WO2015074296A1 - 一种全封闭多速缓冲被动液压缸 - Google Patents

一种全封闭多速缓冲被动液压缸 Download PDF

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Publication number
WO2015074296A1
WO2015074296A1 PCT/CN2013/088526 CN2013088526W WO2015074296A1 WO 2015074296 A1 WO2015074296 A1 WO 2015074296A1 CN 2013088526 W CN2013088526 W CN 2013088526W WO 2015074296 A1 WO2015074296 A1 WO 2015074296A1
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Prior art keywords
piston
shaft
cylinder
hollow shaft
inner cavity
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PCT/CN2013/088526
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English (en)
French (fr)
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周明泉
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周明泉
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Publication of WO2015074296A1 publication Critical patent/WO2015074296A1/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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • F16F9/483—Arrangements for providing different damping effects at different parts of the stroke characterised by giving a particular shape to the cylinder, e.g. conical
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/20—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with the piston-rod extending through both ends of the cylinder, e.g. constant-volume dampers
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/466—Throttling control, i.e. regulation of flow passage geometry

Definitions

  • the invention relates to the field of hydraulic cylinders, and in particular to a fully enclosed multi-speed buffer passive hydraulic cylinder. Background technique
  • the oil pressure buffer is widely used in the fields of automatic opening and closing control systems for automobiles, elevators, cranes and high lift pumps.
  • the principle of the oil pressure buffer in the prior art is when the shaft is impacted by an external force and drives the piston to squeeze the inner tube.
  • the hydraulic oil is discharged from the oil drain hole of the inner tube after being pressed, and the hydraulic oil discharged from the inner tube is also returned to the inner tube by the oil return hole of the inner tube; when the external force disappears, the spring bounces the piston back to the starting point. The next action.
  • the disadvantages of this type of buffer are: (1) The piston maintains a low speed throughout the buffer and reset stroke range, and the buffer speed is not adjustable; (2) The buffer speed is single, and the buffer speed is not adjustable, the buffering moment The impact on the hydraulic cylinder is large, which is easy to damage the cylinder.
  • an object of the present invention is to provide a passive hydraulic cylinder with multi-speed buffering, adjustable buffering speed, and simple structure.
  • a fully enclosed multi-speed buffer passive hydraulic cylinder includes a cylinder block, an end cover, a piston shaft and a piston, the end cover is tightly connected with the open end of the cylinder body, the cylinder body is filled with hydraulic oil, and the piston shaft is coaxially connected
  • the piston is sleeved on the piston shaft, and the piston body is sleeved on the piston shaft, wherein the cylinder inner cavity comprises a plurality of stroke segments of different inner diameters, and the piston moves in the cylinder body and has a clearance fit with each stroke segment. status.
  • the adjacent stroke segments are connected by a tapered transition section.
  • one end of the piston shaft is a hollow shaft, and at least two through holes are arranged on the hollow shaft to connect the hollow shaft inner cavity and the cylinder inner cavity, and the at least two through holes are respectively disposed on the left and right sides of the piston. side.
  • the hollow shaft inner cavity is connected with an adjusting screw, and the head of the adjusting screw extends into the hollow shaft inner cavity and the through hole opening on the right side of the piston is partially blocked.
  • a sealing ring is arranged at a joint between the piston shaft and the cylinder block and the end cover.
  • the outer ring of the piston is provided with a piston seal ring.
  • the hydraulic cylinder is provided with multiple stages of strokes with different inner diameters.
  • the gap between the piston and each stroke section is matched.
  • the gap size is related to the inner diameter of each stroke section. The larger the clearance, the faster the hydraulic oil communication speed on both sides of the piston. The smaller the piston is blocked, the faster the passive moving speed; conversely, the smaller the gap, the larger the piston is blocked, and the slower the passive moving speed of the piston, so as to achieve multi-speed segment buffering, smoother buffering, and reduce the piston shaft during the buffering process. The impact.
  • Cone transitions are provided between adjacent stroke sections of different inner diameters to prevent shocks or bursts caused by sudden changes in speed, which not only prolongs the service life of hydraulic cylinders, but also avoids noise generation.
  • the piston shaft adopts a hollow design at one end.
  • the two sides of the piston are provided with through holes of the inner cavity of the piston shaft and the inner cavity of the hydraulic cylinder, forming a low-speed oil discharge passage, and the adjusting screw is connected in the piston shaft, and the head of the screw is adjusted.
  • the part blocks the through hole on the right side, reduces the effective oil discharge section of the right side through hole, and adjusts the speed of the piston at a low speed to adjust the moving speed of the piston.
  • Figure 1 is a schematic structural view of the present invention
  • end cap 1 end cap 1
  • cylinder 2 piston shaft 3
  • piston 4 left through hole right through hole 6
  • seal 8 slow section 9
  • transition section 10 fast section 11.
  • a fully enclosed multi-speed buffered passive hydraulic cylinder includes an end cap 1, a cylinder block 2, a piston shaft 3, a piston 4, a left through hole 5, a right through hole 6, an adjusting screw 7, a sealing ring 8, a low speed section 9, transition 10, fast segment 11.
  • the end cap 1 is tightly connected to the left end surface of the cylinder block 2, and the cylinder block 2 is filled with hydraulic oil.
  • the piston shaft 3 is coaxially connected in series with the cylinder block 2 and the end cap 1, the piston shaft 3 and the cylinder block 2 and the end cap.
  • the piston 4 is fixed on the piston shaft 3, and the piston 4 is connected to the inner wall of the cylinder via a sealing ring, and the inner cavity of the cylinder is divided into a slow section 9 and a fast section 11 having different inner diameters.
  • the slow section 9 and the fast section 11 are smoothly connected by the tapered transition section 10, the piston 4 is matched with the inner wall of the slow section 9 with a small gap, and the piston 4 is matched with the transition section 10 and the fast section 11 with a large gap;
  • the outer end surface of the shaft is a hollow shaft, and the outer surface of the hollow shaft is provided with one or more left through holes 5 communicating with the inner cavity of the cylinder 2 and the inner cavity of the piston shaft 3 and one or more right through holes 6, the left through holes 5 And the right through hole 6 is respectively disposed on the left and right sides of the piston 4;
  • the inner cavity of the piston shaft 3 is provided with an internal thread, the external thread of the adjusting screw 7 is coupled with the internal thread of the piston shaft 3, and the left end of the adjusting screw 7 is screwed into the piston
  • the length of the shaft 3 to the right through hole 6 is adjustable, and the length of the adjusting screw 7 extending into the piston shaft 3 is adjustable By adjusting the length of the screw shaft 7 to extend into the piston shaft
  • the left through hole 5 quickly drains the oil to the right side of the piston, and the piston 4 moves to the left quickly;
  • the gap between the piston 4 and the inner wall of the transition section 10 gradually decreases, and the hydraulic oil on the left side of the piston 4 passes through
  • the gap and the left through hole 5 are decelerated and drained toward the right side of the piston, the resistance on the piston gradually increases, and the moving speed of the piston 4 decreases;
  • the piston 4 moves to the low speed section 9, the small gap between the piston 4 and the inner wall of the low speed section 9 is matched, the piston
  • the hydraulic oil on the left side of the fourth direction flows slowly to the right side of the piston through the left through hole 5, and the piston 4 is slowly moved to the left by the resistance until it moves to the leftmost end of the cylinder 2.
  • the piston shaft 3 moves quickly under the control of the hydraulic cylinder, then decelerates and moves, and finally moves slowly to complete the buffering.
  • the through hole 5 slowly drains the oil to the left side of the piston, and the piston 4 moves slowly to the right in the low speed section 9; the piston 4 moves to the transition section 10, and the gap between the piston 4 and the inner wall of the transition section 10 gradually increases, and the hydraulic oil on the right side of the piston 4 passes through
  • the gap and the left through hole 6 accelerate toward the left side of the piston, the piston 4 is gradually reduced by the hydraulic resistance, and the piston moves faster; when the piston 4 moves to the fast section 11, the hydraulic oil on the right side of the piston 4 smoothly passes the piston and the fast section
  • the 11 gaps quickly flow to the left and the piston 4 moves to the right quickly.
  • the piston moves slowly, and after the buffer is completed, it is accelerated to reset to the far right.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Actuator (AREA)

Abstract

一种全封闭多速缓冲被动液压缸，包括缸体（2）、端盖（1）、活塞轴（3）和活塞（4），端盖（1）与缸体（2）开口端密闭连接，缸体（2）内充有液压油，活塞轴（3）同轴串接缸体（2）的两端面，活塞（4）套接于活塞轴（3）上，缸体（2）内腔包括多段不同内径的行程段，活塞（4）在缸体内运动与各行程段呈间隙配合状态；活塞轴（3）一端为中空轴，中空轴上设有至少两只通孔（5，6）使中空轴内腔和缸体（2）内腔呈联通状态，至少两只通孔（5，6）分别设置于活塞（4）的左右两侧；中空轴内腔连接有调节螺杆（7），调节螺杆（7）的头部伸入中空轴内腔与活塞（4）右侧的通孔孔口呈部分堵塞状态。以此实现多速度缓冲，减小活塞轴（3）在缓冲过程中所受的冲击。

Description

一种全封闭多速缓冲被动液压缸
技术领域
本发明涉及液压缸领域， 具体涉及一种全封闭多速缓冲被动液压缸。 背景技术
油压缓冲器广泛应用于汽车、 电梯、 起重机及高扬程水泵的启闭自动控制系 统等领域，现有技术中的油压缓冲器原理是当轴心受外力冲击并带动活塞挤压内 管的液压油， 液压油受压后由内管的排油孔排出， 同时由内管排出的液压油也由 内管的回油孔回流到内管；当外力消失时，弹簧将活塞弹回始点等待下次的动作。 这种缓冲器的缺点是： （1 )在整个缓冲和复位行程范围内， 活塞一直保持较低的 速度， 且缓冲的速度不可调； （2)缓冲速度单一， 且缓冲速度不可调， 缓冲瞬间 的对液压缸的冲击力大， 易对气缸造成损伤。
发明内容
为解决现有技术中的不足， 本发明的目的在于提供一种多速缓冲、 缓冲速度 可调、 结构简单的被动液压缸。
本发明采取的技术方案为：
一种全封闭多速缓冲被动液压缸， 包括缸体、 端盖、 活塞轴和活塞， 所述端 盖与缸体开口端密闭连接，缸体内充有液压油，所述活塞轴同轴串接缸体的两端 面， 所述活塞套接于活塞轴上， 其特征在于， 所述缸体内腔包括多段不同内径的 行程段， 所述活塞在缸体内运动与各行程段呈间隙配合状态。
进一步地， 所述相邻行程段间经锥面过渡段连接。
进一步地， 所述活塞轴一端为中空轴， 中空轴上设有至少两只通孔使中空轴 内腔和缸体内腔呈联通状态， 所述至少两只通孔分别设置于活塞的左右两侧。
进一步地， 所述中空轴内腔连接有调节螺杆， 调节螺杆的头部伸入中空轴内 腔与活塞右侧的通孔孔口呈部分堵塞状态。
进一步地， 所述活塞轴与缸体及端盖的连接处设有密封圈。
再进一步地， 所述活塞外圈设有活塞密封圈。
采取以上技术方案后， 本发明的有益效果为：
( 1 )液压缸设有多级不同内径的行程段， 活塞与各行程段间分别间隙配合， 间隙大小与各行程段的内径相关， 间隙越大， 活塞两侧的液压油联通速度越快， 活塞受阻越小， 被动移动速度越快； 反之， 间隙越小， 活塞受阻越大， 活塞被动 移动速度越慢， 以此实现多速度段缓冲， 使缓冲更加平滑， 减小活塞轴在缓冲过 程中所受的冲击。
(2) 不同内径的相邻行程段间设置锥面过渡段， 防止速度突变而引发的冲 击或爆缸， 既延长了液压缸的使用寿命， 又避免噪音的产生。
( 3 ) 活塞轴采取一端中空设计， 活塞的两侧设有联通活塞轴内腔和液压缸 缸体内腔的通孔， 形成低速排油通道， 活塞轴内连接调节螺杆， 通过调节螺杆的 头部堵塞右侧的通孔，减小右侧通孔的有效排油截面来整低速排油速度， 从而调 整活塞的移动速度。 附图说明
图 1为本发明的结构示意图；
图中： 端盖 1， 缸体 2， 活塞轴 3， 活塞 4， 左通孔 右通孔 6， 调节螺杆 7， 密封圈 8， 慢速段 9， 过渡段 10， 快速段 11。 具体实施方式
以下结合附图对本发明的具体实施方式做进一步详述：
如图所示一种全封闭多速缓冲被动液压缸包括端盖 1， 缸体 2， 活塞轴 3， 活 塞 4， 左通孔 5， 右通孔 6， 调节螺杆 7， 密封圈 8， 低速段 9， 过渡段 10， 快速 段 11。 所述端盖 1与缸体 2左端面密闭连接， 缸体 2内充满液压油， 所述活塞 轴 3同轴串接于缸体 2和端盖 1， 活塞轴 3与缸体 2及端盖 1间设有密封圈 8， 所述活塞 4固定于活塞轴 3上， 活塞 4经密封圈与缸体内壁连接，所述缸体内腔 分为内径不同的慢速段 9和快速段 11， 所述慢速段 9和快速段 11间经锥面过渡 段 10平滑连接， 活塞 4与慢速段 9的内壁小间隙配合， 活塞 4与过渡段 10和快 速段 11大间隙配合； 所述活塞轴 3—端为中空轴， 中空轴的外表面设有联通缸 体 2内腔和活塞轴 3内腔的一个以上的左通孔 5和一个以上的右通孔 6， 所述左 通孔 5和右通孔 6分别设置于活塞 4的左右两侧； 活塞轴 3内腔设有内螺纹，所 述调节螺杆 7外螺纹与活塞轴 3的内螺纹配合连接，调节螺杆 7的左端旋入活塞 轴 3内腔至右通孔 6处，所述调节螺杆 7伸入活塞轴 3内的长度可调，通过旋转 调节螺杆 7调整其伸入活塞轴内的长度，调节螺杆头部堵塞右通孔 6的孔口的程 度， 达到调节油路的大小， 从而调节缓冲速度。
当活塞 4位于快速段 11，活塞轴 3受向左的力时，活塞轴 3拉动活塞 4左移， 活塞 4与快速段 11的内壁间有较大间隙， 活塞 4左侧的液压油经间隙及左通孔 5向活塞右侧快速排油， 活塞 4快速向左移动； 当活塞 4运动到过渡段 10， 活塞 4与过渡段 10内壁间间隙逐渐减小， 活塞 4左侧的液压油经间隙及左通孔 5向 活塞右侧减速排油， 活塞上的阻力逐渐增大， 活塞 4移动速度减低； 活塞 4运动 到低速段 9时， 活塞 4与低速段 9内壁间小间隙配合， 活塞 4左侧的液压油基本 经左通孔 5向活塞右侧缓慢流动，活塞 4受阻力加大而缓慢左移直至运动至缸体 2的最左端。 整个运动过程中， 活塞轴 3在液压缸的控制下先快速移动， 再减速 移动， 最后缓慢移动， 完成缓冲。
当活塞 4位于慢速段 9， 活塞轴 3受向右的力时， 活塞轴 3带动活塞 4向右 侧移动， 活塞 4右侧的液压油依次经右通孔 6、 活塞轴内腔、 左通孔 5向活塞左 侧缓慢排油， 活塞 4在低速段 9缓慢右移； 活塞 4运动至过渡段 10， 活塞 4与 过渡段 10内壁间间隙逐渐增大， 活塞 4右侧的液压油经间隙及左通孔 6向活塞 左侧加速流动， 活塞 4受液压阻力逐渐减小， 活塞运动速度加快； 活塞 4运动至 快速段 11时，活塞 4右侧的液压油顺畅地由活塞与快速段 11间的间隙快速向左 流动， 活塞 4快速向右移。 整个过程中， 活塞先缓慢移动， 完成缓冲后再加速移 动复位至最右侧。

Claims

O 2015/074296 to *il ¾ff ^fe -Η· PCT/CN2013/088526 、 一种全封闭多速缓冲被动液压缸， 包括缸体、 端盖、 活塞轴和活塞， 所述端 盖与缸体开口端密闭连接， 缸体内充有液压油， 所述活塞轴同轴串接缸体的 两端面， 所述活塞套接于活塞轴上， 其特征在于， 所述缸体内腔包括多段不 同内径的行程段， 所述活塞在缸体内运动与各行程段呈间隙配合状态。
、 根据权利要求 1所述的一种全封闭多速缓冲被动液压缸， 其特征在于， 所述 相邻行程段间经锥面过渡段连接。
、 根据权利要求 1所述的一种全封闭多速缓冲被动液压缸， 其特征在于， 所述 活塞轴一端为中空轴， 中空轴上设有至少两只通孔使中空轴内腔和缸体内腔 呈联通状态， 所述至少两只通孔分别设置于活塞的左右两侧。
、 根据权利要求 3所述的一种全封闭多速缓冲被动液压缸， 其特征在于， 所述 中空轴内腔连接有调节螺杆， 调节螺杆的头部伸入中空轴内腔与活塞右侧的 通孔孔口呈部分堵塞状态。
、 根据权利要求 1所述的一种全封闭多速缓冲被动液压缸， 其特征在于， 所述 活塞轴与缸体及端盖的连接处设有密封圈。
、 根据权利要求 1所述的一种全封闭多速缓冲被动液压缸， 其特征在于， 所述 活塞外圈设有活塞密封圈。
PCT/CN2013/088526 2013-11-21 2013-12-04 一种全封闭多速缓冲被动液压缸 WO2015074296A1 (zh)

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