Fan double-bearing spring buffering structure

Abstract

The present application provides a fan double-bearing spring buffering structure, comprising: a bearing cylinder; a rotor assembly having a hub and a shaft, the hub has a central axial boss, one end of the shaft is fixedly connected to the axial boss, and the other end extends through the bearing cylinder; two bearings are arranged above and below in the bearing cylinder and sleeved with the shaft, and the inner ring of one of the bearings abuts against the axial boss; a first elastic member is arranged between the outer rings of the two bearings to have an axial spacing between the two bearings; and a second elastic member is arranged between the lower side of the inner ring of the other bearing and an inner limiting member engaged with the other end of the shaft. In this way, an elastic supporting axial force is formed, when the rotor assembly is subjected to external impact and generates an axial displacement force, the dynamic scaling of the axial spacing can guide the axial cooperative deformation of the first and second elastic members and share and dissipate energy, achieving a bidirectional elastic buffering effect.

Description

Technical Field

[0001] This invention relates to a fan buffer structure, and more particularly to a fan double-bearing spring buffer structure that absorbs axial impact by means of multiple elastic elements cooperating with bearings. Background Technology

[0002] With the booming development of the electronics industry and automotive electronics, the performance and reliability requirements of high-power chips and hermetic chassis are becoming increasingly stringent. To maintain the operational stability of the fan rotor assembly at high speeds, existing technologies typically employ a double bearing structure arranged axially opposite each other within the bearing housing to house the rotor shaft. This provides dynamic radial and axial support, ensuring that the fan can continuously perform high-efficiency fluid conduction cooling.

[0003] However, existing dual-bearing fan structures still exhibit numerous structural defects in practical applications such as transportation (vehicles, aviation, and ships) or harsh environmental testing. Please refer to... Figure 1 As shown, in the existing conventional dual-bearing structure 1 of a fan, the first bearing 12 and the second bearing 13, located within the bearing housing 11, are typically fixed together by a rigid fixing part 111 within the bearing housing 11. When subjected to extreme overload impacts such as drops, impacts, or external vibrations during transportation or assembly, the rotor assembly 14 generates enormous axial impact energy due to inertia and gravity. Because the first bearing 12 and the second bearing 13 are rigidly fixed structures without any elastic adjustment or buffering space, this enormous axial impact force is directly and rigidly transmitted to the bearing interior, causing localized abnormal wear, pitting, or even breakage of the bearing raceways and balls. Over long-term operation, this will lead to abnormal fan noise and vibration, and in severe cases, even shaft jamming and failure, significantly shortening the lifespan of the cooling system. This has become a long-standing pain point in automotive shockproof applications that the industry urgently needs to address.

[0004] Although the industry has proposed a traditional wind turbine structure using a dual-bearing, dual-spring configuration, please refer to the configuration of this prior art. It places two springs on the outer sides of two bearings (i.e., at the top of the first bearing and the bottom of the second bearing, respectively), and the two bearings are axially positioned by a rigid structure. However, because the two springs are firmly isolated by the two bearings and the intermediate rigid structure, they are independent entities in terms of the force transmission path. When the rotor assembly is subjected to extreme impact displacement in one direction (such as a downward gravitational impact), only the single spring on the affected side can absorb the pressure in an isolated, unidirectional manner; at this time, the spring on the other side, lacking a transmission coupling path, is completely in a state of idle rotation, unable to cooperate in bearing the force.

[0005] Furthermore, since all the impact energy cannot be shared by the two springs simultaneously, when the single spring is subjected to a sudden high gravitational acceleration during a drop or impact, it is very easy for it to exceed its elastic limit due to overload, or even be directly compressed to the spring dead point. Once the single-sided spring reaches its compression limit, the entire buffer structure will instantly turn into a rigid structure, allowing the subsequent residual impact force to directly and hardly strike the bearing raceway and balls without any obstruction, causing abnormal wear, pitting, or even breakage of the bearing. It is completely impossible to achieve true bidirectional elastic buffering in all postures. This structural defect is the technical bottleneck that the industry urgently needs to solve in the dual-bearing structure of fans. Summary of the Invention

[0006] To effectively solve the above-mentioned technical problems, the purpose of this invention is to address the shortcomings of existing technologies, such as the rigid fixed structure between the dual bearings of a fan lacking buffer space, and the isolated spatial layout and mechanical transmission of existing dual-spring structures lacking axial linkage mechanism. This leads to the single-sided spring being prone to overload and reaching the compression dead point when subjected to instantaneous high gravitational acceleration impact, resulting in a hard-on rigid impact, causing abnormal wear, pitting, cracking, and shortened service life of the bearing raceway and balls. Therefore, this invention provides a fan dual-bearing spring buffer structure.

[0007] To achieve the above objectives, the present invention provides a fan dual-bearing spring buffer structure, mainly comprising a first bearing and a second bearing disposed inside a bearing housing and mounted on a shaft of a rotor assembly. The rotor assembly has a hub and the shaft, with an axial boss formed at the center of the hub. One end of the shaft is connected and fixed to the axial boss, and the axial boss axially abuts against the upper end face of a first inner ring of the first bearing. The other end of the shaft extends into the bearing housing and is provided with an inner limiting member. The first bearing, located inside the bearing housing and mounted on the shaft, includes a first outer ring and a first inner ring, with one end face of the first inner ring axially abutting against the axial boss. A first elastic member is disposed on the shaft, with one end of the first elastic member abutting against... The first elastic element contacts the first outer ring of the first bearing, and the other end of the first elastic element extends away from the first bearing; a second bearing, located inside the bearing housing and mounted on the shaft, includes a second outer ring and a second inner ring, the second outer ring abutting against the other end of the first elastic element, so that the first bearing and the second bearing maintain an axial distance through the first elastic element; and a second elastic element, sleeved on the shaft, one end of the second elastic element abutting against the bottom of the second inner ring, and the other end of the second elastic element axially abutting against the inner limiting member of the shaft; wherein, the first elastic element and the second elastic element form an axially supporting force on the first bearing and the second bearing to achieve the effect of axial bidirectional elastic buffering.

[0008] The bearing sleeve has a limiting part at its top end, which axially abuts against the end face of the first outer ring.

[0009] The rotor assembly further has a plurality of fan blades arranged around the hub.

[0010] The shaft has an annular groove adjacent to the other end of the shaft, and the inner limiting member is disposed on the annular groove, so that the second elastic member is axially limited between the second inner ring of the second bearing and the inner limiting member.

[0011] The bearing cylinder has an outer limiting member on its inner wall, which is located adjacent to the bottom of the second outer ring and is used to axially limit the second outer ring.

[0012] The bearing cylinder has an annular groove on its inner wall, and the outer limiting member is embedded in the annular groove.

[0013] The improved features of this invention are applicable not only to rotor assemblies subjected to unidirectional displacement loads, but also to rotor assemblies subjected to transient, high-gravitational-acceleration axial dynamic overload impacts. When the rotor assembly generates an axial impact force relative to the bearing sleeve toward the first bearing or the second bearing, the displacement force can be transmitted through the scaling of the axial distance between the first bearing and the second bearing, and is absorbed bidirectionally by the first elastic element and the second elastic element.

[0014] In summary, the fan dual-bearing spring buffer structure of the present invention, through the axial linkage configuration of the first and second elastic elements, overcomes the technical bottlenecks of existing technologies where the dual bearings are rigidly fixed and lack buffer space, and where the isolated configuration of the dual springs in the previous invention is prone to overload and hard impact. The present invention not only provides excellent bidirectional synergistic buffering when the fan is subjected to extreme impacts in all postures by dynamically scaling the axial distance between the two bearings, but also maintains a constant and high-precision displacement preload under normal conditions, and completely eliminates physical interference during the extension and contraction of the elastic elements. Attached Figure Description

[0015] Figure 1 This is a cross-sectional schematic diagram of an existing fan with dual bearings.

[0016] Figure 2 This is a schematic cross-sectional view of the combined fan dual-bearing spring buffer structure of the present invention.

[0017] Figure 3 This is a schematic diagram illustrating the operation of the fan dual-bearing spring buffer structure of the present invention under axial impact.

[0018] Explanation of reference numerals in the attached drawings: Fan dual-bearing spring buffer structure -2; Bearing cylinder -20; Limiting part -201; Annular slot -202; Outer limiting member -203; Rotor assembly -21; Hub -210; Shaft -211; Axial boss -212; Annular groove -213; Fan blade -214; First bearing -22; First outer ring -221; First inner ring -222; First elastic member -23; Second bearing -24; Second outer ring -241; Second inner ring -242; Second elastic member -25; Inner limiting member -251. Detailed Implementation

[0019] The above-mentioned objectives of the present invention and its structural and functional characteristics will be described with reference to the preferred embodiments shown in the accompanying drawings.

[0020] Please see Figure 2 As shown, it is a combined cross-sectional schematic diagram of the fan dual bearing spring buffer structure of the present invention. As shown in the figure, the present invention provides a fan dual bearing spring buffer structure 2, including: a bearing cylinder 20, a rotor assembly 21, a first bearing 22, a first elastic element 23, a second bearing 24 and a second elastic element 25.

[0021] The bearing cylinder 20 has an axially extending accommodating space inside, and a limiting portion 201 extending radially towards the center is formed at the top of the inner wall surface of the bearing cylinder 20. The rotor assembly 21 includes a hub 210, a plurality of fan blades 214 disposed around the hub 210, and a shaft 211. An axial boss 212 is formed at the center of the hub 210, which is an axially protruding portion at the center of the hub 210. One end of the shaft 211 is a fixed end and is connected and fixed to the axial boss 212, while the other end is a free end that passes through the accommodating space of the bearing cylinder 20, and an annular groove 213 is recessed on the peripheral wall surface adjacent to the free end.

[0022] The first bearing 22 and the second bearing 24 are sequentially arranged from top to bottom within the receiving space of the bearing cylinder 20 and are together sleeved on the outer periphery of the shaft 211 of the rotor assembly 21. The first bearing 22 has a first outer ring 221 and a first inner ring 222. The top surface of the first outer ring 221 axially abuts against the limiting portion 201 of the bearing cylinder 20, while the top surface of the first inner ring 222 axially abuts against the axial boss 212 at the center of the hub 210. The first elastic member 23 is sleeved on the outer periphery of the shaft 211 and sandwiched between the first bearing 22 and the second bearing 24. One end of the first elastic member 23 abuts against the bottom end surface of the first outer ring 221 of the first bearing 22, and the other end of the first elastic member 23 extends away from the first bearing 22 and directly abuts against the second bearing 24 axially. The second bearing 24 has a second outer ring 241 and a second inner ring 242. The other end of the first elastic member 23 abuts against the top surface of the second outer ring 241, so that the first bearing 22 and the second bearing 24 maintain an axial distance by means of the support of the first elastic member 23.

[0023] The second elastic member 25 is sleeved on the outer periphery of the shaft 211 of the rotor assembly 21, and one end face of the second elastic member 25 axially abuts against the bottom end face of the second inner ring 242 of the second bearing 24. An inner limiting member 251 (e.g., a retaining ring, protrusion, or bolt) is fastened to the annular groove 213 of the shaft 211. The inner limiting member 251 is located below the second elastic member 25, allowing the other end face of the second elastic member 25 to axially abut against the inner limiting member 251, and the inner limiting member 251 is securely assembled in the annular groove 213 of the shaft 211. Under normal conditions, the axial elastic force released by the second elastic member 25 can be transmitted to the second inner ring 242 of the second bearing 24 through the inner limiting member 251, maintaining the first inner ring 222 and the second inner ring 242 in a pre-compression position axially, providing a constant displacement preload for the overall structure. In addition, the inner wall of the bearing cylinder 20 is further provided with an annular groove 202, and an outer limiting member 203 (e.g., a retaining ring) is embedded in the annular groove 202. The outer limiting member 203 is adjacent to the bottom of the second outer ring 241 and is used to axially limit and block the second outer ring 241.

[0024] Please see Figure 3As shown, this illustrates an embodiment of the invention. When the rotor assembly 21 generates an axial displacement force relative to the bearing cylinder 20 toward the second bearing 24, for example, due to a transient downward fall, vibration, or impact causing the shaft 211 to axially move away from the limiting portion 201, the shaft 211 will drive the inner limiting member 251, which is assembled in the annular groove 213, to simultaneously move toward the bottom side of the second bearing 24. Since the second elastic member 25 is disposed between the second inner ring 242 and the inner limiting member 251, the axial displacement of the inner limiting member 251 will cause the second elastic member 25 to undergo axial elastic deformation, thereby absorbing part of the axial impact energy transmitted from the shaft 211. On the other hand, the second outer ring 241 of the second bearing 24 is elastically supported by the first elastic member 23 and can generate a slight axial adjustment within the axial distance formed between the first bearing 22 and the second bearing 24. When the second outer ring 241 is displaced toward the outer limiting member 203 and is axially limited by the outer limiting member 203, the outer limiting member 203 can serve as a stop reference for the second outer ring 241, so that the first elastic member 23 and the second elastic member 25 form corresponding elastic reaction forces on the outer ring side and the inner ring side, respectively. In this way, the inertial force generated by the downward axial impact will not directly and rigidly concentrate on a single bearing, but can be dispersed, buffered and dissipated through the axial mechanical path formed by the inner limiting member 251, the second elastic member 25, the second bearing 24, the first elastic member 23 and the outer limiting member 203, thereby reducing the risk of the first bearing 22 and the second bearing 24 being subjected to instantaneous hard impact.

[0025] Furthermore, when the rotor assembly 21 generates an axial displacement force relative to the bearing cylinder 20 toward the first bearing 22, the axial boss 212 formed at the center of the hub 210 provides an axial pushing force to the first inner ring 222 of the first bearing 22, causing a corresponding change in the axial distance between the first bearing 22, the first elastic member 23, and the second bearing 24; at the same time, the shaft 211 also provides relative elastic support to the second inner ring 242 through the inner limiting member 251 and the second elastic member 25, so that the first elastic member 23 and the second elastic member 25 can form cooperative elastic deformation on the outer ring side and the inner ring side of the two bearings, respectively. In other words, the present invention does not isolate the two elastic elements on the outside of the two bearings, but rather uses the first elastic element 23 disposed between the first outer ring 221 and the second outer ring 241, and the second elastic element 25 disposed between the second inner ring 242 and the inner limiting element 251, to create a dynamically scalable axial distance between the first bearing 22 and the second bearing 24, and to form an axially elastic support relationship between the outer ring side and the inner ring side that can cooperate with each other. Therefore, regardless of whether the rotor assembly 21 generates axial impact displacement toward the first bearing 22 or toward the second bearing 24, the impact energy can be dispersed and absorbed along the continuous mechanical path formed by the bearing sleeve 20, the first bearing 22, the first elastic element 23, the second bearing 24, the second elastic element 25, and the shaft 211, thereby achieving bidirectional elastic buffering and reducing the possibility of axial movement, abnormal noise, wear, or bearing damage when the rotor assembly 21 operates at high speed or is subjected to external impact.

Claims

1. A fan dual-bearing spring buffer structure, characterized in that, include: One bearing sleeve; A rotor assembly has a hub and a shaft. An axial boss is formed at the center of the hub. One end of the shaft is connected and fixed to the axial boss, and the other end of the shaft extends into the bearing sleeve and is provided with an inner limiting member. A first bearing is located inside the bearing housing and mounted on the shaft. It includes a first outer ring and a first inner ring. One end face of the first inner ring is axially abutted by the axial boss. A first elastic element is sleeved on the shaft, one end of the first elastic element abuts against the first outer ring of the first bearing, and the other end of the first elastic element extends away from the first bearing; A second bearing, located within the bearing housing and mounted on the shaft, includes a second outer ring and a second inner ring. The second outer ring abuts against the other end of the first elastic member, thereby maintaining an axial distance between the first bearing and the second bearing by the first elastic member; and A second elastic element is sleeved on the shaft, with one end of the second elastic element abutting the bottom of the second inner ring and the other end of the second elastic element axially abutting the inner limiting element of the shaft. The first and second elastic elements form an axial force that provides elastic support on the first and second bearings, thereby achieving a bidirectional elastic buffering effect.

2. The fan dual-bearing spring buffer structure as described in claim 1, characterized in that, The bearing sleeve has a limiting part at its top end, which axially abuts against the end face of the first outer ring.

3. The fan dual-bearing spring buffer structure as described in claim 1, characterized in that, The rotor assembly also has a plurality of fan blades arranged around the hub.

4. The fan dual-bearing spring buffer structure as described in claim 1, characterized in that, The shaft has an annular groove adjacent to the other end of the shaft, and the inner limiting member is provided on the annular groove, so that the second elastic member is axially limited between the second inner ring of the second bearing and the inner limiting member.

5. The fan dual-bearing spring buffer structure as described in claim 1, characterized in that, The inner wall of the bearing cylinder is provided with an outer limiting member, which is adjacent to the bottom of the second outer ring and is used to axially limit the second outer ring.

6. The fan dual-bearing spring buffer structure as described in claim 5, characterized in that, The inner wall of the bearing cylinder is provided with an annular groove, and the outer limiting member is embedded in the annular groove.

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