Dynamic leveling and throw control device for thrust pad of vertical motor and working method of dynamic leveling and throw control device

Abstract

The invention relates to the technical field of large vertical motor equipment, in particular to a vertical motor thrust pad dynamic leveling and throw control device and a working method. The device comprises a hydraulic execution unit, a sensing detection unit, a control unit and a hydraulic supply unit, the hydraulic execution unit comprises a hydraulic oil cylinder and an oil inlet electromagnetic valve, the sensing detection unit comprises a temperature-pressure integrated sensor, a displacement sensor and a pressure relay, the control unit comprises a controller, and the hydraulic supply unit comprises a high-pressure oil pump, a hydraulic oil tank, a low-pressure filter, a high-pressure energy storage device, an electromagnetic pressure release valve and a diverter valve. An oil outlet of the hydraulic oil tank is sequentially connected with a low-pressure filter and a high-pressure oil pump, an outlet of the high-pressure oil pump is connected with a pressure relay and a high-pressure energy storage device, and an outlet of the high-pressure energy storage device is connected with a diverter valve in series. Through the micro-amplitude adjustment and pressure closed-loop control structure of the hydraulic oil cylinder, the pressure deviation of each thrust pad can be controlled within 5%, and the stress uniformity is greatly optimized.

Description

Technical Field

[0001] This invention relates to the field of large vertical motor equipment technology, specifically to a dynamic leveling and swing control device and working method for the thrust bearing of a vertical motor. Background Technology

[0002] The existing support and adjustment structure for large vertical motor thrust bearings mainly adopts a rigid support bolt design, which has the following inherent defects: Insufficient adjustment precision: The rigid bolts are mechanically rigid connections, and micron-level height fine-tuning cannot be achieved during the adjustment process. As a result, multiple thrust bearings are difficult to reach a completely horizontal state when the motor is running normally, and the force deviation of each bearing generally exceeds 15%, which seriously affects the overall service life of the thrust bearing.

[0003] Uneven force transmission: Due to uneven adjustment of the thrust bearing pressure, some bearings are already close to their temperature limit when they are running. When there are load fluctuations during motor operation, some bearings are prone to overload, which can lead to bearing burn-out and other malfunctions.

[0004] Poor ease of swing adjustment: When the swing of the motor drive end flange is out of tolerance, it is necessary to disassemble the motor end cover, thrust bearing cover and other parts and then retighten the bolts for adjustment, or it is necessary to adjust the insulating pad between the mirror plate and the thrust head. For large units, a single adjustment usually takes more than 8 hours, and the accuracy needs to be retested after adjustment, which seriously affects the efficiency of equipment operation and maintenance.

[0005] Lack of dynamic response capability: Rigid structures cannot respond in real time to changes in the operating conditions of the motor (such as component deformation caused by temperature rise, force offset caused by load fluctuation), and cannot achieve dynamic leveling and swing correction, thus limiting the stability of equipment operation.

[0006] The auxiliary components are highly dependent and cumbersome to adjust: the traditional structure requires the installation of a mirror plate and an insulating pad under the thrust head. The swing adjustment is achieved by grinding the thickness of the insulating pad. The grinding accuracy is difficult to control and is time-consuming and labor-intensive. Each grinding adjustment requires repeated disassembly and testing, which further extends the downtime. Summary of the Invention

[0007] Therefore, the technical problem to be solved by the present invention is to overcome the problem of insufficient adjustment accuracy in the prior art, thereby providing a dynamic leveling and swing control device for vertical motor thrust bearing blocks.

[0008] To address the aforementioned technical problems, this invention provides a dynamic leveling and sway control device for vertical motor-driven thrust bearings, comprising a hydraulic actuation unit, a sensing and detection unit, a control unit, and a hydraulic supply unit. The hydraulic actuation unit includes a hydraulic cylinder and an inlet solenoid valve. The sensing and detection unit includes a temperature-pressure integrated sensor, a displacement sensor, and a pressure relay. The control unit includes a controller. The hydraulic supply unit includes a high-pressure oil pump, a hydraulic oil tank, a low-pressure filter, a high-pressure energy storage device, an electromagnetic pressure relief valve, and a flow divider valve. The outlet of the hydraulic oil tank is sequentially connected to the low-pressure filter and the high-pressure oil pump. The outlet of the high-pressure oil pump is connected to the pressure relay and the high-pressure energy storage device. The outlet of the high-pressure energy storage device is connected in series with the flow divider valve. The outlet of the flow divider valve has branch oil lines matching the number of thrust bearings. Each branch oil line is connected to the inlet solenoid valve of the corresponding hydraulic cylinder. The hydraulic cylinder is located at the bottom of the thrust bearing. The outlet of the hydraulic cylinder is connected to the electromagnetic pressure relief valve. The outlet of the electromagnetic pressure relief valve is connected to the hydraulic oil tank. The displacement sensor and the pressure relay are electrically connected to the controller.

[0009] Furthermore, the controller is equipped with a data processing module, which includes a temperature compensation module, a pressure equalization processing module, a swing analysis module, and a swing data mean calculation module. The temperature compensation module stores a temperature threshold, the pressure equalization processing module stores a pressure deviation threshold, the swing analysis module stores a swing threshold, and the swing data mean calculation module is set to a 5-minute data acquisition cycle, automatically calculates the swing mean in each cycle, and transmits it to the swing analysis module.

[0010] Furthermore, the top of the hydraulic cylinder is provided with a cylinder top spherical surface, which abuts against the bottom of the thrust bearing.

[0011] Furthermore, the bottom of the thrust pad is made of alloy or non-metallic wear-resistant material.

[0012] Furthermore, the pressure-temperature integrated sensor adopts a built-in structure and is installed on the side wall of the oil chamber of the hydraulic cylinder, with the probe of the pressure-temperature integrated sensor flush with the inner wall of the hydraulic cylinder.

[0013] Furthermore, the displacement sensor is mounted on a concrete foundation or motor base. The detection ends of the displacement sensor correspond to the X and Y directions of the motor drive end flange, respectively. The distance between the sensor and the surface of the motor drive end flange is 1.5-2.0 mm, the detection accuracy is ±0.001 mm, and the measurement range is 0-5 mm.

[0014] Furthermore, it also includes an overflow valve, which is connected in parallel with the high-pressure oil pump.

[0015] Furthermore, the hydraulic oil tank has a built-in oil temperature cooler and a level gauge, and a drain valve is installed at the bottom of the hydraulic oil tank.

[0016] Furthermore, the high-voltage energy storage device is a bladder-type energy storage device.

[0017] The present invention also provides a working method for using the aforementioned vertical motor thrust bearing dynamic leveling and sway control device, comprising: During equipment operation, the spherical surface at the top of the hydraulic cylinder directly contacts the thrust bearing, and the high-pressure energy storage device maintains a constant pressure of 20-25 MPa. When the pressure relay detects that the pressure of the high-pressure energy storage device is ≤20 MPa, the controller starts the high-pressure oil pump to replenish the pressure to 25 MPa and then stops the machine. When the integrated pressure-temperature sensor detects that the pressure of a hydraulic cylinder is insufficient and requires oil replenishment, the controller drives the corresponding inlet solenoid valve to open, and the high-pressure energy storage device directly supplies oil to the hydraulic cylinder. The integrated pressure-temperature sensor collects the oil pressure and oil temperature data of each hydraulic cylinder in real time and transmits them to the controller. The controller compares the pressure of each thrust bearing with the reference bearing pressure. When the deviation exceeds 5%, the controller drives the corresponding inlet solenoid valve to open, and the high-pressure energy storage device supplies oil or the solenoid pressure relief valve releases pressure. The thrust bearing is adjusted by the piston extension and retraction of the hydraulic cylinder. The height is adjusted until the pressure is balanced; the displacement sensor continuously collects swing data, and the swing data average calculation module automatically calculates the average swing in the X / Y direction within the cycle every 5 minutes. If the average value exceeds the 0.02mm threshold, the controller analyzes the swing direction and deviation pattern, and synchronously drives the oil inlet solenoid valve or solenoid pressure relief valve of the corresponding 2-3 hydraulic cylinders to act, and adjusts and corrects the posture through multi-watt linkage; during normal operation, the oil inlet solenoid valve and solenoid pressure relief valve remain closed, and the high-pressure energy storage device and the hydraulic cylinder sealing structure work together to maintain stable oil pressure. Pressure regulation and swing regulation are reduced by threshold triggering and cycle average judgment to reduce the frequency of action; before the initial start, the displacement sensor detects the spindle deviation by manually turning the cylinder 3-5 times, and the controller drives the energy storage device to supply oil to each hydraulic cylinder to complete the swing calibration.

[0018] The technical solution of this invention has the following advantages: The vertical motor thrust bearing dynamic leveling and swing control device provided by this invention, through the above-described structural design, has the following significant advantages compared to existing rigid support structures: 1. Significantly improved force uniformity: Through the micro-adjustment of the hydraulic cylinder and the closed-loop pressure control structure, the pressure deviation of each thrust bearing can be controlled within 5%. Compared with the traditional rigid structure (deviation of more than 15%), the force uniformity is greatly optimized, and the service life of the thrust bearing is extended by more than 30%.

[0019] 2. Highly efficient and convenient swing adjustment: No need to disassemble parts. The swing is detected in real time by displacement sensor, and the controller drives the corresponding hydraulic cylinder to achieve dynamic correction. The adjustment response time is ≤0.5s, and the time for a single swing correction is reduced from more than 8 hours in the traditional way to a few seconds, improving operation and maintenance efficiency by 99%.

[0020] 3. Enhanced operational stability: The built-in pressure-temperature integrated sensor and temperature compensation structure ensure pressure detection accuracy, the normally closed solenoid valve and combined sealing structure ensure stable oil pressure, and the spherical hydraulic cylinder adapts to the angle deflection of the thrust bearing within a certain range. The vibration amplitude of the equipment is reduced by more than 40%, and the failure rate is reduced by 60%.

[0021] 4. Excellent adaptability and safety: The rated pressure, stroke, cylinder diameter and number of hydraulic cylinders can be matched according to the motor model. The safety structure of the high-pressure oil pump and relief valve avoids overload damage. It can be adapted to large vertical motors of different power levels from 0.5MW to 300MW, with a wide range of applications.

[0022] 5. Significantly reduced energy consumption and losses: The high-pressure energy storage device achieves the mode of "intermittent pressure replenishment of hydraulic oil pump and normal oil supply of energy storage device", which reduces the frequency of oil pump start-up and shutdown by more than 80%, avoids temperature rise caused by long-term operation (oil temperature is controlled within 45℃), extends the service life of hydraulic oil pump by 50%, and reduces system energy consumption by 30%.

[0023] The summary section is provided to present the chosen concepts in a simplified form, which will be further described in the detailed description below. The summary section is not intended to identify essential or necessary features of this disclosure, nor is it intended to limit the scope of this disclosure. Attached Figure Description

[0024] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0025] Figure 1 A schematic diagram of the overall structure assembly of the vertical motor provided by the present invention; Figure 2 Hydraulic system layout diagram of the vertical motor thrust bearing dynamic leveling and swing control device provided by the present invention; Figure 3 The control logic diagram of the vertical motor thrust bearing dynamic leveling and swing control device provided by the present invention; Figure 4 Control logic diagram of the high-voltage energy storage device for the vertical motor thrust bearing dynamic leveling and swing control device provided by the present invention; Figure 5 The thrust bearing pressure adjustment control logic diagram of the vertical motor thrust bearing dynamic leveling and swing control device provided by the present invention; Figure 6The swing adjustment control logic diagram of the vertical motor thrust bearing dynamic leveling and swing control device provided by the present invention; Figure 7 A cross-sectional view of the hydraulic cylinder of the vertical motor thrust bearing dynamic leveling and swing control device provided by the present invention.

[0026] Explanation of reference numerals in the attached figures: 1. Thrust pad; 2. Hydraulic cylinder; 3. Pressure-temperature integrated sensor; 4. Oil inlet solenoid valve; 5. Displacement sensor; 7. High-pressure oil pump; 8. Relief valve; 9. Drive end flange; 10. Cylinder top spherical surface; 11. Hydraulic oil tank; 12. Low-pressure filter; 15. High-pressure energy storage device; 16. Solenoid pressure relief valve; 17. Diverter valve; 18. Pressure relay. Detailed Implementation

[0027] In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit or scope of this disclosure. Therefore, the drawings and description are to be considered exemplary in nature and not restrictive.

[0028] The preferred embodiments of this disclosure are described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are for illustration and explanation only and are not intended to limit this disclosure.

[0029] Please see Figures 1 to 7 As shown, this invention provides a dynamic leveling and sway control device for a vertical motor thrust bearing 1, including a hydraulic actuation unit, a sensing and detection unit, a control unit, and a hydraulic supply unit; the hydraulic actuation unit includes a hydraulic cylinder 2 and an inlet solenoid valve 4; the sensing and detection unit includes a temperature-pressure integrated sensor, a displacement sensor 5, and a pressure relay 18; the control unit includes a controller; the hydraulic supply unit includes a high-pressure oil pump 7, a hydraulic oil tank 11, a low-pressure filter 12, a high-pressure energy storage device 15, an electromagnetic pressure relief valve 16, and a flow divider valve 17; the hydraulic oil tank 11... The oil outlet is connected in sequence to the low-pressure filter 12 and the high-pressure oil pump 7. The outlet of the high-pressure oil pump 7 is connected to the pressure relay 18 and the high-pressure energy storage device 15. The outlet of the high-pressure energy storage device 15 is connected in series with the diverter valve 17. The outlet of the diverter valve 17 is provided with branch oil circuits matching the number of thrust bearings 1. Each branch oil circuit is connected to the inlet solenoid valve 4 of the corresponding hydraulic cylinder 2. The hydraulic cylinder 2 is located at the bottom of the thrust bearing 1. The oil outlet of the hydraulic cylinder 2 is connected to the electromagnetic pressure relief valve 16. The outlet of the electromagnetic pressure relief valve 16 is connected to the hydraulic oil tank 11. The displacement sensor 5 and the pressure relay 18 are electrically connected to the controller.

[0030] The hydraulic actuator is the core component for leveling and sway correction, and is set up one-to-one with each thrust pad 1; The hydraulic actuator is the core component for leveling and sway correction, and is configured one-to-one with each thrust pad 1. It includes a hydraulic cylinder 2 and an inlet solenoid valve 4, and its specific structural features are as follows: Hydraulic cylinder 2: The cylinder body is made of 45 steel with heat treatment (hardness HB220-250), with an inner diameter of 80-150mm, a rated working pressure of 10-20MPa, and an adjustable stroke of 5-20mm; the piston adopts a combined sealing structure (PTFE+O-ring) to ensure no leakage under high pressure. The top of the hydraulic cylinder 2 is provided with a cylinder top spherical surface 10, which abuts against the bottom of the thrust bearing 1. That is, the top of the hydraulic cylinder 2 contacts the bottom of the thrust bearing 1 through the spherical surface. The radius of the spherical surface is 800-1000mm, which can adapt to angular deviation within a certain range, ensuring uniform force transmission and that the compressive stress does not exceed the allowable value. The bottom of the thrust pad 1 is made of alloy or non-metallic wear-resistant material, meaning that the alloy or non-metallic wear-resistant material on the thrust pad 1 is in direct contact with the motor thrust head. This eliminates the need for the mirror plate and insulating pad below the thrust head in the traditional structure, and only requires ensuring that the perpendicularity between the lower end face of the thrust head and the main shaft is ≤0.01mm / m.

[0031] Normally closed solenoid valve - installed on the oil inlet and outlet lines of hydraulic cylinder 2: adopts a high-frequency solenoid directional valve with a response time of ≤10ms, and is installed at the oil inlet and outlet of hydraulic cylinder 2 respectively. The valve body is made of stainless steel 304, the rated working pressure is matched with the cylinder, and it remains closed during normal operation. The oil pressure in the cylinder is stabilized by sealing the valve port.

[0032] When installing the hydraulic actuator, a mounting hole is machined under each thrust pad 1 of the motor thrust bearing housing, and the hydraulic cylinder 2 is fixed with bolts. The spherical surface 10 at the top of the cylinder fits against the bottom of the pad. After tightening, the initial value of the horizontality of the thrust pad 1 is checked.

[0033] The sensing and detection unit is the core component of condition monitoring, including a pressure-temperature integrated sensor 3, a displacement sensor 5, and a pressure relay 18. Its specific structural features are as follows: The pressure-temperature integrated sensor 3 adopts a built-in structure and is installed on the side wall of the oil chamber of the hydraulic cylinder 2. The probe of the pressure-temperature integrated sensor 3 is flush with the inner wall of the hydraulic cylinder 2. The pressure measurement range is 0-30MPa with an accuracy of ±0.5%FS, and the temperature measurement range is -20℃-120℃ with an accuracy of ±0.3℃. It is electrically connected to the control unit via an aviation plug.

[0034] The displacement sensor 5 is a high-precision eddy current displacement sensor 5, with at least two sensors installed. Each sensor is fixed to a concrete foundation or motor base by a rigid bracket. The detection end corresponds to the X and Y directions of the motor drive end flange 9. The distance between the displacement sensor 5 and the surface of the motor drive end flange 9 is 1.5-2.0 mm. The detection accuracy is ±0.001 mm, and the range is 0-5 mm. The sensor is connected to the control unit via a shielded cable. The displacement sensor 5 continuously collects swing data and uploads it to the control unit in a 5-minute data acquisition cycle.

[0035] Pressure relay 18 is installed on high-pressure energy storage device 15 to monitor the pressure of the energy storage device.

[0036] During the installation of the sensing unit, mounting holes are machined at the corresponding positions on the side wall of the oil chamber of the hydraulic cylinder 2; PTFE thread sealant is wrapped around the mounting thread section of the pressure-temperature integrated sensor 3, and a copper washer is fitted onto the probe end. After aligning with the mounting holes, a torque wrench is used to tighten the screws to a torque of 35 N·m to ensure that the probe is flush with the inner wall of the cylinder and that the copper washer is compacted; sensor brackets are welded to the motor base in the X and Y directions corresponding to the motor drive end flange 9 to fix the displacement sensor 5 and calibrate the detection spacing and direction.

[0037] The control unit is the core control component of the device, including a controller, a data processing module, and a human-machine interface. Its specific structural features are as follows: The controller uses a PLC controller and supports high-speed pulse output. The controller is electrically connected to the sensing unit, oil inlet solenoid valve 4, solenoid pressure relief valve 16 and hydraulic supply unit through shielded cables. The cable laying path is far away from the motor power cable to avoid electromagnetic interference.

[0038] The data processing module is located inside the controller. The data processing module includes a temperature compensation module, a pressure equalization processing module, a swing analysis module, and a swing data mean calculation module. The temperature compensation module stores the temperature threshold, the pressure equalization processing module stores the pressure deviation threshold, the swing analysis module stores the swing threshold, and the swing data mean calculation module is set to a 5-minute data acquisition cycle, automatically calculates the swing mean in each cycle, and transmits it to the swing analysis module.

[0039] The hydraulic supply unit is a power source component, including a high-pressure oil pump 7, a relief valve 8, and a hydraulic oil tank 11. Its specific structural features are as follows: The low-pressure filter 12 is installed at the inlet of the high-pressure oil pump 7. It adopts a low-pressure return oil filter structure, with the housing material being aluminum alloy. The filtration accuracy is 10μm, and the rated flow rate matches the oil pump displacement (30L / min for 8-10 units, 50L / min for more than 10 units). The built-in stainless steel filter screen is removable and washable.

[0040] The high-pressure oil pump 7 adopts a variable displacement piston pump with a rated working pressure of 20MPa. The displacement is matched according to the number of bearings (20-30mL / r for 8-10 bearings, 30-40mL / r for more than 10 bearings). It is driven by a three-phase asynchronous motor with a power of 2.2-5.5kW (2.2-3kW for ≤10 bearings, 3-5.5kW for >10 bearings). A pressure transmitter (range 0-30MPa, accuracy ±0.5%FS, 4-20mA analog output) is installed at the oil pump outlet.

[0041] The relief valve 8 is a pilot-operated relief valve, installed in the main oil circuit at the outlet of the high-pressure oil pump 7, and connected in parallel with the high-pressure oil pump 7. The rated working pressure is 20MPa. When the system pressure exceeds 25MPa (1.25 times the rated pressure), it automatically releases pressure to protect the hydraulic oil pump and the main oil circuit.

[0042] The high-pressure energy storage device 15 adopts a bladder-type energy storage unit with a rated pressure of 20MPa and a volume of 10-30L (matched according to the number of thrust bearings 1; 15-20L for 8-10 bearings, 20-30L for more than 10 bearings), and is made of 304 stainless steel. A pressure relay 18 (range 0-30MPa, accuracy ±0.1MPa) is installed at the inlet of the energy storage unit, with a set pressure threshold of 20-25MPa, and is connected in series in the main oil circuit between the outlet of the high-pressure oil pump 7 and the integrated diverter valve 17. It adopts a combination of O-rings and retaining rings for sealing, which is suitable for high-pressure working conditions without leakage.

[0043] Electromagnetic pressure relief valve 16: One two-position two-way electromagnetic directional valve is installed at the oil outlet of each hydraulic cylinder 2 as electromagnetic pressure relief valve 16. The response time is ≤10ms, the valve body is made of stainless steel 304, the rated working pressure is 20MPa, and the start and stop are controlled by the controller to achieve precise pressure relief of a single cylinder.

[0044] The hydraulic oil tank 11 has a capacity of 50-100L, with a built-in oil temperature cooler and level gauge. A drain valve is installed at the bottom of the tank, and the oil used is anti-wear hydraulic oil (viscosity grade 46).

[0045] When the pressure of the energy storage device is ≤20MPa, the controller starts the hydraulic oil pump to replenish the pressure to 25MPa and then stops; when the hydraulic cylinder 2 needs to replenish oil, the high-pressure energy storage device 15 directly supplies oil without starting the oil pump; the signal output terminals of the pressure-temperature integrated sensor 3, displacement sensor 5, and pressure relay 18 are connected to the analog input module of the controller; the digital output module of the controller is connected to the control terminals of the oil inlet solenoid valve 4, the solenoid pressure relief valve 16, and the high-pressure oil pump 7.

[0046] All hydraulic lines use high-pressure seamless steel pipes, with main oil lines having a diameter of 20-30mm and branch oil lines having a diameter of 10-15mm. Pipe joints use compression fittings.

[0047] Hydraulic pipeline connection: 20# high-pressure seamless steel pipe is used. The main oil circuit flows through low-pressure filter 12 → hydraulic oil pump → pressure relay 18 → high-pressure energy storage device 15 → diversion valve 17. The diameter of the main oil circuit is 25mm. The diameter of the branch oil circuit from the diversion valve 17 to each inlet solenoid valve 4 is 12mm (8-10 thrust bearings 1). First, connect the main oil circuit, then install the low-pressure filter 12, hydraulic oil pump, overflow valve 8, pressure relay 18, high-pressure energy storage device 15, and diverter valve 17 in sequence. Next, connect each branch oil circuit: diverter valve 17 → inlet solenoid valve 4 → hydraulic cylinder 2. Finally, connect the main return oil circuit: hydraulic cylinder 2 → solenoid pressure relief valve 16 → hydraulic oil tank 11. The bending radius of the pipeline should be ≥ 5 times the pipe diameter, and the joints should use compression fittings. After assembly, perform staged pressure tests: the high-pressure energy storage device 15 should be pressure-held at 25MPa / 1 hour individually, and the entire system should be pressure-held at 20MPa / 30 minutes, with no leakage in either case. Check the flow deviation of each branch of the diverter valve 17 (ensure ≤ 3%), and calibrate the threshold of the pressure relay 18 (20-25MPa).

[0048] Electrical connection: Connect the sensor to the analog input module of the controller via a shielded cable. Connect the oil inlet solenoid valve 4, the solenoid pressure relief valve 16, and the high-pressure oil pump 7 to the digital output module. The human-machine interface communicates with the controller. Both ends of the cable are grounded.

[0049] Initialization and debugging: Inject No. 46 anti-wear hydraulic oil into the hydraulic oil tank 11 until the level gauge is at the middle position, start the controller, and set one of the thrust bearings 1 as the "reference bearing", pressure deviation threshold (5%), and swing threshold (0.02mm) through the human-machine interface; manually control the oil intake of each hydraulic cylinder 2 to make the thrust bearing 1 initially fit with the lower end face of the motor thrust head, and then manually rotate the spindle 3-5 times to allow the displacement sensor 5 to fully sense the swing deviation of the spindle. The controller automatically collects the swing data at each position and analyzes the deviation pattern, drives the corresponding cylinder to adjust the height of the thrust bearing 1, and completes the initial swing calibration (the entire automatic adjustment process ≤2 minutes); finally, manually control the action of each hydraulic cylinder 2 to verify the smoothness of the adjustment.

[0050] The present invention also provides a working method for using the aforementioned vertical motor thrust bearing 1 dynamic leveling and sway control device, comprising: During operation, the spherical surface 10 at the top of the hydraulic cylinder directly contacts the thrust bearing 1, and the high-pressure energy storage device 15 maintains a constant pressure of 20-25 MPa. When the pressure relay 18 detects that the pressure of the high-pressure energy storage device 15 is ≤20 MPa, the controller starts the high-pressure oil pump 7 to replenish the pressure to 25 MPa and then stops the machine. When the pressure-temperature integrated sensor 3 detects that the pressure of a hydraulic cylinder 2 is insufficient and needs to be replenished, the controller drives the corresponding inlet solenoid valve 4 to open, and the high-pressure energy storage device 15 directly supplies oil to the hydraulic cylinder 2. The pressure-temperature integrated sensor 3 collects the oil pressure and oil temperature data of each hydraulic cylinder 2 in real time and transmits them to the controller. The controller compares the pressure of each thrust bearing 1 with the reference bearing pressure. When the deviation exceeds 5%, the controller drives the corresponding inlet solenoid valve 4 to open, and the high-pressure energy storage device 15 supplies oil or the solenoid pressure relief valve 16 relieves pressure, which is adjusted by the piston extension and retraction of the hydraulic cylinder 2. The thrust bearing 1 is adjusted until the pressure is balanced; the displacement sensor 5 continuously collects swing data, and the swing data average calculation module automatically calculates the average swing value in the X / Y direction within the cycle every 5 minutes. If the average value exceeds the 0.02mm threshold, the controller analyzes the swing direction and deviation pattern, and synchronously drives the oil inlet solenoid valve 4 or solenoid pressure relief valve 16 of the corresponding 2-3 hydraulic cylinders 2 to act, and adjusts and corrects the posture through multi-bearing linkage; during normal operation, the oil inlet solenoid valve 4 and the solenoid pressure relief valve 16 remain closed, and the high-pressure energy storage device 15 and the hydraulic cylinder 2's sealing structure work together to maintain stable oil pressure. Pressure regulation and swing adjustment are both reduced by threshold triggering and cycle average judgment to reduce the frequency of action; before the initial start, the displacement sensor 5 senses the spindle deviation by manually turning the cylinder 3-5 times, and the controller drives the energy storage device to supply oil to each hydraulic cylinder 2 to complete the swing calibration.

[0051] Obviously, the above embodiments are merely illustrative examples for clear explanation and are not intended to limit the implementation. Those skilled in the art will recognize that other variations or modifications can be made based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations here. However, obvious variations or modifications derived therefrom are still within the scope of protection of this invention.

Claims

1. A vertical motor thrust bearing dynamic leveling and swing control device, characterized in that, It includes a hydraulic actuator, a sensor detection unit, a control unit, and a hydraulic supply unit; The hydraulic actuator includes a hydraulic cylinder (2) and an inlet solenoid valve (4). The sensing and detection unit includes a temperature-pressure integrated sensor, a displacement sensor (5), and a pressure relay (18). The control unit includes a controller. The hydraulic supply unit includes a high-pressure oil pump (7), a hydraulic oil tank (11), a low-pressure filter (12), a high-pressure energy storage device (15), an electromagnetic pressure relief valve (16), and a flow divider valve (17). The outlet of the hydraulic oil tank (11) is connected in sequence to the low-pressure filter (12) and the high-pressure oil pump (7). The outlet of the high-pressure oil pump (7) is connected to the pressure relay (18) and the high-pressure energy storage device (15). The outlet of the high-pressure energy storage device (15) is connected in series with the diverter valve (17). The outlet of the diverter valve (17) is provided with branch oil circuits matching the number of thrust pads (1). Each branch oil circuit is connected to the inlet solenoid valve (4) of the corresponding hydraulic cylinder (2). The hydraulic cylinder (2) is located at the bottom of the thrust pad (1). The outlet of the hydraulic cylinder (2) is connected to the electromagnetic pressure relief valve (16). The outlet of the electromagnetic pressure relief valve (16) is connected to the hydraulic oil tank (11). The displacement sensor (5) and the pressure relay (18) are electrically connected to the controller.

2. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 1, characterized in that, The controller is equipped with a data processing module, which includes a temperature compensation module, a pressure equalization processing module, a swing analysis module, and a swing data mean calculation module. The temperature compensation module stores the temperature threshold, the pressure equalization processing module stores the pressure deviation threshold, the swing analysis module stores the swing threshold, and the swing data mean calculation module is set to a 5-minute data acquisition cycle, automatically calculating the swing mean in each cycle and transmitting it to the swing analysis module.

3. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 1, characterized in that, The top of the hydraulic cylinder (2) is provided with a cylinder top spherical surface (10), which abuts against the bottom of the thrust bearing (1).

4. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 3, characterized in that, The bottom of the thrust pad (1) is made of alloy or non-metallic wear-resistant material.

5. The vertical motor thrust bearing dynamic leveling and swing control device according to any one of claims 1-4, characterized in that, The pressure-temperature integrated sensor (3) adopts a built-in structure and is installed on the side wall of the oil chamber of the hydraulic cylinder (2). The probe of the pressure-temperature integrated sensor (3) is flush with the inner wall of the hydraulic cylinder (2).

6. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 5, characterized in that, The displacement sensor (5) is installed on a concrete foundation or motor base. The detection end of the displacement sensor (5) corresponds to the X and Y directions of the motor drive end flange (9) respectively. The distance between the sensor and the surface of the motor drive end flange (9) is 1.5-2.0mm. The detection accuracy is ±0.001mm and the range is 0-5mm.

7. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 6, characterized in that, It also includes an overflow valve (8), which is connected in parallel with the high-pressure oil pump (7).

8. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 7, characterized in that, The hydraulic oil tank (11) has a built-in oil temperature cooler and a level gauge, and a drain valve is provided at the bottom of the hydraulic oil tank (11).

9. The vertical motor thrust bearing dynamic leveling and swing control device according to claim 1, characterized in that, The high-voltage energy storage device (15) is a bladder-type energy storage device.

10. The working method of the vertical motor thrust bearing dynamic leveling and swing control device according to any one of claims 1-9, characterized in that, include: When the equipment is running, the spherical surface (10) at the top of the cylinder directly contacts the thrust bearing (1), and the high-pressure energy storage device (15) maintains a normal pressure of 20-25MPa. When the pressure relay (18) detects that the pressure of the high-pressure energy storage device (15) is ≤20MPa, the controller starts the high-pressure oil pump (7) to replenish the pressure to 25MPa and then stops the machine. When the integrated pressure-temperature sensor detects that the pressure of a certain hydraulic cylinder (2) is insufficient and needs to be replenished, the controller drives the corresponding inlet solenoid valve (4) to open, and the high-pressure energy storage device (15) directly supplies oil to the hydraulic cylinder (2). The integrated pressure-temperature sensor (3) collects the oil pressure and oil temperature data of each hydraulic cylinder (2) in real time and transmits them to the controller. The controller compares the pressure of each thrust bearing (1) with the reference bearing pressure. When the deviation exceeds 5%, the controller drives the corresponding inlet solenoid valve (4) to open, and the high-pressure energy storage device (15) supplies oil or the solenoid pressure relief valve (16) relieves the pressure through the hydraulic cylinder (2). The piston extension adjusts the height of the thrust pad (1) until the pressure is balanced; the displacement sensor (5) continuously collects swing data, and the swing average calculation module automatically calculates the average swing value in the X / Y direction within the cycle every 5 minutes. If the average value exceeds the threshold of 0.02mm, the controller analyzes the swing direction and deviation law, and synchronously drives the oil inlet solenoid valve (4) or solenoid pressure relief valve (16) of the corresponding 2-3 hydraulic cylinders (2) to act, and adjusts and corrects the posture through multi-watt linkage; during normal operation, the oil inlet solenoid valve (4) and solenoid pressure relief valve (16) remain closed, and the high pressure energy storage device (15) and the hydraulic cylinder (2) seal structure work together to maintain stable oil pressure. Pressure regulation and swing adjustment are both reduced by threshold triggering and cycle average judgment to reduce the frequency of action; before the initial start, the displacement sensor (5) senses the spindle deviation by manually turning the cylinder 3-5 times, and the controller drives the energy storage device to supply oil to each hydraulic cylinder (2) to complete the swing calibration.

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