CN115031965B - Test bed for simulating bearing slip in high-speed rotating machinery and design method - Google Patents
Test bed for simulating bearing slip in high-speed rotating machinery and design method Download PDFInfo
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Abstract
The invention discloses a test bed for simulating bearing slip in high-speed rotating machinery and a design method thereof; the test bed comprises a high-rotation-speed servo motor positioned on a platform base; the high-speed servo motor is connected with 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, 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, the multi-order half-power bandwidth algorithm based on the neural network is used for estimating the damping ratio of the multi-degree-of-freedom system, and the estimation precision is high; the invention can realize the slip research under the working conditions of variable rotation speed, rigidity, load, temperature and lubrication of the bearing, 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 rotation speed, so that the slip state of the actual bearing with adjustable and controllable parameter matching is simulated.
Description
Technical Field
The invention relates to the technical field of mechanical bearing test tables, in particular to a test table for simulating bearing slip in high-speed rotating machinery and a design method.
Background
Rolling bearings are used as important parts of high-speed rotating machinery, and the working environment of the rolling bearings is more and more severe, and the rolling bearings are mainly expressed as follows: the rotational speed is high and the operating temperature is also much higher than the ambient temperature. The DN value of the bearing (the inner diameter D (mm) of the bearing inner ring multiplied by the rotating speed N (r/min)) is higher, so that faults such as slipping and rubbing, fatigue failure, movement instability and the like of the bearing are frequently caused, wherein the common faults are bearing slipping faults, and the common faults account for about 34% of the total fault number.
Numerous practices and studies have shown that load matching, load reversing, lubricant temperature and flow, bearing stiffness, rate of change of speed and eccentric mass are important causes of slip. In the actual running process of the high-speed rotating machine, the high-speed rotating machine comprises a strong coupling relation of the mutual correlation of rotating speed, rigidity, load, temperature and lubrication state, and the situation that multiple bearings slip simultaneously often occurs. Therefore, it is necessary to design a multi-bearing slip test system which can simultaneously and independently study the above factors and can realize the matching study of the factors which are matched with the actual running condition of the high-speed rotating machine. At present, the existing design method of the bearing slipping test bed does not consider the influence of the factors on bearing slipping at the same time, and good research effects and application values 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 frequency and vibration mode is accurate, but the damping ratio analysis result is not ideal. Studies have shown that the effect of damping on the structural dynamic response is more pronounced for elongated flexible structures. However, the damping ratio of the structure is influenced by a plurality of factors such as structural form, material types, structural dimensions and the like, and the mode test is easily limited by the quality of measured data and the identification method, so that the identification accuracy of the damping ratio is limited. How to improve the damping ratio recognition 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 is widely applied to damping ratio estimation of a multi-degree-of-freedom system in actual engineering. Because the mode parameters of the multi-degree-of-freedom system have stronger coupling, the damping ratio estimated by the traditional half-power bandwidth algorithm can generate larger errors.
Disclosure of Invention
The invention aims to: based on the problems in the background art, the invention provides a test bed and a design method for simulating bearing slip in high-speed rotating machinery, wherein the test bed structure can realize slip research under the working conditions of bearing variable rotation speed, variable stiffness, variable load, variable temperature and variable lubrication, and analyze multi-station multi-bearing coupling slip mechanism. Meanwhile, the dynamic characteristics of the test bed can be identical to those of a real high-speed rotating machine through identifying modal parameters and designing critical rotating speed, so that the actual bearing slipping running state with adjustable and controllable parameter matching is 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 above purpose, the invention adopts the following technical scheme:
a test bed for simulating bearing slip in a high-speed rotating machine comprises a high-rotation-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; the two sides of the loading bearing system are respectively provided with an axial bidirectional loading system along the axial left and right directions, and the 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 is used as a test accompanying system and 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 on the outer side of the high-speed rotating shaft, the first bearing seat is of an up-down detachable structure, is sleeved on the 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 four-point angular contact ball bearing 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 the vertical through hole of the first bearing seat;
further, the loading bearing system comprises a loading bearing, a second bearing, 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, is installed on the outer ring of the loading bearing in a matching manner, is installed on the second bearing seat in the vertical direction through the rubber base, and is embedded into the second oil collecting device fixed on the platform base.
Further, 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, wherein the first bearing support, the first supporting support, the first screw rod, the first straight rod type ball joint bearing and the first force sensor are symmetrically distributed along two sides of the high-speed rotating shaft; one end of the first screw rod is connected with a first bearing support fixed on the platform base, the first screw rod is 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 rod type ball joint bearing; the fixed end of the first straight-bar ball joint bearing is connected to the corresponding through hole on the loading bearing seat; the lower part of the first straight rod type ball joint bearing is also provided with a first support seat for supporting, and the first support seat is fixed on the platform base; the fixed ends of the first straight-bar ball joint bearings are respectively provided with a first force sensor for displaying the tension and compression load; the first force sensors on two sides are installed in opposite directions, and the distance is larger than the thickness of the loading bearing seat.
Further, 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 which are symmetrically distributed at two sides of the loading bearing seat in the direction perpendicular to the high-speed rotating shaft; 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; the fixed end of the second straight rod type ball joint bearing is provided with a positioning block matched with the through groove of the loading bearing seat, and the positioning block is used for realizing the matching with the loading bearing seat; and a second force sensor is also arranged 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 seat bottom plate, a third bearing seat, 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, the third bearing seat is sleeved on the outer ring of the cylindrical roller bearing and is embedded into the third oil collecting device, and the third bearing seat is connected with the third variable stiffness support through a third bearing seat bottom plate; the third rigidity-variable support obtains different rigidities by changing the thickness of the support; 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 bolts and sealing rings; the third bearing seat is of an upper and lower detachable structure; the third temperature sensor is arranged in the vertical through hole of the third bearing seat; the third eddy current displacement sensor is arranged opposite to the cylindrical roller bearing retainer and is used for measuring the rotating speed of the cylindrical roller bearing retainer; the third vibration acceleration sensor is arranged on the third bearing seat and is used for measuring vibration signals of the third bearing seat in 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 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 and is embedded into a fourth oil collecting device, and is connected with a fourth variable stiffness support through a fourth bearing base plate; the fourth variable stiffness support obtains different stiffness by changing the thickness of the support; the fourth oil collecting device comprises a left part and a right part which are symmetrical and is fixedly connected with a fourth bearing seat through bolts and sealing rings; the fourth bearing seat is of an upper and lower detachable structure; the fourth temperature sensor is arranged in the vertical through hole of the fourth bearing seat; the fourth eddy current displacement sensor is arranged 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 arranged on the fourth bearing seat and is used for measuring vibration signals of the fourth bearing seat in three directions of XYZ.
Further, the motor rotation speed control system comprises a programmable controller 11 and a driver 12, and the rotation speed of the high-rotation-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 lubrication system comprises an oil temperature controller, a lubrication pump and a lubrication spray pipe; the oil temperature controller regulates the temperature of the lubricating oil to be changed within the range of 0-200 ℃ in real time; the lubricating oil pump regulates the flow of lubricating oil in real time and supplies the lubricating oil to each bearing system through the lubricating spray pipe.
The design method of the test bed for simulating the bearing slip in the high-speed rotating machine is based on the design method, and is characterized by comprising the following steps of:
s1, calculating the compression resistance and bending stiffness of a bearing seat, a variable stiffness support and a bearing seat bottom plate by using Patran, then calculating the contact stiffness of a bearing roller, and connecting the calculated stiffness in series to obtain the overall support stiffness;
s2, calculating critical rotation speeds of the test bed under different overall support rigidities by designing the support rigidities of the bearings;
s3, calculating the mode frequency mode shape of each step 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; specifically, the total frequency response function expression 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 i-th order modal coefficient, where P i K is the i-th order modal excitation force of the structure i For the ith order modal stiffness of the structure, +.>
Is the ith order mode shape of the structure; f (f) i Undamped free vibration frequency for the ith order mode; zeta type toy i Is the modal damping ratio of the ith order; n is the degree of freedom of the test bed; i is the mode order;
fitting out mode curves l of each order except the kth order by using a neural network i,i≠k (f) Solving the amplitude of the rest of the mode curves of each order at the frequency corresponding to the k-th order mode half power point and the peak valueThe values are accumulated, and the damping ratio estimation error is reduced; the neural network estimation curve approximation algorithm is as follows:
wherein x= [ x ] 1 ,x 2 ,...,x n ] T Inputting for the neural network, wherein n is the number of input neurons; h (x) = [ h ] 1 (x),h 2 (x),...,h m (x)] T Outputting hidden layers of the neural network, wherein m is the number of the hidden layers, and h j (x) The output of the jth neuron which is the hidden layer;
a coordinate vector that is a central point of a gaussian basis function of neurons of an hidden layer, i=1, 2,., n, j=1, 2,., 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; epsilon is the approximation error of the neural network;
wherein ,
the weight is estimated; />
Each order mode curve approximated by the neural network;
by means of
Solving the amplitude values of the rest of the mode curves of each order at the frequency corresponding to the k-th order mode half power point and the peak value to be x respectively i1 ，x i2 and xi3 The method comprises the steps of carrying out a first treatment on the surface of the According to the mode superposition principle, the response amplitude at the peak value of the total frequency response function dominated by the k-th order mode in the multi-degree-of-freedom system is approximately expressed as:
wherein ,Xk For the k-th order modal peak value estimated according to the traditional half-power bandwidth algorithm, a larger error exists compared with 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 the frequency response function of each order mode other than the kth order mode at the kth order mode, wherein beta k ＝f/f k For the k-th order frequency ratio, f k Undamped free vibration frequency for a kth order mode;
according to the definition of a half-power method, the mode frequency response function curve of the kth order meets the following condition
Meanwhile, the amplitude influence caused by the other modes of each order is considered, and the frequency response function curves can be respectively listed>
The left and right half power point magnitudes are related to peak point magnitudes as follows:
solving the corresponding k-th order modal damping ratio xi according to the formula (6) k Half power point f of kth order mode k1 and fk2 。
The beneficial effects are that:
the test bed for simulating the bearing slip in the high-speed rotating machine provided by the invention sets the rotation speed, lubrication, load, rigidity and eccentric change according to the actual operation parameter curve of the actual high-speed rotating machine, and simultaneously researches the bearing slip rules under the variable rotation speed working condition, the variable load working condition, the variable lubrication working condition, the variable temperature working condition and the variable rigidity working condition, thereby meeting the requirement of simulating the actual operation working condition of the actual high-speed rotating machine. The critical rotating speed of the test bed is changed by designing the bearing supporting rigidity, and the dynamic characteristics of the test bed are ensured to be the same as those of a real high-speed rotating machine by identifying modal parameters such as rigidity, damping ratio, frequency and the like. The slip 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 slip is met. Aiming at the phenomenon of multi-bearing slipping which is frequently caused by high-speed rotating machinery, the test bed can simultaneously carry out coupling research on slipping of a plurality of bearings and search the mechanism of multi-bearing slipping. Through setting up lubricating system, can realize the regulation to lubricating oil temperature and flow, research lubrication and bearing slip's relation.
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 operates, 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 operation parameter curve of the actual high-speed rotating machine, and the requirements of simulating the actual operation working condition of the actual high-speed rotating machine are met.
In addition, the invention provides a multi-order half-power bandwidth method based on a neural network to estimate the damping ratio, overcomes the defect of low estimation precision of the damping ratio of the multi-degree-of-freedom system by the traditional half-power bandwidth estimation method, and obtains a better estimation effect.
Drawings
FIG. 1 is a schematic diagram of a test bed for simulating mechanical bearing slip at high speed rotation provided by the invention;
FIG. 2 is a schematic diagram of the control principle of the matching system provided by the invention;
FIG. 3 is a graph of overall bending and compressive stiffness calculations for a double inner ring half angular contact ball bearing system in accordance with an embodiment of the present invention;
FIG. 4 is a Campbell diagram with variable stiffness support in an embodiment of the present invention;
FIG. 5 is a simulation diagram of a test bed mode shape in an embodiment of the present invention;
fig. 6 is a schematic diagram of an improved multi-level half-power bandwidth method provided by the present invention.
Reference numerals illustrate:
1-a platform base; 2-a motor support; 3-a high-rotation-speed servo motor; 4-diaphragm coupling; 5-a high-speed rotating shaft; 6-round nuts; 7-a stop washer; 8, positioning sleeves; 9-positioning the shaft; 10-eccentric disc; 11-a programmable controller; 12-a driver; 13-an oil temperature controller; 14-a lubricating oil pump; 15-lubricating spray pipe; 16-four-point angular contact ball bearings; 17-a first bearing seat; 18-a first oil collection device; 19-a first temperature sensor; 20-cylindrical roller bearings; 21-a third variable stiffness support; 22-a third bearing floor; 23-a third bearing block; 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 bearings; 29-fourth variable stiffness support; 30-fourth bearing pedestal bottom plate; 31-fourth bearing seat; 32-fourth oil collecting device; 33-fourth temperature sensor; 34-a fourth eddy current displacement sensor; 35-fourth vibration acceleration sensor; 36-loading the bearing; 37-a second bearing block; 38-a rubber base; 39-loading bearing seats; 40-a second oil collecting device; 41-a first load bearing support; 42-a first support stand; 43-a first screw; 44-a first straight-bar ball joint bearing; 45-a first force sensor; 46-a second load bearing support; 47-a second screw rod; 48-a second straight rod type ball joint bearing; 49-a second force sensor.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
The invention firstly provides a test bed for simulating bearing slipping in high-speed rotating machinery, the structure of the test bed is shown in figure 1, the test bed can realize slipping research under the working conditions of variable bearing rotational speed, variable stiffness, variable load, variable temperature and variable lubrication, multiple-working-condition multi-bearing coupling slipping mechanism is analyzed, dynamic characteristics of the test bed are identical to those of a real high-speed rotating machinery through identifying modal parameters and designing critical rotating speeds, and then the slip running state of each parameter-matched adjustable controllable actual bearing is simulated. 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 10KN, and the adjustable temperature of lubricating oil is 0-200 ℃.
The test bed comprises 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 coupler 4. An I-shaped motor support 2 is also arranged between the high-rotation-speed servo motor 3 and the platform base 1. The motor support 2 is designed into an I-shaped structure, so that the weight can be effectively reduced, and necessary support can be 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, the elastic deformation of the diaphragm type coupler 4 is utilized to compensate the relative displacement between the two rotating shafts, the installation coaxiality of the rotating shaft of the high-speed servo motor 3 and the high-speed rotating shaft 5 can be ensured, and the influence of the coaxiality problem under the high rotating speed on the slip test result is reduced.
The high-rotation-speed servo motor 3 is controlled by a motor rotation speed control system. The motor rotation speed control system comprises a programmable controller 11 and a driver 12, and adjusts the rotation speed of the high-rotation-speed servo motor 3 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 preset by a 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 bearing slip influence under acceleration and deceleration working conditions.
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 two sides of the loading bearing system are respectively provided with an axial bidirectional loading system along the axial left and right directions, and the two sides are respectively provided with a radial bidirectional loading system along the radial direction. The following describes the bearing systems and the bidirectional loading system in sequence.
The four-point angular contact ball bearing system is used as a test accompanying 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 on the outer side of the high-speed rotating shaft 5, the first bearing seat 17 is of an up-down 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 installed in the vertical through hole of the first bearing seat 17;
the loading bearing system comprises a loading bearing 36, a second bearing 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 in a long plate shape, is installed on the outer ring of the loading bearing 36 in a matching manner, is installed on the second bearing seat 37 in the vertical direction through the rubber base 38, and is embedded and fixed in the second oil collecting device 40 of the platform base 1.
The rubber mount 38 is used to provide proper support force for the loading bearing housing 39 and is less stiff, enabling flexible support. The second oil collecting device 40 is made of transparent plastic into four parts and is connected together through bolts. The loading bearing seat 39 is respectively provided with two through holes and two rectangular through grooves, and the 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 the 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, is arranged in parallel with the high-speed rotating shaft 5, and the other end of the first screw rod is connected with a rotatable end of a first straight-rod ball joint bearing 44; the fixed end of the first straight rod type ball joint bearing 44 is connected to the corresponding through hole on the loading bearing seat 39; the lower part of the first straight rod type ball joint bearing 44 is also provided with a first supporting support 42 for supporting, and the first supporting support 42 is fixed on the platform base 1; a first force sensor 45 for displaying the tension and compression load is respectively arranged at the fixed end of the first straight-bar-type ball joint bearing 44; the first force sensors 45 on both sides are mounted opposite each other with a spacing greater than the thickness of the load bearing housing 39. The bearing loading direction, load magnitude and load change rate are changed by motor/manual adjustment of the first screw 43 rotation direction and rotation speed, with the tension and compression load being 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 symmetrically distributed on two sides of the loading bearing seat 39 in the direction perpendicular to the high-speed rotating shaft 5; 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 as to realize the matching with the loading bearing seat 39, ensure that the applied radial force always points to the axis of the high-speed rotating shaft 5, and realize stable and reliable radial bidirectional loading; the fixed end of the second straight rod type ball joint bearing 48 is also provided with a second force sensor 49. The bearing loading direction, load magnitude and load change rate are changed by adjusting the rotational direction and rotational speed of the screw second 47. 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 seat bottom plate 22, a third bearing seat 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 is embedded into the third oil collecting device 24, and the cylindrical roller bearing is connected with the third variable stiffness support 21 through the third bearing seat bottom plate 22, so that the influence of different support stiffness on bearing slip can be studied. 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 bolts and sealing rings; the third bearing seat 23 is an up-down 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, so that the research requirement of the relation between the slip of the bearing and the temperature of the outer ring of the bearing is met. The third eddy current displacement sensor 26 is arranged 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. A third vibration acceleration sensor 27 is mounted on the third bearing block 23 for measuring vibration signals of the third bearing block 23 in three directions XYZ.
The cylindrical roller bearing system realizes the recycling and the instant storage of the lubricating oil through the third oil collecting device 24. The temperature sensor is arranged at the oil outlet to realize sample extraction of lubricating oil and real-time temperature measurement of the lubricating oil under different slip working conditions, and the temperature sensor is used for analyzing the relation between bearing slip and lubricating oil components and temperature. The overall variable stiffness support parameters are shown in table 1 below, wherein the variable stiffness support thicknesses are 5mm, 15mm, 30mm, and 40mm in order.
TABLE 1 Total variable stiffness parameters for cylindrical roller bearing systems
The eccentric disc 10 is arranged between the loading bearing system and the cylindrical roller bearing system, a certain number of through holes are uniformly formed in the circumferential direction of the eccentric disc 10, so that the eccentric mass can be conveniently changed, and the research requirement of the eccentric force on the bearing slip under the high-speed rotation working condition is met.
The double half inner ring angular contact ball bearing system is similar to the 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 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; 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 and is embedded into a fourth oil collecting device 32, and is connected with the fourth rigidity-changing support 29 through a fourth bearing base plate 30; the fourth rigidity-variable support obtains different rigidities 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 bolts and sealing rings; the fourth bearing seat 31 is of an up-and-down detachable structure; the fourth temperature sensor 33 is installed in the vertical through hole of the fourth bearing housing 31; the fourth eddy current displacement sensor 34 is arranged opposite to the retainer of the double-half inner ring angular contact ball bearing 28 and is used for measuring the rotating speed of the retainer of the double-half inner ring angular contact ball bearing 28; the fourth vibration acceleration sensor 35 is mounted on the fourth bearing housing 31 for measuring vibration signals of the fourth bearing housing 31 in three directions of XYZ. The fourth variable stiffness support 29 parameters are shown in Table 2 below, and the compressive and flexural stiffness calculations are shown in FIG. 3, wherein the variable stiffness support thicknesses are 5mm, 15mm, 30mm and 40mm, respectively.
Table 2 overall variable stiffness parameters for double half inner ring angular contact ball bearing systems
And a lubricating system for supplying lubricating oil to each bearing system is also arranged above the test bed. The lubrication system comprises an oil temperature controller 13, a lubrication pump 14 and a lubrication spray pipe 15; the oil temperature controller 13 adjusts the temperature of the lubricating oil to be changed within the range of 0-200 ℃ in real time; the lubricating oil pump 14 regulates the flow of lubricating oil in real time and supplies the respective bearing systems through the lubricating nipple 15. The system can meet the research requirement of lubricating oil flow and temperature on the bearing slip influence.
The test bed design method based on the device specifically comprises the following steps:
and S1, calculating the compression resistance and the bending stiffness of the bearing seat, the variable stiffness support and the bearing seat bottom plate by using Patran, as shown in figure 3. The contact stiffness of the bearing rollers was recalculated as shown in table 3 below:
TABLE 3 calculation results of contact displacement and stiffness of rollers with inner and outer races under different loads
Finally, the rigidity obtained by calculation is connected in series to obtain the overall supporting rigidity;
s2, changing the critical rotation speed of the test bed by designing bearing supporting rigidity, wherein the critical rotation speeds corresponding to different supporting rigidity are shown in a table 4:
table 4 critical rotation speed of test stand
The calculation result of the critical rotation speed is shown in fig. 4.
S3, calculating the mode frequency mode shape of each step of the test bed; the mode frequency and mode shape calculations for the different orders are shown in table 5 below and in fig. 5.
Table 5 modal frequencies of test stand
S4, estimating the damping ratio of the test bed by using a multi-order half-power bandwidth method based on a neural network; the principle of the algorithm is shown in fig. 6, and in particular,
the total frequency response function expression 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 i-th order modal coefficient, where P i K is the i-th order modal excitation force of the structure i For the ith order modal stiffness of the structure, +.>
Is the ith order mode shape of the structure; f (f) i Undamped free vibration frequency for the ith order mode; zeta type toy i Is the modal damping ratio of the ith order; n is the degree of freedom of the test bed; i is the mode order;
when the damping ratio of the k-th order mode of the multi-degree-of-freedom system is estimated by using a half-power bandwidth method, the influence of the other modes is mainly concentrated in the half-power frequency band of the k-th order mode. The invention utilizes the neural network to fit the modal curves l of all orders except the kth order i,i≠k (f) Solving the half power point of the k-th order mode and the amplitude values of the rest mode curves of each order at the frequency corresponding to the peak value, accumulating the amplitudes, and reducing the damping ratio estimation error; the neural network estimation curve approximation algorithm is as follows:
wherein x= [ x ] 1 ,x 2 ,...,x n ] T Inputting for the neural network, wherein n is the number of input neurons; h (x) = [ h ] 1 (x),h 2 (x),...,h m (x)] T Outputting hidden layers of the neural network, wherein m is the number of the hidden layers, and h j (x) The output of the jth neuron which is the hidden layer;
a coordinate vector that is a central point of a gaussian basis function of neurons of an hidden layer, i=1, 2,., n, j=1, 2,., 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; epsilon is the approximation error of the neural network;
wherein ,
the weight is estimated; />
Is a neural netEach order of modal curves of complex approximation; />
By means of
Solving the amplitude values of the rest of the mode curves of each order at the frequency corresponding to the k-th order mode half power point and the peak value to be x respectively i1 ，x i2 and xi3 The method comprises the steps of carrying out a first treatment on the surface of the According to the mode superposition principle, the response amplitude at the peak value of the total frequency response function dominated by the k-th order mode in the multi-degree-of-freedom system is approximately expressed as:
wherein ,Xk For the k-th order modal peak value estimated according to the traditional half-power bandwidth algorithm, a larger error exists compared with 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 the frequency response function of each order mode other than the kth order mode at the kth order mode, wherein beta k ＝f/f k For the k-th order frequency ratio, f k Undamped free vibration frequency for a kth order mode;
according to the definition of a half-power method, the mode frequency response function curve of the kth order meets the following condition
Meanwhile, the amplitude influence caused by the other modes of each order is considered, and the frequency response function curves can be respectively listed>
The left and right half power point magnitudes are related to peak point magnitudes as follows:
solving for the correspondence according to equation (6)Mode damping ratio xi of the kth order k Half power point f of kth order mode k1 and fk2 . The results of the overall damping ratio estimation of the test stand are shown in Table 6:
table 6 estimation of the overall damping ratio of the test stand
The foregoing is only a preferred embodiment of the invention, it being 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 present invention, and such modifications and adaptations are intended to be comprehended within the scope of the invention.
Claims (8)
1. The test bed for simulating bearing slip in the high-speed rotating machinery is characterized by 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 the high-speed rotating shaft (5) through the 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; the two sides of the loading bearing system are respectively provided with an axial bidirectional loading system along the axial left and right directions, and the two sides of the loading bearing system are respectively provided with a radial bidirectional loading system along the radial direction; a lubricating system for supplying lubricating oil to each bearing system is also arranged above the test bed;
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 seat bottom plate (22), a third bearing seat (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 is embedded into the third oil collecting device (24), and the third oil collecting device is connected with the third variable stiffness 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 bolts and sealing rings; the third bearing seat (23) is of an upper-lower detachable structure; the third temperature sensor (25) is arranged in the vertical through hole of the third bearing seat (23); the third eddy current displacement sensor (26) is arranged 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 arranged on the third bearing seat (23) and is used for measuring vibration signals of the third bearing seat (23) in three directions of XYZ;
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 (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); 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) and is embedded into the fourth oil collecting device (32), and is connected with the fourth rigidity-variable support (29) through a fourth bearing seat bottom 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 bolts and sealing rings; the fourth bearing seat (31) is of an upper-lower detachable structure; the fourth temperature sensor (33) is arranged in the vertical through hole of the fourth bearing seat (31); the fourth eddy current displacement sensor (34) is arranged opposite to the retainer of the double-half inner ring angular contact ball bearing (28) and is used for measuring the rotating speed of the retainer of the double-half inner ring angular contact ball bearing (28); 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 of XYZ.
2. A test stand for simulating bearing slip in a high speed rotating machine 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 housing (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-down 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 arranged in the vertical through hole of the first bearing seat (17).
3. A test bench for simulating bearing slip in a high speed rotating machine according to claim 1, characterized in that the loading bearing system comprises a loading bearing (36), a second bearing housing (37), a rubber mount (38), a loading bearing housing (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 in a long plate shape, is installed on the outer ring of the loading bearing (36) in a matching mode, is installed on the second bearing seat (37) in the vertical direction through the rubber base (38), and is embedded and fixed in a second oil collecting device (40) of the platform base (1).
4. A test bench for simulating bearing slip in a high speed rotating machine according to claim 3, characterized in that the axial bi-directional loading system comprises a first load bearing support (41), a first support (42), a first screw (43), a first straight rod ball joint bearing (44) and a first force sensor (45) symmetrically distributed along both 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), the first screw rod is 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 a first straight-rod ball joint bearing (44); the fixed end of the first straight rod type ball joint bearing (44) is connected to the corresponding through hole on the loading bearing seat (39); the lower part of the first straight rod type ball joint bearing (44) is also provided with a first supporting support (42) for supporting, and the first supporting support (42) is fixed on the platform base (1); a first force sensor (45) for displaying the tension and compression load is respectively arranged at the fixed end of the first straight-bar-type ball joint bearing (44); the first force sensors (45) on the two sides are installed in opposite directions, and the distance between the first force sensors is larger than the thickness of the loading bearing seat (39).
5. A test bed for simulating bearing slip in a high speed rotating machine according to claim 3, wherein the radial bi-directional loading system comprises a second load bearing support (46), a second lead screw (47), a second straight rod ball joint bearing (48) and a second force sensor (49) symmetrically distributed on both sides of the loading bearing support (39) 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 perpendicular 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) and used for realizing the matching with the loading bearing seat (39); and a second force sensor (49) is also arranged at the fixed end of the second straight rod type ball joint bearing (48).
6. A test stand for simulating bearing slip in a high speed rotating machine according to claim 1, characterized in that the 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-rotation-speed servo motor (3) and the platform base (1).
7. A test bench for simulating bearing slip in a high speed rotating machine according to claim 1, characterized in that the lubrication system comprises an oil temperature controller (13), a lubrication pump (14) and a lubrication lance (15); the oil temperature controller (13) is used for adjusting the temperature of the lubricating oil to be changed within the range of 0-200 ℃ in real time; the lubricating oil pump (14) regulates the flow of lubricating oil in real time and supplies the lubricating oil to each bearing system through the lubricating spray pipe (15).
8. The test bed design method for simulating bearing slip in a high-speed rotating machine according to any one of claims 1-7, comprising the steps of:
s1, calculating the compression resistance and bending stiffness of a bearing seat, a variable stiffness support and a bearing seat bottom plate by using Patran, then calculating the contact stiffness of a bearing roller, and connecting the calculated stiffness in series to obtain the overall support stiffness;
s2, calculating critical rotation speeds of the test bed under different overall support rigidities by designing the support rigidities of the bearings;
s3, calculating the mode frequency mode shape of each step 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 method comprises the steps of,
the total frequency response function expression 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 i-th order modal coefficient, where P i K is the i-th order modal excitation force of the structure i For the ith order modal stiffness of the structure, +.>
Is the ith order mode shape of the structure; f (f) i Undamped free vibration frequency for the ith order mode; zeta type toy i Is the modal damping ratio of the ith order; n is the degree of freedom of the test bed; i is the mode order;
fitting out mode curves l of each order except the kth order by using a neural network i,i≠k (f) Solving the half power point of the k-th order mode and the amplitude values of the rest mode curves of each order at the frequency corresponding to the peak value, accumulating the amplitudes, and reducing the damping ratio estimation error; the neural network estimation curve approximation algorithm is as follows:
wherein x= [ x ] 1 ,x 2 ,...,x n ] T Inputting for the neural network, wherein n is the number of input neurons; h (x) = [ h ] 1 (x),h 2 (x),...,h m (x)] T Outputting hidden layers of the neural network, wherein m is the number of the hidden layers, and h j (x) The output of the jth neuron which is the hidden layer;
a coordinate vector that is a central point of a gaussian basis function of neurons of an hidden layer, i=1, 2,., n, j=1, 2,., 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; epsilon is the approximation error of the neural network;
wherein ,
the weight is estimated; />
Each order mode curve approximated by the neural network;
by means of
Solving the amplitude values of the rest of the mode curves of each order at the frequency corresponding to the k-th order mode half power point and the peak value to be x respectively i1 ，x i2 and xi3 The method comprises the steps of carrying out a first treatment on the surface of the According to the mode superposition principle, the response amplitude at the peak value of the total frequency response function dominated by the k-th order mode in the multi-degree-of-freedom system is approximately expressed as:
wherein ,Xk For the k-th order modal peak value estimated according to the traditional half-power bandwidth algorithm, a larger error exists compared with 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 the frequency response function of each order mode other than the kth order mode at the kth order mode, wherein beta k ＝f/f k For the k-th order frequency ratio, f k Undamped free vibration frequency for a kth order mode;
according to the definition of a half-power method, the mode frequency response function curve of the kth order meets the following condition
Meanwhile, the amplitude influence caused by the other modes of each order is considered, and the frequency response function curves can be respectively listed>
The left and right half power point magnitudes are related to peak point magnitudes as follows: />
Solving the corresponding k-th order modal damping ratio xi according to the formula (6) k Half power point f of kth order mode k1 and fk2 。
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