WO2023142279A1 - 液压间隙自调专用驱动凸轮组合式气门驱动装置 - Google Patents

液压间隙自调专用驱动凸轮组合式气门驱动装置 Download PDF

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Publication number
WO2023142279A1
WO2023142279A1 PCT/CN2022/089486 CN2022089486W WO2023142279A1 WO 2023142279 A1 WO2023142279 A1 WO 2023142279A1 CN 2022089486 W CN2022089486 W CN 2022089486W WO 2023142279 A1 WO2023142279 A1 WO 2023142279A1
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Prior art keywords
piston
oil
drive
hydraulic
valve
Prior art date
Application number
PCT/CN2022/089486
Other languages
English (en)
French (fr)
Inventor
崔立澜
Original Assignee
江苏卓联精密机械有限公司
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 江苏卓联精密机械有限公司 filed Critical 江苏卓联精密机械有限公司
Priority to EP22923097.4A priority Critical patent/EP4339424A1/en
Publication of WO2023142279A1 publication Critical patent/WO2023142279A1/zh
Priority to US18/485,877 priority patent/US11988116B2/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • 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
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L2001/2444—Details relating to the hydraulic feeding circuit, e.g. lifter oil manifold assembly [LOMA]
    • 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 driving cam combination type valve driving device for hydraulic clearance self-adjustment.
  • 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.
  • the existing combined engine valve driving device cannot automatically adjust the valve clearance.
  • the hydraulic clearance adjuster can be used to adjust the hydraulic clearance throughout the whole process, the hydraulic clearance adjuster will easily extend excessively during the engine driving lift process and increase the subsequent The positive power lift of the valve, and then there is a problem affecting its positive power and brake lift, that is, the hydraulic lash adjuster does not match the combined engine valve drive device.
  • the technical problem to be solved by the present invention is: in order to solve the problem that the combined engine valve driving device cannot automatically adjust the valve clearance in the prior art, and the hydraulic clearance adjuster is not compatible with the combined engine valve driving device, a hydraulic pressure regulator is now provided.
  • the clearance self-adjusting special driving cam combined valve driving device in order to solve the problem that the combined engine valve driving device cannot automatically adjust the valve clearance in the prior art, and the hydraulic clearance adjuster is not compatible with the combined engine valve driving device.
  • a special drive cam combined valve drive device for hydraulic clearance self-adjustment including:
  • the driver has a main piston slidably installed in the main piston hole, an actuating piston slidably installed in the actuating piston hole, and a driving oil circuit connected between the main piston hole and the actuating piston hole, and the actuating piston runs through the actuating piston hole.
  • the inner oil passage communicated with the piston hole, and the driver is fixedly installed on the rocker shaft;
  • the rocker arm is equipped with a hydraulic clearance adjuster, the rocker arm is rotatably installed on the rocker arm shaft, and the oil supply circuit is opened on the rocker arm shaft;
  • a dedicated driving cam is located on one side of the positive power cam of the engine, and has a base circle and a drive lift boss on the base circle;
  • the valve bridge located under the actuator piston and the hydraulic lash adjuster has the auxiliary piston slidingly installed in the auxiliary piston hole and the oil drain passage connected to the auxiliary piston hole, the driving valve is connected with the auxiliary piston, and the actuator piston is set opposite to the valve bridge.
  • the effective active area of the piston to be pushed by the liquid in the execution piston hole to move along its sliding direction is smaller than the effective active area of the auxiliary piston to be pushed by the liquid in the auxiliary piston to move along its sliding direction;
  • the driving oil circuit is connected with the oil supply circuit through the positioning pressure control unit; when the rocker arm does not drive the displacement of the valve bridge and the oil supply circuit supplies oil to the driving oil circuit, the hydraulic action of the piston in the driving oil circuit is executed.
  • the bottom protrudes to contact the valve bridge, and the inner oil passage communicates with the oil drain passage; when the special drive cam rotates to the base circle and slides or rolls to fit the main piston, the main piston extends to the contact base circle under the hydraulic pressure of the drive oil circuit.
  • the positioning pressure control unit blocks the drive oil circuit and the oil supply circuit, and a hydraulic linkage is formed between the main piston and the auxiliary piston, so that the drive lift boss can be
  • the driving valve connected to the auxiliary piston is driven by the main piston to displace;
  • the positive power cam is located at one end of the rocker arm
  • the hydraulic lash adjuster is located at the other end of the rocker arm
  • the positive power cam, hydraulic lash adjuster and valve bridge are located at the rocker arm.
  • the main piston, dedicated drive cam, actuating piston and valve bridge are located below the driver.
  • the actuating piston is located between the rocker arm shaft and the hydraulic clearance adjuster.
  • the oil supply circuit supplies oil to the drive oil circuit unidirectionally through the positioning pressure control unit.
  • a shaft hole matching the rocker shaft is provided on the driver, the rocker shaft passes through the shaft hole, and the driver is fixedly connected to the rocker shaft through a positioning pressure control unit.
  • the positioning pressure control unit includes a positioning screw and a one-way assembly, and the positioning screw has an oil cavity and an oil inlet channel communicating with the oil cavity. on the rocker shaft;
  • the positioning screw is threadedly connected with the driver to fix the driver on the rocker shaft, the oil chamber is kept in communication with the driving oil circuit, the oil supply circuit is in communication with the oil inlet channel, and the one-way assembly is arranged on the positioning screw , and make the oil inlet channel communicate with the oil chamber in one direction.
  • the rocker shaft is provided with a positioning surface matching the positioning screw, and the inner end surface of the positioning screw is in contact with the positioning surface.
  • the one-way assembly includes an elastic element and a one-way ball, one end of the elastic element is against the inner wall of the oil cavity, and the other end is against the connection between the oil inlet passage and the oil cavity.
  • the drive oil passage includes a main piston oil passage and an actuating piston oil passage both opened in the driver, one end of the main piston oil passage communicates with the main piston hole, and the other end communicates with the oil chamber, and the actuating piston One end of the oil passage communicates with the oil cavity, and the other end communicates with the inner oil passage.
  • the driver is provided with a main elastic element, which is used to drive the main piston to retract when the pressure in the drive oil circuit is released.
  • the actuator is provided with an actuator elastic element, which is used to drive the actuator piston to retract when the pressure is released in the drive oil circuit, and the actuator piston hole is provided with an actuator piston limiting unit, which is used to Limit the maximum travel of the actuator piston along the axial direction of the actuator piston hole.
  • the driver of the hydraulic clearance self-adjusting special-purpose drive cam combined valve driving device of the present invention is fixed on the rocker shaft, and there is no engine power consumption and no motion wear caused by motion friction between the driver and the rocker shaft , the special driving cam is separated from the main piston when the driver is not working, which effectively reduces the wear between the special driving cam and the main piston and the noise of the engine, reduces friction loss, and improves the utilization rate of the engine output power.
  • the cam automatically adjusts the driving valve through the hydraulic clearance, the driving lift is not affected by the initial clearance setting, is stable and consistent, and is easy to use and maintain. When it is dirty, it will not cause the accumulation of impurities, thereby improving the stability and reliability of work;
  • the hydraulic gap adjuster is used to compensate the gap between it and the valve bridge under the action of hydraulic pressure, so as to realize the hydraulic automatic adjustment of the valve without gap in the whole process, and there is no need to adjust the valve gap during use, so as to avoid the influence of the change of the system gap on the driving and positive power performance, and reduce the It reduces engine noise and improves engine timing accuracy, and solves the problem of compatibility between valve drive function and hydraulic clearance adjustment function;
  • valve bridge is subjected to the hydraulic pressure difference toward the rocker arm by using the actuator piston, so as to balance the thrust of the valve bridge on the valve bridge generated by the hydraulic lash adjuster, and prevent the hydraulic lash adjuster from extending excessively during the drive lift. And increase the subsequent positive power lift of the valve.
  • Fig. 1 is the schematic diagram when special driving cam and main piston are separated among the present invention
  • Fig. 2 is the schematic diagram when hydraulic linkage is formed between main piston and auxiliary piston hydraulic pressure 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 the schematic diagram when the rocker arm drives the displacement of the valve bridge in the present invention
  • Fig. 5 is a three-dimensional schematic diagram of the special driving cam combined valve driving device for hydraulic clearance self-adjustment of the present invention
  • Fig. 6 is a top view schematic diagram of the special driving cam combined valve driving device for hydraulic clearance self-adjustment of the present invention.
  • Fig. 7 is a schematic cross-sectional view of the driver installed on the rocker shaft in the present invention.
  • Fig. 8 is a schematic cross-sectional view of the hydraulic clearance adjuster installed on the rocker arm in the present invention.
  • driver 1-1
  • main piston hole 1-2
  • shaft hole 1-3
  • execution piston hole
  • Execution piston, 7-1 inner oil passage, 7-2, joint part of execution piston, 7-3, joint seat of execution piston;
  • Positioning and pressure control unit 9-1, positioning screw, 9-11, oil chamber, 9-12, oil inlet channel, 9-2, elastic element, 9-3, one-way ball;
  • the main elastic element 11.
  • the executive elastic element 12.
  • the main elastic element support 13.
  • a hydraulic clearance self-adjusting special drive cam combination valve driving device the engine is a four-stroke engine, the driving valve 18 and the non-driving valve 19 of the valve group are exhaust valves in the engine, the
  • the valve drive consists of:
  • the driver 1 has a main piston 4 slidably installed in the main piston hole 1-1, an actuating piston 7 slidably installed in the actuating piston hole 1-3, and a piston connected between the main piston hole 1-1 and the actuating piston hole 1-3.
  • the driving oil passage 8 between the actuator piston 7 runs through the inner oil passage 7-1 communicating with the actuator piston hole 1-3, and the driver 1 is fixedly installed on the rocker shaft 16;
  • the rocker arm 3 is equipped with a hydraulic gap adjuster 6, and the rocker arm 3 is rotated and installed on the rocker arm shaft 16;
  • the special-purpose drive cam 15 is located on one side of the positive power cam 14 of the engine, and has a base circle portion 15-1 and a drive lift boss 15-2 positioned on the base circle portion 15-1; the drive lift boss 15-2 specifically has two , are respectively the exhaust gas recirculation drive lift boss and the compression release drive lift boss, the exhaust gas recirculation drive lift boss is used to make the drive valve 18 perform the exhaust gas recirculation operation, and the compression release drive lift boss is used to make the drive valve 18 perform the compression release operation;
  • the valve bridge 2 located under the actuator piston 7 and the hydraulic clearance adjuster 6 has the auxiliary piston 5 slidably installed in the auxiliary piston hole 2-1 and the oil drain passage 2-2 connected with the auxiliary piston hole 2-1, and drives the valve 18 Connected with the auxiliary piston 5, the execution piston 7 is set opposite to the valve bridge 2.
  • the effective area of the execution piston 7 to be pushed by the liquid in the execution piston hole 1-3 to move along its sliding direction is smaller than that of the auxiliary piston 5 to be used by the auxiliary piston.
  • the effective area where the liquid in the piston hole 2-1 pushes and moves along its sliding direction;
  • the driving oil circuit 8 communicates with the oil supply circuit 17 through the positioning pressure control unit 9; in the state where the rocker arm 3 does not drive the displacement of the valve bridge 2 and the oil supply circuit 17 supplies oil to the driving oil circuit 8,
  • the actuator piston 7 stretches out to contact the valve bridge 2 under the hydraulic pressure of the drive oil circuit 8, and the inner oil channel 7-1 communicates with the oil drain channel 2-2; 4.
  • the main piston 4 When sliding or rolling, the main piston 4 extends out to contact the base circle part 15-1 under the hydraulic pressure of the driving oil circuit 8; when the special driving cam 15 turns to the driving lift boss 15-2 and the main piston 4 slides or rolls
  • the positioning pressure control unit 9 blocks the driving oil circuit 8 and the oil supply circuit 17, and a hydraulic linkage is formed between the main piston 4 and the auxiliary piston 5, so that the driving lift boss 15-2 can be driven by the main piston 4 and the auxiliary piston 5
  • the connected driving valve 18 is displaced; if there is a plane or curved surface on the main piston 4, then the base circle portion 15-1 and the driving lift boss 15-2 are all in contact with the plane or curved surface when cooperating with the main piston 4, In this way, the so-called sliding fit is formed with the main piston 4 respectively;
  • the rollers are in contact with each other to form a so-called rolling fit with the main piston 4 .
  • the positive power cam 14 is located at one end of the rocker arm 3, the hydraulic lash adjuster 6 is located at the other end of the rocker arm 3, the positive power cam 14, the hydraulic lash adjuster 6 and the valve bridge 2 are located under the rocker arm 3, the main piston 4, the special The drive cam 15, the actuator piston 7 and the valve bridge 2 are located under the driver 1, the actuator piston 7 is located between the rocker arm shaft 16 and the hydraulic lash adjuster 6, and the hydraulic lash adjuster 6 is in contact with the middle part of the upper side of the valve bridge 2 , this layout method can improve the stability of the structure and increase the carrying capacity.
  • the oil supply circuit 17 supplies oil to the driving oil circuit 8 in one direction through the positioning pressure control unit 9 in this embodiment. To stop, forcing the oil in the drive oil circuit 8 not to flow back into the oil supply circuit 17, so as to realize the rigid hydraulic linkage between the main piston 4 and the auxiliary piston 5;
  • a shaft hole 1-2 matching the rocker shaft 16 is provided on the driver 1 in this embodiment, the rocker shaft 16 passes through the shaft hole 1-2, and the driver 1 is positioned by the positioning pressure control unit 9 and The rocker shaft 16 is fixedly connected.
  • the positioning and pressure control unit 9 includes a positioning screw 9-1 and a one-way assembly, and the positioning screw 9-1 has an oil chamber 9-11 and an oil inlet passage 9-12 communicating with the oil chamber 9-11;
  • the driving oil passage 8 includes the main piston oil passage 8-1 and the executive piston oil passage 8-2, both of which are opened in the driver 1.
  • One end of the main piston oil passage 8-1 communicates with the main piston hole 1-1, and the other end communicates with the oil passage 8-1.
  • the cavity 9-11 is connected, and one end of the executive piston oil passage 8-2 is connected with the oil chamber 9-11, and the other end is connected with the inner oil passage 7-1;
  • the oil supply passage 17 is arranged on the rocker shaft 16;
  • the positioning and pressure control unit 9 composed of the positioning screw 9-1 and the one-way assembly has the advantage of simple structure; in addition, during installation, only the positioning screw 9-1 needs to be tightened on the driver 1, and the positioning and pressure control can be realized at the same time
  • the fixing of the unit 9 on the driver 1 and the fixing of the driver 1 on the rocker shaft 16 simplify the assembly process and improve production efficiency;
  • the positioning screw 9-1 is threadedly connected with the driver 1 to fix the driver 1 on the rocker shaft 16, the oil chamber 9-11 is kept in communication with the driving oil circuit 8, and the oil supply circuit 17 is connected to the oil inlet passage 9- 12 communicates, and the one-way component is arranged on the set screw 9-1, and makes the oil inlet channel 9-12 communicate with the oil chamber 9-11 in one direction.
  • the rocker shaft 16 is provided with a positioning surface 16-1 that matches the positioning screw 9-1, and the inner end surface of the positioning screw 9-1 is in contact with the positioning surface 16-1, so that the driver 1 is fixed.
  • the positioning screw 9 - 1 can also directly abut against the outer peripheral surface of the rocker shaft 16 to realize fixing the driver 1 on the rocker shaft 16 .
  • the one-way assembly includes an elastic element 9-2 and a one-way ball 9-3.
  • the elastic element 9-2 is specifically a compression spring. One end of the elastic element 9-2 is against the inner wall of the oil chamber 9-11, and the other end is against the inner wall of the oil chamber 9-11.
  • the one-way ball 9-3 resists the connection between the oil inlet passage 9-12 and the oil chamber 9-11 to prevent the oil from
  • the oil in the chamber 9-11 enters the oil inlet passage 9-12, but when the oil inlet passage 9-12 supplies oil to the oil chamber 9-11, the elastic element 9-2 will be compressed, and the one-way ball 9-3 Open the connection between the oil inlet passage 9-12 and the oil chamber 9-11, and the oil inlet passage 9-12 communicates with the oil chamber 9-11; thereby the structure of the positioning pressure control unit 9 can be continuously simplified, and the production cost can be reduced; it is worthwhile It should be noted that, in this embodiment, the one-way valve can also be directly used instead of the one-way component.
  • the driver 1 is provided with a main elastic element 10, which is used to drive the main piston 4 to retract when the pressure is released in the drive oil circuit 8; thus, the main piston 4 is kept in an initial position separated from the special driving cam 15 by the elastic force of the main elastic element 10 , only when the driving oil circuit 8 is filled with oil, the main piston 4 can move to contact the special driving cam 15 after the hydraulic force overcomes the elastic force of the main elastic element 10; the main elastic element 10 can use a compression spring, and the specific installation structure can be The following method is adopted: the opening of the main piston hole 1-1 faces downward, the lower end of the main piston hole 1-1 is fixed with a main elastic element support 12, one end of the main elastic element 10 is against the main elastic element support 12, and the other end is against the main elastic element support 12. Live main piston 4.
  • the actuator 1 is provided with an executing elastic element 11, which can specifically be a compression spring, which is used to drive the actuator piston 7 to retract when the pressure is released in the drive oil circuit 8, and the actuator piston hole 1-3 is provided with an actuator piston limiter.
  • Bit unit 13 the execution piston limit unit 13 is used to limit the maximum stroke of the execution piston 7 along the axial direction of the execution piston hole 1-3; thereby utilizing the elastic force of the execution elastic element 11 to keep the execution piston 7 at the initial position separated from the valve bridge 2 , the actuator piston 7 can move to contact the valve bridge 2 only after the hydraulic pressure is used to overcome the elastic force of the actuator elastic element 11 when the drive oil circuit 8 is filled with oil;
  • the specific installation structure can adopt the following method: the actuator piston hole 1-3 The opening of the actuator is facing downward, and the lower end of the actuator piston hole 1-3 is fixed to the actuator piston limiting unit 13.
  • the actuator piston 7 and the actuator piston When the limit unit 13 contacts, the execution piston 7 reaches the maximum stroke of downward displacement; in order to realize the stable sealing contact between the execution piston 7 and the valve bridge 2, the execution piston 7 has an execution piston joint 7-2 and an execution piston joint seat 7-3.
  • the joint seat 7-3 of the execution piston and the joint part 7-2 of the execution piston form a spherical pair connection or a rotary joint connection.
  • the joint seat 7-3 of the execution piston is used to contact the valve bridge 2.
  • the inner oil passage 7- 1 correspondingly, sequentially penetrate the actuator piston 7, the actuator piston joint part 7-2 and the actuator piston joint seat 7-3.
  • the camshaft of the engine drives the positive power cam 14 and the special driving cam 15 to rotate;
  • the solenoid valve of the engine is closed, the oil supply circuit 17 stops the oil supply, and the drive oil circuit 8 has no oil pressure.
  • the main piston 4 and the execution piston 7 integrated in the driver 1 are in the closed position under the action of the spring force.
  • the special driving cam 15 does not contact the main piston 4 of the driver 1, and the driving lift of the special driving cam 15 will not be transmitted to the driver 1 and drive valve 18, only when the positive power cam 14 turns to the positive power lift process, the positive power lift is rotated by the rocker arm 3 and driven by the hydraulic clearance adjuster 6 to drive the displacement of the valve bridge 2, and the drive valve 18 and the non-drive valve are opened at the same time.
  • the valve 19 completes the normal positive power lift of the valve;
  • the solenoid valve of the engine is opened, as shown in Figure 2, when the positive power cam 14 is in the base circle and the special driving cam 15 is in the base circle part 15-1, the oil supply circuit 17 passes through the one-way assembly in the positioning pressure control unit 9
  • One-way oil supply to the drive oil circuit 8 the drive oil circuit 8 is filled with oil, the oil in the drive oil circuit 8 makes the main piston 4 and the execution piston 7 stretch out against the spring force, and respectively contact the special drive cam 15 and the valve without clearance Bridge 2, the executive piston 7 is in sealing connection with the valve bridge 2, and the inner oil passage 7-1 moves to communicate with the oil drain passage 2-2; as shown in Figure 3, when the special drive cam 15 turns to the drive lift boss 15- 2 When in contact with the main piston 4, the driving lift boss 15-2 pushes and drives the main piston 4, and the one-way component in the positioning pressure control unit 9 is closed due to hydraulic backflow, and the driving oil circuit 8 is closed, between the main piston 4 and the auxiliary piston 5 A hydraulic linkage is formed, and the auxiliary piston 5 is
  • valve bridge 2 positive power lift, and at the same time separate the valve bridge 2 from the executive piston 7, automatically open the oil drain passage 2-2 in the valve bridge 2, and the oil in the auxiliary piston hole 2-1 passes through the oil drain passage under the pressure of the driving valve 18 2-2 discharge, auxiliary piston 5 resets, retracts to the unstretched position, and makes the whole valve mechanism return to positive power attitude.
  • the upper end opening of the inner oil passage 7-1 is located on the upper end surface of the actuating piston 7.
  • the inner oil passage 7-1 is an equal-diameter hole
  • the difference between the cross-sectional area of the inner peripheral wall of the actuating piston hole 1-3 and the sliding connection part of the actuating piston 7 and the cross-sectional area of the inner oil passage 7-1 is the execution piston 7
  • the inner oil passage 7-1 is a two-stage stepped hole with a large upper end and a smaller lower end
  • the cross-sectional area of the sliding connection part on the inner peripheral wall of the execution piston hole 1-3 and the execution piston 7 is the same as that of the inner oil passage 7- 1
  • the difference between the minimum values of the cross-sectional area is the effective area of the actuator piston 7; if the inner oil passage 7-1 is a two-stage stepped hole with a small upper end and a larger lower end
  • the cross-sectional area of the sliding connection part between the inner peripheral wall of the execution piston hole 1-3 and the execution piston 7 is the effective area of the execution piston 7;
  • the cross-sectional area of the inner peripheral wall of the auxiliary piston hole 2-1 and the sliding connection part of the auxiliary piston 5 is the effective active area of the auxiliary piston 5;
  • the effective active area of the actuator piston 7 is smaller than the effective active area of the auxiliary piston 5, so that the valve bridge 2 receives an upward hydraulic differential force on the drive valve 18 side during the drive lift, so as to balance the middle part of the valve bridge 2 by the hydraulic clearance adjuster 6
  • the generated downward thrust prevents the hydraulic slack adjuster 6 from overextending and increasing the positive power lift of the valve.

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Abstract

一种液压间隙自调专用驱动凸轮组合式气门驱动装置，包括固定安装在摇臂轴（16）上的驱动器（1）及安装有液压间隙调节器（6）的摇臂（3），驱动器（1）设置有主活塞（4）和执行活塞（7），主活塞孔（1-1）和执行活塞孔（1-3）之间设置驱动油路（8），驱动油路（8）通过定位控压单元（9）与供油路（17）连通；驱动油路（17）供油时主活塞（4）和副活塞（5）液压联动，打开驱动气门（18）。本驱动器（1）和摇臂轴（16）之间无运动摩擦引起的发动机功率消耗和无运动磨损，提高了工作的稳定性和可靠性；使用时无须再调节气门间隙，避免系统间隙变化对驱动及正功性能的影响，降低了发动机噪音并提高了发动机正时准确性，解决了气门驱动功能与液压间隙调节功能兼容问题。

Description

液压间隙自调专用驱动凸轮组合式气门驱动装置 技术领域
本发明涉及发动机气门驱动装置技术领域，尤其是一种液压间隙自调专用驱动凸轮组合式气门驱动装置。
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。
现有的组合式发动机气门驱动装置不能自动调节气门间隙，虽然增加液压间隙调节器能够全程进行液压间隙调节，但是在发动机驱动升程过程中液压间隙调节器又会容易过度伸出而增加随后的气门正功升程，进而出现影响其正功和制动升程的问题，也就是液压间隙调节器与组合式发动机气门驱动装置不匹配。
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组合式发动机气门驱动装置无法自动调节气门间隙，而液压间隙调节器又与组合式发动机气门驱动装置不兼容的问题，现提供一种液压间隙自调专用驱动凸轮组合式气门驱动装置。
本发明解决其技术问题所采用的技术方案是：一种液压间隙自调专用驱动凸轮组合式气门驱动装置，包括：
驱动器，具有滑动安装在主活塞孔内的主活塞、滑动安装在执行活塞孔内的执行活塞以及连通在主活塞孔和执行活塞孔之间的驱动油路，所述执行活塞 上贯穿有与执行活塞孔连通的内油道，所述驱动器固定安装在摇臂轴上；
摇臂，安装有液压间隙调节器，所述摇臂转动安装在摇臂轴上，供油路开设在摇臂轴上；
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；
位于执行活塞和液压间隙调节器下方的气门桥，具有滑动安装在副活塞孔内的副活塞和连通副活塞孔的泄油道，驱动气门与副活塞连接，执行活塞与气门桥相对设置，执行活塞用于被执行活塞孔内的液体推动而沿其滑动方向移动的有效作用面积小于副活塞用于被副活塞内的液体推动而沿其滑动方向移动的有效作用面积；
以及定位控压单元，驱动油路通过定位控压单元与供油路连通；在摇臂未驱动气门桥位移及供油路向驱动油路供油的状态下，执行活塞在驱动油路的液压作用下伸出接触气门桥，内油道与泄油道连通；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，定位控压单元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，使驱动升程凸台得以通过主活塞带动与副活塞相连的驱动气门位移；
在摇臂通过液压间隙调节器带动气门桥位移的状态下，泄油道和内油道随气门桥的位移而分离，主活塞与副活塞之间解除液压联动，副活塞孔内机油泄出，副活塞在气门桥内复位。
为了便于布局及提高结构的紧凑性，进一步地，所述正功凸轮位于摇臂的一端，液压间隙调节器位于摇臂的另一端，所述正功凸轮、液压间隙调节器及气门桥位于摇臂的下方，所述主活塞、专用驱动凸轮、执行活塞及气门桥位于 驱动器的下方。
为了便于布局及提高结构的紧凑性，进一步地，所述执行活塞位于摇臂轴与液压间隙调节器之间。
为了实现刚性的液压联动，进一步地，所述供油路通过定位控压单元单向向驱动油路供油。
为了提高结构的紧凑性，进一步地，所述驱动器上开设与摇臂轴相匹配的轴孔，所述摇臂轴穿过轴孔，所述驱动器通过定位控压单元与摇臂轴固定连接。
为了便于制造及简化装配流程，进一步地，所述定位控压单元包括定位螺钉和单向组件，所述定位螺钉内具有油腔及与油腔连通的进油通道，所述供油路设置在摇臂轴上；
所述定位螺钉与驱动器螺纹连接以此将驱动器固定在摇臂轴上，所述油腔保持与驱动油路连通，所述供油路与进油通道连通，所述单向组件设置在定位螺钉上，并使进油通道与油腔单向连通。
为了提高固定效果，进一步地，所述摇臂轴上开设有与定位螺钉相匹配的定位面，所述定位螺钉的内端端面与所述定位面接触。
进一步地，所述单向组件包括弹性元件和单向球，所述弹性元件一端抵住油腔的内壁，另一端抵住进油通道与油腔之间的连通处。
进一步地，所述驱动油路包括均开设在驱动器内的主活塞油道和执行活塞油道，所述主活塞油道的一端与主活塞孔连通，另一端与油腔连通，所述执行活塞油道的一端与油腔连通，另一端与内油道连通。
进一步地，所述驱动器上设置有主弹性元件，用于在驱动油路内泄压时带动主活塞回缩。
进一步地，所述驱动器上设置有执行弹性元件，用于在驱动油路内泄压时 带动执行活塞回缩，所述执行活塞孔处设置有执行活塞限位单元，执行活塞限位单元用于限制执行活塞沿执行活塞孔轴向的最大行程。
本发明的有益效果是：本发明的液压间隙自调专用驱动凸轮组合式气门驱动装置其驱动器固定在摇臂轴上，驱动器和摇臂轴之间无运动摩擦引起的发动机功率消耗和无运动磨损，驱动器非工作时专用驱动凸轮与主活塞分离，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，提高了发动机输出动力的利用率，驱动器工作时专用驱动凸轮通过液压间隙自动调节驱动气门，驱动升程不受初始间隙设置影响，稳定一致，使用维护简单，同时正功凸轮每转动一圈，驱动油路能够自动泄油一次，循环流动的机油在过脏时不会引起杂质的堆积，从而提高工作的稳定性和可靠性；
利用液压间隙调节器在液压作用下补偿其与气门桥之间的间隙，实现全程气门无间隙液压自动调节，使用时无须再调节气门间隙，避免系统间隙变化对驱动及正功性能的影响，降低了发动机噪音并提高了发动机正时准确性，解决了气门驱动功能与液压间隙调节功能兼容问题；
同时利用执行活塞使气门桥受到朝向摇臂的液压力差，以平衡气门桥由液压间隙调节器产生在气门桥上的朝向气门桥的推力，防止液压间隙调节器在驱动升程时过度伸出而增加随后的气门正功升程。
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是本发明中专用驱动凸轮与主活塞分离时的示意图；
图2是本发明中主活塞与副活塞液压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是本发明中摇臂带动气门桥位移时的示意图；
图5是本发明液压间隙自调专用驱动凸轮组合式气门驱动装置的三维示意图；
图6是本发明液压间隙自调专用驱动凸轮组合式气门驱动装置的俯视示意图；
图7是本发明中驱动器安装在摇臂轴上的剖视示意图；
图8是本发明中液压间隙调节器安装在摇臂上的剖示意图；
图中：1、驱动器，1-1、主活塞孔，1-2、轴孔，1-3、执行活塞孔；
2、气门桥，2-1、副活塞孔，2-2、泄油道；
3、摇臂，4、主活塞，5、副活塞，6、液压间隙调节器；
7、执行活塞，7-1、内油道，7-2、执行活塞关节部，7-3、执行活塞关节座；
8、驱动油路，8-1、主活塞油道，8-2、执行活塞油道；
9、定位控压单元，9-1、定位螺钉，9-11、油腔，9-12、进油通道，9-2、弹性元件，9-3、单向球；
10、主弹性元件，11、执行弹性元件，12、主弹性元件支座，13、执行活塞限位单元；
14、正功凸轮，14-1、主升程凸台；
15、专用驱动凸轮，15-1、基圆部，15-2、驱动升程凸台；
16、摇臂轴，16-1、定位面；
17、供油路，18、驱动气门，19、非驱动气门。
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1-8所示，一种液压间隙自调专用驱动凸轮组合式气门驱动装置，发动机为四冲程发动机，气门组的驱动气门18和非驱动气门19均为发动机中的排气门，该气门驱动装置包括：
驱动器1，具有滑动安装在主活塞孔1-1内的主活塞4、滑动安装在执行活塞孔1-3内的执行活塞7以及连通在主活塞孔1-1和执行活塞孔1-3之间的驱动油路8，执行活塞7上贯穿有与执行活塞孔1-3连通的内油道7-1，驱动器1固定安装在摇臂轴16上；
摇臂3，安装有液压间隙调节器6，摇臂3转动安装在摇臂轴16上；
专用驱动凸轮15，位于发动机正功凸轮14的一侧，并具有基圆部15-1和位于基圆部15-1上的驱动升程凸台15-2；驱动升程凸台15-2具体有两个，分别为废气再循环驱动升程凸台和压缩释放驱动升程凸台，废气再循环驱动升程凸台用于使驱动气门18执行废气再循环操作，压缩释放驱动升程凸台用于使驱动气门18执行压缩释放操作；
位于执行活塞7和液压间隙调节器6下方的气门桥2，具有滑动安装在副活塞孔2-1内的副活塞5和连通副活塞孔2-1的泄油道2-2，驱动气门18与副活 塞5连接，执行活塞7与气门桥2相对设置，执行活塞7用于被执行活塞孔1-3内的液体推动而沿其滑动方向移动的有效作用面积小于副活塞5用于被副活塞孔2-1内的液体推动而沿其滑动方向移动的有效作用面积；
以及定位控压单元9，驱动油路8通过定位控压单元9与供油路17连通；在摇臂3未驱动气门桥2位移及供油路17向驱动油路8供油的状态下，执行活塞7在驱动油路8的液压作用下伸出接触气门桥2，内油道7-1与泄油道2-2连通；当专用驱动凸轮15转至基圆部15-1与主活塞4滑动或滚动配合时，主活塞4在驱动油路8的液压作用下伸出至接触基圆部15-1；当专用驱动凸轮15转至驱动升程凸台15-2与主活塞4滑动或滚动配合时，定位控压单元9阻断驱动油路8与供油路17，主活塞4与副活塞5之间形成液压联动，使驱动升程凸台15-2得以通过主活塞4带动与副活塞5相连的驱动气门18位移；如若，主活塞4上具有一平面或曲面，则基圆部15-1和驱动升程凸台15-2在与主活塞4配合时，均为与该平面或曲面接触，以此分别与主活塞4构成所谓的滑动配合；如若，主活塞4上转动安装有滚轮，则基圆部15-1和驱动升程凸台15-2在与主活塞4配合时，均为与该滚轮接触，以此分别与主活塞4构成所谓的滚动配合。
在摇臂3通过液压间隙调节器6带动气门桥2位移的状态下，泄油道2-2和内油道7-1随气门桥2的位移而分离，主活塞4与副活塞5之间解除液压联动，副活塞孔2-1内机油泄出，副活塞5在气门桥2内复位；值得注意的是，正功凸轮14转动时通过摇臂3带动气门桥2位移的结构，为常规技术，例如：正功凸轮14转至其基圆与摇臂3配合时，摇臂3和气门桥2均不发生位移，正功凸轮14转至主升程凸台14-1与摇臂3配合时，主升程凸台14-1推动摇臂3，由摇臂3通过液压间隙调节器6带动气门桥2位移。
正功凸轮14位于摇臂3的一端，液压间隙调节器6位于摇臂3的另一端， 正功凸轮14、液压间隙调节器6及气门桥2位于摇臂3的下方，主活塞4、专用驱动凸轮15、执行活塞7及气门桥2位于驱动器1的下方，执行活塞7位于摇臂轴16与液压间隙调节器6之间，液压间隙调节器6具体和气门桥2上侧面的中间部位接触，该布局方式能够提高结构的稳定性，并能提升承载能力。
为了实现刚性液压联动，本实施例中供油路17通过定位控压单元9单向向驱动油路8供油，在主活塞4与副活塞5液压联动时，利用定位控压单元9的反向截止，迫使驱动油路8中的油液不会反流到供油路17中，以此实现主活塞4与副活塞5之间的刚性液压联动；
为了提高结构的紧凑性，本实施例中驱动器1上开设与摇臂轴16相匹配的轴孔1-2，摇臂轴16穿过轴孔1-2，驱动器1通过定位控压单元9与摇臂轴16固定连接。
本实施例中定位控压单元9包括定位螺钉9-1和单向组件，定位螺钉9-1内具有油腔9-11及与油腔9-11连通的进油通道9-12；
驱动油路8包括均开设在驱动器1内的主活塞油道8-1和执行活塞油道8-2，主活塞油道8-1的一端与主活塞孔1-1连通，另一端与油腔9-11连通，执行活塞油道8-2的一端与油腔9-11连通，另一端与内油道7-1连通；
供油路17设置在摇臂轴16上；
由定位螺钉9-1和单向组件组成的定位控压单元9具有结构简单的优点；另外，在安装时，只需要将定位螺钉9-1拧紧在驱动器1上，便能够同时实现定位控压单元9在驱动器1上的固定，以及驱动器1在摇臂轴16上的固定，从而简化装配流程，提升生产效率；
本实施例中定位螺钉9-1与驱动器1螺纹连接以此将驱动器1固定在摇臂轴16上，油腔9-11保持与驱动油路8连通，供油路17与进油通道9-12连通， 单向组件设置在定位螺钉9-1上，并使进油通道9-12与油腔9-11单向连通。
本实施例中摇臂轴16上开设有与定位螺钉9-1相匹配的定位面16-1，定位螺钉9-1的内端端面与定位面16-1接触，以此实现将驱动器1固定在摇臂轴16上；值得注意的是，定位螺钉9-1还能够通过直接抵紧摇臂轴16外周面的方式，实现将驱动器1固定在摇臂轴16上。
本实施例中单向组件包括弹性元件9-2和单向球9-3，弹性元件9-2具体采用压缩弹簧，弹性元件9-2一端抵住油腔9-11的内壁，另一端抵住进油通道9-12与油腔9-11之间的连通处，其中，单向球9-3抵住进油通道9-12与油腔9-11之间的连通处，以防止油腔9-11中的油液进入到进油通道9-12，但是，进油通道9-12向油腔9-11供油时，弹性元件9-2会被压缩，单向球9-3打开进油通道9-12与油腔9-11之间的连通处，进油通道9-12与油腔9-11连通；从而能够继续简化定位控压单元9的结构，缩减生产成本；值得注意的是，本实施例中亦可直接采用单向阀替代单向组件。
驱动器1上设置有主弹性元件10，用于在驱动油路8内泄压时带动主活塞4回缩；从而利用主弹性元件10的弹力使主活塞4保持与专用驱动凸轮15分离的初始位置，只有在驱动油路8充油时，利用液压力克服主弹性元件10的弹力后，主活塞4才能够移动至接触专用驱动凸轮15；主弹性元件10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1-1的开口朝下，主活塞孔1-1的下端固定有主弹性元件支座12，主弹性元件10的一端抵住主弹性元件支座12，另一端抵住主活塞4。
驱动器1上设置有执行弹性元件11，执行弹性元件11具体可采用压缩弹簧，用于在驱动油路8内泄压时带动执行活塞7回缩，执行活塞孔1-3处设置有执行活塞限位单元13，执行活塞限位单元13用于限制执行活塞7沿执行活塞孔1-3 轴向的最大行程；从而利用执行弹性元件11的弹力使执行活塞7保持与气门桥2分离的初始位置，只有在驱动油路8充油时，利用液压力克服执行弹性元件11的弹力后，执行活塞7才能够移动至接触气门桥2；具体安装结构则可采用以下方式：执行活塞孔1-3的开口朝下，执行活塞孔1-3的下端固定执行活塞限位单元13，执行弹性元件11的一端抵住执行活塞限位单元13，另一端抵住执行活塞7，执行活塞7与执行活塞限位单元13接触时，执行活塞7到达向下位移的最大行程；为了实现执行活塞7稳定的与气门桥2进行密封接触，执行活塞7上具有执行活塞关节部7-2和执行活塞关节座7-3，执行活塞关节座7-3与执行活塞关节部7-2之间形成球面副连接或转动副连接，执行活塞关节座7-3用于和气门桥2接触，内油道7-1则相应的依次贯穿执行活塞7、执行活塞关节部7-2及执行活塞关节座7-3。
本实施例的工作原理为：
发动机的凸轮轴带动正功凸轮14和专用驱动凸轮15转动；
发动机的电磁阀关闭，供油路17停止供油，驱动油路8无油压，如图1所示，集成在驱动器1内的主活塞4和执行活塞7在弹簧力作用下处于关闭位置，并分别与专用驱动凸轮15和气门桥2分离，在专用驱动凸轮15转动过程中，专用驱动凸轮15与驱动器1的主活塞4不接触，专用驱动凸轮15的驱动升程不会传递到驱动器1和驱动气门18，只有在正功凸轮14转至正功升程过程中，正功升程通过摇臂3转动并由液压间隙调节器6带动气门桥2位移，同时打开驱动气门18和非驱动气门19，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，在正功凸轮14处于基圆和专用驱动凸轮15均处于基圆部15-1时，供油路17通过定位控压单元9中的单向组件向驱动油路8单向供油，驱动油路8充油，驱动油路8中的油液使主活塞4和执行 活塞7克服弹簧力而伸出，分别无间隙接触专用驱动凸轮15和气门桥2，执行活塞7与气门桥2密封连接，内油道7-1随之移动至与泄油道2-2连通；如图3所示，当专用驱动凸轮15转至驱动升程凸台15-2与主活塞4接触时，驱动升程凸台15-2推动驱动主活塞4，定位控压单元9内的单向组件由于液压回流关闭，封闭驱动油路8，主活塞4和副活塞5之间形成液压联动，副活塞5随主活塞4发生位移，从而由气门桥2内的副活塞5驱动打开与其相连的驱动气门18，实现发动机按专用驱动凸轮15的驱动升程打开驱动气门18；如图4所示，当正功凸轮14开始转至主升程凸台14-1与主活塞4接触时，摇臂3向下推动气门桥2，驱动气门18和非驱动气门19实现正功升程实现正功升程，同时使气门桥2与执行活塞7分离，自动打开气门桥2内的泄油道2-2，副活塞孔2-1内的机油在驱动气门18压力作用下通过泄油道2-2排出，副活塞5复位，缩回到未伸展位置，使整个气门机构恢复到正功姿态。
本实施例中执行活塞油道8-2经内油道7-1与执行活塞孔1-3连通时，内油道7-1的上端开口位于执行活塞7的上端面，在此情况下：如内油道7-1为等径孔时，执行活塞孔1-3内周壁上与执行活塞7滑动连接部位的横截面面积与内油道7-1横截面面积的差值为执行活塞7的有效作用面积；如内油道7-1为上端大下端小的两级阶梯孔时，执行活塞孔1-3内周壁上与执行活塞7滑动连接部位的横截面面积与内油道7-1横截面面积的最小值之间的差值为执行活塞7的有效作用面积；如内油道7-1为上端小下端大的两级阶梯孔时，执行活塞孔1-3内周壁上与执行活塞7滑动连接部位的横截面面积与内油道7-1横截面面积的最大值之间的差值为执行活塞7的有效作用面积；
执行活塞油道8-2从执行活塞孔1-3的上端与执行活塞孔1-3连通时(即内油道7-1的上端开口不位于执行活塞7的上端面)，在此情况下：执行活塞孔1-3 内周壁上与执行活塞7滑动连接部位的横截面面积为执行活塞7的有效作用面积；
副活塞孔2-1内周壁上与副活塞5滑动连接部位的横截面面积为执行副活塞5的有效作用面积；
设计时执行活塞7的有效作用面积小于副活塞5的有效作用面积，使驱动升程时气门桥2在驱动气门18侧受到向上的液压差力，以平衡气门桥2中部由液压间隙调节器6产生的向下推力，防止液压间隙调节器6过度伸出而增加气门正功升程。
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 (11)

  1. 一种液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：包括：
    驱动器(1)，具有滑动安装在主活塞孔(1-1)内的主活塞(4)、滑动安装在执行活塞孔(1-3)内的执行活塞(7)以及连通在主活塞孔(1-1)和执行活塞孔(1-3)之间的驱动油路(8)，所述执行活塞(7)上贯穿有与执行活塞孔(1-3)连通的内油道(7-1)，所述驱动器(1)固定安装在摇臂轴(16)上；
    摇臂(3)，安装有液压间隙调节器(6)，所述摇臂(3)转动安装在摇臂轴(16)上；
    专用驱动凸轮(15)，位于发动机正功凸轮(14)的一侧，并具有基圆部(15-1)和位于基圆部(15-1)上的驱动升程凸台(15-2)；
    位于执行活塞(7)和液压间隙调节器(6)下方的气门桥(2)，具有滑动安装在副活塞孔(2-1)内的副活塞(5)和连通副活塞孔(2-1)的泄油道(2-2)，驱动气门(18)与副活塞(5)连接，执行活塞(7)与气门桥(2)相对设置，执行活塞(7)用于被执行活塞孔(1-3)内的液体推动而沿其滑动方向移动的有效作用面积小于副活塞(5)用于被副活塞孔(2-1)内的液体推动而沿其滑动方向移动的有效作用面积；
    以及定位控压单元(9)，驱动油路(8)通过定位控压单元(9)与供油路(17)连通；在摇臂(3)未驱动气门桥(2)位移及供油路(17)向驱动油路(8)供油的状态下，执行活塞(7)在驱动油路(8)的液压作用下伸出接触气门桥(2)，内油道(7-1)与泄油道(2-2)连通；当专用驱动凸轮(15)转至基圆部(15-1)与主活塞(4)滑动或滚动配合时，主活塞(4)在驱动油路(8)的液压作用下伸出至接触基圆部(15-1)；当专用驱动凸轮(15)转至驱动升程凸台(15-2)与主活塞(4)滑动或滚动配合时，定位控压单元(9)阻断驱 动油路(8)与供油路(17)，主活塞(4)与副活塞(5)之间形成液压联动，使驱动升程凸台(15-2)得以通过主活塞(4)带动与副活塞(5)相连的驱动气门(18)位移；
    在摇臂(3)通过液压间隙调节器(6)带动气门桥(2)位移的状态下，泄油道(2-2)和内油道(7-1)随气门桥(2)的位移而分离，主活塞(4)与副活塞(5)之间解除液压联动，副活塞孔(2-1)内机油泄出，副活塞(5)在气门桥(2)内复位。
  2. 根据权利要求1所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述正功凸轮(14)位于摇臂(3)的一端，液压间隙调节器(6)位于摇臂(3)的另一端，所述正功凸轮(14)、液压间隙调节器(6)及气门桥(2)位于摇臂(3)的下方，所述主活塞(4)、专用驱动凸轮(15)、执行活塞(7)及气门桥(2)位于驱动器(1)的下方。
  3. 根据权利要求1所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述执行活塞(7)位于摇臂轴(16)与液压间隙调节器(6)之间。
  4. 根据权利要求1所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述供油路(17)通过定位控压单元(9)单向向驱动油路(8)供油。
  5. 根据权利要求4所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述驱动器(1)上开设与摇臂轴(16)相匹配的轴孔(1-2)，所述摇臂轴(16)穿过轴孔(1-2)，所述驱动器(1)通过定位控压单元(9)与摇臂轴(16)固定连接。
  6. 根据权利要求5所述的液压间隙自调专用驱动凸轮组合式气门驱动装置， 其特征在于：所述定位控压单元(9)包括定位螺钉(9-1)和单向组件，所述定位螺钉(9-1)内具有油腔(9-11)及与油腔(9-11)连通的进油通道(9-12)，所述供油路(17)设置在摇臂轴(16)上；
    所述定位螺钉(9-1)与驱动器(1)螺纹连接以此将驱动器(1)固定在摇臂轴(16)上，所述油腔(9-11)保持与驱动油路(8)连通，所述供油路(17)与进油通道(9-12)连通，所述单向组件设置在定位螺钉(9-1)上，并使进油通道(9-12)与油腔(9-11)单向连通。
  7. 根据权利要求6所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述摇臂轴(16)上开设有与定位螺钉(9-1)相匹配的定位面(16-1)，所述定位螺钉(9-1)的内端端面与所述定位面(16-1)接触。
  8. 根据权利要求6所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述单向组件包括弹性元件(9-2)和单向球(9-3)，所述弹性元件(9-2)一端抵住油腔(9-11)的内壁，另一端抵住进油通道(9-12)与油腔(9-11)之间的连通处。
  9. 根据权利要求6所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述驱动油路(8)包括均开设在驱动器(1)内的主活塞油道(8-1)和执行活塞油道(8-2)，所述主活塞油道(8-1)的一端与主活塞孔(1-1)连通，另一端与油腔(9-11)连通，所述执行活塞油道(8-2)的一端与油腔(9-11)连通，另一端与内油道(7-1)连通。
  10. 根据权利要求1所述的液压间隙自调专用驱动凸轮组合式气门驱动装置，其特征在于：所述驱动器(1)上设置有主弹性元件(10)，用于在驱动油路(8)内泄压时带动主活塞(4)回缩。
  11. 根据权利要求1所述的液压间隙自调专用驱动凸轮组合式气门驱动装 置，其特征在于：所述驱动器(1)上设置有执行弹性元件(11)，用于在驱动油路(8)内泄压时带动执行活塞(7)回缩，所述执行活塞孔(1-3)处设置有执行活塞限位单元(13)，执行活塞限位单元(13)用于限制执行活塞(7)沿执行活塞孔(1-3)轴向的最大行程。
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