WO2021008155A1 - 一种实现气门开启次数可变的液压气门机构及内燃机 - Google Patents

一种实现气门开启次数可变的液压气门机构及内燃机 Download PDF

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Publication number
WO2021008155A1
WO2021008155A1 PCT/CN2020/080041 CN2020080041W WO2021008155A1 WO 2021008155 A1 WO2021008155 A1 WO 2021008155A1 CN 2020080041 W CN2020080041 W CN 2020080041W WO 2021008155 A1 WO2021008155 A1 WO 2021008155A1
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Prior art keywords
valve
hydraulic
oil
hole
sleeve
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PCT/CN2020/080041
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English (en)
French (fr)
Inventor
王兆宇
谢宗法
韩康
Original Assignee
龙口中宇投资控股有限公司
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Application filed by 龙口中宇投资控股有限公司 filed Critical 龙口中宇投资控股有限公司
Priority to EP20786427.3A priority Critical patent/EP3943717A4/en
Priority to US15/733,893 priority patent/US11111825B1/en
Publication of WO2021008155A1 publication Critical patent/WO2021008155A1/zh

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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
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/14—Tappets; Push rods
    • 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
    • F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
    • 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
    • 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
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—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
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/101—Electromagnets
    • 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/103—Electric motors
    • 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/105—Hydraulic motors
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • F01L2303/02—Initial camshaft settings
    • 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
    • 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
    • F01L2313/00—Rotary valve drives
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/04—Sensors
    • F01L2820/041—Camshafts position or phase sensors

Definitions

  • the invention relates to a valve mechanism of an internal combustion engine, and in particular to a hydraulic valve mechanism and an internal combustion engine capable of achieving variable valve opening times within a working cycle of the internal combustion engine.
  • the intake valve opens during the intake process and the exhaust valve opens during the exhaust process, that is, the intake valve and the exhaust valve only need to be opened once in a working cycle.
  • the exhaust valve needs to be opened for the second time at the end of the compression stroke, so that the internal combustion engine can generate braking power and improve driving safety; Energy saving and emission reduction.
  • the intake valve needs to be opened twice during the exhaust stroke to achieve exhaust gas recirculation (EGR) or improve exhaust thermal management performance. Due to frequent changes in operating conditions of the internal combustion engine, it is necessary for the internal combustion engine to smoothly switch between a single valve opening operation mode and a two opening (or multiple opening) operation mode during operation.
  • EGR exhaust gas recirculation
  • the JackBrake engine brake device is a typical exhaust valve multiple opening device, which is realized by charging or de-energizing the solenoid valve, so that the brake oil passage of the swing arm shaft is flushed or not flushed. In the oil state, the brake piston is in the extended or retracted position to switch between multiple openings and single openings of the exhaust valve.
  • the Jakob engine brake device also has problems such as large exhaust cam lift, deep piston crown valve pits, and relatively complex structure.
  • the present invention provides a hydraulic valve mechanism that enables an internal combustion engine to achieve a single valve opening working mode, a two-opening working mode, or even a multiple-opening working mode within a working cycle.
  • This kind of hydraulic valve mechanism with variable valve opening times effectively expands the working mode of the internal combustion engine and has a significant effect on the energy saving, emission reduction and driving safety of the vehicle.
  • a hydraulic valve mechanism with variable valve opening times including:
  • the housing is provided with a first oil passage and a second oil passage;
  • An air distribution cam the air distribution cam has a main protrusion and at least one auxiliary protrusion, the air distribution cam can realize rotation, and the air distribution cam is arranged on the outside of the housing;
  • the hydraulic rotary valve is arranged in the housing and forms a hydraulic rotary valve oil cavity with the housing.
  • the hydraulic rotary valve includes a valve sleeve and a valve core with an axial hole.
  • the valve core is installed in the inner hole of the valve sleeve, and the valve core and the valve sleeve are wound around It rotates on the same axis and is provided with radial oil holes at corresponding axial positions.
  • the hydraulic rotary valve is in the open state.
  • the hydraulic rotary valve is closed; the hydraulic rotary valve oil cavity is connected with the first oil passage, and the spool axial hole is connected with the second oil passage;
  • the hydraulic drive component is supported by the housing and forms a hydraulic drive oil cavity with the housing.
  • the hydraulic drive component is driven by the air distribution cam, and the hydraulic drive oil cavity is in communication with the first oil passage;
  • the valve drive component is supported by the housing and forms a valve drive oil cavity with the housing.
  • the valve drive oil cavity communicates with the first oil passage.
  • auxiliary protrusions in the air distribution cam are arranged at positions other than the main protrusions in the air distribution cam;
  • valve spool is driven to rotate by the valve camshaft through a hydraulic rotary valve transmission mechanism, and the rotation speed ratio of the valve spool is N, where N is a positive integer;
  • the hydraulic rotary valve core is evenly distributed on the same circumference with the same number of radial oil holes as the speed ratio N, and the radial oil holes of the valve core are through holes and communicate with the axial holes of the valve core;
  • the hydraulic rotary valve is sleeved on the circumference of the axial position corresponding to the radial oil hole of the valve core, and radial oil holes matching the auxiliary protrusion of the valve cam are distributed.
  • the radial oil hole of the valve sleeve is open hole;
  • the end of the valve sleeve is provided with gear teeth, and the gear teeth are connected with the hydraulic rotary valve adjusting mechanism, and the hydraulic rotary valve adjusting mechanism drives the gear teeth to rotate, thereby driving the valve sleeve to rotate;
  • the valve sleeve is driven to rotate by the valve camshaft through a hydraulic rotary valve transmission mechanism, and the speed ratio between the valve sleeve and the valve camshaft is N, where N is a positive integer;
  • the hydraulic rotary valve is sleeved on the same circle
  • the radial oil holes of the valve sleeve are through holes;
  • the hydraulic rotary valve core is distributed on the circumference of the axial position corresponding to the radial oil holes of the valve sleeve
  • the radial oil hole of the valve core is a through hole and communicates with the axial hole of the valve core;
  • the end of the valve core is provided with gear teeth,
  • the gear teeth are connected with the hydraulic rotary valve adjustment mechanism, and the hydraulic rotary valve adjustment mechanism drives the gear teeth to rotate, thereby driving the valve core to rotate.
  • the central angle of the inner arc of the radial oil hole of the valve sleeve, the central angle of the outer arc of the radial oil hole of the valve core, and the product of the sum of the two central angles multiplied by the speed ratio N is greater than or equal to the same
  • the matching angle of the valve cam is occupied by the rising section of the auxiliary protrusion.
  • the hydraulic rotary valve adjusting mechanism includes a motor or a proportional electromagnet, and the motor or the proportional electromagnet meshes with the gear teeth through a gear, a rack or a tooth sector.
  • a hydraulic one-way valve is provided in the housing, the hydraulic one-way valve inlet is in communication with the second oil passage, and the hydraulic one-way valve outlet is in communication with the first oil passage.
  • the housing is provided with a hydraulic accumulator, the accumulator and the housing form an energy storage oil cavity, and the energy storage oil cavity is in communication with the second oil passage.
  • the hydraulic drive component is directly matched with the gas valve cam; or, in another solution, the hydraulic drive component fluid is matched with the gas valve cam through a roller swing arm, and the fixed end of the roller swing arm is supported by a ball head, The ball head is arranged on the shell, and the roller swing arm is in contact with the hydraulic drive component.
  • the present invention also provides an internal combustion engine, including the hydraulic valve mechanism with variable valve opening times.
  • the internal combustion engine lubrication system When the hydraulic valve mechanism with variable valve opening times of the present invention is installed on an internal combustion engine, the internal combustion engine lubrication system is communicated with the second oil passage provided on the housing.
  • the crankshaft of the internal combustion engine rotates, the crankshaft drives the valve camshaft to operate, and the valve camshaft drives the main protrusion and the auxiliary protrusion of the valve cam to drive the hydraulic tappet in the hydraulic drive component, and work together with the tappet spring to make the hydraulic tappet
  • the column makes a reciprocating linear motion.
  • the internal combustion engine lubrication system provides low pressure oil to the second oil passage on the housing.
  • the hydraulic valve mechanism with variable valve opening times of the present invention is provided with a first oil passage on the housing, and the first oil passage connects the hydraulic drive oil cavity, the hydraulic rotary valve oil cavity and the valve drive oil cavity.
  • the hydraulic rotary valve is closed, and the main protrusion drives the hydraulic tappet to make the hydraulic tappet in the first oil passage
  • the hydraulic oil in the first oil passage flows into the valve drive oil chamber, pushing the hydraulic piston in the valve drive component to overcome the force of the valve spring to open the valve, and the valve is in a normal opening and closing state; if the auxiliary protrusion drives the hydraulic tappet to do Reciprocating linear motion.
  • the hydraulic rotary valve is in the open state, and the auxiliary protrusion drives the hydraulic tappet to make the hydraulic oil in the first oil passage flow into the second oil passage through the hydraulic rotary valve.
  • the valve is closed, so the valve is in a working cycle Only a single opening is realized.
  • the main protrusion drives the hydraulic tappet in the hydraulic drive component to make a reciprocating linear motion, the hydraulic rotary valve is in the closed state, and the valve is in the normal opening and closing state; if the auxiliary protrusion is driven The hydraulic tappet makes a reciprocating linear motion. At this time, the hydraulic rotary valve is closed.
  • the auxiliary protrusion drives the hydraulic tappet to increase the oil pressure in the first oil passage.
  • the hydraulic oil from the first oil passage flows into the valve drive oil chamber to push the valve.
  • the hydraulic piston in the driving part overcomes the force of the valve spring to open the valve, so that the valve can be opened twice in the same working cycle. If there are two auxiliary protrusions on the valve cam, the valve can be opened three times in the same working cycle, and so on.
  • the air distribution camshaft drives the valve core to rotate synchronously with the camshaft through the hydraulic rotary valve transmission mechanism.
  • the motor or proportional electromagnet drives the end gears on the valve sleeve through the hydraulic rotary valve adjustment mechanism to make the valve sleeve rotate, thereby changing the opening time of the hydraulic rotary valve. Change the opening time of the hydraulic rotary valve so that the matching auxiliary protrusion rising section is in the opening period of the hydraulic rotary valve.
  • the auxiliary protrusion drives the hydraulic tappet to rise, the oil in the first oil passage flows into the second through the hydraulic rotary valve.
  • Oil passage the valve cannot be opened, and the internal combustion engine is in a single valve opening mode; change the opening time of the hydraulic rotary valve so that the matching auxiliary protrusion rising section is in the closing period of the hydraulic rotary valve, then the auxiliary protrusion drives the hydraulic tappet to rise
  • the valve is opened, and the internal combustion engine is in a secondary or even multiple-open working mode.
  • the hydraulic accumulator is used to store and release the hydraulic pressure energy, which can reduce the fluctuation of the hydraulic pressure in the second oil passage and make the second oil passage Stable hydraulic oil is added to the first oil passage through the hydraulic one-way valve.
  • hydraulic drive components include hydraulic tappet/tappet sleeve matching pairs
  • hydraulic rotary valves include valve core/valve sleeve matching pairs
  • valve drive components include hydraulic piston/piston sleeve matching pairs.
  • the present invention can not only realize the variable valve opening times, but also realize the continuous variable of the lift and valve phase of the intake valve or exhaust valve at the same time.
  • the intake valve In the exhaust brake working mode, the intake valve is re-opened in the original expansion (work) stroke, which can realize the second intake (the first intake is the intake process) and reduce the exhaust brake work Thermal load in mode improves braking efficiency.
  • the internal combustion engine valve can be opened multiple times in the same working cycle, which greatly expands the operating mode of the internal combustion engine.
  • Fig. 1 is a schematic diagram of a hydraulic valve mechanism with variable valve opening times according to the present invention.
  • Fig. 2 is a sectional view taken along line A-A in Fig. 1.
  • Fig. 3 is a B-B sectional view in Fig. 2.
  • Figure 4 is a schematic diagram of the outline structure of the hydraulic valve mechanism of the present invention
  • Figure 5 is a schematic diagram of hydraulic drive components with a roller swing arm.
  • Fig. 6 is a schematic diagram of the valve lift and the lift of the tappet in the single-open working mode of the present invention.
  • Fig. 7 is a schematic diagram of valve lift and tappet lift in the second opening mode of the present invention.
  • Valve cam 1-1 main protrusion 1-2, auxiliary protrusion
  • Valve assembly Hydraulic check valve 7-1, Check valve spring 7-2, Check valve core
  • Hydraulic accumulator 8-1 energy storage piston 8-2, energy storage spring 8-3, energy storage oil chamber
  • roller swing arm 10 ball head 11, valve camshaft 11-1, camshaft gear 12, stepper motor
  • This embodiment provides a hydraulic valve mechanism with variable valve opening times, as shown in FIGS. 1 to 6, including a valve cam 1, a hydraulic drive component 2, a hydraulic rotary valve 3, a housing 4, and a valve drive component 5.
  • the valve driving component 5 drives the valve in the valve assembly 6, and the valve assembly 6 is a prior art, including a valve and a valve spring, and will not be repeated.
  • the housing 4 is provided with a first oil passage 4-1 and a second oil passage 4-2.
  • the valve cam 1 includes a main protrusion 1-1 and an auxiliary protrusion 1-2.
  • the valve cam 1 is an exhaust cam or an intake cam.
  • the main protrusion 1-1 of the exhaust cam is the protrusion that opens the exhaust valve during the exhaust stroke, and the auxiliary protrusion 1-2 of the exhaust cam is set in the exhaust corresponding to the intake stroke, compression stroke and power stroke.
  • the main protrusion 1-1 of the intake cam is the protrusion that opens the intake valve during the intake stroke, and the auxiliary protrusion 1-2 of the intake cam is set in the compression stroke, power stroke and exhaust
  • Hydraulic drive component 2 including hydraulic tappet 2-1, tappet sleeve 2-2 and tappet spring 2-3, hydraulic tappet 2-1 and tappet sleeve 2-2 form a hydraulic tappet/tap sleeve matching pair ,
  • the hydraulic drive component 2 is installed on the housing 4 and forms a hydraulic drive oil cavity 2-4 with the housing 4.
  • the hydraulic drive oil cavity 2-4 communicates with the first oil passage 4-1, and the hydraulic valve in the hydraulic drive component 2
  • the column 2-1 is driven by the valve cam 1.
  • the hydraulic rotary valve 3 is arranged in the housing 4 and forms a hydraulic rotary valve oil chamber 3-3 with the housing 4.
  • the hydraulic rotary valve 3 includes a valve sleeve 3-2 and a valve core axial hole 3-1-3
  • the spool 3-1 and the spool 3-1 are installed in the inner hole of the valve sleeve 3-2 to form the valve core/valve sleeve matching pair.
  • the spool 3-1 and the valve sleeve 3-2 rotate around the same axis and are in corresponding
  • the radial oil holes are respectively provided at the axial positions.
  • valve core radial oil holes 3-1-1 and the valve sleeve radial oil holes 3-2-1 When the valve core radial oil holes 3-1-1 and the valve sleeve radial oil holes 3-2-1 are connected, the hydraulic rotary valve 3 is in the open state; When the core radial oil hole 3-1-1 and the valve sleeve radial oil hole 3-2-1 are mutually staggered, the hydraulic rotary valve 3 is closed; the hydraulic rotary valve oil cavity 3-3 and the first oil passage 4-1 The valve core axial hole 3-1-3 communicates with the second oil passage 4-2.
  • the valve drive component 5 includes a hydraulic piston 5-1 and a piston sleeve 5-2.
  • the hydraulic piston 5-1 and the piston sleeve 5-2 form a hydraulic piston/piston sleeve pair; the valve drive component 5 is supported by the housing 4 and is connected to the housing
  • the body forms a valve drive oil chamber 5-3, which communicates with the first oil passage 4-1; when the valve core radial oil hole 3-1-1 and the valve sleeve radial oil hole 3-2- 1.
  • the hydraulic rotary valve 3 is in the closed state when they are staggered, and the main protrusion 1-1 or the auxiliary protrusion 1-2 of the valve cam 1 drives the hydraulic tappet 2-1 in the hydraulic drive component 2 to make the hydraulic drive oil chamber 2-
  • the volume reduction of 4 produces high-pressure oil, which enters the valve drive oil chamber 5-3 through the first oil passage 4-1, and pushes the hydraulic piston 5-1 to open the valve.
  • the internal combustion engine lubrication system is in communication with the second oil passage 4-2 provided on the housing 4.
  • the crankshaft of the internal combustion engine rotates, the crankshaft drives the valve camshaft 11 to operate, and the valve camshaft 11 drives the main protrusion 1-1 and the auxiliary protrusion 1-2 of the valve cam 1 to drive the hydraulic tappet 2 in the hydraulic drive component 2 -1, and work with the tappet spring 2-3 to make the hydraulic tappet 2-1 make a reciprocating linear motion.
  • the internal combustion engine lubrication system provides low-pressure oil to the second oil passage 4-2 on the housing 4.
  • a hydraulic valve mechanism with variable valve opening times is provided with a first oil passage 4-1 on the housing 4.
  • the first oil passage 4-1 drives the oil chamber 2-4 and the hydraulic rotary valve oil
  • the cavity 3-3 communicates with the valve drive oil cavity 5-3.
  • auxiliary protrusion 1-2 drives the hydraulic tappet 2-1 to make a reciprocating linear motion, at this time the radial oil hole 3-1-1 of the spool of the hydraulic rotary valve 3 rotates exactly to the radial oil hole 3-2 of the valve sleeve.
  • the main protrusion 1-1 drives the hydraulic tappet 2-1 in the hydraulic drive component 2 to make a reciprocating linear motion, the hydraulic rotary valve 3 is in the closed state, and the valve is in the normal opening state.
  • the crankshaft drives the valve camshaft 11 to operate.
  • the valve camshaft 11 is provided with a camshaft gear 11-1.
  • the hydraulic rotary valve transmission mechanism includes a camshaft gear 11-1, an intermediate transmission gear 3-6 and Spool end gear 3-1-2.
  • the valve spool 3-1 is driven by the valve spool 11 to realize synchronous rotation through the hydraulic rotary valve transmission mechanism.
  • the rotation speed ratio N of the valve spool 11 and the valve spool 3-1 is 2.
  • valve sleeve 3-2 of the hydraulic rotary valve 3 is distributed on the circumference of the axial position corresponding to the radial oil hole 3-1-1 of the valve core, which matches the auxiliary protrusion 1-2 of the valve cam 1
  • the two valve sleeve radial oil holes 3-2-1, the valve sleeve radial oil holes 3-2-1 are also through holes and communicate with the hydraulic rotary valve oil cavity 3-3.
  • the end of the valve sleeve 3-2 is provided with valve sleeve end gears 3-2-2, and the valve sleeve end gears 3-2-2 are connected with the hydraulic rotary valve adjusting mechanism.
  • the hydraulic rotary valve adjusting mechanism includes a stepping motor 12. Tooth sector 3-4 and tooth sector shaft 3-5, stepping motor 12 and tooth sector shaft 3-5 are all supported by housing 4, stepping motor 12 drives tooth sector shaft 3-5 to make tooth sector 3- 4 rotates, the tooth fan 3-4 drives the end gear 3-2-2 of the valve sleeve to rotate, and then drives the valve sleeve radial oil hole 3-2-1 on the valve sleeve 3-2 to rotate.
  • the hydraulic rotary valve adjusting mechanism makes the radial oil hole 3-2-1 on the valve sleeve 3-2 rotate forward or reverse within a set angle range to change the opening and closing time of the hydraulic rotary valve.
  • valve lift curve B1 and the tappet lift curve B there are valve lift curve B1 and the tappet lift curve B; the main protrusion 1-1 corresponds to the valve lift curve A1 and the tappet lift Curve A. Therefore, the valve can be opened twice at the corresponding positions of the main protrusion 1-1 and the auxiliary protrusion 1-2 in one working cycle of the internal combustion engine.
  • the opening period of the hydraulic rotary valve is from the beginning of the communication between the radial oil hole 3-1-1 of the valve core and the radial oil hole 3-2-1 of the valve sleeve to the radial oil hole 3-1-1 of the valve core and the valve sleeve diameter. To the oil hole 3-2-1 just stagger the end of the cam angle experienced.
  • the product of the central angle of the inner arc of the radial oil hole 3-2-1 of the valve sleeve and the central angle of the outer arc of the valve core radial oil hole 3-1-1 multiplied by the speed ratio N is the hydraulic rotation During the valve opening period, the opening period of the hydraulic rotary valve should be greater than or equal to the matching cam angle of the auxiliary protrusion rising section to ensure that the valve cannot be opened in the auxiliary protrusion rising section.
  • the oil pressure in the second oil passage 4-2 is unstable, and the hydraulic accumulator 8 is used to store and release hydraulic pressure energy.
  • the accumulating piston 8-1 compresses the accumulating spring 8-2, and the volume of the accumulating oil chamber 8-3 increases and the pressure decreases; when the accumulating oil chamber 8
  • the energy storage spring 8-2 expands, the volume of the energy storage oil chamber 8-3 decreases and the pressure increases.
  • the oil pressure in the accumulator oil chamber 8-3 and the second oil passage 4-2 can be kept stable, and at the same time, the second oil passage 4-2 can be directed to the first oil passage 4-1 through the hydraulic check valve 7 Replenish stable hydraulic oil.
  • a roller swing arm can be added between the hydraulic tappet and the valve cam.
  • the hydraulic tappet 2-1 of the hydraulic drive component 2 is matched with the valve cam 1 through the roller swing arm 9.
  • the fixed end of the roller swing arm 9 is supported by the ball head 10, which is set in the housing 4
  • the roller swing arm 9 is in contact with the hydraulic tappet 2-1 of the hydraulic drive component 2, and the roller swing arm 9 and the tappet spring 2-3 work together to make the hydraulic tappet 2-1 make a reciprocating linear motion.
  • the strokes of the hydraulic tappet 2-1 and the hydraulic piston 5-1 are different at the same time, so that the valve lift is different from that of the hydraulic piston 5-1.
  • the lift of the tappet has a set proportional relationship, that is, the lift ratio is realized, as shown in Figure 6 and Figure 7.
  • the lift ratio is equal to the ratio of the cross-sectional area of the hydraulic tappet 2-1 and the hydraulic piston 5-1.
  • the corresponding position of the auxiliary protrusion of the intake cam is set in the power stroke, and the corresponding position of the auxiliary protrusion of the exhaust cam is set in the late compression stroke and the early intake stroke.
  • the intake valve is opened again during the expansion (work) stroke, which can realize the second intake (the first intake is the intake process), and reduce the exhaust brake working mode. Thermal load improves braking efficiency.
  • auxiliary protrusions of the exhaust cam and the auxiliary protrusions of the intake cam are arranged in a variety of different positions, and the internal combustion engine can also realize a variety of different functions.
  • the opening time of the hydraulic rotary valve 3 is changed by the hydraulic rotary valve adjusting mechanism, so as to realize the switching between the two (or multiple) valve opening mode and the single opening mode of the valve.
  • the opening time of the hydraulic rotary valve 3 is changed by the hydraulic rotary valve adjusting mechanism, so as to realize the switching between the two (or multiple) valve opening mode and the single opening mode of the valve.
  • This embodiment discloses an internal combustion engine, including a hydraulic valve mechanism with variable valve opening times described in Example 1.
  • the housing 4 of the hydraulic valve mechanism is mounted on the top of the cylinder head of the internal combustion engine and is integrated with the valve assembly of the internal combustion engine. Cooperate.
  • the valve cam 1 in the hydraulic valve train is a valve cam set on the valve camshaft of an internal combustion engine.
  • the center line of the spool 3-1 in the hydraulic rotary valve 3 is parallel to the valve camshaft 11.
  • the gear in the rotary valve transmission mechanism meshes with the camshaft gear 11-1 provided on the valve camshaft 11 through the intermediate transmission gear 3-6.
  • 4 sets of hydraulic drive components 2, 8 sets of valve drive components 5 (single cylinder 4 valve structure) and 4 sets of hydraulic rotary valves 3 are arranged in the housing 4, and the intermediate transmission gears 3-6 are arranged in the housing 4.
  • the middle part of the spool is driven by a set of intermediate transmission gears 3-6 to drive multiple valve cores 3-1 to rotate.
  • the valve sleeve 3-2 of the hydraulic rotary valve 3 is driven by the stepping motor 12 through the gear sector shaft 3-5 and the gear sector 3-4 drives to achieve rotation.
  • the center line of the spool 3-1 in the hydraulic rotary valve 3 and the valve camshaft 11 are staggered.

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Abstract

一种气门开启次数可变的液压气门机构及内燃机，包括壳体（4）、带有一个主凸起（1-1）和至少一个副凸起（1-2）的配气凸轮（1）、具有液压开关阀作用的液压回转阀（3）、液压驱动部件（2）和气门驱动部件（5）等。液压驱动部件（2）、液压回转阀（3）和气门驱动部件（5）之间油路相通。解决了现有技术中只能通过高频电磁阀实施气门多次开启的问题，能有效实现在同一工作循环内气门单次开启工作模式、两次或多次开启工作模式，且能够根据内燃机的工况需要实现各种工作模式之间的迅速平稳切换。对改善内燃机排气热管理性能，实施进气门二次进气，实现缸内排气制动等具有重要作用。

Description

一种实现气门开启次数可变的液压气门机构及内燃机 技术领域
本发明涉及内燃机的气门机构，特别是涉及内燃机在一个工作循环内实现气门开启次数可变的液压气门机构及内燃机。
背景技术
传统内燃机在工作状态时，进气过程时进气门开启，排气过程时排气门开启，即进气门和排气门在一个工作循环内仅需要实现单次开启即可。但随着内燃机技术的不断发展和完善，在某些情况下迫切需要内燃机在一个工作循环内实现气门两次开启甚至多次开启。例如，当商用汽车在坡度较大的公路上长时间处于下坡行驶时，需要排气门在压缩冲程末期实现第二次开启，使内燃机产生制动功率，提高行驶安全性；为了实现内燃机的节能减排，在某些运行工况下，需要进气门在排气冲程时实现二次开启，以实现废气再循环(EGR)或改善排气热管理性能。由于内燃机运行工况变换频繁，需要内燃机在运行过程中即可平稳实现气门单次开启工作模式和两次开启(或多次开启)工作模式之间的切换。
目前，皆可博(JackBrake)发动机制动装置是一种典型的排气门多次开启装置，并通过电磁阀的充电或断电实现，使摆臂轴制动油道处于冲油或不冲油状态，制动活塞则处于伸出或缩回位置，实现排气门的多次开启与单次开启之间的切换。但皆可博发动机制动装置也存在排气凸轮升程大、需要设置深的活塞顶气门凹坑、结构相对复杂等问题。
发明内容
为了克服现有技术的不足，本发明提供了一种使内燃机在一个工作循环内实现气门单次开启工作模式、两次开启工作模式、甚至多次开启工作模式的液压气门机构，并在运行过程中实现各种工作模式之间的平稳切换，这种气门开启次数可变的液压气门机构有效扩展了内燃机的工作模式，对汽车的节能减排及行驶安全具有重大作用。
一种气门开启次数可变的液压气门机构，包括：
壳体，设有第一油道和第二油道；
配气凸轮，配气凸轮带有一个主凸起和至少一个副凸起，配气凸轮能够实现 转动，配气凸轮设于壳体的外部；
液压回转阀，设于壳体内并与壳体形成液压回转阀油腔，液压回转阀包括阀套和设有轴向孔的阀芯，阀芯安装于阀套内孔，阀芯和阀套绕同一轴线转动并在相对应的轴向位置上分别设有径向油孔，当阀芯和阀套的径向油孔相连通时液压回转阀处于开通状态，当阀芯和阀套的径向油孔相互错开时液压回转阀则处于关闭状态；液压回转阀油腔与第一油道连通，阀芯轴向孔与第二油道连通；
液压驱动部件，通过壳体支撑并与壳体形成液压驱动油腔，液压驱动部件由配气凸轮驱动，液压驱动油腔与第一油道连通；
气门驱动部件，通过壳体支撑并与壳体形成气门驱动油腔，气门驱动油腔与与第一油道相通，当阀芯和阀套的径向油孔相互错开时液压回转阀处于关闭状态，液压驱动部件驱动气门驱动部件使相应气门打开；
进一步的，所述配气凸轮中副凸起设于所述配气凸轮中非主凸起设置的位置；
进一步的，所述配气凸轮轴通过液压回转阀传动机构带动所述阀芯实现转动，配气凸轮轴与阀芯的转速比为N,N为正整数；
进一步的，所述液压回转阀芯在同一圆周上均匀分布有与转速比N相同数量的径向油孔，所述阀芯径向油孔为通孔且与阀芯轴向孔相通；所述液压回转阀套在阀芯径向油孔对应的轴向位置的圆周上，分布着与所述配气凸轮的副凸起相匹配的径向油孔，所述阀套径向油孔为通孔；
进一步的，所述阀套端部设有轮齿，轮齿与液压回转阀调节机构连接，由液压回转阀调节机构带动轮齿转动进而带动阀套实现转动；
或者，所述配气凸轮轴通过液压回转阀传动机构带动所述阀套实现转动，配气凸轮轴与阀套的转速比为N,N为正整数；所述液压回转阀套在同一圆周上均匀分布有与转速比N相同数量的径向油孔，所述阀套径向油孔为通孔；所述液压回转阀芯在阀套径向油孔对应的轴向位置的圆周上，分布着与所述配气凸轮的副凸起相匹配的径向油孔，所述阀芯径向油孔为通孔且与阀芯轴向孔相通；所述阀芯端部设有轮齿，轮齿与液压回转阀调节机构连接，由液压回转阀调节机构带动轮齿转动进而带动阀芯实现转动。
进一步的，所述阀套径向油孔的内圆弧中心角、所述阀芯径向油孔的外圆弧 中心角，两中心角之和乘以转速比N之积大于等于与之相匹配的副凸起上升段所占配气凸轮转角。
进一步的，所述液压回转阀调节机构包括电机或比例电磁铁，电机或比例电磁铁通过齿轮或齿条或齿扇与所述的轮齿啮合。
进一步的，所述壳体内设置液压单向阀，液压单向阀入口与第二油道连通，液压单向阀出口与第一油道连通。
进一步的，所述壳体设置液压蓄能器，蓄能器与壳体形成蓄能油腔，蓄能油腔与第二油道连通。
进一步的，所述液压驱动部件与配气凸轮直接配合；或者，在另一方案中，所述液压驱动部件液通过滚轮摆臂与配气凸轮配合，滚轮摆臂的固定端通过球头支撑，球头设置于壳体上，滚轮摆臂与液压驱动部件接触。
本发明还提供了一种内燃机，包括所述的一种气门开启次数可变的液压气门机构。
本发明的一种气门开启次数可变的液压气门机构安装在内燃机上时，内燃机润滑系统与壳体上设置的第二油道连通。当内燃机曲轴转动时，曲轴驱动配气凸轮轴运转，配气凸轮轴带动配气凸轮的主凸起和副凸起驱动液压驱动部件中的液压挺柱，并与挺柱弹簧共同作用使液压挺柱做往复直线运动。同时，内燃机润滑系统给壳体上的第二油道提供低压油液。
本发明的一种气门开启次数可变的液压气门机构在壳体上设置第一油道，所述第一油道将液压驱动油腔、液压回转阀油腔和气门驱动油腔连通。当内燃机处于气门单次开启工作模式时，若主凸起驱动液压驱动部件中的液压挺柱做往复直线运动，则液压回转阀处于关闭状态，主凸起驱动液压挺柱使得第一油道内的油压升高，第一油道的液压油流入气门驱动油腔，推动气门驱动部件中的液压活塞克服气门弹簧力将气门打开，气门处于正常启闭状态；若副凸起驱动液压挺柱做往复直线运动，此时液压回转阀处于开通状态，副凸起驱动液压挺柱使第一油道内的液压油通过液压回转阀流入第二油道，气门处于关闭状态，因此气门在一个工作循环内只实现了单次开启。
当内燃机处于气门两次或多次开启工作模式时，主凸起驱动液压驱动部件中的液压挺柱做往复直线运动，液压回转阀处于关闭状态，气门处于正常启闭状态； 若副凸起驱动液压挺柱做往复直线运动，此时液压回转阀处于关闭状态，副凸起驱动液压挺柱使得第一油道内的油压升高，第一油道的液压油流入气门驱动油腔，推动气门驱动部件中的液压活塞克服气门弹簧力将气门打开，使气门在同一工作循环内，实现二次开启。若配气凸轮上设置两个副凸起，则气门在同一工作循环内，实现三次开启，依次类推。
当在壳体上装有滚轮摆臂时，随着凸轮轴转动，配气凸轮驱动滚轮摆臂绕球头作摆动，滚轮摆臂推动液压挺柱，液压挺柱在滚轮摆臂和挺柱弹簧的共同作用下作往复直线运动。
配气凸轮轴通过液压回转阀传动机构驱动阀芯与凸轮轴同步转动。电机或比例电磁铁通过液压回转阀调节机构驱动阀套上的端部轮齿可使阀套转动，从而改变液压回转阀的开通时刻。改变液压回转阀开通时刻使与之相匹配的副凸起上升段处于液压回转阀开通期内，则副凸起驱动液压挺柱上升时，第一油道内的油液通过液压回转阀流入第二油道，气门无法开启，内燃机处于气门单次开启工作模式；改变液压回转阀开通时刻使与之相匹配的副凸起上升段处于液压回转阀关闭期内，则副凸起驱动液压挺柱上升时，第一油道内的油液流入气门驱动油腔，气门开启，内燃机处于二次开启甚至多次开启工作模式。
当配气凸轮的主凸起或副凸起处于下降过程时，则随着液压挺柱的下降，液压驱动油腔的体积增大，第一油道内液压油的压力降至低于第二油道内液压油的压力时，液压单向阀开启，第二油道通过液压单向阀向第一油道内补充液压油，保证液压油始终充满液压驱动油腔、气门驱动油腔和第一油道。
由于液压回转阀是间歇开启和关闭，导致第二油道内的油压不稳定，利用液压蓄能器储存和释放液压压力能，可减小第二油道内液压压力的波动，使第二油道通过液压单向阀向第一油道内补充稳定的液压油。
本发明的一种气门开启次数可变的液压气门机构中，液压驱动部件中的液压挺柱、液压回转阀中的阀芯和气门驱动部件中的液压活塞等都是运动件，要减少油液的泄漏，必须采用间隙密封。因此，液压驱动部件包括液压挺柱/挺柱套配副，液压回转阀包括阀芯/阀套配副，气门驱动部件包括液压活塞/活塞套配副等。
显然，若在液压回转阀的阀套上设置与主凸起对应的径向油孔，可以实现主凸起所对应的气门升程变小、气门提前关闭等功能。因此，本发明不但能够实现 气门开启次数可变，而且能够同时实现进气门或排气门的升程和配气相位的连续可变。
与现有技术相比，本发明的有益效果是：
(1)使排气门在压缩冲程后期和进气冲程初期再次开启，可实现排气制动工作模式；
(2)使进气门在排气冲程开启，可使部分废气倒流回进气管，并参加下一循环的燃烧过程，改善排气热管理性能；
(3)在排气制动工作模式下，使进气门在原膨胀(做功)冲程再开启，可实现第二次进气(第一次进气为进气过程)，降低排气制动工作模式下的热负荷，改善制动效率。
(4)且能根据具体情况实现气门两次(或多次)开启模式与单次开启模式的切换，切换过程平稳、迅速、无冲击。
(5)本发明通过气门开启次数可变的液压气门机构，能够实现内燃机气门在同一工作循环内的多次开启，极大地扩展了内燃机的工作模式。
附图说明
构成本发明的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。
图1为本发明的一种气门开启次数可变的液压气门机构示意图。
图2为图1中的A-A剖面图。
图3为图2中的B-B剖面图。
图4为本发明的液压气门机构外形结构示意图
图5为带滚轮摆臂的液压驱动部件示意图。
图6为本发明单次开启工作模式时的气门升程和挺柱升程示意图。
图7为本发明二次开启模式时的气门升程和挺柱升程示意图。
附图标记：
1、配气凸轮 1-1、主凸起 1-2、副凸起
2、液压驱动部件 2-1、液压挺柱 2-2、挺柱套 2-3、挺柱弹簧 2-4、液压驱动油腔
3、液压回转阀 3-1、阀芯 3-1-1、阀芯径向油孔 3-1-2、阀芯端部齿 轮 3-1-3、阀芯轴向孔 3-2、阀套 3-2-1、阀套径向油孔 3-2-2、阀套端部轮齿 3-3、液压回转阀油腔 3-4、齿扇 3-5、齿扇轴 3-6、中间传动齿轮
4、壳体 4-1、第一油道 4-2、第二油道
5、气门驱动部件 5-1、液压活塞 5-2、活塞套 5-3、气门驱动油腔
6、气门组件 7、液压单向阀 7-1、单向阀弹簧 7-2、单向阀芯
8、液压蓄能器 8-1、蓄能活塞 8-2、蓄能弹簧 8-3、蓄能油腔
9、滚轮摆臂 10、球头 11、配气凸轮轴 11-1、凸轮轴齿轮 12、步进电机
具体实施方式
为使本发明要解决的技术问题、技术方案和优点更加清楚，下面将结合附图及具体实施例进行详细描述。
实施例1
本实施例提供一种气门开启次数可变的液压气门机构，如图1至图6所示，包括配气凸轮1、液压驱动部件2、液压回转阀3、壳体4、气门驱动部件5。气门驱动部件5驱动气门组件6中气门，气门组件6为现有技术，包括气门和气门弹簧，不再赘述。
壳体4设有第一油道4-1和第二油道4-2。
配气凸轮1包括一个主凸起1-1和一个副凸起1-2。配气凸轮1为排气凸轮或进气凸轮。排气凸轮的主凸起1-1是在排气冲程使排气门开启的凸起，排气凸轮的副凸起1-2设置在进气冲程、压缩冲程和做功冲程相对应的排气凸轮的某一位置；进气凸轮的主凸起1-1是在进气冲程使进气门开启的凸起，进气凸轮的副凸起1-2设置在压缩冲程、做功冲程和排气冲程相对应的进气凸轮的某一位置。
液压驱动部件2，包括液压挺柱2-1、挺柱套2-2和挺柱弹簧2-3，液压挺柱2-1与挺柱套2-2组成液压挺柱/挺柱套配副，液压驱动部件2安装在壳体4上并与壳体4形成液压驱动油腔2-4，液压驱动油腔2-4与第一油道4-1连通,液压驱动部件2中的液压挺柱2-1由配气凸轮1驱动。
液压回转阀3，设于壳体4内并与壳体4形成液压回转阀油腔3-3，液压回转阀3包括阀套3-2和设有阀芯轴向孔3-1-3的阀芯3-1，阀芯3-1安装于阀套 3-2的内孔组成阀芯/阀套配副，阀芯3-1和阀套3-2绕同一轴线转动，并在相对应的轴向位置上分别设有径向油孔，当阀芯径向油孔3-1-1和阀套径向油孔3-2-1相连通时液压回转阀3处于开通状态；当阀芯径向油孔3-1-1和阀套径向油孔3-2-1相互错开时液压回转阀3则处于关闭状态；液压回转阀油腔3-3与第一油道4-1连通，阀芯轴向孔3-1-3与第二油道4-2连通。
气门驱动部件5，包括液压活塞5-1与活塞套5-2，液压活塞5-1与活塞套5-2组成液压活塞/活塞套配副；气门驱动部件5通过壳体4支撑并与壳体形成气门驱动油腔5-3，气门驱动油腔5-3与第一油道4-1相通；当阀芯径向油孔3-1-1和阀套径向油孔3-2-1相互错开时液压回转阀3处于关闭状态，配气凸轮1的主凸起1-1或副凸起1-2驱动液压驱动部件2中的液压挺柱2-1使液压驱动油腔2-4的体积减小产生高压油液，高压油液经第一油道4-1进入气门驱动油腔5-3，推动液压活塞5-1使气门打开。
本实施例中的一种气门开启次数可变的液压气门机构安装在内燃机上时，内燃机润滑系统与壳体4上设置的第二油道4-2连通。当内燃机曲轴转动时，曲轴驱动配气凸轮轴11运转，配气凸轮轴11带动配气凸轮1的主凸起1-1和副凸起1-2驱动液压驱动部件2中的液压挺柱2-1，并与挺柱弹簧2-3共同作用使液压挺柱2-1做往复直线运动。同时，内燃机润滑系统给壳体4上的第二油道4-2提供低压油液。
本实施例中的一种气门开启次数可变的液压气门机构在壳体4上设置第一油道4-1，第一油道4-1将液压驱动油腔2-4、液压回转阀油腔3-3和气门驱动油腔5-3连通。当内燃机处于气门单次开启工作模式时，若主凸起1-1驱动液压驱动部件2中的液压挺柱2-1做往复直线运动，液压回转阀3的阀芯径向油孔3-1-1和阀套径向油孔3-2-1错开，液压回转阀3处于关闭状态，主凸起1-1驱动液压挺柱2-1使得第一油道4-1内的油压升高，第一油道4-1的液压油流入气门驱动油腔5-3，推动气门驱动部件5中的液压活塞5-1克服气门弹簧力将气门打开，气门处于正常启闭状态。若副凸起1-2驱动液压挺柱2-1做往复直线运动，此时液压回转阀3的阀芯径向油孔3-1-1恰好转动到与阀套径向油孔3-2-1相连通的位置，液压回转阀3处于开通状态，副凸起1-2驱动液压挺柱2-1使第一油道4-1内的液压油依次通过液压回转阀油腔3-3、阀套径向油孔3-2-1、阀芯径向油孔 3-1-1、阀芯轴向孔3-1-3流入到第二油道4-2内，液压活塞5-1无法克服气门弹簧力将气门打开，气门处于关闭状态，因此气门在一个工作循环内只实现了单次开启。
当内燃机处于气门两次或多次开启工作模式时，主凸起1-1驱动液压驱动部件2中的液压挺柱2-1做往复直线运动，液压回转阀3处于关闭状态，气门处于正常启闭状态；若副凸起1-2驱动液压挺柱2-1做往复直线运动，此时液压回转阀3的阀芯径向油孔3-1-1和阀套径向油孔3-2-1错开，液压回转阀3处于关闭状态，副凸起1-2驱动液压挺柱2-1使得第一油道4-1内的油压升高，第一油道4-1的液压油流入气门驱动油腔5-3，推动气门驱动部件5中的液压活塞5-1克服气门弹簧力将气门打开，使气门在同一工作循环内实现二次开启。
当内燃机处于运转状态时，曲轴驱动配气凸轮轴11运转，配气凸轮轴11上设置凸轮轴齿轮11-1，液压回转阀传动机构包括凸轮轴齿轮11-1、中间传动齿轮3-6和阀芯端部齿轮3-1-2。配气凸轮轴11通过液压回转阀传动机构带动阀芯3-1实现同步转动，在本实施例中配气凸轮轴11与阀芯3-1的转速比N为2。在液压回转阀3的阀芯3-1的同一圆周上均匀分布有与转速比N相同数量的2个阀芯径向油孔3-1-1，阀芯径向油孔3-1-1是通孔且与阀芯轴向孔3-1-3相通。液压回转阀3的阀套3-2在阀芯径向油孔3-1-1对应的轴向位置的圆周上，分布着与所述配气凸轮1的副凸起1-2相匹配的2个阀套径向油孔3-2-1，阀套径向油孔3-2-1也为通孔且与液压回转阀油腔3-3连通。
阀套3-2的端部设有阀套端部轮齿3-2-2，阀套端部轮齿3-2-2与液压回转阀调节机构连接，液压回转阀调节机构包括步进电机12、齿扇3-4和齿扇轴3-5，步进电机12和齿扇轴3-5均通过壳体4进行支撑，步进电机12驱动齿扇轴3-5使齿扇3-4转动，齿扇3-4带动阀套端部轮齿3-2-2转动进而带动阀套3-2上的阀套径向油孔3-2-1实现转动。液压回转阀调节机构使阀套3-2上的径向油孔3-2-1在设定角度范围正向或反向转动以改变液压回转阀的开通时刻和关闭时刻。
转动阀套3-2进而改变液压回转阀3的开通时刻，使与之相匹配的副凸起1-2上升段处于液压回转阀开通期内，如图6所示。当液压回转阀3处于开通状态时，副凸起1-2驱动液压挺柱2-1使第一油道4-1内的液压油依次通过液压回转阀油 腔3-3、阀套径向油孔3-2-1、阀芯径向油孔3-1-1、阀芯轴向孔3-1-3流入到第二油道4-2内，液压活塞5-1无法克服气门弹簧力将气门打开，副凸起1-2无法使气门开启。在图6所示副凸起1-2对应位置，只有液压挺柱2-1的升程曲线B，而气门升程为零；在主凸起1-1的对应位置上有气门升程曲线A1和挺柱升程曲线A。因此，气门在内燃机一个工作循环内只实现了在主凸起1-1位置的单次开启，气门升程曲线为A1。
将阀套3-2逆阀芯3-1转动方向转动设定的角度，使液压回转阀开通期由图6所示的位置移动到如图7所示的位置。在图7中，当副凸起1-2驱动液压挺柱2-1运动时，液压回转阀3中的阀芯径向油孔3-1-1和阀套径向油孔3-2-1错开，液压回转阀3处于关闭状态，副凸起1-2驱动液压挺柱2-1使得第一油道4-1内的油压升高，第一油道4-1的液压油流入气门驱动油腔5-3，推动气门驱动部件5中的液压活塞5-1克服气门弹簧力将气门打开。在图7所示的副凸起1-2对应位置，有气门升程曲线B1和挺柱升程曲线B；主凸起1-1对应的位置上有气门升程曲线A1和挺柱升程曲线A。因此气门在内燃机一个工作循环内实现了在主凸起1-1和副凸起1-2的对应位置的两次开启。
液压回转阀开通期是指从阀芯径向油孔3-1-1与阀套径向油孔3-2-1刚刚连通开始到阀芯径向油孔3-1-1与阀套径向油孔3-2-1刚刚错开结束所经历的凸轮转角。因此，阀套径向油孔3-2-1的内圆弧中心角与阀芯径向油孔3-1-1的外圆弧中心角之和乘以转速比N的积即为液压回转阀开通期，该液压回转阀开通期应该大于等于与之相匹配的副凸起上升段所占配气凸轮转角，以保证在副凸起上升段气门无法开启。
当配气凸轮1的主凸起1-1或副凸起1-2处于下降段时，随着液压挺柱2-1的下降，液压驱动油腔2-4的体积增大，第一油道4-1内的液压油压力逐渐降低。当第一油道4-1内液压油的压力降至低于第二油道4-2内液压油的压力时，液压单向阀7的单向阀芯7-2在压差的作用下向上移动，压缩单向阀弹簧7-1从而使液压单向阀7开启，第二油道4-2通过液压单向阀7向第一油道4-1内补充液压油，保证液压油始终充满液压驱动油腔2-4、气门驱动油腔5-3和液压回转阀油腔3-3。
由于液压回转阀3是间歇开通和关闭，导致第二油道4-2内的油压不稳定， 利用液压蓄能器8储存和释放液压压力能。当蓄能油腔8-5的瞬时压力增大时，蓄能活塞8-1压缩蓄能弹簧8-2，蓄能油腔8-3的体积增大、压力降低；当蓄能油腔8-5的瞬时压力减小时，蓄能弹簧8-2伸长，蓄能油腔8-3的体积减小、压力增大。从而使蓄能油腔8-3和第二油道4-2内的油压保持稳定，同时，能够使第二油道4-2通过液压单向阀7向第一油道4-1内补充稳定的液压油。
为了减小配气凸轮与液压挺柱之间的摩擦，可在液压挺柱和配气凸轮之间增加滚轮摆臂。如图5所示，液压驱动部件2的液压挺柱2-1通过滚轮摆臂9与配气凸轮1配合，滚轮摆臂9的固定端通过球头10支撑，球头10设置于壳体4上，滚轮摆臂9与液压驱动部件2的液压挺柱2-1相接触，滚轮摆臂9与挺柱弹簧2-3共同作用使液压挺柱2-1作往复直线运动。
在液压气门机构中，由于液压挺柱2-1与液压活塞5-1的横截面积不同，使得同一时刻液压挺柱2-1与液压活塞5-1的行程不同，从而使气门升程与挺柱升程存在设定的比例关系，即实现了升程比，如图6与图7所示。升程比等于液压挺柱2-1与液压活塞5-1的横截面积之比。
将排气凸轮的副凸起对应位置设置在压缩冲程后期和进气冲程初期，当内燃机处于气门两次或多次开启工作模式时，使排气门在压缩冲程后期和进气冲程初期再次开启，可实现缸内排气制动工作模式，如图7所示。
将进气凸轮的副凸起对应位置设置在排气冲程，当内燃机处于气门两次或多次开启工作模式时，进气门在排气冲程内实现二次开启，可使部分废气倒流回进气管，并参与下一循环的燃烧过程，可提高排气温度，改善排气热管理性能。
将进气凸轮的副凸起对应位置设置在做功冲程，同时将排气凸轮的副凸起对应位置设置在压缩冲程后期和进气冲程初期。在排气制动工作模式下，使进气门在膨胀(做功)冲程再次开启，可实现第二次进气(第一次进气为进气过程)，降低排气制动工作模式下的热负荷，改善制动效率。
将排气凸轮的副凸起和进气凸轮的副凸起设置在多种不同的位置，还可以使内燃机实现多种不同的功能。
根据具体情况通过液压回转阀调节机构来改变液压回转阀3的开通时刻，实现气门两次(或多次)开启模式与单次开启模式的切换。通过转动液压回转阀3的阀套3-2设定的角度，即可实现两次(或多次)开启模式与单次开启模式的切 换，因而切换过程平稳、迅速、无冲击。
实施例2
本实施例公开了一种内燃机，包括实施例1所述的一种气门开启次数可变的液压气门机构，该液压气门机构中壳体4安装于内燃机缸盖顶部，且与内燃机的气门组件进行配合。
如图4所示，液压气门机构中配气凸轮1为设于内燃机配气凸轮轴的配气凸轮，液压回转阀3中的阀芯3-1中心线与配气凸轮轴11平行设置，液压回转阀传动机构中齿轮通过中间传动齿轮3-6与设于配气凸轮轴11的凸轮轴齿轮11-1相互啮合。在最优方案中，壳体4内设置4套液压驱动部件2、8套气门驱动部件5(单缸4气门结构)和4套液压回转阀3，中间传动齿轮3-6设于壳体4的中部，且通过一套中间传动齿轮3-6带动多个阀芯3-1进行转动，液压回转阀3中的阀套3-2由步进电机12通过齿扇轴3-5和齿扇3-4带动实现转动。
在其他实施例中，液压回转阀3中的阀芯3-1中心线与配气凸轮轴11交错设置。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (10)

  1. 一种气门开启次数可变的液压气门机构，其特征在于，包括：
    壳体，设有第一油道和第二油道；
    配气凸轮，配气凸轮带有一个主凸起和至少一个副凸起，配气凸轮能够实现转动，配气凸轮设于壳体的外部；
    液压回转阀，设于壳体内并与壳体形成液压回转阀油腔，液压回转阀包括阀套和设有轴向孔的阀芯，阀芯安装于阀套内孔，阀芯和阀套绕同一轴线转动并在相对应的轴向位置上分别设有径向油孔，当阀芯和阀套的径向油孔相连通时液压回转阀处于开通状态，当阀芯和阀套的径向油孔相互错开时液压回转阀则处于关闭状态；液压回转阀油腔与第一油道连通，阀芯的轴向孔与第二油道连通；
    液压驱动部件，通过壳体支撑并与壳体形成液压驱动油腔，液压驱动部件由配气凸轮驱动，液压驱动油腔与第一油道连通；
    气门驱动部件，通过壳体支撑并与壳体形成气门驱动油腔，气门驱动油腔与与第一油道相通，当阀芯和阀套的径向油孔相互错开时液压回转阀处于关闭状态，液压驱动部件驱动气门驱动部件使相应气门打开。
  2. 根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述配气凸轮中副凸起设于所述配气凸轮中非主凸起设置的位置。
  3. 根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述配气凸轮轴通过液压回转阀传动机构带动所述阀芯实现转动，配气凸轮轴与阀芯的转速比为N,N为正整数；
    或者，所述配气凸轮轴通过液压回转阀传动机构带动所述阀套实现转动，配气凸轮轴与阀套的转速比为N,N为正整数。
  4. 根据权利要求3所述的一种气门开启次数可变的液压气门机构，其特征在于，所述阀芯在其同一轴向位置均匀分布有与转速比N相同数量的径向油孔，所述阀芯径向油孔为通孔且与阀芯轴向孔相通；所述阀套在其同一轴向位置设有与配气凸轮的副凸起相匹配的径向油孔，阀套径向油孔为通孔，阀套径向油孔所在轴向位置与阀芯径向油孔所在轴向位置相对应；
    或者，所述阀套在其同一轴向位置均匀分布有与转速比N相同数量的径向油孔，所述阀套径向油孔为通孔；所述阀芯在其同一轴向位置设有与配气凸轮的副凸起相匹配的径向油孔，阀芯径向油孔为通孔且与阀芯轴向孔相通，阀芯径向 油孔所在轴向位置与阀套径向油孔所在轴向位置相对应。
  5. 根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述阀套径向油孔的内圆弧中心角、所述阀芯径向油孔的外圆弧中心角，两中心角之和乘以转速比N之积大于等于与之相匹配的副凸起上升段所占配气凸轮转角。
  6. 根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述阀套端部设有轮齿，轮齿与液压回转阀调节机构连接，由液压回转阀调节机构带动轮齿转动进而带动阀套实现转动；
    或者，所述阀芯端部设有轮齿，轮齿与液压回转阀调节机构连接，由液压回转阀调节机构带动轮齿转动进而带动阀芯实现转动。
  7. 根据权利要求6所述的一种气门开启次数可变的液压气门机构，其特征在于，所述液压回转阀调节机构包括电机或比例电磁铁、齿轮或齿条或齿扇，齿轮或齿条或齿扇与所述的轮齿啮合。
  8. 根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述壳体内设置液压单向阀，单向阀入口与第二油道连通，单向阀出口与第一油道连通；
    进一步的，根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述壳体设置液压蓄能器，蓄能器与壳体形成蓄能油腔，蓄能油腔与第二油道连通。
  9. 根据权利要求1所述的一种气门开启次数可变的液压气门机构，其特征在于，所述液压驱动部件通过滚轮摆臂与所述配气凸轮配合，滚轮摆臂的固定端通过球头支撑，球头设置于壳体上，滚轮摆臂与液压驱动部件接触。
  10. 一种内燃机，包括权利要求1-9中任一项所述的一种气门开启次数可变的液压气门机构。
PCT/CN2020/080041 2019-07-12 2020-03-18 一种实现气门开启次数可变的液压气门机构及内燃机 WO2021008155A1 (zh)

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