A modular piston assembly

Abstract

The application discloses a block type piston assembly, which comprises a piston body composed of a first block and a second block, and each of the first block and the second block is provided with a first flow channel part and a second flow channel part; the first block and the second block are inserted in a staggered mode relative to a piston central axis, so that the first flow channel part of the first block and the second flow channel part of the second block are in common communication to form a first unloading flow channel, and the second flow channel part of the first block and the first flow channel part of the second block are in common communication to form a second unloading flow channel; the end faces of the piston body are in a stepped mode and comprise a first platform close to a piston body axis and a second platform away from the axis, and the first platform is more axially protruded to the outside of the piston than the second platform. The application has the effects of optimizing the internal flow channel structure and the end face layout of the piston, and solving the problems of difficult machining of a complex flow channel, poor sealing of a split structure and low unloading efficiency in the prior art.

Description

Technical Field

[0001] This application relates to the field of piston technology, and in particular to a modular piston assembly. Background Technology

[0002] As a core component of devices such as hydraulic shock absorbers, the piston's end-face structure and internal unloading flow channel design directly determine the efficiency of pressure balance and the smoothness of movement. To achieve smooth start-up, existing technologies typically create a single unloading hole on the piston end face. However, this design of holes evenly distributed on the same plane fails to consider the differences in the path of oil flowing into the flow channel from different positions in the piston cavity, resulting in uneven flow resistance, a sluggish pressure balance process, and difficulty in completely eliminating the "stick-slip" phenomenon during startup.

[0003] To further optimize the flow channel, some designs attempt to incorporate more complex irregular or asymmetrical unloading channels within the piston. However, the one-piece piston structure makes precision machining of such complex internal cavities extremely difficult. Even with a modular structure, if the splicing method is not optimized in conjunction with the flow channel design, the integrity and consistency of the assembled flow channel cannot be guaranteed. Furthermore, under high pressure, the joint surfaces of the splices can easily become weak points for leakage, thus disrupting the pressure balance function.

[0004] Furthermore, in existing piston designs, the end openings of the unloading flow channel generally lack targeted protection and guidance structures. The sharp angles at the opening edges not only increase local resistance and noise in oil flow but also cause continuous shear damage to the lip of the mating seal under high-pressure cycling impact, becoming a contributing factor to early seal failure. Therefore, there is an urgent need in this field for a piston solution with innovative designs in end face structure, flow channel layout, and sealing coordination. Utility Model Content

[0005] This application proposes a modular piston assembly, which aims to optimize the internal flow channel structure and end face layout of the piston to solve the problems of difficult processing of complex flow channels, poor sealing performance of split structures, and low unloading efficiency in the prior art.

[0006] Specifically, this modular piston assembly employs mirror-symmetrical first and second modules, which are staggered relative to the piston's central axis, allowing their respective first and second flow channels to connect and form multiple interconnected unloading channels. Simultaneously, the piston body's end faces are constructed in a stepped shape, including a first platform and a second platform with different axial protrusions, with the end openings of the first and second flow channels respectively positioned on different platforms.

[0007] It enables: First, the staggered plug structure decomposes the complex internal flow channel into a simple flow channel part that is easy to be precision machined. While reducing the manufacturing difficulty, the tight combination of the blocks ensures the flow channel sealing and eliminates leakage at the joint surface; Second, the design of the stepped end face and the differentiated platform opening provides the optimal inflow and outflow path for the oil, and can optimize the pressure balance process according to the principle of fluid dynamics.

[0008] This improves the overall performance of the piston assembly: it achieves efficient and low-cost machining of complex internal cavities, ensures the sealing reliability of the unloading flow channel under high pressure, and ultimately significantly improves the piston's starting smoothness, running accuracy and service life. At the same time, through the optimized end face and flow channel opening structure, the impact on the seals is reduced, further ensuring the long-term reliability of the sealing system.

[0009] The modular piston assembly provided in this application adopts the following technical solution: A modular piston assembly, comprising: The piston body is composed of a first block and a second block that are mirror images of each other, and each block is provided with a first flow channel and a second flow channel. The first block and the second block are inserted in a staggered manner relative to the piston's central axis, such that the first flow channel of the first block and the second flow channel of the second block are connected together to form a first unloading flow channel, and the second flow channel of the first block and the first flow channel of the second block are connected together to form a second unloading flow channel. The piston body has stepped end faces at both ends, including a first platform close to the piston body axis and a second platform away from the axis. The first platform protrudes more axially outward from the piston than the second platform. The end openings of the first flow channel and the second flow channel are respectively provided on the second platform and the first platform.

[0010] By adopting the above technical solution, the first and second components are assembled in a mirror image to form the piston body. The first flow channel is a complete aperture that penetrates the first component body, and the second flow channel is a complete aperture that penetrates the second component body. By interlocking the first and second components relative to the piston's central axis, the first flow channel on the first component and the second flow channel on the second component are aligned vertically and connected to form a longer, high-precision, continuously variable diameter first unloading flow channel that penetrates the piston body. Similarly, the second flow channel on the first component and the first flow channel on the second component form a second unloading flow channel. By intelligently "decomposing" the traditionally difficult-to-manufacture integrated complex spatial flow channel into simple flow channel sections that are easy to manufacture on two independent modules, and then "reassembling" them through plug-in connection, and combining the specially designed stepped end faces at both ends of the piston, the openings at both ends of the reassembled unloading flow channel are respectively set on the first platform and the second platform at different heights. This makes each unloading flow channel itself a highly efficient fluid self-regulating management system. When the piston works, the oil flows in from the lower second platform end opening, the flow cross section converges, forming a highly efficient jet that can quickly penetrate the viscous resistance of the oil, rapidly establish initial pressure balance, and achieve instantaneous response and extremely low start-up friction. After being smoothly guided in the curved flow channel, the oil flows out from the higher first platform end opening, the flow cross section expands, the flow velocity slows down, and the kinetic energy is absorbed, thereby effectively calming pressure fluctuations and turbulence, ensuring the smoothness and quietness of the oil inflow. During this process, the multiple unloading channels evenly distributed on the piston end face work together to optimize and balance the global hydraulic load, completely avoiding piston wear, jamming and abnormal vibration caused by uneven unloading force in traditional designs.

[0011] The system ultimately achieves efficient and smooth conversion of unbalanced pressure into balanced axial driving force at the structural level, thus achieving excellent results at the system level with minimal starting friction, stable operation and extremely low noise. It systematically overcomes the inherent defects of existing technologies, such as difficult processing of complex flow channels, poor sealing of split structures and low unloading efficiency.

[0012] Preferably, the first platform is provided with a recessed portion, which causes the edge of the first platform to naturally form an annular shoulder.

[0013] Preferably, the end of the second flow channel is provided with a flow guide port, and the flow cross section of the flow guide port gradually converges towards the interior of the flow channel.

[0014] Preferably, the inner diameter of the first flow channel gradually increases from its end opening into the flow channel; and / or, the second flow channel is a straight channel extending axially along the piston.

[0015] Preferably, the joint surface between the first and second pieces is a stepped structure, including mutually cooperating bosses and grooves.

[0016] Preferably, a bend is formed at the transition between the first platform and the second platform, and a buffer groove is provided at the bend.

[0017] Preferably, the piston body has an annular toothed groove in the middle of its outer wall, and the piston body is provided with an elastic seal, which is interference-fitted with the toothed groove.

[0018] Preferably, the tooth groove group includes a first tooth groove near the top surface of the piston body, a second tooth groove near the bottom surface of the piston body, and a third tooth groove located between the first tooth groove and the second tooth groove, wherein the depth of the second tooth groove is greater than the depth of the first tooth groove and the third tooth groove.

[0019] Preferably, the bottom surface of the elastic seal is an inclined surface.

[0020] In summary, this application includes at least one of the following beneficial technical effects: 1. Achieved efficient, precise, and low-cost manufacturing of complex piston structures. By designing the piston body as being composed of two mirror-image blocks interlocked, the traditionally difficult-to-machine integrated complex spatial unloading flow channel is decomposed into simple flow channel sections that are easy to manufacture on two independent blocks. This perfectly solves the machining problem of complex internal flow channels in high-performance pistons and avoids the shortcomings of high cost and insufficient material properties of 3D printing technology, laying the foundation for the large-scale economical production of high-performance pistons. 2. Significantly improved piston dynamic performance, achieving rapid and smooth start-up and quiet operation. Through a stepped end-face design, the openings at both ends of the continuously variable diameter unloading channel are positioned on platforms of different heights, creating optimal inflow and outflow paths for the oil. Each channel itself constitutes a highly efficient bidirectional adaptive fluid management system. This not only quickly balances pressure and greatly reduces starting friction at startup, but also effectively smooths pressure fluctuations and turbulence throughout the entire operating process, thus achieving excellent results in rapid start-up, smooth operation, and extremely low noise. 3. The sealing reliability and structural durability of the piston have been comprehensively enhanced. By interference fitting of elastic seals in the outer wall tooth groove assembly, and the buffer groove design at the platform transition to eliminate stress concentration, the piston, together with the stepped structure of the interlocking surface, ensures high rigidity and long service life under high pressure and high frequency reciprocating motion. Attached Figure Description

[0021] Figure 1 This is a cross-sectional view of the modular piston assembly in this embodiment; Figure 2 This is a top view of the modular piston assembly in this embodiment; Figure 3 This is a bottom view of the modular piston assembly in this embodiment.

[0022] Reference numerals: 1. Piston body; 11. First assembly; 111. Groove; 12. Second assembly; 121. Boss; 13. First flow channel; 14. Second flow channel; 15. First unloading flow channel; 16. Second unloading flow channel; 17. First platform; 18. Second platform; 2. Recess; 3. Shoulder; 4. Guide port; 5. Buffer groove; 6. Gear assembly; 61. First tooth groove; 62. Second tooth groove; 63. Third tooth groove; 7. Elastic seal; 71. Gear ring assembly. Detailed Implementation

[0023] The following is in conjunction with the appendix Figures 1-3 This application will be described in further detail.

[0024] This application discloses a modular piston assembly.

[0025] Reference Figures 1-3 The piston body 1 is composed of a first assembly 11 and a second assembly 12 joined together by mirror-image insertion. Both the first assembly 11 and the second assembly 12 are machined with a through first flow channel 13 and a second flow channel 14. The first flow channel 13 and the second flow channel 14 are evenly distributed on the piston body 1. By inserting the first assembly 11 and the second assembly 12 relative to the piston's central axis, the first flow channel 13 of the first assembly 11 and the second flow channel 14 of the second assembly 12 are connected to form a first unloading flow channel 15. At the same time, the second flow channel 14 of the first assembly 11 and the first flow channel 13 of the second assembly 12 are connected to form a second unloading flow channel 16. Thus, the first unloading flow channel 15 and the second unloading flow channel 16 are also evenly distributed on the piston body 1.

[0026] The piston body 1 has a stepped structure design at both ends, including a first platform 17 close to the axis of the piston body 1 and a second platform 18 away from the axis. The first platform 17 protrudes more axially outward from the piston than the second platform 18. The end openings of the first flow channel 13 and the second flow channel 14 are respectively set on the second platform 18 and the first platform 17, forming a staggered opening layout.

[0027] Furthermore, a recessed portion 2 is provided on the first platform 17. The processing of the recessed portion 2 causes the edge of the first platform 17 to naturally form an annular shoulder 3. A guide port 4 is provided at the end of the second flow channel portion 14. The flow cross section of the guide port 4 gradually converges towards the inside of the flow channel to optimize the fluid dynamics performance. The guide port 4 is adjacent to the shoulder 3, making the guide port 4 shaped like a sieve, which guides the oil to smoothly enter the flow channel, reduces flow resistance and eddy current generation, reduces hydraulic shock and cavitation noise, improves the stability of the unloading process, and has a better guiding effect.

[0028] The inner diameter of the first flow channel 13 gradually increases from its end opening into the flow channel, forming a gradually expanding structure. The lower part of the first flow channel 13 is inclined in the opposite direction to the piston body 1 axis. The second flow channel 14 is a straight channel extending along the piston axis, and the inner diameter of the second flow channel 14 is larger than the inner diameter of the upper part of the first flow channel 13. Through the precise design of the flow channel geometry, the complex requirements of the shock absorber for bidirectional damping force characteristics are met, and the adaptability to working conditions is improved.

[0029] An angle is formed at the transition between the first platform 17 and the second platform 18, and a buffer groove 5 is provided at the angle to eliminate the stress concentration at the sharp angle and provide a release space for the thermal deformation and stress deformation of the material. The stress dispersion design significantly improves the fatigue resistance and reliability of the piston.

[0030] A toothed groove group 6 with multiple annular grooves is formed in the middle of the outer wall of the piston body 1. The toothed groove group 6 includes a first toothed groove 61 near the top surface of the piston body 1, a second toothed groove 62 near the bottom surface of the piston body 1, and four third toothed grooves 63 located between the first toothed groove 61 and the second toothed groove 62. The depth of the second toothed groove 62 is greater than the depth of the first toothed groove 61 and the third toothed groove 63. An elastic seal 7 is interference-fitted in the middle of the outer wall of the piston body 1. The center of the elastic seal 7 has an integrally formed toothed ring group 71 for cooperating with the toothed groove group 6. The toothed ring group 71 of the elastic seal 7 is interference-fitted with the toothed groove group 6 to enhance the cooperation effect between the seal and the toothed groove group 6. The multi-groove structure and interference fit provide mechanical locking of the seal, greatly enhancing the seal's resistance to torsion and displacement, and preventing leakage caused by loosening. The bottom surface of the elastic seal 7 is machined as a slope to facilitate the displacement of the elastic seal 7 in the fluid.

[0031] Specifically, the piston body 1 is formed by the vertical mirror image assembly of the first component 11 and the second component 12. The first flow channel 13 is a complete aperture penetrating the body of the first component 11, and the second flow channel 14 is a complete aperture penetrating the body of the second component 12. By interlocking the first component 11 and the second component 12 with a misalignment relative to the piston's central axis, the first flow channel 13 on the first component 11 and the second flow channel 14 on the second component 12 are vertically aligned and connected to form a longer, high-precision, continuously variable diameter first unloading flow channel 15 that penetrates the piston body 1. Similarly, the second flow channel 14 on the first component 11 and the first flow channel 13 on the second component 12 form a second unloading flow channel 16. By intelligently disassembling the traditionally difficult-to-manufacture integrated complex spatial flow channel into simple flow channel sections that are easy to manufacture on two independent modules, and then connecting them through plug-in, and combining the specially designed stepped end faces at both ends of the piston, the openings at both ends of the recombined unloading flow channel are respectively set on the first platform 17 and the second platform 18 with different heights at both ends, so that each unloading flow channel constitutes a highly efficient fluid self-regulating management system. Among them, when the upper end face of the first unloading flow channel 15 is a compression surface and the lower end face is a rebound surface, firstly, through uniform distribution The first unloading channel 15 and the second unloading channel 16 optimize the overall load. Secondly, for the upper end face, the first unloading channel 15 initially acts as a high-efficiency, high-speed oil jet, responsible for rapidly and accurately penetrating the viscous resistance of the oil and quickly establishing initial pressure balance, which is key to achieving instantaneous response. Then, the oil is smoothly guided within the curved channel and finally flows out from the large-diameter end of the higher first platform 17. The flow cross-section expands, the flow velocity decreases, and the kinetic energy is absorbed, effectively calming pressure fluctuations and turbulence, ensuring the smoothness and quietness of the oil inflow. The second unloading channel 16 initially serves as a stable main pressure relief channel. Leveraging its low flow resistance, it receives and smoothly releases large volumes of oil, maintaining pressure balance stability. Then, the flow cross-section contracts, accelerating the oil to form a highly efficient jet. This results in a strong jet alternating with a smooth, homogeneous flow on the piston body 1, avoiding piston wear, jamming, and abnormal vibration caused by uneven unloading force in traditional designs. This allows for the instantaneous and efficient conversion of unbalanced pressure into a balanced axial driving force, thereby achieving system-level efficiency. The design achieves excellent results with minimal starting friction, extremely smooth operation, and very low noise. At the same time, the small-diameter flow channel opening is set at the lower second platform 18, making it closer to the oil area with high flow velocity and high kinetic energy near the cylinder wall, which facilitates the passage of high-pressure oil and its acceleration into a high-efficiency jet. The large-diameter flow channel opening is set at the higher first platform 17, so that its opening faces the relatively calm and stable oil area near the piston axis, which can smoothly receive and release a large amount of oil, avoiding turbulence, cavitation, and noise caused by direct impact on the cylinder wall or entrainment in eddies.Furthermore, the internal flow channel structure and end face layout of the piston are optimized to solve the problems of difficult processing of complex flow channels, poor sealing of split structures, and low unloading efficiency in the existing technology.

[0032] Furthermore, in this embodiment, the joint surface of the first assembly block 11 and the second assembly block 12 is designed as a stepped structure. The upper end of the second assembly block 12 is provided with a stepped boss 121, and the lower end of the first assembly block 11 is provided with a groove 111 that cooperates with the boss 121. During installation, precise positioning and self-locking are achieved through the convex-concave fit. Its function is to enhance the circumferential and radial constraints between the assembly blocks and resist shearing and vibration during operation. The effect is to ensure the structural integrity and dimensional stability of the piston body 1 after assembly. The advantage is that it fundamentally solves the defects of easy misalignment and easy leakage of the joint surface of the split piston, and achieves high rigidity and high sealing performance.

[0033] Furthermore, in this embodiment, there is no particular limitation on the specific number of the third tooth groove 63.

[0034] Furthermore, in this embodiment, the end shape of the first flow channel is arc-shaped, so that the second platform, which has a limited length in the radial direction, conforms to the geometric contour of the piston end face edge. This allows the flow channel opening to extend as far as possible to the outermost edge of the second platform, thereby establishing an efficient fluid interface in the most critical area where the oil kinetic energy is highest. This provides the oil with a smooth transition path without impact, and can very naturally "catch" and guide the high-speed oil in the piston cavity sidewall area into the flow channel. This reduces turbulence and energy loss from the source, improves the flow efficiency, and maximizes the effective flow cross-sectional area while increasing the overall structural size, ensuring the flow rate.

[0035] It should be noted that the various embodiments of this application can be arbitrarily combined into new embodiments, provided that the solutions do not conflict and the technical solutions can coexist.

[0036] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. A modular piston assembly, characterized in that, include: The piston body (1) is composed of a first assembly (11) and a second assembly (12) mirror images of each other, and each assembly is provided with a first flow channel (13) and a second flow channel (14). The first assembly (11) and the second assembly (12) are inserted in a staggered manner relative to the piston central axis, so that the first flow channel (13) of the first assembly (11) and the second flow channel (14) of the second assembly (12) are connected to form a first unloading flow channel (15), and the second flow channel (14) of the first assembly (11) and the first flow channel (13) of the second assembly (12) are connected to form a second unloading flow channel (16). The piston body (1) has two stepped end faces, including a first platform (17) close to the axis of the piston body (1) and a second platform (18) away from the axis. The first platform (17) protrudes more axially outward from the piston than the second platform (18). The end openings of the first flow channel (13) and the second flow channel (14) are respectively provided on the second platform (18) and the first platform (17).

2. The modular piston assembly according to claim 1, characterized in that: The first platform (17) is provided with a recess (2), which causes the edge of the first platform (17) to naturally form an annular shoulder (3).

3. The modular piston assembly according to claim 1, characterized in that: The end of the second flow channel (14) is provided with a flow guide (4), and the flow cross section of the flow guide (4) gradually converges towards the inside of the flow channel.

4. The modular piston assembly according to claim 1, characterized in that: The inner diameter of the first flow channel (13) gradually increases from its end opening into the flow channel; and / or, the second flow channel (14) is a straight channel extending along the piston axis.

5. The modular piston assembly according to claim 1, characterized in that: The joint surface of the first piece (11) and the second piece (12) is a stepped structure, including a boss (121) and a groove (111) that cooperate with each other.

6. The modular piston assembly according to claim 1, characterized in that: The transition between the first platform (17) and the second platform (18) is formed by a bend, and a buffer groove (5) is provided at the bend.

7. The modular piston assembly according to claim 1, characterized in that: The piston body (1) has an annular toothed groove group (6) in the middle of its outer wall, and the piston body (1) has an elastic seal (7) which is interference-fitted with the toothed groove group (6).

8. The modular piston assembly according to claim 7, characterized in that: The tooth groove group (6) includes a first tooth groove (61) near the top surface of the piston body (1), a second tooth groove (62) near the bottom surface of the piston body (1), and a third tooth groove (63) located between the first tooth groove (61) and the second tooth groove (62). The depth of the second tooth groove (62) is greater than the depth of the first tooth groove (61) and the third tooth groove (63).

9. The modular piston assembly according to claim 7 or 8, characterized in that: The bottom surface of the elastic seal (7) is an inclined surface.

Images