Air storage and supply control method and system for air cylinder

Abstract

The invention relates to the technical field of industrial automation, in particular to an air storage and supply control method and system for an air cylinder. According to the air storage and supply control method, accurate air pressure management of the lifting air cylinder is achieved through cooperative control of the multiple stages of air storage tanks and the pressurization assembly. And in the ascending working condition, gas pressure is increased through the pressurizing assembly and then conveyed to the second gas storage tank, thrust is provided for the lifting air cylinder, and the driving load of the servo motor in the ascending stage is remarkably reduced. And in the descending working condition, controllable thrust is applied to the lifting rod through pressure maintaining gas of the second gas storage tank, descending impact is buffered, and meanwhile the load of the servo motor during descending is relieved. The pressure range is dynamically and automatically switched according to the ascending / descending working condition, high-pressure assistance is achieved during ascending, and the pressure is relieved to the low pressure during descending to achieve the buffering effect. And during dormancy, an air path is automatically disconnected and pressure is maintained, and air pressure is reserved for next-time quick starting.

Description

Technical Field

[0001] This application relates to the field of industrial automation technology, and particularly to a control method and system for storing and supplying air for cylinders. Background Art

[0002] In the field of industrial automation, there are significant technical bottlenecks in the lifting mechanism where cylinders of large multi-station three-dimensional devices cooperate with servo motors. The traditional air supply system uses a single air source for direct air supply or a simple design with an air storage tank for buffering, resulting in the servo motor bearing excessive load during the lifting process, high energy consumption, and difficulty in ensuring smooth movement. Specifically, in the rising stage, there is a lack of effective air pressure assistance, and the motor needs to output full power; during the descent, there is insufficient buffering, which is prone to impact vibration; the air pressure supply is disconnected from the real-time working conditions, and it is impossible to dynamically adjust according to parameters such as speed and stroke. Although existing technologies have tried to improve through methods such as fixed pressurization or mechanical damping, they generally have problems such as poor adaptability, response lag, and complex structures, and it is difficult to meet the requirements of modern production with high precision and high energy efficiency. Especially for application scenarios such as large multi-station stamping equipment, there is an urgent need for a control method that can intelligently match the air pressure output with the motion characteristics to reduce the load on the servo motor and improve the overall performance of the system. Summary of the Invention

[0003] In view of this, this application provides a control method and system for storing and supplying air for cylinders, which can intelligently match the air pressure output with the motion characteristics to reduce the load on the servo motor and improve the overall performance of the system.

[0004] In a first aspect, a control method for storing and supplying air for a cylinder provided by this application is applied to an air supply device for a lifting cylinder that assists a lifting servo motor. The air supply device for the lifting cylinder includes an air source, a first air storage tank, a pressurization component, and a second air storage tank connected in sequence. The second air storage tank is connected to the lifting cylinder. The method includes: controlling the air source to input gas into the first air storage tank until it reaches a first set pressure range; when the lifting cylinder is in a commanded rising working condition, controlling the pressurization component to connect the first air storage tank and the second air storage tank and perform pressurization until the second air storage tank reaches a second set pressure range, and controlling the second air storage tank to be connected to the lifting cylinder; when the lifting cylinder is in a commanded descending working condition, controlling the second air storage tank to be connected to the lifting cylinder, controlling the second air storage tank to release pressure to a third pressure set range, and controlling the pressurization component to close and monitor the air pressure of the second air storage tank; when the lifting cylinder is in a commanded descending working condition, if the air pressure of the second air storage tank exceeds the third set pressure range, then perform pressure relief until it returns to the third set pressure range; and if the lifting cylinder stops working for more than a first preset duration, then control the pressurization component to close and control the second air storage tank to be disconnected from the lifting cylinder.

[0005] In combination with the first aspect, in a possible implementation manner, when the lifting cylinder is in the commanded rising working condition, controlling the supercharging assembly to connect the first air storage tank and the second air storage tank and perform supercharging until the pressure in the second air storage tank reaches a second set pressure range, and controlling the second air storage tank to communicate with the lifting cylinder, includes: obtaining a rising command, and obtaining a corresponding rising stroke according to the rising command; if the rising stroke is less than or equal to a first stroke, controlling the supercharging assembly to perform supercharging at a first supercharging multiple; if the rising stroke is greater than the first stroke and less than or equal to a second stroke, controlling the supercharging assembly to perform supercharging at a second supercharging multiple; and if the rising stroke is greater than the second stroke, controlling the supercharging assembly to perform supercharging at a third supercharging multiple; wherein, the second stroke is greater than the first stroke, the third supercharging multiple is greater than the second supercharging multiple, and the second supercharging multiple is greater than the first supercharging multiple.

[0006] In combination with the first aspect, in a possible implementation manner, the method further includes: when the lifting cylinder is in the commanded rising working condition: if the air pressure in the first air storage tank drops to a fourth set pressure range, monitoring the air pressure change of the second air storage tank during the supercharging process of the supercharging assembly; if the decrease amplitude of the second air storage tank is greater than a preset amplitude, controlling the supercharging assembly to increase the supercharging ratio; and controlling to increase the input rate of the gas source to input gas into the first air storage tank; wherein, the fourth set pressure range is less than the first set pressure range.

[0007] In combination with the first aspect, in a possible implementation manner, when the lifting cylinder is in the commanded rising working condition, controlling the supercharging assembly to connect the first air storage tank and the second air storage tank and perform supercharging until the pressure in the second air storage tank reaches a second set pressure range, and controlling the second air storage tank to communicate with the lifting cylinder, includes: obtaining a corresponding real-time rising speed according to the rising command in the commanded rising working condition; and matching a corresponding supercharging ratio according to the real-time rising speed, and controlling the supercharging assembly to perform supercharging according to the supercharging ratio; wherein, the supercharging ratio is proportional to the real-time rising speed.

[0008] In combination with the first aspect, in a possible implementation manner, the second gas storage tank is provided with a second pressure relief valve; wherein, when the lifting cylinder is in the commanded descending working condition, if the air pressure in the second gas storage tank exceeds the third set pressure range, pressure relief is performed until it returns to the third set pressure range, including: obtaining the real-time descending speed in the commanded descending working condition; if the air pressure in the second gas storage tank exceeds the third set pressure range, opening the second pressure relief valve; matching the second opening degree of the second pressure relief valve according to the real-time descending speed, and the second opening degree is inversely proportional to the real-time descending speed; and if the air pressure in the second gas storage tank returns to the third set pressure range, closing the second pressure relief valve.

[0009] In combination with the first aspect, in a possible implementation manner, the first gas storage tank is provided with a first drain valve, and the second gas storage tank is provided with a second drain valve; wherein, the gas storage and air supply control method for the cylinder further includes: regularly opening the first drain valve and the second drain valve to perform the drainage work.

[0010] In combination with the first aspect, in a possible implementation manner, it further includes: when the lifting cylinder is in an abnormal descending working condition, controlling the pressurizing assembly to connect the first gas storage tank and the second gas storage tank and perform pressurization, so that the inside of the second gas storage tank is maintained within a fourth set pressure range, and controlling the second gas storage tank to be connected to the lifting cylinder; wherein, the fourth set pressure range is greater than or equal to the second set pressure range, the real-time descending speed corresponding to the abnormal descending working condition is greater than the real-time descending speed corresponding to the commanded descending working condition, or the change range of the real-time descending speed corresponding to the abnormal descending working condition within the unit reference time period is greater than the preset speed change range.

[0011] In combination with the first aspect, in a possible implementation manner, the second gas storage tank is provided with a second pressure relief valve; the gas storage and air supply control method for the cylinder further includes: when the lifting cylinder is in a fine-tuning working condition, controlling the pressurizing assembly and the second pressure relief valve to work together to keep the inside of the second gas storage tank within a fifth set pressure range; the fifth set pressure range is less than the second set pressure range; closing the pressurizing assembly; and controlling the second gas storage tank to be connected to the lifting cylinder.

[0012] In combination with the first aspect, in a possible implementation manner, when the lifting cylinder is in the fine-tuning working condition, controlling the booster assembly and the second pressure relief valve to work together to maintain the second air storage tank within the fifth set pressure range includes: when the lifting cylinder is in the fine-tuning working condition, detecting the air pressure of the second air storage tank; if the air pressure of the second air storage tank is less than the fifth set pressure range, controlling the second pressure relief valve to close, and controlling the booster assembly to connect the first air storage tank and the second air storage tank and perform pressurization until the second air storage tank reaches the fifth set pressure range; if the air pressure of the second air storage tank is greater than the fifth set pressure range, controlling the booster assembly to close, and controlling the second pressure relief valve to open until the second air storage tank reaches the fifth set pressure range.

[0013] In a second aspect, the present application provides an air storage and air supply control system for a cylinder, which is applied to an air supply device for a lifting cylinder of an auxiliary lifting servo motor. The air supply device for the lifting cylinder includes an air source, a first air storage tank, a booster assembly, and a second air storage tank connected in sequence. The second air storage tank is connected to the lifting cylinder. The system includes: a first air storage tank air pressure control module configured to control the air source to input gas into the first air storage tank until it reaches the first set pressure range; a rising control module configured to, when the lifting cylinder is in the commanded rising working condition, control the booster assembly to connect the first air storage tank and the second air storage tank and perform pressurization until the second air storage tank reaches the second set pressure range, and control the second air storage tank to communicate with the lifting cylinder; a descending control module configured to, when the lifting cylinder is in the commanded descending working condition, control the second air storage tank to communicate with the lifting cylinder, control the second air storage tank to release pressure to the third pressure set range, and control the booster assembly to close and monitor the air pressure of the second air storage tank; when the lifting cylinder is in the commanded descending working condition, if the air pressure of the second air storage tank exceeds the third set pressure range, then perform pressure relief until it returns to the third set pressure range; and a shutdown module configured to, if the lifting cylinder stops working for more than a first preset duration, control the booster assembly to close and control the second air storage tank to disconnect from the lifting cylinder.

[0014] The air storage and air supply control method and system provided by the present application have the following beneficial effects: (1) Through the collaborative control of the multi-stage gas storage tank and the pressurization component, the present invention realizes precise air pressure management of the lifting cylinder. In the ascending working condition, the gas pressure is boosted by the pressurization component and then delivered to the second gas storage tank to provide thrust for the lifting cylinder, significantly reducing the driving load of the servo motor during the ascending stage; in the descending working condition, the pressurized gas in the second gas storage tank is used to apply a controllable thrust to the lifting rod to buffer the descending impact, while reducing the load of the servo motor during descent; the pressure range is dynamically and automatically switched according to the ascending / descending working conditions, with high-pressure assistance during ascent and pressure relief to a lower pressure during descent for buffering, and real-time monitoring and pressure relief to ensure that the air pressure is stable within the third set range during descent, preventing the descending resistance caused by overpressure; during dormancy, the gas circuit is automatically disconnected and the pressure is maintained, reducing energy consumption while retaining the air pressure reserve for quick activation next time; (2) The present invention selects different pressurization modes according to the stroke length: a lower pressurization multiple is adopted for shorter strokes, a medium pressurization multiple for medium strokes, and a higher pressurization multiple for longer strokes; this hierarchical pressurization method can provide appropriate air pressure support for different lifting requirements, avoiding energy waste and ensuring the smoothness of the lifting process. This intelligent pressure regulation mechanism can also extend the service life of pneumatic components and reduce unnecessary mechanical wear, and is particularly suitable for application in automated production scenarios with frequent changes in the lifting stroke, such as automotive part stamping production lines, etc.; the entire control process realizes the precise matching of air pressure output and actual working conditions, optimizing the energy consumption efficiency and improving the overall performance of the system; (3) The present invention also introduces a speed-pressure linkage control mechanism. When the system receives an ascending command, it not only judges the stroke length but also dynamically matches the optimal pressurization ratio according to the real-time ascending speed required by the command. When rapid ascent is needed, the system automatically adopts a higher pressurization ratio to provide stronger thrust support for the cylinder, ensuring that the servo motor can still maintain a stable load under high-speed working conditions; conversely, when ascending at a low speed, the pressurization ratio is reduced to avoid energy waste or mechanical impact caused by excessive air pressure; this on-demand adjustment method makes the air pressure output precisely match the movement speed, meeting the power requirements under different working conditions and optimizing the overall energy efficiency performance. Especially in automated production lines that require variable-speed movement, this control method can adapt to speed changes in real time, always maintaining the best air pressure assistance effect, effectively improving the system response speed and smoothness, while reducing the operating load of the servo motor; (4) The present invention introduces a speed - adaptive pressure - relief control mechanism. When the system detects a descending condition, it will monitor the current real - time descending speed in real time and accordingly intelligently adjust the opening degree of the second pressure - relief valve. This dynamic adjustment achieves an accurate match between the air - pressure buffer force and the real - time descending speed, forming a closed - loop control effect. In specific implementation, the physical property of the back - pressure gas of the lifting rod is utilized, and the system damping is adjusted by controlling the pressure - relief speed, achieving a softer linear deceleration effect. In practical applications, this intelligent buffering mechanism can effectively prevent impact vibration during heavy - load descending, protect the safety of the equipment, while reducing the braking load of the servo motor and extending the service life of the transmission system. It enables the lifting mechanism to maintain an ideal descending curve under different load conditions, significantly improving the operation quality and reliability of the equipment; (5) The present invention introduces a precise pressure control mechanism under fine - tuning conditions. The system will start a special pressure management mode: by coordinately controlling the pressurizing component and the second pressure - relief valve, the pressure of the second gas storage tank is stabilized within a fifth set range lower than the conventional working pressure. This low - pressure holding mode can provide a softer buffer thrust support for the lifting cylinder, providing a certain supporting force for the lifting cylinder to perform fine - tuning lifting. This control method is particularly suitable for operation scenarios that require high - precision positioning, such as precision assembly or inspection stations, and can effectively eliminate the "crawling" or "jitter" phenomena that are prone to occur during fine - tuning of traditional pneumatic systems. By reducing the working pressure, the system obtains smoother motion characteristics and finer control resolution, while reducing energy consumption and equipment wear. Brief Description of the Drawings

[0015] Figure 1 The figure shows a schematic diagram of the method steps of a gas storage and gas supply control method for a cylinder provided by an embodiment of the present application.

[0016] Figure 2 The figure shows a schematic diagram of a gas supply device for a lifting cylinder provided by an embodiment of the present application.

[0017] Figure 3 The figure shows a schematic diagram of a pressurizing component provided by an embodiment of the present application.

[0018] Figure 4 The figure shows a schematic diagram of the method steps for controlling the pressurization multiple according to the ascending stroke.

[0019] Figure 5 The figure shows a schematic diagram of the control steps when air - pressure oscillation occurs in the second gas storage tank.

[0020] Figure 6 The figure shows a schematic diagram of the method steps for controlling the pressurization multiple according to the real - time ascending speed.

[0021] Figure 7 The figure shows a schematic diagram of the method steps for controlling the pressure - relief opening degree according to the real - time descending speed.

[0022] Figure 8 Shown is a schematic diagram of the pressure control steps in the abnormal decline condition.

[0023] Figure 9 Shown is a schematic diagram of the pressure control steps in the fine-tuning condition.

[0024] Figure 10 It is a schematic diagram of the air pressure control steps for the second gas storage tank in the fine-tuning condition.

[0025] Figure 11 Shown is a schematic diagram of the system structure of the gas storage and supply control system for the cylinder. Detailed implementation manners

[0026] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present application.

[0027] An exemplary gas storage and supply control method for the cylinder is as follows: Figure 1 Shown is a schematic diagram of the method steps of a gas storage and supply control method for a cylinder provided in an embodiment of the present application. Figure 2 Shown is a schematic diagram of the air supply device for the lifting cylinder provided in an embodiment of the present application. The present application provides a gas storage and supply control method for the cylinder. This method is applied to the air supply device for the lifting cylinder of the auxiliary lifting servo motor. Referring to Figure 2 , the air supply device for the lifting cylinder includes a gas source 1, a first gas storage tank 2, a boosting assembly 3, and a second gas storage tank 4 connected in sequence. The boosting assembly includes an electronically controlled boosting valve. The second gas storage tank 4 is connected to the lifting cylinder 5. The lifting cylinder 5 and the servo motor are both assembled on the lifting mechanism, and the lifting table is mainly driven by the servo motor to lift.

[0028] In one embodiment, as Figure 1 shown, the gas storage and supply control method for the cylinder includes: Step 110: Control the gas source 1 to input gas into the first gas storage tank 2 until it reaches the first set pressure range.

[0029] In this step, the gas source 1 fills the first gas storage tank 2, so that there is a certain air pressure in the first gas storage tank 2 for the use of the second gas storage tank 4.

[0030] When the lifting cylinder 5 is in the commanded rising condition, step 120 is executed: control the boosting assembly 3 to connect the first gas storage tank 2 and the second gas storage tank 4 and perform boosting until the pressure in the second gas storage tank 4 reaches the second set pressure range, and then control the second gas storage tank 4 to be connected to the lifting cylinder 5.

[0031] In this step, the commanded rising condition is determined by the processor, that is, controlling the lifting platform to perform the lifting action. The second set pressure range is set according to the boosting requirement. For example, in the pneumatic circuit of the lifting cylinder of a large multi-station three-dimensional in the automotive parts stamping automation production line, the first set pressure range of the first gas storage tank 2 is generally set to 0.5 - 0.6 Mpa. Correspondingly, the second set pressure range of the second gas storage tank 4 is generally set to 1 - 1.2 Mpa. The gas in the first gas storage tank 2 is boosted by the boosting assembly 3 and then transported into the second gas storage tank 4. The boosting multiple can be set to 2 times. The air pressure in the second gas storage tank 4 is transported into the lifting cylinder 5. The air pressure in the second gas storage tank 4 exerts a certain thrust on the lifting rod of the lifting cylinder 5, thereby assisting the servo motor to rise and reducing the rising driving load of the servo motor. The second set pressure range can be set according to the boosting requirement of the lifting cylinder for the servo motor. The higher the boosting requirement, the larger the second set pressure range.

[0032] When the lifting cylinder 5 is in the commanded descending condition, step 130 is executed: control the second gas storage tank 4 to be connected to the lifting cylinder 5, control the second gas storage tank 4 to release pressure to the third pressure set range, and control the boosting assembly 3 to close and monitor the air pressure of the second gas storage tank 4.

[0033] In this step, the commanded descending condition is determined by the processor, that is, controlling the lifting platform to perform the descending action. In this condition, the closing of the boosting assembly 3 makes the second gas storage tank 4 in a pressure-holding state. The second gas storage tank 4 is connected to the lifting cylinder 5. When the servo motor drives the lifting platform to descend, the lifting platform presses the lifting rod to retract. The air pressure in the pressure-holding second gas storage tank 4 can exert a certain thrust on the lifting rod, and this thrust can play a buffering role in the descending of the lifting platform, avoiding the lifting platform from descending too fast and at the same time reducing the descending driving load of the servo motor. During the retraction process of the lifting cylinder 5 when the lifting platform descends, a small amount of gas will be back-pressed into the second gas storage tank 4, and the air pressure of the second gas storage tank 4 is detected during this period. The second gas storage tank 4 is provided with a second pressure relief valve 401. At the same time, when the commanded descending condition is obtained, first close the boosting assembly 3, and then release the pressure of the second gas storage tank 4 to the third pressure set range, so that the air pressure of the second gas storage tank 4 is lower than the second set pressure range, avoiding the air pressure in the second gas storage tank 4 exerting too much thrust on the lifting rod and generating too much descending resistance. The third pressure set range can be set between 0.4 times and 0.8 times of the second pressure set range. This value can be adjusted according to the actual measurement during the operation of the lifting platform. If the resistance caused by the pressure-holding of the second gas storage tank 4 is too large, just lower the third pressure set range.

[0034] When the lifting cylinder 5 is in the commanded descending condition, step 140 is executed. If the air pressure in the second air storage tank 4 exceeds the third set pressure range, pressure relief is performed until it returns to the third set pressure range.

[0035] In this step, during the retraction process of the lifting cylinder 5 when the lifting platform descends, a small amount of gas is back-pressured into the second air storage tank 4. During this period, the air pressure in the second air storage tank 4 is detected. If the air pressure in the second air storage tank 4 is greater than the third set pressure range, it may generate an excessive thrust on the lifting rod. Pressure relief is promptly performed to keep the second air storage tank 4 within the third set pressure range, avoiding excessive thrust on the lifting rod due to the air pressure in the second air storage tank 4 and generating excessive descending resistance.

[0036] Judge whether the lifting cylinder 5 has stopped working for more than the first preset duration. If so, execute step 150, control the booster assembly 3 to close, and control the disconnection between the second air storage tank 4 and the lifting cylinder 5.

[0037] In this step, when the lifting cylinder 5 has been out of operation for too long, it can be considered to be in a dormant state. There is no need for the booster assembly 3 to intervene in the work. The booster assembly 3 is closed and the second air storage tank 4 is disconnected from the lifting cylinder 5, so that the second air storage tank 4 is in a pressure-holding state, storing a certain amount of air pressure for the next use.

[0038] The air storage and air supply control method provided in this embodiment realizes precise air pressure management of the lifting cylinder through the coordinated control of multiple air storage tanks and the booster assembly. In the ascending condition, the gas pressure is boosted by the booster assembly 3 and then supplied to the second air storage tank 4 to provide thrust for the lifting cylinder 5, significantly reducing the driving load of the servo motor in the ascending stage. In the descending condition, the pressurized gas in the second air storage tank 4 is used to apply a controllable thrust to the lifting rod to buffer the descending impact and at the same time reduce the load of the servo motor during descending. The pressure range is dynamically and automatically switched according to the ascending / descending conditions, with high-pressure assistance (the second set pressure range) during ascending and pressure relief to a lower pressure (the third set pressure range) during descending to play a buffering role. Monitor and relieve pressure in real time to ensure that the air pressure is stable within the third set range during descending, preventing descending resistance caused by overpressure. Automatically disconnect the air circuit and hold pressure during dormancy, reducing energy consumption and at the same time reserving air pressure for quick activation next time.

[0039] Figure 3 The figure shows a schematic diagram of the booster assembly provided by an embodiment of the present application. Specifically, as Figure 3As shown, the supercharging assembly 3 includes a residual pressure release three-way valve 301, a gas distribution seat 302, a low-pressure pressure reducing valve 303, an electronically controlled supercharging valve 304, and a high-pressure pressure reducing valve 305. One port of the residual pressure release three-way valve 301 is connected to the first gas storage tank 2, and one port of the residual pressure release three-way valve 301 is communicated with the electronically controlled supercharging valve 304. The residual pressure release three-way valve 301 is mainly used for disconnecting the gas source and exhausting gas. The gas distribution seat 302 is mainly used for gas path shunting and fixedly installing the residual pressure release three-way valve 301. The low-pressure pressure reducing valve 303 and the high-pressure pressure reducing valve 305 are pressure reducing valves with a reverse flow function, which can prevent damage to the internal structure of the pressure reducing valve due to different pressure magnitudes on both sides. The pipeline joints at the rear section of the low-pressure pressure reducing valve 303 are all high-pressure pipe joints.

[0040] Figure 4 The figure shows a schematic diagram of the method steps for controlling the supercharging multiple according to the rising stroke. In one embodiment, as Figure 4 shown, when the lifting cylinder 5 is in the commanded rising working condition, step 120 includes: Step 121, obtain a rising command and obtain the corresponding rising stroke according to the rising command.

[0041] Step 122, if the rising stroke is less than or equal to the first stroke, control the supercharging assembly 3 to perform supercharging at the first supercharging multiple.

[0042] Step 123, if the rising stroke is greater than the first stroke and less than or equal to the second stroke, control the supercharging assembly 3 to perform supercharging at the second supercharging multiple.

[0043] Step 124, if the rising stroke is greater than the second stroke, control the supercharging assembly 3 to perform supercharging at the third supercharging multiple.

[0044] In this embodiment, the second stroke is greater than the first stroke, the third supercharging multiple is greater than the second supercharging multiple, and the second supercharging multiple is greater than the first supercharging multiple. By dynamically adjusting the supercharging multiple according to the rising stroke of the lifting cylinder, this embodiment achieves more precise air pressure control. When the lifting cylinder is in the commanded rising working condition, the system first obtains the rising command and determines the corresponding rising stroke. The rising command is issued by the processor, and then different supercharging modes are selected according to the stroke length: a lower supercharging multiple is used for a shorter stroke, a medium supercharging multiple is used for a medium stroke, and a higher supercharging multiple is used for a longer stroke. This hierarchical supercharging method can provide just the right air pressure support for different lifting requirements, avoiding energy waste and ensuring the smoothness of the lifting process. During short-stroke operations, the lower air pressure output can prevent system overload; while during long-stroke operations, the higher supercharging multiple can effectively share the load pressure of the servo motor. At the same time, this intelligent pressure regulation mechanism can also extend the service life of pneumatic components, reduce unnecessary mechanical wear, and is particularly suitable for application in automated production scenarios with frequent changes in lifting strokes, such as automotive parts stamping production lines. The entire control process achieves precise matching of air pressure output and actual working conditions, optimizing energy consumption efficiency and improving the overall performance of the system.

[0045] Figure 5 The figure shows a schematic diagram of the control steps when the second air storage tank has air pressure oscillation. In one embodiment, as Figure 5 shown, when the lifting cylinder 5 is in the commanded rising working condition, the air storage and air supply control method for the cylinder further includes: Step 1201: If the air pressure in the first air storage tank 2 drops to the fourth set pressure range, monitor the air pressure change of the second air storage tank 4 during the process of the supercharging component 3 performing supercharging.

[0046] Step 1202: If the decrease amplitude of the second air storage tank 4 is greater than the preset amplitude, control the supercharging component 3 to increase the supercharging ratio.

[0047] Step 1203: Control to increase the input rate of the gas from the gas source 1 to the first air storage tank 2.

[0048] In this embodiment, the fourth set pressure range is smaller than the first set pressure range. By dynamically monitoring and adjusting the air pressure parameters, the response ability and stability of the air storage and gas supply system are further optimized. When the air pressure in the first air storage tank drops to the fourth set range, the system will immediately activate the pressurization monitoring mechanism and track the air pressure fluctuations in the second air storage tank in real time. Once it is detected that the air pressure in the second air storage tank drops too fast, the system will implement dual adjustment measures simultaneously: on the one hand, increase the magnification of the pressurization component (for example, increase it to 1.5 - 2 times), so as to quickly supplement high-pressure gas; on the other hand, accelerate the air supply speed from the air source to the first air storage tank, for example, increase it to 1.5 - 2 times the input rate. This linkage adjustment mechanism effectively solves the possible problem of gas supply lag and ensures that the system pressure balance can be quickly restored during air pressure fluctuations. By setting the fourth pressure range as the trigger threshold, the system can intervene in the adjustment in advance when the air pressure has not been completely exhausted, avoiding unstable lifting actions or servo motor overload caused by sudden pressure drops. This forward-looking pressure management strategy is particularly suitable for continuous operation scenarios, can maintain the continuous and stable output of the air pressure system, not only ensures the boosting effect of the lifting cylinder, but also extends the service life of pneumatic components. The entire adjustment process realizes the real-time matching of air pressure supply and demand changes, significantly improving the dynamic response ability and overall reliability of the system.

[0049] Figure 6 The figure shows a schematic diagram of the method steps for controlling the pressurization multiple according to the real-time rising speed. In one embodiment, as Figure 6 shown, when the lifting cylinder 5 is in the commanded rising working condition, step 120 includes: Step 125, obtaining the corresponding real-time rising speed according to the rising command in the commanded rising working condition.

[0050] Step 126, matching the corresponding pressurization multiple according to the real-time rising speed, and controlling the pressurization component 3 to perform pressurization according to the pressurization multiple.

[0051] In this embodiment, the pressurization multiple is proportional to the real-time rising speed. By introducing a speed-pressure linkage control mechanism, the intelligent adjustment of the boosting effect of the lifting cylinder is realized. When the system receives a rising command, it not only judges the stroke length, but also dynamically matches the optimal pressurization multiple according to the real-time rising speed required by the command. When a rapid rise is needed, the system automatically adopts a higher pressurization multiple to provide stronger thrust support for the cylinder, ensuring that the servo motor can still maintain a stable load under high-speed working conditions; conversely, when rising at a low speed, the pressurization multiple is reduced to avoid energy waste or mechanical shock caused by excessive air pressure.

[0052] The relationship between the preset real-time rising speed v and the pressurization ratio h is set in advance. For example, the lowest rising speed that the lifting platform can reach is v1, the highest rising speed is v2, the lowest pressurization ratio that the pressurization component 3 can reach is h1, and the highest pressurization ratio is h2. The pressurization ratio changes uniformly with the real-time rising speed, that is, the pressurization ratio and the real-time rising speed are linearly corresponding to each other, h = h1 + (v - v1) × [(h2 - h1) / (v2 - v1)]. For example, v1 is 2 mm / s, v2 is 10 mm / s, h1 is 0.2, h2 is 3, and the slope of the pressurization multiple is (h2 - h1) / (v2 - v1) = 2.8 / 8 = 0.35, then h = 0.2 + (v - 2) × 2.8 / 8 = 0.2 + 0.35(v - 2).

[0053] This on-demand adjustment method enables the air pressure output to be precisely matched with the movement speed, which not only meets the power requirements under different working conditions but also optimizes the overall energy efficiency performance. Especially in an automated production line that requires variable-speed movement, this control method can adapt to speed changes in real time, always maintain the best air pressure assistance effect, effectively improve the system response speed and stability, and at the same time reduce the operating load of the servo motor.

[0054] Figure 7 The following shows a schematic diagram of the method steps for controlling the pressure relief opening according to the real-time descending speed. In one embodiment, as Figure 7 shown, the second air storage tank 4 is provided with a second pressure relief valve 401. When the lifting cylinder 5 is in the commanded descending working condition, step 140 includes: Step 141, obtain the real-time descending speed of the commanded descending working condition.

[0055] Step 142, if the air pressure in the second air storage tank 4 exceeds the third set pressure range, open the second pressure relief valve 401.

[0056] Step 143, match the second opening degree of the second pressure relief valve 401 according to the real-time descending speed, and the second opening degree is inversely proportional to the real-time descending speed.

[0057] Step 144, if the air pressure in the second air storage tank 4 returns to the third set pressure range, close the second pressure relief valve 401.

[0058] In this embodiment, when the lifting cylinder 5 descends, the lifting rod returns a small amount of gas to the second air storage tank 4. The faster the real-time descending speed, the faster the retraction speed of the lifting cylinder 5. At this time, a smaller second opening degree corresponds to a smaller air pressure discharge amount in the second air storage tank 4, and the second air storage tank 4 with a slower air pressure reduction can slow down the retraction of the lifting rod to a certain extent, thereby slowing down the real-time descending speed, playing a better linear buffering role. It can avoid the air pressure in the second air storage tank 4 dropping too fast and insufficient support for the lifting rod, which may accelerate the real-time descending speed of the lifting cylinder 5.

[0059] Preset the inverse relationship between the real-time descending speed a and the second opening degree d. For example, the minimum descending speed that the lifting platform can reach is a1, the maximum descending speed is a2, the minimum opening degree that the electronic control pressure boosting valve can reach is d1, and the maximum opening degree is d2. Then d = m + k / a, where the coefficient k = a1a2(d2 - d1) / (a2 - a1), and m = d2 - k / a1. The inverse mapping formula can be obtained as follows: d = a1a2(d2 - d1) / a(a2 - a1) + (a1d2 - a2d1) / (a1 - a2).

[0060] Verify the above formula with an example: The range of the descending speed a is 3 mm / s to 10 mm / s, and the range of the second opening degree d is 0.1 to 1. k = 27 / 7, m = -2 / 7. Substituting into the above inverse mapping formula, we get d = 27 / 7 / a - 2 / 7. When a is 3 mm / s, d ≈ 1; when a is 10 mm / s, d is approximately equal to 0.1.

[0061] This embodiment significantly improves the motion smoothness of the lifting cylinder during the descending process by introducing a speed-adaptive pressure relief control mechanism. When the system detects the descending working condition, it will monitor the current real-time descending speed in real time and intelligently adjust the opening degree of the second pressure relief valve accordingly. When the real-time descending speed increases, the system automatically reduces the opening degree of the pressure relief valve to slow down the real-time descending speed of the air pressure in the second air storage tank 4, thereby generating a greater buffering resistance to effectively suppress the excessive descent. Conversely, when the speed decreases, the opening degree can be increased to increase the pressure relief speed and thus return to the third set pressure range faster. This dynamic adjustment achieves an accurate match between the air pressure buffering force and the real-time descending speed, forming a closed-loop control effect. This embodiment utilizes the physical property of the backpressure gas of the lifting rod and adjusts the system damping by controlling the pressure relief speed to achieve a softer linear deceleration effect. In practical applications, this intelligent buffering mechanism can effectively prevent the impact vibration during heavy-load descent, protect the safety of the equipment, and at the same time reduce the braking load of the servo motor and extend the service life of the transmission system. It enables the lifting mechanism to maintain an ideal descending curve under different load conditions, significantly improving the operation quality and reliability of the equipment.

[0062] In one embodiment, the first air storage tank 2 is provided with a first drain valve 206, and the second air storage tank 4 is provided with a second drain valve 406. The control method for storing and supplying air for the cylinder includes: Step 160: Regularly open the first drain valve 206 and the second drain valve 406 to perform the drainage work.

[0063] This embodiment effectively addresses the common problem of moisture accumulation in pneumatic systems by providing a timed drainage function. The system automatically and periodically opens the drain valves of the first and second air tanks to promptly drain any condensed moisture from the compressed air. This timed drainage mechanism prevents long-term retention of moisture within the air tanks, thereby avoiding problems such as pipe corrosion and valve sticking. This significantly increases the service life and reliability of pneumatic components and prevents fluctuations in the power assist effect caused by moisture. Specifically, step 160 has no logical precedence relationship with steps 110 through 150 and can be executed during or before or after the execution of any of the steps.

[0064] Figure 8 The figure shows the pressure control steps during abnormal descent. Figure 8 As shown, the gas storage and delivery control method for the cylinder also includes: Step 170: When the lifting cylinder 5 is in an abnormal descending condition, the boosting assembly 3 is controlled to connect the first air tank 2 and the second air tank 4 and perform boosting, so that the pressure in the second air tank 4 is maintained within a fourth set pressure range, and the second air tank 4 is controlled to connect with the lifting cylinder 5.

[0065] In this embodiment, the fourth set pressure range is greater than or equal to the second set pressure range, and the real-time descent speed corresponding to the abnormal descent condition is greater than the real-time descent speed corresponding to the commanded descent condition, or the amplitude of the real-time descent speed corresponding to the abnormal descent condition within a unit reference time period is greater than the preset speed amplitude. When applied, this embodiment introduces an active air pressure compensation mechanism for abnormal conditions, significantly enhancing the system's safety protection capabilities. When an abnormal increase or sharp fluctuation in the real-time descent speed is detected, the system immediately initiates an emergency response procedure, rapidly replenishing high-pressure gas to the second air tank via the booster assembly to maintain the pressure within the higher fourth set pressure range. This active boost compensation provides additional support for the lift cylinder in emergency situations, effectively suppressing uncontrolled descent. Compared to conventional passive buffering methods, this design offers faster response and stronger braking force, allowing it to quickly stabilize abnormal motion conditions. In particular, in emergency situations such as sudden load changes or mechanical failures, this mechanism can buy the system valuable reaction time, preventing equipment damage or safety accidents. Furthermore, by setting the fourth pressure range to no less than the normal operating pressure (which is defined as the second set pressure range), sufficient buffering force is ensured even under abnormal conditions. This intelligent safety protection design not only retains the energy-saving advantages of the original system, but also significantly enhances the reliability and safety of the equipment, providing double protection for the automated production line.

[0066] Figure 9 The figure shows the pressure control steps during fine-tuning operation. Figure 2As shown, the second air storage tank 4 is provided with a second pressure relief valve 401. As Figure 9 shown, the air storage and supply control method for the cylinder further includes: When the lifting cylinder 5 is in the fine-tuning working condition, perform step 180, control the boosting assembly 3 and the second pressure relief valve 401 to work together, and keep the second air storage tank 4 within the fifth set pressure range. In this step, the fifth set pressure range is less than the second set pressure range.

[0067] Step 190, close the boosting assembly 3.

[0068] Step 200, control the second air storage tank 4 to communicate with the lifting cylinder 5.

[0069] In the application of this embodiment, a precise pressure control mechanism in the fine-tuning working condition is introduced, which significantly improves the control performance of the system during precision operations. When the lifting cylinder enters the fine adjustment working condition, the system will start a special pressure management mode: by jointly controlling the boosting assembly and the second pressure relief valve, the pressure of the second air storage tank is stabilized within the fifth set range lower than the normal working pressure. This low-pressure holding mode can provide a softer buffer thrust support for the lifting cylinder, provide a certain supporting force for the lifting cylinder to perform fine-tuning lifting. Ensure that the pressure of the system is stable within the fifth set pressure range during the fine-tuning working condition, close the boosting assembly 3 when reaching the second set pressure range, and keep the air path between the second air storage tank 4 and the lifting cylinder 5 connected. This control method is particularly suitable for operation scenarios that require high-precision positioning, such as precision assembly or inspection stations, and can effectively eliminate the "crawling" or "jitter" phenomena that are prone to occur during fine-tuning of traditional pneumatic systems. By reducing the working pressure, the system obtains smoother motion characteristics and finer control resolution, while reducing energy consumption and equipment wear.

[0070] Figure 10 It is a schematic diagram of the air pressure control steps for the second air storage tank during the fine-tuning working condition. In one embodiment, as Figure 10 shown, when the lifting cylinder 5 is in the fine-tuning working condition, step 180 includes: Step 181, when the lifting cylinder 5 is in the fine-tuning working condition, detect the air pressure of the second air storage tank 4.

[0071] Step 182, if the air pressure of the second air storage tank 4 is less than the fifth set pressure range, control the second pressure relief valve 401 to close, and control the boosting assembly 3 to connect the first air storage tank 2 and the second air storage tank 4 and perform boosting until the second air storage tank 4 reaches the fifth set pressure range.

[0072] Step 183, if the air pressure of the second air storage tank 4 is greater than the fifth set pressure range, control the boosting assembly 3 to close, and control the second pressure relief valve 401 to open until the second air storage tank 4 reaches the fifth set pressure range.

[0073] When this embodiment is applied, through the closed-loop control of real-time air pressure detection and dynamic adjustment, pressure regulation is carried out under the fine-tuning working condition. When the detected pressure is lower than the fifth set range, the pressure relief valve is immediately closed and the pressurization component is started to perform precise pressure compensation; when the pressure is too high, the pressurization component is closed and the pressure relief valve is opened for appropriate discharge. This two-way adjustment mechanism ensures that the pressure in the second gas storage tank is always stable in the low-pressure range most suitable for fine-tuning operations, providing just the right flexible driving force for the lifting cylinder. Compared with the conventional single pressure control, this design has three prominent advantages: First, the problem of pressure fluctuation existing in the traditional system is eliminated through real-time feedback adjustment, making the fine-tuning action smoother and more precise; second, the low-pressure working mode greatly reduces the inertial effect of the cylinder movement, effectively avoiding overshoot during precise positioning; finally, the intelligent switching of the pressurization and pressure relief functions realizes the precise delivery of energy, avoiding unnecessary energy consumption. This refined pressure management is especially suitable for applications in scenarios with strict requirements for positioning accuracy, such as precision instrument assembly or high-precision detection processes. It can improve the control accuracy of the pneumatic system to a new level and extend the service life of pneumatic components at the same time. The entire control process responds quickly and adjusts delicately, enabling the equipment to maintain sufficient action sensitivity under the fine-tuning working condition and achieve sub-millimeter positioning accuracy.

[0074] An exemplary air storage and air supply control system for a cylinder is as follows: Figure 11 The system structure diagram of the air storage and air supply control system for a cylinder is shown. The present application also provides an air storage and air supply control system for a cylinder, which is applied to the air supply device of a lifting cylinder that assists a lifting servo motor. The air supply device of the lifting cylinder includes a gas source 1, a first gas storage tank 2, a pressurization component 3, and a second gas storage tank 4 connected in sequence. The second gas storage tank 4 is connected to the lifting cylinder 5, as Figure 11 shown. The air storage and air supply control system for a cylinder includes: a first gas storage tank air pressure control module 1101, a rising control module 1102, a descending control module 1103, and a shutdown module 1104.

[0075] The first gas storage tank air pressure control module 1101 is configured to: control the gas source 1 to input gas into the first gas storage tank 2 until it reaches the first set pressure range.

[0076] The rising control module 1102 is configured to: when the lifting cylinder 5 is in the command rising working condition, control the pressurization component 3 to connect the first gas storage tank 2 and the second gas storage tank 4 and perform pressurization until the second gas storage tank 4 reaches the second set pressure range, and control the second gas storage tank 4 to be connected to the lifting cylinder 5.

[0077] The descending control module 1103 is configured to: when the lifting cylinder 5 is in the commanded descending working condition, control the second gas storage tank 4 to communicate with the lifting cylinder 5, control the second gas storage tank 4 to release pressure to the third pressure setting range, and control the booster assembly 3 to close and monitor the air pressure of the second gas storage tank 4; when the lifting cylinder 5 is in the commanded descending working condition, if the air pressure of the second gas storage tank 4 exceeds the third set pressure range, perform pressure relief until it returns to the third set pressure range.

[0078] The shutdown module 1104 is configured to: if the lifting cylinder 5 stops working for more than the first preset duration, control the booster assembly 3 to close and control the second gas storage tank 4 to disconnect from the lifting cylinder 5.

[0079] The gas storage and supply control method provided in this embodiment realizes precise air pressure management of the lifting cylinder through the coordinated control of the multi-stage gas storage tank and the booster assembly. In the ascending working condition, the gas pressure is boosted by the booster assembly 3 and then delivered to the second gas storage tank 4 to provide thrust for the lifting cylinder 5, significantly reducing the driving load of the servo motor in the ascending stage. In the descending working condition, the pressurized gas in the second gas storage tank 4 is used to apply a controllable thrust to the lifting rod to buffer the descending impact and at the same time reduce the load of the servo motor during descending. Dynamically and automatically switch the pressure range according to the ascending / descending working condition, with high-pressure assistance (the second set pressure range) during ascending and pressure relief to a lower pressure (the third set pressure range) during descending to play a buffering role. Monitor and relieve pressure in real time to ensure that the air pressure is stable within the third set range during descending and prevent the descending resistance caused by overpressure. Automatically disconnect the gas path and maintain pressure during dormancy to reduce energy consumption, while retaining the air pressure reserve for quick activation next time.

[0080] The basic principles of the present application have been described above in conjunction with specific embodiments. However, it should be noted that the advantages, advantages, effects, etc. mentioned in the present application are only examples and not limitations, and it cannot be considered that these advantages, advantages, effects, etc. are essential for each embodiment of the present application. In addition, the above-disclosed specific details are only for the purpose of illustration and easy understanding, rather than limitations, and these details do not limit the present application to necessarily adopt the above specific details to implement.

[0081] The block diagrams of the devices, apparatuses, equipment, and systems involved in the present application are only illustrative examples and do not intend to require or imply that they must be connected, arranged, and configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, equipment, and systems can be connected, arranged, and configured in any manner. Words such as "including", "comprising", "having", etc. are open-ended words, meaning "including but not limited to", and can be used interchangeably with each other. The words "or" and "and" used herein refer to the word "and / or" and can be used interchangeably with each other, unless the context clearly indicates otherwise. The word "such as" used herein refers to the phrase "such as but not limited to" and can be used interchangeably with each other.

[0082] It should also be noted that in the devices, equipment and methods of the present application, each component or each step can be decomposed and / or recombined. These decompositions and / or recombinations shall be regarded as equivalent solutions of the present application.

[0083] The above description of the disclosed aspects is provided to enable any person skilled in the art to make or use the present application. Various modifications to these aspects will be readily apparent to those skilled in the art, and the general principles defined herein can be applied to other aspects without departing from the scope of the present application. Therefore, the present application is not intended to be limited to the aspects shown herein, but to be accorded the widest scope consistent with the principles and novel features disclosed herein.

[0084] The above are only the preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, etc. made within the spirit and principles of the present application shall be included within the protection scope of the present application.

Claims

1. A gas storage and supply control method for a cylinder, which is applied to a lifting cylinder air supply device of an auxiliary lifting servo motor. The lifting cylinder air supply device includes an air source, a first gas storage tank, a boosting component, and a second gas storage tank that are connected in sequence. The second gas storage tank is connected to the lifting cylinder, and is characterized in that, The method includes: Controlling the gas source to input gas into the first gas storage tank until it reaches the first set pressure range; When the lifting cylinder is in the commanded rising working condition, controlling the boosting component to connect the first gas storage tank and the second gas storage tank and perform boosting until the second gas storage tank reaches the second set pressure range, and controlling the second gas storage tank to be connected to the lifting cylinder; When the lifting cylinder is in the commanded descending working condition, controlling the second gas storage tank to be connected to the lifting cylinder, controlling the second gas storage tank to relieve pressure to the third pressure set range, and controlling the boosting component to close and monitor the air pressure of the second gas storage tank; When the lifting cylinder is in the commanded descending working condition, if the air pressure of the second gas storage tank exceeds the third set pressure range, then perform pressure relief until it returns to the third set pressure range; and If the lifting cylinder stops working for more than the first preset duration, then control the boosting component to close and control the second gas storage tank to be disconnected from the lifting cylinder.

2. The air storage and supply control method for a cylinder according to claim 1, characterized in that, The step of, when the lifting cylinder is in the commanded rising working condition, controlling the boosting component to connect the first gas storage tank and the second gas storage tank and perform boosting until the second gas storage tank reaches the second set pressure range, and controlling the second gas storage tank to be connected to the lifting cylinder includes: Obtaining a rising command and obtaining the corresponding rising stroke according to the rising command; If the rising stroke is less than or equal to the first stroke, then control the boosting component to perform boosting at the first boosting multiple; If the rising stroke is greater than the first stroke and less than or equal to the second stroke, then control the boosting component to perform boosting at the second boosting multiple; and If the rising stroke is greater than the second stroke, then control the boosting component to perform boosting at the third boosting multiple; Wherein, the second stroke is greater than the first stroke, the third boosting multiple is greater than the second boosting multiple, and the second boosting multiple is greater than the first boosting multiple.

3. The air storage and supply control method for a cylinder according to claim 1, characterized in that It further includes: When the lifting cylinder is in the commanded rising working condition: if the air pressure in the first gas storage tank drops to the fourth set pressure range, then monitor the change in the air pressure of the second gas storage tank during the boosting process of the boosting component; if the decrease amplitude of the second gas storage tank is greater than the preset amplitude, then control the boosting component to increase the boosting ratio; And controlling to increase the input rate of the gas input by the gas source into the first gas storage tank; Wherein, the fourth set pressure range is less than the first set pressure range.

4. The air storage and supply control method for a cylinder according to claim 1, wherein The step of, when the lifting cylinder is in the commanded rising working condition, controlling the boosting component to connect the first gas storage tank and the second gas storage tank and perform boosting until the second gas storage tank reaches the second set pressure range, and controlling the second gas storage tank to be connected to the lifting cylinder includes: Obtaining the corresponding real-time rising speed according to the rising command in the commanded rising working condition; and Matching the corresponding boosting ratio according to the real-time rising speed, and controlling the boosting component to perform boosting according to the boosting ratio; wherein, the boosting ratio is proportional to the real-time rising speed.

5. The air storage and supply control method for a cylinder according to claim 1, characterized in that, The second gas storage tank is provided with a second pressure relief valve; When the lifting cylinder is in the commanded descending working condition, if the air pressure in the second air storage tank exceeds the third set pressure range, then perform pressure relief until it returns to the third set pressure range, including: Obtain the real-time descending speed of the commanded descending working condition; If the air pressure in the second air storage tank exceeds the third set pressure range, then open the second pressure relief valve; Match the second opening degree of the second pressure relief valve according to the real-time descending speed, and the second opening degree is inversely proportional to the real-time descending speed; and If the air pressure in the second air storage tank returns to the third set pressure range, then close the second pressure relief valve.

6. The air storage and supply control method for a cylinder according to claim 1, characterized in that, The first air storage tank is provided with a first drain valve, and the second air storage tank is provided with a second drain valve; This air storage and air supply control method for the cylinder further includes: Regularly open the first drain valve and the second drain valve to perform drainage work.

7. The air storage and supply control method for a cylinder according to claim 1, wherein It further includes: When the lifting cylinder is in an abnormal descending working condition, control the pressurizing component to connect the first air storage tank and the second air storage tank and perform pressurization, so that the inside of the second air storage tank is maintained within the fourth set pressure range, and control the second air storage tank to communicate with the lifting cylinder; Wherein, the fourth set pressure range is greater than or equal to the second set pressure range, the real-time descending speed corresponding to the abnormal descending working condition is greater than the real-time descending speed corresponding to the commanded descending working condition, or the change amplitude of the real-time descending speed corresponding to the abnormal descending working condition within the unit reference time period is greater than the preset speed change amplitude.

8. The air storage and supply control method for a cylinder according to claim 1, characterized in that The second air storage tank is provided with a second pressure relief valve; This air storage and air supply control method for the cylinder further includes: When the lifting cylinder is in the fine-tuning working condition, control the pressurizing component and the second pressure relief valve to work together to keep the inside of the second air storage tank within the fifth set pressure range; the fifth set pressure range is less than the second set pressure range; Close the pressurizing component; and Control the second air storage tank to communicate with the lifting cylinder.

9. The air storage and supply control method for a cylinder according to claim 8, wherein When the lifting cylinder is in the fine-tuning working condition, control the pressurizing component and the second pressure relief valve to work together to keep the inside of the second air storage tank within the fifth set pressure range, including: When the lifting cylinder is in the fine-tuning working condition, detect the air pressure in the second air storage tank; If the air pressure in the second air storage tank is less than the fifth set pressure range, control the second pressure relief valve to close, and control the pressurizing component to connect the first air storage tank and the second air storage tank and perform pressurization until the inside of the second air storage tank reaches the fifth set pressure range; If the air pressure in the second air storage tank is greater than the fifth set pressure range, control the pressurizing component to close, and control the second pressure relief valve to open until the inside of the second air storage tank reaches the fifth set pressure range.

10. A gas storage and supply control system for a cylinder, which is applied to an air supply device for a lifting cylinder of an auxiliary lifting servo motor. The lifting cylinder air supply device includes an air source, a first gas storage tank, a pressurization assembly, and a second gas storage tank that are connected in sequence. The second gas storage tank is connected to the lifting cylinder, and is characterized in that, The system includes: A first air storage tank air pressure control module, configured to: control the air source to input gas into the first air storage tank until it reaches the first set pressure range; The rising control module is configured to: when the lifting cylinder is in the commanded rising working condition, control the pressurizing assembly to connect the first air storage tank and the second air storage tank and perform pressurization until the pressure in the second air storage tank reaches the second set pressure range, and control the second air storage tank to be connected to the lifting cylinder; The descending control module is configured to: when the lifting cylinder is in the commanded descending working condition, control the second air storage tank to be connected to the lifting cylinder, control the second air storage tank to release pressure to the third pressure set range, and control the pressurizing assembly to close and monitor the air pressure in the second air storage tank; when the lifting cylinder is in the commanded descending working condition, if the air pressure in the second air storage tank exceeds the third set pressure range, perform pressure release until it returns to the third set pressure range; and The shutdown module is configured to: if the lifting cylinder stops working for more than the first preset duration, control the pressurizing assembly to close and control the second air storage tank to be disconnected from the lifting cylinder.

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