Oil cylinder adapting to unbalance loading working condition

Abstract

The utility model discloses an oil cylinder adapting to an unbalance loading working condition, and solves the problem that an oil cylinder in the prior art is poor in adaptability and construction performance under a small turning radius working condition. The oil cylinder comprises a cylinder body, a piston and a piston rod, a guide sleeve is arranged at the outer end of the cylinder body, the piston is fixedly arranged on the piston rod, and a first guide seal and a first combined seal which are in contact with the inner wall of the cylinder body are arranged on the outer wall of the piston. A second guide seal and a second combined seal which are in contact with the piston rod are arranged on the inner wall of the guide sleeve. Through the cooperation of the first guide seal and the first combined seal and the cooperation of the second guide seal and the second combined seal, the lateral unbalance loading force generated when the turning radius is small is buffered as much as possible through the guide seals, and the adaptability and the construction performance of the oil cylinder under the working condition of the small turning radius are improved.

Description

Technical Field

[0001] This utility model relates to the field of TBM / shield tunneling machine propulsion technology, and in particular to a hydraulic cylinder. Background Technology

[0002] In the tunnel boring machine (TBM) process, the propulsion cylinder plays a crucial role in propulsion. However, when faced with the requirements of construction with small turning radii, traditional propulsion cylinders, such as... Figure 1 , 2 As shown, the piston used is ( Figure 1 ), guide sleeve ( Figure 2 All existing propulsion cylinders employ two buffer seals in conjunction with copper metal seals, meeting usage requirements in new product applications. However, after long-term use and wear, the clearances between the piston, guide sleeve, cylinder, and piston rod increase. Simply replacing the seals without altering the original structure results in renewed leakage after a short period. Furthermore, with the increased clearances between the piston, guide sleeve, cylinder inner wall, and piston rod, the original seals lose their guiding function. Under heavy loads, the cylinder is prone to uneven loading, leading to uneven wear and scoring between the piston and cylinder inner wall, further exacerbating leakage. Therefore, the above analysis shows that existing propulsion cylinders, due to limitations in their internal structure and control methods, often fail to meet the demands for precise turning and stable propulsion, easily resulting in insufficient thrust, poor turning accuracy, and accelerated equipment wear (cylinder damage), affecting construction efficiency and quality. Utility Model Content

[0003] To address the shortcomings in the aforementioned background technology, this utility model proposes a hydraulic cylinder adapted to off-center load conditions, which solves the problem of poor adaptability and construction performance of existing hydraulic cylinders under small turning radius conditions.

[0004] The technical solution of this utility model is implemented as follows: A hydraulic cylinder adapted to eccentric load conditions includes a cylinder body, a piston, and a piston rod. A guide sleeve is provided at the outer end of the cylinder body. The piston is fixedly mounted on the piston rod. A first guide seal and a first combined seal are provided on the outer wall of the piston, contacting the inner wall of the cylinder body. A second guide seal and a second combined seal are provided on the inner wall of the guide sleeve, contacting the piston rod. The addition of a first guide seal between the piston and the cylinder body, with the first guide seal and the first combined seal working together, increases the sealing area between the piston and the cylinder body, improving the sealing effect. Similarly, the addition of a second guide seal between the guide sleeve and the piston rod, with the second guide seal and the second combined seal working together, increases the sealing area between the piston rod and the guide sleeve, further improving the sealing effect. Through the synergy of the first guide seal and the first combined seal, and the synergy of the second guide seal and the second combined seal, the guide seals can buffer as much of the lateral eccentric load force as possible during small turning radii, improving the adaptability and operational performance of the hydraulic cylinder under small turning radius conditions.

[0005] Further preferably, the piston outer wall is provided with N first guide seals, where N≥2. The N first guide seals are divided into two groups and arranged opposite to each other, with a first combined seal located between the two groups of first guide seals. The first guide seals not only improve the sealing performance between the piston outer wall and the cylinder inner wall, but also work with the first combined seals to buffer the lateral load force during small turning radii.

[0006] In one implementation, the first combined seal is a Step seal or a Gladwell ring.

[0007] In another embodiment, the first combined seal includes a wear-resistant ring and a sealing ring, with the sealing ring located on both sides of the wear-resistant ring.

[0008] Further preferably, the inner wall of the guide sleeve is provided with M second guide seals, where M ≥ 2. The M second guide seals are arranged in the same direction and are all located outside the second combined seal. The second guide seals not only improve the sealing performance between the outer wall of the piston rod and the inner wall of the guide sleeve, but also work with the first combined seal to buffer the lateral load force when the turning radius is small.

[0009] In one implementation, the second combined seal is a Step seal or a Gladwell ring.

[0010] In another embodiment, the second combined seal includes a wear-resistant ring and a sealing ring, with the sealing ring located on both sides of the wear-resistant ring.

[0011] Further preferably, the sealing ring is an O-ring or a Y-ring.

[0012] Further preferably, both the first guide seal and the second guide seal are configured in an S-shape, a triangular sawtooth shape, or a rectangular tooth shape.

[0013] Further preferably, both the front and rear end faces of the piston are rounded to avoid interference with the inner wall of the cylinder when the turning radius is small.

[0014] The beneficial effects of this utility model are as follows: By adding a first guide seal between the piston and the cylinder, and with the first guide seal and the first combined seal working together, the sealing area between the piston and the cylinder is increased, thus improving the sealing effect. Similarly, by adding a second guide seal between the guide sleeve and the piston rod, and with the second guide seal and the second combined seal working together, the sealing area between the piston rod and the guide sleeve is increased, further improving the sealing effect. Through the synergy of the first guide seal and the first combined seal, and the synergy of the second guide seal and the second combined seal, this utility model allows the guide seals to buffer as much lateral load as possible during small turning radii, improving the adaptability and operational performance of the hydraulic cylinder under small turning radius conditions.

[0015] This utility model employs a multi-layered special design for the first and second guide seals, increasing the sealing area while using sealing materials with strong resistance to high pressure and dynamic loads to further enhance sealing performance. Furthermore, it allows the propulsion cylinder to effectively buffer lateral load forces in the axial and circumferential directions under small turning radius conditions through the first and second guide seals. This significantly improves the overall lifespan of the cylinder, alleviates the impact of high-pressure hydraulic fluid, achieves a highly reliable sealing effect, and ensures smooth tunneling and construction quality. Attached Figure Description

[0016] To more clearly illustrate the embodiments of this utility model, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of a traditional hydraulic cylinder piston structure.

[0018] Figure 2 A schematic diagram of the guide sleeve structure of a traditional propulsion cylinder;

[0019] Figure 3 This is a schematic diagram of the structure of this utility model;

[0020] Figure 4 This is a schematic diagram of the piston structure of this utility model;

[0021] Figure 5 This is a schematic diagram of the guide sleeve structure of this utility model;

[0022] Figure 6 A schematic diagram showing the S-shaped configuration of the first or second guide seal;

[0023] Figure 7 A schematic diagram showing the triangular sawtooth shape of either the first or second guide seal;

[0024] Figure 8 A schematic diagram showing the rectangular toothed configuration of the first or second guide seal. Detailed Implementation

[0025] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0026] Example 1, such as Figure 3 As shown, a hydraulic cylinder adapted to off-center load conditions includes a cylinder body 1, a piston 2, and a piston rod 3. A guide sleeve 4 is provided at the outer end of the cylinder body 1, and the guide sleeve 4 is connected to the open end of the cylinder body by bolts, forming a sealed connection between the guide sleeve and the cylinder body. The piston is located inside the cylinder body, and the piston 2 is fixedly mounted on the piston rod 3. The piston is fixed to the front part of the piston rod, and the rear part of the piston rod extends through the guide sleeve 4, similar to existing technology. The outer wall of the piston 2 is provided with a first guide seal 5 and a first combined seal 6 that contact the inner wall of the cylinder body 1. The inner wall of the guide sleeve 4 is provided with a second guide seal 7 and a second combined seal 8 that contact the piston rod 3. The addition of the first guide seal between the piston and the cylinder body, and the synergistic sealing of the first guide seal and the first combined seal, increases the sealing area between the piston and the cylinder body, improving the sealing effect. Similarly, the addition of the second guide seal between the guide sleeve and the piston rod, and the synergistic sealing of the second guide seal and the second combined seal, further increases the sealing area between the piston rod and the guide sleeve, improving the sealing effect. Through the synergy of the first guide seal and the first combined seal, as well as the synergy of the second guide seal and the second combined seal, the guide seals can buffer the lateral load force as much as possible when the turning radius is small, thereby improving the adaptability and construction performance of the hydraulic cylinder under small turning radius conditions.

[0027] Example 2: A hydraulic cylinder adapted to off-center load conditions includes a cylinder body 1, a piston 2, and a piston rod 3. A guide sleeve 4 is provided at the outer end of the cylinder body 1, and the guide sleeve 4 is connected to the open end of the cylinder body by bolts, forming a sealed connection between the guide sleeve and the cylinder body. The piston is located inside the cylinder body, and the piston 2 is fixedly mounted on the piston rod 3. The piston is fixed to the front part of the piston rod, and the rear part of the piston rod extends through the guide sleeve 4, similar to existing technology. The outer wall of the piston 2 is provided with a first guide seal 5 and a first combined seal 6 that contact the inner wall of the cylinder body 1. The inner wall of the guide sleeve 4 is provided with a second guide seal 7 and a second combined seal 8 that contact the piston rod 3. The addition of the first guide seal between the piston and the cylinder body, and the synergistic sealing of the first guide seal and the first combined seal, increases the sealing area between the piston and the cylinder body, improving the sealing effect. The addition of the second guide seal between the guide sleeve and the piston rod, and the synergistic sealing of the second guide seal and the second combined seal, further increases the sealing area between the piston rod and the guide sleeve, improving the sealing effect.

[0028] like Figure 4As shown, in this embodiment, the piston 2 has N first guide seals 5 on its outer wall, where N ≥ 2. The N first guide seals 5 are arranged in two groups and opposite to each other, with the first combined seal 6 located between the two groups of first guide seals 5. Taking N=4 as an example, the four first guide seals are arranged in pairs, with the two first guide seals in the same group facing the same direction. The two groups of first guide seals face opposite to each other, meaning they are symmetrically arranged on both sides of the first combined seal 6, reducing the pressure on the first combined seal 6. Simultaneously, the first guide seals, in conjunction with the first combined seal, increase the contact area between the piston seal and the cylinder inner wall, thereby maximizing the buffering of lateral load forces during small turning radii. Preferably, in this embodiment, the first combined seal 6 is a Step seal or a Glyd ring. One or two first combined seals can be provided as needed; this embodiment uses one as an example. The first guide seal is made of a sealing material with strong resistance to high pressure and dynamic loads, such as a polyurethane sealing ring, which can effectively solve the problem of re-leakage failure of the propulsion cylinder.

[0029] Example 3: A hydraulic cylinder adapted to off-center load conditions includes a cylinder body 1, a piston 2, and a piston rod 3. A guide sleeve 4 is provided at the outer end of the cylinder body 1, and the guide sleeve 4 is connected to the open end of the cylinder body by bolts, forming a sealed connection between the guide sleeve and the cylinder body. The piston is located inside the cylinder body, and the piston 2 is fixedly mounted on the piston rod 3. The piston is fixed to the front part of the piston rod, and the rear part of the piston rod extends through the guide sleeve 4, similar to existing technologies. The outer wall of the piston 2 is provided with a first guide seal 5 and a first combined seal 6 that contact the inner wall of the cylinder body 1. The inner wall of the guide sleeve 4 is provided with a second guide seal 7 and a second combined seal 8 that contact the piston rod 3. The addition of the first guide seal between the piston and the cylinder body, and the synergistic sealing of the first guide seal and the first combined seal, increases the sealing area between the piston and the cylinder body, improving the sealing effect. Similarly, the addition of the second guide seal between the guide sleeve and the piston rod, and the synergistic sealing of the second guide seal and the second combined seal, further increases the sealing area between the piston rod and the guide sleeve, improving the sealing effect. The first guide seal is made of a sealing material with strong resistance to high pressure and dynamic load, such as a polyurethane sealing ring, which can effectively solve the problem of leakage failure of the propulsion cylinder.

[0030] like Figure 5As shown, in this embodiment, the piston 2 has N first guide seals 5 on its outer wall, where N ≥ 2. The N first guide seals 5 are divided into two groups and arranged opposite each other, with the first combined seal 6 located between the two groups of first guide seals 5. In this embodiment, taking N=4 as an example, the four first guide seals are divided into two groups of two, with the two first guide seals in the same group facing the same direction. The two groups of first guide seals face opposite each other, that is, the two groups of first guide seals are symmetrically arranged on both sides of the first combined seal 6, reducing the pressure of the first combined seal 6. At the same time, the first guide seals cooperate with the first combined seal to increase the contact area between the piston seal and the inner wall of the cylinder, thereby allowing the guide seal to buffer the lateral load force during small turning radii as much as possible. In this embodiment, preferably, the first combined seal 6 includes a wear-resistant ring and a sealing ring, with the sealing ring located on both sides of the wear-resistant ring; that is, the combination of the sealing ring and the wear-resistant ring can also play a sealing and supporting role; together with the first guide seal, it can also effectively buffer the lateral load force during small turning radii. In this embodiment, the sealing ring is an O-ring or a Y-ring, preferably an O-ring. In moving parts, the O-ring maintains contact with the moving surface through elastic deformation and friction, thereby preventing leakage.

[0031] Example 4: A hydraulic cylinder adapted to off-center load conditions, further optimized based on Examples 1, 2, or 3. In this example, the inner wall of the guide sleeve 4 is provided with M second guide seals 7, where M ≥ 2. The M second guide seals 7 are arranged in the same direction and are all located outside the second combined seal 8. In this example, M=5 is used as an example, and they are arranged towards the second combined seal 8; this increases the contact area between the piston rod and the inner wall of the guide sleeve, thereby allowing the guide seal to buffer as much of the lateral off-center load force as possible during small turning radii. In this example, the second combined seal 8 is preferably a Step seal or a Glyd ring. One or two second combined seals can be provided as needed; one is used as an example in this example. The second guide seal is made of a sealing material with strong resistance to high pressure and dynamic load, such as a polyurethane sealing ring, which can effectively solve the problem of re-leakage failure of the propulsion cylinder.

[0032] Example 5: A hydraulic cylinder adapted to off-center load conditions, further optimized based on Examples 1, 2, or 3. In this example, the inner wall of the guide sleeve 4 is provided with M second guide seals 7, where M ≥ 2. The M second guide seals 7 are arranged in the same direction and are all located outside the second combined seal 8. In this example, M=5 is used as an example, and they are arranged towards the second combined seal 8; this increases the contact area between the piston rod and the inner wall of the guide sleeve, thereby allowing the guide seals to buffer as much of the lateral off-center load force as possible during small turning radii. Preferably, one or two second combined seals can be provided in this example; one is used as an example in this example. The second combined seal 8 includes a wear-resistant ring and a sealing ring. The sealing ring is located on both sides of the wear-resistant ring, i.e., a combination of the sealing ring and the wear-resistant ring ring, which can also play a sealing and supporting role; together with the second guide seal, it can also effectively buffer the lateral off-center load force during small turning radii. In this example, the sealing ring is an O-ring or a Y-ring, preferably an O-ring. In moving parts, the O-ring maintains contact with the moving surface through elastic deformation and friction, thereby preventing leakage. The second guide seal is made of a sealing material with strong resistance to high pressure and dynamic load, such as a nitrile rubber sealing ring, which can also effectively solve the problem of leakage failure of the propulsion cylinder.

[0033] Example 6: A hydraulic cylinder adapted to off-center loading conditions, further optimized based on any one of Examples 1-5, such as... Figure 6 , 7 As shown in Figures 8 and 9, in this embodiment, both the first guide seal 5 and the second guide seal 7 are S-shaped, triangular sawtooth, or rectangular toothed; under small turning radius conditions, the first and second guide seals effectively buffer lateral load forces in the axial and circumferential directions. The piston 2 has rounded corners on both its front and rear ends to avoid interference with the cylinder wall when the turning radius is small.

[0034] In the description of this utility model, it should be understood that the terms "vertical", "horizontal", "up", "down", "front", "back", "left", "right", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0035] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0036] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A hydraulic cylinder adapted to off-center load conditions, comprising a cylinder body (1), a piston (2) and a piston rod (3), wherein a guide sleeve (4) is provided at the outer end of the cylinder body (1), and the piston (2) is fixedly mounted on the piston rod (3), characterized in that: The piston (2) has a first guide seal (5) and a first combined seal (6) on its outer wall that are in contact with the inner wall of the cylinder (1), and the guide sleeve (4) has a second guide seal (7) and a second combined seal (8) on its inner wall that are in contact with the piston rod (3).

2. The load biasing condition adaptive ram of claim 1, wherein: The piston (2) has N first guide seals (5) on its outer wall, where N ≥ 2. The N first guide seals (5) are arranged in two groups and are opposite to each other. The first combined seal (6) is located between the two groups of first guide seals (5).

3. The load biasing condition adaptive ram of claim 1, wherein: The first combined seal (6) is a Step seal or a Gladwell ring.

4. The load biasing condition adaptive ram of claim 1, wherein: The first combined seal (6) includes a wear-resistant ring and a sealing ring, with the sealing ring located on both sides of the wear-resistant ring.

5. The cylinder adapted to the partial load working condition according to any one of claims 1-4, characterized in that: The inner wall of the guide sleeve (4) is provided with M second guide seals (7), M≥2, the M second guide seals (7) are arranged in the same direction and are all located outside the second combined seal (8).

6. The load biasing condition adaptive ram of claim 5, wherein: The second combination seal (8) is a Step seal or a Gladwell ring.

7. The load biasing condition adaptive ram of claim 5, wherein: The second combined seal (8) includes a wear-resistant ring and a sealing ring, with the sealing ring located on both sides of the wear-resistant ring.

8. The load biasing condition adaptive oil cylinder of claim 4 or 7, wherein: The sealing ring is an O-ring or a Y-ring.

9. The load biasing condition adaptive ram of claim 1, wherein: The first guide seal (5) and the second guide seal (7) are both S-shaped, triangular sawtooth, or rectangular toothed.

10. The load biasing condition adaptive ram of claim 1 or 9, wherein: The piston (2) has rounded corners on both the front and rear ends.

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