Axial-radial two-way stress heavy-load bearing seat structure for impeller

Abstract

The invention is applicable to the technical field of impeller bearing seats, and provides a shaft-diameter bidirectional stress heavy-load bearing seat structure for an impeller, which comprises a fan bearing seat, a bearing seat, a bearing seat and a bearing seat, the axial thrust bearing, the thrust washer and the radial bearing are sequentially mounted in the bearing mounting cavity, axial force and radial force of the impeller rotating shaft are borne through the layered bearing design, and the combined load resisting capacity is remarkably improved. According to the lubricating system, an oil main hole is communicated with a spiral condenser pipe, high-temperature lubricating oil is forcibly cooled in cooperation with heat dissipation fins, an independent vaporization channel is arranged at the position of a bearing with large local heat productivity through fan-shaped oil evaporation holes in the inner wall of a bearing installation cavity, friction temperature rise is effectively reduced, and the service life of the bearing is prolonged. The bearing seat solves the problems that a traditional bearing seat is easy to wear and fails in lubrication under high-speed and heavy-load working conditions, has the advantages of high bearing capacity, high heat dissipation efficiency, convenience in maintenance and the like, and is suitable for high-power equipment such as a negative-pressure fan of a sanitation vehicle.

Description

Technical Field

[0001] The present invention is applicable to the technical field of impeller bearing seats, and provides a heavy-duty bearing seat structure for an impeller that is subjected to bidirectional force in both the axial and radial directions. Background Art

[0002] In the structure of sanitation vehicles, the dust collection module usually uses a negative pressure fan to achieve a high-power dust collection function. The impeller of the negative pressure fan is generally a fan blade curved surface structure. During its rotation, the force is relatively complex and it needs to withstand the axial force and radial force of the constantly changing load at the same time. The ordinary bearing seat structure generally uses multiple ball bearings as the rotary support of the impeller shaft. Conventional ball bearings can only withstand radial forces, and the axial force generated by the rotation of the impeller shaft due to the fan impeller can only be borne by structures such as limit steps. During long-term use, the connection positions of various components are prone to wear, which eventually leads to various problems such as axial movement and radial runout of the rotating shaft, seriously affecting the service life of the impeller shaft. In actual use, it is generally necessary to inject lubricating oil into the bearing seat to ensure the smooth operation of the impeller shaft, but at the same time, the impeller shaft will generate a lot of heat during continuous high-speed rotation, which will cause the lubricating oil temperature to be too high, especially at the connection positions with bearings, etc., and may even cause the lubricating oil to vaporize at high temperature, greatly affecting the lubrication performance. Summary of the Invention

[0003] To this end, the present invention provides a heavy-duty bearing seat structure with bidirectional force on the shaft diameter for the impeller, which bears the radial force during the operation of the impeller shaft through the radial bearing, and bears the axial force during the operation of the impeller shaft through the axial thrust bearing. At the same time, a condenser is arranged at the upper end of the fan bearing seat to cool and liquefy the vaporized lubricating oil, thereby improving the lubrication effect.

[0004] In order to achieve the above-mentioned object, the present invention provides the following technical solution: a heavy-duty bearing seat structure for an impeller with bidirectional force on the shaft diameter, comprising:

[0005] A fan bearing seat, wherein a lubrication cavity is provided at the center of the interior of the fan bearing seat, and bearing mounting cavities are respectively provided on the left and right sides of the lubrication cavity. The two bearing mounting cavities extend from the left and right sides of the lubrication cavity to the left and right ends of the fan bearing seat, respectively. An axial thrust bearing, a thrust washer, and a radial bearing are sequentially provided in the two bearing mounting cavities from one side of the lubrication cavity to one side of the end of the fan bearing seat;

[0006] An impeller shaft is disposed in the fan bearing seat, with both ends of the impeller shaft extending beyond the left and right ends of the fan bearing seat. The impeller shaft passes through the left bearing mounting cavity, the lubrication cavity, and the right bearing mounting cavity from left to right in sequence. The axial thrust bearing, the thrust washer, and the radial bearing in the bearing mounting cavity are all mounted on the impeller shaft.

[0007] Two side end covers are fixedly mounted on the left and right ends of the fan bearing seat, respectively, and the end of the side end cover facing the fan bearing seat abuts against the radial bearing;

[0008] The impeller mechanism and the rotating shaft driving wheel are respectively fixedly installed on the left and right ends of the impeller rotating shaft.

[0009] Furthermore, a main oil hole is provided at the top of the lubrication cavity, and both ends of the main oil hole are connected to the lubrication cavity and the outside of the fan bearing seat.

[0010] Furthermore, the upper end of the oil main hole is connected to a condensing device, which includes a condensing pipe, and the condensing pipe is connected to the oil main hole.

[0011] Furthermore, a plurality of oil evaporation holes are provided on the upper portion of the inner side wall of the bearing mounting cavity. The plurality of oil evaporation holes are arranged in a fan shape, and the oil evaporation holes are connected to the oil main hole through an oil evaporation pipeline.

[0012] Furthermore, the condenser tube is a spiral coil structure that rises in a spiral, and a plurality of heat dissipation fins are fixedly provided on the outside of the condenser tube.

[0013] Furthermore, an oil discharge hole is provided at the bottom of the lubrication cavity, and an oil drain plug is installed in the oil discharge hole.

[0014] Furthermore, a cursor is provided on the side of the lubrication cavity.

[0015] Furthermore, at least one lip seal ring is installed on the shaft section of the impeller shaft located at the side end cover position.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] 1. The solution of the present invention uses two sets of axial thrust bearings and radial bearings arranged on opposite sides to simultaneously withstand the variable load axial and radial forces of the impeller shaft under high-speed rotation conditions. Compared with the traditional single-bearing structure, it has a greater load capacity, can effectively reduce the wear rate of the impeller shaft, and improve operational stability and service life;

[0018] 2. A condenser is connected to the upper end of the main oil hole. At the same time, a number of oil evaporation holes are set on the upper part of the inner wall of the bearing installation cavity with greater heat generation and connected to the condenser. The condenser is used to condense and recover the lubricating oil vaporized by heat inside the fan bearing seat to prevent the oil temperature from being too high and ensure the lubrication effect under continuous high-speed working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 This is a structural schematic diagram of a heavy-duty bearing seat structure for an impeller with a bidirectional load bearing for the shaft diameter mentioned in the present invention;

[0020] Figure 2 for Figure 1 Schematic diagram of the assembly structure between the various components inside the bearing seat of the wind turbine;

[0021] Figure 3 This is a schematic cross-sectional view of the internal structure of a heavy-duty bearing seat structure for an impeller with bidirectional loads, as mentioned in the present invention;

[0022] Figure 4 Schematic diagram of the internal structure of the fan bearing seat mentioned in the present invention;

[0023] Figure 5 It is a structural schematic diagram of the condensing device mentioned in the present invention.

[0024] In the picture:

[0025] 100, fan bearing seat, 110, lubrication chamber, 120, oil main hole, 130, oil unloading hole, 140, oil drain plug, 150, bearing mounting chamber, 160, oil evaporation hole, 170, oil evaporation pipeline, 180, cursor;

[0026] 200, impeller shaft;

[0027] 300, axial thrust bearing;

[0028] 400, thrust washer;

[0029] 500, radial bearing;

[0030] 600, side end cap;

[0031] 700, condensing device, 710, condensing tube, 720, cooling fins;

[0032] 800, impeller mechanism;

[0033] 900. Rotating shaft drive wheel. DETAILED DESCRIPTION

[0034] The preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are only used to illustrate and explain the present invention, and are not used to limit the present invention.

[0035] For example, see the attached Figure 1As shown, the present invention provides a shaft diameter bidirectional force heavy-duty bearing seat structure for an impeller, including a fan bearing seat 100, an impeller shaft 200 is arranged in the fan bearing seat 100, and both ends of the impeller shaft 200 are arranged beyond the left and right ends of the fan bearing seat 100, and an impeller mechanism 800 and a shaft driving wheel 900 are fixedly installed at both ends of the impeller shaft 200. During actual operation, the power source drives the shaft driving wheel 900 to rotate through a chain sprocket or a pulley mechanism, and then transmits power to the impeller mechanism 800 through the impeller shaft 200, as shown in the attached figure. Figure 4 As shown, a lubrication cavity 110 is provided at the center of the fan bearing seat 100, and bearing mounting cavities 150 are provided on the left and right sides of the lubrication cavity 110 respectively. The two bearing mounting cavities 150 extend from the left and right sides of the lubrication cavity 110 to the left and right ends of the fan bearing seat 100 respectively. An oil main hole 120 is provided at the top of the lubrication cavity 110. The two ends of the oil main hole 120 are connected to the lubrication cavity 110 and the outside of the fan bearing seat 100. The lubrication cavity 110 is provided with a lubrication cavity 110. 0 is provided with an oil discharge hole 130 at the bottom, and an oil drain plug 140 is installed in the oil discharge hole 130. A cursor 180 is provided on the side of the lubrication cavity 110. The lubrication cavity 110 is mainly used to store the engine oil and other lubricating grease injected from the oil main hole 120. The oil discharge hole 130 can quickly drain the old oil when the lubricating oil is replaced, reducing downtime. The cursor 180 intuitively displays the oil level, which is convenient for regular replenishment of lubricating oil. The lubrication cavity 110 is connected to the left and right bearing mounting cavities 150. Figure 2 , Attachment Figure 3As shown, the two bearing mounting cavities 150 are sequentially provided with an axial thrust bearing 300, a thrust washer 400 and a radial bearing 500 from one side of the lubrication cavity 110 to one side of the end of the fan bearing seat 100. Among them, one side of the axial thrust bearing 300 abuts against the bottom of the bearing mounting cavity 150, and the other side abuts against the thrust washer 400, while the other side of the thrust washer 400 abuts against the inner ring of the radial bearing 500, forming a stepped load-bearing structure. Lubricating grease can be filled from the gap between the three structures to the entire bearing mounting cavity 150. 0, and the impeller shaft 200 passes through the bearing mounting cavity 150 on the left, the lubrication cavity 110 and the bearing mounting cavity 150 on the right from left to right. At the same time, the axial thrust bearing 300, the thrust washer 400 and the radial bearing 500 in the bearing mounting cavity 150 are all installed on the impeller shaft 200. Specifically, the radial bearing 500 adopts a deep groove ball bearing. The impeller shaft 200 is respectively matched with the shaft ring of the axial thrust bearing 300, the inner ring of the thrust washer 400 and the inner ring of the radial bearing 500. When the impeller rotates The airflow will generate axial thrust, which is mainly borne by the axial thrust bearing 300. The radial load caused by the weight of the impeller shaft 200 and the centrifugal force of the impeller mechanism 800 is borne by the radial bearing 500. The axial thrust bearing 300 and the radial bearing 500 are arranged in layers. The axial and radial loads are borne by different bearings to avoid composite stress concentration. This structure avoids the early fatigue of the traditional single bearing caused by composite loads and significantly improves its service life. The left and right ends of the fan bearing seat 100 are respectively fixed with side end covers 600. The side end covers The end portion of 600 facing the fan bearing seat 100 abuts against the radial bearing 500 to provide axial preload. The side end cap 600 generally applies axial compression through bolts to eliminate bearing clearance and reduce vibration during high-speed operation. At least one lip seal is installed on the shaft section of the impeller shaft 200 located at the side end cap 600 (in this embodiment, two lip seals are used to improve sealing effect and fault tolerance). The lip seal is tightly attached to the impeller shaft 200 through an elastic lip, effectively preventing lubricating oil from escaping and external dust from entering.

[0036] In some of these embodiments, as shown in the attached Figure 3 , Attachment Figure 5As shown, the upper end of the oil main hole 120 is connected to a condensing device 700, and the condensing device 700 includes a condensing tube 710, which is connected to the oil main hole 120. The condensing tube 710 is a spirally rising spiral coil structure, and a number of heat dissipation fins 720 are fixedly provided on the outside of the condensing tube 710. At the same time, in order to further improve the condensation effect, a number of oil evaporation holes 160 are provided on the upper part of the inner wall of the bearing mounting cavity 150. The oil evaporation holes 160 are arranged in a fan shape. The oil evaporation holes 160 are connected to the oil main hole 120 through an oil evaporation pipeline 170. After the high-temperature lubricating oil is vaporized, it will enter the condensing tube 710 in two ways. One is The oil enters the condenser 710 directly through the main oil hole 120 at the upper end of the lubrication cavity 110, and then enters the main oil hole 120 through the oil evaporation hole 160 via the oil evaporation pipeline 170 and then flows into the condenser 710. The heat is then dissipated by forced convection with the air through the heat dissipation fins 720, and returns to the cavity after cooling. The arrangement of several oil evaporation holes 160 on the upper part of the inner wall of the bearing mounting cavity 150 can meet the cooling effect of the lubricating oil in these high-heating positions of the bearing. The spiral coil design increases the oil residence time and expands the heat dissipation area while maintaining a lower overall height of the condenser 710. Combined with the heat dissipation fins 720, the condensation effect is greatly improved.

[0037] The solution of this embodiment has at least the following innovative features:

[0038] 1. The axial / radial bearing 500 split layout solves the problem of heavy-load composite stress;

[0039] 2. Oil mist lubrication + condensation cycle to achieve zero overheating protection.

[0040] Compared with traditional solutions currently on the market, it has significant advantages and, after small-scale testing, has good commercial prospects.

[0041] In the description of the present invention, it is necessary to understand that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention. The directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0042] The above are merely preferred embodiments of the present invention. Anyone skilled in the art may utilize the above-described technical solutions to modify the present invention or modify them into equivalent technical solutions. Therefore, any simple modification or equivalent replacement based on the technical solutions of the present invention falls within the scope of protection claimed by the present invention.

Claims

1. A heavy-duty bearing seat structure for an impeller with bidirectional load bearing for the shaft diameter, characterized in that: include: A fan bearing seat (100), wherein a lubrication cavity (110) is provided at a central position inside the fan bearing seat (100), and bearing mounting cavities (150) are respectively provided on the left and right sides of the lubrication cavity (110), and the two bearing mounting cavities (150) extend from the left and right sides of the lubrication cavity (110) to the left and right ends of the fan bearing seat (100), and an axial thrust bearing (300), a thrust washer (400) and a radial bearing (500) are sequentially provided in the two bearing mounting cavities (150) from one side of the lubrication cavity (110) to one side of the end of the fan bearing seat (100); An impeller shaft (200) is arranged in the fan bearing seat (100), and both ends of the impeller shaft (200) are arranged beyond the left and right ends of the fan bearing seat (100). The impeller shaft (200) passes through the left bearing mounting cavity (150), the lubrication cavity (110), and the right bearing mounting cavity (150) in sequence from left to right. The axial thrust bearing (300), the thrust washer (400), and the radial bearing (500) in the bearing mounting cavity (150) are all installed on the impeller shaft (200); Two side end covers (600) are fixedly mounted on the left and right ends of the fan bearing seat (100), respectively, and the end of the side end cover (600) facing the fan bearing seat (100) abuts against the radial bearing (500); The impeller mechanism (800) and the rotating shaft driving wheel (900) are respectively fixedly mounted on the left and right ends of the impeller rotating shaft (200).

2. The heavy-duty bearing seat structure for an impeller with bidirectional load bearing for the impeller according to claim 1, characterized in that: An oil main hole (120) is provided at the top of the lubricating cavity (110), and both ends of the oil main hole (120) are in communication with the lubricating cavity (110) and the outside of the fan bearing seat (100).

3. The heavy-duty bearing seat structure for an impeller with bidirectional load bearing for the shaft diameter according to claim 2, characterized in that: The upper end of the oil main hole (120) is connected to a condensing device (700), and the condensing device (700) includes a condensing pipe (710), and the condensing pipe (710) is in communication with the oil main hole (120).

4. The heavy-duty bearing seat structure for an impeller with bidirectional load bearing for the shaft diameter according to claim 3, characterized in that: A plurality of oil evaporation holes (160) are provided on the upper portion of the inner side wall of the bearing mounting cavity (150), the plurality of oil evaporation holes (160) are arranged in a fan shape, and the oil evaporation holes (160) are connected to the oil main hole (120) via an oil evaporation pipeline (170).

5. The heavy-duty bearing seat structure for an impeller with bidirectional load bearing for the shaft diameter according to claim 4, characterized in that: The condenser tube (710) is a spiral coil structure that rises in a spiral, and a plurality of heat dissipation fins (720) are fixedly provided on the outside of the condenser tube (710).

6. A heavy-duty bearing seat structure for an impeller with bidirectional loads according to any one of claims 1 to 5, characterized in that: An oil discharge hole (130) is provided at the bottom of the lubrication cavity (110), and an oil discharge plug (140) is installed in the oil discharge hole (130).

7. The heavy-duty bearing seat structure for an impeller with bidirectional load bearing for the shaft diameter according to claim 6, characterized in that: A cursor (180) is provided on the side of the lubrication cavity (110).

8. The heavy-duty bearing seat structure for an impeller with bidirectional loads according to claim 7, characterized in that: At least one lip seal ring is installed on the shaft section of the impeller shaft (200) located at the side end cover (600).

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