CN108920804A - Refrigeration equipment frequency-changeable compressor excitation load emulated computation method - Google Patents
Refrigeration equipment frequency-changeable compressor excitation load emulated computation method Download PDFInfo
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Abstract
The present invention relates to simulation calculation fields,Aiming at the problem that excitation load of the refrigeration equipment frequency-changeable compressor under all working Frequency point can not disposably be obtained when limit member emulation,Propose a kind of refrigeration equipment frequency-changeable compressor excitation load emulated computation method,Vibration displacement test data of the test point under all working Frequency point is tested out using vibration test system and establishes the emulation primary data that the simulation model of frequency-changeable compressor obtains frequency-changeable compressor using finite element simulation,Root calculates the calculating displacement data one under all Frequency points according to emulation primary data and calculates displacement data two,Then according to vibration displacement test data,It calculates displacement data one and calculates the excitation load that displacement data two calculates frequency-changeable compressor,Simulation model of the frequency-changeable compressor with pipeline can further be established and obtain pipeline emulation primary data,Primary data is emulated according to pipeline and above-mentioned excitation load carries out the evaluation for calculating the pipeline vibration reliability suitable for refrigeration equipment of pipeline stress.
Description
Technical Field
The invention relates to the field of simulation calculation, in particular to a simulation calculation method of an excitation load.
Background
The refrigerating equipment adopting the variable frequency compressor comprises a main loop consisting of the variable frequency compressor, a condenser, a pipeline, an evaporator communicated with the condenser and a throttling element communicated with the evaporator and the condenser, wherein the throttling element is generally realized by adopting a capillary tube, the variable frequency compressor generally comprises a rigid body of the variable frequency compressor and a liquid storage tank communicated with the rigid body of the variable frequency compressor, the pipeline comprises an exhaust pipeline and a gas return pipeline, the rigid body of the variable frequency compressor is communicated with the condenser through the exhaust pipeline, the liquid storage tank is communicated with the evaporator through the gas return pipeline, once the pipeline has cracks or breaks, the refrigerant can be leaked to cause the refrigerating equipment to be incapable of working, so the vibration reliability of the pipeline in the refrigerating equipment is very important, the vibration reliability of the pipeline can be evaluated by the vibration stress of the corresponding pipeline when the compressor works, and the accurate vibration stress can be realized by tests, if a test mode is adopted, the problems of complex test process, low precision and high cost exist, generally, guidance is provided through finite element simulation calculation results in the early stage of pipeline design, but because the frequency conversion compressor used by the refrigeration equipment has a complex structure and more vibration excitation sources, accurate loads are difficult to obtain through direct test of tests, the finite element simulation cannot input the accurate loads, the simulation results and the test tests cannot be aligned, and the application of the finite element simulation technology in the frequency conversion compressor pipeline vibration analysis is greatly limited.
Chinese patent publication No. CN102562568B discloses a load test analysis method for a rotor compressor for a refrigeration equipment, which adopts a load test method, and the method only describes a load calculation method at a single frequency point, because there are many frequency points of a general inverter compressor, if it is desired to obtain a load at each frequency point, the method needs to calculate for many times separately, and at the same time, a load at only one frequency point can be input at a time in finite element simulation calculation, and the stress at one frequency point is calculated, so that the simulation calculation amount is large and difficult to realize, and thus, the problems of large calculation amount and low efficiency of the load of the inverter compressor exist.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the method solves the problem that the excitation load of the variable frequency compressor of the refrigeration equipment at all working frequency points cannot be obtained at one time during finite element simulation in the prior art, and provides a simulation calculation method for the excitation load of the variable frequency compressor of the refrigeration equipment.
The invention solves the technical problems and adopts the technical scheme that:
the method for simulating and calculating the excitation load of the variable-frequency compressor of the refrigeration equipment comprises the following steps:
the method comprises the following steps that firstly, vibration displacement test data of a test point on the variable frequency compressor under all working frequency points are obtained by adopting a vibration test system, wherein the test point at least comprises a test point I and a test point II, the test point I is positioned at an exhaust port of a rigid body of the variable frequency compressor, and the test point II is positioned at an air suction port of a liquid storage tank;
establishing a simulation model of the variable frequency compressor and carrying out finite element vibration simulation, taking the position corresponding to the test point in the simulation model as an observation point, marking the observation points corresponding to the test point I and the test point II as an observation point I and an observation point II, and only applying a rotation moment in the vertical direction at the load action point of the simulation model to obtain simulation displacement data I of the observation point at any determined working frequency point and displacement frequency response amplitude data I at all working frequency points; only applying radial force in the direction of a connecting line of the observation point I and the observation point II at the load action point to obtain simulation displacement data II of the observation point under the determined working frequency point and displacement frequency response amplitude data II under all the working frequency points; calculating first calculated displacement data when the observation point only acts on the rotation moment under all working frequency points according to the first simulated displacement data and the first displacement frequency response amplitude data, and calculating second calculated displacement data when the observation point only acts on the radial force under all working frequency points according to the second simulated displacement data and the second displacement frequency response amplitude data;
calculating according to the first calculated displacement data, the second calculated displacement data and the vibration displacement test data to obtain excitation loads of the finite element simulation time-varying frequency compressor at all working frequency points;
the sequence of the first step and the second step can be interchanged.
Preferably, in the second step, a connecting line of the first observation point and the second observation point is taken as an X direction, a direction perpendicular to the connecting line of the first observation point and the second observation point in a horizontal plane is taken as a Y direction, a vertical direction is taken as a Z direction, and X is setiαkAnd yiαkRespectively as observation point i under k-th load condition and determined working frequency point fαDisplacement in the lower X and Y directions, XijkAnd yijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjLower X-and Y-directional displacements, wherein fα∈fjJ is 1-p, p is the number of working frequency points of the variable frequency compressor, i is 1-n, n is a positive integer representing the number of observation points and equal to the number of test points, k is a positive integer, k is equal to the load condition represented by 1, namely, a rotating moment M in the vertical direction is applied to the load action point, and k is equal to 2, namely, a radial force F in the direction of connecting a first observation point and a second observation point is applied to the load action point; let AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjDisplacement frequency response amplitude in lower X and Y directions, AxiαkAnd AyiαkRespectively as observation point i under k-th load condition and determined working frequency point fαDisplacement frequency response amplitude values in the lower X direction and the lower Y direction;
the simulation displacement data one comprises xiα1And yiα1The displacement frequency response amplitude data includes Axi11、Axi21......Axiα1......Axip1And Ayi11、Ayi21......Ayiα1......Ayip1Simulation displacement data twoIncluding xiα2And yiα2The second displacement frequency response amplitude data comprises Axi12、Axi22......Axiα2......Axip2And Ayi12、Ayi22......Ayiα2......Ayip2The first calculated displacement data includes xij1And yij1The second calculated displacement data comprises xij2And yij2，
Preferably, in the first step, a line connecting the first test point and the second test point is taken as an X direction, a direction perpendicular to the line connecting the first test point and the second test point in a horizontal plane is taken as a Y direction, and X 'is set'ijAnd y'ijFor a test point i corresponding to an observation point i at any operating frequency point fjThe vibration displacement in the X direction and the Y direction respectively, and the vibration displacement test data comprises X'ijAnd y'ij；
In the third step, the frequency conversion compressor is arranged at each working frequency point f when finite element simulation is carried outjThe lower excitation load being the rotation moment MjAnd a radial force FjThen (M)j,Fj)＝Uj -1*VjWherein
further, the third step is followed by the following steps:
and fourthly, establishing a simulation model of the variable frequency compressor with the pipeline, carrying out finite element vibration simulation to obtain pipeline simulation initial data of any observation point C on the pipeline, and calculating the vibration stress of the observation point C at all working frequency points according to the excitation load of the variable frequency compressor at all working frequency points and the pipeline simulation initial data.
Preferably, a connecting line of the observation point I and the observation point II is taken as an X direction, a direction perpendicular to the connecting line of the observation point I and the observation point II in a horizontal plane is taken as a Y direction, and a vertical direction is taken as a Z direction, and the frequency conversion compressor is recorded at each working frequency point fjThe lower excitation load being the rotation moment MjAnd a radial force FjThe fourth step comprises the following steps:
s1, establishing a simulation model of the variable frequency compressor with the pipeline, applying a Z-direction rotating moment M to a load action point by adopting finite element simulation, obtaining vibration stress frequency response curves of any observation point C on the pipeline corresponding to the simulation model of the variable frequency compressor with the pipeline in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point fjLower vibration stress frequency response amplitude and any determined working frequency point fβThe vibration stress of the observation point C at each working frequency point fjThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcj1、Aycj1And Azcj1J ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, and the observation point C is at the determined frequency point fβThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcβ1、Aycβ1And Azcβ1Observation point C at determined frequency point fβThe lower vibration stress in X, Y and Z directions is Xcβ1、ycβ1And zcβ1，fβ∈fj；
S2, applying X-direction radial force F to a load action point by adopting finite element simulation to obtain vibration stress frequency response curves of any observation point C on the pipeline corresponding to the simulation model of the variable-frequency compressor with the pipeline in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point FjMagnitude of lower stress response and any one determined operating frequency point fβThe vibration stress of the observation point C at each working frequency point fjThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcj2、Aycj2And Azcj2Observation point C at determined frequency point fβThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcβ2、Aycβ2And Azcβ2Observation point C at determined frequency point fβThe lower vibration stress in X, Y and Z directions is Xcβ2、ycβ2And zcβ2Wherein j ranges from 1 to P, P is the number of working frequency points of the variable frequency compressor, and fβ∈fj；
S3, applying a Z-direction rotation moment M and an X-direction radial force F on a load action point of the simulation model by utilizing finite element simulation to obtain vibration stress frequency response curves of the observation point C in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point F through the vibration stress frequency response curvesjThe frequency response amplitudes of the vibration stress in the lower X direction, the lower Y direction and the lower Z direction are respectively marked as Axcj3、Aycj3And Azcj3；
S4, calculating the vibration stress of the observation point C in the simulation model with the pipeline of the variable frequency compressor at the corresponding position on the pipeline, wherein the rotation moment M of any observation point C on the pipeline in the Z directionjAnd X-direction radial force FjAnd each operating frequency point fjThe lower X-, Y-and Z-direction vibration stresses are denoted as deltaxcj、δycjAnd deltazcjThen, then
Wherein,
wherein,
wherein,
the steps S1, S2 and S3 are interchangeable.
Further, the verification step between the third step and the fourth step is as follows: and obtaining vibration displacement data of the observation point I and the observation point II under all working frequency points by adopting finite element simulation calculation according to the excitation load, comparing the vibration displacement data under the same working frequency points in the same direction with the vibration displacement test data of the test point I and the test point II in the step I, entering the step 4 if the difference value of the vibration displacement data and the test point II is within a preset error, and otherwise, exiting, checking and adjusting a simulation model of the variable frequency compressor and then carrying out simulation calculation again.
Preferably, a connecting line of the first test point and the second test point is taken as an X direction, and a direction perpendicular to the connecting line of the first test point and the second test point in a horizontal plane is taken as a Y direction, wherein the verifying step comprises the following steps:
t1, line x'ijAnd y'ijFor a test point i corresponding to an observation point i at any operating frequency point fjAnd vibration displacement corresponding to the X direction and the Y direction, wherein the value range of i is 1-n, n is a positive integer representing the number of the test points, and the vibration displacement test data comprises X'ijAnd y'ij(ii) a Recording each operating frequency point fjThe lower excitation load being the rotation moment MjAnd a radial force Fj(ii) a Taking the connecting line of the observation point I and the observation point II as the X direction, and taking the direction which is vertical to the connecting line of the observation point I and the observation point II in the horizontal planeThe direction is Y direction, the vertical direction is Z direction, the finite element simulation is adopted to apply X radial force F and Z rotation moment M on the load action point, the displacement frequency response amplitude data III under all working frequency points of the observation point is obtained, and A is setxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjThe displacement frequency response amplitude values of the lower X direction and the lower Y direction, k is a positive integer, k is equal to 1 to represent that the load condition is that the rotating moment M in the vertical direction is applied at the load acting point, k is equal to 2 to represent that the load condition is that the radial force F in the direction of connecting the first observation point and the second observation point is applied at the load acting point, k is equal to 3 to represent that the rotating moment M and the radial force F in the same direction are synchronously applied at the load acting point, and the displacement frequency response amplitude data III comprises Ax1j3、Ay1j3、Ax2j3、Ay2j3；
T2, recording the vertical rotation moment M exerted by the observation point I at the load action pointjEach frequency point fjThe displacements in the X-direction and Y-direction are X'1j1And y'1j1Recording the vertical rotation moment M applied to the load action point by the observation point IIjEach frequency point fjThe displacements in the X-direction and Y-direction are X'2j1And y'2j1Let xiαkAnd yiαkRespectively as observation point i under k-th load condition and determined working frequency point fαSimulating displacement in the lower X direction and the lower Y direction, i ranges from 1 to n, n is a positive integer representing the number of observation points, j ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, fα∈fj，AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjThe displacement frequency response amplitude of the lower X direction and the lower Y direction
T3, recording observation point-application of X direction at load application pointRadial force FjAnd each frequency point fjThe displacements in the X-direction and Y-direction are X'1j2And y'1j2Recording the radial force F applied to the load acting point in the X direction by the observation point IIjAnd each frequency point fjThe displacements in the X-direction and Y-direction are X'2j1And y'2j1Then, then
T4, recording test point I corresponding to observation point I at each frequency point fjThe calculated vibration displacements in the lower X and Y directions are respectively Dx1jAnd Dy1jThen, then
Wherein,
wherein,
recording the frequency points f of the test point II corresponding to the observation point IIjThe calculated vibration displacements in the lower X and Y directions are respectively Dx2jAnd Dy2j，
Wherein,
wherein,
t5, calculating the calculated vibration displacement (D) of the first test point in the X direction and the Y directionx1j，Dy1j) And vibration displacement test data (x'1jAnd y'1j) Calculating the calculated vibration displacement (D) of the test point two in the X direction and the Y directionx2j，Dy2j) And vibration displacement test data (x'2jAnd y'2j) Judging whether the data error I and the data error II are smaller than or equal to an error threshold value, if so, entering a step IV, otherwise, exiting, checking and adjusting a simulation model of the variable frequency compressor and then carrying out simulation calculation again;
the sequences of the step T1, the step T2 and the step T3 can be interchanged.
Preferably, in the first step, the vibration testing system comprises a variable frequency compressor, a pipeline, a controller, a frequency converter for driving the compressor to operate and a collecting unit for collecting vibration displacement test data of the testing point, the variable frequency compressor comprises a variable frequency compressor rigid body (2) and a liquid storage tank (1), an exhaust port (4) is arranged at the top of the variable frequency compressor rigid body (2), an air suction port (3) is arranged at the top of the liquid storage tank (1), the exhaust port and the air suction port are respectively connected with the pipeline, and the controller is used for controlling the temperature and the pressure of the system so that the temperature and the pressure of the testing point I and the testing point II are respectively consistent with the temperature and the pressure of corresponding positions under the overall operation load equivalent working condition of the.
Further, the acquisition unit comprises a vibration signal acquisition instrument and an acceleration sensor; and/or the pipeline is a hose.
Preferably, the load action point is located on the surface of the rigid shell of the inverter compressor corresponding to the simulation model.
The invention has the beneficial effects that:
1) the excitation load under all working frequency points of the variable frequency compressor is calculated through a finite element simulation and algorithm, the calculated amount is small, the efficiency is high, and the complex operation of calculating frequency points one by one in the traditional simulation is avoided.
2) The invention also provides a method for calculating the pipeline vibration stress of the variable frequency compressor under all working frequency points by using a finite element simulation and an algorithm, the method can obtain the pipeline stress values of the variable frequency compressor under all the working frequency points by program calculation only by obtaining a group of initial data through finite element calculation, and compared with test tests and traditional simulation, the method has the characteristics of high efficiency and strong practicability.
3) The method comprises the steps of firstly calculating vibration displacement data of the test point I and the test point II under all working frequency points, comparing the vibration displacement data under the same working frequency points in the same direction with vibration displacement test data of the test point I and the test point II in the step I, and further calculating the stress of pipelines under all working frequencies if the difference value of the vibration displacement data and the test data is within a preset error, otherwise, adjusting a simulation model to ensure the accuracy of excitation load and further ensure the accuracy of subsequent stress calculation.
Drawings
FIG. 1 is a flow chart of a simulation calculation method of pipeline vibration stress in an embodiment of the present invention;
FIG. 2 is a front view and a coordinate system of the inverter compressor in an embodiment of the present invention;
FIG. 3 is a top view and a coordinate system of the inverter compressor according to the embodiment of the present invention;
wherein, 1 is a liquid storage tank, 2 is a rigid body of the variable frequency compressor, 3 is an air suction port of the liquid storage tank, and 4 is an air exhaust port of the rigid body of the variable frequency compressor.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings and embodiments.
The invention aims to solve the problem that the excitation load of a variable frequency compressor of refrigeration equipment under all working frequency points cannot be obtained at one time in finite element simulation in the prior art, and provides a simulation calculation method for the excitation load of the variable frequency compressor of the refrigeration equipment, which comprises the following steps:
the method comprises the following steps of firstly, obtaining vibration displacement test data of a test point on the variable frequency compressor under all working frequency points by adopting a vibration test system, wherein the test point at least comprises a test point I and a test point II, the test point I is positioned at an exhaust port of a rigid body of the variable frequency compressor, and the test point II is positioned at an air suction port of a liquid storage tank.
Establishing a simulation model of the variable frequency compressor and carrying out finite element vibration simulation, taking the position corresponding to the test point in the simulation model as an observation point, marking the observation points corresponding to the test point I and the test point II as an observation point I and an observation point II, and only applying a rotation moment in the vertical direction at the load action point of the simulation model to obtain simulation displacement data I of the observation point at any determined working frequency point and displacement frequency response amplitude data I at all working frequency points; only applying radial force in the direction of a connecting line of the observation point I and the observation point II at the load action point to obtain simulation displacement data II of the observation point under the determined working frequency point and displacement frequency response amplitude data II under all the working frequency points; and calculating first calculated displacement data when the observation point only acts on the rotating moment under all working frequency points according to the first simulated displacement data and the first displacement frequency response amplitude data, and calculating second calculated displacement data when the observation point only acts on the radial force under all working frequency points according to the second simulated displacement data and the second displacement frequency response amplitude data.
And step three, calculating according to the calculated displacement data I, the calculated displacement data II and the vibration displacement test data to obtain the excitation load of the finite element simulation time-varying frequency compressor at all working frequency points.
Considering that the first step and the second step are finally used for inputting the calculation of the third step, there is essentially no precedence order, that is, the order of the first step and the second step can be interchanged or synchronously performed, and considering that the time of the first step is longer than that of the second step, the second step can be performed first and then again.
Examples
As shown in fig. 1, in this embodiment, a vibration test system is used to test vibration displacement test data of a test point at all operating frequency points and establish a simulation model of the inverter compressor to obtain simulation initial data of the inverter compressor by finite element simulation, where the simulation initial data includes the simulation displacement data one, the displacement frequency response amplitude data one, the simulation displacement data two and the displacement frequency response amplitude data two, the first calculated displacement data of an observation point at all operating frequency points when only the rotation torque acts is calculated according to the simulation displacement data one and the displacement frequency response amplitude data one, the second calculated displacement data of the observation point at all operating frequency points when only the radial force acts is calculated according to the simulation displacement data two and the displacement frequency response amplitude data two, and then the excitation load of the inverter compressor is calculated according to the vibration displacement test data, the first calculated displacement data and the second calculated displacement data, and then verifying the accuracy of the excitation load, if the verification is passed, establishing a simulation model of the variable frequency compressor with the pipeline, obtaining pipeline simulation initial data of the pipeline by adopting finite element simulation, calculating the stress of the pipeline according to the pipeline simulation initial data and the excitation load to generate a stress report, otherwise, exiting the process, adjusting, checking and adjusting the simulation model of the variable frequency compressor, and then carrying out simulation calculation again.
Step one, obtaining an upper test point of a variable frequency compressor by adopting a vibration test systemThe vibration displacement test data under all the working frequency points at least comprises a first test point and a second test point, as shown in fig. 2 and fig. 3, the first test point is located at an exhaust port 4 at the top of the rigid body 2 of the variable frequency compressor, the second test point is located at an air suction port 3 at the top of the liquid storage tank 1, specifically, a connecting line of the first test point and the second test point can be an X direction, a direction perpendicular to the connecting line of the first test point and the second test point in a horizontal plane is a Y direction, the original point is selected for calculation convenience, an intersection point of the circle center of the rigid body of the variable frequency compressor and the X direction can be selected as the original point, and the vibration'ijAnd y'ijWherein, x'ijAnd y'ijFor a test point i corresponding to an observation point i at any operating frequency point fjAnd the test points I and the test points II are placed in the embodiment as typical test points according to the vibration displacement corresponding to the X direction and the Y direction, and the excitation load of the inverter compressor can be calculated more accurately as the number of the test points is more.
The vibration testing system comprises a variable frequency compressor, a pipeline, a controller, a frequency converter and a collecting unit, wherein the frequency converter is used for driving the compressor to operate, the collecting unit is used for collecting vibration displacement test data of a testing point, the variable frequency compressor comprises a rigid variable frequency compressor body 2 and a liquid storage tank 1, an exhaust port 4 is arranged at the top of the rigid variable frequency compressor body 2, an air suction port 3 is arranged at the top of the liquid storage tank 1, pipelines are respectively connected onto the exhaust port and the air suction port, and the controller is used for controlling the temperature and the pressure of the system so that the temperature and the pressure of a testing point I and the temperature and the pressure of a testing point. Wherein, the acquisition unit can include vibration signal collection appearance and acceleration sensor, in order to reduce the constraint of pipeline to frequency conversion compressor, improves frequency conversion compressor's load test accuracy, and the pipeline can be the hose.
Establishing a simulation model of the variable frequency compressor and carrying out finite element vibration simulation, taking the position corresponding to the test point in the simulation model as an observation point, marking the observation points corresponding to the test point I and the test point II as an observation point I and an observation point II, and only applying a rotating moment in the vertical direction at a load action point of the simulation model to obtain simulation displacement data I of the observation point at any determined working frequency point and displacement frequency response amplitude data I at all working frequency points; only applying radial force in the direction of a connecting line of the observation point I and the observation point II at the load action point to obtain simulation displacement data II of the observation point under the determined working frequency point and displacement frequency response amplitude data II of all the working frequency points; and calculating first calculated displacement data when the observation point only acts on the rotation moment under all working frequency points according to the first simulated displacement data and the first displacement frequency response amplitude data, and calculating second calculated displacement data when the observation point only acts on the radial force under all working frequency points according to the second simulated displacement data and the second displacement frequency response amplitude data, wherein the load acting point is positioned on the surface of the rigid shell of the variable frequency compressor corresponding to the simulated model.
Specifically, a coordinate system adopted in the finite element simulation needs to be corresponding to and consistent with a coordinate system in the vibration test system, a connecting line of the observation point I and the observation point II can be taken as an X direction, a direction perpendicular to the connecting line of the observation point I and the observation point II in a horizontal plane is taken as a Y direction, a vertical direction is taken as a Z direction, an intersection point of the circle center of the corresponding variable frequency compressor rigid body in the simulation model and the X direction can be selected as an origin, and X is setiαkAnd yiαkRespectively as observation point i under k-th load condition and determined working frequency point fαDisplacement in the lower X and Y directions, XijkAnd yijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjLower X-and Y-directional displacements, wherein fα∈fjJ is 1-p, p is the number of working frequency points of the variable frequency compressor, i is 1-n, n is a positive integer representing the number of observation points and equal to the number of test points, k is a positive integer, k is equal to the load condition represented by 1, namely, a rotating moment M in the vertical direction is applied to the load action point, and k is equal to 2, namely, a radial force F in the direction of connecting a first observation point and a second observation point is applied to the load action point; let AxijkAnd AyijkRespectively observation point i under k load condition and any working frequencyPoint fjDisplacement frequency response amplitude in lower X and Y directions, AxiαkAnd AyiαkRespectively as observation point i under k-th load condition and determined working frequency point fαDisplacement frequency response amplitude values in the lower X direction and the lower Y direction;
the simulated displacement data one includes xiα1And yiα1The displacement frequency response amplitude data includes Axi11、Axi21......Axiα1......Axip1And Ayi11、Ayi21......Ayiα1......Ayip1The simulation displacement data two comprises xiα2And yiα2The second displacement frequency response amplitude data comprises Axi12、Axi22......Axiα2......Axip2And Ayi12、Ayi22......Ayiα2......Ayip2Calculating displacement data-including xij1And yij1Calculating the displacement data two includes xij2And yij2，
Calculating according to the first calculated displacement data, the second calculated displacement data and the vibration displacement test data to obtain excitation loads of the finite element simulation time-varying frequency compressor at all working frequency points;
specifically, the inverter compressor is set at each working frequency point f when finite element simulation is carried outjThe lower excitation load being the rotation moment MjAnd a radial force FjThen, thenWherein,
the above-mentioned rotating moment MjAnd a radial force FjThe calculation of (2) can be automatically calculated by an editable program.
Even if the load of each frequency point is obtained by adopting the method, the stress can be calculated by inputting the load of a certain frequency point at one time by the existing finite element simulation technology, the time for calculating the stress in each simulation is several hours, and if the stress of all the frequency points is obtained, the stress of each frequency point can be obtained by performing simulation calculation for many times, so that the problems of large simulation calculation amount and low efficiency of pipeline stress exist. In order to quickly and accurately obtain the vibration stress of the pipeline for evaluating the vibration reliability of the pipeline, the third step further includes the following steps:
and fourthly, establishing a simulation model of the variable frequency compressor with the pipeline, carrying out finite element vibration simulation to obtain pipeline simulation initial data of any observation point C on the pipeline, and calculating the vibration stress of the observation point C at all working frequency points according to the excitation load of the variable frequency compressor at all working frequency points and the pipeline simulation initial data.
In order to ensure the accuracy of the excitation load, the following verification steps are further included between the third step and the fourth step: and (4) obtaining vibration displacement data of the observation point I and the observation point II under all working frequency points by adopting finite element simulation calculation according to the excitation load, comparing the vibration displacement data of the same working frequency point in the same direction with the vibration displacement test data of the test point I and the test point II in the step I, entering the step 4 if the difference value of the vibration displacement data of the same working frequency point and the vibration displacement test data of the test point I and the test point II is within a preset error, and otherwise, exiting, checking and adjusting the simulation model and then carrying out simulation calculation again.
Specifically, the connection line of the first test point and the second test point is taken as the X direction, and the direction perpendicular to the connection line of the first test point and the second test point in the horizontal plane is taken as the Y direction, and the verification step comprises the following steps:
t1, line x'ijAnd y'ijFor a test point i corresponding to an observation point i at any operating frequency point fjThe vibration displacement corresponding to the X direction and the Y direction, and the value of iThe range is 1-n, n is a positive integer to represent the number of the test points, and the vibration displacement test data comprises x'ijAnd y'ij(ii) a Recording each operating frequency point fjThe lower excitation load being the rotation moment MjAnd a radial force Fj(ii) a Taking a connecting line of the observation point I and the observation point II as an X direction, taking a direction perpendicular to the connecting line of the observation point I and the observation point II in a horizontal plane as a Y direction, taking a vertical direction as a Z direction, adopting finite element simulation to apply X radial force F and Z rotation moment M on a load action point, obtaining displacement frequency response amplitude data III under all working frequency points of the observation point, and setting AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjThe displacement frequency response amplitude values of the lower X direction and the lower Y direction, k is a positive integer, k is equal to 1 to represent that the load condition is that a rotating moment M in the vertical direction is exerted at the load action point, k is equal to 2 to represent that the load condition is that a radial force F in the direction connecting a first observation point and a second observation point is exerted at the load action point, k is equal to 3 to represent that the rotating moment M and the radial force F in the same direction are synchronously exerted at the load action point, and the displacement frequency response amplitude data III comprises Ax1j3、Ay1j3、Ax2j3、Ay2j3。
T2, recording the vertical rotation moment M exerted by the observation point I at the load action pointjEach frequency point fjThe displacements in the X-direction and Y-direction are X'1j1And y'1j1Recording the vertical rotation moment M exerted by the observation point II on the load action pointjEach frequency point fjThe displacements in the X-direction and Y-direction are X'2j1And y'2j1Let xiαkAnd yiαkRespectively as observation point i under k-th load condition and determined working frequency point fαSimulating displacement in the lower X direction and the lower Y direction, i ranges from 1 to n, n is a positive integer representing the number of observation points, j ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, fα∈fj，AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjThe displacement frequency response amplitude of the lower X direction and the lower Y direction
T3, noting that the observation point-applied X-direction radial force F at the load application pointjAnd each frequency point fjThe displacements in the X-direction and Y-direction are X'1j2And y'1j2Recording the radial force F applied to the load acting point in the X direction by the observation point IIjAnd each frequency point fjThe displacements in the X-direction and Y-direction are X'2j1And y'2j1Then, then
T4, recording test point I corresponding to observation point I at each frequency point fjThe calculated vibration displacements in the lower X and Y directions are respectively Dx1jAnd Dy1jThen, then
Wherein,
wherein,
recording the frequency points f of the test point II corresponding to the observation point IIjThe calculated vibration displacements in the lower X and Y directions are respectively Dx2jAnd Dy2j，
Wherein,
wherein,
t5, calculating the calculated vibration displacement (D) of the first test point in the X direction and the Y directionx1j，Dy1j) And vibration displacement test data (x'1jAnd y'1j) Calculating the calculated vibration displacement (D) of the test point two in the X direction and the Y directionx2j，Dy2j) And vibration displacement test data (x'2jAnd y'2j) And judging whether the data error I and the data error II are smaller than or equal to the error threshold value, if so, entering the step four, otherwise, exiting, checking and adjusting the simulation model of the variable frequency compressor and then carrying out simulation calculation again.
The sequence of the step T1, the step T2 and the step T3 can be interchanged, and the step T2, the step T3, the step T4 and the step T5 can be calculated by a program.
Specifically, the fourth step includes the following steps:
s1, establishing a simulation model of the variable frequency compressor with the pipeline, applying a Z-direction rotating moment M to a load action point by adopting finite element simulation, obtaining vibration stress frequency response curves of any observation point C on the pipeline corresponding to the simulation model of the variable frequency compressor with the pipeline in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point fjLower vibration stress frequency response amplitude and any determined working frequency point fβThe vibration stress of the observation point C at each working frequency point fjLower X-, Y-and Z-direction vibratory stress frequency responseAmplitude values of Axcj1、Aycj1And Azcj1J ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, and the observation point C is at the determined frequency point fβThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcβ1、Aycβ1And Azcβ1Observation point C at determined frequency point fβThe lower vibration stress in X, Y and Z directions is Xcβ1、ycβ1And zcβ1，fβ∈fj。
S2, applying X-direction radial force F to a load action point by adopting finite element simulation to obtain vibration stress frequency response curves of any observation point C on the pipeline corresponding to the simulation model of the variable-frequency compressor with the pipeline in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point FjMagnitude of lower stress response and any one determined operating frequency point fβThe vibration stress of the observation point C at each working frequency point fjThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcj2、Aycj2And Azcj2Observation point C at determined frequency point fβThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcβ2、Aycβ2And Azcβ2Observation point C at determined frequency point fβThe lower vibration stress in X, Y and Z directions is Xcβ2、ycβ2And zcβ2Wherein j ranges from 1 to P, P is the number of working frequency points of the variable frequency compressor, and fβ∈fj。
S3, applying a Z-direction rotation moment M and an X-direction radial force F on a load action point of the simulation model by utilizing finite element simulation to obtain vibration stress frequency response curves of the observation point C in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point F through the vibration stress frequency response curvesjThe frequency response amplitudes of the vibration stress in the lower X direction, the lower Y direction and the lower Z direction are respectively marked as Axcj3、Aycj3And Azcj3。
S4, calculating the vibration stress of the observation point C in the simulation model with the pipeline of the variable frequency compressor at the corresponding position on the pipeline, and calculating the Z-direction rotation moment M of any observation point C on the pipelinejAnd X-direction radial force FjAnd each operating frequency point fjThe lower X-, Y-and Z-direction vibration stresses are denoted as deltaxcj、δycjAnd deltazcjThen, then
Wherein,
wherein,
wherein,
step S1, step S2 and step S3 are interchangeable, δxcj、δycjAnd deltazcjThe calculation of (2) can be automatically calculated by an editable program.
Through the steps, a set of initial data can be obtained only through finite element calculation, the stress values of the pipelines under all working frequency points of the variable frequency compressor can be obtained through program calculation, and compared with test tests and traditional simulation, the method has the advantages of being high in efficiency and strong in practicability.
Finally, a pipeline stress report can be generated based on the calculated stress.
It should be noted that the above-mentioned drawings are only for illustrating the principles of the present invention, and since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly, all suitable modifications and equivalents may be resorted to, falling within the scope of the invention.
Claims (10)
1. The method for simulating and calculating the excitation load of the variable-frequency compressor of the refrigeration equipment is characterized by comprising the following steps of:
the method comprises the steps that firstly, vibration displacement test data of a test point on the variable frequency compressor under all working frequency points are obtained by a vibration test system, wherein the test point at least comprises a test point I and a test point II, the test point I is positioned at an exhaust port (4) of a rigid body (2) of the variable frequency compressor, and the test point II is positioned at an air suction port (3) of a liquid storage tank (1);
establishing a simulation model of the variable frequency compressor and carrying out finite element vibration simulation, taking the position corresponding to the test point in the simulation model as an observation point, marking the observation points corresponding to the test point I and the test point II as an observation point I and an observation point II, and only applying a rotation moment in the vertical direction at the load action point of the simulation model to obtain simulation displacement data I of the observation point at any determined working frequency point and displacement frequency response amplitude data I at all working frequency points; only applying radial force in the direction of a connecting line of the observation point I and the observation point II at the load action point to obtain simulation displacement data II of the observation point under the determined working frequency point and displacement frequency response amplitude data II under all the working frequency points; calculating first calculated displacement data when the observation point only acts on the rotation moment under all working frequency points according to the first simulated displacement data and the first displacement frequency response amplitude data, and calculating second calculated displacement data when the observation point only acts on the radial force under all working frequency points according to the second simulated displacement data and the second displacement frequency response amplitude data;
calculating according to the first calculated displacement data, the second calculated displacement data and the vibration displacement test data to obtain excitation loads of the finite element simulation time-varying frequency compressor at all working frequency points;
the sequence of the first step and the second step can be interchanged.
2. The simulation calculation method for exciting load of inverter compressor of refrigeration equipment according to claim 1, wherein in the second step, a connecting line of the first observation point and the second observation point is taken as an X direction, a direction perpendicular to the connecting line of the first observation point and the second observation point in a horizontal plane is taken as a Y direction, a vertical direction is taken as a Z direction, and X is setiαkAnd yiαkRespectively as observation point i under k-th load condition and determined working frequency point fαDisplacement in the lower X and Y directions, XijkAnd yijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjLower X-and Y-directional displacements, wherein fα∈fjJ ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, i ranges from 1 to n,n is a positive integer representing the number of observation points and equal to the number of test points, k is a positive integer, k is equal to 1 representing a load condition that a vertical rotation moment M is applied at a load action point, and k is equal to 2 representing a load condition that a radial force F in a connecting line direction of a first observation point and a second observation point is applied at the load action point; let AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjDisplacement frequency response amplitude in lower X and Y directions, AxiαkAnd AyiαkRespectively as observation point i under k-th load condition and determined working frequency point fαDisplacement frequency response amplitude values in the lower X direction and the lower Y direction;
the simulation displacement data one comprises xiα1And yiα1The displacement frequency response amplitude data includes Axi11、Axi21......Axiα1......Axip1And Ayi11、Ayi21......Ayiα1......Ayip1The simulation displacement data two comprises xiα2And yiα2The second displacement frequency response amplitude data comprises Axi12、Axi22......Axiα2......Axip2And Ayi12、Ayi22......Ayiα2......Ayip2The first calculated displacement data includes xij1And yij1The second calculated displacement data comprises xij2And yij2，
3. The simulation calculation method for excitation load of the inverter compressor of the refrigeration equipment as claimed in claim 2, wherein in the first step, a connecting line of the first test point and the second test point is taken as an X direction, a direction perpendicular to the connecting line of the first test point and the second test point in a horizontal plane is taken as a Y direction, and X 'is set'ijAnd y'ijFor a test point i corresponding to an observation point i at any operating frequency point fjThe vibration displacement in the X direction and the Y direction is testedThe test data comprises x'ijAnd y'ij；
In the third step, the frequency conversion compressor is arranged at each working frequency point f when finite element simulation is carried outjThe lower excitation load being the rotation moment MjAnd a radial force FjThen (M)j,Fj)＝Uj -1*VjWhereinvj＝(x′1jy′1jx′2jy2j... ... x′njy′nj)T。
4. the method for simulating and calculating the excitation load of the inverter compressor of the refrigeration equipment according to claim 1, wherein the step three is followed by the step of:
and fourthly, establishing a simulation model of the variable frequency compressor with the pipeline, carrying out finite element vibration simulation to obtain pipeline simulation initial data of any observation point C on the pipeline, and calculating the vibration stress of the observation point C at all working frequency points according to the excitation load of the variable frequency compressor at all working frequency points and the pipeline simulation initial data.
5. The simulation calculation method for exciting load of inverter compressor of refrigeration equipment according to claim 4, wherein the line connecting the observation point I and the observation point II is taken as X direction, the direction perpendicular to the line connecting the observation point I and the observation point II in the horizontal plane is taken as Y direction, and the vertical direction is taken as Z direction, and the inverter compressor is recorded at each working frequency point fjThe lower excitation load being the rotation moment MjAnd a radial force FjThe fourth step comprises the following steps:
s1, establishing a simulation model of the variable frequency compressor with the pipeline, applying a Z-direction rotating moment M to a load action point by adopting finite element simulation to obtain vibration stress frequency response curves of any observation point C on the pipeline corresponding to the simulation model of the variable frequency compressor with the pipeline in the X direction, the Y direction and the Z direction, and vibrating the stress frequency response curvesObtaining observation points C at each working frequency point f by dynamic stress frequency response curvejLower vibration stress frequency response amplitude and any determined working frequency point fβThe vibration stress of the observation point C at each working frequency point fjThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcj1、Aycj1And Azcj1J ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, and the observation point C is at the determined frequency point fβThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcβ1、Aycβ1And Azcβ1Observation point C at determined frequency point fβThe lower vibration stress in X, Y and Z directions is Xcβ1、ycβ1And zcβ1，fβ∈fj；
S2, applying X-direction radial force F to a load action point by adopting finite element simulation to obtain vibration stress frequency response curves of any observation point C on the pipeline corresponding to the simulation model of the variable-frequency compressor with the pipeline in the X direction, the Y direction and the Z direction, and obtaining the vibration stress frequency response curves of the observation point C at each working frequency point FjMagnitude of lower stress response and any one determined operating frequency point fβThe vibration stress of the observation point C at each working frequency point fjThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcj2、Aycj2And Azcj2Observation point C at determined frequency point fβThe vibration stress frequency response amplitudes in the lower X direction, the lower Y direction and the lower Z direction are respectively Axcβ2、Aycβ2And Azcβ2Observation point C at determined frequency point fβThe lower vibration stress in X, Y and Z directions is Xcβ2、ycβ2And zcβ2Wherein j ranges from 1 to P, P is the number of working frequency points of the variable frequency compressor, and fβ∈fj；
S3, applying a Z-direction rotation moment M and an X-direction radial force F on a load action point of the simulation model by using finite element simulation to obtain vibration stress frequency response curves of an observation point C in the X direction, the Y direction and the Z directionThe vibration stress frequency response curve obtains observation points C at each working frequency point fjThe frequency response amplitudes of the vibration stress in the lower X direction, the lower Y direction and the lower Z direction are respectively marked as Axcj3、Aycj3And Azcj3；
S4, calculating the vibration stress of the observation point C in the simulation model with the pipeline of the variable frequency compressor at the corresponding position on the pipeline, wherein the rotation moment M of any observation point C on the pipeline in the Z directionjAnd X-direction radial force FjAnd each operating frequency point fjThe lower X-, Y-and Z-direction vibration stresses are denoted as deltaxcj、δycjAnd deltazcjThen, then
Wherein,
wherein,
wherein,
the steps S1, S2 and S3 are interchangeable.
6. The method for simulating and calculating the excitation load of the inverter compressor of the refrigeration equipment according to claim 4, wherein the step three and the step four further comprise the following verification step: and obtaining vibration displacement data of the observation point I and the observation point II under all working frequency points by adopting finite element simulation calculation according to the excitation load, comparing the vibration displacement data under the same working frequency points in the same direction with the vibration displacement test data of the test point I and the test point II in the step I, entering the step 4 if the difference value of the vibration displacement data and the test point II is within a preset error, and otherwise, exiting, checking and adjusting a simulation model of the variable frequency compressor and then carrying out simulation calculation again.
7. The method for simulating and calculating the excitation load of the inverter compressor of the refrigeration equipment as recited in claim 6, wherein a connecting line of the first test point and the second test point is taken as an X direction, and a direction perpendicular to the connecting line of the first test point and the second test point in a horizontal plane is taken as a Y direction, and the verifying step comprises:
t1, line x'ijAnd y'ijFor a test point i corresponding to an observation point i at any operating frequency point fjAnd vibration displacement corresponding to the X direction and the Y direction, wherein the value range of i is 1-n, n is a positive integer representing the number of the test points, and the vibration displacement test data comprises X'ijAnd y'ij(ii) a Recording each operating frequency point fjThe lower excitation load being the rotation moment MjAnd a radial force Fj(ii) a Taking a connecting line of the observation point I and the observation point II as an X direction, taking a direction perpendicular to the connecting line of the observation point I and the observation point II in a horizontal plane as a Y direction, taking a vertical direction as a Z direction, adopting finite element simulation to apply X radial force F and Z rotation moment M on a load action point, obtaining displacement frequency response amplitude data III under all working frequency points of the observation point, and setting AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjThe displacement frequency response amplitude of the lower X direction and the Y direction, k is a positive integer, k is equal to 1 to represent the load condition that the rotating moment M in the vertical direction is applied at the load acting point, k is equal to 2 to represent the load condition that the radial force F in the direction connecting the first observation point and the second observation point is applied at the load acting point, and k is equal to 3 to represent the load condition that the rotating moment in the same direction is synchronously applied at the load acting pointMoment of dynamic force M and radial force F, displacement frequency response amplitude data III includes Ax1j3、Ay1j3、Ax2j3、Ay2j3；
T2, recording the vertical rotation moment M exerted by the observation point I at the load action pointjEach frequency point fjThe displacements in the X-direction and Y-direction are X'1j1And y'1j1Recording the vertical rotation moment M applied to the load action point by the observation point IIjEach frequency point fjThe displacements in the X-direction and Y-direction are X'2j1And y'2j1Let xiαkAnd yiαkRespectively as observation point i under k-th load condition and determined working frequency point fαSimulating displacement in the lower X direction and the lower Y direction, i ranges from 1 to n, n is a positive integer representing the number of observation points, j ranges from 1 to p, p is the number of working frequency points of the variable frequency compressor, fα∈fj，AxijkAnd AyijkRespectively as an observation point i under the k load condition and an arbitrary working frequency point fjThe displacement frequency response amplitude of the lower X direction and the lower Y direction
T3, noting that the observation point-applied X-direction radial force F at the load application pointjAnd each frequency point fjThe displacements in the X-direction and Y-direction are X'1j2And y'1j2Recording the radial force F applied to the load acting point in the X direction by the observation point IIjAnd each frequency point fjThe displacements in the X-direction and Y-direction are X'2j1And y'2j1Then, then
T4, recording test point I corresponding to observation point I at each frequency point fjThe calculated vibration displacements in the lower X and Y directions are respectively Dx1jAnd Dy1jThen, then
Wherein,
wherein,
recording the frequency points f of the test point II corresponding to the observation point IIjThe calculated vibration displacements in the lower X and Y directions are respectively Dx2jAnd Dy2j，
Wherein,
wherein,
t5, calculating the calculated vibration displacement (D) of the first test point in the X direction and the Y directionx1j，Dy1j) And vibration displacement test data (x'1jAnd y'1j) Calculating the calculated vibration displacement (D) of the test point two in the X direction and the Y directionx2j，Dy2j) And vibration displacement test data (x'2jAnd y'2j) Judging whether the data error I and the data error II are smaller than or equal to an error threshold value, if so, entering a step IV, otherwise, exiting, checking and adjusting a simulation model of the variable frequency compressor and then carrying out simulation calculation again;
the sequences of the step T1, the step T2 and the step T3 can be interchanged.
8. The simulation calculation method of the excitation load of the inverter compressor of the refrigeration equipment according to claim 1, it is characterized in that in the first step, the vibration testing system comprises a variable frequency compressor, a pipeline, a controller, a frequency converter for driving the compressor to operate and an acquisition unit for acquiring vibration displacement test data of the measuring point, the variable frequency compressor comprises a variable frequency compressor rigid body (2) and a liquid storage tank (1), an exhaust port (4) is arranged at the top of the variable frequency compressor rigid body (2), an air suction port (3) is arranged at the top of the liquid storage tank (1), the controller is used for controlling the temperature and the pressure of the system to enable the temperature and the pressure of the first test point and the second test point to be respectively consistent with the temperature and the pressure of the corresponding position of the refrigeration equipment under the complete machine operation load equivalent working condition.
9. The method for simulating and calculating the excitation load of the inverter compressor of the refrigeration equipment according to claim 1, wherein the acquisition unit comprises a vibration signal acquisition instrument and an acceleration sensor; and/or the pipeline is a hose.
10. The method for calculating excitation load simulation of a variable frequency compressor of refrigeration equipment according to claim 1, wherein the load action point is located on the surface of the rigid shell of the variable frequency compressor corresponding to the simulation model.
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| CN110245425B (en) * | 2019-06-17 | 2020-10-23 | 珠海格力电器股份有限公司 | Air conditioner compressor excitation identification method and computer device |
| CN111797518A (en) * | 2020-06-23 | 2020-10-20 | 电子科技大学 | Load solving method under low-frequency torque compensation of compressor |
| CN111797518B (en) * | 2020-06-23 | 2023-04-18 | 电子科技大学 | Load solving method under low-frequency torque compensation of compressor |
| CN112665774A (en) * | 2021-01-11 | 2021-04-16 | 哈尔滨工业大学 | Hydraulic pipeline joint lateral force testing method based on DIC |
| CN113128101A (en) * | 2021-05-12 | 2021-07-16 | 四川长虹空调有限公司 | Method for evaluating vibration and low-frequency noise of variable-frequency air conditioner pipeline |
| CN113218049A (en) * | 2021-05-12 | 2021-08-06 | 四川长虹空调有限公司 | Method for quickly matching compressor and pipeline of variable frequency air conditioner |
| CN113239489A (en) * | 2021-05-12 | 2021-08-10 | 四川长虹空调有限公司 | Simulation evaluation method for vibration of variable-frequency single-rotor compressor |
| CN113218049B (en) * | 2021-05-12 | 2022-04-01 | 四川长虹空调有限公司 | Method for quickly matching compressor and pipeline of variable frequency air conditioner |
| CN113128101B (en) * | 2021-05-12 | 2022-07-12 | 四川长虹空调有限公司 | Method for evaluating vibration and low-frequency noise of variable-frequency air conditioner pipeline |
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