WO2015143938A1 - 端部供油的机油控制阀及可变气门正时系统 - Google Patents

端部供油的机油控制阀及可变气门正时系统 Download PDF

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WO2015143938A1
WO2015143938A1 PCT/CN2015/071000 CN2015071000W WO2015143938A1 WO 2015143938 A1 WO2015143938 A1 WO 2015143938A1 CN 2015071000 W CN2015071000 W CN 2015071000W WO 2015143938 A1 WO2015143938 A1 WO 2015143938A1
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Prior art keywords
piston
compression spring
control valve
curve
oil control
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PCT/CN2015/071000
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English (en)
French (fr)
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张文豪
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舍弗勒技术股份两合公司
张文豪
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Publication of WO2015143938A1 publication Critical patent/WO2015143938A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves

Definitions

  • the invention relates to an oil control valve (OCV) for end oil supply and a variable valve timing (VVT) system.
  • OCV oil control valve
  • VVT variable valve timing
  • the oil control valve is one of the core components of the variable valve timing system.
  • the existing oil control valve is divided into two types: an oil control valve for the end oil supply and an oil control valve for the side oil supply according to the oil supply mode.
  • the conventional oil supply control valve for the end portion includes two parts of a proportional electromagnet 1 and a hydraulic body 2.
  • the proportional electromagnet 1 includes a movable armature 10.
  • the hydraulic body 2 includes: a valve body 20, one end of which is fixedly connected with the proportional electromagnet 1; a piston 21 movably located in the valve body 20; and a push rod 22, which are respectively axially opposite to the movable armature 10 and the piston 21 A fixed connection; a compression spring 23 located in the valve body 20 and in a compressed state, one end of the compression spring 23 abutting against the end of the piston 21 away from the push rod 22.
  • the compression spring 23 is a cylindrical coil spring, and as shown in FIG. 3, the stiffness (also called the spring constant) of the compression spring 23 is constant, so that the deformation force generated is linear with the length of the spring, and The larger the length of the spring, the smaller the deformation force generated by the compression spring 23.
  • the function of the oil control valve is that the engine ECU receives the signal from each sensor, and after the analysis and calculation, issues a control command to the oil control valve, and the oil control valve is located at the initial position by the control piston 21 according to the control command of the engine ECU (also referred to as the left Limit position), intermediate position or right limit position to select different oil paths connected to the phase adjuster to make the phase
  • the regulator is in three different working states: advance, lag or hold.
  • the existing oil control valve for the end oil supply has the following disadvantages: a piston valve clamping phenomenon occurs when the piston moves to the vicinity of the initial position during the returning process, so that the piston cannot be quickly returned to the initial position, and the piston is lowered. The speed and accuracy of the phase adjuster.
  • the current flowing into the coil of the proportional electromagnet changes when the piston is stuck, the flow of the hydraulic oil flowing out from the oil outlet of the oil control valve does not change. , affecting the flow characteristics of the oil control valve.
  • the problem to be solved by the invention is that there is a stuck phenomenon when the piston of the oil control valve of the existing oil supply end is returned, which affects the flow characteristic of the oil control valve and reduces the adjustment speed and accuracy of the phase adjuster.
  • an oil control valve for end oil supply comprising:
  • valve body a piston movably located within the valve body
  • a compression spring located in the valve body and in a compressed state, one end of the compression spring abutting the end of the piston away from the push rod;
  • a position closest to the movable armature in the moving stroke of the piston is an initial position, and a position farthest from the movable armature is a right limit position, and a midpoint of the initial position and the right limit position is an intermediate position ;
  • the compression spring is a variable stiffness compression spring
  • a curve of a relationship between a deformation force generated by the compression spring and a length of the spring is a first curve, and the first curve is a line segment and has a curve in which the piston moves from the intermediate position to the right extreme position a first endpoint and a second endpoint;
  • the relationship between the deformation force generated by the compression spring and the length of the spring is a second curve, and the second curve has the first curve during the movement of the piston from the intermediate position to the initial position.
  • An extension line extending from the second end point to the first end point of the first curve is located below the second curve.
  • the second curve is a line segment.
  • the compression spring is an equal pitch concave shaft coil spring.
  • the maximum outer diameter of the compression springs at both ends in the axial direction is equal.
  • variable valve timing system comprising the oil control valve of any of the above.
  • the compression spring in the oil control valve is a variable stiffness compression spring, which not only causes the deformation force of the compression spring to be equal to the electromagnetic force of the movable armature but also the piston from the middle during the movement from the intermediate position to the right limit position.
  • the deformation force generated by the compression spring is greater than the electromagnetic force of the movable armature, so that the deformation force generated by the compression spring can not only offset the electromagnetic force, but also at least partially offset the fluid force and prevent the piston from appearing.
  • the stuck phenomenon allows the piston to quickly return to the initial position.
  • Figure 1 is an axial sectional view of a conventional oil control valve for end oil supply
  • Figure 2 is a perspective view showing the structure of the compression spring of Figure 1;
  • Figure 3 is a graph showing the relationship between the deformation force generated by the compression spring shown in Figure 2 and the length of the compression spring;
  • Figure 4 is a flow rate characteristic diagram of the oil control valve shown in Figure 1, the abscissa indicates the current flowing into the coil of the proportional electromagnet, and the ordinate indicates the flow rate of the hydraulic oil flowing out from the oil outlet of the oil control valve;
  • Figure 5 is a graph showing the relationship between the fluid force and the piston position of the piston of the oil control valve of Figure 1 at various positions;
  • Figure 6 is an axial sectional view of an oil control valve for oil supply at an end in one embodiment of the present invention.
  • Figure 7 is a plan view showing the structure of the compression spring of Figure 6;
  • Figure 8 is a graph showing the relationship between the deformation force generated by the compression spring shown in Figure 7 and the length of the compression spring.
  • the piston 21 when the piston 21 is in various positions, it is subjected to electromagnetic force transmitted by the movable armature 10 and the push rod 22, and the deformation force applied by the compression spring 23.
  • the piston 21 By making the electromagnetic force opposite to the direction of the deformation force and equal in magnitude, the piston 21 can be moved at a constant speed during the movement stroke.
  • the piston 21 receives a flow force in addition to the electromagnetic force and the deformation force, so that the sum of the forces applied to the piston 21 is the fluid force.
  • the piston 21 is moved from the intermediate position b to the initial position.
  • the fluid force is the same as the direction of the electromagnetic force, and the direction of the deforming force is opposite, and the magnitude of the fluid force changes substantially in a gradually increasing manner. Therefore, when the piston 21 moves from the intermediate position b to the vicinity of the initial position a, a large fluid force hinders the piston 21 from continuing to move, causing the piston 21 to become stuck and cannot be quickly returned to the initial position.
  • the present invention provides an improved end oil supply oil control valve in which the compression spring is a variable stiffness compression spring that not only moves the piston from the intermediate position to the right extreme position,
  • the deformation force generated by the compression spring is equal to the electromagnetic force of the movable armature, and during the movement of the piston from the intermediate position to the initial position, the deformation force generated by the compression spring is greater than the electromagnetic force of the movable armature, so that the compression spring is
  • the deformation force not only can offset the electromagnetic force, but also can offset at least part of the fluid force, preventing the piston from becoming stuck, so that the piston can quickly return to the initial position.
  • the oil supply control valve of the end portion of the present embodiment includes two parts of a proportional electromagnet 10 and a hydraulic body 20.
  • the proportional electromagnet 10 includes a movable armature 100.
  • the hydraulic body 20 includes: a valve body 200, one end of which is fixedly connected with the proportional electromagnet 10; a piston 210 that is movably located in the valve body 200; and a push rod 220 that is axially opposite to the movable armature 100 and the piston 210, respectively.
  • a fixed connection a compression spring 230 located in the valve body 200 and in a compressed state, one end of the compression spring 230 abutting against the end of the piston 210 away from the push rod 220.
  • the compression spring 230 is a variable stiffness compression spring, and in the present embodiment, as shown in FIG. 7, the compression spring 230 is an equal pitch concave shaft spring.
  • the concave-concave coil spring means that along the axial direction of the coil spring, the outer diameter of the coil spring is gradually reduced to a minimum value D2 by linearly varying from D1, and then gradually increased to D3 in a linearly varying manner.
  • the relationship between the deformation force generated by the compression spring 230 and the length of the spring is a first curve S1
  • the first curve S1 is a line segment, and has a first end.
  • Point C and second end point D the length of the spring corresponding to the first end point C is the length of the compression spring 230 when the piston 210 is in the intermediate position, and the length of the spring corresponding to the second end point D is the compression spring 230 when the piston 210 is in the right extreme position. length;
  • the relationship between the deformation force generated by the compression spring 230 and the length of the spring is the second curve S2
  • the second curve S2 is a line segment
  • the second curve S2 has a a third end point E, and an end point coincident with the first end point C, the length of the spring corresponding to the third end point E is the length of the compression spring 230 when the piston 210 is in the initial position;
  • An extension line S3 of the first curve S1 extending from the second end point D to the first end point C is located below the second curve S2.
  • the position closest to the movable armature 100 within the moving stroke of the piston 210 is the initial position, and the position farthest from the movable armature 100 is the right extreme position, the initial position and the right extreme position.
  • the midpoint is the intermediate position.
  • the piston 210 when the piston 210 is at each position, it is subjected to an electromagnetic force transmitted by the movable armature 100 and the push rod 220, and a deformation force applied by the compression spring 230, which is equal in magnitude and direction.
  • the compression spring 230 On the contrary, and both are linear with the length of the spring, the larger the length of the spring, the smaller the electromagnetic force and the deforming force.
  • the electromagnetic force of the piston 210 and the length of the spring have the following relationship: the electromagnetic force and the length of the spring during the movement of the piston 210 from the intermediate position to the right extreme position in the direction A
  • the relationship between the relationship curve and the deformation force and the length of the spring coincides with the first curve S1; during the movement of the piston 210 from the intermediate position to the initial position in the direction B, the electromagnetic force and the length of the spring
  • the relationship between the first curve S1 is extended from the second end point D to the first end point C. Extend the extension line S3. Since the extension line S3 is located below the second curve S2, the piston 210 is subjected to a deformation force greater than the electromagnetic force during the movement of the piston 210 from the intermediate position to the initial position.
  • the piston 210 is also subjected to a fluid force that is the same as the electromagnetic force and opposite to the deformation force. Since the deformation force generated by the compression spring 230 is greater than the electromagnetic force, the deformation force generated by the compression spring 230 can not only be used to cancel the electromagnetic force, but also can at least partially offset the fluid force, preventing the piston 210 from becoming stuck, so that the piston The 210 can be quickly returned to the initial position, improving the flow characteristics of the oil control valve, which in turn increases the speed and accuracy of the phase adjuster.
  • the electromagnetic force and the deformation force of the piston 210 are equal in magnitude and opposite in direction, the electromagnetic The force and deformation forces can cancel each other out, allowing the piston 210 to move relatively evenly.
  • the relationship between the deformation force generated by the compression spring 230 and the length of the spring may be other types of curves during the movement of the piston 210 from the intermediate position to the initial position in the direction B.
  • the relationship curve is a straight line, the manufacture of the compression spring 230 can be made more convenient.
  • the maximum outer diameter of the compression springs 230 at both ends in the axial direction is equal, that is, D1 is equal to D3, so that when the piston 210 gradually compresses the compression spring 230 in the direction A, the compression spring 230 is compressed.
  • the deformation can be performed along the moving direction of the piston 210 to prevent the compression spring 230 from being inclined (i.e., the axis of the compression spring 230 is not parallel to the moving direction of the piston 210).
  • the present invention also provides a variable valve timing system comprising the above-described oil supply control valve for the end.

Abstract

一种端部供油的机油控制阀，该机油控制阀包括：可动电枢（100）；阀体（200）；可移动地位于所述阀体内的活塞（210）；推杆（220），沿轴向的两端分别与可动电枢（100）、活塞（210）固定连接；位于阀体（200）内并呈压缩状态的压缩弹簧（230），压缩弹簧（230）的一端抵靠活塞（210）远离推杆（220）的端部；压缩弹簧（230）为变刚度压缩弹簧。还公开了一种包括该机油控制阀的可变气门正时系统。该机油控制阀解决了现有端部供油的机油控制阀的活塞回位时存在卡滞现象、影响了机油控制阀的流量特性、降低了相位调节器的调节速度和准确性的问题。

Description

端部供油的机油控制阀及可变气门正时系统
本申请要求2014年3月28日提交中国专利局、申请号为201410123947.1、发明名称为“端部供油的机油控制阀及可变气门正时系统”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
本发明涉及一种端部供油的机油控制阀(Oil Control Valve，简称OCV)及一种可变气门正时(Variable Valve Timing，简称VVT)系统。
背景技术
机油控制阀是可变气门正时系统的核心部件之一。现有机油控制阀按供油方式分为端部供油的机油控制阀和侧面供油的机油控制阀两种。
如图1所示，现有一种端部供油的机油控制阀包括比例电磁铁1和液压体2两个部分。其中，比例电磁铁1包含可动电枢10。液压体2包含：阀体20，一端与比例电磁铁1固定连接；可移动地位于阀体20内的活塞21；推杆22，沿轴向的两端分别与可动电枢10、活塞21固定连接；位于阀体20内并呈压缩状态的压缩弹簧23，压缩弹簧23的一端抵靠活塞21远离推杆22的端部。
如图2所示，压缩弹簧23为圆柱形螺旋弹簧，且结合图3所示，压缩弹簧23的刚度(也称弹性系数)为常数，使其所产生形变力与弹簧长度呈线性关系，且弹簧长度越大，压缩弹簧23所产生形变力越小。
机油控制阀的作用在于：发动机ECU接收各传感器传来的信号，经分析、计算后发出控制指令给机油控制阀，机油控制阀根据发动机ECU的控制指令通过控制活塞21位于初始位置(也称左极限位置)、中间位置或右极限位置来选择连接至相位调节器的不同油路，使相位 调节器处于提前、滞后或保持这三个不同的工作状态。
继续参考图1所示，在机油控制阀的一种工作状态下，在电磁力的作用下，可动电枢10带着推杆22一起移动，使得活塞21从初始位置沿逐渐增大压缩弹簧23压缩量的方向A移动；在机油控制阀的另一种工作状态下，压缩弹簧23逐渐恢复形变，使得活塞21沿逐渐减小压缩弹簧23压缩量的方向B回位直至到达初始位置。
但是，现有端部供油的机油控制阀存在以下不足：活塞在回位过程中移动至初始位置附近时存在卡滞现象(solenoid valve clamping phenomenon)，使活塞不能快速回位至初始位置，降低了相位调节器的调节速度和准确性。另外，参考图4中圆圈P所示，在活塞出现卡滞时，虽然通入比例电磁铁中线圈的电流有发生变化，但从机油控制阀出油口流出的液压油流量却并未发生变化，影响了机油控制阀的流量特性。
发明内容
本发明要解决的问题是：现有端部供油的机油控制阀的活塞回位时存在卡滞现象，影响了机油控制阀的流量特性，降低了相位调节器的调节速度和准确性。
为解决上述问题，本发明提供了一种端部供油的机油控制阀，包括：
可动电枢；
阀体；
可移动地位于所述阀体内的活塞；
推杆，沿轴向的两端分别与所述可动电枢、活塞固定连接；
位于所述阀体内并呈压缩状态的压缩弹簧，所述压缩弹簧的一端抵靠所述活塞远离推杆的端部；
所述活塞的移动行程内最靠近所述可动电枢的位置为初始位置、最远离所述可动电枢的位置为右极限位置，所述初始位置和右极限位置的中点为中间位置；
所述压缩弹簧为变刚度压缩弹簧；
所述活塞从所述中间位置移动至所述右极限位置的过程中，所述压缩弹簧所产生形变力与弹簧长度之间的关系曲线为第一曲线，所述第一曲线为线段，并具有第一端点和第二端点；
所述活塞从所述中间位置移动至所述初始位置的过程中，所述压缩弹簧所产生形变力与弹簧长度之间的关系曲线为第二曲线，所述第二曲线具有与所述第一端点重合的端点；
所述第一曲线自所述第二端点至第一端点方向延伸的延长线位于所述第二曲线下方。
可选的，所述第二曲线为线段。
可选的，所述压缩弹簧为等节距的中凹形螺旋弹簧。
可选的，所述压缩弹簧沿轴向的两端的最大外径相等。
另外，本发明还提供了一种可变气门正时系统，包括上述任一所述的机油控制阀。
与现有技术相比，本发明的技术方案具有以下优点：
机油控制阀中的压缩弹簧为变刚度压缩弹簧，不仅使活塞在从中间位置移动至右极限位置的过程中，压缩弹簧所产生形变力等于可动电枢所受电磁力，还使活塞从中间位置移动至初始位置的过程中，压缩弹簧所产生形变力大于可动电枢所受电磁力，使得压缩弹簧所产生形变力不仅能够抵消电磁力，还能够至少抵消部分流体力，防止了活塞出现卡滞现象，使得活塞能够快速回位至初始位置。
附图说明
图1是现有一种端部供油的机油控制阀的轴向剖面图；
图2是图1中压缩弹簧的立体结构示意图；
图3是图2所示压缩弹簧所产生形变力与压缩弹簧长度之间的关系曲线图；
图4是图1所示机油控制阀的流量特性曲线图，横坐标表示通入比例电磁铁中线圈的电流，纵坐标表示从机油控制阀出油口流出的液压油的流量；
图5是图1所示机油控制阀的活塞在各个位置所受流体力与活塞位置之间的关系曲线图；
图6是本发明的一个实施例中端部供油的机油控制阀的轴向剖面图；
图7是图6中压缩弹簧的平面结构示意图；
图8是图7所示压缩弹簧所产生形变力与压缩弹簧长度之间的关系曲线图。
具体实施方式
经研究发现，造成现有端部供油的机油控制阀的活塞在回位过程中移动至初始位置附近时存在卡滞现象，使活塞不能快速回位至初始位置的原因如下：
继续参考图1所示，理论上讲，活塞21位于各个位置时，会受到由可动电枢10和推杆22传递的电磁力、以及由压缩弹簧23施加的形变力。通过使所述电磁力与所述形变力方向相反、大小相等，能够使得活塞21在移动行程内匀速移动。
但是，实际情况是，活塞21除了会受到所述电磁力及形变力之外，还会受到流体力(flow force)，使得活塞21所受作用力的总和为所述流体力。结合图5所示，在活塞21从中间位置b移动至初始位 置a的回位过程中，所述流体力与电磁力方向相同、与形变力方向相反，且流体力的大小基本上以逐渐增大的方式变化。因此，当活塞21从中间位置b移动至初始位置a的附近时，较大的流体力会阻碍活塞21继续移动，使活塞21出现卡滞现象，不能快速回位至初始位置。
鉴于此，本发明提供了一种改进的端部供油的机油控制阀，该机油控制阀中的压缩弹簧为变刚度压缩弹簧，不仅使活塞在从中间位置移动至右极限位置的过程中，压缩弹簧所产生形变力等于可动电枢所受电磁力，还使活塞从中间位置移动至初始位置的过程中，压缩弹簧所产生形变力大于可动电枢所受电磁力，使得压缩弹簧所产生形变力不仅能够抵消电磁力，还能够至少抵消部分流体力，防止了活塞出现卡滞现象，使得活塞能够快速回位至初始位置。
技术术语解释：
线性关系：两个变量之间存在一次函数关系。
为使本发明的上述目的、特征和优点能够更为明显易懂，下面结合附图对本发明的具体实施例做详细的说明。
如图6所示，本实施例的端部供油的机油控制阀包括比例电磁铁10和液压体20两个部分。其中，比例电磁铁10包含可动电枢100。液压体20包含：阀体200，一端与比例电磁铁10固定连接；可移动地位于阀体200内的活塞210；推杆220，沿轴向的两端分别与可动电枢100、活塞210固定连接；位于阀体200内并呈压缩状态的压缩弹簧230，压缩弹簧230的一端抵靠活塞210远离推杆220的端部。
压缩弹簧230为变刚度压缩弹簧，且在本实施例中，如图7所示，压缩弹簧230为等节距的中凹形螺旋弹簧。在本发明中，中凹形螺旋弹簧是指：沿螺旋弹簧轴向，螺旋弹簧的外径由D1先以线性变化方式逐渐减小至最小值D2，接着以线性变化方式逐渐增大至D3。
结合图6和图8所示，在本实施例中，在活塞210的移动行程内， 压缩弹簧230所产生形变力与弹簧长度之间具有如下关系曲线：
活塞210沿方向A从中间位置移动至右极限位置的过程中，压缩弹簧230所产生形变力与弹簧长度之间的关系曲线为第一曲线S1，第一曲线S1为线段，并具有第一端点C和第二端点D，第一端点C对应的弹簧长度为活塞210位于中间位置时压缩弹簧230的长度，第二端点D对应的弹簧长度为活塞210位于右极限位置时压缩弹簧230的长度；
活塞210沿方向B从中间位置移动至初始位置的过程中，压缩弹簧230所产生形变力与弹簧长度之间的关系曲线为第二曲线S2，第二曲线S2为线段，第二曲线S2具有第三端点E、以及与第一端点C重合的端点，第三端点E对应的弹簧长度为活塞210位于初始位置时压缩弹簧230的长度；
第一曲线S1自第二端点D至第一端点C方向延伸的延长线S3位于第二曲线S2下方。
在本发明中，活塞210的移动行程内最靠近可动电枢100的位置为所述初始位置、最远离可动电枢100的位置为所述右极限位置，所述初始位置和右极限位置的中点为所述中间位置。
如前所述，活塞210位于各个位置时，会受到由可动电枢100和推杆220传递的电磁力、以及由压缩弹簧230施加的形变力，所述电磁力与形变力大小相等、方向相反，且均与弹簧长度呈线性关系，弹簧长度越大，所述电磁力、形变力越小。
因此，在活塞210的移动行程内，活塞210所受电磁力与弹簧长度之间具有如下关系曲线：活塞210沿方向A从中间位置移动至右极限位置的过程中，所述电磁力与弹簧长度之间的关系曲线与所述形变力与弹簧长度之间的关系曲线重合，均为第一曲线S1；活塞210沿方向B从中间位置移动至初始位置的过程中，所述电磁力与弹簧长度之间的关系曲线为第一曲线S1自第二端点D至第一端点C方向延 伸的延长线S3。由于延长线S3位于第二曲线S2下方，因此，活塞210从中间位置移动至初始位置的过程中，活塞210所受形变力大于电磁力。
由前面所述可知，在活塞210沿方向B从中间位置移动至初始位置的过程中，活塞210还会受到流体力，所述流体力方向与所述电磁力相同、与所述形变力相反。由于压缩弹簧230所产生形变力大于所述电磁力，因此，压缩弹簧230所产生形变力不仅能够用来抵消电磁力，还能够至少抵消部分流体力，防止了活塞210出现卡滞现象，使得活塞210能够快速回位至初始位置，改善了机油控制阀的流量特性，进而能够提高相位调节器的调节速度和准确性。
另外，在活塞210沿方向B从中间位置移动至初始位置或沿方向A从初始位置移动至中间位置的过程中，由于活塞210所受电磁力与形变力大小相等、方向相反，使得所述电磁力与形变力能够相互抵消，使活塞210能够较为匀速地移动。
在本实施例的变换例中，活塞210沿方向B从中间位置移动至初始位置的过程中，压缩弹簧230所产生形变力与弹簧长度之间的关系曲线也可以为其他类型的曲线。当该关系曲线为直线时，能使压缩弹簧230的制造更为方便。
在本实施例中，结合图6和图7所示，压缩弹簧230沿轴向的两端的最大外径相等，即D1等于D3，使得活塞210沿方向A逐渐压缩压缩弹簧230时，压缩弹簧230能够沿着活塞210的移动方向发生变形，防止压缩弹簧230发生倾斜(即压缩弹簧230的轴线不平行于活塞210移动方向)。
另外，本发明还提供了一种可变气门正时系统，它包含上述端部供油的机油控制阀。
虽然本发明披露如上，但本发明并非限定于此。任何本领域技术人员，在不脱离本发明的精神和范围内，均可作各种更动与修改，因 此本发明的保护范围应当以权利要求所限定的范围为准。

Claims (5)

  1. 一种端部供油的机油控制阀，包括：
    可动电枢；
    阀体；
    可移动地位于所述阀体内的活塞；
    推杆，沿轴向的两端分别与所述可动电枢、活塞固定连接；
    位于所述阀体内并呈压缩状态的压缩弹簧，所述压缩弹簧的一端抵靠所述活塞远离推杆的端部；
    所述活塞的移动行程内最靠近所述可动电枢的位置为初始位置、最远离所述可动电枢的位置为右极限位置，所述初始位置和右极限位置的中点为中间位置；
    其特征在于，所述压缩弹簧为变刚度压缩弹簧；
    所述活塞从所述中间位置移动至所述右极限位置的过程中，所述压缩弹簧所产生形变力与弹簧长度之间的关系曲线为第一曲线，所述第一曲线为线段，并具有第一端点和第二端点；
    所述活塞从所述中间位置移动至所述初始位置的过程中，所述压缩弹簧所产生形变力与弹簧长度之间的关系曲线为第二曲线，所述第二曲线具有与所述第一端点重合的端点；
    所述第一曲线自所述第二端点至第一端点方向延伸的延长线位于所述第二曲线下方。
  2. 如权利要求1所述的机油控制阀，其特征在于，所述第二曲线为线段。
  3. 如权利要求1或2所述的机油控制阀，其特征在于，所述压缩弹簧为等节距的中凹形螺旋弹簧。
  4. 如权利要求1所述的机油控制阀，其特征在于，所述压缩弹簧沿轴向的两端的最大外径相等。
  5. 一种可变气门正时系统，其特征在于，包括权利要求1至4任 一项所述的机油控制阀。
PCT/CN2015/071000 2014-03-28 2015-01-19 端部供油的机油控制阀及可变气门正时系统 WO2015143938A1 (zh)

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