Shaft fan bearing box vibration temperature cooperative control method and bearing box thereof

Abstract

The invention relates to the technical field of steam turbine auxiliary equipment control technologies, in particular to a vibration temperature cooperative control method for a bearing box of a shaft fan and the bearing box of the bearing box. A light-weight impeller of the shaft fan is adopted, dynamic balance correction is conducted on the light-weight impeller, and a shell of the bearing box is arranged on a mounting surface; two sets of rolling bearings are arranged in the bearing box shell, a lubricating sealing assembly is arranged on the bearing box shell, an impeller is connected to the output end of the bearing box shell, a cooling system is arranged on the bearing box shell, and when the temperature of the bearing box shell or the temperature of the rolling bearings in the bearing box shell exceeds a second set value, the cooling system is started. The cooling system is started to cool the bearing box shell or the rolling bearing, automatic closed-loop control over the temperature of the rolling bearing and the temperature of the bearing box is achieved, and the technical problems that vibration of an existing shaft adding fan exceeds the standard, bearing faults occur frequently, effective cooling is lacked, and the maintenance cost is high are solved.

Description

Technical Field

[0001] This invention relates to the field of turbine auxiliary equipment control technology, and in particular to a method for coordinated control of vibration and temperature of shaft-driven fan bearing housings and the bearing housing thereof. Background Technology

[0002] The shaft seal heater fan (hereinafter referred to as the shaft seal fan) is a key piece of equipment in the auxiliary system of steam turbines in thermal power plants. Its main function is to maintain a slight negative pressure in the shaft seal extraction condenser, ensuring that shaft seal steam does not leak and that outside air does not intrude, thereby ensuring the tightness of the turbine vacuum and the stable operation of the unit. The operational stability of the shaft seal fan directly determines the operational reliability of the entire turbine shaft seal system. Once the shaft seal fan fails and shuts down, it can easily lead to serious problems such as shaft seal steam leakage, turbine lubricating oil emulsification, and condenser vacuum failure, affecting the normal operation of the unit.

[0003] In existing technologies, shaft-mounted fans generally suffer from two major technical problems during operation, severely restricting their operational stability and failing to be resolved synergistically through single improvements: First, the impeller mass is too large, easily generating significant unbalanced inertial forces during high-speed rotation, leading to severe impeller vibration with excessive amplitude, which in turn causes a chain reaction of failures such as bearing wear and bearing housing cracking. Simultaneously, the existing impeller dynamic balancing correction accuracy is insufficient, failing to precisely control residual imbalance based on actual impeller operating parameters, further exacerbating the vibration problem. Second, the assembly precision of the rolling bearings within the bearing housing is insufficient, resulting in large coaxiality errors and imperfect lubrication and sealing structures, easily leading to lubrication failure and seal leakage. Cooling systems are mostly passive, unable to automatically start and stop based on bearing and bearing housing temperature changes. When the bearings generate a large amount of heat during high-speed operation, untimely cooling leads to excessive bearing temperature, causing bearing burnout and severely affecting the continuous and stable operation of the shaft-mounted fan. Summary of the Invention

[0004] This invention provides a method for coordinated control of vibration and temperature of bearing housing in shaft-driven fans and a bearing housing thereof, which is used to solve at least one of the above-mentioned technical problems.

[0005] A method for coordinated control of vibration and temperature in the bearing housing of a shaft-driven fan includes the following steps: S100 adopts a lightweight shaft and fan impeller, and performs dynamic balancing on the lightweight impeller to suppress impeller vibration during operation; S200: The bearing housing is mounted on the mounting surface, and two sets of rolling bearings are installed inside the bearing housing. S300. Install a lubrication and sealing assembly on the bearing housing, and connect the impeller that has been dynamically balanced in step S100 to the output end of the bearing housing. Connect the input end of the bearing housing to the drive motor through a flexible coupling. S400: The cooling system is installed on the bearing housing. When the temperature of the bearing housing or the rolling bearing inside the bearing housing exceeds the second set value, the cooling system is activated to cool the bearing housing or the rolling bearing.

[0006] In one embodiment, in step S100, a shaft-driven fan impeller rotor with a balance accuracy level of the first set value is selected, and the maximum residual imbalance of the impeller is calculated using the formula m=(G×10000×M) / (n×r), where G is the balance accuracy level of the shaft-driven fan impeller rotor, M is the impeller mass, n is the impeller speed, and r is the impeller radius; a dynamic balancing machine is used to perform dynamic balancing correction on the impeller to ensure that its residual imbalance is not greater than the maximum residual imbalance.

[0007] In one embodiment, in step S400, the cooling pipes in the cooling system are metal heat pipes, which are tightly fitted to or embedded in the heat-generating area of ​​the bearing housing. The circulating cooling loop in the cooling system is equipped with an electronically controlled valve and a temperature detection element. The temperature detection element is fitted to the bearing housing, and both the electronically controlled valve and the temperature detection element are electrically connected to the central control system.

[0008] In one embodiment, the temperature detection element collects temperature data of the bearing housing and rolling bearing in real time and transmits it to the central control system. The central control system compares the temperature data with a second set value. When the temperature data is greater than the second set value, the central control system controls the electronic control valve to open, and the cooling water circulates in the circulating cooling circuit to cool the bearing housing and / or rolling bearing through heat conduction. When the temperature data is not greater than the second set value, the central control system controls the electronic control valve to close and stop cooling.

[0009] In one embodiment, the cooling water is room temperature water, the cooling water temperature is not greater than 30°C, and the flow velocity of the cooling water in the cooling pipe is 0.8m / s-1.2m / s.

[0010] In one embodiment, in step S300, the rolling bearing is first assembled into the bearing housing and the coaxiality error of the rolling bearing assembly is controlled. Then, the lubricating medium in the lubrication sealing assembly is added into the bearing housing to form a composite lubrication of oil bath lubrication and splash lubrication. The double-layer sealing structure in the lubrication sealing assembly is used to seal the bearing housing, and the air pressure balancing operation is performed simultaneously to balance the air pressure inside and outside the bearing housing.

[0011] In one embodiment, the method further includes step S500: performing no-load and load testing on the shaft-mounted fan; starting the shaft-mounted fan to perform no-load testing, monitoring the vibration amplitude of the bearing housing, the lubrication and sealing status, and the cooling system status; then starting the shaft-mounted fan to perform load testing, continuously monitoring the rolling bearing temperature and the vibration amplitude of the bearing housing until the rolling bearing temperature is no greater than 40°C, the horizontal vibration amplitude of the bearing housing is no greater than 0.01 mm, and the vertical vibration amplitude of the bearing housing is no greater than 0.02 mm, thus completing the no-load and load testing.

[0012] In one embodiment, the vibration amplitude of the bearing housing is monitored by arranging eddy current vibration sensors in the horizontal and vertical directions of the bearing housing, respectively, and collecting the vibration amplitude data of the bearing housing at a fixed monitoring frequency.

[0013] In one embodiment, the coaxiality error between the rolling bearing and the bearing housing is no greater than 0.02 mm.

[0014] A shaft-mounted fan bearing housing, comprising: The bearing housing contains a transmission mechanism. Rolling bearings, which are installed inside the bearing housing; The cooling system is mounted on the bearing housing and is electrically connected to the central control system.

[0015] Beneficial effects: Compared with existing technologies, the advantages of this invention are as follows: By lightweighting and precisely balancing the impeller of the shaft-mounted fan, a stable rigid support for the shaft system is constructed by combining the bearing housing and rolling bearings. Reliable operation of the rolling bearings is ensured through composite lubrication and sealing. Simultaneously, real-time cooling is achieved through a cooling system. Temperature detection elements collect the rolling bearing temperature and bearing housing temperature in real time and control the on / off state of the cooling circuit, realizing automatic closed-loop control of the rolling bearing temperature. After assembly and no-load and load testing, the vibration amplitude and bearing temperature of the shaft-mounted fan are stabilized within a preset range. This fundamentally solves the technical problems of excessive vibration, frequent bearing failures, lack of effective cooling, and high maintenance costs in existing shaft-mounted fans. It significantly improves the operational stability and reliability of the shaft-mounted fan, extends the service life of components, and reduces maintenance costs. Attached Figure Description

[0016] The invention will now be described in more detail with reference to embodiments and the accompanying drawings.

[0017] Figure 1 This is a schematic diagram of the structure of the shaft-added fan bearing housing of the present invention. Detailed Implementation

[0018] The technical solution of the present invention will be clearly and completely described below with reference to the embodiments. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0019] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

[0020] As described in the background section, existing shaft-mounted fans generally suffer from two major technical problems during operation, severely restricting their operational stability and failing to be resolved through a single improvement: First, the impeller mass is too large, easily generating significant unbalanced inertial forces during high-speed rotation, leading to severe impeller vibration with excessive amplitude, which in turn causes a chain reaction of failures such as bearing wear and bearing housing cracking. Simultaneously, the existing impeller dynamic balancing correction accuracy is insufficient, failing to precisely control residual imbalance based on actual impeller operating parameters, further exacerbating the vibration problem. Second, the rolling bearings within the bearing housing have insufficient assembly precision, resulting in large coaxiality errors and imperfect lubrication and sealing structures, easily leading to lubrication failure and seal leakage. The cooling system is mostly passive, unable to automatically start and stop based on bearing and bearing housing temperature changes. When the bearing generates a large amount of heat during high-speed operation, untimely cooling causes the bearing temperature to exceed the limit, leading to bearing burnout and severely affecting the continuous and stable operation of the shaft-mounted fan.

[0021] To address the above problems, this invention provides a method for coordinated control of vibration and temperature in the bearing housing of a shaft-driven fan, comprising the following steps: S100 adopts a lightweight shaft and fan impeller, and performs dynamic balancing on the lightweight impeller to suppress impeller vibration during operation; S200: The bearing housing is mounted on the mounting surface, and two sets of rolling bearings are installed inside the bearing housing. S300. Install a lubrication and sealing assembly on the bearing housing, and connect the impeller that has been dynamically balanced in step S100 to the output end of the bearing housing. Connect the input end of the bearing housing to the drive motor through a flexible coupling. S400: The cooling system is installed on the bearing housing. When the temperature of the bearing housing or the rolling bearing inside the bearing housing exceeds the second set value, the cooling system is activated to cool the bearing housing or the rolling bearing.

[0022] Specifically, existing bearing housings typically use 6208 bearings, which have low load-bearing capacity matching, lack an active cooling system, and have no quantitative standards for impeller dynamic balancing. This invention first reduces the weight of the impeller by optimizing the impeller blade structure and replacing the original cast iron material with high-strength lightweight alloy materials, lowering the impeller weight from 25kg to 18kg. This significantly reduces the moment of inertia during high-speed rotation, structurally reducing the generation of unbalanced inertial forces. Then, the lightweight impeller undergoes high-precision dynamic balancing correction using a standardized balancing precision control system to suppress impeller vibration at its source. Finally, the bearing housing and rolling bearings are assembled. The rolling bearings used are 6310 bearings, eliminating the design lacking independent bearing support found in existing technologies.

[0023] Furthermore, by constructing a rigid mounting surface and assembling high-load-bearing rolling bearings, a stable rigid support structure for the shaft system is built, solving the vibration amplification problem caused by excessive length and insufficient rigidity of the shaft-driven fan transmission system in existing technologies. Simultaneously, lubrication and sealing components are installed on the bearing housing to optimize the bearing lubrication environment and improve sealing performance, reducing frictional heat generation and lubricant leakage, thus providing a stable environment for bearing operation. After assembling the shaft system and impeller, an active cooling system is installed on the bearing housing to replace the natural heat dissipation method in existing technologies. This achieves threshold-triggered automatic control of the rolling bearing and bearing housing temperatures. Finally, through no-load and load testing, the fan's vibration amplitude, rolling bearing temperature, lubrication and sealing status, and cooling system linkage performance are comprehensively tested to ensure that all operating parameters meet preset standards, guaranteeing the stability of the fan after it is put into operation.

[0024] Furthermore, the lightweight impeller and dynamic balancing correction in this invention reduce the impact of vibration on the rolling bearings and reduce the additional heat generated by vibration friction in the rolling bearings. The construction of high-load rolling bearings and rigid shaft systems improves the overall stability of the fan operation and provides a structural basis for the precise control of the cooling system. The stable operation of the cooling system avoids lubrication failure caused by high temperatures in the rolling bearings and bearing housing, further reducing rolling bearing wear and vibration aggravation, and solving the technical problems of vibration and temperature mutual influence and frequent failures in existing shaft-driven fans.

[0025] Preferably, in step S100, a shaft-mounted fan impeller rotor with a balance accuracy level of the first set value is selected, and the maximum residual imbalance of the impeller is calculated by the formula m=(G×10000×M) / (n×r), where G is the balance accuracy level of the shaft-mounted fan impeller rotor, M is the impeller mass, n is the impeller speed, and r is the impeller radius; a dynamic balancing machine is used to perform dynamic balancing correction on the impeller to ensure that its residual imbalance is not greater than the maximum residual imbalance.

[0026] Specifically, in one embodiment, the balance accuracy level of the shaft-mounted fan impeller rotor is first determined to be G6.3 (i.e., the first set value) according to the international standard ISO1940-1. This accuracy level is selected based on the rated operating speed of the shaft-mounted fan (3000 r / min), the structural characteristics of the cantilever installation, and the actual operating conditions of the thermal power plant. Compared with the existing technology's correction method without a clear accuracy level, this significantly improves the standardization of dynamic balance control. Subsequently, based on the actual operating parameters of the fan, the maximum residual imbalance of the impeller is accurately calculated using the formula m=(G×10000×M) / (n×r). This formula provides a clear quantitative target for impeller dynamic balance correction, avoiding the technical problems of large differences in impeller balance accuracy and unstable vibration suppression effect caused by inconsistent correction standards.

[0027] Furthermore, a high-precision hard-bearing dynamic balancing machine is used to perform double-sided balancing correction on the impeller. During the correction process, the imbalance on both sides of the impeller is monitored in real time. The imbalance is gradually adjusted by precise counterweights until the residual imbalance of the impeller is no greater than the calculated maximum residual imbalance, ensuring that the unbalanced inertial force of the impeller is reduced to the minimum under the high-speed rotation condition of 3000r / min.

[0028] Furthermore, this invention, through quantified balance accuracy levels, precise formula calculations, and standardized correction processes, makes impeller dynamic balance correction more standardized and rigorous, effectively improving the consistency and stability of impeller dynamic balance. The impeller corrected by this method experiences significantly reduced vibration excitation during high-speed operation, laying the foundation for subsequent control of the overall vibration amplitude of the shaft-driven fan.

[0029] Preferably, in step S400, the cooling pipes in the cooling system are metal heat pipes, which are tightly fitted to or embedded in the heat-generating area of ​​the bearing housing. The circulating cooling loop in the cooling system is equipped with an electronically controlled valve and a temperature detection element, which are fitted to the bearing housing. The electronically controlled valve and the temperature detection element are both electrically connected to the central control system.

[0030] Specifically, in one embodiment of the present invention, the pipes in the cooling system are U-shaped copper heat pipes. This material has good thermal conductivity and can quickly transfer the heat generated by the bearing housing and rolling bearing to the cooling water. At the same time, it has good mechanical strength, is suitable for the working conditions of thermal power plants, and is not easily damaged by vibration or collision. The cooling pipes are closely fitted to or embedded in the heat-generating area of ​​the bearing housing, that is, the outer side of the mounting cavity of the rolling bearing. This area is the core area of ​​frictional heat generation when the rolling bearing rotates at high speed. The precise arrangement greatly improves the heat exchange efficiency. The electrically controlled valves installed on the circulating cooling circuit are electromagnetic switching valves commonly used in thermal power plants, which have the characteristics of fast response, good sealing performance, and high reliability. Furthermore, the tight fit between the metal heat pipe and the bearing housing allows for real-time and accurate acquisition of temperature data from the bearing housing and internal rolling bearings, avoiding the problems of delayed temperature acquisition and large errors caused by loose sensor installation. Simultaneously, the electrical connection between the electronic control valve and temperature sensing element and the power plant's existing central control system eliminates the need for an additional control host, achieving integration of the cooling system with the overall power plant control system. This facilitates real-time monitoring of the cooling system's operating status and provides a stable signal transmission and control execution channel for subsequent automatic closed-loop temperature control.

[0031] Furthermore, the use of the cooling system not only ensures the cooling effect but also achieves high compatibility with the existing equipment in the power plant. The modification cost is low and the construction difficulty is small. At the same time, the compact installation method will not change the overall layout of the shaft fan, making it suitable for the limited equipment installation space in thermal power plants.

[0032] Preferably, the temperature detection element collects the temperature data of the bearing housing and rolling bearing in real time and transmits it to the central control system. The central control system compares the temperature data with a second set value. When the temperature data is greater than the second set value, the control system opens the electronic control valve, and the cooling water circulates in the cooling loop to cool the bearing housing and / or rolling bearing through heat conduction. When the temperature data is not greater than the second set value, the central control system closes the electronic control valve to stop cooling.

[0033] Specifically, the temperature detection element collects temperature data of the bearing housing and rolling bearing in real time at a fixed sampling frequency, and transmits the data to the central control system in real time via electrical signals. The central control system analyzes and compares the collected temperature data in real time, with the comparison benchmark being a preset second set value. In one embodiment of the present invention, the second set value is 40°C. This set value is selected by combining the rated operating temperature of the rolling bearing, the high-temperature environment of the thermal power plant in summer, and the lubrication failure temperature of the rolling bearing, which can effectively avoid lubrication failure, burnout, and other failures of the rolling bearing caused by excessive temperature.

[0034] Furthermore, when the temperature data exceeds the second set value, the central control system immediately sends an electrical signal control command. Upon receiving the command, the electronically controlled valve quickly opens, allowing cooling water to enter the circulating cooling circuit. Through heat conduction between the cooling pipes and the bearing housing, the heat generated by the high-speed rotation of the rolling bearing is quickly carried away, achieving effective cooling of the bearing housing and / or the rolling bearing. During the cooling process, the temperature detection element continuously collects temperature data and feeds it back to the central control system. When the temperature data drops back to no more than the second set value, the central control system immediately sends a shutdown command. Upon receiving the command, the electronically controlled valve quickly closes, the cooling water circulation stops, and the cooling system ends this cooling operation.

[0035] Furthermore, the method of this invention achieves precise and intelligent control of the cooling system. Compared with the natural heat dissipation method in the prior art, the cooling efficiency is improved by more than 10 times. Under extreme operating conditions such as ambient temperature above 50°C in summer and high load operation of the unit, the rolling bearing temperature can be stably controlled within a safe range, completely solving the problem of overheating of the bearing in the shaft plus fan in the prior art. At the same time, the control logic of starting and stopping on demand avoids the ineffective operation of the cooling system, reduces the consumption of cooling water, and achieves energy-saving operation.

[0036] Preferably, the cooling water is room temperature water, the cooling water temperature is not greater than 30℃, and the flow velocity of the cooling water in the cooling pipe is 0.8m / s-1.2m / s.

[0037] Specifically, the cooling water used is ambient temperature water from the power plant's open water system, with the temperature controlled to not exceed 30℃. This temperature creates a reasonable temperature difference between the cooling water and the heat-generating area of ​​the bearing housing, ensuring sufficient heat exchange efficiency and rapid heat removal while preventing thermal expansion and contraction deformation of the bearing housing caused by excessively low cooling water temperature. Furthermore, the power plant's open water system provides a stable supply of ambient temperature water, eliminating the need for an additional chiller unit and fully utilizing the power plant's existing water resources, thus reducing the operating costs of the cooling system. The flow velocity of the cooling water in the cooling pipes is 0.8m / s-1.2m / s. This velocity range is selected based on the inner diameter, length, and heat exchange area of ​​the cooling pipes. If the velocity is too low, the cooling water will remain in the pipes for too long, causing the water temperature to rise too quickly after heat exchange, resulting in decreased cooling efficiency. If the velocity is too high, it will exacerbate the erosion and wear between the cooling pipes and the bearing housing, while also increasing the water supply pressure of the power plant's open water system and increasing energy consumption. With a flow velocity range of 0.8m / s to 1.2m / s, it ensures rapid flow of cooling water in the pipeline for efficient heat exchange, while also effectively protecting the cooling pipeline and bearing housing from erosion and wear. It is also compatible with the conventional water supply pressure of open water systems in power plants, eliminating the need for additional booster equipment.

[0038] Furthermore, by precisely defining the cooling water parameters, this invention achieves a balance between cooling efficiency, equipment reliability, and operational economy. This ensures that the cooling system can quickly and effectively control the bearing temperature within a safe range, while avoiding equipment damage and increased energy consumption caused by unreasonable parameters. At the same time, by using ambient temperature water from the power plant's open water system as the cooling water source, it achieves seamless integration with the power plant's existing water supply system, eliminating the need for additional cooling water sources and reducing system modification and operation and maintenance costs.

[0039] Preferably, in step S300, the rolling bearing is first assembled into the bearing housing and the coaxiality error of the rolling bearing assembly is controlled. Then, the lubricating medium in the lubrication sealing assembly is added into the bearing housing to form a composite lubrication of oil bath lubrication and splash lubrication. The double-layer sealing structure in the lubrication sealing assembly is used to seal the bearing housing, and the air pressure balancing operation is performed simultaneously to balance the air pressure inside and outside the bearing housing.

[0040] Specifically, the rolling bearing is first assembled. After assembly, the lubricating medium from the lubrication and sealing assembly is added to the bearing housing. The lubricating medium is turbine oil suitable for the high-speed operation of the rolling bearing, ensuring that the rolling bearing forms a composite lubrication mode combining oil bath lubrication and splash lubrication during operation. Oil bath lubrication provides continuous and sufficient lubrication to the core rotating parts of the bearing, while splash lubrication provides lubrication to the outer ring, cage, and other parts of the bearing, achieving comprehensive lubrication of all rotating parts of the bearing and significantly reducing frictional resistance and frictional heat generation during rolling bearing operation. Subsequently, a double-layer skeleton seal structure in the lubrication and sealing assembly is used to seal the bearing housing. Compared with the single-layer seal in the existing technology, the double-layer skeleton seal has better sealing performance, effectively preventing lubricating oil leakage, and preventing external contaminants such as dust, moisture, and oil from entering the bearing housing and contaminating the lubricating medium, which would lead to accelerated bearing wear. Furthermore, while sealing, a pressure balancing operation is performed simultaneously. By installing a vent on the top of the bearing housing, the air pressure inside and outside the bearing housing is balanced, which avoids the problem of lubricating oil leakage caused by the increase in air pressure due to the rise in temperature inside the bearing housing. At the same time, it can also prevent external contaminants from being sucked into the bearing housing due to excessively low air pressure inside the bearing housing.

[0041] Furthermore, this invention significantly reduces rolling bearing failures caused by assembly, lubrication, and sealing issues; the composite lubrication mode achieves comprehensive lubrication of all rotating parts of the rolling bearing, reducing frictional heat generation by more than 30% and effectively reducing the temperature rise of the rolling bearing; the combination of double-layer sealing and air pressure balance greatly improves the sealing reliability of the bearing housing, reduces the lubricating oil leakage rate to zero, and prevents contaminant intrusion, extending the service life of the lubricating medium and reducing maintenance costs; high-precision coaxiality control reduces the additional load on the rolling bearing and extends the actual service life of the rolling bearing.

[0042] Preferably, the process also includes step S500: performing no-load and load testing on the shaft-mounted fan; starting the shaft-mounted fan to perform no-load testing, monitoring the vibration amplitude of the bearing housing, the lubrication and sealing status, and the cooling system status; then starting the shaft-mounted fan to perform load testing, continuously monitoring the rolling bearing temperature and the vibration amplitude of the bearing housing until the rolling bearing temperature is no greater than 40°C, the horizontal vibration amplitude of the bearing housing is no greater than 0.01 mm, and the vertical vibration amplitude of the bearing housing is no greater than 0.02 mm, thus completing the no-load and load testing.

[0043] Specifically, the first step is to conduct no-load testing. No-load testing is carried out with the fan unconnected to any load and the inlet and outlet air ducts unsealed. After starting the shaft-mounted fan, the vibration amplitude of the bearing housing, the working status of the lubrication and sealing system, and the operating status of the cooling system are monitored. The vibration amplitude is monitored to determine whether the shaft assembly accuracy and impeller dynamic balance meet the standards. The oil level of the lubrication and sealing system is checked for stability and whether there is any lubricating oil leakage. The amount of lubricating medium added is determined to be reasonable and the sealing structure is reliable. By artificially simulating a scenario where the bearing temperature exceeds the second set value, the linkage performance of the cooling system, such as temperature acquisition, signal transmission, and valve opening and closing, is verified to be normal. After the no-load commissioning is successful, load commissioning is carried out. Load commissioning is conducted under actual operating conditions with the fan connected to the actual load and the inlet and outlet air ducts closed. The temperature of the rolling bearing and the vibration amplitude of the bearing housing are continuously monitored. During the monitoring process, it is observed whether the rolling bearing temperature can be stabilized within the preset range, whether the cooling system can automatically start and stop according to temperature changes, and whether the vibration amplitude can remain stable. The no-load and load commissioning is completed when the rolling bearing temperature is no greater than 40℃, the horizontal vibration amplitude of the bearing housing is no greater than 0.01mm, and the vertical vibration amplitude of the bearing housing is no greater than 0.02mm. The fan can then be put into formal operation.

[0044] Furthermore, the phased and comprehensive commissioning and verification process in this invention can accurately identify potential problems in the assembly and system configuration of the wind turbine, and make timely adjustments and rectifications to ensure that there are no hidden faults after the wind turbine is put into operation. The no-load commissioning focuses on verifying the independent working performance of each system, while the load commissioning focuses on verifying the collaborative working performance of each system, taking into account both the local and the overall situation, making the commissioning and verification more comprehensive and thorough.

[0045] Preferably, the vibration amplitude of the bearing housing is monitored by arranging eddy current vibration sensors in the horizontal and vertical directions of the bearing housing, and collecting the vibration amplitude data of the bearing housing at a fixed monitoring frequency.

[0046] Specifically, eddy current vibration sensors are selected as the vibration monitoring elements. These sensors offer advantages such as high measurement accuracy, fast response speed, strong anti-interference capability, and non-contact measurement. They are adaptable to the high-speed rotation of the shaft-mounted fan, avoiding the problems of large measurement errors and short service life caused by wear of contact sensors. The sensors are arranged horizontally and vertically on the bearing housing. This arrangement comprehensively captures the vibration of the bearing housing during operation, avoiding the incomplete vibration monitoring and omission of key vibration data caused by unidirectional arrangements. The horizontal sensor mainly monitors the radial vibration of the fan rotor, while the vertical sensor mainly monitors the axial vibration of the fan and the vibration transmission from the foundation. The combination of these two types of sensors forms a complete vibration monitoring data system. The sensor monitoring frequency is set to a fixed value, selected based on the rated speed of the shaft-mounted fan (3000 r / min). This ensures accurate capture of every vibration fluctuation of the bearing housing, guaranteeing the real-time and accurate vibration amplitude data. The collected vibration amplitude data is transmitted to the central control system in real time, facilitating real-time monitoring and analysis of the fan's operating status by staff.

[0047] Furthermore, this invention enables precise, real-time, and comprehensive monitoring of the vibration amplitude of the bearing housing, providing objective and reliable data for commissioning and verification, and ensuring that the criteria for determining the vibration amplitude are uniform and accurate. At the same time, the real-time vibration monitoring data also provides an important reference for the subsequent operation and maintenance of the fan. By analyzing the trend of vibration amplitude changes, staff can promptly detect abnormalities in the operation of the fan, carry out maintenance and rectification in advance, achieve predictive maintenance of the equipment, and significantly reduce the failure rate of the fan.

[0048] Preferably, the coaxiality error between the rolling bearing and the bearing housing is no greater than 0.02 mm.

[0049] Specifically, the coaxiality error between the rolling bearing and the bearing housing is controlled to be no more than 0.02mm. Press fitting is used during assembly to avoid problems such as bearing deformation and bearing hole damage caused by assembly methods such as hammering.

[0050] Furthermore, strictly controlling the coaxiality error between the rolling bearing and the bearing housing to within 0.02mm effectively avoids problems such as misalignment between the outer and inner rings and uneven contact stress between the rolling elements and the raceway caused by excessive coaxiality error during bearing operation. This significantly reduces the additional load on the rolling bearing, lowers the frictional resistance during bearing operation by more than 40%, and significantly reduces frictional heat generation. It also avoids vibration amplification caused by additional load, providing an important guarantee for controlling the overall vibration amplitude of the shaft-driven fan. In addition, strict control of coaxiality error ensures that each rolling element of the bearing bears the load evenly, avoiding problems such as early wear and fatigue spalling caused by local rolling element overload, and significantly extending the actual service life of the bearing.

[0051] A shaft-driven fan bearing housing includes: a bearing housing shell, a rolling bearing, and a cooling system. The bearing housing shell has a transmission mechanism inside, the rolling bearing is disposed inside the bearing housing shell, and the cooling system is disposed on the bearing housing shell and electrically connected to a central control system.

[0052] Specifically, such as Figure 1 As shown, the bearing housing is integrally cast from cast iron. Cast iron has good rigidity, thermal conductivity, and shock absorption. The integral casting process avoids the problems of insufficient rigidity and low assembly precision caused by splicing in split bearing housings. It can provide a stable mounting base for rolling bearings. At the same time, the good thermal conductivity can quickly transfer the heat generated by the rolling bearings to the surface of the housing, providing good conditions for heat exchange in the cooling system. The rolling bearings are set inside the bearing housing and are arranged in two symmetrical sets. This can provide stable double-point support for the drive shaft system of the fan, replacing the traditional single-point support or no independent support design. This greatly improves the rigidity of the shaft system and reduces the bending deformation and vibration of the shaft system.

[0053] Furthermore, the cooling system is installed on the bearing housing and is highly integrated with the structural design of the bearing housing. The cooling pipes are closely fitted to or embedded in the heat-generating area of ​​the bearing housing, without requiring additional installation space. At the same time, the cooling system is electrically connected to the central control system, enabling seamless integration with the aforementioned control methods. It automatically starts and stops according to the temperature changes of the bearing, achieving precise temperature control.

[0054] Furthermore, the bearing housing of the present invention is compatible with the aforementioned vibration and temperature synergistic control method, effectively achieving synergy between vibration suppression and temperature control. Simultaneously, the bearing housing is an independent structure, with dimensions and installation interfaces conforming to the traditional shaft-mounted fan installation layout. It can directly replace the bearing support structure of the traditional shaft-mounted fan, eliminating the need for significant modifications to the overall fan layout. This results in low modification costs and minimal construction difficulty, making it suitable for upgrading existing shaft-mounted fans in thermal power plants. In addition, the integrated design of the bearing housing ensures high integration of components, a compact structure, and minimal space occupation, adapting to the limited equipment installation space in thermal power plants. It also facilitates equipment transportation, installation, and subsequent maintenance.

[0055] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0056] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0057] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0058] In this invention, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0059] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A method for coordinated control of vibration and temperature in a shaft-driven fan bearing housing, characterized in that, Includes the following steps: S100 adopts a lightweight shaft and fan impeller, and performs dynamic balancing on the lightweight impeller to suppress impeller vibration during operation; S200: The bearing housing is mounted on the mounting surface, and two sets of rolling bearings are installed inside the bearing housing. S300. Install a lubrication and sealing assembly on the bearing housing, and connect the impeller that has been dynamically balanced in step S100 to the output end of the bearing housing. Connect the input end of the bearing housing to the drive motor through a flexible coupling. S400: The cooling system is installed on the bearing housing. When the temperature of the bearing housing or the rolling bearing inside the bearing housing exceeds the second set value, the cooling system is activated to cool the bearing housing or the rolling bearing.

2. The method for coordinated vibration and temperature control of shaft-mounted fan bearing housing according to claim 1, characterized in that, In step S100, a shaft-mounted fan impeller rotor with a balance accuracy level of the first set value is selected. The maximum residual imbalance of the impeller is calculated using the formula m=(G×10000×M) / (n×r), where G is the balance accuracy level of the shaft-mounted fan impeller rotor, M is the impeller mass, n is the impeller speed, and r is the impeller radius. A dynamic balancing machine is used to perform dynamic balancing correction on the impeller to ensure that its residual imbalance is not greater than the maximum residual imbalance.

3. The method for coordinated control of vibration and temperature of shaft-mounted fan bearing housing according to claim 1, characterized in that, In step S400, the cooling pipes in the cooling system are metal heat pipes, which are tightly fitted to or embedded in the heat-generating area of ​​the bearing housing. The circulating cooling loop in the cooling system is equipped with an electronically controlled valve and a temperature detection element. The temperature detection element is fitted to the bearing housing. The electronically controlled valve and the temperature detection element are both electrically connected to the central control system.

4. The method for coordinated control of vibration and temperature of shaft-mounted fan bearing housing according to claim 3, characterized in that, The temperature detection element collects the temperature data of the bearing housing and rolling bearing in real time and transmits it to the central control system. The central control system compares the temperature data with the second set value. When the temperature data is greater than the second set value, the control valve is opened and the cooling water circulates in the cooling loop to cool the bearing housing and / or rolling bearing through heat conduction. When the temperature data is not greater than the second set value, the central control system closes the control valve to stop cooling.

5. The method for coordinated vibration and temperature control of the bearing housing of a shaft-driven fan according to claim 4, characterized in that, The cooling water is at room temperature, with a temperature not exceeding 30℃, and the flow velocity of the cooling water in the cooling pipes is 0.8m / s-1.2m / s.

6. The method for coordinated vibration and temperature control of the bearing housing of a shaft-driven fan according to claim 1, characterized in that, In step S300, the rolling bearing is first assembled into the bearing housing and the coaxiality error of the rolling bearing assembly is controlled. Then, the lubricating medium in the lubrication sealing assembly is added into the bearing housing to form a composite lubrication of oil bath lubrication and splash lubrication. The double-layer sealing structure in the lubrication sealing assembly is used to seal the bearing housing, and the air pressure balancing operation is performed simultaneously to balance the air pressure inside and outside the bearing housing.

7. The method for coordinated vibration and temperature control of shaft-mounted fan bearing housing according to claim 1, characterized in that, The process also includes step S500: performing no-load and load testing on the shaft-mounted fan; starting the shaft-mounted fan to perform no-load testing, monitoring the vibration amplitude of the bearing housing, the lubrication and sealing status, and the cooling system status; then starting the shaft-mounted fan to perform load testing, continuously monitoring the rolling bearing temperature and the vibration amplitude of the bearing housing until the rolling bearing temperature is no greater than 40°C, the horizontal vibration amplitude of the bearing housing is no greater than 0.01 mm, and the vertical vibration amplitude of the bearing housing is no greater than 0.02 mm, at which point the no-load and load testing are complete.

8. The method for coordinated control of vibration and temperature of shaft-driven fan bearing housing according to claim 7, characterized in that, Monitoring the vibration amplitude of the bearing housing is achieved by placing eddy current vibration sensors in the horizontal and vertical directions of the bearing housing and collecting vibration amplitude data at a fixed monitoring frequency.

9. The method for coordinated control of vibration and temperature of shaft-mounted fan bearing housing according to claim 1, characterized in that, The coaxiality error between the rolling bearing and the bearing housing is no greater than 0.02 mm.

10. A shaft-mounted fan bearing housing, used to implement the vibration and temperature coordinated control method for the shaft-mounted fan bearing housing according to any one of claims 1-9, characterized in that, include: The bearing housing contains a transmission mechanism. A rolling bearing, which is disposed inside the bearing housing; A cooling system is installed on the bearing housing and is electrically connected to the central control system.

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