Synchronous hydraulic system and hydraulic synchronous calibration method

Abstract

The present application belongs to the technical field of high-pressure and large-flow hydraulic components and hydraulic systems, and relates to a theoretical model and practical application of a fluid pressure actuator, and the technical points are to control the fluid supply on the backflow path by using a speed reduction valve to control the action of a servo hydraulic cylinder; in particular, a synchronous hydraulic system and a hydraulic synchronous calibration method are provided, and the hydraulic system with adjustable backflow speed of the present application can push a product and make the product return at a uniform and stable speed when the product is reset, and is especially suitable for lifting control of a product driven by an oil cylinder with a large counterweight and a set distance. The working principle of the present application is to add a speed reduction valve to the circuit of the hydraulic cylinder, the speed reduction valve adjusts the relative position of the valve core through a screw, changes the size of the oil flow through the hole, adjusts the oil flow rate, changes the oil return flow rate of the corresponding oil cylinder, and controls the synchronous action of all the oil cylinders. The non-magnetic characteristic of the present application is especially suitable for high-precision environments such as medical treatment.

Description

Technical Field

[0001] This invention relates to the field of high-pressure, high-flow hydraulic components and hydraulic systems, and in particular to a synchronous hydraulic system and a hydraulic synchronization calibration method. Background Technology

[0002] High-pressure, high-flow hydraulic components are a type of fluid pressure actuator, typically used in real-world applications. Unlike small lifting and other power structures used in laboratories, products using high-pressure, high-flow hydraulic components in real-world applications are usually large in size and weight. In certain situations, it may be necessary to arrange two or more high-pressure, high-flow hydraulic components around the large product based on the location of the product's stress points.

[0003] This type of lifting operation with multiple components places high demands on the synchronization of all components. If any component fails to move synchronously, it will cause the overall product movement to become sluggish, affecting normal operation. In some cases, it may even cause the equipment to break down while other components are still applying force. Summary of the Invention

[0004] To address the shortcomings of existing production technologies, the applicant provides a synchronous hydraulic system and a hydraulic synchronization calibration method that can precisely control the return oil flow rate of each high-pressure, high-flow hydraulic component, ensuring that all high-pressure, high-flow hydraulic components return at the same speed. In terms of the product, this ensures a uniform and reliable reset.

[0005] The technical solution adopted in this invention is as follows:

[0006] A synchronous hydraulic system includes multiple independent hydraulic cylinders. Each hydraulic cylinder has a deceleration valve connected to its return oil line, and the return oil flow rate of each deceleration valve is adjustable. Each deceleration valve adjusts the return oil flow rate of its own return oil line to synchronize the retraction action of all hydraulic cylinders. The adjustment structure includes a coarse adjustment structure and a micro-adjustment structure that are detachable from each other.

[0007] As a further improvement to the above technical solution:

[0008] The system includes a frame, on which a control box and at least two hydraulic cylinders are mounted, with the hydraulic circuits of all hydraulic cylinders converging into the control box.

[0009] The control box contains:

[0010] The hydraulic circuits for all hydraulic cylinders are integrated within the control box.

[0011] The deceleration valve is an independent deceleration valve on the return oil line of each hydraulic cylinder. The deceleration valve includes a housing and a hollow valve core. The housing is also equipped with a screw for pushing the valve core. The housing and the valve core are respectively provided with through holes that allow oil to flow through.

[0012] The coaxiality of the through holes on the housing and valve core affects the return oil flow rate.

[0013] The housing includes:

[0014] The positioning housing is fixed inside the control box.

[0015] The oil outlet housing is nested and sealed with the positioning housing. An oil outlet through-hole is provided on the oil outlet housing.

[0016] The screw extends into the positioning housing, pushing the valve core to move; the valve core moves within the oil outlet housing.

[0017] The knob includes a coarse adjustment section and a differential screw fine adjustment section that is detachably connected to the coarse adjustment section.

[0018] The coarse adjustment section is constantly inserted into the positioning housing; the differential screw fine adjustment section is equipped with a positioning screw sleeve, which is sleeved with the outer wall of the housing. The differential screw fine adjustment section, the coarse adjustment section, the positioning screw sleeve, and the housing constitute a micro-propulsion structure.

[0019] An elastic element connects the valve core and the screw, and the axial displacement of the screw is buffered by the elastic element before acting on the valve core.

[0020] Alternatively, an elastic element can be installed on the side of the valve core away from the screw knob, so that the screw knob abuts and pushes the valve core.

[0021] The valve core and the screw knob are both formed with steps at opposite ends, and the elastic element is sleeved on the steps at both ends.

[0022] A first through hole is made on the valve core, and a second through hole is made on the housing.

[0023] The first through hole is a tapered hole, with the oil outlet end of the first through hole being the smaller end; the second through hole is a stepped hole, with the oil outlet diameter of the second through hole being larger than the larger end diameter of the first through hole.

[0024] Each hydraulic cylinder is equipped with a counterweight.

[0025] The housing is equipped with a mounting position to accommodate the hydraulic cylinder. The top of the mounting position is provided with a flip cover plate, which limits the position of the top of the hydraulic cylinder.

[0026] A hydraulic synchronization calibration method utilizing a synchronous hydraulic system includes the following steps:

[0027] After adding counterweights to the hydraulic cylinders, the control box controls the lifting of all hydraulic cylinders on the frame, and the hydraulic cylinders reset and fall back down, thus obtaining the fall speed of each hydraulic cylinder before adjustment.

[0028] Based on the difference in the return speed of each hydraulic cylinder, adjust the knob of each hydraulic cylinder individually until the return speed of all hydraulic cylinders is the same. At this point, the return oil flow rate controlled by the deceleration valve of each hydraulic cylinder per unit time may be the same or different.

[0029] Under the same working conditions, lock the deceleration valve screw knob of each hydraulic cylinder to ensure that all hydraulic cylinders lift and lower synchronously.

[0030] The beneficial effects of this invention are as follows:

[0031] The present invention provides a synchronous hydraulic system and a hydraulic synchronization calibration method. The key technical point is that the fluid supply on the return path is controlled by a deceleration valve to control the action of the servo hydraulic cylinder. It is applicable to the synchronous return oil reset of multiple high-pressure and high-flow hydraulic cylinders, and is especially suitable for the lifting control of multi-cylinder driven products with large counterweights.

[0032] This invention adds a deceleration valve to the oil cylinder circuit. By rotating the screw built into the deceleration valve, the relative position of the valve core is adjusted, the size of the oil flow through the orifice is changed, thereby adjusting the oil flow rate and changing the return oil flow rate of the corresponding oil cylinder, thus controlling the descent action of all oil cylinders to be synchronized.

[0033] Furthermore, this invention also provides an optimized solution, namely, adding a threaded sleeve to the original conventional structure, transforming the conventional structure into a micro-propulsion structure, further controlling the flow rate for fine-tuning. It also possesses the ability to retract the valve core during reverse rotation and to be reciprocated for adjustment.

[0034] This invention does not contain any magnetic devices such as motors, and the overall system has non-magnetic characteristics, making it particularly suitable for high-precision environments such as medical settings.

[0035] The system provided by this invention allows for a maximum distance of 3m between adjacent hydraulic cylinders. If conventional hydraulic cylinders are used for lifting, the height difference caused by the asynchronous operation at both ends can lead to jamming of large and heavy products. The synchronous hydraulic system of this invention can effectively ensure that the hydraulic cylinders at both ends or multiple ends are in a synchronous lifting state, which is especially suitable for lifting equipment products with large spacing or large size. Attached Figure Description

[0036] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0037] Figure 2 This is a bottom view of the overall structure of the present invention.

[0038] Figure 3 This is a schematic diagram showing the location of the synchronous control box of the present invention. One side of the swing arm is hidden in the diagram. The deceleration valve port of the return oil line is exposed.

[0039] Figure 4 This is a cross-sectional view of the synchronous control box of the present invention, with the cross-section located at the deceleration valve.

[0040] Figure 5 for Figure 4The enlarged view of section A is used to show the deceleration valve and its internal structure. The arrows in the view indicate the direction of oil flow.

[0041] Figure 6 This is a schematic diagram of the differential screw propulsion structure.

[0042] The components include: 1. Frame; 2. Hydraulic cylinder; 3. Counterweight; 4. Control box; 5. Deceleration valve; 6. Guide wheel assembly.

[0043] 501. Positioning housing; 502. Oil outlet housing; 503. Valve core; 504. Oil inlet channel; 505. First through hole; 506. Second through hole; 507. Screw knob; 508. Spring; 509. Screw sleeve. Detailed Implementation

[0044] The specific embodiments of the present invention will now be described with reference to the accompanying drawings.

[0045] like Figures 1-5 As shown, the synchronous hydraulic system of this embodiment includes multiple independent hydraulic cylinders. Each hydraulic cylinder has a deceleration valve 5 connected to its return oil line. The return oil flow of each deceleration valve 5 is adjustable. Each deceleration valve 5 adjusts the return oil flow of its own return oil line to synchronize the descent action of all hydraulic cylinders.

[0046] The system includes a frame 1, on which a control box 4 and at least two hydraulic cylinders are mounted. The oil circuits of all hydraulic cylinders converge into the control box 4.

[0047] Control box 4 contains:

[0048] The hydraulic circuits for all hydraulic cylinders are integrated within control box 4.

[0049] The deceleration valve 5 is an independent deceleration valve 5 on the return oil line of each hydraulic cylinder. The deceleration valve 5 includes a housing and a hollow valve core 503. A screw 507 for pushing the valve core 503 is also provided on the housing. Through holes that allow oil to flow are opened on the housing and the valve core 503 respectively.

[0050] The coaxiality of the through holes on the housing and valve core 503 affects the return oil flow rate.

[0051] The housing includes:

[0052] Positioning housing 501 is fixedly located inside control box 4.

[0053] The oil outlet housing 502 is nested and sealed with the positioning housing 501, and the oil outlet housing 502 has a through hole for oil outlet.

[0054] The screw 507 extends into the positioning housing 501, pushing the valve core 503 to move; the valve core 503 is displaced in the oil outlet housing 502.

[0055] An elastic element connects the valve core 503 and the screw 507. The axial displacement of the screw 507 is buffered by the elastic element and then acts on the valve core 503.

[0056] The valve core 503 and the screw knob 507 are both formed with steps at opposite ends, and the elastic element is sleeved on the steps at both ends.

[0057] A first through hole 505 is provided on the valve core 503, and a second through hole 506 is provided on the housing.

[0058] The first through hole 505 is a tapered hole, and the oil outlet end of the first through hole 505 is the small end; the second through hole 506 is a stepped hole, and the diameter of the oil outlet end of the second through hole 506 is larger than the diameter of the large end of the first through hole 505.

[0059] Each hydraulic cylinder is equipped with a counterweight of 3.

[0060] The housing is equipped with a mounting position to accommodate the hydraulic cylinder. The top of the mounting position is provided with a flip cover plate, which limits the position of the top of the hydraulic cylinder.

[0061] The hydraulic synchronization calibration method using a synchronous hydraulic system in this embodiment includes the following steps:

[0062] After adding counterweight 3 to the hydraulic cylinders, the control box 4 controls all the hydraulic cylinders on the frame 1 to rise, and then the hydraulic cylinders reset and fall back down, thus obtaining the fall speed of each hydraulic cylinder before adjustment.

[0063] Based on the difference in the retraction speed of each hydraulic cylinder, adjust the screw knob 507 of each hydraulic cylinder until the retraction speed of all hydraulic cylinders is the same. At this point, the return oil flow rate controlled by the deceleration valve 5 of all hydraulic cylinders per unit time may be the same or different.

[0064] Under the same working conditions, lock the deceleration valve 5 screw knob 507 of each hydraulic cylinder to ensure that all hydraulic cylinders lift and lower synchronously.

[0065] The specific structure and working principle of this invention are as follows:

[0066] The purpose of this invention is to provide a high-pressure, high-flow hydraulic system in which multiple high-pressure, high-flow hydraulic components maintain synchronous lifting and lowering. The key technical point is to add a deceleration valve 5 to the return oil line of each high-pressure, high-flow hydraulic component. The return oil flow rate of each high-pressure, high-flow hydraulic component may not be equal; the ultimate goal is to adjust the return oil flow rate to make the reset speed of all components equal.

[0067] Since the lifting state of all components must be synchronized, the technical problem is that when different cylinders 2 return oil and fall, due to the different operating conditions of each cylinder 2 and the different degrees of friction of the oil seals, they may not be able to descend synchronously. Therefore, this invention only improves the oil return process.

[0068] The following section uses two hydraulic cylinders 2 as an example to explain in detail the principle of oil return flow rate control of the present invention.

[0069] Example 1

[0070] like Figure 1 and Figure 2 The diagram illustrates one design example of the present invention. Two hydraulic cylinders 2 to be synchronized are mounted on a frame 1, along with a control box 4. The control box 4 used in this invention adds a deceleration valve 5 to the conventional control box 4, located on the return oil line. Each hydraulic cylinder 2 has a separate deceleration valve 5 on its return oil line. In this embodiment, the deceleration valve 5 can only be a manual deceleration valve because the electromagnetic force emitted by the proportional electromagnet in an electric deceleration valve would affect the non-magnetic environment used in medical applications.

[0071] like Figure 3 and Figure 4 As shown, the deceleration valve 5 is built into the control box 4, in conjunction with the reference. Figure 5 It can be seen that the deceleration valve 5 includes a valve body shell, a valve core 503 built into the shell, and a screw 507 for pushing the valve core 503. Both the valve core 503 and the valve body shell have through holes. The first through hole 505 is opened on the valve core 503, and the second through hole 506 is opened on the oil outlet shell 502. When the valve core 503 moves to the coaxial position of the two through holes, the return oil flow rate is the maximum. During the movement of the valve core 503, the degree of eccentricity of the two through holes affects the oil flowing out per unit time, that is, it affects the return oil flow rate.

[0072] like Figure 5 As shown, the valve body shell is composed of two sections joined together, with each section sealed to the wall of the control box 4. The two sections are the oil outlet shell 502 and the positioning shell 501. The oil outlet shell 502 is coaxially embedded within the positioning shell 501, and an oil outlet hole is provided on the outer wall of the oil outlet shell 502. The oil outlet hole is never obstructed by the positioning shell 501, ensuring that the return oil flow rate is only affected by the single factor of the valve core 503's movement.

[0073] The design of the two-section housing is also based on the fact that the spliced ​​structure can provide a longer deformation path for the spring 508 and screw while reducing material costs, making it easier to fine-tune the oil flow rate and increase the adjustment range.

[0074] A valve core 503 is movably disposed inside the oil outlet housing 502. One end of the valve core 503 extends into the positioning housing 501 and has an oil inlet channel 504 coaxially formed. A first through hole 505 is formed in the circumferential array of the valve core 503. The oil inlet channel 504 and the through hole on the valve core 503 are both connected to the hollow inner cavity of the valve core 503.

[0075] An elastic element is fitted onto the oil inlet channel 504 of the valve core 503. In this embodiment, the elastic element is a spring 508. One end of the spring 508 abuts against the end of the screw 507 that extends into the positioning housing 501, and the other end of the spring 508 abuts against the oil inlet channel 504 of the valve core 503. When the screw 507 is rotated, the axial relative position between the screw 507 and the positioning housing 501 changes. For example, when the screw 507 gradually penetrates into the positioning housing 501, it pushes the spring 508. The spring 508 buffers the thrust of the screw 507 and transforms it into a smaller, more precise forward thrust, finely adjusting the movement distance of the valve core 503, thereby achieving a slow and high-precision adjustment of the relative position between the first through hole 505 and the second through hole 506. Generally, after gradually rotating the screw 507 in and adjusting the oil flow rate until the return oil speed of all cylinders 2 is the same, the screw 507 can be locked to ensure that all cylinders 2 of the equipment rise and fall synchronously. Therefore, the reset of valve core 503 can be disregarded.

[0076] Furthermore, if the displacement range of the valve core 503 is large enough, when the first through hole 505 and the second through hole 506 are relatively displaced, the return oil flow gradually increases from a small value to a maximum value. That is, the flow is at its maximum when the first through hole 505 and the second through hole 506 are coaxial, and then gradually decreases. Therefore, under these conditions, unidirectional pushing of the valve core 503 can achieve the purpose of increasing or decreasing the return oil speed, and the problem of reverse reset of the valve core 503 does not need to be considered.

[0077] As a further optimization of the solution, the present invention also proposes a structure and method for resetting the valve core 503 when the screw knob 507 is rotated in the opposite direction.

[0078] When the valve core 503 is pushed forward, the oil flow rate increases. If the movement path length of the valve core 503 is insufficient to meet the requirement that the oil flow rate gradually increases and then decreases during the continuous pushing of the valve core 503, an elastic element, such as a spring, can be set at the end of the valve core 503 away from the screw button 507. In this way, when the screw button 507 rotates in the opposite direction, the valve core 503 can be reset.

[0079] It should be noted that each hydraulic cylinder 2 is equipped with a counterweight 3. The purpose of the counterweight 3 is to prevent problems such as vibration, abnormal noise, and pressure drop when the hydraulic cylinder 2 is unloaded. In addition, the counterweight 3 is also used to simulate the load during actual use in the later stage, so as to more accurately simulate and predict the load range that can be borne.

[0080] Example 2

[0081] Since manual adjustment is prone to errors, this embodiment proposes a structure to improve the accuracy of manual adjustment, so that the axial distance advanced by a single turn of the screw 507 is shorter during manual rotation, thereby achieving the purpose of fine adjustment.

[0082] like Figure 6 As shown, the specific structure is as follows: A differential screw propulsion structure is adopted. Based on the above embodiment 1, the original spring 508 is removed, and spring 510 is replaced by one located on the side of the valve core away from the screw knob. A threaded sleeve 509 is added and fitted onto the positioning housing 501. The threaded sleeve 509 passes through the differential screw fine-tuning section 510, which is a screw with different pitches. The center of the differential screw fine-tuning section 510 is concave and coaxially formed with an irregularly shaped column, such as a hexagonal prism, which matches the irregularly shaped hole, such as a hexagonal hole, on the end face of the coarse-tuning section. A magnet can also be added according to actual needs, allowing the coarse-tuning section and the differential screw fine-tuning section to connect and rotate simultaneously. The coarse-tuning section is the screw knob 507 in the aforementioned conventional structure.

[0083] Thus, the differential screw fine-tuning section 509, coarse-tuning section, screw sleeve 508, and positioning housing 501 form a new differential screw micro-propulsion mechanism. The combination of the differential screw fine-tuning section and coarse-tuning section is equivalent to a double-helix screw, the screw sleeve 508 and positioning housing 501 are equivalent to a base or fixed nut, and the valve core 503 is equivalent to a movable nut. When the hand-held part is rotated, the axial distance advanced by a single rotation is the product of the sum of the leads of the two screw sections and the number of screw rotations, which is less than the single-turn adjustment amount when using the coarse-tuning section alone, making it more conducive to precise adjustment.

[0084] As an alternative implementation, it can be used only in the following ways: Figure 5 In the indicated orientation, a spring is installed on the left side of the valve core 503, and a screw 507 is directly installed on the right side of the valve core 503. The screw 507 directly abuts against the valve core 503, pushing the valve core 503. In this way, when the screw 507 rotates forward and backward, the valve core 503 moves accordingly, allowing for adjustment of the oil outlet area to increase or decrease at any time.

[0085] The application scenarios of this application include: synchronous sliding and jacking of large components, heavy-load long-distance jacking construction, etc.

[0086] Scene 1

[0087] In applications such as medical beds and CT scanners, hydraulic cylinders 2 are installed at both the head and foot of the CT scanner. These two hydraulic cylinders 2 must be raised and lowered completely synchronously to achieve horizontal movement of the CT scanner. If the two hydraulic cylinders 2 are not synchronized, the CT scanner will no longer be in a horizontal plane, posing a safety hazard to the user and patient, and may also cause the CT scanner to jam and damage the equipment.

[0088] First, before the medical bed board is installed on top of the hydraulic cylinder lifting structure, start the hydraulic cylinder lifting and then allow it to fall naturally. Obtain the difference in the fall speed between the two sets of hydraulic cylinders. Based on this difference, calculate the difference in return oil flow rate between the two sets of hydraulic cylinders. If calculation is not used, a practical method is employed. Adjust the deceleration valve 5 on the return oil line with the faster fall speed. First, adjust the coarse adjustment section separately. When the return oil flow rates of the two return oil lines are close and the fall speeds of the two sets of hydraulic cylinders are similar, install the differential screw fine adjustment section to precisely adjust the oil speed in the two lines.

[0089] If a non-circular hole connection is used, the system can be adjusted by rotating in the opposite direction if the adjustment is excessive; or the flow rate of another pipeline can be finely adjusted to ultimately obtain a fully synchronized hydraulic system.

[0090] This invention does not contain any magnetic devices such as motors, and the overall system has non-magnetic characteristics, making it particularly suitable for high-precision environments such as medical settings.

[0091] Applying the synchronous hydraulic system of this invention to CT equipment, replacing the conventional hydraulic system, ensures that the return oil speed of the two cylinders 2 at the head and foot of the bed is exactly the same, thereby ensuring that the two cylinders 2 rise and fall completely synchronously. If more cylinders 2 need to rise and fall synchronously, the deceleration valve 5 on the return oil line of each cylinder 2 can be adjusted to make the fall speed of each cylinder 2 the same, thus achieving the goal of complete synchronization of multiple cylinders 2.

[0092] The frame 1 of the present invention also includes a detachable flip-top cover structure located on top of the hydraulic cylinder 2, which facilitates the assembly and disassembly of the hydraulic cylinder 2. A vertical guide wheel assembly 6 is provided below the hydraulic cylinder 2 to ensure the vertical movement accuracy of the hydraulic cylinder 2 during its upward and downward movements.

[0093] Scene 2

[0094] In long-distance jacking construction, such as during the construction of industrial buildings or stadiums, large prefabricated components, such as large roof trusses and wall panels, need to be jacked into place over long distances. In this case, multiple sets of hydraulic cylinders can be arrayed according to the expected interval length. First, all hydraulic cylinders are started, and after the cylinders are raised and lowered, the difference in falling speed is recorded. Starting from the return oil pipe with the fastest falling speed, the coarse adjustment section is used individually to adjust the falling speed of this cylinder to be close to that of the cylinder with the slowest falling speed. After adjusting the falling speed of all hydraulic cylinders to be similar, the differential screw fine adjustment section is installed to precisely adjust the return oil speed of all hydraulic cylinders.

[0095] After assembling the differential screw fine-tuning section, the specific fine-tuning operation steps are as follows: Start all hydraulic cylinders to lift to their maximum height. Place a level plate or horizontal line at each lifting height. When a height difference occurs during the cylinder's descent, adjust each pipeline according to the height difference. Then, continue descent for a certain period, and again measure using the level plate or horizontal line. Based on the distance difference between each cylinder and the level plate or horizontal line, readjust the deceleration valve. Repeat the operation until all hydraulic cylinders descent completely synchronously. This configuration is suitable for heavy-duty, long-distance jacking construction.

[0096] The above description is an explanation of the present invention and not a limitation thereof. The scope of the present invention is defined by the claims. Within the scope of protection of the present invention, any form of modification may be made.

Claims

1. A synchronous hydraulic system, characterized in that: It includes multiple independent hydraulic cylinders, each hydraulic cylinder has a deceleration valve (5) connected to its return oil line, and the return oil flow of each deceleration valve (5) is adjustable; each deceleration valve (5) adjusts the return oil flow of its own return oil line to synchronize the fall action of all hydraulic cylinders; the adjustment structure includes a coarse adjustment structure and a micro-propulsion structure that can be disassembled from each other. The system includes a frame (1), on which a control box (4) and at least two hydraulic cylinders are mounted, with the oil circuits of all hydraulic cylinders converging into the control box (4). The control box (4) is equipped with: The hydraulic circuits for all hydraulic cylinders are integrated within the control box (4). The deceleration valve (5) is provided on the return oil line of each hydraulic cylinder. The deceleration valve (5) includes a housing and a hollow valve core (503). A screw (507) for pushing the valve core (503) is also provided on the housing. Through holes that allow oil to flow are opened on the housing and the valve core (503). The knob (507) includes a coarse adjustment section and a differential screw fine adjustment section that is detachably connected to the coarse adjustment section.

2. The synchronous hydraulic system as described in claim 1, characterized in that: The housing includes: The positioning housing (501) is fixedly located inside the control box (4). The oil outlet housing (502) is nested and sealed with the positioning housing (501), and the oil outlet housing (502) has an oil outlet through hole. The screw (507) extends into the positioning housing (501) and pushes the valve core (503) to move; the valve core (503) is displaced in the oil outlet housing (502).

3. The synchronous hydraulic system as described in claim 2, characterized in that: The coarse adjustment section is constantly inserted into the positioning housing (501); the differential screw fine adjustment section is equipped with a positioning screw sleeve, which is sleeved with the outer wall of the housing. The differential screw fine adjustment section, the coarse adjustment section, the positioning screw sleeve, and the housing constitute a micro-propulsion structure.

4. The synchronous hydraulic system as described in claim 3, characterized in that: An elastic element is connected between the valve core (503) and the screw (507). The axial displacement of the screw (507) is buffered by the elastic element and then acts on the valve core (503). Alternatively, an elastic element may be provided on the side of the valve core (503) away from the screw button (507), and the screw button (507) may abut against and push the valve core (503).

5. The synchronous hydraulic system as described in claim 1, characterized in that: Each hydraulic cylinder is equipped with a counterweight (3).

6. The synchronous hydraulic system as described in claim 1, characterized in that: The frame (1) is equipped with a mounting position for accommodating the hydraulic cylinder. The top of the mounting position is provided with a flip cover plate, which limits the position of the top of the hydraulic cylinder.

7. A hydraulic synchronization calibration method using the synchronous hydraulic system of claim 1, characterized in that, Includes the following steps: After the counterweight (3) is applied to the hydraulic cylinder, the control box (4) controls all the hydraulic cylinders on the frame (1) to rise and fall back down, thus obtaining the fall speed of each hydraulic cylinder before adjustment. Based on the difference in the return speed of each hydraulic cylinder, adjust the screw knob (507) of each hydraulic cylinder until the return speed of all hydraulic cylinders is the same. At this time, the return oil flow rate controlled by the deceleration valve (5) of all hydraulic cylinders per unit time is the same or different. Under the same working conditions, lock the deceleration valve (5) screw knob (507) of each hydraulic cylinder to ensure that all hydraulic cylinders lift and lower synchronously.

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