Rapid mechanism design method for on-load tap-changer of converter transformer

Abstract

The invention discloses a rapid mechanism design method for a converter transformer on-load tap-changer, and relates to the field of on-load tap-changer design and manufacture, and the method comprises the steps: 1, carrying out the simulation of a rapid mechanism, and building a simulation model of the rapid mechanism; step 2, evaluating residual energy; step 3, performing simulation analysis on the energy storage assembly, setting various parameters, analyzing the energy storage assembly of the quick mechanism, and checking the impact force on the claw clamping part of the energy storage mechanism; if the impact force of the claw clamping part does not meet the design requirement through analysis in the third step, the fourth step is carried out; and 4, optimizing the structure of the energy storage assembly, redesigning the mechanical structure of the rapid mechanism by combining the test condition in the step 3 and the related parameters influencing the residual energy in the step 2, reducing the residual energy, and then repeating the step 3 by using a new energy storage assembly structure. According to the method, factors influencing the collision energy are analyzed in the design process, targeted structure optimization is carried out according to the simulation result, and then the rapid mechanism meeting the use requirement is designed.

Description

Technical Field

[0001] The present application relates to the field of design and manufacture of on-load tap changers, and in particular to a rapid mechanism design method for an on-load tap changer of a converter transformer. Background Art

[0002] A converter transformer (CT) is a power transformer that connects the AC system to the converter bridge, providing AC / DC conversion and electrical isolation. It is a core component of HVDC transmission projects. The on-load tap-changer (OLTC) is a crucial component of the converter transformer. By adjusting the tap position, it changes the transformer's transformation ratio, thereby regulating voltage. It allows voltage regulation while the transformer is under load, which is crucial for compensating for AC voltage fluctuations and stabilizing DC voltage. The OLTC, located within the converter transformer, is the only critical component that moves during transformer switching. Each gear change requires eight mechanical movements to be completed in a timed sequence within 100 milliseconds, placing extremely high demands on timing accuracy, spatial precision, timing stability, and switching reliability.

[0003] The rapid switching of the on-load tap changer is usually achieved by releasing the rack and pinion quick mechanism, which has the characteristics of large initial torque, large rotation angle, good positioning, accurate action and reliable operation. Figure 1 The switching process of the on-load tap changer is as follows: the electric mechanism 1 drives the linkage with the top gear box 2, and the power is transmitted to the external insulating shaft 3 through the top gear box 2. The movement of the insulating shaft 3 is output in two parts through the gear speed change at the bottom of the diverter switch. One part is output upward to the fast mechanism of the diverter switch 4, and the other part is output downward to the grooved wheel mechanism of the tap selector 5.

[0004] Referring to the quick mechanism in the invention patent "A combination on-load tap changer" with reference to announcement number CN106024443B, the quick mechanism adopts a bolt release mechanism, and the quick mechanism includes a base, an eccentric wheel, an upper slide box, a lower slide box, a guide rod, a cam plate, a claw, a reset spring and an energy storage spring; a sector gear is coaxially fixed on the cam plate, and a rack meshing with the sector gear is fixed on the lower slide box; the guide rod is fixed on the base, the upper slide box and the lower slide box are slidably installed on the guide rod, and the energy storage spring is arranged between the upper slide box and the lower slide box.

[0005] The energy storage spring is mounted on the guide rod between the upper and lower slide boxes. When the circular eccentric rotates, it moves the upper slide box along the guide rod, compressing the energy storage spring between them. Because the claws lock the cam plate, the lower slide box remains in its original position. When the release position is reached, the upper slide box's side arm moves the corresponding claw away from the locked cam plate, releasing the lower slide box. The transmission force is transmitted to the cam plate's sleeve shaft via the rack and sector gear, actuating the contact switching mechanism. Simultaneously, the claws, acted upon by the return spring, re-engage with the cam plate, relocking the cam plate and preparing for the next actuation.

[0006] With respect to the above-mentioned related technologies, the quick mechanism of the gun release will generate a large impact force during the release process, which may easily cause damage to the mechanical structure and increase the probability of failure. In order to reduce the failure risk of the on-load tap changer and extend the service life of the on-load tap changer, the applicant has designed a quick mechanism design method for the converter transformer on-load tap changer. During the design process of the quick mechanism, the design reduces the impact of the impact force and reduces the impact of the release of the quick mechanism gun. Summary of the Invention

[0007] In order to reduce the impact of the release of the impact force of the bolt mechanism, the present application provides a rapid mechanism design method for a converter transformer on-load tap changer.

[0008] The rapid mechanism design method for the converter transformer on-load tap changer provided in this application adopts the following technical solutions: The rapid mechanism design method of the converter transformer on-load tap-changer includes: Step 1: Rapid mechanism simulation, establishing a simulation model of the rapid mechanism; Step 2: residual energy evaluation. The expression of residual energy E is as follows: , , , E v : Residual kinetic energy of the rapid mechanism; E k : Residual spring potential energy of the rapid mechanism; m: Mass of the equivalent rapid mechanism sliding box (including the rapid mechanism sliding box and its driven parts); v: Velocity of the rapid mechanism sliding box; k: Equivalent spring stiffness of the main and auxiliary springs; x: Position of the sliding box; Step 3: Simulate and analyze the energy storage component. Set various parameters and analyze the remaining energy of the energy storage component of the fast mechanism based on the expression in step 2. If the impact force analysis in step 3 meets the design requirements, it is recorded as a qualified solution; if the impact force analysis in step 3 does not meet the design requirements, proceed to step 4; Step 4: Optimize the energy storage component structure. Based on the test results of step 3 and the relevant parameters affecting the residual energy in step 2, redesign the mechanical structure of the fast mechanism to reduce the residual energy. Then repeat step 3 with the new energy storage component structure. Step 5: Based on the qualified solution in step 3, adjust the mechanical performance parameters of the energy storage component through simulation analysis and comparison to optimize the design of the mechanical performance parameters.

[0009] By adopting the above technical solution, a simulation analysis is performed on the designed on-load tap-changer quick mechanism. By analyzing the residual energy of the quick mechanism, the relevant factors affecting the impact force are understood. Using simulation software, after simulating the energy storage component structure, the impact force on the claw clamping part is efficiently checked to determine whether it meets the design requirements, which helps to quickly design a quick mechanism that meets the requirements. If the design requirements are not met, the expression of the residual energy E can be used to quickly determine the factors affecting the collision force (residual energy). Combined with the parts with excessive collision force in the simulation analysis, it facilitates targeted structural optimization of the quick mechanism, helps to quickly identify key influencing factors, and optimize the quick mechanism.

[0010] Optionally, in the design process of the rapid mechanism, the main and auxiliary spring stiffnesses have been determined, so the equivalent spring stiffness k is certain; when analyzing the residual energy, the position of the selected slide box is determined, so the spring potential energy E of the rapid mechanism is k is certain; the mass of each component of the rapid mechanism has been determined during design, so the equivalent mass m is also determined; the residual energy E can be reflected by the speed of the sliding box of the rapid mechanism: , k0 and c0 are controllable design parameters, ; .

[0011] By adopting the above technical solution, the relationship is simplified, making it easier to analyze the residual energy of the fast mechanism.

[0012] Optionally, in step four, optimizing the structure of the energy storage assembly includes providing a buffer component, wherein the buffer component includes deceleration elastic members provided on both sides of the movement direction of the sliding box, and the deceleration elastic members are compressed before the sliding box collides.

[0013] By adopting the above technical solution, a buffer component is provided to absorb the impact force of the sliding box, which helps to significantly reduce the residual capacity and reduce the collision force.

[0014] Optionally, the buffer component includes a fixed sleeve fixed to the base, a cylinder fixed in the fixed sleeve, a piston slidably inserted in the cylinder, a piston rod fixed on the piston, a spring baffle fixed to the end of the piston rod away from the piston, and a damping control valve installed at the end of the cylinder away from the piston, and the buffer components are arranged in groups of two at both ends of the sliding direction of the downward sliding box; the deceleration spring sleeve is arranged on the cylinder, and the deceleration spring is abutted between the fixed sleeve and the spring pressure plate.

[0015] By adopting the above technical solution, the combination of spring deceleration and damping deceleration helps to more efficiently eliminate the impact force of the sliding box, helps to reduce the volume of the buffer component, and helps to optimize the overall structural layout of the rapid mechanism.

[0016] Optionally, step five includes analysis and optimization of the main spring stiffness, analysis and optimization of the deceleration spring stiffness, and analysis and optimization of the damping of the damping control valve.

[0017] By adopting the above technical solution, after the structural optimization is completed, the mechanical performance of the main spring, deceleration spring and damping control valve is further optimized to achieve better overall mechanical performance.

[0018] Optionally, step 2 further includes collision force evaluation. The collision force F of the buffer component is expressed as follows: , m h : Equivalent inertia of the buffer component; v1: Velocity of the buffer component before collision; v2: Velocity of the buffer component after collision; Δt: Collision time.

[0019] By adopting the above technical solutions, the system's remaining capacity can be fed back from the perspective of collision force, and analyzed from another perspective, which helps to adapt to various design requirements.

[0020] Optionally, the time required for the collision is extremely short, and the collision time in different collision processes is the same; the buffer component is in a stationary state before the collision, and the speed of the buffer component before the collision is 0m / s 2 The mass of the sliding box is much larger than that of the buffer component. Let the velocity v2 of the buffer component after collision be the velocity v of the sliding box. Then the magnitude of the collision force F is proportional to the velocity of the fast mechanism after collision: , .

[0021] By adopting the above technical solution, the relationship is simplified, making it easier to analyze the collision force of the buffer component.

[0022] Optionally, step four also includes setting a main spring and a secondary spring, the energy storage spring includes a main spring and a secondary spring, the main spring is abutted between the lower sliding box and the upper sliding box, and the secondary spring is slidably set between the lower sliding box and the upper sliding box, the length of the secondary spring is smaller than the length of the main spring and the secondary spring only starts to compress after the main spring is compressed to a certain stroke.

[0023] By adopting this technical solution and combining it with a formula for calculating residual energy, the speed of the sliding box during a collision is positively correlated with the residual energy. This residual energy is primarily provided by the spring. By providing a primary and secondary spring, they jointly exert force during the switching process, ensuring switching speed. Immediately before a collision, the secondary spring expands to its maximum length, no longer exerting force on the sliding box. This reduces the residual energy in the system before a collision occurs. This allows the switching system's angular velocity to be increased to a certain level as quickly as possible while maintaining maximum stability until the end of its travel.

[0024] Optionally, step four also includes optimizing the claw card structure, optimizing the claw card structure to enhance the impact resistance of the claw card; the claw card is rotatably installed on the side of the base close to the sliding box, and the claw card is provided in pair with the movable ends facing each other; a card block is provided on the side wall of the sliding box corresponding to the movable end of the claw card, and the two ends of the card block can respectively abut against the ends of the two claw cards for limiting, and a supporting plate is provided on the side of the claw away from the sliding box, and the supporting plate is fixed on the base; a reset spring is provided between the claw and the abutment plate, and the reset spring presses the claw card toward the sliding box; a roller is provided at the end of the claw card as a shift claw, and when the shift claw abuts against the card block, the corresponding shift claw is located on the movement trajectory of the shift fork of the sliding box.

[0025] By adopting the above technical solution, the structure of the claw is optimized, the strength of the claw is improved, and the ability of the claw to withstand impact is enhanced; the claw that contacts the upper slide box fork uses a roller structure, which can effectively reduce the impact force of the fork on the claw.

[0026] Optionally, in step three, if the impact force is greater than 5000N, the energy storage component is optimized and re-simulated; if the impact force is less than 5000N, the energy storage component is listed as a qualified solution.

[0027] In summary, this application includes at least one of the following beneficial technical effects: 1. The expression of residual energy E can be used to quickly determine the factors affecting the collision force (residual energy). Combined with the locations where the collision force is excessive in simulation analysis, this facilitates targeted structural optimization of the rapid mechanism, helps to quickly identify key influencing factors, and optimizes the structural design of the rapid mechanism. By first optimizing the overall structure of the rapid mechanism and then analyzing and optimizing the mechanical properties of specific components after obtaining the optimal structure, the design optimization efficiency of the rapid mechanism is improved. 2. The buffer component combines spring deceleration with damping deceleration, which can more effectively absorb the impact force of the sliding box with a shorter sliding distance, helping to reduce the volume of the buffer component and optimize the overall structural layout of the rapid mechanism; 3. The energy storage spring adopts a combination of main and auxiliary springs to increase the angular velocity of the switching system to a certain level as quickly as possible while maintaining stability as much as possible before the end of the stroke; 4. By optimizing the structure of the claw, the impact force on the entire claw is reduced and the structural strength of the claw itself is improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 This is a schematic diagram of the overall structure of the on-load tap-changer; Figure 2 This is the structural diagram of energy storage component 1 Figure 1 ; Figure 3 This is the structural diagram of energy storage component 1 Figure 2 ; Figure 4 is the result of dynamic simulation of energy storage component one; Figure 5 This is a schematic diagram of the buffer component principle of the energy storage component 2; Figure 6 is the dynamic simulation result of energy storage component 2; Figure 7 It is a structural diagram of energy storage component three; Figure 8 This is a schematic diagram of the installation structure of the main spring and auxiliary spring in the energy storage component three; Figure 9 is the dynamic simulation result of energy storage component three; Figure 10 is a cross-sectional view of a buffer component in energy storage assembly four; Figure 11 It is a schematic diagram of the overall structure of the energy storage component four; Figure 12 This is the dynamic simulation result of energy storage component four.

[0029] Figure numerals: 1. electric mechanism; 2. top gear box; 3. insulating shaft; 31. limit plate; 4. switching switch; 5. tap selector; 6. base; 61. limit block; 7. upper slide box; 71. shift fork; 8. lower slide box; 81. clamping block; 9. buffer component; 91. cylinder; 92. piston; 93. piston rod; 94. spring baffle; 95. deceleration spring; 96. damping control valve; 961. one-way valve plate; 962. one-way valve spring; 963. one-way valve seat; 97. fixing sleeve; 10. energy storage spring; 101. main spring; 102. auxiliary spring; 103. spring seat; 11. claw; 111. shift claw; 112. limit claw; 12. return spring; 13. guide rod; 14. eccentric wheel drive component. DETAILED DESCRIPTION

[0030] The present application discloses a method for quickly designing a mechanism for a converter transformer on-load tap changer. The method includes: Step 1: Rapid mechanism simulation: Create a mechanical model of the rapid mechanism in AMESim simulation software and analyze the movement of the rapid mechanism through simulation.

[0031] refer to Figure 2 and Figure 3 The cam 11 is provided with a plurality of springs 12 for sliding the upper and lower frames 8, and the springs 13 are provided with a plurality of springs 13 for sliding the upper and lower frames 8. The cam 11 is provided with a plurality of springs 12 for sliding the upper and lower frames 8, and the springs 13 are provided with a plurality of springs 12 for sliding the upper and lower frames 8. When the upper and lower frames 7 are moved to the bottom, the shift fork 71 on the upper and lower frames 7 toggles the latch claw, and the limit of the lower frame 8 disappears. The elastic force of the energy storage spring 10 is instantly released, and the lower frame 8 moves quickly, and the lower frame 8 drives the insulating shaft 3 to rotate quickly to switch. After the lower frame 8 moves to the bottom, the claw 11 on the other side automatically pops out and blocks the other end of the limit plate 31, fixing the position of the lower frame 8.

[0032] When designing the rapid mechanism, considering the large rapid action force of the contacts, if the base 6 supporting the rapid mechanism is too thin and the mechanical rigidity is insufficient, the base 6 will easily deform and installation will be inconvenient. Therefore, the base 6 of the rapid mechanism is designed as an integral cast steel part to ensure the reliability of its structural strength.

[0033] Step 2: Residual energy and collision force assessment.

[0034] Residual energy assessment: At the moment before the sliding box 8 collides with the buffer component 9 on the base 6, the switch core has completed its action. The energy in the system at this time is called residual energy. Therefore, the residual energy of the quick mechanism is mainly composed of the kinetic energy of the quick mechanism and the potential energy of the spring. The expression of residual energy E is as follows: , , , E v : Residual kinetic energy of rapid mechanism; E k : Residual spring potential energy of the quick mechanism; m: the mass of the equivalent quick mechanism sliding box 8 (including the quick mechanism sliding box 8 and its driven parts); v: speed of the sliding box 8 of the fast mechanism; k: equivalent spring stiffness of the main and auxiliary springs 102; x: 8 positions down the slide box.

[0035] In the design process of the quick mechanism, the stiffness of the main and auxiliary springs 102 has been determined, so the equivalent spring stiffness k is certain; when analyzing the residual energy, the position of the selected slide box 8 is also determined, so the spring potential energy E of the quick mechanism is k is constant; therefore, the residual energy of the rapid mechanism is primarily affected by kinetic energy. Since the masses of each component of the rapid mechanism are already determined during design, the equivalent mass m is also determined. Therefore, for a given rapid mechanism, its residual energy can also be reflected by the speed of the rapid mechanism's sliding box 8: , k0 and c0 are controllable parameters calculated based on the design data, , .

[0036] Therefore, the residual energy can be evaluated by measuring the speed of the quick mechanism lowering box 8 through the speed sensor. The greater the speed, the greater the residual energy of the quick mechanism.

[0037] Collision force assessment: In addition to directly studying the system energy, the residual energy of the rapid mechanism can also be analyzed by analyzing the collision process between the sliding box 8 and the buffer component 9 on the base 6. Because the collision force between the sliding box 8 and the buffer component 9 on the base 6 is much greater than the other forces acting on them during the collision, the collision process can be simplified and assumed to be only the collision force. For the buffer component 9, the collision process is: , m h : Equivalent inertia of the buffer component 9; v1: The speed of the buffer component 9 before the collision, which is 0 m / s 2 ; v2: velocity of the buffer component 9 after collision; F: collision force; Δt: collision time.

[0038] Since the time required for collision is extremely short, the collision time can be set to be the same in different collision processes; since the mass of the sliding box 8 is much larger than the buffer component 9, the speed v2 after the collision is the speed v of the sliding box 8. The magnitude of the collision force is proportional to the speed of the fast mechanism before the collision: , .

[0039] Therefore, the residual energy of the quick mechanism can be evaluated by measuring the collision force between the sliding box 8 and the buffer component 9 on the base 6 through the impact force sensor. The greater the collision force, the more residual energy of the quick mechanism before the collision.

[0040] Step 3: Simulation analysis of energy storage components.

[0041] Based on the energy storage component in the fast mechanism designed in step 1, simulation verification is performed, and the energy storage component of the traditional fast mechanism is set as energy storage component 1. Figure 2 and Figure 3 The stiffness of the energy storage spring 10 between the upper sliding box 7 and the lower sliding box 8 is set to 8N / mm, the preload force is 100N, and the stiffness of the laminated spring in the buffer component 9 is set to 300N / mm. The dynamic simulation results of the energy storage component 1 are shown as follows: Figure 4 As shown, it can be seen that the trigger mechanism, i.e., the claw 11, is subjected to a large force (the impact force of the shift fork 71), reaching more than 100,000 N, and the base 6 is subjected to a force of about 75,000 N. According to the design requirements, in order to ensure the service life of the rapid mechanism, the impact force should not exceed 5,000 N. This shows that the structure of the energy storage component 1 does not meet the design requirements.

[0042] If the impact force analyzed in step three meets the design requirements, it is recorded as a qualified solution; if the impact force of the claw 11 analyzed in step three does not meet the design requirements, proceed to step four.

[0043] Step 4: Optimize the energy storage component structure. Based on the test results of step 3 and the relevant parameters affecting the residual energy in step 2, redesign the mechanical structure of the fast mechanism to reduce the residual energy. Then repeat step 3 with the new energy storage component structure.

[0044] The structure of the energy storage component does not meet the design requirements and needs to be improved. After analyzing the above data, the fork 71 and the base 6 are subjected to too much force. It is necessary to add a buffer component 9 for the collision between the sliding box 8 and the fork 71 and the collision between the sliding box 8 and the base 6. Figure 5A deceleration elastic member is added between the side wall of the sliding box 8 and the base 6 to form a second energy storage component. The deceleration elastic member is a spiral deceleration spring 95. The deceleration spring 95 is sleeved on the guide rod 13. Before the sliding box 8 collides, it first hits the deceleration spring 95 to buffer and absorb part of the remaining energy.

[0045] Repeat step 3 to simulate the energy storage component 2. Set the energy storage spring 10 stiffness to 8N / mm, no preload, the deceleration spring 95 stiffness to 100N / mm, and the compression stroke to 20mm. The dynamic simulation results of the energy storage component 2 are as follows: Figure 6 As shown, it can be seen that the forces on the optimized claw 11 and the buffer are greatly reduced, but the force on the claw 11 is still very large, exceeding 5000N, and the energy storage component still needs to be further optimized.

[0046] Repeat step 4 to further optimize the energy storage component. The optimized energy storage component is energy storage component 3. On the one hand, the residual energy and collision force are further reduced. On the other hand, the ability of the claw 11 to withstand impact is enhanced, and the structure of the claw 11 is optimized.

[0047] refer to Figure 7 The claw card 11 of the energy storage component three is rotatably mounted on the side of the base 6 close to the sliding box 8. The rotating shafts of the two claw cards 11 are coaxial and respectively located on both sides of the rotating shaft. The claw card 11 is provided with a shift claw 111 that is shifted by the shift fork 71 of the upper sliding box 7 and a limit claw 112 that limits the position of the sliding box 8; the shift claws 111 of the two claw cards 11 are connected by a return spring 12, and the end of the shift claw 111 is rotatably mounted with a roller. At the same time, at least one roller falls on the movement trajectory of the shift fork 71 of the upper sliding box 7; the two ends of the sliding box 8 are respectively provided with a card block 81 connected to the limit claw 112 of the claw card 11, and the two card blocks 81 are respectively engaged with the limit claws 112 of the two claw cards 11. The claw card 11 is directly linked with the upper sliding box 7 and the lower sliding box 8. The length of the upper claw 111 and the limit claw 112 of the claw card 11 is effectively shortened, which greatly improves the overall strength of the claw; a rotating roller is provided at the end of the claw 111, which can remove part of the impact force of the fork 71 and reduce the collision of the claw card 11 as a whole.

[0048] refer to Figure 8Energy storage assembly three also includes a secondary spring 102, which begins to compress only after the main spring 101 (originally the main spring 101) has been compressed to a certain stroke. This is to ensure that the switching system's angular velocity reaches a certain level as quickly as possible and remains as stable as possible until the end of its stroke. The inner diameter of secondary spring 102 matches the diameter of guide rod 13. Secondary spring 102 is mounted on guide rod 13, which slides over spring seats 103. These seats are located at either end of secondary spring 102, and the main spring 101 is mounted on these seats at both ends. These seats are located within upper and lower slide boxes 7 and 8, which have sliding holes that mate with the slide rails, preventing the spring seats 103 from passing through these holes. The length of secondary spring 102 is shorter than that of main spring 101, ensuring that secondary spring 102 only begins to compress after the main spring 101 has been compressed to a certain stroke.

[0049] Repeat step 3 to simulate the energy storage component 3. Set the stiffness of the main spring 101 to 7.2N / mm, no preload, the stiffness of the auxiliary spring 102 to 3.03N / mm, the preload force to 20N, the stiffness of the deceleration spring 95 to 15N / mm, and the stroke to 30mm. Perform dynamic simulation on the energy storage component 3. The dynamic simulation results of the energy storage component 3 are referenced. Figure 9 The stiffness of main spring 101 is set to 7.2 N / mm with no preload, the stiffness of auxiliary spring 102 is set to 3.03 N / mm with a preload of 20 N, and the stiffness of deceleration spring 95 is set to 15 N / mm with a travel of 30 mm. While meeting the motion requirements of the switching system, the impact force of claw 11 is significantly reduced, reaching a maximum of approximately 4250 N. This meets the basic design requirements and is considered a qualified solution.

[0050] 4250N is close to the test standard. Referring to the above ideas, the energy storage component is further optimized, the energy storage component 4 is designed, and the structure of the buffer component 9 is optimized, such as Figure 10 and Figure 11 As shown, a buffer component 9 is fixed on the base 6, and the buffer components 9 are respectively arranged at both ends of the movement direction of the sliding box 8; the buffer component 9 includes a fixed sleeve 97 fixed to the base 6, a cylinder 91 fixed in the fixed sleeve 97, a piston 92 slidably inserted in the cylinder 91, a piston rod 93 fixed on the piston 92, a spring baffle 94 fixed on the end of the piston rod 93 away from the piston 92, a deceleration spring 95 sleeved on the cylinder 91 and a damping control valve 96 installed at the end of the cylinder 91 away from the piston 92, and the buffer components 9 are respectively arranged at both ends of the sliding direction of the sliding box 8 in groups of two; the deceleration spring 95 is abutted between the fixed sleeve 97 and the spring pressure plate.

[0051] Damping control valve 96 comprises a check valve seat 963, a check valve spring 962, and a check valve disc 961. Check valve disc 961 is provided with a narrow orifice. When piston rod 93 is impacted and moves rightward, the oil in cylinder 91 is squeezed. At this point, the oil and check valve spring 962 act together to press the check valve disc 961 against the check valve seat 963. Oil can only flow to the outside through the orifice in the center of the check valve disc 961, thereby generating a large damping force. This, together with deceleration spring 95, acts as a shock absorber. When piston rod 93 returns to its original position under the action of deceleration spring 95, the oil pressure in cylinder 91 decreases. Since check valve spring 962 has a very low stiffness, external hydraulic oil can easily push open check valve disc 961, allowing for smooth oil replenishment, ensuring that cylinder 91 is always filled with oil, ready for the next impact.

[0052] When the lowering box 8 is near the end of its stroke, the impact buffer member 9 is decelerated, thereby achieving the purpose of reducing the impact force on the base 6 and the claw 11. The damping of the deceleration spring 95 and the damping control valve 96 reduces the impact force of the lowering box 8.

[0053] refer to Figure 11 The claw card 11 of the energy storage component four is rotatably mounted on the base 6, and a blocking block 81 is provided on the side wall of the sliding box 8 corresponding to the movable end of the claw card 11. The two ends of the blocking block 81 can respectively abut against the end of the claw card 11 for limiting the position. A supporting plate is provided on the side of the claw away from the sliding box 8, and the supporting plate is fixed on the base 6. A return spring 12 is provided between the claw and the abutting plate, and a spring groove for installing the return spring 12 is provided on the abutting plate; the return spring 12 presses the claw card 11 toward the sliding box 8 to achieve automatic limiting; a roller is provided at the end of the claw card 11 as a shift claw 111, and when the shift claw 111 abuts against the blocking block 81, the corresponding shift claw 111 is located on the movement trajectory of the shift fork 71 of the sliding box 8.

[0054] The stiffness of the main spring 101 is set to 9N / mm, the preload is 100N, the stiffness of the auxiliary spring 102 is set to 4N / mm, the stiffness of the deceleration spring 95 is set to 20N / mm, and the damping is (1.5N / (mm / s), 0N / (mm / s)). The dynamic simulation results of the energy storage component 4 are as follows: Figure 12 As can be seen from the figure, the force on the claw 11 is about 2200N, the deceleration and buffering impact force is about 1100N, and the impact force on the base 6 is 0N, which meets the dynamic design requirements.

[0055] The process also includes step five, based on the qualified solution from step three, adjusting the mechanical performance parameters of the energy storage components through simulation analysis and comparison to determine the optimal solution. Taking energy storage component four as an example, this includes stiffness analysis and optimization of the main spring 101, the deceleration spring 95, and the damping control valve 96.

[0056] In the first simulation example of the stiffness of the main spring 101, the stiffness of the main spring 101 is set to 7N / mm, the preload force is set to 100N, and there is no deceleration spring 95. The simulation result diagram is obtained. It can be seen from the diagram that the impact force of the base 6 reaches 15000N and the impact force of the claw 11 reaches 10000N.

[0057] In the second simulation example of the stiffness of main spring 101, the stiffness of main spring 101 was set to 9 N / mm, the preload was set to 100 N, and there was no deceleration spring 95. The simulation results show that the impact force of base 6 reached 14,000 N, and the impact force of claw 11 reached 8,500 N. This shows that appropriately increasing the stiffness of main spring 101 can reduce the impact force of claw 11.

[0058] The stiffness coefficient and preload of the main and auxiliary springs 102 affect the actuation time of the quick mechanism, as well as the impact force between the quick mechanism claw 11, the impact force between the lower slide cover and the deceleration spring 95, and the impact force between the deceleration spring 95 and the base 6. Therefore, it is necessary to adjust the stiffness coefficient and preload of the main and auxiliary springs 102 to achieve the purpose of optimal design. From the above two sets of simulation results of the stiffness of the main spring 101, it can be concluded that appropriately increasing the stiffness of the main spring 101 can help reduce the impact force of the claw 11.

[0059] In the first simulation example of the deceleration spring 95 stiffness, the main spring 101 stiffness was set to 9 N / mm, the preload force was set to 100 N, the auxiliary spring 102 stiffness was set to 4 N / mm, the deceleration spring 95 stiffness was set to 15 N / mm, and the claw 11 spring stiffness was set to 5 N / mm, with a preload force of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 7500 N, the impact force of the base 6 is 7500 N, and the impact force of the claw 11 reaches 11000 N.

[0060] In the second simulation example of the deceleration spring 95 stiffness, the main spring 101 stiffness was set to 9 N / mm, the preload force was set to 100 N, the auxiliary spring 102 stiffness was set to 4 N / mm, the deceleration spring 95 stiffness was set to 20 N / mm, and the claw 11 spring stiffness was set to 5 N / mm, with a preload force of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 6000 N, the impact force of the base 6 is 6000 N, and the impact force of the claw 11 reaches 10000 N.

[0061] In the third simulation example of the deceleration spring 95 stiffness, the main spring 101 stiffness was set to 7 N / mm, the preload force was set to 100 N, the auxiliary spring 102 stiffness was set to 3 N / mm, the deceleration spring 95 stiffness was set to 10 N / mm, and the claw 11 spring stiffness was set to 5 N / mm, with a preload force of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 7200 N, the impact force of the base 6 is 7200 N, and the impact force of the claw 11 reaches 10,000 N.

[0062] In the fourth simulation example of the deceleration spring 95 stiffness, the main spring 101 stiffness was set to 7 N / mm, the preload force was set to 100 N, the auxiliary spring 102 stiffness was set to 3 N / mm, the deceleration spring 95 stiffness was set to 20 N / mm, and the claw 11 spring stiffness was set to 5 N / mm, with a preload force of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 7100 N, the impact force of the base 6 is 6000 N, and the impact force of the claw 11 reaches 9100 N.

[0063] The stiffness coefficient of deceleration spring 95 affects the deceleration effect of the lower slide cover, as well as the impact force between the lower slide cover and deceleration spring 95, the impact force between the claw 11, and the impact force between the base 6. Therefore, the stiffness coefficient of deceleration spring 95 needs to be adjusted to achieve the purpose of optimal design. From the above four sets of deceleration spring 95 stiffness simulation results, it can be concluded that appropriately increasing the stiffness of deceleration spring 95 can help reduce the impact force of the buffer, the impact force of the claw 11, and the impact force of the base 6.

[0064] In damping simulation example 1, the stiffness of main spring 101 is set to 9 N / mm, the preload is set to 100 N, the stiffness of auxiliary spring 102 is set to 4 N / mm, the stiffness of deceleration spring 95 is set to 20 N / mm, the damping coefficient is set to 0.5 N*s / mm, and the spring stiffness of claw 11 is set to 5 N / mm, with a preload of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 640 N, the impact force of base 6 is 500 N, and the impact force of claw 11 reaches 7500 N.

[0065] In damping simulation example 2, the stiffness of main spring 101 is set to 9 N / mm, the preload is set to 100 N, the stiffness of auxiliary spring 102 is set to 4 N / mm, the stiffness of deceleration spring 95 is set to 20 N / mm, the damping coefficient is set to 0.8 N*s / mm, and the spring stiffness of claw 11 is set to 5 N / mm, with a preload of 100 N. The simulation results show that the impact force of the lower cover and buffer is 900 N, the impact force of base 6 is 700 N, and the impact force of claw 11 reaches 4750 N.

[0066] In damping simulation example three, the stiffness of main spring 101 is set to 9 N / mm, the preload is set to 100 N, the stiffness of auxiliary spring 102 is set to 4 N / mm, the stiffness of deceleration spring 95 is set to 20 N / mm, the damping coefficient is set to 1.0 N*s / mm, and the spring stiffness of claw 11 is set to 5 N / mm, with a preload of 100 N. The simulation results show that the impact force of the lower cover and buffer is 1000 N, the impact force of base 6 is 800 N, and the impact force of claw 11 reaches 3200 N.

[0067] In damping simulation example 4, the stiffness of main spring 101 is set to 9 N / mm, the preload is set to 100 N, the stiffness of auxiliary spring 102 is set to 4 N / mm, the stiffness of deceleration spring 95 is set to 20 N / mm, the damping coefficient is set to 1.2 N*s / mm, and the spring stiffness of claw 11 is set to 5 N / mm, with a preload of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 1500 N, the impact force of base 6 is 1000 N, and the impact force of claw 11 reaches 2300 N.

[0068] In damping simulation example five, the stiffness of main spring 101 is set to 9 N / mm, the preload is set to 100 N, the stiffness of auxiliary spring 102 is set to 4 N / mm, the stiffness of deceleration spring 95 is set to 20 N / mm, the damping coefficient is set to 1.5 N*s / mm, and the spring stiffness of claw 11 is set to 5 N / mm, with a preload of 100 N. The simulation results show that the impact force of the lower slide cover and buffer is 1300 N, the impact force of base 6 is 1100 N, and the impact force of claw 11 reaches 1600 N.

[0069] The results of the five damping simulation examples above show that increasing the damper's damping coefficient helps reduce the impact force on claw 11, but it also increases the impact force on the buffer and base 6. Therefore, the damping coefficient of an actual damper needs to comprehensively consider the forces acting on various components to achieve the best balance. Based on this analysis, step six is ​​added.

[0070] The above are all preferred embodiments of the present application, and are not intended to limit the scope of protection of the present application. Therefore, any equivalent changes made based on the structure, shape, and principle of the present application should be included in the scope of protection of the present application.

Claims

1. A fast mechanism design method for a converter transformer on-load tap-changer, characterized by: include, Step 1: Rapid mechanism simulation, establishing a simulation model of the rapid mechanism; Step 2: residual energy evaluation. The expression of residual energy E is as follows: ， ， ， E v : Residual kinetic energy of the rapid mechanism; E k : Residual spring potential energy of the quick mechanism; m: the mass of the equivalent quick mechanism sliding box (8) (including the quick mechanism sliding box (8) and the parts driven by it); v: the speed of the quick mechanism sliding box (8); k: the equivalent spring stiffness of the main and auxiliary springs (102); x: the position of the sliding box (8); Step 3: Simulate and analyze the energy storage component. Set various parameters and analyze the remaining energy of the energy storage component of the fast mechanism based on the expression in step 2. If the impact force analysis in step 3 meets the design requirements, it will be recorded as a qualified solution; If the impact force analyzed in step 3 does not meet the design requirements, proceed to step 4; Step 4: Optimize the energy storage component structure. Based on the test results of step 3 and the relevant parameters affecting the residual energy in step 2, redesign the mechanical structure of the fast mechanism to reduce the residual energy. Then repeat step 3 with the new energy storage component structure. Step 5: Based on the qualified solution in step 3, adjust the mechanical performance parameters of the energy storage component through simulation analysis and comparison to optimize the design of the mechanical performance parameters.

2. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 1, characterized in that: During the design of the quick mechanism, the stiffness of the main and auxiliary springs (102) has been determined, so the equivalent spring stiffness k is certain; when analyzing the residual energy, the position of the selected slide box (8) is determined, so the spring potential energy E of the quick mechanism is k is certain; the mass of each component of the rapid mechanism has been determined during the design, so the equivalent mass m is also determined; the residual energy E can be reflected by the speed of the sliding box (8) of the rapid mechanism: , k0 and c0 are controllable design parameters, ; .

3. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 2, characterized in that: Step 4, optimizing the structure of the energy storage component includes setting a buffer component (9), wherein the buffer component (9) includes deceleration elastic members arranged on both sides of the movement direction of the sliding box (8), and the sliding box (8) begins to compress the deceleration elastic members before a collision occurs.

4. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 3 is characterized in that: The buffer component (9) includes a fixed sleeve (97) fixed to the base (6), a cylinder (91) fixed in the fixed sleeve (97), a piston (92) slidably inserted in the cylinder (91), a piston rod (93) fixed on the piston (92), a spring baffle (94) fixed to the end of the piston rod (93) away from the piston (92), and a damping control valve (96) installed at the end of the cylinder (91) away from the piston (92). The buffer components (9) are arranged in pairs at both ends of the sliding direction of the lower slide box (8); the deceleration spring (95) is sleeved on the cylinder (91), and the deceleration spring (95) is arranged between the fixed sleeve (97) and the spring pressure plate.

5. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 4, characterized in that: Step five includes the analysis and optimization of the stiffness of the main spring (101), the analysis and optimization of the stiffness of the deceleration spring (95), and the analysis and optimization of the damping of the damping control valve (96).

6. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 3, characterized in that: Step 2 also includes collision force evaluation. The collision force F of the buffer component (9) is expressed as follows: ， m h : Equivalent inertia of the buffer component (9); v1: Velocity of the buffer component (9) before collision; v2: Velocity of the buffer component (9) after collision; Δt: Collision time.

7. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 6, characterized in that: The time required for the collision is extremely short. It is assumed that the collision time in different collision processes is the same; the buffer component (9) is in a stationary state before the collision, and the speed of the buffer component (9) before the collision is 0m / s 2 The mass of the sliding box (8) is much larger than that of the buffer component (9). Let the velocity v2 of the buffer component (9) after the collision be the velocity v of the sliding box (8). Then the magnitude of the collision force F is proportional to the magnitude of the velocity of the fast mechanism after the collision: , .

8. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 5, characterized in that: Step 4 also includes setting a main spring and a secondary spring (102). The energy storage spring (10) includes a main spring (101) and a secondary spring (102). The main spring (101) is abutted and set between the lower sliding box (8) and the upper sliding box (7). The secondary spring (102) is slidably set between the lower sliding box (8) and the upper sliding box (7). The length of the secondary spring (102) is less than the length of the main spring (101) and the secondary spring (102) begins to compress after the main spring (101) is compressed to a certain stroke.

9. The method for designing a fast mechanism of a converter transformer on-load tap changer according to claim 5, characterized in that: Step 4 also includes optimizing the structure of the claw card (11), optimizing the structure of the claw card (11) and enhancing the impact resistance of the claw card (11); the claw card (11) is rotatably mounted on the side of the base (6) close to the sliding box (8), and the claw card (11) is provided in a pair with the movable ends facing each other; a clamping block (81) is provided on the side wall of the sliding box (8) corresponding to the movable end of the claw card (11), and the two ends of the clamping block (81) can respectively abut against the ends of the two claw cards (11) to limit the position, and the clamping claw A supporting plate is provided on a side away from the sliding box (8), and the supporting plate is fixed on the base (6); a return spring (12) is provided between the claw and the supporting plate, and the return spring (12) presses the claw (11) toward the sliding box (8); a roller is provided at the end of the claw (11) as a shifting claw (111), and when the shifting claw (111) is in contact with the clamping block (81), the corresponding shifting claw (111) is located on the movement track of the shifting fork (71) of the sliding box (8).

10. The method for designing a fast mechanism of a converter transformer on-load tap changer according to any one of claims 3 to 9, characterized in that: In step three, if the impact force is greater than 5000N, the energy storage component is optimized and re-simulated; if the impact force is less than 5000N, the energy storage component is listed as a qualified solution.

Images