CN102146820A - Air valve seating control device for hydraulic drive air valve mechanism of engine - Google Patents
Air valve seating control device for hydraulic drive air valve mechanism of engine Download PDFInfo
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- CN102146820A CN102146820A CN2010101055910A CN201010105591A CN102146820A CN 102146820 A CN102146820 A CN 102146820A CN 2010101055910 A CN2010101055910 A CN 2010101055910A CN 201010105591 A CN201010105591 A CN 201010105591A CN 102146820 A CN102146820 A CN 102146820A
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- 230000007246 mechanism Effects 0.000 title claims abstract description 17
- 239000003921 oil Substances 0.000 claims abstract description 49
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 23
- 238000000034 method Methods 0.000 abstract description 15
- 230000008569 process Effects 0.000 abstract description 9
- 230000009471 action Effects 0.000 description 8
- 230000009467 reduction Effects 0.000 description 7
- 238000005336 cracking Methods 0.000 description 5
- 239000010729 system oil Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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Abstract
一种发动机液压驱动气门机构气门落座控制装置。主要由液压活塞、液压油道、单向阀、液压活塞腔和可变节流通道等组成。液压活塞腔设置可变节流通道的主油道和装有单向阀的旁通油道与液压系统连通，液压活塞驱动气门运动。该装置采用单向阀使液压气门机构在气门打开与关闭过程中液压流通面积不同；采用可变节流通道，使气门关闭过程中节流流通面积随气门升程可变，进而控制发动机液压气门机构的气门落座速度，实现气门的软着陆。
The utility model relates to a valve seating control device of an engine hydraulic drive valve mechanism. It is mainly composed of hydraulic pistons, hydraulic oil passages, check valves, hydraulic piston chambers and variable throttle passages. The hydraulic piston cavity is provided with a main oil channel with a variable throttle channel and a bypass oil channel equipped with a check valve to communicate with the hydraulic system, and the hydraulic piston drives the valve to move. The device uses a check valve to make the hydraulic flow area of the hydraulic valve mechanism different during the valve opening and closing process; it uses a variable throttle channel to make the throttle flow area variable with the valve lift during the valve closing process, and then controls the engine hydraulic valve mechanism. The valve seating speed can achieve soft landing of the valve.
Description
Technical field
The present invention relates to the four stroke engine distribution device.Especially hydraulic driving mode drives the hydraulic variable valve mechanism of valve motion.
Technical background
Fully variable valve actuator for air can realize that valve maximum lift, valve opening continue angle and port timing three's continuous variable, thereby have the good energy-conservation emission reduction effect.Valve is by cam drive in traditional valve mechanism, and the seating velocity of valve can directly be controlled by cam profile.Existing full variable valve actuating mechanism adopts hydraulic driving mode usually, as the cam hydraulic driving mode, and electric liquid driving mode etc.For hydraulic valve mechanism, owing to cancelled the direct control of camshaft, cause valve crash speed excessive to valve, valve seat is produced serious impact, even the serious accident that causes valve to turn around.Therefore the process of taking a seat of tackling motor hydraulic valve mechanism control effectively.
Summary of the invention
The object of the present invention is to provide a kind of valve crash speed control gear that can be used for hydraulic valve mechanism.Hydraulic pressure circulation area when this device adopts one-way valve to make valve opening and close is different, and in valve falling process, the hydraulic throttle area is changed with the size of valve lift, and then reach the purpose of controlling hydraulic valve mechanism valve crash speed, valve is pulled off a soft landing.
Motor hydraulic valve of the present invention mechanism air valve drop control gear, comprise hydraulic piston, hydraulic pressure oil duct, one-way valve, variable restrictor passage and hydraulic piston, the hydraulic piston lower end is connected with valve assembly, the main oil gallery of the variable restrictor passage of hydraulic piston setting is interconnected with bypass oil duct and hydraulic system that one-way valve is housed, the top of hydraulic piston is the tapered protrusion structure, and the top tapered protruding structure of hydraulic piston and mail gallery holes constitute the variable restrictor passage.Hydraulic piston also can adopt the top not have the flat-tope structure of tapered protrusion, constitutes the variable restrictor passage by the cylindrical side of hydraulic piston and the side oil channel hole on the piston sleeve.
Motor hydraulic valve of the present invention mechanism air valve drop control gear, hydraulic piston drives valve motion, is full of the hydraulic fluid that drives the hydraulic piston motion in the piston cavity, and is connected with hydraulic system by oil duct; One-way valve is installed in the bypass oil duct that leads to piston cavity, when the hydraulic system oil pressure during greater than the piston cavity oil pressure one-way valve open, when hydraulic system oil pressure closed check valve during smaller or equal to the piston cavity oil pressure; The orifice size of variable restrictor passage changes with the size of valve lift, and is installed in the main oil gallery that leads to piston cavity.The concrete working procedure of this device can be divided into following two stages:
In the valve opening stage, hydraulic oil flows into piston cavity from hydraulic system.When valve lift hour, because the orifice size of variable restrictor passage is less, make the hydraulic system oil pressure be higher than the cracking pressure that piston cavity oil pressure and pressure reduction have reached one-way valve, one-way valve opens, hydraulic oil flows in the piston cavity by one-way valve, and the hydraulic oil circulation area that flows into piston cavity this moment is that the circulation area of variable restrictor passage adds the one-way valve open area.
Fall the stage after rise at valve, valve promotes small piston under the effect of valve spring begins to fall after rise, and hydraulic oil flows out from piston cavity.Because the piston cavity oil pressure is usually above the hydraulic system oil pressure, closed check valve can not flow out hydraulic oil by the bypass oil duct.This moment, hydraulic oil only flowed out piston cavity by the variable restrictor passage.Because the throttling action of variable restrictor passage and its orifice size can produce strong throttling action valve crash speed is reduced gradually thus with the reducing and diminish of valve lift, and valve is pulled off a soft landing.
By above-mentioned explanation as can be seen, in valve lift hour, the present invention has following two characteristics: the one, because the effect of one-way valve makes valve fall the hydraulic oil circulation area of the hydraulic oil circulation area in stage less than open stage after rise; The 2nd, the orifice size of variable restrictor passage can reducing and diminish with valve lift.These two characteristics have guaranteed that valve flows out piston cavity in the process of taking a seat hydraulic oil has reasonable circulation area, thereby produce comparatively ideal throttling action, make valve realize steadily taking a seat.
Description of drawings
Fig. 1 is a structural principle schematic representation of the present invention; By main oil gallery 1, one-way valve 2, bypass oil duct 3, variable restrictor passage 4, piston cavity 5, hydraulic piston 6, valve assembly 7 compositions such as grade, wherein variable restrictor passage 4 is arranged in main oil gallery 1, and one-way valve 2 is arranged in bypass oil duct 3.
Fig. 2 is the structural representation of embodiment of the present invention 1; Mainly by piston sleeve 8, one-way valve 9, bypass oil duct 10, mail gallery holes 11, throttling dish 12, piston cavity 13, piston 14 compositions such as grade of band tapered protrusion.
Fig. 3 is the structural representation of embodiment of the present invention 2; Mainly by piston sleeve 8, one-way valve 9, bypass oil duct 15, piston upper shield 16, piston sleeve side oil channel hole 17, compositions such as piston cavity 18 and flat head piston 19.
Describe specific implementation process of the present invention in detail below in conjunction with drawings and Examples.
Specific embodiment 1
As shown in Figure 2, one-way valve 9 mainly is made up of spring and steel ball, is installed in the bypass oil duct 10; The variable restrictor passage is made of the tapered protrusion and the mail gallery holes 11 of piston 14, is arranged in the minimum flow area of main oil gallery control main oil gallery; Piston cavity 13 is made of piston 14, throttling dish 12 and piston sleeve 8 etc.; Piston cavity 13 is communicated with hydraulic system by bypass oil duct 10 and mail gallery holes 11.Concrete working procedure is as follows:
Phase I is the valve opening procedure.Can be divided into two periods again in this process, in first period, the tapered protrusion of piston 14 is arranged in mail gallery holes 11, the hydraulic oil circulation area of variable restrictor passage is less, forms bigger throttling action, makes the cracking pressure of the hydraulic oil pressure reduction of piston cavity 13 and hydraulic system greater than one-way valve 9, this moment one-way valve opens, hydraulic oil can enter piston cavity 13 from bypass oil duct 10 and mail gallery holes 11, and the pressure that promotion piston 14 overcomes valve spring makes valve opening, and valve lift increases gradually; In second period, increase along with valve lift, the tapered protrusion of piston 14 is left mail gallery holes 11, this moment, the mail gallery holes circulation area increased, and throttling action is corresponding to diminish, and piston cavity 13 reduces gradually with the hydraulic oil pressure reduction of hydraulic system, when its during less than the cracking pressure of one-way valve 9, closed check valve, hydraulic oil only enter piston cavity 13 by mail gallery holes 11, continue to promote the increase of valve lift.
Second stage is that valve falls process after rise.After valve arrives maximum lift, valve will begin to fall after rise, be in closed condition at this stage one-way valve 9, and hydraulic oil flows out from piston cavity 13 by mail gallery holes 11.This stage also can be divided into two periods, and in first period, because valve lift big (generally greater than 2mm), still outside mail gallery holes 11, this moment, the mail gallery holes circulation area was bigger for the tapered protrusion of piston 14, and valve falls speed after rise and increases gradually; In second period, because the tapered protrusion of piston 14 begins to enter within the mail gallery holes 11, thereby the circulation area that makes the variable restrictor passage reduces gradually with the reduction of valve lift, this variable restrictor passage forms strong throttling action, valve speed is reduced gradually, finally realize the soft landing of valve.
The bypass oil duct 10 of one-way valve 9 is housed, can arranges one or morely as required, lead to respectively in the piston cavity 13.
As shown in Figure 3, one-way valve 9 is installed in the bypass oil duct 15; The variable restrictor passage is made of the cylindrical side of flat head piston 19 and the side oil channel hole 17 on the piston sleeve 8, the minimum flow area of control main oil gallery; Piston cavity 18 is formed by piston 19, piston sleeve 8 and piston upper shield 16.Piston cavity 18 links to each other with hydraulic system with the main oil gallery that side oil channel hole 17 is set by bypass oil duct 15.Its concrete working procedure is as follows:
Phase I is the valve opening procedure.In this course, the working procedure of this device can be divided into two periods.In first period, because piston 19 has hidden most of area in side oil channel hole 17 and has formed the variable restrictor passage, this moment, the circulation area of variable restrictor passage was less, throttling action is obvious, the pressure reduction of hydraulic oil is greater than the cracking pressure of one-way valve 9 before and after the variable restrictor passage, and this moment, one-way valve 9 was opened, and hydraulic oil can enter the piston cavity 18 from bypass oil duct 15 and side oil channel hole 17, oil pressure in the piston cavity is raise gradually, and promote the elastic force that piston 19 overcomes valve spring and make valve motion; In second period, along with valve lift increases gradually, piston 19 comes downwards to the position that can not hide side oil channel hole 17, the hydraulic oil circulation area of main oil gallery is bigger, cause the pressure reduction of one-way valve 9 front and back to reduce gradually, when its during less than the cracking pressure of one-way valve 9, closed check valve, hydraulic oil only enters in the piston cavity 18 by the side oil channel hole 17 of main oil gallery, continues to promote valve motion.
Second stage is that valve falls process after rise.This stage one-way valve 9 is closed, and hydraulic oil can only flow out from main oil gallery by side oil channel hole 17.This stage also can be divided into two periods.In first period, because valve lift big (generally greater than 2mm), side oil channel hole 17 is failed to hide in the position of piston 19, and hydraulic oil circulation this moment area more greatly and does not change with the change of valve lift, makes valve fall speed after rise and increases gradually; In second period,, form the variable restrictor passage because piston 19 begins to hide side oil channel hole 17, the circulation area of this variable restrictor passage reduces and diminishes with valve lift, form strong throttling action, valve crash speed is reduced gradually, realize the soft landing of valve.
Claims (3)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101055910A CN102146820A (en) | 2010-02-04 | 2010-02-04 | Air valve seating control device for hydraulic drive air valve mechanism of engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101055910A CN102146820A (en) | 2010-02-04 | 2010-02-04 | Air valve seating control device for hydraulic drive air valve mechanism of engine |
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| Publication Number | Publication Date |
|---|---|
| CN102146820A true CN102146820A (en) | 2011-08-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101055910A Pending CN102146820A (en) | 2010-02-04 | 2010-02-04 | Air valve seating control device for hydraulic drive air valve mechanism of engine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103388502A (en) * | 2013-07-31 | 2013-11-13 | 哈尔滨工程大学 | Full changeable electro-hydraulic air valve driving device |
| CN107100689A (en) * | 2017-06-28 | 2017-08-29 | 吉林大学 | A kind of solenoid-operated hydraulic drive-type fully variable valve actuator for air |
-
2010
- 2010-02-04 CN CN2010101055910A patent/CN102146820A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103388502A (en) * | 2013-07-31 | 2013-11-13 | 哈尔滨工程大学 | Full changeable electro-hydraulic air valve driving device |
| CN103388502B (en) * | 2013-07-31 | 2016-01-27 | 哈尔滨工程大学 | A kind of full changeable electro-hydraulic air valve drive unit |
| CN107100689A (en) * | 2017-06-28 | 2017-08-29 | 吉林大学 | A kind of solenoid-operated hydraulic drive-type fully variable valve actuator for air |
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Application publication date: 20110810 |