Hydraulic cylinder for differential regulation

Abstract

This utility model discloses a hydraulic cylinder for differential speed adjustment, including a cylinder barrel, a piston assembly, and a differential speed adjustment assembly. The rod chamber of the cylinder barrel is provided with a working oil port. The piston assembly includes a piston body and a hollow piston rod. The piston body has a first through section, a moving cavity section, and a second through section connected sequentially on its end face facing the rod chamber from the rodless cavity of the cylinder barrel. The inner diameters of the first through section and the second through section are different and both are smaller than the inner diameter of the moving cavity section. The inner end of the piston rod is connected to the second through section, and the outer end extends out of the cylinder barrel. The differential speed adjustment assembly includes a differential speed adjustment block placed in the moving cavity section. The differential speed adjustment block is provided with a first oil passage. The first oil passage is connected to one of the first through section and the second through section, and is opposite to the periphery of the other. This hydraulic cylinder can change the hydraulic oil flow without the need for a throttle valve, and has a lower failure rate compared to existing hydraulic differential speed adjustment structures.

Description

Technical Field

[0001] This utility model belongs to the field of hydraulic cylinder technology, specifically relating to a hydraulic cylinder for differential speed adjustment. Background Technology

[0002] For hydraulically driven engineering equipment, the extension and retraction speeds of the hydraulic cylinders need to be differentially controlled according to their actual working conditions. For example, in a dump truck, when dumping slag, the hydraulic cylinder extends at a certain speed to lift the cargo box. When lowering the cargo box, the hydraulic cylinder needs to retract at a lower speed to ensure that the cargo box is placed stably on the chassis.

[0003] In the existing technology, the differential speed adjustment of hydraulic cylinders is mostly controlled by throttle valves. However, the additional valves and pipelines are sensitive to the cleanliness of hydraulic oil. In particular, the valve cores of the valves are easily contaminated and stuck, which increases the risk of failures such as leakage and blockage. Utility Model Content

[0004] To address the aforementioned defects or deficiencies, this utility model provides a hydraulic cylinder for differential speed adjustment, aiming to solve the technical problem that existing hydraulic cylinder differential speed adjustment technology relies on throttle valves, leading to an increased risk of failure.

[0005] To achieve the above objectives, this utility model provides a hydraulic cylinder for differential adjustment, including a cylinder barrel, a piston assembly, and a differential adjustment assembly. The rod chamber of the cylinder barrel is provided with a working oil port. The piston assembly includes a piston body and a hollow piston rod. The piston body has a first through-port section, a moving cavity section, and a second through-port section sequentially connected to each other on its end face facing the rod chamber from the rodless chamber of the cylinder barrel. The inner diameters of the first through-port section and the second through-port section are different and both are smaller than the inner diameter of the moving cavity section. The inner end of the piston rod is connected to the second through-port section, and the outer end extends out of the cylinder barrel. The differential adjustment assembly includes a differential adjustment block placed in the moving cavity section. The differential adjustment block is provided with a first oil passage. The first oil passage is connected to one of the first through-port section and the second through-port section, and is opposite to the periphery of the other.

[0006] In this embodiment of the present invention, the differential adjustment block is further provided with a second oil passage, which extends along the central axis of the differential adjustment block, and the first oil passage is located outside the second oil passage.

[0007] In this embodiment of the present invention, the inner diameter of the second oil passage is smaller than the inner diameter of the first and second passage sections. The differential adjustment assembly also includes a plunger disposed in the rodless cavity of the cylinder. The plunger is used to penetrate the second oil passage and forms an oil passage gap with the side wall of the second oil passage.

[0008] In this embodiment of the invention, the extension length of the plunger is set to be greater than the distance between the end face of the piston body facing the rodless cavity and the end face of the piston rod facing the rodless cavity, and the shaft diameter of the plunger is smaller than the inner diameter of the piston rod, so that the plunger can extend into the piston rod.

[0009] In this embodiment of the utility model, the plunger component includes a first plunger portion and a second plunger portion disposed at the end of the first plunger portion away from the cylinder. The first plunger portion is a cylinder and is used to pass through the first through section and pass through the second oil passage. The second plunger portion is arranged in a tapering manner from the first plunger portion toward the piston rod. The second plunger portion is used to pass through the first through section, the second oil passage and the second through section in sequence and extend into the piston rod.

[0010] In this embodiment of the invention, there are at least two first oil passages, and at least two first oil passages are arranged sequentially and at intervals around the second oil passage.

[0011] In this embodiment of the utility model, the piston body includes a piston body and a baffle. The piston body has an installation port section, a moving cavity section and a second passage section connected in sequence on the end face of the rodless cavity facing the cylinder barrel towards the rod cavity. The inner diameters of the installation port section, the moving cavity section and the second passage section are arranged to decrease in sequence. The baffle is placed in the installation port section and is detachably connected to the piston body. A first passage section is formed on the baffle.

[0012] In this embodiment of the invention, the piston assembly further includes a connecting bolt, which is connected in series with the baffle, the piston body, and the piston rod.

[0013] In this embodiment of the present invention, the piston body has a connecting mounting cavity section and a third through section sequentially arranged on the end face of the rod chamber facing the cylinder and towards the rodless chamber. The third through section is connected to the second through section, and the inner diameter of the third through section is larger than the inner diameter of the second through section and smaller than the inner diameter of the mounting cavity section. The end of the piston rod extends into the mounting cavity section and is connected to the piston body.

[0014] In this embodiment of the invention, the piston rod includes a rod body and an oil pipe passing through the rod body. The end of the rod body extends into the mounting cavity and is connected to the piston body, and the oil pipe extends into the third through-hole section.

[0015] Through the above technical solution, the differential speed regulating hydraulic cylinder provided in this utility model embodiment has the following beneficial effects:

[0016] When using the aforementioned differential speed regulating hydraulic cylinder, the rod chamber of the cylinder barrel is provided with a working oil port, and the piston rod is hollow. When the piston rod extends, hydraulic oil enters the rodless chamber of the cylinder barrel along the piston rod, and the hydraulic oil in the rod chamber of the cylinder barrel is discharged from the working oil port. When the piston rod retracts, hydraulic oil enters the rod chamber along the working oil port, and the hydraulic oil in the rodless chamber is discharged from the piston rod.

[0017] The piston body and differential adjustment block are designed to achieve differential control of the piston rod extension and retraction. The periphery of the first and second passage sections limits the differential adjustment block. When hydraulic oil enters the rodless chamber along the piston rod, the differential adjustment block moves along the moving section under the action of the hydraulic oil until it abuts against the periphery of the first passage section. When hydraulic oil is discharged from the rodless chamber along the piston rod, the differential adjustment block moves along the moving section under the action of the hydraulic oil until it abuts against the periphery of the second passage section. Because the inner diameters of the first and second passage sections are different, when the differential adjustment block abuts against the periphery of the passage section with the larger inner diameter, the first oil passage is open to that passage section, allowing hydraulic oil to pass normally through it. However, when the differential adjustment block abuts against the periphery of the passage section with the smaller inner diameter, the first oil passage abuts against that passage section's periphery. Due to the blocking effect of the passage section's periphery, the hydraulic oil experiences increased resistance as it passes through the differential adjustment block, resulting in a reduced hydraulic oil flow rate within the cylinder and a decreased piston rod movement speed. Compared to existing differential adjustment schemes, this method eliminates the need for a throttle valve to change the hydraulic oil flow rate, leading to a lower failure rate.

[0018] Other features and advantages of this invention will be described in detail in the following detailed description section. Attached Figure Description

[0019] The accompanying drawings are provided to illustrate the present invention and form part of the specification. They are used together with the following detailed description to explain the present invention, but do not constitute a limitation thereof. In the drawings:

[0020] Figure 1 This is a partial structural diagram of a differential speed regulating hydraulic cylinder according to an embodiment of the present invention;

[0021] Figure 2 yes Figure 1 A schematic diagram of the rod chamber oil inlet state in the illustrated embodiment;

[0022] Figure 3 yes Figure 1 A schematic diagram of the rodless chamber oil inlet state in the illustrated embodiment;

[0023] Figure 4 This is a partial structural diagram of a hydraulic cylinder for differential speed adjustment according to another embodiment of the present invention.

[0024] Explanation of reference numerals in the attached figures

[0025] 1. Cylinder; 11. Rod chamber; 12. Rodless chamber; 2. Piston body; 21. First through-hole section; 22. Second through-hole section moving chamber; 23. Second through-hole section; 24. Piston body; 25. Baffle; 26. Connecting bolt; 27. Third through-hole section; 3. Piston rod; 31. Oil pipe; 32. Rod body; 4. Differential adjustment block; 41. First oil passage; 42. Second oil passage; 5. Plunger component; 51. First plunger part; 52. Second plunger part. Detailed Implementation

[0026] The specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the scope of this utility model.

[0027] The following is for reference. Figures 1 to 4 This invention describes a hydraulic cylinder for differential speed regulation.

[0028] This utility model provides a hydraulic cylinder for differential speed adjustment, wherein the hydraulic cylinder for differential speed adjustment includes:

[0029] Cylinder 1, the rod chamber 11 of cylinder 1 is provided with a working oil port;

[0030] The piston assembly includes a piston body 2 and a hollow piston rod 3. The piston body 2 has a first through section 21, a moving cavity section 22 and a second through section 23 connected in sequence on the end face of the rodless cavity 12 facing the cylinder 1 and the rod cavity 11. The inner diameters of the first through section 21 and the second through section 23 are different and both are smaller than the inner diameter of the moving cavity section 22. The inner end of the piston rod 3 is connected to the second through section 23 and the outer end extends out of the cylinder 1.

[0031] The differential adjustment assembly includes a differential adjustment block 4 placed in the moving cavity section 22. The differential adjustment block 4 is provided with a first oil passage 41. The first oil passage 41 is configured to communicate with one of the first passage section 21 and the second passage section 23, and is configured to be opposite to the periphery of the other.

[0032] When using the aforementioned differential speed regulating hydraulic cylinder, the rod chamber 11 of the cylinder barrel 1 is provided with a working oil port, and the piston rod 3 is hollow. When the piston rod 3 extends, hydraulic oil enters the rodless chamber 12 of the cylinder barrel 1 along the piston rod 3, and the hydraulic oil in the rod chamber 11 of the cylinder barrel 1 is discharged from the working oil port. When the piston rod 3 retracts, hydraulic oil enters the rod chamber 11 along the working oil port, and the hydraulic oil in the rodless chamber 12 is discharged from the piston rod 3.

[0033] The piston body 2 and the differential adjustment block 4 are configured to achieve differential control of the extension and retraction of the piston rod 3. The periphery of the first passage section 21 and the second passage section 23 serves to limit the differential adjustment block 4. When hydraulic oil enters the rodless chamber 12 along the piston rod 3, the differential adjustment block 4 moves along the moving chamber section 22 under the action of the hydraulic oil until it comes into contact with the periphery of the first passage section 21. When the hydraulic oil is discharged from the rodless chamber 12 along the piston rod 3, the differential adjustment block 4 moves along the moving chamber section 22 under the action of the hydraulic oil until it comes into contact with the periphery of the second passage section 23. Because the inner diameters of the first passage section 21 and the second passage section 23 are different, when the differential adjustment block 4 abuts against the periphery of the passage section with the larger inner diameter, the first oil passage 41 communicates with that passage section, and hydraulic oil can pass normally through the first oil passage 41. When the differential adjustment block 4 abuts against the periphery of the passage section with the smaller inner diameter, the first oil passage 41 abuts against the periphery of that passage section. Under the blocking action of the periphery of the passage section, the resistance encountered by the hydraulic oil when passing through the differential adjustment block 4 increases, the hydraulic oil flow in the cylinder 1 decreases, and the moving speed of the piston rod 3 also decreases. Compared with the existing differential adjustment scheme, the hydraulic oil flow can be changed without the need to set a throttle valve, resulting in a lower failure rate.

[0034] Specifically, depending on actual needs, the extension speed of piston rod 3 can be slowed down or the retraction speed of piston rod 3 can be slowed down.

[0035] See Figure 1 If the retraction speed of piston rod 3 is slowed down, the inner diameter of the first passage section 21 is larger than the inner diameter of the second passage section 23. The first oil passage 41 is configured to communicate with the first passage section 21 and is positioned opposite the periphery of the second passage section 23. When hydraulic oil enters the rodless chamber 12 along piston rod 3, the differential adjustment block 4 moves to abut against the first passage section 21. At this time, the first oil passage 41 is connected to the first passage section 21, allowing hydraulic oil to pass smoothly, and piston rod 3 extends quickly. However, when hydraulic oil exits the rodless chamber 12 along piston rod 3, the differential adjustment block 4 moves to abut against the second passage section 23, the first oil passage 41 is closed, the resistance increases and the flow rate decreases when hydraulic oil passes through, and the retraction speed of piston rod 3 slows down.

[0036] See Figure 4 If the piston rod 3 extension speed is slowed down, the inner diameter of the first passage section 21 is smaller than the inner diameter of the second passage section 23, and the first oil passage 41 is positioned opposite the periphery of the first passage section 21 and communicates with the second passage section 23. When hydraulic oil enters the rodless chamber 12, the differential speed adjusting block 4 abuts against the first passage section 21, the first oil passage 41 is closed, the hydraulic oil resistance increases, the flow rate decreases, and the piston rod 3 extension speed slows down; while when hydraulic oil exits the rodless chamber 12, the differential speed adjusting block 4 abuts against the second passage section 23, the first oil passage 41 communicates with the second passage section 23, the hydraulic oil passes normally, and the piston rod 3 retracts normally.

[0037] In this embodiment of the invention, the differential adjustment block 4 is further provided with a second oil passage 42, which extends along the central axis of the differential adjustment block 4. The first oil passage 41 is located outside the second oil passage 42. When the first oil passage 41 is closed, the second oil passage 42 can still provide a certain flow path for the hydraulic oil. Furthermore, since the second oil passage 42 extends along the central axis of the differential adjustment block 4, it always maintains communication with the first passage section 21 and the second passage section 23, preventing complete blockage of the hydraulic oil flow path.

[0038] Specifically, there are at least two first oil passages 41, and at least two first oil passages 41 are arranged alternately around the second oil passage 42.

[0039] like Figures 1 to 4 As shown in this embodiment of the invention, the inner diameter of the second oil passage 42 is smaller than the inner diameter of the first passage section 21 and the second passage section 23. The differential adjustment assembly also includes a plunger 5 disposed in the rodless chamber 12 of the cylinder 1. The plunger 5 is used to penetrate the second oil passage 42 and forms an oil passage gap with the side wall of the second oil passage 42. By forming an oil passage gap with the side wall of the second oil passage 42, the resistance to hydraulic oil can be increased, thereby further slowing down the retraction speed of the plunger 5. At the same time, limiting the inner diameter of the second oil passage 42 to be smaller than the inner diameter of the first passage section 21 and the second passage section 23 ensures that the plunger 5 can pass normally through the first passage section 21 and the second passage section 23, and avoids the gap between the plunger 5 and the peripheral side wall of the first passage section 21 and the second passage section 23 being too small, which would affect the normal flow of hydraulic oil.

[0040] like Figures 1 to 4 As shown, in this embodiment of the invention, the extension length of the plunger 5 is set to be greater than the distance between the end face of the piston body 2 facing the rodless cavity 12 and the end face of the piston rod 3 facing the rodless cavity 12. The shaft diameter of the plunger 5 is smaller than the inner diameter of the piston rod 3, so that the plunger 5 can extend into the piston rod 3. Specifically, an oil pipe 31 is provided inside the piston rod 3. It can be understood that when the plunger 5 extends into the oil pipe 31, the flow area at the opening of the oil pipe 31 facing the rodless cavity 12 decreases, and the resistance of the hydraulic oil through the opening increases, thereby further limiting the moving speed of the piston rod 3.

[0041] exist Figure 1In the embodiment where the inner diameter of the first through section 21 is larger than that of the second through section 23, the piston rod 3 retraction process is as follows: Hydraulic oil is discharged from the rodless chamber 12 along the piston rod 3. The differential adjustment block 4 moves to abut against the second through section 23, the first oil passage 41 is closed, and the hydraulic oil can only be discharged along the second oil passage 42, reducing the flow rate and slowing down the retraction speed of the piston rod 3. As the piston rod 3 continues to retract, the plunger 5 enters the second oil passage 42, and the hydraulic oil can only be discharged along the oil passage gap, further reducing the flow rate and further slowing down the retraction speed of the piston rod 3. When the piston body 2 is about to approach the bottom wall of the cylinder 1, the piston body 2 extends into the oil pipe 31. The flow area of ​​the opening of the oil pipe 31 facing the rodless chamber 12 decreases, the resistance of the hydraulic oil through the opening increases, and the flow rate decreases again, slowing down the retraction speed of the piston rod 3 once more. Through the above design, a multi-stage adjustment of the retraction speed of the piston rod 3 is achieved, which can both ensure the retraction speed of the piston rod 3 and make the piston rod 3 more stable at the end of the retraction stroke. For example, when this differential adjustment hydraulic cylinder is applied to the truck bed of a dump truck, the piston rod 3 extends, the truck bed tilts and dumps the cargo, and the piston rod 3 retracts, the truck bed falls back onto the vehicle body. Through this multi-stage adjustment, the speed at which the truck bed falls back can be effectively reduced, thus reducing the impact between the truck bed and the vehicle body when the truck bed falls back.

[0042] like Figure 3 As shown in this embodiment of the invention, the plunger component 5 includes a first plunger portion 51 and a second plunger portion 52 located at the end of the first plunger portion 51 away from the cylinder 1. The first plunger portion 51 is cylindrical and is used to pass through the first through-hole section 21 and into the second oil passage 42. The second plunger portion 52 is tapered from the first plunger portion 51 toward the piston rod 3. The second plunger portion 52 is used to sequentially pass through the first through-hole section 21, the second oil passage 42, and the second through-hole section 23 and extend into the piston rod 3. The tapered second plunger portion 52 serves as a guide, facilitating the insertion of the plunger component 5 into the differential adjustment block 4. Furthermore, when the second plunger portion 52 enters or exits the second oil passage 42, the oil passage gap gradually decreases or increases, resulting in a more stable flow rate within the cylinder 1.

[0043] It is understandable that the inner diameter of the moving cavity section 22 is larger than the inner diameters of the first passage section 21 and the second passage section 23. If it is integrally formed, the differential adjustment block 4 cannot be placed in the moving cavity section 22. Therefore, in this embodiment of the utility model, the piston body 2 adopts a split design, including the piston body 24 and the baffle 25. The piston body 24 has a mounting port section, a moving cavity section 22 and a second passage section 23 connected in sequence on the end face of the rodless cavity 12 facing the cylinder 1 and the rod cavity 11. The inner diameters of the mounting port section, the moving cavity section 22 and the second passage section 23 are set to decrease in sequence. The baffle 25 is placed in the mounting port section and is detachably connected to the piston body 24. The first passage section 21 is formed on the baffle 25.

[0044] like Figure 3 As shown in this embodiment of the invention, the piston assembly further includes a connecting bolt 26, which connects the baffle 25, piston body 24, and piston rod 3 in series. This split design not only facilitates the installation of the differential adjustment block 4 but also makes the entire piston body 2 easier to manufacture and maintain. By detaching and connecting the baffle 25 to the piston body 2, it can be quickly separated when internal structural repairs or component replacements are required, improving work efficiency.

[0045] like Figure 2 and Figure 3 As shown in this embodiment of the invention, the piston body 2 has a mounting cavity section and a third through section 27 sequentially connected on the end face of the rod chamber 11 facing the cylinder 1 and towards the rodless chamber 12. The third through section 27 communicates with the second through section 23, and the inner diameter of the third through section 27 is larger than the inner diameter of the second through section 23 but smaller than the inner diameter of the mounting cavity section. The end of the piston rod 3 extends into the mounting cavity section and connects to the piston body 2. The mounting cavity section facilitates the docking of the piston rod 3 with the piston body 24, improving the reliability of the connection. The periphery of the third through section 27 is used to stop the piston rod 3. Furthermore, the end of the piston rod 3 also has a stepped surface, which abuts against the periphery of the mounting cavity section.

[0046] like Figure 1 and Figure 3 As shown, in this embodiment of the invention, the piston rod 3 includes a rod body 32 and an oil pipe 31 passing through the rod body 32. The end of the rod body 32 extends into the mounting cavity and connects to the piston body 2, while the oil pipe 31 extends into the third through-hole section 27. The piston rod 3 is a split design for easy assembly. The oil pipe 31 extends into the third through-hole section 27, and a seal can be provided at the end faces of the oil pipe 31 and the rod body 32 facing the rodless cavity 12 to prevent hydraulic oil from entering the gap between the rod body 32 and the oil pipe 31.

[0047] In this embodiment of the present invention, a static seal is provided between the piston rod 3 and the piston body 2, and a dynamic seal is provided on the outer peripheral wall of the piston body 2 to cooperate with the inner wall of the cylinder 1.

[0048] In the description of this utility model, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0049] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0050] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0051] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A hydraulic cylinder for differential speed adjustment, characterized in that, The differential speed regulating hydraulic cylinder includes: Cylinder (1), the rod chamber (11) of the cylinder (1) is provided with a working oil port; The piston assembly includes a piston body (2) and a hollow piston rod (3). The piston body (2) has a first through section (21), a moving section (22), and a second through section (23) connected in sequence on the end face of the rodless cavity (12) facing the cylinder (1) towards the rod cavity (11). The inner diameters of the first through section (21) and the second through section (23) are different and both are smaller than the inner diameter of the moving section (22). The inner end of the piston rod (3) is connected to the second through section (23), and the outer end extends out of the cylinder (1). The differential adjustment assembly includes a differential adjustment block (4) placed in the moving cavity section (22). The differential adjustment block (4) is provided with a first oil passage (41). The first oil passage (41) is configured to communicate with one of the first passage section (21) and the second passage section (23), and is configured to be opposite to the periphery of the other.

2. The hydraulic cylinder for differential adjustment according to claim 1, characterized in that, The differential adjustment block (4) is also provided with a second oil passage (42), which extends along the central axis of the differential adjustment block (4), and the first oil passage (41) is located outside the second oil passage (42).

3. The hydraulic cylinder for differential adjustment according to claim 2, characterized in that, The inner diameter of the second oil passage (42) is smaller than the inner diameter of the first passage section (21) and the second passage section (23). The differential adjustment assembly also includes a plunger (5) disposed in the rodless cavity (12) of the cylinder (1). The plunger (5) is used to penetrate the second oil passage (42) and form an oil passage gap with the side wall of the second oil passage (42).

4. The hydraulic cylinder for differential adjustment according to claim 3, characterized in that, The extension length of the plunger (5) is set to be greater than the distance between the end face of the piston body (2) facing the rodless cavity (12) and the end face of the piston rod (3) facing the rodless cavity (12). The shaft diameter of the plunger (5) is smaller than the inner diameter of the piston rod (3) so that the plunger (5) can extend into the piston rod (3).

5. The hydraulic cylinder for differential adjustment according to claim 4, characterized in that, The plunger component (5) includes a first plunger portion (51) and a second plunger portion (52) located at the end of the first plunger portion (51) away from the cylinder (1). The first plunger portion (51) is a cylinder and is used to pass through the first through section (21) and pass through the second oil passage (42). The second plunger portion (52) is arranged in a tapering manner from the first plunger portion (51) toward the piston rod (3). The second plunger portion (52) is used to pass through the first through section (21), the second oil passage (42) and the second through section (23) in sequence and extend into the piston rod (3).

6. The hydraulic cylinder for differential adjustment according to claim 2, characterized in that, The number of the first oil passage (41) is at least two, and at least two of the first oil passages (41) are arranged sequentially and at intervals around the second oil passage (42).

7. The differential speed regulating hydraulic cylinder according to any one of claims 1 to 6, characterized in that, The piston body (2) includes a piston body (24) and a baffle (25). The piston body (24) has an installation port section, a moving cavity section (22) and a second passage section (23) connected in sequence on the end face of the rodless cavity (12) facing the cylinder (1) towards the rod cavity (11). The inner diameters of the installation port section, the moving cavity section (22) and the second passage section (23) are arranged to decrease in sequence. The baffle (25) is placed in the installation port section and is detachably connected to the piston body (24). The first passage section (21) is formed on the baffle (25).

8. The hydraulic cylinder for differential adjustment according to claim 7, characterized in that, The piston assembly also includes a connecting bolt (26), which is connected in series with the baffle (25), the piston body (24) and the piston rod (3).

9. The differential adjustment hydraulic cylinder according to any one of claims 1 to 6, characterized in that, The piston body (2) has a connecting mounting section and a third passage section (27) on the end face of the rod chamber (11) facing the cylinder (1) and the rodless chamber (12). The third passage section (27) is connected to the second passage section (23), and the inner diameter of the third passage section (27) is larger than the inner diameter of the second passage section (23) and smaller than the inner diameter of the mounting section. The end of the piston rod (3) extends into the mounting section and is connected to the piston body (2).

10. The hydraulic cylinder for differential adjustment according to claim 9, characterized in that, The piston rod (3) includes a rod body (32) and an oil pipe (31) passing through the rod body (32). The end of the rod body (32) extends into the mounting cavity and is connected to the piston body (2). The oil pipe (31) extends into the third passage section (27).

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