Integrated slide built-in coupling type servo booster oil cylinder

Abstract

This application provides an integrated slide-mounted, built-in coupled servo booster cylinder, comprising a cylinder barrel with an integrated booster actuator inside, including a first pressure chamber, a second pressure chamber, and an internal oil passage connecting the two chambers, distributed axially along the cylinder barrel. It also includes a first piston rod and a second piston rod capable of relative axial movement, with a non-rigid contact force transmission interface between the second and first piston rods. A modular slide guide unit is located outside the cylinder barrel, including a front mounting assembly and a rear mounting assembly, both equipped with guide mechanisms for sliding engagement with an external frame. This application integrates the booster mechanism, significantly reducing axial and radial installation space. Simultaneously, through pressure coupling design, it achieves output thrust far exceeding that of comparable cylinders with conventional system pressure. Combined with servo closed-loop control, it achieves high-precision, high-response control of pressure and position.

Description

Technical Field

[0001] This application relates to the technical field of hydraulic transmission and high-precision forging equipment, and in particular to a built-in coupled servo booster cylinder with an integrated slide. Background Technology

[0002] In the field of heavy precision manufacturing, hydraulic cylinders, as core power components, directly determine the processing capacity and precision of equipment. To obtain output thrust of hundreds of tons or even higher, traditional technical solutions usually face a dilemma: one is to use an ultra-high pressure pump station system, which results in bulky equipment, increased energy consumption, and difficulties in sealing and maintenance; the other is to use a split structure of "main cylinder + external booster", which can increase local pressure, but causes problems such as long axial dimensions, slow system response, and low integration; the third is to use a traditional single-cylinder structure, where the radial dimension of the cylinder is particularly large, resulting in a bulky machine tool transmission structure design and inconvenient operation.

[0003] Furthermore, the installation of conventional hydraulic cylinders and the main frame often relies on tedious on-site debugging, making it difficult to guarantee alignment accuracy. Moreover, during high-speed reciprocating motion, uneven loading can easily lead to wear and loss of precision. The stroke control of the hydraulic cylinder also largely depends on externally mounted sensors, which suffer from installation errors and signal delays, making it difficult to achieve micron-level precise closed-loop control. Therefore, existing technologies struggle to achieve a balance between ultra-high output thrust, extremely high motion control precision, and convenient and reliable integration within limited space constraints in an economical and efficient manner. This has become a key technological bottleneck restricting the development of high-end forging and straightening equipment towards compactness and intelligence. Summary of the Invention

[0004] To address the challenge of achieving a balance between ultra-high output thrust, extremely high motion control precision, and convenient and reliable integration within limited space constraints using existing technologies, this application provides a built-in coupled servo booster cylinder with an integrated slide.

[0005] The integrated sliding block built-in coupling servo booster cylinder provided in this application adopts the following technical solution: An integrated sliding block with built-in coupling servo booster cylinder includes a cylinder barrel. An integrated booster actuator is disposed within the cylinder barrel, including a first pressure chamber, a second pressure chamber, and a built-in oil passage connecting the two chambers, distributed axially along the cylinder barrel. It also includes a first piston rod and a second piston rod capable of relative axial movement, with a non-rigid force transmission interface formed between the second piston rod and the first piston rod. A modular slide guide unit is provided outside the cylinder, which includes a front mounting component fixedly connected to the front end of the cylinder and a rear mounting component fixedly connected to the rear end of the cylinder. The front mounting component and the rear mounting component are provided with guide mechanisms for sliding cooperation with an external frame, so that the hydraulic cylinder constitutes a power slide module that can be plugged in as a whole.

[0006] Furthermore, the inner wall of the cylinder is provided with a front guide sleeve and a rear guide sleeve with a front opening and a rear opening in the first pressure chamber, and a rear end cover is provided at the rear end of the cylinder. One end of the second piston rod slides in the second pressure chamber, and the other end slides through the opening of the rear guide sleeve; One end of the first piston rod slides in the rear guide sleeve, and the other end slides through the opening of the front guide sleeve.

[0007] Furthermore, both the first piston rod and the second piston rod are configured with a T-shaped cross-section; The large end of the second piston rod divides the second pressure chamber into a guide chamber and a pressurizing oil chamber, and the pressurizing oil chamber is connected to an oil port; The large end of the first piston rod divides the first pressure chamber into a retraction oil chamber and a working oil chamber, and the working oil chamber and the booster oil chamber are connected through the built-in oil passage.

[0008] Furthermore, the built-in oil passage is formed in the second piston rod and extends through both ends of the second piston rod axially; The second piston rod has a radially arranged oil guide groove at one end near the first piston rod. The built-in oil passage is connected to the oil guide groove, and the oil pressure of the working oil chamber and the pressurizing oil chamber is balanced through the oil guide groove.

[0009] Furthermore, a displacement sensor is installed on the end cap, and a blind hole is provided in the second piston rod along its axial direction for the displacement sensor detection rod to be inserted.

[0010] Furthermore, the detection rod of the displacement sensor is coaxially arranged with the second piston rod, and the built-in oil passages are eccentrically arranged on the second piston rod and are provided in several places.

[0011] Furthermore, the cylinder sidewall is provided with an overtravel protection mechanism for detecting the extreme stroke position of the large end of the second piston rod at the location corresponding to the guide cavity.

[0012] Furthermore, the overtravel protection mechanism includes a trigger rod that slides through the cylinder sidewall, a sealing cover plate and a micro switch mounted on the cylinder sidewall; One end of the trigger rod extends into the guide cavity, and the other end slides through the sealing cover plate in a sealing seal. When the large end of the second piston rod moves to the limit stroke position, its large end sidewall pushes against the trigger rod, so that the other end of the trigger rod triggers the micro switch. A reset spring is provided between the end of the trigger rod near the guide cavity and the sealing cover plate. When the reset spring is in the initial state, the end of the trigger rod near the guide cavity protrudes from the inner wall of the guide cavity.

[0013] Furthermore, a top head is detachably mounted on the front end of the first piston rod and slidably disposed in the front guide sleeve.

[0014] Furthermore, both the front slide assembly and the rear slide assembly include multiple guide rails. The front slide assembly is equipped with pads for supporting span fine-tuning, a lead screw, and a trapezoidal bolt assembly for position locking. The rear slide assembly is equipped with replaceable adjusting pads for axial dimension fine-tuning and a screw assembly for final locking.

[0015] In summary, this application includes at least one of the following beneficial technical effects: 1. Revolutionary space utilization and high power density: By fully integrating the pressure coupling booster mechanism, the external booster is eliminated, allowing the booster cylinder to obtain super thrust while maintaining an extremely compact axial and radial structure. The installation space requirement is significantly reduced compared to the traditional split booster solution, achieving a leapfrog improvement in power density. 2. Excellent output performance and precise control: Based on the pressure equalization of the through oil chamber and the thrust coupling principle of the dual piston area, it can output a huge force value far exceeding that of the standard cylinder of the same class with a conventional system pressure (such as 18MPa); combined with the direct measurement of the built-in displacement sensor and the closed-loop control of the servo proportional valve, it realizes micron-level high-precision and high-response synchronous control of output pressure and piston position. 3. Convenient integration and reliable operation: The modular slide design makes the booster cylinder a standard unit that can be installed and used immediately, greatly simplifying the main unit assembly process and ensuring installation alignment accuracy; the dual guiding system (inner cylinder guide sleeve and outer slide guide rail) ensures linearity and stability of movement under extreme off-center loads; the non-rigid connection force transmission method reduces internal stress concentration, and the overtravel protection mechanism provides redundant safety barriers, jointly ensuring long-term reliability and service life; 4. By forming a non-rigid contact force transmission interface between the first and second piston rods, over-constraint is eliminated, allowing for a small radial compensation space between the two piston rods during movement. This reduces the lateral load to zero or close to zero, and ensures uniform pressure on each seal. This significantly reduces the asymmetric wear of high-pressure seals. Compared to traditional rigid booster cylinders, the system maintenance cycle and seal life are expected to be improved by more than 30%, solving the reliability problem under high-frequency booster conditions in actual production. 5. The oil pressure balance between the working oil chamber and the booster oil chamber is achieved by connecting the internal oil passage through a radial guide groove. On the one hand, compared with the external pipeline setting in conventional technology, this solution has extremely low oil circuit resistance, extremely short pressure wave propagation time, shortened booster response time, and reduced overall axial length. On the other hand, the guide groove ensures that the working oil chamber and the booster oil chamber can be in a conductive state under any condition of the first piston rod and the second piston rod, so that the hydraulic support force on the non-rigid interface between the two is always self-balanced with the load pressure. Even if the first piston rod is subjected to lateral force, the interface oil film can provide uniform radial support, further improving the anti-eccentric load capability. 6. Maintainability and adaptability: The modular design facilitates disassembly and maintenance; by replacing piston components of different specifications or adjusting the system pressure, it can be flexibly adapted to process requirements of different tonnages and strokes, and has a wide range of applications. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the overall structure of an embodiment of this application; Figure 2 This is a longitudinal sectional view of an embodiment of this application; Figure 3 This is a cross-sectional structural schematic diagram of the overtravel protection mechanism according to an embodiment of this application; Figure 4 This is a schematic diagram of the structure of the second piston rod in an embodiment of this application, where a is a front end view and b is a partial sectional view.

[0018] Figure label: 1. Front flange; 2. Cylinder; 3. Front guide sleeve; 4. Rear guide sleeve; 5. First piston rod; 51. Retraction oil chamber; 52. Working oil chamber; 6. Second piston rod; 61. Guide cavity; 62. Pressurization oil chamber; 63. Internal oil passage; 64. Blind hole; 65. Oil guide groove; 7. Rear flange; 8. Rear end cover; 9. Displacement sensor; 10. Protective cover; 11. Pad; 12. Lead screw; 13. Top head; 14. Adjusting shim; 15. Guide rail plate; 19. Top rod; 20. Sealing ring; 21. Sealing cover plate; 22. Return spring; 23. Micro switch. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0020] Reference Figures 1-4 This application discloses an integrated sliding block with built-in coupling servo booster cylinder, which includes a cylinder barrel 2. An integrated booster execution unit is disposed inside the cylinder barrel 2, including a first pressure chamber and a second pressure chamber distributed along the axial direction of the cylinder barrel 2, and an internal oil passage 63 for connecting the two. It also includes a first piston rod 5 and a second piston rod 6 that can move relative to each other along the axial direction. A non-rigid contact force transmission interface is formed between the second piston rod 6 and the first piston rod 5. A modular slide guide unit is provided outside the cylinder 2, which includes a front mounting component fixedly connected to the front end of the cylinder 2 and a rear mounting component fixedly connected to the rear end of the cylinder 2. The front mounting component and the rear mounting component are provided with guide mechanisms for sliding cooperation with the external frame, so that the hydraulic cylinder constitutes a power slide module that can be plugged in as a whole.

[0021] Specifically, the inner wall of the cylinder 2 is provided with a front guide sleeve 3 and a rear guide sleeve 4 with a front opening and a rear opening in the first pressure chamber, and the rear end of the cylinder 2 is provided with a rear end cover 8 and a protective cover 10. One end of the second piston rod 6 slides in the second pressure chamber, and the other end slides through the opening of the rear guide sleeve 4; One end of the first piston rod 5 slides in the rear guide sleeve 4, and the other end slides through the opening of the front guide sleeve 3. A top head 13 is detachably installed at the front end of the first piston rod 5 and is slidably disposed in the front guide sleeve 3.

[0022] Both the first piston rod 5 and the second piston rod 6 are configured with a T-shaped cross section; The large end of the second piston rod 6 divides the second pressure chamber into a guide chamber 61 and a booster oil chamber 62, with the booster oil chamber 62 connected to the oil port. The large end of the first piston rod 5 divides the first pressure chamber into a retraction oil chamber 51 and a working oil chamber 52. The working oil chamber 52 is connected to the booster oil chamber 62 through an internal oil passage 63. The internal oil passage 63 is located in the second piston rod 6 and extends through both ends of the second piston rod 6 axially. Specifically, a radially arranged oil guide groove 65 is provided at the end of the second piston rod 6 closest to the first piston rod 5 (i.e., the front end). The internal oil passage 63 is connected to the oil guide groove 65, and the oil pressure of the working oil chamber 52 and the booster oil chamber 62 is balanced through the oil guide groove 65. Figure 2 and Figure 4 As shown.

[0023] In addition, refer to Figure 1 and Figure 2 A displacement sensor 9 is installed on the end cap, and a blind hole 64 is provided in the second piston rod 6 along its axial direction for the insertion of the detection rod of the displacement sensor 9. The detection rod of the displacement sensor 9 is coaxially arranged with the second piston rod 6, and several internal oil passages 63 are eccentrically arranged on the second piston rod 6.

[0024] Additionally, refer to Figure 2 and Figure 3 The side wall of cylinder 2, corresponding to the guide cavity 61, is provided with an overtravel protection mechanism for detecting the extreme stroke position of the large end of the second piston rod 6. The overtravel protection mechanism includes a trigger rod 19 that slides through the side wall of cylinder 2, a sealing cover plate 21 and a micro switch 23 installed on the side wall of cylinder 2; One end of the trigger rod 19 extends into the guide cavity 61, and the other end slides through the sealing cover plate 21; when the large end of the second piston rod 6 moves to the limit stroke position, its large end side wall pushes against the trigger rod 19, so that the other end of the trigger rod 19 triggers the micro switch 23. A return spring 22 is provided between the end of the trigger rod 19 near the guide cavity 61 and the sealing cover plate 21. When the return spring 22 is in the initial state, the end of the trigger rod 19 near the guide cavity 61 protrudes from the inner wall of the guide cavity 61. The trigger rod 19 is sealed and slidably connected to the sealing cover plate 21 through the sealing ring 20.

[0025] Furthermore, referring to Figure 1 and Figure 2 Both the front and rear slide assemblies include multiple guide rails 15. The front slide assembly is equipped with pads 11 for supporting span fine-tuning, lead screws, and trapezoidal bolt assemblies for position locking. The rear slide assembly is equipped with replaceable adjusting shims 14 for axial dimension fine-tuning and screw assemblies for final locking. Specifically, the front slide assembly includes a front flange 1 fixedly connected to the front end of the cylinder body. The front flange 1 is provided with two opposing pads 11 and two sets of lead screws 12 for adjusting the distance between the two pads 11. Multiple guide rails 15 are provided on the side wall of the front flange 1. The specific structure of these guide rails is prior art and can be easily implemented by those skilled in the art, so there is no need to elaborate. As for the rear slide assembly, the rear flange 7, adjusting shims 14, and screw assemblies are also prior art and can be easily implemented by those skilled in the art, so there is no need to elaborate.

[0026] Therefore, during assembly, first press the rear guide sleeve 4 into the step inside the cylinder 2, then install the first piston rod 5 and the front guide sleeve 3 in sequence, and tighten and fix the front end of the front guide sleeve 3 with screws. Install the second piston rod 6 from the rear end of the cylinder 2, ensuring that its rod end face (200mm in diameter) is precisely aligned with the rear end face of the first piston rod 5 to form a contact interface. Then install the rear end cover 8 and fix the displacement sensor 9 to the rear end cover 8, allowing its detection rod to extend into the blind hole 64 in the center of the second piston rod 6. Next, install the protective cover 10. Finally, position and tighten the front slide assembly (including the front flange 1, pad 11, lead screw 12, and guide plate 15) and the rear slide assembly (including the rear flange 7, adjusting pad 14, and guide plate 15) through the stop, forming a complete module. In addition, according to the needs of the straightening process, a detachable mandrel 13 can be installed at the front end of the first piston rod 5. The mandrel 13 serves as a power output terminal and can be replaced according to different straightening molds or workpiece shapes to directly contact and apply pressure to the workpiece.

[0027] The booster cylinder is embedded in the guide rail of the main frame via the guide rail plate 15 on its slide. The mounting axial clearance and orientation of the booster cylinder can be finely adjusted by adjusting the thickness of the adjusting shim 14. After adjustment, the screw assembly of the rear flange 7 is tightened. The support span of the shim block 11 can also be adjusted by rotating the lead screw 12 and the trapezoidal bolt assembly is tightened.

[0028] When a pressing action is required, the servo proportional valve controls the pressure oil to simultaneously enter the booster oil chamber 62 and the working oil chamber 52, which are connected by the built-in oil passage 63. This equal oil pressure pushes the second piston rod 6 forward, and its rod end then contacts and pushes the first piston rod 5. When the second piston rod 6 accelerates, it first compresses the oil film between the contact interface of the second piston rod 6 and the first piston rod 5, and the oil pressure gradually increases, then pushes the first piston rod 5, forming a force-pressure-force conversion process. Essentially, it is a low-pass filter that filters out the high-frequency components of the impact, facilitating precise force closed-loop control and soft landing function, avoiding overshoot caused by rigid impact, and also significantly reducing equipment vibration and noise.

[0029] Then, due to the synchronous action of hydraulic pressure on the large end area of ​​the second piston rod 6 and the annular area of ​​the working oil chamber 52 at the large end of the first piston rod 5, the thrust generated at both locations is coupled through the contact surface, forming a huge total output force, which is then transmitted to the workpiece through the mandrel 13. During this process, the displacement sensor 9 provides real-time feedback on the precise position, forming a closed-loop control.

[0030] Furthermore, in traditional booster cylinders, the first piston rod 5 and the second piston rod 6 are typically designed with threads, welding, or integral components (rigid connection). Under long stroke or high pressure conditions, even slight deformation of the cylinder body or machining errors can lead to coaxiality errors between the two piston rods. This error translates into enormous lateral forces in a rigid system, causing severe uneven wear on the guide sleeve and sealing ring 20, and even causing creeping, thus shortening their lifespan. This application, however, eliminates over-constraint by forming a non-rigid contact force transmission interface between the two piston rods, allowing for a small radial compensation space during movement. This reduces the lateral load to zero or near zero, ensuring uniform pressure on each seal and significantly reducing asymmetric wear on high-pressure seals. Compared to traditional rigid booster cylinders, the system maintenance cycle and seal life are expected to increase by more than 30%, solving the reliability problem under high-frequency booster conditions in actual production.

[0031] Furthermore, the oil pressure balance between the working oil chamber 52 and the booster oil chamber 62 is achieved by connecting the internal oil passage 63 through the radial oil guide groove 65. On the one hand, compared with the external pipeline setting in conventional technology, this solution has extremely low oil circuit resistance, extremely short pressure wave propagation time, shortened booster response time, and reduced overall axial length. On the other hand, the oil guide groove 65 ensures that the working oil chamber 52 and the booster oil chamber 62 can be in a conductive state under any condition of the first piston rod 5 and the second piston rod 6, so that the hydraulic support force on the non-rigid interface between the two is always self-balanced with the load pressure, and even if the first piston rod 5 is subjected to lateral force, the interface oil film can provide uniform radial support, further improving the anti-eccentric load capability.

[0032] During the return stroke, pressurized oil enters the retraction chamber 51, and the pressurized chamber 62 and the working chamber 52 begin to return oil via the guide groove 65 and the built-in oil passage 63. The first piston rod 5 and the second piston rod 6 return under the action of pressure difference. Throughout the process, the overtravel protection mechanism in the guide chamber 61 is in standby mode, providing mechanical protection against overtravel. The protective cover 10 forms a second layer of mechanical protection to ensure the safety of the rear structure of the cylinder.

[0033] In a specific example, for instance, the working pressure of the booster cylinder system in this application is P=18MPa. The piston diameter of the second piston rod 6 in the booster oil chamber 62 is D2=380mm, and the rod diameter is d2=200mm; the piston diameter of the first piston rod 5 is D1=400mm, and the rod diameter is d1=240mm. In this example, pressurized oil is supplied to the continuously connected booster oil chamber 62 and working oil chamber 52 via a servo proportional valve. The system pressure P acts simultaneously on the large end area A1 of the second piston rod 6 and the effective area A2 of the first piston rod 5 near the working oil chamber 52. The calculated coupled thrust is: ; Based on these structural parameters, the displacement of the second piston rod 6 is detected by the displacement sensor 9, forming a closed-loop precise control of the output pressure and position. This application demonstrates excellent space utilization and output performance.

[0034] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A built-in coupled servo booster cylinder with an integrated slide, comprising a cylinder barrel, characterized in that, The cylinder is equipped with an integrated booster actuator, including a first pressure chamber, a second pressure chamber, and an internal oil passage for connecting the two, distributed along the cylinder axial direction. It also includes a first piston rod and a second piston rod that can move relative to each other along the axial direction, and a non-rigid contact force transmission interface is formed between the second piston rod and the first piston rod. A modular slide guide unit is provided outside the cylinder, which includes a front mounting component fixedly connected to the front end of the cylinder and a rear mounting component fixedly connected to the rear end of the cylinder. The front mounting component and the rear mounting component are provided with guide mechanisms for sliding cooperation with an external frame, so that the hydraulic cylinder constitutes a power slide module that can be plugged in as a whole.

2. The built-in coupled servo booster cylinder with an integrated slide as described in claim 1, characterized in that, The inner wall of the cylinder is provided with a front guide sleeve and a rear guide sleeve with a front opening and a rear opening in the first pressure chamber, and a rear end cover is provided at the rear end of the cylinder. One end of the second piston rod slides in the second pressure chamber, and the other end slides through the opening of the rear guide sleeve; One end of the first piston rod slides in the rear guide sleeve, and the other end slides through the opening of the front guide sleeve.

3. The built-in coupled servo booster cylinder with an integrated slide as described in claim 2, characterized in that, Both the first piston rod and the second piston rod are configured with a T-shaped cross section; The large end of the second piston rod divides the second pressure chamber into a guide chamber and a pressurizing oil chamber, and the pressurizing oil chamber is connected to an oil port; The large end of the first piston rod divides the first pressure chamber into a retraction oil chamber and a working oil chamber, and the working oil chamber and the booster oil chamber are connected through the built-in oil passage.

4. The built-in coupled servo booster cylinder with an integrated slide as described in claim 3, characterized in that, The built-in oil passage is opened in the second piston rod and passes through both ends of the second piston rod axially; The second piston rod has a radially arranged oil guide groove at one end near the first piston rod. The built-in oil passage is connected to the oil guide groove, and the oil pressure of the working oil chamber and the pressurizing oil chamber is balanced through the oil guide groove.

5. The built-in coupled servo booster cylinder with an integrated slide as described in claim 2, characterized in that, A displacement sensor is installed on the end cap, and a blind hole is provided in the second piston rod along its axial direction for the displacement sensor detection rod to be inserted.

6. The built-in coupled servo booster cylinder with an integrated slide as described in claim 5, characterized in that, The detection rod of the displacement sensor is coaxially arranged with the second piston rod, and the built-in oil passages are eccentrically arranged on the second piston rod and there are several of them.

7. The built-in coupled servo booster cylinder with an integrated slide as described in claim 3, characterized in that, The cylinder sidewall is provided with an overtravel protection mechanism for detecting the extreme stroke position of the large end of the second piston rod at the location corresponding to the guide cavity.

8. The built-in coupled servo booster cylinder with an integrated slide as described in claim 7, characterized in that, The overtravel protection mechanism includes a trigger rod that slides through the cylinder sidewall, a sealing cover plate and a micro switch installed on the cylinder sidewall; One end of the trigger rod extends into the guide cavity, and the other end slides through the sealing cover plate in a sealing seal. When the large end of the second piston rod moves to the limit stroke position, its large end sidewall pushes against the trigger rod, so that the other end of the trigger rod triggers the micro switch. A reset spring is provided between the end of the trigger rod near the guide cavity and the sealing cover plate. When the reset spring is in the initial state, the end of the trigger rod near the guide cavity protrudes from the inner wall of the guide cavity.

9. A built-in coupled servo booster cylinder with an integrated slide as described in claim 2, characterized in that, The front end of the first piston rod is detachably mounted with a top head that is slidably disposed in the front guide sleeve.

10. The built-in coupled servo booster cylinder with an integrated slide as described in claim 1, characterized in that, Both the front slide assembly and the rear slide assembly include multiple guide rails. The front slide assembly is equipped with a pad for supporting the span fine adjustment, a lead screw, and a trapezoidal bolt assembly for position locking. The rear slide assembly is equipped with a replaceable adjusting pad for axial dimension fine adjustment and a screw assembly for final locking.

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