WO2021238229A1 - 液压挺柱 - Google Patents

液压挺柱 Download PDF

Info

Publication number
WO2021238229A1
WO2021238229A1 PCT/CN2021/070619 CN2021070619W WO2021238229A1 WO 2021238229 A1 WO2021238229 A1 WO 2021238229A1 CN 2021070619 W CN2021070619 W CN 2021070619W WO 2021238229 A1 WO2021238229 A1 WO 2021238229A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure relief
hydraulic
valve
spring
tappet
Prior art date
Application number
PCT/CN2021/070619
Other languages
English (en)
French (fr)
Inventor
王立峰
王秀强
Original Assignee
潍坊力创电子科技有限公司
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 潍坊力创电子科技有限公司 filed Critical 潍坊力创电子科技有限公司
Publication of WO2021238229A1 publication Critical patent/WO2021238229A1/zh

Links

Images

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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets

Definitions

  • the invention relates to the technical field of an engine valve mechanism, in particular to a hydraulic tappet.
  • the function of the tappet in the engine valve train is to transmit the thrust of the camshaft to the push rod (or valve stem), and to withstand the lateral force exerted by the camshaft when it rotates.
  • the tappet is equipped with an adjusting screw on its top to adjust the valve clearance.
  • the reserved valve clearance can solve the problem of lax valve closing caused by thermal expansion, but due to the existence of the valve clearance, the valve mechanism will cause shock and noise during operation. In order to solve this contradiction, some engines use hydraulic tappets.
  • a well-known hydraulic tappet 40A is installed at one end of the rocker arm 30.
  • the tappet body 42A is fixedly connected to the rocker arm and communicates with the oil circuit through an oil port 421A.
  • An oil drain gap 46A is provided between the outer circumferential surface of the cylinder 42A and the inner circumferential surface of the plunger 41A.
  • the engine oil supplies oil to the hydraulic chamber 43A through the oil inlet 421A and the one-way valve 44A, and slowly drains the oil through the oil drain gap 46A; the plunger Under the combined action of the oil pressure and the return spring 45A, 41A moves downward relative to the tappet body 42A, compresses the valve 60 and eliminates the valve clearance, but it is not enough to overcome the elastic force of the valve spring 50, and the valve 60 is still closed.
  • the cam 10 pushes the tappet 42A through the push rod 20 and the rocker arm 30, the oil pressure of the hydraulic chamber 43A rises, and the one-way valve 44A closes and pushes The plunger 41A descends, and the plunger 41A pushes the valve 60 to open.
  • the high-pressure oil drains a part of the oil through the oil drain gap 46A.
  • the one-way valve 44A opens to replenish the oil in the hydraulic chamber 43A. . Repeat the above actions in the loop.
  • the working length of the hydraulic tappet is continuously and automatically adjusted, so that the valve mechanism maintains normal operation and the valve adjustment mechanism has no gap, which reduces the impact and noise between the parts.
  • the present invention provides a hydraulic tappet to solve the problem of relative movement between the tappet body and the plunger when the cam is working and the valve is opened, which affects the valve opening stroke.
  • a hydraulic tappet includes a tappet body and a plunger.
  • One end of the tappet body is provided with an oil inlet and the other end is open.
  • the plunger extends from the open end of the tappet body and connects with
  • the tappet body forms a hydraulic chamber, the inner side of the oil inlet is provided with a one-way valve that can communicate the engine oil circuit with the hydraulic chamber under the action of the engine oil pressure, and the hydraulic chamber is provided with a valve After the opening pressure is eliminated, a return spring used to return the plunger relative to the tappet body;
  • a pressure relief passage communicating with the hydraulic chamber is opened, the pressure relief passage is provided with a sealing cone, a pressure relief valve core and a pressure relief spring are arranged in the pressure relief passage, and the pressure is not affected by the valve opening pressure.
  • the pressure relief valve core is pushed away from the sealing cone by the pressure relief spring to form an oil leakage gap.
  • the pressure relief valve core overcomes the elastic force of the pressure relief spring and interacts with the sealing cone. The surface contact realizes the sealing of the hydraulic chamber.
  • the pressure relief valve core includes a valve ball.
  • the pressure relief spring is arranged in a pressure relief channel communicating with the small head end of the sealing cone, and abuts between the pressure relief valve core and a step surface of the pressure relief channel.
  • a spring seat is movably arranged in the hydraulic chamber, the spring seat is provided with a through hole, the through hole communicates with the hydraulic chamber and the pressure relief channel, and the return spring is arranged in the spring seat .
  • one end of the spring seat abuts against the other end of the plunger and there is a gap between the corresponding end surface of the tappet body.
  • the one-way valve includes a one-way valve core, a limit spring and a one-way valve seat, a sealing cone is provided on the inner side of the oil inlet, and the limit spring is arranged in the one-way valve seat,
  • the one-way valve seat is installed on the tappet body of the hydraulic chamber, and the limit spring presses the one-way valve core against the sealing cone of the oil inlet.
  • the return spring is clamped between the one-way valve seat and the spring seat.
  • the pressure relief channel communicates with the oil pan.
  • the hydraulic tappet is arranged on any transmission component between the cam of the engine valve mechanism and the valve, and the oil inlet of the tappet body is in communication with the engine oil circuit.
  • the hydraulic tappet is arranged on the rocker arm of the engine valve mechanism, and the oil inlet is communicated with the engine oil circuit arranged on the rocker arm.
  • the working length of the hydraulic tappet of the present invention can be extended or shortened, and can automatically compensate for the thermal expansion gap of the parts of the valve train.
  • the working length of the hydraulic tappet is almost unchanged (only slightly shortened in the initial stage of cam operation, and the amount of shortening is controllable), and the valve opening stroke is more "precise".
  • the hydraulic tappet disclosed in the present invention can be installed on any transmission component between the cam of the engine valve mechanism and the valve, preferably on the rocker arm.
  • Figure 1 is a reference diagram of a known hydraulic tappet in use
  • Figure 2 is a cross-sectional view of the structure of the hydraulic tappet in Figure 1;
  • Figure 3 is a structural cross-sectional view of an embodiment of a hydraulic tappet of the present invention.
  • a hydraulic tappet 40B is arranged on the rocker arm of the engine valve mechanism (see the position of the hydraulic tappet 40A in FIG. 1).
  • One end of the tappet body 42B is provided with an oil inlet 421B and the other end is open.
  • the plunger 41B extends from the open end of the tappet body 42B and forms a hydraulic chamber 43B with the tappet body 42B.
  • the oil inlet 421B is connected to
  • the engine oil circuit (not shown in the figure) on the rocker arm 30 is connected, and a check valve 44B is provided inside the oil inlet 421B. Under the action of the engine oil pressure, the check valve 44B can connect the engine oil circuit with the hydraulic pressure.
  • the cavity 43B communicates.
  • the specific structure of the one-way valve 44B includes a one-way valve core 442B, a limit spring 443B, and a one-way valve seat 441B.
  • the inner side of the oil inlet 421B is provided with a sealing cone, and the limit spring 443B is provided on the one-way valve seat 441B.
  • the one-way valve seat 441B is provided with an oil through hole and is installed on the tappet body 42B of the hydraulic chamber.
  • the limit spring 443B presses the one-way valve core 442B against the sealing cone of the oil inlet 421.
  • the one-way valve core 442B is preferably a valve ball, such as a steel ball.
  • the hydraulic chamber 43B is provided with a return spring 45B for returning the plunger 41B relative to the tappet body 42B after the valve opening pressure is eliminated.
  • a spring seat 49B is movably arranged in the hydraulic chamber 43B.
  • the spring seat 49B is provided with a through hole 491B.
  • the through hole 491B communicates with the hydraulic chamber 43B and the pressure relief channel 411B.
  • the return spring 45B is arranged in the spring seat 49B and clamped on the one-way valve. Between the seat 441B and the spring seat 45B. Under the action of the elastic force of the return spring 45B, one end of the spring seat 49B abuts against the plunger 41B and the other end has a gap S between the corresponding end surface of the tappet body 42B.
  • the design clearance S is a suitable value (refer to the design for the size of the cold valve clearance of the traditional engine).
  • the outer peripheral surface of the plunger 41B is in sliding fit with the inner peripheral surface of the tappet body 42B, and the fit gap ensures the smooth sliding and sealing of the plunger, and the oil must not leak from there.
  • the plunger 41B is provided with a pressure relief channel 411B communicating with the hydraulic chamber 43B, and the pressure relief channel 411B communicates with the oil pan 70.
  • the pressure relief channel 411B is provided with a sealing cone 46B, and the pressure relief channel 411B is provided with a pressure relief valve core 47B and a pressure relief spring 48B.
  • the pressure relief valve core 47B includes a valve ball, such as a steel ball.
  • the elastic force of the pressure relief spring 48B should be able to ensure that when the engine oil reaches the maximum value, the pressure relief valve core 47B can still be separated from the sealing cone 46B to form an oil leakage gap, and when the cam working hydraulic chamber 43B forms a high pressure, the pressure relief valve core 47B The sealing cone 46B can be sealed quickly.
  • the pressure relief spring 48B is arranged in the pressure relief passage 411B communicating with the small end of the sealing cone 46B, and abuts between the pressure relief valve core 47B and a step surface of the pressure relief passage.
  • the pressure relief valve core 47B When not affected by the valve opening pressure, the pressure relief valve core 47B is pushed away from the sealing cone 46B by the pressure relief spring 48B; when subjected to the valve opening pressure, the pressure relief valve core 47B overcomes the elastic force of the pressure relief spring 48B and interacts with the sealing cone The contact of the surface 46B realizes the sealing of the hydraulic chamber 43B.
  • the hydraulic tappet 40B is arranged on the rocker arm, but the arrangement position of the hydraulic tappet 40B is not limited to this, and it can be arranged on any transmission component between the cam of the engine valve mechanism and the valve.
  • the present invention is not limited to the above-mentioned embodiments, and all improvements made based on the concept, principle, structure and method of the present invention will fall within the protection scope of the present invention.
  • An oil leakage gap can be formed between the pressure relief valve core and the sealing cone of the present invention.
  • the engine oil can enter the hydraulic chamber through the oil inlet and the one-way valve, and slowly leak through the oil leakage gap. Therefore, the working length of the hydraulic tappet of the present invention can be extended or shortened, and can automatically compensate for the thermal expansion gap of the parts of the valve train. Compared with the traditional hydraulic tappet, when the cam is working, the working length of the hydraulic tappet is almost unchanged (only slightly shortened in the initial stage of cam operation, and the amount of shortening is controllable), and the valve opening stroke is more "precise".

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

一种液压挺柱（40A），包括：其挺柱体（42A）的一端开设有进油口（421B），另一端敞口，其柱塞（41A）从挺柱体（42A）的敞口端伸入并与挺柱体（42A）形成液压腔（43A），进油口的内侧设置有在发动机机油压力作用下可将发动机机油油路与液压腔（43A）连通的单向阀，液压腔内设置有回位弹簧（45A）；柱塞（41A）的外周面与挺柱体（42A）的内周面滑动密封配合，柱塞（41A）开设有与液压腔（43A）相通的泄压通道，泄压通道内设置有泄压阀芯（47B）和泄压弹簧（48B），在不受气门开启压力作用时泄压阀芯（47B）被泄压弹簧（48B）顶离密封锥面形成漏油间隙，在受到气门开启压力作用时泄压阀芯（47B）克服泄压弹簧的弹力并与密封锥面（46B）接触实现密封。在凸轮工作、气门开启时，挺柱体与柱塞的相对位置不会发生变化，保证了发动机的性能。

Description

液压挺柱
声明
本发明要求下述专利申请的优先权：
发明名称：液压挺柱，申请日：2020年5月26日，申请号：CN202010460474.X。
技术领域
本发明涉及发动机配气机构技术领域，尤其涉及一种液压挺柱。
背景技术
挺柱在发动机配气机构中所起的作用是将凸轮轴的推力传给推杆(或气门杆)，并承受凸轮轴旋转时所施加的侧向力。挺柱在其顶部装有调节螺钉，用来调节气门间隙。预留的气门间隙可以解决由于热膨胀造成的气门关闭不严问题，但是由于气门间隙的存在，配气机构在工作时会造成冲击并产生噪声。为了解决这一矛盾，有的发动机上采用了液压挺柱。
一种公知的液压挺柱40A，如图1和图2共同所示，其安装于摇臂30的一端，挺柱体42A与摇臂固定连接并通过油口421A与机油油路相连通，挺柱体42A的外圆周面与柱塞41A的内圆周面之间设置有泄油间隙46A。
当发动机气门60处在关闭时刻时(凸轮10没有转到工作面)，发动机机油通过进油口421A、单向阀44A为液压腔43A供油，并通过泄油间隙46A缓慢泄油；柱塞41A在机油压力和回位弹簧45A的共同作用下，相对于挺柱体42A向下运动，压紧气门60，消除气门间隙，但不足以克服气门弹簧50的弹力，气门60仍关闭。
当发动机工作在气门60开启时刻时(凸轮10转到工作面)，凸轮10通过推杆20、摇臂30推动挺柱体42A运动，液压腔43A机油压力升高，单向阀44A关闭，推动柱塞41A下行，柱塞41A推动气门60开启。在柱塞41A下行的过程中，由于液压腔43A内机油压力很高，高压机油通过泄油间隙46A泄流掉一部分机油，气门开启过程结束后，单向阀44A开启，为液压腔43A补充机油。重复循环以上动作。通过液压腔内的液压油的泄漏及补充，不断自动调节液压挺柱的工作长度，从而使配气机构保持正常工作而气门调节机构又没有间隙存在，减少了零部件之间的冲击和噪声。
但上述液压挺柱存在以下问题：
1)泄油间隙要求高，加工难度较大；
2)由于泄油间隙的存在，在凸轮工作、气门开启时，挺柱体与柱塞存在相对移动，影 响气门的开启行程，特别是在发动机速度变化时，不同的转速泄油量不同，造成挺柱体与柱塞的相对移动量不同，影响发动机性能。在大型发动机上，由于气门开启力较大，影响更为明显。
发明内容
针对现有技术的上述不足，本发明提供一种液压挺柱，以解决在凸轮工作、气门开启时，挺柱体与柱塞存在相对移动，影响气门开启行程的问题。
为解决上述技术问题，本发明采用的技术方案是：
一种液压挺柱，包括：挺柱体和柱塞，所述挺柱体的一端开设有进油口另一端敞口，所述柱塞从所述挺柱体的敞口端伸入并与所述挺柱体形成液压腔，所述进油口的内侧设置有在发动机机油压力作用下可将发动机机油油路与所述液压腔连通的单向阀，所述液压腔内设置有在气门开启压力消除后用于使所述柱塞相对于所述挺柱体回位的回位弹簧；所述柱塞的外周面与所述挺柱体的内周面滑动密封配合，所述柱塞开设有与所述液压腔相通的泄压通道，所述泄压通道设置有密封锥面，所述泄压通道内设置有泄压阀芯和泄压弹簧，在不受气门开启压力作用时所述泄压阀芯被所述泄压弹簧顶离所述密封锥面形成漏油间隙，在受到气门开启压力作用时所述泄压阀芯克服所述泄压弹簧的弹力并与所述密封锥面接触实现所述液压腔的密封。
其中，所述泄压阀芯包括一阀球。
其中，所述泄压弹簧设置在与所述密封锥面的小头端相通的泄压通道内，并顶靠在所述泄压阀芯与所述泄压通道的一个台阶面之间。
其中，所述液压腔内活动设置有弹簧座，所述弹簧座开设有通孔，所述通孔连通所述液压腔和所述泄压通道，所述回位弹簧设置于所述弹簧座内。
其中，所述弹簧座在所述回位弹簧作用下一端顶靠于所述柱塞另一端与所述挺柱体的相应端面间具有间隙。
其中，所述单向阀包括单向阀芯、限位弹簧和单向阀座，所述进油口的内侧设置有密封锥面，所述限位弹簧设置于所述单向阀座内，所述单向阀座安装于所述液压腔的挺柱体上，所述限位弹簧将所述单向阀芯顶靠于所述进油口的密封锥面。
其中，所述回位弹簧夹压于所述单向阀座与所述弹簧座之间。
其中，所述泄压通道与油底壳相通。
其中，所述液压挺柱设置于发动机配气机构的凸轮到气门间的任何一个传动部件上，所 述挺柱体的进油口与发动机机油油路连通。
其中，所述液压挺柱设置于所述发动机配气机构的摇臂上，所述进油口与设置于所述摇臂上的发动机机油油路连通。
本发明采用上述技术方案后，所达到的技术效果是：
当凸轮不工作时，由于此时液压柱塞不受气门开启压力作用，泄压阀芯被泄压弹簧顶离所述泄压通道的密封锥面，发动机机油通过进油口、单向阀进入液压腔，同时通过泄压阀芯与密封锥面的间隙缓慢泄漏，这时，液压挺柱在发动机机油压力及回位弹簧的共同作用下，其挺柱体和柱塞分别(直接或间接)贴近凸轮和气门，消除了气门间隙。当凸轮工作时，液压腔机油压力升高，泄压阀芯克服泄压弹簧的弹力，液压腔成为封闭的腔，无论发动机转速如何变化，挺柱体与柱塞的相对位置不会发生变化，保证了发动机的性能。
由于本发明的泄压阀芯与密封锥面之间可以形成漏油间隙，在凸轮没有工作时，发动机的机油可以通过进油口和单向阀进入液压腔，并通过该漏油间隙缓慢泄漏，因而本发明液压挺柱的工作长度既可伸长，也可缩短，可以自动补偿配气机构部件的热膨胀间隙。相对于传统的液压挺柱，在凸轮工作时，液压挺柱的工作长度几乎没有变化(仅仅在凸轮工作的初始阶段微量缩短，缩短量可控)，气门开启行程更“精确”。
本发明所揭示的液压挺柱，可以安装在发动机配气机构的凸轮到气门间的任何一个传动部件上，优选设置在摇臂上。
附图说明
图1是一种公知的液压挺柱的使用状态参考图；
图2是图1中液压挺柱的结构剖视图；
图3是本发明一种液压挺柱实施例的结构剖视图；
图中：10-凸轮，20-推杆，30-摇臂,40A-液压挺柱，41A-柱塞，42A-挺柱体，421A-进油口，43A-液压腔，44A-单向阀，45A-回位弹簧，46A-泄油间隙，40B-液压挺柱，41B-柱塞，411B-泄油孔，42B-挺柱体，421B-进油口，43B-液压腔，44B-单向阀，45B-回位弹簧，46B-密封锥面，47B-泄压阀芯，48B-泄压弹簧，49B-弹簧座，491B-通孔，50-气门弹簧，60-气门,70-油底壳，S-间隙。
具体实施方式
下面结合附图和实施例对本发明进一步说明。
如图3所示并参考图1，一种液压挺柱40B，设置于发动机配气机构的摇臂上(参见图1 中液压挺柱40A的位置)。挺柱体42B的一端开设有进油口421B、另一端敞口，柱塞41B从挺柱体42B的敞口端伸入并与挺柱体42B形成液压腔43B，进油口421B与设置于摇臂30上的发动机机油油路(图中未示出)连通，进油口421B的内侧设置有单向阀44B，在发动机机油压力作用下，单向阀44B可将发动机机油油路与液压腔43B连通。单向阀44B的具体结构是，包括单向阀芯442B、限位弹簧443B和单向阀座441B，进油口421B的内侧设置有密封锥面，限位弹簧443B设置于单向阀座441B内，单向阀座441B开设有通油孔并安装于液压腔的挺柱体42B上，限位弹簧443B将单向阀芯442B顶靠于进油口421的密封锥面。单向阀芯442B优选的是一个阀球，例如钢球。
液压腔43B内设置有在气门开启压力消除后用于使柱塞41B相对于挺柱体42B回位的回位弹簧45B。液压腔43B内活动设置有弹簧座49B，弹簧座49B开设有通孔491B，通孔491B连通液压腔43B和泄压通道411B，回位弹簧45B设置于弹簧座49B内并夹压于单向阀座441B与弹簧座45B之间。在回位弹簧45B弹力的作用下,弹簧座49B一端顶靠于柱塞41B另一端与挺柱体42B的相应端面间具有间隙S。设计间隙S为合适的值(可参考设计为传统发动机冷态气门间隙的大小)，当发动机处于启动状态发动机机油压力没有建立时，保证气门机构的正常工作。
柱塞41B的外周面与挺柱体42B的内周面滑动配合，其配合间隙保证柱塞的顺利滑动且密封，机油不得从该处泄漏。柱塞41B开设有与液压腔43B相通的泄压通道411B，泄压通道411B与油底壳70相通。泄压通道411B设置有密封锥面46B，泄压通道411B内设置有泄压阀芯47B和泄压弹簧48B，优选的，泄压阀芯47B包括一阀球，例如钢球。泄压弹簧48B的弹力应能保证在发动机的机油达到最高值时，泄压阀芯47B依然能够脱离密封锥面46B形成漏油间隙，且凸轮工作液压腔43B形成高压时，泄压阀芯47B能够迅速将密封锥面46B密封。泄压弹簧48B设置在与密封锥面46B的小头端相通的泄压通道411B内，并顶靠在泄压阀芯47B与泄压通道的一个台阶面之间。在不受气门开启压力作用时，泄压阀芯47B被泄压弹簧48B顶离密封锥面46B；在受到气门开启压力作用时，泄压阀芯47B克服泄压弹簧48B的弹力并与密封锥面46B接触实现液压腔43B的密封。
上述实施例的工作原理及达到的技术效果是：
当凸轮10不工作(凸轮10没有转到工作面)时，由于此时液压挺柱不受气门开启压力作用，泄压阀芯47B被泄压弹簧48B顶离泄压通道的密封锥面46B形成漏油间隙，发动机机油通过进油口421B、单向阀44B进入液压腔43B，并通过泄压阀芯47B与密封锥面46B的间 隙缓慢泄漏，这时，液压挺柱在发动机机油压力及回位弹簧45B的共同作用下，其挺柱体42B和柱塞41B分别(直接或间接)贴近凸轮10和气门60，消除了气门间隙，且可伸缩自动补偿各部件由于热胀冷缩等的影响。当凸轮工作(凸轮10转到工作面)时，液压腔43B机油压力升高，泄压阀芯47B克服泄压弹簧48B的弹力，液压腔43B成为封闭的腔，相对于传统的液压挺柱(工作长度缩短)，无论发动机转速如何变化，本发明的挺柱体42B与柱塞41B的相对位置不会发生变化，保证了发动机的性能。
本实施例中，液压挺柱40B设置于摇臂，但液压挺柱40B的设置位置不局限于此，其可以设置于发动机配气机构的凸轮到气门间的任何一个传动部件上。
本发明不局限于上述实施例，一切基于本发明的构思、原理、结构及方法所做出的种种改进，都将落入本发明的保护范围之内。
工业实用性
本发明的泄压阀芯与密封锥面之间可以形成漏油间隙，在凸轮没有工作时，发动机的机油可以通过进油口和单向阀进入液压腔，并通过该漏油间隙缓慢泄漏，因而本发明液压挺柱的工作长度既可伸长，也可缩短，可以自动补偿配气机构部件的热膨胀间隙。相对于传统的液压挺柱，在凸轮工作时，液压挺柱的工作长度几乎没有变化(仅仅在凸轮工作的初始阶段微量缩短，缩短量可控)，气门开启行程更“精确”。

Claims (10)

  1. 一种液压挺柱，包括：
    挺柱体和柱塞，所述挺柱体的一端开设有进油口另一端敞口，所述柱塞从所述挺柱体的敞口端伸入并与所述挺柱体形成液压腔，所述进油口的内侧设置有在发动机机油压力作用下可将发动机机油油路与所述液压腔连通的单向阀，所述液压腔内设置有在气门开启压力消除后用于使所述柱塞相对于所述挺柱体回位的回位弹簧；其特征在于，
    所述柱塞的外周面与所述挺柱体的内周面滑动密封配合；
    所述柱塞开设有与所述液压腔相通的泄压通道，所述泄压通道设置有密封锥面，所述泄压通道内设置有泄压阀芯和泄压弹簧，在不受气门开启压力作用时所述泄压阀芯被所述泄压弹簧顶离所述密封锥面形成漏油间隙，在受到气门开启压力作用时所述泄压阀芯克服所述泄压弹簧的弹力并与所述密封锥面接触实现所述液压腔的密封。
  2. 如权利要求1所述的液压挺柱，其特征在于，所述泄压阀芯包括一阀球。
  3. 如权利要求1所述的液压挺柱，其特征在于，所述泄压弹簧设置在与所述密封锥面的小头端相通的泄压通道内，并顶靠在所述泄压阀芯与所述泄压通道的一个台阶面之间。
  4. 如权利要求1所述的液压挺柱，其特征在于，所述液压腔内活动设置有弹簧座，所述弹簧座开设有通孔，所述通孔连通所述液压腔和所述泄压通道，所述回位弹簧设置于所述弹簧座内。
  5. 如权利要求4所述的液压挺柱，其特征在于，所述弹簧座在所述回位弹簧作用下一端顶靠于所述柱塞、另一端与所述挺柱体的相应端面间具有间隙。
  6. 如权利要求5所述的液压挺柱，其特征在于，所述单向阀包括单向阀芯、限位弹簧和单向阀座，所述进油口的内侧设置有密封锥面，限位弹簧设置于所述单向阀座内，所述单向阀座安装于所述液压腔的挺柱体上，所述限位弹簧将所述单向阀芯顶靠于所述进油口的密封锥面。
  7. 如权利要求6所述的液压挺柱，其特征在于，所述回位弹簧夹压于所述单向阀座与所述弹簧座之间。
  8. 如权利要求1所述的液压挺柱，其特征在于，所述泄压通道与油底壳相通。
  9. 如权利要求1所述的液压挺柱，其特征在于，所述液压挺柱设置于发动机配气机构的凸轮到气门间的任何一个传动部件上，所述挺柱体的进油口与发动机机油油路连通。
  10. 如权利要求9所述的液压挺柱，其特征在于，所述液压挺柱设置于所述发动机配气机构的摇臂上，所述进油口与设置于所述摇臂上的发动机机油油路连通。
PCT/CN2021/070619 2020-05-26 2021-01-07 液压挺柱 WO2021238229A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202010460474.XA CN111472859B (zh) 2020-05-26 2020-05-26 液压挺柱
CN202010460474.X 2020-05-26

Publications (1)

Publication Number Publication Date
WO2021238229A1 true WO2021238229A1 (zh) 2021-12-02

Family

ID=71764794

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2021/070619 WO2021238229A1 (zh) 2020-05-26 2021-01-07 液压挺柱

Country Status (2)

Country Link
CN (1) CN111472859B (zh)
WO (1) WO2021238229A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107869368A (zh) * 2016-09-27 2018-04-03 浙江师范大学 一种压电驱动的液压式无凸轮轴气门驱动机构

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111472859B (zh) * 2020-05-26 2024-05-03 潍坊力创电子科技有限公司 液压挺柱

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB584302A (en) * 1944-12-28 1947-01-10 Lewis Redman Ord Improvements in and relating to valve tappets
JP2006336655A (ja) * 2005-06-01 2006-12-14 Schaeffler Kg 機械的なバルブクリアランス調整装置を備えた動弁機構
CN101076655A (zh) * 2004-10-14 2007-11-21 雅各布斯车辆系统公司 用于内燃机中可变气门致动的系统和方法
CN105545400A (zh) * 2016-02-04 2016-05-04 杭州新坐标科技股份有限公司 一种无限位卡簧的柱状式液压挺柱
CN110541761A (zh) * 2019-09-30 2019-12-06 江苏卓联精密机械有限公司 快速充油的发动机制动液压控制装置
CN111472859A (zh) * 2020-05-26 2020-07-31 潍坊力创电子科技有限公司 液压挺柱

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3967602A (en) * 1974-06-10 1976-07-06 Brown William G Hydraulic valve lifter for reciprocating internal combustion engines
CN2864104Y (zh) * 2005-09-30 2007-01-31 无锡开普动力有限公司 一种发动机用液压挺柱
CN101907000A (zh) * 2010-06-29 2010-12-08 绵阳富临精工机械有限公司 发动机气门间隙自动调整的液压挺柱
CN204200292U (zh) * 2014-11-05 2015-03-11 吴昌华 一种柴油机配气机构
CN206246167U (zh) * 2016-12-08 2017-06-13 蚌埠市广瑞机械有限公司 一种便于进油和泄油的液压挺柱
CN206246165U (zh) * 2016-12-08 2017-06-13 蚌埠市广瑞机械有限公司 一种用于汽车发动机气门间隙调整的液压挺柱
CN107060937B (zh) * 2017-02-20 2018-05-11 山东大学 全可变液压气门机构气门升程控制装置及内燃机
CN212250173U (zh) * 2020-05-26 2020-12-29 潍坊力创电子科技有限公司 液压挺柱

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB584302A (en) * 1944-12-28 1947-01-10 Lewis Redman Ord Improvements in and relating to valve tappets
CN101076655A (zh) * 2004-10-14 2007-11-21 雅各布斯车辆系统公司 用于内燃机中可变气门致动的系统和方法
JP2006336655A (ja) * 2005-06-01 2006-12-14 Schaeffler Kg 機械的なバルブクリアランス調整装置を備えた動弁機構
CN105545400A (zh) * 2016-02-04 2016-05-04 杭州新坐标科技股份有限公司 一种无限位卡簧的柱状式液压挺柱
CN110541761A (zh) * 2019-09-30 2019-12-06 江苏卓联精密机械有限公司 快速充油的发动机制动液压控制装置
CN111472859A (zh) * 2020-05-26 2020-07-31 潍坊力创电子科技有限公司 液压挺柱

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107869368A (zh) * 2016-09-27 2018-04-03 浙江师范大学 一种压电驱动的液压式无凸轮轴气门驱动机构

Also Published As

Publication number Publication date
CN111472859A (zh) 2020-07-31
CN111472859B (zh) 2024-05-03

Similar Documents

Publication Publication Date Title
WO2021238229A1 (zh) 液压挺柱
US6474277B1 (en) Method and apparatus for valve seating velocity control
US20110067661A1 (en) Lost motion variable valve actuation system with valve catch piston
WO2021253812A1 (zh) 发动机缸内制动系统及与其配套的液压挺柱
US7617807B2 (en) Engine and valvetrain with dual pushrod lifters and independent lash adjustment
US5193496A (en) Variable action arrangement for a lift valve
US20080083382A1 (en) Pushrod engine with multiple independent lash adjusters for each pushrod
US7543555B2 (en) Hydraulic lash compensation device with mechanical lift loss feature
CN212250173U (zh) 液压挺柱
JPS5888411A (ja) 内燃機関の動弁装置
CN206246165U (zh) 一种用于汽车发动机气门间隙调整的液压挺柱
CN212250172U (zh) 液压挺柱
CN212716797U (zh) 与气门桥集成一体的液压挺柱
JP2005507046A (ja) 給排気弁のための液圧式のアクチュエータ
CN110043339A (zh) 非顶置式配气机构发动机的液压摇臂
CN113286933B (zh) 选择性地复位空动发动机阀门机构组件
CN209671027U (zh) 非顶置式配气机构发动机的液压摇臂
US5347963A (en) Lash adjustment system for an internal combustion engine
JPH01232103A (ja) エンジンのバルブ駆動装置
JPS59162311A (ja) 密封式油圧リフタ
JP4263333B2 (ja) 油圧ラッシュアジャスタ
JPH1073010A (ja) エンジンの動弁装置
JPS5836802Y2 (ja) エンジンの油圧タペツト装置
JPH085287Y2 (ja) ラツシユアジヤスタ
JP2000087707A (ja) 内燃機関の動弁機構

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: 21813205

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21813205

Country of ref document: EP

Kind code of ref document: A1