High-pressure large-flow hydraulic oil cylinder

Abstract

The invention discloses a high-pressure large-flow hydraulic oil cylinder, which belongs to the technical field of hydraulic cylinders, and comprises a cylinder body and a piston structure, the piston structure divides the cylinder body into a high-pressure oil liquid cavity and a rod cavity, and the piston structure comprises a first side wall, a second side wall and a third side wall which are sequentially communicated from the high-pressure oil liquid cavity to the rod cavity; a first gap, a second gap and a third gap are respectively formed between the first side wall, the second side wall and the third side wall and the inner wall of the cylinder body, the gap widths of the second gap, the first gap and the third gap are sequentially reduced, a first annular groove is formed in the first side wall and is communicated with the first gap, and a third annular groove is formed in the third side wall and is communicated with the third gap; one end of the third annular groove communicates with the third gap, and the other end communicates with the high-pressure oil cavity through a high-pressure channel. By arranging the three-section type gap between the piston structure and the inner wall of the cylinder body, different effects of oil liquid in different gaps are achieved, and it is guaranteed that the piston structure stably moves under the high-pressure and large-flow condition.

Description

Technical Field

[0001] This invention relates to the field of hydraulic cylinder technology, and in particular to a high-pressure, high-flow hydraulic cylinder. Background Technology

[0002] A hydraulic cylinder is a hydraulic actuator that converts hydraulic energy into mechanical energy, performing linear reciprocating motion (or oscillating motion). It has a simple structure and reliable operation. When used to achieve reciprocating motion, it eliminates the need for a speed reduction device, has no transmission backlash, and provides smooth movement. Therefore, it is widely used in the hydraulic systems of various machines. There are many types of hydraulic cylinders. The core difference between high-pressure, high-flow hydraulic cylinders and ordinary hydraulic cylinders lies in the high-pressure, high-flow operating conditions. The impact of high-pressure, high-flow oil on the cylinder's inner wall can cause problems such as seal wear, lubrication failure, and response delay in the piston structure.

[0003] Traditional hydraulic cylinder piston structures are designed to balance sealing and lubrication in a single structure. They achieve sealing and lubrication solely through a fixed gap between the piston and cylinder wall and the passive coordination of a single seal. While simple in structure, this design is unsuitable for high-pressure, high-flow-rate applications. The balance between sealing and lubrication relies on compromises. For example, traditional piston structures use a fixed gap between the piston and cylinder wall. This gap must be at least as large as the minimum gap for oil film formation and not exceed the maximum gap for sealing. Therefore, a compromise value is chosen. However, this design is unsuitable for high-pressure, high-flow-rate oil, and the formed oil film is easily washed away and broken. Increasing the gap, on the other hand, affects the sealing effect. Thus, the existing balanced design of hydraulic cylinders has certain defects. Summary of the Invention

[0004] The purpose of this invention is to solve the problem that hydraulic cylinders are difficult to balance lubrication and sealing under high pressure and high flow conditions, and to provide a high pressure and high flow hydraulic cylinder with a three-stage clearance design, which provides good sealing and stable lubrication under high pressure and high flow conditions.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows: A high-pressure, high-flow hydraulic cylinder includes a cylinder body and a piston structure. The piston structure divides the cylinder body into a high-pressure oil chamber and a rod chamber. The piston structure includes a first sidewall, a second sidewall, and a third sidewall that are sequentially connected from the high-pressure oil chamber to the rod chamber. The first sidewall, the second sidewall, and the third sidewall form a first gap, a second gap, and a third gap with the inner wall of the cylinder body, respectively. The gap widths of the second gap, the first gap, and the third gap decrease sequentially. A first annular groove is formed on the first sidewall, and the first annular groove communicates with the first gap. A third annular groove is formed on the third sidewall, one end of the third annular groove communicates with the third gap, and the other end communicates with the high-pressure oil chamber through a high-pressure channel.

[0006] Preferably, the bottom of the piston structure is also provided with a connecting hole, and the first annular groove is connected to the high-pressure oil chamber through the connecting hole.

[0007] Preferably, the internal volume of the first annular groove is greater than the internal volume of the third annular groove.

[0008] Preferably, the length of the second sidewall is greater than the lengths of the first sidewall and the third sidewall, respectively.

[0009] Preferably, a second annular groove is formed on the second sidewall, the second annular groove is connected to the second gap, and the opening diameter of the second annular groove is wider than the bottom diameter.

[0010] Preferably, the second annular groove is provided in multiple parts and is evenly distributed along the length direction of the second sidewall.

[0011] Preferably, the high-pressure channel includes multiple branch channels and a main channel connected to the branch channels. The branch channels are connected to the third annular groove, and the main channel is connected to the high-pressure oil chamber.

[0012] Preferably, the branch channels are circumferentially distributed on the main channel, and the bottom of the piston structure connected to the main channel is the channel opening. The channel opening is set in a conical structure, and the end near the high-pressure oil chamber is the large-diameter end of the conical structure.

[0013] Preferably, the bottom end of the cylinder is provided with an oil inlet, one end of which is connected to the high-pressure oil chamber, and the other end is provided with an oil inlet pipe. The oil inlet is inclined at an angle between 30-60° and the cylinder axis.

[0014] Preferably, the top of the cylinder block is further provided with a cylinder head and an exhaust valve, a piston rod is installed on the top of the piston structure, the piston rod passes through the cylinder head, and a sealing structure is provided at the connection between the piston rod and the cylinder head.

[0015] Compared with the prior art, the present invention has the following beneficial effects: 1. This invention achieves different effects for the oil in different gaps by setting a three-section gap between the piston structure and the inner wall of the cylinder. When the oil enters the first gap from the high-pressure oil chamber, the first annular groove provides a storage function, reducing the pressure of the high-pressure oil and allowing the oil to enter the second gap at a stable low pressure. Because the oil pressure and flow rate are stable, it is easier to generate a lubricating oil film in the second gap, avoiding wear during piston structure movement. The oil directly enters the third annular groove from the high-pressure oil chamber, forming a throttling effect, effectively preventing the oil from flowing into the rod chamber from the third gap and causing oil leakage. This avoids the force of the oil pushing the piston structure being consumed. Moreover, the throttling effect of the third annular groove can also affect the oil in the second gap from entering the third gap, thereby ensuring that the oil can be stored in the second gap for a long time, maintaining the lubrication time and prolonging the lubrication effect.

[0016] 2. By providing a separate connecting hole on the first annular groove, which is not connected to the high-pressure channel, the present invention allows the oil in the high-pressure oil chamber to enter the first annular groove when it comes into contact with the piston structure, forming a liquid storage effect, thereby quickly providing enough oil to the second gap and reducing the wear of the piston structure during the initial movement.

[0017] 3. By also creating an annular groove on the second sidewall to store excess oil, the present invention can further extend the lubrication time provided by the oil.

[0018] 4. By setting an inclined oil inlet, the present invention can ensure that the high-pressure oil is directed towards the piston structure better, avoiding impact on the cylinder block and affecting the response speed of the piston structure. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the overall structure of the high-pressure, high-flow hydraulic cylinder of the present invention.

[0020] Figure 2 This is a schematic diagram of the piston structure of the present invention.

[0021] Figure 3 This is a magnified structural diagram of region A of the present invention.

[0022] Figure 4 This is a schematic diagram of the cross-sectional structure of the high-pressure channel of the present invention.

[0023] Figure 5 This is a schematic diagram of the cross-sectional structure of the high-voltage channel of the present invention.

[0024] In the diagram: 1. Cylinder block, 2. Piston structure, 3. Piston rod, 4. Cylinder head, 5. Sealing structure, 6. Exhaust valve, 7. Oil inlet, 8. Oil inlet pipe, 9. First side wall, 10. Second side wall, 11. Third side wall, 12. First annular groove, 13. Second annular groove, 14. Third annular groove, 15. High-pressure channel, 16. First gap, 17. Second gap, 18. Third gap, 19. Connecting hole, 20. Branch channel, 21. Main channel, 22. Channel opening. Detailed Implementation

[0025] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below in conjunction with specific embodiments.

[0026] like Figure 1 As shown, a high-pressure, high-flow hydraulic cylinder includes a cylinder body 1 and a piston structure 2. The piston structure 2 divides the cylinder body 1 into a high-pressure oil chamber and a rod chamber. An oil inlet 7 is provided at the bottom end of the cylinder body 1. One end of the oil inlet 7 communicates with the high-pressure oil chamber, and the other end is provided with an oil inlet pipe 8. The oil inlet 7 is inclined at an angle between 30° and 60° with the axis of the cylinder body 1. A cylinder head 4 and an exhaust valve 6 are also provided at the top of the cylinder body 1. A piston rod 3 is mounted on the top of the piston structure 2, passing through the cylinder head 4, and a sealing structure 5 is provided at the connection between the piston rod 3 and the cylinder head 4.

[0027] Piston hydraulic cylinders can be divided into single-rod and double-rod structures, and according to the action of hydraulic pressure, they can be classified as single-acting or double-acting. In a single-acting hydraulic cylinder, pressurized oil is supplied to only one chamber of the cylinder, and the cylinder moves in one direction by hydraulic pressure. Reverse movement is achieved by external forces, such as spring force, self-weight, or external loads. In a double-acting hydraulic cylinder, the piston moves in both directions by alternating oil supply to the two chambers, which is accomplished by hydraulic pressure. This application selects a single-acting hydraulic cylinder as an embodiment of a high-pressure, high-flow hydraulic cylinder for description. Therefore, the piston structure 2 divides the cylinder body 1 into a high-pressure oil chamber, which is the pressurized oil inlet chamber, and a rod chamber, which is the oil-free inlet chamber. The oil inlet 7 in the high-pressure oil chamber is used to introduce high-pressure, high-flow oil, while the exhaust valve 6 in the rod chamber acts as a suction and exhaust valve, balancing the air pressure in the rod chamber and assisting the operation of the piston structure 2. The sealing structure 5 on the cylinder head 4 is also to provide lubrication for the piston rod 3 during movement and to prevent dust and impurities from entering the rod chamber.

[0028] Since this application is for a high-pressure, high-flow hydraulic cylinder, the pressure oil driving the piston structure 2 is in a high-pressure, high-flow state. In order to avoid the high-pressure, high-flow oil directly impacting the inner wall of the cylinder body 1, reducing the service life of the cylinder body 1, and to avoid the oil not directly acting on the piston structure 2 and affecting the response rate of the piston structure 2, the oil inlet 7 is set to an inclined state, and the angle between it and the axis of the cylinder body 1 is between 30-60°. This ensures that the high-pressure, high-flow oil sprayed from the oil inlet 7 can quickly contact the piston structure 2, thereby reducing energy loss and improving response efficiency.

[0029] like Figure 2 and Figure 3 As shown, the piston structure 2 includes a first sidewall 9, a second sidewall 10, and a third sidewall 11 that are sequentially connected from the high-pressure oil chamber to the rod chamber. The first sidewall 9, the second sidewall 10, and the third sidewall 11 form a first gap 16, a second gap 17, and a third gap 18 with the inner wall of the cylinder body 1, respectively. The gap widths of the second gap 17, the first gap 16, and the third gap 18 decrease sequentially. A first annular groove 12 is formed on the first sidewall 9, and the first annular groove 12 is connected to the first gap 16. A third annular groove 14 is formed on the third sidewall 11, and one end of the third annular groove 14 is connected to the third gap 18, while the other end is connected to the high-pressure oil chamber through a high-pressure channel 15. The side wall of piston structure 2 is not in contact with the inner wall of cylinder 1. If they were in contact, friction would inevitably occur between piston structure 2 and cylinder 1, leading to mutual wear and damage to the entire hydraulic cylinder. However, the side wall of piston structure 2 and the inner wall of cylinder 1 need to be sealed; otherwise, oil will flow into the rod chamber through the gap between them. Oil leakage will reduce the operating power of piston structure 2 and affect the normal use of the hydraulic cylinder. Therefore, a three-section clearance structure is designed to achieve both sealing to reduce oil leakage and lubrication to prevent wear with cylinder 1. Since piston structure 2 is a cylindrical structure, the clearances mentioned below are described based on one side of piston structure 2, and the other symmetrical side will not be described further.

[0030] In this embodiment, the tail of piston structure 2 is the high-pressure oil chamber, and the head of piston structure 2 is the rod chamber. Oil pushes piston structure 2 forward from the tail, causing piston rod 3 to extend. The principle of piston structure 2 balancing sealing and lubrication is explained in two parts. The first part explains the direction of oil flow as follows: When oil contacts piston structure 2, it first enters the first gap 16 from the tail. The first gap 16 is connected to the first annular groove 12, so the oil enters the first annular groove 12. The first annular groove 12 is equivalent to a liquid storage cavity. After the oil enters the cavity and fills the first annular groove 12, it enters the second gap 17. Since the third annular groove 14 is connected to the high-pressure oil chamber through the high-pressure channel 15, the oil also enters the third annular groove 14 along the high-pressure channel 15 while entering the first gap 16 from the tail.

[0031] The second part explains the effect of the oil in each gap as follows: When the oil is in the second gap 17, it can lubricate the piston structure 2 and the cylinder 1. When the oil is in the third annular groove 14, the high-pressure oil forms a throttling effect, which can seal the piston structure 2 and the cylinder 1. The lubrication effect is due to the oil film formed within the second gap 17, which serves as a lubricant. The sealing involves a throttling effect. Because the third annular groove 14 is indirectly connected to the high-pressure oil chamber, the oil within it is also under high pressure, quickly filling the groove. The oil is not like water, but a fluid; the oil accumulates in the third annular groove 14, forming a high-pressure annular band. The fluid molecules squeeze each other, increasing intermolecular friction and making dispersion difficult. Furthermore, because the width of the third gap 18 is much smaller than the diameter of the third annular groove 14, the oil needs to increase its flow rate to flow through the third gap 18, inevitably reducing pressure. Without high pressure, the oil has even less chance of flowing through the third gap 18. It is worth noting that the seal mentioned here is not completely closed; a small amount of oil can still leak out. However, this small leakage will not affect the thrust of the oil on the piston structure 2. The principle of the throttling effect achieving the oil seal is existing technology and will not be elaborated upon here.

[0032] The oil in the second gap 17 is supplied by the first annular groove 12. The first annular groove 12 is used as a "reservoir". After the high-pressure oil enters the first annular groove 12, it is equivalent to a pressure reduction. When the oil flows from the first annular groove 12 into the second gap 17, the oil pressure in the second gap 17 is lower than the pressure in the high-pressure oil chamber. This prevents the high-pressure, high-flow oil from directly scouring the second gap 17 and damaging the oil film inside the second gap 17. The first annular groove 12 also acts as a flow stabilizer. Even if the oil pressure in the high-pressure oil chamber is uneven, it will not affect the stable flow of the oil in the second gap 17.

[0033] As we know from the above, the gap width of the first gap 16, the second gap 17, and the third gap 18 is the largest of the two gaps. Therefore, a thicker oil film can be formed in the second gap 17, providing sufficient lubrication. Even if the piston structure 2 continues to advance forward, the oil film in the second gap 17 will not be quickly consumed and thinned, leading to lubrication failure. Moreover, the oil in the second gap 17 is continuously supplied by the first annular groove 12. The first gap 16 is set to have a gap width smaller than that of the second gap 17 because: Firstly, the first gap 16 needs to act as the initial entry channel for the oil, and it directly contacts the oil in the high-pressure oil chamber. This oil lacks guidance and has a large pressure and flow rate. If it is designed to be wider, although it can quickly fill the first annular groove 12, the width will affect the reduction of the oil pressure, resulting in excessive pressure of the oil entering the second gap 17 and damaging the oil film. At the same time, the first gap 16 can also serve as a lubricant, so it cannot be designed to be too narrow. If it is the same width as the third gap 18, then the first annular groove 12 will have the same sealing effect as the third annular groove 14, affecting the delivery of oil in the second gap 17 and thus affecting the lubrication effect.

[0034] The third gap 18 is located at the end closest to the rod chamber. Since the gap width of the third gap 18 is the smallest, and the third annular groove 14 can also act as a seal after being filled with oil, the oil in the third annular groove 14 is equivalent to intercepting the third gap 18, reducing the outflow of oil in the second gap 17. The oil pressure in the first annular groove 12 at the front end of the second gap 17 is greater than that in the second gap 17, so the oil pressure in the second gap 17 is the smallest, and there will be no leakage to the high-pressure area. There is only loss when the piston structure 2 moves, which prolongs the time the oil is in the second gap 17 and greatly improves the lubrication effect.

[0035] like Figure 3 and Figure 4As shown, in another embodiment of this application, a connecting hole 19 is also provided at the bottom of the piston structure 2. The first annular groove 12 is connected to the high-pressure oil chamber through the connecting hole 19. As can be seen from the above, the oil in the first annular groove 12 needs to flow into the second gap 17. Therefore, in order to ensure sufficient oil delivery and quickly fill the first annular groove 12, the connecting hole 19 is provided so that the oil in the high-pressure oil chamber can flow in not only through the first gap 16, but also through the connecting hole 19 into the first annular groove 12. In this way, even if the first gap 16 is not set with a large width, the first annular groove 12 can be filled with oil in the first time. When the piston structure 2 initially moves, the second gap 17 can form an oil film that provides lubrication. Since the first annular groove 12 is opened around the circumference of the piston structure 2, the connecting hole 19 can be drilled vertically from the tail of the piston structure 2 near the edge and connected to the first annular groove 12. Multiple connecting holes 19 can be provided, which can improve the efficiency of filling the first annular groove 12 with oil and form a uniform annular band of oil. The internal volume of the first annular groove 12 is larger than that of the third annular groove 14. Because the first annular groove 12 serves as a liquid reservoir, its volume is set relatively large to improve the reservoir effect. This can be achieved by changing the groove opening width or the groove depth. The presence of the connecting hole 19 ensures that even with a large internal volume, the first annular groove 12 can quickly fill with oil. Conversely, the third annular groove 14 serves a throttling function. A larger volume would reduce the throttling effect. Furthermore, to avoid affecting lubrication through sealing, the length of the third sidewall 11 is not designed to be long. Therefore, the volume of the third annular groove 14 needs to be smaller than that of the first annular groove 12.

[0036] The length of the second sidewall 10 is greater than the lengths of the first sidewall 9 and the third sidewall 11. Based on the different functions of the oil in each gap, it can be seen that in order to improve the lubrication effect of the piston structure 2, the bottom length of the second sidewall 10 is set to be the longest among the three sidewalls. In this way, the second gap 17 is also the longest. The longest lubrication band can ensure sufficient lubrication. In a further design, the third sidewall 11 can be designed to be the shortest. The length of the first sidewall 9 is between the third sidewall 11 and the second sidewall 10. This is because the third gap 18 corresponding to the third sidewall 11 is only used for sealing. When the total length of the piston structure 2 is fixed, setting it to be too long will easily occupy the lubrication length and affect the overall lubrication effect. The first sidewall 9 corresponds to the first gap 16. The oil can also play a certain lubrication role in the first gap 16, so the first sidewall 9 can be set to be longer than the third sidewall 11. However, since the width of the first gap 16 is smaller than the second gap 17, the first sidewall 9 should be shorter than the second sidewall 10.

[0037] In another embodiment of this application, a second annular groove 13 is provided on the second sidewall 10. The second annular groove 13 communicates with the second gap 17. The opening diameter of the second annular groove 13 is wider than the bottom diameter. Although the oil stored in the second gap 17 is not easily leaked from the third gap 18, the oil in the second gap 17 will decrease as the piston structure 2 moves. Therefore, by setting the second annular groove 13 as a reservoir, when the second gap 17 is full, the excess oil is stored. In this way, as the oil in the second gap 17 decreases, the second annular groove 13 and the first gap 16 simultaneously replenish the oil to the second gap 17, thus maintaining the oil capacity in the second gap 17, thereby extending the lubrication time and improving the lubrication effect. The opening of the second annular groove 13 is wider and the bottom is narrower, forming a shape like... Figure 2 The cross-section shown is trapezoidal, which prevents oil from accumulating in the second annular groove 13. Multiple second annular grooves 13 are provided, evenly distributed along the length of the second sidewall 10. If the second gap 17 is long, multiple second annular grooves 13 can be provided to ensure that oil is evenly distributed to all gaps in the second gap 17.

[0038] The first annular groove 12, the second annular groove 13 and the third annular groove 14 mentioned above are all opened around the circumference of the piston structure 2 to match the cylindrical piston structure 2. This is to ensure that when the oil fills the annular groove, it has a more sufficient and uniform contact with the inner wall of the cylinder 1.

[0039] like Figure 4 and Figure 5 As shown, the high-pressure channel 15 includes multiple branch channels 20 and a main channel 21 connected to the branch channels 20. The branch channels 20 are connected to the third annular groove 14, and the main channel 21 is connected to the high-pressure oil chamber. The branch channels 20 are circumferentially distributed on the main channel 21. The bottom of the main channel 21 is connected to the piston structure 2, which is a channel opening 22. The channel opening 22 is set in a conical structure, and the end near the high-pressure oil chamber is the large-diameter end of the conical structure. The main channel 21 connects to the high-pressure oil chamber, allowing oil to flow into the branch channel 20 and then into the third annular groove 14. The branch channel 20 is provided to ensure the third annular groove 14 is filled efficiently and facilitates processing. If there were no branch channel 20 and the main channel 21 directly connects to the third annular groove 14, the main channel 21 would need to be located at the edge of the piston structure 2 to connect with the third annular groove 14. If a connecting hole 19 is added, it would result in more holes in the piston structure 2, making it prone to damage under high pressure and high flow impact. The conical structure at the channel opening 22 of the main channel 21 is also designed to better collect the oil into the main channel 21 and improve the efficiency of entering the third annular groove 14.

[0040] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0041] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A high-pressure, high-flow-rate hydraulic cylinder, comprising a cylinder body (1) and a piston structure (2), wherein the piston structure (2) divides the cylinder body (1) into a high-pressure oil chamber and a rod chamber, characterized in that, The piston structure (2) includes a first sidewall (9), a second sidewall (10), and a third sidewall (11) arranged sequentially from the high-pressure oil chamber to the rod chamber. The first sidewall (9), the second sidewall (10), and the third sidewall (11) form a first gap (16), a second gap (17), and a third gap (18) with the inner wall of the cylinder (1), respectively. The gap widths of the second gap (17), the first gap (16), and the third gap (18) decrease sequentially. A first annular groove (12) is opened on the first sidewall (9), and the first annular groove (12) communicates with the first gap (16). A third annular groove (14) is opened on the third sidewall (11), one end of the third annular groove (14) communicates with the third gap (18), and the other end communicates with the high-pressure oil chamber through a high-pressure channel (15).

2. The high-pressure, high-flow hydraulic cylinder according to claim 1, characterized in that, The piston structure (2) is also provided with a connecting hole (19) at the bottom, and the first annular groove (12) is connected to the high-pressure oil chamber through the connecting hole (19).

3. A high-pressure, high-flow hydraulic cylinder according to claim 2, characterized in that, The internal volume of the first annular groove (12) is greater than the internal volume of the third annular groove (14).

4. A high-pressure, high-flow hydraulic cylinder according to claim 1, characterized in that, The length of the second sidewall (10) is greater than the lengths of the first sidewall (9) and the third sidewall (11), respectively.

5. A high-pressure, high-flow hydraulic cylinder according to claim 1, characterized in that, A second annular groove (13) is provided on the second sidewall (10). The second annular groove (13) is connected to the second gap (17). The groove opening width of the second annular groove (13) is greater than the groove bottom opening width.

6. A high-pressure, high-flow hydraulic cylinder according to claim 5, characterized in that, The second annular groove (13) is provided in multiple ways and is evenly distributed along the length of the second sidewall (10).

7. A high-pressure, high-flow hydraulic cylinder according to claim 1, characterized in that, The high-pressure channel (15) includes multiple branch channels (20) and a main channel (21) connected to the branch channels (20). The branch channels (20) are connected to the third annular groove (14), and the main channel (21) is connected to the high-pressure oil chamber.

8. A high-pressure, high-flow hydraulic cylinder according to claim 7, characterized in that, The branch channels (20) are circumferentially distributed on the main channel (21). The bottom of the piston structure (2) connected to the main channel (21) is the channel opening (22). The channel opening (22) is set in a conical structure, and the end near the high-pressure oil chamber is the large-diameter end of the conical structure.

9. A high-pressure, high-flow hydraulic cylinder according to claim 1, characterized in that, The bottom end of the cylinder (1) is provided with an oil inlet (7). One end of the oil inlet (7) is connected to the high-pressure oil chamber, and the other end is provided with an oil inlet pipe (8). The oil inlet (7) is inclined and the included angle between it and the axis of the cylinder (1) is between 30° and 60°.

10. A high-pressure, high-flow hydraulic cylinder according to claim 1, characterized in that, The top of the cylinder (1) is also provided with a cylinder head (4) and an exhaust valve (6). A piston rod (3) is installed on the top of the piston structure (2). The piston rod (3) passes through the cylinder head (4), and a sealing structure (5) is provided at the connection between the piston rod (3) and the cylinder head (4).

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