CN110094244A - The electro-hydraulic full variable gas distribution actuator of one kind and its control method - Google Patents
The electro-hydraulic full variable gas distribution actuator of one kind and its control method Download PDFInfo
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- CN110094244A CN110094244A CN201910393529.7A CN201910393529A CN110094244A CN 110094244 A CN110094244 A CN 110094244A CN 201910393529 A CN201910393529 A CN 201910393529A CN 110094244 A CN110094244 A CN 110094244A
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- oil pocket
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- valve
- low pressure
- piston rod
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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
- F01L9/10—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
- 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 purpose of the present invention is to provide a kind of electro-hydraulic full variable gas distribution actuator and its control methods, including hydraulic piston, hydraulic system；Hydraulic piston includes upper housing, lower plate, piston rod, upper housing is fixed on lower plate, the upper column oil pocket communicated, lower column oil pocket are set in upper housing, piston rod is mounted in lower column oil pocket, the lower end of piston rod is extend out to outside lower plate, and it is in contact always with air valve valve stem top, high pressure oil port and the first low pressure hydraulic fluid port and the second low pressure hydraulic fluid port are opened up in upper housing, first low pressure hydraulic fluid port is connected to fuel tank by first switch valve, second low pressure hydraulic fluid port is connected to fuel tank, and high pressure oil port is connected to hydraulic system.The more original actuator of the present invention is smaller compared to its volume, structure obtains greatly simplified while reducing difficulty of processing, can be realized the real-time closed-loop control of trim analysis, greatly improves the reliability of system, have very high practical value.
Description
Technical field
The present invention relates to a kind of engines, specifically engine valve actuating mechanism.
Background technique
The difference of the more traditional cam air distribution system of full variable gas distribution system is that it is possible to the needs according to full working scope to each
Item trim analysis is flexibly controlled, and full variable gas distribution system has very big development space in terms of promoting engine efficiency,
Promotion simultaneously for engine economy is highly beneficial.Full variable gas distribution system sends out more strokes more than novel four stroke
Motivation is essential, is a main trend of alternate-engine development.
Wherein electro-hydraulic full variable gas distribution system is a kind of structure type being more easily achieved, and the height for having both electric-control system can
The characteristics of high-output power of control property, high response speed and hydraulic system, be the ideal form for realizing full variable gas distribution, electro-hydraulic
The core component of complete variable match system is electro-hydraulic full variable gas distribution executive device.
Summary of the invention
The purpose of the present invention is to provide the real-time closed-loop controls that can be realized trim analysis, and system reliability is greatly improved
The electro-hydraulic full variable gas distribution actuator of one kind and its control method.
The object of the present invention is achieved like this:
A kind of electro-hydraulic full variable gas distribution actuator of the invention, it is characterized in that: including hydraulic piston, hydraulic system；The liquid
Pressing piston includes upper housing, lower plate, piston rod, and upper housing is fixed on lower plate, and the upper column communicated is arranged in upper housing
Oil pocket, lower column oil pocket, the diameter of lower column oil pocket are greater than the diameter of upper column oil pocket, and piston rod is mounted on lower column oil pocket
In, the lower end of piston rod is extend out to outside lower plate, and is in contact always with air valve valve stem top, and the upper column oil pocket is
Actively can oil pocket, lower column oil pocket is low pressure oil pocket, and connection is opened up in upper housing actively can the high pressure oil port of oil pocket and first low
Press oil port and be connected to low pressure oil pocket the second low pressure hydraulic fluid port, the first low pressure hydraulic fluid port by first switch valve be connected to fuel tank, second
Low pressure hydraulic fluid port is connected to fuel tank, and high pressure oil port is connected to hydraulic system.
Electro-hydraulic full variable gas distribution actuator of the invention a kind of can also include:
1, the hydraulic system includes filter, hydraulic pump, accumulator, and hydraulic pump is connected to fuel tank, accumulation of energy by filter
Device connects hydraulic pump by flowline, and flowline is connected to high pressure oil port by second switch valve, and flowline is connected to by oil return pipe
Fuel tank installs overflow valve on oil return pipe.
2, buffering hydraulic fluid port is set in upper housing, and buffering hydraulic fluid port is connected to actively energy oil pocket by overflow hole, and buffering hydraulic fluid port passes through
Third switch valve is connected to fuel tank.
It 3, is clearance seal between the head of piston rod and its external upper enclosure inner wall.
A kind of electro-hydraulic full variable gas distribution control method of the invention, it is characterized in that: being executed using following electro-hydraulic full variable gas distribution
Device: including hydraulic piston, hydraulic system；The hydraulic piston includes upper housing, lower plate, piston rod, and upper housing is fixed on down
The upper column oil pocket communicated, lower column oil pocket are set on bottom plate, in upper housing, and the diameter of lower column oil pocket is greater than upper column oil pocket
Diameter, piston rod is mounted in lower column oil pocket, and the lower end of piston rod is extend out to outside lower plate, and with air valve valve rod top
Portion is in contact always, and the upper column oil pocket is main kinetic energy oil pocket, and lower column oil pocket is low pressure oil pocket, opens up connection in upper housing
Actively can the high pressure oil port of oil pocket with the first low pressure hydraulic fluid port and be connected to the second low pressure hydraulic fluid port of low pressure oil pocket, the first low pressure hydraulic fluid port
It is connected to fuel tank by first switch valve, the second low pressure hydraulic fluid port is connected to fuel tank, and high pressure oil port is connected to hydraulic system；
Original state lower air valve is in close state, and first switch valve, second switch valve, third switch valve all remain powered off
Closed state；
When air valve is opened, the energization of second switch valve switchs to open state, and rest switch valve remains off, high pressure oil warp
Second switch valve enters function of tonic chord oil pocket, passes through air valve valve rod greater than spring for valve when acting on active force downward on piston rod
When the upward active force of transmitting, air valve is moved downward, by the intracavitary hydraulic oil of low pressure oil through the second low pressure hydraulic fluid port during downlink
It is discharged in fuel tank；
The driving signal of second switch valve is the pwm signal with duty ratio, by changing the duty ratio of its driving signal,
It realizes control to the uninterrupted for flowing through second switch valve, and then controls piston rod and air valve opening speed；
Before air valve reaches setting lift, the power-off of second switch valve switchs to closed state, and rest switch valve still keeps closing
Closed state, function of tonic chord oil pocket is isolated from the outside in sealing state at this time, and function of tonic chord oil pocket keeps size constant, piston rod movement
Stop, making air valve also keep lift constant, until air valve close moment；
When closing air valve, second switch valve is remained off, and first switch valve is powered simultaneously with third switch valve to be switched to
Open state, function of tonic chord oil pocket is connected to low pressure oil way reduces the oil pressure in it, piston rod under the promotion of spring for valve on
Row, the duty ratio by changing first switch valve drive signal change the closing velocity of air valve；
Before air valve is taken a seat, first switch valve is powered off remains closing as second switch valve, in function of tonic chord oil pocket
Hydraulic oil low pressure oil way is entered by overflow hole, piston rod and air valve movement velocity are reduced by the aperture of overflow hole, realized
It takes a seat buffering.
Present invention has an advantage that
1, the hydraulic piston 1 in the electro-hydraulic full variable gas distribution executive device designed by the present invention only uses a function of tonic chord oil
Whole controls to air valve movement can be realized in chamber, and there are three major parts for hydraulic piston 1, thus structure obtains very big letter
Change.
2, since there is only a pair of of precision-fit surfaces between piston rod 4 and oil pocket wall surface in hydraulic piston 1, thus add
Work difficulty is lower easy to form.
3, the present invention uses real-time closed-loop control strategy, is conducive to the accuracy of raising system, by changing three electromagnetism
Phase relation between valve drive signal can arbitrarily change every trim analysis, realize the various air valve characteristics of motion, thus be
System has very high flexibility and accuracy.
4, the present invention uses three independent switch valves, controls each hydraulic oil port, it is whole to not only reduce system
The cost of body, and the response speed of system is improved, while the function opposite independent of each solenoid valve, it is advantageously implemented items
The independent control of trim analysis, is easy to the design of electric-control system.
Detailed description of the invention
Fig. 1 is hydraulic piston schematic diagram；
Fig. 2 is hydraulic piston top view；
Fig. 3 a is hydraulic piston bottom view, and Fig. 3 b is A-A view；
Fig. 4 is schematic structural view of the invention；
Fig. 5 is the schematic diagram of hydraulic piston original state；
Fig. 6 is the correspondence diagram of solenoid-driven signal and air valve molded line.
Specific embodiment
It illustrates with reference to the accompanying drawing and the present invention is described in more detail:
In conjunction with Fig. 1-6, the electro-hydraulic full variable gas distribution actuator of the present invention includes: hydraulic piston 1；Switch valve 13,14,15 forms
Control valve group；Overflow valve 16, accumulator 17, hydraulic pump 18, filter 19, fuel tank 20 and its attached pipe fitting form hydraulic
System.
Hydraulic piston 1 is made of three parts, is respectively as follows: upper housing 2, lower plate 5, piston rod 4, upper housing 2 and lower plate 5
Between be equipped with washer and prevent hydraulic oil from revealing, be attached from bottom to top by screw assemblies therebetween, piston rod 4 and lower plate
It is equipped with combined seal ring between 5, is provided with fixing screw hole on lower plate, is fixed from top to bottom by screw.
The column oil pocket for having upper and lower two diameters different inside upper housing 2, the two interconnect.Piston rod 4 is installed on directly
It is clearance seal between 4 side of piston rod and oil pocket wall surface at the biggish oil pocket of diameter, is two that boundary is connected to originally with piston rod 4
A column oil pocket is divided into upper and lower two different new oil pockets.Oil pocket above piston rod 4 is function of tonic chord oil pocket 11, the oil
Chamber is provided with high pressure oil port 3, low pressure hydraulic fluid port 12, buffering hydraulic fluid port 8, and high pressure oil port 8 is connect by solenoid valve 15 with pressure duct, low pressure
Hydraulic fluid port and buffering hydraulic fluid port pass through solenoid valve 14,13 respectively and connect with low pressure line；Low pressure oil pocket 7 below piston rod 4 directly connects
Logical low pressure line.
The oil pocket being relatively large in diameter in the diameter of piston rod 4 and upper housing 2 is identical, thus piston rod 4 can not move to diameter compared with
In small oil pocket region, it can be effectively prevented because piston rod 4 is driven by inertia, pour in small oil cavity upwards, block each oil
Mouth leads to thrashing in turn.
The hydraulic piston 1 that the present invention designs is installed on the surface of engine air valve and its associated component, and keeps air valve
Being overlapped between valve rod axis and 4 axis of piston rod.The bottom of piston rod 4 should be remained with air valve valve stem top simultaneously connects
Touching.When air valve is taken a seat completely, piston rod 4 should be located at initial position, and the original state of hydraulic piston is as shown in Fig. 5.
In hydraulic piston 1, this pair of of precision-fit surface of oil pocket wall only in piston rod 4 and upper housing 2 is easy to process
Molding.Hydraulic piston overall structure is simple, is easy to minimize.
The start-up time that air valve is controlled at the time of energization by changing solenoid valve 15, changes accounting for for 15 driving signal of solenoid valve
Empty ratio controls the conduction time length of solenoid valve 15 to control the opening speed of air valve, and the lift that can control air valve is big
Length that is small, being powered by control solenoid valve 13,14 with 15 power-off time interval of solenoid valve, just can control the maximum lift of air valve
Duration, the different moments taken a seat in air valve cut off 14 power supply of solenoid valve, thus it is possible to vary air valve is taken a seat the degree of buffering.Pass through
Change the phase relation between 13,14,15 driving signal of solenoid valve, the different air valve characteristics of motion, control strategy may be implemented
Simply it is easily achieved.
The overall work mode of electro-hydraulic full variable gas distribution executive device is that air valve is moved downward by pressure duct hydraulic oil
Driving, valve lift maintenance by keep function of tonic chord oil pocket 11 closed realization, air valve take a seat by spring for valve into
The buffering of taking a seat of row driving, air valve is realized by overflow hole 10.
The present invention is acquired air valve displacement information in real time by displacement sensor and feeds back to control using Closed-loop Control Strategy is implemented
System processed, control system is according to the control signal of displacement information adjusting solenoid valve 13,14,15, so that the air valve characteristics of motion be made to accord with
Close target.
Electro-hydraulic full variable gas distribution systematic schematic diagram is as shown in figure 4, solenoid valve 15 is mainly used for controlling the unlatching of air valve, electromagnetism
Valve 14 is mainly used for controlling the closing of air valve, and cushioning control valve 13 is for controlling air valve buffering.
System initial state lower air valve is in close state, and 4 state of piston rod of hydraulic piston 1 is as shown in Fig. 5 at this time,
Three solenoid valves are all normally closed type valve, and three solenoid valves all remain powered off closed state when initial.
Process when air valve is opened is that the energization of solenoid valve 15 switchs to open state, remaining solenoid valve remains off.It is high
Pressure oil enters function of tonic chord oil pocket 11 through solenoid valve 15, increases the oil pressure in the oil pocket rapidly, downward on piston rod 4 when acting on
Active force be greater than spring for valve transmitted by air valve valve rod upward active force when, air valve starts to move downward, downlink process
It is middle hydraulic oil in low pressure oil pocket 7 to be discharged in fuel tank through low pressure hydraulic fluid port 6.
The driving signal of solenoid valve 15 is the pwm signal with certain duty ratio, by the duty for changing its driving signal
Than the control to the uninterrupted for flowing through solenoid valve 15 can be realized.In turn, piston rod 4 and air valve opening speed are controlled
Purpose.
When air valve will reach setting lift, the power-off of solenoid valve 15 switchs to closed state, remaining solenoid valve is still kept
Closed state.Function of tonic chord oil pocket 11 is isolated from the outside in sealing state at this time, and only a small amount of hydraulic oil can pass through piston rod 4
Gap leakage between upper housing oil pocket wall surface to low pressure oil pocket 7, due to used clearance seal make leakage rate seldom and
And more slowly, while the entire maximum lift duration of air valve only has millisecond magnitude, thus reveals the shadow to valve lift
Sound can be ignored.It is therefore believed that function of tonic chord oil pocket 11 keeps size constant, the movement of piston rod 4 stops, and keeps air valve also
Lift is constant, until air valve close moment.
When air valve is closed, solenoid valve 15 is remained off, and solenoid valve 14 is powered simultaneously with solenoid valve valve 13 to be switched to open
State, be connected to due to function of tonic chord oil pocket 11 with low pressure oil way reduces the oil pressure in it by the pushing away at spring for valve of piston rod 4 at this time
Dynamic lower uplink is identical as the control method principle of opening speed when air valve will take a seat, can be by changing solenoid valve 14
The duty ratio of driving signal changes the closing velocity of air valve.
When air valve will take a seat, the power-off of solenoid valve 14 remains closing as solenoid valve 15.At this point, the function of tonic chord is oily
Hydraulic oil in chamber 11 can only enter low pressure oil way by overflow hole 10, due to overflow hole aperture very little, cause flow is limited to make
The volume change speed for obtaining function of tonic chord oil pocket slows down, so that reaching reduces piston rod 4 and air valve movement velocity, realizes buffering of taking a seat
Effect.
Above each process is summarized, as shown in Fig. 6: the energization of change solenoid valve 15 can be passed through at the time of air valve is opened
Time changing, the opening speed of air valve are adjusted by changing the duty ratio of solenoid valve 15, the length of 15 conduction time of solenoid valve
The duration of the short lift size for determining air valve, maximum lift is powered by the power-off of solenoid valve 15 with solenoid valve 13,14 simultaneously
Between time difference adjust.The close moment of air valve can be adjusted by changing the energization moment of solenoid valve 14, simultaneously
The duty ratio for changing 14 driving signal of solenoid valve can change the closing velocity of air valve, in the different phase cutting electricity that air valve is taken a seat
Different degrees of buffering effect of taking a seat can be realized in the power supply of magnet valve 14.
Claims (6)
1. a kind of electro-hydraulic full variable gas distribution actuator, it is characterized in that: including hydraulic piston, hydraulic system；The hydraulic piston packet
Upper housing, lower plate, piston rod are included, upper housing is fixed on lower plate, and upper column oil pocket, the lower prop communicated is arranged in upper housing
Shape oil pocket, the diameter of lower column oil pocket are greater than the diameter of upper column oil pocket, and piston rod is mounted in lower column oil pocket, piston rod
Lower end is extend out to outside lower plate, and is in contact always with air valve valve stem top, and the upper column oil pocket is main kinetic energy oil pocket,
Lower column oil pocket is low pressure oil pocket, and the connection actively high pressure oil port of energy oil pocket and the first low pressure hydraulic fluid port and company are opened up in upper housing
Second low pressure hydraulic fluid port of logical low pressure oil pocket, the first low pressure hydraulic fluid port are connected to fuel tank, the connection of the second low pressure hydraulic fluid port by first switch valve
Fuel tank, high pressure oil port are connected to hydraulic system.
2. the electro-hydraulic full variable gas distribution actuator of one kind according to claim 1, it is characterized in that: the hydraulic system includes filter
Clear device, hydraulic pump, accumulator, hydraulic pump are connected to fuel tank by filter, and accumulator connects hydraulic pump, flowline by flowline
It is connected to high pressure oil port by second switch valve, flowline is connected to fuel tank by oil return pipe, installs overflow valve on oil return pipe.
3. the electro-hydraulic full variable gas distribution actuator of one kind according to claim 1 or 2, it is characterized in that: being arranged in upper housing slow
Hydraulic fluid port is rushed, buffering hydraulic fluid port is connected to actively energy oil pocket by overflow hole, and buffering hydraulic fluid port is connected to fuel tank by third switch valve.
4. the electro-hydraulic full variable gas distribution actuator of one kind according to claim 1 or 2, it is characterized in that: the head of piston rod with
It is clearance seal between its external upper enclosure inner wall.
5. the electro-hydraulic full variable gas distribution actuator of one kind according to claim 3 and its control method, it is characterized in that: piston rod
Head and its external upper enclosure inner wall between be clearance seal.
6. a kind of electro-hydraulic full variable gas distribution control method, it is characterized in that: using following electro-hydraulic full variable gas distribution actuator: including liquid
Press piston, hydraulic system；The hydraulic piston includes upper housing, lower plate, piston rod, and upper housing is fixed on lower plate, on
The upper column oil pocket communicated, lower column oil pocket are set in shell, and the diameter of lower column oil pocket is greater than the diameter of upper column oil pocket, living
Stopper rod is mounted in lower column oil pocket, and the lower end of piston rod is extend out to outside lower plate, and with air valve valve stem top phase always
Contact, the upper column oil pocket are main kinetic energy oil pocket, and lower column oil pocket is low pressure oil pocket, and the main kinetic oil of connection is opened up in upper housing
The high pressure oil port of chamber is with the first low pressure hydraulic fluid port and is connected to the second low pressure hydraulic fluid port of low pressure oil pocket, and the first low pressure hydraulic fluid port passes through first
Switch valve is connected to fuel tank, and the second low pressure hydraulic fluid port is connected to fuel tank, and high pressure oil port is connected to hydraulic system；
Original state lower air valve is in close state, and first switch valve, second switch valve, third switch valve all remain powered off closing
State；
When air valve is opened, the energization of second switch valve switchs to open state, and rest switch valve remains off, and high pressure oil is through second
Switch valve enters function of tonic chord oil pocket, is transmitted greater than spring for valve by air valve valve rod when acting on active force downward on piston rod
Upward active force when, air valve moves downward, and is discharged to the intracavitary hydraulic oil of low pressure oil through the second low pressure hydraulic fluid port during downlink
In fuel tank；
The driving signal of second switch valve is the pwm signal with duty ratio, by changing the duty ratio of its driving signal, is realized
Control to the uninterrupted for flowing through second switch valve, and then control piston rod and air valve opening speed；
Before air valve reaches setting lift, the power-off of second switch valve switchs to closed state, and rest switch valve still remains turned-off shape
State, function of tonic chord oil pocket is isolated from the outside in sealing state at this time, and function of tonic chord oil pocket keeps size constant, and piston rod movement stops
Only, air valve is made also to keep lift constant, until air valve close moment；
When closing air valve, second switch valve is remained off, and first switch valve is powered simultaneously with third switch valve to be switched to open
State, function of tonic chord oil pocket is connected to low pressure oil way reduces the oil pressure in it, piston rod uplink under the promotion of spring for valve, leads to
Cross the closing velocity for changing the duty ratio change air valve of first switch valve drive signal；
Before air valve is taken a seat, the power-off of first switch valve remains closing, the liquid in function of tonic chord oil pocket as second switch valve
Pressure oil enters low pressure oil way by overflow hole, reduces piston rod by the aperture of overflow hole and air valve movement velocity, realization are taken a seat
Buffering.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201910393529.7A CN110094244B (en) | 2019-05-13 | 2019-05-13 | Electro-hydraulic fully-variable gas distribution actuator and control method thereof |
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| CN201910393529.7A CN110094244B (en) | 2019-05-13 | 2019-05-13 | Electro-hydraulic fully-variable gas distribution actuator and control method thereof |
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| CN110094244B CN110094244B (en) | 2021-09-10 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111022140A (en) * | 2019-12-26 | 2020-04-17 | 哈尔滨工程大学 | Hydraulically controlled fully-variable valve actuating mechanism of internal combustion engine |
| CN111120029A (en) * | 2019-12-26 | 2020-05-08 | 哈尔滨工程大学 | Rotary plunger type fully-variable valve actuating mechanism of internal combustion engine |
| CN111502793A (en) * | 2020-05-11 | 2020-08-07 | 江苏科技大学 | Electromagnetic direct-drive pump control exhaust valve system of marine low-speed diesel engine |
| CN114790925A (en) * | 2021-12-30 | 2022-07-26 | 哈尔滨工程大学 | Rotary plunger type internal combustion engine fully-variable valve actuating mechanism with seating buffer function |
| CN115476701A (en) * | 2022-10-17 | 2022-12-16 | 潍柴动力股份有限公司 | Motor torque determination method and device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111120029A (en) * | 2019-12-26 | 2020-05-08 | 哈尔滨工程大学 | Rotary plunger type fully-variable valve actuating mechanism of internal combustion engine |
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| CN111502793A (en) * | 2020-05-11 | 2020-08-07 | 江苏科技大学 | Electromagnetic direct-drive pump control exhaust valve system of marine low-speed diesel engine |
| CN111502793B (en) * | 2020-05-11 | 2021-04-23 | 江苏科技大学 | Electromagnetic direct-drive pump control exhaust valve system of marine low-speed diesel engine |
| CN114790925A (en) * | 2021-12-30 | 2022-07-26 | 哈尔滨工程大学 | Rotary plunger type internal combustion engine fully-variable valve actuating mechanism with seating buffer function |
| CN115476701A (en) * | 2022-10-17 | 2022-12-16 | 潍柴动力股份有限公司 | Motor torque determination method and device |
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| CN110094244B (en) | 2021-09-10 |
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