WO2015039571A1 - 一种双向可调节凸轮轴相位器锁止机构及油路 - Google Patents

一种双向可调节凸轮轴相位器锁止机构及油路 Download PDF

Info

Publication number
WO2015039571A1
WO2015039571A1 PCT/CN2014/086004 CN2014086004W WO2015039571A1 WO 2015039571 A1 WO2015039571 A1 WO 2015039571A1 CN 2014086004 W CN2014086004 W CN 2014086004W WO 2015039571 A1 WO2015039571 A1 WO 2015039571A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
spring
lock pin
locking mechanism
oil passage
Prior art date
Application number
PCT/CN2014/086004
Other languages
English (en)
French (fr)
Inventor
林建刚
Original Assignee
奇瑞汽车股份有限公司
芜湖普威技研有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 奇瑞汽车股份有限公司, 芜湖普威技研有限公司 filed Critical 奇瑞汽车股份有限公司
Publication of WO2015039571A1 publication Critical patent/WO2015039571A1/zh

Links

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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • the present invention relates to the field of camshaft phasers, and more particularly to a bidirectional adjustable camshaft phaser locking mechanism and oil passage. Background technique
  • variable valve timing system VVT
  • boost technology have become mainstream, especially VVT systems have become the standard for engines.
  • the system adjusts the phase of the engine cam through the equipped control and execution system, so that the valve opening and closing time changes with the engine speed to improve the charging efficiency and increase the engine power.
  • the camshaft phaser is used to obtain the position of the camshaft relative to the crankshaft.
  • the camshaft phase is important for the operation of the gasoline engine.
  • the output curve of the engine is adjusted to determine the fuel injection and ignition timing, and the signal is sent to the electronic control unit (ECU). Carry out implementation.
  • camshaft phasers were all unidirectionally adjusted phasers.
  • the camshafts could only be rotated in one direction to change the valve timing.
  • the adjusted phaser has not been able to fully take into account all operating conditions of the engine. Especially in idle conditions, because the engine oil pressure is low, the phaser cannot work, and the basic position is not the best phase, which can not guarantee the best performance and emission requirements.
  • the two-way adjustable camshaft phaser can be well integrated, and the locking position can be fixed at a certain angle according to engine development requirements, taking into account the phase requirements of all operating conditions of the engine.
  • the unlocking of the two-way adjustable phaser and ensuring accurate return has been a technical problem. Summary of the invention
  • embodiments of the present invention provide a bidirectional adjustable camshaft phaser locking mechanism and an oil circuit. It is convenient for the two-way adjustable phaser to be smoothly unlocked and to return to the initial position smoothly and accurately during the shutdown.
  • the technical solution is as follows:
  • a bidirectional adjustable camshaft phaser locking mechanism and an oil circuit comprising at least: a rotor, a stator, a sprocket, a cover plate, a lock pin, a lock pin spring, a spring bracket, and the rotor is provided with a pressure Differential valve.
  • the rotor is provided with a return spring bracket, and the return spring bracket is positioned with the rotor through a card slot disposed thereon.
  • the return spring bracket is mounted with two return springs, and the other end of the return spring is fixed to the stator by bolts, and the two return springs have opposite torques.
  • the rotor includes at least: an A chamber oil passage, a B chamber oil passage, a differential pressure valve mounting hole, a rotor oil passage, an oil groove, and a lock pin mounting hole;
  • the rotor oil passage is disposed on the rotor, a pressure difference valve mounting hole, the oil groove, the lock pin mounting hole, the lock pin mounting hole is provided with the lock pin, the spring bracket, and one end of the lock pin is provided with the oil groove
  • the differential pressure valve is disposed in the differential pressure valve mounting hole, and the differential pressure valve is in communication with the rotor oil passage.
  • the cover plate is provided with a cover oil passage and a lock pin hole.
  • the related oil passage includes at least: the cover oil passage, the A chamber oil passage, the B chamber oil passage, the rotor oil passage, and the oil groove.
  • the rotor cooperates with the stator to form a camshaft phaser advance chamber A and a retard chamber B.
  • the advance chamber A communicates with the A chamber oil passage.
  • the lag chamber B communicates with the B chamber oil passage.
  • the differential pressure valve includes at least: a casing, a left spring, a spool valve, and a right spring; the casing is installed in a main blade mounting hole of the rotor, and the sliding valve is disposed in the casing, The left spring and the right spring are disposed on the spool.
  • the differential pressure valve When the rotor rotates to the right, the differential pressure valve is in a hysteresis adjustment state, the spool valve is located at a right portion of the inner casing, and compresses the right spring; when the rotor rotates to the left, the pressure difference The valve is in an advanced adjustment state, the spool valve is located on a left side portion of the outer casing, and compresses the left spring.
  • the rotor is disposed in the stator, the lock pin and the spring bracket are disposed on the rotor, and the lock pin spring is disposed in the lock pin;
  • the sprocket is provided with the cover plate at the front of the stator.
  • FIG. 1 is a front elevational view showing a schematic diagram of a two-way adjustable camshaft phaser locking mechanism and an oil passage structure according to an embodiment of the present invention
  • Figure 2 is a right side view of Figure 1 provided by an embodiment of the present invention.
  • FIG. 3 is a schematic structural view of the lock mechanism of the bidirectional adjustable camshaft phaser locking mechanism and the oil passage of the A-A cross-sectional view of FIG. 1 according to the embodiment of the present invention
  • Figure 4 is a cross-sectional view taken along line B-B of Figure 1 according to an embodiment of the present invention
  • Figure 5 is a front elevational view showing the structure of the rotor of Figure 3 according to an embodiment of the present invention
  • Figure 6 is a cross-sectional view taken along line D-D of Figure 5 according to an embodiment of the present invention.
  • Figure 7 is a front elevational view showing the structure of the cover plate of Figure 3 according to an embodiment of the present invention.
  • FIG. 8 is a schematic structural diagram of an enlarged initial state of the D portion of FIG. 3 according to an embodiment of the present invention
  • FIG. 9 is a schematic structural diagram of a two-way adjustable camshaft phaser locking mechanism and a hysteresis state of the oil passage according to an embodiment of the present invention
  • FIG. 10 is a schematic structural diagram of a two-way adjustable camshaft phaser locking mechanism and an advance adjustment state of an oil passage according to an embodiment of the present invention
  • FIG. 11 is a schematic diagram of the enlarged lag adjustment structure of the E portion of FIG. 9 according to the embodiment of the present invention
  • FIG. 12 is a schematic diagram of the F-stage enlarged advance adjustment structure of FIG. 10 according to an embodiment of the present invention.
  • cover plate 4. 1 cover oil passage; 4. 2 lock pin hole;
  • an embodiment of the present invention provides a bidirectional adjustable camshaft phaser locking mechanism and an oil circuit, the locking mechanism comprising at least: a rotor 1, a stator 2 Components such as the sprocket 3, the cover 4, the lock pin 5, the lock pin spring 6, the spring bracket 7, the differential pressure valve 8, the return spring 9, the return spring bracket 10, and the associated oil passage; specifically, preferably, The rotor 1 is disposed in the stator 2.
  • the rotor 1 is provided with a lock pin 5 and a spring bracket 7.
  • the lock pin 5 is provided with a lock pin spring 6; the rear part of the stator 2 is provided with a sprocket 3, and the front part of the stator 2 is provided with
  • the cover plate 4 is provided with a cover oil passage 4.1, a lock pin hole 4. 2; a pressure difference valve 8 is mounted on the rotor 1, and the rotor 1 is provided with a return spring bracket. 1 0, the return spring bracket 10 is provided with a card slot, and is positioned by the card slot and the rotor 1; the return spring bracket 10 is mounted with two return springs 9 to prevent the external solenoid valve from working when the engine is abnormally stopped.
  • the rotor 1 includes at least: A chamber oil passage 1. 1 , B chamber oil passage 1. 2, differential pressure valve mounting hole 1. 3, rotor oil passage 1.
  • the lock pin 5 is provided in the lock pin mounting hole 1. 6.
  • the lock pin mounting hole 1. 6 is provided with a lock pin 5,
  • the inner side of the lock pin 5 is provided with an oil groove 1. 5, when the camshaft phaser is returned, the lock pin 5 can be accurately returned;
  • the differential pressure valve mounting hole is 1. 3 is installed with the differential pressure valve 8
  • the differential pressure valve 8 is in communication with the rotor oil passage 1.4.
  • the second oil passage of the A chamber is provided on the rotor 1.
  • the oil passage of the A chamber is provided on the rotor 1. 1.
  • the oil passage of the chamber B is 1. 2.
  • the oil passage of the rotor 1. 4, oil tanks 1. 5 and so on.
  • the rotor 1 and the stator 2 cooperate to form a camshaft phaser advance chamber A and a retard chamber B.
  • the differential pressure valve 8 When the differential pressure valve 8 is in the locked state, the advance chamber A and the A chamber oil passage 1 1 ⁇ 8 ⁇ The first phase, the B-chamber oil channel 1. 2 and the B-chamber oil channel 1. 2; the differential pressure valve 8 at least: the outer casing 8. 1, the left spring 8. 2, the sliding valve 8.3, the right spring 8 4, The right spring 8 is provided on the housing 8.1.
  • the sliding valve 8.3 is provided with a left spring 8. 2, the right spring 8 is provided in the outer casing of the rotor 1.
  • the inner portion of the outer casing 8.1 is located in the outer portion of the outer casing 8.1.
  • the left side of the outer casing 8.1 is compressed, and the left side of the outer casing 8.1 is compressed, and the left side of the outer casing is 8.1, and the left side is compressed.
  • Spring 8.1 The left side of the outer casing 8.1 is compressed, and the left side of the outer casing 8.1 is compressed, and the left side of the outer casing is 8.1, and the left side is compressed.
  • the amount of oil entering the camshaft phaser advance chamber A and the retard chamber B through the external solenoid valve is controlled by the external solenoid valve to control the pressure difference between the advance chamber A and the retard chamber B. 5 ⁇ The spring force of the left spring 8.2 or the right spring 8.4 to overcome the elastic force movement, so that the oil can enter the rotor oil passages 1. 4 to unlock the action; when the advance chamber A pressure is greater than the lag
  • the hole in the pressure difference valve 8 is moved to the rotor oil passage 1.
  • the hole in the outer casing of the differential pressure valve 8 enters the rotor oil passage. 4, then through the cover oil passage 4.1 into the lock pin hole 4. 2 push the lock pin 5 out of the lock pin hole 4.
  • the external solenoid valve enters the engine oil of the camshaft phaser advance chamber A and the retard chamber B by controlling the oil passing through the A chamber oil passages 1. 1 and B chamber oil passages 1.2.
  • the amount is used to control the angle of the phaser rotor 1 to the locked position, so as to achieve accurate return after the external solenoid valve
  • the camshaft phaser In order to prevent the external solenoid valve from working when the engine is abnormally stopped, the camshaft phaser cannot return to the initial position. Since the spring return torque of the two return springs 9 mounted on the phaser return spring bracket 10 is reversed, the phase is When the device is in the locked state, the elastic force reaches an equilibrium state, thereby ensuring that the rotor 1 is returned to the locked state position by the elastic traction of the two return springs 9 under abnormal stopping conditions, and the lock pin spring 6 applies an elastic force to secure the lock pin. 5 ⁇ Accurately return the lock pin hole 4.2.
  • the embodiment of the present invention has the advantages that a plurality of oil passages are disposed on the cover plate 4 and on the rotor 1 to facilitate quick unlocking; and the locking mechanism has a simple structure, compact arrangement, convenient use, and manufacturing cost. low.

Landscapes

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

Abstract

一种双向可调节凸轮轴相位器锁止结构及油路，锁止机构至少包括：转子（1）、定子（2）、链轮（3）、盖板（4）、锁销（5）、锁销弹簧（6）、弹簧支架（7），转子（1）上设置有压差阀。通过在转子（1）上设置一个压差阀，通过外部电磁阀控制提前室和滞后室的压力差来推动压差阀中的滑阀克服左弹簧或者右弹簧的弹力移动，使机油能进入转子油道进行双向可调的相位器顺利解锁，通过设置两个回位弹簧（9），可以实现在异常停机时使凸轮轴相位器能够顺利准确的回到初始位置。

Description

一种双向可调节凸轮轴相位器锁止机构及油路
本申请要求于 2013 年 9 月 23 日提交中国专利局、 申请号为 201310442661.5、发明名称为 "一种双向可调节凸轮轴相位器锁止机构及油路" 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
本发明涉及凸轮轴相位器领域，特别涉及一种双向可调节凸轮轴相位器锁 止机构及油路。 背景技术
随着现代汽车研发技术的不断进步， 用户对汽车的舒适性， 对发动机的动 力性和经济性要求也在不断提高， 随之而来的新技术也层出不穷， 目前可变气 门正时系统（VVT )技术和增压技术已成为主流， 特别是 VVT 系统基本已成为 发动机的标配。 该系统通过配备的控制及执行系统， 对发动机凸轮的相位进行 调节， 从而使得气门开启、 关闭的时间随发动机转速的变化而变化， 以提高充 气效率， 增加发动机功率。
凸轮轴相位器是用来取得凸轮轴相对于曲轴的位置的， 凸轮轴相位对汽油 机的工作很重要，调整发动机的输出曲线， 以确定喷油、 点火时间， 发信号给 电子控制单元（ECU )进行实施。
以往的凸轮轴相位器都是单向调节的相位器， 凸轮轴只能往一个方向转动 来改变气门正时， 随着排放法规的不断加严以及对发动机动力性、 经济性的双 向要求， 单向调节的相位器已无法全面兼顾发动机的所有工况。 特别是怠速工 况下， 因为发动机油压低， 相位器无法工作， 而基础位置又不是最佳相位， 不 能保证最佳性能及排放要求。 而双向可调凸轮轴相位器却能很好全面兼顾， 可 以根据发动机开发要求， 将锁止位置固定在某一特定角度下， 兼顾发动机所有 的运行工况下对相位的要求。但是双向可调相位器的解锁及保证准确回位一直 是个技术难题。 发明内容
为了解决现有技术的问题， 本发明实施例提供了一种双向可调节凸轮轴相 位器锁止机构及油路。便于双向可调的相位器顺利解锁并且在停机时能够顺利 准确的回到初始位置。 所述技术方案如下：
一种双向可调节凸轮轴相位器锁止机构及油路， 该锁止机构至少包括： 转 子、 定子、 链轮、 盖板、 锁销、 锁销弹簧、 弹簧支架， 所述转子上设置有压差 阀。
具体地， 所述转子上设置有回位弹簧支架， 所述回位弹簧支架通过其上设 置的卡槽与所述转子定位。
具体地， 所述回位弹簧支架上安装有两个回位弹簧， 所述回位弹簧另一端 通过螺栓与所述定子固联， 所述两个回位弹簧扭力相反。
具体地， 所述转子至少包括： A室油道、 B室油道、 压差阀安装孔、 转子 油道、 油槽、 锁销安装孔； 所述转子上设置有所述转子油道、 所述压差阀安装 孔、 所述油槽、 所述锁销安装孔， 所述锁销安装孔内设置有所述锁销、 所述弹 簧支架， 所述的锁销一端设有所述油槽， 所述压差阀安装孔内设置有所述压差 阀， 所述压差阀与所述转子油道相通。
具体地， 所述盖板上设置有盖板油道、 锁销孔。
具体地， 所述相关油路至少包括： 所述盖板油道、 所述 A室油道、 所述 B 室油道、 所述转子油道、 所述油槽。
具体地，所述转子与所述定子配合形成凸轮轴相位器提前室 A和滞后室 B， 所述压差阀处于锁止状态时， 所述提前室 A与所述 A室油道相通， 所述滞后室 B与所述 B室油道相通。
具体地， 所述压差阀至少包括： 外壳、 左弹簧、 滑阀、 右弹簧； 所述外壳 安装在所述转子的主叶片安装孔内， 所述外壳内设置有所述滑阀， 所述滑阀上 设置有所述左弹簧、 所述右弹簧。
所述转子向右旋转时， 所述压差阀处于滞后调节状态， 所述滑阀位于所述 外壳内右侧部位， 并压缩所述右弹簧； 所述转子向左旋转时， 所述压差阀处于 提前调节状态， 所述滑阀位于所述外壳内左侧部位， 并压缩所述左弹簧。
具体地， 所述转子设置在所述定子内， 所述转子上设置有所述锁销、 所述 弹簧支架， 所述锁销内设置有所述锁销弹簧； 所述定子后部设置有所述链轮， 所述定子前部设置有所述盖板。 本发明实施例提供的技术方案的有益效果是：
通过在转子上设置一个压差阀，通过外部电磁阀控制提前室和滞后室的压 力差来推动压差阀中的滑阀克服左弹簧或者右弹簧的弹力移动，使机油能进入 转子油道进行解锁动作； 轻松解决双向可调的相位器顺利解锁问题， 通过设置 两个回位弹簧， 可以实现在异常停机时使凸轮轴相位器顺利准确的回到初始位 置。 附图说明
为了更清楚地说明本发明实施例中的技术方案， 下面将对实施例描述中所 需要使用的附图作简单地介绍， 显而易见地， 下面描述中的附图仅仅是本发明 的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下， 还可以根据这些附图获得其他的附图。
图 1是本发明实施例提供的双向可调节凸轮轴相位器锁止机构及油路结构 示意图的主视图；
图 2是本发明实施例提供的图 1的右视图；
图 3是本发明实施例提供的图 1中 A-A剖视双向可调节凸轮轴相位器锁止 机构及油路的锁止状态结构示意图；
图 4是本发明实施例提供的图 1中 B-B剖视图；
图 5是本发明实施例提供的图 3中转子结构示意图的正面视图；
图 6是本发明实施例提供的图 5中 D-D剖视图；
图 7是本发明实施例提供的图 3中盖板结构示意图的正面视图；
图 8是本发明实施例提供的图 3中 D部放大初始状态结构示意图； 图 9是本发明实施例提供的双向可调节凸轮轴相位器锁止机构及油路的滞 后调节状态结构示意图；
图 10是本发明实施例提供的双向可调节凸轮轴相位器锁止机构及油路的 提前调节状态结构示意图；
图 11是本发明实施例提供的图 9中 E部放大滞后调节结构示意图； 图 12是本发明实施例提供的图 10中 F部放大提前调节结构示意图。
图中各符号表示含义如下：
1转子； 1. 1A室油道； 1. 2B室油道； 1. 3压差阀安装孔； 1. 4转子油道； 1. 5油槽； 1. 6锁销安装孔； 2定子
3链轮
4盖板 4. 1盖板油道； 4. 2锁销孔;
5锁销
6锁销弹簧；
7弹簧支架；
8压差阀； 8. 1、 外壳； 8. 2、 弹簧； 8. 3、 滑阀； 8. 4、 弹簧;
9回位弹簧；
10回位弹簧支架；
A提前室；
B滞后室 。 具体实施方式
为使本发明的目的、 技术方案和优点更加清楚， 下面将结合附图对本发明 实施方式作进一步地详细描述。
参见图 1、 图 2、 图 3、 图 7所示， 本发明实施例提供了一种双向可调节凸 轮轴相位器锁止机构及油路， 该锁止机构至少包括： 转子 1、 定子 2、 链轮 3、 盖板 4、 锁销 5、 锁销弹簧 6、 弹簧支架 7、 压差阀 8、 回位弹簧 9、 回位弹簧 支架 10等零部件及相关油路； 具体地， 作为优选， 所述转子 1设置在定子 2 内， 转子 1上设置有锁销 5、 弹簧支架 7， 锁销 5内设置有锁销弹簧 6 ; 定子 2 后部设置有链轮 3， 定子 2前部设置有盖板 4， 所述盖板 4上设置有盖板油道 4. 1、 锁销孔 4. 2 ; 所述转子 1上安装有压差阀 8， 所述转子 1上设置有回位弹 簧支架 1 0， 回位弹簧支架 10上设置有卡槽， 通过卡槽与转子 1定位； 所述回 位弹簧支架 10上安装有两个回位弹簧 9，以防止发动机异常停机时外部电磁阀 不能工作， 而导致凸轮轴相位器无法回到初始位置， 所述回位弹簧 9另一端通 过螺栓与定子 2固联， 两个回位弹簧 9扭力相反； 在相位器处于锁止状态时弹 力达到平衡状态， 能够确保异常停机状况下， 通过两个回位弹簧 9的弹力牵引 以保证转子 1回到锁止状态位置， 所述锁销弹簧 6施加的弹力可以保证锁销 5 能够准确回位至锁销孔 4. 2中。
参见图 3、 图 4、 图 5、 图 6所示， 所述转子 1至少包括： A室油道 1. 1、 B 室油道 1. 2、 压差阀安装孔 1. 3、 转子油道 1. 4、 油槽 1. 5、 锁销安装孔 1. 6 ; 所述转子 1上加工有转子油道 1. 4、压差阀安装孔 1. 3、 油槽 1. 5、 锁销安装孔 1. 6， 锁销安装孔 1. 6内设置有锁销 5、 弹簧支架 7， 所述的锁销 5—端设有油 槽 1. 5， 在凸轮轴相位器回位时能够保证锁销 5准确回位； 压差阀安装孔 1. 3 内安装压差阀 8， 压差阀 8与转子油道 1. 4相通。
所述相关油路至少包括： 在盖板 4上设置的盖板油道 4. 1 ; 在转子 1上设 置的 A室油道 1. 1、 B室油道 1. 2、 转子油道 1. 4、 油槽 1. 5等。
同时参见图 3、 图 8所示， 所述转子 1与定子 2配合形成凸轮轴相位器提 前室 A和滞后室 B，压差阀 8处于锁止状态时，提前室 A与 A室油道 1. 1相通， B室油道 1. 2与 B室油道 1. 2相通； 所述压差阀 8至少包括： 外壳 8. 1、 左弹 簧 8. 2、滑阀 8. 3、右弹簧 8. 4 ;所述外壳 8. 1安装在转子 1的主叶片安装孔内， 外壳 8. 1内设置有滑阀 8. 3， 滑阀 8. 3上设置有左弹簧 8. 2、 右弹簧 8. 4， 压差 阀 8处于初始状态时， 滑阀 8. 3位于外壳 8. 1内中间部位。
同时参见图 9、 图 11所示， 所述转子 1向右旋转时， 所述压差阀 8处于滞 后调节状态， 使滑阀 8. 3位于外壳 8. 1内右侧部位， 并压缩右弹簧 8. 4。
同时参见图 1 0、 图 12所示， 所述转子 1向左旋转时， 所述压差阀 8处于 提前调节状态， 使滑阀 8. 3位于外壳 8. 1内左侧部位， 并压缩左弹簧 8. 1。
本发明实施例的工作原理：
通过外部电磁阀控制机油经 A室油道 1. 1和 B室油道 1. 2进入凸轮轴相位 器提前室 A和滞后室 B的机油量，从而控制提前室 A和滞后室 B的压力差来推 动压差阀 8中的滑阀 8. 3克服左弹簧 8. 2或者右弹簧 8. 4的弹力移动，使机油 能进入转子油道 1. 4进行解锁动作； 当提前室 A压力大于滞后室 B时， 压差阀 8内的滑阀 8. 3向滞后室 B方向移动， 处于滞后调节状态， 机油从 A室通过压 差阀 8的外壳 8. 1上的孔进入转子油道 1. 4，再经盖板油道 4. 1进入锁销孔 4. 2 推动锁销 5脱离锁销孔 4. 2， 达到解锁的目的， 此时凸轮相位器滞后调节； 当 提前室 A室压力小于滞后室 B室时，压差阀 8内的滑阀 8. 3向提前室 A方向移 动， 处于提前调节状态， 机油从滞后室 B通过压差阀 8的外壳 8. 1上的孔进入 转子油道 1. 4， 再经盖板油道 4. 1进入锁销孔 4. 2推动锁销 5脱离锁销孔 4. 2 , 达到解锁的目的， 此时凸轮相位器提前调节。
当凸轮轴相位器工作后需要回到初始位置时， 外部电磁阀通过控制机油经 A室油道 1. 1和 B室油道 1. 2进入凸轮轴相位器提前室 A和滞后室 B的机油量 来控制相位器转子 1转动到锁止位置角度，从而达到准确回位后外部电磁阀复 位， 机油通过油槽 1. 5进入锁销安装孔 1. 6给锁销 5施加锁止压力， 与锁销弹 簧 6—起作用来保证锁销 5能够顺利进入盖板 4上的锁销孔 4. 2中，从而达到 解锁的目的。
为防止发动机异常停机时外部电磁阀不能工作， 而导致凸轮轴相位器无法 回到初始位置， 由于在相位器回位弹簧支架 10上安装的两个回位弹簧 9的弹 簧扭力相反， 所以在相位器处于锁止状态时弹力达到平衡状态， 从而能够确保 异常停机状况下， 通过两个回位弹簧 9的弹力牵引来保证转子 1回到锁止状态 位置， 锁销弹簧 6施加弹力来保证锁销 5能够准确回位锁销孔 4. 2中。
此外， 本发明实施例还具有的优点， 由于在盖板 4上和在转子 1上设置有 多道油路， 便于实现迅速解锁； 而且该锁止机构结构简单， 布置紧凑， 使用方 便， 制作成本低。
以上所述仅为本发明的较佳实施例， 并不用以限制本发明， 凡在本发明的 精神和原则之内， 所作的任何修改、 等同替换、 改进等， 均应包含在本发明的 保护范围之内。

Claims

权 利 要 求 书
1、 一种双向可调节凸轮轴相位器锁止机构及油路， 该锁止机构至少包括： 转子 (1)、 定子 (2)、 链轮 (3)、 盖板 (4)、 锁销 (5)、 锁销弹簧 (6)、 弹簧支架 (7)， 其特征在于， 所述转子（1)上设置有压差阀（8)。
2、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述转子（1)上设置有回位弹簧支架（1 0)， 所述回位弹簧支架（10)通过 其上设置的卡槽与所述转子（1)定位。
3、 根据权利要求 2所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述回位弹簧支架（10)上安装有两个回位弹簧（9)， 所述回位弹簧（9) 另一端通过螺栓与所述定子（2)固联， 所述两个回位弹簧（9)扭力相反。 4、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述转子（1)至少包括： A 室油道（1. 1)、 B 室油道（1. 2)、 压差阀安装 孔（1. 3)、 转子油道（1. 4)、 油槽（1. 5)、 锁销安装孔（1. 6) ; 所述转子（1)上设置 有所述转子油道（1. 4)、 所述压差阀安装孔（1. 3)、 所述油槽（1. 5)、 所述锁销安 装孔（1. 6)， 所述锁销安装孔（1. 6)内设置有所述锁销（5)、 所述弹簧支架（7)， 所述的锁销（5)—端设有所述油槽（1. 5)， 所述压差阀安装孔（1. 3)内设置有所述 压差阀（8)， 所述压差阀（8)与所述转子油道（1.
4)相通。
5、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述盖板（4)上设置有盖板油道（4. 1)、 锁销孔（4. 2) 。
6、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述相关油路至少包括： 所述盖板油道（4. 1)、 所述 A 室油道（1. 1)、 所述 B室油道（1. 2)、 所述转子油道（1. 4)、 所述油槽（1. 5) 。
7、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于，所述转子（1)与所述定子（2)配合形成凸轮轴相位器提前室 A和滞后室 B， 所述压差阀（8)处于锁止状态时， 所述提前室 A与所述 A室油道（1. 1)相通， 所 述滞后室 B与所述 B室油道（1. 2)相通。
8、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述压差阀（8)至少包括： 外壳（8. 1)、 左弹簧（8. 2)、 滑阀（8. 3)、 右 弹簧（8. 4) ; 所述外壳（8. 1)安装在所述转子（1)的主叶片安装孔内， 所述外壳 (8. 1)内设置有所述滑阀（8. 3)， 所述滑阀（8. 3)上设置有所述左弹簧（8. 2)、 所 述右弹簧（8. 4)。
9、 根据权利要求 1所述的双向可调节凸轮轴相位器锁止机构及油路， 其特 征在于， 所述转子（1)向右旋转时， 所述压差阀（8)处于滞后调节状态， 所述滑 阀（8. 3)位于所述外壳（8. 1)内右侧部位，并压缩所述右弹簧（8. 4)；所述转子（1) 向左旋转时， 所述压差阀（8)处于提前调节状态， 所述滑阀（8. 3)位于所述外壳 (8. 1)内左侧部位， 并压缩所述左弹簧 (8. 2) 。
10、 根据权利要求 1 所述的双向可调节凸轮轴相位器锁止机构及油路， 其 特征在于， 所述转子（1)设置在所述定子（2)内， 所述转子（1)上设置有所述锁销 (5)、 所述弹簧支架（7)， 所述锁销（5)内设置有所述锁销弹簧（6) ; 所述定子（2) 后部设置有所述链轮（3)， 所述定子（2)前部设置有所述盖板（4) 。
PCT/CN2014/086004 2013-09-23 2014-09-05 一种双向可调节凸轮轴相位器锁止机构及油路 WO2015039571A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201310442661.5A CN103498710B (zh) 2013-09-23 2013-09-23 一种双向可调节凸轮轴相位器锁止机构及油路
CN201310442661.5 2013-09-23

Publications (1)

Publication Number Publication Date
WO2015039571A1 true WO2015039571A1 (zh) 2015-03-26

Family

ID=49863957

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/086004 WO2015039571A1 (zh) 2013-09-23 2014-09-05 一种双向可调节凸轮轴相位器锁止机构及油路

Country Status (2)

Country Link
CN (1) CN103498710B (zh)
WO (1) WO2015039571A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205162A1 (de) * 2015-03-23 2016-03-31 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102017112471B3 (de) 2017-06-07 2018-09-13 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103498710B (zh) * 2013-09-23 2016-03-16 奇瑞汽车股份有限公司 一种双向可调节凸轮轴相位器锁止机构及油路
CN104747246B (zh) * 2015-03-31 2017-12-12 安徽江淮汽车集团股份有限公司 一种进气vvt油路
CN108593031A (zh) * 2018-06-08 2018-09-28 陕西鑫联仪器仪表有限公司 转子及包含其的容积式流量计
CN111102031B (zh) * 2018-10-26 2023-08-22 舍弗勒技术股份两合公司 凸轮轴相位器及其工作方法
DE102021130428B3 (de) 2021-11-22 2023-03-23 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Steuerpin
DE102023001117A1 (de) 2023-03-22 2024-09-26 Mercedes-Benz Group AG Nockenwellensteller für eine Verbrennungskraftmaschine sowie Verbrennungskraftmaschine für ein Kraftfahrzeug

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10033229A1 (de) * 2000-07-07 2002-01-17 Porsche Ag Nockenwelle zur Betätigung von Ventilen einer Brennkraftmaschine
JP2006300018A (ja) * 2005-04-25 2006-11-02 Mazda Motor Corp エンジンの可変バルブタイミング装置
CN201321880Y (zh) * 2008-11-26 2009-10-07 绵阳新晨动力机械有限公司 一种发动机可变凸轮轴相位调节器
CN102052112A (zh) * 2009-10-28 2011-05-11 通用汽车环球科技运作公司 包括带有双锁定位置的凸轮相位器的发动机组件
US20130000576A1 (en) * 2011-07-03 2013-01-03 Denso Corporation Valve characteristics control apparatus
CN103498710A (zh) * 2013-09-23 2014-01-08 奇瑞汽车股份有限公司 一种双向可调节凸轮轴相位器锁止机构及油路

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000337112A (ja) * 1999-05-31 2000-12-05 Unisia Jecs Corp 内燃機関のバルブタイミング変更装置
JP2001289013A (ja) * 2000-04-04 2001-10-19 Denso Corp 可変バルブタイミング装置
JP4161880B2 (ja) * 2003-11-12 2008-10-08 トヨタ自動車株式会社 内燃機関のバルブタイミング制御装置
CN102367749B (zh) * 2011-10-18 2013-03-27 奇瑞汽车股份有限公司 一种可变气门正时装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10033229A1 (de) * 2000-07-07 2002-01-17 Porsche Ag Nockenwelle zur Betätigung von Ventilen einer Brennkraftmaschine
JP2006300018A (ja) * 2005-04-25 2006-11-02 Mazda Motor Corp エンジンの可変バルブタイミング装置
CN201321880Y (zh) * 2008-11-26 2009-10-07 绵阳新晨动力机械有限公司 一种发动机可变凸轮轴相位调节器
CN102052112A (zh) * 2009-10-28 2011-05-11 通用汽车环球科技运作公司 包括带有双锁定位置的凸轮相位器的发动机组件
US20130000576A1 (en) * 2011-07-03 2013-01-03 Denso Corporation Valve characteristics control apparatus
CN103498710A (zh) * 2013-09-23 2014-01-08 奇瑞汽车股份有限公司 一种双向可调节凸轮轴相位器锁止机构及油路

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205162A1 (de) * 2015-03-23 2016-03-31 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102017112471B3 (de) 2017-06-07 2018-09-13 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Also Published As

Publication number Publication date
CN103498710A (zh) 2014-01-08
CN103498710B (zh) 2016-03-16

Similar Documents

Publication Publication Date Title
WO2015039571A1 (zh) 一种双向可调节凸轮轴相位器锁止机构及油路
JP6279127B2 (ja) 油圧により係合されるロックピンを備えた可変カムシャフトタイミング機構
US9464542B2 (en) Variable valve timing apparatus for internal combustion engine
WO2010109971A1 (ja) 弁開閉時期制御装置
US20070277757A1 (en) Vane-type cam phaser having bias spring system to assist intermediate position pin locking
US9010289B2 (en) Control device for hydraulic variable valve timing mechanism
CN103939165B (zh) 内燃机的阀门正时控制装置及其组装方法
JP2010209780A (ja) 内燃機関の可変動弁機構
JP2014185520A (ja) 内燃機関のバルブタイミング制御システム及び内燃機関のバルブタイミング制御装置のロック解除機構
CN103306769A (zh) 可变气门正时控制装置
KR101755466B1 (ko) 연속 가변 밸브 타이밍 장치의 림프홈 제어방법
US8606490B2 (en) Device and method for controlling internal combustion engine
US9115651B2 (en) Method of controlling CVVT according to current control for oil control valve
US9140197B2 (en) Valve timing control apparatus
CN101994535A (zh) 一种连续可变气门正时相位器
US20140069363A1 (en) Variable valve timing device
US9206712B2 (en) Variable valve timing device
JP3761018B2 (ja) 内燃機関の制御装置
JP4035770B2 (ja) 弁開閉時期制御装置
CN203640796U (zh) 一种双锁销中置式中央锁止相位器
CN103670571A (zh) 一种双锁销中置式中央锁止相位器
JP6264845B2 (ja) 弁開閉時期制御装置
JP2008303754A (ja) 内燃機関の制御装置
WO2013115174A1 (ja) 内燃機関の可変バルブタイミング制御装置
KR101620273B1 (ko) Cvvt의 중간위상 조정장치

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14846530

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205 DATED 09/09/2016)

122 Ep: pct application non-entry in european phase

Ref document number: 14846530

Country of ref document: EP

Kind code of ref document: A1