Differential self-adjusting multi-cylinder hydraulic synchronization device

Abstract

This utility model discloses a differential self-adjusting multi-cylinder hydraulic synchronization device, involving multiple cylinder synchronization control technology. The utility model includes hydraulic cylinder I, hydraulic cylinder II, and a differential compensation valve. Hydraulic cylinder I and hydraulic cylinder II are equipped with a screw-nut pair for converting the linear motion of the hydraulic cylinder piston into rotational motion. Each screw in the screw-nut pair has a transmission component. The compensation valve core of the differential compensation valve has a relatively rotatable rotating shaft. The rotating shaft has a spline-fitted in-situ transmission component II and a threadedly fitted in-situ transmission component I forming the screw-nut pair. After the axial motion of hydraulic cylinder I and hydraulic cylinder II is converted into rotational motion, it is transmitted to the in-situ transmission components I and II respectively. When there is a displacement difference between the two, there is a speed difference in rotation. This speed difference in rotation enables the rotating shaft to rotate, thereby driving the compensation valve core to move axially, achieving displacement compensation between the two hydraulic cylinders.

Description

Technical Field

[0001] This utility model relates to the technology of synchronous control of multiple hydraulic cylinders, and in particular to a differential self-adjusting multi-cylinder hydraulic synchronization device. Background Technology

[0002] Synchronous control of hydraulic cylinders is used in many engineering fields, especially when precise positional control of large, heavy structures is required, often necessitating synchronized, high-precision movements of multiple hydraulic cylinders. However, limited by existing hydraulic control technology, high-precision automatic adjustment of multiple hydraulic cylinders is often achieved through electrical regulation or a combination of electrical and mechanical regulation.

[0003] However, in some harsh working conditions with high explosion-proof requirements, a high-precision synchronization system based on pure mechanical hydraulics is often better suited to the working conditions and can avoid the problem of poor synchronization caused by electrical component failure.

[0004] Currently, there are systems that use coaxial motors and servo valves to control the synchronous control system of hydraulic cylinders. However, because the servo valve control relies on position data from electrical signals, its synchronization accuracy is low. Furthermore, the control system needs to continuously compare the positions of the digital cylinders and output appropriate control signals to the servo valves, leading to a complex electrical control system. In multi-cylinder synchronization applications where high precision is not required, only coaxial motors are used to achieve relatively coarse synchronization. However, when the hydraulic cylinder stroke is long, the synchronization deviation increases, resulting in asynchronous motion control.

[0005] For example, the invention patent application with publication number CN118416991A, publication date August 22, 2024, entitled "A Mechanically Synchronized High-Pressure Roller Mill," includes a machine body and a fixed roller assembly and a moving roller assembly mounted on the machine body. It also includes connecting supports mounted on both ends of the moving roller assembly opposite to the fixed roller assembly. Both sets of connecting supports are connected to a counteracting rod via spherical bearings. A synchronous rocker arm is mounted at the end of the counteracting rod. Both sets of synchronous rocker arms are mounted on a synchronous shaft, and synchronous bearing seats are mounted at both ends of the synchronous shaft, which are fixed to the machine body. This invention patent application sets up a mechanical synchronization device to force the roller system to operate synchronously. This method can cause one of the hydraulic cylinders to become pressurized, posing a risk of damage to the hydraulic cylinder. Utility Model Content

[0006] In order to overcome the defects and deficiencies in the existing technology, this utility model provides a differential automatic adjustment multi-cylinder hydraulic synchronization device. The purpose of this utility model is to set up a set of purely mechanical differential automatic adjustment multi-cylinder hydraulic synchronization device, which does not require electrical correction and will not cause hydraulic cylinder pressure buildup, thereby improving the synchronization accuracy of multiple hydraulic cylinders.

[0007] To address the problems existing in the prior art, the present invention is achieved through the following technical solution.

[0008] This utility model provides a differential self-adjusting multi-cylinder hydraulic synchronization device, including hydraulic cylinder I, hydraulic cylinder II, and differential compensation valve; a nut I is fixedly mounted on the piston inside hydraulic cylinder I, and a lead screw I is threadedly connected to the nut I. One end of the lead screw I extends out of hydraulic cylinder I, and the lead screw I is rotatably mounted on hydraulic cylinder I without axial displacement; a transmission component I is fixedly mounted on the end of the lead screw I extending out of hydraulic cylinder I, and the rotation of the lead screw I drives the transmission component I to rotate; the nut I and the lead screw I form a lead screw nut pair;

[0009] A nut II is fixedly mounted on the piston inside the hydraulic cylinder II. The nut II is threadedly connected to a lead screw II. One end of the lead screw II extends out of the hydraulic cylinder II. The lead screw II is mounted on the hydraulic cylinder II in a rotatable manner but without axial displacement. A transmission component II is fixedly mounted on the end of the lead screw II that extends out of the hydraulic cylinder II. When the lead screw II rotates, it drives the transmission component II to rotate. The nut II and the lead screw II form a lead screw nut pair.

[0010] The differential compensation valve is a three-position four-way valve, including port T, port P, port A, and port B. Port T is connected to the return oil of the hydraulic cylinder system, and port P is connected to the pressure oil source. Port A is connected to piston chamber I of hydraulic cylinder I or hydraulic cylinder II. Port B is connected to piston chamber II of hydraulic cylinder I or hydraulic cylinder II. The differential compensation valve also includes a compensation valve core and a rotating shaft. One end of the rotating shaft is connected to the compensation valve core. The rotating shaft rotates relative to the compensation valve core, and the rotating shaft can generate axial displacement to drive the compensation valve core to move axially within the differential compensation valve.

[0011] The rotating shaft extends from the shaft of the differential compensation valve and is equipped with in-situ transmission component I and in-situ transmission component II. The rotating shaft is threadedly engaged with the central shaft hole of in-situ transmission component I to form a lead screw and nut pair. The rotating shaft is connected to the central shaft hole of in-situ transmission component II through a spline. Transmission component I is driven by in-situ transmission component I, and transmission component II is driven by in-situ transmission component II.

[0012] The transmission relationship between the various components of this utility model is as follows: the piston in hydraulic cylinder I is fixedly connected to nut I. When the piston moves axially, nut I moves axially synchronously with the piston, thereby driving lead screw I to perform passive rotational motion (lead screw I only rotates without axial displacement); similarly, when the piston in hydraulic cylinder II moves axially, nut II moves axially synchronously with the piston, thereby driving lead screw II to perform passive rotational motion.

[0013] Transmission component I is connected to the original position transmission component I. When the lead screw I undergoes passive rotation, it drives transmission component I to rotate, which in turn drives the original position transmission component I to rotate. The original position transmission component I only rotates without axial displacement, meaning it rotates in its original position. Similarly, transmission component II is connected to the original position transmission component II. When the lead screw II undergoes passive rotation, it drives transmission component II to rotate, which in turn drives the original position transmission component II to rotate. The original position transmission component II only rotates without axial displacement, meaning it rotates in its original position. It should be noted that when transmission component I drives the original position transmission component I to rotate, and when transmission component II drives the original position transmission component II to rotate, the rotation directions of the original position transmission components I and II are the same.

[0014] Since the in-situ transmission component II is splinedly connected to the rotating shaft, when the in-situ transmission component II rotates, it drives the rotating shaft to rotate. The in-situ transmission component I and the rotating shaft form a screw-nut pair, with the rotating shaft acting as the screw and the in-situ transmission component I acting as the nut. When the rotational speeds of the in-situ transmission component I and the in-situ transmission component II relative to the rotating shaft are the same, the rotating shaft and the in-situ transmission component I remain relatively stationary, that is, the rotating shaft does not produce axial movement. Once there is a speed difference between the in-situ transmission component I and the in-situ transmission component II relative to the rotating shaft, the rotating shaft and the in-situ transmission component I produce relative movement. Under the cooperation of the screw-nut pair between the rotating shaft and the in-situ transmission component I, the rotating shaft produces axial displacement relative to the in-situ transmission component I and the in-situ transmission component II. After the rotating shaft produces axial displacement, it drives the compensation valve core to move axially within the differential compensation valve.

[0015] This invention utilizes the principle of differential self-adjustment, achieved through a process of "displacement difference → mechanical motion difference → valve position adjustment → oil circuit compensation." Specifically, when the piston movements of hydraulic cylinder I and hydraulic cylinder II are asynchronous (i.e., when the extension strokes of the hydraulic rods are asynchronous, for example, the piston in hydraulic cylinder I moves faster than the piston in hydraulic cylinder II), the displacement difference between the two will cause the rotational speed of lead screw I to be faster than that of lead screw II, which in turn causes the rotational speed of transmission component I to be faster than that of transmission component II.

[0016] The rapid rotation of transmission component I increases the rotational speed of the original transmission component I, meaning that the rotational speed of the original transmission component I is faster than that of the original transmission component II. This causes a mismatch between the rotational speed of the rotating shaft and the rotational speed of the original transmission component I, resulting in a speed difference that causes axial displacement of the rotating shaft (the amount of displacement generated by the rotating shaft is proportional to the displacement difference between the pistons of hydraulic cylinders I and II). The axial movement of the rotating shaft drives the axial movement of the compensation valve core of the differential compensation valve, causing the three-position four-way valve to switch positions. If the displacement of hydraulic cylinder I is ahead, the movement of the compensation valve core will connect the oil port P of the differential compensation valve with the piston chamber II of hydraulic cylinder I, simultaneously causing the piston of hydraulic cylinder I to... The piston chamber I is connected to port T of the differential compensation valve (ports A and B of the differential compensation valve are connected to hydraulic cylinder I). This means that the oil flow to hydraulic cylinder I is reduced by adjusting the oil circuit (to slow down the movement speed of the piston in hydraulic cylinder I). If ports A and B of the differential compensation valve are connected to hydraulic cylinder II, when the displacement of hydraulic cylinder I is ahead, the port P of the differential compensation valve is connected to piston chamber I of hydraulic cylinder II, and the port T of the differential compensation valve is connected to piston chamber II of hydraulic cylinder II. This means that the oil flow to hydraulic cylinder II is increased to increase the movement speed of the piston in hydraulic cylinder II, until the displacement difference between the two is reduced to within the error range, and the differential compensation valve core returns to the neutral position.

[0017] After the displacement difference between hydraulic cylinder I and hydraulic cylinder II is eliminated, the rotation speeds of transmission component I and transmission component II become consistent. The driving forces of the original-position transmission component I and original-position transmission component II on the rotating shaft are balanced, and the rotating shaft no longer moves axially. The differential compensation valve returns to the neutral position (during the oil circuit compensation process, the original-position transmission component I and original-position transmission component II generate a new speed difference until the speed difference is eliminated. At this time, the rotating shaft returns to the neutral position, and the valve core of the differential compensation valve returns to the neutral position). The oil circuit returns to its initial state, and the two hydraulic cylinders maintain synchronous movement.

[0018] This invention converts the displacement difference between hydraulic cylinders into axial movement of the rotating shaft through a mechanical structure (a lead screw and nut pair consisting of lead screw I and nut I, a lead screw and nut pair consisting of lead screw II and nut II, a rotating shaft and in-situ transmission component I, transmission component I, transmission component II, and in-situ transmission component II). Dynamic compensation is then achieved through oil circuit adjustment of the differential compensation valve, ultimately eliminating synchronization errors. The entire process requires no electrical control, relying entirely on mechanical-hydraulic linkage, making it suitable for harsh environments or scenarios with high explosion-proof requirements.

[0019] More preferably, the differential compensation valve is provided with a bearing that cooperates with the rotating shaft.

[0020] More preferably, the transmission ratio between transmission component I and in-situ transmission component I is the same as the transmission ratio between transmission component II and in-situ transmission component II.

[0021] More preferably, the transmission component I, transmission component II, in-situ transmission component I, and in-situ transmission component II are all gears, with transmission component I meshing with in-situ transmission component I and transmission component II meshing with in-situ transmission component II.

[0022] More preferably, the transmission component I, transmission component II, in-situ transmission component I, and in-situ transmission component II are all synchronous belt pulleys, with transmission component I and in-situ transmission component I being driven by a synchronous belt; and transmission component II and in-situ transmission component II being driven by a synchronous belt.

[0023] More preferably, the transmission component I, transmission component II, in-situ transmission component I, and in-situ transmission component II are all sprockets, with transmission component I and in-situ transmission component I being driven by a chain; and transmission component II and in-situ transmission component II being driven by a chain.

[0024] In a further preferred embodiment, the differential self-adjusting multi-cylinder hydraulic synchronization device further includes an in-situ limiting seat, on which a limiting chuck I for limiting the axial movement of the in-situ transmission component I along the rotation axis and a limiting chuck II for limiting the axial movement of the in-situ transmission component II along the rotation axis are provided.

[0025] More preferably, a plurality of ball bearings are provided on the surface of the limiting chuck I that contacts the original position transmission component I; a plurality of ball bearings are provided on the surface of the limiting chuck II that contacts the original position transmission component II.

[0026] More preferably, the in-situ limiting seat is further provided with a limiting chuck Ⅲ for limiting the movement of the transmission component Ⅰ along the axial direction of the lead screw Ⅰ, and a limiting chuck VI for limiting the movement of the transmission component Ⅱ along the axial direction of the lead screw Ⅱ.

[0027] More preferably, the hydraulic rods connected to the pistons on hydraulic cylinders I and II are partially hollow structures, with lead screw I extending into one end of hydraulic cylinder I and inserted into the hollow portion of the hydraulic rod of hydraulic cylinder I; and lead screw II extending into one end of hydraulic cylinder II and inserted into the hollow portion of the hydraulic rod of hydraulic cylinder II.

[0028] Further preferably, a sealing limiting member I is provided between the lead screw I and the cylinder body of the hydraulic cylinder I, the sealing limiting member I restricting the axial displacement of the lead screw I and serving as a seal between the lead screw I and the cylinder body of the hydraulic cylinder I; a sealing limiting member II is provided between the lead screw II and the cylinder body of the hydraulic cylinder II, the sealing limiting member II restricting the axial displacement of the lead screw II and serving as a seal between the lead screw II and the cylinder body of the hydraulic cylinder II.

[0029] Compared with the prior art, the beneficial technical effects of this utility model are as follows:

[0030] 1. This invention enables high-precision, dynamically adaptive synchronous adjustment. It constructs a real-time response synchronous control mechanism through a closed-loop logic of "displacement difference - mechanical motion difference - valve position adjustment - oil circuit compensation." When hydraulic cylinders I and II experience displacement deviations due to load, leakage, or other factors, the difference is converted into a screw speed difference through the screw-nut pair, which is then transmitted to the in-situ transmission component as a speed difference, ultimately driving the rotating shaft to move axially and triggering the differential compensation valve. This mechanically hard-connected transmission method has no signal conversion delay, dynamically eliminating or controlling synchronization errors within a very small range, significantly improving the accuracy of multi-cylinder coordinated action and solving the problem of accumulated synchronization deviations in traditional coaxial flow dividers over long strokes.

[0031] 2. This utility model adopts a purely mechanical hydraulic drive, adaptable to extreme working conditions. Synchronization is achieved entirely through the hydraulic adjustment of the lead screw and nut pair, gears (or synchronous belt pulleys and sprockets), and differential compensation valve, without the need for electrical sensors, controllers, or other components. This characteristic enables it to stably adapt to harsh working conditions with strict requirements for high temperature, high humidity, dust, strong electromagnetic interference, and explosion-proof applications. It avoids the risk of electrical component failure in extreme environments, significantly improving the reliability and durability of multi-hydraulic cylinder systems in special industrial scenarios (such as mining machinery, metallurgical equipment, and explosion-proof production lines).

[0032] 3. This utility model modularizes the structure of the multi-cylinder hydraulic synchronization device, resulting in strong scalability and compatibility. For multi-cylinder synchronization requirements, the synchronization logic of two cylinders can be extended to more hydraulic cylinders simply through the linkage design of the differential compensation valve (e.g., adding a transmission assembly and differential compensation valve for each new set of hydraulic cylinders, or setting a differential compensation valve between adjacent hydraulic cylinders), without needing to reconstruct the core control logic, thus adapting to collaborative scenarios with different numbers of cylinders.

[0033] 4. The transmission component of this utility model can flexibly adopt various forms such as gear meshing, synchronous belt drive or chain drive, and through a unified transmission ratio design (the transmission ratios of transmission component I and original transmission component I, and transmission component II and original transmission component II are the same), the accuracy of displacement difference conversion is ensured, and the system's compatibility with different installation spaces and transmission efficiency requirements is improved.

[0034] 5. This utility model exhibits high motion stability, minimal wear, and a long service life. The limiting chucks I and II of the in-situ limiting seat mechanically restrict the axial displacement of the in-situ transmission components. Combined with a ball bearing structure, this reduces contact friction, ensuring that the transmission components perform only pure rotational motion and avoiding transmission errors or structural wear caused by axial movement. The bearing design between the rotating shaft and the differential compensation valve reduces relative motion resistance. The sealing limiting component between the lead screw and the cylinder body ensures the hydraulic oil sealing performance without hindering lead screw rotation, thus reducing overall mechanical wear and extending the service life of the multi-cylinder hydraulic synchronization device.

[0035] 6. This invention features sensitive adjustment response and no cumulative error. Compared to servo control systems that rely on electrical feedback, the synchronization compensation of this device is based on the direct transmission of mechanical displacement differences, resulting in an extremely short response link from the generation of deviation to hydraulic circuit adjustment. Furthermore, the compensation process itself reacts to the hydraulic cylinder movement through the hydraulic circuit, forming an instantaneous closed loop of "deviation-compensation-deviation elimination," avoiding the error accumulation caused by signal delay or algorithm iteration in traditional control systems, and ensuring the stability of synchronization accuracy during long-term operation.

[0036] 7. This utility model features a simplified structure and low maintenance costs. It eliminates complex electrical control modules, with core components consisting of mechanical transmission parts and hydraulic valves. The structure is intuitive and highly standardized. Routine maintenance only requires addressing common mechanical issues such as lubrication of transmission parts and aging of seals, without requiring specialized electrical debugging skills. This significantly reduces the difficulty and cost of operation and maintenance, making it particularly suitable for industrial scenarios with limited equipment maintenance resources.

[0037] 8. Compared with existing hydraulic synchronization systems that use mechanical structures for forced synchronization, this utility model will not cause pressure buildup in the hydraulic cylinder body, and will not cause damage to the hydraulic cylinder. Attached Figure Description

[0038] Figure 1 This is a schematic diagram of the differential self-adjusting multi-cylinder hydraulic synchronization device of this utility model;

[0039] Reference numerals in the attached drawings: 1. Hydraulic cylinder I, 2. Hydraulic cylinder II, 3. Differential compensation valve, 4. Nut I, 5. Lead screw I, 6. Transmission component I, 7. Nut II, 8. Lead screw II, 9. Transmission component II, 10. Piston chamber I, 11. Piston chamber II, 12. Compensation valve core, 13. Rotary shaft, 14. In-situ transmission component I, 15. In-situ transmission component II, 16. Bearing, 17. Piston, 18. Hydraulic rod. Detailed Implementation

[0040] The technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0041] As a preferred embodiment of this utility model, please refer to the appendix to the specification. Figure 1As shown, this embodiment discloses a differential self-adjusting multi-cylinder hydraulic synchronization device, which includes a hydraulic cylinder I1, a hydraulic cylinder II2, and a differential compensation valve 3; a nut I4 is fixedly mounted on the piston 17 inside the hydraulic cylinder I1, and a lead screw I5 is threadedly connected to the nut I4. One end of the lead screw I5 extends out of the hydraulic cylinder I1, and the lead screw I5 is rotatably mounted on the hydraulic cylinder I1 without axial displacement; a transmission component I6 is fixedly mounted on the end of the lead screw I5 extending out of the hydraulic cylinder I1, and the rotation of the lead screw I5 drives the rotation of the transmission component I6; the nut I4 and the lead screw I5 form a lead screw nut pair;

[0042] A nut II7 is fixedly mounted on the piston 17 inside the hydraulic cylinder II2. The nut II7 is threadedly connected to a lead screw II8. One end of the lead screw II8 extends out of the hydraulic cylinder II2. The lead screw II8 is rotatable but not axially displaced while mounted on the hydraulic cylinder II2. A transmission component II9 is ​​fixedly mounted on the end of the lead screw II8 extending out of the hydraulic cylinder II2. When the lead screw II8 rotates, it drives the transmission component II9 to rotate. The nut II7 and the lead screw II8 form a lead screw nut pair.

[0043] The differential compensation valve 3 is a three-position four-way valve, including port T, port P, port A, and port B. Port T is connected to the return oil of the hydraulic cylinder system, port P is connected to the pressure oil source, and port A is connected to the piston chamber I10 of hydraulic cylinder I1 or hydraulic cylinder II2. Figure 1 The diagram shows the connection structure where oil port A connects to piston chamber I10 of hydraulic cylinder I1; oil port B connects to piston chamber II11 of hydraulic cylinder I1 or hydraulic cylinder II2. Figure 1 The diagram shows the connection structure where oil port A is connected to piston chamber II11 of hydraulic cylinder I1. The differential compensation valve 3 also includes a compensation valve core 12 and a rotating shaft 13. One end of the rotating shaft 13 is connected to the compensation valve core 12. The rotating shaft 13 rotates relative to the compensation valve core 12. The rotating shaft 13 can generate axial displacement to drive the compensation valve core 12 to move axially within the differential compensation valve 3.

[0044] The rotating shaft 13 extends out of the shaft of the differential compensation valve 3 and is equipped with in-situ transmission component I14 and in-situ transmission component II15. The rotating shaft 13 is threadedly engaged with the central shaft hole of the in-situ transmission component I14 to form a lead screw and nut pair. The rotating shaft 13 is connected to the central shaft hole of the in-situ transmission component II15 through a spline. Transmission component I6 is connected to the in-situ transmission component I14, and transmission component II9 is ​​connected to the in-situ transmission component II15.

[0045] The transmission relationship between the various components of this utility model is as follows: the piston 17 in the hydraulic cylinder I1 is fixedly connected to the nut I4. When the piston 17 moves axially, the nut I4 moves axially synchronously with the piston 17, thereby driving the lead screw I5 to perform passive rotational motion (the lead screw I5 only rotates without axial displacement); similarly, when the piston 17 in the hydraulic cylinder II2 moves axially, the nut II7 moves axially synchronously with the piston 17, thereby driving the lead screw II8 to perform passive rotational motion.

[0046] Transmission component I6 is connected to the in-situ transmission component I14. When the lead screw I5 rotates passively, it drives transmission component I6 to rotate, which in turn drives the in-situ transmission component I14 to rotate. The in-situ transmission component I14 only rotates without axial displacement, meaning it rotates in its original position. Similarly, transmission component II9 is ​​connected to the in-situ transmission component II15. When the lead screw II8 rotates passively, it drives transmission component II9 to rotate, which in turn drives the in-situ transmission component II15 to rotate. The in-situ transmission component II15 only rotates without axial displacement, meaning it rotates in its original position. It should be noted that when transmission component I6 drives the in-situ transmission component I14 to rotate, and when transmission component II9 drives the in-situ transmission component II15 to rotate, the rotation directions of the in-situ transmission components I14 and II15 are the same.

[0047] Since the in-situ transmission component II15 is splinedly connected to the rotating shaft 13, when the in-situ transmission component II15 rotates, it drives the rotating shaft 13 to rotate. The in-situ transmission component I14 and the rotating shaft 13 form a screw-nut pair, with the rotating shaft 13 acting as a screw and the in-situ transmission component I14 acting as a nut. When the rotational speeds of the in-situ transmission component I14 and the in-situ transmission component II15 relative to the rotating shaft 13 are the same, the rotating shaft 13 and the in-situ transmission component I14 remain relatively stationary, that is, the rotating shaft 13 does not produce axial movement. Once there is a speed difference between the rotational speeds of the in-situ transmission component I14 and the in-situ transmission component II15 relative to the rotating shaft 13, the rotating shaft 13 and the in-situ transmission component I14 produce relative movement. Under the cooperation of the screw-nut pair between the rotating shaft 13 and the in-situ transmission component I14, the rotating shaft 13 produces axial displacement relative to the in-situ transmission component I14 and the in-situ transmission component II15. After the rotating shaft 13 produces axial displacement, it drives the compensation valve core 12 to move axially within the differential compensation valve 3.

[0048] This invention utilizes the principle of differential self-adjustment through "displacement difference → mechanical motion difference → valve position adjustment → oil circuit compensation". Specifically, when the pistons 17 of hydraulic cylinder I1 and hydraulic cylinder II2 move asynchronously (i.e., when the extension stroke of hydraulic rod 18 is asynchronous, for example, the moving speed of piston 17 in hydraulic cylinder I1 is faster than the moving speed of piston 17 in hydraulic cylinder II2), the displacement difference between the two will cause the rotation speed of lead screw I5 to be faster than the rotation speed of lead screw II8, which in turn causes the rotation speed of transmission component I6 to be faster than the rotation speed of transmission component II9.

[0049] The rapid rotation of transmission component I6 increases the rotational speed of the original-position transmission component I14, meaning that the rotational speed of the original-position transmission component I14 is faster than that of the original-position transmission component II15. This causes a mismatch between the rotational speed of the rotating shaft 13 and the rotational speed of the original-position transmission component I14, resulting in a speed difference. This causes the rotating shaft 13 to undergo axial displacement (the displacement of the rotating shaft 13 is proportional to the displacement difference between the pistons 17 of hydraulic cylinders I1 and II2). The axial movement of the rotating shaft 13 drives the axial movement of the compensation valve core 12 of the differential compensation valve 3. When the differential compensation valve switches positions, if ports A and B of the differential compensation valve are connected to hydraulic cylinder I, when hydraulic cylinder I1 moves ahead, the movement of compensation valve core 12 will cause port P of differential compensation valve 3 to connect with piston chamber II11 of hydraulic cylinder I1, and simultaneously connect piston chamber I10 of hydraulic cylinder I1 with port T of differential compensation valve 3; that is, by adjusting the oil circuit, the oil inlet of hydraulic cylinder I1 is reduced (to slow down the movement speed of piston 17 in hydraulic cylinder I1), until the displacement difference between the two is reduced to within the error range.

[0050] If the oil ports A and B of the differential compensation valve 3 are connected to the hydraulic cylinder II 2, when the displacement of the hydraulic cylinder I 1 is ahead, the oil port P of the differential compensation valve 3 is connected to the piston chamber I 10 of the hydraulic cylinder II 2, and the oil port T of the differential compensation valve 3 is connected to the piston chamber II 11 of the hydraulic cylinder II 2, that is, the oil intake of the hydraulic cylinder II 2 is increased, so as to increase the movement speed of the piston in the hydraulic cylinder II 2.

[0051] After the displacement difference between hydraulic cylinder I1 and hydraulic cylinder II2 is eliminated, the rotation speeds of transmission component I6 and transmission component II9 are consistent, the driving force of in-situ transmission component I14 and in-situ transmission component II15 on the rotating shaft 13 is balanced, the rotating shaft 13 no longer moves axially, and the differential compensation valve 3 returns to the neutral position (during the oil circuit compensation process, a new speed difference is generated between in-situ transmission component I14 and in-situ transmission component II15 until the speed difference is eliminated, at which point the rotating shaft 13 returns to the neutral position, and the valve core of the differential compensation valve 3 returns to the neutral position), the oil circuit returns to its initial state, and the two hydraulic cylinders maintain synchronous movement.

[0052] This invention utilizes a mechanical structure (a lead screw and nut pair consisting of lead screw I5 and nut I4, a lead screw and nut pair consisting of lead screw II8 and nut II7, a lead screw and nut pair consisting of rotating shaft 13 and in-situ transmission component I14, transmission component I6, transmission component II9, and in-situ transmission component II15) to convert the displacement difference between hydraulic cylinders into axial movement of rotating shaft 13. Dynamic compensation is then achieved through oil circuit adjustment of differential compensation valve 3, ultimately eliminating synchronization errors. The entire process requires no electrical control, relying entirely on mechanical-hydraulic linkage, making it suitable for harsh environments or scenarios with high explosion-proof requirements.

[0053] In one embodiment of this invention, the rotating shaft 13 can rotate relative to the differential compensation valve 3, and simultaneously drive the compensation valve core 12 of the differential compensation valve 3 to move axially. To reduce the resistance between the rotating shaft 13 and the differential compensation valve 3, a bearing 16 is provided on the differential compensation valve 3. This bearing 16 cooperates with the rotating shaft 13 to reduce the rotational resistance and axial movement resistance of the rotating shaft 13. Furthermore, to ensure the sealing performance of the differential compensation valve 3, a sealing packing that cooperates with the rotating shaft 13 is provided on the differential compensation valve 3 to prevent hydraulic oil leakage from the gap between the rotating shaft 13 and the differential compensation valve 3.

[0054] In another embodiment of this invention, the dimensions of transmission component I6 and transmission component II9 may be different. A suitable transmission component size can be selected based on the distance between hydraulic cylinder I1 and hydraulic cylinder II2. However, it is necessary to ensure that the transmission ratio between transmission component I6 and the in-situ transmission component I14 is the same as the transmission ratio between transmission component II9 and the in-situ transmission component II15. This setting ensures that the axial rotational speed applied to the rotating shaft 13 is the same during the conversion of the displacement of hydraulic cylinders I1 and II2 into rotation. A speed difference will only occur when the displacements of hydraulic cylinders I1 and II2 are different, thus causing axial displacement of the rotating shaft 13.

[0055] As an example of this embodiment, please refer to the appendix to the specification. Figure 1 As shown, the transmission component I6, transmission component II9, in-situ transmission component I14, and in-situ transmission component II15 are all gears. Transmission component I6 meshes with in-situ transmission component I14, and transmission component II9 meshes with in-situ transmission component II15.

[0056] As another example of this embodiment, the transmission component I6, transmission component II9, in-situ transmission component I14, and in-situ transmission component II15 are all synchronous belt pulleys. Transmission component I6 and in-situ transmission component I14 are driven by a synchronous belt; transmission component II9 and in-situ transmission component II15 are driven by a synchronous belt.

[0057] As another example of this embodiment, the transmission component I6, transmission component II9, in-situ transmission component I14 and in-situ transmission component II15 are all sprockets. Transmission component I6 and in-situ transmission component I14 are driven by a chain; transmission component II9 and in-situ transmission component II15 are driven by a chain.

[0058] The three examples above illustrate specific implementation schemes for transmission component I6, transmission component II9, in-situ transmission component I14, and in-situ transmission component II15. Gears, synchronous pulleys, or sprockets are specifically used, and the choice can be made based on the spacing between hydraulic cylinders and the applicable working conditions.

[0059] In another preferred embodiment of this utility model, the differential self-adjusting multi-cylinder hydraulic synchronization device further includes an in-situ limiting seat (not shown in the figure). The in-situ limiting seat is provided with a limiting chuck I for limiting the axial movement of the in-situ transmission component I14 along the rotation shaft 13, and a limiting chuck II for limiting the axial movement of the in-situ transmission component II15 along the rotation shaft 13. In this embodiment, the axial positions of the in-situ transmission component I14 and the in-situ transmission component II15 are limited by the chuck I and the chuck II, respectively, to prevent the in-situ transmission component I14 and the in-situ transmission component II15 from moving axially with the rotation shaft 13, thereby affecting the meshing transmission (or synchronous belt transmission or chain transmission) between them and the transmission component I6 and the transmission component II9.

[0060] To further reduce the frictional impact of the chuck on the in-situ transmission components and decrease their resistance, in this embodiment, a plurality of ball bearings are provided on the surface of the limiting chuck I that contacts the in-situ transmission component I 14; and a plurality of ball bearings are provided on the surface of the limiting chuck II that contacts the in-situ transmission component II 15. By using these ball bearings, sliding friction is transformed into rolling friction, thereby reducing friction and decreasing resistance.

[0061] As an optimized solution in this embodiment, the in-situ limiting seat is further provided with a limiting chuck III (not shown in the figure) for limiting the axial movement of transmission component I6 along lead screw I5, and a limiting chuck VI (not shown in the figure) for limiting the axial movement of transmission component II9 along lead screw II8. The limiting chucks III and VI are provided to restrict the axial movement of transmission component I6 and transmission component II9 and prevent them from moving axially.

[0062] In another embodiment of this invention, the hydraulic rods 18 connected to the piston 17 on hydraulic cylinders I1 and II2 are partially hollow. Lead screw I5 extends into one end of hydraulic cylinder I1 and is inserted into the hollow portion of the hydraulic rod 18; lead screw II8 extends into one end of hydraulic cylinder II2 and is inserted into the hollow portion of the hydraulic rod 18. This ensures the stability of the rotational movement of lead screws I5 and II8, and also allows lead screws I5 and II8 to be matched with the piston 17.

[0063] As a scheme to limit the axial movement of lead screws I5 and II8 in this embodiment, a sealing limiting member I (not shown in the figure) is provided between lead screw I5 and the cylinder body of hydraulic cylinder I1. The sealing limiting member I limits the axial displacement of lead screw I5 and is used for sealing between lead screw I5 and the cylinder body of hydraulic cylinder I1. A sealing limiting member II is provided between lead screw II8 and the cylinder body of hydraulic cylinder II2. The sealing limiting member II limits the axial displacement of lead screw II8 and is used for sealing between lead screw II8 and the cylinder body of hydraulic cylinder II2. As an example, the sealing limiting member can be a stepped assembly that mates with lead screw I5 and / or lead screw II8, and a corresponding sealing ring is provided to ensure the sealing performance of the hydraulic cylinder.

Claims

1. A differential self-regulating multi-cylinder hydraulic synchronizing device, characterized by: It includes hydraulic cylinder I (1), hydraulic cylinder II (2) and differential compensation valve (3); a nut I (4) is fixedly mounted on the piston (17) inside the hydraulic cylinder I (1), and a screw I (5) is threadedly connected to the nut I (4). One end of the screw I (5) extends out of the hydraulic cylinder I (1), and the screw I (5) is rotatably mounted on the hydraulic cylinder I (1) without axial displacement; a transmission component I (6) is fixedly mounted on the end of the screw I (5) extending out of the hydraulic cylinder I (1), and the screw I (5) drives the transmission component I (6) to rotate when it rotates; the nut I (4) and the screw I (5) form a screw-nut pair; A nut II (7) is fixedly mounted on the piston (17) inside the hydraulic cylinder II (2). The nut II (7) is threadedly connected to a lead screw II (8). One end of the lead screw II (8) extends out of the hydraulic cylinder II (2). The lead screw II (8) is rotatably mounted on the hydraulic cylinder II (2) without axial displacement. A transmission component II (9) is fixedly mounted on the end of the lead screw II (8) extending out of the hydraulic cylinder II (2). When the lead screw II (8) rotates, it drives the transmission component II (9) to rotate. The nut II (7) and the lead screw II (8) form a lead screw nut pair. The differential compensation valve (3) is a three-position four-way valve, including port T, port P, port A and port B. Port T is connected to the return oil of the hydraulic cylinder system, and port P is connected to the pressure oil source. Port A is connected to the piston chamber I (10) of hydraulic cylinder I (1) or hydraulic cylinder II (2). Port B is connected to the piston chamber II (11) of hydraulic cylinder I (1) or hydraulic cylinder II (2). The differential compensation valve (3) also includes a compensation valve core (12) and a rotating shaft (13). One end of the rotating shaft (13) is connected to the compensation valve core (12). The rotating shaft (13) rotates relative to the compensation valve core (12). The rotating shaft (13) can generate axial displacement to drive the compensation valve core (12) to move axially within the differential compensation valve (3). The rotating shaft (13) extends out of the shaft of the differential compensation valve (3) and is equipped with in-situ transmission component I (14) and in-situ transmission component II (15). The rotating shaft (13) is threadedly engaged with the central shaft hole of the in-situ transmission component I (14) to form a screw and nut pair. The rotating shaft (13) is connected to the central shaft hole of the in-situ transmission component II (15) by a spline. The transmission component I (6) is connected to the in-situ transmission component I (14) and the transmission component II (9) is connected to the in-situ transmission component II (15).

2. The differential self-regulating multi-cylinder hydraulic synchronizer of claim 1, wherein: The differential compensation valve (3) is provided with a bearing (16) that cooperates with the rotating shaft (13).

3. The differential self-regulating multi-cylinder hydraulic synchronizer of claim 1, wherein: The transmission ratio between transmission component I (6) and in-situ transmission component I (14) is the same as the transmission ratio between transmission component II (9) and in-situ transmission component II (15).

4. A self-regulated differential multi-cylinder hydraulic synchronizer according to any one of claims 1-3, characterized in that: The transmission components I (6), II (9), I (14) and II (15) are all gears. Transmission component I (6) meshes with I (14) for transmission, and transmission component II (9) meshes with II (15) for transmission.

5. A self-regulated differential multi-cylinder hydraulic synchronizer according to any one of claims 1-3, characterized in that: The transmission components I (6), II (9), I (14), and II (15) are all synchronous pulleys. Transmission component I (6) and I (14) are driven by synchronous belts; transmission component II (9) and I (15) are driven by synchronous belts.

6. A self-regulated differential multi-cylinder hydraulic synchronizer according to any one of claims 1-3, characterized in that: The transmission components I (6), II (9), I (14) and II (15) are all sprockets. Transmission component I (6) and I (14) are driven by a chain; transmission component II (9) and I (15) are driven by a chain.

7. A self-regulated differential multi-cylinder hydraulic synchronizer according to any one of claims 1-3, characterized in that: The differential self-adjusting multi-cylinder hydraulic synchronization device also includes an in-situ limiting seat, on which a limiting chuck I is provided for limiting the axial movement of the in-situ transmission component I (14) along the rotation axis (13), and a limiting chuck II is provided for limiting the axial movement of the in-situ transmission component II (15) along the rotation axis (13).

8. The differential self-regulating multi-cylinder hydraulic synchronizer of claim 7, wherein: The limiting chuck I has several balls on the surface that contacts the original position transmission component I (14); the limiting chuck II has several balls on the surface that contacts the original position transmission component II (15).

9. The differential self-regulating multi-cylinder hydraulic synchronizer of claim 7, wherein: The original position limiting seat is also provided with a limiting chuck Ⅲ for limiting the movement of transmission component I (6) along the axial direction of lead screw I (5), and a limiting chuck VI for limiting the movement of transmission component II (9) along the axial direction of lead screw II (8).

10. A self-regulated differential multi-cylinder hydraulic synchronizer according to any one of claims 1-3, characterized in that: The hydraulic rods (18) connected to the piston (17) on the hydraulic cylinders I (1) and II (2) are partially hollow. The lead screw I (5) extends into one end of the hydraulic cylinder I (1) and is inserted into the hollow part of the hydraulic rod (18) of the hydraulic cylinder I (1); the lead screw II (8) extends into one end of the hydraulic cylinder II (2) and is inserted into the hollow part of the hydraulic rod (18) of the hydraulic cylinder II (2).

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