Mandrel and piston type liquid-gas buffer

Abstract

The invention belongs to the technical field of buffers, and particularly relates to a mandrel type and piston type liquid-gas buffer which overcomes the conventional technical prejudice of technicians in the field (generally research and development are carried out in the direction of improving the machining precision of a conical structure), and a conical column structure is improved into an equal-diameter cylindrical structure. The diameter of the cylindrical structure is equal to that of an inner hole in the core shaft seat, a plurality of damping grooves are formed in the shaft rod, and the groove structure is gradually sparse. On one hand, the machining difficulty of the cylindrical structure with the equal diameter and the requirement for the machining precision are greatly reduced, the cost is relatively reduced, in addition, the cylindrical structure and the inner hole in the mandrel base are equal in diameter, the damping grooves are formed in the surface of the mandrel body, the buffering performance is better, the damping groove structure serves as an oil channel, buffering force can be evenly distributed, and the service life of the mandrel is prolonged. And when an impactor with larger kinetic energy impacts, the condition that the mandrel is stuck on the mandrel seat is avoided.

Description

Technical Field

[0001] The invention belongs to the technical field of buffers, and in particular relates to a core shaft and piston type liquid-gas buffer. Background Art

[0002] Cranes used in ports and construction sites, vehicles on railways, rolling mills in the metallurgical industry, and elevators in high-rise buildings are all prone to collisions during operation. In order to avoid the huge loads caused by these collisions, affecting the normal operation of the machinery or even causing damage to the machine parts, buffers are generally installed.

[0003] As a key component in the buffer, the mandrel plays an important role in guiding the movement of the piston rod, controlling the flow of oil, and adjusting the buffering force. During the buffering process, the mandrel can affect the flow speed and direction of the oil through its specific structural design, thereby realizing the precise control of the buffering force. However, the mandrel in the traditional solution, that is, a cylindrical structure from thin to thick, has gradually exposed many shortcomings in long-term application. The mandrel of this structure is difficult to distribute the force evenly during buffering, resulting in unstable buffering effect. At the same time, when facing complex working conditions, its adaptability is poor and it is difficult to meet the diverse buffering needs. In addition, due to structural limitations, jamming is prone to occur during the buffering operation, affecting the smoothness and reliability of the buffer. When an impactor with greater kinetic energy hits, the inner rod is easily stuck at the bottom of the mandrel, which not only limits the further improvement of the overall performance of the oil-gas buffer, but may also cause damage to the equipment.

[0004] The above information disclosed in the above background technology section is only used to enhance the understanding of the background technology of the technology described in this article. Therefore, the background technology may contain certain information that does not form the prior art known in this country to those skilled in the art. Summary of the invention

[0005] In order to solve the defects of the prior art mentioned above, the present invention proposes a mandrel and piston type liquid-gas buffer.

[0006] The technical solution adopted by the present invention is as follows:

[0007] A core shaft comprises a shaft body, wherein the two sides of the shaft body are respectively a front end of a shaft rod and a rear end of the shaft rod, the front end of the shaft rod is connected to a core shaft seat, the core shaft seat is provided with an inner hole, the inner hole is sleeved on the outer side of the shaft body, and the rear end of the shaft rod is connected to a cylinder base. It is characterized in that the shaft body is a cylindrical structure of equal diameter, the cylindrical structure has the same diameter as the inner hole on the core shaft seat, and the surface of the shaft body is provided with an oil channel with a groove structure.

[0008] The depth of the groove structure decreases in sequence from the spindle seat to the cylinder base.

[0009] The groove structure is a plurality of linear grooves, which are coaxial with the core shaft and are distributed in an annular array on the outer peripheral surface of the shaft rod.

[0010] The number of the linear grooves decreases from the front end to the rear end of the shaft rod.

[0011] The groove structure is a grid-type groove, and the grid-type grooves are evenly distributed on the outer peripheral surface of the shaft rod.

[0012] The number of the grid-shaped grooves decreases from the front end to the rear end of the shaft rod.

[0013] The groove structure is a spiral groove, and the spiral grooves are evenly distributed on the outer circumference of the shaft rod. The number of the spiral grooves decreases from the front end to the rear end of the shaft rod.

[0014] The cross-sectional shapes of the linear grooves, grid grooves and spiral grooves are all one of fan-shaped grooves, triangular grooves, semicircular grooves and rectangular grooves.

[0015] A piston type liquid-gas buffer comprises an outer sleeve and a piston rod inserted at the left end of the outer sleeve, an isolation piston is installed in the inner cavity of the piston rod, the left end of the isolation piston is a nitrogen chamber, and the right end is an oil chamber, a cylinder base is arranged at the end of the oil chamber away from the isolation piston, a mandrel seat is installed at the right end of the piston rod, the mandrel seat is provided with an inner hole, the new mandrel provided by the present invention is inserted in the inner hole, and the right end of the mandrel is connected to the cylinder base at the right end of the outer sleeve; the interior of the outer sleeve and the right end of the piston rod and the left end of the cylinder base together form an oil chamber for containing hydraulic oil.

[0016] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are:

[0017] As is common technical knowledge in the art, the shaft rod in the prior art is a conical column structure of unequal diameters, with a small diameter at one end connected to the core shaft seat and a large diameter at the other end connected to the cylinder base. During the operation of the buffer, the gap between the shaft rod and the inner hole is an oil channel. As the core shaft moves toward the core shaft seat, the oil channel becomes narrower and narrower, and the damping effect becomes greater and greater. The disadvantage of this conical structure is that the conical structure is difficult to process, and errors are prone to occur in the processing taper, resulting in uneven taper. The distribution of the buffering force is difficult to be uniform during buffering, and the inner rod is prone to get stuck when facing complex working conditions. Living at the bottom of the mandrel; through the above, the conical column structure is improved into a cylindrical structure of equal diameter, the cylindrical structure is equal in diameter to the inner hole on the mandrel seat, and a plurality of groove structure oil channels are arranged on the shaft rod. On the one hand, the processing difficulty and the requirements for processing accuracy of the cylindrical structure of equal diameter are greatly reduced, and the cost is relatively reduced. In addition, the cylindrical structure is equal in diameter to the inner hole on the mandrel seat, and the surface of the shaft body is provided with a groove structure oil channel. In the process of displacement of the mandrel toward the mandrel seat, the groove structure serves as an oil channel, which can achieve uniform distribution of buffering force. When an impactor with greater kinetic energy hits, the mandrel will not get stuck in the mandrel seat. The above design is extremely clever. The core invention of this technical solution is that it overcomes the conventional technical prejudice of technicians in this field (usually from the direction of improving the processing accuracy of the conical structure). Through the above simple improvement, the more troublesome technical problems in this field are effectively solved, and unexpected technical effects are achieved. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The present invention will now be described by way of example with reference to the accompanying drawings, in which:

[0019] Figure 1 A schematic diagram of an implementation of the oil channel in the core shaft of the present invention;

[0020] Figure 2-4 They are Figure 1 Schematic diagram of the AA, BB, and CC cross-section structures;

[0021] Figure 5 A schematic diagram of an implementation of the oil channel in the core shaft of the present invention;

[0022] Figure 6-7 They are Figure 5 Schematic diagram of the DD and EE cross-section structures;

[0023] Figure 8 A schematic diagram of an implementation of the oil channel in the core shaft of the present invention;

[0024] Figure 9-10 They are Figure 8Schematic diagram of the cross-section structure of FF and GG;

[0025] Fig.11 It is a schematic diagram of the structure of the piston type liquid-gas buffer in the present invention. DETAILED DESCRIPTION

[0026] To make the purpose, technical scheme and advantages of the embodiments of the present application clearer, the technical scheme in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all of the embodiments. The components of the embodiments of the present application usually described and shown in the drawings here can be arranged and designed in various configurations. Therefore, the following detailed description of the embodiments of the present application provided in the drawings is not intended to limit the scope of the application claimed for protection, but merely represents the selected embodiments of the present application. Based on the embodiments of the present application, all other embodiments obtained by those skilled in the art without making creative work belong to the scope of protection of the present application.

[0027] This embodiment introduces an innovative design of the mandrel 7, the specific structure is as follows Figure 1-11 As shown, the mandrel 7 is mainly composed of the following parts:

[0028] The shaft body 8 has two ends, namely, the front end 9 of the shaft and the rear end 10 of the shaft. The front end 9 of the shaft is connected to the mandrel seat 5, and the mandrel seat 5 is provided with an inner hole 6, which is tightly sleeved on the outside of the shaft. The rear end 10 of the shaft is connected to the cylinder base 4. The uniqueness of this design is that the shaft adopts a cylindrical structure of equal diameter, and the diameter of this cylindrical structure is completely consistent with the inner hole 6 on the mandrel seat 5. In addition, the surface of the shaft body 8 is carefully designed with an oil channel with a groove structure, and the depth of the groove structure decreases from the mandrel seat 5 to the cylinder base 4.

[0029] In the prior art, the shaft rod usually adopts a conical column structure with unequal diameters, that is, the end connected to the core shaft seat 5 has a smaller diameter, while the end connected to the cylinder base 4 has a larger diameter. When the buffer is operating, the gap between the shaft rod and the inner hole 6 acts as an oil channel. However, as the core shaft 7 moves toward the core shaft seat 5, this oil channel will gradually narrow, resulting in a gradual increase in the damping effect. The disadvantage of this conical structure is that it is difficult to process, and the taper processing is prone to errors, resulting in uneven taper distribution, and then it is difficult to evenly distribute the buffering force during the buffering process. It has poor adaptability to complex working conditions, and under the action of a high kinetic energy impactor, the inner rod is easily stuck at the bottom of the core shaft 7.

[0030] In view of the above problems, the present embodiment innovates the conical column structure into a cylindrical structure of equal diameter, and keeps the same diameter as the inner hole 6 on the spindle seat 5. At the same time, multiple oil channels with groove structures are cleverly arranged on the shaft rod. This improvement not only significantly reduces the difficulty of processing and the requirements for precision, thereby effectively controlling the cost, but also ensures the perfect match between the cylindrical structure and the inner hole 6 of the spindle seat 5. More importantly, the groove structure on the surface of the shaft body 8 serves as an oil channel, which can ensure the uniform distribution of the buffering force during the movement of the spindle 7 toward the spindle seat 5, and can effectively avoid the spindle 7 from getting stuck at the spindle seat 5 even when facing a large kinetic energy impactor.

[0031] The design of the mandrel 7 in this embodiment shows several significant innovations, as follows:

[0032] Applications of equal diameter cylindrical structures:

[0033] Compared with the conventional unequal diameter conical column structure, the present embodiment adopts an equal diameter cylindrical structure. This change not only simplifies the processing process and reduces the requirements for processing accuracy, but also significantly improves cost-effectiveness.

[0034] The equal-diameter structure ensures perfect matching between the shaft and the inner hole 6 of the mandrel seat 5, reduces matching problems caused by machining errors, and thus improves overall stability and reliability.

[0035] Design of the groove structure oil channel:

[0036] An oil channel with a groove structure is carefully designed on the surface of the shaft body 8. This innovative design optimizes the flow path of the oil, making the oil flow smoother and more even during the buffering process.

[0037] The groove structure not only provides a stable oil channel, but also helps to achieve a more uniform damping effect during the cushioning process, thereby improving the performance of the shock absorber.

[0038] Solved the defects of traditional cone structure:

[0039] The traditional conical structure is prone to uneven taper during processing, which makes it difficult to evenly distribute the buffer force and has poor adaptability to complex working conditions. This embodiment effectively solves these problems by adopting an equal-diameter cylindrical structure and a groove structure oil channel, so that the core shaft 7 can maintain a stable and uniform buffer force output during the buffering process.

[0040] Improved buffer adaptability and durability:

[0041] The design of the equal-diameter cylindrical structure and the groove structure oil channel enables the core shaft 7 to maintain better stability and durability when facing a large kinetic energy impactor. This design also improves the adaptability of the buffer to different working conditions, enabling it to perform well in a wider range of application scenarios.

[0042] In summary, the design of the core shaft 7 in this embodiment shows significant innovations in terms of structure, function and adaptability, and provides new ideas and directions for the technical development in related fields.

[0043] In one embodiment, see Figure 1 The groove structure is designed as a plurality of linear grooves 11. These linear grooves 11 are coaxial with the core shaft 7 and are distributed on the outer peripheral surface of the shaft in a ring array. The linear structure grooves are like straight flow channels, allowing the fluid to flow in an orderly manner in a specific direction, providing stable and direct buffering support for the buffer.

[0044] For further information, see Figure 2-4 The number of the linear grooves 11 decreases from the front end 9 to the rear end of the shaft rod, and optionally, decreases from 6 evenly distributed grooves to 2, from 4 evenly distributed grooves to 1, or from 7 evenly distributed grooves to 2, etc. This design can adjust the flow speed and damping effect of the oil according to the buffering requirements. During the movement of the core shaft 7, as the number of the linear grooves 11 decreases, the oil flow rate is slower, thereby achieving more precise buffering control.

[0045] In another embodiment, see Figure 5 , the groove structure is designed as a grid-type groove 12. The grid-type grooves 12 are evenly distributed on the outer peripheral surface of the shaft, forming a grid-like pattern. The intricate mesh layout of the grooves in the reticular structure fully regulates the flow path of the fluid, giving the buffer a stronger ability to adapt to complex working conditions, effectively improving the buffering performance while broadening its application range. This design not only increases the flow path of the oil, but also improves the uniformity and stability of the oil flow.

[0046] For further information, see Figure 6 , 7 The number of the grid-shaped grooves 12 decreases from the front end 9 to the rear end of the shaft. During the movement of the core shaft 7, as the number of the grid-shaped grooves 12 decreases, the corresponding oil flow rate becomes slower. This design can adjust the flow rate and damping effect of the oil according to the buffering requirements, thereby achieving more precise buffering control.

[0047] In another optional embodiment, see Figure 8The groove structure is designed as a spiral groove 13. The spiral grooves 13 are evenly distributed on the outer circumference of the shaft. The spiral structure grooves are like precise spiral tracks, which can make the fluid in the buffering process produce a unique spiral flow, greatly optimize the distribution of the buffering force, and achieve a more stable and efficient buffering effect.

[0048] For further information, see Fig. 9 , 10 , the number of spiral grooves 13 decreases from the front end 9 to the rear end of the shaft. As the number of spiral grooves 13 decreases, the corresponding oil flow rate becomes slower. This design can also adjust the flow rate and damping effect of the oil according to the buffering requirements, providing more precise buffering control.

[0049] In an optional embodiment, in all the above embodiments, whether it is a linear groove 11, a grid groove 12 or a spiral groove 13, its cross-sectional shape is designed as a fan-shaped groove 14. This design not only increases the contact area of ​​the oil, but also helps to improve the uniformity and stability of the oil flow. It is worth mentioning that the cross-sectional shape is not limited to the fan-shaped groove 14, and can also be designed as a triangular groove, a semicircular groove, a rectangular groove, etc.

[0050] In summary, these optional implementations provide a variety of different groove structure designs to meet the buffering requirements in different application scenarios. By adjusting the shape, density and distribution of the groove structure, the oil flow rate and damping effect can be finely controlled, thereby improving the performance and adaptability of the buffer.

[0051] A piston-type hydraulic buffer with a sophisticated structure and perfect functions. Fig.11 , mainly including a jacket 1 and a piston rod 2 assembly inserted into the left end of the jacket 1. A key isolation piston 3 is provided inside the piston rod 2 assembly, which divides the internal space into two parts: the left side is a nitrogen chamber for storing nitrogen to provide a buffering force; the right side is an oil chamber for containing hydraulic oil to achieve a damping effect. At the far end of the oil chamber, that is, the end away from the isolation piston 3, a cylinder base 4 is provided for closing the oil chamber and supporting the hydraulic oil therein. A mandrel seat 5 is cleverly installed at the right end of the piston rod 2, and a precise inner hole 6 is provided in the mandrel seat 5 for inserting and fixing the mandrel 7 provided in the present invention. The right end of the mandrel 7 is firmly connected to the cylinder base 4 at the right end of the jacket 1, thereby forming a stable mechanical structure. The internal space of the jacket 1, together with the right end part of the piston rod 2 and the left end part of the cylinder base 4, encloses a closed oil chamber, which is filled with an appropriate amount of hydraulic oil to provide the necessary damping force during the buffering process.

[0052] As described above, the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit the same. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that the technical solutions described in the aforementioned embodiments may still be modified, or some of the technical features thereof may be replaced by equivalents. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A spindle, comprising a shaft body (8), the two sides of the shaft body (8) are a shaft front end (9) and a shaft rear end (10), the shaft front end (9) is connected to a spindle seat (5), the spindle seat (5) is provided with an inner hole (6), the inner hole (6) is sleeved on the outer side of the shaft body (8), the shaft rear end (10) is connected to a cylinder base (4), characterized in that: The shaft body (8) is a cylindrical structure with an equal diameter, and the cylindrical structure has the same diameter as the inner hole (6) on the spindle seat (5). An oil channel with a damping groove structure is provided on the surface of the shaft body (8).

2. A mandrel according to claim 1, characterized in that: The cross section of the groove structure gradually narrows in the direction from the spindle seat (5) to the cylinder base (4).

3. A mandrel according to claim 1, characterized in that: The groove structure is a plurality of linear grooves (11), the plurality of linear grooves (11) are coaxial with the core shaft (7), and are distributed in an annular array on the outer peripheral surface of the shaft rod.

4. A mandrel according to claim 3, characterized in that: The number of the linear grooves (11) decreases from the front end (9) to the rear end of the shaft rod.

5. A mandrel according to claim 1, characterized in that: The groove structure is a grid-type groove (12), and the grid-type groove (12) is evenly distributed on the outer peripheral surface of the shaft rod.

6. A mandrel according to claim 5, characterized in that: The number of the grid-shaped grooves (12) decreases from the front end (9) to the rear end of the shaft rod.

7. A mandrel according to claim 1, characterized in that: The groove structure is a spiral groove (13), and the spiral groove (13) is evenly distributed on the outer peripheral surface of the shaft rod.

8. A mandrel according to claim 7, characterized in that: The number of the spiral grooves (13) decreases from the front end (9) to the rear end of the shaft.

9. A mandrel according to any one of claims 3 to 8, characterized in that: The cross-sectional shape of the linear groove (11), the grid-shaped groove (12) and the spiral groove (13) is one of a fan-shaped groove (14), a triangular groove, a semicircular groove or a rectangular groove.

10. A piston type liquid-gas buffer, characterized in that: The invention comprises a sleeve (1) and a piston rod (2) inserted at the left end of the sleeve (1); an isolation piston (3) is installed in the inner cavity of the piston rod (2); the left end of the isolation piston (3) is a nitrogen cavity and the right end is an oil cavity; a cylinder base (4) is provided at the end of the oil cavity away from the isolation piston (3); a mandrel seat (5) is installed at the right end of the piston rod (2); the mandrel seat (5) is provided with an inner hole (6); a mandrel (7) according to any one of claims 1 to 8 is inserted in the inner hole (6); the right end of the mandrel (7) is connected to the cylinder base (4) at the right end of the sleeve (1); the interior of the sleeve (1) and the right end of the piston rod (2) and the left end of the cylinder base (4) together form an oil cavity for containing hydraulic oil.

Images