Dual-redundancy rapid opening and closing control system for hydraulic operating mechanism

Abstract

The invention relates to a dual-redundancy rapid opening and closing control system for a hydraulic operating mechanism, the dual-redundancy rapid opening and closing control system comprises a control valve assembly, a rapid opening and tripping assembly and a rapid closing and tripping assembly, the control valve assembly comprises a control valve seat and a valve core, and the rapid opening and tripping assembly comprises an opening and tripping frame body and an opening connecting rod assembly. The opening connecting rod assembly is fixedly connected with an opening repulsive force disc, an opening coil is fixedly connected into the opening tripping frame body, the opening connecting rod assembly pushes the valve element to move rightwards to achieve rapid opening, the rapid closing tripping assembly comprises a closing tripping frame body and a closing connecting rod assembly, and the closing connecting rod assembly is fixedly connected with a closing repulsive force disc. According to the invention, the opening tripping and the closing tripping both adopt dual-redundancy design, the opening operation and the closing operation both adopt electromagnetic force driving, and meanwhile, a conventional opening electromagnetic valve and a conventional closing electromagnetic valve are reserved; the failure of one tripping assembly does not affect the reliable action of the other tripping assembly.

Description

Technical Field

[0001] The invention relates to the technical field of circuit breakers, and in particular to a dual-redundancy rapid opening and closing 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 dual-redundant rapid opening and closing control system for a hydraulic operating mechanism, which solves the problems of slow electromagnet response, long action time, limited opening speed improvement, and a full opening time of about 50ms in conventional SF6 circuit breakers, which cannot meet the problems 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 dual-redundant rapid opening and closing control system for a hydraulic operating mechanism, including a control valve assembly, a rapid opening release assembly and a rapid closing release assembly, wherein the control valve assembly includes a control valve seat and a valve core, the rapid opening release assembly includes an opening release frame and an opening connecting rod assembly, the opening connecting rod assembly pushes the valve core to move to the right to achieve rapid opening, the rapid closing release assembly includes a closing release frame and a closing connecting rod assembly, and the closing connecting rod assembly pushes the valve core to move to the left to achieve rapid closing.

[0006] As an optimization, a switch-off repulsion disk is fixedly connected to the switch-off connecting rod assembly, a switch-off coil adapted to the switch-off repulsion disk is fixedly connected to the switch-off trip frame, and one end of the switch-off connecting rod assembly extends into the control valve seat.

[0007] As an optimization, a closing repulsion disk is fixedly connected to the closing linkage assembly, a closing coil adapted to the closing repulsion disk is fixedly connected to the closing release frame, and one end of the closing linkage assembly extends into the control valve seat.

[0008] As an optimization, the control valve assembly also includes a gate-opening solenoid valve that controls the valve core to move to the right to realize gate-opening, and a gate-closing solenoid valve that controls the valve core to move to the left to realize gate-closing. 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. The control valve seat is fixedly connected with a left valve core seat and a right valve core seat wrapped around the left and right ends of the valve core. The valve core is fixedly connected with an A3 piston, an A2 piston and an A1 piston in sequence. The left side of the A3 piston and the left valve core seat form an A3 chamber. The right side of the A1 piston and the right valve core seat form the A1 chamber, and the right side of the A2 piston is connected with the left side of the A3 piston through a connecting hole. In the open state, the right side of the A2 piston and the right valve core seat form the A2 chamber and the A2 chamber is connected with the high-pressure oil port. The pressure 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.

[0009] As an optimization, the stroke of the opening connecting rod assembly is smaller than the stroke of the valve core. During the opening process, after the opening 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 opening.

[0010] As an optimization, the stroke of the closing link assembly is smaller than the stroke of the valve core. During the closing process, after the closing link assembly pushes the valve core to move a certain distance, the pressure difference between the pressurized cross-sectional area S1+S2 and S3 drives the valve core to continue to move to the left to achieve closing.

[0011] 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 chamber. When the opening connecting rod assembly pushes the valve core to move to the right, the sliding valve is driven to be turned on. When the closing connecting rod assembly pushes the valve core to move to the left, the sliding valve is driven to be turned on.

[0012] As an optimization, a crank arm is hinged on the control valve seat, a sliding valve push rod is slidably connected in the control valve seat, the gate-opening connecting rod assembly pushes the crank arm to swing to the right, and the crank arm drives the sliding valve core of the sliding valve to move to the right through the sliding valve push rod to achieve conduction.

[0013] As an optimization, a driving rod is hinged on the control valve seat, and a sliding valve pull rod is fixedly connected to the sliding valve core of the sliding valve. The closing connecting rod assembly pushes one end of the driving rod to swing to the left, and the other end of the driving rod swings to the right to drive the sliding valve pull rod to the right, thereby realizing the conduction of the sliding valve.

[0014] 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.

[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) Both the opening tripping and closing tripping adopt a dual redundant design. Both the opening and closing operations are driven by electromagnetic force. At the same time, the conventional opening solenoid valve and closing solenoid valve are retained. The failure of one set of tripping devices will not affect the reliable operation of the other set.

[0018] (4) The fast circuit breaker closing and tripping also adopts fast tripping technology, while retaining the conventional closing electromagnet. The closing time is shortened to 45ms, the mechanical dispersion is ±0.5ms, and the closing time is stable, which is suitable for phase selection closing to suppress the excitation surge current of the commutation transformer. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 is an internal cross-sectional view of the present invention; Figure 2 It is an internal cross-sectional view of the control valve assembly of the present invention in the open state; Figure 3 It is an internal cross-sectional view of the control valve assembly of the present invention in a closed state; Figure 4 It is a cross-sectional view of the valve core of the present invention; Figure 5 It is a cross-sectional view of the right valve core seat of the present invention; Figure 6 It is an internal cross-sectional view of the rapid opening and releasing assembly of the present invention; Figure 7 It is an internal cross-sectional view of the rapid closing and releasing assembly of the present invention; Figure 8 It is a left side view of the control valve assembly of the present invention; Fig. 9 For the present invention Figure 8 Sectional view of the middle AA plane; Fig.10 is a cross-sectional view of a slide valve of the present invention; Fig.11 It is a right side view of the control valve assembly of the present invention; As shown in the figure: 1. Control valve seat, 2. Left valve core seat, 3. Right valve core seat, 31. Flow oil channel, 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. Opening top rod, 9. Opening connecting rod, 10. Left pressure plate, 11. Opening connecting nut, 12. Opening connecting rod, 13. Opening support rod, 14. Opening pressure plate, 15. Opening coil, 16. Opening buffer pad, 17. Opening repulsion disk, 18. Opening spacer, 19. Opening guide sleeve, 20. Opening buffer cap, 21. Opening adjustment screw, 22. Opening buffer plate, 23. Crank arm, 24. Crank arm mounting seat, 25 , adjusting bolt, 26, sliding valve push rod, 27, crank arm reset spring, 28, sliding valve seat, 29, sliding valve core, 30, sliding valve reset spring, 31, closing push rod, 32, closing connecting rod, 33, closing connecting rod, 34, closing coil, 35, closing repulsion disk, 36, closing pressure plate, 37, closing buffer pad, 38, closing adjustment screw, 39, closing buffer plate, 40, closing buffer cap, 45, driving rod, 46, driving rod mounting seat, 47, driving rod reset spring, 48, driving rod baffle, 49, sliding valve pull rod, 50, closing connecting rod guide seat, 51, crank arm baffle, 52, opening connecting rod guide seat, T, low pressure oil port, P, high pressure oil port, Z, variable oil port. DETAILED DESCRIPTION

[0020] In order to clearly illustrate the technical features of this solution, this solution is described below through a specific implementation method.

[0021] like Figures 1 to 11 As shown, a dual redundant rapid opening and closing control system for a hydraulic operating mechanism of the present invention comprises a control valve assembly, a rapid opening release assembly and a rapid closing release assembly, wherein the rapid opening release assembly is installed on the left side of the control valve assembly, and the rapid closing release assembly is installed on the right side of the control valve assembly.

[0022] 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.

[0023] like Figure 2 , 3As 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.

[0024] The left valve core seat 2 is provided with a plurality of radial holes for connecting with the low-pressure oil port T, and 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.

[0025] 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.

[0026] 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.

[0027] 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.

[0028] 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.

[0029] 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.

[0030] 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 3 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.

[0031] 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 2 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.

[0032] like Figure 6 As shown, the rapid opening and closing release assembly includes an opening and closing release frame and an opening and closing connecting rod assembly that is slidably connected in the opening and closing release frame along the moving direction of the valve core 4, the opening and closing connecting rod assembly is fixedly connected to a opening and closing repulsion disk 17, and the opening and closing release frame is fixedly connected to a opening and closing coil 15 that is adapted to the opening and closing repulsion disk 17, one end of the opening and closing connecting rod assembly extends into the control valve seat 1 and pushes the valve core 4 to move to the right to realize rapid opening.

[0033] like Figure 6 As shown, specifically, the opening brake release frame includes a plurality of opening brake pressure plates 14 arranged side by side and a plurality of opening brake support rods 13 passing through the opening brake pressure plates 14, the right end of the opening brake support rod 13 is threadedly connected to the left pressure plate 10, and the opening brake support rod 13 is also sleeved with an opening brake coil 15, an opening brake buffer pad 16, the opening brake support rod 13 and a plurality of opening brake spacers, etc., and each component is fastened to the opening brake support rod 13 by nuts.

[0034] The opening connecting rod assembly includes an opening connecting rod 12, an opening connecting rod 9 and an opening top rod 8 arranged in sequence from left to right. The opening connecting rod 9 is threadedly connected to the right end of the opening connecting rod 12 and is prevented from loosening by the opening connecting nut 11. The opening connecting rod 12 is guided by the opening connecting rod guide seat 52.

[0035] The two opening repulsion discs 17 and the opening coils 15 are respectively provided with two. The two opening repulsion discs 17 are respectively a main repulsion disc and an auxiliary repulsion disc, and the two opening coils 15 are respectively a main opening coil and an auxiliary opening coil. The two opening repulsion discs 17 are fixed on the opening connecting rod 12, and an opening spacer 18 is installed between the two opening repulsion discs 17.

[0036] The opening brake buffer pad 16 is arranged on the side of the opening brake repulsion disk 17 away from the opening brake coil 15, and the opening brake buffer pad 16 is preferably made of polyurethane. Both opening brake repulsion disks 17 are located between the opening brake coil 15 and the opening brake buffer pad 16. When the main and auxiliary opening brake coils are energized at any one or both times, the electromagnetic forces generated do not affect each other, that is, when the main and auxiliary opening brake coils are energized, only the main repulsion disk is pushed to move, and the auxiliary repulsion disk is not affected, and vice versa. When any set of opening brake 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.

[0037] The assembly method of the opening repulsion disk 17 and the opening connecting rod 12 can be threaded fit, clearance fit, or one thread and one clearance fit. Preferably, the main and auxiliary repulsion disks and the opening connecting rod 12 are all threaded fit. In order to optimize the movement quality of the moving component and reduce the difficulty of component processing, according to the force form, it is preferred that the thread of the main repulsion disk and the opening connecting rod is larger than the connecting thread of the auxiliary repulsion disk and the opening connecting rod. The assembly direction 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 middle opening connecting rod can be processed and formed by one clamping, avoiding the processing error caused by secondary clamping.

[0038] The left end of the opening connecting rod assembly is fixedly connected with an opening buffer cap 20, and the left end of the opening trip frame is fixedly connected with an opening buffer plate 22 through an opening adjusting screw 21, thereby achieving buffering and limiting the leftward movement of the opening connecting rod assembly and preventing the repulsion disk from hitting the opening coil.

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

[0040] The structure of the quick opening and closing release assembly pushing the control valve in the present application, in which the opening and closing link assembly and the valve core of the control valve are changed from a direct-connected structure to a split structure, 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 opening and closing link 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 gate-opening connecting rod assembly is smaller than the stroke of the valve core 8. During the gate-opening process, after the gate-opening 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 realize gate-opening. Specifically, at the initial stage of the gate-opening repulsion disk 17, a larger repulsive force acts on the gate-opening repulsion disk 17. At the end of the movement of the gate-opening repulsion disk 17, in order to reduce the impact of the valve core on the valve port, the gate-opening 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. Since 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 7 As shown, the rapid closing and releasing assembly includes a closing and releasing frame and a closing connecting rod assembly that is slidably connected in the closing and releasing frame along the moving direction of the valve core 4, the closing connecting rod assembly is fixedly connected to a closing repulsion disk 35, the closing and releasing frame is fixedly connected to a closing coil 34 that is adapted to the closing repulsion disk 35, one end of the closing connecting rod assembly extends into the control valve seat 1 and pushes the valve core 4 to move to the left to achieve rapid closing.

[0043] like Figure 7 As shown, specifically, the closing and tripping frame includes a plurality of closing pressure plates 36 arranged side by side and a plurality of closing support rods passing through the closing pressure plates 36. The left end of the closing support rod is threadedly connected to the right pressure plate 7. The closing support rod is also equipped with a closing coil 34, a closing buffer pad 37, etc., and each component is fastened to the closing support rod by nuts.

[0044] The closing link assembly includes a closing link 33, a closing connecting rod 32 and a closing top rod 31 arranged in sequence from right to left. The closing connecting rod 32 is threadedly connected to the left end of the closing link 33 and is prevented from loosening by a closing connecting nut. The closing link 33 is guided by a closing link guide seat 50.

[0045] The closing buffer pad 37 is arranged on a side of the closing repulsion disk 35 away from the closing coil 34 , and the closing buffer pad 37 is preferably made of polyurethane.

[0046] The right end of the closing link assembly is fixedly connected with a closing buffer cap 40, and the right end of the closing release frame is fixedly connected with a closing buffer plate 39 through a closing adjustment screw 38, thereby achieving buffering and limiting the rightward movement of the closing link assembly and preventing the repulsion disk from hitting the opening coil.

[0047] The end of the closing link assembly is sealed and penetrated into the A1 cavity. Specifically, the closing push rod 31 at the left end of the closing link assembly is sealed and penetrated into the A1 cavity.

[0048] The stroke of the closing link assembly is smaller than the stroke of the valve core 8. During the closing process, after the closing link assembly pushes the valve core 8 to move a certain distance to the left, the pressure difference of the pressure-bearing cross-sectional area S1+S2 relative to S3 drives the valve core 8 to continue to move to the left to achieve closing. Specifically, at the initial stage of the action of the closing repulsion disk 35, a large repulsive force acts on the closing repulsion disk 35. At the end of the movement of the closing repulsion disk 35, in order to reduce the impact of the valve core on the valve port, the closing repulsion disk 35 only drives the valve core 4 to move a large part of the stroke to the left. At this time, the A2 piston 42 is disengaged from the right valve core seat 3, the variable oil port Z is high-pressure oil, and the A1 chamber is connected to the variable oil port Z. Since S1+S2>S3, the combined force on the valve core 4 is to the left, thereby pushing the valve core 4 to move to the left for the remaining small part of the stroke. This structure can 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.

[0049] like Fig. 9 As shown, the control valve seat 1 is provided with a channel, in which a slide valve is installed. Fig.10 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.

[0050] When the opening connecting rod assembly pushes the valve core 4 to move to the right, the sliding valve is turned on. When the closing connecting rod assembly pushes the valve core 4 to move to the left, the sliding valve is turned on. After the opening connecting rod assembly and the closing connecting rod assembly return to their positions, the sliding valve core 29 is pushed to return to the left by the reset spring 30 to close the sliding valve.

[0051] When the operating mechanism is in the opening or 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; when the repulsion release device controls the operating mechanism to quickly open or close the gate, 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.

[0052] In order to realize that when the opening connecting rod assembly pushes the valve core 4 to move to the right, the sliding valve is turned on. Fig. 9 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 gate-opening 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.

[0053] A sliding valve push rod 26 is slidably connected in the control valve seat 1, and the opening connecting rod assembly pushes the crank arm 23 to swing to the right, 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 to the left.

[0054] 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, and a crank arm baffle 51 is fixedly connected to the control valve seat 1 to limit the swing of the crank arm 23 to the right.

[0055] In order to realize that when the closing link assembly pushes the valve core 4 to move to the left, the slide valve is turned on. Fig. 9 As shown, a driving rod 45 is hinged on the right side of the control valve seat 1 through a pin shaft, so that both ends of the driving rod 45 can swing in opposite directions, and both ends of the driving rod 45 are fork-shaped structures. The closing connecting rod 32 is located in the fork-shaped structure at one end, and a sliding valve pull rod 49 is fixed to the sliding valve core 29 of the sliding valve, and the sliding valve pull rod 49 is located in the fork-shaped structure at the other end. A nut located on the right side of the driving rod 45 is threadedly connected to the sliding valve pull rod 49, and the triggering of the sliding valve can be adjusted by adjusting the position of the nut.

[0056] The closing connecting rod assembly pushes one end of the driving rod 45 to swing to the left, and the other end of the driving rod 45 swings to the right to drive the slide valve pull rod 49 to the right, thereby realizing the conduction of the slide valve. The control valve seat 1 is provided with a driving rod reset spring 47 that drives the driving rod 45 to reset. The control valve seat 1 is fixed with a driving rod baffle 48 to limit the swing of the driving rod 45 to the left.

[0057] In order to ensure the stability of the opening time and eliminate the potential hidden dangers that affect the opening time, the method for adjusting the gap between the main and auxiliary repulsion plates and the main and auxiliary opening coils in the rapid opening trip assembly 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.

[0058] (2) Assemble the quick tripping release assembly to the control valve, place the quick tripping 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 tripping coil, and use a wrench to turn the tripping connecting rod to tighten the tool.

[0059] (3) Adjust the position of the trip connection nut 11 on the trip connection rod 9, use a wrench to tighten the thin nut to lock the trip connection rod, tighten the buffer device at the rear end of the quick trip 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 branch coil, as well as the distance between the auxiliary repulsion disk and the auxiliary branch coil. The requirement is 1.5 to 2 mm.

[0060] (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).

[0061] The method for adjusting the gap between the closing coil and the closing repulsion disk is the same as above.

[0062] 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.

[0063] Method of use of the present invention: 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 a rapid opening release assembly.

[0064] When the opening operation is performed through the opening solenoid valve 6, the opening solenoid valve 6 is energized, and the low-pressure oil from the low-pressure oil port T is introduced into the A1 chamber, so that the A1 chamber is filled with low-pressure oil. Since S3>S2, the combined force on 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.

[0065] When the circuit breaker is quickly opened by the rapid opening release assembly, the opening coil 15 is energized by the 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 reverse induced eddy currents on the opening 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 opening 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 initial stage of the action of the opening gate repulsion disk 17, a relatively large repulsive force acts on the opening gate repulsion disk 17. At the final stage of the movement of the opening gate repulsion disk 17, in order to reduce the impact of the valve core on the valve port, the opening gate 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. 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.

[0066] There are two control modes for the closing operation, one is to perform the closing operation through the closing solenoid valve 5, and the other is to achieve fast closing of the circuit breaker through the fast closing release component.

[0067] When the closing operation is performed through the closing solenoid valve 5, 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 to 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.

[0068] When the circuit breaker is quickly closed by the fast closing release assembly, the closing coil 34 is energized by the 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 closing repulsion disk 35. 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 closing repulsion disk 35 moves to the left, thereby driving the closing connecting rod assembly to move to the left, pushing the valve core 4 to move to the left, controlling the valve reversal, and realizing the rapid closing action of the mechanism. At the initial stage of the movement of the closing repulsion disk 35, a relatively large repulsive force acts on the closing repulsion disk 35. At the final stage of the movement of the closing repulsion disk 35, in order to reduce the impact of the valve core on the valve port, the closing repulsion disk 35 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 right valve core seat 3, and the variable oil port Z is high-pressure oil. The A1 chamber is connected to the variable oil port Z. Since S1+S2>S3, the resultant force on the valve core 4 is to the left, thereby pushing the valve core 4 to move to the left for a small part of the remaining stroke. This structure can reduce the mechanical impact of the valve core and the valve core seat sealing part in the control valve, thereby greatly improving the service life of the control valve.

[0069] 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 dual-redundant rapid opening and closing control system for a hydraulic operating mechanism, characterized in that: The invention comprises a control valve assembly, a rapid opening release assembly and a rapid closing release assembly, wherein the control valve assembly comprises a control valve seat (1) and a valve core (4), the rapid opening release assembly comprises an opening release frame and an opening connecting rod assembly, the opening connecting rod assembly pushes the valve core (4) to move rightward to achieve rapid opening, and the rapid closing release assembly comprises a closing release frame and a closing connecting rod assembly, the closing connecting rod assembly pushes the valve core (4) to move leftward to achieve rapid closing.

2. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 1, characterized in that: A switch-off repulsion disk (17) is fixedly connected to the switch-off connecting rod assembly, a switch-off coil (15) adapted to the switch-off repulsion disk (17) is fixedly connected to the switch-off trip frame, and one end of the switch-off connecting rod assembly extends into the control valve seat (1).

3. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 1, characterized in that: A closing repulsion disk (35) is fixedly connected to the closing link assembly, a closing coil (34) adapted to the closing repulsion disk (35) is fixedly connected to the closing release frame, and one end of the closing link assembly extends into the control valve seat (1).

4. A dual-redundant rapid opening and closing 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.

5. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 4, characterized in that: The stroke of the opening connecting rod assembly is smaller than the stroke of the valve core (8). During the opening process, after the opening 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 opening.

6. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 4, characterized in that: The stroke of the closing link assembly is smaller than the stroke of the valve core (8). During the closing process, after the closing link assembly pushes the valve core (8) to move a certain distance, the valve core (8) is driven to continue to move to the left through the pressure difference between the pressure cross-sectional area S1+S2 and S3 to achieve closing.

7. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 4, characterized in that: The control valve seat (1) is provided with a slide valve, the two ends of the slide valve being connected to the variable oil port (Z) and the A1 chamber, the opening connecting rod assembly pushing the valve core (4) to move to the right side drives the slide valve to be turned on, and the closing connecting rod assembly pushing the valve core (4) to move to the left side drives the slide valve to be turned on.

8. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 7, characterized in that: A crank arm (23) is hingedly connected to the control valve seat (1), a slide valve push rod (26) is slidably connected inside the control valve seat (1), the gate-opening connecting rod assembly pushes the crank arm (23) to swing rightward, and the crank arm (23) drives the slide valve core (29) of the slide valve to move rightward through the slide valve push rod (26) to achieve conduction.

9. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 7, characterized in that: A driving rod (45) is hingedly connected to the control valve seat (1), and a sliding valve pull rod (49) is fixedly connected to the sliding valve core (29) of the sliding valve. The closing connecting rod assembly pushes one end of the driving rod (45) to swing leftward, and the other end of the driving rod (45) swings rightward to drive the sliding valve pull rod (49) to the right, thereby achieving conduction of the sliding valve.

10. A dual-redundant rapid opening and closing control system for a hydraulic operating mechanism according to claim 4, 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.

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