说明书 Instruction manual
配气相位和气门升程均独立连续可调的调节方法及装置 技术领域 本发明属于发动机技术领域,具体来说涉及一种发动机配气相位和气门 升程均独立连续可调的调节方法, 同时还涉及该调节方法所用的装置。 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the field of engine technology, and in particular to an adjustment method in which an engine valve phase and a valve lift are independently and continuously adjustable. It also relates to the apparatus used in the adjustment method.
背景技术 发动机在不同工况下对配气相位和气门升程都有着不同的要求。根据发 动机的转速调节配气相位以及根据发动机的负荷对进气量的要求调节气门升 程, 是提高和改善发动机动力特性、 燃油经济性和减少有害气体排放的重要 技术手段之一。 目前, 配气相位和气门升程的调节方法主要有: 1 ) 采用不 同的凸轮来实现对配气相位的调节, 这种方法只能在很少的几种特定转速下 获得最佳配气相位, 存在不能实现相位的连续调节等缺点。 2 ) 通过改变凸 轮轴与曲轴之间的相对角度实现对配气相位的调节, 这类方法存在若增大提 前角时就会减小滞后角, 减小提前角则必然增大滞后角, 不能满足随发动机 转速的增减对气门提前角和滞后角同时增加或同时减小的调节要求等缺点。 3 ) 采用液压驱动气门, 并利用电磁阀或其他液压阀控制驱动气门的液压油 路来实现对配气相位或升程的调节, 这类方法存在需配置较多的电磁阀或其 他液压阀、 结构及控制复杂、 电磁阀高频响应性能欠佳等缺点。 4 ) 对凸轮 机构的从动件增加放大机构来实现气门升程的调节, 这种方法存在机构较复 杂、 高速动态特性欠佳等缺点。 由于上述可变配气相位和可变升程技术存在 诸多缺陷, 使配置有可变配气相位和可变气门升程系统的发动机对燃油经济 性和有害气体 放指标的改善效果不明显。 目前大多数发动机都没有配置可 变配气相位和可变升程装置, 气虹进气量的控制采用节气门, 节气门的使用 不利于进气道气流的流动, 增加了发动机的泵气损失, 发动机的燃油经济性
和有害气体排放指标均较差。 BACKGROUND OF THE INVENTION Engines have different requirements for valve timing and valve lift under different operating conditions. Adjusting the valve timing according to the engine speed and adjusting the valve lift according to the engine load is one of the important technical means to improve and improve engine power characteristics, fuel economy and reduce harmful gas emissions. At present, the adjustment methods of the valve timing and valve lift are mainly as follows: 1) Different cams are used to adjust the phase of the valve. This method can only obtain the best valve phase at a few specific speeds. There are disadvantages such as the inability to achieve continuous adjustment of the phase. 2) Adjusting the phase of the valve by changing the relative angle between the camshaft and the crankshaft. In this type of method, if the advance angle is increased, the lag angle will be reduced. If the advance angle is decreased, the lag angle will be increased. It satisfies the shortcomings such as the increase or decrease of the engine speed, the adjustment requirement of the valve advance angle and the retard angle simultaneously increasing or decreasing at the same time. 3) Hydraulically actuated valves are used, and solenoid valves or other hydraulic valves are used to control the hydraulic oil circuit that drives the valves to adjust the phase or lift of the valve. In this type of method, there are many solenoid valves or other hydraulic valves that need to be configured. The structure and control are complex, and the high-frequency response performance of the solenoid valve is not good. 4) The amplifying mechanism is added to the follower of the cam mechanism to realize the adjustment of the valve lift. This method has the disadvantages of complicated mechanism and high dynamic characteristics. Due to the above-mentioned limitations of the variable valve timing and variable lift technology, the engine with the variable valve phase and the variable valve lift system has no obvious improvement effect on the fuel economy and the harmful gas discharge index. At present, most engines are not equipped with a variable valve phase and a variable lift device. The control of the gas intake air volume uses a throttle valve. The use of the throttle valve is not conducive to the flow of the intake air flow, which increases the pumping loss of the engine. , engine fuel economy And harmful gas emission indicators are poor.
发明内容 本发明的目的在于提供一种发动机配气相位和气门升程均连续、独立可 调, 能提高发动机燃油经济性、 改善动力性和排放性的配气相位和气门升程 均独立连续可调的调节方法。 本发明的另一目的在于提供该配气相位和气门升程均独立连续可调的 调节装置。 本发明的目的及解决其主要技术问题是采用以下技术方案来实现的: 本发明的一种配气相位和气门升程均独立连续可调的调节方法, 包括: SUMMARY OF THE INVENTION An object of the present invention is to provide a continuous and independent adjustment of an engine valve phase and a valve lift, which can improve engine fuel economy, improve power and emissions, and independently and continuously adjust the valve phase and valve lift. Adjustment method of adjustment. Another object of the present invention is to provide an adjustment device in which the valve timing and valve lift are independently and continuously adjustable. The object of the present invention and the main technical problem of the present invention are achieved by the following technical solutions: A method for independently and continuously adjusting the valve phase and valve lift of the present invention includes:
( 1 ) 在液压式可变凸轮从动件的可变配气机构的凸轮油缸与气门油缸 之间的液压油路中并联一个配气相位调节器和一个气门升程调节器; (1) a gas distribution phase adjuster and a valve lift adjuster are connected in parallel in the hydraulic oil circuit between the cam cylinder and the valve cylinder of the variable valve train of the hydraulic variable cam follower;
( 2 ) 配气相位调节器包括配气相位调节器油缸、 配气相位调节器活塞、 配气相位调节器活塞回位装置和配气相位调节器卩艮位装置, 通过配气相位调 节器活塞回位装置产生的回位力使配气相位调节器活塞始终保持向零位方向 运动的趋势, 通过配气相位调节器限位装置控制配气相位调节器活塞从零位 到配气相位调节器限位装置之间的行程, 控制流入配气相位调节器油缸的油 作持续角, 实现配气相位连续可变控制; 其中: 配气相位调节器活塞处于零 位时的配气相位调节器活塞回位力和配气相位调节器活塞达到最大可调行程 时的回位力所对应的油压均小于液压系统克服气门弹簧预紧力而打开气门所 对应的油压; (2) The gas distribution phase adjuster includes a gas distribution phase adjuster cylinder, a gas distribution phase adjuster piston, a gas distribution phase adjuster piston return device, and a gas distribution phase adjuster clamp device, through the gas distribution phase adjuster piston The return force generated by the returning device causes the valve of the valve phase adjuster to keep moving toward the zero position. The valve of the valve phase adjuster is controlled by the valve phase adjuster from the zero position to the valve phase adjuster. The stroke between the limiting devices controls the oil flowing into the cylinder of the gas distribution phase adjuster as a continuous angle to realize continuous variable control of the valve timing phase; wherein: the valve of the gas distribution phase adjuster when the piston of the gas distribution phase adjuster is at the zero position The oil pressure corresponding to the return force and the return force of the valve phase adjuster piston reaching the maximum adjustable stroke is less than the oil pressure corresponding to the opening of the valve by the hydraulic system against the valve spring preload;
( 3 ) 气门升程调节器包括气门升程调节器油缸、 气门升程调节器活塞、 气门升程调节器活塞回位装置和气门升程调节器限位装置, 通过气门升程调 节器活塞回位装置产生的回位力使气门升程调节器活塞始终保持向零位方向
运动的趋势, 通过气门升程调节器限位装置控制气门升程调节器活塞从零位 到气门升程调节器限位装置之间的行程, 从而控制流入气门升程调节器的油 液容积, 进而控制流入气门油缸的油量, 最终实现控制气门升程连续可变控 制; 其中: 液压系统克服气门升程调节器活塞处于零位时的气门升程调节器 活塞回位力而推动气门升程调节器活塞运动所对应的油压大于系统克服气门 弹簧预紧力而打开气门所对应的油压, 气门升程调节器活塞达到最大可调行 程时气门升程调节器活塞回位力所对应的油压小于气门达到所需最小升程时 气门弹簧作用力所对应的油压。 上述的配气相位和气门升程均独立连续可调的调节方法, 其中: 液压油 路设有补油装置, 其油压小于系统克艮配气相位调节器活塞处于零位时的活 塞回位力而使配气相位调节器活塞运动所对应的油压。 上述的配气相位和气门升程均独立连续可调的调节方法, 其中: 配气相 位调节器和气门升程调节器的限位装置为限制杆、 限位块或限位套等。 上述的配气相位和气门升程均独立连续可调的调节方法, 其中: 配气相 位调节器和气门升程调节器的活塞回位装置为液压装置、 气压装置、 电磁装 置或 /和弹簧等。 本发明的配气相位和气门升程均独立连续可调的调节装置, 包括凸轮、 气门, 凸轮与气门之间设有液压系统, 其中: 在凸轮油缸与气门油缸之间的 液压油路中并联一个配气相位调节器和一个气门升程调节器, 配气相位调节 器包括配气相位调节器油缸、 配气相位调节器活塞、 配气相位调节器弹簧、 配气相位调节器限位 ^干, 配气相位调节器活塞位于配气相位调节器油缸内, 配气相位调节器活塞后端设有配气相位调节器弹簧和配气相位调节器限位 杆; 气门升程调节器包括气门升程调节器油缸、 气门升程调节器活塞、 气门 升程调节器弹簧、 气门升程调节器限位杆, 气门升程调节器活塞位于气门升 程调节器油缸内, 气门升程调节器的活塞后端设有气门升程调节器弹簧和限 位杆。 上述的配气相位和气门升程均独立连续可调的调节装置, 其中: 液压系
统克服配气相位调节器弹簧预紧力和配气相位调节器活塞达到最大可调行程 时的配气相位调节器弹簧的作用力而推动配气相位调节器活塞运动所对应的 油压均小于液压系统克月艮气门弹簧预紧力而打开气门所对应的油压; 液压系 统克服气门升程调节器弹簧预紧力而推动气门升程调节器活塞运动所对应的 油压大于系统克服气门弹簧预紧力而打开气门所对应的油压, 气门升程调节 器活塞达到最大可调行程时气门升程调节器弹簧的作用力所对应的油压小于 气门达到所需最小升程时气门弹簧的作用力所对应的油压。 上述的配气相位和气门升程均独立连续可调的调节装置, 其中: 配气相 位调节器弹簧可由在配气相位调节器活塞后腔 1入压力油或引入压力油和弹 簧的组合等方式等效替代。 上述的配气相位和气门升程均独立连续可调的调节装置, 其中: 气门升 程调节器弹簧可由在气门升程调节器活塞后腔 I入压力油或引入压力油和弹 簧的组合等方式等效替代。 本发明与现有技术相比具有明显的优点和有益效果。 由以上技术方案可 知, 本发明采用液压容积调节式调节方法, 使发动机在各种转速和负荷条件 下都能获得合适的配气相位和气门升程, 取消节气门, 减少泵气功率损失, 改善进排气条件, 防止废气倒流, 减少有用功损失, 提高燃油的燃烧效率, 降低有害气体排放, 改善发动机性能; 采用容积控制, 控制精确、 调节筒单; 配气相位和气门升程的调节范围宽, 可在发动机全工况下连续调整, 极大提 高和改善了发动机各工况下的动力性、 经济性和排放性; 对于发动机一定的 工况条件下, 相位调节器和气门升程调节器都只需进行相应的限位杆的位置 调节, 系统即可自动进行自适应运转, 无需针对发动机每一个循环都进行高 频、 反复的调节动作, 具有良好的系统自适应性和动态响应特性; 发动机所 有进气门和排气门的相位调节器, 可共用一个驱动装置, 所有进气门的升程 调节器, 可共用一个驱动装置, 结构筒单, 经济性好; 配气相位调节器和气 门升程调节器分别独立调节配气相位和气门升程, 发动机的配气相位调节和 气门升程调节相互独立, 可以满足各种工况的调节需求。
附图说明 图 1为本发明装置的结构示意图。 图中标己: (3) The valve lift adjuster includes a valve lift adjuster cylinder, a valve lift adjuster piston, a valve lift adjuster piston return device, and a valve lift adjuster limit device, and the piston is lifted through the valve lift adjuster. The return force generated by the position device keeps the valve lift regulator piston in the direction of zero The trend of movement, controlling the stroke between the valve lift regulator piston from the zero position to the valve lift regulator limit device by the valve lift adjuster limit device, thereby controlling the volume of oil flowing into the valve lift adjuster, In turn, the amount of oil flowing into the valve cylinder is controlled, and finally the control valve lift continuously variable control is realized; wherein: the hydraulic system overcomes the valve lift regulator piston return force when the valve lift regulator piston is at the zero position, and pushes the valve lift The oil pressure corresponding to the movement of the regulator piston is greater than the oil pressure corresponding to the opening of the valve by the system against the preload of the valve spring, and the piston return force of the valve lift adjuster is reached when the valve lift adjuster piston reaches the maximum adjustable stroke. The oil pressure is less than the oil pressure corresponding to the valve spring force when the valve reaches the required minimum lift. The above-mentioned gas distribution phase and valve lift are independently and continuously adjustable adjustment methods, wherein: the hydraulic oil circuit is provided with an oil replenishing device, and the oil pressure is smaller than the piston return position when the piston of the system 艮 gas distribution phase adjuster is at the zero position The force corresponds to the oil pressure corresponding to the movement of the valve phase adjuster piston. The above-mentioned gas distribution phase and valve lift are independent and continuously adjustable adjustment methods, wherein: the restriction device of the gas distribution phase adjuster and the valve lift adjuster is a limit rod, a limit block or a limit sleeve. The above-mentioned valve phase and valve lift are independently and continuously adjustable, wherein: the piston returning device of the valve phase adjuster and the valve lift adjuster is a hydraulic device, a pneumatic device, an electromagnetic device or/and a spring, etc. . The gas distribution phase and the valve lift of the invention are independent and continuously adjustable adjusting devices, including a cam and a valve, and a hydraulic system is provided between the cam and the valve, wherein: the hydraulic oil circuit between the cam cylinder and the valve cylinder is connected in parallel A gas distribution phase adjuster and a valve lift regulator, the gas distribution phase adjuster includes a gas distribution phase adjuster cylinder, a gas distribution phase adjuster piston, a gas distribution phase adjuster spring, a gas distribution phase adjuster limit The gas distribution phase adjuster piston is located in the gas distribution phase adjuster cylinder, and the rear end of the valve of the gas distribution phase adjuster is provided with a gas distribution phase adjuster spring and a gas distribution phase adjuster limit rod; the valve lift adjuster includes a valve lift Process adjuster cylinder, valve lift adjuster piston, valve lift adjuster spring, valve lift adjuster limit rod, valve lift adjuster piston are located in the valve lift regulator cylinder, the valve lift adjuster piston A valve lift adjuster spring and a limit rod are provided at the rear end. The above-mentioned valve phase and valve lift are independent and continuously adjustable adjusting devices, among which: hydraulic system Overcoming the valve pre-tightening force of the valve phase adjuster and the force of the valve phase adjuster spring when the valve of the valve phase adjuster reaches the maximum adjustable stroke, the oil pressure corresponding to the piston movement of the valve phase adjuster is smaller than The hydraulic system presses the valve spring preload to open the oil pressure corresponding to the valve; the hydraulic system overcomes the valve lift adjuster spring preload and pushes the valve lift adjuster piston to correspond to the oil pressure greater than the system overcomes the valve spring Preloading force to open the oil pressure corresponding to the valve, when the valve lift adjuster piston reaches the maximum adjustable stroke, the force corresponding to the force of the valve lift adjuster spring is smaller than the valve spring when the valve reaches the required minimum lift The oil pressure corresponding to the force. The above-mentioned valve phase and valve lift are independent and continuously adjustable adjusting devices, wherein: the valve phase adjuster spring can be inserted into the rear chamber of the piston of the valve phase adjuster into the pressure oil or a combination of the pressure oil and the spring. Equivalent replacement. The above-mentioned valve timing and valve lift are independent and continuously adjustable adjusting devices, wherein: the valve lift regulator spring can be inserted into the rear oil chamber of the valve lift regulator piston into the pressure oil or a combination of the pressure oil and the spring. Equivalent replacement. The present invention has significant advantages and advantageous effects over the prior art. According to the above technical solution, the invention adopts a hydraulic volume adjustment type adjustment method, so that the engine can obtain a proper valve phase and valve lift under various speed and load conditions, cancel the throttle valve, reduce the pump power loss, and improve. Intake and exhaust conditions, prevent exhaust gas backflow, reduce useful work loss, improve fuel combustion efficiency, reduce harmful gas emissions, improve engine performance; use volume control, control accuracy, adjust the cylinder; gas distribution phase and valve lift adjustment range Wide, continuous adjustment under full engine operating conditions, greatly improving and improving the power, economy and emissions under various engine operating conditions; phase adjuster and valve lift adjustment for certain engine operating conditions The controller only needs to adjust the position of the corresponding limit rod, and the system can automatically perform adaptive operation. It does not need to perform high-frequency and repeated adjustment actions for each cycle of the engine, and has good system adaptability and dynamic response characteristics. ; All the intake and exhaust valve phase regulators of the engine can share one The drive unit, the lift adjuster of all intake valves, can share a single drive unit, the structure is simple, and the economy is good; the valve phase adjuster and the valve lift adjuster independently adjust the valve phase and valve lift respectively. The engine's valve timing adjustment and valve lift adjustment are independent of each other, which can meet the adjustment requirements of various working conditions. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic structural view of a device of the present invention. In the picture:
1、 凸轮; 2、 气门; 3、 液压系统; 4、 凸轮油缸; 5、 气门油缸; 6、 液 压油路; 7、 配气相位调节器; 8、 配气相位调节器油虹; 9、 配气相位调节 器活塞; 10、 配气相位调节器弹簧; 11、 配气相位调节器卩艮位杆; 12、 气门 弹簧; 13、 凸轮油虹活塞; 14、 气门油缸活塞; 15、 气门升程调节器; 16、 气门升程调节器油缸; 17、 气门升程调节器活塞; 18、 气门升程调节器弹簧; 19、 气门升程调节器限位杆。 1, cam; 2, valve; 3, hydraulic system; 4, cam cylinder; 5, valve cylinder; 6, hydraulic oil circuit; 7, gas phase adjuster; 8, gas phase regulator oil rainbow; Gas phase regulator piston; 10, gas phase adjuster spring; 11, gas phase adjuster clamp; 12, valve spring; 13, cam oil rainbow piston; 14, valve cylinder piston; 15, valve lift Regulator; 16, valve lift regulator cylinder; 17, valve lift regulator piston; 18, valve lift adjuster spring; 19, valve lift adjuster limit rod.
具体实施方式: 以下结合附图及较佳实施例, 对依据本发明的具体实施方式、 结构、 特 征及其功效, 详细说明 ¾口后。 实施例 1 一种配气相位和气门升程均独立连续可调的调节方法, 包括: BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, the specific embodiments, structures, features and effects according to the present invention will be described in detail below with reference to the accompanying drawings and preferred embodiments. Embodiment 1 An independent and continuously adjustable adjustment method for a valve phase and a valve lift includes:
( 1 ) 在液压式可变凸轮从动件的可变配气机构的凸轮油缸与气门油缸 之间的液压油路中并联一个配气相位调节器和一个气门升程调节器, 配气相 位调节器和气门升程调节器分别独立调节配气相位和气门升程; (1) A gas distribution phase adjuster and a valve lift regulator are connected in parallel in the hydraulic oil circuit between the cam cylinder and the valve cylinder of the variable valve train of the hydraulic variable cam follower, and the valve phase adjustment The valve and the valve lift adjuster independently adjust the valve phase and the valve lift;
( 2 ) 配气相位调节器包括配气相位调节器油缸、 配气相位调节器活塞、 配气相位调节器活塞回位装置和配气相位调节器卩艮位装置, 通过配气相位调 节器活塞回位装置产生的回位力使配气相位调节器活塞始终保持向零位 (配 气相位调节器油缸容积为零的位置) 方向运动的趋势, 通过配气相位调节器 限位装置控制配气相位调节器活塞从零位到配气相位调节器限位装置之间的
行程, 控制流入配气相位调节器油缸的油液容积, 进而控制油液流入气门油 缸的时刻及其对应于凸轮转动时的有效工作持续角, 实现配气相位连续可变 控制; 其中: 配气相位调节器活塞处于零位时的配气相位调节器活塞回位力 和配气相位调节器活塞达到最大可调行程时的回位力所对应的油压均小于液 压系统克月艮气门弹簧预紧力而打开气门所对应的油压。 (2) The gas distribution phase adjuster includes a gas distribution phase adjuster cylinder, a gas distribution phase adjuster piston, a gas distribution phase adjuster piston return device, and a gas distribution phase adjuster clamp device, through the gas distribution phase adjuster piston The returning force generated by the returning device keeps the valve of the valve phase adjuster in the direction of zero position (the position of the valve phase adjuster cylinder is zero), and the valve is controlled by the valve phase adjuster limiter. Position regulator piston from zero position to the valve phase regulator limiter The stroke controls the volume of the oil flowing into the cylinder of the gas distribution phase adjuster, thereby controlling the timing of the oil flowing into the valve cylinder and the effective working angle corresponding to the rotation of the cam, thereby realizing the continuously variable control of the valve phase; When the position regulator piston is in the zero position, the valve return force of the valve phase adjuster and the return force of the valve phase adjuster piston reaching the maximum adjustable stroke are less than the hydraulic system. Press the force to open the valve corresponding to the oil pressure.
( 3 ) 气门升程调节器包括气门升程调节器油缸、 气门升程调节器活塞、 气门升程调节器活塞回位装置和气门升程调节器限位装置, 通过气门升程调 节器活塞回位装置产生的回位力使气门升程调节器活塞始终保持向零位 (气 门升程调节器油缸容积为零的位置) 方向运动的趋势, 通过气门升程调节器 限位装置控制气门升程调节器活塞从零位到气门升程调节器限位装置之间的 行程, 从而控制流入气门升程调节器的油液容积, 进而控制流入气门油缸的 油量, 最终实现控制气门升程连续可变控制; 其中: 液压系统克服气门升程 调节器活塞处于零位时的气门升程调节器活塞回位力而推动气门升程调节器 活塞运动所对应的油压大于系统克月艮气门弹簧预紧力而打开气门所对应的油 压, 气门升程调节器活塞达到最大可调行程时气门升程调节器活塞回位力所 对应的油压小于气门达到所需最小升程时气门弹簧作用力所对应的油压。 液压油路设有补油装置, 其油压小于系统克艮配气相位调节器活塞处于 零位时的活塞回位力而使配气相位调节器活塞运动所对应的油压。 配气相位调节器和气门升程调节器的限位装置为限制杆、 限位块或限位 套等。 配气相位调节器和气门升程调节器的活塞回位装置为液压装置、 气压装 置、 电磁装置或 /和弹簧等。 实施例 2 一种配气相位和气门升程均独立连续可调的调节装置, 包括凸轮 1、 气 门 2, 凸轮 1与气门 2之间设有液压系统 3 , 其中: 在凸轮油缸 4与气门油 缸 5之间的液压油路 6中并联一个配气相位调节器 Ί和气门升程调节器 15 ,
其中: 配气相位调节器 7 包括配气相位调节器油缸 8、 配气相位调节器活塞 9、 配气相位调节器弹簧 10、 配气相位调节器限位 4干 11 , 配气相位调节器活 塞 9位于配气相位调节器油缸 8内, 配气相位调节器活塞 9后端设有配气相 位调节器弹簧 10和配气相位调节器限位杆 11 ; 气门升程调节器 15包括气门 升程调节器油缸 16、 气门升程调节器活塞 17、 气门升程调节器弹簧 18、 气 门升程调节器限位杆 19 , 气门升程调节器活塞 17位于气门升程调节器油缸 16内, 气门升程调节器活塞 17后端设有气门升程调节器弹簧 18和气门升程 调节器限位杆 19。 液压系统克艮配气相位调节器弹簧 10 预紧力和配气相位调节器活塞 9 达到最大可调行程时的配气相位调节器弹簧 10 的作用力而推动配气相位调 节器活塞 9运动所对应的油压均小于液压系统克服气门弹簧 12预紧力而打 开气门 2所对应的油压。 液压系统克服气门升程调节器弹簧 18预紧力而推 动气门升程调节器活塞 17运动所对应的油压大于系统克服气门弹簧 12预紧 力而打开气门 2所对应的油压, 气门升程调节器活塞 17达到最大可调行程 时气门升程调节器弹簧 18 的作用力所对应的油压小于气门 2达到所需最小 升程时气门弹簧 12的作用力所对应的油压。 配气相位调节器弹簧 10可由在配气相位调节器活塞 9后腔引入压力油或 引入压力油和弹簧的组合等方式等效替代。 气门升程调节器弹簧 18可由在气门升程调节器活塞 17后腔引入压力油或 引入压力油和弹簧的组合等方式等效替代。 (3) The valve lift adjuster includes a valve lift adjuster cylinder, a valve lift adjuster piston, a valve lift adjuster piston return device, and a valve lift adjuster limit device, and the piston is lifted through the valve lift adjuster. The return force generated by the position device keeps the valve lift regulator piston always moving toward the zero position (the position of the valve lift regulator cylinder is zero), and the valve lift is controlled by the valve lift adjuster limit device. The stroke of the regulator piston from the zero position to the valve lift regulator limit device, thereby controlling the volume of oil flowing into the valve lift regulator, thereby controlling the amount of oil flowing into the valve cylinder, and finally achieving continuous control of the valve lift. Variable control; wherein: the hydraulic system overcomes the valve lift adjuster piston return force when the valve lift adjuster piston is at the zero position, and pushes the valve lift adjuster piston movement corresponding to the oil pressure is greater than the system 艮月艮 valve spring pre Pressing the oil pressure corresponding to the valve, the valve lift adjuster piston reaches the maximum adjustable stroke, and the valve lift adjuster piston return force It should be less than the hydraulic force of the valve spring for the valve to the hydraulic pressure corresponding to the desired minimum lift. The hydraulic oil circuit is provided with an oil replenishing device, and the oil pressure is less than the hydraulic pressure corresponding to the piston returning force when the piston of the system 艮 gas distribution phase adjuster is at the zero position, and the piston of the gas distribution phase adjuster is moved. The limit devices of the valve phase adjuster and the valve lift adjuster are limit rods, limit blocks or limit sleeves. The piston returning device of the valve phase adjuster and the valve lift adjuster is a hydraulic device, a pneumatic device, an electromagnetic device or/and a spring. Embodiment 2 An independent and continuously adjustable adjusting device for the valve phase and the valve lift includes a cam 1, a valve 2, and a hydraulic system 3 between the cam 1 and the valve 2, wherein: the cam cylinder 4 and the valve cylinder A gas distribution phase adjuster Ί and a valve lift adjuster 15 are connected in parallel between the hydraulic oil circuit 6 of 5; Wherein: the gas distribution phase adjuster 7 includes a gas distribution phase adjuster cylinder 8, a gas distribution phase adjuster piston 9, a gas distribution phase adjuster spring 10, a gas distribution phase adjuster limit 4 dry 11, a gas distribution phase adjuster piston 9 is located in the gas distribution phase adjuster cylinder 8, and the rear end of the gas distribution phase adjuster piston 9 is provided with a gas distribution phase adjuster spring 10 and a gas distribution phase adjuster limit rod 11; the valve lift adjuster 15 includes a valve lift The regulator cylinder 16, the valve lift regulator piston 17, the valve lift adjuster spring 18, the valve lift adjuster limit lever 19, the valve lift adjuster piston 17 are located in the valve lift regulator cylinder 16, the valve lift The valve adjuster piston 17 is provided with a valve lift adjuster spring 18 and a valve lift adjuster limit lever 19 at the rear end. Hydraulic system 艮 艮 调 调 phase adjuster spring 10 preload and valve phase adjuster piston 9 reaches the maximum adjustable stroke of the valve phase adjuster spring 10 to push the valve phase adjuster piston 9 movement The corresponding oil pressure is less than the hydraulic pressure corresponding to the opening of the valve 2 by the hydraulic system against the preload of the valve spring 12. The hydraulic system overcomes the preload force of the valve lift adjuster spring 18 and pushes the valve lift adjuster piston 17 to move the oil pressure corresponding to the oil pressure corresponding to the system to overcome the preload of the valve spring 12 and open the valve 2, the valve lift When the regulator piston 17 reaches the maximum adjustable stroke, the force corresponding to the force of the valve lift adjuster spring 18 is less than the oil pressure corresponding to the force of the valve spring 12 when the valve 2 reaches the required minimum lift. The valve timing adjuster spring 10 can be equivalently replaced by a combination of introducing pressure oil or introducing a combination of pressure oil and spring in the rear chamber of the valve phase adjuster piston 9. The valve lift adjuster spring 18 may be equivalently replaced by a combination of introducing pressurized oil or introducing a combination of pressurized oil and spring in the rear chamber of the valve lift regulator piston 17.
工作过程如下: 配气相位调节器活塞 9在凸轮油缸活塞 13后端与凸轮 1相接触处为凸 轮基圓时, 在配气相位调节器弹簧 10 弹簧力 (回位力) 的作用下处于零位 (配气相位调节器油缸 8容积为零的位置)。 调节配气相位调节器限位 4干 11 的位置就可以控制配气相位调节器活塞 9从零位到相位调节器限位杆 11之间
的行程, 从而控制流入配气相位调节器油缸 8的油液容积, 进而控制油液流 入气门油缸 5的时刻及其对应于凸轮 1转动时的有效工作持续角, 最终实现 控制配气相位连续可变控制。 气门升程调节器活塞 17在凸轮油虹活塞 13后端与凸轮 1相接触处为凸 轮基圓时, 在气门升程调节器弹簧 18 弹簧力 (回位力) 的作用下处于零位 (气门升程调节器油缸 16容积为零的位置)。调节气门升程调节器限位杆 19 的位置就可以控制气门升程调节器活塞 17 从零位到气门升程调节器限位杆 19之间的行程, 从而控制流入气门升程调节器油缸 16的油液容积, 进而控 制油液流入气门油缸 5的油量, 最终达到调节、 控制气门升程的目的。 当发动机处于最高转速运转时,将配气相位调节器限位杆 11调节至与配 气相位调节器活塞 9后端的间隙为零且推动配气相位调节器活塞 9至零位, 则可以流入配气相位调节器 Ί的油液容积为零。 凸轮 1处于升程时, 在凸轮 油虹活塞 13 的作用下液压系统油压升高, 当油压升高至系统作用于气门油 缸活塞 14的力大于气门弹簧 12预紧力时, 液压油流入气门油缸 5并推动气 门油缸活塞 14运动同时气门 1打开并且开度不断加大直至凸轮 1升程结束。 当凸轮 1处于回程时, 气门 2在气门弹簧 12的作用下回落, 油液向凸轮油 虹 4回流, 同时油压降氐, 当油压降氐至系统作用于气门油虹活塞 14的力 小于气门弹簧 12预紧力时, 气门 2关闭。 如上所述, 该过程中, 油液流入 气门油缸 5的时刻最早, 油液从气门油缸 5中全部流出的时刻最晚, 配气相 位获得最大提前角、 最大滞后角和最大有效工作持续角。 当发动机处于最低转速运转时,将配气相位调节器限位杆 11调节至与配 气相位调节器活塞 9后端的间隙为其调节范围的最大值, 则可以流入配气相 位调节器 7的油液容积为最大。 凸轮 1处于升程时, 在凸轮油虹活塞 14的 作用下液压系统油压升高, 当油压升高至系统作用于配气相位调节器活塞 9 的力大于配气相位调节器弹簧 10预紧力时, 配气相位调节器活塞 9开始运 动, 液压油首先流入配气相位调节器油缸 8并且流入的容积不断加大直至配 气相位调节器活塞 9后端与配气相位调节器限位杆 11接触。配气相位调节器 活塞 9运动停止后系统油压进一步升高, 当油压升高至系统作用于气门油缸
活塞 14的力大于气门弹簧 12预紧力时, 液压油才开始流入气门油缸 5推动 气门油虹活塞 14运动同时气门 2打开并且开度不断加大直至凸轮 1升程结 束。 当凸轮 1处于回程时, 气门 2首先在气门弹簧 12的作用下回落, 油液 向凸轮油虹 4回流, 同时油压降氐, 当油压降氐至系统作用于气门油虹活塞 14的力小于气门弹簧 12预紧力时, 气门 2关闭。 气门 2关闭后, 配气相位 调节器 7中的油液在配气相位调节器弹簧力作用下也在开始向凸轮油虹 4回 流直至配气相位调节器活塞 9回到零位。 如上所述, 该过程中, 油液流入气 门油缸 5的时刻最晚, 油液从气门油缸 5中全部流出的时刻最早, 配气相位 获得最小提前角、 最小滞后角和最小有效工作持续角。 当发动机处于最高与最低转速之间运转时, 根据发动机的工作情况将配 气相位调节器限位杆 11调节至合理值, 系统即可获得合理的提前角、滞后角 和有效工作持续角。 当发动机处于最高负荷运转时,将气门升程调节器限位杆 19调节至与气 门升程调节器活塞 17 后端的间隙为零且推动气门升程调节器活塞 17 至零 位, 则可以流入气门升程调节器 15 的油量为零。 凸轮 1 处于升程时, 在凸 轮油虹活塞 13 的作用下液压系统油压升高, 当油压升高至系统作用于气门 油缸活塞 14的力大于气门弹簧 12预紧力时, 液压油流入气门油缸 5并推动 气门油虹活塞 14 运动同时气门打开并且开度不断加大直至凸轮升程结束。 当凸轮 1处于回程时, 气门 2在气门弹簧 12的作用下回落, 油液向凸轮油 虹 4回流, 同时油压降氐, 当油压降氐至系统作用于气门油虹活塞 14的力 小于气门弹 12簧预紧力时, 气门 2关闭。 如上所述, 该过程中, 凸轮油缸 4 中流出的油全部流入气门油缸 5 , 气门 2升程达到最大。 当发动机处于最低负荷运转时,将气门升程调节器限位杆 19调节至与气 门升程调节器活塞 17 后端的间隙为其调节范围的最大值, 则可以流入气门 升程调节器 15的油量为最大。 凸轮 1处于升程时, 在凸轮油缸活塞 13的作 用下液压系统油压升高, 当油压升高至系统作用于气门油虹活塞 14 的力大 于气门弹簧 12预紧力时, 液压油首先流入气门油缸 5推动气门油缸活塞 14 运动同时气门 2打开。 随着气门 2升程的加大, 系统油压进一步升高, 当油
压升高至系统作用于气门升程调节器活塞 17 的力大于气门升程调节器弹簧 18预紧力时, 液压油流入气门升程调节器油缸 16推动气门升程调节器活塞 17运动并且流入容积不断加大直至气门升程调节器活塞 17后端与气门升程 调节器限位杆 19接触。 在气门升程调节器活塞 17运动的同时气门升程也在 不断加大, 气门升程调节器活塞 17 停止后, 系统油压进一步升高, 气门升 程继续加大直至凸轮升程结束。 当凸轮 1处于回程时, 气门 2在气门弹簧 12 的作用下回落, 油液向凸轮油虹 4回流, 同时油压降氐, 当油压降低至系统 作用于气门升程调节器活塞 17的力小于气门升程调节器活塞 17后端的弹簧 力时, 气门升程调节器活塞 17 在弹簧力作用下也开始返回, 气门升程调节 器 16内的油液也开始向凸轮油虹 4回流直至气门升程调节器活塞 17回到零 位 (气门升程调节器油缸容积为零的位置)。 在气门升程调节器活塞 17回位 的过程中气门 2也在不断回落, 系统油压不断降氐, 当油压降氐至作用于气 门油缸活塞 14的力小于气门弹簧 12预紧力时, 气门 2关闭。 如上所述, 该 过程中, 凸轮油虹 4中流出的油流入气门升程调节器 7的容积最大, 而流入 气门油缸 5的容积最小, 气门升程达到最小。 当发动机处于最大与最小负荷之间运转时, 才艮据发动机的工作情况将气 门升程调节器限位杆 19调节至合理值, 系统即可获得合理的气门升程。 当发动机处于需要同时进行配气相位、 气门升程调节时, 根据发动机的 工况同时分别将配气相位调节器限位杆 11、 气门升程调节器卩艮位杆 19调节 至合理位置, 系统即可获得合理的配气相位和气门升程。 The working process is as follows: When the rear end of the cam cylinder piston 13 is in the cam base circle at the rear end of the cam cylinder piston 13 , the valve 9 is at zero under the spring force (return force) of the valve phase adjuster spring 10 Position (position where the gas phase adjuster cylinder 8 has a volume of zero). Adjusting the position of the valve phase adjuster limit 4 dry 11 can control the valve phase adjuster piston 9 from the zero position to the phase adjuster limit lever 11 The stroke, thereby controlling the volume of oil flowing into the gas phase regulator cylinder 8, thereby controlling the timing of the oil flowing into the valve cylinder 5 and its effective working angle corresponding to the rotation of the cam 1, and finally achieving the control of the gas distribution phase continuously Variable control. The valve lift adjuster piston 17 is at the zero position (valve force) under the action of the spring lift (return force) of the valve lift adjuster spring 18 when the rear end of the cam oil rainbow piston 13 is a cam base circle at the contact with the cam 1 The position of the lift regulator cylinder 16 is zero). Adjusting the position of the valve lift adjuster limit lever 19 controls the stroke between the valve lift adjuster piston 17 from the zero position to the valve lift adjuster limit lever 19, thereby controlling the flow into the valve lift regulator cylinder 16 The volume of the oil, which in turn controls the amount of oil flowing into the valve cylinder 5, ultimately achieves the purpose of regulating and controlling the valve lift. When the engine is running at the highest speed, the valve phase adjuster limit lever 11 is adjusted to zero with the clearance of the rear end of the valve phase adjuster piston 9 and the valve phase adjuster piston 9 is pushed to the zero position, and then the flow can be flown in. The gas phase regulator has a zero oil volume. When the cam 1 is in the lift, the hydraulic system hydraulic pressure rises under the action of the cam oil rainbow piston 13, and when the oil pressure rises until the force of the system acting on the valve cylinder piston 14 is greater than the preload of the valve spring 12, the hydraulic oil flows in. The valve cylinder 5 pushes the valve cylinder piston 14 to move while the valve 1 is opened and the opening is continuously increased until the end of the cam 1 lift. When the cam 1 is in the return stroke, the valve 2 is retracted by the valve spring 12, the oil returns to the cam oil rainbow 4, and the oil pressure drops, and when the oil pressure drops to the system, the force acting on the valve oil rainbow piston 14 is less than When the valve spring 12 is preloaded, the valve 2 is closed. As described above, in this process, the timing at which the oil flows into the valve cylinder 5 is the earliest, and the time at which the oil flows out from the valve cylinder 5 at the latest is the latest, and the valve phase obtains the maximum advance angle, the maximum retard angle, and the maximum effective working angle. When the engine is at the minimum speed operation, the valve phase adjuster limit lever 11 is adjusted to the clearance of the rear end of the valve phase adjuster piston 9 to the maximum value of the adjustment range thereof, and the oil of the valve phase adjuster 7 can be flown. The volume of the liquid is the largest. When the cam 1 is in the lift, the hydraulic system hydraulic pressure rises under the action of the cam oil rainbow piston 14, and when the oil pressure rises to the system, the force acting on the valve phase adjuster piston 9 is greater than the valve phase adjuster spring 10 When tightening, the valve phase adjuster piston 9 starts to move, and the hydraulic oil first flows into the valve phase adjuster cylinder 8 and the volume of the inflow continues to increase until the rear end of the valve phase adjuster piston 9 and the valve phase adjuster limit The rod 11 is in contact. After the valve of the valve phase adjuster piston 9 stops, the oil pressure of the system further rises. When the oil pressure rises, the system acts on the valve cylinder. When the force of the piston 14 is greater than the preload of the valve spring 12, the hydraulic oil begins to flow into the valve cylinder 5 to push the valve oil rainbow piston 14 to move while the valve 2 is opened and the opening degree is continuously increased until the end of the lift of the cam 1. When the cam 1 is in the return stroke, the valve 2 first falls back under the action of the valve spring 12, the oil returns to the cam oil rainbow 4, and the oil pressure drops, when the oil pressure drops to the force of the system acting on the valve oil rainbow piston 14. When the valve spring 12 is less than the preload, the valve 2 is closed. After the valve 2 is closed, the oil in the valve phase adjuster 7 is also started to return to the cam oil rainbow 4 under the spring force of the valve phase regulator until the valve phase adjuster piston 9 returns to the zero position. As described above, in this process, the time when the oil flows into the valve cylinder 5 is the latest, the time when the oil flows out from the valve cylinder 5 at the earliest, and the valve phase obtains the minimum advance angle, the minimum retard angle, and the minimum effective working angle. When the engine is running between the highest and lowest speeds, the valve phase adjuster limit lever 11 is adjusted to a reasonable value according to the operating condition of the engine, and the system can obtain a reasonable advance angle, a retard angle and an effective working angle. When the engine is at the maximum load operation, the valve lift adjuster limit lever 19 is adjusted to zero with the clearance of the rear end of the valve lift adjuster piston 17 and the valve lift adjuster piston 17 is pushed to the zero position, and the valve can be flowed in. The lift regulator 15 has zero oil. When the cam 1 is in the lift, the hydraulic system oil pressure rises under the action of the cam oil rainbow piston 13, and when the oil pressure rises until the force of the system acting on the valve cylinder piston 14 is greater than the preload force of the valve spring 12, the hydraulic oil flows in. The valve cylinder 5 pushes the valve oil rainbow piston 14 to move while the valve is opened and the opening is continuously increased until the cam lift ends. When the cam 1 is in the return stroke, the valve 2 is retracted by the valve spring 12, the oil returns to the cam oil rainbow 4, and the oil pressure drops, and when the oil pressure drops to the system, the force acting on the valve oil rainbow piston 14 is less than When the valve spring 12 spring preload, the valve 2 is closed. As described above, in the process, all of the oil flowing out of the cam cylinder 4 flows into the valve cylinder 5, and the lift of the valve 2 is maximized. When the engine is at the minimum load operation, the valve lift adjuster limit lever 19 is adjusted to the clearance with the rear end of the valve lift adjuster piston 17 to the maximum value of the adjustment range thereof, and the oil of the valve lift adjuster 15 can be flown. The amount is the largest. When the cam 1 is in the lift, the hydraulic pressure of the hydraulic system rises under the action of the cam cylinder piston 13. When the oil pressure rises until the force of the system acting on the valve oil rainbow piston 14 is greater than the preload of the valve spring 12, the hydraulic oil first The inflow valve cylinder 5 pushes the valve cylinder piston 14 to move while the valve 2 is open. As the valve 2 lift increases, the system oil pressure rises further, when the oil When the pressure is raised until the force of the system acting on the valve lift regulator piston 17 is greater than the preload force of the valve lift adjuster spring 18, the hydraulic oil flowing into the valve lift regulator cylinder 16 pushes the valve lift adjuster piston 17 to move and flows in. The volume continues to increase until the rear end of the valve lift adjuster piston 17 is in contact with the valve lift adjuster limit lever 19. At the same time as the valve lift adjuster piston 17 moves, the valve lift is also continuously increased. After the valve lift adjuster piston 17 is stopped, the system oil pressure is further increased, and the valve lift continues to increase until the cam lift ends. When the cam 1 is in the return stroke, the valve 2 is retracted by the valve spring 12, the oil returns to the cam oil rainbow 4, and the oil pressure drops, when the oil pressure drops to the force of the system acting on the valve lift regulator piston 17. When the spring force is less than the spring force at the rear end of the valve lift adjuster piston 17, the valve lift adjuster piston 17 also starts to return under the action of the spring force, and the oil in the valve lift adjuster 16 also starts to return to the cam oil rainbow 4 until the valve The lift adjuster piston 17 returns to the zero position (the position of the valve lift regulator cylinder is zero). During the return of the valve lift regulator piston 17, the valve 2 is also continuously falling, the system oil pressure is continuously lowered, and when the oil pressure drops to a force acting on the valve cylinder piston 14 less than the preload of the valve spring 12, Valve 2 is closed. As described above, in this process, the oil flowing out of the cam oil rainbow 4 flows into the valve lift adjuster 7 with the largest volume, and the volume flowing into the valve cylinder 5 is the smallest, and the valve lift is minimized. When the engine is running between the maximum and minimum loads, the valve lift adjuster limit lever 19 is adjusted to a reasonable value according to the operating conditions of the engine, and the system can obtain a reasonable valve lift. When the engine is in need of simultaneous gas distribution phase and valve lift adjustment, the valve phase adjuster limit rod 11 and the valve lift adjuster clamp rod 19 are simultaneously adjusted to a reasonable position according to the operating conditions of the engine, the system A reasonable valve timing and valve lift can be obtained.
以上所述, 仅是本发明的较佳实施例而已, 并非对本发明作任何形式上 的限制, 任何未脱离本发明技术方案内容, 依据本发明的技术实质对以上实 施例所作的任何筒单修改、 等同变化与修饰, 均仍属于本发明技术方案的范 围内。
The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way. Any modification to the above embodiments can be made according to the technical essence of the present invention without departing from the technical scope of the present invention. And equivalent changes and modifications are still within the scope of the technical solution of the present invention.