Heavy-load hydraulic cylinder, equipment and control method of heavy-load hydraulic cylinder

Abstract

The invention discloses a heavy-load hydraulic cylinder, equipment and a control method of the heavy-load hydraulic cylinder. The heavy-load hydraulic cylinder comprises a cylinder body and a plunger rod. Specifically, a first oil inlet channel is arranged at the bottom of the cylinder body; the plunger rod is movably arranged in the cylinder body, a plurality of static pressure cavities, a plurality of first oil cavities and a plurality of second oil cavities are formed in the plunger rod, and the static pressure cavities, the first oil cavities and the second oil cavities are evenly distributed in the circumferential direction of the plunger rod and in the axis direction of the plunger rod. The first oil cavity and the second oil cavity are symmetrically arranged on the two sides of the static pressure cavity. Wherein the first oil inlet channel is communicated with the first oil cavities and the second oil cavities, the plunger rod is further provided with a second oil inlet channel, and the second oil inlet channel is communicated with the static pressure cavities. The problems that in the prior art, a heavy-load hydraulic cylinder is uneven in bearing and poor in unbalance loading resistance can be solved at least.

Description

Technical Field

[0001] This application relates to the field of hydraulic transmission technology, and more specifically, to a heavy-duty hydraulic cylinder, equipment, and a control method for the heavy-duty hydraulic cylinder. Background Technology

[0002] In related technologies, the moving parts of heavy-duty hydraulic cylinders rely on the mechanical contact support of guide sleeves and seals. During startup and low-speed operation, the contact friction resistance changes nonlinearly, easily leading to low-speed crawling and poor motion stability. Simultaneously, contact friction causes wear on the moving parts, shortening the lifespan of the hydraulic cylinder and creating clearances, resulting in poor operating accuracy. Furthermore, when subjected to asymmetrical or overturning moment loads, existing heavy-duty hydraulic cylinders with single-chamber or simple multi-chamber hydrostatic support structures are prone to uneven oil film thickness, localized pressure loss, and even piston rod contact, leading to operational jamming, vibration, or loss of accuracy. Summary of the Invention

[0003] The main objective of this application is to provide a heavy-duty hydraulic cylinder, equipment, and control method for the heavy-duty hydraulic cylinder, so as to solve the problems of uneven load distribution and poor resistance to eccentric loads in the prior art.

[0004] According to one aspect of this application, a heavy-duty hydraulic cylinder is provided, comprising: The cylinder block has a first oil inlet channel at its bottom. A plunger rod is movably disposed within the cylinder body. The plunger rod is provided with a plurality of static pressure chambers, a plurality of first oil chambers, and a plurality of second oil chambers. The plurality of static pressure chambers, the plurality of first oil chambers, and the plurality of second oil chambers are all evenly distributed along the circumferential direction of the plunger rod and along the axial direction of the plunger rod. The first oil chambers and the second oil chambers are symmetrically disposed on both sides of the static pressure chambers. The first oil inlet channel is connected to each of the first oil chambers and each of the second oil chambers. The plunger rod is also provided with a second oil inlet channel, which is connected to each of the static pressure chambers.

[0005] Furthermore, along the circumferential direction of the plunger rod, the extended area of ​​the first oil cavity is equal to the extended area of ​​the second oil cavity.

[0006] Furthermore, the plunger rod is also provided with a plurality of throttles, which are evenly distributed along the circumferential direction of the plunger rod. Each of the plurality of throttles is provided in a one-to-one correspondence with a plurality of static pressure chambers. The throttles are used to regulate the pressure of the hydraulic oil entering the static pressure chamber.

[0007] Furthermore, the second oil inlet channel includes: The first oil inlet section has one end connected to an external oil supply device and the other end connected to a plurality of the throttles respectively. The second oil inlet section includes multiple second oil inlet sections, multiple throttles and multiple static pressure chambers are arranged in a one-to-one correspondence. One end of the second oil inlet section is connected to the oil outlet of the throttle, and the other end of the second oil inlet section is connected to the static pressure chamber. Each of the second oil inlet sections includes a first connecting section and a second connecting section. The first connecting section extends along the axial direction of the plunger rod and is perpendicularly connected to the second connecting section. The second connecting section extends along the interior of the plunger rod toward the outer peripheral side of the plunger rod.

[0008] Furthermore, both the first connecting segment and the second connecting segment include multiple segments. The multiple first connecting segments are evenly distributed along the circumferential direction of the plunger rod, and the multiple second connecting segments are evenly distributed along the circumferential direction of the plunger rod. The center lines of every two adjacent second connecting segments intersect to form an included angle A, and the angles of each included angle A are equal.

[0009] Furthermore, the plunger rod is provided with an oil inlet channel, which extends along the axial direction of the plunger rod and connects the first oil chamber, the second oil chamber, and the first oil inlet channel. Along the radial direction of the plunger rod, the plunger rod is also provided with a plurality of third oil inlet sections, and the plurality of third oil inlet sections are provided one-to-one with a plurality of first oil chambers, and each of the third oil inlet sections is connected to the oil inlet channel of the oil chamber; Along the radial direction of the plunger rod, the plunger rod is also provided with a plurality of fourth oil inlet sections, each of which is provided in a corresponding manner to a plurality of second oil chambers, and each of the fourth oil inlet sections is connected to the oil inlet channel of the oil chamber.

[0010] Furthermore, the oil inlet channel of the oil chamber is located at a position off-center from the center of the plunger rod.

[0011] Furthermore, the heavy-duty hydraulic cylinder is also equipped with a controller, a pressure detection element, a displacement detection element, and a tilt angle detection element. The controller is electrically connected to the pressure detection element, the displacement detection element, and the tilt angle detection element. The pressure detection element is disposed in the cylinder and is used to detect the pressure inside the cylinder; The displacement detection element is disposed on the plunger rod and is used to detect the displacement of the plunger rod; The tilt angle detection element is disposed on the plunger rod and is used to detect the tilt angle of the plunger rod.

[0012] Secondly, this application also provides a device comprising the aforementioned heavy-duty hydraulic cylinder.

[0013] Thirdly, this application also provides a control method for a heavy-duty hydraulic cylinder, which is used to control the aforementioned heavy-duty hydraulic cylinder. The control method for the heavy-duty hydraulic cylinder includes the following steps: S1: Hydraulic oil is supplied to the static pressure chamber through the second oil inlet channel; S2: Hydraulic oil is supplied to the cylinder body through the first oil inlet channel; S3: After the plunger rod moves to the target position in the cylinder, the first oil inlet channel and the second oil inlet channel maintain a stable oil supply.

[0014] In this application, a static pressure chamber, a first oil chamber, and a second oil chamber are provided on the plunger rod. The first and second oil chambers are symmetrically arranged on both sides of the static pressure chamber along the axial direction of the plunger rod. High-pressure hydraulic oil is introduced into the static pressure chamber through a second oil inlet channel, forming a static pressure oil film that directly bears most of the radial load, reducing contact wear between the plunger rod and the cylinder body. The symmetrically distributed first and second oil chambers are supplied with oil through the first oil inlet channel, which radially centers the plunger rod, counteracting the tilting caused by eccentric loading, avoiding localized stress concentration, and significantly improving the operational stability and service life of the hydraulic cylinder under heavy loads and high-frequency reciprocating motion. Attached Figure Description

[0015] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, are illustrative and descriptive, serving to explain this application and do not constitute an undue limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the structure of a heavy-duty hydraulic cylinder disclosed in an embodiment of this application; Figure 2 for Figure 1 A sectional view from a first-person perspective; Figure 3 for Figure 2 A magnified view of a portion of region A in the middle; Figure 4 for Figure 1 A cross-sectional view from a second-person perspective; Figure 5 for Figure 1 A cross-sectional view from a third-person perspective; Figure 6 This is a schematic diagram (I) of the structure of a piston rod of a heavy-duty hydraulic cylinder disclosed in an embodiment of this application; Figure 7 for Figure 6 A sectional view; Figure 8 This is a schematic diagram of the second oil inlet section on the plunger rod of a heavy-duty hydraulic cylinder disclosed in an embodiment of this application; Figure 9 This is a schematic diagram (II) of the structure of a piston rod of a heavy-duty hydraulic cylinder disclosed in an embodiment of this application; Figure 10 for Figure 9 A sectional view; Figure 11 This is a schematic diagram of the fourth oil inlet section on the plunger rod of a heavy-duty hydraulic cylinder disclosed in an embodiment of this application; Figure 12 This is a schematic diagram of the third oil inlet section on the plunger rod of a heavy-duty hydraulic cylinder disclosed in an embodiment of this application.

[0016] The above figures include the following reference numerals: 100. Heavy-duty hydraulic cylinder; 10. Cylinder body; 11. First oil inlet channel; 12. First oil inlet; 13. Second oil inlet; 20. Piston rod; 21. Static pressure chamber; 22. First oil chamber; 23. Second oil chamber; 24. Second oil inlet channel; 241. First oil inlet section; 242. Second oil inlet section; 2421. First connecting section; 2422. Second connecting section; 25. Throttling device; 26. Oil chamber inlet channel; 27. Third oil inlet section; 28. Fourth oil inlet section. Detailed Implementation

[0017] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0018] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0019] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0020] As described in the background section, in related technologies, the kinematic pairs of heavy-duty hydraulic cylinders rely on the mechanical contact support of guide sleeves and seals. During startup and low-speed operation, the contact friction resistance changes non-linearly, easily leading to low-speed crawling and poor motion stability. Simultaneously, contact friction causes wear on the kinematic pairs, shortening the lifespan of the hydraulic cylinder and creating gaps due to wear, resulting in poor operating accuracy. Furthermore, existing heavy-duty hydraulic cylinders, when subjected to asymmetrical or overturning moment loads, are prone to uneven oil film thickness, localized pressure loss, and even piston rod contact with the static pressure bearing structure, leading to operational jamming, vibration, or loss of accuracy. Therefore, this application provides a new heavy-duty hydraulic cylinder. This heavy-duty hydraulic cylinder solves the problems of uneven load distribution and poor resistance to eccentric loads by simultaneously setting a static pressure chamber and symmetrically arranging a first oil chamber and a second oil chamber on both sides of the static pressure chamber. The following description of the heavy-duty hydraulic cylinder of this application will be provided in conjunction with the accompanying drawings.

[0021] See Figures 1 to 12 As shown, this application embodiment provides a heavy-duty hydraulic cylinder 100. The heavy-duty hydraulic cylinder 100 includes a cylinder body 10 and a piston rod 20.

[0022] Specifically, a first oil inlet channel 11 is provided at the bottom of the cylinder body 10; the plunger rod 20 is movably disposed inside the cylinder body 10, and the plunger rod 20 is provided with a plurality of static pressure chambers 21, a plurality of first oil chambers 22 and a plurality of second oil chambers 23. The plurality of static pressure chambers 21, the plurality of first oil chambers 22 and the plurality of second oil chambers 23 are evenly distributed along the circumferential direction of the plunger rod 20, and along the axial direction of the plunger rod 20, the first oil chambers 22 and the second oil chambers 23 are symmetrically disposed on both sides of the static pressure chambers 21; wherein, the first oil inlet channel 11 is connected to each of the first oil chambers 22 and each of the second oil chambers 23, and the plunger rod 20 is also provided with a second oil inlet channel 24, which is connected to each of the static pressure chambers 21.

[0023] In actual operation, the static pressure chamber 21 is independently supplied with oil through the second oil inlet channel 24, forming an oil film between the plunger rod 20 and the cylinder body 10. This effectively avoids metal-to-metal contact between the plunger rod 20 and the inner wall of the cylinder body 10, significantly reducing friction and wear. It also provides extremely high radial and axial rigidity, ensuring stable operation of the plunger rod 20 under heavy loads and high transmission efficiency. Furthermore, in this application, the first oil chamber 22 and the second oil chamber 23 are symmetrically arranged on both sides of the static pressure chamber 21 along the axial direction of the plunger rod 20, and both are connected to the first oil inlet channel 11 located at the bottom of the cylinder body 10. This arrangement ensures that the support pressure on both sides of the static pressure chamber 21 remains automatically balanced. When the plunger rod 20 is subjected to an eccentric load and tends to tilt to one side, the clearance on that side decreases, the oil film resistance increases, and the pressure rises; simultaneously, the clearance on the other side increases, and the pressure decreases. This pressure difference generates a restoring force opposite to the direction of offset, automatically pushing the plunger rod 20 back to the center position.

[0024] Meanwhile, in this application, there are multiple static pressure chambers 21, first oil chambers 22, and second oil chambers 23, and these multiple static pressure chambers 21, first oil chambers 22, and second oil chambers 23 are all evenly distributed along the circumference of the plunger rod 20. This ensures that the oil film pressure is evenly distributed along the circumference of the plunger rod 20, avoiding problems such as plunger rod 20 jamming or uneven wear caused by excessively high or low pressure in some local oil chambers. For example, the number of static pressure chambers 21, first oil chambers 22, and second oil chambers 23 can be 2, 3, 4, or more. In this application, it is preferred that there are 4 static pressure chambers 21, first oil chambers 22, and second oil chambers 23. The oil film pressure of the four chambers forms a continuous pressure ring along the circumference, avoiding the circumferential pressure blind zone present in two chambers (180° apart) (for example, two chambers can only handle left-right loads and cannot effectively counteract tilting forces in the front-rear direction). This ensures that regardless of the angle of the load, it can be quickly offset by the oil film pressure of the corresponding chamber, preventing localized contact between the plunger rod 20 and the cylinder block 10. Furthermore, the four chambers are paired, allowing for coordinated pressure adjustment between opposite chambers to quickly balance radial forces, preventing the plunger rod 20 from jamming or wearing unevenly. This is particularly suitable for high-frequency reciprocating motion under heavy load conditions. For example, when the plunger rod 20 is biased to the left, the pressure in the left chamber increases, and the pressure in the right chamber adaptively compensates.

[0025] Furthermore, in this application, the first oil inlet channel 11 and the second oil inlet channel 24 are independently configured, allowing for adjustment of the oil supply pressure and flow rate into the first oil chamber 22, the second oil chamber 23, and the static pressure chamber 21, respectively. For different heavy loads, the oil supply pressure of the static pressure chamber 21 can be adjusted to match the load requirements. The oil supply flow rate of the first oil chamber 22 and the second oil chamber 23 can also be adjusted according to the reciprocating speed of the piston rod 20, optimizing the anti-tilting effect of the piston rod 20 and improving the smoothness of its movement. This independently adjustable design enables the hydraulic cylinder to adapt to different heavy-load conditions, improving the versatility and adaptability of the equipment.

[0026] Furthermore, in this application, the first oil inlet channel 11 is connected to each of the first oil chambers 22 and each of the second oil chambers 23. Within the support range of the static pressure chamber 21, the first oil chambers 22 and the second oil chambers 23 play a major driving role, while the static pressure chamber 21 mainly plays a static pressure support role. When the load exceeds the support range of the static pressure chamber 21, the pressure in the first oil chambers 22 and the second oil chambers 23 increases, and the amount of hydraulic oil entering the first oil chambers 22 and the second oil chambers 23 increases. This further improves the stability of the oil film formed between the plunger rod 20 and the inner wall of the cylinder body 10, avoids oil film collapse causing friction between the plunger rod 20 and the cylinder body 10, and thus extends the service life of the heavy-duty hydraulic cylinder 100.

[0027] In other words, in this application, a static pressure chamber 21, a first oil chamber 22, and a second oil chamber 23 are provided on the plunger rod 20. Along the axial direction of the plunger rod 20, the first oil chamber 22 and the second oil chamber 23 are symmetrically arranged on both sides of the static pressure chamber 21. The static pressure chamber 21 introduces high-pressure hydraulic oil through the second oil inlet channel 24, forming a static pressure oil film that directly bears most of the radial load, reducing contact wear between the plunger rod 20 and the cylinder body 10. The symmetrically distributed first oil chamber 22 and second oil chamber 23 are supplied with oil through the first oil inlet channel 11, which radially centers the plunger rod 20, counteracting the tilting of the plunger rod 20 caused by eccentric loading, avoiding local stress concentration, and significantly improving the operational stability and service life of the hydraulic cylinder under heavy load and high-frequency reciprocating motion.

[0028] like Figure 1 As shown in this application, the cylinder body 10 is provided with a first oil inlet 12 communicating with the first oil inlet channel 11, and a second oil inlet 13 communicating with the second oil inlet channel 24 is also provided on the cylinder body 10. This arrangement facilitates communication with the oil inlet channel on the plunger rod 20.

[0029] like Figure 6 and Figure 9As shown, along the circumferential direction of the plunger rod 20, the extended area of ​​the first oil chamber 22 is equal to the extended area of ​​the second oil chamber 23. It can be understood that the extended area refers to the actual bearing area of ​​the first oil chamber 22 and the second oil chamber 23 on the outer circumferential side of the plunger rod 20, which can form an effective static pressure oil film with the inner wall of the cylinder block 10 and generate radial constraint force. In this application, the first oil chamber 22 and the second oil chamber 23 are located on both sides of the static pressure chamber 21 and are supplied with oil through the same first oil inlet channel 11. Therefore, in actual operation, the oil pressure inside the first oil chamber 22 and the second oil chamber 23 is basically the same. Along the circumferential direction of the plunger rod 20, when the extended areas of the first oil chamber 22 and the second oil chamber 23 are equal, under the same oil supply pressure, the radial constraint force generated by the oil films on both sides is consistent in magnitude, forming a bidirectional symmetrical clamping stabilizing effect, and more accurately offsetting off-center loads.

[0030] Under heavy load conditions, if the plunger rod 20 experiences radial off-center loading due to axial load deviation and motion inertia (such as tilting to the left), the oil chambers with equal extension areas on both sides can adaptively adjust through oil film pressure (increasing pressure in the left oil chamber and simultaneously compensating on the right), forming a centering reaction force of equal magnitude and opposite direction. This precisely counteracts the off-center loading, preventing the plunger rod 20 from tilting to either side and ensuring that it remains at the central axis of the cylinder block 10. Simultaneously, the symmetrical extension areas of the oil chambers ensure that the hydraulic pressure on both sides of the plunger rod 20 is uniform during extension and retraction, reducing vibration and shaking. Combined with the supporting effect of the hydrostatic chamber 21, this further enhances the precision of linear motion under low-speed, heavy-load conditions.

[0031] Figure 1 , Figures 6 to 10 As shown, the plunger rod 20 is also provided with a plurality of throttles 25, which are evenly distributed along the circumferential direction of the plunger rod 20. Each throttle 25 corresponds to one of the plurality of static pressure chambers 21, and the throttles 25 are used to regulate the pressure of the hydraulic oil entering the static pressure chambers 21. Exemplarily, in this application, the number of throttles 25 can be 2, 3, 4, or more. In this application, the accompanying drawings show the case where there are 4 throttles 25. The throttles 25 can be diaphragm feedback throttles, etc.

[0032] Specifically, in actual operation, since the radial load of the heavy-duty hydraulic cylinder 100 may have uneven circumferential distribution, the throttle valves 25 are set one-to-one with the static pressure chambers 21, allowing the oil supply pressure of each static pressure chamber 21 to be independently adjustable. In this application, the four throttle valves 25 are evenly distributed along the circumference of the plunger rod 20, which can cooperate with the circumferential layout of the static pressure chambers 21. When the plunger rod 20 experiences circumferential load fluctuations due to motion inertia or off-center loading, the evenly distributed independent throttle valves 25 can respond synchronously, and the pressure of each static pressure chamber 21 is adjusted collaboratively to maintain the dynamic balance of the oil film pressure in the circumference of the plunger rod 20, preventing the local oil film from rupturing due to insufficient pressure (causing direct contact wear between the plunger rod 20 and the cylinder body 10). Especially under harsh operating conditions such as low speed, heavy load, and frequent start-stop, the throttle valves 25 can effectively avoid creeping and extend the life of seals and moving parts.

[0033] Furthermore, in this application, the throttle 25 is a diaphragm feedback throttle, which can adjust the flow rate in real time according to the actual load of each static pressure chamber 21 to ensure pressure balance and smooth operation.

[0034] like Figure 8 and Figure 10 As shown, the second oil inlet channel 24 includes a first oil inlet section 241 and a second oil inlet section 242. One end of the first oil inlet section 241 is connected to an external oil supply device (not shown in the figure), and the other end of the first oil inlet section 241 is connected to a plurality of throttles 25 respectively. The second oil inlet section 242 includes a plurality of sections, and the plurality of second oil inlet sections 242, the plurality of throttles 25 and the plurality of static pressure chambers 21 are arranged in a corresponding manner. One end of the second oil inlet section 242 is connected to the oil outlet of the throttle 25, and the other end of the second oil inlet section 242 is connected to the static pressure chamber 21. Each second oil inlet section 242 includes a first connecting section 2421 and a second connecting section 2422. The first connecting section 2421 extends along the axial direction of the plunger rod 20, and the first connecting section 2421 and the second connecting section 2422 are perpendicularly connected. The second connecting section 2422 extends along the interior of the plunger rod 20 toward the outer peripheral side of the plunger rod 20. In this application, the number of second oil inlet sections 242 is set in a one-to-one correspondence with the number of static pressure chambers 21 and throttles 25, that is, the number of second oil inlet sections 242 is 4.

[0035] Specifically, in this application, the first oil inlet section 241 is used to connect the external oil supply device and the throttle 25. In this application, the first oil inlet section 241 is further divided into four branches through the main oil inlet pipeline, entering the diaphragm feedback throttle. After the hydraulic oil pressure is regulated by the diaphragm feedback throttle, it then enters the four static pressure chambers 21 through the second oil inlet section 242. This arrangement ensures that the pressure of the oil source entering each static pressure chamber 21 is the same and stable. Simultaneously, the independent oil supply to each static pressure chamber 21 facilitates precise pressure regulation of a single static pressure chamber 21, enhancing the system's controllability. It is understood that since each static pressure chamber 21 has an independent oil circuit (composed of the throttle 25 and the second oil inlet section 242) directly supplied, the system can respond more quickly to load changes or motion state adjustments, thereby improving the dynamic performance of the entire hydraulic cylinder.

[0036] Meanwhile, the first connecting section 2421 extends along the axis of the plunger rod 20, directly extending axially from the branch point of the first oil inlet section 241 to the circumferential position of the corresponding static pressure chamber 21, thus straightening the path; the second connecting section 2422 extends radially, vertically penetrating to the static pressure chamber 21 on the outer periphery of the plunger rod 20, without the need for detours. This axial + radial vertical path minimizes the flow distance of the oil from the throttle 25 to the static pressure chamber 21, reducing flow resistance and effectively avoiding pressure loss and oil stagnation caused by pipe bends or excessive length. This ensures that the pressure regulated by the throttle 25 is accurately transmitted to the static pressure chamber 21, maintaining oil film stability.

[0037] Furthermore, since the piston rod 20 needs to simultaneously arrange the connecting oil passages of the first oil chamber 22 and the second oil chamber 23, the structure of the second oil inlet channel 24 can make full use of the internal space of the piston rod 20, and will not interfere with the oil passages or external sealing structures of the first oil chamber 22 and the second oil chamber 23 located on both sides of the static pressure chamber 21. It can also reduce the overall volume of the hydraulic cylinder, which is conducive to integrating more functional components in a limited space.

[0038] like Figure 5 and Figure 8 As shown, both the first connecting segment 2421 and the second connecting segment 2422 comprise multiple segments. The multiple first connecting segments 2421 are evenly distributed along the circumferential direction of the plunger rod 20, and the multiple second connecting segments 2422 are also evenly distributed along the circumferential direction of the plunger rod 20. The centerlines of every two adjacent second connecting segments 2422 intersect to form an angle A, and all angles A are equal. In this application, there are four first connecting segments 2421 and four second connecting segments 2422.

[0039] It is understandable that the circumferentially uniform arrangement of the first connecting section 2421 and the second connecting section 2422 on the plunger rod 20 ensures that the oil path to each hydrostatic chamber 21 is symmetrical and uniform when the hydraulic cylinder is subjected to radial or axial loads. Furthermore, in this application, when multiple second connecting sections 2422 are arranged at equal angles around the central axis, each second connecting section 2422 exhibits rotational symmetry in the circumferential direction of the plunger rod 20. When there is an eccentric load or impact, the multi-point symmetrical support can automatically balance the torque, suppressing the plunger rod 20 from tilting or jamming, and enhancing its resistance to eccentric loads. In addition, this arrangement can avoid unbalanced inertial forces or hydraulic oil pulsation caused by structural asymmetry, reducing the vibration and noise of the plunger rod 20 during operation, and contributing to improving the dynamic stiffness and reliability of the heavy-duty hydraulic cylinder 100.

[0040] like Figures 1 to 5 , Figure 7 , Figure 11 as well as Figure 12 As shown, the plunger rod 20 is provided with an oil inlet channel 26, which extends along the axial direction of the plunger rod 20 and connects the first oil chamber 22, the second oil chamber 23, and the first oil inlet channel 11. Along the radial direction of the plunger rod 20, the plunger rod 20 is also provided with a plurality of third oil inlet sections 27, which are arranged one-to-one with a plurality of first oil chambers 22, and each third oil inlet section 27 is connected to the oil inlet channel 26. Along the radial direction of the plunger rod 20, the plunger rod 20 is also provided with a plurality of fourth oil inlet sections 28, which are arranged one-to-one with a plurality of second oil chambers 23, and each fourth oil inlet section 28 is connected to the oil inlet channel 26.

[0041] Specifically, in this application, the oil inlet channel 26 extends along the axial direction of the plunger rod 20, serving as the main channel for centralized oil supply. This allows the hydraulic oil entering the cylinder 10 from the first oil inlet channel 11 to maintain stable axial pressure, avoiding pressure drop caused by varying oil passage lengths. The third oil inlet section 27 serves as a radial branch channel into the first oil chamber 22, and the fourth oil inlet section 28 serves as a radial branch channel into the second oil chamber 23. This synchronously distributes the hydraulic oil in the oil inlet channel 26 to each of the first and second oil chambers 22 and 23, ensuring that each chamber receives hydraulic oil with almost the same pressure and flow rate. This avoids uneven thrust caused by differences in flow path length or resistance, ensuring symmetrical force distribution and smooth movement of the plunger rod 20. When subjected to eccentric loads or impact loads, the oil chambers in each direction can work together to provide uniform reaction force or compensating force, effectively suppressing tilting, jamming, or localized wear of the plunger rod 20.

[0042] Furthermore, when the load exceeds the support range of the static pressure chamber 21, and the oil film formed between the first oil chamber 22 and the second oil chamber 23 and the inner wall of the cylinder 10 is required for support, this oil circuit with unified oil supply through the oil inlet channel 26 and branch sections directly reaching the first oil chamber 22 and the second oil chamber 23 can instantly transmit oil pressure changes to all oil chambers, and the pressure response of each oil chamber is lag-free. It can quickly balance the load through the pressure difference on both sides, and avoid the static pressure oil film from collapsing due to untimely overload response.

[0043] Furthermore, in this application, the oil inlet channel 26 is dedicated to supplying oil to the first oil chamber 22 and the second oil chamber 23, and is completely independent of the second oil inlet channel 24, with their pressure fluctuations not affecting each other. Moreover, the radial third oil inlet section 27 and fourth oil inlet section 28 are only responsible for transporting the oil in the oil inlet channel 26 to the corresponding oil chamber, and will not intersect with the second oil inlet channel 24 leading to the static pressure chamber 21, further ensuring the decoupling of the drive / auxiliary support function from the suspension support function.

[0044] Furthermore, in this application, the third oil inlet section 27, the fourth oil inlet section 28, and the oil inlet channel 26 are integrated inside the plunger rod 20, simplifying external pipeline connections, reducing the risk of hydraulic oil leakage, and improving system sealing and long-term operational reliability, making it particularly suitable for high-pressure, heavy-load conditions. This design also facilitates a more compact hydraulic cylinder structure.

[0045] like Figure 11 and Figure 12 As shown, the oil inlet channel 26 is located off-center from the center of the plunger rod 20. It is understood that the plunger rod 20 primarily bears axial compression or tensile loads under heavy load conditions, and its central region is the critical path for stress transmission. The eccentric arrangement of the oil inlet channel 26 avoids weakening the core stress area, maximizing the mechanical strength and rigidity of the plunger rod 20. Simultaneously, this arrangement allows for independent layout of the first oil inlet channel 11 and the second oil inlet channel 24, ensuring that their functions do not interfere with each other. It is worth noting that in this application, the eccentric arrangement may result in different lengths of the third oil inlet sections 27 and the fourth oil inlet sections 28 leading to the first oil chamber 22 and the second oil chamber 23. However, in this application, the conventional function of the first oil chamber 22 and the second oil chamber 23 is to provide axial drive and radial auxiliary support during overload, rather than high-precision pressure control; therefore, a certain margin of error is required for pressure uniformity. Even with a small pressure difference, under the action of equal areas, the final output thrust can remain balanced, preventing overturning moments.

[0046] Furthermore, the heavy-duty hydraulic cylinder 100 is also equipped with a controller (not shown in the figure), a pressure detection element (not shown in the figure), a displacement detection element (not shown in the figure), and a tilt angle detection element (not shown in the figure). The controller is electrically connected to the pressure detection element, the displacement detection element, and the tilt angle detection element. The pressure detection element is located on the cylinder body 10 and is used to detect the pressure within the cylinder body 10; the displacement detection element is located on the piston rod 20 and is used to detect the displacement of the piston rod 20; the tilt angle detection element is located on the piston rod 20 and is used to detect the tilt angle of the piston rod 20. For example, the pressure detection element is a pressure sensor, the displacement detection element is a displacement sensor, and the tilt angle detection element is a tilt angle sensor.

[0047] It is understood that in this application, by integrating a controller, pressure detection element, displacement detection element and tilt angle detection element on the heavy-duty hydraulic cylinder 100, and realizing the electrical connection between each sensor and the controller, a closed-loop intelligent sensing and control system is formed.

[0048] Specifically, the pressure detection element can be installed on the cylinder block 10 to collect oil pressure data of the static pressure chamber 21, the first oil chamber 22, and the second oil chamber 23 in real time. It can quickly identify anomalies such as a sudden pressure drop in the static pressure chamber 21 (oil film nearing collapse) and pressure imbalance in the first and second oil chambers 22 (uneven thrust / auxiliary support force), providing real-time basis for overload compensation and pressure adjustment, and preventing structural damage caused by deteriorating operating conditions. The displacement detection element is used to track the axial movement trajectory of the piston rod 20 in real time, accurately feeding back displacement deviations to ensure precise arrival at the target position during heavy-load drive, while avoiding displacement drift during long-stroke motion and adapting to corresponding positioning requirements. The tilt angle detection element is used to monitor the tilt angle of the piston rod 20 in real time, directly capturing abnormal postures caused by off-center loading. Especially when the load exceeds the adjustment range of the static pressure chamber 21, it can quickly trigger radial compensation adjustment of the first and second oil chambers 22 and 23, preventing tilting from exacerbating oil film compression.

[0049] When the tilt angle detection element identifies off-center load and the pressure detection element confirms that the pressure in the static pressure chamber 21 has reached its adjustment limit, the controller immediately instructs the first oil chamber 22 and the second oil chamber 23 to fine-tune the pressure difference, quickly sharing the overload radial force while maintaining the stability of the oil film in the static pressure chamber 21, achieving precise compensation under overload conditions. After the overload subsides, the supporting force of the first oil chamber 22 and the second oil chamber 23 is gradually reduced, restoring the dominant position of the static pressure chamber 21. The oil pressure in the cylinder block 10 is corrected by displacement detection data to control the smooth movement speed of the plunger rod 20 (without overshoot or lag); the oil supply pressure of the static pressure chamber 21 is calibrated by pressure detection data to maintain a constant oil film thickness; and the attitude is corrected in real time by tilt angle data to avoid movement deviation caused by off-center load. The combination of these three factors achieves "crawling-free, high-precision, and stable attitude" movement.

[0050] Secondly, this application also provides a device that includes the aforementioned heavy-duty hydraulic cylinder 100. Therefore, the device provided in this embodiment includes all the technical effects of the aforementioned heavy-duty hydraulic cylinder 100. Since the technical effects of the heavy-duty hydraulic cylinder 100 have been described in detail above, they will not be repeated here.

[0051] Thirdly, this application also provides a control method for a heavy-duty hydraulic cylinder, which is used to control the aforementioned heavy-duty hydraulic cylinder 100. The control method includes the following steps: S1: Hydraulic oil is supplied to the static pressure chamber 21 through the second oil inlet channel 24; S2: Hydraulic oil is supplied to the cylinder 10 through the first oil inlet channel 11; S3: After the plunger rod 20 moves to the target position in the cylinder block 10, the first oil inlet channel 11 and the second oil inlet channel 24 maintain stable oil supply.

[0052] Specifically, in actual operation, during the pre-suspension stage: firstly, the hydraulic station of the static pressure chamber 21 is opened, and the hydraulic oil is delivered to each static pressure chamber 21 after being regulated by the throttle 25 through the second oil inlet channel 24, causing the plunger rod 20 to suspend within the cylinder body 10. At this time, a uniform oil film is formed between the plunger rod 20 and the cylinder body 10, achieving non-contact support. During this process, the pressure inside the cylinder body 10 is detected by a pressure detection element to ensure stable oil film support. Furthermore, the diaphragm-type feedback throttle adjusts the flow rate in real time according to the actual load of the static pressure chamber 21, ensuring pressure balance and smooth movement. In this application, the plunger rod 20 is first placed in a suspended state, achieving zero-friction start-up. The plunger rod 20 is already in a suspended state before starting to move, completely eliminating the stick-slip effect (creeping phenomenon) during the transition from static friction to dynamic friction, which is crucial for precision motion. Simultaneously, it avoids huge frictional torque and wear during startup.

[0053] During the driving phase, after a uniform oil film is formed, the hydraulic cylinder is activated. Hydraulic oil is injected into the cylinder body 10 through the first oil inlet channel 11. The hydraulic oil then enters the first oil chamber 22 and the second oil chamber 23 through the oil chamber inlet channel 26. Hydraulic oil also overflows through the oil outlet holes on the first and second oil chambers 22 and 23, forming an oil film between the plunger rod 20 and the cylinder body 10. During this process, the pressure inside the cylinder body 10 is monitored by a pressure detection element to ensure stable oil film support. That is, only after step S1 is completed and the plunger rod 20 is reliably suspended is oil supplied through the first oil inlet channel 11 to drive the plunger rod 20 axially. The driving occurs under conditions without solid contact; the thrust is entirely transmitted by the oil, avoiding potential damage, jamming, or loss of accuracy that could result from forced driving under contact friction. Due to the extremely low motion resistance (only fluid shear force), the energy required for driving is significantly reduced, and the system efficiency is significantly improved. The piston rod 20 in the suspended state has uniform motion inertia, and the control system can more accurately control its acceleration, speed and position.

[0054] During the pressure holding and positioning phase, when the hydraulic oil in the cylinder 10 pushes the plunger rod 20 to move axially, and the plunger rod 20 moves to the target position, both the first oil inlet channel 11 and the second oil inlet channel 24 maintain continuous oil supply and pressure holding. During this process, the tilt detection element installed on the plunger rod 20 detects whether the plunger rod 20 has shifted. That is, after reaching the target position, the oil circuit is not immediately cut off; instead, the hydrostatic system and the drive system simultaneously stabilize the oil supply pressure. The plunger rod 20 continues to maintain a non-contact suspended state at the target position, eliminating static friction, creep, and positioning drift caused by the disappearance of the oil film due to pressure relief, the plunger rod 20 sinking and contacting the cylinder 10. Continuous pressure ensures oil film thickness and system rigidity, allowing the plunger rod 20 to maintain positional stability even under varying loads, achieving true "rigid" pressure holding. Because the suspended state is maintained, the system can instantly and smoothly transition from the pressure holding state to the next drive phase, with extremely fast response speed. When the piston rod 20 in the hydraulic cylinder needs to be reset to its initial position, the piston rod 20 is gradually reset by gradually reducing the oil supply.

[0055] In other words, in this application, the three-step control process reserves response space for the auxiliary support of the first oil chamber 22 and the second oil chamber 23 under overload conditions. When the load exceeds the adjustment range of the static pressure chamber 21, the controller can fine-tune the pressure distribution of the first oil chamber 22 and the second oil chamber 23 in stages S2 and S3 based on pressure and tilt angle detection data. Radial auxiliary support can be achieved simply by adjusting the pressure parameters without changing the core timing, which greatly simplifies the control logic and improves the reliability of the system.

[0056] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects: This application provides a multi-chamber hydrostatic support system between the piston rod 20 and the cylinder body 10 by simultaneously providing a hydrostatic chamber 21, a first oil chamber 22, and a second oil chamber 23 on the piston rod 20. This system forms a uniform bearing oil film, reducing contact wear between the piston rod 20 and the cylinder body 10. The symmetrically distributed first oil chamber 22 and second oil chamber 23 are supplied with oil through the first oil inlet channel 11, which radially centers the piston rod 20, counteracting the tilting caused by eccentric loading, avoiding localized stress concentration, and significantly improving the operational stability and service life of the hydraulic cylinder under heavy loads and high-frequency reciprocating motion.

[0057] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0058] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0059] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A heavy-duty hydraulic cylinder, characterized in that, include: Cylinder body (10), the bottom of which is provided with a first oil inlet channel (11); A plunger rod (20) is movably disposed within the cylinder body (10). The plunger rod (20) is provided with a plurality of static pressure chambers (21), a plurality of first oil chambers (22), and a plurality of second oil chambers (23). The plurality of static pressure chambers (21), the plurality of first oil chambers (22), and the plurality of second oil chambers (23) are all evenly distributed along the circumferential direction of the plunger rod (20), and along the axial direction of the plunger rod (20), the first oil chambers (22) and the second oil chambers (23) are symmetrically disposed on both sides of the static pressure chambers (21). The first oil inlet channel (11) is connected to each of the first oil chambers (22) and each of the second oil chambers (23), and the plunger rod (20) is also provided with a second oil inlet channel (24), which is connected to each of the static pressure chambers (21).

2. The heavy-duty hydraulic cylinder according to claim 1, characterized in that, Along the circumferential direction of the plunger rod (20), the extended area of ​​the first oil cavity (22) is equal to the extended area of ​​the second oil cavity (23).

3. The heavy-duty hydraulic cylinder according to claim 1, characterized in that, The plunger rod (20) is also provided with a plurality of throttles (25), which are evenly distributed along the circumferential direction of the plunger rod (20). The plurality of throttles (25) are provided in a one-to-one correspondence with the plurality of static pressure chambers (21). The throttles (25) are used to regulate the pressure of the hydraulic oil entering the static pressure chamber (21).

4. The heavy-duty hydraulic cylinder according to claim 3, characterized in that, The second oil inlet channel (24) includes: The first oil inlet section (241) has one end connected to an external oil supply device and the other end connected to a plurality of the throttles (25); The second oil inlet section (242) includes multiple sections, and multiple second oil inlet sections (242), multiple throttles (25) and multiple static pressure chambers (21) are arranged in a one-to-one correspondence. One end of the second oil inlet section (242) is connected to the oil outlet of the throttle (25), and the other end of the second oil inlet section (242) is connected to the static pressure chamber (21). Each of the second oil inlet sections (242) includes a first connecting section (2421) and a second connecting section (2422). The first connecting section (2421) extends along the axial direction of the plunger rod (20). The first connecting section (2421) and the second connecting section (2422) are perpendicularly connected. The second connecting section (2422) extends along the interior of the plunger rod (20) toward the outer peripheral side of the plunger rod (20).

5. The heavy-duty hydraulic cylinder according to claim 4, characterized in that, Both the first connecting segment (2421) and the second connecting segment (2422) include multiple segments. The multiple first connecting segments (2421) are evenly distributed along the circumferential direction of the plunger rod (20), and the multiple second connecting segments (2422) are evenly distributed along the circumferential direction of the plunger rod (20). The center lines of every two adjacent second connecting segments (2422) intersect to form an included angle A, and the angles of each included angle A are equal.

6. The heavy-duty hydraulic cylinder according to claim 1, characterized in that, The plunger rod (20) is provided with an oil inlet channel (26), which extends along the axial direction of the plunger rod (20) and connects the first oil chamber (22), the second oil chamber (23) and the first oil inlet channel (11). Along the radial direction of the plunger rod (20), the plunger rod (20) is also provided with a plurality of third oil inlet sections (27), the plurality of third oil inlet sections (27) are provided one-to-one with a plurality of first oil chambers (22), and each of the third oil inlet sections (27) is connected to the oil inlet channel (26) of the oil chamber; Along the radial direction of the plunger rod (20), a plurality of fourth oil inlet sections (28) are also provided on the plunger rod (20). The plurality of fourth oil inlet sections (28) are provided one-to-one with the plurality of second oil chambers (23), and each of the fourth oil inlet sections (28) is connected to the oil inlet channel (26) of the oil chamber.

7. The heavy-duty hydraulic cylinder according to claim 6, characterized in that, The oil inlet channel (26) is located at a position off the center of the plunger rod (20).

8. The heavy-duty hydraulic cylinder according to any one of claims 1 to 7, characterized in that, The heavy-duty hydraulic cylinder (100) is also equipped with a controller, a pressure detection element, a displacement detection element, and a tilt angle detection element. The controller is electrically connected to the pressure detection element, the displacement detection element, and the tilt angle detection element. The pressure detection element is disposed in the cylinder (10) and is used to detect the pressure inside the cylinder (10); The displacement detection element is disposed on the plunger rod (20) and is used to detect the displacement of the plunger rod (20); The tilt angle detection element is disposed on the plunger rod (20) and is used to detect the tilt angle of the plunger rod (20).

9. A device, characterized in that, The device includes a heavy-duty hydraulic cylinder (100) as described in any one of claims 1 to 8.

10. A control method for a heavy-duty hydraulic cylinder, characterized in that, The control method for the heavy-duty hydraulic cylinder is used to control the heavy-duty hydraulic cylinder (100) according to any one of claims 1 to 8, and the control method for the heavy-duty hydraulic cylinder includes the following steps: S1: Hydraulic oil is supplied to the static pressure chamber (21) through the second oil inlet channel (24); S2: Hydraulic oil is supplied to the cylinder (10) through the first oil inlet channel (11); S3: When the plunger rod (20) moves to the target position in the cylinder (10), the first oil inlet channel (11) and the second oil inlet channel (24) maintain stable oil supply.

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