Hydraulic cylinder structure for stamping vibration simulation

Abstract

A hydraulic cylinder structure for simulating stamping vibration includes an upper end cap assembly, a lower end cap assembly, a cylindrical cylinder body, a piston assembly, and a buffer structure. The cylindrical cylinder body connects the upper and lower end cap assemblies and together defines a piston working chamber. The piston assembly is disposed within the piston working chamber and includes a piston rod and a punch adapter fixed to the end of the piston rod. The buffer structure includes a main buffer oil chamber formed by a plunger boss at the bottom of the piston rod and a valve sleeve groove on the lower end cap assembly. The main buffer oil chamber is connected to an external hydraulic system through a radial oil inlet hole on the lower end cap assembly. A damping effect is generated through the main buffer oil chamber in conjunction with a high-pressure relief channel to absorb impact energy.

Description

Hydraulic cylinder structure for stamping vibration simulation Technical Field

[0001] This invention relates to the field of hydraulic transmission technology, and in particular to a cylinder structure for simulating stamping vibration. Prior Technology

[0002] During operation, large stamping presses experience instantaneous impact forces of up to hundreds of tons. These massive impact loads lead to fatigue cracks in the machine mechanism, loosening of connecting parts, and other problems. Furthermore, the impact vibrations can affect the machining accuracy of workpieces. Therefore, reducing the impact of stamping shocks on equipment is a major challenge. Analyzing the causes and hazards of stamping shocks on large equipment requires simulating the on-site conditions to reproduce the stamping impact process. However, existing stamping vibration simulation technologies have the following problems: deficiencies in the buffer system make it difficult to effectively absorb high-frequency impact energy, allowing residual vibrations to be transmitted to the machine frame; insufficient dynamic response, with the reset mechanism relying on an external hydraulic system, resulting in a large response delay and failing to meet the rapid reset requirements of continuous stamping.

[0003] Therefore, there is an urgent need for a structure for simulating stamping vibration, in order to provide a simulation platform with high simulation efficiency, low energy consumption, and long lifespan. Summary of the Invention

[0004] Therefore, one of the objectives of this invention is to provide a cylinder structure for simulating stamping vibration that overcomes at least one disadvantage of the prior art.

[0005] Therefore, the novel cylinder structure for simulating stamping vibration includes:

[0006] One upper end cap assembly;

[0007] The lower end cap assembly defines a valve sleeve groove and a radial oil inlet hole;

[0008] A cylindrical body connects the upper end cap assembly and the lower end cap assembly, and together they define a piston working chamber;

[0009] A piston assembly, disposed within the piston working chamber and including a piston rod, and a punch adapter fixed to the end of the piston rod, wherein the bottom of the piston rod has a plunger boss; and

[0010] A buffer structure includes a main buffer oil chamber formed by the piston boss at the bottom of the piston rod and the valve sleeve groove of the lower end cover assembly. The main buffer oil chamber is connected to an external hydraulic system through the radial oil inlet hole on the lower end cover assembly.

[0011] In some embodiments, the plunger boss has a limiting step surface, and there is a high-pressure relief channel between the limiting step surface and the lower end cap assembly.

[0012] In some embodiments, an annular pneumatic chamber is provided between the piston rod and the cylindrical cylinder. A floating isolation ring is provided in the annular pneumatic chamber. The radial inner circumference and radial outer circumference of the floating isolation ring are respectively engaged with the outer circumferential guide surface of the piston rod and the inner wall surface of the cylindrical cylinder. The lower end of the floating isolation ring is provided with a downwardly extending isolation cutting edge. In the initial state, the isolation cutting edge closes the high-pressure relief channel.

[0013] In some embodiments, the floating isolation ring, the cylindrical cylinder, and the lower end cap assembly together define a low-pressure oil return chamber, and the lower end cap assembly defines at least one axial oil return hole. The low-pressure oil return chamber is connected to an external oil tank through the axial oil return hole.

[0014] In some embodiments, the outer peripheral guide surface of the piston rod is provided with a radially extending damping flange, the damping flange having a lower limiting surface and an upper limiting surface, and the upper end cap assembly having a lower stop surface; when the oil pressure of the high pressure relief channel acts on the isolation blade, the floating isolation ring moves upward and pushes the lower limiting surface of the damping flange, causing the piston rod to reset until the upper limiting surface of the damping flange abuts against the lower stop surface of the upper end cap assembly.

[0015] In some embodiments, a first sealing assembly and a second sealing assembly are also included, with the first sealing assembly and the second sealing assembly respectively provided on the radially inner and radially outer circumferential sides of the floating isolation ring. The first sealing assembly and the second sealing assembly are respectively provided on the mating surfaces of the floating isolation ring with the piston rod and the cylindrical cylinder.

[0016] In some embodiments, the first sealing assembly includes a mating back support ring and a first sealing ring, the back support ring being used to prevent the first sealing ring from undergoing plastic deformation and to provide rigid support.

[0017] In some embodiments, a sealing and protective assembly is provided between the upper end cap assembly and the piston rod, the sealing and protective assembly including a main sealing ring for forming a dynamic sealing interface.

[0018] In some embodiments, the sealing and protective assembly also includes a dustproof oil seal for isolating external particulate matter.

[0019] In some embodiments, the sealing and protective assembly also includes a wear-resistant ring for providing radial support and motion guidance to the piston rod.

[0020] This novel structure possesses at least the following advantages: It absorbs impact energy by generating a damping effect through the main buffer oil chamber in conjunction with the high-pressure relief channel; simultaneously, the floating isolation ring compresses the gas within the annular pneumatic chamber, converting energy into the reset power of the floating isolation ring, thus closing the high-pressure relief channel; the high-pressure oil pushes the isolation blade to move the floating isolation ring upwards, and the floating isolation ring then drives the piston rod to reset via the damping flange, achieving self-adjustment and reset. This structure also allows for adjustment of the initial pressure of the annular pneumatic chamber and the inlet pressure of the main buffer oil chamber to adapt to the stamping simulation requirements of different tonnages, demonstrating good compatibility. Simple Explanation of the Diagram

[0021] Other features and effects of this invention will be clearly presented in the embodiments with reference to the drawings, wherein: Figure 1 is a schematic diagram of an overall structure of an embodiment of the hydraulic cylinder structure for simulating stamping vibration of the present invention; Figure 2 is an exploded view of the overall structure of this embodiment; Figure 3 is a cross-sectional schematic diagram of this embodiment, illustrating the position of a piston assembly in the stamping state; and Figure 4 is a cross-sectional schematic diagram of this embodiment, illustrating the position of the piston assembly in the reset state. Implementation

[0022] Before this invention is described in detail, it should be noted that similar elements are represented by the same reference numerals in the following description.

[0023] As shown in Figures 1 and 2, the new cylinder structure for simulating stamping vibration includes an upper end cap assembly 1, a lower end cap assembly 2, and a cylindrical cylinder body 3. The upper end cap assembly 1 and the lower end cap assembly 2 are axially fixedly connected by high-strength connecting bolts. The two ends of the cylindrical cylinder body 3 form a sealing fit with the upper end cap assembly 1 and the lower end cap assembly 2, respectively, which together define a piston working chamber 100. A piston assembly 40 that slides axially is provided in the piston working chamber 100.

[0024] The piston assembly 40 includes a piston rod 4 and a punch adapter 5. The piston rod 4 has a flange-type end face formed along its axial end. The punch adapter 5 is fixedly connected to the flange-type end face by high-strength fasteners, and its projected area is similar to the area of ​​the flange-type end face of the piston rod 4. The top working surface of the punch adapter 5 constitutes the impact contact surface of the stamping die to simulate the impact force of the die on the workpiece during actual stamping.

[0025] Furthermore, a sealing and protective assembly 60 is provided on the mating end face between the upper end cap assembly 1 and the piston rod 4. The sealing and protective assembly 60 includes, in sequence, a dustproof oil seal 6, a main sealing ring 7, and a wear-resistant ring 8. The dustproof oil seal 6 is used to effectively prevent external particles from entering the piston working chamber 100; the main sealing ring 7 ensures that a dynamic sealing interface is formed when the piston rod 4 slides axially, so that the cylinder structure can work reliably under high pressure and high frequency impact conditions, and extend the service life of the cylinder structure; the wear-resistant ring 8 provides radial support for the piston rod 4 and plays a role in precision motion guidance, while better maintaining the mating clearance between it and the piston rod 4.

[0026] As shown in Figure 3, the cylinder structure also includes a buffer structure, which includes an annular pneumatic chamber 9 formed between the piston rod 4 and the cylindrical cylinder 3. The annular pneumatic chamber 9 is connected to an external air source through several pneumatic through holes opened on the cylindrical cylinder 3. A floating isolation ring 12 is provided inside the annular pneumatic chamber 9.

[0027] As shown in Figures 2, 3, and 4, the lower end cap assembly 2 defines a valve sleeve groove 21 and a radial oil inlet 22. The piston rod 4 has a plunger boss 41 at its bottom. The buffer structure also includes a main buffer oil chamber 10. The main buffer oil chamber 10 is formed by the engagement of the plunger boss 41 at the bottom of the piston rod 4 and the corresponding valve sleeve groove 21 of the lower end cap assembly 2, and its volume dynamically changes with the stroke of the piston rod 4. The main buffer oil chamber 10 is connected to an external hydraulic system through the radial oil inlet 22 on the lower end cap assembly 2.

[0028] The plunger boss 41 has a limiting step surface 42. A high-pressure relief channel 11 is formed between the lower end cap assembly 2 and the end face opposite to the limiting step surface 42 of the plunger boss 41.

[0029] The lower end of the floating isolation ring 12 is provided with a downwardly extending isolation blade 121. In the initial state, the piston rod 4 is reset, and the isolation blade 121 abuts against the lower end cover assembly 2 under the action of air pressure in the annular air pressure chamber 9 to close the high-pressure relief channel 11. Specifically, the lower end cover assembly 2 is provided with a protruding annular valve seat 23, and the lower end cover assembly 2 defines at least one axial oil return hole 24. When the isolation blade 121 abuts against the annular valve seat 23, the high-pressure relief channel 11 is closed. At this time, the floating isolation ring 12, the lower end cover assembly 2, and the cylindrical cylinder 3 together define a low-pressure oil return chamber 13. The low-pressure oil return chamber 13 is connected to an external oil tank through the axial oil return hole 24. In this embodiment, multiple sets of axial oil return holes 24 are provided, and the multiple sets of axial oil return holes 24 are evenly distributed along the outer periphery of the annular valve seat 23.

[0030] During the impact state, as the piston rod 4 moves downward until the limiting step surface 42 abuts against the annular valve seat 23, high-pressure oil acts on the isolation cutting edge 121. Under the action of the high-pressure oil, the floating isolation ring 12 moves upward to open the high-pressure relief channel 11.

[0031] The floating isolation ring 12 has at least two axially spaced first sealing components 14 on its radial inner circumference side, which together with the outer circumferential guide surface of the piston rod 4 form a main sealing pair; the floating isolation ring 12 has a second sealing component 15 on its radial outer circumference side, which together with the inner wall surface of the cylindrical cylinder 3 form an auxiliary sealing pair; this ensures that the annular air pressure chamber 9 and the low-pressure return oil chamber 13 are isolated from each other, and prevents the medium from flowing between each other and causing performance failure.

[0032] In this embodiment, each of the first sealing components 14 includes a back support ring 141 and a first sealing ring 142 that are configured to cooperate with each other. The back support ring 141 is used to prevent the first sealing ring 142 from undergoing plastic deformation and to provide rigid support for the first sealing ring 142.

[0033] In this embodiment, a damping flange 43 extending radially is provided on the outer peripheral guide surface of the piston rod 4. The damping flange 43 has an upper limiting surface 431 and a lower limiting surface 432. The upper end cap assembly 1 has a lower stop surface 16. The floating isolation ring 12 has an upper bearing surface 122. The upper limiting surface 431 abuts against the lower stop surface 16 of the upper end cap assembly 1 in the initial state; the lower limiting surface 432 abuts against the upper bearing surface 122 of the floating isolation ring 12 during the impact stroke.

[0034] During operation, under the impact of the punch, the piston rod 4 moves downward and compresses the oil in the main buffer oil chamber 10, causing the oil pressure to rise sharply. This generates a damping effect through the high-pressure relief channel 11, absorbing the impact energy and slowing down the downward speed of the piston rod 4 to avoid rigid collisions. The volume of the main buffer oil chamber 10 changes with the stroke of the piston rod 4. Combined with the oil replenishment mechanism of the external hydraulic system, the buffering force can be flexibly adjusted to adapt to different impact vibration simulation requirements.

[0035] Meanwhile, the structure can be adapted to the stamping simulation requirements of different tonnages by adjusting the initial pressure of the annular air pressure chamber 9 and the oil inlet pressure of the main buffer oil chamber 10.

[0036] The sudden increase in oil pressure acts on the isolation edge 121 of the floating isolation ring 12 along the high-pressure relief channel 11, pushing the floating isolation ring 12 upward and simultaneously driving the piston rod 4 upward to reset via the lower limit surface 432 of the damping flange 43. At this time, the volume of the annular air pressure chamber 9 decreases and the air pressure increases, forming a reaction force that pushes the floating isolation ring 12 downward to contact the isolation edge 121 and the annular valve seat 23, forming an air pressure balance reset. The low-pressure oil is then returned to the oil tank through the axial return oil hole 24, completing the buffer cycle. This structure realizes high-frequency, high-load impact action, replicating the vibration frequency and impact force characteristics of the stamping equipment.

[0037] This hydraulic cylinder structure can not only accurately reproduce the impact force, frequency and vibration characteristics of the real stamping process, but also reduce equipment wear through buffering and energy management mechanisms, providing a high-simulation, low-energy-consumption and long-life simulation platform for stamping process research and development, mold performance testing and vibration reliability testing.

[0038] However, the above description is merely an embodiment of this invention and should not be construed as limiting the scope of implementation of this invention. Any simple equivalent changes and modifications made in accordance with the scope of the patent application and the contents of the patent specification shall still fall within the scope of this invention.

[0039] 1: Upper cover assembly 100: Piston working chamber 10: Main buffer oil chamber 11: High-pressure relief channel 12: Floating isolation ring 121: Isolation blade edge 122: Upper bearing surface 13: Low-pressure return oil chamber 14: First sealing assembly 141: Backrest Ring 142: First sealing ring 15: Second sealing assembly 16: Lower stop face 2: Lower end cover assembly 21: Valve sleeve groove 22: Radial oil inlet hole 23: Annular valve seat 24: Axial oil return hole 3:Tubular cylinder 40: Piston assembly 4: Piston rod 41: Plunger Boss 42: Limiting step surface 43: Damping flange 431: Upper Limit Plane 432: Lower Limit Plane 5: Punch adapter seat 60: Sealing and protection components 6: Dustproof oil seal 7: Main sealing ring 8: Wear-resistant ring 9: Annular air pressure chamber

Claims

1. A hydraulic cylinder structure for simulating stamping vibration, comprising: An upper end cap assembly; a lower end cap assembly defining a valve sleeve groove and a radial oil inlet; a cylindrical cylinder connecting the upper end cap assembly and the lower end cap assembly and jointly defining a piston working chamber; a piston assembly disposed within the piston working chamber and including a piston rod and a punch adapter fixed to the end of the piston rod, the piston rod having a plunger boss at its bottom; and a buffer structure including a main buffer oil chamber formed by the engagement of the plunger boss at the bottom of the piston rod and the valve sleeve groove of the lower end cap assembly, the main buffer oil chamber being connected to an external hydraulic system through the radial oil inlet on the lower end cap assembly.

2. The hydraulic cylinder structure for simulating stamping vibration as described in claim 1, wherein, The plunger boss has a limiting step surface, and there is a high pressure relief channel between the limiting step surface and the lower end cap assembly.

3. The hydraulic cylinder structure for simulating stamping vibration as described in claim 2, wherein, An annular pneumatic chamber is provided between the piston rod and the cylindrical cylinder. A floating isolation ring is provided inside the annular pneumatic chamber. The radial inner circumference and radial outer circumference of the floating isolation ring are respectively engaged with the outer circumferential guide surface of the piston rod and the inner wall surface of the cylindrical cylinder. The lower end of the floating isolation ring is provided with a downwardly extending isolation cutting edge. In the initial state, the isolation cutting edge closes the high pressure relief channel.

4. The hydraulic cylinder structure for simulating stamping vibration as described in claim 3, wherein, The floating isolation ring, the cylindrical cylinder and the lower end cover assembly together define a low-pressure oil return chamber. The lower end cover assembly defines at least one axial oil return hole. The low-pressure oil return chamber is connected to an external oil tank through the axial oil return hole.

5. The hydraulic cylinder structure for simulating stamping vibration as described in claim 3, wherein, The piston rod has a radially extending damping flange on its outer peripheral guide surface. The damping flange has a lower limiting surface and an upper limiting surface. The upper end cap assembly has a lower stop surface. When the oil pressure of the high pressure relief channel acts on the isolation blade, the floating isolation ring moves upward and pushes the lower limiting surface of the damping flange, causing the piston rod to reset until the upper limiting surface of the damping flange abuts against the lower stop surface of the upper end cap assembly.

6. The cylinder structure for simulating stamping vibration as described in claim 3 further includes a first sealing assembly and a second sealing assembly, wherein the first sealing assembly and the second sealing assembly are respectively provided on the mating surfaces of the floating isolation ring, the piston rod, and the cylindrical cylinder body.

7. The hydraulic cylinder structure for simulating stamping vibration as described in claim 6, wherein, The first sealing assembly includes a mating back support ring and a first sealing ring, the back support ring being used to prevent the first sealing ring from undergoing plastic deformation and to provide rigid support.

8. The hydraulic cylinder structure for simulating stamping vibration as described in claim 1, wherein, A sealing and protective assembly is provided between the upper end cap assembly and the piston rod, the sealing and protective assembly including a main sealing ring for forming a dynamic sealing interface.

9. The hydraulic cylinder structure for simulating stamping vibration as described in claim 8, wherein, The sealing and protective assembly also includes a dustproof oil seal for isolating external particles.

10. The cylinder structure for simulating stamping vibration as described in claim 8, wherein, The sealing and protective assembly also includes a wear-resistant ring for providing radial support and motion guidance to the piston rod.

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