WO2023092941A1 - 专用固定式双活塞液压发动机气门驱动装置 - Google Patents

专用固定式双活塞液压发动机气门驱动装置 Download PDF

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Publication number
WO2023092941A1
WO2023092941A1 PCT/CN2022/089490 CN2022089490W WO2023092941A1 WO 2023092941 A1 WO2023092941 A1 WO 2023092941A1 CN 2022089490 W CN2022089490 W CN 2022089490W WO 2023092941 A1 WO2023092941 A1 WO 2023092941A1
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WIPO (PCT)
Prior art keywords
oil
valve
piston
driving
drive
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2022/089490
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English (en)
French (fr)
Inventor
唐华学
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jiangsu Jointek Precision Machinery Co Ltd
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Jiangsu Jointek Precision Machinery Co Ltd
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
Application filed by Jiangsu Jointek Precision Machinery Co Ltd filed Critical Jiangsu Jointek Precision Machinery Co Ltd
Priority to EP22897041.4A priority Critical patent/EP4339426B1/en
Publication of WO2023092941A1 publication Critical patent/WO2023092941A1/zh
Priority to US18/485,338 priority patent/US11970959B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • 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
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • the invention relates to the technical field of engine valve driving devices, in particular to a special fixed double-piston hydraulic engine valve driving device.
  • compression release engine brakes The concept and operation of compression release engine brakes is well known in the heavy commercial vehicle industry. Cost, power, reliability and engine change requirements are often factors in determining whether engine braking will be employed. There are several different types of compression release engine brakes in practice, with dedicated cam engine brake systems being favored due to their independence and high performance.
  • Existing engine valve drive devices integrated in the valve train mainly include dedicated or integrated rocker brakes. These rocker brakes mostly still partly or completely swing with other moving parts in the valve train when they are in use or closed, requiring additional wear-resistant and biasing devices, which increases the complexity and cost of the system; When moving the valve (driving the valve), because the swing of the rocker arm will also generate adverse side loads on the brake valve, causing excessive wear and damage to the valve, which will affect the performance and reliability of the engine.
  • the technical problem to be solved by the present invention is: in order to solve the rocker arm brake swinging with other moving parts in the valve train in the prior art, additional wear-resistant and biasing devices are needed, and problems such as eccentric wear and fracture failure caused by the lateral load of the valve are needed. , now provides a special fixed double-piston hydraulic engine valve driving device.
  • a special fixed double-piston hydraulic engine valve driving device comprising:
  • the special driving cam is located on one side of the positive power cam of the engine, and has a base circle and a driving lift boss on the base circle.
  • the positive power cam is used to drive the displacement of the valve bridge through the positive power rocker arm;
  • a driver having a primary piston slidably mounted in the primary piston bore and a secondary piston slidably mounted in the secondary piston bore;
  • the drive oil circuit is kept connected between the main piston hole and the auxiliary piston hole;
  • the drive oil circuit communicates with the oil supply circuit through the control valve;
  • the driver is fixedly connected to the rocker shaft; that is, the driver does not swing with the dedicated drive cam, thereby avoiding the rotation between the driver and the rocker shaft. And produce sports wear, improve engine output power.
  • the driver is provided with a shaft hole matching the rocker shaft, the rocker shaft passes through the shaft hole, the driver is threaded with a positioning pin, and the driver It is fixedly connected with the rocker shaft through the positioning pin.
  • the driver is provided with an active elastic element, which is used to drive the main piston to retract when the drive oil circuit drains oil;
  • the special drive cam is separated from the main piston when it is not working, which effectively reduces the wear between the special drive cam and the main piston and the noise of the engine, reduces friction loss, and improves the engine output power.
  • the main piston can be extended by overcoming the elastic force of the active elastic element through the oil filling of the drive oil circuit, and contacted with the special driving cam, so that the main piston can automatically extend or retract with the construction of the hydraulic linkage.
  • the driving lift of the special driving cam is not affected by the initial gap setting, stable and consistent, and easy to use and maintain.
  • the driver is provided with a driven elastic element for moving the auxiliary piston away from the driving valve.
  • the oil pressure of the piston maintains the auxiliary piston in the retracted position, and drives the auxiliary piston to retract when the oil is drained from the drive oil circuit.
  • a safety oil drain hole is opened on the inner peripheral wall of the auxiliary piston;
  • the auxiliary piston When the auxiliary piston moves beyond the maximum extension position, the auxiliary piston no longer blocks the safety oil drain hole, and the driving oil circuit communicates with the safety oil drain hole through the auxiliary piston hole.
  • the driving valve is connected to the driven pin
  • the driver is provided with an adjusting bolt for adjusting the position of the auxiliary piston.
  • the oil supply circuit supplies oil to the drive oil circuit in one direction through the control valve.
  • the oil supply circuit includes a control oil supply channel and a drive oil supply channel, and the drive oil supply channel supplies oil to the drive oil circuit in one direction through the control valve;
  • the control oil supply channel is used to provide different forces for the control valve to open or close the control valve when the internal oil pressure changes.
  • the control valve has a one-way oil supply function and a pressure relief function
  • the control valve includes a valve body, an elastic return element and a one-way mechanism
  • the valve body is provided with a main oil passage, an auxiliary oil passage and A communication passage
  • the valve body is slidably installed in the valve hole
  • the main oil passage communicates with the auxiliary oil passage through the communication passage
  • the one-way mechanism is arranged in the communication passage to allow the oil in the main oil passage to flow in one direction Entering the auxiliary oil passage
  • the elastic return element is used to drive the valve body to reset;
  • An oil drain channel is opened on the driver or the rocker shaft to control the communication between the oil supply channel and one end of the valve hole;
  • a pressure relief chamber is formed between the valve body and the valve hole, and when the valve body is in the closed position, the driving oil circuit communicates with the oil relief passage through the pressure relief chamber;
  • valve body is provided with a pressure relief cavity, and when the valve body is in the closed position, the driving oil circuit communicates with the oil discharge channel through the pressure relief cavity.
  • control valve is installed on the rocker shaft or the driver.
  • the special fixed double-piston hydraulic engine valve driving device of the present invention adopts the design that the main piston and the auxiliary piston are all integrated on a special driver, which reduces oil consumption, and is equipped with a special driving cam design, thereby realizing
  • the optimized design of the valve driving device that operates independently of the positive power valve mechanism reduces the interference and influence of the valve driving device on the operation of the positive power valve mechanism;
  • the auxiliary piston can completely transmit the driving force to the driving valve along the direction of the driving valve movement , to avoid the side load of the actuated valve.
  • the installation position of the driver is not affected by the position of the driving valve, which is convenient for flexible arrangement.
  • Fig. 1 is the schematic diagram when the special-purpose fixed double-piston hydraulic engine valve driving device of the present invention is driving the oil circuit to drain oil;
  • Fig. 2 is a schematic diagram when hydraulic linkage is formed between the main piston and the auxiliary piston in the present invention
  • Fig. 3 is the schematic diagram when the special drive cam drives the displacement of the drive valve in the present invention
  • Fig. 4 is a schematic diagram when the positive power cam drives the displacement of the valve bridge in the present invention
  • Fig. 5 is a three-dimensional schematic diagram of the special fixed double-piston hydraulic engine valve driving device of the present invention.
  • Fig. 6 is a top view schematic diagram of the special fixed double-piston hydraulic engine valve driving device of the present invention.
  • Fig. 7 is a schematic diagram of explosion when the driver, control valve and rocker shaft of the present invention cooperate with each other;
  • Fig. 8 is the schematic diagram that main piston is installed on the driver among the present invention.
  • Fig. 9 is a schematic diagram of the control valve installed on the driver in the present invention.
  • Fig. 10 is a schematic diagram of the auxiliary piston being installed on the driver in the present invention.
  • Oil supply passage, 5-1 control oil supply passage, 5-2, drive oil supply passage;
  • a special fixed double-piston hydraulic engine valve driving device the engine is a four-stroke engine, the driving valve 15 and the non-driving valve 16 of the valve group are exhaust valves in the engine, and the cam of the engine A positive power cam 18 is installed on the shaft;
  • the positive power valve mechanism refers to the structure that the positive power cam 18 of the engine drives the displacement of the valve bridge 20 through the positive power rocker arm 1, which is a conventional technology.
  • the positive power cam 18 turns to the main lift boss 18-1 to cooperate with the positive power rocker arm 1, and the main lift boss 18-1 pushes the positive power rocker arm 1 , the displacement of the valve bridge 20 is driven by the positive power rocker arm 1, so that the displacement of the driving valve 15 and the non-driving valve 16 are simultaneously driven by the valve bridge 20 to simultaneously open the driving valve 15 and the non-driving valve 16;
  • the valve drive has:
  • the special-purpose drive cam 19 is installed on the camshaft and is positioned at one side of the positive power cam 18 of the engine.
  • the special-purpose drive cam 19 has a base circle portion 19-1 and a drive lift boss 19-2 positioned on the base circle portion 19-1; Specifically, there are two drive lift bosses 19-2, which are the exhaust gas recirculation drive lift boss 19-2 and the compression release drive lift boss 19-2.
  • the exhaust gas recirculation drive lift boss 19-2 is used to make the drive valve 15 perform exhaust gas recirculation. Cyclic operation, compression release drive lift boss 19-2 is used to make the drive valve 15 perform compression release operation;
  • the driver 4 has a primary piston 2 slidably installed in the primary piston hole 4-1 and a secondary piston 3 slidably mounted in the secondary piston hole 4-2;
  • the driving oil circuit 4-3 is opened in the driver 4 and kept connected between the main piston hole 4-1 and the auxiliary piston hole 4-2;
  • control valve 6 the control valve 6 is installed on the rocker shaft 17 or the driver 4, if the control valve 6 is integrated in the rocker shaft 17, it can save space; the driving oil circuit 4-3 passes through the control valve 6 and the oil supply circuit 5 connectivity;
  • the driver 4 itself is fixedly connected to the rocker shaft 17; for example, the driver 4 is provided with a shaft hole 4-4 that matches the rocker shaft 17, and the rocker shaft 17 passes through the shaft hole 4-4, and the driver 4
  • the upper thread is connected with a positioning pin 7, and the positioning pin 7 can fix the driver 4 itself on the rocker shaft 17 by abutting against the outer peripheral wall of the rocker shaft 17 or being embedded in the rocker shaft 17; the drive oil circuit 4 -3 then can pass alignment pin 7 or not pass alignment pin 7.
  • the driver 4 is provided with an active elastic element 8, which is used to drive the main piston 2 to retract when the oil is drained from the drive oil circuit 4-3;
  • the main piston 2 When the control valve 6 is opened, the main piston 2 stretches out to contact the special driving cam 19 under the action of hydraulic pressure; when the control valve 6 is closed, the main piston 2 retracts to separate from the special driving cam 19 under the action of the active elastic element 8;
  • the element 8 can adopt a compression spring, and the specific installation structure can adopt the following method: the opening of the main piston hole 4-1 faces downward, the lower end of the main piston 2 is fixed with an active limiter 9, and one end of the active elastic element 8 is against the active limiter. The other end of the position member 9 is against the main piston 2, and when the main piston 2 is in contact with the active limiter 9, the main piston 2 reaches the maximum stroke of the downward displacement.
  • the driver 4 is provided with a driven elastic element 11 for moving the secondary piston 3 away from the driving valve 15, and the driven elastic element 11 needs to provide
  • the oil pressure on the auxiliary piston 3 during oil filling maintains the auxiliary piston 3 in the retracted position, and drives the auxiliary piston 3 to retract when the oil is drained from the drive oil circuit 4-3;
  • a safety oil drain hole 4-6 is provided on the inner peripheral wall of the auxiliary piston hole 4-2;
  • the auxiliary piston 3 When the auxiliary piston 3 moves to the maximum extension position, the auxiliary piston 3 no longer blocks the safety oil drain hole 4-6, and the driving oil circuit 4-3 communicates with the safety oil drain hole 4-6 through the auxiliary piston hole 4-2, so as to Exclude excess machine oil accumulated in the drive oil circuit 4-3.
  • This embodiment also includes a driven pin 10 opposite to the auxiliary piston 3, and the driving valve 15 is connected to the driven pin 10; specifically, the driven pin 10 has a stepped structure, and the stepped surface 10-1 of the driven pin 10 is against the valve.
  • the upper end of the driven pin 10 protrudes from the upper side of the valve bridge 20, the upper end of the driving valve 15 is against the driven pin 10, and the upper end of the non-driving valve 16 is against the valve bridge 20;
  • the driver 4 is provided with an adjusting bolt 13 for adjusting the position of the auxiliary piston 3;
  • the position can be adjusted;
  • the driven elastic element 11 can adopt a compression spring, and the specific installation structure can adopt the following method: the opening of the auxiliary piston hole 4-2 faces downward, and the upper end of the auxiliary piston 3 is fixed with a driven limiter 12, the lower end of the adjusting bolt 13 extends into the auxiliary piston 3, the upper end of the driven elastic element 11 is against the driven limiter 12, and the lower end of the driven elastic element 11 is against the lower end of the adjusting bolt 13, thereby realizing the auxiliary
  • the piston 3 can move upwards under the action of the driven elastic element 11 .
  • control valve 6 is set so that when it is opened, the oil supply circuit 5 supplies oil to the drive oil circuit 4-3 in one direction through the control valve 6;
  • the oil supply passage 5 includes a control oil supply passage 5-1 and a driving oil supply passage 5-2, and the driving oil supply passage 5-2 supplies oil to the driving oil passage 4-3 in one direction through the control valve 6;
  • the control oil supply channel 5-1 is used to provide different forces for the control valve 6 to realize the opening or closing of the control valve 6 when the internal oil pressure changes;
  • the control valve 6 includes a valve body 6-1, an elastic return element 6-2 and a one-way mechanism
  • the valve body 6-1 is provided with a main oil passage 6-13 and an auxiliary oil passage 6 -11 and the communication passage 6-12
  • the valve body 6-1 is slidably installed in the valve hole 17-1
  • the main oil passage 6-13 communicates with the auxiliary oil passage 6-11 through the communication passage 6-12
  • the one-way mechanism is set on
  • the communication passage 6-12 is used to allow the oil in the main oil passage 6-13 to enter the auxiliary oil passage 6-11 in one direction.
  • the one-way mechanism includes an elastic element 6-4 and a one-way ball 6-5.
  • the element 6-4 can specifically adopt a compression spring, one end of which is against the inner wall of the auxiliary oil passage 6-11, and the other end is against the one-way ball 6-5, and the one-way ball 6-5 is against the communication channel 6-12 to prevent
  • the oil in the auxiliary oil passage 6-11 enters the main oil passage 6-13 through the communication passage 6-12, but it can allow the oil in the main oil passage 6-13 to flow to the auxiliary oil passage 6 through the communication passage 6-12.
  • a one-way valve can also be directly used instead of a one-way mechanism;
  • the elastic return element 6-2 specifically adopts a compression spring, which is used to drive the valve body 6-1 to reset.
  • One end of the elastic return element 6-2 is against the valve body 6-1, and the other end is against the rocker shaft 17 or installed on the rocker shaft. Circlip on the arm shaft 17;
  • the driver 4 or the rocker shaft 17 is provided with an oil drain channel 4-5, and the control oil supply channel 5-1 and the elastic return element 6-2 are respectively located at both ends of the valve hole 17-1;
  • a pressure relief chamber 6-3 is formed between the valve body 6-1 and the valve hole 17-1.
  • the driving oil circuit 4-3 passes through the pressure relief chamber 6-3 and Oil drain channel 4-5 is connected;
  • valve body 6-1 is provided with a pressure relief chamber 6-3, and when the valve body 6-1 is in the closed position, the driving oil passage 4-3 communicates with the oil relief passage 4-5 through the pressure relief chamber 6-3.
  • the camshaft of the engine drives the positive power cam 18 and the special driving cam 19 to rotate;
  • the electromagnetic valve of the engine is closed, as shown in Figure 1, the valve body 6-1 moves to the closed position under the action of the elastic return element 6-2, the control valve 6 is in the closed state, and the oil circuit 4-3 is driven to drain, and the There is no oil pressure inside, the main piston 2 resets under the action of the active elastic element 8, and separates from the special driving cam 19, the auxiliary piston 3 resets under the action of the driven elastic element 11, and separates from the driven pin 10, and the special driving cam
  • the driving lift of 19 is not transmitted, only when the positive power cam 18 turns to the main lift boss 18-1 and contacts the positive power rocker arm 1, the positive power rocker arm 1 rotates to drive the displacement of the valve bridge 20, and simultaneously opens the drive valve 15 and The non-driven valve 16 completes the normal positive power lift of the valve;
  • the solenoid valve of the engine is opened, as shown in Figure 2, the oil supply passage 5-1 is controlled to fill the bottom of the valve hole 17-1, the valve body 6-1 is pushed to the open position, and the oil supply passage 5-2 is driven in one direction
  • the drive oil circuit 4-3 supplies oil, and a hydraulic linkage relationship is formed between the main piston 2 and the auxiliary piston 3, and the main piston 2 stretches out to contact the special driving cam 19 under hydraulic pressure; as shown in Figure 3, when the special driving cam 19 When the driving lift boss 19-2 is in contact with the main piston 2, the driving lift boss 19-2 pushes the main piston 2, and the auxiliary piston 3 extends downwards to contact and push the driven pin 10, and is connected to the driven pin 10
  • the drive valve 15 can be moved and opened, and the engine is opened by the lift of the special drive cam 19; as shown in Figure 4, when the positive power cam 18 began to turn to the positive power lift, the positive power rocker Pushing down the valve bridge 20, the driving valve 15 and the non-driving valve 16 realize positive work lift.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

提供一种专用固定式双活塞液压发动机气门驱动装置，包括专用驱动凸轮（19）、驱动器（4）、驱动油路（4-3）及控制阀（6），控制阀（6）开启时，主活塞（2）与副活塞（3）之间保持液压联动，控制阀（6）关闭时，驱动油路（4-3）通过控制阀（6）泄油；发动机气门驱动装置将主活塞（2）和副活塞（3）全部集成在专用的驱动器（4）上，减少了机油消耗，并配以专用驱动凸轮（19）的设计，从而实现了与正功气门机构分别独立运作的气门驱动装置的优化设计，故而降低了气门驱动装置对正功气门机构运作的干涉和影响；副活塞（3）完全沿气门运动方向将驱动力传动至驱动气门（15），避免了驱动气门（15）的侧向载荷。驱动器（4）安装位置不受驱动气门位置的影响，便于灵活布置。

Description

专用固定式双活塞液压发动机气门驱动装置 技术领域
本发明涉及发动机气门驱动装置技术领域，尤其是一种专用固定式双活塞液压发动机气门驱动装置。
背景技术
压缩释放发动机制动器的概念和操作在重型商用车辆工业中是众所周知的。成本，功率，可靠性和发动机更改要求经常是确定是否将采用发动机制动器的影响因素。在实际应用中存在几种不同类型的压缩释放式发动机制动器，其中专用凸轮式发动机制动系统由于其独立性及高性能受到青睐。
现有的集成在气门机构中的发动机气门驱动装置主要有专用或集成的摇臂式制动器。这些摇臂式制动器无论在使用或关闭时大多仍部分或全部随气门机构中其它运动件摆动，需要附加耐磨和偏压装置，增加了系统的复杂性和成本；摇臂式制动器在打开制动气门(驱动气门)时，因为摇臂的摆动还会对制动气门产生不利的侧向载荷，造成气门过度磨损和损坏，进而影响发动机性能和可靠性。
发明内容
本发明要解决的技术问题是：为了解决现有技术中摇臂式制动器随气门机构中其它运动件摆动，需要附加耐磨和偏压装置，气门侧向载荷引起的偏磨、断裂失效等问题，现提供一种专用固定式双活塞液压发动机气门驱动装置。
本发明解决其技术问题所采用的技术方案是：一种专用固定式双活塞液压发动机气门驱动装置，包括：
专用驱动凸轮，位于发动机正功凸轮的一侧，并具有基圆部和位于基圆部上的驱动升程凸台，所述正功凸轮用于通过正功摇臂带动气门桥位移；
驱动器，具有滑动安装在主活塞孔内的主活塞和滑动安装在副活塞孔内的副活塞；
驱动油路，保持连通在主活塞孔和副活塞孔之间；
以及控制阀，所述驱动油路通过控制阀与供油路连通；
在供油路向驱动油路供油及控制阀开启的状态下，当专用驱动凸轮转至基圆部与主活塞滑动或滚动配合时，主活塞在驱动油路的液压作用下伸出至接触基圆部；当专用驱动凸轮转至驱动升程凸台与主活塞滑动或滚动配合时，控制阀阻断驱动油路与供油路，主活塞与副活塞之间形成液压联动，驱动升程凸台得以通过主活塞带动副活塞位移，使副活塞为发动机驱动气门提供相对气门桥移动的动力；
在控制阀关闭的状态下，驱动油路通过控制阀泄油，主活塞与副活塞之间解除液压联动。
为了避免驱动器与摇臂轴之间的磨损，及减少噪音，进一步地，所述驱动器与摇臂轴固定连接；即，驱动器不随专用驱动凸轮摆动，从而实现避免驱动器与摇臂轴之间因转动而产生运动磨损，提高发动机输出功率。
为了便于制造及简化装配流程，进一步地，所述驱动器上开设有与摇臂轴相匹配的轴孔，所述摇臂轴穿过轴孔，所述驱动器上螺纹连接有定位销，所述驱动器通过定位销与摇臂轴固定连接。
为了降低专用驱动凸轮与主活塞之间的磨损，以及降低噪音，进一步地，所述驱动器上设置有主动弹性元件，用于在驱动油路泄油时带动主活塞回缩；
利用在主动弹性元件的设置，使专用驱动凸轮非工作时与主活塞分离，有效的降低了专用驱动凸轮与主活塞之间的磨损及发动机的噪音，降低摩擦损耗，提高发动机输出功率，专用驱动凸轮工作时又能够通过驱动油路的充油使主活 塞克服主动弹性元件的弹力而伸出，与专用驱动凸轮接触，从而实现主活塞能够随液压联动的构建与否而自动伸出或缩回，无需复杂的控制，专用驱动凸轮的驱动升程不受初始间隙设置影响，稳定一致，使用维护简单。
为了提高驱动气门的打开精度，进一步地，所述驱动器上设置有用于使副活塞朝远离驱动气门方向移动的从动弹性元件，从动弹性元件需提供能够克服在驱动油路充油时对副活塞的油压并维持副活塞处于回缩位置，且在驱动油路泄油时带动副活塞回缩。
为了防止驱动油路累积机油过量，引起副活塞超行程的问题，进一步地，所述副活塞的内周壁上开设有安全泄油孔；
所述副活塞在回缩位置与最大伸出位置之间移动时，副活塞挡住安全泄油孔，驱动油路与安全泄油孔不连通；
所述副活塞移动至越过最大伸出位置时，副活塞不再挡住安全泄油孔，驱动油路通过副活塞孔与安全泄油孔连通。
进一步地，还包括与副活塞相对设置的从动销，所述驱动气门连接在从动销上；
在供油路向驱动油路供油及控制阀开启的状态下，当专用驱动凸轮转至基圆部与主活塞滑动或滚动配合时，副活塞与从动销分离；当专用驱动凸轮转至驱动升程凸台与主活塞滑动或滚动配合时，副活塞能够移动至与从动销接触，并通过从动销推动驱动气门位移；
利用从动弹性元件的设置，克服在驱动油路充油时对副活塞的油压并维持副活塞处于回缩位置并与从动销分离，只有专用驱动凸轮带动主活塞，使主活塞通过液压联动带动副活塞，方可使副活塞克服从动弹性元件的弹力而伸出，以接触并推动从动销，连接在从动销上的驱动气门得以发生移动而打开；
为了提高驱动气门的打开精度，进一步地，所述驱动器上设置有用于调节副活塞位置的调节螺栓。
为了实现精确的液压联动，进一步地，所述控制阀被设置呈在其开启时，供油路通过控制阀单向向驱动油路供油。
为了便于操纵控制阀的开启或关闭，进一步地，所述供油路包括控制供油道和驱动供油道，所述驱动供油道通过控制阀单向向驱动油路供油；
所述控制供油道用于在内部油压变化时为控制阀提供不同的作用力实现控制阀的开启或关闭。
为了实现控制阀具有单向供油功能和泄压功能，进一步地，所述控制阀包括阀体、弹性回位元件以及单向机构，所述阀体上开设有主油道、副油道和连通通道，所述阀体滑动安装在阀孔内，所述主油道通过连通通道与副油道连通，所述单向机构设置在连通通道内，用于允许主油道内的油液单向进入到副油道中，所述弹性回位元件用于带动阀体复位；
所述驱动器或摇臂轴上开设有泄油通道，控制供油道和阀孔的一端连通；
当控制供油道通入到阀孔内的油液在阀体上的压力大于弹性回位元件的弹力时，阀体处于开启位置，驱动供油道与主油道连通，副油道与驱动油路连通，且驱动油路不与泄油通道连通，此状态为，控制阀开启；
当控制供油道通入到阀孔内的油液在阀体上的压力小于弹性回位元件的弹力时，弹性回位元件驱动阀体移动至关闭位置，驱动油路和泄油通道连通，此状态为，控制阀关闭。
进一步地，所述阀体与阀孔之间形成有泄压腔，所述阀体位于关闭位置时，驱动油路通过泄压腔和泄油通道连通；
或者所述阀体上开设有泄压腔，所述阀体位于关闭位置时，驱动油路通过 泄压腔和泄油通道连通。
进一步地，所述控制阀安装在摇臂轴或驱动器上。
本发明的有益效果是：本发明专用固定式双活塞液压发动机气门驱动装置采用将主活塞和副活塞全部集成在专用的驱动器上，减少了机油消耗，并配以专用驱动凸轮的设计，从而实现了与正功气门机构分别独立运作的气门驱动装置的优化设计，故而降低了气门驱动装置对正功气门机构运作的干涉和影响；副活塞能够完全沿驱动气门运动方向将驱动力传动至驱动气门，避免了驱动气门的侧向载荷。驱动器安装位置不受驱动气门位置的影响，便于灵活布置。
附图说明
下面结合附图和实施例对本发明进一步说明。
图1是本发明专用固定式双活塞液压发动机气门驱动装置在驱动油路泄油时的示意图；
图2是本发明中主活塞与副活塞之间形成液压联动时的示意图；
图3是本发明中专用驱动凸轮带动驱动气门位移时的示意图；
图4是本发明中正功凸轮带动气门桥位移时的示意图；
图5是本发明专用固定式双活塞液压发动机气门驱动装置的三维示意图；
图6是本发明专用固定式双活塞液压发动机气门驱动装置的俯视示意图；
图7是本发明驱动器、控制阀及摇臂轴相互配合时爆炸示意图；
图8是本发明中主活塞安装在驱动器上的示意图；
图9是本发明中控制阀安装在驱动器上的示意图；
图10是本发明中副活塞安装在驱动器上的示意图；
图中：1、正功摇臂，2、主活塞，3、副活塞；
4、驱动器，4-1、主活塞孔，4-2、副活塞孔，4-3、驱动油路，4-4、轴孔，4-5、泄油通道，4-6、安全泄油孔；
5、供油路，5-1、控制供油道，5-2、驱动供油道；
6、控制阀，6-1、阀体，6-11、副油道，6-12、连通通道，6-13、主油道，6-2、弹性回位元件，6-3、泄压腔，6-4、弹性元件，6-5、单向球；
7、定位销，8、主动弹性元件，9、主动限位件，10、从动销，10-1、台阶面，11、从动弹性元件，12、从动限位件，13、调节螺栓，15、驱动气门，16、非驱动气门；
17、摇臂轴，17-1、阀孔；
18、正功凸轮，18-1、主升程凸台；
19、专用驱动凸轮，19-1、基圆部，19-2、驱动升程凸台；
20、气门桥。
具体实施方式
现在结合附图对本发明作进一步详细的说明。这些附图均为简化的示意图，仅以示意方式说明本发明的基本结构，因此其仅显示与本发明有关的构成，方向和参照(例如，上、下、左、右、等等)可以仅用于帮助对附图中的特征的描述。因此，并非在限制性意义上采用以下具体实施方式，并且仅仅由所附权利要求及其等同形式来限定所请求保护的主题的范围。
实施例1
如图1-10所示，一种专用固定式双活塞液压发动机气门驱动装置，发动机为四冲程发动机，气门组的驱动气门15和非驱动气门16均为发动机中的排气门，发动机的凸轮轴上安装有正功凸轮18；
本实施例中正功气门机构是指发动机的正功凸轮18通过正功摇臂1带动气门桥20位移的结构，为常规技术，例如：正功凸轮18转至其基圆与正功摇臂1配合时，正功摇臂1和气门桥20均不发生位移，正功凸轮18转至主升程凸台18-1与正功摇臂1配合时，主升程凸台18-1推动正功摇臂1，由正功摇臂1带动气门桥20位移，从而由于气门桥20同时带动驱动气门15和非驱动气门16位移，以同时打开驱动气门15和非驱动气门16；
该气门驱动装置具有：
专用驱动凸轮19，安装在凸轮轴上，且位于发动机正功凸轮18的一侧，专用驱动凸轮19具有基圆部19-1和位于基圆部19-1上的驱动升程凸台19-2；驱动升程凸台19-2具体有两个，分别为废气再循环驱动升程凸台19-2和压缩释放驱动升程凸台19-2，废气再循环驱动升程凸台19-2用于使驱动气门15执行废气再循环操作，压缩释放驱动升程凸台19-2用于使驱动气门15执行压缩释放操作；
驱动器4，具有滑动安装在主活塞孔4-1的主活塞2和滑动安装在副活塞孔4-2内的副活塞3；
驱动油路4-3，开设在驱动器4内，并保持连通在主活塞孔4-1和副活塞孔4-2之间；
以及控制阀6，控制阀6安装在摇臂轴17或驱动器4上，如控制阀6集成在摇臂轴17内，则能够节省空间；驱动油路4-3通过控制阀6与供油路5连通；
在供油路5向驱动油路4-3供油及控制阀6开启的状态下，当专用驱动凸轮19转至基圆部19-1与主活塞2滑动或滚动配合时，主活塞2在驱动油路4-3的液压作用下伸出至接触基圆部19-1；当专用驱动凸轮19转至驱动升程凸台19-2与主活塞2滑动或滚动配合时，控制阀6阻断驱动油路4-3与供油路5， 主活塞2与副活塞3之间形成液压联动，驱动升程凸台19-2得以通过主活塞2带动副活塞3位移，使副活塞3为发动机驱动气门15提供相对气门桥20移动的动力，具体地，副活塞3在发动机正功摇臂1未驱动气门桥20位移的状态下，能够推动驱动气门15位移，使驱动气门15打开；
在控制阀6关闭的状态下，驱动油路4-3通过控制阀6泄油，主活塞2与副活塞3之间解除液压联动。
本实施例中驱动器4自身与摇臂轴17固定连接；例如，驱动器4上开设有与摇臂轴17相匹配的轴孔4-4，摇臂轴17穿过轴孔4-4，驱动器4上螺纹连接有定位销7，定位销7通过抵接摇臂轴17外周壁或嵌入到摇臂轴17内的方式，均能够实现将驱动器4自身固定在摇臂轴17上；驱动油路4-3则可穿过定位销7或不穿过定位销7。
如图7所示，本实施例中驱动器4上设置有主动弹性元件8，用于在驱动油路4-3泄油时带动主活塞2回缩；
控制阀6开启时，主活塞2在液压作用下伸出至接触专用驱动凸轮19；控制阀6关闭时，主活塞2在主动弹性元件8作用下回缩至与专用驱动凸轮19分离；主动弹性元件8可采用压缩弹簧，具体安装结构则可采用以下方式：主活塞孔4-1的开口朝下，主活塞2的下端固定有主动限位件9，主动弹性元件8的一端抵住主动限位件9，另一端抵住主活塞2，主活塞2与主动限位件9接触时，主活塞2到达向下位移的最大行程。
如图10所示，本实施例中驱动器4上设置有用于使副活塞3朝远离驱动气门15方向移动的从动弹性元件11，从动弹性元件11需提供能够克服在驱动油路4-3充油时对副活塞3的油压并维持副活塞3处于回缩位置，且在驱动油路4-3泄油时带动副活塞3回缩；
本实施例中副活塞孔4-2的内周壁上开设有安全泄油孔4-6；
副活塞3在回缩位置与最大伸出位置之间移动时，副活塞3挡住安全泄油孔4-6，驱动油路4-3与安全泄油孔4-6不连通；
副活塞3移动至越过最大伸出位置时，副活塞3不再挡住安全泄油孔4-6，驱动油路4-3通过副活塞孔4-2与安全泄油孔4-6连通，以排除驱动油路4-3内所累积超量的机油。
本实施例中还包括与副活塞3相对设置的从动销10，驱动气门15连接在从动销10上；具体地，从动销10呈阶梯式结构，从动销10的台阶面10-1抵住气门桥20的下侧，从动销10的上端凸出于气门桥20的上侧面，驱动气门15的上端抵住从动销10，非驱动气门16的上端抵住气门桥20；
在供油路5向驱动油路4-3供油及控制阀6开启的状态下，当专用驱动凸轮19转至基圆部19-1与主活塞2滑动或滚动配合时，副活塞3与从动销10分离；当专用驱动凸轮19转至驱动升程凸台19-2与主活塞2滑动或滚动配合时，副活塞3能够移动至与从动销10接触，并通过从动销10推动驱动气门15位移；
本实施例中驱动器4上设置有用于调节副活塞3位置的调节螺栓13；例如，调节螺栓13与驱动器4螺纹连接并由锁紧螺母固定在驱动器4上以此实现调节螺栓13及副活塞3的位置可调；本实施例中从动弹性元件11可采用压缩弹簧，具体安装结构则可采用以下方式：副活塞孔4-2的开口朝下，副活塞3的上端固定有从动限位件12，调节螺栓13的下端伸入到副活塞3内，从动弹性元件11的上端抵住从动限位件12，从动弹性元件11的下端抵住调节螺栓13的下端，从而实现副活塞3能够在从动弹性元件11的作用下向上移动。
本实施例中控制阀6被设置呈在其开启时，供油路5通过控制阀6单向向驱动油路4-3供油；
本实施例中供油路5包括控制供油道5-1和驱动供油道5-2，驱动供油道5-2通过控制阀6单向向驱动油路4-3供油；
控制供油道5-1用于在内部油压变化时为控制阀6提供不同的作用力实现控制阀6的开启或关闭；
如图9所示，具体地，控制阀6包括阀体6-1、弹性回位元件6-2以及单向机构，阀体6-1上开设有主油道6-13、副油道6-11和连通通道6-12，阀体6-1滑动安装在阀孔17-1内，主油道6-13通过连通通道6-12与副油道6-11连通，单向机构设置在连通通道6-12内，用于允许主油道6-13内的油液单向进入到副油道6-11中，单向机构包括弹性元件6-4和单向球6-5，弹性元件6-4具体可采用压缩弹簧，其一端抵住副油道6-11的内壁，另一端抵住单向球6-5，单向球6-5抵住连通通道6-12，以防止副油道6-11中的油液通过连通通道6-12进入到主油道6-13，但是，能够允许主油道6-13内的油液通过连通通道6-12向副油道6-11流动，值得注意的是，本实施例中亦可直接采用单向阀替代单向机构；
弹性回位元件6-2具体采用压缩弹簧，用于带动阀体6-1复位，弹性回位元件6-2一端抵住阀体6-1，另一端抵住摇臂轴17或安装在摇臂轴17上的卡簧；
驱动器4或摇臂轴17上开设有泄油通道4-5，控制供油道5-1和弹性回位元件6-2分别位于阀孔17-1的两端；
如图2所示，当控制供油道5-1通入到阀孔17-1内的油液在阀体6-1上的压力大于弹性回位元件6-2的弹力时，阀体6-1处于开启位置，驱动供油道5-2与主油道6-13连通，副油道6-11与驱动油路4-3连通，且驱动油路4-3不与泄油通道4-5连通，此状态为，控制阀6开启；
如图1所示，当控制供油道5-1通入到阀孔17-1内的油液在阀体6-1上的 压力小于弹性回位元件6-2的弹力时，弹性回位元件6-2驱动阀体6-1移动至关闭位置，驱动供油道5-2与主油道6-13不连通，副油道6-11与驱动油路4-3不连通，但与泄油通道4-5连通，此状态为，控制阀6关闭。
本实施例中阀体6-1与阀孔17-1之间形成有泄压腔6-3，阀体6-1位于关闭位置时，驱动油路4-3通过泄压腔6-3和泄油通道4-5连通；
或者阀体6-1上开设有泄压腔6-3，阀体6-1位于关闭位置时，驱动油路4-3通过泄压腔6-3和泄油通道4-5连通。
本实施例的工作原理为：
发动机的凸轮轴带动正功凸轮18和专用驱动凸轮19转动；
发动机的电磁阀关闭，如图1所示，阀体6-1在弹性回位元件6-2的作用下移动至关闭位置，控制阀6处于关闭状态，驱动油路4-3泄油，其内部无油压，主活塞2在主动弹性元件8的作用下复位，并与专用驱动凸轮19分离，副活塞3在从动弹性元件11的作用下复位，并与从动销10分离，专用驱动凸轮19的驱动升程不发生传递，只有正功凸轮18转至主升程凸台18-1与正功摇臂1接触时，正功摇臂1转动以驱动气门桥20位移，同时打开驱动气门15和非驱动气门16，完成通常的气门正功升程；
发动机的电磁阀开启，如图2所示，控制供油道5-1向阀孔17-1的底部充油，推动阀体6-1处于开启位置，驱动供油道5-2单向向驱动油路4-3供油，主活塞2与副活塞3之间构建成液压联动关系，主活塞2在液压作用下伸出接触专用驱动凸轮19；如图3所示，当专用驱动凸轮19转至驱动升程凸台19-2与主活塞2接触时，驱动升程凸台19-2推动主活塞2，副活塞3随之向下伸出，以接触并推动从动销10，连接在从动销10上的驱动气门15得以发生移动而打开，实现发动机按专用驱动凸轮19的升程打开驱动气门15；如图4所示，当正 功凸轮18开始转至正功升程时，正功摇臂1向下推动气门桥20，驱动气门15和非驱动气门16实现正功升程。
上述依据本发明的理想实施例为启示，通过上述的说明内容，相关工作人员完全可以在不偏离本项发明技术思想的范围内，进行多样的变更以及修改。本项发明的技术性范围并不局限于说明书上的内容，必须要根据权利要求范围来确定其技术性范围。

Claims (13)

  1. 一种专用固定式双活塞液压发动机气门驱动装置，其特征在于：包括：
    专用驱动凸轮(19)，位于发动机正功凸轮(18)的一侧，并具有基圆部(19-1)和位于基圆部(19-1)上的驱动升程凸台(19-2)，所述正功凸轮(18)用于通过正功摇臂(1)带动气门桥(20)位移；
    驱动器(4)，具有滑动安装在主活塞孔(4-1)内的主活塞(2)和滑动安装在副活塞孔(4-2)内的副活塞(3)；
    驱动油路(4-3)，保持连通在主活塞孔(4-1)和副活塞孔(4-2)之间；
    以及控制阀(6)，所述驱动油路(4-3)通过控制阀(6)与供油路(5)连通；
    在供油路(5)向驱动油路(4-3)供油及控制阀(6)开启的状态下，当专用驱动凸轮(19)转至基圆部(19-1)与主活塞(2)滑动或滚动配合时，主活塞(2)在驱动油路(4-3)的液压作用下伸出至接触基圆部(19-1)；当专用驱动凸轮(19)转至驱动升程凸台(19-2)与主活塞(2)滑动或滚动配合时，控制阀(6)阻断驱动油路(4-3)与供油路(5)，主活塞(2)与副活塞(3)之间形成液压联动，驱动升程凸台(19-2)得以通过主活塞(2)带动副活塞(3)位移，使副活塞(3)为发动机驱动气门(15)提供相对气门桥(20)移动的动力；
    在控制阀(6)关闭的状态下，驱动油路(4-3)通过控制阀(6)泄油，主活塞(2)与副活塞(3)之间解除液压联动。
  2. 根据权利要求1所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述驱动器(4)与摇臂轴(17)固定连接。
  3. 根据权利要求2所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述驱动器(4)上开设有与摇臂轴(17)相匹配的轴孔(4-4)， 所述摇臂轴(17)穿过轴孔(4-4)，所述驱动器(4)上连接有定位销(7)，所述驱动器(4)通过定位销(7)与摇臂轴(17)固定连接。
  4. 根据权利要求2所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述驱动器(4)上设置有主动弹性元件(8)，用于在驱动油路(4-3)泄油时带动主活塞(2)回缩。
  5. 根据权利要求2所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述驱动器(4)上设置有用于使副活塞(3)朝远离驱动气门(15)方向移动的从动弹性元件(11)，从动弹性元件(11)需提供能够克服在驱动油路(4-3)充油时对副活塞(3)的油压并维持副活塞(3)处于回缩位置，且在驱动油路(4-3)泄油时带动副活塞(3)回缩。
  6. 根据权利要求5所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述副活塞孔(4-2)的内周壁上开设有安全泄油孔(4-6)；
    所述副活塞(3)在回缩位置与最大伸出位置之间移动时，副活塞(3)挡住安全泄油孔(4-6)，驱动油路(4-3)与安全泄油孔(4-6)不连通；
    所述副活塞(3)移动至越过最大伸出位置时，副活塞(3)不再挡住安全泄油孔(4-6)，驱动油路(4-3)通过副活塞孔(4-2)与安全泄油孔(4-6)连通。
  7. 根据权利要求5所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：还包括与副活塞(3)相对设置的从动销(10)，所述驱动气门(15)连接在从动销(10)上；
    在供油路(5)向驱动油路(4-3)供油及控制阀(6)开启的状态下当专用驱动凸轮(19)转至基圆部(19-1)与主活塞(2)滑动或滚动配合时，副活塞(3)与从动销(10)分离；当专用驱动凸轮(19)转至驱动升程凸台(19-2) 与主活塞(2)滑动或滚动配合时，副活塞(3)能够移动至与从动销(10)接触，并通过从动销(10)推动驱动气门(15)位移。
  8. 根据权利要求1所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述驱动器(4)上设置有用于调节副活塞(3)位置的调节螺栓(13)。
  9. 根据权利要求1所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述控制阀(6)被设置呈在其开启时，供油路(5)通过控制阀(6)单向向驱动油路(4-3)供油。
  10. 根据权利要求9所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述供油路(5)包括控制供油道(5-1)和驱动供油道(5-2)，所述驱动供油道(5-2)通过控制阀(6)单向向驱动油路(4-3)供油；
    所述控制供油道(5-1)用于在内部油压变化时为控制阀(6)提供不同的作用力实现控制阀(6)的开启或关闭。
  11. 根据权利要求10所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述控制阀(6)包括阀体(6-1)、弹性回位元件(6-2)以及单向机构，所述阀体(6-1)上开设有主油道(6-13)、副油道(6-11)和连通通道(6-12)，所述阀体(6-1)滑动安装在阀孔(17-1)内，所述主油道(6-13)通过连通通道(6-12)与副油道(6-11)连通，所述单向机构设置在连通通道(6-12)内，用于允许主油道(6-13)内的油液单向进入到副油道(6-11)中，所述弹性回位元件(6-2)用于带动阀体(6-1)复位；
    所述驱动器(4)或摇臂轴(17)上开设有泄油通道(4-5)，控制供油道(5-1)和阀孔(17-1)的一端连通；
    当控制供油道(5-1)通入到阀孔(17-1)内的油液在阀体(6-1)上的压力大于弹性回位元件(6-2)的弹力时，阀体(6-1)处于开启位置，驱动供油道(5-2) 与主油道(6-13)连通，副油道(6-11)与驱动油路(4-3)连通，且驱动油路(4-3)不与泄油通道(4-5)连通；
    当控制供油道(5-1)通入到阀孔(17-1)内的油液在阀体(6-1)上的压力小于弹性回位元件(6-2)的弹力时，弹性回位元件(6-2)驱动阀体(6-1)移动至关闭位置，驱动油路(4-3)和泄油通道(4-5)连通。
  12. 根据权利要求11所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述阀体(6-1)与阀孔(17-1)之间形成有泄压腔(6-3)，所述阀体(6-1)位于关闭位置时，驱动油路(4-3)通过泄压腔(6-3)和泄油通道(4-5)连通；
    或者所述阀体(6-1)上开设有泄压腔(6-3)，所述阀体(6-1)位于关闭位置时，驱动油路(4-3)通过泄压腔(6-3)和泄油通道(4-5)连通。
  13. 根据权利要求1所述的专用固定式双活塞液压发动机气门驱动装置，其特征在于：所述控制阀(6)安装在摇臂轴(17)或驱动器(4)上。
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