CN115031965A - Test bed for simulating bearing slipping in high-speed rotating machinery and design method - Google Patents
Test bed for simulating bearing slipping in high-speed rotating machinery and design method Download PDFInfo
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Abstract
The invention discloses a test bed for simulating bearing slippage in high-speed rotating machinery and a design method; the test bed comprises a high-rotating-speed servo motor positioned on a platform base; the high-speed servo motor is connected with the high-speed rotating shaft through a diaphragm coupling; the high-speed rotating shaft is sequentially connected with a four-point angular contact ball bearing system, a loading bearing system, a cylindrical roller bearing system and a double-half inner ring angular contact ball bearing system along the axial direction; two sides of the loading bearing system are respectively provided with a bidirectional loading system along the axial direction and the radial direction; in addition, a multi-order half-power bandwidth algorithm based on a neural network is also disclosed, and is used for the damping ratio estimation of a multi-degree-of-freedom system, and the estimation precision is higher; the invention can realize the sliding research of the bearing under the working conditions of variable rotating speed, rigidity, load, temperature and lubrication, and the dynamic characteristics of the test bed are the same as those of a real high-speed rotating machine by changing the supporting rigidity and the critical rotating speed, thereby simulating the actual bearing sliding state with adjustable and controllable matching parameters.
Description
Technical Field
The invention relates to the technical field of mechanical bearing test beds, in particular to a test bed for simulating bearing slippage in high-speed rotating machinery and a design method.
Background
As important parts of high-speed rotating machinery, rolling bearings have increasingly severe working environments, which are mainly characterized in that: the rotation speed is high and the working temperature is much higher than the ambient temperature. The DN value (the inner diameter D (mm) of the bearing inner ring multiplied by the rotating speed N (r/min)) of the bearing is higher, so that the bearing often has faults such as slipping, fatigue failure, movement instability and the like, wherein the bearing slipping faults are common and account for about 34 percent of the total number of faults.
Numerous practices and studies have shown that load matching, load reversal, lubrication oil temperature and flow, bearing stiffness, rate of speed change, and eccentric mass are important causes of slip. During the actual operation of the high-speed rotating machine, the rotating speed, the rigidity, the load, the temperature and the lubrication state are in a strong coupling relation with each other, and the condition that multiple bearings slip at the same time often occurs. Therefore, it is necessary to design a multi-bearing skid test system which can simultaneously and independently research the factors and can realize matching research of the factors matched with the actual operating conditions of the high-speed rotating machinery. At present, the existing design method of the bearing slipping test bed does not consider the influence of the factors on the bearing slipping at the same time, and better research effect and application value are difficult to obtain.
The dynamics of the structure are determined by the modal parameters of the structure, including frequency, mode shape and damping ratio. At present, the analysis on the frequency and the vibration mode is more accurate, but the damping ratio analysis result is not ideal. Research has shown that the effect of damping on the dynamic response of a structure is more pronounced for an elongated flexible structure. However, the size of the damping ratio of the structure is influenced by a plurality of factors such as the structure form, the material type, the structure size and the like, and meanwhile, the modal test is easily limited by the quality of the measured data and the identification method, so that the identification precision of the damping ratio is limited. How to improve the damping ratio identification accuracy is becoming an important research topic.
The traditional half-power bandwidth method is widely applied and convenient to calculate, but is derived from a single-degree-of-freedom system and widely applied to damping ratio estimation of a multi-degree-of-freedom system in actual engineering. Because the modal parameters of the multi-degree-of-freedom system have strong coupling, the traditional half-power bandwidth algorithm can generate large errors when estimating the damping ratio.
Disclosure of Invention
The purpose of the invention is as follows: based on the problems in the background technology, the invention provides a test bed for simulating the bearing slipping in high-speed rotating machinery and a design method thereof, wherein the test bed structure can realize the slipping research of the bearing under the working conditions of variable rotating speed, variable rigidity, variable load, variable temperature and variable lubrication, and analyze the multi-working-condition multi-bearing coupling slipping mechanism. Meanwhile, the dynamic characteristics of the test bed can be the same as those of a real high-speed rotating machine by identifying modal parameters and designing critical rotating speed, and the adjustable and controllable actual bearing slipping running state matched with each parameter is further simulated. The invention designs a multi-order half-power bandwidth algorithm based on a neural network and provides a damping ratio estimation method for a multi-degree-of-freedom system.
The technical scheme is as follows: in order to achieve the purpose, the invention adopts the technical scheme that:
a test bed for simulating bearing slippage in high-speed rotating machinery comprises a high-speed servo motor positioned on a platform base; the high-speed servo motor is connected with one end of the high-speed rotating shaft through a diaphragm coupler; the high-speed rotating shaft is sequentially connected with a four-point angular contact ball bearing system, a loading bearing system, an eccentric disc, a cylindrical roller bearing system, a double-half inner ring angular contact ball bearing system, a stop washer and a round nut along the axial direction; the high-rotation-speed servo motor is controlled by a motor rotation speed control system; two sides of the loading bearing system are respectively provided with an axial bidirectional loading system along the axial left and right directions, and two sides of the loading bearing system are respectively provided with a radial bidirectional loading system along the radial direction; and a lubricating system for supplying lubricating oil to each bearing system is also arranged above the test bed.
Further, the four-point angular contact ball bearing system serving as an accompanying test system comprises a four-point angular contact ball bearing, a first bearing seat, a first oil collecting device and a first temperature sensor; the four-point angular contact ball bearing is sleeved outside the high-speed rotating shaft, the first bearing seat is of an up-down detachable structure, is sleeved on an outer ring of the four-point angular contact ball bearing and is embedded in the first oil collecting device, and two parallel positioning shafts are further arranged below the first bearing seat along the axial direction; the first oil collecting device and the first bearing seat are fixedly arranged on the platform base; the first temperature sensor is arranged in a vertical through hole of the first bearing seat;
further, the loading bearing system comprises a loading bearing, a second bearing seat, a rubber base, a loading bearing seat and a second oil collecting device; the loading bearing is sleeved on the outer ring of the high-speed rotating shaft, the loading bearing seat is in a long plate shape and is installed on the outer ring of the loading bearing in a matching mode, the loading bearing seat is installed on the second bearing seat through the rubber base in the vertical direction, and the loading bearing is embedded into the second oil collecting device fixed on the platform base.
Furthermore, the axial bidirectional loading system comprises a first bearing support, a first supporting support, a first screw rod, a first straight rod type ball joint bearing and a first force sensor which are symmetrically distributed along two sides of the high-speed rotating shaft; one end of the first screw rod is connected to a first bearing support fixed on the platform base and arranged in parallel with the high-speed rotating shaft, and the other end of the first screw rod is connected with the rotatable end of the first straight-bar type ball joint bearing; the fixed end of the first straight-bar type ball joint bearing is connected to a corresponding through hole on the loading bearing seat; the lower part of the first straight-bar type ball joint bearing is also provided with a first supporting support for supporting, and the first supporting support is fixed on the platform base; first force sensors for displaying tension and compression loads are respectively arranged at the fixed ends of the first straight rod type ball joint bearings; the first force sensors on the two sides are arranged back to back, and the distance between the first force sensors is larger than the thickness of the loading bearing pedestal.
Furthermore, the radial bidirectional loading system comprises a second bearing support, a second screw rod, a second straight rod type ball joint bearing and a second force sensor, wherein the second bearing support, the second screw rod, the second straight rod type ball joint bearing and the second force sensor are perpendicular to the direction of the high-speed rotating shaft and are symmetrically distributed on two sides of the loading bearing seat; one end of the second screw rod is connected with a second bearing support fixed on the platform base, and the other end of the second screw rod is connected with the rotatable end of the second straight-rod type ball joint bearing along the direction vertical to the high-speed rotating shaft; a positioning block matched with the loading bearing seat through groove is arranged at the fixed end of the second straight rod type ball joint bearing and used for realizing the matching with the loading bearing seat; and a second force sensor is also installed at the fixed end of the second straight rod type ball joint bearing.
Further, the cylindrical roller bearing system is used as a test system and comprises a cylindrical roller bearing, a third variable-stiffness support, a third bearing pedestal bottom plate, a third bearing pedestal, a third oil collecting device, a third temperature sensor, a third eddy current displacement sensor and a third vibration acceleration sensor; the cylindrical roller bearing is sleeved on the outer ring of the high-speed rotating shaft, and the third bearing seat is sleeved on the outer ring of the cylindrical roller bearing, embedded into the third oil collecting device and connected with the third variable-rigidity support through a third bearing seat bottom plate; the third variable stiffness bearing obtains different stiffness by changing the thickness of the bearing; the third oil collecting device comprises a left part and a right part which are symmetrical, and is fixedly connected with a third bearing seat through a bolt and a sealing ring; the third bearing seat is of a structure which can be disassembled up and down; the third temperature sensor is arranged in a vertical through hole of the third bearing seat; the third eddy current displacement sensor is arranged right opposite to the cylindrical roller bearing retainer and used for measuring the rotating speed of the cylindrical roller bearing retainer; the third vibration acceleration sensor is mounted on the third bearing seat and used for measuring vibration signals of the third bearing seat in the three directions of XYZ.
Further, the double-half inner ring angular contact ball bearing system is used as a test system and comprises a double-half inner ring angular contact ball bearing, a fourth variable-stiffness support, a fourth bearing seat bottom plate, a fourth bearing seat, a fourth oil collecting device, a fourth temperature sensor, a fourth eddy current displacement sensor and a fourth vibration acceleration sensor; the double-half inner ring angular contact ball bearing is sleeved on the outer ring of the high-speed rotating shaft, and the positions of the inner ring of the double-half inner ring angular contact ball bearing and the position of the inner ring of the cylindrical roller bearing are fixed through a positioning sleeve; the fourth bearing seat is sleeved on the outer ring of the double-half inner ring angular contact ball bearing, is embedded into the fourth oil collecting device and is connected with the fourth variable-stiffness support through a fourth bearing base plate; the fourth variable stiffness bearing obtains different stiffness by changing the thickness of the bearing; the fourth oil collecting device comprises a left part and a right part which are symmetrical, and is fixedly connected with the fourth bearing seat through a bolt and a sealing ring; the fourth bearing seat is of a vertically detachable structure; the fourth temperature sensor is arranged in a vertical through hole of the fourth bearing seat; the fourth eddy current displacement sensor is arranged right opposite to the double-half inner ring angular contact ball bearing retainer and used for measuring the rotating speed of the double-half inner ring angular contact ball bearing retainer; the fourth vibration acceleration sensor is installed on the fourth bearing seat and used for measuring vibration signals of the fourth bearing seat in the three directions of XYZ.
Further, the motor rotating speed control system comprises a programmable controller 11 and a driver 12, and the rotating speed of the high-rotating-speed servo motor is adjusted according to a given change rate; an I-shaped motor support is further arranged between the high-rotation-speed servo motor and the platform base.
Further, the lubricating system comprises an oil temperature controller, a lubricating oil pump and a lubricating spray pipe; the oil temperature controller adjusts the temperature of the lubricating oil to change within the range of 0-200 ℃ in real time; the lubricating oil pump adjusts the flow of the lubricating oil in real time and supplies the lubricating oil to each bearing system through a lubricating spray pipe.
A design method of a test bed for simulating bearing slippage in high-speed rotating machinery is based on the test bed, and is characterized by comprising the following steps:
step S1, utilizing Patran to calculate the compression resistance and bending resistance rigidity of the bearing seat, the variable rigidity support and the bearing seat bottom plate, then calculating the contact rigidity of the bearing roller, and connecting the calculated rigidity in series to obtain the total support rigidity;
step S2, respectively calculating the critical rotating speed of the test bed under different overall supporting rigidity by designing the supporting rigidity of the bearing;
step S3, calculating mode frequency vibration modes of each order of the test bed;
s4, estimating the damping ratio of the test bed by using a multi-order half-power bandwidth method based on a neural network; in particular, the amount of the solvent to be used,
the expression of the total frequency response function of the test bed is set as follows:
wherein f is the excitation frequency of the external simple harmonic load; x (f) is the spectral amplitude;
is the ith order mode coefficient, where P i Is the i-th order modal excitation force of the structure, K i For the i-th order modal stiffness of the structure,
is the ith order mode shape of the structure; f. of i Undamped free vibration frequency of the ith-order mode; xi i Is the ith order modal damping ratio; n is the degree of freedom of the test bed; i is the modal order;
fitting a modal curve l of each order except the k order by using a neural network i,i≠k (f) Solving the amplitude of the modal curve of each order at the frequency corresponding to the peak value and the k-th order modal half-power point, and accumulating the amplitude to reduce the estimation error of the damping ratio; the neural network estimation curve approximation algorithm is as follows:
wherein x is [ x ] 1 ,x 2 ,...,x n ] T Inputting by a neural network, wherein n is the number of input neurons; h ═ h 1 ,h 2 ,...,h m ] T For the output of hidden layer of neural network, m is the number of hidden layers, h j The output of the jth neuron of the hidden layer;
a coordinate vector that is the center point of the hidden layer neuron gaussian basis function, i 1, 2.. and n, j 1, 2.. and m; b is a mixture of j The width of the Gaussian basis function of the jth neuron of the hidden layer of the neural network;
l i,i≠k (x)＝W *T h(x)+ε (3)
wherein ,W* Is an ideal weight value; epsilon is the approximation error of the neural network;
wherein ,
is the estimated weight;
each order modal curve approximated by the neural network;
by using
Solving the amplitude values of modal curves of the k-th order and other orders at the frequency corresponding to the peak value as x respectively i1 ，x i2 and xi3 (ii) a According to the mode superposition principle, the response amplitude at the peak value of the total frequency response function dominated by the kth order mode in the multi-degree-of-freedom system is approximately expressed as:
wherein ,Xk A large error exists in comparison with the k-th order modal peak value of the total frequency response function for the k-th order modal peak value estimated according to the traditional half-power bandwidth algorithm;
representing a damping ratio estimation error correction term representing an approximation of a frequency response function of each order except the k-th order mode at the k-th order mode, wherein beta k ＝f/f k Is the k-th order frequency ratio, f k Undamped free vibration frequency of a k-order mode;
defined according to a half-power method, the k-th order modal frequency response function curve satisfies
Meanwhile, the amplitude influence brought by other modes of each order is considered, and frequency response function curves can be listed respectively
The relationship between the left and right half-power point amplitudes and the peak point amplitude is as follows:
solving the corresponding k-th order modal damping ratio xi according to the formula (6) k And half power f of the k-th mode k1 and fk2 。
Has the beneficial effects that:
the test bed for simulating the bearing slip in the high-speed rotating machine, provided by the invention, sets the rotating speed, lubrication, load, rigidity and eccentric change according to the actual operating parameter curve of the real high-speed rotating machine, and simultaneously researches the bearing slip rule under the conditions of variable rotating speed, variable load, variable lubrication, variable temperature and variable rigidity, thereby meeting the requirement of simulating the bearing slip under the actual operating conditions of the real high-speed rotating machine. The bearing support rigidity is designed to change the critical rotating speed of the test bed, and modal parameters such as rigidity, damping ratio and frequency are identified to ensure that the dynamic characteristics of the test bed are the same as those of a real high-speed rotating machine. The sliding mechanism research can be carried out by changing the supporting rigidity, and meanwhile, the radial and axial matching bidirectional loading can be realized, so that the requirement of the research on the relation between load matching and bearing sliding is met. Aiming at the multi-bearing slipping phenomenon frequently occurring in high-speed rotating machinery, the test bed can simultaneously carry out coupling research on slipping of a plurality of bearings and search a multi-bearing slipping mechanism. By arranging the lubricating system, the temperature and the flow of the lubricating oil can be regulated, and the relation between lubrication and bearing slipping is researched.
Aiming at the problem that the load, the rotating speed and the lubrication are mutually associated and matched when the actual high-speed rotating machine runs, the motor rotating speed control system, the lubrication system, the radial bidirectional loading system, the axial bidirectional loading system, the eccentric disc and the like in the test bed can be set according to the actual high-speed rotating machine running parameter curve, so that the requirement of simulating the actual running working condition of the actual high-speed rotating machine is met.
In addition, the invention provides a multi-order half-power bandwidth method based on the neural network to estimate the damping ratio, overcomes the defect of low estimation precision of the traditional half-power bandwidth estimation method on the damping ratio of a multi-degree-of-freedom system, and obtains a good estimation effect.
Drawings
FIG. 1 is a schematic structural diagram of a test bed for simulating the slipping of a mechanical bearing under high-speed rotation provided by the invention;
FIG. 2 is a schematic diagram of the control principle of the matching system provided by the present invention;
FIG. 3 is a calculation chart of the total bending and compression rigidity of the double-half inner ring angular contact ball bearing system in the embodiment of the invention;
FIG. 4 is a Campbell diagram under variable stiffness support in an embodiment of the present invention;
FIG. 5 is a simulation diagram of the mode shape of the test bed according to an embodiment of the present invention;
fig. 6 is a schematic diagram of an improved multi-step half-power bandwidth method provided by the present invention.
Description of the reference numerals:
1-a platform base; 2-a motor support; 3-high rotation speed servo motor; 4-diaphragm coupling; 5-high speed rotating shaft; 6-round nut; 7-a stop washer; 8, positioning a sleeve; 9-positioning the shaft; 10-eccentric disc; 11-a programmable controller; 12-a driver; 13-oil temperature controller; 14-a lubricating oil pump; 15-lubrication of the nozzle; 16-four point angular contact ball bearings; 17-a first bearing seat; 18-a first oil collecting device; 19-a first temperature sensor; 20-cylindrical roller bearings; 21-a third variable stiffness support; 22-a third bearing housing floor; 23-a third bearing seat; 24-a third oil collecting device; 25-a third temperature sensor; 26-a third eddy current displacement sensor; 27-a third vibration acceleration sensor; 28-double half inner ring angular contact ball bearing; 29-a fourth variable stiffness support; 30-a fourth bearing seat bottom plate; 31-a fourth bearing seat; 32-a fourth oil collecting device; 33-a fourth temperature sensor; 34-a fourth eddy current displacement sensor; 35-a fourth vibration acceleration sensor; 36-load bearing; 37-a second bearing block; 38-a rubber base; 39-loading the bearing seat; 40-a second oil collecting device; 41-a first load bearing support; 42-a first support pedestal; 43-a first screw rod; 44-a first straight-bar ball joint bearing; 45-a first force sensor; 46-a second load bearing support; 47-second lead screw; 48-a second straight-bar ball joint bearing; 49-second force sensor.
Detailed Description
The present invention will be further described with reference to the accompanying drawings.
The invention firstly provides a test bed for simulating bearing slippage in high-speed rotating machinery, the structure of which is shown in figure 1, the test bed can realize the slippage research of a bearing under the working conditions of variable rotating speed, variable rigidity, variable load, variable temperature and variable lubrication, analyze the coupling slippage mechanism of a multi-working-condition multi-bearing, enable the dynamic characteristics of the test bed to be the same as those of real high-speed rotating machinery by identifying modal parameters and designing critical rotating speed, and further simulate the slippage running state of an actual bearing with adjustable and controllable matching parameters. The matching control principle is shown in fig. 2. The rated rotation speed of the test bed designed by the invention is 30000r/min, the axial and radial rated loads are both 10KN, and the adjustable temperature of the lubricating oil is 0-200 ℃.
The test bed has a specific structure comprising a high-rotation-speed servo motor 3 positioned on a platform base 1; the high-speed servo motor 3 is connected with one end of a high-speed rotating shaft 5 through a diaphragm coupling 4. An I-shaped motor support 2 is also arranged between the high-speed servo motor 3 and the platform base 1. The motor support 2 is designed to be of an I-shaped structure, so that the mass can be effectively reduced, and necessary support is provided for the high-rotation-speed servo motor 3.
The high-speed servo motor 3 and the high-speed rotating shaft 5 are connected through the diaphragm type coupler 4, relative displacement between the two rotating shafts is compensated by elastic deformation of the diaphragm type coupler 4, installation coaxiality of the high-speed servo motor 3 rotating shaft and the high-speed rotating shaft 5 can be guaranteed, and influence of the coaxiality problem on a slipping test result under the high rotating speed is reduced.
The high-speed servo motor 3 is controlled by a motor speed control system. The motor rotating speed control system comprises a programmable controller 11 and a driver 12, and the rotating speed of the high-rotating-speed servo motor 3 is adjusted according to a given change rate; the motor rotating speed control system adopts a closed-loop control algorithm, and a speed change track curve is programmed and set in advance through the programmable controller 11, so that the speed of the high-rotating-speed servo motor 3 is adjusted upwards or downwards according to a specified change rate. The system can meet the research requirements of different speed change rates on the influence of bearing slippage under the working conditions of acceleration and deceleration.
The high-speed rotating shaft 5 is sequentially connected with a four-point angular contact ball bearing system, a loading bearing system, an eccentric disc 10, a cylindrical roller bearing system, a double-half inner ring angular contact ball bearing system, a stop washer 7 and a round nut 6 along the axial direction; two sides of the loading bearing system are respectively provided with an axial bidirectional loading system along the axial left and right directions, and two sides of the loading bearing system are respectively provided with a radial bidirectional loading system along the radial direction. The bearing systems and the bi-directional loading system are described in turn below.
The four-point angular contact ball bearing system is used as an accompanying test system and comprises a four-point angular contact ball bearing 16, a first bearing seat 17, a first oil collecting device 18 and a first temperature sensor 19; the four-point angular contact ball bearing 16 is sleeved outside the high-speed rotating shaft 5, the first bearing seat 17 is of a vertically detachable structure, is sleeved on the outer ring of the four-point angular contact ball bearing 16 and is embedded in the first oil collecting device 18, and two parallel positioning shafts 9 are further arranged below the four-point angular contact ball bearing along the axial direction; the first oil collecting device 18 and the first bearing seat 17 are fixedly arranged on the platform base 1; the first temperature sensor 19 is mounted in the vertical through hole of the first bearing block 17;
the loading bearing system comprises a loading bearing 36, a second bearing seat 37, a rubber base 38, a loading bearing seat 39 and a second oil collecting device 40; the loading bearing 36 is sleeved on the outer ring of the high-speed rotating shaft 5, the loading bearing seat 39 is long plate-shaped and is installed on the outer ring of the loading bearing 36 in a matching way, and the loading bearing seat is installed on the second bearing seat 37 through the rubber base 38 in the vertical direction and is embedded and fixed in the second oil collecting device 40 of the platform base 1.
The rubber base 38 is used for providing proper supporting force for the loading bearing seat 39, and has low rigidity, so that flexible support can be realized. The second oil collecting device 40 is made of transparent plastic and is divided into four parts which are connected together through bolts. The loading bearing seat 39 is respectively provided with two through holes and two rectangular through grooves, and the circle center positions of the two through holes and the center positions of the two rectangular through grooves are horizontally symmetrical about the axis of the high-speed rotating shaft 5.
The axial bidirectional loading system comprises a first bearing support 41, a first supporting support 42, a first screw rod 43, a first straight rod type ball joint bearing 44 and a first force sensor 45 which are symmetrically distributed along two sides of the high-speed rotating shaft 5; one end of a first screw rod 43 is connected with a first bearing support 41 fixed on the platform base 1 and arranged in parallel with the high-speed rotating shaft 5, and the other end is connected with the rotatable end of a first straight-bar type ball joint bearing 44; the fixed end of the first straight-bar type ball joint bearing 44 is connected to the corresponding through hole on the loading bearing seat 39; a first supporting support 42 for supporting is further arranged at the lower part of the first straight rod type ball joint bearing 44, and the first supporting support 42 is fixed on the platform base 1; first force sensors 45 for displaying tension and compression loads are respectively arranged at the fixed ends of the first straight rod type ball joint bearings 44; the first force sensors 45 on both sides are arranged oppositely, and the distance is larger than the thickness of the loading bearing seat 39. The rotation direction and the rotation speed of the first screw rod 43 are adjusted through a motor/manually, the bearing loading direction, the load size and the load change rate are changed, and the tension and compression load is displayed by the first force sensor 45.
The radial bidirectional loading system comprises a second bearing support 46, a second screw rod 47, a second straight rod type ball joint bearing 48 and a second force sensor 49 which are perpendicular to the direction of the high-speed rotating shaft 5 and symmetrically distributed on two sides of the loading bearing seat 39; one end of a second screw rod 47 is connected with a second bearing support 46 fixed on the platform base 1, and the other end of the second screw rod is connected with the rotatable end of a second straight-rod type ball joint bearing 48 along the direction vertical to the high-speed rotating shaft 5; the fixed end of the second straight rod type ball joint bearing 48 is provided with a positioning block matched with the through groove of the loading bearing seat 39, so that the second straight rod type ball joint bearing is matched with the loading bearing seat 39, the applied radial force is ensured to be always directed to the axis of the high-speed rotating shaft 5, and stable and reliable radial bidirectional loading is realized; a second force sensor 49 is also mounted at the fixed end of the second straight rod type ball joint bearing 48. The bearing loading direction, the load size and the load change rate are changed by adjusting the second 47 rotating direction and the rotating speed of the screw rod. The load is displayed by the second force sensor 49.
The cylindrical roller bearing system is used as a test system and comprises a cylindrical roller bearing 20, a third variable stiffness support 21, a third bearing pedestal bottom plate 22, a third bearing pedestal 23, a third oil collecting device 24, a third temperature sensor 25, a third eddy current displacement sensor 26 and a third vibration acceleration sensor 27; the cylindrical roller bearing 20 is sleeved on the outer ring of the high-speed rotating shaft 5, the third bearing seat 23 is sleeved on the outer ring of the cylindrical roller bearing 20 and embedded into the third oil collecting device 24, and the third variable-rigidity support 21 is connected with the third bearing seat bottom plate 22, so that the research on the influence of different support rigidity on the bearing slipping can be realized. The third oil collecting device 24 comprises a left part and a right part which are symmetrical and fixedly connected with the third bearing seat 23 through bolts and sealing rings; the third bearing seat 23 is of a vertically detachable structure; the third temperature sensor 25 is installed in the vertical through hole of the third bearing seat 23, and is used for measuring the temperature of the outer ring of the bearing in real time, and the research requirement of the relation between the bearing slip and the temperature of the outer ring of the bearing is met. The third eddy current displacement sensor 26 is installed opposite to the retainer of the cylindrical roller bearing 20 and is used for measuring the rotating speed of the retainer of the cylindrical roller bearing 20. The third vibration acceleration sensor 27 is mounted on the third bearing housing 23, and is configured to measure vibration signals of the third bearing housing 23 in three directions XYZ.
The cylindrical roller bearing system realizes the recycling and instant storage of lubricating oil through the third oil collecting device 24. The temperature sensors are arranged at the oil outlet to realize the sample extraction of the lubricating oil and the real-time temperature measurement of the lubricating oil under different slipping working conditions, and the temperature sensors are used for analyzing the relationship between the bearing slipping and the lubricating oil components and the temperature. The overall variable stiffness support parameters are shown in table 1 below, where the variable stiffness support thicknesses are 5mm, 15mm, 30mm, and 40mm in that order.
TABLE 1 Overall variable stiffness parameters for cylindrical roller bearing systems
The eccentric disc 10 is installed between the loading bearing system and the cylindrical roller bearing system, a certain number of through holes are uniformly processed along the circumferential direction of the eccentric disc 10, so that the eccentric quality is convenient to change, and the research requirement of the influence of the eccentric force on the bearing slipping under the high-speed rotation working condition is met.
The double-half inner ring angular contact ball bearing system is similar to a cylindrical roller bearing system in structure. The testing system comprises a double-half inner ring angular contact ball bearing 28, a fourth variable stiffness support 29, a fourth bearing pedestal bottom plate 30, a fourth bearing pedestal 31, a fourth oil collecting device 32, a fourth temperature sensor 33, a fourth eddy current displacement sensor 34 and a fourth vibration acceleration sensor 35; the double-half inner ring angular contact ball bearing 28 is sleeved on the outer ring of the high-speed rotating shaft 5, and the positions of the inner ring of the double-half inner ring angular contact ball bearing 28 and the inner ring of the cylindrical roller bearing 20 are fixed through the positioning sleeve 8; the fourth bearing seat 31 is sleeved on the outer ring of the double-half inner ring angular contact ball bearing 28, embedded into the fourth oil collecting device 32 and connected with the fourth variable stiffness support 29 through the fourth bearing base plate 30; the fourth variable stiffness support obtains different stiffness by changing the thickness of the support; the fourth oil collecting device 32 comprises a left part and a right part which are symmetrical, and is fixedly connected with the fourth bearing seat 31 through a bolt and a sealing ring; the fourth bearing seat 31 is of a vertically detachable structure; the fourth temperature sensor 33 is installed in the vertical through hole of the fourth bearing seat 31; the fourth eddy current displacement sensor 34 is installed right opposite to the double-half inner ring angular contact ball bearing 28 retainer and used for measuring the rotating speed of the double-half inner ring angular contact ball bearing 28 retainer; the fourth vibration acceleration sensor 35 is mounted on the fourth bearing seat 31, and is used for measuring vibration signals of the fourth bearing seat 31 in three directions XYZ. The fourth variable stiffness support 29 parameters are shown in table 2 below and the compressive and bending stiffness calculations are shown in fig. 3, where the variable stiffness bearing thicknesses are 5mm, 15mm, 30mm and 40mm, respectively.
TABLE 2 Overall variable stiffness parameter of double-half inner ring angular contact ball bearing system
And a lubricating system for supplying lubricating oil to each bearing system is also arranged above the test bed. The lubricating system comprises an oil temperature controller 13, a lubricating oil pump 14 and a lubricating spray pipe 15; the oil temperature controller 13 adjusts the temperature of the lubricating oil to change within the range of 0-200 ℃ in real time; the lubricating oil pump 14 adjusts the flow rate of the lubricating oil in real time and supplies the lubricating oil to each bearing system through a lubricating spray pipe 15. The system can meet the research requirements of lubricating oil flow and temperature on the bearing slipping influence.
The following provides a test bed design method based on the device, which specifically comprises the following steps:
and step S1, calculating the compression and bending rigidity of the bearing seat, the variable-rigidity support and the bearing seat bottom plate by using Patran, as shown in figure 3. The contact stiffness of the bearing rollers was then calculated as shown in table 3 below:
TABLE 3 results of calculation of contact displacement and rigidity of rollers with inner and outer races under different loads
Finally, serially connecting the calculated rigidity to obtain the total supporting rigidity;
step S2, changing the critical rotating speed of the test bed by designing the bearing supporting rigidity, wherein the corresponding critical rotating speed under different supporting rigidities is shown in a table 4:
TABLE 4 test bench Critical speed
The results of the critical rotational speed calculation are shown in fig. 4.
Step S3, calculating mode frequency vibration modes of each order of the test bed; the mode shapes of the modal frequencies of the different orders are shown in table 5 below, and the modal frequencies and mode shape calculation results are shown in fig. 5.
TABLE 5 test bench modal frequencies
Step S4, estimating the damping ratio of the test bed by using a multi-order half-power bandwidth method based on a neural network; the algorithm principle is as shown in fig. 6, and in particular,
the expression of the total frequency response function of the test bed is set as follows:
wherein f is the excitation frequency of the external simple harmonic load; x (f) is the spectral amplitude;
is the ith order mode coefficient, where P i Is the i-th order modal excitation force of the structure, K i For the i-th order modal stiffness of the structure,
is the ith order mode shape of the structure; f. of i Undamped free vibration frequency of the ith-order mode; xi shape i Is the ith order modal damping ratio; n is the degree of freedom of the test bed; i is the modal order;
when the damping ratio of the kth order mode of the multi-degree-of-freedom system is estimated by using a half-power bandwidth method, the influence of the rest orders of the modes is mainly concentrated in the half-power frequency band of the kth order mode. The invention uses the neural network to fit the modal curve l of each order except the k order i,i≠k (f) Solving the amplitude of the modal curve of each order at the frequency corresponding to the peak value and the k-th order modal half-power point, and accumulating the amplitude to reduce the estimation error of the damping ratio; the neural network estimation curve approximation algorithm is as follows:
wherein x is [ x ] 1 ,x 2 ,...,x n ] T Inputting the neural network, wherein n is the number of input neurons; h ═ h 1 ,h 2 ,...,h m ] T For the output of hidden layer of neural network, m is the number of hidden layers, h j The output of the jth neuron of the hidden layer;
a coordinate vector of a center point of a gaussian basis function of an implicit layer neuron, i 1,2, a, n, j 1,2, a, m; b j The width of the Gaussian basis function of the jth neuron of the hidden layer of the neural network;
l i,i≠k (x)＝W *T h(x)+ε (3)
wherein ,W* Is an ideal weight value; epsilon is the approximation error of the neural network;
wherein ,
is the estimated weight;
each order modal curve approximated by the neural network;
by using
Solving the amplitude values of modal curves of the rest orders at the frequency corresponding to the peak value and the modal half-power point of the kth order are x respectively i1 ，x i2 and xi3 (ii) a According to the mode superposition principle, the response amplitude at the peak value of the total frequency response function dominated by the kth order mode in the multi-degree-of-freedom system is approximately expressed as:
wherein ,Xk A large error exists in comparison with the k-th order modal peak value of the total frequency response function for the k-th order modal peak value estimated according to the traditional half-power bandwidth algorithm;
representing damping ratio estimation error correction term representing modes of orders other than the k-th modeApproximation of frequency response function at k-th order mode, where k ＝f/f k Is the k-th order frequency ratio, f k Undamped free vibration frequency for a kth order mode;
defined according to a half-power method, the k-th order modal frequency response function curve satisfies
Meanwhile, the amplitude influence brought by other modes of each order is considered, and frequency response function curves can be listed respectively
The relationship between the left and right half-power point amplitudes and the peak point amplitude is as follows:
solving the corresponding k-th order modal damping ratio xi according to the formula (6) k And half power point f of the k-th order mode k1 and fk2 . The results of the test stand global damping ratio estimate are shown in table 6:
TABLE 6 test bench Overall damping ratio estimate
The above description is only of the preferred embodiments of the present invention, and it should be noted that: it will be apparent to those skilled in the art that various modifications and adaptations can be made without departing from the principles of the invention and these are intended to be within the scope of the invention.
Claims (10)
1. A test bed for simulating bearing slippage in high-speed rotating machinery is characterized by comprising a high-speed servo motor (3) positioned on a platform base (1); the high-speed servo motor (3) is connected with one end of the high-speed rotating shaft (5) through a diaphragm coupler (4); the high-speed rotating shaft (5) is sequentially connected with a four-point angular contact ball bearing system, a loading bearing system, an eccentric disc (10), a cylindrical roller bearing system, a double-half inner ring angular contact ball bearing system, a stop washer (7) and a round nut (6) along the axial direction; the high-rotation-speed servo motor (3) is controlled by a motor rotation speed control system; two sides of the loading bearing system are respectively provided with an axial bidirectional loading system along the axial left and right directions, and two sides of the loading bearing system are respectively provided with a radial bidirectional loading system along the radial direction; and a lubricating system for supplying lubricating oil to each bearing system is also arranged above the test bed.
2. Test bench for simulating bearing skidding in high-speed rotating machinery according to claim 1, characterized in that the four-point angular contact ball bearing system comprises a four-point angular contact ball bearing (16), a first bearing seat (17), a first oil collecting device (18) and a first temperature sensor (19) as a test-accompanying system; the four-point angular contact ball bearing (16) is sleeved on the outer side of the high-speed rotating shaft (5), the first bearing seat (17) is of an up-and-down detachable structure, is sleeved on the outer ring of the four-point angular contact ball bearing (16) and is embedded into the first oil collecting device (18), and two parallel positioning shafts (9) are further arranged below the four-point angular contact ball bearing along the axial direction; the first oil collecting device (18) and the first bearing seat (17) are fixedly arranged on the platform base (1); the first temperature sensor (19) is mounted in a vertical through hole of the first bearing block (17).
3. A test bench for simulating bearing slippage in high speed rotating machinery according to claim 1, wherein the load bearing system comprises a load bearing (36), a second bearing seat (37), a rubber base (38), a load bearing seat (39) and a second oil catcher (40); the loading bearing (36) is sleeved on the outer ring of the high-speed rotating shaft (5), the loading bearing seat (39) is in a long plate shape and is installed on the outer ring of the loading bearing (36) in a matching mode, the loading bearing seat is installed on the second bearing seat (37) through a rubber base (38) in the vertical direction, and the loading bearing is embedded into a second oil collecting device (40) fixed on the platform base (1).
4. A test bench for simulating bearing skid in high-speed rotating machinery according to claim 3, wherein the axial bidirectional loading system comprises a first bearing support (41), a first supporting support (42), a first lead screw (43), a first straight-bar type ball joint bearing (44) and a first force sensor (45) which are symmetrically distributed along two sides of the high-speed rotating shaft (5); one end of the first screw rod (43) is connected with a first bearing support (41) fixed on the platform base (1) and arranged in parallel with the high-speed rotating shaft (5), and the other end of the first screw rod is connected with the rotatable end of the first straight-bar type ball joint bearing (44); the fixed end of the first straight-bar type ball joint bearing (44) is connected to a corresponding through hole on the loading bearing seat (39); a first supporting support (42) for supporting is further arranged at the lower part of the first straight-bar-type ball joint bearing (44), and the first supporting support (42) is fixed on the platform base (1); first force sensors (45) for displaying tension and compression loads are respectively arranged at the fixed ends of the first straight rod type ball joint bearings (44); the first force sensors (45) on the two sides are arranged oppositely, and the distance is larger than the thickness of the loading bearing seat (39).
5. A test bench for simulating bearing skid in high-speed rotating machinery according to claim 3, wherein the radial bidirectional loading system comprises a second bearing support (46), a second lead screw (47), a second straight-bar type ball joint bearing (48) and a second force sensor (49), which are symmetrically distributed on two sides of a loading bearing seat (39) in a direction perpendicular to the direction of the high-speed rotating shaft (5); one end of the second screw rod (47) is connected with a second bearing support (46) fixed on the platform base (1), and the other end of the second screw rod is connected with the rotatable end of a second straight-rod type ball joint bearing (48) along the direction vertical to the high-speed rotating shaft (5); a positioning block matched with the through groove of the loading bearing seat (39) is arranged at the fixed end of the second straight rod type ball joint bearing (48) and used for realizing the matching with the loading bearing seat (39); and a second force sensor (49) is also installed at the fixed end of the second straight rod type ball joint bearing (48).
6. A test bench for simulating bearing slippage in high-speed rotating machinery according to claim 1, characterized in that the cylindrical roller bearing system comprises a cylindrical roller bearing (20), a third variable stiffness support (21), a third bearing pedestal base plate (22), a third bearing pedestal (23), a third oil collecting device (24), a third temperature sensor (25), a third eddy current displacement sensor (26) and a third vibration acceleration sensor (27) as a test system; the cylindrical roller bearing (20) is sleeved on the outer ring of the high-speed rotating shaft (5), and the third bearing seat (23) is sleeved on the outer ring of the cylindrical roller bearing (20), embedded into the third oil collecting device (24) and connected with the third variable-rigidity support (21) through a third bearing seat bottom plate (22); the third oil collecting device (24) comprises a left part and a right part which are symmetrical, and is fixedly connected with the third bearing seat (23) through a bolt and a sealing ring; the third bearing seat (23) is of a vertically detachable structure; the third temperature sensor (25) is arranged in a vertical through hole of the third bearing seat (23); the third eddy current displacement sensor (26) is arranged right opposite to the retainer of the cylindrical roller bearing (20) and used for measuring the rotating speed of the retainer of the cylindrical roller bearing (20); the third vibration acceleration sensor (27) is arranged on the third bearing seat (23) and is used for measuring vibration signals of the third bearing seat (23) in three XYZ directions.
7. The test bench for simulating bearing slip in high-speed rotating machinery according to claim 1, wherein the double-half inner ring angular contact ball bearing system comprises a double-half inner ring angular contact ball bearing (28), a fourth variable stiffness support (29), a fourth bearing seat bottom plate (30), a fourth bearing seat (31), a fourth oil collecting device (32), a fourth temperature sensor (33), a fourth eddy current displacement sensor (34) and a fourth vibration acceleration sensor (35) as a test system; the double-half inner ring angular contact ball bearing (28) is sleeved on the outer ring of the high-speed rotating shaft (5), and the positions of the inner ring of the double-half inner ring angular contact ball bearing (28) and the inner ring of the cylindrical roller bearing (20) are fixed through a positioning sleeve (8); a fourth bearing seat (31) is sleeved on the outer ring of the double-half inner ring angular contact ball bearing (28), embedded into a fourth oil collecting device (32) and connected with a fourth variable stiffness support (29) through a fourth bearing base plate (30); the fourth oil collecting device (32) comprises a left part and a right part which are symmetrical, and is fixedly connected with the fourth bearing seat (31) through a bolt and a sealing ring; the fourth bearing seat (31) is of a structure which can be disassembled up and down; the fourth temperature sensor (33) is arranged in a vertical through hole of the fourth bearing seat (31); the fourth eddy current displacement sensor (34) is installed over against the double-half inner ring angular contact ball bearing (28) retainer and is used for measuring the rotating speed of the double-half inner ring angular contact ball bearing (28) retainer; the fourth vibration acceleration sensor (35) is mounted on the fourth bearing seat (31) and used for measuring vibration signals of the fourth bearing seat (31) in three directions of XYZ.
8. A test rig for simulating bearing slippage in a high speed rotating machine according to claim 1, wherein said motor speed control system comprises a programmable controller (11) and a driver (12) for adjusting the speed of the high speed servo motor (3) at a given rate of change; an I-shaped motor support (2) is further arranged between the high-rotating-speed servo motor (3) and the platform base (1).
9. A test bench for simulating bearing slippage in high speed rotating machinery according to claim 1, wherein the lubrication system comprises an oil temperature controller (13), a lubrication oil pump (14) and a lubrication nozzle (15); the oil temperature controller (13) adjusts the temperature of the lubricating oil to change within the range of 0-200 ℃ in real time; the lubricating oil pump (14) adjusts the flow of the lubricating oil in real time and supplies the lubricating oil to each bearing system through a lubricating spray pipe (15).
10. Test bench design method for simulating bearing skidding in high speed rotating machinery according to any of claims 1-9, characterized in that it comprises the following steps:
step S1, utilizing Patran to calculate the compression resistance and bending resistance rigidity of the bearing seat, the variable rigidity support and the bearing seat bottom plate, then calculating the contact rigidity of the bearing roller, and connecting the calculated rigidity in series to obtain the total support rigidity;
step S2, respectively calculating the critical rotating speed of the test bed under different overall supporting rigidity by designing the supporting rigidity of the bearing;
step S3, calculating mode frequency vibration modes of each order of the test bed;
s4, estimating the damping ratio of the test bed by using a multi-order half-power bandwidth method based on a neural network; in particular, the amount of the solvent to be used,
the expression of the total frequency response function of the test bed is set as follows:
wherein f is the excitation frequency of the external simple harmonic load; x (f) is the spectral amplitude;
is the ith order mode coefficient, where P i I order modal excitation force, K, of the structure i For the i-th order modal stiffness of the structure,
is the ith order mode shape of the structure; f. of i Undamped free vibration frequency of the ith-order mode; xi shape i Is the ith order modal damping ratio; n is the degree of freedom of the test bed; i is the modal order;
fitting a modal curve l of each order except the k order by using a neural network i,i≠k (f) Solving the k-th order modal half-power point and the amplitudes of other orders of modal curves at the frequency corresponding to the peak value, and accumulating the amplitudes to reduce the damping ratio estimation error; the neural network estimation curve approximation algorithm is as follows:
wherein x is [ x ] 1 ,x 2 ,...,x n ] T Inputting by a neural network, wherein n is the number of input neurons; h ═ h 1 ,h 2 ,...,h m ] T Is the output of the hidden layer of the neural network, m is the number of the hidden layers, h j The output of the jth neuron of the hidden layer;
a coordinate vector that is the center point of the hidden layer neuron gaussian basis function, i 1, 2.. and n, j 1, 2.. and m; b is a mixture of j For the jth hidden layer of a neural networkThe width of the neuron gaussian basis function;
l i,i≠k (x)＝W *T h(x)+ε (3)
wherein ,W* Is an ideal weight value; epsilon is the approximation error of the neural network;
wherein ,
to estimate the weight;
each order modal curve approximated by the neural network;
by using
Solving the amplitude values of modal curves of the k-th order and other orders at the frequency corresponding to the peak value as x respectively i1 ，x i2 and xi3 (ii) a According to a mode superposition principle, the response amplitude at the k-th order mode-dominated total frequency response function peak value in the multi-degree-of-freedom system is approximately expressed as:
wherein ,Xk A large error exists between the k-th order modal peak value estimated according to the traditional half-power bandwidth algorithm and the k-th order modal peak value of the total frequency response function;
representing a damping ratio estimation error correction term representing an approximation of a modal frequency response function of orders other than the k-th order mode at the k-th order mode, where beta k ＝f/f k Is the k-th order frequencyRatio, f k Undamped free vibration frequency of a k-order mode;
defined according to a half-power method, the k-th order modal frequency response function curve satisfies
Meanwhile, the amplitude influence brought by other modes of each order is considered, and frequency response function curves can be listed respectively
The relationship between the left and right half-power point amplitudes and the peak point amplitude is as follows:
solving the corresponding k-th order modal damping ratio xi according to the formula (6) k And half power point f of the k-th order mode k1 and fk2 。
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