Offset test bench for testing comprehensive performance of tilting-pad radial sliding bearing under high-temperature and high-specific-pressure working conditions

Abstract

The invention belongs to the technical field of bearing performance testing, and particularly relates to an offset test bench for testing comprehensive performance of a tilting-pad radial sliding bearing under high-temperature and high-specific-pressure working conditions, which is used for testing the comprehensive performance of the tilting-pad radial sliding bearing (test bearing) under the high-temperature and high-specific-pressure working conditions. Comprising a rotor shaft, a driving system, a loading system, a lubricating system and a testing system, the driving system is used for driving the rotor shaft to rotate; the loading system is used for loading a load to the test bearing; the lubricating system is used for supplying temperature-adjustable lubricating oil to the accompanying test bearing, the loading bearing and the test bearing; the test system is used for acquiring test data. Compared with the prior art, the test device solves the problems that a test device in the prior art cannot reach high-temperature and heavy-load test conditions, so that a bearing performance result under a high-temperature and high-specific-pressure extreme working condition (shot by a missile) cannot be obtained; the tilting-pad sliding bearing high-temperature heavy-load test bench constructed by the scheme realizes high-temperature heavy-load working condition assessment of the bearing.

Description

Technical Field

[0001] The invention belongs to the technical field of bearing performance testing, and in particular relates to an offset test bench for testing the comprehensive performance of a tilting pad radial sliding bearing under high temperature and high specific pressure conditions. Background Art

[0002] Sliding bearings are widely used in large ship gas turbines abroad due to their excellent operating performance. However, since the generators in ship gas turbines need to maintain high-speed operation for a long time during combat, the temperature of the system will increase significantly, and after the viscosity of the lubricating oil decreases, the bearing capacity of the sliding bearing will also be greatly affected; at the same time, considering the extreme conditions during combat, such as the impact caused by being hit by shells or missiles, it is of great significance to conduct high-temperature and heavy-load working condition assessment of tilting pad radial sliding bearings. Therefore, the comprehensive performance test of sliding bearings is still one of the key issues studied at home and abroad.

[0003] The invention patent application with application number: 202111332889.X discloses a positive fluid-supported tilting pad sliding bearing test bench, including a main shaft; a power input system coupled to the main shaft for providing rotational power to the main shaft; a loading system installed in the middle of the main shaft for providing loading to the main shaft; a left half bearing system including a first loading seat and a first flexible loading device for installing a first tilting pad sliding bearing to be tested, the first tilting pad sliding bearing to be tested is sleeved on the left side of the main shaft, and the first flexible loading device acts on the first loading seat; a right half bearing system including a second loading seat and a second flexible loading device for installing a second tilting pad sliding bearing to be tested, the second tilting pad sliding bearing to be tested is sleeved on the right side of the main shaft, and the second flexible loading device acts on the second loading seat. This invention can be used to solve the problem that the prior art cannot simulate the actual engineering environment vibration test well, and has the advantages of simple structure and high test accuracy, but it will be subject to the upper limit of the loading device under high load and cannot meet the test conditions under extreme working conditions of high temperature and heavy load.

[0004] The invention patent application with application number: 202311752399.4 discloses a five-degree-of-freedom loading wind turbine main shaft sliding bearing test bench, including a base and a separate loading system, a main shaft sliding bearing system, a measuring system and a transmission system arranged on the base; the separate loading system is used to provide five-degree-of-freedom loading force to the sliding bearing in the main shaft sliding bearing system through six loading elements; the main shaft sliding bearing system is used to support and stabilize the main shaft selection, and the separate loading system, the measuring system and the transmission system are connected in series in the entire test bench; the measuring system is used to monitor the loading force provided by the separate loading system, the load on the bearing in the main shaft sliding bearing system and the torque size and working condition parameters provided by the low-speed motor in the transmission system; the transmission system is used to provide a torque to the main shaft sliding bearing system to drive the main shaft to rotate. This invention can simulate the working conditions of the bearings when a real wind turbine is running, and test and verify the radial sliding bearings and thrust bearings of the wind turbine main shaft, but it cannot complete the test conditions of high temperature and heavy load.

[0005] The utility model patent application with application number: 202320541826.3 discloses a radial loading device for a sliding bearing test bench, which is composed of a base, a bracket, a connecting bolt, a loading bearing, a high-pressure oil inlet pipe, a loading bracket, a hydraulic cylinder, a connecting flange, a pin A, a loading shaft, a pin B, and a cotter pin. The radial loading device of the utility model can load the bracket through the hydraulic cylinder according to the test requirements, and apply a radial load to the loading shaft through the force transmission of the loading bearing, thereby achieving a radial loading effect on the entire test bench. The radial loading device of this invention is easy to install and the loading method is safer, but it cannot form a uniform load on the radial sliding bearing, which causes the measurement results to easily produce large deviations and are not in line with reality.

[0006] The above patents have achieved to some extent that the comprehensive performance of sliding bearings can be measured more accurately under different working conditions, but none of them can meet the test conditions of the high temperature and heavy load extreme working conditions of the generator in the ship gas turbine. It can be seen that there is a lack of systematic research on the test method for forming high temperature and high pressure ratio conditions on the tilting pad sliding bearing-rotor shaft system, and it is impossible to obtain the comprehensive performance conditions under extreme conditions of high temperature and high pressure ratio. In order to develop sliding bearings used in large ship gas turbines in my country, it is necessary to develop an offset test bench to test the comprehensive performance of tilting pad radial sliding bearings under high temperature (high temperature resistance above 120°C) and high pressure ratio conditions (average pressure ratio exceeds 4.5MPa, maximum oil film pressure exceeds 20MPa). Summary of the invention

[0007] The purpose of the present invention is to solve the above-mentioned problem and provide an offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high pressure ratio conditions, so as to solve the problem that the test equipment for sliding bearing performance testing in the prior art cannot meet the test conditions of high temperature and heavy load extreme conditions (missile hit) of the generator in the ship gas turbine, and thus cannot obtain the bearing performance results under extreme conditions of high temperature and high pressure ratio. The high temperature and heavy load test bench for tilting pad sliding bearings constructed by this scheme realizes the working condition assessment of the bearings under the extreme conditions of high temperature and heavy load of the generator in the ship gas turbine.

[0008] The purpose of the present invention is achieved through the following technical solutions:

[0009] An offset test bench for testing the comprehensive performance of a tilting pad radial sliding bearing under high temperature and high specific pressure conditions, which is used to test the comprehensive performance of a tilting pad radial sliding bearing under high temperature and high specific pressure conditions, and includes a drive system, a loading system, a lubrication system and a test system;

[0010] The loading system comprises a test bearing, a rotor shaft, a loading bearing and a hydraulic loading machine; the test bearing, the loading bearing and the test tilting pad radial sliding bearing (the test bearing) are respectively sleeved and supported on the rotor shaft; the loading bearing is arranged between the test bearing and the test tilting pad radial sliding bearing, and the loading bearing is arranged close to the test tilting pad radial sliding bearing to form an offset loading structure; the hydraulic loading machine applies a load to the loading bearing, and the loading bearing transfers the load to the test tilting pad radial sliding bearing through the rotor shaft;

[0011] The driving system is used to drive the rotor shaft to rotate;

[0012] The lubrication system is used to supply temperature-controlled lubricating oil to the test bearing, the loading bearing and the test tilting pad radial sliding bearing;

[0013] The test system is used to obtain test data of an offset test bench and a tilting pad radial sliding bearing.

[0014] Preferably, the loading bearing is arranged close to the test tilting pad radial sliding bearing. When the load is distributed in the center (positive loading structure), only half of the pressure output load of the hydraulic loader can be applied to the test bearing (test tilting pad radial sliding bearing), and its loading utilization rate is only 50% at most. Therefore, the hydraulic loader must apply at least 2 times the loading load required for the measurement to achieve the target performance measurement. Under such a high load, whether the drive motor can continuously drive the rotor shaft to rotate is also a difficult problem; therefore, this solution is aimed at high temperature and heavy load conditions. The test bench adopts an offset loading scheme, which can achieve a loading utilization rate of 80% to 90% or even higher, so as to reduce the output requirements of the hydraulic loader and the drive motor while maximally assessing the load-bearing capacity of the test tilting pad radial sliding bearing. In addition, this test bench will adopt an offset loading scheme, which can not only reduce the output requirements of the hydraulic loader, but also more accurately simulate the offset load conditions that the bearing (test tilting pad radial sliding bearing) may encounter in actual work.

[0015] Preferably, the hydraulic loading head of the hydraulic loading machine is connected with a radial pressure plate, and the hydraulic loading machine applies a uniform radial force to the loading bearing through the radial pressure plate. Considering that if the loading force acts directly on the loading bearing (or the bearing seat on which the loading bearing is assembled), it will cause the bearing shell to produce an eccentric load, a radial pressure plate is designed on the hydraulic loading head of the hydraulic loading machine. When the hydraulic loading machine is working, the force is loaded on the radial pressure plate, and the radial pressure plate acts on the loading bearing to achieve uniform loading of the radial force.

[0016] Preferably, the lubrication system comprises a lubrication oil tank, a lubrication oil cooler, a lubrication oil filter, a lubrication oil delivery pump and an electric heater;

[0017] The electric heater is arranged in the lubricating oil tank and is used to heat the lubricating oil to increase the temperature of the lubricating oil;

[0018] The lubricating oil filter is connected to the lubricating oil tank through a lubricating oil delivery pump, and the lubricating oil cooler is connected to the lubricating oil filter;

[0019] The accompanying test bearing, the loading bearing and the test tilting pad radial sliding bearing are connected to a lubricating oil cooler.

[0020] Preferably, the test bearing, the loading bearing and the test tilting pad radial sliding bearing are also connected to the lubricating oil tank through an oil return pipeline to achieve lubricating oil recovery;

[0021] A magnetic net integrated device is also provided between the companion test bearing, the loading bearing, the test tilting pad radial sliding bearing and the lubricating oil tank for filtering the recovered lubricating oil.

[0022] Preferably, the lubrication system further comprises a first lubricating oil temperature sensor, a second lubricating oil temperature sensor and a third lubricating oil temperature sensor;

[0023] The first lubricating oil temperature sensor is arranged downstream of the lubricating oil cooler and is used to measure the temperature of the lubricating oil input into the test bearing, the loading bearing and the test tilting pad radial sliding bearing;

[0024] The second lubricating oil temperature sensor and the third lubricating oil temperature sensor are respectively arranged outside and inside the lubricating oil tank, and are used to measure the temperature outside and inside the lubricating oil tank respectively.

[0025] The lubrication system achieves effective temperature control of the lubricating oil through the coordinated use of electric heaters and multiple sensors, and can then change the test temperature conditions to meet the needs of the test conditions (such as normal temperature, high temperature, etc.); and, through different types of second lubricating oil temperature sensors and third lubricating oil temperature sensors, the temperature inside and outside the lubricating oil tank is tested to ensure the reliability of temperature measurement.

[0026] Preferably, the drive system comprises a drive motor and a coupling;

[0027] The driving motor is a variable frequency motor;

[0028] The output end of the driving motor is connected to the rotor shaft through a coupling. The driving system can drive the entire bearing-rotor shaft system (including the rotor shaft and loading system of this test bench) and can achieve stepless speed regulation.

[0029] Preferably, the companion bearing is assembled in the first fixed bearing seat, the loading bearing is assembled in the floating bearing seat, and the test tilting pad radial sliding bearing is assembled in the second fixed bearing seat;

[0030] The bottom of the floating bearing seat has no support.

[0031] Preferably, the test system comprises a sensor group and a data acquisition card which are communicatively connected;

[0032] The sensor group comprises:

[0033] a first pressure sensor for measuring the oil film pressure of the test tilting pad radial sliding bearing, a first displacement sensor for measuring the oil film thickness of the test tilting pad radial sliding bearing, a first temperature sensor for measuring the oil film temperature of the test tilting pad radial sliding bearing, and,

[0034] Tension and compression sensors for measuring radial loads on hydraulic loaders, and,

[0035] a rotation speed sensor for measuring the rotation speed of the rotor shaft, a second displacement sensor for measuring the displacement of the rotor shaft, and

[0036] A second temperature sensor for measuring the oil inlet temperature of the lubrication system, a second pressure sensor for measuring the oil inlet pressure of the lubrication system, a flow sensor for measuring the oil inlet flow of the lubrication system and a third temperature sensor for measuring the oil outlet temperature of the lubrication system.

[0037] More preferably, the data acquisition card is connected to a computer for communication. The computer displays the maximum pressure in real time through LabVIEW, so as to better observe the real-time changes of the test tilting pad radial sliding bearing, and also processes and displays the pressure of the hydraulic loader, the average specific pressure of the test bearing (test tilting pad radial sliding bearing), the oil film pressure of the five pads, and the maximum oil film pressure and bearing pad temperature calculated therefrom, so that the relevant test data such as the pad temperature and oil film pressure of the test tilting pad radial sliding bearing can be displayed in real time in the form of a visualized icon or curve, which greatly facilitates the observation of the performance during actual operation.

[0038] More preferably, the maximum oil film pressure P is obtained by theoretically calculating the oil film pressure at the measuring point of the pad and the maximum oil film pressure of the pad under various pressure ratios and performing comparative analysis on the actual test data. max Conversion formula with measuring point pressure x: P max =-0.007869x 3 +0.2031x 2 +0.7175x+0.08896, therefore, the maximum oil film pressure P can be calculated based on the oil film pressure x at the measuring point obtained in real time by the first pressure sensor. max .

[0039] Preferably, the extreme operating conditions applied by the offset test bench to the tilting pad radial sliding bearing include: an average specific pressure exceeding 4.5 MPa, a maximum pressure exceeding 20 MPa, and a maximum temperature exceeding 120°C.

[0040] Compared with the prior art, the present invention has the following beneficial effects:

[0041] The test bench of the present invention can provide high temperature and high specific pressure working conditions and apply bias loads to conduct comprehensive performance tests on tilting pad radial sliding bearings, and conduct comprehensive performance test studies on tilting pad radial sliding bearings in consideration of the extreme environments that ships may encounter during actual service. Ultimately, the evolution laws of static characteristics (bearing capacity, flow, friction power consumption, temperature rise, axis trajectory) and dynamic characteristics (stiffness, damping) and stability (instability speed) of the generator sliding bearings in ship gas turbines under high temperature and high specific pressure bias loads can be revealed, thereby optimizing the structure and parameters of the tilting pad radial sliding bearings, and forming a structural design and performance analysis method for tilting pad radial sliding bearings for ships under the action of systematic alternating loads, thereby providing technical support for the modification and stable operation of the tilting pad radial sliding bearings of ship gas turbine generators, and ensuring the upgrading of ship gas turbines ranked first in the national innovation project. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] Figure 1 It is a structural schematic diagram of the offset test bench of the present invention;

[0043] Figure 2 It is a structural schematic diagram of the loading system (loading bearing part) of the present invention;

[0044] Figure 3 It is a schematic diagram of the lubricating oil circuit connection structure of the lubricating system of the present invention;

[0045] Figure 4 A schematic diagram of the circuit connection structure of the test system of the present invention;

[0046] Figure 5 It is a schematic diagram of the hydraulic oil circuit connection structure of the loading system of the present invention;

[0047] Figure 6 The interface diagram of LabVIEW configured in Example 1;

[0048] In the figure: 1-driving motor; 2-coupling; 3-first oil seal; 4-accompanying test bearing; 5-first fixed bearing seat upper cover; 6-first fixed bearing seat lower cover; 7-pad; 8-first fixed bearing seat; 9-rotor shaft; 10-second oil seal; 11-floating bearing seat; 12-loading bearing; 13-hydraulic loader; 14-test tilting pad radial sliding bearing; 15-second fixed bearing seat upper cover; 16-second fixed bearing seat lower cover; 17-third oil seal; 18-base;

[0049] 201-hydraulic loading head; 202-loading connection seat; 203-bracket; 204-radial pressure plate; 205-hydraulic motor; 206-hydraulic oil pump; 207-hydraulic oil tank; 208-hydraulic oil filter; 209-three-position four-way electromagnetic reversing valve; 210-one-way throttle valve; 211-hydraulic lock; 212-relief valve; 213-accumulator; 214-hydraulic pressure gauge;

[0050] 301-first ball valve; 302-lubricating oil tank; 303-safety valve; 304-electric control box; 305-differential pressure controller; 306-second ball valve; 307-third ball valve; 308-pressure switch; 309-first lubricating oil temperature sensor; 310-lubricating oil cooler; 311-magnetic network integrated device; 312-lubricating oil filter; 313-second lubricating oil temperature sensor; 314-air filter; 315-seismic pressure gauge; 316-pressure gauge switch; 317-check valve; 318-lubricating oil delivery pump; 319-electric heater; 320-liquid level gauge; 321-liquid level controller; 322-third lubricating oil temperature sensor;

[0051] 401-computer; 402-data acquisition card; 403-lubricating oil station; 404-lubricating oil outlet pipe; 405-lubricating oil return pipe. DETAILED DESCRIPTION

[0052] The present invention is described in detail below with reference to the accompanying drawings and specific embodiments.

[0053] Example 1

[0054] An offset test bench for testing the comprehensive performance of a tilting pad radial sliding bearing 14 under high temperature and high specific pressure conditions, such as Figure 1-Figure 6 As shown, the test for testing the comprehensive performance of the tilting pad radial sliding bearing 14 under high temperature and high specific pressure conditions includes a drive system, a loading system, a lubrication system and a test system;

[0055] The loading system includes a test bearing 4, a rotor shaft 9, a loading bearing 12 and a hydraulic loading machine 13; the test bearing 4, the loading bearing 12 and the test tilting pad radial sliding bearing 14 are respectively sleeved on the rotor shaft 9; the loading bearing 12 is arranged between the test bearing 4 and the test tilting pad radial sliding bearing 14, and the loading bearing 12 is arranged close to the test tilting pad radial sliding bearing 14 to form an offset loading structure; the hydraulic loading machine 13 applies a load to the loading bearing 12, and the loading bearing 12 transfers the load to the test tilting pad radial sliding bearing 14 through the rotor shaft 9;

[0056] The driving system is used to drive the rotor shaft 9 to rotate;

[0057] The lubrication system is used to supply temperature-controlled lubricating oil to the companion bearing 4, the loading bearing 12 and the test tilting pad radial sliding bearing 14;

[0058] The test system is used to obtain test data of the offset test bench and the tilting pad radial sliding bearing 14 .

[0059] More specifically, in this embodiment:

[0060] The offset test bench is used to test the comprehensive performance of the test bearing (in this embodiment, the test tilting pad radial sliding bearing 14, which includes 5 arc-shaped pads) under high temperature and high specific pressure conditions. Figure 1 As shown, it specifically includes a driving system, a loading system, a lubrication system and a testing system, as well as a rotor shaft 9 driven by the driving system.

[0061] The drive system is composed of a drive motor 1 and a coupling 2. The output end of the drive motor 1 is connected to the rotor shaft 9 through the coupling 2, and the drive motor 1 can drive the rotor shaft 9 to rotate through the transmission of the coupling 2. The drive motor 1 adopts a variable frequency motor, and thus it can achieve stepless speed regulation of the speed of the rotor shaft 9; the coupling 2 adopts a double flange plum blossom coupling 2 to ensure a reliable connection between the drive motor 1 and the rotor shaft 9 while avoiding the load applied to the rotor shaft 9 by the loading system through the loading bearing 12, which affects the normal operation of the drive motor 1 or causes structural damage. The drive motor 1 is installed on the cast iron base 18 at the bottom through the motor seat.

[0062] The loading system includes a test bearing 4, a rotor shaft 9, a loading bearing 12 and a hydraulic loader 13. The test bearing 4 (the test bearing 4 in this embodiment also adopts a tilting pad radial sliding bearing) is assembled in the first fixed bearing seat 8, the loading bearing 12 (the loading bearing 12 in this embodiment adopts a sliding circular bearing) is assembled in the floating bearing seat 11, the test tilting pad radial sliding bearing 14 is assembled in the second fixed bearing seat, and the hydraulic loader 13 is also connected to the hydraulic pump station to provide sufficient hydraulic loading force.

[0063] The test bearing 4, the loading bearing 12 and the test tilting pad radial sliding bearing 14 are sequentially sleeved on the rotor shaft 9, the test bearing 4 is arranged close to the end of the rotor shaft 9 connected to the drive motor 1, the test tilting pad radial sliding bearing 14 is arranged away from the end of the rotor shaft 9 connected to the drive motor 1, the loading bearing 12 is located between the test bearing 4 and the test tilting pad radial sliding bearing 14, and the loading bearing 12 is arranged close to the test tilting pad radial sliding bearing 14; the output end of the hydraulic loader 13 is arranged toward the loading bearing 12, and the bottom of the floating bearing seat 11 corresponding to the loading bearing 12 does not contact the cast iron base 18 (the bottom has no support), and then the load (loading force) applied by the hydraulic loader 13 to the loading bearing 12 will first act on the rotor shaft 9, and then the load will be applied to the test tilting pad radial sliding bearing 14 through the rotor shaft 9, forming an offset loading structure.

[0064] In the offset loading structure, the loading force is applied close to the test tilting pad radial sliding bearing 14. Therefore, according to the moment balance, it can be known that due to the short force arm, the test tilting pad radial sliding bearing 14 will bear a larger component force, and then the loading utilization rate can reach 80-90%, thereby reducing the output requirements of the hydraulic loader 13 and maximally assessing the load-bearing capacity of the test tilting pad radial sliding bearing 14. In the conventional positive center distribution, only half of the output load of the hydraulic loader 13 can be applied to the test tilting pad radial sliding bearing 14, that is, the loading utilization rate is only 50%. Therefore, for the test conditions required for the test tilting pad radial sliding bearing 14, the hydraulic loader 13 needs to load at least 2 times the load to achieve it. Under this high load, whether the drive motor 1 can still drive the rotor shaft 9 to rotate causes great difficulties to the structure and power of the drive motor 1. It can be seen that the offset loading structure can effectively improve the loading utilization rate to obtain a higher specific pressure test condition.

[0065] The first fixed bearing seat 8 is composed of a first fixed bearing seat upper cover 5 and a first fixed bearing seat lower cover 6 installed on a cushion block 7 that acts as a shock absorber, and both sides of the first fixed bearing seat 8 are sealed by first oil seals 3 respectively; the first fixed bearing seat 8 is assembled on a cast iron base 18.

[0066] The two sides of the floating bearing seat 11 are sealed by the second oil seal 10. Figure 2As shown, the loading bearing 12 is sleeved on the outside of the rotor shaft 9 and assembled inside the floating bearing seat 11, and the output end (hydraulic loading head 201) of the hydraulic loading machine 13 applies load to the loading bearing 12. The hydraulic loading machine 13 is installed on the bracket 203 through the loading connection seat 202, and the bracket 203 is further fastened and installed on the cast iron base 18 by bolts. The hydraulic loading head 201 passes through the bracket 203 and extends into the interior and abuts against the floating bearing seat 11; considering that if the loading force acts directly on the floating bearing seat 11, it will cause the loading bearing 12 to generate an eccentric load, so a radial pressure plate 204 is designed to be connected to one end of the hydraulic loading head 201, and then when the hydraulic loading machine 13 is working, the force is first loaded on the radial pressure plate 204, and then the radial pressure plate 204 acts evenly on the floating bearing seat 11 to achieve uniform loading of radial force.

[0067] The second fixed bearing seat is composed of a second fixed bearing seat upper cover 15 and a second fixed bearing seat lower cover 16, and both sides of the second fixed bearing seat are sealed by third oil seals 17; the second fixed bearing seat is installed on a cast iron base 18. When the load loading test is carried out, the radial load of the rotor shaft 9 is balanced by the test tilting pad radial sliding bearing supported by the second fixed bearing seat.

[0068] The hydraulic pump station connected to the hydraulic loader 13 provides a pressure source for the hydraulic loader 13 to drive the hydraulic loader 13 to generate a loading force, such as Figure 5 As shown, the two are connected by explosion-proof oil pipes. The hydraulic pump station is composed of hydraulic motor 205, hydraulic oil tank 207, hydraulic oil pump 206 and accumulator 213. Among them: hydraulic motor 205 is a three-phase asynchronous motor of LZJ, with a specific model of YCB132S, adapted to 380V voltage, rated power of 5.5kW, and can provide sufficient power to drive the entire hydraulic system; hydraulic oil pump 206 uses an axial piston pump of Jiangsu Hongda High Pressure Oil Pump Manufacturing Co., Ltd., model 10YCY14-1B, with a rated pressure of up to 31.5MPa and a rated speed of 1500rpm, ensuring that it can provide stable and strong oil pressure; accumulator 213 uses NXQ series bladder accumulator of Ningbo Fenghua Yasheng Hydraulic Manufacturing Co., Ltd., with a model of NXQ-A-10-31.5, a volume of 10 liters, and a maximum pressure of 31.5MPa, which helps the system to buffer pressure when a quick response is required and maintain the system's pressure stability. In addition, the hydraulic loader 13 is an integrated design, which can well meet the loading requirements while saving space. Its model is HSG series 100*100-FA, and its basic parameters are shown in Table 1.

[0069] Table 1 Basic parameters of hydraulic loader

[0070] model HSG 100*100-FA Nominal pressure(MPa) 16 Cylinder diameter (mm) 100 Rod diameter(mm) 50 Maximum stroke (mm) 800 Minimum stroke of non-hinge shaft connection (mm) 40

[0071] The hydraulic loading oil circuit diagram of the hydraulic system is as follows Figure 5 As shown, stable and reliable loading is provided for the hydraulic loader 13, wherein: the hydraulic motor 205 drives the hydraulic oil pump 206 to work, and the hydraulic oil in the hydraulic oil tank 207 flows to the three-position four-way electromagnetic reversing valve 209 after passing through the hydraulic oil filter 208, and then flows through the hydraulic lock 211 after entering the one-way throttle valve 210, and finally pushes the piston rod in the hydraulic cylinder body of the hydraulic loader 13 to move, thereby realizing loading. The three-position four-way electromagnetic reversing valve 209 can change the flow direction of the hydraulic oil to achieve the extension and retraction of the piston rod of the hydraulic loader 13; the one-way throttle valve 210 can adjust the flow of the inlet and outlet oil to control the speed of the piston rod movement; the hydraulic lock 211 can achieve one-way flow of the hydraulic oil to prevent oil return, thereby ensuring that the cylinder of the hydraulic loader 13 remains stationary when the external load is generated; the overflow valve 212 can adjust the pressure generated by the hydraulic loader 13; the accumulator 213, as an energy storage device, can be used for vibration reduction and shock absorption, and can convert compression energy into hydraulic energy and release it to maintain pressure; the hydraulic pressure gauge 214 can measure the pressure and display it in real time.

[0072] Therefore, when the loading system is loading, first, the hydraulic pump station drives the hydraulic oil pump 206 by the hydraulic motor 205 to output the hydraulic oil with pressure, and the hydraulic oil is pumped to the hydraulic loader 13 through the explosion-proof oil pipe. The hydraulic loader 13 drives the hydraulic loading head 201 to apply the load to the loading bearing 12. Combined with the offset structure, the test bench can apply a heavy load that makes the average specific pressure of the test tilting pad radial sliding bearing 14 reach more than 4.5MPa, and the system has a good pressure maintenance effect. It can still output the load stably under long-term working conditions, and there will be no pressure loss that causes inaccurate test results, effectively realizing the assessment of the test tilting pad radial sliding bearing 14 under high specific pressure conditions. In addition, the offset loading scheme adopted by this test bench can not only reduce the output demand of the hydraulic loader 13, but also more accurately simulate the offset load situation that the test tilting pad radial sliding bearing 14 may encounter in actual work.

[0073] like Figure 3The figure shows the wiring diagram of the lubrication system. The lubrication system is a lubrication oil station 403, through which lubrication oil is supplied to and recovered from each bearing in the loading system and the test bearing. The lubrication system specifically includes a lubrication oil tank 302, a lubrication oil delivery pump 318, a lubrication oil filter 312 and a lubrication oil cooler 310 connected in sequence. The lubrication oil cooler 310 outputs the lubrication oil to each bearing of the test bench, and the lubrication oil returned by each bearing is recovered into the lubrication oil tank 302. The lubricating oil tank 302 is a carbon steel oil tank, and an electric heater 319 is also provided in the lubricating oil tank 302 to heat the lubricating oil and increase the oil temperature; a second lubricating oil temperature sensor 313 and a third lubricating oil temperature sensor 322 are provided to detect the ambient temperature outside the lubricating oil tank 302 and the temperature of the lubricating oil in the lubricating oil tank 302, respectively, and then obtain the temperature difference between the inside and outside of the lubricating oil tank 302 by feedback control to ensure that the temperature of the lubricating oil in the lubricating oil tank 302 does not exceed the limit temperature. The second lubricating oil temperature sensor 313 and the third lubricating oil temperature sensor 322 are different types of temperature sensors. Specifically, the second lubricating oil temperature sensor 313 is a platinum thermal resistor, and the third lubricating oil temperature sensor 322 is a platinum thermal resistor. The temperature sensor 322 is a bimetallic thermometer; a magnetic mesh integrated device 311 is provided to filter the lubricating oil recovered into the lubricating oil tank 302; a liquid level meter 320 and a liquid level controller 321 are provided, the liquid level meter 320 is used to detect the lubricating oil level in the lubricating oil tank 302, and the liquid storage amount is controlled by the liquid level controller 321 according to the liquid level obtained by the liquid level meter 320 to avoid too much or too little lubricating oil in the lubricating oil tank 302; an air filter 314 is also provided on the lubricating oil tank 302 to ensure that the lubricating oil tank 302 is ventilated while preventing impurities in the air from entering the interior of the lubricating oil tank 302; a first ball valve 301 (ball valve G1) is also provided at the bottom of the lubricating oil tank 302. The lubricating oil delivery pump 318 adopts a vertical gear pump; a one-way valve 317 and a safety valve 303 connected to the lubricating oil tank 302 are also provided on the pipeline between the lubricating oil delivery pump 318 and the lubricating oil filter 312; the one-way valve 317 prevents the lubricating oil from flowing back from the lubricating oil delivery pump 318, and the safety valve 303 is used to recover the lubricating oil in the pipeline when there is too much lubricating oil in the pipeline and the oil pressure is too high. The lubricating oil filter 312 is a double-tube filter, one for use and one for backup; the upstream and downstream of the lubricating oil filter 312 are respectively connected to a differential pressure controller 305 to measure the pressure difference between the inlet and outlet of the lubricating oil filter 312. A valved passage is also connected in parallel between the upstream and downstream of the lubricating oil cooler 310, so that the lubricating oil can pass through the valved passage when there is no need to cool the lubricating oil; the lubricating oil cooler 310 is a shell-and-tube cooler, and its cooling source is cooling water. Its upstream and downstream are controlled by the second ball valve 306 (ball valve G1.1 / 4), and the cooling water inlet and outlet for heat exchange are controlled by the third ball valve 307 (ball valve G1.1 / 2).Downstream of the lubricating oil cooler 310, a pressure switch 308, a shockproof pressure gauge 315, a pressure gauge switch 316 and a first lubricating oil temperature sensor 309 (platinum thermal resistor) are also connected to detect the state of the lubricating oil output by the lubricating system to each bearing. In addition, the lubricating system also includes an electric control box 304, which is electrically connected to each sensor and each control valve in the lubricating system to receive data and instruct actions to achieve control of the lubricating system.

[0074] After the lubricating oil station 403 supplies the lubricating oil, the lubricating oil is transported through the pipeline, and the lubricating oil that passes through the lubricating oil filter 312 flows to the bearing seats where the test tilting pad radial sliding bearing 14, the accompanying test bearing 4 and the loading bearing 12 are located after passing through the hydraulic distributor, and finally flows back to the lubricating oil tank 302 through the return oil pipeline after lubricating each bearing, so as to realize the circulating oil supply. The lubricating oil supply temperature of the lubricating bearing can be adjusted between room temperature and high temperature according to actual needs to realize different temperature working conditions.

[0075] The lubricating oil station 403 in this embodiment can preferably be of XYZ-63G type. Through the use of the electric heater 319, the lubricating oil cooler 310 and various temperature sensors, the temperature of the lubricating oil output to each bearing can be controlled. For example, the lubricating oil can be adjusted to room temperature or high temperature to provide different temperature conditions. Therefore, the lubrication system can provide the test bench with a maximum test condition of more than 120°C.

[0076] Test systems such as Figure 4As shown, the sensor group includes a computer 401, a data acquisition card 402, and various sensors. The sensor group is connected to the data acquisition card 402 for communication, and the collected data has been sent to the data acquisition card 402. The data acquisition card 402 is then connected to the computer 401 for communication, and the various data are collected in the computer 401 for processing and display. The test system mainly completes the collection, display and storage of bearing performance parameters such as oil film pressure, oil film temperature, and axis trajectory of the tilting pad radial sliding bearing 14, as well as parameters such as the speed, vibration amplitude, and radial loading force of the rotor shaft 9 through the sensor group and the data acquisition card 402. More specifically, the sensor group consists of a pressure sensor for measuring the oil film pressure of the test tilting pad radial sliding bearing 14, an eddy current displacement sensor for measuring the oil film thickness of the test tilting pad radial sliding bearing 14, a temperature sensor for measuring the oil film temperature of the test tilting pad radial sliding bearing 14, a tension and pressure sensor for measuring the radial loading force of the hydraulic loader 13, a Hall speed sensor for measuring the rotational speed of the rotor shaft 9, an eddy current displacement sensor for measuring the displacement of the rotor shaft 9, a temperature sensor for measuring the return oil temperature, pressure, and flow rate in the lubricating oil return pipe 405 of the lubricating oil station 403 (lubricating system), a pressure sensor, a flow rate sensor, and a temperature sensor for measuring the oil outlet temperature in the lubricating oil outlet pipe 404 of the lubricating oil station 403 (wherein, the sensor for measuring the parameters of the lubricating oil station 403 can directly use the data of the corresponding sensor set in the lubricating system). After the collected data are input into the computer 401, LabVIEW is used to realize the visualization transformation of the data, and the test data and test results are presented in the form of visualized icons or curves, including: real-time display of the maximum pressure, so as to better observe its real-time changes, processing and displaying the pressure of the hydraulic loader 13, the average specific pressure of the test tilting pad radial sliding bearing 14, the oil film pressure of the five pads in the test tilting pad radial sliding bearing 14, and the maximum oil film pressure, and the pad temperature of the test tilting pad radial sliding bearing 14. Figure 6 The interface shown can display relevant test data such as pad temperature and oil film pressure of the test tilting pad radial sliding bearing 14 in real time, which greatly facilitates the observation of the performance of the bearing during actual operation. Among them, the sensors (including but not limited to tension and pressure sensors) at the hydraulic loading head 201 are connected by precise threads to ensure stable force transmission and precise measurement and control during loading.

[0077] Considering that arranging sensor measuring points by slotting on the pad of the test tilting pad radial sliding bearing 14 will reduce the pressure at that point to a certain extent and affect its bearing capacity, resulting in a deviation between the theoretical calculated pressure and the actual measured pressure at the measuring point position, and the number of pressure measuring points arranged on the pad is limited, and the measuring point position is not at the maximum oil film pressure point, it is impossible to arrange the sensor exactly at the maximum pressure and directly measure the maximum pressure value. Therefore, this embodiment also proposes a method for converting the actual pressure value at the bearing measuring point and the maximum pressure value of the pad, so that the maximum oil film pressure value on the pad can be quickly calculated by obtaining the oil film pressure value of the measuring point during the actual test.

[0078] The conversion method is: Through theoretical calculation, various specific pressures can be obtained that are close to the maximum pressure P max The measuring point pressure P3 and the maximum pressure P max The polynomial fitting mapping relationship is shown in the following formula (I):

[0079]

[0080] Considering the influence of the grooves on the surface of the tile, there is a deviation between the theoretical pressure P3 at the measuring point and its actual measured value x. The conversion coefficient k can be further introduced to obtain P3 = kx. Through experiments, it can be determined that k = 1.3527. Then, the maximum oil film pressure value P on the tile can be quickly calculated from the oil film pressure value x at the measuring point. max The conversion relationship is formula (II):

[0081] P max =-0.007869x 3 +0.2031x 2 +0.7175x+0.08896 (II);

[0082] In summary, the test bench can realize automatic control and manual operation, and can proportionally restore the original bearing-rotor shaft 9 system of the maneuvering turbine section of the ship's gas turbine; the drive system can drive the entire bearing-rotor shaft 9 system, and can realize stepless speed regulation; the loading system can realize adjustable and controllable load loading, and can realize relatively precise control of the magnitude of the loading force; the lubrication system can realize stable oil supply (oil supply temperature is adjustable) and oil return, the oil supply pressure and flow are both controllable and adjustable, and the control and collection of lubricating oil pressure, temperature, and flow information can be realized, and finally the test bearing (test tilting pad radial sliding bearing 14) can be operated under extremely high pressure, high temperature and heavy load conditions (missile hit) with an average pressure ratio exceeding 4.5MPa, a maximum pressure of the pad exceeding 20MPa, and a maximum temperature exceeding 120°C, which makes up for the defect that the existing technology cannot be tested under such extreme conditions. The test system can monitor the operating status of the tilting pad radial sliding bearing 14 in real time, collect, save and display the lubrication performance parameters of the tilting pad radial sliding bearing 14 under different test conditions, and present the data and results in the form of visual icons or curves ( Figure 6 ).

[0083] Therefore, the high-pressure and high-temperature rotor shaft 9 sliding bearing comprehensive performance test bench designed by the present invention will provide design basis, theoretical foundation and experimental support for breaking through and mastering the dynamic design technology of the ship gas turbine rotor shaft 9 sliding bearing as soon as possible and solving related major engineering problems, thereby ensuring the upgrading of the ship gas turbine ranked first in the national innovation project.

[0084] The above description of the embodiments is to facilitate the understanding and use of the invention by those skilled in the art. It is obvious that those skilled in the art can easily make various modifications to these embodiments and apply the general principles described herein to other embodiments without creative work. Therefore, the present invention is not limited to the above embodiments, and improvements and modifications made by those skilled in the art based on the disclosure of the present invention without departing from the scope of the present invention should be within the scope of protection of the present invention.

Claims

1. An offset test bench for testing the comprehensive performance of a tilting pad radial sliding bearing under high temperature and high specific pressure conditions, used for testing the comprehensive performance of a tilting pad radial sliding bearing (14) under high temperature and high specific pressure conditions, characterized in that: Including driving system, loading system, lubrication system and testing system; The loading system comprises a rotor shaft (9), a test bearing (4), a loading bearing (12) and a hydraulic loading machine (13); the test bearing (4), the loading bearing (12) and the test tilting pad radial sliding bearing (14) are respectively sleeved and supported on the rotor shaft (9); the loading bearing (12) is arranged between the test bearing (4) and the test tilting pad radial sliding bearing (14), and the loading bearing (12) is arranged close to the test tilting pad radial sliding bearing (14) to form an offset loading structure; the hydraulic loading machine (13) applies a load to the loading bearing (12), and the loading bearing (12) transmits the load to the test tilting pad radial sliding bearing (14) through the rotor shaft (9); The driving system is used to drive the rotor shaft (9) to rotate; The lubrication system is used to supply temperature-controllable lubricating oil to the test bearing (4), the loading bearing (12) and the test tilting pad radial sliding bearing (14); The test system is used to obtain test data of an offset test bench and a tilting pad radial sliding bearing (14).

2. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1 is characterized in that: The loading bearing (12) is arranged close to the test tilting pad radial sliding bearing (14).

3. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1 is characterized in that: The hydraulic loading head (201) of the hydraulic loading machine (13) is connected to a radial pressure plate (204), and the hydraulic loading machine (13) applies a uniform radial force to the loading bearing (12) through the radial pressure plate (204).

4. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1 is characterized in that: The lubrication system comprises a lubrication oil tank (302), a lubrication oil cooler (310), a lubrication oil filter (312), a lubrication oil delivery pump (318) and an electric heater (319); The electric heater (319) is arranged in the lubricating oil tank (302) and is used to heat the lubricating oil; The lubricating oil filter (312) is connected to the lubricating oil tank (302) via a lubricating oil delivery pump (318), and the lubricating oil cooler (310) is connected to the lubricating oil filter (312); The test bearing (4), the loading bearing (12) and the test tilting pad radial sliding bearing (14) are connected to a lubricating oil cooler (310); the test bearing (4), the loading bearing (12) and the test tilting pad radial sliding bearing (14) are also connected to a lubricating oil tank (302) to achieve lubricating oil recovery; A magnetic net integrated device (311) is also provided between the test bearing (4), the loading bearing (12), the test tilting pad radial sliding bearing (14) and the lubricating oil tank (302) for filtering the recovered lubricating oil.

5. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 4, characterized in that: The lubrication system further comprises a first lubrication oil temperature sensor (309), a second lubrication oil temperature sensor (313) and a third lubrication oil temperature sensor (322); The first lubricating oil temperature sensor (309) is arranged downstream of the lubricating oil cooler (310) and is used to measure the lubricating oil temperature of the input test bearing (4), the loading bearing (12) and the test tilting pad radial sliding bearing (14); The second lubricating oil temperature sensor (313) and the third lubricating oil temperature sensor (322) are respectively arranged outside and inside the lubricating oil tank (302), and are used to measure the temperature outside and inside the lubricating oil tank (302), respectively.

6. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1, characterized in that: The driving system comprises a driving motor (1) and a coupling (2); The driving motor (1) is a variable frequency motor; The output end of the driving motor (1) is connected to the rotor shaft (9) via a coupling (2).

7. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1, characterized in that: The test bearing (4) is assembled inside the first fixed bearing seat (8), the loading bearing (12) is assembled inside the floating bearing seat (11), and the test tilting pad radial sliding bearing (14) is assembled inside the second fixed bearing seat; The bottom of the floating bearing seat (11) has no support.

8. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1, characterized in that: The test system comprises a sensor group and a data acquisition card (402) which are communicatively connected; The sensor group comprises: A first pressure sensor for measuring the oil film pressure of a test tilting pad radial sliding bearing (14), a first displacement sensor for measuring the oil film thickness of a test tilting pad radial sliding bearing (14), a first temperature sensor for measuring the oil film temperature of a test tilting pad radial sliding bearing (14), a tension and pressure sensor for measuring the radial load of a hydraulic loader (13), a rotation speed sensor for measuring the rotation speed of a rotor shaft (9), a second displacement sensor for measuring the displacement of the rotor shaft (9), a second temperature sensor for measuring the oil inlet temperature of a lubrication system, a second pressure sensor for measuring the oil inlet pressure of the lubrication system, a flow sensor for measuring the oil inlet flow rate of the lubrication system, and a third temperature sensor for measuring the oil outlet temperature of the lubrication system.

9. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 8, characterized in that: The oil film pressure x at the measuring point obtained by the first pressure sensor shows the maximum oil film pressure P max , its conversion relationship: P max =-0.007869x 3 +0.2031x 2 +0.7175x+0.08896。 10. The offset test bench for testing the comprehensive performance of tilting pad radial sliding bearings under high temperature and high specific pressure conditions according to claim 1, characterized in that: The extreme working conditions applied by the offset test bench to the tilting pad radial sliding bearing (14) for testing include: an average specific pressure exceeding 4.5 MPa, a maximum pressure exceeding 20 MPa, and a maximum temperature exceeding 120°C.

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