CN107327329B - The electro-hydraulic full variable valve gear of one kind and control method - Google Patents
The electro-hydraulic full variable valve gear of one kind and control method Download PDFInfo
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- CN107327329B CN107327329B CN201710580553.2A CN201710580553A CN107327329B CN 107327329 B CN107327329 B CN 107327329B CN 201710580553 A CN201710580553 A CN 201710580553A CN 107327329 B CN107327329 B CN 107327329B
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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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The invention discloses a kind of electro-hydraulic full variable valve gear and control methods, 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 five high pressure oil port, lift control port, cushioning control hydraulic fluid port, cylinder body restriction and A, B, C, D, E hydraulic cavities, by controlling the pressure of this 5 intracavitary hydraulic oil, the movement such as the unlatching of engine air valve is realized and takes a seat；The phase of engine air valve unlatching, lift can be changed by the power loss moment that obtains of change two-position three-way valve, lift control valve, cushioning control valve, the soft readjustment of valve lift and phase and the duration that air valve is opened are realized, to realize the complete variable of air valve movement.
Description
Technical field
The invention belongs to engine air valve technology fields, and in particular to the electro-hydraulic full variable valve gear of one kind and controlling party
Method.
Background technique
Along with being on the rise for World Environment Problems and international energy crisis, seriously threatened human society can
Sustainable development.With the high speed development of internal combustion engine industry, demand of the people to petroleum resources is growing day by day, therefrom bring ring
Border pollution and the problems such as energy shortage, also come one after another, what energy conservation and environmental protection already had to face as Development of I. C. Engine Industry
Two major issues.In order to can effectively solve both of these problems, countries in the world are harmful to the economy and control that improve engine
Emission request is higher and higher, 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 one after another, 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.Hair 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 intake and exhaust valves using mechanical cam mechanism, due to cam
Molded line is fixed, thus the trim analysis such as its valve stroke, valve timing are all fixed and invariable, and actuated by cams mode is adjusted
Can not achieve can be changed entirely, can not be adjusted in engine operation, be typically only capable to guarantee to optimize engine under a certain operating condition
Performance.
In order to better solve the above problem, there is researcher to propose Zona free, i.e. cancellation engine is matched
Camshaft and driven member in mechanism of qi structure, and valve is driven with electromagnetism, electro-hydraulic, electrical or other modes.Variable gas distribution technology
It has obtained widely promoting as a kind of higher technological means of cost performance, which mainly passes through the gazogene for improving engine
Structure come achieve the purpose that improve engine performance because valve actuating mechanism is directly related to the degree of perfection of engine combustion process,
Therefore there is important influence to the superiority and inferiority of its dynamic property, economy and emission performance.Research and develop at this stage without cam variable gas distribution
Mechanism has apparent distribution advantage compared to traditional valve actuating mechanism, but at these without in cam variable valve actuating mechanism, electromagnetism
Driving method is difficult to meet requirement of the high pressure admission to valve opening and closing frequency and lift, the electrically driven requirement for sealing simultaneously
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.
Summary of the invention
The purpose of the present invention is to provide the soft of a kind of restriction that can break through cam profile, realization valve lift and phase
Property adjust and air valve open the duration realize continuous variable electro-hydraulic full variable valve gear and control method.
The object of the present invention is achieved like this:
The invention discloses a kind of electro-hydraulic full variable valve gear and control methods, including cushioning control valve 15, lift control
Valve 16 processed, filter 18, hydraulic motor 19, accumulator 20, overflow valve 21, solenoid directional control valve 22, electro-hydraulic entirely may be used at low-pressure reservoir 17
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；It is connected with accumulator 20, hydraulic motor 19 and mistake after solenoid directional control valve 22 in turn
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 conducting wire
On valve 15 processed, lift control valve 16 and solenoid directional control valve 22.
Include for a kind of electro-hydraulic full variable valve gear and control method, the electro-hydraulic full variable gas distribution actuator 23
Cylinder body throttle orifice 2, high pressure oil port 3, main piston 4, lower cover plate 5, lift control port 8, take a seat buffer 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 and lower cover plate 5 are located at the upper and lower ends sealed cylinder block 11 of cylinder body 11, main piston 4 and damper piston
10 will be divided into five hydraulic cavities of A, B, C, D, E inside cylinder body 11, be provided with low pressure hydraulic fluid port 13 above damper piston 10 in A hydraulic cavities,
It is provided with to take a seat at cylinder body 11 where C hydraulic cavities and buffers hydraulic fluid port 9, high pressure oil port 3, E liquid are provided at the cylinder body 11 where D hydraulic cavities
It is provided with lift control port 8 at cylinder body 11 where pressure chamber, 4 rear end of main piston is connected with cylinder valve and spring for valve.
Preferably, two hydraulic cavities of described A, the 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 partition on cylinder body 11, two hydraulic cavities of B, C are separated, has a cylinder body throttle orifice 2 on partition；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.
Preferably, the cylinder body 11 is up-narrow and down-wide convex structure, and upper and lower structure is cylindrical body or cube structure；
Upper cover plate 14 is uniformly distributed along the circumference multiple countersunk head threaded holes 1, and upper cover plate 14 is mounted on cylinder body 11 by countersunk head threaded hole 1 by bolt
On, upper cover plate 14 is equipped with spring base towards the side of A hydraulic cavities, for installing buffer spring 12；Lower cover plate 5 is uniformly distributed along the circumference
Lower cover plate 5 is mounted on cylinder body by two circle countersunk head threaded holes, bolt by the small circle countersunk head threaded hole 7 of diameter, passes through diameter
Electro-hydraulic full variable gas distribution actuator 23 is mounted in cylinder head by a big circle countersunk head threaded hole 6；Lower cover plate is also provided at 5 center
Circular hole, Circularhole diameter is identical as 10 diameter of damper piston, is equipped with sealing ring in circular hole and 10 junction of damper piston.
Preferably, the high pressure oil port 3 connects with solenoid directional control valve 22, lift control port 8 and lift control valve 16
Connect, taking a seat buffers hydraulic fluid port 9 and connect with cushioning control valve 15, and low pressure hydraulic fluid port 13 is connected with low pressure oil rail.
Preferably, the solenoid directional control valve 22 is two-bit triplet reversal valve.
A kind of electro-hydraulic full variable valve gear and control method, electro-hydraulic full variable gas distribution actuator 23 are started in multi-cylinder
When working in machine, is opened in A hydraulic cavities and be directly connected to adjacent electro-hydraulic full variable gas distribution execution there are two symmetrical hydraulic fluid port
In the A hydraulic cavities of device 23, the hydraulic fluid port of end takes back low-pressure reservoir 17.
The invention discloses a kind of electro-hydraulic full variable valve gear and control method, the specific implementation steps of control method
Include:
(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 pressure oil is poured by high pressure oil port into D hydraulic cavities, A, B, C, E liquid
Pressure chamber is in low-pressure state, and under the action of hydraulic coupling, main piston pushes 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 passes through buffering low pressure hydraulic fluid port
It is 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 in E hydraulic cavities
Oil pressure increases, and main piston is in equilibrium state under the effect of the elastic force of 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) solenoid directional control valve power loss, hydraulic fluid pressure is lower in D hydraulic cavities, and lift control valve power loss, each cavity pressure changes
Become, main piston spring-loaded moves upwards, and air valve starts to take a seat；
(7) cushioning control valve obtains electric, takes a seat and buffers hydraulic fluid port closing, and the hydraulic oil in C hydraulic cavities passes through cylinder body restriction stream
Enter B hydraulic cavities, the damper piston in B hydraulic cavities moves upwards under the action of hydraulic coupling is 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, and 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 power loss, and the pressure in B hydraulic cavities and C hydraulic cavities declines, damper piston
It moves downward, prepares for buffering next time under spring force.
Preferably, hydraulic oil is full of in the A hydraulic cavities, and hydraulic oil is in low-pressure state always.
The beneficial effects of the present invention are:
This electro-hydraulic full variable valve gear structure disclosed in this invention is simple, 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, and are suitable for
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, realizes the soft readjustment of valve lift and phase and air valve realizes continuous variable in opening the duration；
Always 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, 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 is taken a seat punching so as to so that seating velocity is effectively reduced in the stage of taking a seat in air valve, reduce air valve
It hits, reduces the vibration noise of engine.
Detailed description of the invention
Fig. 1 is the structural schematic diagram in the present invention under electro-hydraulic full variable gas distribution actuator original state；
Fig. 2 is the structural schematic diagram of electro-hydraulic full variable gas distribution actuator upper cover plate in the present invention；
Fig. 3 is the structural schematic diagram of electro-hydraulic full variable gas distribution actuator lower cover plate in the present invention；
Fig. 4 is the systematic schematic diagram of electro-hydraulic full variable valve gear in the present invention；
Fig. 5 is the position view of each component under electro-hydraulic full variable gas distribution actuator maximum lift state in the present invention；
Fig. 6 is that electro-hydraulic full variable gas distribution actuator is taken a seat the position view of each component under buffer status in the present invention；
Fig. 7 is the control signal schematic representation of electronic control system in the present invention.
Specific embodiment
The present invention is described further with reference to the accompanying drawing.
Embodiment 1
The present invention discloses a kind of electro-hydraulic full variable valve gear and control method, the specific implementation of 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 power loss shape
A, B, C, D, E hydraulic cavities of state, electro-hydraulic full variable gas distribution actuator are in low-pressure state, wherein full of hydraulic in A hydraulic cavities
Oil, and hydraulic oil is in low-pressure state always；
(2) it is powered to solenoid directional control valve, high pressure liquid pressure oil is poured by high pressure oil port into D hydraulic cavities, A, B, C, E liquid
Pressure chamber is in low-pressure state, and under the action of hydraulic coupling, main piston pushes 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 passes through buffering low pressure hydraulic fluid port
It is 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
Intracavitary hydraulic fluid pressure is pressed to increase, main piston is under the effect of the elastic force of hydraulic coupling and spring for valve in C, D, E hydraulic cavities
Equilibrium state；
(5) Fig. 5 is combined, when air valve reaches maximum lift, air valve enters the maximum lift duration；
(6) solenoid directional control valve power loss, hydraulic fluid pressure is lower in D hydraulic cavities, and lift control valve power loss, each cavity pressure changes
Become, main piston spring-loaded moves upwards, and air valve starts to take a seat；Wherein, the power loss of lift control valve and solenoid directional control valve
Interval time is very short, in this way it is possible to prevente effectively from cause when taking a seat and starting since main piston upper cavity pressure is excessive air valve again to
Lower movement；
(7) cushioning control valve obtains electric, takes a seat and buffers hydraulic fluid port closing, and the hydraulic oil in C hydraulic cavities passes through cylinder body restriction stream
Enter B hydraulic cavities, the damper piston in B hydraulic cavities moves upwards under the action of hydraulic coupling is 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, and the speed moved upwards reduces, that is, gas
The speed that valve is taken a seat reduces, and the state of full variable gas distribution actuator electro-hydraulic at this time is as shown in Figure 6；
(8) air valve is taken a seat completely, cushioning control valve power loss, and the pressure in B hydraulic cavities and C hydraulic cavities declines, damper piston
It moves downward, prepares for buffering next time under spring force.
During the entire process of the running of electro-hydraulic full variable valve gear, electric phase is obtained by change solenoid directional control valve, just
It can change the phase of air valve unlatching；Change lift control valve obtains electric phase, so that it may change the maximum lift of air valve；Change
The power loss phase of solenoid directional control valve and lift control valve, so that it may change the duration of air valve unlatching；By changing cushioning control
Valve obtains electric phase, so that it may change the seating velocity of air valve indirectly.
In conjunction with 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；It is connected with accumulator 20, hydraulic motor 19 and mistake after solenoid directional control valve 22 in turn
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 conducting wire
On valve 15 processed, lift control valve 16 and solenoid directional control valve 22, for control each valve unlatching and closing time and unlatching or
The duration of closure, to change the pressure change of hydraulic oil in tetra- hydraulic cavities of B, C, D, E, to control the fortune of main piston 4
It is dynamic, and then control the movement of engine air valve, realize the soft readjustment of valve lift and phase and connect opening duration realization
Continue variable purpose.
In conjunction with Fig. 1, electro-hydraulic full variable gas distribution actuator 23 includes cylinder body throttle orifice 2, high pressure oil port 3, main piston 4, lower cover
Plate 5, lift control port 8, take a seat buffer hydraulic fluid port 9, damper piston 10, cylinder body 11, buffer spring 12, low pressure hydraulic fluid port 13 and on
Cover board 14；
Upper cover plate 14 and lower cover plate 5 are located at the upper and lower ends sealed cylinder block 11 of cylinder body 11, main piston 4 and damper piston
10 will be divided into five hydraulic cavities of A, B, C, D, E inside cylinder body 11, be provided with low pressure hydraulic fluid port 13 above damper piston 10 in A hydraulic cavities,
It is provided with to take a seat at cylinder body 11 where C hydraulic cavities and buffers hydraulic fluid port 9, high pressure oil port 3, E liquid are provided at the cylinder body 11 where D hydraulic cavities
It is provided with lift control port 8 at cylinder body 11 where pressure chamber, 4 rear end of main piston is connected with cylinder valve and spring for valve.
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, 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 partition, two hydraulic cavities of B, C are separated, have a cylinder body throttle orifice 2 on partition, for taking a seat in buffering course in air valve,
So that the pressure of 12 cavity of resorption of damper piston rises rapidly；Main piston 4 will be divided into tri- hydraulic cavities of C, D, E below partition, 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 upper and lower structure is cylindrical body or cube structure；In conjunction with Fig. 2, upper cover
Plate 14 is uniformly distributed along the circumference multiple countersunk head threaded holes 1, and upper cover plate 14 is mounted on cylinder body 11 by bolt by countersunk head threaded hole 1,
Upper cover plate 14 is equipped with spring base towards the side of A hydraulic cavities, for installing buffer spring 12；
In conjunction with Fig. 3, lower cover plate 5 is uniformly distributed along the circumference two circle countersunk head threaded holes, a bolt circle countersunk head screw thread small by diameter
Lower cover plate 5 is mounted on cylinder body by hole 7, by the big circle countersunk head threaded hole 6 of diameter by electro-hydraulic full variable gas distribution actuator 23
It is mounted in cylinder head；Circular hole is also provided at 5 center of lower cover plate, Circularhole diameter is identical as 10 diameter of damper piston, circular hole with
10 junction of damper piston is equipped with sealing ring.
In conjunction with Fig. 1 and Fig. 4, high pressure oil port 3 connects with solenoid directional control valve 22, lift control port 8 and lift control valve 16
Connect, taking a seat buffers hydraulic fluid port 9 and connect with cushioning control valve 15, and low pressure hydraulic fluid port 13 is connected with low pressure oil rail.
For a kind of electro-hydraulic full variable valve gear, electro-hydraulic full variable gas distribution actuator 23 works in multicylinder engine
When, open that there are two the A liquid that symmetrical hydraulic fluid port is directly connected to adjacent electro-hydraulic full variable gas distribution actuator 23 in A hydraulic cavities
It presses in chamber, the hydraulic fluid port of end takes back low-pressure reservoir 17.
Embodiment 2
In conjunction with Fig. 4, the electro-hydraulic full variable valve gear of one kind disclosed in this invention includes electro-hydraulic full variable gas distribution actuator
23, 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 electromagnetic valve controlling system three parts.
The present invention includes a kind of electro-hydraulic full variable gas distribution actuator, it is characterized in that: include five chambers of A, B, C, D, E, wherein A
Hydraulic oil in chamber is in low-pressure state always, and the hydraulic oil port 13 in A chamber is connected with low pressure oil rail.Remaining four chamber hydraulic oil
Pressure can change with the motion conditions of piston, control main piston 4 by controlling the pressure of hydraulic oil in this four chamber
Movement, and then the movement of engine air valve is controlled, realize the soft readjustment of engine air valve.
There is the restriction 2 obtained by optimization on cylinder body 11, have a hydraulic fluid port 9 in C chamber, is closed when hydraulic fluid port 9 is in
When closed state, restriction 2 is started to work, and when hydraulic fluid port 9 is in the open state, restriction 2 does not have traffic flow, i.e. A chamber substantially
Interior spring 12 is in free state.
There is a piston 10 between A chamber and B chamber, two chamber of A, B is separated, when the pressure rise of the intracavitary hydraulic oil of B
When, by pushing in-migration compressed spring 12 on piston 10.C, the variable diameter piston 4 in D, E chamber separates C and D, D with E chamber,
There is the hydraulic oil port for connecting external oil circuit 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 threaded holes 1, in order to by upper cover
Plate 14 is connected with cylinder body 11.There is the spring base for placing spring in the other side of counter sink 1 on upper cover plate 14.
On the lower cover plate 5 of actuator, in its center, there is diameter hole identical with piston diameter to have on hole
Sealing ring for sealing piston.In addition, on lower cover plate 5, also uniformly distributed two circle countersunk head threaded hole, the wherein small circle 7 of diameter
For connecting with actuator cylinder body 11, the big circle 6 of diameter is then used to for actuator being fixed in cylinder head.
In conjunction with Fig. 1, Fig. 4 to Fig. 7, the electro-hydraulic full variable gas distribution actuator includes upper cover plate bolt 1, cylinder body throttle orifice
2, high pressure oil port 3, main piston 4, lower cover plate 5, actuator fixing bolt 6, lower cover plate 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.
In conjunction with Fig. 4, high pressure oil port 3 connects with two-position three-way valve 22.Lift control port 8 connects with lift control valve 16.
It takes a seat and buffers hydraulic fluid port 9 and connect with cushioning control valve 15.In the interstitial hole of lower cover plate 5, sealing ring is installed, for sealing E
Chamber.
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, at this point, A, B, C, D, E chamber of full variable gas distribution actuator are in low-pressure state；
When two-bit triplet solenoid valve 22 obtains electric lift control valve 16 with 15 power loss of cushioning control valve, start in D chamber
Full of high pressure oil, A, B, C, E are in low-pressure state, and at this time under the action of hydraulic coupling, main piston 5 starts that air valve is pushed to move down,
Air valve is opened.During air valve is opened, the volume of C chamber increases, main at this time to buffer the offer low pressure of low pressure hydraulic fluid port 9 by taking a seat
Oil, throttle orifice are flowed without liquid substantially at this moment；
When air valve is close to maximum lift, lift control valve 16 it is electric, as shown in fig. 7, E intracavitary hydraulic oil at this time
Mouth 8 is begun to shut off, and the intracavitary hydraulic fluid pressure of E increases, and main piston is in C chamber hydraulic coupling, D chamber hydraulic coupling, E chamber hydraulic coupling and gas
The elastic force effect of valve spring is lower to be in equilibrium state, and air valve reaches maximum lift, and air valve enters the maximum lift duration, holds at this time
The state of row device is as shown in Figure 5；
When air valve starts to take a seat, the first power loss of two-position three-way valve 22, intracavitary in D at this time, 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 22 power loss of two-position three-way valve, lift control
The also power loss of valve 16, main piston starts to move upwards under spring force at this time, and air valve is taken a seat.As shown in fig. 7, in the time
It is 30 or so, the first power loss of two-position three-way valve 22, the power loss again of lift control valve 16；
When air valve, which approaches, takes a seat, in order to reduce the seating velocity of air valve, cushioning control valve 15 must be electric, and C is intracavitary
Hydraulic oil port 9 is closed, and C intracavitary hydraulic oil can enter B chamber, the damper piston 10 in B chamber by the restriction 2 in Fig. 1 at this time
It is moved upwards under the action of hydraulic coupling is with buffer spring 12, as spring 12 is compressed, the pressure of hydraulic oil in B chamber and C chamber
Rise, the C chamber hydraulic coupling downward to main piston 4 is caused to increase, the speed that main piston 4 moves upwards reduces, i.e. air valve is taken a seat speed
Degree reduces, and the state of actuator is as shown in Figure 6 at this time；
After air valve is taken a seat completely, 15 power loss of cushioning control valve, at this point, C and B intracavitary pressure declines, damper piston
10 under spring force, moves downward, and prepares for buffering next time, the state of actuator is as shown in Figure 1 at this time.
Electric phase is obtained by change two-position three-way valve 22, so that it may change the phase of air valve unlatching；By changing lift
Control valve 16 obtains electric phase, so that it may change the maximum lift of air valve；By changing two-position three-way valve and lift control valve 16
Power loss phase, so that it may change air valve unlatching duration；Electric phase is obtained by change cushioning control valve 15, so that it may
Connect the seating velocity for changing air valve.
In multicylinder engine, two hydraulic fluid ports in A chamber are coupled in the A chamber of adjacent full variable gas distribution actuator, end
The hydraulic fluid port at end takes back low-pressure reservoir.
The foregoing is only a preferred embodiment of the present invention, is not intended to restrict the invention, for the skill of this field
For art personnel, the invention may be variously modified and varied.All within the spirits and principles of the present invention, made any to repair
Change, equivalent replacement, improvement etc., should all be included in the protection scope of the present invention.
Claims (1)
1. a kind of electro-hydraulic full variable valve gear, it is characterised in that: including cushioning control valve (15), lift control valve (16), low
It is pressure oil case (17), filter (18), hydraulic motor (19), accumulator (20), overflow valve (21), solenoid directional control valve (22), 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；It is connected with accumulator (20), hydraulic horse after solenoid directional control valve (22) in turn
Up to (19) and filter (18), it is eventually connected to low-pressure reservoir (17)；Solenoid directional control valve (22) is straight by another pipeline simultaneously
It is connected to low-pressure reservoir (17), is connected by overflow valve (21) with accumulator (20) on pipe line in succession；Electronic control system is logical
It crosses conducting wire and is connected respectively to cushioning control valve (15), on lift control valve (16) and solenoid directional control valve (22)；
The electro-hydraulic full variable gas distribution actuator (23) include cylinder body throttle orifice (2), high pressure oil port (3), main piston (4), under
Cover board (5), lift control port (8), taking a seat buffers hydraulic fluid port (9), damper piston (10), cylinder body (11), buffer spring (12), low
Press oil port (13) and upper cover plate (14)；
Upper cover plate (14) and lower cover plate (5) are located at the upper and lower ends sealed cylinder block (11) of cylinder body (11), main piston (4) and slow
Five hydraulic cavities of A, B, C, D, E will be divided into inside cylinder body (11) by rushing piston (10), is provided with above damper piston (10) in A hydraulic cavities
Low pressure hydraulic fluid port (13), is provided with to take a seat at the cylinder body (11) where C hydraulic cavities and buffers hydraulic fluid port (9), the cylinder body (11) where D hydraulic cavities
Place is provided with high pressure oil port (3), is provided with lift control port (8) at the cylinder body (11) where E hydraulic cavities, and main piston (4) rear end connects
It is connected to cylinder valve and spring for valve；
Described 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, A hydraulic cavities
In be 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) on；Cylinder body has a partition on (11), and two hydraulic cavities of B, C are separated, and has a cylinder body throttle orifice (2) on partition；Main piston (4)
Tri- hydraulic cavities of C, D, E will be divided into below partition, under any circumstance, main piston (4) will not block hydraulic oil port；
The cylinder body (11) is up-narrow and down-wide convex structure, and upper and lower structure is cylindrical body or cube structure；Upper cover plate
(14) be uniformly distributed along the circumference multiple countersunk head threaded holes (1), and upper cover plate (14) is mounted on cylinder body by countersunk head threaded hole (1) by bolt
(11) on, upper cover plate (14) is equipped with spring base towards the side of A hydraulic cavities, for installing buffer spring (12)；Lower cover plate (5)
Be uniformly distributed along the circumference two circle countersunk head threaded holes, and lower cover plate (5) is mounted on cylinder by small circle countersunk head threaded hole (7) of diameter by bolt
On body, electro-hydraulic full variable gas distribution actuator (23) is mounted in cylinder head by big circle countersunk head threaded hole (6) of diameter；Under
It is also provided with circular hole at cover board (5) center, Circularhole diameter is identical as damper piston (10) diameter, connects in circular hole and damper piston (10)
The place of connecing is equipped with sealing ring；
The high pressure oil port (3) connects with solenoid directional control valve (22), lift control port (8) and lift control valve (16) phase
It connects, taking a seat buffers hydraulic fluid port (9) and connect with cushioning control valve (15), and low pressure hydraulic fluid port (13) is connected with low pressure oil rail；
The solenoid directional control valve (22) is two-bit triplet reversal valve；
When electro-hydraulic full variable gas distribution actuator (23) works in multicylinder engine, opened in A hydraulic cavities there are two symmetrical hydraulic fluid port
It is directly connected in the A hydraulic cavities of adjacent electro-hydraulic full variable gas distribution actuator (23), the hydraulic fluid port of end takes back low pressure oil
Case (17).
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108590799B (en) * | 2018-03-30 | 2020-05-05 | 江苏大学 | Hydraulically-driven fully-variable valve actuating mechanism |
| 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 |
| CN114233696B (en) * | 2020-09-09 | 2024-05-28 | 北京机械设备研究所 | Small-size pressure boost and pressurize device |
| CN112412566B (en) * | 2020-11-05 | 2022-03-29 | 天津大学 | Control method of variable valve mechanism based on slide valve control |
| 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 |
Citations (7)
| 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 |
| 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 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10143959A1 (en) * | 2001-09-07 | 2003-03-27 | Bosch Gmbh Robert | Hydraulically controled actuator for valve, especially gas replacement valve in combustion engine, has control piston with area of working surface(s) changing along piston displacement path |
-
2017
- 2017-07-17 CN CN201710580553.2A patent/CN107327329B/en active Active
Patent Citations (7)
| 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 |
| 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 |
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