WO2015192602A1 - 高压开关用液压操动机构及其液压工作缸 - Google Patents

高压开关用液压操动机构及其液压工作缸 Download PDF

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Publication number
WO2015192602A1
WO2015192602A1 PCT/CN2014/092207 CN2014092207W WO2015192602A1 WO 2015192602 A1 WO2015192602 A1 WO 2015192602A1 CN 2014092207 W CN2014092207 W CN 2014092207W WO 2015192602 A1 WO2015192602 A1 WO 2015192602A1
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WIPO (PCT)
Prior art keywords
piston
auxiliary piston
rod
cavity
auxiliary
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2014/092207
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English (en)
French (fr)
Inventor
顾根泉
赵羡丽
王亚辉
陶平
刘振华
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
PING GAO GROUP CO Ltd
Henan Pinggao Electric Co Ltd
State Grid Corp of China SGCC
Original Assignee
PING GAO GROUP CO Ltd
Henan Pinggao Electric Co Ltd
State Grid Corp of China SGCC
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Filing date
Publication date
Application filed by PING GAO GROUP CO Ltd, Henan Pinggao Electric Co Ltd, State Grid Corp of China SGCC filed Critical PING GAO GROUP CO Ltd
Publication of WO2015192602A1 publication Critical patent/WO2015192602A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1409—Characterised by the construction of the motor unit of the straight-cylinder type with two or more independently movable working pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1414—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F15B15/1452—Piston sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/17—Characterised by the construction of the motor unit of the straight-cylinder type of differential-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/24—Other details, e.g. assembly with regulating devices for restricting the stroke
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/22—Power arrangements internal to the switch for operating the driving mechanism
    • H01H3/24—Power arrangements internal to the switch for operating the driving mechanism using pneumatic or hydraulic actuator
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic

Definitions

  • the invention relates to a hydraulic operating mechanism for operating a high-pressure switch for operating a high-voltage switch, and the hydraulic working cylinder of the present invention is used in a hydraulic operating mechanism of a high-pressure switch.
  • Ultra-high voltage and ultra-high voltage switches such as circuit breakers and earthing switches, have high speed requirements for opening or closing due to their high voltage level and large breaking current (the circuit breaker requires high opening speed, and the grounding switch requires The brake speed is high, which requires the operating mechanism to provide greater operating work.
  • the hydraulic operating mechanism is commonly used in the existing ultra-high pressure and ultra-high pressure switches.
  • the hydraulic operating mechanism is characterized by constant charging and maintaining and instantaneous action.
  • Chinese Patent Publication No. 101527206A is a hydraulic operating mechanism of a high-voltage circuit breaker, which includes a working cylinder for outputting power and a piston rod for controlling the working cylinder.
  • Control valve, hydraulic operating mechanism In the specific application, the piston rod of the working cylinder and the moving end of the main fracture of the corresponding high-voltage switch are connected by a linkage mechanism, and the control valve controls the expansion and contraction of the piston rod of the working cylinder through the oil passage.
  • the working cylinder in the hydraulic operating mechanism is a conventional double-acting cylinder, including a cylinder block and a piston rod, and first and second oil ports are respectively arranged on the rod cavity and the rodless cavity of the cylinder body, and the control valve is adopted.
  • the cylinder has a rod cavity, a rodless cavity oil inlet, and a drain control to drive the piston and the piston rod to operate.
  • the main goal of the hydraulic operating mechanism is to meet the mechanical characteristics of the circuit breaker, and the main concern for the mechanical characteristics is the speed of the working cylinder.
  • the operating time of the hydraulic working cylinder during the opening operation is only about 30ms.
  • the speed of the moving system should be accelerated to 10m/s or more during the initial acceleration phase of the piston rod of the working cylinder.
  • a brake buffer and a closing buffer are also provided in the working cylinder for deceleration protection.
  • the hydraulic system must provide sufficient energy.
  • the opening speed required by the circuit breaker is the average speed within the specified time period or the stroke period.
  • the operating function of the mechanism is to increase the acceleration of the initial acceleration phase of the working cylinder.
  • the specific measures are to increase the energy stored in the accumulator, the size of the hydraulic working cylinder, the hydraulic components and the external dimensions of the hydraulic mechanism, which not only leads to the size of the entire hydraulic mechanism.
  • An object of the present invention is to provide a hydraulic working cylinder capable of reducing acceleration after a piston rod moving speed reaches a demand, and a hydraulic operating mechanism for a high pressure switch using the hydraulic working cylinder.
  • a hydraulic operating mechanism for a high-pressure switch comprising a hydraulic working cylinder and a control valve
  • the hydraulic working cylinder comprises a cylinder body having an inner cavity, a main piston sealed and slidingly fitted in a cavity of the cylinder body, and the inner cavity of the cylinder body is main
  • the piston is divided into a rod cavity on the left side of the main piston and a rodless cavity on the right side of the main piston.
  • the main piston is fixed with a piston rod extending in the left and right direction and disposed in the rod cavity, and is characterized in that:
  • the rod cavity of the cylinder body is slidably mounted in the left-right direction with an auxiliary piston independent of the piston rod, and the total area of the left-side pressure acting surface of the auxiliary piston facing the left side capable of being subjected to hydraulic oil and the auxiliary piston facing the right
  • the total area of the right pressure acting surface that can be affected by the hydraulic oil has an area difference between the auxiliary piston and the rightward movement of the auxiliary piston under the action of the hydraulic oil filled in the rod cavity, and the auxiliary piston is further provided on the right side.
  • a force applying end for applying a rightward acceleration force to the main piston during movement
  • the rod-shaped chamber is provided with a movement stroke set by the auxiliary piston, respectively, at the left and right limit positions of the movement stroke of the auxiliary piston
  • Auxiliary piston stopper left and right retaining structure the position of the right structure is provided to limit the rightward movement of the main piston while the speed reaches the set value of the auxiliary piston is blocked by the right limit stop means.
  • the auxiliary piston has inner and outer corresponding faces respectively adjacent to the piston rod and the inner wall surface of the rod cavity, and the inner corresponding surface is in active engagement with the piston rod gap, and the outer corresponding surface is correspondingly arranged with the inner wall of the rod cavity a sealing fit structure, the outer corresponding surface and the inner wall of the rod cavity are correspondingly provided with two sliding sealing cooperation structures of left and right, and the outer corresponding surface and the inner wall of the rod cavity are left between the two sliding sealing fit structures a decompression gap and a decompression hole communicating with the outside atmosphere in the decompression gap, and a decompression step surface facing the right side of the decompression gap on the auxiliary piston .
  • the auxiliary piston is a sleeve structure having an inner hole, the inner corresponding surface is a hole wall surface of the inner hole of the auxiliary piston, the outer corresponding surface is an outer peripheral surface of the auxiliary piston, and the limiting structure comprises a left limit structure
  • the right limit structure the left limit structure is a closing buffer sleeve disposed on the inner wall of the rod cavity with a right limiting surface for the left movement stop of the auxiliary piston, and the right limit structure is disposed on the inner wall of the rod cavity a limiting boss having a left limiting surface for a right movement stop of the auxiliary piston, the force applying end being a right end surface of the auxiliary piston, the sliding sealing engagement structure comprising a left sliding sealing fit structure and a right sliding sealing fit structure, left
  • the sliding seal fitting structure comprises a sealing ring mounted on a positioning boss disposed on a corresponding outer surface of the auxiliary piston and a rod cavity inner wall slidingly sealingly fitted with the sealing ring, and the right sliding sealing fitting structure comprises being
  • a hydraulic working cylinder comprising a cylinder having an inner cavity, a main piston sealingly slidingly fitted in a cavity of the cylinder, and a cylinder
  • the inner cavity of the body is divided by the main piston into a rod cavity on the left side of the main piston and a rodless cavity on the right side of the main piston, and the main piston is fixed with a piston extending in the left and right direction and penetrating in the rod cavity a rod characterized in that: in the rod cavity of the cylinder body, an auxiliary piston independent of the piston rod is slidably arranged in the left-right direction, and the total pressure of the left-side pressure acting surface of the auxiliary piston facing the left side capable of being subjected to hydraulic oil Between the area and the total area of the right pressure acting surface of the auxiliary piston facing to the right, which is capable of being subjected to hydraulic oil, there is an area difference of driving the auxiliary piston to the right under the action of the hydraulic oil filled in the rod cavity, on the auxiliary piston There is also a biasing end
  • the auxiliary piston has inner and outer corresponding faces respectively adjacent to the piston rod and the inner wall surface of the rod cavity, and the inner corresponding surface is in active engagement with the piston rod gap, and the outer corresponding surface is correspondingly arranged with the inner wall of the rod cavity a sealing fit structure, the outer corresponding surface and the inner wall of the rod cavity are correspondingly provided with two sliding sealing cooperation structures of left and right, and the outer corresponding surface and the inner wall of the rod cavity are left between the two sliding sealing fit structures a decompression gap and a decompression hole communicating with the outside atmosphere in the decompression gap, and a decompression step surface facing the right side of the decompression gap on the auxiliary piston .
  • the auxiliary piston is a sleeve structure having an inner hole, the inner corresponding surface is a hole wall surface of the inner hole of the auxiliary piston, the outer corresponding surface is an outer peripheral surface of the auxiliary piston, and the limiting structure comprises a left limit structure
  • the right limit structure the left limit structure is a closing buffer sleeve disposed on the inner wall of the rod cavity with a right limiting surface for the left movement stop of the auxiliary piston, and the right limit structure is disposed on the inner wall of the rod cavity a limiting boss having a left limiting surface for a right movement stop of the auxiliary piston, the force applying end being a right end surface of the auxiliary piston, the sliding sealing engagement structure comprising a left sliding sealing fit structure and a right sliding sealing fit structure, left
  • the sliding seal fitting structure comprises a sealing ring mounted on a positioning boss disposed on a corresponding outer surface of the auxiliary piston and a rod cavity inner wall slidingly sealingly fitted with the sealing ring, and the right sliding sealing fitting structure comprises being
  • the hydraulic working cylinder of the present invention is provided with an auxiliary piston which is moved by the hydraulic oil in the rod chamber to the direction of the rodless chamber (right side) in the rod cavity of the cylinder block, and the auxiliary piston is passed through the limiting structure.
  • the motion control is within the set working stroke range, so that in the initial acceleration phase of the working cylinder, that is, the working stroke section of the auxiliary piston, the hydraulic force to the right is generated on the auxiliary piston and the main piston, and the urging end of the auxiliary piston
  • the main piston will be moved to the right directly or through hydraulic oil, and the motion system can be accelerated to the required speed quickly, and then the force on the main piston drives the motion system to complete the opening action.
  • the opening force of the working cylinder is increased, which is advantageous for increasing the acceleration of the motion system and increasing the speed of the movement.
  • the position setting of the limiting device can ensure that the auxiliary piston reaches the right limit position of the working stroke while the main piston moving speed reaches the required state, and is blocked by the right limiting device. Block, when the auxiliary piston stops moving and no longer exerts a force on the main piston. Under the action of the main piston, the motion system continues to accelerate, but its acceleration is reduced due to the stop of the auxiliary piston, so that the main piston The maximum speed is not too high. This is advantageous in reducing the diameter of the working cylinder and the piston and reducing the operating work of the hydraulic mechanism.
  • the auxiliary piston acts as a buffer before the closing of the closing piston to improve the stability of the hydraulic mechanism.
  • the hydraulic operating mechanism for the high-pressure switch of the present invention adopts a working cylinder with an auxiliary piston, which can reduce the diameter of the working cylinder and the piston, and reduce the maximum speed, thereby improving the transmission efficiency of the hydraulic system.
  • This is beneficial to reduce the operating work of the hydraulic operating mechanism, and is also advantageous for reducing the structural dimensions of other hydraulic components and the entire operating mechanism, achieving miniaturization of the hydraulic mechanism and reducing product cost.
  • the maximum speed of the motion system is reduced, the kinetic energy of the motion system is reduced, and the shock vibration generated during the operation is also reduced, which is advantageous for improving the reliability and stability of the product.
  • FIG. 1 is a schematic structural view of an embodiment of a hydraulic working cylinder of the present invention
  • Figure 2 is a schematic structural view of the auxiliary piston of Figure 1;
  • Figure 3 is a schematic structural view of the piston rod and the main piston of Figure 1;
  • Figure 4 is a schematic view showing the structure of the hydraulic operating mechanism of the present invention.
  • the embodiment of the hydraulic working cylinder of the present invention is shown in Figs. 1-3.
  • the hydraulic working cylinder includes a cylinder block 11 having an inner cavity, and a main piston 18 that is slidably fitted in the inner cavity of the cylinder block 11 and is inside the cylinder block 11.
  • the cavity is divided by the main piston 18 into a rod cavity on the left side of the main piston 18 and a rodless cavity on the right side of the main piston 18.
  • the main piston 18 is fixed with a left and right direction extending through the rod cavity.
  • the piston rod 1 is slidably fitted in the rod chamber of the cylinder block 11 in the left-right direction with an auxiliary piston 9 independent of the piston rod 1.
  • the left end portion of the cylinder body 11 having the rod cavity is provided with a left nut 5 having an inner hole which is rotatably engaged with the inner wall of the rod cavity.
  • the left end of the piston rod 1 is transmitted from the inner hole of the left nut 5 to the outside of the cylinder block 11, and the left end of the left nut 5 is left.
  • the part is a non-threaded cylinder, and a sealing ring 3 is arranged between the circumferential surface of the cylinder and the inner wall of the cylinder 11 having a rod cavity, and the inner wall of the nut 5 of the left nut 5 near the left end surface is provided with an annular groove for installing the dustproof ring 2.
  • Two sealing rings 6 are disposed on the inner wall of the left nut 5 on the right side of the dust ring 2, and the inner wall of the left side of the left nut 5 has a stepped surface for mounting the closing buffer sleeve 7.
  • the right end portion of the rodless chamber 11 is provided with a right nut 15 having an inner hole which is rotatably engaged with the inner wall of the rodless chamber, and a seal ring 16 and a seal ring 17 are disposed between the outer peripheral surface of the right nut 15 and the inner wall of the rodless chamber.
  • the inner wall of the rodless cavity on the left side of the right nut 15 is provided with a stepped surface for mounting the opening buffer sleeve 14.
  • a wear ring 12 and a seal ring 13 are attached to the outer peripheral surface of the main piston 18 at intervals.
  • the cylinder 11 is also provided with a cylinder 11 hydraulic oil passage 19 through which the inner chamber penetrates.
  • An annular limiting boss 21 is provided on the inner wall surface of the cylinder chamber 11 having the rod cavity, and the limiting boss 21 is located on the left side of the opening in which the hydraulic passage 19 communicates with the cylinder block 11, and the right side of the auxiliary piston 9.
  • the stepped surface provided on the left side of the limiting boss 21 serves as a right limiting structure provided on the cylinder block 11 for blocking the rightward movement of the auxiliary piston 9.
  • An annular groove is formed in a middle portion of the outer peripheral surface of the limiting boss 21 and a sealing ring 10 is installed.
  • the right side of the closing buffer sleeve 7 has a stepped surface as a left limit provided on the cylinder 11 for blocking the leftward movement of the auxiliary piston 9. Bit structure.
  • An annular positioning boss 20 is disposed on the outer peripheral surface of the auxiliary piston 9.
  • the central portion of the outer peripheral surface of the positioning boss 20 defines an annular groove and is mounted with a sealing ring 8.
  • the stepped surface on the left side of the positioning boss 20 serves as an auxiliary piston 9 to the left.
  • the left limiting surface that is in contact with the closing buffer sleeve 7 during the movement, and the step surface on the right side of the positioning boss 20 serves as a limiting boss 21 corresponding to the inner cavity of the cylinder 11 during the rightward movement of the auxiliary piston 9.
  • the left limit step surface blocks the right limiting surface of the fit
  • the auxiliary piston 9 is entirely a sleeve structure having an inner hole
  • the piston rod 1 passes through the auxiliary piston 9
  • the main piston 18 is located on the right side of the auxiliary piston 9.
  • the right end surface of the auxiliary piston 9 faces the main piston 18 to constitute an urging end for applying an urging force to the main piston 18.
  • the auxiliary piston 9 has a hole wall surface close to the inner hole of the piston rod 1 as an auxiliary piston 9 corresponding to the inner corresponding surface of the piston rod 1, and the auxiliary piston 9 also has an outer peripheral surface close to the inner wall surface of the rod cavity as the auxiliary piston 9 corresponding to the rod cavity The outer surface of the wall.
  • the inner hole of the auxiliary piston 9 is in active engagement with the piston rod 1.
  • the outer circumference of the auxiliary piston 9 and the inner wall of the rod cavity are correspondingly provided with two sliding sealing structures of left and right, wherein the left sliding sealing fit structure is the above-mentioned positioning boss
  • the seal ring 8 provided on the 20 and the inner wall surface of the rod cavity which is in sliding engagement with the seal ring 8 are provided.
  • the right sliding seal fitting structure is provided with a seal ring 10 and an outer peripheral surface of the auxiliary piston 9 which is slidably engaged with the seal ring 10 on the above-mentioned limit boss 21.
  • a cavity formed between the right limiting surface provided on the auxiliary piston 9 and the left limiting structure provided on the cylinder 11 , the cavity being penetrated by the decompression hole 22 provided in the cylinder 11 , and the hole
  • the cavity is disposed between the left and right sliding sealing engagement structures to form a decompression gap that does not communicate with the rod cavity.
  • the end faces of the auxiliary piston 9 are subjected to the high pressure of the hydraulic system, and the pressure receiving space between the auxiliary piston 9 and the inner cavity of the cylinder 11 is communicated with the pressure reducing hole 22, and the force receiving area of the left end of the auxiliary piston 9 is used. It is larger than the force area of its right end, so that under the action of the high pressure oil of the hydraulic system, a large rightward force is generated on the auxiliary piston 9.
  • the hydraulic force generated on the auxiliary piston 9 and the main piston 18 is used to quickly accelerate the motion system to the required speed, and then the main piston 18 The upper force drives the motion system to complete the opening action.
  • the opening force of the working cylinder is increased, which is advantageous for increasing the acceleration of the motion system and increasing the speed of the movement.
  • the auxiliary piston 9 stops moving due to the stop of the left limiting surface provided on the limiting boss 21, and the force of the auxiliary piston 9 is reduced, under the action of the main piston 18,
  • the motion system continues to accelerate, but its acceleration is reduced, so that its maximum motion speed is not too high, and the right end of the main piston 18 collides with the opening buffer sleeve 14, Under the buffering action of the opening buffer sleeve 14, the motion system stops moving and completes the opening process.
  • the right end of the main piston 18 is subjected to the hydraulic oil force, and when the closing process of the main piston 18 to the left is about to be completed, the auxiliary piston 9 buffers the main piston 18 to improve the stability of the hydraulic mechanism.
  • the auxiliary piston may not be sleeve-shaped, or may be a block shape, a tile shape, a semi-annular shape or a C-shaped cross section, and the outer peripheral surface of the auxiliary piston and the cylinder body are The inner wall of the rod cavity is slidably sealed and the inner wall of the auxiliary piston is also slidably sealed with the outer peripheral surface of the piston rod.
  • the present invention in order to realize the total area of the left side pressure acting surface of the auxiliary piston which is capable of being subjected to hydraulic oil to the left.
  • a means for providing a decompression gap between the outer surface of the auxiliary piston and the inner wall of the rod cavity is adopted in A means for providing a decompression gap between the outer surface of the auxiliary piston and the inner wall of the rod cavity.
  • other conventional structures such as the structure in which the right end portion of the auxiliary piston passes through the cylinder can be used, and the conventional structure capable of reducing the pressure acting surface on the right side of the auxiliary piston can be used. In the decompression gap, it is not necessary to assist the seal between the outer surface of the piston and the cylinder, and it can be omitted.
  • the sealing ring of the sliding sealing structure may not be disposed on the positioning boss of the auxiliary piston, and a boss for mounting the sealing ring may be additionally disposed on the auxiliary piston.
  • the closing buffer sleeve may not be provided, and the limit boss is arranged on the inner wall of the rod cavity of the cylinder body, and the limit is limited.
  • the right side of the boss acts as a left limiting surface that blocks the auxiliary piston from moving to the left.
  • the hydraulic operating mechanism for the high-pressure switch of the present invention has the same structure as that of the hydraulic working cylinder embodiment described above, and will not be described herein.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
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Abstract

一种高压开关用液压操动机构及其液压工作缸，该液压工作缸包括具有内腔的缸体（11）、密封滑动装配于缸体（11）的内腔中的主活塞（18），缸体（11）的有杆腔中沿左右方向滑动装配有与活塞杆（1）相互独立的辅助活塞（9），辅助活塞（9）的朝向左方的能够受液压油作用的左侧压力作用面的总面积与辅助活塞（9）朝向右方的能够受液压油作用的右侧压力作用面的总面积之间具有面积差，有杆腔中对应于辅助活塞（9）设定的运动行程而设置有分别在辅助活塞（9）的运动行程的左右两极限位处阻挡辅助活塞左、右限位结构。该液压工作缸能够在活塞杆（1）运动速度达到要求后减小活塞杆（1）的加速度，同时提供使用该液压工作缸的液压操动机构。

Description

高压开关用液压操动机构及其液压工作缸 技术领域
本发明涉及用于操动高压开关进行分、合闸动作的高压开关用液压操动机构，本发明的液压工作缸则用于高压开关的液压操动机构中。
背景技术
超高压、特高压开关，如断路器、接地开关等，由于其电压等级高、开断电流大而对分闸或合闸的速度要求较高(断路器要求分闸速度高，接地开关要求合闸速度高)，这就要求其操动机构能提供较大的操作功。目前，只有液压机构可以满足超高压、特高压开关进行分、合闸动作对操作功的要求。现有超高压、特高压开关中所普遍应用的便是液压操动机构，液压操动机构的特点是常充压保持、瞬时动作。
现有的此类液压操动机构的结构如中国专利公开号101527206A、名称为一种高压断路器液压操动机构中所公开的，其包括输出动力的工作缸、控制工作缸的活塞杆动作的控制阀，液压操动机构在具体应用时，工作缸的活塞杆与相应的高压开关的主断口的动端通过连杆机构相连，控制阀通过油路控制工作缸的活塞杆伸缩运动。此类液压操动机构中的工作缸为常规的双作用缸，包括缸体和活塞杆，在缸体的有杆腔和无杆腔上分别设有第一、二油口，通过控制阀的对缸体有杆腔、无杆腔进油、泄油的控制而驱动活塞及活塞杆动作。
液压操动机构的主要目标是满足断路器对机械特性的要求，而对机械特性比较关注的主要是工作缸运动速度的高低。以断路器为例，其分闸操作时液压工作缸的动作时间只有30ms左右，在如此短的时间内，工作缸的活塞杆初始加速运动阶段要将运动系统的速度加速到10m/s以上，而之后又为了防止过大的压力冲击造成的损害，后期的减速阶段又要把速度快速降低到零，为此在工作缸中还设有分闸缓冲器和合闸缓冲器进行减速保护。在初始加速运动阶段，液压系统必须提供足够大的能量，在减速阶段，缓冲器又需要吸收大部分运动系统的动能。而断路器要求的分闸速度是规定时间段内或行程段内的平均速度，为了能够满足要求，在液压工作缸的初始加速阶段的加速度及速度较低时，只能通过加大液压操动机构的操作功以提高工作缸的初始加速阶段的加速度，具体措施是加大储能器储存的能量、液压工作缸的尺寸、液压元件及液压机构的外形尺寸，这样不但导致整个液压机构尺寸较大而造成成本和占地面积的提高，而且在增大操作功后，由于液压作用力将持续作用在活塞上而将导致其加速度始终保持在较高的程度，这样就造成操作中活塞杆的最高速度将远远高于平均 速度，这样在减速阶段不但将损失较大的能量，而且导致操作中产生的冲击振动也比较大。
发明内容
本发明的目的在于提供一种能够在活塞杆运动速度达到要求后减小加速度的液压工作缸，同时提供使用该液压工作缸的高压开关用液压操动机构。
本发明的技术方案是：
一种高压开关用液压操动机构，包括液压工作缸、控制阀，液压工作缸包括具有内腔的缸体、密封滑动装配于缸体的内腔中的主活塞，缸体的内腔被主活塞分隔为处于主活塞左侧的有杆腔和处于主活塞右侧的无杆腔，主活塞上固定有穿设于所述有杆腔中的沿左右方向延伸的活塞杆，其特征在于：所述缸体的有杆腔中沿左右方向滑动装配有与活塞杆相互独立的辅助活塞，辅助活塞的朝向左方的能够受液压油作用的左侧压力作用面的总面积与辅助活塞朝向右方的能够受液压油作用的右侧压力作用面的总面积之间具有在有杆腔中充入的液压油作用下驱动辅助活塞向右运动的面积差，辅助活塞上还设有在向右运动时对主活塞施加向右加速的作用力的施力端，所述有杆腔中对应于辅助活塞设定的运动行程而设置有分别在辅助活塞的运动行程的左右两极限位处阻挡辅助活塞左、右限位结构，所述右限位结构的位置被设置为在主活塞向右运动速度达到设定值的同时辅助活塞被右限位装置阻挡停止。
所述辅助活塞具有分别靠近活塞杆和有杆腔内壁面的内、外对应面，所述内对应表面与活塞杆间隙活动配合，所述外对应面与有杆腔的内壁上对应设有滑动密封配合结构，所述外对应面与有杆腔的内壁上对应设有左、右两个滑动密封配合结构，外对应面与有杆腔的内壁之间于两滑动密封配合结构之间留有减压空隙并在缸体上开设有与所述减压空隙相通的与外界大气相通的减压孔，所述辅助活塞上于所述减压空隙的左侧设有朝右的减压台阶面。
所述辅助活塞为具有内孔的套管结构，所述内对应面为辅助活塞的内孔的孔壁面，所述外对应面为辅助活塞的外周面，所述限位结构包括左限位结构和右限位结构，左限位结构为具有对辅助活塞向左运动止挡的右限位面的设置在有杆腔内壁的合闸缓冲套，右限位结构为设置在有杆腔内壁的具有对辅助活塞向右运动止挡的左限位面的限位凸台，所述施力端为辅助活塞的右端面，所述滑动密封配合结构包括左滑动密封配合结构和右滑动密封配合结构，左滑动密封配合结构包括安装在设置于辅助活塞外对应面的定位凸台上的密封圈和与所述密封圈滑动密封配合的有杆腔内壁，右滑动密封配合结构包括安装在设置于有杆腔内壁的限位凸台上的密封圈和与所述密封圈滑动配合的辅助活塞外对应面。
一种液压工作缸，包括具有内腔的缸体、密封滑动装配于缸体的内腔中的主活塞，缸 体的内腔被主活塞分隔为处于主活塞左侧的有杆腔和处于主活塞右侧的无杆腔，主活塞上固定有穿设于所述有杆腔中的沿左右方向延伸的活塞杆，其特征在于：所述缸体的有杆腔中沿左右方向滑动装配有与活塞杆相互独立的辅助活塞，辅助活塞的朝向左方的能够受液压油作用的左侧压力作用面的总面积与辅助活塞朝向右方的能够受液压油作用的右侧压力作用面的总面积之间具有在有杆腔中充入的液压油作用下驱动辅助活塞向右运动的面积差，辅助活塞上还设有在向右运动时对主活塞施加向右加速的作用力的施力端，所述有杆腔中对应于辅助活塞设定的运动行程而设置有分别在辅助活塞的运动行程的左右两极限位处阻挡辅助活塞左、右限位结构，所述右限位结构的位置被设置为在主活塞向右运动速度达到设定值的同时辅助活塞被右限位装置阻挡停止。
所述辅助活塞具有分别靠近活塞杆和有杆腔内壁面的内、外对应面，所述内对应表面与活塞杆间隙活动配合，所述外对应面与有杆腔的内壁上对应设有滑动密封配合结构，所述外对应面与有杆腔的内壁上对应设有左、右两个滑动密封配合结构，外对应面与有杆腔的内壁之间于两滑动密封配合结构之间留有减压空隙并在缸体上开设有与所述减压空隙相通的与外界大气相通的减压孔，所述辅助活塞上于所述减压空隙的左侧设有朝右的减压台阶面。
所述辅助活塞为具有内孔的套管结构，所述内对应面为辅助活塞的内孔的孔壁面，所述外对应面为辅助活塞的外周面，所述限位结构包括左限位结构和右限位结构，左限位结构为具有对辅助活塞向左运动止挡的右限位面的设置在有杆腔内壁的合闸缓冲套，右限位结构为设置在有杆腔内壁的具有对辅助活塞向右运动止挡的左限位面的限位凸台，所述施力端为辅助活塞的右端面，所述滑动密封配合结构包括左滑动密封配合结构和右滑动密封配合结构，左滑动密封配合结构包括安装在设置于辅助活塞外对应面的定位凸台上的密封圈和与所述密封圈滑动密封配合的有杆腔内壁，右滑动密封配合结构包括安装在设置于有杆腔内壁的限位凸台上的密封圈和与所述密封圈滑动配合的辅助活塞外对应面。
本发明的液压工作缸在缸体的有杆腔内设置了受到有杆腔中的液压油作用下向朝向无杆腔的方向(右方)运动的辅助活塞，而且通过限位结构将辅助活塞的运动控制在设定的工作行程范围内，这样在工作缸的初始加速阶段，也即辅助活塞的工作行程段，辅助活塞和主活塞上均产生向右的液压作用力，而且辅助活塞的施力端将直接或通过液压油推动主活塞向右运动，可较快的把运动系统加速度到需要的速度，然后由主活塞上的作用力带动运动系统完成分闸动作。这样，在加速运动阶段，由于辅助活塞上作用力的加入，增大了工作缸的分闸作用力，有利于增大运动系统的加速度，使运动速度快速增加。而且限位装置的位置设置，能够保证在主活塞运动速度达到需要的同时辅助活塞到达工作行程的右极限位置而被右限位装置阻 挡，这时辅助活塞停止运动而不再对主活塞施加作用力，在主活塞的作用下，运动系统继续作加速运动，但其加速度由于辅助活塞的停止的而减小，使主活塞的其最高运动速度不至过高。这样有利于减小工作缸及活塞的直径，减小液压机构的操作功。合闸操作时，辅助活塞在合闸结束前起缓冲作用，提高液压机构动作的稳定性。
本发明的高压开关用液压操动机构采用带有辅助活塞的工作缸，可以减小工作缸及活塞的直径，最高速度的降低，可提高液压系统的传动效率。这都有利于减小液压操动机构的操作功，也有利于减小其它液压元件及整个操动机构的结构尺寸，实现液压机构小型化，降低产品成本。另外，由于降低了运动系统的最高速度，使运动系统的动能减小，操作中产生的冲击振动也减小，有利于提高产品的可靠性与稳定性。
附图说明
图1是本发明的液压工作缸的实施例的结构示意图；
图2是图1中的辅助活塞的结构示意图；
图3是图1中的活塞杆及主活塞的结构示意图；
图4是本发明液压操纵机构的结构示意图。
具体实施方式
本发明的液压工作缸的实施例如图1-3所示：该液压工作缸包括具有内腔的缸体11，密封滑动装配于缸体11的内腔中的主活塞18，缸体11的内腔被主活塞18分隔为处于主活塞18左侧的有杆腔和处于主活塞18右侧的无杆腔，主活塞18上固定有穿设于所述有杆腔中的沿左右方向延伸的活塞杆1，缸体11的有杆腔中沿左右方向滑动装配有与活塞杆1相互独立的辅助活塞9。
缸体11有杆腔左端部设有与有杆腔内壁旋转配合的具有内孔的左螺母5，活塞杆1的左端从左螺母5的内孔传出缸体11之外，左螺母5左端部分为无螺纹的圆柱体，圆柱体圆周面与缸体11有杆腔内壁之间设有密封圈3，左螺母5靠近左端面的螺母5内孔壁设有安装防尘圈2的环形槽，位于防尘圈2右侧的左螺母5内孔壁上间隔设有两密封圈6，位于左螺母5右侧缸体11有杆腔内壁设有用于安装合闸缓冲套7的台阶面。缸体11无杆腔右端部设有与无杆腔内壁旋转配合的具有内孔的右螺母15，右螺母15外周面与无杆腔内壁之间设有密封圈16和密封圈17。右螺母15左侧无杆腔内壁设有用于安装分闸缓冲套14的台阶面。主活塞18外周面上间隔安装有耐磨环12及密封圈13。缸体11中还设有与缸体 11内腔贯通的液压油通道19。缸体11的有杆腔的内壁面上设有环形的限位凸台21，限位凸台21处于液压通道19与缸体11连通的开口的左侧、以及辅助活塞9的右侧。限位凸台21左侧具有的台阶面作为缸体11上设置的用于挡止辅助活塞9向右运动的右限位结构。限位凸台21外周面的中部开设环形凹槽并安装有密封圈10，合闸缓冲套7右侧具有台阶面作为缸体11上设置的用于挡止辅助活塞9向左运动的左限位结构。
辅助活塞9外周面上设有环形的定位凸台20，定位凸台20外周面的中部开设环形凹槽并安装有密封圈8，定位凸台20左侧具有的台阶面作为辅助活塞9向左运动过程中与合闸缓冲套7接触配合的左限位面，定位凸台20右侧具有的台阶面作为辅助活塞9向右运动过程中与缸体11内腔对应设置的限位凸台21的左限位台阶面挡止配合的右限位面，所述辅助活塞9整体为具有内孔的套管结构，活塞杆1穿过辅助活塞9，并且主活塞18位于辅助活塞9的右侧，辅助活塞9的右端面则朝向主活塞18而构成用于对主活塞18施加加速作用力的施力端。辅助活塞9具有靠近活塞杆1的内孔的孔壁面作为辅助活塞9对应活塞杆1的内对应面，辅助活塞9还具有靠近有杆腔内壁面的外周面作为辅助活塞9对应有杆腔内壁面的外对应面。辅助活塞9内孔与活塞杆1间隙活动配合，辅助活塞9外周上和有杆腔的内壁上对应设有左、右两个滑动密封配合结构，其中左滑动密封配合结构为上述的定位凸台20上设置的密封圈8以及与密封圈8对应滑动配合的有杆腔的内壁面。右滑动密封配合结构为上述限位凸台21上设置密封圈10及与密封圈10对应滑动配合的辅助活塞9的外周面。上述的辅助活塞9上所设置的右限位面和缸体11上设置的左限位结构之间形成的空腔，该空腔与设置在缸体11上的减压孔22贯通，并且该空腔设于上述的左、右两滑动密封配合结构之间而形成与有杆腔相互不连通的减压空隙。
上述实施例在使用时，辅助活塞9的两端面承受液压系统的高压，由于辅助活塞9与缸体11内腔之间形成减压空隙与减压孔22相通，辅助活塞9左端的受力面积大于其右端的受力面积，从而在液压系统高压油的作用下，辅助活塞9上会产生一个大的向右的作用力。分闸操作时，在加速运动阶段也即辅助活塞9工作行程段，利用辅助活塞9及主活塞18上产生的液压作用力，较快的把运动系统加速度到需要的速度，然后由主活塞18上的作用力带动运动系统完成分闸动作。这样，在加速运动阶段，由于辅助活塞9上作用力的加入，增大了工作缸的分闸作用力，有利于增大运动系统的加速度，使运动速度快速增加。在运动速度达到要求的速度后，辅助活塞9由于限位凸台21上设置的左限位面的挡止而停止运动，由于减少了辅助活塞9的作用力，在主活塞18的作用下，运动系统继续作加速运动，但其加速度减小，使其最高运动速度不至过高,主活塞18右端与分闸缓冲套14碰撞接触， 在分闸缓冲套14的缓冲作用下，运动系统停止运动，完成分闸过程。合闸操作时，主活塞18右端受液压油作用力，主活塞18向左运动过程中合闸过程即将完成时，辅助活塞9对主活塞18起缓冲作用，提高液压机构动作的稳定性。
在本发明的液压工作缸其它实施例中，辅助活塞也可以不是套管状，也可以是块状，瓦片状，半环状或其截面为C型，此时辅助活塞外周面与缸体有杆腔内壁滑动密封配合且辅助活塞内壁也要与活塞杆外周面滑动密封配合；另外，本发明中为了能够实现辅助活塞的朝向左方的能够受液压油作用的左侧压力作用面的总面积与辅助活塞朝向右方的能够受液压油作用的右侧压力作用面的总面积之间具有在有杆腔中充入的液压油作用下驱动辅助活塞向右运动的面积差，是采用了在辅助活塞外对应面与有杆腔内壁之间设有减压空隙的手段。当然在其它实施例中，也可以采用辅助活塞的右端部分穿出缸体的结构等其它的常规的能够以减小辅助活塞右侧压力作用面的结构，此时，由于形成面积差并不依赖于减压空隙，从而辅助活塞外对应面与缸体之间的密封则是没有必要的，而可以省去。
在其它实施例中，滑动密封结构的密封圈可以不设置在辅助活塞的定位凸台上，在辅助活塞上另设安装密封圈的凸台。
在其它实施例中，当辅助活塞结构采用上述的瓦片状，半环状或截面为C型时，可以不设置合闸缓冲套，在缸体有杆腔内壁设置限位凸台，限位凸台右侧面作为挡止辅助活塞向左运动的左限位面。
本发明的高压开关用液压操动机构，其采用的液压工作缸的结构与上述液压工作缸实施例的结构完全相同，此处不再赘述。

Claims (6)

  1. 一种高压开关用液压操动机构，包括液压工作缸、控制阀，液压工作缸包括具有内腔的缸体、密封滑动装配于缸体的内腔中的主活塞，缸体的内腔被主活塞分隔为处于主活塞左侧的有杆腔和处于主活塞右侧的无杆腔，主活塞上固定有穿设于所述有杆腔中的沿左右方向延伸的活塞杆，其特征在于：所述缸体的有杆腔中沿左右方向滑动装配有与活塞杆相互独立的辅助活塞，辅助活塞的朝向左方的能够受液压油作用的左侧压力作用面的总面积与辅助活塞朝向右方的能够受液压油作用的右侧压力作用面的总面积之间具有在有杆腔中充入的液压油作用下驱动辅助活塞向右运动的面积差，辅助活塞上还设有在向右运动时对主活塞施加向右加速的作用力的施力端，所述有杆腔中对应于辅助活塞设定的运动行程而设置有分别在辅助活塞的运动行程的左右两极限位处阻挡辅助活塞左、右限位结构，所述右限位结构的位置被设置为在主活塞向右运动速度达到设定值的同时辅助活塞被右限位装置阻挡停止。
  2. 根据权利要求1所述的高压开关用液压操动机构，其特征在于：所述辅助活塞具有分别靠近活塞杆和有杆腔内壁面的内、外对应面，所述内对应表面与活塞杆间隙活动配合，所述外对应面与有杆腔的内壁上对应设有滑动密封配合结构，所述外对应面与有杆腔的内壁上对应设有左、右两个滑动密封配合结构，外对应面与有杆腔的内壁之间于两滑动密封配合结构之间留有减压空隙并在缸体上开设有与所述减压空隙相通的与外界大气相通的减压孔，所述辅助活塞上于所述减压空隙的左侧设有朝右的减压台阶面。
  3. 根据权利要求2所述的高压开关用液压操动机构，其特征在于：所述辅助活塞为具有内孔的套管结构，所述内对应面为辅助活塞的内孔的孔壁面，所述外对应面为辅助活塞的外周面，所述限位结构包括左限位结构和右限位结构，左限位结构为具有对辅助活塞向左运动止挡的右限位面的设置在有杆腔内壁的合闸缓冲套，右限位结构为设置在有杆腔内壁的具有对辅助活塞向右运动止挡的左限位面的限位凸台，所述施力端为辅助活塞的右端面，所述滑动密封配合结构包括左滑动密封配合结构和右滑动密封配合结构，左滑动密封配合结构包括安装在设置于辅助活塞外对应面的定位凸台上的密封圈和与所述密封圈滑动密封配合的有杆腔内壁，右滑动密封配合结构包括安装在设置于有杆腔内壁的限位凸台上的密封圈和与所述密封圈滑动配合的辅助活塞外对应面。
  4. 一种液压工作缸，包括具有内腔的缸体、密封滑动装配于缸体的内腔中的主活塞，缸体的内腔被主活塞分隔为处于主活塞左侧的有杆腔和处于主活塞右侧的无杆腔，主活塞上固定有穿设于所述有杆腔中的沿左右方向延伸的活塞杆，其特征在于：所述缸体的有杆腔中沿左右方向滑动装配有与活塞杆相互独立的辅助活塞，辅助活塞的朝向左方的能够受液压油作用的左侧压力作用面的总面积与辅助活塞朝向右方的能够受液压油作用的右侧压力作用面的总面积之间具有在有杆腔中充入的液压油作用下驱动辅助活塞向右运动的面积差，辅助活塞上还设有在向右运动时对主活塞施加向右加速的作用力的施力端，所述有杆腔中对应于辅助活塞设定的运动行程而设置有分别在辅助活塞的运动行程的左右两极限位处阻挡辅助活塞左、右限位结构，所述右限位结构的位置被设置为在主活塞向右运动速度达到设定值的同时辅助活塞被右限位装置阻挡停止。
  5. 根据权利要求4所述的液压工作缸，其特征在于：所述辅助活塞具有分别靠近活塞杆和有杆腔内壁面的内、外对应面，所述内对应表面与活塞杆间隙活动配合，所述外对应面与有杆腔的内壁上对应设有滑动密封配合结构，所述外对应面与有杆腔的内壁上对应设有左、右两个滑动密封配合结构，外对应面与有杆腔的内壁之间于两滑动密封配合结构之间留有减压空隙并在缸体上开设有与所述减压空隙相通的与外界大气相通的减压孔，所述辅助活塞上于所述减压空隙的左侧设有朝右的减压台阶面。
  6. 根据权利要求5所述的液压工作缸，其特征在于：所述辅助活塞为具有内孔的套管结构，所述内对应面为辅助活塞的内孔的孔壁面，所述外对应面为辅助活塞的外周面，所述限位结构包括左限位结构和右限位结构，左限位结构为具有对辅助活塞向左运动止挡的右限位面的设置在有杆腔内壁的合闸缓冲套，右限位结构为设置在有杆腔内壁的具有对辅助活塞向右运动止挡的左限位面的限位凸台，所述施力端为辅助活塞的右端面，所述滑动密封配合结构包括左滑动密封配合结构和右滑动密封配合结构，左滑动密封配合结构包括安装在设置于辅助活塞外对应面的定位凸台上的密封圈和与所述密封圈滑动密封配合的有杆腔内壁，右滑动密封配合结构包括安装在设置于有杆腔内壁的限位凸台上的密封圈和与所述密封圈滑动配合的辅助活塞外对应面。
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