CN107327329A - A kind of electro-hydraulic full variable valve gear and control method - Google Patents
A kind of electro-hydraulic full variable valve gear and control method Download PDFInfo
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- CN107327329A CN107327329A CN201710580553.2A CN201710580553A CN107327329A CN 107327329 A CN107327329 A CN 107327329A CN 201710580553 A CN201710580553 A CN 201710580553A CN 107327329 A CN107327329 A CN 107327329A
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- 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
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- 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
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- 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
- F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The invention discloses one kind electro-hydraulic full variable valve gear and control method, belong to engine air valve technology field, electro-hydraulic full variable valve gear includes the appurtenances such as cushioning control valve, lift control valve, low-pressure reservoir, filter, hydraulic motor, accumulator, overflow valve, solenoid directional control valve, electro-hydraulic full variable gas distribution actuator, electronic control system and oil pipe；On full variable gas distribution actuator, there are high pressure hydraulic fluid port, lift control port, cushioning control hydraulic fluid port, five hydraulic cavities of cylinder body restriction and A, B, C, D, E, by the pressure for the hydraulic oil for controlling this 5 intracavitary, the unlatching of engine air valve is realized and the action such as take a seat；By change two-position three-way valve, lift control valve, cushioning control valve the dead electricity moment can just change engine air valve open phase, lift, the duration that valve lift and the soft readjustment of phase and air valve are opened is realized, so as to realize the complete variable of air valve motion.
Description
Technical field
The invention belongs to engine air valve technology field, and in particular to a kind of electro-hydraulic full variable valve gear and controlling party
Method.
Background technology
Along with being on the rise for World Environment Problems and international energy crisis, what it had seriously threatened human society can
Sustainable development.With the high speed development of internal combustion engine industry, people are growing day by day to the demand of petroleum resources, the ring brought therefrom
The problems such as border pollution and energy shortage, also comes one after another, and energy-conservation and environmental protection already have to what is faced as Development of I. C. Engine Industry
Two major issues.In order to be able to effectively solve the two problems, countries in the world are harmful to the economy and control for improving engine
The equal more and more higher of emission request, saving fuel oil controls noxious emission, has become the core direction of internal-combustion engine technology development.
In order to solve energy conservation and environmental protection, various internal combustion engine new technologies emerge in an endless stream, and change the distribution of engine valve
Timing and valve stroke are to improve engine performance, improve the thermal efficiency and reduce a kind of important method of noxious emission.Send out at present
The variable valve actuation mode of motivation includes actuated by cams, electromagnetic drive, electrically driven, electro-hydraulic driving etc..
Traditional engine valve actuation system controls inlet valve and exhaust valve using mechanical cam mechanism, due to cam
Molded line is fixed, thus the trim analysis such as its valve stroke, valve timing is all changeless, and actuated by cams mode is adjusted
It can not realize complete variable, it is impossible to be adjusted in engine operation, be typically only capable to ensure to optimize engine under a certain operating mode
Performance.
In order to preferably solve the above problems, there is researcher to propose Zona free, that is, cancel engine and match somebody with somebody
Camshaft and driven member in mechanism of qi structure, and with electromagnetism, electro-hydraulic, electric or other modes driving valve.Variable gas distribution technology
Obtain widely promoting as a kind of higher technological means of cost performance, the technology is mainly by improving the gazogene of engine
Structure improves the purpose of engine performance to reach, because valve actuating mechanism is directly connected to the degree of perfection of engine combustion process,
Therefore the quality to its dynamic property, economy and discharge performance has important influence.Research and develop at this stage without cam variable gas distribution
Mechanism has an obvious distribution advantage compared to traditional valve actuating mechanism, but at these without in cam variable valve actuating mechanism, electromagnetism
Type of drive is difficult to while meet the requirement that high pressure admission opens and closes frequency and lift to valve, electrically driven for sealedly requirement
Strictly, the full variable valve actuation device of electro-hydraulic driving can break through the restriction of cam profile, realize valve lift and phase
Soft readjustment, and then improve the overall performance of engine, therefore the mode of electro-hydraulic driving is easiest to realize.
The content of the invention
It is an object of the invention to provide a kind of restriction that can break through cam profile, realize the soft of valve lift and phase
Property regulation and air valve realizes the electro-hydraulic full variable valve gear and control method of continuous variable opening the duration.
The object of the present invention is achieved like this：
The invention discloses one kind electro-hydraulic full variable valve gear and control method, including cushioning control valve 15, lift control
Valve 16 processed, low-pressure reservoir 17, filter 18, hydraulic motor 19, accumulator 20, overflow valve 21, solenoid directional control valve 22, electro-hydraulic entirely may be used
Become the appurtenances such as distribution actuator 23, electronic control system and oil pipe；
Electro-hydraulic full variable gas distribution actuator 23 includes hydraulic fluid port, cushioning control valve 15, lift control valve 16 and solenoid directional control valve
22 are connected by oil pipe with hydraulic fluid port respectively；Accumulator 20, hydraulic motor 19 and mistake are connected with turn after solenoid directional control valve 22
Filter 18, is eventually connected to low-pressure reservoir 17；Solenoid directional control valve 22 is directly connected to low-pressure reservoir by another pipeline simultaneously
17, it is connected by overflow valve 21 with accumulator 20 on pipe line；Electronic control system is connected respectively to buffering control by wire
On valve 15 processed, lift control valve 16 and solenoid directional control valve 22.
For one kind electro-hydraulic full variable valve gear and control method, described electro-hydraulic full variable gas distribution actuator 23 includes
Cylinder body throttle orifice 2, high pressure hydraulic fluid port 3, main piston 4, lower cover 5, lift control port 8, take a seat buffering hydraulic fluid port 9, damper piston 10,
Cylinder body 11, buffer spring 12, low pressure hydraulic fluid port 13 and upper cover plate 14；
Upper cover plate 14 is located at the upper and lower ends sealed cylinder block 11 of cylinder body 11, main piston 4 and damper piston with lower cover 5 respectively
10 will be divided into the top of damper piston 10 in five hydraulic cavities of A, B, C, D, E, A hydraulic cavities inside cylinder body 11 is provided with low pressure hydraulic fluid port 13, C
It is provided with cylinder body 11 where hydraulic cavities at buffering hydraulic fluid port 9 of taking a seat, the cylinder body 11 where D hydraulic cavities and is provided with high pressure hydraulic fluid port 3, E liquid
Lift control port 8 is provided with cylinder body 11 where pressure chamber, the rear end of main piston 4 is connected with cylinder valve and spring for valve.
It is preferred that, described two hydraulic cavities of A, B are located at cylinder body top, damper piston 10 be located at two hydraulic cavities of A, B it
Between, buffer spring 12 is installed, the upper end of buffer spring 12 is fixed on upper cover plate 14, and lower end is fixed on buffering in A hydraulic cavities
On piston 10；There is a dividing plate on cylinder body 11, the hydraulic cavities of B, C two are separated, have a cylinder body throttle orifice 2 on dividing plate；Main piston 4 will be every
Tri- hydraulic cavities of C, D, E are divided into below plate, under any circumstance, main piston 4 will not block hydraulic oil port.
It is preferred that, described cylinder body 11 is up-narrow and down-wide convex structure, and structure up and down is cylinder or cube structure；
Upper cover plate 14 is uniformly distributed along the circumference multiple countersunk head screwed holes 1, and upper cover plate 14 is arranged on cylinder body 11 by bolt by countersunk head screw thread mouth 1
On, upper cover plate 14 is provided with spring base towards the side of A hydraulic cavities, for installing buffer spring 12；Lower cover 5 is uniformly distributed along the circumference
Lower cover 5 is arranged on cylinder body by two circle countersunk head screwed holes, bolt by the small circle countersunk head screwed hole 7 of diameter, passes through diameter
Electro-hydraulic full variable gas distribution actuator 23 is arranged in cylinder head by a big circle countersunk head screwed hole 6；The center of lower cover 5 is also provided with
Circular hole, Circularhole diameter is identical with the diameter of damper piston 10, and sealing ring is provided with circular hole and the junction of damper piston 10.
It is preferred that, described high pressure hydraulic fluid port 3 connects with solenoid directional control valve 22, lift control port 8 and lift control valve 16
Connect, buffering of taking a seat hydraulic fluid port 9 connects with cushioning control valve 15, and low pressure hydraulic fluid port 13 is connected with low pressure oil rail.
It is preferred that, described solenoid directional control valve 22 is two-bit triplet reversal valve.
For one kind electro-hydraulic full variable valve gear and control method, electro-hydraulic full variable gas distribution actuator 23 starts in multi-cylinder
When being worked in machine, two symmetrical hydraulic fluid ports are provided with A hydraulic cavities and are directly connected to adjacent electro-hydraulic full variable gas distribution execution
In the A hydraulic cavities of device 23, the hydraulic fluid port of end takes back low-pressure reservoir 17.
The invention discloses one kind electro-hydraulic full variable valve gear and control method, its control method implements step
Including：
(1) cylinder valve is closed, and cushioning control valve, lift control valve and solenoid directional control valve are in power failure state, electro-hydraulic complete
A, B, C, D, E hydraulic cavities of variable gas distribution actuator are in low-pressure state；
(2) it is powered to solenoid directional control valve, high pressure liquid force feed is poured into by high pressure hydraulic fluid port into D hydraulic cavities, A, B, C, E hydraulic pressure
Chamber is in low-pressure state, in the presence of hydraulic coupling, and main piston promotes air valve to move down, and air valve is opened；
(3) during air valve is opened, the volume of C hydraulic cavities constantly increases, and low-pressure hydraulic oil is by buffering low pressure hydraulic fluid port
Poured into C hydraulic cavities；
(4) when air valve is close to maximum lift, lift control valve is powered, and lift control port is closed, hydraulic pressure in E hydraulic cavities
Oil pressure is raised, and poised state is under the elastic force effect of main piston hydraulic coupling and spring for valve in C, D, E hydraulic cavities；
(5) when air valve reaches maximum lift, air valve enters the maximum lift duration；
(6) hydraulic fluid pressure step-down in solenoid directional control valve dead electricity, D hydraulic cavities, lift control valve dead electricity, each cavity pressure changes
Become, main piston spring-loaded is moved upwards, and air valve starts to take a seat；
(7) cushioning control valve obtains electric, and buffering of taking a seat hydraulic fluid port is closed, and the hydraulic oil in C hydraulic cavities passes through cylinder body restriction stream
The damper piston entered in B hydraulic cavities, B hydraulic cavities is moved upwards in the presence of hydraulic coupling with buffer spring, B hydraulic cavities and C liquid
The hydraulic fluid pressure in chamber is pressed to rise, main piston is increased by downward hydraulic coupling, the speed moved upwards reduces, that is, gas
The speed that valve is taken a seat reduces；
(8) air valve is taken a seat completely, cushioning control valve dead electricity, and B hydraulic cavities decline with the pressure in C hydraulic cavities, damper piston
Move downward under spring force, be that buffering is prepared next time.
It is preferred that, hydraulic oil is full of in described A hydraulic cavities, and hydraulic oil is in low-pressure state all the time.
The beneficial effects of the present invention are：
This electro-hydraulic full variable valve gear disclosed in this invention is simple in construction, and difficulty of processing is small, easy to assembly；
This electro-hydraulic full variable valve gear and control method disclosed in this invention are not only suitable for diesel engine, are applied to again
Gasoline engine, universal strong；
This electro-hydraulic full variable valve gear and control method disclosed in this invention can make engine air valve in full work
Under condition, realize the soft readjustment of valve lift and phase and air valve realizes continuous variable in the duration is opened；
All the time low pressure oil, Neng Gou are full of in this electro-hydraulic full variable valve gear disclosed in this invention in A hydraulic cavities
Damper piston is lubricated during electro-hydraulic full variable gas distribution actuator work, reduces impact, so as to increase the service life of device.
This electro-hydraulic full variable valve gear disclosed in this invention can be controlled using the buffer spring 12 in A hydraulic cavities
The size of hydraulic coupling in B hydraulic cavities, takes a seat punching so as to so that air valve effectively reduces seating velocity in the stage of taking a seat, reduce air valve
Hit, reduce the vibration noise of engine.
Brief description of the drawings
Fig. 1 is the structural representation under electro-hydraulic full variable gas distribution actuator original state in the present invention；
Fig. 2 is the structural representation of electro-hydraulic full variable gas distribution actuator upper cover plate in the present invention；
Fig. 3 is the structural representation of electro-hydraulic full variable gas distribution actuator lower cover in the present invention；
Fig. 4 is the systematic schematic diagram of electro-hydraulic full variable valve gear in the present invention；
Fig. 5 in the present invention under electro-hydraulic full variable gas distribution actuator maximum lift state each component position view；
Fig. 6 takes a seat the position view of each component under buffer status for electro-hydraulic full variable gas distribution actuator in the present invention；
Fig. 7 is the control signal schematic diagram of electronic control system in the present invention.
Embodiment
The present invention is described further below in conjunction with the accompanying drawings.
Embodiment 1
The present invention disclose one kind electro-hydraulic full variable valve gear and control method, the specific implementation of its control method and
Principle is as follows：
(1) Fig. 4 is combined, cylinder valve is closed, and cushioning control valve, lift control valve and solenoid directional control valve are in dead electricity shape
State, A, B, C, D, E hydraulic cavities of electro-hydraulic full variable gas distribution actuator are in low-pressure state, wherein, hydraulic pressure is full of in A hydraulic cavities
Oil, and hydraulic oil is in low-pressure state all the time；
(2) it is powered to solenoid directional control valve, high pressure liquid force feed is poured into by high pressure hydraulic fluid port into D hydraulic cavities, A, B, C, E hydraulic pressure
Chamber is in low-pressure state, in the presence of hydraulic coupling, and main piston promotes air valve to move down, and air valve is opened；
(3) during air valve is opened, the volume of C hydraulic cavities constantly increases, and low-pressure hydraulic oil is by buffering low pressure hydraulic fluid port
Poured into C hydraulic cavities；
(4) when air valve is close to maximum lift, lift control valve is powered, as shown in Figure 7；Lift control port is closed, E liquid
The rise of intracavitary hydraulic fluid pressure is pressed, is under the elastic force effect of main piston hydraulic coupling and spring for valve in C, D, E hydraulic cavities
Poised state；
(5) Fig. 5 is combined, when air valve reaches maximum lift, air valve enters the maximum lift duration；
(6) hydraulic fluid pressure step-down in solenoid directional control valve dead electricity, D hydraulic cavities, lift control valve dead electricity, each cavity pressure changes
Become, main piston spring-loaded is moved upwards, and air valve starts to take a seat；Wherein, the dead electricity of lift control valve and solenoid directional control valve
Interval time is very short, so it is possible to prevente effectively from take a seat start when caused because main piston upper cavity pressure is excessive air valve again to
Lower motion；
(7) cushioning control valve obtains electric, and buffering of taking a seat hydraulic fluid port is closed, and the hydraulic oil in C hydraulic cavities passes through cylinder body restriction stream
The damper piston entered in B hydraulic cavities, B hydraulic cavities is moved upwards in the presence of hydraulic coupling with buffer spring, B hydraulic cavities and C liquid
The hydraulic fluid pressure in chamber is pressed to rise, main piston is increased by downward hydraulic coupling, the speed moved upwards reduces, that is, gas
The speed that valve is taken a seat reduces, and the state of now electro-hydraulic full variable gas distribution actuator is as shown in Figure 6；
(8) air valve is taken a seat completely, cushioning control valve dead electricity, and B hydraulic cavities decline with the pressure in C hydraulic cavities, damper piston
Move downward under spring force, be that buffering is prepared next time.
During the entire process of electro-hydraulic full variable valve gear running, by change solenoid directional control valve electric phase, just
The phase of air valve unlatching can be changed；Change lift control valve obtains electric phase, it is possible to change the maximum lift of air valve；Change
The dead electricity phase of solenoid directional control valve and lift control valve, it is possible to change the duration of air valve unlatching；By changing cushioning control
Valve electric phase, it is possible to indirectly change air valve seating velocity.
With reference to Fig. 4, the electro-hydraulic full variable valve gear of one kind disclosed by the invention, including the control of cushioning control valve 15, lift
It is valve 16, low-pressure reservoir 17, filter 18, hydraulic motor 19, accumulator 20, overflow valve 21, solenoid directional control valve 22, electro-hydraulic complete variable
The appurtenances such as distribution actuator 23, electronic control system and oil pipe；
Electro-hydraulic full variable gas distribution actuator 23 includes hydraulic fluid port, cushioning control valve 15, lift control valve 16 and solenoid directional control valve
22 are connected by oil pipe with hydraulic fluid port respectively；Accumulator 20, hydraulic motor 19 and mistake are connected with turn after solenoid directional control valve 22
Filter 18, is eventually connected to low-pressure reservoir 17；Solenoid directional control valve 22 is directly connected to low-pressure reservoir by another pipeline simultaneously
17, it is connected by overflow valve 21 with accumulator 20 on pipe line；Electronic control system is connected respectively to buffering control by wire
On valve 15 processed, lift control valve 16 and solenoid directional control valve 22, for control the unlatching of each valve and closing time and unlatching or
The duration of closure, so as to change the pressure change of hydraulic oil in the hydraulic cavities of B, C, D, E tetra-, so as to control the fortune of main piston 4
It is dynamic, and then the motion of engine air valve is controlled, realize the soft readjustment of valve lift and phase and realize company opening the duration
Continuous variable purpose.
With reference to Fig. 1, electro-hydraulic full variable gas distribution actuator 23 includes cylinder body throttle orifice 2, high pressure hydraulic fluid port 3, main piston 4, lower cover
Plate 5, lift control port 8, buffering of taking a seat hydraulic fluid port 9, damper piston 10, cylinder body 11, buffer spring 12, low pressure hydraulic fluid port 13 and upper lid
Plate 14；
Upper cover plate 14 is located at the upper and lower ends sealed cylinder block 11 of cylinder body 11, main piston 4 and damper piston with lower cover 5 respectively
10 will be divided into the top of damper piston 10 in five hydraulic cavities of A, B, C, D, E, A hydraulic cavities inside cylinder body 11 is provided with low pressure hydraulic fluid port 13, C
It is provided with cylinder body 11 where hydraulic cavities at buffering hydraulic fluid port 9 of taking a seat, the cylinder body 11 where D hydraulic cavities and is provided with high pressure hydraulic fluid port 3, E liquid
Lift control port 8 is provided with cylinder body 11 where pressure chamber, the rear end of main piston 4 is connected with cylinder valve and spring for valve.
Two hydraulic cavities of A, B are located at cylinder body top, and damper piston 10 is located between two hydraulic cavities of A, B, pacifies in A hydraulic cavities
Equipped with buffer spring 12, the upper end of buffer spring 12 is fixed on upper cover plate 14, and lower end is fixed on damper piston 10；Cylinder body 11
On have a dividing plate, the hydraulic cavities of B, C two are separated, have a cylinder body throttle orifice 2 on dividing plate, used in taking a seat buffering course in air valve,
So that the pressure of the cavity of resorption of damper piston 12 rises rapidly；Main piston 4 will be divided into tri- hydraulic cavities of C, D, E below dividing plate, in office
In the case of what, main piston 4 will not block hydraulic oil port.
Cylinder body 11 is up-narrow and down-wide convex structure, and structure up and down is cylinder or cube structure；With reference to Fig. 2, upper lid
Plate 14 is uniformly distributed along the circumference multiple countersunk head screwed holes 1, and upper cover plate 14 is arranged on cylinder body 11 by bolt by countersunk head screw thread mouth 1, on
Cover plate 14 is provided with spring base towards the side of A hydraulic cavities, for installing buffer spring 12；
With reference to Fig. 3, lower cover 5 is uniformly distributed along the circumference two circle countersunk head screwed holes, and bolt passes through the small circle countersunk head screw thread of diameter
Lower cover 5 is arranged on cylinder body by hole 7, by the big circle countersunk head screwed hole 6 of diameter by electro-hydraulic full variable gas distribution actuator 23
In cylinder head；The center of lower cover 5 is also provided with circular hole, and Circularhole diameter is identical with the diameter of damper piston 10, circular hole with
The junction of damper piston 10 is provided with sealing ring.
With reference to Fig. 1 and Fig. 4, high pressure hydraulic fluid port 3 connects with solenoid directional control valve 22, lift control port 8 and lift control valve 16
Connect, buffering of taking a seat hydraulic fluid port 9 connects with cushioning control valve 15, and low pressure hydraulic fluid port 13 is connected with low pressure oil rail.
For the electro-hydraulic full variable valve gear of one kind, electro-hydraulic full variable gas distribution actuator 23 works in multicylinder engine
When, the A liquid that two symmetrical hydraulic fluid ports are directly connected to adjacent electro-hydraulic full variable gas distribution actuator 23 is provided with A hydraulic cavities
Press in chamber, the hydraulic fluid port of end takes back low-pressure reservoir 17.
Embodiment 2
With reference to Fig. 4, the electro-hydraulic full variable valve gear of one kind disclosed in this invention includes electro-hydraulic full variable gas distribution actuator
23rd, solenoid directional control valve 22, lift control valve 16, cushioning control valve 15, low-pressure reservoir 17, filter 18, hydraulic motor 19, accumulation of energy
The appurtenances such as device 20, overflow valve 21 and oil pipe and the part of electromagnetic valve controlling system three.
The present invention includes a kind of electro-hydraulic full variable gas distribution actuator, it is characterized in that：Including five chambers of A, B, C, D, E, wherein A
The hydraulic oil port 13 that hydraulic oil in chamber is in low-pressure state, A chambers all the time is connected with low pressure oil rail.Remaining four chamber hydraulic oil
Pressure can change with the motion conditions of piston, by controlling the pressure of hydraulic oil in this four chamber to control main piston 4
Motion, and then the motion of engine air valve is controlled, realize the soft readjustment of engine air valve.
There is a restriction 2 obtained by optimization on cylinder body 11, have a hydraulic fluid port 9 in C chambers, closed when hydraulic fluid port 9 is in
During closed state, restriction 2 is started working, and when hydraulic fluid port 9 is in opening, restriction 2 is substantially without traffic flow, i.e. A chambers
Interior spring 12 is in free state.
There is a piston 10 between A chambers and B chambers, the chamber of A, B two is separated, when the pressure rise of B intracavitary hydraulic oil
When, by promoting in-migration compression spring 12 on piston 10.Reducing piston 4 in C, D, E chamber is by C and D, and D and E chambers are separated,
There is the hydraulic oil port of the outside oil circuit of connection in C, D, E chamber.Under any circumstance, piston 4 will not block hydraulic oil port.
On the upper cover plate 14 of actuator, be uniformly distributed along the circumference 4 or 6 countersunk head screwed holes 1, in order to by upper lid
Plate 14 is connected with cylinder body 11.The opposite side of counter sink 1 on upper cover plate 14, there is the spring base for placing spring.
On the lower cover 5 of actuator, the heart, has a diameter and piston diameter identical hole, on hole, has wherein
Sealing ring for sealing piston.In addition, on lower cover 5, also uniform two circles countersunk head screwed hole, the wherein small circle 7 of diameter
For being connected with actuator cylinder body 11, the big circle 6 of diameter is then used for actuator being fixed in cylinder head.
With reference to Fig. 1, Fig. 4 to Fig. 7, described electro-hydraulic full variable gas distribution actuator includes upper cover plate screw 1, cylinder body throttle orifice
2nd, high pressure hydraulic fluid port 3, main piston 4, lower cover 5, actuator fixing bolt 6, lower cover fixing screws 7, lift control port 8, fall
Seat buffering hydraulic fluid port 9, damper piston 10, cylinder body 11, buffer spring 12, low pressure hydraulic fluid port 13, upper cover plate 14.
With reference to Fig. 4, high pressure hydraulic fluid port 3 connects with two-position three-way valve 22.Lift control port 8 connects with lift control valve 16.
Buffering of taking a seat hydraulic fluid port 9 connects with cushioning control valve 15.In the interstitial hole of lower cover 5, sealing ring is installed, for sealing E chambers.
Engine air valve is in the closed state, two-position three-way valve 22, lift control valve 16 and cushioning control valve 15 are all located
In power failure state, now, A, B, C, D, E chamber of full variable gas distribution actuator are in low-pressure state；
When two-bit triplet magnetic valve 22 obtains electric, when lift control valve 16 is with cushioning control 15 dead electricity of valve, start in D chambers
Full of hydraulic oil, A, B, C, E are in low-pressure state, now in the presence of hydraulic coupling, and main piston 5 starts to promote air valve to move down,
Air valve is opened.During air valve is opened, the volume increase of C chambers is now main to provide low pressure by buffering low pressure hydraulic fluid port 9 of taking a seat
Oil, throttle orifice flows without liquid substantially at this moment；
When air valve is close to maximum lift, lift control valve 16 obtains electric, as shown in fig. 7, the now hydraulic oil of E intracavitary
Mouth 8 is begun to shut off, the rise of E intracavitary hydraulic fluid pressure, and main piston is in C chambers hydraulic coupling, D chambers hydraulic coupling, E chambers hydraulic coupling and air valve
The elastic force effect of spring is lower to be in poised state, and air valve reaches maximum lift, and air valve enters the maximum lift duration, now performed
The state of device is as shown in Figure 5；
When air valve starts to take a seat, the first dead electricity of two-position three-way valve 22, now in D intracavitary, hydraulic oil is in low pressure shape
State, under spring force, air valve start to take a seat, within the of short duration time after the dead electricity of two-position three-way valve 22, lift control
The also dead electricity of valve 16, now main piston start upward motion under spring force, air valve is taken a seat.As shown in fig. 7, being in the time
30 or so, the first dead electricity of two-position three-way valve 22, the dead electricity again of lift control valve 16；
When air valve is close to when taking a seat, in order to reduce the seating velocity of air valve, cushioning control valve 15 obtains electric, C intracavitary
Hydraulic oil port 9 is closed, the damper piston 10 that now hydraulic oil of C intracavitary can be entered in B chambers, B chambers by the restriction 2 in Fig. 1
Moved upwards in the presence of hydraulic coupling with buffer spring 12, as spring 12 is compressed, the pressure of B chambers and hydraulic oil in C chambers
Rise, cause the hydraulic coupling increase that C chambers are downward to main piston 4, speed that main piston 4 is moved upwards reduces, be i.e. air valve is taken a seat speed
Degree reduces, and now the state of actuator is as shown in Figure 6；
After air valve is taken a seat completely, the dead electricity of cushioning control valve 15, now, C and the pressure of B intracavitary decline, damper piston
10 under spring force, moves downward, and is that buffering prepares next time, now the state of actuator is as shown in Figure 1.
By change two-position three-way valve 22 electric phase, it is possible to change air valve unlatching phase；By changing lift
Control valve 16 electric phase, it is possible to change the maximum lift of air valve；By changing two-position three-way valve and lift control valve 16
Dead electricity phase, it is possible to change air valve unlatching duration；By change cushioning control valve 15 electric phase, it is possible to
Connect the seating velocity for changing air valve.
In multicylinder engine, two hydraulic fluid ports in A chambers are coupled with the A chambers of adjacent full variable gas distribution actuator, end
The hydraulic fluid port at end takes back low-pressure reservoir.
The preferred embodiments of the present invention are the foregoing is only, are not intended to limit the invention, for the skill of this area
For art personnel, the present invention can have various modifications and variations.Within the spirit and principles of the invention, that is made any repaiies
Change, equivalent substitution, improvement etc., should be included in the scope of the protection.
Claims (9)
1. a kind of electro-hydraulic full variable valve gear and control method, it is characterised in that：Controlled including cushioning control valve (15), lift
Valve (16), low-pressure reservoir (17), filter (18), hydraulic motor (19), accumulator (20), overflow valve (21), solenoid directional control valve
(22), the appurtenances such as electro-hydraulic full variable gas distribution actuator (23), electronic control system and oil pipe；
Electro-hydraulic full variable gas distribution actuator (23) includes hydraulic fluid port, cushioning control valve (15), lift control valve (16) and electromagnetic switch
Valve (22) is connected by oil pipe with hydraulic fluid port respectively；Accumulator (20), hydraulic pressure horse are connected with turn after solenoid directional control valve (22)
Up to (19) and filter (18), low-pressure reservoir (17) is eventually connected to；Solenoid directional control valve (22) is straight by another pipeline simultaneously
It is connected on low-pressure reservoir (17), pipe line and is connected by overflow valve (21) with accumulator (20) in succession；Electronic control system is led to
Wire is crossed to be connected respectively on cushioning control valve (15), lift control valve (16) and solenoid directional control valve (22).
2. one kind electro-hydraulic full variable valve gear and control method according to claim 1, it is characterised in that：Described electricity
The full variable gas distribution actuator (23) of liquid includes cylinder body throttle orifice (2), high pressure hydraulic fluid port (3), main piston (4), lower cover (5), lift
Control port (8), take a seat buffering hydraulic fluid port (9), damper piston (10), cylinder body (11), buffer spring (12), low pressure hydraulic fluid port (13) and
Upper cover plate (14)；
Upper cover plate (14) is located at the upper and lower ends sealed cylinder block (11) of cylinder body (11) with lower cover (5) respectively, and main piston (4) is with delaying
Rush piston (10) and will be divided into inside cylinder body (11) in five hydraulic cavities of A, B, C, D, E, A hydraulic cavities and be provided with above damper piston (10)
Low pressure hydraulic fluid port (13), cylinder body (11) place where C hydraulic cavities is provided with take a seat buffering hydraulic fluid port (9), the cylinder body (11) where D hydraulic cavities
Place is provided with high pressure hydraulic fluid port (3), and cylinder body (11) place where E hydraulic cavities is provided with lift control port (8), and main piston (4) rear end connects
It is connected to cylinder valve and spring for valve.
3. one kind electro-hydraulic full variable valve gear and control method according to claim 2, it is characterised in that：Described A,
Two hydraulic cavities of B are located at cylinder body top, and damper piston (10) is located between two hydraulic cavities of A, B, and buffering is provided with A hydraulic cavities
Spring (12), the upper end of buffer spring (12) is fixed on upper cover plate (14), and lower end is fixed on damper piston (10)；Cylinder body
(11) there is a dividing plate on, the hydraulic cavities of B, C two are separated, have a cylinder body throttle orifice (2) on dividing plate；Main piston (4) is by below dividing plate
Tri- hydraulic cavities of C, D, E are divided into, under any circumstance, main piston (4) will not block hydraulic oil port.
4. one kind electro-hydraulic full variable valve gear and control method according to claim 2, it is characterised in that：Described cylinder
Body (11) is up-narrow and down-wide convex structure, and structure up and down is cylinder or cube structure；Upper cover plate (14) is uniformly distributed along the circumference
Upper cover plate (14) is arranged on cylinder body (11) by multiple countersunk head screwed holes (1), bolt by countersunk head screw thread mouth (1), upper cover plate
(14) side towards A hydraulic cavities is provided with spring base, for installing buffer spring (12)；Lower cover (5) is uniformly distributed along the circumference two
Countersunk head screwed hole is enclosed, lower cover (5) is arranged on cylinder body by bolt by the small circle countersunk head screwed hole (7) of diameter, by straight
Electro-hydraulic full variable gas distribution actuator (23) is arranged in cylinder head by the big circle countersunk head screwed hole (6) in footpath；Lower cover (5) center
Place is also provided with circular hole, and Circularhole diameter is identical with damper piston (10) diameter, is provided with circular hole with damper piston (10) junction
Sealing ring.
5. one kind electro-hydraulic full variable valve gear and control method according to claim 1 or 2, it is characterised in that：It is described
High pressure hydraulic fluid port (3) connect with solenoid directional control valve (22), lift control port (8) connects with lift control valve (16), takes a seat slow
Rush hydraulic fluid port (9) with cushioning control valve (15) to connect, low pressure hydraulic fluid port (13) is connected with low pressure oil rail.
6. one kind electro-hydraulic full variable valve gear and control method according to claim 1, it is characterised in that：Described electricity
Magnetic reversal valve (22) is two-bit triplet reversal valve.
7. one kind electro-hydraulic full variable valve gear and control method according to claim 1, it is characterised in that：It is electro-hydraulic entirely
Two symmetrical hydraulic fluid ports are provided with when change distribution actuator (23) works in multicylinder engine, in A hydraulic cavities to be directly connected to respectively
Into the A hydraulic cavities of adjacent electro-hydraulic full variable gas distribution actuator (23), the hydraulic fluid port of end takes back low-pressure reservoir (17).
8. a kind of electro-hydraulic full variable valve gear and control method, it is characterised in that concrete implementation step includes：
(1) cylinder valve is closed, and cushioning control valve, lift control valve and solenoid directional control valve are in power failure state, electro-hydraulic complete variable
A, B, C, D, E hydraulic cavities of distribution actuator are in low-pressure state；
(2) it is powered to solenoid directional control valve, high pressure liquid force feed is poured into by high pressure hydraulic fluid port into D hydraulic cavities, at A, B, C, E hydraulic cavities
In low-pressure state, in the presence of hydraulic coupling, main piston promotes air valve to move down, and air valve is opened；
(3) during air valve is opened, the volume of C hydraulic cavities constantly increases, and low-pressure hydraulic oil is by buffering low pressure hydraulic fluid port to C liquid
Pressure intracavitary is poured into；
(4) when air valve is close to maximum lift, lift control valve is powered, and lift control port is closed, hydraulic oil pressure in E hydraulic cavities
Power is raised, and poised state is under the elastic force effect of main piston hydraulic coupling and spring for valve in C, D, E hydraulic cavities；
(5) when air valve reaches maximum lift, air valve enters the maximum lift duration；
(6) hydraulic fluid pressure step-down in solenoid directional control valve dead electricity, D hydraulic cavities, lift control valve dead electricity, each cavity pressure changes,
Main piston spring-loaded is moved upwards, and air valve starts to take a seat；
(7) cushioning control valve obtains electric, and buffering of taking a seat hydraulic fluid port is closed, and the hydraulic oil in C hydraulic cavities flows into B liquid by cylinder body restriction
The damper piston in chamber, B hydraulic cavities is pressed to be moved upwards in the presence of hydraulic coupling with buffer spring, in B hydraulic cavities and C hydraulic cavities
Hydraulic fluid pressure rise, main piston is increased by downward hydraulic coupling, and the speed moved upwards reduces, that is, air valve is taken a seat
Speed reduce；
(8) air valve is taken a seat completely, cushioning control valve dead electricity, and B hydraulic cavities decline with the pressure in C hydraulic cavities, and damper piston is in bullet
Moved downward in the presence of spring force, be that buffering is prepared next time.
9. one kind electro-hydraulic full variable valve gear and control method according to claim 8, it is characterised in that：Described A
Hydraulic oil is full of in hydraulic cavities, and hydraulic oil is in low-pressure state all the time.
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108590799A (en) * | 2018-03-30 | 2018-09-28 | 江苏大学 | A kind of Fully variable valve train of hydraulic-driven |
| CN110094244A (en) * | 2019-05-13 | 2019-08-06 | 哈尔滨工程大学 | The electro-hydraulic full variable gas distribution actuator of one kind and its control method |
| CN112412566A (en) * | 2020-11-05 | 2021-02-26 | 天津大学 | Control method of variable valve mechanism based on slide valve control |
| CN114135358A (en) * | 2021-11-24 | 2022-03-04 | 中船动力研究院有限公司 | Control driving device for valve mechanism and internal combustion engine |
| CN114233696A (en) * | 2020-09-09 | 2022-03-25 | 北京机械设备研究所 | Small-size pressure boost and pressurizer |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07259518A (en) * | 1994-03-25 | 1995-10-09 | Mitsubishi Motors Corp | Variable valve system of internal combustion engine |
| US20040055547A1 (en) * | 2001-09-07 | 2004-03-25 | Udo Diehl | Hydraulically controlled actuator for actuating a valve |
| CN1544800A (en) * | 2003-11-27 | 2004-11-10 | ����һ | Pressure differential style air valve variation control system |
| CN1959073A (en) * | 2006-11-01 | 2007-05-09 | 宁波华液机器制造有限公司 | Variable pneumatic door control system |
| CN101975098A (en) * | 2010-09-30 | 2011-02-16 | 哈尔滨工程大学 | Camless electrohydraulic variable valve timing system based on fuel medium |
| CN102305222A (en) * | 2011-08-24 | 2012-01-04 | 天津大学 | Electro-hydraulic variable valve device with energy accumulator buffer function and energy storage method thereof |
| CN103388502A (en) * | 2013-07-31 | 2013-11-13 | 哈尔滨工程大学 | Full changeable electro-hydraulic air valve driving device |
| CN103277163B (en) * | 2013-05-07 | 2015-06-24 | 宁波华液机器制造有限公司 | Variable-lift driver |
-
2017
- 2017-07-17 CN CN201710580553.2A patent/CN107327329B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07259518A (en) * | 1994-03-25 | 1995-10-09 | Mitsubishi Motors Corp | Variable valve system of internal combustion engine |
| US20040055547A1 (en) * | 2001-09-07 | 2004-03-25 | Udo Diehl | Hydraulically controlled actuator for actuating a valve |
| CN1544800A (en) * | 2003-11-27 | 2004-11-10 | ����һ | Pressure differential style air valve variation control system |
| CN1959073A (en) * | 2006-11-01 | 2007-05-09 | 宁波华液机器制造有限公司 | Variable pneumatic door control system |
| CN101975098A (en) * | 2010-09-30 | 2011-02-16 | 哈尔滨工程大学 | Camless electrohydraulic variable valve timing system based on fuel medium |
| CN102305222A (en) * | 2011-08-24 | 2012-01-04 | 天津大学 | Electro-hydraulic variable valve device with energy accumulator buffer function and energy storage method thereof |
| CN103277163B (en) * | 2013-05-07 | 2015-06-24 | 宁波华液机器制造有限公司 | Variable-lift driver |
| CN103388502A (en) * | 2013-07-31 | 2013-11-13 | 哈尔滨工程大学 | Full changeable electro-hydraulic air valve driving device |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108590799A (en) * | 2018-03-30 | 2018-09-28 | 江苏大学 | A kind of Fully variable valve train of hydraulic-driven |
| CN108590799B (en) * | 2018-03-30 | 2020-05-05 | 江苏大学 | Hydraulically-driven fully-variable valve actuating mechanism |
| CN110094244A (en) * | 2019-05-13 | 2019-08-06 | 哈尔滨工程大学 | The electro-hydraulic full variable gas distribution actuator of one kind and its control method |
| CN110094244B (en) * | 2019-05-13 | 2021-09-10 | 哈尔滨工程大学 | Electro-hydraulic fully-variable gas distribution actuator and control method thereof |
| CN114233696A (en) * | 2020-09-09 | 2022-03-25 | 北京机械设备研究所 | Small-size pressure boost and pressurizer |
| CN114233696B (en) * | 2020-09-09 | 2024-05-28 | 北京机械设备研究所 | Small-size pressure boost and pressurize device |
| CN112412566A (en) * | 2020-11-05 | 2021-02-26 | 天津大学 | Control method of variable valve mechanism based on slide valve control |
| CN114135358A (en) * | 2021-11-24 | 2022-03-04 | 中船动力研究院有限公司 | Control driving device for valve mechanism and internal combustion engine |
| CN114135358B (en) * | 2021-11-24 | 2022-08-26 | 中船动力研究院有限公司 | Control driving device for valve mechanism and internal combustion engine |
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