WO2014110969A1 - 可变气门升程驱动装置 - Google Patents

可变气门升程驱动装置 Download PDF

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Publication number
WO2014110969A1
WO2014110969A1 PCT/CN2013/090810 CN2013090810W WO2014110969A1 WO 2014110969 A1 WO2014110969 A1 WO 2014110969A1 CN 2013090810 W CN2013090810 W CN 2013090810W WO 2014110969 A1 WO2014110969 A1 WO 2014110969A1
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WO
WIPO (PCT)
Prior art keywords
valve
gear
swing arm
shaft
rotation center
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2013/090810
Other languages
English (en)
French (fr)
Inventor
尹吉
刘胜强
林文
刘涛
王宁
张帅
陈涛
孙建军
侯振鹏
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Great Wall Motor Co Ltd
Original Assignee
Great Wall Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201310016079.2A external-priority patent/CN103925036B/zh
Priority claimed from CN201310014309.1A external-priority patent/CN103925029B/zh
Application filed by Great Wall Motor Co Ltd filed Critical Great Wall Motor Co Ltd
Publication of WO2014110969A1 publication Critical patent/WO2014110969A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • Variable valve lift drive device The present application is filed on January 15, 201, the Chinese Patent Office, Application No. 201 31 0014309. K The invention is entitled “Variable Valve Lift Drive” and January 15, 2013 Japanese Patent Application No. 201 310016079. The priority of the Chinese patent application entitled “Variable Valve Lifting Device” is incorporated herein by reference.
  • the present invention relates to engine components, and more particularly to a variable valve lift drive.
  • valve lift refers to the height at which the valve moves from just opening to fully opening, that is, the opening height of the valve.
  • the cam profile of the camshaft used in the engine is different, and the valve lift obtained is also different.
  • the valve lift of a conventional engine is fixed, that is, there is only one cam profile of the camshaft, and the lift design is a balance selection of the engine under full working conditions, so the lift is impossible to make the engine Both the high-speed zone and the low-speed zone are well-received. As a result, the engine does not get the best high-speed efficiency, and the optimal low-speed torque is not obtained, but the performance is balanced under all working conditions.
  • variable valve lift technology (VVL, va ri ab le va l ve lift ) can change the valve lift according to different operating conditions of the engine, so that the engine can get good response in both the high speed zone and the low speed zone, thereby improving the engine.
  • High speed power and low speed torque The specific performance is as follows: Matching the appropriate valve lift at different engine speeds, the system uses a smaller valve lift at low speed, which is beneficial to increase the intensity of the airflow in the cylinder, increase the combustion speed, reduce the inflation time, and thus improve the low speed of the engine. Torque, reducing fuel consumption, and using a larger valve lift at high speeds can significantly increase the charge factor, which in turn increases the power output at high speeds.
  • the existing variable valve lift technology can be divided into a segmented variable valve lift and a continuously variable valve lift according to its control effect. Compared with the segmented variable valve lift, the continuously variable valve lift can better match the combustion system of the engine and has certain advantages.
  • different valve lifts are obtained by changing the cam profile of the camshaft.
  • the specific method is to use a combined camshaft, wherein the combined camshaft is provided with a plurality of cams having different profiles, and the different cam profiles on the combined camshaft drive the valve links to reciprocate, thereby The valve lift is variable.
  • the camshaft, the valve connecting rod and the like are subjected to different degrees of impact loads, thereby reducing the service life of the components.
  • the combined camshaft is more complex and of higher quality than the conventional camshaft, which increases the machining cost and fuel consumption of the engine.
  • Embodiments of the present invention provide a variable valve lift driving device to improve the service life of components and reduce the processing cost and fuel consumption of the engine.
  • the variable valve lift driving device provided by the present invention includes a valve, a valve connecting valve connected to the valve, a valve rocker arm connected to the valve connecting rod, and a driving device.
  • a cam shaft that opens or closes a valve, a swing arm and an adjustment gear are disposed between the valve rocker arm and the cam shaft;
  • the swing arm is provided with a first rotation center and a second rotation center, and the adjustment gear is provided with a drive
  • the camshaft rotates
  • the swing arm is swung around the first rotation center to drive the valve link to linearly reciprocate to realize the opening or closing of the valve.
  • the adjustment gear rotates around its gear shaft
  • the driving portion is rotated around the gear shaft to make the first The center of rotation rotates about the second center of rotation.
  • the driving portion is a through hole provided on the adjusting gear and a rotating shaft disposed in the through hole, the first rotating center is a first through hole, and the rotating shaft is disposed at the first pass Inside the hole.
  • the second rotation center is a second through hole
  • the second through hole is provided with a pin shaft
  • the pin shaft is coaxially disposed with the gear shaft of the adjustment gear
  • the pin is mounted with the cam cooperative Swing arm roller.
  • the adjusting gear is a helical gear
  • the helical gear is meshed with a transmission gear
  • the transmission gear is connected with a driving source.
  • the camshaft is supported on the bearing housing, and the bearing seat is further provided with a mounting hole, and the gear shaft is disposed in the mounting hole.
  • a pin is arranged between the gear shaft and the mounting hole, and the pin is sealed by a screw plug, and the screw plug is provided with a drain hole.
  • the rotating shaft is provided with a return spring, one end of the return spring is connected with the adjusting gear, and the other end is connected with the swing arm.
  • the valve includes a first valve and a second valve
  • the valve link includes a first valve link connected to the first valve and a second valve link connected to the second valve
  • the valve rocker arm includes a first valve rocker arm coupled to the first valve link and a second valve rocker arm coupled to the second valve link, the camshaft driving the first valve and the first a two-valve opening or closing
  • the swing arm includes a first swing arm and a second swing arm
  • the adjustment gear includes a first adjustment gear and a second adjustment gear
  • the first swing arm and the first adjustment a gear is disposed between the first valve rocker arm and a camshaft
  • the second swing arm and a second adjustment gear are disposed between the second valve rocker arm and the camshaft
  • the second swing arm has the first rotation center and the second rotation center
  • the first adjustment gear is provided with a first driving portion
  • the second adjustment gear is provided with a second driving portion
  • the second rotation center on the first swing arm is coaxial with the first gear shaft
  • the second center of rotation on the second swing arm and the second gear shaft are coaxially disposed.
  • the first gear shaft and the second gear shaft are coaxially disposed.
  • the first adjustment gear is meshed with a first transmission gear
  • the second adjustment gear is meshed with a second transmission gear
  • the first transmission gear is rigidly coupled to the first transmission shaft
  • the second The transmission gear is rigidly coupled to the second transmission shaft
  • the second transmission shaft drives the first transmission shaft to rotate.
  • the first transmission shaft is sleeved on the second transmission shaft and connected by a radially extending positioning pin, and the first transmission shaft is provided with a sliding slot for sliding the positioning pin in the circumferential direction. Further, the second transmission gear and the second transmission shaft are connected by the positioning pin.
  • the first driving portion is a first rotating shaft rigidly connected to the first adjusting gear
  • the first rotating center is a third through hole
  • the first rotating shaft is disposed in the third through hole
  • the second driving portion is a second rotating shaft rigidly connected to the second adjusting gear
  • the third rotating center is a fourth through hole
  • the second rotating shaft is disposed in the fourth through hole.
  • the second center of rotation is a fifth through hole, and the first through hole is disposed in the fifth through hole, and the first pin shaft is mounted with a first swing arm roller that cooperates with a cam of the cam shaft;
  • the fourth rotating center is a sixth through hole, the sixth through hole is provided with a second pin, and the second pin is mounted with a second swing arm roller that cooperates with the cam of the cam shaft.
  • the circumferential position of the first center of rotation relative to the second center of rotation changes, thereby achieving a varying valve lift, achieving a different valve lift drive depending on the engine Use the operating conditions to change the valve lift.
  • the method of realizing the variable valve lift is different, and the camshaft, the valve connecting rod and the like are not impacted by changing the cam with different profiles to drive the valve linkage, and the cam is extended.
  • the service life of the shaft, the valve linkage and the like are related; and since a plurality of cams having different profiles are not disposed on the camshaft, the camshaft used in conjunction with the swing arm in the embodiment of the present invention has a simple structure and quality. Small, reducing engine processing costs and fuel consumption.
  • FIG. 1 is a schematic structural view of a variable valve lift driving device according to Embodiment 1 of the variable valve lift driving device of the present invention
  • FIG. 2 is a schematic exploded view of FIG. 1
  • FIG. 3 is a structural structure of the adjusting gear shown in FIG.
  • Figure 4 is a schematic view of the structure of the swing arm shown in Figure 2
  • Figure 5 is a front view of the adjustment gear shown in Figure 2
  • Figure 6 is a schematic view of the structure of the bearing block shown in Figure 2
  • FIG. 8 is a graph showing the relationship between different valve lifts and crank angles
  • FIG. 9 is a variable valve lift provided by Embodiment 2 of the variable valve lift driving device of the present invention.
  • FIG. 10 is a schematic structural view of the driving device;
  • FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The technical solutions in the embodiments of the present invention will be clearly described below in conjunction with the drawings in the embodiments of the present invention.
  • the variable valve lift driving device comprises a valve, a valve connecting rod connected to the valve, a valve rocker arm connected to the valve connecting rod, and a cam shaft driving the valve to open or close, in the valve rocker arm and a swing arm and an adjustment gear are arranged between the camshafts; a rotating center and a second rotating center, wherein the adjusting gear is provided with a driving portion, and when the cam shaft rotates, the swing arm is swung around the first rotating center to drive the valve link to linearly reciprocate to realize opening or closing of the valve, and adjusting the gear winding When the gear shaft of the own shaft rotates, the driving portion is rotated around the gear shaft to rotate the first center of rotation about the second center of rotation.
  • the adjustment gear rotates about its own gear shaft
  • the drive portion is rotated about the gear shaft to rotate the first center of rotation about the second center of rotation.
  • the circumferential position of the first center of rotation relative to the second center of rotation changes, thereby achieving a varying valve lift, achieving a different valve lift drive depending on the engine Use the operating conditions to change the valve lift.
  • the manner of the door lift is different, and the camshaft, the valve connecting rod and the like are not impacted by changing the cam with different profiles to drive the valve linkage, and the camshaft and the valve linkage are extended.
  • the camshaft used in conjunction with the swing arm in the embodiment of the present invention has a simple structure and a small mass, and reduces the engine. Processing costs and fuel consumption.
  • variable valve lift driving device 1 Embodiment of variable valve lift driving device 1
  • variable valve lift driving device includes a valve 1, a valve link 2 connected to the valve 1, a valve rocker arm 3 connected to the valve link 2, and a driving valve 1 opened or closed.
  • a camshaft ⁇ between the valve rocker arm 3 and the camshaft 7 is provided with a swing arm 4 and an adjustment gear 5;
  • the swing arm 4 is provided with a first rotation center 42 and a second rotation center 41, and the adjustment gear 5 is provided
  • the driving portion 52 when the cam shaft 7 rotates, drives the swing arm 4 to swing around the first rotation center 42 to drive the valve rod 2 to linearly reciprocate to realize opening or closing of the valve 1, and the adjusting gear 5 is driven around the gear shaft 5 1 of the gear shaft 5
  • the driving portion 52 is rotated about the gear shaft 51 to rotate the first rotation center 42 around the second rotation center 41.
  • variable valve lift driving device when the first rotating center is located at one position, a valve lift can be realized, and when the adjusting gear rotates around its own gear shaft, the driving portion is driven around the gear shaft.
  • Rotating to rotate the first center of rotation about the second center of rotation As the first center of rotation rotates about the second center of rotation, the circumferential position of the first center of rotation relative to the second center of rotation changes, thereby achieving a varying valve lift, achieving a different valve lift drive depending on the engine Use the operating conditions to change the valve lift.
  • variable valve lift is implemented in the embodiment of the present invention
  • the combined camshaft is used to realize the variable valve lift, and the valve link motion is not driven by changing the cams having different profiles. Impact on camshafts, valve linkages, etc., prolonging the service life of camshafts, valve linkages, etc.; and because there are no cams with different profiles on the camshaft,
  • the camshaft used in the swing arm of the embodiment of the invention has a simple structure and small mass, and reduces the processing cost and fuel consumption of the engine.
  • variable valve lift drive integrates both the drive center and the adjustment center on the swing arm, simplifying the structure and reducing the number of components compared to the structure in which the drive center and adjustment center are placed on two components. The number of uses.
  • the adjustment of the position of the first rotation center is achieved by the rotation of the first rotation center around the second rotation center, we can keep the position of the second rotation center unchanged during the adjustment process only to make the first rotation center plane.
  • the movement of the swing arm is simple, and the assembly relationship between the swing arm and other related components is relatively simple, thereby reducing the requirements for machining accuracy and assembly precision.
  • the gear shaft can be referred to as the rotating portion of the adjusting gear, and the adjusting gear of the present invention adjusts the position of the first rotating center, so that the rotating portion and the driving portion can be integrated on the adjusting gear.
  • the rotating portion and the driving portion are disposed on the two components, the structure is simplified, and the number of components used is reduced.
  • FIG. 3 is a schematic structural view of an adjustment gear according to an embodiment of the present invention
  • FIG. 4 is a schematic structural view of a swing arm according to an embodiment of the present invention. As shown in FIG. 3 and FIG.
  • the driving portion on the adjusting gear 5 in this embodiment is a through hole provided on the adjusting gear 5 and a rotating shaft 521 provided in the through hole
  • the swing arm 4 is A center of rotation 42 is a first through hole
  • a rotating shaft 521 is disposed in the first through hole. That is, the rotating shaft simultaneously passes through the through hole on the adjusting gear and the first through hole on the swing arm to realize the connection of the adjusting gear and the swing arm, that is, the first rotating center 42 and the rotating shaft 521 are coaxially disposed.
  • the rotation shaft 522 directly drives the drive center 42 of the swing arm 4 to rotate by a certain angle with respect to the adjustment center 41 of the swing arm 4, so that the angular displacement of the connection between the drive center 42 and the adjustment center 41 can be easily controlled, simplifying The structure and control process.
  • the rotating shaft 521 is preferably formed integrally with the adjusting gear 5, on the one hand simplifying the machining and assembly process and on the other hand avoiding the rotation of the rotating shaft itself.
  • a bearing 21 is disposed between the rotating shaft and the first through hole.
  • the swing arm 4 is rotated about the rotating shaft 122 to open and close the valve.
  • the present invention provides a return spring 522 on the rotating shaft 521, one end of the return spring 522 and the adjusting gear. 5 Connect and connect the other end to the swing arm 4.
  • the return spring 522 drives the swing arm 4 back.
  • the specific implementation of the return spring may be a torsion spring. One end of the torsion spring is inserted into the groove 45 of the swing arm as shown in Fig.
  • the large end of the cam on the camshaft drives the swing arm to rotate in one direction.
  • the small end of the cam contacts the swing arm, and the torsion spring drives the swing arm to rotate in the opposite direction around the drive center. , to achieve the return of the swing arm.
  • the groove 45 makes the return spring 522 easier to fix on the swing arm 4, which is convenient and quick to install, and improves the working stability of the swing arm.
  • the embodiment also provides an annular boss 523 on the rotating shaft 521 and at both ends of the return spring 522 to ensure the stability of the work.
  • the embodiment is provided with an arc deduplication structure 53 and a drain groove 54 on the adjustment gear 5.
  • the heavy structure can reduce the quality while ensuring the strength.
  • the oil drain groove can prevent oil from being stored during the work, increase the weight, and affect the stability of the system work.
  • the second rotation center 41 is a second through hole, and the second through hole is provided with a pin shaft, and the pin shaft is coaxially disposed with the gear shaft of the adjustment gear, and the pin shaft is mounted with Cam-fitted swing arm roller 43.
  • the cam shaft 7 drives the swing arm roller 43 to swing the swing arm 4 around the rotating shaft 521 to realize the opening or closing of the valve 1, and the adjustment gear rotates to rotate the swing arm about the gear shaft 51 to adjust the position of the first rotating center 42.
  • the adjustment gear 5 is a helical gear, the helical gear is meshed with a transmission gear 6, and the transmission gear 6 is connected to a drive source (not shown).
  • the drive source can be a motor or can be a motor and a shifting mechanism connected to the motor, such as a speed reducer.
  • the driving source drives the transmission gear to rotate, and the transmission gear drives the adjustment gear that meshes with the rotation to realize the adjustment of the first rotation center position of the swing arm.
  • the adjustment gear can also be a spur gear that is simpler and more convenient to machine.
  • the cam shaft 7 is supported on the bearing housing 8, and the bearing housing 8 is further provided with a mounting hole 82 through which the gear shaft 51 is bored. In this way, the bearing seat simultaneously functions as a fixed support camshaft and an adjustment gear, which simplifies the structure of the system.
  • an oil passage is arranged around the mounting hole on the bearing seat, and the oil passage is connected to the oil inlet 831 and the oil outlet 832, and an independent oil passage is arranged on the bearing seat to lubricate better result.
  • a pin 81 is provided between the gear shaft 51 and the mounting hole 82, and the pin 81 is sealed by the screw plug 84, and the screw plug 84 is provided with a drain hole.
  • the pin ⁇ can further fix the gear shaft, and the oil drain hole on the screw plug can drain the lubricating oil of the gear shaft.
  • variable valve lift driving device of the present invention includes a valve 1, a valve link 2 connected to the valve 1, a valve rocker arm 3 connected to the valve link 2, and a drive valve opened or closed.
  • Figure 7 shows a total of four rotation centers A, B, C, the contact point of the swing arm 4 with the valve rocker arm 3 is E, the connection line AB of the rotation center A, B and the connection line BC of the rotation center B, C The angle is ⁇ .
  • Case 1 Engine high speed full load operation
  • the ECU (electric control unit) electronic control unit determines the position where the rotation center C should be located, and then calculates the position at which the adjustment gear 5 should be located and infers the angle at which the stepping motor needs to be rotated, and then The signal of the angle is transmitted to the stepping motor. Finally, the stepping motor rotates according to the signal to drive the transmission gear 6.
  • the transmission gear 6 drives the adjustment gear 5 to rotate, so that the rotation center c rotates around the rotation center B until the rotation center reaches the predetermined position.
  • the angle ⁇ is a small angle, such as 125°.
  • the contact point of the swing arm 4 with the valve rocker arm 3 is at the left end position of the swing arm, so that the larger valve lift 1 shown in Fig. 8 can be obtained.
  • the engine can achieve high torque at high speeds.
  • Case 2 The engine is working at low speed and full load
  • the ECU controls the stepping motor in the same way to turn the adjustment gear 3 to another predetermined position.
  • the angle ⁇ between the line AB and the line BC increases, for example, ⁇ is 130°, and the contact point is ⁇ to the right. Therefore, the valve lift 2 obtained is lowered relative to the valve lift 1, but the valve opening and closing timings are constant, so that the engine can obtain a large torque at a low speed in cooperation with the variable valve timing system.
  • Case 3 Partial load operation of the engine
  • the ECU controls the stepping motor in the same way to turn the adjustment gear 3 to another predetermined position.
  • the angle ⁇ between the line AB and the line BC continues to increase, for example, ⁇ is 130° - 160°, and is continuously variable within the angle range.
  • Contact point ⁇ Continue to move to the right. Therefore, the valve lift 3 obtained continues to decrease relative to the valve lift 2, but the valve opening and closing timings are unchanged, so that in conjunction with the variable valve timing system, the pumping loss can be reduced and the engine fuel consumption can be reduced.
  • the ECU controls the stepping motor in the same way to turn the adjustment gear 3 to another predetermined position.
  • the angle ⁇ between the line AB and the line BC continues to increase, for example, ⁇ is 160°.
  • Contact point ⁇ Continue to move to the right.
  • the valve lift 4 thus obtained continues to decrease relative to the valve lift 3, but the valve opening and closing timings are constant, so that the engine idle speed stability is best achieved in conjunction with the variable valve timing system.
  • FIG. 9 is a schematic structural diagram of Embodiment 2 of a variable valve lift driving device according to an embodiment of the present invention
  • FIG. 10 is a schematic exploded view of FIG.
  • the variable valve lift driving device includes a first valve 1a and a second valve 1b, a first valve link 2a connected to the first valve 1a, and a second valve lb connected to the second valve lb.
  • a two-valve link 2b a first valve rocker arm 3a connected to the first valve link 2a, and a second valve rocker arm 3b connected to the second valve link 2b, and driving the first valve 1a and the second valve 1b to open Or a closed camshaft 7, wherein a first swing arm 4a and a first adjustment gear 5a are provided between the first valve rocker arm 3a and the camshaft 7, and between the second valve rocker arm 5b and the camshaft 7
  • the first swing arm 4a is provided with a first rotation center 41a and a second rotation center 42a
  • the second swing arm 4b is provided with a first rotation center 41b and a second The rotation center 42b
  • the first adjustment gear 5a is provided with a first driving portion 51a
  • the second adjustment gear 5b is provided with a second driving portion (blocked, not shown), and the first swing arm is driven when the cam shaft 7 rotates 4a swings around the first rotation
  • variable valve lift driving device when the first rotating center 41 a is located at one position, the first valve can realize a valve lift, when the first adjusting gear is wound around the first
  • the gear shaft rotates
  • the first driving portion is rotated about the first gear shaft to rotate the first rotation center 41 a around the second rotation center 42a.
  • the circumferential position of the first center of rotation 41a relative to the second center of rotation 42a changes, achieving a valve lift of the first valve change.
  • the second valve when the first rotating center 41b is at a position, the second valve can realize a valve lift, and when the second adjusting gear rotates around its second gear shaft, the second driving portion is rotated around the second gear shaft so that First A center of rotation 41b rotates about the second center of rotation 42b.
  • the valve lift driving device provided by the present invention can change the valve lift according to different operating conditions of the engine.
  • variable valve lift is implemented in the embodiment of the present invention
  • the combined camshaft is used to realize the variable valve lift, and the valve link motion is not driven by changing the cams having different profiles. Impact on camshafts, valve linkages, etc., prolonging the service life of camshafts, valve linkages, etc.; and because there are no cams with different profiles on the camshaft,
  • the camshaft used in the swing arm of the embodiment of the invention has a simple structure and small mass, and reduces the processing cost and fuel consumption of the engine.
  • the adjustment process of the valve lift is similar to the adjustment process of the valve lift of the first valve and the second valve described above, and the present invention will not be described herein.
  • the first rotation center 41a can be referred to as the drive center of the valve lift of the first valve
  • the second rotation center 42a can be called It is the adjustment center of the valve lift of the first valve
  • the first rotation center 41b can be referred to as the drive center of the valve lift of the second valve
  • the second rotation center 42b can be referred to as the adjustment center of the valve lift of the second valve.
  • variable valve lift driving device integrateds the driving center and the adjusting center on the swing arm, and is simplified compared to the structure in which the driving center and the adjusting center are disposed on the two components.
  • the structure reduces the number of parts used. Further, since the adjustment of the position of the first rotation center 41a is achieved by the rotation of the first rotation center 41a around the second rotation center 42a, the adjustment of the position of the first rotation center 41b is to surround the second rotation center 42b through the first rotation center 41b.
  • the rotation is realized, so that we can keep the positions of the second rotation center 42a and the second rotation center 42b unchanged during this adjustment process only to make the first rotation center 41a and the first rotation center 41b move in a plane, so that the swing arm
  • the movement form is simple, and the assembly relationship between the swing arm and other related components is relatively simple, thereby reducing the requirements for machining accuracy and assembly precision.
  • the first gear shaft can be referred to as the rotating portion of the first adjustment gear
  • the second gear can be
  • the gear shaft is referred to as a rotating portion of the second adjusting gear
  • the first adjusting gear is used to adjust the position of the first rotating center 41 a
  • the second adjusting gear is used to adjust the position of the first rotating center 41 b.
  • first valve is driven by the first swing arm
  • second valve is driven by the second swing arm
  • first rotation center 41 a of the first swing arm is adjusted by the first adjustment gear
  • first rotation center 41b is adjusted by the second adjustment gear, so that when the working faces of the first swing arm and the second swing arm are the same, we can realize the first change by driving the first adjustment gear and the second adjustment gear.
  • the valve lift of the same or different valve and the second valve will now be described by taking different valve lifts as an example. Only the differences are described in the preferred embodiment, and the commonalities with the above-described embodiment 2 are not repeated.
  • the second rotation center 42a is coaxially disposed with the first gear shaft, and the second rotation center 42b and the second gear shaft are coaxially disposed.
  • the driving force causes the first swing arm to also rotate around the first gear shaft, thereby realizing the first swing arm.
  • the beneficial effect achieved by the coaxial arrangement of the second center of rotation 42b and the second gear shaft is based on the beneficial effect of the coaxial arrangement of the second center of rotation 42a and the first gear shaft.
  • the first gear shaft and the second gear shaft are coaxially disposed. That is, the first gear shaft and the second gear shaft shown in FIG. 10 are both shafts 52a.
  • the shaft 52a is fixed in various manners. For example, a mounting hole 82 is provided in the bearing housing 8 for supporting the cam shaft 7, and the shaft 52a is bored in the mounting hole 82. In this way, the bearing seat simultaneously functions as a fixed support camshaft and an adjustment gear, which simplifies the structure of the system.
  • the first adjustment gear 5a is meshed with the first transmission gear 6a, and the second adjustment gear 5b Engaged with a second transmission gear 6b, the first transmission gear 6a is rigidly connected (for example, an interference press) on the first transmission shaft 7a, and the second transmission gear 6b is rigidly coupled to the second transmission shaft 7b, the second transmission shaft 7b
  • the first transmission shaft 7a is driven to rotate. This has the beneficial effect that only the second drive shaft 7b is connected to the drive source, such as a motor, to reduce the number of components.
  • first transmission shaft and the second transmission shaft may also be respectively connected to the driving source, so that it is easier to realize a different valve lift of the first valve and the second valve, so that eddy current is generated during the intake. Improve engine performance.
  • the first transmission shaft 7a is a hollow shaft and is sleeved on the second transmission shaft 7b, and is connected by a radially extending positioning pin 9. Further, a chute 71a for sliding the positioning pin 9 in the circumferential direction is provided on the first transmission shaft 7a.
  • the relative rotation of the first transmission shaft and the second transmission shaft is realized by the sliding of the positioning pin in the sliding groove, so that the first transmission gear and the second transmission gear generate a certain phase difference
  • the angle at which the first rotation center 41a on the first swing arm and the first rotation center 41b on the second swing arm rotate is inconsistent, and the valve lifts of the first valve and the second valve are also inconsistent.
  • the phase difference between the first transmission gear and the second transmission gear can be achieved by setting different lengths of the chute.
  • the invention is not limited thereto, and the first valve can also be realized by changing the shape and size of the working faces of the first swing arm and the second swing arm or the initial positions of the first rotation center 41 a and the first rotation center 41 b. A valve lift different from the second valve.
  • the second transmission gear 6b and the second transmission shaft 7b of the embodiment of the present invention are connected by a positioning pin 9.
  • the axial dimension of the second transmission gear is lengthened, and a section without teeth is designed, and a through hole 61b is opened in the radial direction in the area, and the positioning pin is inserted into the through hole 61b to realize the second transmission gear 6b. It is rigidly connected to the second transmission shaft 7b.
  • the first driving portion 51 a is a first rotating shaft rigidly connected to the first adjusting gear 5 a
  • the first rotating center 41 a is a third through hole
  • the first rotating shaft is disposed in the third through hole
  • the second driving portion is a second rotating shaft rigidly connected to the second adjusting gear 5b.
  • the first rotating center 41b is a fourth through hole
  • the second rotating shaft is disposed in the fourth through hole. That is, the first rotation center 41a is coaxially disposed with the first rotation axis, and the second rotation center 42a and the second rotation axis are coaxially disposed.
  • the first rotating shaft directly drives the first rotating center 41a of the first swing arm 4a with respect to the first swing arm 4a.
  • the second rotation center 42a rotates through a certain angle
  • the second rotation shaft directly drives the first rotation center 41b of the second swing arm 4b to rotate through a certain angle with respect to the second rotation center 42b of the second swing arm 4b, thereby being able to easily Controlling the angular displacement of the line between the drive center and the adjustment center on the swing arm simplifies the structure and control process.
  • the first rotating shaft is preferably integrally formed with the first adjusting gear, and the second rotating shaft and the second adjusting gear are preferably integrally formed to simplify the processing and assembly process. Due to the first
  • the rotating shaft and the driving center of the first swing arm are coaxially disposed, and the driving centers of the second rotating shaft and the second swing arm are coaxially disposed, so that the first swing arm rotates around the first rotating shaft to realize opening of the first valve and When closed, the second swing arm rotates around the second rotating shaft to open and close the second valve.
  • the second rotation center 42a is a fifth through hole, and the first through hole is disposed in the fifth through hole, and the first pin shaft is mounted with a first swing arm roller 43a that cooperates with the cam of the cam shaft;
  • the second rotation center 42b is a sixth through hole, the second through hole is provided with a second pin shaft, and the second pin shaft is mounted with a second swing arm roller 43b that cooperates with the cam of the cam shaft.
  • the cam of the cam shaft 7 drives the first swing arm roller 43a and the second swing arm roller 43b to swing the first swing arm 4a around the first rotating shaft to open or close the first valve, and the second swing arm 4b surrounds.
  • the second rotation axis swings to open or close the second valve. As shown in FIG. 9 and FIG.
  • the first valve rocker arm 3a is further connected with a hydraulic tappet 10a
  • the second valve rocker arm 3b is also connected with a hydraulic tappet 10b
  • the hydraulic tappets 10a, 10b can make the camshaft 7
  • the contact between the upper cam and the swing arm rollers 43a, 43b, and the contact between the valve rocker arms 3a, 3b and the working portions of the swing arms 4a, 4b maintain a zero clearance.

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

Abstract

本发明公开了一种可变气门升程驱动装置，涉及发动机部件，用来提高零部件的使用寿命，降低发动机的加工成本和燃油消耗量。所述可变气门升程驱动装置包括气门、与气门连接的气门连杆、与气门连杆连接的气门摇臂、以及驱动气门打开或闭合的凸轮轴，在气门摇臂和凸轮轴之间设有摆臂和调整齿轮；所述摆臂上设有第一旋转中心和第二旋转中心，所述调整齿轮上设有驱动部，凸轮轴转动时带动摆臂围绕第一旋转中心摆动以驱动气门连杆直线往复运动实现气门的打开或闭合，调整齿轮绕自身的齿轮轴转动时带动驱动部围绕齿轮轴转动以使第一旋转中心围绕第二旋转中心转动。本发明用于实现气门升程的连续可变。

Description

可变气门升程驱动装置 本申请要求于 201 3 年 1 月 15 日提交中国专利局、 申请号为 201 31 0014309. K 发明名称为 "可变气门升程驱动装置" 和 201 3年 1月 15 日提交中国专利局、 申请号为 201 310016079. 2、 发明名称为 "可变气 门升程驱动装置"的中国专利申请的优先权， 其全部内容通过引用结合在 本申请中。
技术领域 本发明涉及发动机部件， 尤其涉及一种可变气门升程驱动装置。
背景技术 气门是发动机中的一个重要部件， 用于向发动机内输入燃料并排出燃 烧后的废气。 在发动机领域中， 气门升程指的是气门从刚刚打开到完全打 开所运动的高度， 也就是气门的开启高度。 发动机中使用的凸轮轴的凸轮 型线不同， 所获得的气门升程也不同。 传统发动机的气门升程是固定不变 的， 即其凸轮轴的凸轮型线只有一种， 其升程设计是对发动机在全工况下 的平衡性选择，因此该升程不可能使发动机在高速区和低速区都得到良好 响应，结果是发动机既得不到最佳的高速效率，也得不到最佳的低速扭矩， 只是得到了在全工况下较为平衡的性能。
可变气门升程技术 （VVL , va r i ab l e va l ve l i f t ) 能够根据发动机的 不同工况改变其气门升程，使发动机在高速区和低速区都能得到良好的响 应， 从而改善发动机的高速功率和低速扭矩。 具体表现为： 在发动机不同 转速下匹配合适的气门升程， 低转速时系统使用较小的气门升程， 这样有 利于增加缸内气流的强度提高燃烧速度， 减少充气时间， 进而提高发动机 的低速扭矩， 降低燃油消耗， 而高转速时使用更大的气门升程则可以显著 提高充量系数， 进而提升高转速时的功率输出。 现有的可变气门升程技术按照其控制效果可分为分段可变气门升程 和连续可变气门升程。 与分段可变气门升程相比， 连续可变气门升程可以 更好地配合发动机的燃烧系统， 具有一定的优越性。 现有的可变气门升程 驱动装置中， 大多是通过改变凸轮轴的凸轮型线来获得不同的气门升程。 具体的做法是使用组合式的凸轮轴，该组合式凸轮轴上设有多个具有不同 型线的凸轮，通过该组合式凸轮轴上的不同凸轮型线来驱动气门连杆往复 运动， 从而使气门升程可变。 但是在使用该可变气门升程驱动装置变换气门升程的过程中， 凸轮 轴、 气门连杆等相关零部件均承受了不同程度的冲击载荷， 降低了零部件 的使用寿命。 而且组合式的凸轮轴比传统的凸轮轴结构复杂、 质量大， 增 加了发动机的加工成本和燃油消耗量。
发明内容
本发明实施例提供一种可变气门升程驱动装置，以提高零部件的使用 寿命， 降低发动机的加工成本和燃油消耗量。 为达到上述目的， 本发明的实施例釆用如下技术方案： 本发明提供的可变气门升程驱动装置包括气门、与气门连接的气门连 杆、 与气门连杆连接的气门摇臂、 以及驱动气门打开或闭合的凸轮轴， 在 气门摇臂和凸轮轴之间设有摆臂和调整齿轮；所述摆臂上设有第一旋转中 心和第二旋转中心， 所述调整齿轮上设有驱动部， 凸轮轴转动时带动摆臂 围绕第一旋转中心摆动以驱动气门连杆直线往复运动实现气门的打开或 闭合，调整齿轮绕自身的齿轮轴转动时带动驱动部围绕齿轮轴转动以使第 一旋转中心围绕第二旋转中心转动。 具体而言，所述驱动部为设在所述调整齿轮上的通孔和设在通孔内的 转动轴， 所述第一旋转中心为第一通孔， 所述转动轴设在第一通孔内。
具体而言， 第二旋转中心为第二通孔， 第二通孔内设有销轴， 销轴与 所述调整齿轮的齿轮轴同轴设置，且所述销轴上安装有与所述凸轮配合的 摆臂滚子。 优选地， 所述调整齿轮为斜齿轮， 斜齿轮啮合有传动齿轮， 传动齿轮 连接有驱动源。 进一步地， 所述凸轮轴支撑在轴承座上， 轴承座上还设有安装孔， 齿 轮轴穿设在安装孔内。 进一步地， 在齿轮轴与安装孔之间设有销钉， 且销钉通过螺塞密封， 螺塞上设有泄油孔。 为使摆臂顺利回位， 所述转动轴上设有回位弹簧， 回位弹簧的一端与 调整齿轮连接、 另一端与摆臂连接。
进一步地， 所述气门包括第一气门和第二气门， 所述气门连杆包括与 所述第一气门连接的第一气门连杆和与所述第二气门连接的第二气门连 杆，所述气门摇臂包括与所述第一气门连杆连接的第一气门摇臂和与所述 第二气门连杆连接的第二气门摇臂，所述凸轮轴可驱动所述第一气门和第 二气门打开或闭合， 其特征在于， 所述摆臂包括第一摆臂和第二摆臂， 所 述调整齿轮包括第一调整齿轮和第二调整齿轮，所述第一摆臂和第一调整 齿轮设置于所述第一气门摇臂和凸轮轴之间，所述第二摆臂和第二调整齿 轮设置于所述第二气门摇臂和凸轮轴之间；所述第一摆臂和第二摆臂上均 具有所述第一旋转中心和第二旋转中心，所述第一调整齿轮上设有第一驱 动部， 所述第二调整齿轮上设有第二驱动部， 凸轮轴转动时带动第一摆臂 围绕第一摆臂上的第一旋转中心摆动以驱动第一气门连杆直线往复运动 实现第一气门的打开或闭合，并且凸轮轴转动时带动第二摆臂围绕第二摆 臂上的第一旋转中心摆动以驱动第二气门连杆直线往复运动实现第二气 门的打开或闭合；第一调整齿轮绕自身的第一齿轮轴转动时带动第一驱动 部围绕第一齿轮轴转动以使第一摆臂上的第一旋转中心围绕第一摆臂上 的第二旋转中心转动，第二调整齿轮绕自身的第二齿轮轴转动时带动第二 驱动部围绕第二齿轮轴转动以使第二摆臂上的第一旋转中心围绕第二摆 臂上的第二旋转中心转动。 优选地， 所述第一摆臂上的第二旋转中心和所述第一齿轮轴同轴设 置， 所述第二摆臂上的第二旋转中心和所述第二齿轮轴同轴设置。 进一步地， 所述第一齿轮轴和所述第二齿轮轴同轴设置。 为简化系统结构， 所述第一调整齿轮啮合有第一传动齿轮， 所述第二 调整齿轮啮合有第二传动齿轮，所述第一传动齿轮刚性连接在第一传动轴 上， 所述第二传动齿轮刚性连接在第二传动轴上， 所述第二传动轴带动所 述第一传动轴转动。
具体而言， 所述第一传动轴套设在第二传动轴上， 并通过径向延伸的 定位销连接， 且在第一传动轴上设有使定位销沿周向滑动的滑槽。 进一步地， 所述第二传动齿轮和所述第二传动轴通过所述定位销连 接。
具体而言，所述第一驱动部为与所述第一调整齿轮刚性连接的第一转 动轴， 所述第一旋转中心为第三通孔， 所述第一转动轴设在第三通孔内； 所述第二驱动部为与所述第二调整齿轮刚性连接的第二转动轴，所述第三 旋转中心为第四通孔， 所述第二转动轴设在第四通孔内。 其次， 所述第二旋转中心为第五通孔， 第五通孔内设有第一销轴， 第 一销轴上安装有与所述凸轮轴的凸轮配合的第一摆臂滚子；所述第四旋转 中心为第六通孔， 第六通孔内设有第二销轴， 第二销轴上安装有与所述凸 轮轴的凸轮配合的第二摆臂滚子。 对于本发明实施例提供的可变气门升程驱动装置而言，当第一旋转中 心位于一个位置处时可以实现一种气门升程，当调整齿轮绕自身的齿轮轴 转动时带动驱动部围绕齿轮轴转动以使第一旋转中心围绕第二旋转中心 转动。 随着第一旋转中心围绕第二旋转中心转动， 第一旋转中心相对第二 旋转中心的周向位置随之改变， 因此实现了变化的气门升程， 达到了气门 升程驱动装置根据发动机的不同使用工况对气门升程进行改变的目的。本 实现可变气门升程的方式不同，不会由于变更具有不同型线的凸轮来驱动 气门连杆运动而对凸轮轴、 气门连杆等零部件产生冲击作用， 延长了凸轮 轴、 气门连杆等相关零部件的使用寿命； 而且由于不会在凸轮轴上设置多 个具有不同型线的凸轮，因此与本发明实施例中的摆臂配合使用的凸轮轴 结构简单、 质量小， 降低了发动机的加工成本和燃油消耗量。
附图说明
为了更清楚地说明本发明实施例或现有技术中的技术方案，下面将对 实施例所需要使用的附图作简单地介绍。 图 1为本发明可变气门升程驱动装置之实施例 1提供的可变气门升程 驱动装置的结构示意图； 图 2为图 1的分解结构示意图； 图 3为图 2所示调整齿轮的结构示意图； 图 4为图 2所示摆臂的结构示意图； 图 5为图 2所示调整齿轮的主视图； 图 6为图 2所示轴承座的结构示意图； 图 7为本发明实施例提供的可变气门升程驱动装置的主视图； 图 8为不同气门升程随曲轴转角的变化关系曲线图； 图 9为本发明可变气门升程驱动装置之实施例 2提供的可变气门升程 驱动装置的结构示意图； 图 10为图 9的分解结构示意图。 具体实施方式 下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进 行清楚地描述。 本发明实施例提供的可变气门升程驱动装置， 包括气门、 与气门连接 的气门连杆、 与气门连杆连接的气门摇臂、 以及驱动气门打开或闭合的凸 轮轴， 在气门摇臂和凸轮轴之间设有摆臂和调整齿轮； 所述摆臂上设有第 一旋转中心和第二旋转中心， 所述调整齿轮上设有驱动部， 凸轮轴转动时 带动摆臂围绕第一旋转中心摆动以驱动气门连杆直线往复运动实现气门 的打开或闭合，调整齿轮绕自身的齿轮轴转动时带动驱动部围绕齿轮轴转 动以使第一旋转中心围绕第二旋转中心转动。这样当第一旋转中心位于一 个位置处时可以实现一种气门升程，当调整齿轮绕自身的齿轮轴转动时带 动驱动部围绕齿轮轴转动以使第一旋转中心围绕第二旋转中心转动。随着 第一旋转中心围绕第二旋转中心转动，第一旋转中心相对第二旋转中心的 周向位置随之改变， 因此实现了变化的气门升程， 达到了气门升程驱动装 置根据发动机的不同使用工况对气门升程进行改变的目的。本发明实施例 门升程的方式不同，不会由于变更具有不同型线的凸轮来驱动气门连杆运 动而对凸轮轴、 气门连杆等零部件产生冲击作用， 延长了凸轮轴、 气门连 杆等相关零部件的使用寿命；而且由于不会在凸轮轴上设置多个具有不同 型线的凸轮， 因此与本发明实施例中的摆臂配合使用的凸轮轴结构简单、 质量小， 降低了发动机的加工成本和燃油消耗量。
下面结合附图来详细说明本发明提供的可变气门升程驱动装置的优 选实施例。 可变气门升程驱动装置之实施例 1
图 1为本发明可变气门升程驱动装置之实施例 1提供的可变气门升程 驱动装置的结构示意图， 图 2为图 1 的分解结构示意图。 如图 1 和图 2 所示， 该可变气门升程驱动装置包括气门 1、 与气门 1连接的气门连杆 2、 与气门连杆 2连接的气门摇臂 3、以及驱动气门 1打开或闭合的凸轮轴 Ί , 在气门摇臂 3和凸轮轴 7之间设有摆臂 4和调整齿轮 5 ; 摆臂 4上设有第 一旋转中心 42和第二旋转中心 41 , 调整齿轮 5上设有驱动部 52 , 凸轮轴 7转动时带动摆臂 4围绕第一旋转中心 42摆动以驱动气门连杆 2直线往 复运动实现气门 1的打开或闭合， 调整齿轮 5绕自身的齿轮轴 5 1转动时 带动驱动部 52围绕齿轮轴 5 1转动以使第一旋转中心 42围绕第二旋转中 心 41转动。 这样本发明实施例提供的可变气门升程驱动装置中，当第一旋转中心 位于一个位置处时可以实现一种气门升程，当调整齿轮绕自身的齿轮轴转 动时带动驱动部围绕齿轮轴转动以使第一旋转中心围绕第二旋转中心转 动。 随着第一旋转中心围绕第二旋转中心转动， 第一旋转中心相对第二旋 转中心的周向位置随之改变， 因此实现了变化的气门升程， 达到了气门升 程驱动装置根据发动机的不同使用工况对气门升程进行改变的目的。本发 明实施例中实现可变气门升程的方式与现有技术中使用组合式凸轮轴实 现可变气门升程的方式不同，不会由于变更具有不同型线的凸轮来驱动气 门连杆运动而对凸轮轴、气门连杆等零部件产生冲击作用，延长了凸轮轴、 气门连杆等相关零部件的使用寿命；而且由于不会在凸轮轴上设置多个具 有不同型线的凸轮，因此与本发明实施例中的摆臂配合使用的凸轮轴结构 简单、 质量小， 降低了发动机的加工成本和燃油消耗量。
从上面描述的第一旋转中心位置的调节过程可知，能够将第一旋转中 心称为气门升程的驱动中心， 将第二旋转中心称为气门升程的调整中心， 因此本发明实施例提供的可变气门升程驱动装置将驱动中心和调整中心 都集成在摆臂上，相比于将其驱动中心和调整中心设置于两个零部件上的 结构而言， 简化了结构， 减少了零部件的使用数量。 此外， 由于第一旋转 中心位置的调整是通过第一旋转中心围绕第二旋转中心转动实现的，因此 我们可以在此调整过程中保持第二旋转中心的位置不变只是使第一旋转 中心作平面运动， 这样摆臂的运动形式简单， 摆臂与其他相关零部件的装 配关系也比较简单， 从而降低了其对加工精度和装配精度的要求。 同理， 能够将齿轮轴称为调整齿轮的转动部， 本发明釆用调整齿轮来 调整第一旋转中心的位置，可以 4艮好地将转动部和驱动部均集成在调整齿 轮上， 相比于将转动部和驱动部设置于两个零部件上的结构而言， 简化了 结构， 减少了零部件的使用数量。 图 3为本发明实施例中调整齿轮的结构示意图，图 4为本发明实施例 中摆臂的结构示意图。 如图 3和图 4所示， 本实施例中调整齿轮 5上的驱 动部为设在调整齿轮 5上的通孔和设在通孔内的转动轴 521 , 摆臂 4的第 一旋转中心 42为第一通孔， 转动轴 521设在第一通孔内。 也就是转动轴 同时穿过调整齿轮上的通孔和摆臂上的第一通孔实现调整齿轮和摆臂的 连接， 即第一旋转中心 42和转动轴 521 同轴设置。 这样转动轴 522直接 驱动摆臂 4的驱动中心 42相对于摆臂 4的调整中心 41转过一定的角度， 因此能够简便地控制驱动中心 42和调整中心 41之间连线的角位移量，简 化了结构和控制过程。 其中转动轴 521优选与调整齿轮 5—体成型， 一方 面简化加工和装配工艺， 另一方面避免转动轴自身的转动。 同时为了使摆 臂的转动更平顺， 在所述转动轴和所述第一通孔之间设置了轴承 21。
另外在上述实施例中， 由于转动轴 122和摆臂 4的驱动中心 42同轴 设置， 摆臂 4便围绕转动轴 122转动实现气门的打开与关闭。 为了便于在 凸轮轴上的凸轮的最大端越过摆臂后使摆臂顺利回位， 如图 3所示， 本发 明在转动轴 521上设置回位弹簧 522 , 回位弹簧 522的一端与调整齿轮 5 连接、 另一端与摆臂 4连接。 这样回位弹簧 522带动摆臂 4回位。 回位弹 簧的具体实现形式可以为扭簧， 扭簧的一端插入如图 4 所示摆臂的凹槽 45中， 另一端插入图 5所示调整齿轮 5的安装孔 55中。 这样凸轮轴上凸 轮的大端驱动摆臂在一个方向上转动， 当凸轮的最大端转动越过摆臂之 后，凸轮的小端与摆臂接触，此时扭簧带动摆臂围绕驱动中心反方向转动， 实现摆臂的回位。 凹槽 45使回位弹簧 522更容易固定在摆臂 4上， 安装 方便快捷， 提高了摆臂的工作稳定性。 为了防止回位弹簧 522发生轴向传 动，本实施例还在转动轴 521上且在回位弹簧 522的两端设置了环形凸台 523 , 以保证工作的稳定性。 为了降低调整齿轮的重量， 如图 3和图 5所 示， 本实施例在调整齿轮 5上设置了弧形去重结构 53和泄油槽 54。 一方 面去重结构可以在保证强度的情况下减轻质量，另一方面泄油槽可以防止 其在工作过程中存油， 增加重量， 影响系统工作的稳定性。
此外， 如图 4所示， 第二旋转中心 41为第二通孔， 第二通孔内设有 销轴， 销轴与所述调整齿轮的齿轮轴同轴设置， 且销轴上安装有与凸轮配 合的摆臂滚子 43。 这样凸轮轴 7驱动摆臂滚子 43以使摆臂 4围绕转动轴 521摆动实现气门 1的打开或闭合，调整齿轮转动带动摆臂围绕齿轮轴 51 转动以调节第一旋转中心 42的位置。 其中， 调整齿轮 5为斜齿轮， 斜齿轮啮合有传动齿轮 6 , 传动齿轮 6 连接有未图示的驱动源。 驱动源可以为电机， 或者可以为电机以及与电机 连接的变速机构， 如减速器。 驱动源驱动传动齿轮旋转， 传动齿轮带动与 之啮合的调整齿轮转动以实现摆臂的第一旋转中心位置的调整。当然在本 发明的其它实施例中， 调整齿轮也可以为结构更简单、 更方便加工的直齿 轮。 此外， 凸轮轴 7支撑在轴承座 8上， 轴承座 8上还设有安装孔 82 , 齿轮轴 51穿设在安装孔 82内。这样轴承座同时起到固定支撑凸轮轴和调 整齿轮的作用， 简化了系统的结构。
为提高齿轮轴的润滑效果，本实施例在轴承座上位于所述安装孔的周 围设有油道， 油道连接进油口 831和出油口 832 , 轴承座上设置独立的油 道， 润滑效果更好。
作为上述实施例的进一步改进，在齿轮轴 51与安装孔 82之间设有销 81 , 且销 81通过螺塞 84密封， 螺塞 84上设有泄油孔。 销 τ可以更 进一步固定齿轮轴， 螺塞上的泄油孔可以泄掉齿轮轴的润滑油。 对于一个气缸有两个进气门， 同时一个摆臂对应一个进气门而言， 如 果改变其中一个摆臂的工作面 44的弧面的半径、 弧长， 以及平面的长度， 便可以通过一个可变气门升程驱动装置实现两个不同气门升程的目的。 下面结合图 7和图 8 ,以一个具体的实施例介绍发动机在不同工况下， 本发明的可变气门升程驱动装置的工作原理和工作过程。
图 7为本发明实施例提供的可变气门升程驱动装置的主 视图， 图 8 为不同气门升程随曲轴转角的变化关系曲线图。 从图 7可以看出， 本发明 的可变气门升程驱动装置包括气门 1、 与气门 1连接的气门连杆 2、 与气 门连杆 2连接的气门摇臂 3、 以及驱动气门打开或闭合的凸轮轴 7和设在 气门摇臂 3和凸轮轴 7之间的摆臂 4和调整齿轮 5 , 调整齿轮 5啮合有传 动齿轮 6 , 传动齿轮 6连接有未图示的驱动源， 如步进电机。 图 7所示共 有四个转动中心 A、 B、 C , 摆臂 4与气门摇臂 3 的接触点为 E , 转动中 心 A、 B的连线 AB与转动中心 B、 C的连线 BC间的夹角为 β 。 工况 1 : 发动机高速全负荷工作
首先， 在该工况下 ECU ( electric control unit ) 电子控制单元确定转 动中心 C应处的位置， 然后据此计算调整齿轮 5应所处的位置并推断出 步进电机需要转动的角度， 再将该角度的信号传给步进电机， 最后步进电 机根据此信号转动以带动传动齿轮 6, 传动齿轮 6带动调整齿轮 5转动使 转动中心 c 围绕转动中心 B转动直至转动中心到达预定位置， 此时角 β 为一较小角， 例如 125° 。 且此时摆臂 4与气门摇臂 3的接触点 Ε在摆臂 上靠左端的位置， 因此可以获得图 8所示的较大的气门升程 1。 在与可变 气门正时系统的配合下， 可使发动机在高速时达到较大扭矩。 工况 2: 发动机在低速全负荷工作
ECU用相同的方法控制步进电机将调整齿轮 3转到另一预定位置。 此时连线 AB与连线 BC的夹角 β增大， 例如 β为 130° , 接触点为 Ε向 右移动。 因此获得的气门升程 2相对于气门升程 1有所下降， 但气门开启 和关闭时刻不变， 所以在与可变气门正时系统的配合下， 可使发动机在低 速时得到较大扭矩。 工况 3 : 发动机部分负荷工作
ECU用相同的方法控制步进电机将调整齿轮 3转到另一预定位置。 此时连线 AB与连线 BC的夹角 β继续增大， 例如 β为 130° -160° , 且 在该角度范围内连续可变。 接触点 Ε 继续向右移动。 因此获得的气门升 程 3相对于气门升程 2继续下降， 但气门开启和关闭时刻不变， 所以在与 可变气门正时系统的配合下， 可降低泵气损失， 降低发动机油耗。
工况 4: 发动机怠速
ECU用相同的方法控制步进电机将调整齿轮 3转到另一预定位置。 此时连线 AB与连线 BC的夹角 β继续增大， 例如 β为 160° 。 接触点 Ε 继续向右移动。 因此获得的气门升程 4相对于气门升程 3继续下降， 但气 门开启和关闭时刻不变， 所以在与可变气门正时系统的配合下， 可使发动 机怠速稳定性最好。 可变气门升程驱动装置之实施例 2
图 9为本发明实施例提供的可变气门升程驱动装置之实施例 2的结构 示意图， 图 10为图 9的分解结构示意图。 如图 9和图 10所示， 该可变气 门升程驱动装置包括第一气门 l a和第二气门 lb、 与第一气门 l a连接的 第一气门连杆 2a和与第二气门 lb连接的第二气门连杆 2b、 与第一气门 连杆 2a连接的第一气门摇臂 3a和与第二气门连杆 2b连接的第二气门摇 臂 3b、以及驱动第一气门 la和第二气门 lb打开或闭合的凸轮轴 7 ,其中， 在第一气门摇臂 3a和凸轮轴 7之间设有第一摆臂 4a和第一调整齿轮 5a, 在第二气门摇臂 5b和凸轮轴 7之间设有第二摆臂 4b和第二调整齿轮 5b; 第一摆臂 4a上设有第一旋转中心 41 a和第二旋转中心 42a, 第二摆臂 4b 上设有第一旋转中心 41b和第二旋转中心 42b , 第一调整齿轮 5a上设有 第一驱动部 51 a,第二调整齿轮 5b上设有第二驱动部（被挡住，没有图示）， 凸轮轴 7转动时带动第一摆臂 4a围绕第一摆臂 4a上的第一旋转中心 41 a 摆动以驱动第一气门连杆 2a直线往复运动实现第一气门 l a 的打开或闭 合，并且凸轮轴 7转动时带动第二摆臂 4b围绕第二摆臂 4b上的第一旋转 中心 41 b摆动以驱动第二气门连杆 2 b直线往复运动实现第二气门 1 b的打 开或闭合； 第一调整齿轮 5a绕自身的第一齿轮轴 52a转动时带动第一驱 动部 51a围绕第一齿轮轴 52a转动以使第一旋转中心 41 a围绕第二旋转中 心 42a转动， 第二调整齿轮 5b绕自身的第二齿轮轴 52a转动时带动第二 驱动部围绕第二齿轮轴 52a转动以使第一旋转中心 41b围绕第二旋转中心 42b转动。 这样在本发明实施例提供的可变气门升程驱动装置中，当第一旋转中 心 41 a位于一个位置处时第一气门可以实现一种气门升程， 当第一调整齿 轮绕自身的第一齿轮轴转动时带动第一驱动部围绕第一齿轮轴转动以使 第一旋转中心 41 a围绕第二旋转中心 42a转动。 随着第一旋转中心 41 a围 绕第二旋转中心 42a转动， 第一旋转中心 41 a相对第二旋转中心 42a的周 向位置随之改变， 实现了第一气门变化的气门升程。 同理当第一旋转中心 41b位于一个位置处时第二气门可以实现一种气门升程， 当第二调整齿轮 绕自身的第二齿轮轴转动时带动第二驱动部围绕第二齿轮轴转动以使第 一旋转中心 41b围绕第二旋转中心 42b转动。随着第一旋转中心 41b围绕 第二旋转中心 42b转动，第一旋转中心 41b相对第二旋转中心 42b的周向 位置随之改变， 实现了第二气门变化的气门升程。 因此本发明提供的气门 升程驱动装置能够根据发动机的不同使用工况对气门升程进行改变。本发 明实施例中实现可变气门升程的方式与现有技术中使用组合式凸轮轴实 现可变气门升程的方式不同，不会由于变更具有不同型线的凸轮来驱动气 门连杆运动而对凸轮轴、气门连杆等零部件产生冲击作用，延长了凸轮轴、 气门连杆等相关零部件的使用寿命；而且由于不会在凸轮轴上设置多个具 有不同型线的凸轮，因此与本发明实施例中的摆臂配合使用的凸轮轴结构 简单、 质量小， 降低了发动机的加工成本和燃油消耗量。
甚至更多个气门，气门升程的调节过程和上述第一气门和第二气门的气门 升程的调节过程类似， 本发明在此不作赘述。 从上面描述的第一旋转中心 41 a和第二旋转中心 42a位置的调节过程 可知， 能够将第一旋转中心 41 a称为第一气门的气门升程的驱动中心， 将 第二旋转中心 42a称为第一气门的气门升程的调整中心。 同理， 能够将第 一旋转中心 41b 称为第二气门的气门升程的驱动中心， 将第二旋转中心 42b称为第二气门的气门升程的调整中心。 因此本发明实施例提供的可变 气门升程驱动装置将驱动中心和调整中心都集成在摆臂上，相比于将其驱 动中心和调整中心设置于两个零部件上的结构而言， 简化了结构， 减少了 零部件的使用数量。 此外， 由于第一旋转中心 41 a位置的调整是通过第一 旋转中心 41a围绕第二旋转中心 42a转动实现的，第一旋转中心 41b位置 的调整是通过第一旋转中心 41b围绕第二旋转中心 42b转动实现的，因此 我们可以在此调整过程中保持第二旋转中心 42a和第二旋转中心 42b的位 置不变只是使第一旋转中心 41 a和第一旋转中心 41b作平面运动，这样摆 臂的运动形式简单， 摆臂与其他相关零部件的装配关系也比较简单， 从而 降低了其对加工精度和装配精度的要求。 同理， 能够将第一齿轮轴称为第一调整齿轮的转动部， 并能够将第二 齿轮轴称为第二调整齿轮的转动部，本发明釆用第一调整齿轮来调整第一 旋转中心 41 a的位置， 第二调整齿轮来调整第一旋转中心 41b的位置， 可 以 4艮好地将转动部和驱动部均集成在调整齿轮上，相比于将转动部和驱动 部设置于两个零部件上的结构而言， 简化了结构， 减少了零部件的使用数 量。
需要进一步说明的是， 由于第一气门由第一摆臂驱动， 第二气门由第 二摆臂驱动， 而且第一摆臂的第一旋转中心 41 a通过第一调整齿轮调节， 第二摆臂的第一旋转中心 41b通过第二调整齿轮调节，这样在第一摆臂和 第二摆臂的工作面相同的情况下，我们可以通过改变第一调整齿轮和第二 调整齿轮的驱动方式实现第一气门和第二气门相同或不同的气门升程。下 面就以不同气门升程为例介绍本发明的优选实施例。在优选实施例中只介 绍不同之处， 与上述实施例 2的共同之处不再重复。 首先， 第二旋转中心 42a和第一齿轮轴同轴设置， 第二旋转中心 42b 和第二齿轮轴同轴设置。 这样当第一调整齿轮围绕第一齿轮轴转动时， 第 一驱动部对第一摆臂施加驱动力时，该驱动力使第一摆臂也围绕第一齿轮 轴转动， 从而实现第一摆臂围绕第二旋转中心 42a转动。 这样仅使第一旋 转中心 41 a和第二旋转中心 42a之间连线转过一定的角度即可， 因此能够 简便地控制该连线的角位移量。第二旋转中心 42b和第二齿轮轴同轴设置 达到的有益效果参照第二旋转中心 42a 和第一齿轮轴同轴设置的有益效 果。
作为上述实施例的进一步改进，所述第一齿轮轴和所述第二齿轮轴同 轴设置。 即图 10所示的第一齿轮轴和第二齿轮轴均为轴 52a。 这样一方 面是便于装配，另一方面可以实现第一摆臂的第二旋转中心 42a和第二摆 臂的第二旋转中心 42b的同轴， 控制起来更方便一些。 其中轴 52a的固定 方式有多种， 例如， 在用来支撑凸轮轴 7的轴承座 8上设置安装孔 82 , 轴 52a穿设在安装孔 82内。 这样轴承座同时起到固定支撑凸轮轴和调整 齿轮的作用， 简化了系统的结构。 其次， 第一调整齿轮 5a啮合有第一传动齿轮 6a, 第二调整齿轮 5b 啮合有第二传动齿轮 6b , 第一传动齿轮 6a刚性连接 （例如过盈压装） 在 第一传动轴 7a上， 第二传动齿轮 6b刚性连接在第二传动轴 7b上， 第二 传动轴 7b带动第一传动轴 7a转动。这样达到的有益效果是只需第二传动 轴 7b连接驱动源， 例如电机即可， 减少零部件的数量。 当然在本发明的 其它实施例中， 第一传动轴和第二传动轴也可以分别连接驱动源， 那样更 容易实现第一气门与第二气门不同的气门升程， 使进气时产生涡流， 提高 发动机性能。
实现第一气门与第二气门不同气门升程的具体方法有多种，例如第一 传动轴 7a为空心轴且套设在第二传动轴 7b上，并通过径向延伸的定位销 9连接， 且在第一传动轴 7a上设有使定位销 9沿周向滑动的滑槽 71 a。 这 样在第二传动轴转动时，由于定位销在滑槽中滑动实现了第一传动轴与第 二传动轴的相对转动，使第一传动齿轮和第二传动齿轮产生了一定的相位 差， 因此第一摆臂上的第一旋转中心 41a 和第二摆臂上的第一旋转中心 41b转过的角度不一致， 第一气门与第二气门的气门升程也就不一致。 通 过滑槽不同长度的设置可以实现第一传动齿轮和第二传动齿轮相位差的 大小。 当然不发明并不限于此， 也可以通过改变第一摆臂和第二摆臂的工 作面的形状和尺寸或是第一旋转中心 41 a和第一旋转中心 41b的初始位置 来实现第一气门与第二气门不同的气门升程。
为简化系统结构， 本发明实施例第二传动齿轮 6b 和第二传动轴 7b 通过定位销 9连接。 具体为将第二传动齿轮的轴向尺寸加长， 并设计一段 没有齿的区域， 并在该区域沿径向开设通孔 61b , 将定位销穿设在该通孔 61b内实现第二传动齿轮 6b与第二传动轴 7b的刚性连接。
具体而言， 第一驱动部 51 a为与第一调整齿轮 5a刚性连接的第一转 动轴， 第一旋转中心 41 a为第三通孔， 第一转动轴设在第三通孔内； 第二 驱动部为与第二调整齿轮 5b 刚性连接的第二转动轴， 第一旋转中心 41b 为第四通孔， 第二转动轴设在第四通孔内。 也就是第一旋转中心 41 a和第 一转动轴同轴设置， 第二旋转中心 42a和第二转动轴同轴设置。 这样第一 转动轴直接驱动第一摆臂 4a的第一旋转中心 41 a相对于第一摆臂 4a的第 二旋转中心 42a转过一定的角度， 第二转动轴直接驱动第二摆臂 4b的第 一旋转中心 41b相对于第二摆臂 4b的第二旋转中心 42b转过一定的角度， 因此能够简便地控制摆臂上驱动中心和调整中心之间连线的角位移量，简 化了结构和控制过程。 其中第一转动轴与第一调整齿轮优选一体成型， 第 二转动轴与第二调整齿轮优选一体成型， 以简化加工和装配工艺。 由于第
―转动轴和第一摆臂的驱动中心同轴设置，第二转动轴和第二摆臂的驱动 中心同轴设置，因此第一摆臂便围绕第一转动轴转动实现第一气门的打开 与关闭， 第二摆臂便围绕第二转动轴转动实现第二气门的打开与关闭。 此外， 第二旋转中心 42a为第五通孔， 第五通孔内设有第一销轴， 第 一销轴上安装有与所述凸轮轴的凸轮配合的第一摆臂滚子 43a; 第二旋转 中心 42b为第六通孔， 第六通孔内设有第二销轴， 第二销轴上安装有与所 述凸轮轴的凸轮配合的第二摆臂滚子 43b。 这样凸轮轴 7的凸轮驱动第一 摆臂滚子 43a、 第二摆臂滚子 43b以使第一摆臂 4a围绕第一转动轴摆动 实现第一气门的打开或闭合， 第二摆臂 4b围绕第二转动轴摆动实现第二 气门的打开或闭合。 如图 9和图 10所示， 第一气门摇臂 3a上还连接有液压挺柱 10a, 第 二气门摇臂 3b上还连接有液压挺柱 10b , 液压挺柱 10a、 10b能够使凸轮 轴 7上的凸轮与摆臂滚子 43a、 43b之间的接触、 以及气门摇臂 3a、 3b与 摆臂 4a、 4b的工作部之间的接触保持零间隙。 以上所述， 仅为本发明的具体实施方式， 但本发明的保护范围并不局 限于此， 任何熟悉本技术领域的技术人员在本发明揭露的技术范围内， 可 轻易想到的变化或替换， 都应涵盖在本发明的保护范围之内。 因此， 本发 明的保护范围应以所述权利要求的保护范围为准。

Claims

权 利 要 求 书
1、 一种可变气门升程驱动装置， 包括气门、 与气门连接的气门连杆、 与气门连杆连接的气门摇臂、 以及驱动气门打开或闭合的凸轮轴， 其特征 在于， 在气门摇臂和凸轮轴之间设有摆臂和调整齿轮； 所述摆臂上设有第 一旋转中心和第二旋转中心， 所述调整齿轮上设有驱动部， 凸轮轴转动时 带动摆臂围绕第一旋转中心摆动以驱动气门连杆直线往复运动实现气门的 打开或闭合， 调整齿轮绕自身的齿轮轴转动时带动驱动部围绕齿轮轴转动 以使第一旋转中心围绕第二旋转中心转动。
2、 根据权利要求 1所述的可变气门升程驱动装置， 其特征在于， 所述 驱动部为设在所述调整齿轮上的通孔和设在通孔内的转动轴， 所述第一旋 转中心为第一通孔， 所述转动轴设在第一通孔内。
3、 根据权利要求 1或 2所述的可变气门升程驱动装置， 其特征在于， 第二旋转中心为第二通孔， 第二通孔内设有销轴， 销轴与所述调整齿轮的 齿轮轴同轴设置， 且所述销轴上安装有与所述凸轮配合的摆臂滚子。
4、 根据权利要求 1所述的可变气门升程驱动装置， 其特征在于， 所述 调整齿轮为斜齿轮， 斜齿轮啮合有传动齿轮， 传动齿轮连接有驱动源。
5、 根据权利要求 1所述的可变气门升程驱动装置， 其特征在于， 所述 凸轮轴支撑在轴承座上， 轴承座上还设有安装孔， 齿轮轴穿设在安装孔内。
6、 根据权利要求 5所述的可变气门升程驱动装置， 其特征在于， 在齿 轮轴与安装孔之间设有销钉， 且销钉通过螺塞密封， 螺塞上设有泄油孔。
7、 根据权利要求 2所述的可变气门升程驱动装置， 其特征在于， 所述 转动轴上设有回位弹簧， 回位弹簧的一端与调整齿轮连接、 另一端与摆臂 连接。
8、 根据权利要求 1所述的可变气门升程驱动装置， 其特征在于， 所述 气门包括第一气门和第二气门， 所述气门连杆包括与所述第一气门连接的 第一气门连杆和与所述第二气门连接的第二气门连杆， 所述气门摇臂包括 与所述第一气门连杆连接的第一气门摇臂和与所述第二气门连杆连接的第 二气门摇臂， 所述凸轮轴可驱动所述第一气门和第二气门打开或闭合， 其 特征在于， 所述摆臂包括第一摆臂和第二摆臂， 所述调整齿轮包括第一调 整齿轮和第二调整齿轮， 所述第一摆臂和第一调整齿轮设置于所述第一气 门摇臂和凸轮轴之间， 所述第二摆臂和第二调整齿轮设置于所述第二气门 摇臂和凸轮轴之间； 所述第一摆臂和第二摆臂上均具有所述第一旋转中心 和第二旋转中心， 所述第一调整齿轮上设有第一驱动部， 所述第二调整齿 轮上设有第二驱动部， 凸轮轴转动时带动第一摆臂围绕第一摆臂上的第一 旋转中心摆动以驱动第一气门连杆直线往复运动实现第一气门的打开或闭 合， 并且凸轮轴转动时带动第二摆臂围绕第二摆臂上的第一旋转中心摆动 以驱动第二气门连杆直线往复运动实现第二气门的打开或闭合； 第一调整 齿轮绕自身的第一齿轮轴转动时带动第一驱动部围绕第一齿轮轴转动以使 第一摆臂上的第一旋转中心围绕第一摆臂上的第二旋转中心转动， 第二调 整齿轮绕自身的第二齿轮轴转动时带动第二驱动部围绕第二齿轮轴转动以 使第二摆臂上的第一旋转中心围绕第二摆臂上的第二旋转中心转动。
9、 根据权利要求 8所述的可变气门升程驱动装置， 其特征在于， 所述 第一摆臂上的第二旋转中心和所述第一齿轮轴同轴设置， 所述第二摆臂上 的第二旋转中心和所述第二齿轮轴同轴设置。
10、 根据权利要求 9所述的可变气门升程驱动装置， 其特征在于， 所 述第一齿轮轴和所述第二齿轮轴同轴设置。
11、 根据权利要求 10所述的可变气门升程驱动装置， 其特征在于， 所 述第一调整齿轮啮合有第一传动齿轮， 所述第二调整齿轮啮合有第二传动 齿轮， 所述第一传动齿轮刚性连接在第一传动轴上， 所述第二传动齿轮刚 性连接在第二传动轴上， 所述第二传动轴带动所述第一传动轴转动。
12、 根据权利要求 11所述的可变气门升程驱动装置， 其特征在于， 所 述第一传动轴套设在第二传动轴上， 并通过径向延伸的定位销连接， 且在 第一传动轴上设有使定位销沿周向滑动的滑槽。
13、 根据权利要求 12所述的可变气门升程驱动装置， 其特征在于， 所 述第二传动齿轮和所述第二传动轴通过所述定位销连接。
14、 根据权利要求 8-13中任一项所述的可变气门升程驱动装置， 其特 征在于， 所述第一驱动部为与所述第一调整齿轮刚性连接的第一转动轴， 所述第一旋转中心为第三通孔， 所述第一转动轴设在第三通孔内； 所述第 二驱动部为与所述第二调整齿轮刚性连接的第二转动轴， 所述第三旋转中 心为第四通孔， 所述第二转动轴设在第四通孔内。
15、 根据权利要求 14所述的可变气门升程驱动装置， 其特征在于， 所 述第二旋转中心为第五通孔， 第五通孔内设有第一销轴， 第一销轴上安装 有与所述凸轮轴的凸轮配合的第一摆臂滚子； 所述第四旋转中心为第六通 孔， 第六通孔内设有第二销轴， 第二销轴上安装有与所述凸轮轴的凸轮配 合的第二摆臂滚子。
PCT/CN2013/090810 2013-01-15 2013-12-28 可变气门升程驱动装置 Ceased WO2014110969A1 (zh)

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CN201554511U (zh) * 2009-10-23 2010-08-18 上海汽车集团股份有限公司 机械式连续可变气门升程驱动装置

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JP2006336623A (ja) * 2005-06-06 2006-12-14 Toyota Motor Corp 動弁装置の調整方法
US20090126666A1 (en) * 2005-09-08 2009-05-21 Mitsuru Sugimoto Engine valve operating system
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