Rapid opening control system for hydraulic operating mechanism

Abstract

The invention relates to a quick opening control system for a hydraulic operating mechanism, which comprises a control valve assembly and an electromagnetic repulsion tripping assembly, and is characterized in that the control valve assembly comprises a control valve seat and a valve core; the control valve assembly further comprises an opening electromagnetic valve for controlling the valve element to move towards the right side to achieve opening and a closing electromagnetic valve for controlling the valve element to move towards the left side to achieve closing, and the electromagnetic repulsion tripping assembly comprises a tripping assembly frame body and a connecting rod assembly connected into the tripping assembly frame body in a sliding mode in the moving direction of the valve element. The connecting rod assembly is fixedly connected with a repulsive force disc, an opening coil matched with the repulsive force disc is fixedly connected into the tripping assembly frame body, and one end of the connecting rod assembly extends into the control valve seat and pushes the valve element to move towards the right side to achieve rapid opening. The opening time of the circuit breaker is shortened to be within 8ms; and electromagnetic repulsion driving and dual-redundancy design are adopted, so that the reliable action of the opening electromagnetic valve is not influenced when an electromagnetic repulsion tripping assembly fails.

Description

Technical Field

[0001] The invention relates to the technical field of circuit breakers, and in particular to a fast opening control system for a hydraulic operating mechanism. Background Art

[0002] With the expansion of the scale of power systems and the rapid growth of grid system loads, the short-circuit current of power systems has increased year by year, and large short-circuit currents have threatened the safe operation of grid equipment. In order to quickly cut off the fault short-circuit current and better protect grid equipment. In recent years, fast circuit breakers have become a hot topic of concern and research in the industry. High-voltage and ultra-high-voltage fast circuit breakers need to be equipped with high-power fast hydraulic operating mechanisms, and the research and development of fast tripping devices is the key to realizing the fast action function of the operating mechanism.

[0003] The opening time of conventional high-voltage circuit breakers is generally around 20 milliseconds, and new fast circuit breakers need to shorten the opening time to within a few milliseconds. The opening time can generally be divided into two parts: the operating mechanism control action time and the circuit breaker movement opening time. Because the high-voltage and ultra-high-voltage circuit breakers have a large moving mass and require a lot of operating power, the opening time that can be shortened by increasing their opening speed is relatively small, so shortening the operating mechanism control action time is more critical. Conventional control valves are generally controlled by solenoid valves, and the action time is relatively long. If this time is to be significantly shortened, a new type of fast tripping device must be designed. Summary of the invention

[0004] In view of the deficiencies in the prior art, the present invention provides a rapid tripping control system for a hydraulic operating mechanism, which solves the problems of slow electromagnet response, long action time, and limited tripping speed improvement in existing conventional SF6 circuit breakers. The full breaking time is about 50ms, which cannot meet the needs of dynamic topology adjustment and rapid isolation of important equipment failures.

[0005] The present invention is achieved through the following technical scheme, which provides a rapid gate-off control system for a hydraulic operating mechanism, including a control valve assembly and an electromagnetic repulsion release assembly, wherein the control valve assembly includes a control valve seat and a valve core, the control valve assembly also includes a gate-off solenoid valve for controlling the valve core to move to the right to achieve gate-off, and a gate-off solenoid valve for controlling the valve core to move to the left to achieve gate-off, the electromagnetic repulsion release assembly includes a release assembly frame and a connecting rod assembly slidably connected to the release assembly frame along the movement direction of the valve core, a repulsion disk is fixedly connected to the connecting rod assembly, a gate-off coil adapted to the repulsion disk is fixedly connected to the release assembly frame, one end of the connecting rod assembly extends into the control valve seat and pushes the valve core to move to the right to achieve rapid gate-off.

[0006] As an optimization, the control valve seat is provided with a low-pressure oil port, a variable oil port and a high-pressure oil port arranged from left to right, and a left valve core seat and a right valve core seat wrapped around the left and right ends of the valve core are fixedly connected in the control valve seat, and an A3 piston, an A2 piston and an A1 piston are fixedly connected to the valve core in sequence, the left side of the A3 piston and the left valve core seat constitute an A3 chamber, the right side of the A1 piston and the right valve core seat constitute an A1 chamber, the right side of the A2 piston is connected with the left side of the A3 piston through a connecting hole, and in the open state, the right side of the A2 piston and the right valve core seat constitute an A2 chamber and the A2 chamber is connected with the high-pressure oil port, the pressurized cross-sectional areas of the A3 piston, the A2 piston and the A1 piston are S3, S2 and S1 respectively, and S1<S2<S3, S1+S2>S3; the closing solenoid valve is connected with the high-pressure oil port and the A1 chamber, and the opening solenoid valve is connected with the low-pressure oil port and the A1 chamber.

[0007] As an optimization, the end seal of the connecting rod assembly penetrates into the A3 cavity.

[0008] As an optimization, the stroke of the connecting rod assembly is smaller than the stroke of the valve core. During the gate opening process, after the connecting rod assembly pushes the valve core to move a certain distance, the oil pressure difference between the pressurized cross-sectional areas S3 and S2 drives the valve core to continue to move to the right to achieve gate opening.

[0009] As an optimization, a sliding valve is installed in the control valve seat, and both ends of the sliding valve are connected to the variable oil port and the A1 cavity. When the connecting rod assembly pushes the valve core to move to the right, the sliding valve is driven to be connected.

[0010] As an optimization, a crank arm is hinged on the control valve seat, and a sliding valve push rod is slidably connected in the control valve seat. The connecting rod assembly pushes the crank arm to swing to the right, and the sliding valve is driven to be connected through the sliding valve push rod. A crank arm reset spring is installed on the control valve seat to drive the crank arm to swing to the left.

[0011] As an optimization, an adjusting bolt is threadedly connected to the crank arm, and the sliding valve push rod is pushed by the end of the adjusting bolt.

[0012] As an optimization, a flow oil passage connecting the A1 cavity and the variable oil port is opened on the right valve core seat, and the inner diameter of the flow oil passage at the smallest cross-section is 0.1-1mm.

[0013] As an optimization, a buffer pad is provided on the side of the repulsion disk away from the opening coil.

[0014] As an optimization, two of the repulsion disks and two of the opening coils are provided respectively.

[0015] The beneficial effects of the present invention are: (1) Compared with conventional circuit breakers, the breaking time of fast circuit breakers is shortened from 50ms to less than 25ms, which can quickly clear faults and is suitable for the rapid clearing of UHV converter transformer explosion prevention faults.

[0016] (2) Use a large flow control valve to quickly transmit oil pressure and improve the output power and transmission efficiency of the hydraulic mechanism, which can shorten the mechanical separation time of the contacts from 8-10ms to less than 4ms and the circuit breaker opening time to less than 8ms.

[0017] (3) It adopts electromagnetic repulsion drive and dual redundant design. It is equipped with two sets of repulsion disks and opening coils. At the same time, the conventional opening solenoid valve is retained. When the electromagnetic repulsion release component fails, it will not affect the reliable operation of the opening solenoid valve; the closing operation adopts the closing solenoid valve. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is an internal cross-sectional view of the present invention; Figure 2 It is a cross-sectional view of the interior of the electromagnetic repulsion release assembly of the present invention; Figure 3 It is an internal cross-sectional view of the control valve assembly of the present invention in the open state; Figure 4 It is an internal cross-sectional view of the control valve assembly of the present invention in a closed state; Figure 5 It is a cross-sectional view of the valve core of the present invention; Figure 6 It is a cross-sectional view of the right valve core seat of the present invention; Figure 7 It is a left side view of the control valve assembly of the present invention; Figure 8 For the present invention Figure 7 Sectional view of the middle AA plane; Fig. 9 is a cross-sectional view of a slide valve of the present invention; As shown in the figure: 1. Control valve seat, 2. Left valve core seat, 3. Right valve core seat, 31. Oil passage, 4. Valve core, 41. A1 piston, 42. A2 piston, 43. A3 piston, 44. Connecting hole, 5. Closing solenoid valve, 6. Opening solenoid valve, 7. Right pressure plate, 8. Push rod, 9. Connecting rod, 10. Left pressure plate, 11. Connecting nut, 12. Connecting rod, 13. Support rod, 14. Pressure plate, 15. Opening wire Ring, 16, buffer pad, 17, repulsion plate, 18, spacer, 19, guide sleeve, 20, buffer cap, 21, adjusting screw, 22, buffer plate, 23, crank arm, 24, crank arm mounting seat, 25, adjusting bolt, 26, slide valve push rod, 27, crank arm return spring, 28, slide valve seat, 29, slide valve core, 30, slide valve return spring, T, low pressure oil port, P, high pressure oil port, Z, variable oil port. DETAILED DESCRIPTION

[0019] In order to clearly illustrate the technical features of this solution, this solution is described below through a specific implementation method.

[0020] like Figures 1 to 9 As shown, a rapid opening control system for a hydraulic operating mechanism of the present invention includes a control valve assembly and an electromagnetic repulsion release assembly.

[0021] The control valve assembly includes a control valve seat 1 and a valve core 4. The valve core 4 moves axially in the control valve seat 1. The valve core 4 in this embodiment moves to the right to realize the opening of the circuit breaker, and moves to the left to realize the closing of the circuit breaker. The control valve assembly also includes an opening solenoid valve 6 for moving the control valve core 4 to the right to realize opening, and a closing solenoid valve 5 for moving the control valve core 4 to the left to realize closing. The opening solenoid valve 6 and the closing solenoid valve 5 are both fixed on the outside of the control valve seat 1. In this embodiment, two opening solenoid valves 6 are provided, namely a main opening solenoid valve and a secondary opening solenoid valve, which are arranged in parallel to ensure the stability of opening.

[0022] like Figure 3 , 4 As shown, the control valve seat 1 is provided with a low-pressure oil port T, a variable oil port Z and a high-pressure oil port P arranged from left to right, and the left and right ends of the control valve seat 1 are fixedly connected with a left valve core seat 2 and a right valve core seat 3 wrapped around the left and right ends of the valve core 8, and the left valve core seat 2 and the right valve core seat 3 are fixed by a left pressure plate 10 and a right pressure plate 7 respectively.

[0023] The left valve core seat 2 is provided with a plurality of radial holes for connecting with the low-pressure oil port T. The right valve core seat 3 is provided with a plurality of radial holes for connecting with the high-pressure oil port P. The variable oil port Z is connected between the left valve core seat 2 and the right valve core seat 3. A double-layer retaining ring sealing structure is provided at the high- and low-pressure oil circuit switching point in the control valve seat 1 to ensure that the sealing ring can withstand bidirectional high pressure and solve the problem of tearing defects on the sealing ring surface caused by sudden oil pressure shock.

[0024] The valve core 4 is fixedly connected with the A3 piston 43, the A2 piston 42 and the A1 piston 41 in sequence. The valve core can be a split structure or an integral structure. For ease of processing, a split structure is preferably used, which consists of a large valve core and a small valve core.

[0025] The A3 piston 43 is inserted into the countersunk hole of the left valve core seat 2, and the left side of the A3 piston 43 and the left valve core seat 2 form a closed A3 chamber. The A1 piston 41 is inserted into the countersunk hole of the right valve core seat 3, and the right side of the A1 piston 41 and the right valve core seat 3 form an A1 chamber. The right side of the A2 piston 42 is connected with the left side of the A3 piston 43 through the connecting hole 44, so the pressure in the A2 chamber is consistent with the pressure in the A3 chamber, and is always in a high-pressure state.

[0026] The A2 piston 42 slides between the right end opening of the left valve core seat 2 and the left end opening of the right valve core seat 3. When in the closed state, the A2 piston 42 blocks the right end opening of the left valve core seat 2. When in the open state, the A2 piston 42 blocks the left end opening of the right valve core seat 3. In the open state, the right side of the A2 piston 42 and the right valve core seat 3 form an A2 chamber, and the A2 chamber is connected to the high-pressure oil port P.

[0027] The pressure cross-sectional areas of the A3 piston 43, the A2 piston 42 and the A1 piston 41 are S3, S2 and S1 respectively. Since the A3 piston 43 is fully inserted into the inner hole of the left valve core seat 2, the pressure cross-sectional area of ​​the A3 piston 43 is also the outer diameter cross-sectional area of ​​the A3 piston 43; since the right end of the A2 piston 42 is inserted into the left end opening of the right valve core seat 3, the pressure cross-sectional area of ​​the A2 piston 42 refers to the outer diameter cross-sectional area of ​​the inserted part of the right end of the A2 piston 42 minus the cross-sectional area of ​​the A1 piston 41; the pressure cross-sectional area of ​​the A1 piston 41 refers to the outer diameter cross-sectional area of ​​the A1 piston 41.

[0028] S1<S2<S3, S1+S2>S3; the closing solenoid valve 5 connects the high-pressure oil port P and the A1 chamber, and the opening solenoid valve 6 connects the low-pressure oil port T and the A1 chamber.

[0029] The right valve core seat 3 is provided with a flow passage 31 connecting the A1 cavity and the variable oil port Z. The inner diameter of the flow passage 31 at the smallest cross section is 0.1-1 mm. Figure 4 As shown, when the gate is opened, the valve core 4 moves to the right, thereby compressing the A1 chamber. The purpose of the oil passage 31 is to allow the oil in the A1 chamber to flow out through the oil passage 31, thereby ensuring the rightward movement of the valve core 4.

[0030] The inner diameter of the smallest cross section of the oil passage 31 is 0.1-1mm and cannot be too large. This is to maintain a certain pressure in the A1 chamber when the switch is closed to prevent the oil passage 31 from being too large and causing the pressure to be released. The specific analysis is as follows: Figure 3 As shown, when the closing operation is performed, the closing solenoid valve 5 is energized to introduce the high-pressure oil in the high-pressure oil port P into the A1 chamber. Since the diameter of the flow oil channel 31 is very small, the pressure in the A1 chamber is maintained at a certain large value. At this time, the A2 chamber and the A3 chamber are also connected to the high-pressure oil in the high-pressure oil port P. Since S1+S2>S3, the resultant force on the valve core 4 is to the left.

[0031] The electromagnetic repulsion trip assembly includes a trip assembly frame and a connecting rod assembly that slides in the trip assembly frame along the moving direction of the valve core 4, the connecting rod assembly is fixedly connected to a repulsion disk 17, and the trip assembly frame is fixedly connected to a trip coil 15 that is adapted to the repulsion disk 17, one end of the connecting rod assembly extends into the control valve seat 1 and pushes the valve core 4 to move to the right to achieve rapid tripping.

[0032] like Figure 2 As shown, specifically, the trip assembly frame includes a plurality of side-by-side pressure plates 14 and a plurality of support rods 13 passing through the pressure plates 14. The right end of the support rod 13 is threadedly connected to the left pressure plate 10. The support rod 13 is also provided with a trip coil 15, a buffer pad 16, a support rod 13 and a plurality of spacers, etc., and each component is fastened to the support rod 13 by nuts.

[0033] The connecting rod assembly comprises a connecting rod 12, a connecting rod 9 and a push rod 8 which are arranged in sequence from left to right. The connecting rod 9 is threadedly connected to the right end of the connecting rod 12 and is prevented from loosening by a connecting nut 11. The connecting rod 12 is guided by a guide seat.

[0034] The repulsion disc 17 and the opening coil 15 are respectively provided with two. The two repulsion discs 17 are fixed on the connecting rod 12, and a spacer sleeve 18 is installed between the two repulsion discs 17.

[0035] The buffer pad 16 is arranged on the side of the repulsion disk 17 away from the opening coil 15, and the buffer pad 16 is preferably made of polyurethane. Therefore, both repulsion disks 17 are located between the opening coil 15 and the buffer pad 16, and the electromagnetic forces generated by the main and auxiliary opening coils are not affected by each other when either or both of them are energized, that is, the main opening coil is energized, which only drives the main repulsion disk to move, and will not affect the auxiliary repulsion disk, and vice versa. If any set of opening coils and repulsion disks work normally, the electromagnetic repulsion tripping device can drive the control valve to complete the oil circuit switching and realize the rapid opening of the switch.

[0036] The assembly method of the repulsion disk 17 and the connecting rod 12 can be a threaded fit, a clearance fit, or a one-thread-one-clearance fit. Preferably, the main and auxiliary repulsion disks and the connecting rod 12 are all threaded fit. In order to optimize the motion quality of the moving component and reduce the difficulty of component processing, according to the force form, the thread of the main repulsion disk and the connecting rod is preferably larger than the connecting thread of the auxiliary repulsion disk and the connecting rod. The assembly directions of the two repulsion disks can be in the same direction or back to back, or face to face. The design structure ensures that the repulsion disk and the intermediate connecting rod can be processed and formed by one clamping, avoiding the processing error caused by secondary clamping.

[0037] The left end of the connecting rod assembly is fixed with a buffer cap 20, and the left end of the trip assembly frame is fixed with a buffer plate 22 through an adjusting screw 21, so as to achieve buffering and limiting of the leftward movement of the connecting rod assembly and prevent the repulsion disk from installing the tripping coil.

[0038] The connecting rod 12, repulsion disc 17 and spacer sleeve in the moving components of the electromagnetic repulsion release assembly are preferably made of aluminum alloy material, which reduces the movement. At the same time, through simulation calculation, the strength of the moving components meets the product requirements. The material of the connecting rod 12 is preferably 2A12-T4, and the raw materials are inspected in accordance with the "Aluminum Alloy Inspection Specifications". The inspection items include tensile strength and elongation. The tensile strength of the material is ≥420MPa, and the elongation is ≥10%. The actual measurement is 501.9MPa and the elongation is 13.75%.

[0039] The end of the connecting rod assembly is sealed and penetrates into the A3 cavity. Specifically, the right end of the top rod 8 at the right end of the connecting rod assembly is sealed and penetrates into the A3 cavity. The top rod 8 and the connecting rod 9 are separate structures. The connecting rod 12 pushes the top rod 8 to move rightward through the connecting rod 9, and the top rod 8 pushes the valve core 4 to the right to realize rapid opening.

[0040] The electromagnetic repulsion release assembly in the present application pushes the structure of the control valve. The connecting rod assembly and the valve core of the control valve of this structure are changed from a direct-connected structure to a split structure, which can effectively solve the problem of large coaxiality caused by the connection between the moving components of the repulsion release device and the moving components of the control valve, that is, the large inclination between the moving components of the two along the center of the axis, which leads to the breakage of the middle connecting rod of the repulsion release device due to uneven force and the jamming of the valve core of the control valve.

[0041] The stroke of the connecting rod assembly is smaller than the stroke of the valve core 8. During the gate opening process, after the connecting rod assembly pushes the valve core 8 to move a certain distance, the valve core 8 is driven to continue to move to the right to realize the gate opening through the oil pressure difference between the pressure-bearing cross-sectional areas S3 and S2. Specifically, at the initial stage of the action of the repulsion disk 17, a large repulsion force acts on the repulsion disk 17. At the end of the movement of the repulsion disk 17, in order to reduce the impact of the valve core on the valve port, the repulsion disk 17 only drives the valve core 4 to move a large part of the stroke. At this time, the A2 piston 42 is disengaged from the left valve core seat 2, the variable oil port Z is low-pressure oil, and the A1 chamber is connected to the variable oil port Z. At this time, due to S3>S2, the combined force on the valve core 4 is to the right, thereby pushing the valve core 4 to move a small part of the remaining stroke. This structure can shorten the mechanism start-up time to within 4ms, and reduce the mechanical impact of the valve core and the valve core seat sealing part in the control valve, greatly improving the service life of the control valve.

[0042] like Figure 8 As shown, the control valve seat 1 is provided with a channel, in which a slide valve is installed. Fig. 9 As shown, the slide valve is composed of a slide valve seat 28, a slide valve core 29 and a slide valve return spring 30. When the slide valve core 29 moves to the right, the interfaces at both ends of the slide valve are connected, and the interfaces at both ends of the slide valve are connected to the variable oil port Z and the A1 cavity respectively. When the connecting rod assembly pushes the valve core 4 to move to the right, the slide valve is driven to be connected. After the connecting rod assembly returns to its position, the return spring 30 pushes the slide valve core 29 to return to the left to realize the closing of the slide valve.

[0043] The slide valve is used to switch the oil circuit between the conventional solenoid valve and the repulsion release assembly. That is, when the operating mechanism is in the opening and closing state, the slide valve is in the closed state, and the conventional solenoid valve can control the opening and closing actions of the operating mechanism; while in the process of the repulsion release device controlling the operating mechanism to quickly open, the slide valve is opened, the channel between the A1 chamber and the variable oil chamber Z is opened, and the control valve is switched to a large flow valve, which can meet the rapid conversion of the oil circuit driven by the repulsion release device, effectively shorten the control valve conversion time, and improve the response speed of the control valve.

[0044] In order to realize that when the connecting rod assembly pushes the valve core 4 to move to the right, the slide valve is turned on. Figure 8 As shown, a crank arm mounting seat 24 is fixedly connected to the left side of the control valve seat 1, and a crank arm 23 is hinged on the crank arm mounting seat 24 through a pin shaft. The other end of the crank arm 23 is a fork-shaped structure, and the connecting rod 9 is located in the fork of the fork-shaped structure. The crank arm 23 is pushed to swing to the right by moving the connecting nut 11 to the right.

[0045] A sliding valve push rod 26 is slidably connected in the control valve seat 1, and the connecting rod assembly pushes the crank arm 23 to swing rightward, and the sliding valve is driven to conduct through the sliding valve push rod 26. A crank arm return spring 27 is installed on the control valve seat 1 to drive the crank arm 23 to swing leftward.

[0046] The crank arm 23 is threadedly connected with an adjusting bolt 25, and the end of the adjusting bolt 25 pushes the slide valve push rod 26. By rotating the adjusting bolt 25, the triggering of the slide valve can be adjusted.

[0047] In order to ensure the stability of the opening time and eliminate the potential hidden dangers that affect the opening time, the gap adjustment method between the main and auxiliary repulsion plates and the main and auxiliary opening coils is as follows: (1) Gap pre-adjustment: Pre-make adjustment shims of different thicknesses. After assembling the repulsion mechanism body, add adjustment shims to make the main and auxiliary repulsion disks lean against the main and auxiliary sub-coils at the same time, so as to make the gap adjustment of the main and auxiliary repulsion disks consistent.

[0048] (2) Assemble the electromagnetic repulsion release assembly to the control valve, place the electromagnetic repulsion release assembly in the closed position, store energy in the mechanism body (extend the energy storage piston 10 to 20 mm), place the gap adjustment tool between the main repulsion disk and the main sub-coil, and use a wrench to turn the connecting rod to tighten the tool.

[0049] (3) Adjust the position of the connecting nut 11 on the connecting rod 9, use a wrench to tighten the thin nut to lock the connecting rod, tighten the buffer device at the rear end of the electromagnetic repulsion release assembly, depressurize the mechanism body, remove the tooling, place the repulsion mechanism in the closed position, and use a feeler gauge to measure the distance between the main repulsion disk and the main sub-coil, and between the sub-repulsion disk and the sub-coil. The requirement is 1.5 to 2 mm.

[0050] (4) To further ensure the accuracy of the gap adjustment, the four-point measurement method is used for re-measurement. Four evenly distributed points on the repulsion disk are taken and measured with a feeler gauge (accuracy of 0.1 mm).

[0051] This adjustment method can effectively ensure the stability of the opening and closing time of the repulsion mechanism, and eliminate potential hidden dangers and problems of the stability of the opening and closing time.

[0052] Method of use of the present invention: When the closing operation is performed, the closing solenoid valve 5 is energized, and the high-pressure oil in the high-pressure oil port P is introduced into the A1 chamber. The A2 chamber and the A3 chamber are also connected with the high-pressure oil in the high-pressure oil port P. Since S1+S2>S3, the combined force on the valve core 4 is to the left, and the high-pressure oil is introduced into the hydraulic working cylinder, causing the working cylinder to move rapidly. The working cylinder is connected to the moving end of the arc extinguishing chamber, driving the rapid movement of the arc extinguishing chamber to achieve closing.

[0053] There are two control modes for the opening operation, one is to perform the opening operation through the opening solenoid valve 6, and the other is to achieve rapid opening of the circuit breaker through the electromagnetic repulsion release component.

[0054] When the opening operation is performed through the opening solenoid valve 6, the opening solenoid valve 6 is energized, and the low-pressure oil of the low-pressure oil port T is introduced into the A1 chamber, so that the A1 chamber is filled with low-pressure oil. At this time, due to S3>S2, the combined force of the valve core 4 is to the right, and the low-pressure oil is introduced into the hydraulic working cylinder, causing the working cylinder to move rapidly. The working cylinder is connected to the moving end of the arc extinguishing chamber, driving the rapid movement of the arc extinguishing chamber to achieve opening.

[0055] In order to realize the rapid conversion of the mechanism oil circuit, a structure is designed to realize the rapid opening of the circuit breaker by the electromagnetic repulsion release assembly. Its working process is briefly described as follows: the opening coil 15 is energized by an external control power supply, and a pulse current is generated in the coil. The pulse current generates an alternating magnetic field around the coil and generates a reverse induced eddy current on the repulsion disk 17. The magnetic field generated by the eddy current interacts with the magnetic field generated by the coil current to generate an electromagnetic force. Driven by the electromagnetic force, the electromagnetic repulsion disk moves to the right, thereby driving the connecting rod assembly to move to the right, pushing the valve core 4 to move to the right, controlling the valve reversal, and realizing the rapid opening action of the mechanism. At the beginning of the movement of the repulsion disk 17, a large repulsion force acts on the repulsion disk 17. At the end of the movement of the repulsion disk 17, in order to reduce the impact of the valve core on the valve port, the repulsion disk 17 only drives the valve core 4 to move a large part of the stroke. At this time, the A2 piston 42 is disengaged from the left valve core seat 2, and the variable oil port Z is low-pressure oil. The A1 chamber is connected to the variable oil port Z. At this time, since S3>S2, the resultant force on the valve core 4 is to the right, thereby pushing the valve core 4 to move a small part of the remaining stroke. This structure can shorten the mechanism startup time to within 4ms, and reduce the mechanical impact on the sealing part of the valve core and the valve core seat in the control valve, thereby greatly improving the service life of the control valve.

[0056] Of course, the above description is not limited to the above examples. Technical features not described in the present invention can be achieved by or by using existing technologies, which will not be described here. The above embodiments and drawings are only used to illustrate the technical scheme of the present invention and are not limitations of the present invention. The present invention is described in detail with reference to the preferred implementation methods. Ordinary technicians in this field should understand that changes, modifications, additions or substitutions made by ordinary technicians in this technical field within the essential scope of the present invention do not depart from the purpose of the present invention, and should also fall within the scope of protection of the claims of the present invention.

Claims

1. A rapid opening control system for a hydraulic operating mechanism, characterized in that: The invention comprises a control valve assembly and an electromagnetic repulsion release assembly, wherein the control valve assembly comprises a control valve seat (1) and a valve core (4), the electromagnetic repulsion release assembly comprises a release assembly frame and a connecting rod assembly slidably connected in the release assembly frame along the moving direction of the valve core (4), the connecting rod assembly is fixedly connected to a repulsion disk (17), the release assembly frame is fixedly connected to a gate-opening coil (15) adapted to the repulsion disk (17), and one end of the connecting rod assembly extends into the control valve seat (1) and pushes the valve core (4) to move to the right to realize rapid gate opening.

2. A fast opening control system for a hydraulic operating mechanism according to claim 1, characterized in that: The control valve assembly further comprises a gate-opening solenoid valve (6) for opening the gate when the control valve core (4) moves to the right, and a gate-closing solenoid valve (5) for closing the gate when the control valve core (4) moves to the left. The control valve seat (1) is provided with a low-pressure oil port (T), a variable oil port (Z) and a high-pressure oil port (P) arranged from left to right. A left valve core seat (2) and a right valve core seat (3) wrapped around the left and right ends of the valve core (8) are fixedly connected in the control valve seat (1). An A3 piston (43), an A2 piston (42) and an A1 piston (41) are fixedly connected to the valve core (4) in sequence. The left side of the A3 piston (43) and the left valve core seat (2) form an A3 chamber. The right side of the A1 piston (41) and the right valve core seat (3) form an A1 chamber, and the right side of the A2 piston (42) and the left side of the A3 piston (43) are connected through a connecting hole (44). In the open state, the right side of the A2 piston (42) and the right valve core seat (3) form an A2 chamber, and the A2 chamber is connected to the high-pressure oil port (P). The pressure-bearing cross-sectional areas of the A3 piston (43), the A2 piston (42) and the A1 piston (41) are S3, S2 and S1 respectively, and S1<S2<S3, S1+S2>S3; the closing solenoid valve (5) is connected to the high-pressure oil port (P) and the A1 chamber, and the opening solenoid valve (6) is connected to the low-pressure oil port (T) and the A1 chamber.

3. A fast opening control system for a hydraulic operating mechanism according to claim 2, characterized in that: The end of the connecting rod assembly is sealed and penetrates into the A3 cavity.

4. A fast opening control system for a hydraulic operating mechanism according to claim 2, characterized in that: The stroke of the connecting rod assembly is smaller than the stroke of the valve core (8). During the gate opening process, after the connecting rod assembly pushes the valve core (8) to move a certain distance, the valve core (8) is driven to continue to move to the right through the oil pressure difference between the pressure-bearing cross-sectional areas S3 and S2 to achieve gate opening.

5. A fast opening control system for a hydraulic operating mechanism according to claim 2, characterized in that: The control valve seat (1) is provided with a slide valve, the two ends of which are connected to the variable oil port (Z) and the A1 chamber, and the connecting rod assembly drives the slide valve to be turned on when the valve core (4) moves to the right.

6. A fast opening control system for a hydraulic operating mechanism according to claim 5, characterized in that: A crank arm (23) is hingedly connected to the control valve seat (1), and a slide valve push rod (26) is slidably connected inside the control valve seat (1). The connecting rod assembly pushes the crank arm (23) to swing rightward, and the slide valve is driven to conduct through the slide valve push rod (26). The control valve seat (1) is provided with a crank arm return spring (27) for driving the crank arm (23) to swing leftward.

7. A fast opening control system for a hydraulic operating mechanism according to claim 6, characterized in that: An adjusting bolt (25) is threadedly connected to the crank arm (23), and the end of the adjusting bolt (25) pushes the slide valve push rod (26).

8. A fast opening control system for a hydraulic operating mechanism according to claim 2, characterized in that: The right valve core seat (3) is provided with an oil passage (31) communicating with the A1 cavity and the variable oil port (Z), and the inner diameter of the oil passage (31) at the smallest cross section is 0.1-1 mm.

9. A fast opening control system for a hydraulic operating mechanism according to claim 1, characterized in that: A buffer pad (16) is provided on the side of the repulsion disk (17) away from the opening coil (15).

10. A fast opening control system for a hydraulic operating mechanism according to claim 1, characterized in that: Two repulsive disks (17) and two opening coils (15) are provided respectively.

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