A double-tube counter-directional compact hydraulic push rod

Abstract

The utility model belongs to the technical field of hydraulic push rod, concretely relates to a double -pipe hetero -directional formula compact type hydraulic push rod, including double -cavity board and two center push rod subassembly, the double -cavity board is opened in two side -by -side hetero -directional round cavity, the both sides of double -cavity board are opened in two symmetrical misaligned misaligned recess, two center push rod subassembly symmetry sets up in two hetero -directional round cavity, and respectively with two misaligned recess corresponding. The utility model discloses through the cooperation of two hetero -directional round cavity that is opened in double -cavity casing and two groups of center push rod subassembly, can make the piston rod that this push rod two -way stretch out in side -by -side state, to reduce the piston rod axial's storage space, not only convenient to carry, still can adapt to the limited space operation demand of rescue, realizes the operation of in -depth push and top, effectively improves the rescue efficiency and the operation flexibility.

Description

Technical Field

[0001] This utility model belongs to the field of hydraulic push rod technology, specifically relating to a dual-tube anisotropic compact hydraulic push rod. Background Technology

[0002] Existing hydraulic push rods generally employ a straight-through hydraulic oil chamber structure in their bidirectional pushing designs, such as the bidirectional hydraulic push rod with Chinese patent application number 202221859907.X and the bidirectional hydraulic jacking rod with application number 201721615803.3. This structure results in an excessively large axial dimension of the piston rod, posing significant drawbacks in special application scenarios such as emergency rescue: on the one hand, it increases the space occupied when carrying equipment, hindering rapid transportation and deployment; on the other hand, when operation is required in confined spaces or locations with short internal gaps, the excessively long push rod makes it difficult to reach the working area, severely impacting the pushing effect and efficiency. Especially in confined space rescue and equipment maintenance, traditional hydraulic push rods often fail to meet actual working conditions due to structural size limitations, reducing rescue efficiency and operational flexibility. Therefore, this utility model proposes a dual-tube anisotropic compact hydraulic push rod to solve the above problems. Utility Model Content

[0003] The purpose of this invention is to provide a compact, dual-tube, anisotropic hydraulic push rod that can solve the aforementioned technical problems.

[0004] The specific technical solution adopted by this utility model is as follows:

[0005] This utility model provides a dual-tube anisotropic compact hydraulic push rod, including a dual-cavity plate and two central push rod assemblies. The dual-cavity plate has two parallel anisotropic circular cavities, and two symmetrically staggered recesses are provided on both sides of the dual-cavity plate. The two central push rod assemblies are symmetrically arranged in the two anisotropic circular cavities and correspond to the two staggered recesses respectively.

[0006] The surface of the dual-cavity plate has two grooves, and each groove contains a symmetrically staggered push input pipe and a return input pipe. The opposite sides of the two push input pipes and the two return input pipes are equipped with connectors. The opposite sides of the two return input pipes are respectively connected to the through holes on both sides of the surface of the dual-cavity plate that correspond to the two opposite circular cavities.

[0007] Preferably, the central push rod assembly includes a piston rod and an oil seal assembly. The piston rod is sleeved in the opposite circular cavity. An oil seal connected to one side of the piston rod is provided on the side of the opposite circular cavity near the misaligned recess. Top support plates are provided on both sides of the double cavity plate. The top support plates are fixedly installed on the other side of the piston rod. The two top support plates correspond to the two misaligned recesses respectively.

[0008] Preferably, the oil seal assembly is configured as two sets, with the two sets of oil seal assemblies respectively disposed on opposite sides of the double-chamber plate and located on both sides of the opposite circular cavity. One set is disposed on the piston rod. The oil seal assembly includes an inner tube, an oil pipe spacer sealing ring and a front sealing ring, with one side of the inner tube inserted into the opposite circular cavity.

[0009] Preferably, the opposite-directional circular cavity is provided with an oil pipe spacer sealing ring and a front sealing ring. The oil pipe spacer sealing ring is sleeved on the outer circumference of the inner tube and is in extrusive contact with the inner wall of the opposite-directional circular cavity. The front sealing ring is sleeved on the inner tube and located on one side of the opposite-directional circular cavity, and is in extrusive contact with the inner wall of the opposite-directional circular cavity. The side of the front sealing ring is attached to the anti-reverse ring, and the anti-reverse ring is integrally set on the outer circumference of the inner tube. The outer diameter of the anti-reverse ring is smaller than the radius of the opposite-directional circular cavity.

[0010] Preferably, a fastening ring and a fastening sealing ring are provided on the opposite-direction circular cavity side corresponding to the misaligned notch. The fastening ring is pressed against the side of the misaligned notch or the side of the double cavity plate by a reinforcing bolt. This design can create a squeezing sealing effect between the embedded tube and the side of the misaligned notch, thereby creating a secondary sealing effect on the embedded tube. A sliding seal is slidably installed on the piston rod, and the sliding seal is located in the embedded tube corresponding to the side of the double cavity plate.

[0011] Preferably, the other side of the inner tube corresponding to the misaligned notch is set to a blocked state, and an injection head is installed on the other side of the inner tube, the injection head being connected to one side of the push input tube.

[0012] Preferably, the outer periphery of the dual-cavity plate is provided with two gripping rings, and the two sides of the gripping rings are respectively fixed on two fastening plates, which are fixed on the sides of the dual-cavity plate. Beneficial effects

[0013] 1. This utility model, through the cooperation of two oppositely oriented circular cavities opened in the double-cavity shell and two sets of central push rod assemblies, allows the piston rods extending in both directions on both sides of the push rod to be in a parallel state, thereby reducing the axial storage space of the piston rods. This not only makes it easy to carry, but also adapts to the needs of limited space operations during rescue, enabling deep pushing operations and effectively improving rescue efficiency and operational flexibility.

[0014] 2. The oil seal assembly of this utility model can be installed in the opposite circular cavity in conjunction with the double cavity shell, which improves the ease of assembly; on the other hand, it can simultaneously seal the oil injection end and the sliding side of the piston rod, which significantly improves the oil sealing effect and the reliability of use. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the main structure of this utility model;

[0016] Figure 2 This is a schematic diagram of the cross-sectional structure of this utility model from a bottom view angle;

[0017] Figure 3 This is a schematic diagram of the central push rod assembly structure of this utility model.

[0018] The attached diagram lists the components represented by each number as follows:

[0019] 1. Double-chamber plate; 11. Misaligned notch; 12. Opposite-direction circular cavity; 2. Central push rod assembly; 21. Piston rod; 22. Oil seal; 23. Top support plate; 24. Embedded tube; 24a. Fastening ring; 24b. Anti-reverse ring; 25. Sliding seal; 26. Front sealing ring; 27. Oil pipe spacer sealing ring; 28. Fastening sealing ring; 29. ​​Injection head; 3. Push input pipe; 4. Return input pipe; 5. Connector; 6. Fastening disc; 7. Holding ring. Detailed Implementation

[0020] To make the objectives and advantages of this utility model clearer, the following detailed description is provided in conjunction with embodiments. It should be understood that the following text is merely used to describe one or more specific embodiments of this utility model and does not strictly limit the scope of protection specifically claimed by this utility model.

[0021] like Figure 1-3 As shown, a dual-tube anisotropic compact hydraulic push rod includes a dual-cavity plate 1 and two central push rod assemblies 2. The dual-cavity plate 1 has two parallel anisotropic circular cavities 12. The dual-cavity plate 1 has two symmetrically staggered recesses 11 on both sides. The two central push rod assemblies 2 are symmetrically arranged in the two anisotropic circular cavities 12 and correspond to the two staggered recesses 11 respectively.

[0022] Two grooves are formed on the surface of the double-cavity plate 1, and symmetrically staggered push input pipes 3 and return input pipes 4 are inserted in both grooves. Connectors 5 are installed on opposite sides of the two push input pipes 3 and the two return input pipes 4. The two connectors 5 are respectively connected to the pipeline output of the external hydraulic pump. The opposite sides of the two return input pipes 4 are respectively connected to the through holes corresponding to the two opposite circular cavities 12 formed on both sides of the surface of the double-cavity plate 1.

[0023] As an optional implementation, the central push rod assembly 2 includes a piston rod 21 and an oil seal assembly. The piston rod 21 is sleeved in the opposite circular cavity 12. An oil seal 22 connected to one side of the piston rod 21 is provided in the opposite circular cavity 12 near the misaligned recess 11. Top support plates 23 are provided on both sides of the double cavity plate 1. The top support plates 23 are fixedly installed on the other side of the piston rod 21. The two top support plates 23 correspond to the two misaligned recesses 11 respectively. The corresponding arrangement of the misaligned recesses 11 and the top support plates 23 keeps the thrust on both sides balanced.

[0024] See attached document Figure 3 The oil seal assembly is configured in two sets, which are respectively located on opposite sides of the double-chamber plate 1 and on both sides of the opposite circular cavity 12. One set is located on the piston rod 21. The oil seal assembly includes an inner tube 24, an oil pipe spacer sealing ring 27 and a front sealing ring 26. One side of the inner tube 24 is inserted into the opposite circular cavity 12. In this way, the two sets of oil seal assemblies can push and adjust the oil seal 22 on the piston rod 21 from both sides, thereby coping with the extension and retraction adjustment of the piston rod 21.

[0025] Furthermore, an oil pipe spacer sealing ring 27 and a front sealing ring 26 are provided inside the counter-rotating circular cavity 12. The oil pipe spacer sealing ring 27 is fitted around the outer periphery of the inner tube 24 and is in compression contact with the inner wall of the counter-rotating circular cavity 12. The front sealing ring 26 is fitted on the inner tube 24 and is located on one side inside the counter-rotating circular cavity 12, and is in compression contact with the inner wall of the counter-rotating circular cavity 12. The side of the front sealing ring 26 is attached to the anti-reverse ring 24b, and the anti-reverse ring 24b is integrally set on the outer periphery of the inner tube 24. The outer diameter of the anti-reverse ring 24b is smaller than the radius of the counter-rotating circular cavity 12. In this way, the front sealing ring 26 and the oil pipe spacer sealing ring 27 can form a double pressure-resistant sealing effect on the counter-rotating circular cavity 12 and the outer wall of the inner tube 24, thereby improving the spacer sealing effect of the inner tube 24 extending into the counter-rotating circular cavity 12.

[0026] See attached document Figure 1 and attached Figure 3 A fastening ring 24a and a fastening sealing ring 28 are provided on the side of the oppositely oriented circular cavity 12 corresponding to the misaligned recess 11. The fastening ring 24a presses the fastening sealing ring 28 against the side of the misaligned recess 11 or the side of the double cavity plate 1 by reinforcing bolts. This design can form a squeezing sealing effect between the inner tube 24 and the side of the misaligned recess 11, thereby forming a secondary sealing effect on the inner tube 24. A sliding sealing element 25 is slidably installed on the piston rod 21. The sliding sealing element 25 is set in the inner tube 24 corresponding to the side of the double cavity plate 1, thereby sealing the sliding adjustment of the piston rod 21 and ensuring the extension and retraction adjustment of the piston rod 21.

[0027] Furthermore, the other side of the embedded tube 24 corresponding to the misaligned notch 11 is set to a blocked state, and an injection head 29 is installed on the other side of the embedded tube 24. The injection head 29 is connected to one side of the push input tube 3, so that the push input tube 3 can push the oil seal 22 in the opposite circular cavity 12, thereby driving the piston rod 21 to move and extend, and achieving the pushing separation effect.

[0028] Furthermore, two gripping rings 7 are provided on the outer periphery of the double-chamber plate 1. The two sides of the gripping rings 7 are respectively fixed on two fastening discs 6, which are fixed on the sides of the double-chamber plate 1. This makes it convenient for the operator to lift the hydraulic push rod through the gripping rings 7.

[0029] Using the above structure, hydraulic oil is first injected into the opposite-direction circular cavity 12 through the push input pipe 3. The hydraulic oil pushes the oil seal 22 to extend the piston rod 21 outward, while the return oil channel connected to the return input pipe 4 remains unobstructed. When it is necessary to retract the piston rod 21, hydraulic oil is injected through the return input pipe 4. The hydraulic oil pushes the oil seal 22 to move in the opposite direction, while the push input pipe 3 serves as a return oil channel to discharge the hydraulic oil. The synchronous action of the two sets of central push rod assemblies 2 is achieved through symmetrically arranged oil seal assemblies. The double sealing structure formed by the embedded tube 24, the oil pipe spacer sealing ring 27, and the front sealing ring 26 ensures that the hydraulic oil does not leak, while the sliding seal 25 ensures dynamic sealing when the piston rod 21 extends or retracts. During operation, the push rod position can be stably controlled by the gripping ring 7 to achieve precise push or retraction operations.

[0030] The above description is merely a preferred embodiment of this utility model. It should be noted that those skilled in the art can make various improvements and modifications without departing from the principle of this utility model, and these improvements and modifications should also be considered within the scope of protection of this utility model. All standard parts used in this application can be purchased from the market, and can be customized according to the description and drawings. The specific connection methods of each part all adopt conventional methods such as bolts, rivets, and welding, which are mature technologies in the prior art. The machinery, parts, and equipment all adopt conventional models in the prior art. This application is mainly used to protect mechanical devices. Structures, devices, and operating methods not specifically described or explained in this utility model, unless otherwise specified or limited, are implemented according to conventional methods in the field.

Claims

1. A compact, dual-tube, anisotropic hydraulic actuator, characterized in that: It includes a double cavity plate (1) and two central push rod assemblies (2). The double cavity plate (1) has two parallel opposite circular cavities (12). The double cavity plate (1) has two symmetrically staggered recesses (11) on both sides. The two central push rod assemblies (2) are symmetrically arranged in the two opposite circular cavities (12) and correspond to the two staggered recesses (11) respectively. The surface of the double cavity plate (1) is provided with two grooves, and each groove is fitted with a symmetrically staggered push input pipe (3) and a return input pipe (4). The opposite sides of the two push input pipes (3) and the two return input pipes (4) are equipped with connectors (5). The opposite sides of the two return input pipes (4) are respectively connected to the through holes on both sides of the surface of the double cavity plate (1) that correspond to the two opposite circular cavities (12).

2. The dual-tube anisotropic compact hydraulic actuator according to claim 1, characterized in that: The central push rod assembly (2) includes a piston rod (21) and an oil seal assembly. The piston rod (21) is sleeved in the opposite circular cavity (12). An oil seal (22) connected to one side of the piston rod (21) is provided on the side of the opposite circular cavity (12) near the misaligned recess (11). Top support plates (23) are provided on both sides of the double cavity plate (1). The top support plates (23) are fixedly installed on the other side of the piston rod (21). The two top support plates (23) correspond to the two misaligned recesses (11) respectively.

3. A dual-tube anisotropic compact hydraulic actuator according to claim 2, characterized in that: The oil seal assembly is configured as two sets, and the two sets of oil seal assemblies are respectively set on opposite sides of the double cavity plate (1) and located on both sides of the opposite circular cavity (12). One set is set on the piston rod (21). The oil seal assembly includes an inner tube (24), an oil pipe spacer sealing ring (27) and a front sealing ring (26). One side of the inner tube (24) is inserted into the opposite circular cavity (12).

4. A dual-tube anisotropic compact hydraulic actuator according to claim 3, characterized in that: The opposite circular cavity (12) is provided with an oil pipe spacer sealing ring (27) and a front sealing ring (26). The oil pipe spacer sealing ring (27) is sleeved on the outer circumference of the inner tube (24) and is in extrusion contact with the inner wall of the opposite circular cavity (12). The front sealing ring (26) is sleeved on the inner tube (24) and is located on one side inside the opposite circular cavity (12) and is in extrusion contact with the inner wall of the opposite circular cavity (12). The side of the front sealing ring (26) is attached to the anti-reverse ring (24b), and the anti-reverse ring (24b) is integrally set on the outer circumference of the inner tube (24). The outer diameter of the anti-reverse ring (24b) is smaller than the radius of the opposite circular cavity (12).

5. A dual-tube anisotropic compact hydraulic actuator according to claim 4, characterized in that: A fastening ring (24a) and a fastening sealing ring (28) are provided on the side of the opposite circular cavity (12) corresponding to the misaligned recess (11). The fastening ring (24a) presses the fastening sealing ring (28) against the side of the misaligned recess (11) or the side of the double cavity plate (1) by means of reinforcing bolts. This design can form a squeezing sealing effect between the embedded tube (24) and the side of the misaligned recess (11), thereby forming a secondary sealing effect on the embedded tube (24). A sliding sealing element (25) is slidably installed on the piston rod (21). The sliding sealing element (25) is set in the embedded tube (24) corresponding to the side of the double cavity plate (1).

6. A dual-tube anisotropic compact hydraulic actuator according to claim 5, characterized in that: The other side of the inner tube (24) corresponding to the misaligned notch (11) is set to a blocked state, and an injection head (29) is installed on the other side of the inner tube (24). The injection head (29) is connected to one side of the push input tube (3).

7. A dual-tube anisotropic compact hydraulic actuator according to claim 6, characterized in that: Two gripping rings (7) are provided on the outer periphery of the double cavity plate (1). The two sides of the gripping rings (7) are respectively fixed on two fastening plates (6), and the fastening plates (6) are fixed on the side of the double cavity plate (1).

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