Disc spring hydraulic mechanism energy storage cylinder, system and control method

Abstract

The application discloses a disc spring hydraulic mechanism energy storage cylinder, system and control method, wherein the energy storage cylinder comprises a cylinder body, the cylinder body comprises a cavity, a piston, a sealing ring and a high-pressure oil passage; the piston is movably arranged in the cavity; the cavity comprises a working chamber and a low-pressure chamber; one end of the working chamber is connected with the high-pressure oil passage, the other end of the working chamber is connected with the low-pressure chamber, and the diameter of the low-pressure chamber is larger than that of the working chamber; the sealing ring is arranged on the outer periphery of the piston and is used for isolating high-pressure oil flowing into the low-pressure chamber from the high-pressure oil passage when the sealing ring is in the working chamber; the high-pressure oil passage is used for inputting high-pressure oil to drive the piston to move towards the low-pressure chamber or outputting high-pressure oil to drive the piston to move away from the low-pressure chamber; and the low-pressure chamber is used for collecting high-pressure oil flowing out from the sealing ring when the sealing ring is separated from the working chamber. The application realizes the energy storage cylinder to stop storing energy by arranging the low-pressure oil chamber with a larger diameter than the working chamber in the energy storage cylinder and realizing high-pressure oil internal leakage at the sealing ring.

Description

Technical Field

[0001] This invention relates to the field of switchgear technology, and in particular to a disc spring hydraulic mechanism accumulator cylinder, system, and control method. Background Technology

[0002] Disc spring hydraulic mechanisms are widely used in the switchgear industry, and their typical structural feature is the use of disc springs for energy storage. In a disc spring hydraulic mechanism, the accumulator cylinder is an essential component, mainly composed of a cylinder body, piston, and cylinder head. Its working principle is as follows: a high-pressure oil pump injects high-pressure oil through a pipeline into the rodless chamber of the accumulator cylinder, pushing the accumulator piston outward, compressing the combined disc spring, and establishing system pressure. Typically, the disc spring hydraulic mechanism determines whether the preset pressure has been reached by monitoring the compression of the combined disc spring, and then shuts off the energy storage motor via a limit switch.

[0003] Currently, accumulators used in disc spring hydraulic mechanisms have the following main problems: When the energy storage pressure reaches the design pressure, if the energy storage control system fails to cut off the energy storage circuit due to a malfunction (such as a mechanical or electrical fault in the limit switch), the hydraulic system pressure will continue to rise, which may lead to damage to hydraulic system parts. For example, the energy storage piston may push open the cylinder head, causing high-pressure oil leakage, or the combined disc spring may be over-compressed. These factors can cause structural damage and may cause personal injury. Summary of the Invention

[0004] This invention provides a disc spring hydraulic mechanism accumulator cylinder, system, and control method to solve the problem of how to prevent the accumulator cylinder from continuing to store energy when the energy storage control system fails to disconnect the energy storage circuit due to a mechanical or electrical fault in the limit switch, and how to prevent the energy storage piston from continuing to move, causing the cylinder head to be pushed open and resulting in high-pressure oil leakage or excessive compression of the combined disc spring.

[0005] The present invention provides a disc spring hydraulic mechanism accumulator cylinder, comprising: a cylinder body, wherein the cylinder body includes a cavity, a piston, a sealing ring and a high-pressure oil passage;

[0006] The piston is movable within the cavity;

[0007] The cavity includes a working chamber and a low-pressure chamber;

[0008] One end of the working chamber is connected to the high-pressure oil channel, and the other end of the working chamber is connected to the low-pressure chamber. The diameter of the low-pressure chamber is larger than the diameter of the working chamber.

[0009] The sealing ring is disposed on the outer periphery of the piston and is used to prevent high-pressure oil entering from the high-pressure oil channel from flowing into the low-pressure chamber when the sealing ring is in the working chamber;

[0010] The high-pressure oil channel is used to input high-pressure oil to push the piston toward the direction of the low-pressure chamber, or to output high-pressure oil to make the piston move away from the low-pressure chamber;

[0011] The low-pressure chamber is used to collect the high-pressure oil that flows out from the sealing ring when the sealing ring is removed from the working chamber.

[0012] Furthermore, the cavity also includes a transition cavity, which is disposed between the working cavity and the low-pressure cavity. The diameter of the transition cavity gradually increases, with the smallest diameter end of the transition cavity connected to the working cavity and the largest diameter end of the transition cavity connected to the low-pressure cavity.

[0013] Furthermore, the height of the transition cavity is greater than the height of the sealing ring.

[0014] Furthermore, the transition cavity is frustum-shaped.

[0015] Furthermore, the angle between the generatrix of the transition cavity and the axis of the transition cavity is greater than zero and less than or equal to 30°.

[0016] Furthermore, the diameter of the low-pressure chamber is greater than a preset value, which is the diameter of the chamber when the entry speed of the high-pressure oil in the high-pressure oil channel is equal to the outflow speed of the high-pressure oil at the sealing ring.

[0017] This invention provides an energy storage system for a disc spring hydraulic mechanism, comprising the energy storage cylinder, connecting rod, combined disc spring, and control components;

[0018] The piston of the energy storage cylinder is connected to the combined disc spring via the connecting rod. The middle part of the connecting rod passes through the bottom of the cylinder body. The connecting rod is used to realize the movement of the piston to drive the combined disc spring to extend and retract synchronously.

[0019] The control components include a motor, an oil pump, a first limit switch, and a second limit switch.

[0020] The oil pump is connected to the high-pressure oil channel, and the motor is connected to the oil pump. The motor is used to drive the oil pump to rotate and draw in and generate high-pressure oil.

[0021] Both the first limit switch and the second limit switch are connected to the combined disc spring;

[0022] The motor, the first limit switch, and the second limit switch are arranged in a series circuit, and both the first limit switch and the second limit switch are normally closed switches.

[0023] The first limit switch is used to cut off the series circuit and stop the motor when the combined disc spring reaches the first compression amount;

[0024] The second limit switch is used to cut off the series circuit when the combined disc spring reaches the second compression amount, so that the motor stops running. The second compression amount is less than the first compression amount.

[0025] This invention provides a control method for an energy storage system based on the disc spring hydraulic mechanism, comprising the following steps:

[0026] When the combined disc spring reaches the first compression amount, the first limit switch is disconnected, cutting off the series circuit, causing the motor to stop running, stopping the input of high-pressure oil from the high-pressure oil channel, thereby stopping the piston from moving and the combined disc spring from compressing.

[0027] When the combined disc spring reaches the second compression level, the series circuit is cut off, causing the motor to stop running and stopping the input of high-pressure oil from the high-pressure oil channel, thereby stopping the piston from moving and the combined disc spring from compressing.

[0028] Furthermore, the method also includes the following steps: when the combined disc spring reaches the third compression amount, the sealing ring on the piston disengages from the working chamber and enters the transition chamber, the gap between the piston and the transition chamber gradually increases, the sealing ring gradually rebounds, and high-pressure oil flows out from the sealing ring, passes through the transition chamber, and enters the low-pressure chamber, and the third compression amount is greater than the second compression amount.

[0029] When the inflow velocity of high-pressure oil from the high-pressure oil channel is equal to the outflow velocity of high-pressure oil from the sealing ring, the piston stops moving toward the low-pressure chamber and the combined disc spring stops compressing.

[0030] Furthermore, the method includes the following steps: when the sealing ring disengages from the working chamber and remains in the transition chamber, the motor stops operating, and some high-pressure oil is released from the high-pressure oil channel to reduce the oil pressure in the chamber. The elastic potential energy of the combined disc spring is greater than the oil pressure in the chamber, causing the piston to move away from the low-pressure chamber. The sealing ring then moves with the piston from the transition chamber into the working chamber to restore the sealing function.

[0031] As can be seen from the above technical solutions, the present invention has the following advantages: The present invention provides a dual protection mechanism to address the problem of over-energy storage in disc spring hydraulic mechanisms. On the one hand, the present invention provides an energy storage system for disc spring hydraulic mechanisms. By adding a second limit switch in the series circuit, when the first limit switch fails, the second limit switch cuts off the series circuit, causing the motor to stop running, thus stopping the energy storage cylinder from storing energy and preventing the piston from moving further, thereby achieving the first layer of protection. On the other hand, the present invention provides an energy accumulator cylinder for a disc spring hydraulic mechanism. When both the first and second limit switches fail, a low-pressure oil chamber with a diameter larger than the working chamber is provided in the energy accumulator cylinder. When the sealing ring moves from the working chamber into the low-pressure chamber with the piston, the gap between the piston and the inner wall of the low-pressure chamber is greater than the gap between the piston and the working chamber. This makes it impossible for the sealing ring to isolate the high-pressure oil, resulting in internal leakage of high-pressure oil. That is, high-pressure oil flows into the low-pressure chamber from the gap between the piston and the inner wall of the low-pressure chamber, and is further discharged through the low-pressure oil channel. This reduces the pressure difference between the top and bottom of the piston, causing the energy accumulator cylinder to stop storing energy. The piston does not have enough power to continue moving, avoiding the problem of high-pressure oil leakage or over-compression of the combined disc spring caused by the cylinder head being pushed open. This provides a second layer of protection. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0033] Figure 1 This is a schematic diagram of a disc spring hydraulic mechanism provided in an embodiment of the present invention;

[0034] Figure 2 This is a schematic diagram of the control component structure in an energy storage system of a disc spring hydraulic mechanism provided in an embodiment of the present invention;

[0035] Figure 3 This is a schematic diagram showing the relationship between the limit switch and the compression amount of the combined disc spring in an energy storage system of a disc spring hydraulic mechanism provided in an embodiment of the present invention;

[0036] Figure 4 This is a schematic diagram showing the state of the working chamber where the sealing ring is about to fall off in a disc spring hydraulic mechanism provided in an embodiment of the present invention;

[0037] Reference numerals: 1. Cylinder block; 2. Piston; 3. Sealing ring; 4. Cylinder head; 5. Combined disc spring; 6. High-pressure oil passage; 7. Low-pressure oil passage; 8. Connecting rod; 9. Working chamber; 10. Transition chamber; 11. Low-pressure chamber; S1. First limit switch; S2. Second limit switch; L1. First compression amount; L2. Second compression amount; L3. Third compression amount; d1. Working chamber diameter; d2. Low-pressure chamber diameter; θ. Angle between the generatrix of the transition chamber and the axis of the transition chamber. Detailed Implementation

[0038] To make the objectives, features, and advantages of this invention more apparent and understandable, the technical solutions of the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the embodiments described below are only some embodiments of this invention, and not all embodiments. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0039] The terms “first,” “second,” “third,” “fourth,” etc. (if present) in the specification and drawings of this invention are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that embodiments of the present application described herein can be implemented, for example, in orders other than those illustrated or described herein. Furthermore, the terms “comprising” and “having,” and any variations thereof, are intended to cover a non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0040] Please see Figure 1 , Figure 1 An energy storage cylinder for a disc spring hydraulic mechanism provided in an embodiment of the present invention includes: a cylinder body 1, wherein the cylinder body 1 includes a cavity, a piston 2, a sealing ring 3, and a high-pressure oil channel 6;

[0041] The piston 2 is movably disposed within the cavity;

[0042] The cavity includes a working chamber 9 and a low-pressure chamber 11;

[0043] One end of the working chamber 9 is connected to the high-pressure oil channel 6, and the other end of the working chamber 9 is connected to the low-pressure chamber 11.

[0044] The diameter of the low-pressure chamber 11 is larger than the diameter of the working chamber 9;

[0045] The sealing ring 3 is disposed in the middle of the outer periphery of the piston 2, and is used to prevent high-pressure oil entering from the high-pressure oil channel 6 from flowing into the low-pressure chamber 11 when the sealing ring 3 is in the working chamber 9;

[0046] The high-pressure oil channel 6 is used to input high-pressure oil to push the piston 2 toward the direction closer to the low-pressure chamber 11, or to output high-pressure oil to make the piston 2 move away from the low-pressure chamber 11.

[0047] The low-pressure chamber 11 is used to collect the high-pressure oil that flows out from the sealing ring 3 when the sealing ring is removed from the working chamber 9.

[0048] like Figure 1 As shown, the diameter of the working chamber 9 is d1, and the diameter of the low-pressure chamber 11 is d2, where d1 < d2.

[0049] Understandably, in practice, high-pressure oil is continuously input from the high-pressure oil channel 6 into the working chamber 9 located above the piston 2. The sealing ring 3, positioned between the piston 2 and the working chamber 9, prevents high-pressure oil from flowing into the lower part of the piston 2, thus causing the high-pressure oil to push the piston 2 towards the low-pressure chamber 11. When the sealing ring 3 moves from the working chamber 9 into the low-pressure chamber 11 along with the piston 2, because the diameter of the working chamber 9 is larger than the diameter of the low-pressure chamber 11, the gap between the piston 2 and the inner wall of the low-pressure chamber 11 is larger than the gap between the piston 2 and the working chamber 9. This prevents the sealing ring 3 from isolating the high-pressure oil, resulting in internal leakage of high-pressure oil. That is, high-pressure oil flows into the low-pressure chamber 11 from the sealing ring 3, reducing the pressure difference between the upper and lower parts of the piston 2. This causes the accumulator to stop storing energy, and the piston 2 lacks sufficient power to continue moving. Therefore, this embodiment can prevent the accumulator from continuing to store energy through internal leakage of high-pressure oil, thus preventing the energy-storing piston 2 from having sufficient power to continue moving.

[0050] In a more specific embodiment, an annular groove is provided in the middle of the outer periphery of the piston 2, and the sealing ring 3 is partially embedded in the annular groove.

[0051] In a more specific embodiment, a transition cavity 10 is further provided between the working cavity 9 and the low-pressure cavity 11. The diameter of the transition cavity 10 gradually increases. The smallest diameter end of the transition cavity 10 is connected to the working cavity 9, and the largest diameter end of the transition cavity 10 is connected to the low-pressure cavity 11.

[0052] Understandably, in practice, the sealing ring 3 directly enters the large-diameter low-pressure chamber 11 from the small-diameter working chamber 9. The sealing ring 3 instantly expands and rebounds. The high-flow-rate high-pressure oil impacts the expanded and rebounded sealing ring 3. During this impact, stress concentration may occur at the contact points between the sealing ring 3 and the surrounding structure, and the edge portions may bear higher pressure, making these areas more susceptible to damage. This embodiment addresses this by providing a transition chamber 10 between the working chamber 9 and the low-pressure chamber 11. The diameter of the transition chamber 10 gradually increases, which controls the expansion and rebound speed of the sealing ring 3, thereby controlling the outflow rate and velocity of the high-pressure oil from the sealing ring 3. This reduces the impact of the high-pressure oil on the sealing ring 3, preventing damage and ensuring the recoverability of the sealing ring 3.

[0053] In a more specific embodiment, the inner wall of the transition cavity 10 is provided with multiple steps with gradually increasing diameters, which causes the sealing ring 3 to expand and rebound step by step.

[0054] In some more specific embodiments, the inner wall of the transition cavity 10 is an inclined surface with a gradually increasing diameter, that is, the transition cavity is a frustum shape. It can be understood that, in specific implementation, the transition cavity 10 must not only meet the requirements of controlling the expansion and rebound speed of the sealing ring 3, but also meet the requirements of the sealing ring 3 being able to be recompressed back into the working cavity 9 after it leaves the working cavity 9. In this embodiment, the inner wall of the transition cavity 10 is an inclined surface, which can reduce the resistance of the inner wall of the transition cavity 10 during the process of the sealing ring 3 being recompressed back into the working cavity 9.

[0055] In a more specific embodiment, the slope is a smooth slope.

[0056] In a more specific embodiment, the height of the transition cavity 10 is greater than the height of the sealing ring 3. It is understood that, in practical implementation, if the height of the transition cavity 10 is less than the height of the sealing ring 3, the difference in expansion and rebound between the upper and lower parts of the sealing ring 3 will be significant. Due to the uneven rebound of the sealing ring 3, stress concentration is likely to occur, leading to material fatigue, shape changes, and other problems. The aging rate of the sealing ring 3 will accelerate. Furthermore, the upper part of the sealing ring 3 is subjected to oil pressure, further exacerbating the stress concentration caused by the difference in rebound between the upper and lower parts. This stress concentration may cause microscopic damage to the internal material of the sealing ring 3, such as the formation of microcracks. In this embodiment, the height of the transition cavity 10 is greater than the height of the sealing ring 3, which helps to reduce the difference in expansion and rebound between the upper and lower parts of the sealing ring 3, ensuring a more uniform distribution of contact pressure and preventing damage to the sealing ring 3 structure.

[0057] In a more specific embodiment, the angle between the generatrix of the transition cavity 10 and the axis of the transition cavity 10 is greater than zero and less than or equal to 30°. As shown in the figure, the angle between the generatrix of the transition cavity 10 and the axis of the transition cavity 10 is θ. It is understood that in specific implementations, an excessively large angle may lead to insufficient generatrix and axis lengths. When the sealing ring 3 is compressed from the transition cavity 10 back to the working cavity 9, problems such as uneven compression and misalignment of the sealing ring 3 may easily occur. When the sealing ring 3 enters the inner hole between the working cavity 9 and the transition cavity 10, there is a risk of the sealing ring being cut and damaged. In this embodiment, the angle is less than 30°, which ensures that the generatrix and axis lengths of the transition cavity 10 are sufficiently long. When the sealing ring 3 is compressed from the transition cavity 10 back to the working cavity 9, problems such as uneven compression and misalignment of the sealing ring 3 are less likely to occur, while also avoiding the risk of the sealing ring being cut and damaged.

[0058] In a more specific embodiment, the angle between the generatrix of the transition cavity 10 and the axis of the transition cavity 10 is greater than or equal to 15°. It is understood that, in practical implementation, if the angle is too small, the generatrix and axis of the transition cavity 10 will be too long, which will require increasing the height of the cylinder body 1, which is not conducive to the compactness of the cylinder body 1 structure.

[0059] In a more specific embodiment, the angle between the generatrix of the transition cavity 10 and the axis of the transition cavity 10 is θ, 15°≤θ≤30°, so that the inner wall of the transition cavity 10 can effectively guide the sealing ring 3 to detach from the working cavity 9, while avoiding the sealing ring 3 from being damaged by high-pressure oil impact due to excessive expansion.

[0060] In a more specific embodiment, a cylinder head 4 is provided at the bottom of the transition cavity 10.

[0061] In a more specific embodiment, the cylinder body 1 further includes a low-pressure oil channel 7, which is connected to the low-pressure chamber 11. The low-pressure oil channel 7 is used to output the high-pressure oil collected by the low-pressure chamber 11. It is understood that, in specific implementations, the space inside the cylinder body 1 is limited. To ensure that the low-pressure chamber 11 can fully collect the high-pressure oil leaking from the sealing ring 3 before the accumulator stops storing energy, this embodiment provides a low-pressure oil channel 7 connected to the low-pressure chamber 11.

[0062] In a more specific embodiment, a low-pressure oil passage is disposed on one side of the low-pressure chamber 11.

[0063] In a more specific embodiment, the distance from the sealing ring 3 to the bottom of the piston 2 is less than the height of the low-pressure chamber 11.

[0064] In a more specific embodiment, the diameter of the low-pressure chamber 11 is greater than a preset value, which is the diameter of the chamber when the entry speed of high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed of high-pressure oil from the sealing ring 3.

[0065] It should be noted that when the entry speed of high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed of high-pressure oil from the sealing ring 3, the accumulator stops accumulating energy, the piston 2 stops moving towards the low-pressure chamber 11, and the combined disc spring 5 stops compressing.

[0066] It can be understood that, in specific implementation, when the diameter of the low-pressure chamber 11 is equal to a preset value, the gap between the low-pressure chamber 11 and the piston 2 is just enough to satisfy the oil outlet speed at the sealing ring 3 being equal to the entry speed of the high-pressure oil from the high-pressure oil channel 6. In this embodiment, the diameter of the low-pressure chamber 11 is larger than the preset value, which has the following advantages:

[0067] On the one hand, the low-pressure chamber 11 is greater than the preset value. Even if the sealing ring 3 enters the low-pressure chamber 11, it can at least ensure that the sealing ring 3 cannot seal and the high-pressure oil leaks internally. This solves the problem of how to prevent the energy storage cylinder from continuing to store energy and prevent the energy storage piston 2 from continuing to move, causing the cylinder head 4 to be pushed open and resulting in high-pressure oil leakage or excessive compression of the combined disc spring 5 when the energy storage control system fails to cut off the energy storage circuit due to mechanical or electrical faults in the limit switch.

[0068] On the other hand, when the low-pressure chamber 11 is greater than the preset value, that is, when the diameter of the transition chamber 10 can reach the preset value, it can ensure that the sealing ring 3 stops storing energy in the transition chamber 10, the piston 2 stops moving towards the low-pressure chamber 11, and the combined disc spring 5 stops compressing. The sealing ring 3 returns from the transition chamber 10 to the working chamber 9. Compared with the sealing ring 3 returning from the low-pressure chamber 11 to the working chamber 9, the deformation change of the sealing ring 3 is smaller, which is beneficial to protect the sealing ring 3.

[0069] On the other hand, since the low-pressure oil channel 7 is located on one side of the low-pressure chamber 11, the flow direction of the high-pressure oil in the low-pressure chamber 11 changes. When the sealing ring 3 falls into the low-pressure chamber 11, it is easy to cause uneven force on the sealing ring 3, which can easily lead to misalignment and damage to the sealing ring 3. This embodiment can ensure that the sealing ring 3 stops storing energy in the transition chamber 10, thus avoiding the recurrence of this problem.

[0070] In a more specific embodiment, the difference between the diameter of the low-pressure chamber 11 and the diameter of the working chamber 9 is greater than 2 mm.

[0071] Therefore, the disc spring hydraulic mechanism accumulator cylinder provided in this embodiment has a smooth sealing structure failure and recovery function, which can ensure that the internal structure of the hydraulic system is not damaged after a failure, improve the safety of the debugging and operation process, and reduce maintenance costs.

[0072] This embodiment provides an energy storage system for a disc spring hydraulic mechanism, including the energy storage cylinder, combined disc spring 5, and control components described in the above embodiment;

[0073] The piston 2 in the energy storage cylinder is connected to the combined disc spring 5 through the connecting rod 8. The middle part of the connecting rod 8 passes through the bottom of the low-pressure chamber 11. The connecting rod 8 is used to realize that the movement of the piston 2 and the extension and retraction of the combined disc spring 5 can be synchronized.

[0074] The control components include a motor, an oil pump, a first limit switch, and a second limit switch.

[0075] The oil pump is connected to the high-pressure oil channel 6, and the motor is connected to the oil pump. The motor is used to drive the oil pump to rotate and draw in and generate high-pressure oil.

[0076] The first limit switch S1 and the second limit switch S2 are both connected to the combined disc spring 5;

[0077] The motor, the first limit switch S1, and the second limit switch S2 are arranged in a series circuit, and both the first limit switch S1 and the second limit switch S2 are normally closed switches.

[0078] The first limit switch S1 is used to cut off the series circuit and stop the motor when the combined disc spring 5 reaches the first compression amount L1.

[0079] The second limit switch S2 is used to cut off the series circuit and stop the motor when the combined disc spring 5 reaches the second compression amount L2. The second compression amount L2 is less than the first compression amount L1.

[0080] In a more specific embodiment, the second limit switch S2 is connected to an alarm device. When the combined disc spring 5 reaches the second compression amount L2, triggering the second limit switch S2 also triggers the alarm device, notifying personnel to handle the fault promptly. Even if the second limit switch S2 fails, the alarm device can still be triggered.

[0081] It is understandable that the existing disc spring hydraulic mechanism energy storage control system mainly consists of a motor oil pump system, a first limit switch S1, other secondary control components and a power supply. The first limit switch S1 is a normally closed micro switch connected in series in the control circuit of the energy storage motor. When the combined disc spring 5 is compressed to the first compression amount L1, the first limit switch S1 is opened, controlling the energy storage motor to stop rotating.

[0082] In this embodiment, regarding the method of preventing over-storage, a second limit switch S2 for high oil pressure warning is added. When the first limit switch S1 fails, and the combined disc spring 5 is compressed to the first compression amount L1 and then continues to be compressed to the second compression amount L2, the second limit switch S2 will cut off the motor circuit and issue an alarm. If the accumulator cylinder of the disc spring hydraulic mechanism has not stopped storing energy at this time, it will rely on the accumulator cylinder structure for protection.

[0083] like Figure 3 As shown, when the combined disc spring 5 is compressed to the third compression amount L3 and is still storing energy, the energy storage piston 2 continues to move downwards. The sealing ring 3 will enter the inclined plane and expand outwards, weakening the sealing effect. This weakening accelerates as the energy storage piston 2 continues to move downwards. During this process, internal leakage occurs and balances with the pressure replenishment process at a certain moment. That is, when the entry speed of high-pressure oil from the high-pressure oil channel 6 equals the outflow speed at the sealing ring 3, the energy storage piston 22 is prevented from continuing to move downwards. In this embodiment, the expansion speed of the sealing ring 3 is controllable, protecting it from damage by excessive hydraulic oil flow. It is also recoverable, eliminating the need for disassembly and repair of the accumulator cylinder and hydraulic system after a failure.

[0084] Compared with existing technologies, the energy storage system of the disc spring hydraulic mechanism in this embodiment provides dual protection. Firstly, it provides a second limit switch S2 for high oil pressure warning, helping maintenance personnel to detect faults promptly. Secondly, the energy storage cylinder structure ensures that over-stored energy will not cause safety accidents, and the recoverable sealing ring 3 in this structure removes the hydraulic system from the troubleshooting and recovery process, greatly improving maintenance efficiency. This embodiment maximizes the energy storage safety of the disc spring hydraulic mechanism and reduces the safety risks caused by mechanical or electrical failures of the first limit switch S1.

[0085] Based on the above-described energy storage system, this embodiment provides a control method, including:

[0086] The method to achieve the first layer of protection is as follows:

[0087] When the combined disc spring 5 reaches the first compression amount L1, the first limit switch S1 is opened, cutting off the series circuit, stopping the motor, stopping the input of high-pressure oil from the high-pressure oil channel 6, so that the piston 2 stops moving and the combined disc spring 5 stops compressing.

[0088] When the combined disc spring 5 reaches the second compression amount L2, the series circuit is cut off, the motor stops running, and the high-pressure oil is stopped from entering from the high-pressure oil channel 6, so that the piston 2 stops moving and the combined disc spring 5 stops compressing.

[0089] In a more specific embodiment, a method for implementing the second layer of protection is provided as follows:

[0090] When the combined disc spring 5 reaches the third compression amount L3, the sealing ring 3 on the piston 2 disengages from the working chamber 9 and enters the transition chamber 10. The gap between the piston 2 and the transition chamber 10 gradually increases, the sealing ring 3 gradually rebounds, and the high-pressure oil enters the low-pressure chamber 11 through the transition chamber 10 and flows out from the low-pressure oil channel 7. The third compression amount L3 is greater than the second compression amount L2.

[0091] When the inflow velocity of high-pressure oil from the high-pressure oil channel 6 is equal to the outflow velocity at the sealing ring 3, the piston 2 stops moving toward the low-pressure chamber 11 and the combined disc spring 5 stops compressing.

[0092] It should be noted that in actual application, when the entry speed of high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed at the sealing ring 3, the force exerted by the high-pressure oil on the piston 2 is equal to the force exerted by the elastic potential energy of the combined disc spring 5 on the piston 2. When the piston 2 is in force balance, the piston 2 stops moving towards the low-pressure chamber 11 and the combined disc spring 5 stops compressing.

[0093] It is understood that this embodiment provides a dual protection control method for preventing over-energy storage in the disc spring hydraulic mechanism. This method increases the protection against over-energy storage in the disc spring hydraulic mechanism and provides early warning of potential risks, thereby enhancing the system's safety.

[0094] In a more specific embodiment, a method for restoring the seal is provided as follows:

[0095] When the sealing ring 3 disengages from the working chamber 9 and enters the transition chamber 10, the piston 2 stops moving. The motor is then manually stopped, and some high-pressure oil is released from the high-pressure oil channel 6 to reduce the oil pressure in the chamber. The elastic potential energy of the combined disc spring 5 is greater than the oil pressure in the chamber, causing the piston 2 to move away from the low-pressure chamber 11. The sealing ring 3 then enters the working chamber 9 from the transition chamber 10 to restore the sealing function.

[0096] It is understood that this embodiment sets a transition cavity 10 between the working chamber 9 and the low-pressure chamber 11, and specifically limits the height of the transition cavity 10, the slope angle, and the diameter of the low-pressure chamber 11. On this basis, the structural integrity and recoverability of the sealing ring 3 can be ensured. Therefore, the sealing ring 3 in this embodiment can restore the sealing function as the piston 2 returns to the working chamber 9.

[0097] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An energy storage system for a disc spring hydraulic mechanism, characterized in that, It includes an energy storage cylinder, a connecting rod (8), a combined disc spring (5), and a control assembly; it includes a cylinder body (1), which includes a cavity, a piston (2), a sealing ring (3), and a high-pressure oil passage (6); The piston (2) is movably disposed within the cavity; The cavity includes a working chamber (9) and a low-pressure chamber (11); One end of the working chamber (9) is connected to the high-pressure oil channel (6), and the other end of the working chamber (9) is connected to the low-pressure chamber (11). The diameter of the low-pressure chamber (11) is larger than the diameter of the working chamber (9). The sealing ring (3) is disposed on the outer periphery of the piston (2) and is used to prevent high-pressure oil entering from the high-pressure oil channel (6) from flowing into the low-pressure chamber (11) when the sealing ring (3) is in the working chamber (9); The high-pressure oil channel (6) is used to input high-pressure oil to push the piston (2) to move closer to the low-pressure chamber (11), or to output high-pressure oil to make the piston (2) move away from the low-pressure chamber (11); The low-pressure chamber (11) is used to collect the high-pressure oil that flows out from the sealing ring (3) when the sealing ring (3) is removed from the working chamber (9); The piston (2) of the energy storage cylinder is connected to the combined disc spring (5) through the connecting rod (8). The middle part of the connecting rod (8) passes through the bottom of the cylinder body (1). The connecting rod (8) is used to realize the movement of the piston (2) to drive the combined disc spring (5) to extend and retract synchronously. The control components include a motor, an oil pump, a first limit switch, and a second limit switch; The oil pump is connected to the high-pressure oil channel (6), and the motor is connected to the oil pump. The motor is used to drive the oil pump to rotate and draw in and generate high-pressure oil. Both the first limit switch and the second limit switch are connected to the combined disc spring (5); The motor, the first limit switch, and the second limit switch are arranged in a series circuit, and both the first limit switch and the second limit switch are normally closed switches. The first limit switch is used to cut off the series circuit and stop the motor when the combined disc spring (5) reaches the first compression amount; The second limit switch is used to cut off the series circuit when the combined disc spring (5) reaches the second compression amount, so that the motor stops running. The second compression amount is less than the first compression amount.

2. The energy storage system of the disc spring hydraulic mechanism according to claim 1, characterized in that, The cavity also includes a transition cavity (10), which is disposed between the working cavity (9) and the low-pressure cavity (11). The diameter of the transition cavity (10) gradually increases. The smallest diameter end of the transition cavity (10) is connected to the working cavity (9), and the largest diameter end of the transition cavity (10) is connected to the low-pressure cavity (11).

3. The energy storage system of the disc spring hydraulic mechanism according to claim 2, characterized in that, The height of the transition cavity (10) is greater than the height of the sealing ring (3).

4. The energy storage system of the disc spring hydraulic mechanism according to claim 2, characterized in that, The transition cavity (10) is frustum-shaped.

5. The energy storage system of the disc spring hydraulic mechanism according to claim 4, characterized in that, The angle between the generatrix of the transition cavity (10) and the axis of the transition cavity (10) is greater than zero and less than or equal to 30°.

6. The energy storage system of a disc spring hydraulic mechanism according to claim 1 or 2, characterized in that, The diameter of the low-pressure chamber (11) is greater than a preset value, which is the diameter of the chamber when the entry speed of the high-pressure oil in the high-pressure oil channel (6) is equal to the outflow speed of the high-pressure oil at the sealing ring (3).

7. A control method for the energy storage system according to claim 1, characterized in that, Includes the following steps: When the combined disc spring (5) reaches the first compression amount, the first limit switch is disconnected, the series circuit is cut off, the motor stops running, and the high-pressure oil is stopped from being input from the high-pressure oil channel (6), so that the piston (2) stops moving and the combined disc spring (5) stops compressing. When the combined disc spring (5) reaches the second compression amount, the series circuit is cut off, the motor stops running, and the high-pressure oil is stopped from being input from the high-pressure oil channel (6), so that the piston (2) stops moving and the combined disc spring (5) stops compressing.

8. The control method according to claim 7, characterized in that, It also includes the following steps: When the combined disc spring (5) reaches the third compression amount, the sealing ring (3) on the piston (2) disengages from the working chamber (9) and enters the transition chamber (10). The gap between the piston (2) and the transition chamber (10) gradually increases, the sealing ring (3) gradually rebounds, and high-pressure oil flows out from the sealing ring (3), passes through the transition chamber (10), and enters the low-pressure chamber (11). The third compression amount is greater than the second compression amount. When the speed at which high-pressure oil enters from the high-pressure oil channel (6) is equal to the speed at which high-pressure oil flows out from the sealing ring (3), the piston (2) stops moving toward the low-pressure chamber (11) and the combined disc spring (5) stops compressing.

9. The control method according to claim 8, characterized in that, It also includes the following steps: When the sealing ring (3) disengages from the working chamber (9) and remains in the transition chamber (10), the motor stops running and releases some high-pressure oil from the high-pressure oil channel (6) to reduce the oil pressure in the chamber. The elastic potential energy of the combined disc spring (5) is greater than the oil pressure in the chamber, causing the piston (2) to move away from the low-pressure chamber (11). The sealing ring (3) then enters the working chamber (9) from the transition chamber (10) along with the piston (2) to restore the sealing function.

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