WO2010081324A1 - 一种双密封阀门结构 - Google Patents

一种双密封阀门结构 Download PDF

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Publication number
WO2010081324A1
WO2010081324A1 PCT/CN2009/073432 CN2009073432W WO2010081324A1 WO 2010081324 A1 WO2010081324 A1 WO 2010081324A1 CN 2009073432 W CN2009073432 W CN 2009073432W WO 2010081324 A1 WO2010081324 A1 WO 2010081324A1
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WIPO (PCT)
Prior art keywords
sealing
seal
valve
valve stem
seat
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PCT/CN2009/073432
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English (en)
French (fr)
Inventor
杨继跃
黄虹宾
杨卫
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广东联塑科技实业有限公司
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Application filed by 广东联塑科技实业有限公司 filed Critical 广东联塑科技实业有限公司
Publication of WO2010081324A1 publication Critical patent/WO2010081324A1/zh

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Classifications

    • 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
    • F16K41/00—Spindle sealings
    • F16K41/02—Spindle sealings with stuffing-box ; Sealing rings

Definitions

  • the present invention relates to a valve structure, and more particularly to a double-sealed valve structure capable of ensuring that a valve meets strict sealing requirements under use conditions, and belongs to the technical field of pipeline valves.
  • FIG. 1 and Figure 2 are schematic views of a prior art sealing system.
  • Figure 1 shows the valve fully open.
  • Figure 2 shows the valve fully closed.
  • This sealing structure can effectively protect the sealing packing to a certain extent and prevent the valve from being inside.
  • Fluid leakage especially in the case of no deformation of the valve stem, can effectively protect the sealing packing to a certain extent, so that the sealing packing is subjected to less fluid pressure during the full opening of the valve.
  • the pressure of the fluid medium inside the valve body is very high, when the valve is opened and the gate is lifted, the valve body is filled with high-pressure fluid, which often causes the valve stem to tilt at a certain angle, or causes the valve stem to undergo a certain deformation.
  • the self-pressing hard seal structure will generate a large gap, thereby affecting the sealing effect of the second layer sealing structure, so that the fluid pressure of the first layer seal (also the main seal) of the seal packing is close to the fluid pressure in the valve body, which is easy to make
  • the sealing packing is gradually aging due to long-term high pressure compression, which is prone to leakage of the medium in the valve, and will eventually be replaced because it cannot be effectively sealed, but the valve should be stopped before replacement. Such operation is not only cumbersome, but also requires stopping the valve and starting the valve. Consume a lot of energy.
  • the technical problem to be solved by the present invention is to overcome the difficulties of the prior art, and an object thereof is to provide a double-sealed valve structure which effectively protects the sealing packing and ensures good sealing performance.
  • a double seal valve structure comprising a valve stem and a valve cover, and a sealing packing is arranged between the valve stem and the valve cover
  • the first layer sealing structure the lower end of the first layer sealing structure is further provided with a second sealing structure
  • the second sealing structure is a self-pressing hard sealing structure, that is, a sealing seat and a valve cover inner wall provided on the valve stem
  • a sealing structure of the metal sealing surface faces the metal sealing surface
  • an auxiliary sealing structure is further disposed between the second sealing structure, the auxiliary sealing structure is a sealing ring sleeved on the valve stem, and the bottom surface of the sealing ring is placed There is a gap between the seal ring and the valve stem to allow the seal ring to move on the seal seat.
  • the present invention provides a sealing ring between the second sealing structures, by which the second sealing structure is ensured that the sealing effect is not affected by the inclination or deformation of the valve stem, in particular because of the existence between the sealing ring and the valve stem.
  • the gap that the sealing ring can move on the sealing seat can make the pressure of the medium on the two sides of the sealing ring different when the valve stem is inclined or deformed, and the sealing ring can move in the direction of small pressure to further ensure the sealing effect.
  • the two sealing pairs formed between the sealing ring and the second sealing structure are in line contact, that is, the upper surface of the sealing ring is in line contact with the inner wall of the valve cover, and the lower surface of the sealing ring and the upper surface of the sealing seat are also lines.
  • the contact and the wire contact structure ensure the tightness of the seal on the one hand, and facilitate the movement of the seal ring under the pressure of the medium on the other hand, thereby ensuring the seal.
  • the line contact is such that the upper surface of the sealing seat on the valve stem, the corresponding inner wall of the valve cover, and the upper and lower sealing surfaces of the sealing ring are curved.
  • the upper surface of the sealing seat on the valve stem and the inner wall of the valve cover are arranged as a conical surface, and the upper and lower sealing surfaces of the sealing ring are arranged as a cylindrical surface.
  • the friction angle ⁇ of the two seal pairs is greater than or equal to the critical friction angle
  • the critical friction angle is an arctangent function of the friction coefficient between the two friction surfaces
  • the friction angle is respectively The angle between the inner wall of the bonnet and the vertical plane of the bonnet centerline, and the angle between the upper surface of the seal seat and the radial plane of the valve stem.
  • the sealing jaw is made of a rigid material or a soft material such as a metal sealing jaw, a rubber sealing jaw or a plastic sealing jaw.
  • the sealing system of the present invention is provided with the sealing cymbal on the valve stem, and the inner cylindrical surface of the sealing cymbal has a certain gap with the valve stem, and can move freely.
  • a sealing surface (referred to as a valve stem sealing surface) is formed on the sealing seat of the valve stem, and a sealing surface (referred to as a bonnet sealing surface) is formed perpendicular to the wall surface of the valve stem inside the valve cover, and the upper and lower sides of the sealing jaw A sealing surface that cooperates with the bonnet sealing surface and the stem sealing surface is separately produced.
  • the sealing cymbal can move in a direction perpendicular to the center line of the bonnet toward a small pressure without the valve being required.
  • the rod and the center line of the bonnet are exactly coincident to ensure zero leakage of the upper seal, thus ensuring effective protection of the stem packing seal during long-term operation of the valve.
  • the sealing surface of the sealing jaw, the matching valve stem sealing surface and the bonnet sealing surface can be made into a tapered surface, or can be made into a cylindrical surface, etc., preferably a valve stem sealing surface and a valve
  • the sealing surface of the cover is made into a conical surface, and the two sealing surfaces of the sealing crucible are made into a cylindrical surface or other curved surface. As a result, the sealing surface of the sealing crucible is in line contact with the sealing surface of the valve stem and the sealing surface of the valve cover, which is better. The sealing effect.
  • the sealing system of the present invention sleeves the sealing cymbal on the valve stem, and the inner cylindrical surface of the sealing cymbal has a certain gap with the valve stem, and can move freely, and when the valve stem is subjected to a large deviation, the The seal ⁇ can be moved in a direction perpendicular to the center line of the bonnet to a small pressure, and the position can be automatically adjusted without strictly matching the center line of the valve stem and the bonnet to ensure zero leakage of the upper seal, thereby ensuring Effectively protect the stem packing seal during long-term operation of the valve.
  • the valve of the prior art has an increase in the number of switches with the increase of the number of switches, and the elasticity of the sealing packing is gradually lost. Therefore, the leakage of the medium in the valve is liable to occur, and the pressure of the medium directly acts between the sealing packing and the valve stem. It will eventually leak out of the gap.
  • the technical solution of the invention provides a sealing ⁇ between the valve cover and the valve flap, which substantially establishes a buffer belt between the medium and the valve stem and the sealing packing, thereby effectively reducing the pressure of the surrounding medium and prolonging the service life of the sealing packing. , increased the safety of the valve.
  • valves are widely used in pipeline systems. Maintaining pipeline operation requires a large amount of energy. Among them, stopping valves and starting valves are one of the sources of energy loss.
  • the technical solution provided by the present invention realizes online replacement of sealing packing without stopping valve operation. In terms of energy saving and consumption reduction, there is a positive effect that can not be ignored.
  • the method provided by the invention has low cost, is easy to operate and popularize, and greatly reduces the operating cost of the pipeline system in the prior art, and is also beneficial to environmental protection. The seal packing can be safely replaced without stopping the valve.
  • Figures 1 and 2 are schematic views of a prior art sealing system, Figure 1 shows the valve fully open, and Figure 2 shows the valve fully closed;
  • Figure 3 is a schematic view of the friction angle ⁇ of the valve stem sealing surface and the plane perpendicular to the center line;
  • Figure 4 is a schematic view of the friction angle ⁇ of the sealing surface on the bonnet and the plane perpendicular to the centerline;
  • FIGs 5 and 6 are schematic views of the sealing system of Embodiment 1; Figure 5 is the case where the valve is fully opened, and Figure 6 is the case where the valve is fully closed.
  • the double seal valve structure shown in Fig. 5 includes a valve flap 1, a valve stem 2, a sealing seat 21 on the valve stem, a valve cover 3, a sealing packing 4, a packing sleeve 5 and a sealing ring 6.
  • the sealing material 4 disposed between the valve stem 2, the packing sleeve 5 and the valve cover 3 is used as a first sealing structure, and the lower end of the first sealing structure is further provided with a second sealing structure, which is a self-pressing hard sealing structure, that is,
  • the sealing structure of the metal sealing surface is faced by the metal seal between the sealing seat 21 disposed on the valve stem and the inner wall of the valve cover 3, and the second sealing structure is further provided with an auxiliary sealing structure, that is, sleeved on the valve stem 2
  • the upper sealing ring 6, the sealing ring 6 is a metal sealing ring, the bottom surface of which is placed on the sealing seat 21 of the valve stem, and there is a gap between the sealing ring 6 and the valve stem 2 to enable the sealing ring to
  • valve flap 1 As shown in Fig. 6, after the valve flap 1 is fully opened, the bottom of the bonnet 3 and the stem sealing seat 21 are pressed against the sealing jaw 6 for sealing purposes, and the sealing packing 4 can be easily replaced.
  • the system establishes a buffer zone between the valve flap, the valve stem and the sealing packing, which effectively reduces the pressure of the surrounding medium and prolongs the service life of the sealing packing, and only needs to lift and lower the valve flap without stopping during the whole operation.
  • the operation of the valve and the actuating valve not only simplifies the operating procedure but also reduces energy consumption.
  • the friction angle of both sealing surfaces must be greater than the critical friction angle, as shown in Fig. 3. 4 shows.
  • the relationship between the two parameters is: the friction angle ⁇ is greater than or equal to the critical friction angle, and the critical friction angle is the value of the arctangent function of the friction coefficient between the two friction surfaces, that is, the friction surface material and the surface A function of roughness.
  • the friction angle ⁇ is the angle between the inner wall of the valve cover and the vertical plane of the center line of the valve cover, and the angle between the surface of the sealing seat and the radial plane of the valve stem.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)

Description

一种双密封阀门结构
[1] 技术领域
[2] 本发明涉及一种阀门结构， 尤其是一种能够保证阀门在使用状态下达到严格密 封要求的双密封阀门结构， 属于管道阀门技术领域。
[3] 背景技术
[4] 目前的阀门尤其是闸阀， 因其流体介质压力高， 当闸板提升后， 阀体内充满高 压流体。 阀杆处的密封一般设有自压式硬密封结构 （也称上密封， 是金属对金 属的密封） ， 即通过设在阀杆上的密封座与阀盖内壁之间的金属密封面对金属 密封面的密封结构， 以便更好地保护阀杆密封填料， 通常将密封填料作为第一 层密封结构， 将自压式硬密封结构作为第二层密封结构。 图 1和图 2是已有技术 密封系统的示意图， 图 1为阀门全开的情况， 图 2为阀门全闭的情况， 这种密封 结构在一定程度上可有效保护密封填料， 防止阀门内的流体泄漏， 特别是在阀 杆不产生变形的情况下， 在一定程度上可有效保护密封填料， 使密封填料在阀 门全开过程中受到较小的流体压力。 然而由于阀体内部的流体介质压力非常高 ， 当阀门打开， 闸板提升后， 阀体内充满高压流体， 经常使得阀杆产生一定角 度的倾斜， 或是使得阀杆产生一定的形变， 此吋， 自压式硬密封结构将会产生 较大间隙， 从而影响第二层密封结构的密封效果， 使得第一层密封 （也是主要 密封） 的密封填料受到的流体压力接近阀体内的流体压力， 容易使得密封填料 受到长期高压的压迫而逐渐老化， 容易发生阀门内的介质泄露， 最终将因不能 有效密封而被更换， 但更换前要停止阀门工作， 这样的操作不仅繁琐， 而且停 止阀门和启动阀门需要消耗大量能量。
[5] 发明内容
[6] 本发明所要解决的技术问题是克服已有技术的困难， 目的在于提供一种有效保 护密封填料， 且保证良好密封性能的双密封阀门结构。
[7] 本发明通过以下技术方案实现上述目的：
[8] 一种双密封阀门结构， 包括阀杆和阀盖， 所述阀杆与阀盖之间设置有密封填料 作为第一层密封结构， 第一层密封结构的下端还设有第二密封结构， 所述第二 密封结构为自压式硬密封结构， 即通过设在阀杆上的密封座与阀盖内壁之间的 金属密封面对金属密封面的密封结构， 所述第二密封结构之间还设置有辅助密 封结构， 所述辅助密封结构为套在阀杆上的密封环， 密封环的底面置于阀杆的 密封座上， 且密封环与阀杆之间还存在使密封环能在密封座上移动的间隙。 本发明通过在第二密封结构之间设置密封环， 通过该密封环确保第二密封结构 不会因为阀杆的倾斜或变形而影响密封效果， 特别是由于密封环与阀杆之间还 存在使密封环能在密封座上移动的间隙， 可使得在阀杆倾斜或变形的吋候， 密 封环两边受到介质压力的大小不同， 密封环可随着往压力小的方向移动， 进一 步确保密封效果。
所述密封环与第二密封结构之间形成的两个密封副均为线接触， 即密封环的上 表面与阀盖内壁为线接触， 密封环的下表面与密封座的上表面也为线接触， 釆 用线接触结构， 一方面可保证密封的紧密性， 另一方面， 可便于密封环在介质 的压力下移动， 从而保证密封。
所述线接触为将阀杆上的密封座上表面、 阀盖对应的内壁、 以及密封环的上下 两个密封面设置成曲面。
进一步的， 所述阀杆上的密封座上表面和阀盖内壁设置为圆锥面， 所述密封环 的上下两个密封面设置为圆柱面。
本发明双密封阀门结构， 两个密封副的摩擦角 Θ大于或等于临界摩擦角， 所述 临界摩擦角为两个摩擦面之间的摩擦系数的反正切函数取值， 所述摩擦角 Θ分别 为阀盖内壁与阀盖中心线垂直平面的夹角， 以及密封座上表面与阀杆径向平面 的夹角。
所述密封圏由刚性材料制成或软性材料制成， 如金属密封圏、 橡胶密封圏或塑 料密封圏。
本发明的密封系统在阀杆上套有所述的密封圏， 该密封圏的内圆柱面与阀杆有 一定的间隙， 可以自由活动。 在阀杆上密封座上制作出密封面 （称为阀杆密封 面） ， 在阀盖内部垂直于阀杆轴线壁面制作出密封面 （称为阀盖密封面） ， 所 述密封圏的上下两面分别制作出与阀盖密封面和阀杆密封面相配合的密封面。 当阀杆上升到接近极限位置， 而阀杆中心线与阀盖中心线出现偏离吋， 所述密 封圏可在垂直于阀盖中心线的面内向着压力小的方向移动， 而不需使阀杆与阀 盖的中心线严格重合就可保证上密封为零泄漏， 从而可保证在阀门长期工作过 程中， 有效保护阀杆填料密封。
[16] 所述密封圏的密封面、 与之相配合的阀杆密封面和阀盖密封面均可以制成锥面 ， 也可以制成圆柱面等曲面， 优选方案是阀杆密封面和阀盖密封面制成圆锥面 ， 密封圏的两个密封面制成圆柱面或其他曲面， 这样的结果是密封圏的密封面 与阀杆密封面和阀盖密封面均为线接触， 具有更好的密封效果。
[17] 与现有技术相比， 本发明具有以下有益效果：
[18] 本发明的密封系统在阀杆上套有所述的密封圏， 该密封圏的内圆柱面与阀杆有 一定的间隙， 可以自由活动， 当阀杆受到较大出现偏离吋， 所述密封圏可在垂 直于阀盖中心线的面内向着压力小的方向移动， 自动调整位置而不需使阀杆与 阀盖的中心线严格重合就可保证上密封为零泄漏， 从而可保证在阀门长期工作 过程中， 有效保护阀杆填料密封。
[19] 现有技术的阀门随着使用吋间的延长， 开关次数的增加， 密封填料弹性逐渐失 效， 此吋容易发生阀门内的介质泄露， 介质的压力直接作用于密封填料与阀杆 之间， 最终将从间隙中泄露出来。 本发明的技术方案在阀盖和阀瓣之间设置了 密封圏， 实质上是在介质与阀杆、 密封填料之间建立了缓冲带， 有效降低了周 围介质压力， 延长了密封填料的使用寿命， 增加了阀门的安全性。
[20] 而且， 阀门在管道系统中应用广泛， 维持管道运行需要大量能源， 其中停止阀 门和启动阀门是损耗能源的来源之一， 本发明提供的技术方案实现了不停止阀 门工作在线更换密封填料， 在节能降耗方面有着不可忽视的积极作用， 同吋， 本发明提供的方法成本低， 便于操作和推广， 使现有技术中的管道系统运行成 本大幅下降， 而且还有利于环境保护。 可以不停止阀门工作就能安全更换密封 填料的。
[21] 附图说明
[22] 图 1和图 2是已有技术密封系统的示意图， 图 1为阀门全开的情况， 图 2为阀门全 闭的情况； [23] 图 3为阀杆密封面与垂直于中心线的平面的摩擦角 Θ的示意图；
[24] 图 4是阀盖上密封面与垂直于中心线的平面的摩擦角 Θ的示意图；
[25] 图 5和图 6为实施例 1的密封系统示意图； 图 5为阀门全开的情况， 图 6为阀门全 闭的情况。
[26] 具体实施方式
[27] 以下通过具体的实施例进一步说明本发明的技术方案。
[28] 实施例 1
[29] 如图 5所示的双密封阀门结构， 包括阀瓣 1、 阀杆 2、 阀杆上的密封座 21、 阀盖 3 、 密封填料 4、 填料压套 5和密封环 6。 阀杆 2、 填料压套 5与阀盖 3之间设置的密 封填料 4作为第一层密封结构， 第一层密封结构的下端还设有第二密封结构， 是 自压式硬密封结构， 即通过设在阀杆上的密封座 21与阀盖 3内壁之间的金属密封 面对金属密封面的密封结构， 所述第二密封结构之间还设置有辅助密封结构， 即套在阀杆 2上的密封环 6， 密封环 6为金属密封环， 其底面置于阀杆的密封座 21 上， 且密封环 6与阀杆 2之间还存在使密封环能在密封座上移动的间隙。 如图 6所 示， 升起阀瓣 1完全打开阀门后， 阀盖 3底部和阀杆密封座 21紧压密封圏 6， 实现 密封目的， 此吋可以很方便地更换密封填料 4。 该系统由于在阀瓣、 阀杆和密封 填料之间建立了缓冲带， 有效降低了周围介质压力， 延长了密封填料的使用寿 命， 而且整个操作过程中， 只需要起落阀瓣而不需要进行停止阀门和启动阀门 的操作， 不仅简化了操作程序， 而且减少了能量消耗。
[30] 为了保证密封圏能够在阀杆密封面与阀盖密封面两个面之间的固体压力下沿径 向移动， 两个密封面的摩擦角 Θ均需大于临界摩擦角， 如图 3、 4所示。 这两个参 数之间的关系为： 摩擦角 Θ大于或等于临界摩擦角， 所述临界摩擦角为两个摩擦 面之间的摩擦系数的反正切函数取值， 也即是摩擦面材质和表面粗糙度的函数 。 所述摩擦角 Θ分别为阀盖内壁与阀盖中心线垂直平面的夹角， 以及密封座上表 面与阀杆径向平面的夹角。

Claims

权利要求书
[1] 一种双密封阀门结构， 包括阀杆和阀盖， 所述阀杆与阀盖之间设置有密封 填料作为第一层密封结构， 第一层密封结构的下端还设有第二密封结构， 所述第二密封结构为自压式硬密封结构， 即通过设在阀杆上的密封座与阀 盖内壁之间的金属密封面对金属密封面的密封结构， 其特征在于所述第二 密封结构之间还设置有辅助密封结构， 所述辅助密封结构为套在阀杆上的 密封环， 密封环的底面置于阀杆的密封座上， 且密封环与阀杆之间还存在 使密封环能在密封座上移动的间隙。
[2] 根据权利要求 1所述的双密封阀门结构， 其特征在于所述密封环与第二密封 结构之间形成的两个密封副均为线接触。
[3] 根据权利要求 2所述的双密封阀门结构， 其特征在于所述线接触为将
阀杆上的密封座上表面、 阀盖对应的内壁、 以及密封环的上下两个密封面 设置成曲面。
[4] 根据权利要求 3所述的双密封阀门结构， 其特征在于所述阀杆上的密封座上 表面和阀盖内壁设置为圆锥面， 所述密封环的上下两个密封面设置为圆柱 面。
[5] 根据权利要求 2或 3或 4所述的双密封阀门结构， 其特征在于两个密封副的摩 擦角大于或等于临界摩擦角， 所述临界摩擦角由两个摩擦面的摩擦系数的 反正切函数取得。
[6] 根据权利要求 5所述的双密封阀门结构， 其特征在于所述摩擦角分别为阀盖 内壁与阀盖中心线垂直平面的夹角， 以及密封座上表面与阀杆径向平面的 夹角。
[7] 根据权利要求 6所述的双密封阀门结构， 其特征在于所述密封圏由刚性材料 制成或软性材料制成。
[8] 根据权利要求 7所述的双密封阀门结构， 其特征在于所述密封圏是金属密封 圏、 橡胶密封圏或塑料密封圏。
PCT/CN2009/073432 2008-12-30 2009-08-21 一种双密封阀门结构 WO2010081324A1 (zh)

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CN101451625B (zh) * 2008-12-30 2013-02-27 广东联塑科技实业有限公司 一种双密封阀门结构
CN106402476A (zh) * 2016-11-14 2017-02-15 东阀门制造（南通）有限公司 一种阀杆金属c型圈密封结构

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CN2063593U (zh) * 1990-01-12 1990-10-10 周明善 双关式闸阀
CN2145292Y (zh) * 1992-12-30 1993-11-03 徐明林 自动加压补偿无泄漏闸阀
US5435520A (en) * 1994-09-07 1995-07-25 Cooper Industries, Inc. Backseat assembly for an expanding gate valve
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