WO2022088418A1 - 液压控制阀及使用该液压控制阀的液压操动机构、断路器 - Google Patents

液压控制阀及使用该液压控制阀的液压操动机构、断路器 Download PDF

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Publication number
WO2022088418A1
WO2022088418A1 PCT/CN2020/136264 CN2020136264W WO2022088418A1 WO 2022088418 A1 WO2022088418 A1 WO 2022088418A1 CN 2020136264 W CN2020136264 W CN 2020136264W WO 2022088418 A1 WO2022088418 A1 WO 2022088418A1
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WIPO (PCT)
Prior art keywords
oil port
valve
valve core
pressure oil
control
Prior art date
Application number
PCT/CN2020/136264
Other languages
English (en)
French (fr)
Inventor
陈维江
钟建英
李海文
林莘
韩彬
刘煜
韩国辉
雷琴
刘宇
段晓辉
魏建巍
孙珂珂
李新刚
Original Assignee
平高集团有限公司
国家电网有限公司
沈阳工业大学
中国电力科学研究院有限公司
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Application filed by 平高集团有限公司, 国家电网有限公司, 沈阳工业大学, 中国电力科学研究院有限公司 filed Critical 平高集团有限公司
Publication of WO2022088418A1 publication Critical patent/WO2022088418A1/zh

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    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0689—Braking of the valve element
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts

Definitions

  • the present application relates to the field of hydraulic valves, in particular to a hydraulic control valve, a hydraulic operating mechanism and a circuit breaker using the hydraulic control valve.
  • the opening and closing speed of the circuit breaker is a key parameter of the performance of the circuit breaker.
  • the opening and closing speed of the circuit breaker is determined by the hydraulic operating mechanism.
  • the hydraulic operating mechanism includes a working cylinder and a hydraulic control valve.
  • the piston in the working cylinder drives the moving contact to open and close, and the hydraulic control valve controls the action of the piston in the working cylinder. Therefore, the opening and closing speed of the circuit breaker is ultimately controlled by hydraulic pressure.
  • the response speed of the valve is determined.
  • the existing hydraulic control valves are mostly two-stage or three-stage valve structures, and the movement of the main valve spool is controlled by the electromagnetic pilot valve (first-stage valve) and the amplifier valve (second-stage valve), or only through the electromagnetic pilot valve (first-stage valve). ) controls the movement of the main valve spool.
  • the action of the hydraulic control valve needs to be driven by the electromagnet, the primary valve is opened (or the secondary valve is opened again) - the main valve spool moves in multiple links, and the response time is long, which cannot meet the rapid opening and closing of the circuit breaker. gate requirements.
  • the Chinese invention patent with the authorization announcement number CN102403139B discloses a repulsion reversing valve for an ultra-high pressure series compensation bypass switch, which includes a valve body, a valve sleeve is arranged in the valve body, and a valve core is slidably assembled in the valve sleeve. , the axial end of the valve core is connected with a repulsion valve, and the repulsion valve drives the valve core to move back and forth.
  • the valve body is provided with a normal high pressure oil port, a control oil port and a normal low pressure oil port in sequence along the moving direction of the valve core.
  • the reciprocating sliding of the valve core can realize one of the control oil port, the normal high pressure oil port and the normal low pressure oil port Conduction, thereby driving the circuit breaker to close and open.
  • the existing repulsive force reversing valve utilizes the fast response speed of the repulsive force valve to meet the demands of the spool to act quickly.
  • the existing repulsion reversing valve also has some drawbacks: the dimensions of the valve sleeve and the valve core in the existing repulsion reversing valve change a lot, and the structure is more complicated. Moreover, the existing valve core achieves sealing by making axial line contact with the valve sleeve after moving in place, and the control accuracy after the valve core moves in place and the machining accuracy of the valve sleeve and the valve core are relatively high.
  • the present application is to provide a hydraulic control valve to solve the technical problems of complex structure and easy oil leakage of the hydraulic control valve; and to provide a hydraulic operating mechanism using the hydraulic control valve to solve the problem that the hydraulic operating mechanism has a complex structure and cannot be easily leaked.
  • the technical problem of ensuring that the moving contact opening and closing is in place or difficult to maintain the opening and closing state; and a circuit breaker using the hydraulic control valve is also provided to solve the above technical problems.
  • a hydraulic control valve comprising:
  • the valve body has a valve cavity inside, and the valve body is sequentially provided with a normal high pressure oil port, a control oil port and a normal low pressure oil port which are connected with the valve cavity in a straight line direction;
  • the valve core controlled by the driving mechanism, is arranged in the valve cavity to reciprocate and slide along the linear direction;
  • the inner wall of the valve cavity is provided with an equal diameter straight section between the normal high pressure oil port and the normally high and low oil port, and a sealing ring is provided on the outer peripheral surface of the valve core and at least one of the inner wall of the equal diameter straight section to realize the valve core and the equal diameter straight section. the sliding seal fit;
  • first limit position There are a first limit position and a second limit position on the reciprocating sliding stroke of the valve core.
  • first limit position When it is at the first limit position, the valve core is located between the normal high pressure oil port and the control oil port, and the normal low pressure oil port is connected with the control oil port;
  • second limit position the valve core is located between the normal low pressure oil port and the control oil port, and the normal high pressure oil port is connected with the control oil port.
  • valve cavity as a whole is an equal-diameter structure with the same inner diameter of the equal-diameter straight section.
  • the valve cavity is of equal diameter as a whole, which is more convenient to process.
  • the hydraulic control valve includes a driving rod, the driving rod and the valve core are arranged coaxially, the driving rod and the valve core are separately fixed or integrally formed, and the outer diameter of the driving rod is smaller than the outer diameter of the valve core to form a piston-type structure;
  • One end of the drive rod extends to the outside of the valve body
  • the driving mechanism is a repulsion mechanism, the repulsion mechanism is separately arranged outside the valve body, the repulsion mechanism is connected with the end of the driving rod that is located outside the valve body, and the repulsion mechanism drives the valve core to slide back and forth and can keep the valve core in the first position. limit and second limit.
  • the repulsion mechanism can drive the valve core to slide back and forth rapidly, and because of the circumferential sealing relationship between the valve core and the valve body, when sliding to the limit position, no impact force will be generated, and the valve core and valve body will not be damaged.
  • the repulsion mechanism is arranged outside the valve body, and the valve core is driven by the drive rod. Since the repulsion mechanism and the valve body are arranged separately, the size of the repulsion mechanism is not limited by the valve body, and a repulsion mechanism with a higher moving speed can be selected.
  • the distance between at least one of the normal high pressure oil port and the normal low pressure oil port and the control oil port is greater than the length of the spool.
  • the distances between the normal high pressure oil port, the normal low pressure oil port and the control oil port are the same.
  • the distance between the two is the same, which ensures that the distance between the forward movement and the reverse movement of the valve core can be kept the same, which is convenient for control.
  • a hydraulic operating mechanism comprising:
  • the working cylinder is used to drive the moving contact to open and close;
  • Hydraulic control valve used to control the expansion and contraction of the piston of the working cylinder
  • the hydraulic control valve includes: a valve body with a valve cavity inside, and a normal high pressure oil port, a control oil port and a normal low pressure oil port which are connected with the valve cavity are sequentially arranged on the valve body along a linear direction;
  • the valve core controlled by the driving mechanism, is arranged in the valve cavity to reciprocate and slide along the linear direction;
  • the inner wall of the valve cavity is provided with an equal diameter straight section between the normal high pressure oil port and the normally high and low oil port, and a sealing ring is provided on the outer peripheral surface of the valve core and at least one of the inner wall of the equal diameter straight section to realize the valve core and the equal diameter straight section. the sliding seal fit;
  • first limit position There are a first limit position and a second limit position on the reciprocating sliding stroke of the valve core.
  • first limit position When it is at the first limit position, the valve core is located between the normal high pressure oil port and the control oil port, and the normal low pressure oil port is connected with the control oil port;
  • second limit position the valve core is located between the normal low pressure oil port and the control oil port, and the normal high pressure oil port is connected with the control oil port.
  • valve cavity as a whole is an equal-diameter structure with the same inner diameter of the equal-diameter straight section.
  • the valve cavity is of equal diameter as a whole, which is more convenient to process.
  • the hydraulic control valve includes a driving rod, the driving rod and the valve core are arranged coaxially, the driving rod and the valve core are separately fixed or integrally formed, and the outer diameter of the driving rod is smaller than the outer diameter of the valve core to form a piston-type structure;
  • One end of the drive rod extends to the outside of the valve body
  • the driving mechanism is a repulsion mechanism, the repulsion mechanism is separately arranged outside the valve body, the repulsion mechanism is connected with the end of the driving rod that is located outside the valve body, and the repulsion mechanism drives the valve core to slide back and forth and can keep the valve core in the first position. limit and second limit.
  • the repulsion mechanism can drive the valve core to slide back and forth rapidly, and because of the circumferential sealing relationship between the valve core and the valve body, when sliding to the limit position, no impact force will be generated, and the valve core and valve body will not be damaged.
  • the repulsion mechanism is arranged outside the valve body, and the valve core is driven by the drive rod. Since the repulsion mechanism and the valve body are arranged separately, the size of the repulsion mechanism is not limited by the valve body, and a repulsion mechanism with a higher moving speed can be selected.
  • the distance between at least one of the normal high pressure oil port and the normal low pressure oil port and the control oil port is greater than the length of the spool.
  • the distances between the normal high pressure oil port, the normal low pressure oil port and the control oil port are the same.
  • the distance between the two is the same, which ensures that the distance between the forward movement and the reverse movement of the valve core can be kept the same, which is convenient for control.
  • circuit breaker of the present application is: a circuit breaker, comprising:
  • the fracture structure includes moving contacts and static contacts
  • Hydraulic operating mechanism used to drive the opening and closing of the moving contact of the fracture structure
  • the hydraulic operating mechanism includes:
  • the working cylinder is used to drive the moving contact to open and close;
  • Hydraulic control valve used to control the expansion and contraction of the piston of the working cylinder
  • the hydraulic control valve includes: a valve body with a valve cavity inside, and a normal high pressure oil port, a control oil port and a normal low pressure oil port which are connected with the valve cavity are sequentially arranged on the valve body along a linear direction;
  • the valve core controlled by the driving mechanism, is arranged in the valve cavity to reciprocate and slide along the linear direction;
  • the inner wall of the valve cavity is provided with an equal diameter straight section between the normal high pressure oil port and the normally high and low oil port, and a sealing ring is provided on the outer peripheral surface of the valve core and at least one of the inner wall of the equal diameter straight section to realize the valve core and the equal diameter straight section. the sliding seal fit;
  • first limit position There are a first limit position and a second limit position on the reciprocating sliding stroke of the valve core.
  • first limit position When it is at the first limit position, the valve core is located between the normal high pressure oil port and the control oil port, and the normal low pressure oil port is connected with the control oil port;
  • second limit position the valve core is located between the normal low pressure oil port and the control oil port, and the normal high pressure oil port is connected with the control oil port.
  • valve cavity as a whole is an equal-diameter structure with the same inner diameter of the equal-diameter straight section.
  • the valve cavity is of equal diameter as a whole, which is more convenient to process.
  • the hydraulic control valve includes a driving rod, the driving rod and the valve core are arranged coaxially, the driving rod and the valve core are separately fixed or integrally formed, and the outer diameter of the driving rod is smaller than the outer diameter of the valve core to form a piston-type structure;
  • One end of the drive rod extends to the outside of the valve body
  • the driving mechanism is a repulsion mechanism, the repulsion mechanism is separately arranged outside the valve body, the repulsion mechanism is connected with the end of the driving rod that is located outside the valve body, and the repulsion mechanism drives the valve core to slide back and forth and can keep the valve core in the first position. limit and second limit.
  • the repulsion mechanism can drive the valve core to slide back and forth rapidly, and because of the circumferential sealing relationship between the valve core and the valve body, when sliding to the limit position, no impact force will be generated, and the valve core and valve body will not be damaged.
  • the repulsion mechanism is arranged outside the valve body, and the valve core is driven by the drive rod. Since the repulsion mechanism and the valve body are arranged separately, the size of the repulsion mechanism is not limited by the valve body, and a repulsion mechanism with a higher moving speed can be selected.
  • the distance between at least one of the normal high pressure oil port and the normal low pressure oil port and the control oil port is greater than the length of the spool.
  • the distances between the normal high pressure oil port, the normal low pressure oil port and the control oil port are the same.
  • the distance between the two is the same, which ensures that the distance between the forward movement and the reverse movement of the valve core can be kept the same, which is convenient for control.
  • the beneficial effects of the hydraulic control valve of the present application are as follows: there are equal diameter straight sections in the valve cavity, the outer peripheral surface of the valve core and the equal diameter straight sections are in sliding and sealing cooperation, no valve sleeve is required, and the valve core and the valve body are circumferentially sealed In this way, the inner diameter of the valve body and the outer diameter of the valve core do not need to be changed too much, so that the overall structure of the valve core and the valve body is relatively simple. In addition, the valve core and the valve body are circumferentially sealed, and the sealing is maintained during the entire reciprocating sliding stroke.
  • the normal and low pressure oil port and the control oil port can be separated, and the requirements for the position after the spool moves in place are not too high. Strict, allowing a certain positional deviation to exist, reducing the difficulty of processing and assembling, and there will be no oil leakage.
  • the beneficial effects of the hydraulic operating mechanism of the present application are: there are equal diameter straight sections in the valve cavity, the outer peripheral surface of the valve core and the equal diameter straight sections are in sliding and sealing cooperation, no valve sleeve is required, and the valve core and the valve body are in a circumferential direction.
  • the inner diameter of the valve body and the outer diameter of the valve core do not need to be changed too much, so that the overall structure of the valve core and the valve body is relatively simple.
  • the valve core and the valve body are circumferentially sealed, and the sealing is maintained during the entire reciprocating sliding stroke.
  • the normal and low pressure oil port and the control oil port can be separated, and the requirements for the position after the spool moves in place are not too high. Strict, allowing a certain position deviation to exist, reducing the difficulty of processing and assembling the hydraulic control valve and the hydraulic operating mechanism, and there will be no oil leakage, thus ensuring that the moving contact controlled by the hydraulic operating mechanism can be smoothly opened and closed in place and remain in the open and closed position.
  • the beneficial effects of the circuit breaker of the present application are as follows: there are equal diameter straight sections in the valve cavity, the outer peripheral surface of the valve core and the equal diameter straight sections are slidably sealed, no valve sleeve is required, and the valve core and the valve body are circumferentially sealed In this way, the inner diameter of the valve body and the outer diameter of the valve core do not need to be changed too much, so that the overall structures of the valve core and the valve body are relatively simple. In addition, the valve core and the valve body are circumferentially sealed, and the sealing is maintained during the entire reciprocating sliding stroke.
  • the normal and low pressure oil port and the control oil port can be separated, and the requirements for the position after the spool moves in place are not too high. Strict, allowing a certain position deviation to exist, reducing the difficulty of processing and assembling the hydraulic control valve and the hydraulic operating mechanism, and there will be no oil leakage, thus ensuring that the moving contact controlled by the hydraulic operating mechanism can be smoothly opened and closed in place and remain in the open and closed position.
  • Fig. 1 is the schematic diagram of the opening position in the hydraulic control valve embodiment 1 of the present application
  • FIG. 2 is a schematic diagram of the closing position in Embodiment 1 of the hydraulic control valve of the present application.
  • valve body 1- valve body; 2- repulsion mechanism; 3- valve cavity; 4- normal high pressure oil port; 5- control oil port; 6- normal low pressure oil port; 7- first sealing ring; 8- drive Rod; 9- valve core; 10- second sealing ring; 11- closing coil; 12- opening coil; 13- capacitor; 14- capacitor switch; 15- repulsion disc; 16- output rod; 17- connecting device; 18-Bistable Spring Retainer
  • the hydraulic control valve includes a valve body 1 , a valve core 9 , a driving rod 8 , and a repulsive force mechanism 2 that drives the valve core 9 to reciprocate.
  • the longitudinal direction of the valve body 1 is the axial direction of the valve body 1
  • the axial direction of the valve body 1 is the left-right direction
  • the repulsion mechanism 2 is located on the left side of the valve body 1 .
  • There is a valve cavity 3 in the valve body 1 the valve cavity 3 extends left and right, and the inner wall of the valve cavity 3 has equal diameters everywhere, so that the valve cavity 3 forms an equal diameter structure.
  • the equal diameter structure indicates that the area of the section of the valve cavity 3 perpendicular to the axial direction is the same.
  • a normal high pressure oil port 4 , a control oil port 5 and a normal low pressure oil port 6 are sequentially arranged on the valve body 1 from left to right, and each oil port is communicated with the inside of the valve cavity 3 .
  • the control oil port 5 and the normal low pressure oil port 6 the spacing between any adjacent two in the left and right direction is the same.
  • a joint is installed at each oil port to connect with the oil pipe joint.
  • the left end of the valve body 1 is provided with a perforation that communicates with the inside and outside of the valve cavity 3, an inner ring groove is formed in the perforation, and a first sealing ring 7 is embedded in the inner ring groove.
  • the function of the first sealing ring 7 is to communicate with the driving rod. 8 Sliding seal fits to prevent oil leakage here. It can be seen from FIG. 1 that the three oil ports are arranged along the radial direction of the valve body 1 and are arranged side by side in the axial direction.
  • valve core 9 The structure of the valve core 9 is shown in FIG. 1 , the valve core 9 is a cylinder as a whole, and is arranged coaxially with the valve body 1 .
  • An outer ring groove is provided on the outer peripheral surface of the valve core 9, and a second sealing ring 10 is embedded in the outer ring groove.
  • the function of the second sealing ring 10 is to ensure that the valve core 9 is sealed with the inner wall of the valve cavity 3 during the sliding process Cooperate to prevent oil leakage.
  • the second sealing ring may be located on the inner wall of the valve cavity, or the second sealing ring may be arranged on both the inner wall of the valve cavity and the outer peripheral surface of the valve core.
  • the axial length of the spool 9 is smaller than the axial distance between the normal high pressure oil port 4 and the control oil port 5 , and is also smaller than the axial distance between the normal low pressure oil port 6 and the control oil port 5 .
  • a driving rod 8 is integrally formed on the left end of the valve core 9.
  • the driving rod 8 and the valve core 9 are arranged coaxially.
  • the outer diameter of the driving rod 8 is smaller than the outer diameter of the valve core 9.
  • the valve core 9 and the driving rod 8 form a piston type Structure.
  • the driving rod 8 is passed leftward from the above-mentioned perforation.
  • the repulsive force mechanism 2 is shown in FIG. 1 , the repulsive force mechanism 2 includes a closing coil 11 and an opening coil 12 which are arranged at intervals along the left and right directions.
  • the closing coil 11 and the opening coil 12 are connected with a capacitor 13 and a capacitor switch 14. , when the capacitor switch 14 is closed, the capacitor 13 supplies power to the corresponding coil.
  • a repulsion disc 15 is arranged between the closing coil 11 and the opening coil 12, and the repulsion disc 15 is a metal disc.
  • the severe current change will cause the repulsion disc 15 to generate A reverse induced current generates a huge repulsive force between the energized coil and the repulsion disc 15, which pushes the repulsion disc 15 to move rapidly.
  • An output rod 16 is fixed on the repulsion disc 15 , and the output rod 16 passes through the closing coil 11 and the opening coil 12 .
  • the output rod 16 and the driving rod 8 are connected through a connecting device 17, and the connecting device 17 here can be a coupling, or a threaded connection sleeve or the like.
  • the repulsion mechanism 2 further includes a bistable spring holding device 18 located at the left end of the closing coil 11 , and the output rod 16 is connected to the bistable spring holding device 18 , wherein the bistable spring holding device 18 is an existing structure. , and will not be repeated here.
  • the bistable spring holding device 18 can keep the valve core 9 at the limit position when the valve core 9 moves to the limit position, so as to prevent the valve core 9 from being driven by hydraulic pressure or other external forces and affecting the opening and closing state of the circuit breaker.
  • the application process of the present application is as follows: when the circuit breaker needs to be closed, the capacitor switch 14 on the closing coil 11 is closed, the capacitor 13 supplies power to the closing coil 11, and the violent current change will cause the repulsion disc 15 to generate a reverse Induced current, the closing coil 11 and the repulsion disc 15 will generate a huge repulsive force, which pushes the repulsion disc 15 to move rapidly to the right, and the output rod 16 and the drive rod 8 drive the spool 9 to quickly move to the right to the position shown in Figure 2
  • the spool 9 is located between the control oil port 5 and the normal low pressure oil port 6, which separates the control oil port 5 from the normal low pressure oil port 6, and makes the control oil port 5 and the normal high pressure oil port. 4 Connected.
  • the bistable spring holding device 18 keeps the valve core 9 at this position, which is the second limit position of the valve core 9 .
  • the capacitor switch 14 on the opening coil 12 is closed, and the capacitor 13 supplies power to the opening coil 12.
  • the severe current change will cause the repulsion disc 15 to generate a reverse induced current, and the opening coil 12 With the repulsion disc 15, a huge repulsive force will be generated, which will push the repulsion disc 15 to move quickly to the left, and the output rod 16 and the drive rod 8 will drive the valve core 9 to move to the left quickly to the position shown in Figure 1.
  • the valve core 9 is located between the control oil port 5 and the normal high pressure oil port 4, separates the control oil port 5 from the normal high pressure oil port 4, and makes the control oil port 5 communicate with the normal low pressure oil port 6.
  • the bistable spring holding device 18 keeps the valve core 9 at this position, which is the first limit position of the valve core 9 .
  • the sealing method between the valve core 9 and the valve body 1 adopts the matching method between the second sealing ring 10 on the valve core 9 and the inner wall of the valve cavity 3 .
  • the valve cavity 3 and the valve core 9 as a whole are All of them are of equal diameter structure, simple in structure, convenient in processing, and convenient in assembly.
  • the axial length of the spool 9 is smaller than the axial distance between the normal high pressure oil port 4 and the control oil port 5 , and is also smaller than the axial distance between the normal low pressure oil port 6 and the control oil port 5 . As long as the spool 9 is located between the normal high pressure oil port 4 and the control oil port 5, the normal high pressure oil port 4 and the control oil port 5 can be separated. The position deviation exists, which reduces the difficulty of processing and assembly.
  • valve core 9 cannot correspond to the oil port when the valve core 9 is at the first limit position and the second limit position, so as to avoid the oil flow at the oil port being blocked.
  • speed of opening and closing can be guaranteed, even if there is a certain overlap between the valve core and the oil port when the valve core is at the limit position, it can still meet the normal use.
  • one end of the driving rod 8 is protruded from the valve body 1, the repulsion mechanism 2 is separately arranged outside the valve body 1, and the size of the repulsion mechanism 2 is not affected by the Due to the restriction of the valve body 1, the size of the coil and the repulsion disc 15 in the repulsion mechanism 2 can be enlarged, thereby increasing the opening and closing speed.
  • the axial length of the valve core is smaller than the axial distance between the normal high pressure oil port and the control oil port, and is also smaller than the axial distance between the normal low pressure oil port and the control oil port.
  • the axial length of the spool can be only smaller than the axial distance between the normal high pressure oil port and the control oil port, but equal to the axial distance between the normal low pressure oil port and the control oil port, and of course, it can also be slightly larger than the normal low pressure oil port. Axial distance between the port and the control port.
  • the axial length of the spool can be only smaller than the axial distance between the normal low pressure oil port and the control oil port, but equal to the axial distance between the normal high pressure oil port and the control oil port. Of course, it can also be slightly larger than the normal high pressure oil port and the control oil port. Axial spacing of ports.
  • each oil port is arranged on the valve body in a radially extending manner.
  • the normal and low pressure oil port may be arranged at the end of the valve body.
  • the normally low pressure oil port is located on the right side of the normally high pressure oil port.
  • the normally low pressure oil port and the normal high pressure oil port can be interchanged.
  • the distance between any two adjacent ones of the normal high pressure oil port, the control oil port and the normal low pressure oil port is the same, so that the reciprocating stroke of the valve core is consistent, which is convenient for control.
  • the two distances may be different.
  • the inner diameter of the valve cavity is the same as a whole, and the entire valve cavity is of an equal diameter structure.
  • the part between the normal low pressure oil port and the normal high pressure oil port forms an equal diameter straight section.
  • the portion of the valve cavity located between the normal low pressure oil port and the normal high pressure oil port is still equal in diameter, while the inner diameter of other parts in the valve cavity can be increased or decreased.
  • the repulsive force mechanism drives the valve core to move back and forth, and relies on the bistable spring holding device to keep the valve core at the first limit position and the second limit position, and the repulsion force mechanism forms a driving mechanism.
  • the repulsion mechanism can be integrated on the valve body.
  • the function of the driving mechanism is to drive the valve core to move back and forth.
  • other forms of driving mechanisms such as electromagnets, may also be used according to the requirements for the opening and closing speed.
  • the reciprocating movement of the spool can also be controlled by means of an electromagnetic pilot valve.
  • the hydraulic operating mechanism includes a working cylinder, and the working cylinder has a piston that drives the moving contacts to open and close.
  • the hydraulic operating mechanism also includes a hydraulic control valve that controls the expansion and contraction of the piston.
  • the structure of the hydraulic control valve is the same as that in the above-mentioned embodiments. It is not repeated here.
  • the circuit breaker includes a fracture structure, the fracture structure includes a moving contact and a static contact, and also includes a hydraulic operating mechanism that drives the moving contact to open and close.
  • the hydraulic operating mechanism is consistent with the hydraulic operating mechanism in the above-mentioned embodiments. This will not be repeated here.

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Abstract

一种液压控制阀及使用该液压控制阀的液压操动机构、断路器，液压控制阀包括阀体（1），内有阀腔（3），阀体（1）上沿直线方向依次设置有与阀腔（3）连通的常高压油口（4）、控制油口（5）和常低压油口（6）；阀芯（9）；阀腔（3）内壁于常高压油口（4）和常低压油口（6）之间设有等径直段，阀芯（9）外周面与所述等径直段内壁中的至少一个上设有密封圈（10），以实现阀芯（9）和等径直段的滑动密封配合；阀芯（9）的往复滑动行程上有第一极限位和第二极限位，位于第一极限位时，阀芯（9）位于常高压油口（4）与控制油口（5）之间，常低压油口（6）与控制油口（5）连通；位于第二极限位时，阀芯（9）位于常低压油口（6）与控制油口（5）之间，常高压油口（4）与控制油口（5）连通。对阀芯（9）运动到位后位置的要求不太严格，允许有一定的位置偏差存在，降低了加工装配的难度。

Description

液压控制阀及使用该液压控制阀的液压操动机构、断路器
相关申请的交叉引用
本申请基于申请号为CN202011156907.9、申请日为2020年10月26日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此以引入方式并入本申请。
技术领域
本申请涉及液压阀领域，具体涉及一种液压控制阀及使用该液压控制阀的液压操动机构、断路器。
背景技术
断路器的分合闸速度是断路器性能的一个关键参数，对于由液压操动机构控制分、合闸的断路器而言，断路器的分合闸速度是由液压操动机构来决定的。液压操动机构包括工作缸和液压控制阀，工作缸中的活塞带动动触头分合闸，液压控制阀控制工作缸中的活塞动作，因此，断路器的分合闸速度最终是由液压控制阀的响应速度来决定的。
现有的液压控制阀多为二级或三级阀结构，由电磁先导阀(一级阀)和放大阀(二级阀)控制主阀阀芯移动，或者仅通过电磁先导阀(一级阀)控制主阀阀芯移动。实际应用中，液压控制阀的动作需经过电磁铁带动、一级阀打开(或者再打开二级阀)-主阀阀芯移动多个环节，响应时间较长，无法满足断路器的快速分合闸的需求。
为解决该问题，授权公告号为CN102403139B的中国发明专利公开了一种特高压串补旁路开关用斥力换向阀，包括阀体，阀体内设有阀套，阀套内滑动装配有阀芯，阀芯的轴向一端连接有斥力阀，斥力阀带动阀芯往复移动。阀体上沿阀芯的移动方向依次开设有常高压油口、控制油口和常低压油口，通过阀芯的往复滑动能够实现控制油口与常高压油口、常低压油口中的其中一个导通，从而带动断路器合闸、分闸动作。现有的斥力换 向阀利用斥力阀响应速度快的特点满足阀芯快速动作的需求。
但现有的斥力换向阀也存在一些弊端：现有斥力换向阀中阀套和阀芯的尺寸变化较多，结构较为复杂。而且现有的阀芯依靠移动到位后与阀套在轴向上进行线接触而实现密封，对阀芯的运动到位后的控制精度，以及阀套和阀芯的加工精度要求较高。若阀芯运动的精准度较差，或者阀芯、阀套的加工精度较低，或者长时间使用后阀口会被破坏，均容易出现阀芯和阀套无法接触密封，从而导致漏油的情况发生。对阀芯运动的精准度以及阀芯、阀套的加工精度要求较高就导致了液压控制阀以及整个液压操动机构的整体加工和使用成本提高。一旦出现漏油的问题，还会导致液压操动机构无法带动断路器等开关分合闸到位或者无法将开关保持在分合闸位置的情况发生。
申请内容
本申请在于提供一种液压控制阀，以解决液压控制阀结构复杂、易漏油的技术问题；还提供一种使用该液压控制阀的液压操动机构，以解决液压操动机构结构复杂、无法保证动触头分合闸到位或不易保持分合闸状态的技术问题；还提供一种使用该液压控制阀的断路器，以解决上述技术问题。
为实现上述目的，本申请液压控制阀的技术方案是：一种液压控制阀，包括：
阀体，内有阀腔，阀体上沿直线方向依次设置有与阀腔连通的常高压油口、控制油口和常低压油口；
阀芯，受驱动机构的控制而沿该直线方向往复滑动地设置在阀腔内；
阀腔内壁于常高压油口和常高低油口之间设有等径直段，阀芯外周面与所述等径直段内壁中的至少一个上设有密封圈，以实现阀芯和等径直段的滑动密封配合；
阀芯的往复滑动行程上有第一极限位和第二极限位，位于第一极限位时，阀芯位于常高压油口与控制油口之间，常低压油口与控制油口连通；位于第二极限位时，阀芯位于常低压油口与控制油口之间，常高压油口与 控制油口连通。
进一步地，所述阀腔整体为与所述等径直段内径相同的等径结构。阀腔整体为等径结构，加工时更加方便。
进一步地，液压控制阀包括驱动杆，驱动杆与阀芯同轴布置，驱动杆与阀芯分体固连或一体成型，驱动杆外径小于阀芯外径而形成活塞式结构；
所述驱动杆的一端延伸至阀体外部；
所述驱动机构为斥力机构，斥力机构分体布置在阀体外部，斥力机构与驱动杆中位于阀体外部的一端相连，斥力机构带动阀芯往复滑动并可将阀芯保持在所述第一极限位和第二极限位。通过斥力机构可以带动阀芯快速往复滑动，而且由于阀芯与阀体之间为周向密封的关系，在滑动至极限位时并不会产生撞击力，不会对阀芯和阀体产生伤害。斥力机构布置在阀体的外部，通过驱动杆带动阀芯动作，由于斥力机构与阀体分体布置，斥力机构的尺寸不受阀体的限制，可以选择更高移动速度的斥力机构。
进一步地，在阀芯的直线移动方向上，常高压油口、常低压油口中的至少一个与控制油口的间距大于所述阀芯的长度。这样设置的目的在于，即使阀芯移动到极限位时有一定的误差，也能够保证阀芯位于对应油口之间，而且尽可能地避免阀芯与油口之间对应，从而遮挡部分油口，从而影响通油量。
进一步地，在阀芯的直线移动方向上，常高压油口、常低压油口与控制油口的间距相同。两者的间距相同，保证阀芯的正向移动和反向移动的距离可以保持相同，便于进行控制。
本申请的液压操动机构的技术方案是：一种液压操动机构，包括：
工作缸，用于带动动触头分合闸；
液压控制阀，用于控制工作缸的活塞伸缩；
液压控制阀包括：阀体，内有阀腔，阀体上沿直线方向依次设置有与阀腔连通的常高压油口、控制油口和常低压油口；
阀芯，受驱动机构的控制而沿该直线方向往复滑动地设置在阀腔内；
阀腔内壁于常高压油口和常高低油口之间设有等径直段，阀芯外周面 与所述等径直段内壁中的至少一个上设有密封圈，以实现阀芯和等径直段的滑动密封配合；
阀芯的往复滑动行程上有第一极限位和第二极限位，位于第一极限位时，阀芯位于常高压油口与控制油口之间，常低压油口与控制油口连通；位于第二极限位时，阀芯位于常低压油口与控制油口之间，常高压油口与控制油口连通。
进一步地，所述阀腔整体为与所述等径直段内径相同的等径结构。阀腔整体为等径结构，加工时更加方便。
进一步地，液压控制阀包括驱动杆，驱动杆与阀芯同轴布置，驱动杆与阀芯分体固连或一体成型，驱动杆外径小于阀芯外径而形成活塞式结构；
所述驱动杆的一端延伸至阀体外部；
所述驱动机构为斥力机构，斥力机构分体布置在阀体外部，斥力机构与驱动杆中位于阀体外部的一端相连，斥力机构带动阀芯往复滑动并可将阀芯保持在所述第一极限位和第二极限位。通过斥力机构可以带动阀芯快速往复滑动，而且由于阀芯与阀体之间为周向密封的关系，在滑动至极限位时并不会产生撞击力，不会对阀芯和阀体产生伤害。斥力机构布置在阀体的外部，通过驱动杆带动阀芯动作，由于斥力机构与阀体分体布置，斥力机构的尺寸不受阀体的限制，可以选择更高移动速度的斥力机构。
进一步地，在阀芯的直线移动方向上，常高压油口、常低压油口中的至少一个与控制油口的间距大于所述阀芯的长度。这样设置的目的在于，即使阀芯移动到极限位时有一定的误差，也能够保证阀芯位于对应油口之间，而且尽可能地避免阀芯与油口之间对应，从而遮挡部分油口，从而影响通油量。
进一步地，在阀芯的直线移动方向上，常高压油口、常低压油口与控制油口的间距相同。两者的间距相同，保证阀芯的正向移动和反向移动的距离可以保持相同，便于进行控制。
本申请断路器的技术方案是：一种断路器，包括：
断口结构，断口结构包括动触头和静触头；
液压操动机构，用于带动断口结构的动触头分合闸；
液压操动机构包括：
工作缸，用于带动所述动触头分合闸；
液压控制阀，用于控制工作缸的活塞伸缩；
液压控制阀包括：阀体，内有阀腔，阀体上沿直线方向依次设置有与阀腔连通的常高压油口、控制油口和常低压油口；
阀芯，受驱动机构的控制而沿该直线方向往复滑动地设置在阀腔内；
阀腔内壁于常高压油口和常高低油口之间设有等径直段，阀芯外周面与所述等径直段内壁中的至少一个上设有密封圈，以实现阀芯和等径直段的滑动密封配合；
阀芯的往复滑动行程上有第一极限位和第二极限位，位于第一极限位时，阀芯位于常高压油口与控制油口之间，常低压油口与控制油口连通；位于第二极限位时，阀芯位于常低压油口与控制油口之间，常高压油口与控制油口连通。
进一步地，所述阀腔整体为与所述等径直段内径相同的等径结构。阀腔整体为等径结构，加工时更加方便。
进一步地，液压控制阀包括驱动杆，驱动杆与阀芯同轴布置，驱动杆与阀芯分体固连或一体成型，驱动杆外径小于阀芯外径而形成活塞式结构；
所述驱动杆的一端延伸至阀体外部；
所述驱动机构为斥力机构，斥力机构分体布置在阀体外部，斥力机构与驱动杆中位于阀体外部的一端相连，斥力机构带动阀芯往复滑动并可将阀芯保持在所述第一极限位和第二极限位。通过斥力机构可以带动阀芯快速往复滑动，而且由于阀芯与阀体之间为周向密封的关系，在滑动至极限位时并不会产生撞击力，不会对阀芯和阀体产生伤害。斥力机构布置在阀体的外部，通过驱动杆带动阀芯动作，由于斥力机构与阀体分体布置，斥力机构的尺寸不受阀体的限制，可以选择更高移动速度的斥力机构。
进一步地，在阀芯的直线移动方向上，常高压油口、常低压油口中的至少一个与控制油口的间距大于所述阀芯的长度。这样设置的目的在于，即使阀芯移动到极限位时有一定的误差，也能够保证阀芯位于对应油口之间，而且尽可能地避免阀芯与油口之间对应，从而遮挡部分油口，从而影 响通油量。
进一步地，在阀芯的直线移动方向上，常高压油口、常低压油口与控制油口的间距相同。两者的间距相同，保证阀芯的正向移动和反向移动的距离可以保持相同，便于进行控制。
本申请的液压控制阀的有益效果是：阀腔内有等径直段，阀芯外周面与等径直段之间滑动密封配合，不需要设置阀套，阀芯与阀体之间是周向密封的方式，阀体的内径尺寸、阀芯的外径尺寸不需要有过大的变化，使得阀芯、阀体的整体结构均较为简单。而且，阀芯与阀体之间为周向密封，在整体往复滑动的行程上均保持密封，阀芯只要位于常高压油口与控制油口之间(第一极限位)就可以隔开常高压油口与控制油口，只要位于常低压油口与控制油口之间(第二极限位)就可以隔开常低压油口与控制油口，对阀芯运动到位后位置的要求不太严格，允许有一定的位置偏差存在，降低了加工装配的难度，而且不会出现漏油的情况。
本申请的液压操动机构的有益效果是：阀腔内有等径直段，阀芯外周面与等径直段之间滑动密封配合，不需要设置阀套，阀芯与阀体之间是周向密封的方式，阀体的内径尺寸、阀芯的外径尺寸不需要有过大的变化，使得阀芯、阀体的整体结构均较为简单。而且，阀芯与阀体之间为周向密封，在整体往复滑动的行程上均保持密封，阀芯只要位于常高压油口与控制油口之间(第一极限位)就可以隔开常高压油口与控制油口，只要位于常低压油口与控制油口之间(第二极限位)就可以隔开常低压油口与控制油口，对阀芯运动到位后位置的要求不太严格，允许有一定的位置偏差存在，降低了液压控制阀以及液压操动机构加工装配的难度，而且不会出现漏油的情况，从而保证液压操动机构控制的动触头能够顺利分合闸到位以及保持在分合闸位置。
本申请的断路器的有益效果是：阀腔内有等径直段，阀芯外周面与等径直段之间滑动密封配合，不需要设置阀套，阀芯与阀体之间是周向密封的方式，阀体的内径尺寸、阀芯的外径尺寸不需要有过大的变化，使得阀芯、阀体的整体结构均较为简单。而且，阀芯与阀体之间为周向密封，在整体往复滑动的行程上均保持密封，阀芯只要位于常高压油口与控制油口 之间(第一极限位)就可以隔开常高压油口与控制油口，只要位于常低压油口与控制油口之间(第二极限位)就可以隔开常低压油口与控制油口，对阀芯运动到位后位置的要求不太严格，允许有一定的位置偏差存在，降低了液压控制阀以及液压操动机构加工装配的难度，而且不会出现漏油的情况，从而保证液压操动机构控制的动触头能够顺利分合闸到位以及保持在分合闸位置。
附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍。
图1是本申请液压控制阀实施例1中分闸位置的示意图；
图2是本申请液压控制阀实施例1中合闸位置的示意图。
附图标记说明：1-阀体；2-斥力机构；3-阀腔；4-常高压油口；5-控制油口；6-常低压油口；7-第一密封圈；8-驱动杆；9-阀芯；10-第二密封圈；11-合闸线圈；12-分闸线圈；13-电容；14-电容开关；15-斥力盘；16-输出杆；17-连接装置；18-双稳弹簧保持装置
具体实施方式
为了使本申请的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本申请进行进一步详细说明。应当理解，此处所描述的具体实施例仅用以解释本申请，并不用于限定本申请，即所描述的实施例仅仅是本申请一部分实施例，而不是全部的实施例。通常在此处附图中描述和示出的本申请实施例的组件可以以各种不同的配置来布置和设计。
因此，以下对在附图中提供的本申请的实施例的详细描述并非旨在限制要求保护的本申请的范围，而是仅仅表示本申请的选定实施例。基于本申请的实施例，本领域技术人员在没有做出创造性劳动的前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明的是，术语“第一”和“第二”等之类的关系术语仅仅用来将一个实体或者操作与另一个实体或操作区分开来，而不一定要求或者暗 示这些实体或操作之间存在任何这种实际的关系或者顺序。而且，术语“包括”、“包含”或者其任何其他变体意在涵盖非排他性的包含，从而使得包括一系列要素的过程、方法、物品或者设备不仅包括那些要素，而且还包括没有明确列出的其他要素，或者是还包括为这种过程、方法、物品或者设备所固有的要素。在没有更多限制的情况下，由语句“包括一个……”限定的要素，并不排除在包括所述要素的过程、方法、物品或者设备中还存在另外的相同要素。
以下结合实施例对本申请的特征和性能作进一步的详细描述。
本申请的液压控制阀的具体实施例1：
如图1至图2所示，液压控制阀包括阀体1、阀芯9、驱动杆8以及带动阀芯9往复移动的斥力机构2。
如图1所示，以阀体1的长度方向为阀体1的轴向，阀体1轴向为左右方向，斥力机构2位于阀体1的左侧。阀体1内有阀腔3，阀腔3左右延伸，而且，阀腔3内壁各处等径，使得阀腔3形成等径结构。等径结构说明阀腔3垂直于轴向的截面的面积相同。在阀体1上由左向右依次设置有常高压油口4、控制油口5和常低压油口6，各油口均与阀腔3内部连通。常高压油口4、控制油口5和常低压油口6三者，任意相邻两者在左右方向上的间距相同。在各油口处均安装有接头，用来与油管接头进行相连。在阀体1的左端端部开设有连通阀腔3内外的穿孔，穿孔内开设有内环槽，内环槽中嵌装有第一密封圈7，第一密封圈7的作用是与驱动杆8滑动密封配合，防止此处漏油。由图1可以看出，三个油口均沿着阀体1的径向延伸布置，且沿轴向并排布置。
阀芯9的结构如图1所示，阀芯9整体为圆柱体，与阀体1同轴布置。在阀芯9的外周面上设置有外环槽，外环槽上嵌装有第二密封圈10，第二密封圈10的作用是保证阀芯9在滑动的过程中与阀腔3内壁密封配合，防止漏油。当然，其他实施例中，第二密封圈可以位于阀腔的内壁上，或者在阀腔的内壁和阀芯外周面上均布置第二密封圈。而且，本实施例中，阀芯9的轴向长度小于常高压油口4与控制油口5的轴向间距，也小于常低压油口6与控制油口5的轴向间距。
在阀芯9的左端上一体成型有驱动杆8，驱动杆8与阀芯9同轴布置，驱动杆8的外径小于阀芯9的外径，阀芯9和驱动杆8形成了活塞式的结构。驱动杆8由上述的穿孔中向左穿出。
斥力机构2如图1所示，斥力机构2包括沿左右方向依次间隔排布的合闸线圈11和分闸线圈12，合闸线圈11和分闸线圈12上均连有电容13和电容开关14，电容开关14关合时，电容13向对应的线圈供电。合闸线圈11和分闸线圈12之间布置有斥力盘15，斥力盘15为金属盘，当合闸线圈11和分闸线圈12的其中一个通电时，剧烈的电流变化会使斥力盘15产生一个反向的感应电流，在通电的线圈与斥力盘15之间产生巨大的排斥力，推动斥力盘15快速运动。在斥力盘15上固定有输出杆16，输出杆16穿过合闸线圈11和分闸线圈12。输出杆16与驱动杆8之间通过连接装置17相连，此处的连接装置17可以为联轴器，或者是螺纹连接套等。
如图1所示，斥力机构2还包括位于合闸线圈11左端的双稳弹簧保持装置18，输出杆16与双稳弹簧保持装置18相连，其中，双稳弹簧保持装置18为现有的结构，在此不再赘述。双稳弹簧保持装置18能够在阀芯9移动至极限位置时，将阀芯9保持在该极限位置，避免阀芯9被液压或其他外力驱动而移动，影响断路器的分合闸状态。本申请中的斥力机构2可以参考授权公告号为CN104362050B的中国申请专利。
本申请的使用过程是：当断路器需要合闸时，合闸线圈11上的电容开关14关合，电容13向合闸线圈11供电，剧烈的电流变化会使斥力盘15产生一个反向的感应电流，合闸线圈11与斥力盘15会产生巨大的排斥力，推动斥力盘15向右快速运动，通过输出杆16、驱动杆8带动阀芯9快速向右移动至图2所示的位置，阀芯9运动到位后，阀芯9位于控制油口5与常低压油口6之间，将控制油口5与常低压油口6隔开，并使控制油口5与常高压油口4连通。阀芯9移动到位后，双稳弹簧保持装置18将阀芯9保持在该位置，该位置为阀芯9的第二极限位。
当断路器需要分闸时，分闸线圈12上的电容开关14关合，电容13向分闸线圈12供电，剧烈的电流变化会使斥力盘15产生一个反向的感应电流，分闸线圈12与斥力盘15会产生巨大的排斥力，推动斥力盘15向左快 速运动，通过输出杆16、驱动杆8带动阀芯9快速向左移动至图1所示的位置，阀芯9运动到位后，阀芯9位于控制油口5与常高压油口4之间，将控制油口5与常高压油口4隔开，并使控制油口5与常低压油口6连通。阀芯9移动到位后，双稳弹簧保持装置18将阀芯9保持在该位置，该位置为阀芯9的第一极限位。
本申请中，阀芯9与阀体1之间的密封方式采用的是阀芯9上的第二密封圈10与阀腔3的内壁之间的配合方式，阀腔3、阀芯9整体上均为等径结构，结构简单，加工方便，而且装配时也较为方便。另外，根据以上的描述，阀芯9的轴向长度小于常高压油口4与控制油口5的轴向间距，也小于常低压油口6与控制油口5的轴向间距。只要阀芯9位于常高压油口4与控制油口5之间，就可以将常高压油口4与控制油口5隔开，对阀芯9运动到位的位置要求并不严格，允许有一定的位置偏差存在，降低了加工和装配的难度。
在实际设计和制作时，需要保证的是，阀芯9在第一极限位和第二极限位时，不能与油口对应，避免油口处过油不畅。当然，在实际使用和制作时，若能够保证分合闸的速度，即使阀芯在极限位时与油口之间有一定的重合之处，也能够满足正常的使用。
其中，由图1和图2以及上述的描述可以知道，驱动杆8的一端由阀体1中穿出，斥力机构2是分体地布置在阀体1的外部，斥力机构2的尺寸不受阀体1的限制，可以将斥力机构2中的线圈以及斥力盘15的尺寸进行加大，从而提高分合闸速度。
本申请的液压控制阀的具体实施例2：
实施例1中，阀芯的轴向长度小于常高压油口与控制油口的轴向间距，也小于常低压油口与控制油口的轴向间距。本实施例中，阀芯的轴向长度可以仅小于常高压油口与控制油口的轴向间距，而等于常低压油口与控制油口的轴向间距，当然，也可以略大于常低压油口与控制油口的轴向间距。或者阀芯的轴向长度可以仅小于常低压油口与控制油口的轴向间距，而等于常高压油口与控制油口的轴向间距，当然，也可以略大于常高压油口与控制油口的轴向间距。
本申请的液压控制阀的具体实施例3：
实施例1中，各油口均径向延伸地布置在阀体上，本实施例中，常低压油口可以设置在阀体的端部。
本申请的液压控制阀的具体实施例4：
实施例1中，常低压油口位于常高压油口的右侧，本实施例中，常低压油口与常高压油口之间可以进行互换。
本申请的液压控制阀的具体实施例5：
实施例1中，常高压油口、控制油口和常低压油口中任意相邻两个之间的间距一致，使得阀芯的往复移动行程一致，方便进行控制。本实施例中，两个间距可以有所差异。
本申请的液压控制阀的具体实施例6：
实施例1中，阀腔的内径整体上相同，阀腔整体为等径结构。位于常低压油口和常高压油口之间的部分形成等径直段。本实施例中，阀腔中位于常低压油口和常高压油口之间的部分仍然等径，而阀腔中其他的部分内径可以进行增大或减小。
本申请的液压控制阀的具体实施例7：
实施例1中，斥力机构带动阀芯往复移动，并依靠双稳弹簧保持装置将阀芯保持在第一极限位和第二极限位，斥力机构形成了驱动机构。本实施例中，斥力机构可以集成于阀体上。
驱动机构的作用是带动阀芯往复移动，基于该目的之下，在其他实施例中，根据对分合闸速度的需求，也可以采用其他形式的驱动机构，例如电磁铁。当然，也可以仍然采用电磁先导阀的方式控制阀芯往复移动。
本申请液压操动机构的具体实施例：
液压操动机构包括工作缸，工作缸中有带动动触头分合闸的活塞，液压操动机构还包括控制活塞伸缩的液压控制阀，液压控制阀的结构与上述各实施例中的一致，在此不再赘述。
本申请断路器的具体实施例：
断路器包括断口结构，断口结构包括动触头和静触头，还包括带动动触头分合闸的液压操动机构，液压操动机构与上述各实施例中的液压操动 机构一致，在此不再赘述。
以上所述，仅为本申请的较佳实施例，并不用以限制本申请，本申请的专利保护范围以权利要求书为准，凡是运用本申请的说明书及附图内容所作的等同结构变化，同理均应包含在本申请的保护范围内。

Claims (10)

  1. 一种液压控制阀，包括：
    阀体，内有阀腔，阀体上沿直线方向依次设置有与阀腔连通的常高压油口、控制油口和常低压油口；
    阀芯，受驱动机构的控制而沿该直线方向往复滑动地设置在阀腔内；
    其特征在于：
    阀腔内壁于常高压油口和常低压油口之间设有等径直段，阀芯外周面与所述等径直段内壁中的至少一个上设有密封圈，以实现阀芯和等径直段的滑动密封配合；
    阀芯的往复滑动行程上有第一极限位和第二极限位，位于第一极限位时，阀芯位于常高压油口与控制油口之间，常低压油口与控制油口连通；位于第二极限位时，阀芯位于常低压油口与控制油口之间，常高压油口与控制油口连通。
  2. 根据权利要求1所述的液压控制阀，其特征在于：所述阀腔整体为与所述等径直段内径相同的等径结构。
  3. 根据权利要求1或2所述的液压控制阀，其特征在于：液压控制阀包括驱动杆，驱动杆与阀芯同轴布置，驱动杆与阀芯分体固连或一体成型，驱动杆外径小于阀芯外径而形成活塞式结构；
    所述驱动杆的一端延伸至阀体外部；
    所述驱动机构为斥力机构，斥力机构分体布置在阀体外部，斥力机构与驱动杆中位于阀体外部的一端相连，斥力机构带动阀芯往复滑动并可将阀芯保持在所述第一极限位和第二极限位。
  4. 根据权利要求1或2所述的液压控制阀，其特征在于：在阀芯的直线移动方向上，常高压油口、常低压油口中的至少一个与控制油口的间距大于所述阀芯的长度。
  5. 根据权利要求1或2所述的液压控制阀，其特征在于：在阀芯的直线移动方向上，常高压油口、常低压油口与控制油口的间距相同。
  6. 一种液压操动机构，包括：
    工作缸，用于带动动触头分合闸；
    液压控制阀，用于控制工作缸的活塞伸缩；
    液压控制阀包括：阀体，内有阀腔，阀体上沿直线方向依次设置有与阀腔连通的常高压油口、控制油口和常低压油口；
    阀芯，受驱动机构的控制而沿该直线方向往复滑动地设置在阀腔内；
    其特征在于：
    阀腔内壁于常高压油口和常高低油口之间设有等径直段，阀芯外周面与所述等径直段内壁中的至少一个上设有密封圈，以实现阀芯和等径直段的滑动密封配合；
    阀芯的往复滑动行程上有第一极限位和第二极限位，位于第一极限位时，阀芯位于常高压油口与控制油口之间，常低压油口与控制油口连通；位于第二极限位时，阀芯位于常低压油口与控制油口之间，常高压油口与控制油口连通。
  7. 根据权利要求6所述的液压操动机构，其特征在于：所述阀腔整体为与所述等径直段内径相同的等径结构。
  8. 根据权利要求6或7所述的液压操动机构，其特征在于：液压控制阀包括驱动杆，驱动杆与阀芯同轴布置，驱动杆与阀芯分体固连或一体成型，驱动杆外径小于阀芯外径而形成活塞式结构；
    所述驱动杆的一端延伸至阀体外部；
    所述驱动机构为斥力机构，斥力机构分体布置在阀体外部，斥力机构与驱动杆中位于阀体外部的一端相连，斥力机构带动阀芯往复滑动并可将阀芯保持在所述第一极限位和第二极限位。
  9. 根据权利要求6或7所述的液压操动机构，其特征在于：在阀芯的直线移动方向上，常高压油口、常低压油口中的至少一个与控制油口的间距大于所述阀芯的长度。
  10. 一种断路器，包括：
    断口结构，断口结构包括动触头和静触头；
    液压操动机构，用于带动断口结构的动触头分合闸；
    其特征在于：
    所述液压操动机构为权利要求6至9中任一权利要求所述的液压操动机构。
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