A gas-liquid damper with high load stability

Abstract

The utility model discloses a kind of pneumatic-hydraulic buffers with high load stability, including outer cylinder and inner cylinder, the outer cylinder one end is open end, inside is equipped with the guide rod of extension setting along its axial direction, guide rod is fixed with the flow guide platform near the open end of outer cylinder, inner cylinder one end is inserted into outer cylinder from the open end of outer cylinder, other end is located at the outside of outer cylinder, inner cylinder is also equipped with the insulation piston of moving along its axial direction, the insertion end of the inner cylinder is fixed with guide seat. The utility model designs the inclination angle of the inner wall of conical hole is greater than the angle of flow guide platform head, and the axial length H1 of conical hole is more than 2 times of the axial length H3 of guide platform, so it can be fully achieved to use hydraulic oil to push insulation piston to move steadily, simultaneously, it plays a sufficient drainage effect to annular hydraulic oil, and the annular area when hydraulic oil is discharged from conical hole is larger, can more evenly push the movement of insulation piston, avoid losing balance to cause insulation piston misplacement.

Description

Technical Field

[0001] This utility model relates to the field of buffer device technology, specifically a gas-liquid buffer with high load stability. Background Technology

[0002] With the continuous advancement of industrial technology, mechanical equipment is developing towards greater carrying capacity and higher operating speeds, placing new demands on the energy absorption and maximum impact force that buffers can withstand. Therefore, buffer devices for ensuring the safety of large mechanical equipment are facing a new challenge: how to safely and smoothly bring colliding machinery to a stop.

[0003] Current hydraulic shock absorbers dissipate impact energy by compressing and reciprocating hydraulic oil between different shock absorber chambers. However, due to limitations in materials and structure, hydraulic shock absorbers are prone to internal piston misalignment under conditions of extremely high energy absorption and ultra-high pressure impacts. Furthermore, because they rely on hydraulic oil to reciprocate between different chambers to dissipate impact energy, they frequently experience issues such as failure to reset, oil leaks, and air leaks. This necessitates regular inspections, maintenance, and frequent manual repairs, increasing maintenance costs.

[0004] This case arose in order to resolve the aforementioned issues. Summary of the Invention

[0005] Technical problems to be solved To address the shortcomings of existing technologies, this invention provides a gas-liquid buffer with high load stability, thus solving the problems mentioned in the background section.

[0006] Technical solution To achieve the above objectives, this utility model provides the following technical solution: a gas-liquid damper with high load stability, comprising an outer cylinder and an inner cylinder. One end of the outer cylinder is open, and a guide rod extending axially is provided inside. A flow guide platform is fixed near the open end of the outer cylinder. One end of the inner cylinder is inserted into the outer cylinder from the open end, and the other end is located outside the outer cylinder. An isolation piston that moves axially is also provided inside the inner cylinder. A guide seat is fixed at the insertion end of the inner cylinder. A guide hole is axially opened in the middle of the guide seat. The guide hole includes a circular hole section and a conical hole connected to the circular hole section. The guide rod has a conical structure, forming a circumferential damping slit with the circular hole section. The outer diameter of the flow guide platform at the end connected to the guide rod is larger than the diameter of the circular hole section, and the inclination angle of the inner wall of the conical hole is larger than the angle of the head of the flow guide platform.

[0007] Preferably, the horizontal length H2 of the circular hole segment is greater than 10 mm.

[0008] Preferably, the axial length H1 of the conical hole is more than twice the axial length H3 of the guide table.

[0009] Preferably, the maximum opening angle of the conical hole is less than the circumferential extension line of its inner wall coinciding with the outer edge of the isolation piston, and the minimum opening angle of the conical hole is greater than the circumferential sidewall of the guide platform. The angle difference between the two is β. The above angle is in the non-loaded state of the gas-liquid buffer.

[0010] Preferably, the circular hole section is larger than the maximum radial dimension of the guide rod. Beneficial effects

[0011] By adopting the above technical solution, this utility model has the following advantages compared with the prior art: This invention relates to a gas-liquid damper with high load stability. The guide hole includes a circular section and a conical hole connected to the circular section. The guide rod has a conical structure, forming a damping slit with the circular section. Hydraulic oil passes through the damping slit to achieve a damping and buffering effect. Furthermore, the horizontal length H2 of the circular section must be greater than 10mm to ensure the stability of the guide rod's movement and prevent the guide rod from easily deviating and causing line contact when the damper is subjected to a violent impact, which could cut or scratch the spindle and affect the valve body strength.

[0012] This invention relates to a gas-liquid damper with high load stability. The inclination angle of the inner wall of the conical bore is greater than the angle of the guide platform head, allowing hydraulic oil to be ejected more smoothly from the annular gap between the two parts during the damping process. Furthermore, the axial length H1 of the conical bore is more than twice the axial length H3 of the guide platform. This ensures that the hydraulic oil can smoothly drive the isolating piston, while also effectively guiding the annular hydraulic oil flow. Additionally, the larger annular area of ​​the hydraulic oil exiting the conical bore allows for more even movement of the isolating piston, preventing imbalance and misalignment. Attached Figure Description

[0013] Figure 1 This is a schematic diagram of the non-loaded structure of this utility model; Figure 2 This is a schematic diagram of the load state structure of this utility model; Figure 3 This is a schematic diagram of the guide hole design in this utility model; Figure 4 This is a schematic diagram of the design of the conical hole in this utility model.

[0014] In the diagram: 1. Outer cylinder; 2. Inner cylinder; 3. Guide rod; 4. Flow guide platform; 5. Guide seat; 6. Isolation piston; 7. Oil chamber; 8. Dynamic oil chamber; 9. Nitrogen chamber; 10. One-way valve; 11. Guide hole; 111. Conical hole; 112. Circular hole section; 12. Sealing plate. Detailed Implementation

[0015] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0016] like Figure 1-2 As shown: A gas-liquid damper with high load stability includes an outer cylinder 1 and an inner cylinder 2. One end of the outer cylinder 1 is open, and a guide rod 3 extending axially is provided inside. A flow guide platform 4 is fixed to the guide rod 3 near the open end of the outer cylinder 1. One end of the inner cylinder 2 is inserted into the outer cylinder 1 from the open end, and the other end is located outside the outer cylinder 1. A guide seat 5 is fixed to the inserted end of the inner cylinder 2. The inner cylinder 2 is sleeved on the flow guide platform 4 and the guide rod 3 through the guide seat 5, and the inner cylinder 2 can move along the guide rod 3. An isolation piston 6 that moves axially is also provided inside the inner cylinder 2. The inner wall of the inner cylinder 2 and the isolation piston 6 form a nitrogen chamber 9 for holding nitrogen gas, and the inner wall of the outer cylinder 1 and the guide seat 5 form an oil chamber 7 for holding hydraulic oil. As the inner cylinder 2 moves along the guide rod 3, the gap between the inner wall of the inner cylinder 2, the guide seat 5, and the isolation piston 6 forms a dynamic oil chamber 8.

[0017] The guide seat 5 is provided with a guide hole 11. The inner diameter of the guide hole 11 is larger than the outer diameter of the guide rod 3 and smaller than the outer diameter of the flow guide platform 4, forming an annular gap between the guide rod 3 and the guide hole 11.

[0018] Specific applications are as follows: When the gas-liquid buffer is subjected to an impact force, the inner cylinder 2 moves relative to the outer cylinder 1 along the guide rod 3, and the guide seat 5 squeezes the oil chamber 7 along the guide rod 3. Since the inner diameter of the guide hole 11 is larger than the outer diameter of the guide rod 3, the hydraulic oil flows to the inner cylinder 2 through the guide hole 11 and forms a dynamic oil chamber 8 between the isolation piston 6 and the guide seat 5, which in turn pushes the isolation piston 6 to squeeze the nitrogen chamber 9, and the nitrogen is compressed and consumes the impact energy.

[0019] During unloading, the high pressure in the nitrogen chamber 9 pushes the isolating piston 6 towards the dynamic oil chamber 8, causing the hydraulic oil in the dynamic oil chamber 8 to return to the oil chamber 7. The volume of the oil chamber 7 continuously increases, eventually pushing the entire inner cylinder 2 to reset. Once the inner cylinder 2 has reset, the gas-liquid buffer also returns to its initial state. Therefore, the gas-liquid buffer of the present invention can form three chambers when subjected to high-speed impact: the nitrogen chamber 9, the oil chamber 7, and the dynamic oil chamber 8. The dynamic oil chamber 8 only appears during loading and unloading.

[0020] The gas-liquid buffer of this invention forms three chambers that compress and absorb energy smoothly upon impact, offering advantages such as high energy absorption, long service life, and simple structure. Especially in the face of sudden high-speed impacts, it can smoothly bring the impacting object to a stop and dissipate the impact energy. In the future, with the continuous increase in speed and load capacity of high-speed and heavy machinery, the performance advantages of the gas-liquid buffer of this invention will become even more pronounced. Furthermore, the reset process of the gas-liquid buffer is achieved by using nitrogen to push the isolation piston 6 to compress the dynamic oil chamber 8, restoring the inner cylinder 2 to its initial state, greatly extending the buffer's service life and making it fully capable of undertaking buffering tasks with extremely large strokes and ultra-high energy absorption.

[0021] The above design achieves the following effects: When the gas-liquid buffer is impacted, the guide rod 3 guides the inner cylinder 2 to retract radially, preventing misalignment. It also ensures accurate reset of the buffer during unloading, avoiding misalignment, damage, and difficulty in automatic reset. Furthermore, when the buffer is impacted, a gap appears between the guide rod 3 and the guide hole 11. Hydraulic oil enters the inner cylinder 2 through this gap, pushing the isolating piston 6 towards the nitrogen chamber 9, forming a dynamic oil chamber 8 between the isolating piston 6 and the guide seat 5. The special liquid impact flow formed by the hydraulic oil entering the inner cylinder 2 around the side of the guide rod 3 generates a uniform impact force on the isolating piston 6, preventing it from losing balance and misaligning under excessive impact.

[0022] As a specific embodiment of the gas-liquid buffer provided by the present invention, please refer to Figure 3 The guide platform 4 has a truncated cone structure. The small-diameter end of the truncated cone structure is connected to the guide rod 3. The guide hole 11 includes a circular hole section 112 and a conical hole 111 connected to the circular hole section 112. The small-diameter end of the conical hole 111 is connected to the circular hole section 112, and the inner diameter of this end is always greater than the outer diameter of the guide rod and less than the outer diameter of the large-diameter end of the guide platform 4 during the movement. The inner diameter of the large-diameter end of the conical hole 111 is greater than the outer diameter of the large-diameter end of the guide platform 4. The shape design of the guide platform 4 and the guide hole 11 allows the hydraulic oil to flow out along the inner side of the guide hole 11 during the initial load of the gas-liquid buffer, forming an annular liquid impact flow. This allows the hydraulic oil to form a uniform annular impact force on the isolating piston 6, further ensuring that the isolating piston 6 will not lose balance and become misaligned when subjected to a huge impact force.

[0023] Secondly, the guide rod 3 has a conical structure, which forms a damping slit with the circular hole section 112. Hydraulic oil passes through the damping slit to achieve the damping and buffering effect. The guide rod 3 has a taper, and the guide rod 3 cooperates with the guide seat 5. During the buffering process, the annular gap (the area through which hydraulic oil passes) becomes smaller and smaller, thus achieving the buffering effect.

[0024] Specifically, when the buffer is impacted, the guide rod 3 guides the inner cylinder 2 to contract axially, gradually reducing the gap between the guide rod 3 and the circular hole section 112. This means the exchanged fluid flow rate decreases, resulting in a gradually increasing buffer damping (i.e., the greater the downward pressure, the greater the resistance experienced by the hydraulic actuator). It should be noted that the circular hole section 112 not only allows for the formation of annular hydraulic oil around the guide rod 3 but also guides the inner cylinder 2 to contract stably axially.

[0025] See appendix Figure 3-4 As shown, the horizontal length H2 of the circular hole section 112 needs to be greater than 10mm to ensure the stability of the guide rod 3's movement. If the circular hole section 112 is missing or its size is too short / thin, it will be difficult to form a uniform annular hydraulic oil around the guide rod 3. At the same time, when the buffer is subjected to a violent impact, the guide rod 3 is prone to slight deviation and contact with the inner wall of the guide seat 5 (during the impact, the inner cylinder 2 does not run smoothly relative to the guide rod 3; if the circular hole section 112 is not provided or its length is too small, line contact will occur, i.e., the guide rod 3 and the valve body will be damaged by impact), resulting in cutting and scratching of the spindle, affecting the strength of the valve body.

[0026] A further design feature is that the inclination angle of the inner wall of the conical bore 111 is greater than the angle of the head of the guide platform 4 (if the inclination angle of the inner wall of the conical bore 111 were equal to the angle of the head of the guide platform 4, it would be prone to large-area collision and wear during the reset process). This allows the hydraulic oil to be sprayed more smoothly from the annular gap between the two parts during the buffering process. Secondly, the axial length H1 of the conical bore 111 is more than twice the axial length H3 of the guide platform, which ensures that the hydraulic oil can be used to push the isolating piston 6 to move smoothly, while also providing sufficient drainage for the annular hydraulic oil. Finally, the extension of the axial length H1 of the conical bore 111 allows for a larger annular area when the hydraulic oil exits the conical bore 111, enabling a more uniform movement of the isolating piston 6.

[0027] The inclination angle of the inner wall of the conical hole 111 needs to be further limited, as shown in the attached figure. Figure 4 As shown, the maximum opening angle of the conical hole 111 is less than the circumferential extension line of its inner wall coinciding with the outer edge of the isolation piston 6 (that is, the angle extension line of the conical hole 111 reaches the outermost end of the inner side of the movable piston, avoiding the hydraulic oil directly impacting the cylinder, resulting in the liquid not fully impacting the movable piston and failing to achieve the desired initial annular impact flow effect). The minimum opening angle is greater than the parallel to the circumferential side wall of the guide platform 4 (that is, it should be greater than the tilt angle of the guide platform 4 to better obtain the annular impact flow of the hydraulic oil, and also to avoid being too close to the head of the guide rod 3 without any gap). The angle difference between the two is β.

[0028] Of course, the smaller the angle difference β between the two, the larger the annular area of ​​the hydraulic oil when it is discharged from the conical hole 111 to the surface of the isolating piston 6, the smoother the movement of the isolating piston 6, and the avoidance of the isolating piston 6 losing balance and becoming misaligned when subjected to huge impact force.

[0029] The above-described embodiments are provided for illustrative purposes. Based on the above description, those skilled in the art can make various changes and modifications without departing from the inventive concept. The technical scope of this utility model is not limited to the contents of the specification; its protection scope must be determined according to the claims.

Claims

1. A gas-liquid damper with high load stability, comprising an outer cylinder and an inner cylinder, wherein one end of the outer cylinder is open, and a guide rod extending axially therein is provided, with a flow guide platform fixed near the open end of the outer cylinder; one end of the inner cylinder is inserted into the outer cylinder from the open end of the outer cylinder, and the other end is located outside the outer cylinder; an isolation piston that moves axially within the inner cylinder is also provided, and a guide seat is fixed at the insertion end of the inner cylinder, characterized in that: The guide seat has a guide hole axially opened in the middle. The guide hole includes a circular hole section and a conical hole connected to the circular hole section. The guide rod has a conical structure and forms a circumferential damping slit with the circular hole section. The outer diameter of the guide platform at the end connected to the guide rod is larger than the diameter of the circular hole section. The inclination angle of the inner wall of the conical hole is larger than the angle of the head of the guide platform.

2. The gas-liquid buffer with high load stability according to claim 1, characterized in that: The horizontal length H2 of the circular hole segment is greater than 10 mm.

3. A gas-liquid buffer with high load stability according to claim 1, characterized in that: The conical hole is extended such that its axial length H1 is more than twice the axial length H3 of the guide table.

4. A gas-liquid buffer with high load stability according to claim 1, characterized in that: The maximum opening angle of the conical hole is less than the circumferential extension line of its inner wall coinciding with the outer edge of the isolation piston, and the minimum opening angle of the conical hole is greater than the circumferential side wall of the guide platform. The angle difference between the two is β. The above angles are in the non-loaded state of the gas-liquid buffer.

5. A gas-liquid buffer with high load stability according to claim 1, characterized in that: The circular hole section is larger than the maximum radial dimension of the guide rod.

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