Mandrel and piston type liquid-gas buffer
By adopting a mandrel with a constant diameter cylindrical structure and groove design, the problems of uneven distribution of buffer force and high processing difficulty of traditional conical structures are solved, achieving a more stable and uniform buffering effect and greater adaptability.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SHANGHAI AIDEYAN IND CO LTD
- Filing Date
- 2025-03-28
- Publication Date
- 2026-04-14
AI Technical Summary
The unequal diameter tapered structure of traditional mandrels leads to uneven distribution of buffering force during the buffering process, resulting in poor adaptability, easy jamming, and high processing difficulty, which affects the stability and reliability of the buffer.
The shaft adopts a cylindrical structure with equal diameter and grooves on its surface to form oil channels. The grooves gradually narrow from the mandrel seat to the cylinder base and are designed as several straight, grid, or spiral grooves to optimize the oil flow path.
It achieves a uniform distribution of buffering force, reduces processing difficulty and cost, improves the stability and adaptability of the buffer, avoids jamming, and enhances the smoothness and reliability of the buffer.
Smart Images
Figure CN224120586U_ABST
Abstract
Description
Technical Field
[0001] This utility model belongs to the field of buffer technology, specifically relating to a mandrel and piston-type liquid-gas buffer. Background Technology
[0002] Cranes used in ports and construction sites, rolling mills on railways, rolling mills in the metallurgical industry, and elevators in high-rise buildings are all prone to collisions during operation. To avoid the enormous loads generated by these collisions, which could affect the normal operation of the machinery or even damage its components, shock absorbers are commonly installed.
[0003] The mandrel, as a key component of the buffer, plays a crucial role in guiding the piston rod movement, controlling the oil flow, and adjusting the buffering force. During buffering, the mandrel, through its specific structural design, can influence the flow speed and direction of the oil, thereby achieving precise control of the buffering force. However, the traditional mandrel design—a cylindrical structure that tapers from thin to thick—has gradually revealed several shortcomings in long-term application. This type of mandrel makes it difficult to distribute force evenly during buffering, leading to unstable buffering effects. Furthermore, its adaptability to complex operating conditions is poor, making it difficult to meet diverse buffering needs. In addition, due to structural limitations, jamming is prone to occur during buffering operation, affecting the smoothness and reliability of the buffer. When impacted by a high-energy object, the inner rod can easily become stuck at the bottom of the mandrel, which not only limits further improvement in the overall performance of the oil-gas buffer but may also damage the equipment.
[0004] The information disclosed in the background section above is only used to enhance the understanding of the background art of the art described herein. Therefore, the background art may contain certain information that does not constitute prior art known to those skilled in the art in this country. Utility Model Content
[0005] To address the shortcomings of the existing technology, this utility model proposes a mandrel and a piston-type liquid-gas buffer.
[0006] The technical solution adopted in this utility model is as follows:
[0007] A mandrel includes a shaft body with a shaft rod front end and a shaft rod rear end on both sides. The shaft rod front end is connected to a mandrel seat, which has an inner hole that fits around the outside of the shaft body. The shaft rod rear end is connected to a cylinder base. The shaft body is a cylindrical structure of equal diameter, and the cylindrical structure has the same diameter as the inner hole on the mandrel seat. The surface of the shaft body has grooved oil channels.
[0008] The cross-section of the groove structure gradually narrows from the mandrel seat to the cylinder base, and specifically, the depth of the groove structure gradually decreases from the mandrel seat to the cylinder base.
[0009] The groove structure consists of several straight grooves, which are coaxial with the mandrel and arranged in a ring array on the outer circumferential surface of the shaft.
[0010] The number of linear grooves decreases sequentially from the front end to the rear end of the shaft.
[0011] The groove structure is a grid-shaped groove, which is evenly distributed on the outer circumferential surface of the shaft.
[0012] The number of the grid-shaped grooves decreases sequentially from the front end to the rear end of the shaft.
[0013] The groove structure is a spiral groove, which is evenly distributed on the outer circumferential surface of the shaft.
[0014] The number of spiral grooves decreases sequentially from the front end to the rear end of the shaft.
[0015] The cross-sectional shape of the straight groove, the grid groove, and the spiral groove is one of the following: fan-shaped groove, triangular groove, semi-circular groove, and rectangular groove.
[0016] A piston-type hydraulic-gas damper includes 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 provided 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 has an inner hole in which the novel mandrel provided by this utility model is inserted. 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, together with the right end of the piston rod and the left end of the cylinder base, forms an oil chamber for containing hydraulic oil.
[0017] In summary, due to the adoption of the above technical solution, the beneficial effects of this utility model are:
[0018] As is common knowledge in this field, the existing shaft is a tapered cylindrical structure with unequal diameters. The end connected to the mandrel seat has a smaller diameter, while the end connected to the cylinder base has a larger diameter. During the operation of the damper, the gap between the shaft and the inner hole serves as an oil passage. As the mandrel moves towards the mandrel seat, the oil passage narrows, and the damping effect increases. The disadvantages of this tapered structure are that it is difficult to manufacture, the taper is prone to errors, resulting in uneven taper. This makes it difficult to distribute the damping force evenly during buffering, leading to poor adaptability to complex working conditions, buffering operation jamming, and the inner rod easily jamming when impacted by a large kinetic energy object. The mandrel is located at its bottom. Through the above, the tapered cylindrical structure is improved into a cylindrical structure of equal diameter. This cylindrical structure has the same diameter as the inner hole on the mandrel seat, and several grooved oil channels are provided on the shaft. On one hand, the machining difficulty and precision requirements of the equal-diameter cylindrical structure are significantly reduced, thus lowering costs. On the other hand, the equal diameter of the cylindrical structure and the grooved oil channels on the shaft surface allow for uniform distribution of buffer force during the mandrel's displacement towards the mandrel seat. This prevents the mandrel from jamming against the mandrel seat even when impacted by a large kinetic energy object. The above design is extremely ingenious. The core utility model of this technical solution lies in its overcoming the conventional technical biases of those skilled in the art (usually focusing on improving the machining precision of the tapered structure). Through the above simple improvement, a rather troublesome technical problem in this field is effectively solved, achieving unexpected technical results. Attached Figure Description
[0019] This utility model will be described by way of example and with reference to the accompanying drawings, wherein:
[0020] Figure 1 This is a schematic diagram of one embodiment of the oil channel in the mandrel of this utility model;
[0021] Figure 2-4 They are respectively Figure 1 Schematic diagram of the cross-sectional structure of AA, BB, and CC in the middle section;
[0022] Figure 5 This is a schematic diagram of one embodiment of the oil channel in the mandrel of this utility model;
[0023] Figure 6-7 They are respectively Figure 5 Schematic diagram of the cross-sectional structure of DD and EE in the middle section;
[0024] Figure 8 This is a schematic diagram of one embodiment of the oil channel in the mandrel of this utility model;
[0025] Figure 9-10 They are respectively Figure 8Schematic diagram of the cross-sectional structure of FF and GG in China;
[0026] Figure 11 This is a schematic diagram of the piston-type liquid-gas buffer in this utility model. Detailed Implementation
[0027] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. The components of the embodiments of this application described and shown in the accompanying drawings can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely represents selected embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.
[0028] This embodiment introduces an innovative mandrel 7 design, the specific structure of which is as follows: Figure 1-11 As shown, the mandrel 7 mainly consists of the following parts:
[0029] The shaft body 8 has a front end 9 and a rear end 10 at its two ends. The front end 9 is connected to a mandrel seat 5, which has an inner hole 6 that fits tightly around the shaft. The rear end 10 is connected to a cylinder base 4. A unique feature of this design is that the shaft adopts a cylindrical structure of equal diameter, which perfectly matches the diameter of the inner hole 6 on the mandrel seat 5. Furthermore, the surface of the shaft body 8 is carefully designed with grooved oil channels. The cross-section of these grooves gradually narrows from the mandrel seat 5 to the cylinder base 4, and specifically, the depth of the grooves gradually decreases from the mandrel seat 5 to the cylinder base 4.
[0030] In existing technologies, shafts typically employ a tapered cylindrical structure with unequal diameters, where the end connected to the spindle seat 5 has a smaller diameter, while the end connected to the cylinder base 4 has a larger diameter. During damper operation, the gap between the shaft and the inner hole 6 acts as an oil passage. However, as the spindle 7 moves towards the spindle seat 5, this oil passage gradually narrows, resulting in a gradual increase in damping effect. The drawback of this tapered structure is its high machining difficulty; errors in tapering are prone to occur, leading to uneven tapering distribution. Consequently, the damping force distribution is uneven during buffering, resulting in poor adaptability to complex working conditions. Furthermore, under the impact of high-energy objects, the inner shaft is prone to jamming at the bottom of the spindle 7.
[0031] To address the aforementioned issues, this embodiment innovates the tapered column structure into a cylindrical structure of equal diameter, maintaining the same diameter as the inner hole 6 on the mandrel seat 5. Simultaneously, multiple grooved oil channels are cleverly incorporated into the shaft. This improvement not only significantly reduces machining difficulty and precision requirements, thereby effectively controlling costs, but also ensures a perfect match between the cylindrical structure and the inner hole 6 of the mandrel seat 5. More importantly, the grooved structure on the surface of the shaft 8, acting as oil channels, ensures a uniform distribution of buffering force as the mandrel 7 moves towards the mandrel seat 5, effectively preventing the mandrel 7 from jamming at the mandrel seat 5 even when facing high-energy impacts.
[0032] The design of the spindle 7 in this embodiment exhibits several significant innovations, as follows:
[0033] Applications of equal-diameter cylindrical structures:
[0034] Compared to traditional tapered cylindrical structures with unequal diameters, this embodiment employs a cylindrical structure with equal diameters. This change not only simplifies the manufacturing process and reduces the requirements for machining accuracy, but also significantly improves cost-effectiveness.
[0035] The equal diameter structure ensures a perfect match between the shaft and the inner hole 6 of the mandrel seat 5, reducing fit problems caused by machining errors, thereby improving the overall stability and reliability.
[0036] Design of grooved oil channels:
[0037] An oil channel with a groove structure was carefully designed on the surface of shaft 8. This innovative design optimizes the flow path of the oil, making the oil flow smoother and more uniform during the buffering process.
[0038] The grooved structure not only provides a stable oil channel, but also helps to achieve a more uniform damping effect during the buffering process, thereby improving the performance of the buffer.
[0039] It solves the defects of traditional conical structures:
[0040] Traditional tapered structures are prone to uneven taper during processing, resulting in inconsistent distribution of buffering force and poor adaptability to complex working conditions. This embodiment effectively solves these problems by adopting a cylindrical structure of equal diameter and a grooved oil channel, enabling the mandrel 7 to maintain a stable and uniform buffering force output during the buffering process.
[0041] Improved the adaptability and durability of the buffer:
[0042] The design of the equal-diameter cylindrical structure and the grooved oil channels enables the mandrel 7 to maintain better stability and durability when facing high-energy impacts. This design also improves the buffer's adaptability to different operating conditions, allowing it to perform excellently in a wider range of applications.
[0043] In summary, the design of the mandrel 7 in this embodiment demonstrates significant innovations in terms of structure, function, and adaptability, providing new ideas and directions for the technological development in related fields.
[0044] In one implementation, see [reference] Figure 1 The groove structure is designed as several straight grooves 11. These straight grooves 11 are coaxial with the mandrel 7 and are distributed in a ring array on the outer circumferential surface of the shaft. The straight groove structure acts like straight flow channels, allowing the fluid to flow in an orderly manner in a specific direction, providing stable and direct cushioning support for the buffer.
[0045] For further details, please refer to [link / reference]. Figure 2-4 The number of linear grooves 11 decreases sequentially from the front end 9 to the rear end of the shaft. Optionally, the number decreases from a uniformly distributed 6 grooves to 2, from a uniformly distributed 4 grooves to 1, or from a uniformly distributed 7 grooves to 2, etc. This design allows for adjustment of the oil flow rate and damping effect according to buffering requirements. As the number of linear grooves 11 decreases during the movement of the spindle 7, the oil flow rate slows down, thereby achieving more precise buffering control.
[0046] In another implementation, 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 circumferential surface of the shaft, forming a grid-like pattern. The intricate mesh-like layout of the groove structure comprehensively regulates the fluid flow path, giving the damper stronger adaptability to complex working conditions and effectively improving its buffering performance while broadening its application range. This design not only increases the oil flow path but also improves the uniformity and stability of the oil flow.
[0047] For further details, please refer to [link / reference]. Figure 6 , 7 The number of mesh-shaped grooves 12 decreases sequentially from the front end 9 to the rear end of the shaft. As the spindle 7 moves, the oil flow rate slows down as the number of mesh-shaped grooves 12 decreases. This design allows for adjustment of the oil flow rate and damping effect according to buffering requirements, thereby achieving more precise buffering control.
[0048] In another alternative implementation, see [link to relevant documentation]. Figure 8The groove structure is designed as a spiral groove 13. The spiral groove 13 is evenly distributed on the outer circumference of the shaft. The spiral groove structure, like a precise spiral track, enables the fluid during the buffering process to generate a unique spiral flow, greatly optimizing the distribution of buffering force and achieving a more stable and efficient buffering effect.
[0049] For further details, please refer to [link / reference]. Figure 9 , 10 The number of spiral grooves 13 decreases sequentially 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 slows down. This design can also adjust the oil flow rate and damping effect according to the buffering requirements, providing more precise buffering control.
[0050] In an optional embodiment, in all the above embodiments, whether it is a straight 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 a fan-shaped groove 14; it can also be designed as a triangular groove, a semi-circular groove, a rectangular groove, etc.
[0051] In summary, these alternative implementations offer a variety of different groove structure designs to meet the buffering requirements of various application scenarios. By adjusting the shape, density, and distribution of the groove structure, precise control over the oil flow velocity and damping effect can be achieved, thereby improving the performance and adaptability of the buffer.
[0052] A piston-type liquid-gas buffer, with a sophisticated structure and complete functions, see reference. Figure 11 The device mainly comprises an outer sleeve 1 and a piston rod 2 assembly inserted into the left end of the outer sleeve 1. Inside the piston rod 2 assembly is a crucial isolating piston 3, which divides the internal space into two parts: the left side is a nitrogen chamber for storing nitrogen to provide cushioning force; the right side is an oil chamber for containing hydraulic oil to achieve a damping effect. At the distal end of the oil chamber, i.e., the end furthest from the isolating piston 3, is a cylinder base 4 for sealing the oil chamber and supporting the hydraulic oil within. A mandrel seat 5 is cleverly installed at the right end of the piston rod 2. This mandrel seat 5 has a precise inner hole 6 for inserting and fixing the mandrel 7 provided in this invention. The right end of the mandrel 7 is firmly connected to the cylinder base 4 at the right end of the outer sleeve 1, thus forming a stable mechanical structure. The internal space of the outer sleeve 1, together with the right end of the piston rod 2 and the left end of the cylinder base 4, forms a sealed oil chamber containing an appropriate amount of hydraulic oil to provide the necessary damping force during the cushioning process.
[0053] The above-described embodiments are only used to illustrate the technical solutions of this utility model, and are not intended to limit it. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this utility model.
Claims
1. A mandrel, comprising a shaft body (8), wherein the two sides of the shaft body (8) are a front end (9) and a rear end (10) of a shaft rod, the front end (9) of the shaft rod is connected to a mandrel seat (5), the mandrel seat (5) is provided with an inner hole (6), the inner hole (6) is sleeved on the outside of the shaft body (8), and the rear end (10) of the shaft rod is connected to a cylinder base (4), characterized in that, The shaft (8) is a cylindrical structure with equal diameter. The cylindrical structure has the same diameter as the inner hole (6) on the mandrel seat (5). The surface of the shaft (8) is provided with an oil channel with a groove structure.
2. A mandrel according to claim 1, characterized in that, The cross-section of the groove structure gradually narrows from the mandrel seat (5) to the cylinder base (4).
3. A mandrel according to claim 1, characterized in that, The groove structure consists of several straight grooves (11), which are coaxial with the mandrel (7) and are arranged in an annular array on the outer circumferential surface of the shaft.
4. A mandrel according to claim 3, characterized in that, The number of linear grooves (11) decreases sequentially from the front end (9) to the rear end of the shaft.
5. A mandrel according to claim 1, characterized in that, The groove structure is a grid-type groove (12), which is evenly distributed on the outer circumferential surface of the shaft.
6. A mandrel according to claim 5, characterized in that, The number of the grid-shaped grooves (12) decreases sequentially from the front end (9) to the rear end of the shaft.
7. A mandrel according to claim 1, characterized in that, The groove structure is a spiral groove (13), which is evenly distributed on the outer circumferential surface of the shaft.
8. A mandrel according to claim 7, characterized in that, The number of spiral grooves (13) decreases sequentially from the front end (9) to the rear end of the shaft.
9. A piston-type liquid-gas buffer, characterized in that, The device includes an outer sleeve (1) and a piston rod (2) inserted at the left end of the outer 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 chamber and the right end is an oil chamber. A cylinder base (4) is provided at the end of the oil chamber away from the isolation piston (3). A spindle seat (5) is installed at the right end of the piston rod (2). The spindle seat (5) is provided with an inner hole (6). A spindle (7) as described in any one of claims 1-8 is inserted in the inner hole (6). The right end of the spindle (7) is connected to the cylinder base (4) at the right end of the outer sleeve (1). The inner cavity of the outer sleeve (1), together with the right end of the piston rod (2) and the left end of the cylinder base (4), forms an oil chamber for containing hydraulic oil.