CN111797518A - Load solving method under low-frequency torque compensation of compressor - Google Patents
Load solving method under low-frequency torque compensation of compressor Download PDFInfo
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- CN111797518A CN111797518A CN202010578495.1A CN202010578495A CN111797518A CN 111797518 A CN111797518 A CN 111797518A CN 202010578495 A CN202010578495 A CN 202010578495A CN 111797518 A CN111797518 A CN 111797518A
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
- G06F17/10—Complex mathematical operations
- G06F17/15—Correlation function computation including computation of convolution operations
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The invention discloses a load solving method under low-frequency torque compensation of a compressor, which is used for calculating each operating frequency point f under a no-torque compensation stateiCompressor load M ofiThen at the frequency f of the loading moment compensationiWithin the range of (a), each vibration maximum frequency point f is calculatedjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofijFitting each frequency point f by MATLAB fitting tooliMoment compensation coefficient lambda ofijEstablishing a library function of a moment compensation coefficient, and finally directly calculating the load M 'of the compressor under the low-frequency torque compensation by calling the library function of the moment compensation coefficient without repeatedly testing'i。
Description
Technical Field
The invention belongs to the technical field of low-frequency torque compensation of compressors, and particularly relates to a load solving method under low-frequency torque compensation of a compressor.
Background
In order to reduce low-frequency vibration and noise, a low-frequency torque compensation technology is an important means in the matching process of the piping of the air-conditioning compressor. The compressor is used as an excitation source, the load characteristic of the compressor can be used as the input of pipe vibration simulation, and the quality of a design scheme is evaluated in the conceptual design stage of the pipe. The low-frequency torque compensation is generally in the range of below 40Hz of the operation of the compressor, and the essence of the low-frequency torque compensation technology is to give an optimal compensation angle, so that the resisting torque of the compressor piping system at the vibration maximum operation frequency point is compensated, and the vibration of the compressor piping system is further reduced. Correspondingly, the change of the piping structure may cause the change of the maximum vibration frequency point of the piping system of the compressor, namely, the optimal compensation angle will be changed accordingly.
At present, the method for obtaining the load of the compressor after low-frequency torque compensation is mainly a test method, and the method obtains the load of the compressor by testing the vibration displacement of a suction and exhaust port of a single compressor and performing reverse thrust on a transfer function matrix. The method has great limitation, firstly, in the aspect of selecting the low-frequency torque compensation angle, the compensation angle is selected based on the vibration maximum frequency point of the single compressor, and generally has difference with the compensation angle of the vibration maximum frequency point of a piping system of the compressor; secondly, if the piping scheme is changed, the compensation angle also needs to be changed, and the test needs to be performed again, so that the test period is long.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a load solving method under low-frequency torque compensation of a compressor, which solves the load of the compressor through the vibration maximum frequency point of a compressor piping system.
In order to achieve the above object, the present invention provides a load solving method under low-frequency torque compensation of a compressor, which is characterized by comprising the following steps:
(1) calculating each operating frequency point f under the state of no moment compensationiLoad M of compressori；
Mi＝Mdi-Mgi
Wherein i represents the number of operating frequency points of the compressor, MdiFor compressor operating frequency fiInstantaneous drive torque, MgiFor compressor operating frequency fiResistance moment in time;
(2) establishing a library function of the moment compensation coefficient;
(2.1) calculating the maximum frequency f of each vibrationjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofij；
If the compressor distribution pipe system is approximately a linear system, then according to the characteristics of the linear system, when the compressor distribution pipe system is at the vibration maximum frequency point fjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofijEqual to the compressor at each frequency point fiThe ratio of the lower moment-compensated load to the moment-less compensated load, i.e.:
λij＝M'i/Mi＝x'i/xi(1)
wherein, M'iFor each operating frequency point f in the state of moment compensationiCompressor load of (M)iFor each operating frequency point f in the state of no moment compensationiCompressor load of x'iOperating frequency points f for a compressor distribution system in the absence of moment compensationiResponse of (c), xiRepresenting each operating frequency point f of the compressor piping system in the state of moment compensationiThe response of (c);
(2.2) setting the frequency f of the load moment compensationiThe range of (A) is 10 Hz-40 Hz; at fiIn the value range of (2), the frequency point f is calculated according to the formula (1)iMoment compensation coefficient lambda ofij；
(2.3) fitting each frequency point f by MATLAB fitting tooliMoment compensation coefficient lambda ofijEstablishing a library function of the moment compensation coefficient;
λij＝Fn(fi,fj) (2)
wherein f isi、fj∈[10Hz,40Hz]，Fn() The library function is represented, specifically as: when f isjEqual to a fixed frequency f1 *When is lambdaij＝F1(fi) (ii) a When f isjEqual to a fixed frequency
When is lambdaij＝F2(fi) (ii) a By analogy, when fjEqual to a fixed frequency
When is lambdaij＝Fn(fi) (ii) a Wherein the content of the first and second substances,
the value of the vibration maximum frequency point of the piping system of the compressor is taken;
(3) calling a library function of a moment compensation coefficient, and calculating the load M of the compressor under the low-frequency torque compensationi'；
M'i＝Mi*λij(3)
The invention aims to realize the following steps:
the invention relates to a load solving method under low-frequency torque compensation of a compressor, which is used for calculating each operating frequency point f under the state of no torque compensationiCompressor load M ofiThen at the frequency f of the loading moment compensationiWithin the range of (a), each vibration maximum frequency point f is calculatedjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofijFitting each frequency point f by MATLAB fitting tooliMoment compensation coefficient lambda ofijEstablishing a library function of a moment compensation coefficient, and finally directly calculating the load M 'of the compressor under the low-frequency torque compensation by calling the library function of the moment compensation coefficient without repeatedly testing'i。
Meanwhile, the load solving method under the low-frequency torque compensation of the compressor further has the following beneficial effects:
(1) under the condition that the piping design scheme is changed, the load of the compressor in a torque compensation state does not need to be tested, but the load is obtained through quick solution calculation of a torque compensation coefficient, so that the test cost is reduced;
(2) under the condition that the piping design scheme needs to be changed for multiple times and matched with the compressor, the problem that the traditional compressor load excitation solving method needs to test for multiple times is solved, the testing cost is reduced, and load input is rapidly provided for vibration simulation.
Drawings
FIG. 1 is a flow chart of a load solving method under low-frequency torque compensation of a compressor according to the present invention;
FIG. 2 is a function of the moment compensation coefficient for a maximum frequency of vibration of 25 Hz;
FIG. 3 is a function of the moment compensation coefficient for a maximum frequency of vibration of 30 Hz.
Detailed Description
The following description of the embodiments of the present invention is provided in order to better understand the present invention for those skilled in the art with reference to the accompanying drawings. It is to be expressly noted that in the following description, a detailed description of known functions and designs will be omitted when it may obscure the subject matter of the present invention.
Examples
FIG. 1 is a flow chart of a load solving method under low-frequency torque compensation of a compressor according to the invention.
In this embodiment, as shown in fig. 1, the method for solving the load under the low-frequency torque compensation of the compressor of the present invention includes the following steps:
s1, solving and calculating to obtain each operating frequency point f of the compressor under the condition of no moment compensation through a theoretical formulaiThe rotational inertia moment is calculated, namely, each operating frequency point f under the state of no moment compensation is calculatediLoad M of compressori；
Mi＝Mdi-Mgi
Wherein i represents the number of operating frequency points of the compressor, MdiFor compressor operating frequency fiInstantaneous drive torque, MgiFor compressor operating frequency fiResistance moment in time;
s2, establishing a library function of the moment compensation coefficient;
s2.1, calculating each vibration maximum frequency point fjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofij；
Because the system of the compressor piping can be approximately considered as a linear system, according to the characteristics of the linear system, when the system of the compressor piping is at the point f of the maximum vibration frequencyjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofijEqual to the compressor at each frequency point fiThe ratio of the lower moment-compensated load to the moment-less compensated load, i.e.:
λij＝M'i/Mi＝x'i/xi(1)
wherein, M'iFor each operating frequency point f in the state of moment compensationiCompressor load of (M)iFor each operating frequency point f in the state of no moment compensationiCompressor load of x'iOperating frequency points f for a compressor distribution system in the absence of moment compensationiResponse of (c), xiRepresenting each operating frequency point f of the compressor piping system in the state of moment compensationiThe response can be displacement, speed, acceleration, stress, strain and the like, and response values can be obtained through vibration testing;
s2.2 setting frequency f of loading moment compensationiThe range of (A) is 10 Hz-40 Hz; at fiIn the value range of (2), the frequency point f is calculated according to the formula (1)iMoment compensation coefficient lambda ofij；
S2.3, compensation factor lambda due to momentijIs at the point f of maximum frequency of vibrationjRelatively, so that if the point of maximum frequency of vibration changes, the compensation factor λijThe change will occur, i.e. the point f of maximum frequency of vibrationjDetermining that the compressor is at each operating frequency point fiMoment compensation coefficient lambda ofijIt was also determined that, therefore, each frequency point f was fitted by a MATLAB fitting tooliMoment compensation coefficient lambda ofijEstablishing a library function of the moment compensation coefficient;
λij＝Fn(fi,fj) (2)
wherein f isi、fj∈[10Hz,40Hz]，Fn() Representing library functions, toolsThe volume is represented as: when f isjEqual to a fixed frequency f1 *When is lambdaij＝F1(fi) (ii) a When f isjEqual to a fixed frequency
When is lambdaij＝F2(fi) (ii) a By analogy, when fjEqual to a fixed frequency
When is lambdaij＝Fn(fi) (ii) a Wherein the content of the first and second substances,
the value of the vibration maximum frequency point of the piping system of the compressor is taken; in the embodiment, n ≧ 2, that is, the established torque compensation coefficient library function should at least include the torque compensation functions at more than two vibration maximum frequency points.
S3, calling a library function of the moment compensation coefficient, and calculating the load M of the compressor under the low-frequency torque compensationi'；
M'i＝Mi*λij(3)
Examples of the invention
In the present embodiment, the response obtained by the vibration test is stress, and f is obtained separatelyj＝f1 *＝25Hz、
The stress data of the pipeline under the state of moment compensation and no moment compensation, namely n is 2.
It should be noted that the range of the optimal frequency point of the moment compensation is generally in the range of [20Hz, 35Hz ], so that the maximum vibration frequency point is selected to establish a moment compensation coefficient function library for 25Hz and 30 Hz.
When f isj＝f1 *And when the frequency is 25Hz, solving to obtain torque compensation coefficient data points under each operating frequency point of the compressor, and performing quasi-function fitting on the data points, wherein the fitting result is shown in figure 2.
λij＝-7.5E-06fi 4+7.5E-04fi 3-2.3E-02fi 2+2.3E-01fi+0.19(fj＝25Hz)
When in use
And then, solving to obtain moment compensation coefficient data points under each operating frequency point of the compressor, and performing quasi-function fitting on the data points, wherein the fitting result is shown in fig. 3.
λij＝1.01E-05fi 4-9.6E-04fi 3+3.5E-02fi 2-6.2E-01f+4.5(fj＝30Hz)
Compressor piping system at [10Hz, 40Hz]During range operation, the load in the vibration simulation is a constant value torque, the frequency response curve of the actual pipeline is solved through simulation, the frequency point corresponding to the maximum response amplitude is recorded as the maximum vibration frequency point, and in the embodiment, the maximum vibration frequency point fj23Hz, when the vibration maximum frequency point is in lambdaijThere is no corresponding f in the function libraryjAt this time, f can be selected to be offjλ corresponding to 23Hz nearest vibration maximum frequency pointijInstead, therefore, we are at λijThe following functions are selected from the library of functions:
λij＝-7.5E-06fi 4+7.5E-04fi 3-2.3E-02fi 2+2.3E-01fi+0.19(fj＝25Hz)
and finally, calculating the load of the compressor under the low-frequency torque compensation.
Although illustrative embodiments of the present invention have been described above to facilitate the understanding of the present invention by those skilled in the art, it should be understood that the present invention is not limited to the scope of the embodiments, and various changes may be made apparent to those skilled in the art as long as they are within the spirit and scope of the present invention as defined and defined by the appended claims, and all matters of the invention which utilize the inventive concepts are protected.
Claims (2)
1. A load solving method under low-frequency torque compensation of a compressor is characterized by comprising the following steps:
(1) calculating each operating frequency point f under the state of no moment compensationiCompressor load M ofi；
Mi＝Mdi-Mgi
Wherein i represents the number of operating frequency points of the compressor, MdiFor compressor operating frequency fiInstantaneous drive torque, MgiFor compressor operating frequency fiResistance moment in time;
(2) establishing a library function of the moment compensation coefficient;
(2.1) establishing and calculating each vibration maximum frequency point fjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofijA linear equation of (c);
if the compressor distribution pipe system is approximately a linear system, then according to the characteristics of the linear system, when the compressor distribution pipe system is at the vibration maximum frequency point fjAt each frequency point f of compressor operationiMoment compensation coefficient lambda ofijEqual to the compressor at each frequency point fiThe ratio of the lower moment-compensated load to the moment-less compensated load, i.e.:
λij＝M′i/Mi＝x′i/xi(1)
wherein, M'iFor each operating frequency point f in the state of moment compensationiCompressor load of (M)iFor each operating frequency point f in the state of no moment compensationiCompressor load of x'iOperating frequency points f for a compressor distribution system in the absence of moment compensationiResponse of (c), xiRepresenting each operating frequency point f of the compressor piping system in the state of moment compensationiThe response of (c);
(2.2) setting the frequency f of the load moment compensationiThe range of (A) is 10 Hz-40 Hz; at fiIn the value range of (2), the frequency point f is calculated according to the formula (1)iMoment compensation coefficient lambda ofij；
(2.2) fitting each frequency point f by MATLAB fitting tooliMoment compensation coefficient lambda ofijEstablishing a library function of the moment compensation coefficient;
λij＝Fn(fi,fj) (2)
wherein f isi、fj∈[10Hz,40Hz]，Fn() The library function is represented, specifically as: when f isjEqual to a fixed frequency f1 *When is lambdaij＝F1(fi) (ii) a When f isjEqual to a fixed frequency
When is lambdaij＝F2(fi) (ii) a By analogy, when fjEqual to a fixed frequency
When is lambdaij＝Fn(fi) (ii) a Wherein the content of the first and second substances,
the value of the vibration maximum frequency point of the piping system of the compressor is taken;
(3) calling a library function of the moment compensation coefficient, and calculating the compressor load M 'under the low-frequency torque compensation'i；
M′i＝Mi*λij。 (3)
2. Load solving method at low frequency torque compensation of compressor, according to claim 1, characterized in that said λijIf the function library of (1) does not find the point of the maximum frequency of vibration, then use the f nearest to the point of the maximum frequency of vibrationjCorresponding lambdaijInstead.
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