CN102094692B - Steplessly variable valve lift mechanism and control method - Google Patents

Steplessly variable valve lift mechanism and control method Download PDF

Info

Publication number
CN102094692B
CN102094692B CN 200910220681 CN200910220681A CN102094692B CN 102094692 B CN102094692 B CN 102094692B CN 200910220681 CN200910220681 CN 200910220681 CN 200910220681 A CN200910220681 A CN 200910220681A CN 102094692 B CN102094692 B CN 102094692B
Authority
CN
Grant status
Grant
Patent type
Prior art keywords
cylinder
oil
piston
cam
passage
Prior art date
Application number
CN 200910220681
Other languages
Chinese (zh)
Other versions
CN102094692A (en )
Inventor
吴爽
Original Assignee
吴爽
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Grant date

Links

Classifications

    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/18Varying inlet or exhaust valve operating characteristics

Abstract

无级可变气门升程机构及其控制方法,其升程机构包括气缸盖上的液压缸导管、液压缸体、双轮廓凸轮、液压缸体弹簧、单向阀和装在液压缸体内的吊杯活塞、压缩活塞、气门端活塞及形成液压缸低压腔、中压腔和高压腔。 Steplessly variable valve lift mechanism and a control method, which comprises a cylinder head lift mechanism of a hydraulic cylinder conduit, a hydraulic cylinder, double contour cam, a hydraulic cylinder spring, the check valve and the hydraulic lifting cylinder is mounted Cup piston, compression piston, and the valve end of the piston cylinder formed low pressure chamber, the pressure chamber and the high pressure chamber. 吊环活塞与压缩活塞之间装平衡弹簧、压缩活塞与气门端活塞之间装缓冲弹簧。 Piston rings and the compression spring mounted between the balance piston, the valve piston and the compression spring between the piston side loading buffer. 单向阀装在液压缸体的内隔板上,液压缸体套装在气门端活塞的活塞杆上,双轮廓凸轮装在液压缸体前端。 A check valve mounted on the partition plate within the hydraulic cylinder, the piston rod of the hydraulic cylinder fitted onto the valve end of the piston, double contour cam mounted on the front end of the cylinder block. 其控制方法包括发动机低、中、高转速时,凸轮的凸圆未压、开始压、最高点、回转及完全回转压整个机构,使机构的动作过程,从而达到控制气门不同升程。 An engine control method comprises a low, medium and high speed, the convex cam is not pressed, the start pressure, the highest point, and a complete revolution of the rotary compression mechanism throughout the course of the operation mechanism, so as to control different valve lift. 本发明发动机可变升程来源发动机的机油压力,控制气门升程,具有成本低、寿命高、经济、环保的优点。 The present invention is a variable lift of the engine oil pressure source of the engine drive, the control valve lift, low cost, high life, economic and environmental advantages.

Description

无级可变气门升程机构及其控制方法 Steplessly variable valve lift mechanism and control method

技术领域 FIELD

[0001] 本发明涉及汽车发动机气门升程机构,特别是涉及无级可变气门升程机构及无级可变气门升程的控制方法。 [0001] The present invention relates to an automobile engine valve lift mechanism, and more particularly to a control method for an infinitely variable valve lift mechanism and a steplessly variable valve lift.

背景技术 Background technique

[0002] 随着汽车行业的发展和石油资源的紧缺,油价不断地攀升和日益严格的环保标准出台,改善发动机的油耗、环保性能显得更为紧迫。 [0002] With the development of the automotive industry and the shortage of petroleum resources, oil prices continue to rise and the introduction of increasingly stringent environmental standards, improve the fuel economy of the engine, the environmental performance is all the more urgent. 传统的发动机气门升程技术多数都是使用的有级升程,即分二个或三个升程,发动机在不同转速下对可燃气进入需求量也不同,发动机处于低转速、低负荷只需较小的进气量即可满足发动机的动力输出,在满足动力输出的工况下可降低燃油消耗率,而发动机处于高速、高负荷时,又需要较大的进气量,而且高速下,发动机充气时间会缩短,进气量不足,具有限制发动机动力的局限性,所以有必要改变发动机气门升程过程,以满足发动机在不同转速下的进气量需求,从而改善发动机动力输出性能和降低发动机燃油消耗率以及燃油在缸内充分燃烧,对降低发动机污染物排放有着重要意义。 Traditional engine valve lift technology employed are mostly lift stage, i.e. two or three sub-lift gas into the engine demand is also to be different at different speeds, the engine is in a low speed, low load only a small amount of intake air to the engine to meet power output, the power output to meet the condition of fuel consumption can be reduced, and the engine is in a high speed, high load, and requires a large amount of intake air, and at high speed, engine inflation time will be shortened, the intake air amount is insufficient, limiting engine power limitations, it is necessary to change the valve lift processes of the engine, the intake air amount to meet the requirements of the engine at different speeds, thereby improving the power output performance of the engine and reduced fuel consumption of the engine and fuel combustion in the cylinder of the engine to reduce emissions of great significance. 于是目前将气门正时升程设计成可变的,以满足发动机复杂工况下对气门的升程不同要求。 So now the valve timing variable lift designed to meet different requirements of engine operating conditions for complex valve lift. 本机构设计成无级升程,其升程是随发动机的内部机油压力的变化而变化,而机油压力是随发动机的转速变化而变化,利用发动机的转速控制气门的升程量,转速低,升程量低,转速高,升程量高,而这恰好为发动机的各种工况提供最理想的升程量,从而使发动机得到最理想的空气量。 This mechanism is designed to steplessly lift, which lift is with the changes in the internal oil pressure of the engine is changed, the oil pressure is with the speed variation of the engine changes, the use of speed control of the engine valve in lift amount, the low rotational speed, low lift amount, the high speed, high lift lift amount, which happens to provide optimal lift amount of the various engine operating conditions, so that the engine air amount obtained optimal.

发明内容 SUMMARY

[0003] 本发明要解决的技术问题,是提供一种利用发动机机油泵随着发动机的转速而线性变化的机油压力来控制气门提升量,满足发动机随转速变化对空气的需求量来控制进气量,从而提高发动机的燃油经济性、动力性、环保性的无级可变气门升程机构及其控制方法。 [0003] The present invention is to solve the technical problem, it is to provide an oil pump by the engine as the rotational speed of the engine oil pressure changes linearly the valve lift amount is controlled to meet the demand for the engine speed dependent control the intake air amount, thereby enhancing the infinitely variable valve fuel economy, power, environmental protection engine lift mechanism and its control method.

[0004] 采用的技术方案是: [0004] The technical solutions adopted are:

[0005] 无级可变气门升程机构,包括气缸盖上的液压缸导管、液压缸体、双轮廓凸轮、液压缸体弹簧、单向阀和装在液压缸体内的吊杯活塞、压缩活塞、气门端活塞。 [0005] The infinitely variable valve lift mechanism, comprising a cylinder head of hydraulic cylinder conduit, a hydraulic cylinder, double contour cam, a hydraulic cylinder spring, and a check valve installed in the hydraulic cylinder piston cup hanging compression piston , the valve end of the piston. 所述的液压缸体装在气缸盖上的液压缸导管内,吊杯活塞、压缩活塞和气门端活塞依次装在液压缸体内,吊杯活塞和压缩活塞之间形成液压缸低压腔、压缩活塞后端和液压缸体内隔板之间形成液压缸中压腔、液压缸体内隔板和气门端活塞之间形成液压缸高压腔。 Said cylinder block mounted in the cylinder head cylinder conduit, the cup hanging piston, compression piston and the valve end of the piston successively loaded hydraulic cylinder, piston and cup hanging compression chamber is formed between the low-pressure cylinder piston, the compression a hydraulic pressure chamber formed between the piston cylinder and the rear end of the hydraulic separator cylinder, a high pressure chamber formed between the cylinder of the hydraulic separator cylinder and a valve piston end. 所述吊杯活塞和压缩活塞均设有弹簧腔,压缩活塞的弹簧腔端与吊杯活塞的弹簧腔端相互套接,平衡弹簧装在压缩活塞和吊环活塞之间的弹簧腔内,平衡弹簧两端分别抵顶在吊杯活塞和压缩活塞上。 The cup hanging piston and the compression piston have a spring chamber, the compression spring chamber end of the piston spring chamber end of each piston and the cup hanging socket, a compression spring mounted on the balance spring chamber between the piston and piston rings, spring balance hanging on both ends abut against the piston and the compression piston cup. 压缩活塞与液压缸体内隔板之间、气门端活塞与液压缸体内限位台之间均装有缓冲弹簧。 Between the compression piston and a hydraulic separator cylinder, it is equipped with a valve end of the buffer spring between the piston and the hydraulic cylinder limit table. 所述单向阀装在液压缸体内隔板上,使液压缸中压腔的液压油通过单向阀向液压缸高压腔单向流通。 The one-way valve means in the hydraulic separator cylinder, the hydraulic oil pressure chamber of the hydraulic cylinder to flow into the high pressure chamber of the hydraulic cylinder through the one-way check valve. 所述液压缸体弹簧套装在气门端活塞的活塞杆上,其一端抵顶在液压缸体的后端。 The hydraulic cylinder spring fitted over the valve end of the piston rod, one end thereof abuts against the rear end of the hydraulic cylinder. 所述双轮廓凸轮为低轮廓凸轮连接高轮廓凸轮且为一整体结构,双轮廓凸轮装在液压缸体的前端,在液压缸体弹簧的作用下,使双轮廓凸轮与液压缸体的前端压紧在一起,其中低轮廓凸轮压在液压缸体上,转动中高轮廓凸轮压在吊杯活塞上。 Said dual cam profile of the cam is connected to a low profile and high profile of the cam is an integral structure, a double profile of the cam at the front end of the hydraulic cylinder, the hydraulic cylinder under the action of the spring, the distal end profile of the cam and the hydraulic pressure double cylinder secured together, wherein the low profile of the cam is pressed against the cylinder block, the high profile of the cam in rotation is pressed against the piston cup hanging.

[0006] 上述的液压缸体上设有第一进油道、第二进油道、第一泄油道、和第一次泄油道。 [0006] provided with a first oil feed passage, a second oil feed passage, a first drain passage, and the first oil drain passage of said cylinder block. 所述气缸盖上的液压缸导管上设有第三进油道、第四进油道和第二泄油道,所述双轮廓凸轮上设有第二次泄油道,当液压缸体处于静止时,第一进油道两端分别与第三进油道和液压缸低压腔连接相通,第二进油道两端分别与第四进油道和液压缸中压腔连接相通;第一泄油道两端与第三泄油道连接相通与液压缸低压腔不相通。 The cylinder head is provided with a hydraulic cylinder on the third catheter into the oil passage, a fourth inlet oil passage and the second oil drain passage, a second drain passage is provided on the double contour cam, when the cylinder block is still, the first intake passage are connected to both ends of the oil inlet in communication with the third oil passage and the low pressure chamber of the hydraulic cylinder, the second intake passage are connected to both ends of a fourth oil inlet and the oil passage communicating the hydraulic cylinder pressure chamber; a first both ends of the drain passage and the drain passage connected to the third hydraulic cylinder communicates with the low pressure chamber do not communicate. 当双轮廓凸轮开始回转到回转90度过程中,第一次泄油道两端分别与液压缸高压腔和第二次泄油道连接相通。 When the double contour cam begins to swing back to 90 degrees during the first drain oil passage are connected to both ends of the cylinder chamber and the high pressure oil passage communicating the second drain.

[0007] 上述的吊杯活塞上设有防止弹簧腔内存入机油的第四泄油道。 It is provided to prevent the spring chamber into the fourth oil drainage passage on the piston [0007] The cup hanging.

[0008] 上述的液压缸体上设有液压缸高压腔快速泄油的第二泄油道。 [0008] The high pressure chamber of the hydraulic cylinder is provided with quick drain of the second oil drain passage of said cylinder block.

[0009] 上述的液压缸体内限位台与气门端活塞之间设有为消除气门间隙的间隙。 [0009] The hydraulic cylinder is provided with an end stop station for the elimination of the valve lash clearance between the piston.

[0010] 无级可变气门升程机构的控制方法: [0010] The infinitely variable valve lift mechanism of the process control method:

[0011] 一、发动机低转速时 [0011] First, when the engine speed is low

[0012] a、双轮廓凸轮的凸圆未压整个机构,机油经第一进油道、第二进油道、第三进油道、第四进油道进入液压缸体内,此时压缩活塞在液压缸低压腔和液压缸中压腔的面积不同,在压力差和平衡弹簧的作用下,压缩活塞的位置会在机构中随机油压力的变化而变化,由于此时压力很小,压缩活塞的提升量很小。 [0012] a, double-convex profile of the cam is not pressing the whole bodies, the oil through the first oil feed passage, a second oil feed passage, into the third oil passage, the oil feed passage into the fourth cylinder body, at this time the compression different low-pressure chamber of the piston in the cylinder and the cylinder pressure chamber in the area under pressure differential and balance spring, compressed position of the piston will vary with the oil pressure variation mechanism, since the pressure is very small at this time, the compression a small amount of lift of the piston.

[0013] b、双轮廓凸轮的凸圆开始压整个机构,低轮廓凸轮压液压缸体,液压缸高压腔处于密封,形成刚性体,推动气门的原始期提升量,同时高轮廓凸轮压吊环杯活塞,机构的所有进油道和泄油道封闭,形成刚性体,将液压缸中压腔的机油经单向阀压进液压缸高压腔,气门端活塞推动气门来增加附加提升量,随着压缩活塞的推动,第一泄油道和第三泄油道相对,泄油通道打开,液压缸低压腔开始泄油变成不是刚性,气门的继续提升量由低轮廓凸轮推动,此时液压缸高压腔不变化,液压缸中压腔在缓冲弹簧和泄油过程的共同作用下也维持不变。 [0013] b, the convex profile of the cam comes to press the double entire mechanism, a cam profile of the low pressure hydraulic cylinder, the hydraulic cylinder in a sealed high pressure chamber to form a rigid body, promote the original amount of lift of the valve, while high pressure profile of the cam rings cup piston, all the oil inlet passage means and the drain passage is closed to form a rigid body, the hydraulic cylinder oil pressure chamber through the check valve is pressed into the high pressure chamber of the hydraulic cylinder, the valve end of the piston pushes the valve lift amount to add additional, as urgings of a compression piston, a first drain passage and the drain passage relative to the third, the oil release passage is opened, the low pressure chamber of the hydraulic cylinder is not started drain becomes rigid, continues to push the valve lift amount by the low profile of the cam, the cylinder case does not change the high pressure chamber, the hydraulic cylinder pressure chamber is maintained constant under the action of recoil spring and drain process.

[0014] C、双轮廓凸轮的凸圆达到最高点,液压缸低压腔通过第三泄油道泄油完毕,液压缸高压腔为封闭,进入液压缸高压腔的机油量少,第三泄油道并未开启,在液压缸体弹簧、缓冲弹簧、平衡弹簧的作用下整个机构随双轮廓凸轮移动,此时第一次泄油道即将开启。 [0014] C, a double convex profile of the cam reaches the highest point, the low-pressure cylinder chamber is completed by a third drainage channel drain, the high pressure chamber of the hydraulic cylinder is closed, the high pressure chamber into the hydraulic cylinder of a small amount of oil, a third drain channel does not open, the hydraulic cylinder spring, buffer spring, the entire profile of the cam mechanism moves with the double action of the balancing spring, this time the first oil drain passage will open.

[0015] d、双轮廓凸轮开始回转,在此之前低轮廓凸轮上的第二次泄油道与第一次泄油道相对,泄油,将液压缸高压腔少量机油泄出。 [0015] d, double contour cam starts to rotate, before the second passage and the drain of the low profile of the cam relative to the first drain passage, drain, the high pressure chamber of the hydraulic cylinder small amount of oil escape.

[0016] e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时,进油道再次开启,开始进油,转速不同,进油压力不同,压缩活塞的位置不同,升程量不同。 [0016] e, double contour cam completely slewed cam highest point means the center of 180 degrees, the oil feed passage opened again to start into the oil, different speeds and different feed oil pressure, different compression position of the piston, different amounts of lift .

[0017] 二、发动机中转速时 [0017] Second, when the engine speed

[0018] a、双轮廓凸轮的凸圆未压整个机构,机油经第一进油道、第二进油道、第三进油道、第四进油道进入液压缸体内,由于此时压力不大,压缩活塞的提升量不大。 [0018] a, double-convex profile of the cam is not pressing the whole bodies, the oil through the first oil feed passage, a second oil feed passage, into the third oil passage, the fourth passage into the oil into the hydraulic cylinder, since this time not much pressure, not to enhance the amount of compression piston.

[0019] b、双轮廓凸轮的凸圆开始压整个机构,由于压缩活塞的位置升高,第一泄油道和第三泄油道相对的时间要比发动机低转速时晚,从液压缸中压腔压入液压缸高压腔的机油也比发动机低转速时要多,其升程量比发动机低转速时要多。 [0019] b, the convex profile of the cam comes to press the double entire mechanism, increases due to the compression position of the piston, a first low speed late drain passage and the drain passage opposite the third time than the engine, the hydraulic cylinder pressed into the cylinder pressure chamber of the high pressure oil chamber is lower than the rotational speed of the engine to which the lift than the low speed of the engine to be more.

[0020] C、双轮廓凸轮的凸圆达到最高点,液压缸低压腔通过第一泄油道和第三泄油道泄油完毕,液压缸高压腔为封闭,在液压缸体弹簧、缓冲弹簧、平衡弹簧的作用下整个机构随双轮廓凸轮移动,此时第一次泄油道即将开启。 [0020] C, a double convex profile of the cam reaches the highest point, the low-pressure cylinder chamber is completed by the first drain passage and the drain passage third drain, the high pressure chamber of the hydraulic cylinder is closed, the hydraulic cylinder spring, buffer spring , the entire action of the spring balanced with the double contour cam mechanism moves, when the first oil drain passage will open.

[0021] d、双轮廓凸轮开始回转,在此之前低轮廓凸轮上的第二次泄油道与第一次泄油道相对,泄油,泄油即将完毕。 [0021] d, double contour cam starts to rotate, before the second passage and the drain of the low profile of the cam relative to the first drain passage, drain, drain soon completed.

[0022] e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时,在此之前,液压缸高压腔机油不多,泄油过程完毕,进油道开始进油,进油压力不同,压缩活塞的位置不同,升程量不同。 [0022] e, go back to completely double contour cam of the cam mechanism and the highest point of the center of 180 degrees, before, small oil hydraulic cylinder high pressure chamber, drainage process is complete, the oil feed passage into the oil starts, the oil pressure into the different , different compression position of the piston, different lift lift amount.

[0023] 三、发动机高转速时 [0023] Third, when the high engine speed

[0024] a、双轮廓凸轮的凸圆未压整个机构,机油经第一进油道、第二进油道、第三进油道、第四进油道进入整个机构,压力大,压缩活塞的提升量很大。 [0024] a, double-convex profile of the cam is not pressing the whole bodies, the oil through the first oil feed passage, a second oil feed passage, into the third oil passage, the oil feed passage into the whole of the fourth means, pressure, compression piston a large amount of lift.

[0025] b、双轮廓凸轮的凸圆开始压整个机构,压缩活塞位置接近最高点,第一泄油道与第三泄油道并未相对,整个机构的液压缸低压腔、液压缸中压腔、液压缸高压腔都密封,从液压缸中压腔压入液压缸高压腔的机油比发动机中转速时多,其升程量比发动机中转速多。 [0025] b, a double convex profile of the cam comes to press the entire mechanism of the compression piston position close to the highest point, the first drain passage and the drain passage is not the third hand, the entire low-pressure chamber of the hydraulic cylinder mechanism, a hydraulic pressure cylinder chamber, the high pressure chamber are sealed cylinder, the cylinder is pressed into the pressure chamber from the high pressure chamber in the hydraulic cylinder when the multi-speed ratio of the engine oil, the engine in which the lift speed than multiple.

[0026] C、双轮廓凸轮的凸圆达到最高点,第一泄油道和第三泄油道相对,液压缸低压腔开始泄油,进入液压缸高压腔机油量达设定最高量,液压缸高压腔通过第二泄油道与汽车缸体的空隙泄油,第一次泄油道即将泄油,在液压缸体弹簧、缓冲弹簧、平衡弹簧的作用下整个机构随双轮廓凸轮移动。 [0026] C, a double convex profile of the cam reaches the highest point, the first drain passage and the drain passage relative to the third hydraulic cylinder low pressure drain chamber starts, the high pressure chamber into the oil amounted to set a maximum amount of hydraulic cylinders, hydraulic a high pressure cylinder chamber through the gap of the second drain passage and the drain cylinder automobile, the first oil drainage passage is about to drain, the hydraulic cylinder spring, buffer spring, the entire profile of the cam mechanism moves with the double action of the balancing spring.

[0027] d、双轮廓凸轮开始回转,在此之前低轮廓凸轮上的第二次泄油道与第一次泄油道相对,泄油,泄完液压缸高压腔未泄完的油。 [0027] d, double contour cam starts to rotate, before the second passage and the drain of the low profile of the cam relative to the first drain passage, drain, vent the high pressure chamber of the hydraulic cylinder is not completely finished oil leakage.

[0028] e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时,在完全回转之前,液压缸高压腔完全泄完,进油道开始进油,转速不同,进油压力不同,压缩活塞的位置不同,升程量不同。 [0028] e, double contour cam completely slewed cam highest point means the center of 180 degrees, until complete revolution, the cylinder pressure chamber completely finished drain oil feed passage starts into the oil, different speeds and different feed oil pressure, different compression position of the piston, different amounts of lift.

[0029] 本发明的可变升程量来源是发动机的机油泵的机油压力,机油压力随着发动机的转速而线性变化,发动机对空气的需求量也随转速而变化,此机构利用机油压力来控制气门的提升量,从而控制进气量,提高发动机的燃油能量利用率,降低发动机污染物的排放量,提高了发动机的功率,具有结构简单、制造成本低、使用寿命高、经济、环保的优点。 [0029] The variable lift amount of the source of the present invention is an engine oil pressure oil pump, the oil pressure as the engine speed varies linearly, the demand for the engine with the speed of the air is also changed, this means using oil pressure lift amount control valve, thereby controlling the intake air amount, the energy of the engine to improve fuel efficiency and reduce engine emissions of pollutants and improve the engine power, has a simple structure, low manufacturing cost, high life, economic, environmental advantage. 油道的开启关闭完全由机构随凸轮的自然运动而开启关闭,运行稳定,完全达到无级可变气门升程。 Oil passage means open and close entirely by the natural movement of the cam with the open and close, stable, fully achieve infinitely variable valve lift.

附图说明 BRIEF DESCRIPTION

[0030] 图I是本发明的结构示意图。 [0030] FIG. I is a schematic structural diagram of the present invention.

[0031] 图2是本发明的双轮廓凸轮结构示意图。 [0031] FIG. 2 is a schematic view of a double profile cam structure according to the present invention.

[0032] 图3是图2的侧视图。 [0032] FIG. 3 is a side view of FIG.

[0033] 图4、图5、图6、图7、图8是发动机低转速时气门升程控制示意图。 [0033] FIG 4, FIG 5, FIG 6, FIG 7, FIG 8 is a schematic view of a valve lift control when the engine speed is low.

[0034] 图9、图10、图11、图12、图13是发动机中转速时气门升程控制示意图。 [0034] FIG 9, FIG 10, FIG 11, FIG 12, FIG 13 is a schematic view of a valve lift controlling engine speed.

[0035] 图14、图15、图16、图17、图18、图19是发动机高转速时气门升程控制示意图。 [0035] FIG 14, FIG 15, FIG 16, FIG 17, FIG 18, FIG 19 is a schematic view of a valve lift control when the high engine speed.

具体实施方式 detailed description

[0036] 无级可变气门升程机构,包括气缸盖上的液压缸导管I、液压缸体2、双轮廓凸轮3、液压缸体弹簧14、单向阀18和装在液压缸体内的吊杯活塞4、压缩活塞9和气门端活塞13。 [0036] The infinitely variable valve lift mechanism, comprising a cylinder head of hydraulic cylinder conduit I, the cylinder block 2, 3 double contour cam, 14, check valve 18 and the hydraulic lifting cylinder spring mounted in the cylinder body Cup piston 4, the compression piston end of the piston 9 and the valve 13. 所述的液压缸体2装在气缸盖上的液压缸导管I内,吊杯活塞4、压缩活塞9和气门端活塞13依次装在液压缸体2内,吊杯活塞4和压缩活塞9之间形成液压缸低压腔23、压缩活塞9后端和液压缸体内隔板24之间形成液压缸中压腔19、液压缸体内隔板24和气门端活塞13之间形成液压缸高压腔17。 The cylinder block 2 is mounted in the conduit I the cylinder cylinder head, 4 a piston cup hanging compression piston end of the piston 9 and the valve 13 are sequentially mounted in the cylinder block 2, a piston 4 and lifting cups of the compression piston 9 a low pressure chamber formed between the cylinder 23, the rear end of the compression piston 9 and a hydraulic separator cylinder pressure chamber formed between the hydraulic cylinder 2419, a high pressure chamber formed between the cylinder 13 of the hydraulic cylinder 24 and the valve end piston separator 17. 所述吊杯活塞4和压缩活塞9均设有弹簧腔,压缩活塞9的弹簧腔端与吊杯活塞4的弹簧腔端相互套接,平衡弹簧5装在压缩活塞9和吊杯活塞4之间的弹簧腔6内,平衡弹簧5两端分别抵顶在吊杯活塞4和压缩活塞9上。 The cup hanging compression piston 9 and the piston 4 are provided with a spring chamber, the compression piston spring chamber end of the cup hanging end of the piston spring chamber 9 of each socket 4, the balancing spring 5 mounted in the cup hanging compression piston 9 and the piston 4 the spring chamber 6, the ends of the spring balance 5 abut against the cup hanging on the piston 4 and the compression piston 9. 压缩活塞9与液压缸体内隔板24之间、气门端活塞13与液压缸体内限位台25之间均装有缓冲弹簧12。 9 between the compression piston 24 of the hydraulic separator cylinder, the valve 13 and the end of the piston cylinder 25 are fitted between the table buffer spring 12 within the limit. 所述的液压缸体内限位台25与气门端活塞13之间设有为消除气门间隙的间隙16。 The stopper hydraulic cylinder units 25 is provided between the end of the valve piston 13 to the valve 16 to eliminate the gap clearance. 所述的单向阀18装在液压缸体内隔板24上,使液压缸中压腔19的液压油通过单向阀18向液压缸高压腔17流通。 The check valve 18 is mounted on the partition plate 24 of the hydraulic cylinder, the hydraulic cylinder of the hydraulic oil pressure chamber 19 flow through the check valve 17 to the hydraulic cylinders 18 high pressure chamber. 所述液压缸体弹簧14套装在气门端活塞13的活塞杆上,其一端抵顶在液压缸体2的后端。 The hydraulic cylinder spring 14 fitted over the rod end of the valve piston 13, one end thereof abuts against the rear end of the cylinder block 2. 所述双轮廓凸轮3为低轮廓凸轮28连接高轮廓凸轮27且为一整体结构,双轮廓凸轮3装在液压缸体2的前端,在液压缸体弹簧14的作用下,使双轮廓凸轮3与液压缸体2的前端压紧在一起,其中低轮廓凸轮28压在液压缸体2上,转动中高轮廓凸轮27压在吊杯活塞4上。 The double contour cam 3 is connected to the low profile of the cam 28 and the high profile of the cam 27 as an integral structure, a double profile of the cam 3 mounted at the front end of the cylinder block 2, cylinder block under the action of the spring 14, so that the double profile of the cam 3 and pressing the front end of the cylinder block 2 together, wherein the low profile of the cam 28 is pressed against the cylinder block 2, the high profile of the cam 27 in rotation is pressed against the suspended piston 4 cup. 所述的液压缸体2上设有第一进油道8、第二进油道11、第一泄油道21、使液压缸高压腔快速泄油的第二泄油道15和第一次泄油道20。 Provided on the cylinder block 2 according to a first inlet oil passage 8, a second oil feed passage 11, the first drain passage 21, the hydraulic cylinder pressure chamber quickly drain a second drain passage 15 and the first drain channel 20. 所述的气缸盖上的液压缸导管I上设有第三进油道7、第四进油道10和第三泄油道22。 Said cylinder head is provided with a hydraulic cylinder pipe I into the oil passage 7 on the third, the fourth oil passage 10 into the drain passage 22 and the third. 所述双轮廓凸轮3上设有第二次泄油道29。 The second double contour cam provided on the drain passage 29 3. 所述吊杯活塞4上设有防止弹簧腔6内存入机油的第四泄油道26。 The cup hanging memory 6 is provided to prevent the spring chamber into the fourth oil drainage passage 26 on the piston 4. 当液压缸体2处于静止时,第一进油道8两端分别与第三进油道7和液压缸低压腔23连接相通,第二进油道11两端分别与第四进油道10和液压缸中压腔19连接相通;第一泄油道21与第三泄油道22连接相通与液压缸低压腔23不相通。 When the hydraulic cylinder 2 is stationary, the oil feed passage 8 across the first and the third feed oil passage, respectively, and a hydraulic cylinder 7 connected to the low pressure chamber 23 communicates, at both ends of the second oil feed passage 11, respectively, and the fourth oil feed passage 10 and the hydraulic cylinder pressure chamber 19 is connected in communication; a first drain passage 21 and the third drain passage 22 is connected in communication with the low pressure chamber of the hydraulic cylinder 23 is not connected. 双轮廓凸轮3开始回转到其回转90度的过程中,第一次泄油道20两端分别与液压缸高压腔17和第二次泄油道29(见图2、3)连接相通,构成可变气门升程机构。 Double contour cam 3 starts its rotation back to 90 degrees during the first drain passage 20 are respectively connected to both ends of the high pressure chamber of the hydraulic cylinder 17 and second drain passage 29 (see FIG. 3) communicating, constituting The variable valve lift mechanism.

[0037] 无级可变气门升程机构的控制方法: [0037] The infinitely variable valve lift mechanism of the process control method:

[0038] 一、发动机低转速时 [0038] First, when the engine speed is low

[0039] a、双轮廓凸轮的凸圆未压整个机构(见图4),机油经第一进油道8、第二进油道 [0039] a, double-convex profile of the cam is not pressing the entire mechanism (see FIG. 4), the oil through the first oil feed passage 8, a second oil feed passage

11、第三进油道7、第四进油道10进入液压缸体2内,此时压缩活塞9在液压缸低压腔23和液压缸中压腔19的面积不同,在压力差和平衡弹簧5的作用下,压缩活塞9的位置会在机构中随机油压力的变化而变化,由于此时压力很小,压缩活塞使提升量很小。 11, the third oil passage 7 into the fourth oil inlet passage 10 into the cylinder block 2, this time in a different area of ​​the compression piston 9 of the hydraulic cylinder 23 and the low pressure chamber of the hydraulic cylinder 19 of the pressure chamber, and the pressure difference balancing spring 5 under the action of the compression position of the piston 9 will vary with the oil pressure variation mechanism, since the pressure is very small at this time, so that the compression piston lift amount is small.

[0040] b、双轮廓凸轮的凸圆开始压整个机构(见图5),低轮廓凸轮28压液压缸体2,液压缸高压腔17处于密封,形成刚性体,推动气门的原始期提升量,同时高轮廓凸轮27压吊杯活塞4,机构的所有进油道和泄油道封闭,形成刚性体,将液压缸中压腔19的机油经单向阀18压进液压缸高压腔17,气门端活塞13推动气门来增加附加提升量,随着压缩活塞9的推动,第一泄油道21和第三泄油道22相对,泄油通道打开,液压缸低压腔23开始泄油变成不是刚性,气门的继续提升量由低轮廓凸轮28推动,此时液压缸高压腔17不变化,液压缸中压腔19在缓冲弹簧12和泄油过程的共同作用下也维持不变。 [0040] b, the convex profile of the cam comes to press the double entire mechanism (see FIG. 5), the low profile of the cam 28 pressing the cylinder block 2, cylinder high pressure chamber 17 is sealed to form a rigid body, promote the original amount of lift of the valve , and all the oil feed passage 27 of the cam profile of the high pressure piston cup hanging 4, and the drain passage means is closed to form a rigid body, the hydraulic cylinder 19 of the oil pressure chamber through the check valve 18 is pressed into the high pressure chamber of the hydraulic cylinder 17, end of the valve piston 13 pushes on the valve to increase the lift amount of additional, as the compression piston 9 is pushed, a first drain passage 21 and the third drainage path 22 relative, the oil release passage is opened, the low pressure chamber of the hydraulic cylinder 23 begins to drain into is not rigid, the valve lift amount is continued, this time the high pressure chamber of the hydraulic cylinder 17 does not change the profile of the cam 28 driven low, the hydraulic cylinder pressure chamber 19 is maintained constant under the action of the buffer spring 12 and drain process.

[0041] C、双轮廓凸轮的凸圆达到最高点(见图6),液压缸低压腔23通过第三泄油道22泄油完毕,液压缸高压腔17为封闭,进入液压缸高压腔的机油量少,第二泄油道15并未开启,在液压缸体弹簧14、缓冲弹簧12、平衡弹簧5的作用下整个机构随双轮廓凸轮移动,此时第一次泄油道20即将开启。 [0041] C, a double convex profile of the cam reaches the highest point (see FIG. 6), the low pressure chamber of the hydraulic cylinder 23 is completed by a third drain drain passage 22, the high pressure chamber of the hydraulic cylinder 17 is closed, the high pressure chamber into the hydraulic cylinder a small amount of oil, a second oil drain passage 15 does not open, the spring in the cylinder block 14, the buffer spring 12, the entire profile of the cam mechanism moves with the double action of a balancing spring 5, this time the first oil drain passage 20 will open .

[0042] d、双轮廓凸轮开始回转(见图7),在此之前低轮廓凸轮28上的第二次泄油道29与第一次泄油道20相对,泄油,将液压缸高压腔少量机油泄出。 [0042] d, double contour cam starts to rotate (see FIG. 7), before the second drainage passage on the low profile of the cam 2829 and the first drain passage 20 opposed to drain, the high pressure chamber of the hydraulic cylinder a small amount of oil escape.

[0043] e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时(见图8),进油道再次开启,开始进油,转速不同,进油压力不同,压缩活塞9的位置不同,升程量不同。 [0043] e, go back to completely double contour cam of the cam mechanism and the highest point 180 degrees from the center (see FIG. 8), the oil feed passage opened again to start into the oil, different speeds, different pressures into the oil, the compressed position of the piston 9 different, different amounts of lift.

[0044] 二、发动机中转速时 [0044] Second, when the engine speed

[0045] a、双轮廓凸轮的凸圆未压整个机构(见图9),机油经第一进油道8、第二进油道 [0045] a, double-convex profile of the cam is not pressing the entire mechanism (see FIG. 9), the oil through the first oil feed passage 8, a second oil feed passage

11、第三进油道7、第四进油道10进入液压缸体内,由于此时压力不大,压缩活塞9的提升量不大。 11, the third oil passage 7 into the fourth oil inlet passage 10 into the hydraulic cylinder, since the pressure is not at this time, the compression piston 9 small lift amount. [0046] b、双轮廓凸轮的凸圆开始压整个机构(见图10),由于压缩活塞9的位置升高,第一泄油道21和第三泄油道22相对的时间要比发动机低转速时晚,从液压缸中压腔19压入液压缸高压腔17的机油也比发动机低转速时要多,其升程量比发动机低转速时要多。 [0046] b, the convex profile of the cam comes to press the double entire mechanism (see FIG. 10), the compression position of the piston 9 rises, low first drain passage 21 and the third drainage path 22 opposite to the engine than the time late rotational speed, the hydraulic pressure from the cylinder chamber of the hydraulic cylinder 19 is pressed into the oil pressure chamber 17 is also to be more than the engine speed is low, which lift the engine than at low rotational speed to be more.

[0047] C、双轮廓凸轮的凸圆达到最高点(见图11),液压缸低油腔23通过第一泄油道21和第三泄油道22泄油完毕,液压缸高压腔17为封闭,在液压缸体弹簧14、缓冲弹簧12、平衡弹簧5的作用下整个机构随双轮廓凸轮移动,此时第一次泄油道20即将开启。 [0047] C, a double convex profile of the cam reaches the highest point (see FIG. 11), the cylinder chamber 2322 low oil drainage passage is completed by the first drain passage 21 and the third drain, the high pressure chamber 17 of the hydraulic cylinder closed, the hydraulic cylinder spring 14, the buffer spring 12, the entire mechanism with the double contour cam moving under the action of a balancing spring 5, this time the first oil drain passage 20 will open.

[0048] d、双轮廓凸轮开始回转(见图12),在此之前低轮廓凸轮28上的第二次泄油道29与第一次泄油道20相对,泄油,泄油即将完毕。 [0048] d, double contour cam starts to rotate (see FIG. 12), before the second drainage passage on the low profile of the cam 2829 and the first drain passage 20 opposed, drain, drain soon completed.

[0049] e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时(见图13),在此之前,液压缸高压腔17机油不多,泄油过程完毕,进油道开始进油,进油压力不同,压缩活塞9的位置不同,升程量不同。 [0049] e, go back to completely double contour cam of the cam mechanism and the highest point 180 degrees from the center (see FIG. 13), before this, a high pressure chamber of the hydraulic cylinder 17 much oil, drain process is complete, the oil feed passage into the Start oil, into the oil pressure is different, the different compression position of the piston 9, up to varying amounts.

[0050] 三、发动机高转速时 [0050] Third, when the high engine speed

[0051] a、双轮廓凸轮的凸圆未压整个机构(见图14),机油经第一进油道8、第二进油道 [0051] a, double-convex profile of the cam is not pressing the entire mechanism (see FIG. 14), the oil through the first oil feed passage 8, a second oil feed passage

11、第三进油道7、第四进油道10进入整个机构,压力大,压缩活塞的提升量很大。 11, the third oil passage 7 into the fourth oil inlet passage 10 into the entire mechanism, pressure, compression of a large lift amount of the piston.

[0052] b、双轮廓凸轮的凸圆开始压整个机构(见图15),压缩活塞9位置接近最高点,第一泄油道21与第三泄油道22并未相对,整个机构的液压缸低压腔23、液压缸中压腔19、液压缸高压腔17都密封,从液压缸中压腔19压入液压缸高压腔17的机油比发动机中转速时多,其升程量比发动机中转速多。 [0052] b, the convex profile of the cam comes to press the double entire mechanism (see FIG. 15), the position of the compression piston 9 close to the highest point, relative, pressure in the first drain passage 21 and the third oil passage drain mechanism 22 is not the entire a low-pressure cylinder chamber 23, the hydraulic cylinder pressure chamber 19, the high pressure chamber of the hydraulic cylinder 17 are sealed from the pressure chamber of the hydraulic cylinder 19 is pressed into the high pressure chamber of the hydraulic cylinder 17 more oil than the rotational speed of the engine, the engine in which the lift ratio speed and more.

[0053] C、双轮廓凸轮的凸圆达到最高点(见图16、17),第一泄油道21和第三泄油道22相对,液压缸低压腔23开始泄油,进入液压缸高压腔机油量达设定最高量,液压缸高压腔17通过第二泄油道15与汽车缸体的空隙泄油,第一次泄油道20即将泄油,在液压缸体弹簧 [0053] C, a double convex profile of the cam reaches the highest point (see FIG. 16, 17), a first drain passage 21 and the third drainage path 22 opposite, low-pressure cylinder chamber 23 begins to drain, the high pressure into the hydraulic cylinder setting a maximum amount of volume of oil chamber, the high pressure chamber of the hydraulic cylinder 17 through the gap of the second drain passage 15 and the drain cylinder automobile, the first oil drain passage 20 is about to drain, the hydraulic cylinder spring

14、缓冲弹簧12、平衡弹簧5的作用下整个机构随双轮廓凸轮移动。 14, the buffer spring 12, the entire profile of the cam mechanism moves with the double action of the spring balance 5.

[0054] d、双轮廓凸轮开始回转(见图18),在此之前低轮廓凸轮28上的第二次泄油道29与第一次泄油道20相对,泄油,泄完液压缸高压腔未泄完的油。 [0054] d, double contour cam starts to rotate (see FIG. 18), before the second drainage passage on the low profile of the cam 2829 and the first drain passage 20 opposed, drain, vent the high pressure hydraulic cylinder End finished oil chamber does not vent.

[0055] e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时(见图19),在完全回转之前,液压缸高压腔17完全泄完,进油道开始进油,转速不同,进油压力不同,压缩活塞9的位置不同,升程量不同。 [0055] e, go back to completely double contour cam of the cam mechanism and the highest point 180 degrees from the center (see FIG. 19), prior to complete rotation, a high pressure chamber of the hydraulic cylinder 17 to vent finish completely, into the oil into the oil passage begins, different speed , into the oil pressure is different, a different position of the piston 9 of the compression, different amounts of lift.

Claims (4)

  1. 1.无级可变气门升程机构,包括气缸盖上的液压缸导管(I)、液压缸体(2)、双轮廓凸轮(3)、液压缸体弹簧(14)、单向阀(18)和装在液压缸体内的吊杯活塞(4)、压缩活塞(9)和气门端活塞(13),其特征在于所述的液压缸体(2)装在气缸盖上的液压缸导管(I)内,吊杯活塞(4)、压缩活塞(9)和气门端活塞(13)依次装在液压缸体(2)内,吊杯活塞(4)和压缩活塞(9)之间形成液压缸低压腔(23),压缩活塞(9)后端和液压缸体内隔板(24)之间形成液压缸中压腔(19)、液压缸体内隔板(24)和气门端活塞(13)之间形成液压缸高压腔(17),所述吊杯活塞(4)和压缩活塞(9)均设有弹簧腔,压缩活塞(9)的弹簧腔端与吊杯活塞⑷的弹簧腔端相互套接,平衡弹簧(5)装在压缩活塞(9)和吊杯活塞⑷之间的弹簧腔(6)内,平衡弹簧(5)两端分别抵顶在吊杯活塞(4)和压缩活塞(9 1. infinitely variable valve lift mechanism, comprising a cylinder head of the cylinder conduit (the I), the cylinder block (2), bis profile of the cam (3), a hydraulic cylinder spring (14), a check valve (18 ) and a hydraulic cylinder mounted on the cup hanging piston (4), a compression piston (9) and the valve end of the piston (13), characterized in that said cylinder block (2) is mounted on a cylinder head of the cylinder conduit ( within the I), lifting the cup of the piston (4), a compression piston (9) and the valve end of the piston (13) are sequentially mounted in the cylinder block (2), lifting the cup of the piston (4) and between the piston (9) form a hydraulic compression a low-pressure cylinder chamber (23), compression piston (9) is formed in the cylinder pressure chamber (19), a hydraulic separator cylinder (24) between the rear end of the piston and the valve cylinder and the hydraulic separator (24) ( forming a high pressure cylinder chamber (17) 13), the lifting piston cup (4) and the compression piston (9) are provided with a spring chamber, the compression piston (9) and the spring chamber end of the cup hanging spring chamber piston ⑷ each socket ends, the balancing spring (5) is mounted on a compression spring between the piston chamber (9) and the piston cup hanging ⑷ (6) inside, (5) at both ends of the balancing spring abut against the piston cup hanging (4), and compression piston (9 )上,压缩活塞(9)与液压缸体内隔板(24)之间、气门端活塞(13)与液压缸体内限位台(25)之间均装有缓冲弹簧(12),所述单向阀(18)装在液压缸体内隔板(24)上,使液压缸中压腔(19)的液压油通过单向阀(18)向液压缸高压腔(17)流通,所述的缸体弹簧(14)套装在气门端活塞(13)的活塞杆上,其一端抵顶在液压缸体(2)的后端,所述双轮廓凸轮(3)为低轮廓凸轮(28)连接高轮廓凸轮(27)且为一整体结构,双轮廓凸轮(3)装在液压缸体(2)的前端,在液压缸·体弹簧(14)的作用下,使双轮廓凸轮(3)与液压缸体(2)的前端压紧在一起,其中低轮廓凸轮(28)压在液压缸体(2)上,转动中高轮廓凸轮(27)压在吊环活塞(4)上;所述的液压缸体(2)上设有第一进油道(8)、第二进油道(11)、第一泄油道(21)和第一次泄油道(20),所述的气缸盖上的液压缸导管(I)上设 On), a compression piston (9) and a hydraulic separator cylinder (24), the valve end of the piston (13) between the hydraulic cylinder limit units (25) are equipped with a buffer spring (12), the said check valve (18) is mounted on a hydraulic separator cylinder (24), the hydraulic cylinder pressure chamber (19) to the hydraulic cylinders of the hydraulic oil pressure chamber (17) through a one-way flow valve (18), the said cylinder spring (14) set at the end of the valve piston (13) rod, one end thereof abuts against the rear end of the cylinder block (2), the dual profile of the cam (3) is a low-profile cam (28 ) connected to the high profile of the cam (27) and as an integral structure, a double profile cams (3) at the front end of the cylinder block (2), under the action of the cylinder-spring body (14) of the profile of the cam-bis (3 the front end) and the cylinder block (2) is pressed together, wherein the low profile of the cam (28) is pressed against the cylinder block (2), the high profile of the cam in rotation (27) presses on the piston rings (4); the the cylinder block is provided with a first oil feed passage (8) (2), a second oil feed passage (11), a first drain passage (21) and the first drain passage (20), said hydraulic cylinder cylinder head duct (I) is provided on the 第三进油道(7)、第四进油道(10)和第三泄油道(22),所述双轮廓凸轮(3)上设有第二次泄油道(29),当液压缸体(2)处于静止时,第一进油道(8)两端分别与第三进油道(7)和液压缸低压腔(23)连接相通,第二进油道(11)两端分别与第四进油道(10)和液压缸中压腔(19)连接相通;第一泄油道(21)与第三泄油道(22)连接相通与液压缸低压腔(23)不相通,双轮廓凸轮(3)开始回转到其回转90度过程中,第一次泄油道(20)两端分别与液压缸高压腔(17)和第二次泄油道(29)连接相通;所述的吊杯活塞(4)上设有防止弹簧腔(6)内存入机油的第四泄油道(26)。 The third oil feed passage (7), a fourth oil inlet passage (10), and a third drainage channel (22), provided with the double contour cam (3) a second drain passage (29), when the hydraulic pressure a cylinder (2) when at rest, a first oil inlet passage (8) are connected to both ends of the oil feed passage in communication with the third (7) and the low pressure chamber of the hydraulic cylinder (23), (11) across the second oil feed passage the oil feed passage, respectively, and the fourth (10) and the hydraulic cylinder pressure chamber (19) communicating; communication with the cylinder connected to the first low-pressure chamber drain passage (21) and the third drain passage (22) (23) is not communication, bis profile of the cam (3) starts its rotation back to 90 degrees during the first drain passage (20) are connected to both ends of the high pressure chamber of the hydraulic cylinder (17) and the second drain passage (29) communicating ; hanging said cup is provided to prevent the piston (4) a spring chamber (6) into the memory of a fourth oil drainage passage (26).
  2. 2.根据权利要求I所述的无级可变气门升程机构,其特征在于所述的液压缸体(2)上设有液压缸高压腔(17)快速泄油的第二泄油道(15)。 The I according infinitely variable valve lift mechanism as claimed in claim, wherein said cylinder block is provided on the high pressure chamber of the hydraulic cylinder (2) (17) fast drainage second drain passage ( 15).
  3. 3.根据权利要求I所述的无级可变气门升程机构,其特征在于所述的液压缸体内限位台(25)与气门端活塞(13)之间设有为消除气门间隙的间隙(16)。 The I according infinitely variable valve lift mechanism as claimed in claim, wherein said stopper hydraulic cylinder units (25) and the end of the piston valve is provided to eliminate the gap between the valve (13) a gap (16).
  4. 4.无级可变气门升程机构的控制方法,其特征在于: A、发动机低转速时a、双轮廓凸轮的凸圆未压整个机构,机油经第一进油道(8)、第二进油道(11)、第三进油道(7)、第四进油道(10)进入液压缸体(2)内,此时压缩活塞(9)在液压缸低压腔(23)和液压缸中压腔(19)的面积不同,在压力差和平衡弹簧(5)的作用下,压缩活塞(9)的位置会在机构中随机油压力的变化而变化,由于此时压力很小,压缩活塞使提升量很小; b、双轮廓凸轮的凸圆开始压整个机构,低轮廓凸轮(28)压液压缸体(2),液压缸高压腔(17)处于密封,形成刚性体,推动气门的原始期提升量,同时高轮廓凸轮(27)压吊杯活塞(4),机构的所有进油道和泄油道封闭,形成刚性体,将液压缸中压腔(19)的机油经单向阀(18)压进液压缸高压腔(17),气门端活塞(13)推动气门来增加附加提升量 4. steplessly variable valve lift mechanism of the process control method, wherein: A, low engine speed a, the convex profile of the cam is not pressed bis entire mechanism, motor oil through the first oil feed passage (8), a second the oil feed passage (11), the third oil feed passage (7), a fourth oil inlet passage (10) into (2) of the hydraulic cylinder, when the compression piston (9) in the low pressure chamber of the hydraulic cylinder (23) and a hydraulic different areas cylinder pressure chamber (19), under pressure differential and balancing spring (5), the compressed position of the piston (9) will vary with the oil pressure variation mechanism, since the pressure is very small at this time, so that the compression piston lift amount is small; B, a double convex profile of the cam comes to press the entire mechanism, the low profile of the cam (28) against the cylinder block (2), a high pressure cylinder chamber (17) is sealed to form a rigid body, to promote lift amount of the original of the valve, while the high profile of the cam (27) against lifting the cup of the piston (4), all the oil inlet passage means and the drain passage is closed to form a rigid body, the hydraulic cylinder pressure chamber (19) oil by a check valve (18) is pressed into the high pressure chamber of the hydraulic cylinder (17), the valve end of the piston (13) pushes on the valve lift amount to add additional 随着压缩活塞(9)的推动,第一泄油道(21)和第三泄油道(22)相对,泄油通道打开,液压缸低压腔(23)开始泄油变成不是刚性,气门的继续提升量由低轮廓凸轮(28)推动,此时液压缸高压腔(17)不变化,液压缸中压腔(19)在缓冲弹簧(12)和泄油过程的共同作用下也维持不变; C、双轮廓凸轮的凸圆达到最高点,液压缸低压腔(23)通过第三泄油道(22)泄油完毕,液压缸高压腔(17)为封闭,进入液压缸高压腔的机油量少,第二泄油道(15)并未开启,在液压缸体弹簧(14)、缓冲弹簧(12)、平衡弹簧(5)的作用下整个机构随双轮廓凸轮移动,此时第一次泄油道(20)即将开启; d、双轮廓凸轮开始回转,在此之前低轮廓凸轮(28)上的第二次泄油道(29)与第一次泄油道(21)相对,泄油,将液压缸高压腔少量机油泄出; e、双轮廓凸轮完全回转至凸轮最高点与机构中 As the compression pushes the piston (9), a first drain passage (21) and a third drainage channel (22) opposite, the oil release passage is opened, the low pressure chamber of the hydraulic cylinder (23) starts to become drain is not rigid, the valve continues to promote a low lift amount of the cam profile (28), this time the high pressure chamber of the hydraulic cylinder (17) does not change, the hydraulic cylinder pressure chamber (19) in the buffer spring (12) and interacts drainage process is maintained without variable; C, double-convex profile of the cam reaches the highest point, the low pressure chamber of the hydraulic cylinder (23) is completed by a third drain drain passage (22), a high pressure cylinder chamber (17) is closed, the high pressure chamber into the hydraulic cylinder a small amount of oil, a second oil drain passage (15) is not open, the hydraulic cylinder spring (14), the buffer spring (12), the whole mechanism moves with the double contour cam under the action of a balancing spring (5), in which case the first a drain passage (20) is about to open; D, double contour cam starts to rotate, before the low profile of the cam (28) of the second drain passage (29) and the first drain passage (21) relative to , drain, the high pressure chamber of the hydraulic cylinder small amount of oil escape; E, double cam profile of the cam completely slewed highest point mechanism 成180度时,进油道再次开启,开始进油,转速不同,进油压力不同,压缩活塞(9)的位置不同,升程量不同; B、发动机中转速时a、双轮廓凸轮的凸圆未压整个机构,机油经第一进油道(8)、第二进油道(11)、第三进油道(7)、第四进油道(10)进入液压缸体(2)内,由于此时压力不大,压缩活塞(9)的提升量不大; b、双轮廓凸轮的凸圆开始压整个机构,由于压缩活塞(9)的位置升高,第一泄油道(21)和第三泄油道(22)相对的时间要比发动机低转速时晚,从液压缸中压腔(19)压入液压缸高压腔(17)的机油也比发动机低转速时要多,其升程量比发动机低转速时要多; C、双轮廓凸轮的凸圆达到最高点,液压缸低油腔(23)通过第一泄油道(21)和第三泄油道(22)泄油完毕,液压缸高压腔(17)为封闭,在液压缸体弹簧(14)、缓冲弹簧(12)、平衡弹簧(5)的作用下 When 180 degrees, the oil feed passage opened again to start into the oil, different speeds and different feed oil pressure, different compression position of the piston (9), up to varying amounts; B, when the engine rotational speed a, the double profile of the cam projection It means not the entire circular pressure, the oil through the first oil feed passage (8), a second oil feed passage (11), the third oil feed passage (7), a fourth oil inlet passage (10) into the cylinder block (2) inside, since the pressure is not at this time, the lift amount of the compression piston (9) is not; B, a double convex profile of the cam comes to press the entire mechanism, increase of the compression piston (9) position, the first drain passage ( 21) and a third drainage channel (22) relative time later than the low engine speed, the hydraulic cylinder from the pressure chamber (19) into the high pressure chamber of the hydraulic cylinder (17) when the oil than at low engine speeds to be more which lift than the low speed of the engine to be more; C, double-convex profile of the cam reaches the highest point, low oil hydraulic cylinder chamber (23) through a first drain passage (21) and a third drainage channel (22 ) drain is completed, the high-pressure cylinder chamber (17) is closed, the hydraulic cylinder spring (14), the buffer spring (12), under the action of a balancing spring (5) 个机构随双轮廓凸轮移动,此时第一次泄油道(20)即将开启; d、双轮廓凸轮开始回转,在此之前低轮廓凸轮(28)上的第二次泄油道(29)与第一次泄油道(20)相对,泄油,泄油即将完毕; e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时,在此之前,液压缸高压腔(17)机油不多,泄油过程完毕,进油道开始进油,进油压力不同,压缩活塞(9)的位置不同,升程量不同; C、发动机高转速时a、双轮廓凸轮的凸圆未压整个机构,机油经第一进油道(8)、第二进油道(11)、第三进油道(7)、第四进油道(10)进入整个机构,压力大,压缩活塞的提升量很大; b、双轮廓凸轮的凸圆开始压整个机构,压缩活塞(9)位置接近最高点,第一泄油道(21)与第三泄油道(22)并未相对,整个机构的液压缸低压腔(23)、液压缸中压腔(19)、液压缸高压腔(17)都密封, With a double contour cam mechanism moves, when the first oil drain passage (20) is about to open; D, double contour cam starts to rotate, before the second drainage passage on the low profile of the cam (28) (29) and the first drain passage (20) opposite, drain, drain soon completed; E, go back to completely double contour cam of the cam mechanism and the highest point of the center of 180 degrees, before this, a high pressure cylinder chamber (17) much oil, drain process is complete, the oil feed passage into the oil starts, the oil pressure into different different compression position of the piston (9), up to varying amounts; C, the high engine speed a, the double-convex profile of the cam is not pressing the whole bodies, the oil through the first oil feed passage (8), a second oil feed passage (11), the third oil feed passage (7), a fourth oil inlet passage (10) into the entire mechanism, pressure, compression piston lift amount is large; B, a double convex profile of the cam comes to press the entire mechanism, the compression piston (9) a position close to the highest point, the first drain passage (21) and the third drain passage (22) not opposing, means the entire low pressure chamber of the hydraulic cylinder (23), the hydraulic cylinder pressure chamber (19), a high pressure cylinder chamber (17) are sealed, 液压缸中压腔(19)压入液压缸高压腔(17)的机油比发动机中转速时多,其升程量比发动机中转速多; C、双轮廓凸轮的凸圆达到最高点,第一泄油道(21)和第三泄油道(22)相对,液压缸低压腔(23)开始泄油,进入液压缸高压腔机油量达设定最高量,液压缸高压腔(17)通过第二泄油道(15)与汽车缸体的空隙泄油,第一次泄油道(20)即将泄油,在液压缸体弹簧(14)、缓冲弹簧(12)、平衡弹簧(5)的作用下整个机构随双轮廓凸轮移动; d、双轮廓凸轮开始回转,在此之前低轮廓凸轮(28)上的第二次泄油道(29)与第一次泄油道(20)相对,泄油,泄完液压缸高压腔未泄完的油;e、双轮廓凸轮完全回转至凸轮最高点与机构中心成180度时,在完全回转之前,液压缸高压腔(17)完全泄完,进油道开始进油,转速不同,进油压力不同,压缩活塞(9)的位置不同,升程量 Hydraulic cylinder pressure chamber (19) into the high pressure chamber of the hydraulic cylinder (17) than the oil when the engine rotational speed, which the lift speed of the engine than the plurality; C, double-convex profile of the cam reaches the highest point, the first drain passage (21) and a third drainage channel (22) opposite, the low-pressure cylinder chamber (23) starts drain, the high pressure chamber into the oil capacity of the hydraulic cylinder to set a maximum amount, the high-pressure cylinder chamber (17) through a first drain two voids drain passage (15) and the cylinder automobile, the first oil drain passage (20) is about to drain, the hydraulic cylinder spring (14), the buffer spring (12), a balancing spring (5) the entire mechanism for moving the action with the double contour cam; D, double contour cam starts to rotate, the low profile of the cam before the second oil drain passage (29) (28) and the first drain passage (20) relatively, drain, complete drainage cylinder high pressure chamber is not completely drain the oil; E, double contour cam completely slewed cam highest point means the center of 180 degrees, until complete revolution, the cylinder pressure chamber (17) is completely finished vent, the oil feed passage into the oil starts, different speed, into the oil pressure is different, a different compression position of the piston (9), the lift amount 不同。 different.
CN 200910220681 2009-12-11 2009-12-11 Steplessly variable valve lift mechanism and control method CN102094692B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 200910220681 CN102094692B (en) 2009-12-11 2009-12-11 Steplessly variable valve lift mechanism and control method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 200910220681 CN102094692B (en) 2009-12-11 2009-12-11 Steplessly variable valve lift mechanism and control method

Publications (2)

Publication Number Publication Date
CN102094692A true CN102094692A (en) 2011-06-15
CN102094692B true CN102094692B (en) 2013-01-02

Family

ID=44127938

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 200910220681 CN102094692B (en) 2009-12-11 2009-12-11 Steplessly variable valve lift mechanism and control method

Country Status (1)

Country Link
CN (1) CN102094692B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102241376A (en) * 2011-06-17 2011-11-16 无锡华联科技集团有限公司 Mobile hydraulic jacking device
CN103953411B (en) * 2014-03-21 2016-06-29 哈尔滨工程大学 Two pressurized exhaust valve mechanism
CN106762000A (en) * 2016-12-22 2017-05-31 天津大学 Hydraulic electrodeless variable valve mechanism based on split rocker arm

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2546635Y (en) 2002-05-30 2003-04-23 长安汽车(集团)有限责任公司 Variable air door lift mechanism
CN1804383A (en) 2006-01-19 2006-07-19 山东大学 Valve timing continuously variable internal combustion engine valve system
CN101078375A (en) 2007-07-27 2007-11-28 奇瑞汽车有限公司 Gasoline engine valve lift and the phase variable system
CN201588701U (en) 2009-12-11 2010-09-22 吴爽 Stepless variable valve lifting mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2546635Y (en) 2002-05-30 2003-04-23 长安汽车(集团)有限责任公司 Variable air door lift mechanism
CN1804383A (en) 2006-01-19 2006-07-19 山东大学 Valve timing continuously variable internal combustion engine valve system
CN101078375A (en) 2007-07-27 2007-11-28 奇瑞汽车有限公司 Gasoline engine valve lift and the phase variable system
CN201588701U (en) 2009-12-11 2010-09-22 吴爽 Stepless variable valve lifting mechanism

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JP特开2005-69132A 2005.03.17

Also Published As

Publication number Publication date Type
CN102094692A (en) 2011-06-15 application

Similar Documents

Publication Publication Date Title
CN101149002A (en) Compressed air engine electrically driven whole-variable valve actuating system
CN101476490A (en) Expansion ratio adjustable pneumatic engine for automobile and its exhaust pressure control method
CN101936198A (en) Cam oil-supply type electro-hydraulic valve driving system
CN201162550Y (en) Electric-hydraulic control variable-distribution apparatus of diesel engine
US5327857A (en) Vehicular drive system using stored fluid power for improved efficiency
CN201593488U (en) Hydraulic piston type gas compressor for natural gas secondary filling stations
CN104989458A (en) Totally-changeable intake and exhaust mechanism of compressed air engine and method of mechanism
US20100236517A1 (en) Four-cycle engine
CN101403342A (en) Engine with variable compression ratio
CN201705395U (en) Engine for compressed air-powered car
US20090199789A1 (en) On demand, stored, positive pressurized air injection for internal combustion engines combustion chambers
CN105370389A (en) Conical centrifugal tensile mechanism
CN101215978A (en) Engine air valve controlling mechanism
US6341585B1 (en) Variable inlet valve damper for an internal combustion engine
CN101446214A (en) Continuously adjustable mechanical hydraulic valve lift device
CN102105657A (en) A control arrangement in a piston engine
CN101377138A (en) Sliding valve type two-mode engine intake valve delaying shutdown system
CN1959072A (en) Electrohydraulic controlled continuously variable gas distribution timing system in internal-combustion engine
CN202628286U (en) Air inlet valve control mechanism of closing cylinder in multi-cylinder engine cylinder-stopping oil-saving system
CN201261386Y (en) Pressure device special for air hybrid automobile
CN2311615Y (en) Waste gas turbine energy recovery apparatus for internal combustion engine
CN1529041A (en) Hydraulic distributing mechanism for engine rotary valve
CN104329164A (en) Free piston engine
US8037873B2 (en) Residual burnt gas scavenging method with double intake valve lift in a direct-injection supercharged internal-combusion engine, notably of diesel type
CN102966403A (en) Device for adjusting lift of intake valve of supercharged engine

Legal Events

Date Code Title Description
C06 Publication
C10 Entry into substantive examination
C14 Grant of patent or utility model
EXPY Termination of patent right or utility model