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

Abstract

The invention discloses a disc spring hydraulic mechanism energy storage cylinder and system and a control method, and the energy storage cylinder comprises a cylinder body which internally comprises a cavity, a piston, a sealing ring and a high-pressure oil channel; the piston is movably arranged in the cavity; the cavity comprises a working cavity and a low-pressure cavity; one end of the working cavity is connected with the high-pressure oil channel, the other end of the working cavity is connected with the low-pressure cavity, and the diameter of the low-pressure cavity is larger than that of the working cavity. The sealing ring is arranged on the periphery of the piston and used for preventing high-pressure oil entering from the high-pressure oil channel from flowing into the low-pressure cavity when the sealing ring is located in the working cavity. The high-pressure oil channel is used for inputting high-pressure oil to push the piston to move towards the low-pressure cavity or outputting the high-pressure oil to enable the piston to move towards the direction away from the low-pressure cavity. And the low-pressure cavity is used for collecting high-pressure oil flowing out of the sealing ring when the sealing ring is separated from the working cavity. The low-pressure oil cavity with the diameter larger than that of the working cavity is formed in the energy storage cylinder, high-pressure oil inner leakage occurs at the position of the sealing ring, and energy storage of the energy storage cylinder is stopped.

Description

Technical Field

[0001] The present invention relates to the technical field of switchgear, and in particular to an energy storage cylinder, system and control method of a disc spring hydraulic mechanism. Background Art

[0002] Disc spring hydraulic mechanism is widely used in the field of switches. Its typical structural feature is the use of disc springs to store energy. In disc spring hydraulic mechanism, the energy storage cylinder is an indispensable component, which is mainly composed of cylinder body, piston and cylinder head. Its working principle is to use oil pump to inject high-pressure oil into the rodless chamber of energy storage cylinder through pipeline, push the energy storage piston outward, compress the combined disc spring, and establish system pressure. Usually, disc spring hydraulic mechanism will judge whether the preset pressure is reached by monitoring the compression amount of the combined disc spring, and turn off the energy storage motor through the travel switch.

[0003] The accumulators currently used in disc spring hydraulic mechanisms have the following main problems: when the energy storage pressure reaches the design pressure, and the energy storage control system cannot cut off the energy storage circuit due to a fault (such as a mechanical or electrical fault in the travel switch), the hydraulic system pressure continues to rise, which may cause damage to the hydraulic system parts, such as the energy storage piston pushing open the cylinder cover to cause high-pressure oil leakage, or excessive compression of the combined disc spring, etc. These factors will cause structural damage and may cause personal injury. Summary of the invention

[0004] The present invention provides a disc spring hydraulic mechanism energy storage cylinder, system and control method, which are used to solve the problem of how to prevent the energy storage cylinder from continuing to store energy and prevent the energy storage piston from continuing to move, causing the cylinder cover to be pushed open and causing leakage of high-pressure oil or excessive compression of the combined disc spring when the energy storage control system fails to cut off the energy storage circuit due to a mechanical or electrical failure of a travel switch.

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

[0006] The piston is movably disposed in the cavity;

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

[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, and the diameter of the low-pressure chamber is greater than the diameter of the working chamber;

[0009] The sealing ring is arranged on the outer periphery of the piston, and is used to isolate the 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 to move toward the direction close to the low-pressure chamber, or to output high-pressure oil to make the piston move toward the direction away from the low-pressure chamber;

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

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

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

[0014] Furthermore, the transition cavity is in a truncated cone shape.

[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 cavity is greater than a preset value, which is the diameter of the cavity when an inlet speed of the high-pressure oil in the high-pressure oil channel is equal to an outlet speed of the high-pressure oil at the sealing ring.

[0017] The present invention provides an energy storage system of a disc spring hydraulic mechanism, comprising the energy storage cylinder, a connecting rod, a combined disc spring and a control assembly;

[0018] The piston of the energy storage cylinder is connected to the combined disc spring through the connecting rod, the middle part of the connecting rod passes through the bottom of the cylinder body, and the connecting rod is used to realize the movement of the piston to drive the combined disc spring disc to synchronously expand and contract;

[0019] The control assembly includes a motor, an oil pump, a first travel switch and a second travel switch:

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

[0021] The first travel switch and the second travel switch are both connected to the combined disc spring;

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

[0023] The first travel switch is used to cut off the series circuit when the combined disc spring reaches a first compression amount, so that the motor stops running;

[0024] The second travel switch is used to cut off the series circuit and stop the motor when the combined disc spring reaches a second compression amount, and the second compression amount is less than the first compression amount.

[0025] The present 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 travel switch is disconnected, the series circuit is cut off, the motor stops running, the high-pressure oil stops being input from the high-pressure oil channel, and the piston stops moving and the combined disc spring stops being compressed;

[0027] When the combined disc spring reaches the second compression amount, the series circuit is cut off, the motor stops running, and the input of high-pressure oil from the high-pressure oil channel is stopped, so that the piston stops moving and the combined disc spring stops compressing.

[0028] Furthermore, the following steps are included: when the combined disc spring reaches the third compression amount, the sealing ring on the piston separates 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 the high-pressure oil flows out from the sealing ring 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 speed of the high-pressure oil from the high-pressure oil channel is equal to the outflow speed of the 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 following steps are included: when the sealing ring detaches from the working chamber and stays in the transition chamber, the motor stops running, and part of the 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, so that the piston moves away from the low-pressure chamber, and the sealing ring enters the working chamber with the piston from the transition chamber to restore the sealing effect.

[0031] It can be seen from the above technical solutions that the present invention has the following advantages: The present invention provides a dual protection mechanism for preventing the disc spring hydraulic mechanism from over-storing energy. On the one hand, the present invention provides an energy storage system for a disc spring hydraulic mechanism, which adds a second travel switch in the series circuit, so that when the first travel switch fails, the series circuit is cut off by the second travel switch, the motor stops running, the energy storage cylinder stops storing energy, and the piston cannot continue to move, thereby achieving the first level of protection. On the other hand, the present invention provides an energy storage cylinder of a disc spring hydraulic mechanism. When the first stroke switch and the second stroke switch both fail, a low-pressure oil chamber with a larger diameter than the working chamber is set in the energy storage cylinder. When the sealing ring moves from the working chamber into the low-pressure chamber as the piston moves, the gap between the piston and the inner wall of the low-pressure chamber is larger than the gap between the piston and the working chamber, so that the sealing ring cannot isolate the high-pressure oil, and high-pressure oil leakage occurs. That is, the 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, resulting in a decrease in the pressure difference between the top and bottom of the piston, so that the energy storage cylinder stops storing energy and the piston does not have enough power to continue moving, thereby avoiding the problem of the cylinder cover being pushed open and causing the high-pressure oil to leak out or the combined disc spring to be over-compressed, thereby achieving the second level of protection. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

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

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

[0035] Figure 3 A schematic diagram of the relationship between a travel switch and a compression amount of a 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 A schematic diagram of a state in which a sealing ring in a disc spring hydraulic mechanism provided in an embodiment of the present invention is about to fall off a working chamber;

[0037] Figure numerals: 1, cylinder body; 2, piston; 3, sealing ring; 4, cylinder head; 5, combined disc spring; 6, high-pressure oil channel; 7, low-pressure oil channel; 8, connecting rod; 9, working chamber; 10, transition chamber; 11, low-pressure chamber; S1, first stroke switch; S2, second stroke 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 DESCRIPTION

[0038] In order to make the purpose, features and advantages of the present invention more obvious and easy to understand, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the embodiments described below are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0039] The terms "first", "second", "third", "fourth", etc. (if any) in the specification and drawings of the present invention are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchanged where appropriate, so that the implementation of the present application described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

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

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

[0042] The chamber 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 greater than the diameter of the working chamber 9;

[0045] The sealing ring 3 is arranged at the middle of the outer periphery of the piston 2, and is used to isolate the 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 to move toward the direction close to the low-pressure chamber 11, or to output high-pressure oil to move the piston 2 away from the low-pressure chamber 11;

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

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

[0049] It is understandable that, in specific implementation, high-pressure oil is continuously input from the high-pressure oil channel 6 into the working chamber 9 located above the piston 2, and the sealing ring 3 disposed between the piston 2 and the working chamber 9 isolates the high-pressure oil from flowing into the bottom of the piston 2, thereby causing the high-pressure oil to push the piston 2 to move toward the low-pressure chamber 11. When the sealing ring 3 moves from the working chamber 9 into the low-pressure chamber 11 as the piston 2 moves, since the diameter of the working chamber 9 is greater 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 greater than the gap between the piston 2 and the working chamber 9, so that the sealing ring 3 cannot isolate the high-pressure oil, and high-pressure oil internal leakage occurs, that is, high-pressure oil flows into the low-pressure chamber 11 from the sealing ring 3, resulting in a decrease in the pressure difference between the top and bottom of the piston 2, so that the energy storage cylinder stops storing energy, and the piston 2 does not have enough power to continue to move. Therefore, this embodiment can prevent the energy storage cylinder from continuing to store energy through the internal leakage of high-pressure oil, so that the energy storage piston 2 does not have enough power to continue to move.

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

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

[0052] It is understandable that, in specific implementation, the sealing ring 3 directly enters the large-diameter low-pressure chamber 11 from the small-diameter working chamber 9, and the sealing ring 3 instantly expands and rebounds. The high-pressure oil with a large flow rate impacts the expanded and rebounded sealing ring 3. When the high-pressure oil impacts, stress concentration may occur at the contact point between the sealing ring 3 and the surrounding structure, and the edge part may be subjected to higher pressure, causing these parts to be more easily damaged. In this embodiment, by setting 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 can control the expansion and rebound speed of the sealing ring 3, and then control the outflow flow and outflow speed of the high-pressure oil from the sealing ring 3, reduce the impact of the high-pressure oil on the sealing ring 3, and then avoid the sealing ring 3 from being damaged, thereby ensuring the recoverability of the sealing ring 3.

[0053] In a more specific embodiment, the inner wall of the transition chamber 10 is provided with a plurality of steps with gradually increasing diameters, so that the sealing ring 3 expands and rebounds step by step.

[0054] In some more specific embodiments, the inner wall of the transition chamber 10 is an inclined surface with a gradually increasing diameter, that is, the transition chamber is in the shape of a truncated cone. It can be understood that, in a specific implementation, the transition chamber 10 must meet the requirements of controlling the expansion and rebound speed of the sealing ring 3, and must also meet the requirements of being able to be compressed back into the working chamber 9 after the sealing ring 3 leaves the working chamber 9. In this embodiment, the inner wall of the transition chamber 10 is an inclined surface, which can reduce the resistance of the inner wall of the transition chamber 10 during the process of the sealing ring 3 being compressed back into the working chamber 9.

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

[0056] In a more specific embodiment, the height of the transition chamber 10 is greater than the height of the sealing ring 3. It is understandable that, in specific implementation, if the height of the transition chamber 10 is less than the height of the sealing ring 3, the difference between the expansion and rebound degree of the upper part of the sealing ring 3 and the expansion and rebound degree of the lower part is large. Due to the uneven rebound of the sealing ring 3, stress concentration is easily generated, resulting in material fatigue, shape change and other problems, and the aging speed of the sealing ring 3 will be accelerated. At the same time, the upper part of the sealing ring 3 is affected by oil pressure, and the stress concentration caused by the difference in the rebound degree of the upper and lower parts of the sealing ring 3 is more serious. This stress concentration may cause microscopic damage to the internal material of the sealing ring 3, such as the generation of microcracks. In this implementation, the height of the transition chamber 10 is greater than the height of the sealing ring 3, which is conducive to narrowing the difference between the expansion and rebound degree of the upper part of the sealing ring 3 and the expansion and rebound degree of the lower part, ensuring that the contact pressure of the sealing ring 3 is evenly distributed as much as possible, and avoiding the damage of the structure of the sealing ring 3.

[0057] In a more specific embodiment, the angle between the busbar of the transition chamber 10 and the axis of the transition chamber 10 is greater than zero and less than or equal to 30°. As shown in the figure, the angle between the busbar of the transition chamber 10 and the axis of the transition chamber 10 is θ. It is understandable that, in specific implementation, too large an angle may lead to insufficient busbar length and axis length. When the sealing ring 3 is compressed from the transition chamber 10 back to the working chamber 9, it is easy to cause problems such as uneven compression and misalignment of the sealing ring 3. When the sealing ring 3 enters the inner hole between the working chamber 9 and the transition chamber 10, there is a risk of damage to the sealing ring cutting. The angle of this embodiment is less than 30°, which can ensure that the busbar and axis length of the transition chamber 10 are long enough. When the sealing ring 3 is compressed from the transition chamber 10 back to the working chamber 9, it is not easy to cause problems such as uneven compression and misalignment of the sealing ring 3, and at the same time avoid the risk of damage to the sealing ring cutting.

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

[0059] In a more specific embodiment, the included angle between the busbar of the transition chamber 10 and the axis of the transition chamber 10 is θ, 15°≤θ≤30°, so that the inner wall of the transition chamber 10 can effectively guide the sealing ring 3 to separate from the working chamber 9, while preventing the sealing ring 3 from expanding too quickly and being damaged by the impact of high-pressure oil.

[0060] In a more specific embodiment, a cylinder cover 4 is disposed at the bottom of the transition chamber 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, and is used to output the high-pressure oil collected by the low-pressure chamber 11. It can be understood that, in a specific implementation, the space in the cylinder body 1 is limited. In order to ensure that the low-pressure chamber 11 can fully collect the high-pressure oil leaking from the sealing ring 3 before the energy storage cylinder stops storing energy, the low-pressure oil channel 7 connected to the low-pressure chamber 11 is provided in this implementation.

[0062] In a more specific embodiment, the low-pressure oil channel 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 smaller 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 entrance speed of the high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed of the high-pressure oil from the sealing ring 3 .

[0065] It should be noted that when the speed at which the high-pressure oil enters the high-pressure oil channel 6 is equal to the speed at which the high-pressure oil flows out of the sealing ring 3, the energy storage cylinder stops storing energy, the piston 2 stops moving toward 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 the preset value, the gap between the low-pressure chamber 11 and the piston 2 just satisfies that the oil outlet speed at the sealing ring 3 is equal to the high-pressure oil entry speed from the high-pressure oil channel 6. The diameter of the low-pressure chamber 11 of this embodiment is greater 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 be sealed and the high-pressure oil leaks out. 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 cover 4 to be pushed open, causing leakage of high-pressure oil or excessive compression of the combined disc spring 5 when the energy storage control system fails due to a mechanical or electrical failure of the travel switch and cannot cut off the energy storage circuit.

[0068] On the other hand, when the low-pressure chamber 11 is greater than the preset value, that is, 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 toward 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. The return deformation of the sealing ring 3 is smaller than that of the sealing ring 3 returning from the low-pressure chamber 11 to the working chamber 9, which is beneficial to protecting the sealing ring 3.

[0069] On the other hand, since the low-pressure oil passage 7 is arranged on one side of the low-pressure chamber 11, the flow direction of the high-pressure oil in the low-pressure chamber 11 changes, and 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 is easy to cause the sealing ring 3 to be misplaced and damaged. This embodiment can ensure that the sealing ring 3 stops storing energy in the transition chamber 10, and can avoid 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 energy storage 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 occurs, improve the safety of the debugging and operation process, and reduce maintenance costs.

[0072] This embodiment provides an energy storage system of a disc spring hydraulic mechanism, including the energy storage cylinder, the combined disc spring 5 and the control assembly 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, and the connecting rod 8 is used to realize the movement of the piston 2 and the expansion and contraction of the combined disc spring 5 synchronously;

[0074] The control assembly includes a motor, an oil pump, a first travel switch and a second travel switch:

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

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

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

[0078] The first travel switch S1 is used to cut off the series circuit when the combined disc spring 5 reaches the first compression amount L1, so that the motor stops running;

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

[0080] In a more specific embodiment, the second travel switch S2 is connected to an alarm device, and when the combined disc spring 5 reaches the second compression amount L2, the second travel switch S2 is triggered and the alarm device is also triggered, notifying the staff to handle the fault in time. Even when the second travel switch S2 fails, the alarm device can be triggered.

[0081] It can be understood that the existing disc spring hydraulic mechanism energy storage control system is mainly composed of a motor oil pump system, a first travel switch S1, other secondary control elements and a power supply, wherein the first travel switch S1 is a normally closed micro switch and is connected in series to the control circuit of the energy storage motor. When the combined disc spring 5 is compressed to the first compression amount L1, the first travel switch S1 is disconnected, and the energy storage motor is controlled to stop rotating.

[0082] In the present embodiment, in order to prevent over-energy storage, firstly, a second travel switch S2 for high oil pressure warning is added. When the first travel switch S1 fails, the combined disc spring 5 is compressed to the first compression amount L1 and then further compressed to the second compression amount L2. The second travel switch S2 will cut off the motor circuit and sound an alarm. If the energy storage cylinder of the disc spring hydraulic mechanism has not stopped storing energy at this time, the energy storage cylinder structure will be relied upon 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 downward, and the sealing ring 3 will enter the inclined surface and then expand outward, the sealing effect will weaken, and the sealing effect will accelerate as the energy storage piston 2 continues to move downward. In this process, internal leakage will occur, and at a certain moment, it will reach a balance with the pressure replenishment process, that is, when the high-pressure oil enters the high-pressure oil channel 6 at a speed equal to the outflow speed at the sealing ring 3, the energy storage piston 22 is prevented from continuing to move downward. The expansion speed of the sealing ring 3 of this embodiment is controllable, which can protect the sealing ring 3 from being damaged by excessive flow of hydraulic oil, and has recoverability, and there is no need to disassemble and repair the energy storage cylinder and the hydraulic system after a failure occurs.

[0084] Compared with the prior art, the energy storage system of the disc spring hydraulic mechanism in this embodiment provides dual protection. First, it provides a second travel switch S2 for high oil pressure warning, which helps maintenance personnel to find faults in time. Second, it ensures that there will be no safety accidents in the energy storage cylinder structure even if there is over-energy storage. The recoverability of the sealing ring 3 in the structure removes the hydraulic system from the maintenance and recovery of the fault, greatly improving the 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 travel switch S1.

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

[0086] The first level of protection is achieved by:

[0087] When the combined disc spring 5 reaches the first compression amount L1, the first travel switch S1 is disconnected, cutting off the series circuit, stopping the motor from running, stopping the input of high-pressure oil from the high-pressure oil channel 6, and realizing 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 being input 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 level 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 separates 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 passes through the transition chamber 10 into the low-pressure chamber 11 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 speed of the high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed 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 force on the piston 2 is balanced, the piston 2 stops moving toward the direction approaching the low-pressure chamber 11 and the combined disc spring 5 stops compressing.

[0093] It can be understood that this embodiment provides a dual protection control method for preventing disc spring hydraulic mechanism from over-storing energy, which increases the protection and early warning risk of disc spring hydraulic mechanism over-storing energy and increases the safety of the system.

[0094] In a more specific embodiment, a method for achieving recovery sealing is provided as follows:

[0095] When the sealing ring 3 is separated from the working chamber 9 and is in the transition chamber 10, after the piston 2 stops moving, the motor is stopped manually, and part of the 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, so that the piston 2 moves away from the low-pressure chamber 11, and the sealing ring 3 enters the working chamber 9 from the transition chamber 10 to restore the sealing effect.

[0096] It can be understood that, in this embodiment, a transition chamber 10 is provided between the working chamber 9 and the low-pressure chamber 11, and specific limitations are made on the height of the transition chamber 10, the angle of the bevel, 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 of this embodiment can return to the working chamber 9 with the piston 2 to restore the sealing function.

[0097] The above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit the same. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that the technical solutions described in the aforementioned embodiments may still be modified, or some of the technical features thereof may be replaced by equivalents. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A disc spring hydraulic mechanism accumulator cylinder, characterized in that: include: A cylinder body (1), wherein the cylinder body (1) comprises a cavity, a piston (2), a sealing ring (3) and a high-pressure oil channel (6); The piston (2) is movably arranged in the cavity; The chamber comprises 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), and the diameter of the low-pressure chamber (11) is greater than the diameter of the working chamber (9); The sealing ring (3) is arranged on the outer periphery of the piston (2) and is used to prevent the high-pressure oil entering from the high-pressure oil passage (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 in a direction close to the low-pressure chamber (11), or to output high-pressure oil to move the piston (2) in a direction away from the low-pressure chamber (11); The low-pressure chamber (11) is used to collect high-pressure oil flowing out from the sealing ring (3) when the sealing ring (3) is separated from the working chamber (9).

2. The disc spring hydraulic mechanism accumulator cylinder according to claim 1, characterized in that: The cavity body further comprises a transition cavity (10), wherein the transition cavity (10) is arranged between the working cavity (9) and the low-pressure cavity (11), and 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 disc spring hydraulic mechanism accumulator cylinder according to claim 2, characterized in that: The height of the transition chamber (10) is greater than the height of the sealing ring (3).

4. The disc spring hydraulic mechanism accumulator cylinder according to claim 2, characterized in that: The transition chamber (10) is in the shape of a truncated cone.

5. The disc spring hydraulic mechanism accumulator cylinder according to claim 4, characterized in that: The included 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. A disc spring hydraulic mechanism accumulator cylinder 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 entrance speed of the high-pressure oil into the high-pressure oil channel (6) is equal to the outflow speed of the high-pressure oil at the sealing ring (3).

7. An energy storage system for a disc spring hydraulic mechanism, characterized in that: It comprises the energy storage cylinder, connecting rod (8), combined disc spring (5) and control assembly as described in any one of claims 1 to 6; The piston (2) of the energy storage cylinder is connected to the combined disc spring (5) via the connecting rod (8), the middle portion of the connecting rod (8) passes through the bottom of the cylinder body (1), and the connecting rod (8) is used to realize the movement of the piston (2) to drive the combined disc spring (5) to synchronously expand and contract; The control assembly includes a motor, an oil pump, a first travel switch and a second travel switch: The oil pump is connected to the high-pressure oil channel (6), and the motor is connected to the oil pump, and the motor is used to drive the oil pump to rotate and suck in and generate high-pressure oil; The first travel switch and the second travel switch are both connected to the combined disc spring (5); The motor, the first travel switch and the second travel switch are arranged in a series circuit, and the first travel switch and the second travel switch are both normally closed switches; The first travel switch is used to cut off the series circuit when the combined disc spring (5) reaches a first compression amount, so that the motor stops running; The second travel switch is used to cut off the series circuit and stop the motor when the combined disc spring (5) reaches a second compression amount, and the second compression amount is smaller than the first compression amount.

8. A control method for the energy storage system according to claim 7, characterized in that: The following steps are involved: When the combined disc spring (5) reaches the first compression amount, the first travel 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 (6), and achieving the stop of movement of the piston (2) and the stop of compression of the combined disc spring (5); When the combined disc spring (5) reaches the second compression amount, the series circuit is cut off, the motor stops running, and the input of high-pressure oil from the high-pressure oil channel (6) is stopped, so that the piston (2) stops moving and the combined disc spring (5) stops compressing.

9. The control method according to claim 8, characterized in that: The following steps are also included: When the combined disc spring (5) reaches the third compression amount, the sealing ring (3) on the piston (2) separates 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 flows out from the sealing ring (3) 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 the high-pressure oil passage (6) is equal to the speed at which high-pressure oil flows out of the sealing ring (3), the piston (2) stops moving toward the low-pressure chamber (11) and the combined disc spring (5) stops compressing.

10. The control method according to claim 9, characterized in that: The following steps are also included: When the sealing ring (3) is separated from the working chamber (9) and stays in the transition chamber (10), the motor stops running and part of the 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, so that the piston (2) moves away from the low-pressure chamber (11), and the sealing ring (3) enters the working chamber (9) along with the piston (2) from the transition chamber (10) to restore the sealing effect.

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