicate, so that the pressure of first end face a of spool control valve 9 is approximately equal to atmospheric pressure, and second end face b of spool control valve 9
Pressure be equal to main oil gallery 6 pressure, then the oil inlet end of plunger shaft 71 and oil outlet end second end face b with spool control valve 9 respectively
Between connect, now the pressure in plunger shaft 71 be equal to main oil gallery 6 pressure, because the pressure of main oil gallery 6 is far smaller than valve
, when rotating, the lift of the second molded line 120 is balanced out by guide rod gap 51, the only first molded line for the pressure of spring, therefore cam 1
110 lift is effective.
When needing inlet valve 11 to realize second port timing, inlet valve 11 is such as needed to realize the port timing of Miller lift
When, control valve 3 is opened, first end face a of spool control valve 9 and second end face b are each via the second oil duct 62 and the first oil duct
61 are connected with main oil gallery 6 respectively so that first end face a of spool control valve 9 and the equalization of pressure of second end face b are in main oil gallery 6
Pressure, but because the area of first end face a of spool control valve 9 is more than the area of second end face b, therefore, spool control valve 9 is the
In the presence of oil pressure pressure differential between end face a and second end face b, the second state is slid into by promotion, as shown in figure 4, now
Connect between the oil inlet end of plunger shaft 71 and second end face b of spool control valve 9, the oil outlet end of plunger shaft 71 and spool control valve 9
Second end face b separated, i other words, the 4th oil duct 64 between plunger shaft 71 and spool control valve 9 is plugged, the 3rd oil duct 63
Due to the check valve 72 in plunger shaft 71 effect and can only oil-feed can not be fuel-displaced so that in valve clearance be full of hydraulic oil,
Then now the pressure in plunger shaft 71 is large enough to overcome the pressure of valve spring, and now valve clearance no longer exists, so this
When cam 1 rotate when, the lift of the first molded line 110 and the second molded line 120 is all effective.
The air distribution system that the present embodiment provides includes inlet valve means as above, and this air distribution system can realize cam
The reliability switching of 1 molded line, so that inlet valve 11 can meet the performance of at least two port timings and kinetics will simultaneously
Ask, and enable reliable switching between two kinds of port timings, this air distribution system can be used for mating scr (SCR
Process, English full name selective catalytic reduction) or dpf (diesel particulate filter, English full name
Diesel particulate filter) post processing diesel engine, optimize scr before temperature and realize dpf regeneration while,
Change this body structure of electromotor as little as possible and oil consumption level, have good market prospect and economic benefit.
The present embodiment additionally provides a kind of port timing changing method, comprises the steps:
First, carried out gap adjustment before implementing the switching of port timing, particularly as follows: in one end of rocker arm shaft 4 and enduring
Guide rod gap 51 is set between post guide rod group 2, and the width in guide rod gap 51 is matched with the lift of the second molded line 120 of cam 1,
The width in preferably guide rod gap 51 equal or slightly larger than cam 1 the second molded line 120 lift, using guide rod gap 51 and rocking arm
Axle 4 wave effect, thus rocker arm shaft 4 the other end and drive piston 8 between plunger shaft 71 in setting valve clearance.
Wherein, as shown in figure 5, with the position between plunger shaft 71 and valve spring for primary importance 527, to drive piston
Position between 8 and inlet valve 11 is the second position 53, between one end of rocker arm shaft 4 and tappet guide rod group 2 between setting guide rod
Gap, further includes: at the second position 53, setting one has the liner of preset height, and the preset height of this liner is equal to cam
The height of 1 the second molded line 120；Make to fit between rocker arm shaft 4 and tappet guide rod group 2 by regulating bolt 5；Take out second
Put the liner at 53, so that there is guide rod gap 51 between rocker arm shaft 4 and tappet guide rod group 2.
By the setting regulative mode in above-mentioned guide rod gap 51, the lever principle in conjunction with rocking lever and valve spring
Elastic force effect close so that valve clearance occurs at primary importance 527 such that it is able to be determined according to the real contour line of cam 1
The valve clearance width of reason, reliable effectively with the switching that ensures the port timing of inlet valve 11.
If the valve stroke of the first port timing is less than the valve stroke of second port timing, such as, risen with common
The valve state of journey as the first port timing, using the valve state of Miller lift as second port timing.
When needing for inlet valve 11 to switch to the first port timing, close electromagnetic valve, so that hydraulic control
Spool control valve 9 slides into first state, and now first end face a of spool control valve 9 is in communication with the outside, the second end of spool control valve 9
Face b is connected with the oil outlet end of main oil gallery 6, the oil inlet end of plunger shaft 71 and plunger shaft 71 simultaneously, so that described cam 1 exists
During rotation, the lift of described second molded line 120 is offset by guide rod gap 51, now the open and-shut mode of described inlet valve 11 only with institute
The lift stating the first molded line 110 of cam 1 matches, now, the first curve 130 in the valve stroke of inlet valve 11 such as Fig. 6
Shown.
When needing for inlet valve 11 to switch to second port timing, open electromagnetic valve so that spool control valve 9 slides into
Second state, now first end face a of spool control valve 9 connect with main oil gallery 6 respectively with second end face b, second end face b and piston
The oil inlet end connection in chamber 71, and disconnect with the oil outlet end of plunger shaft 71, so that when cam 1 rotates, valve clearance is by valve
Spring is offset, and now the open and-shut mode of inlet valve 11 and the lift of the monolithic wheel profile of cam 1 match, now, inlet valve 11
Valve stroke as shown in the second curve 140 in Fig. 6.
In sum, the inlet valve means of the present embodiment include cam 1, valve actuating gear and the inlet valve being sequentially connected with
11, cam 1 rotates and promotes valve actuating gear motion, to control the opening and closing of inlet valve 11；On each section of cam 1
It is equipped with identical many lift profile structure, so that valve actuating gear can drive inlet valve 11 to realize multiple distribution phases respectively
Position；Hydraulic control is provided with valve actuating gear, hydraulic control is used for controlling inlet valve 11 in various distribution phases
Switch between position.This inlet valve means all has many lift profile structure on each section of same cam 1 simultaneously, so that should
Inlet valve means can take into account at least two different requirements to port timing for the operating mode, particularly can meet the Miller of valve simultaneously
Lift and the commonly performance of normal lift and demanding kinetics, and the flexible of different port timings is realized by hydraulic control
Switching, thus optimal performance and the emissions object of realizing electromotor of mobility；The compact conformation of this hydraulic control, to send out
The change of motivation body is less, and is directly used the lubricating oil on electromotor as pressure source it is not necessary to increase extra auxiliary device,
It is rapid, accurate to respond in the handoff procedure of port timing, is capable of flexible, the accurate switching of different air valve lift.
Embodiments of the invention in order to example and description for the sake of and be given, and be not exhaustively or by this
Bright it is limited to disclosed form.Many modifications and variations are obvious for the ordinary skill in the art.Choosing
Selecting and describe embodiment is in order to the principle of the present invention and practical application are more preferably described, and makes those of ordinary skill in the art
It will be appreciated that the present invention is thus design is suitable to the various embodiments with various modifications of special-purpose.
Claims (10)
1. a kind of inlet valve means are it is characterised in that including cam, valve actuating gear and the inlet valve being sequentially connected with, described
Cam rotation promotes valve actuating gear motion, to control the opening and closing of described inlet valve；The contour line bag of described cam
Include the molded line that multistage is respectively provided with different lifts, so that described valve actuating gear can drive inlet valve to realize multiple distributions respectively
Phase place；It is provided with hydraulic control, described hydraulic control is used for controlling inlet valve each on described valve actuating gear
Plant and switch between port timing.
2. inlet valve means according to claim 1 it is characterised in that the contour line of described cam include basic circle, first
Molded line and the second molded line, described first molded line is connected with basic circle by the second molded line, and the lift of described first molded line is more than institute
State the lift of the second molded line.
3. inlet valve means according to claim 2 are it is characterised in that the two ends of described first molded line are respectively by described
Second molded line is connected with basic circle.
4. the inlet valve means according to any one of claim 1-3 are it is characterised in that described valve actuating gear includes
Tappet guide rod group, rocker arm shaft and drive piston, one end of described rocker arm shaft is connected with cam by tappet guide rod group, and described shakes
It is provided with guide rod gap between arm axle and tappet guide rod group；The other end of described rocker arm shaft passes through to drive piston to be connected with inlet valve,
It is provided with plunger shaft, the height of described plunger shaft is valve clearance between described rocker arm shaft and driving piston；Described hydraulic control
Mechanism is arranged between described rocker arm shaft and plunger shaft.
5. inlet valve means according to claim 4 are it is characterised in that described hydraulic control includes:
Main oil gallery；
Spool control valve, slidably sealing be arranged in described rocker arm shaft, described spool control valve be respectively arranged at two ends with first end
Face and second end face, described first end face and second end face are connected with described main oil gallery respectively, and the area of described first end face is big
In the area of second end face, described second end face top is provided with slide valve spring；
Control valve, is arranged between the first end face of described spool control valve and described main oil gallery, for controlling described spool control valve
Slide handover between the first state and a second state；
Check valve, is arranged between oil inlet end and the oil outlet end of described plunger shaft, the oil inlet end of described plunger shaft and spool control valve
Second end face remain connection；Described spool control valve between the first state and a second state slide handover when, described work
Connect between the oil outlet end in plug chamber and the second end face of spool control valve or disconnect.
6. inlet valve means according to claim 5 it is characterised in that
When described control valve is closed, described spool control valve slides into first state in the presence of described slide valve spring, described work
The oil inlet end in plug chamber and oil outlet end are connected respectively between the second end face of described spool control valve；
Described control valve is opened, and described spool control valve slides into the second state, the oil inlet end of described plunger shaft and spool control valve
Connect between second end face, the oil outlet end of described plunger shaft is separated with the second end face of spool control valve.
7. the inlet valve means according to claim 5 or 6 are it is characterised in that between described rocker arm shaft and tappet guide rod group
It is provided with the regulating bolt for adjusting described guide rod gap.
8. a kind of air distribution system is it is characterised in that include the inlet valve means as any one of claim 1-8.
9. a kind of port timing changing method is it is characterised in that comprise the steps:
Gap adjustment: between one end of rocker arm shaft and tappet guide rod group arrange guide rod gap, the width in described guide rod gap with
The lift of the second molded line of cam matches, and is driven between piston in the other end of described rocker arm shaft using described guide rod gap
Piston intracavity setting valve clearance；
Inlet valve is switched to the first port timing: close electromagnetic valve so that the spool control valve of hydraulic control is in guiding valve
First state is slid into, now the first end face of described spool control valve is in communication with the outside, described spool control valve in the presence of spring
Second end face connect with the oil outlet end of main oil gallery, the oil inlet end of plunger shaft and plunger shaft, so that described cam exists simultaneously
During rotation, the lift of described second molded line is offset by guide rod gap, now the open and-shut mode of described inlet valve only with described cam
The lift of the first molded line match；
Described inlet valve is switched to second port timing: open electromagnetic valve, now the first end face of described spool control valve and
Second end face connects with main oil gallery respectively so that described spool control valve slides into the second shape in the presence of both ends of the surface pressure differential
State, described second end face is connected with the oil inlet end of plunger shaft, and disconnects with the oil outlet end of described plunger shaft, so that described convex
When wheel rotates, it is full of hydraulic oil in described valve clearance, now the monolithic wheel of the open and-shut mode of described inlet valve and described cam
The lift of profile matches.
10. port timing changing method according to claim 9 it is characterised in that described one end in rocker arm shaft with very
Between post guide rod group, guide rod gap is set, further includes:
In the liner driving setting one between piston and inlet valve to have preset height, described preset height is equal to described cam
The lift of the second molded line；
Make to fit between described rocker arm shaft and tappet guide rod group by regulating bolt；
Take out described liner, so that having described guide rod gap between described rocker arm shaft and tappet guide rod group.
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| CN201610752707.7A CN106368754B (en) | 2016-08-29 | 2016-08-29 | A kind of inlet valve means, air distribution system and port timing switching method |
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| CN201610752707.7A CN106368754B (en) | 2016-08-29 | 2016-08-29 | A kind of inlet valve means, air distribution system and port timing switching method |
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| CN108757084A (en) * | 2018-06-28 | 2018-11-06 | 潍柴动力股份有限公司 | The inlet valve means and diesel engine of port timing two-stage switching |
| WO2020000640A1 (en) * | 2018-06-28 | 2020-01-02 | 潍柴动力股份有限公司 | Intake valve device capable of implementing two-stage switching of gas distribution phase and diesel engine |
| CN112065527A (en) * | 2020-09-11 | 2020-12-11 | 潍柴动力股份有限公司 | Control oil way structure, rocker shaft assembly and engine assembly |
| CN117552852A (en) * | 2024-01-12 | 2024-02-13 | 潍柴动力股份有限公司 | Engine and valve mechanism thereof |
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| CN106368754B (en) | 2019-01-15 |
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