WO2007022721A1 - Joint d'etancheite de tige - Google Patents

Joint d'etancheite de tige Download PDF

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Publication number
WO2007022721A1
WO2007022721A1 PCT/CN2006/002156 CN2006002156W WO2007022721A1 WO 2007022721 A1 WO2007022721 A1 WO 2007022721A1 CN 2006002156 W CN2006002156 W CN 2006002156W WO 2007022721 A1 WO2007022721 A1 WO 2007022721A1
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WO
WIPO (PCT)
Prior art keywords
ball
seal
socket
sleeve
wedge
Prior art date
Application number
PCT/CN2006/002156
Other languages
English (en)
French (fr)
Inventor
Changxiang Xu
Original Assignee
Zhejiang China Valve Co., Ltd.
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 Zhejiang China Valve Co., Ltd. filed Critical Zhejiang China Valve Co., Ltd.
Priority to US12/064,561 priority Critical patent/US8382067B2/en
Publication of WO2007022721A1 publication Critical patent/WO2007022721A1/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
    • F16K41/04—Spindle sealings with stuffing-box ; Sealing rings with at least one ring of rubber or like material between spindle and housing

Definitions

  • the present invention relates to the sealing of a movable rod, and more particularly to a pole seal and a shoulder seal of a movable rod. Background technique
  • the valve acts as a fluid transfer and control unit with a switching element, such as a ball in a ball valve and a gate in a gate valve.
  • the switch element is inserted horizontally in the fluid passage, and has an open position for allowing the medium to flow past. There is a closed position for preventing the flow of the medium.
  • the movement from open to closed and from off to open is through the valve stem extending outside the body. Realized.
  • the stem extends from the body or bonnet to the outside of the body and requires a seal to prevent fluid leakage along the rod.
  • some valves require only post seals, some require only shoulder seals, and some require both post seals and shoulder seals.
  • valve stems such as the ball valve and the valve stem of the gate valve
  • the valve stem must not be ejected from the outside of the valve body by the internal pressure top when the valve stem packing or packing pressure ring is removed. Therefore, the valve stem should have a shoulder and pressure. Resting on the inside of the stem outlet prevents the stem from opening out of the bottom outlet of the door stuffing box. That is to say, the valve stem, in particular the ball valve stem, has two seals, one is a thrust seal on the inside of the stem exit, and the other is a cylindrical seal in the stuffing box on the outside of the stem exit.
  • the traditional stem shoulder is a flat boss on the rod (see Figure 3a) or a tapered boss (see Figure 3b) with a corresponding flat or tapered pad between the boss and the seat.
  • the stem of the stem disclosed in the patent US Pat. No. 6,129,336 is a ball, and a spherical pad is used between the spherical shoulder and its seat.
  • a conventional pole seal packing is a set of flat pads (see Figure 3a) or a set of V-shaped pads (see Figure 3b). This set of pads is sealed by axial pressure and by a pole. Since the pressure decreases in the axial direction, the holding force of the packing pad against the rod is not uniform in the axial direction. Since the valve stem, the packing, the stuffing box, and the packing pressing ring cannot be completely concentrically mounted and symmetrically pressed, the packing is applied to the rod. The holding force is not uniform along the circumference, so that when When the valve stem is completely sealed, some points have reached the level of over-squeezing which is extremely easy to wear, that is, the prior art sealing packing structure has low material utilization rate and is not wear-resistant.
  • ASME B16. 34-2004 7.1.1 stipulates that the valve body shall be subjected to at least 1. 5 times the rated working pressure without leakage in the half-open state, ie including the stem seal. However, in paragraph 7.1.3, it is added that the valve stem leakage shall not be used as a reason for rejection; the valve stem seal shall not be at least 38 ° C rated pressure when it passes the 1.5 times rated working pressure test. Visible leaks. API 6D/IS0 14313 and other valve standards are also specified. That is to say, the existing valve stem sealing technology can not meet the actual needs, and even the standard has to make concessions at the expense of valve reliability.
  • the first object of the present invention is to provide a cylindrical seal with a radial pole for the movable rod, the shaft, the pin, etc.
  • the second purpose is to provide a shoulder seal for the movable rod, the shaft, the pin, etc.
  • the third The purpose is to provide a movable rod/shaft seal with a cylindrical seal and a shoulder seal, so that the stem post seal and the stem shoulder seal are independently subjected to at least 1.5 times the rated working pressure of the valve, and double the German TA Luf t ( Air Quality Control Technical Directive) requirements.
  • the pole seal of the present invention is a pole seal of a triangular section sleeve, characterized in that the sleeve is sealed by the sleeve against the movable rod while being pressed against the sleeve of the rod outlet by the sleeve pressing ring.
  • the sleeve inner cylindrical surface formed by one side of the triangular cross section of the sleeve serves as the rod sealing surface
  • the outer sleeve surface formed by the other side serves as a sealing surface of the sleeve, and the third side is formed
  • the outer cone surface is used as a pressing surface of the sleeve ring
  • the sleeve has a triangular cross section, which is a truncated triangle when worn and assembled with a compression allowance, and is a wear-free and assembly compression margin. Fully triangular.
  • the pressing force of the sleeve on the sleeve and the reaction force of the sleeve to the sleeve are combined into a radial pressure on the sleeve, acting on the outer cylindrical surface formed by the truncated edge. Therefore, the rod seal assembly of the present invention is no longer needed.
  • the stuffing box that is, the pole seal of the present invention is no longer bound by the stuffing box, and is free to swing with the rod to have a uniform symmetry
  • the radial clamping force provides an efficient, compensated and wear-resistant seal for the moving rod cylinder.
  • the column seal of the triangular section sleeve is free of air bubbles, so the seal is safe and reliable when the temperature changes.
  • the experiment confirmed that when the triangular sealing sleeve is used as the stem column seal, it can be tested without leakage.
  • the bursting pressure of the valve body is equal to 4 times the rated working pressure of the valve.
  • the post seal of the triangular section has the same reliability as the valve body and can meet the requirements of the German TA Lnf t (Air Quality Control Technical Directive).
  • the shoulder seal of the present invention is a spherical wedge/wonk-fitted shoulder seal, characterized in that the spherical wedge is a shoulder on the rod, and the spherical socket is a seat on the rod outlet, through which the shoulder is The closed fit of the seat achieves sealing of the movable rod; the diameter of the ball wedge is equal to or economically slightly larger than the diameter of the socket with which the ball socket is seated, and the center of the ball socket is economically slightly offset from the ball socket a plane of the socket, ensuring that the first closed mating contact of the ball with the socket is at the socket and approaching the large circle of the wedge ball, that is, ensuring that the ball wedge is a small angle wedge relative to the mating ball socket, or even A small operating force on the ball wedge can produce a squeezing force that tends to infinity for the mating ball socket, whereby the hardened metal ball wedge cooperates with the annealed ball socket
  • the seal is completed once it
  • the spherical wedge/socket mating pair when used as the stem shoulder seal, it can be tested without leakage.
  • the bursting pressure of the valve body is equal to 4 times the rated working pressure of the valve.
  • the spherical wedge/wonk-fitted shoulder seal has the same reliability as the valve body and meets the requirements of the German TA Luf t (Air Quality Control Technical Directive).
  • Figure 1 is a partial cross-sectional view of a ball valve stem assembly including a triangular section sleeve post seal and a ball wedge/socket mat shoulder seal of the present invention.
  • Figure 2 is a triangular section seal sleeve taken from the post taken from Figure 1 for illustrating the working principle of the triangular section post seal of the present invention.
  • Figure 3a is a partial cross-sectional view of a conventional valve stem assembly including a set of flat pad post seals and a pair of flat shoulder pad shoulder seals.
  • the figure is a pole seal and a pair including a set of V-shaped pads
  • Figure 4 is a hemisphere supported by a seat ring on its small circle for illustrating the working principle of the ball wedge/well mating shoulder seal of the present invention.
  • Figure 5 is a spherical wedge/pocket shoulder seal fit pair taken from Figure 1 for illustrating the construction and operation of the ball wedge/socket mat shoulder seal of the present invention.
  • Figure 6 is a cross-sectional view of an integral ball valve including a triangular section arbor seal and a spherical wedge/wolt-fit shoulder seal of the present invention.
  • FIG 7 is an assembled perspective view of one of the ball valve 6
  • FIG. 8 is an exploded perspective view of a one-piece ball valve of FIG.
  • Figures 9, 10 and 11 are the same ball-and-wedge needle valve including a triangular section sleeve post seal and two spherical wedge/socket mating pairs of the present invention, wherein a spherical wedge/socket mating pair is used for valve opening and closing The other is the valve body seal pair.
  • the same parts are numbered the same. The best way to implement the invention
  • Figures 1, 6, 7 and 8 show the same ball valve, the same one-piece ball valve, where the same parts use the same part number.
  • this ball valve there is a medium flow control assembly and a stem seal assembly.
  • the flow control assembly is formed by the internal pressure plug 05 engaging the thread of the valve body 01 to fix the switch ball 03 and the valve seat 02 in the valve body.
  • the switch ball 03 captured in the two seats 02 has a through hole that provides full-pass, split-pass, and fully-closed fluid control via the handle 14 on the stem 06 or the drive.
  • the stem seal assembly consists of a triangular section post seal and a spherical wedge/socket mat shoulder seal (see Figure 1).
  • the triangular sealing sleeve 09 is engaged with the sleeve 06 by the sleeve ring 10 and the disc washer 11 and the nut 12 which are fitted on the valve stem 06, and is clamped on the sleeve at the rod outlet of the valve body 01 to provide the valve stem.
  • the cylinder is sealed.
  • the spherical wedge/nove mating pair consists of a ball wedge on the stem 06 and a ball seat on the body 01. While the triangular seal 09 is crimped to provide a post seal on its seat, the ball wedge shoulder is tensioned against its mating ball seat to provide a shoulder seal.
  • Figure 2 shows a triangular section seal sleeve 09 which is removed from the rod seal assembly of Figure 1 and which is placed on the post 06, wherein the press ring 10 is pressed against the sleeve 09 and the F b is the sleeve.
  • F is the resultant force of ⁇ and ⁇ . Since the resultant force F acts radially on the outer surface of the triangular sealing sleeve 09 , the triangular sealing sleeve does not need to be restrained by the stuffing box like the conventional packing of Figs. 3a and 3b, and can be freely swinged with the rod.
  • the spherical wedge/wonk-fitted shoulder seal is a rod seal that utilizes the wedge function of the ball, wherein the stem holder on the valve body is a ball whose economy is slightly offset from its socket.
  • the shoulder on the valve stem is a ball wedge whose diameter is equal to or economically slightly larger than the diameter of the ball socket ball with which it fits, ensuring the ball wedge shoulder
  • the first closing fit of the ball socket is at the socket and close to the wedge circle.
  • the sealing force provided by the tightening nut is axial, which is the direct need for the shoulder seal, not the direct need for the post seal; the axial seal is required for the shoulder seal Tightening, and the column seal requires a radial pressing force; that is, the post seal requires a much larger sealing force than the shoulder seal requires.
  • the sealing power is so large that the post seal is in effect, the shoulder seal is often worn out and fails.
  • the modified V-shaped pad can provide a radial seal component that improves the synchronization of the shoulder seal with the post seal, the yin and yang V-shaped angular gap
  • the air bubble with a large temperature change and the volume change of the disk spring can not keep up with the need for the change of the disc spring, and even the high and low temperature change rod seal failure.
  • the flat shoulder/pad assembly of Figure 3a and the tapered shoulder/pad assembly of Figure 3b will leak.
  • 01 is the valve body
  • 0 2 is the valve seat
  • 03 is the switch ball
  • 04 is the trapezoidal body seal ring
  • 05 is the inner pressure plug
  • 06 is the valve stem
  • 08 is positioning and electric ball
  • 09 is triangular sealing sleeve
  • 10 is sleeve pressure ring
  • 11 is disc spring
  • it is hex nut
  • 13 is nut stop pad
  • 14 is handle
  • 15 is handle Stop pin.
  • Figures 9, 10 and 11 show the same needle valve, the same ball wedge needle valve, where the same parts use the same part number, 21 is the valve body, 22 is the valve cover, 23 is The valve stem, 2 4 is the ball wedge valve flap, 25 is the triangular sealing sleeve, 26 is the ball wedge sealing sleeve, is the lock nut, 28 is the shield, 29 is the handle, 30 is the screw, 31 is the sealing hoop, 3 2 is Hold the hoop, 33 is the drive nut.
  • the ball wedge type valves there is a triangular seal sleeve 25 serving as a post seal, a 26 for the body seal and a 24 ball wedge/socket mat for the opening and closing.
  • a triangular seal sleeve 25 serving as a post seal
  • a 26 for the body seal and a 24 ball wedge/socket mat for the opening and closing.
  • the ball valve and needle valve described above are merely two examples for illustrating the structure of the present invention.
  • anyone in the industry can use the triangular section as the pole seal in other valves and machines according to the above description, using the spherical wedge/wonn mating pair as the shoulder seal and opening and closing pair in other valves and as the shaft in other machines. Thrust bearings and seals.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Taps Or Cocks (AREA)
  • Gasket Seals (AREA)
  • Sealing Devices (AREA)

Description

杆密封 技术领域
本发明涉及活动杆的密封， 特别涉及活动杆的杆柱密封和杆肩密封。 背景技术
很多机器或装置都有传动杆， 从其有流体的腔内伸到腔外传递动力。 这 些杆都需要密封以防止流体沿杆泄漏， 但有的杆仅设置柱面密封， 有的杆仅 设置肩密封， 有的杆既设置柱面密封又设置肩密封。 有时， 这些杆变称为销 或轴。
例如， 阀门作为流体传输与控制单元， 有一个开关元， 如球阀中的球， 闸阀中的闸。开关元横插在流体通道中，有一个允许介质流过去的开通位置， 有一个阻止介质流过去的关闭位置， 其从开到关和从关到开的运动是通过伸 到体外的阀杆来实现的。 阀杆从阀体或阀盖内伸到体外， 需要密封， 阻止流 体沿杆泄漏。 然而， 有的阀门仅需要杆柱密封， 有的阀门又仅需要杆肩密封， 有的阀门既需要杆柱密封， 又需要杆肩密封。
按照相关阀门标准规定， 阀杆， 如球阀和闸阀的阀杆， 不得在卸去阀杆 填料或填料压环的情况下被内部压力顶射出阀体外， 因此， 阀杆应有一个止 肩， 压靠在阀杆出口内侧， 防止阀杆窜出闽门填料函底部出口。 也就是说， 阀杆， 特别是球阀阀杆， 有两个密封， 一个是位于阀杆出口内侧的止推密封， 一个是位于阀杆出口外侧的填料函内的柱面密封。装配时， 阀杆周围的填料， 通过填料压环、 弹性垫圈和同阀杆啮合的螺母， 被压在阀杆出口外侧的填料 函底而提供一个杆柱密封的同时， 再把阀杆止肩拉紧在填料函底对面的阀杆 出口内侧而提供一个杆肩密封。
传统阀杆止肩是杆上的一个平凸台（参见图 3a)或锥凸台（参见图 3b)，在 凸台和止口座间有一个相应的平垫或锥垫。 专利 US6129336披露的阀杆止肩 是一个球， 在球形止肩及其止座间使用的是一个球面垫。 阀杆受力歪斜时， 平面杆肩配合和锥面杆肩配合会虛缝泄漏， 球面配合可绕球心转动而不会虛 缝泄漏。
传统的杆柱密封填料是一组平垫（参见图 3a)或一组 V型垫（参见图 3b)。 这组垫均靠轴向压力而抱杆完成密封。 由于压力沿轴向递减， 因而填料垫对 杆的抱紧力沿轴向不均匀， 由于阀杆、 填料、 填料函、 填料压紧环不可能完 全同心安装、 对称压紧， 因而填料对杆的抱紧力沿周向也不均匀， 以至于当 阀杆整体完成密封时某些点已达极易磨损的过挤压程度， 也就是说， 已有技 术的密封填料结构的材料利用率低而不耐磨。由于密封动力是沿阀杆轴向的， 对阀杆的止推端面的密封作用是直接的， 对阀杆柱面通过填料的密封作用是 间接的， 特别是对于径向密封分力为零的盘根与平垫填料， 根本不可能与端 面密封同时生效， 往往都是当止推肩端面密封生效时填料密封未生效， 当填 料密封生效时止推端面密封累遭挤坏， 虽然 V形截面组垫的阴阳 V形配合可 产生径向密封分力， 但上***阳 V形角度差缝中有排不尽的受温度和压力变 化影响极大的压缩空气， 因此， 同已有技术的其它填料一样， 都是密封调节 不灵敏以至于弹簧补偿无效。
ASME B16. 34-2004的 7. 1. 1款规定， 阀体应在半开状态下， 即包括阀杆 密封在内， 至少承受 1. 5倍额定工作压力***漏。但其 7. 1. 3款又补充规定, 阀杆泄漏不得作为拒收的理由； 阀杆密封， 当其通不过 1. 5倍额定工作压力 测试时， 应至少在 38°C额定压力下无可见泄漏。 API 6D/IS0 14313及其它 阀门标准也如此规定。 也就是说， 现有阀杆密封技术满足不了实际需要， 乃 至标准不得不以牺牲阀门可靠性为代价地对其作出让步。
在欧洲， 为满足德囯 TA Luft (空气质量控制技术指令）要求， 阀门制造 商不得不在现有填料阀杆密封的基础上， 在阀杆上再增加一两圈 "0"型密封 圈。 发明的公开
本发明的第一个目的是为活动杆、 轴、 销等提供一个有径向抱杆分力的 柱面密封， 第二个目的是为活动杆、 轴、 销等提供一个肩密封， 第三个目的 是提供一个有柱面密封和肩密封的活动杆 /轴密封，使阀杆柱密封和阀杆肩密 封分别独立承受至少 1. 5倍阀门额定工作压力， 双倍满足德国 TA Luf t (空 气质量控制技术指令)要求。
本发明的杆柱密封是一种三角截面套的杆柱密封， 其特征是所述的套， 通过套压环， 压在杆出口的套座上的同时， 实现由柱面对活动杆的密封； 所 述套的截面三角形的一条边形成的套内圆柱面用作所述的杆柱密封面， 另一 条边形成的套外锥表面用作所述套座的密封面， 第三条边形成的套外锥表面 用作所述套压环的压紧面； 所述套的截面三角形， 在有磨损和装配压缩余量 时是一截顶三角形， 在无磨损和装配压缩余量时是一完全三角形。 套压环对 套的压紧力和套座对套的反作用力合成为对套的径向压力， 作用于截顶边形 成的外圆柱表面， 因此， 本发明的杆柱密封装配再也不需要填料函， 即本发 明的杆柱密封再也不受填料函的约束而可自由随杆摆动地拥有一个均匀对称 的径向抱杆分力，为活动杆柱面提供一个高效的、补偿灵敏的和耐磨的密封。 此外， 三角截面套的杆柱密封无空气泡， 因此， 温度变化时密封安全可靠。
实验证实， 三角密封套用作阀杆柱密封时， 可随体承受体破裂压力测试 ***漏。 一般地说， 阀体的破裂压力等于阀的 4倍额定工作压力。 也就是说, 三角截面套的杆柱密封拥有和阀体相同的可靠性， 能够满足德国 TA Lnf t (空 气质量控制技术指令)要求。
本发明的杆肩密封是一种球形楔 /窝配合杆肩密封，其特征是所述球形楔 是杆上的止肩， 所述球形窝是杆出口上的止座， 通过所述止肩与所述止座的 闭合配合实现对活动杆的密封； 所述球楔的直径等于或经济地稍大于与其配 合的球窝座的直径， 所述的球窝座的球心经济地稍稍偏离出其窝口平面， 保 证球与窝的首次闭合配合接触就在所述的窝口并逼近所述的楔球大圆， 即保 证所述的球楔相对其所述配合球窝座是小角度楔， 乃至所述球楔上的一个小 小操作力就可对所述配合球窝座产生一个趋于无穷大的挤扩力， 藉此， 淬硬 的金属球楔对退火的配合球窝座的配合， 就象传统的金属对非金属密封副一 样，一旦轻轻操作闭合就完成密封， 而且只要所述球楔有适度的圆度和硬度， 每次操作中无论所述球楔怎样转动和歪斜地挤压和磨损所述配合球窝座， 所 述的配合接触始终在没有直径变化的所述球楔的球面上， 即所述球楔的转动 和歪斜不仅丝亳不影响闭合配合的密封性， 还越磨损， 闭合配合的密封性越 紧密， 越不被磨损。
实验证实，球形楔 /窝配合副用作阀杆肩密封时， 可随体承受体破裂压力 测试***漏。 一般地说， 阀体的破裂压力等于阀的 4倍额定工作压力。 也就 是说， 球形楔 /窝配合杆肩密封拥有和阀体相同的可靠性， 能够满足德国 TA Luf t (空气质量控制技术指令)要求。
可想而知， 有三角截面套杆柱密封和球形楔 /窝配合杆肩密封的活动杆 / 轴密封， 可双倍满足德国 TA Luft (空气质量控制技术指令)要求。
附图的简要说明 图 1 是一个包括有本发明的三角截面套杆柱密封和球形楔 /窝配合杆肩 密封的球阀阀杆总成的局部剖面图。
图 2是一个从图 1中取出来的套在杆柱上的三角截面密封套， 用于说明 本发明的三角截面套杆柱密封的工作原理。
图 3a 是一个包括有一组平垫的杆柱密封和一副平肩垫的杆肩密封的传 统阀杆总成的局部剖面图。图 是一个包括有一组 V型垫的杆柱密封和一副 锥或球肩垫的杆肩密封的传统阀杆总成的局部剖面图。
图 4是一个被座口支承在其小圆上的半球， 用于说明本发明的球形楔 / 窝配合杆肩密封的工作原理。
图 5是一个从图 1中取出来的球形楔 /窝杆肩密封配合副，用于说明本发 明的球形楔 /窝配合杆肩密封的结构和工作。
图 6是一个包括有本发明的三角截面套杆柱密封和球形楔 /窝配合杆肩 密封的一体式球阀的剖面图。
图 7是图 6的一体式球阀的装配透视图， 图 8是图 6的一体式球阀的分 解透视图。
图 9、10和 11是包括有本发明的一个三角截面套杆柱密封和两个球形楔 /窝配合副的同一个球楔针型阀，其中一个球形楔 /窝配合副是作阀门启闭副， 另一个是作阀体密封副。 在三个图中 , 相同的零件用的是相同的零件号。 实现本发明的最佳方式
图 1、 6、 7和 8所显示的都是同一个球阀， 同一个一体式球阀， 其中， 相同的零件用的是相同的零件号。 在这个球阀中， 有一个介质流动控制总成 和一个阀杆密封总成。流动控制总成是通过内压塞 05同阀体 01的螺紋啮合， 把开关球 03和阀座 02固定在阀体中而形成的。被俘获在两个阀座 02中的开 关球 03有一个通孔， 可通过阀杆 06上的手柄 14或驱动器转动提供全通、部 分开通和全闭流体控制。 阀杆密封总成包括一个三角截面套杆柱密封和一个 球形楔 /窝配合杆肩密封 (参见图 1)。 三角密封套 09是通过套装在阀杆 06上 的套压环 10和碟型垫圈 11及螺母 12同杆 06的啮合，夹压在阀体 01的杆出 口处的套座上而为阀杆提供柱面密封的。 球形楔 /窝配合副是由阀杆 06上的 一个球楔肩和闹体 01上的一个球形座组成的。 随着三角密封套 09夹压在其 座上提供杆柱密封的同时， 球楔杆肩被拉紧在其配合球形座上而提供杆肩密 封。
图 2所展示的是一个从图 1的杆密封总成中取出来的套在杆柱 06上的三 角截面密封套 09 , 其中 是套压环 1 0对套 09的压力， Fb是套座对套 09的 反作用力， F是 ^和 ^的合力。 因为合力 F是径向地作用在三角密封套 09 的外表面上的， 所以， 三角密封套再不需要象图 3a和图 3b的传统的填料一 样受填料函的约束而可自由随杆摆动地拥有一个非常均匀对称的径向抱杆分 力、 一个非常强悍的耐磨性和一个非常高效的轴向夹压动力， 乃至碟型弹簧 垫圈 11对磨损和温度变化的补偿更有效更灵敏。 如图 4所示， 一个被座口 B-B支承着的半球， 在其中心施加一个力 P, 就可在点 B对座口产生两个力： f=P/2 s ina, 其中 α是球在 B点的等效锥体 楔角。 由公式不难看出， 支点 Β越靠近大圆（通过球心的圆）， 球的楔功能越 强； 当支点 Β逼近大圆时， 球在支点 Β对配合座的挤扩力 f 就趋于无穷大。 如图 5 所示， 球形楔 /窝配合杆肩密封就是利用球的这种楔功能的一种杆密 封， 其中阀体上的阀杆维持座是一个其球心经济地稍稍偏离出其窝口平面的 球窝座， 如偏出 δ=0. 2隱左右， 阀杆上的止肩是一个其直径等于或经济地稍 大于与其配合的球窝座球直径的球楔， 确保球楔肩与球窝座的首次闭合配合 接触就在窝口并靠近楔球大圆。
在图 3a的传统阀杆总成中， 紧固螺母提供的密封动力是轴向的， 正好是 杆肩密封的直接需要， 不是杆柱密封的直接需要； 杆肩密封所需要的是轴向 压紧力， 而杆柱密封所需要的是径向压紧力； 也就是说， 杆柱密封需要一个 比杆肩密封所需要的大得多的密封动力。 然而， 当密封动力大到使杆柱密封 生效时， 杆肩密封往往会被磨破而失效。 在图 3b的传统改进阀杆总成中， 尽 管改进的 V型垫可以为杆柱密封提供一个改进其同杆肩密封同步问题的径向 密封分力，但阴阳 V形角度差缝中的随温度变化而巨变体积的空气泡，又使碟 形弹簧的补偿调节能力跟不上巨变的需要，乃至高低温变化场合杆密封失效。 此外， 阀杆受力歪斜时， 图 3a的平面肩 /垫装配和图 3b的锥面肩 /垫装配会虛 缝泄漏。 如果用球面肩 /垫代替图 3b的锥面肩 /垫装配， 虽然阀杆受力歪斜时 杆肩装配不会虛缝泄漏， 但肩和座间必须使用一个不能耐高温高压的非金属 止推垫。如果使用三角密封套作阀杆柱密封，使用球形楔 /窝配合作阀杆肩密 封， 则阀杆密封总成就会有一个完全相互匹配的杆柱密封和杆肩密封， 完全 克服前述图 3a和 3b的杆密封的所有缺点， 变得非常理想。 应当指出， 改变三 角密封套的截面三角形的角度可以调整杆柱密封和杆肩密封的匹配特性。
在图 1、 6、 7和 8所示的球阀中， 01是阀体， 02是阀座， 03是开关球， 04是梯形体密封环， 05是内压塞， 06是阀杆， 07是定位与电通簧， 08是定 位与电通球， 09是三角密封套， 10是套压环， 11是碟簧， 是六角螺母， 13是螺母止动垫， 14是手柄， 15是手柄挡销。 在上述说明中未述说的那些 零件， 对业内人士而言， 是不难从传统的意义上理解它们的功能， 因此， 不 再此详述。
图 9、 10和 11所显示的都是同一个针型阀， 同一个球楔针型阀， 其中， 相同的零件用的是相同的零件号， 21是阀体， 22是阀盖， 23是阀杆， 24是 球楔阀瓣， 25是三角密封套， 26是球楔密封套, 是锁紧螺母， 28是护罩， 29是手柄， 30是螺钉， 31是密封箍， 32是抱持箍， 33是驱动螺母。 在这个 球楔针型阀中，有一个用作杆柱密封的三角密封套 25 , —个用作体密封的 26 和一个用作启闭的 24球形楔 /窝配合副。 对业内人士而言， 不难理解这些零 件的功能， 因此， 不再详述。
上述球阀和针型阀仅仅是用来说明本发明的结构的两个实例。 任何业内 人士都可根据上述叙述， 使用三角截面套作其它阀门和机器中的杆柱密封， 使用球形楔 /窝配合副作其它阀门中的杆肩密封和启闭副及作其它机器中的 轴止推轴承和密封。

Claims

权 利 要 求
1. 一种三角截面套的杆柱密封， 其特征是所述的套， 通过套压环， 压 在杆出口的套座上的同时，实现由柱面对活动杆的密封； 所述套的 截面三角形的一条边形成的套内圆柱面用作所述的杆柱密封面，另 一条边形成的套外锥表面用作所述套座的密封面，第三条边形成的 套外锥表面用作所述套压环的压紧面；所述套的截面三角形，在有 磨损和装配压缩余量时是一截顶三角形，在无磨损和装配压缩余量 时是一完全三角形。
2. 一种球形楔 /窝配合杆肩密封，其特征是所述球形楔是杆上的止肩， 所述球形窝是杆出口上的止座，通过所述止肩与所述止座的闭合配 合实现由杆肩对活动杆的密封;所述球楔的直径等于或经济地稍大 于与其配合的球窝座的直径，所述的球窝座的球心经济地稍稍偏离 出其窝口平面，保证球与窝的首次闭合配合接触就在所述的窝口并 逼近所述的楔球大圆，即保证所述的球楔相对其所述配合球窝座是 小角度楔,乃至所述球楔上的一个小小操作力就可对所述配合球窝 座产生一个趋于无穷大的挤扩力。
PCT/CN2006/002156 2005-08-23 2006-08-23 Joint d'etancheite de tige WO2007022721A1 (fr)

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