CN111797518B - 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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- CN111797518B CN111797518B CN202010578495.1A CN202010578495A CN111797518B CN 111797518 B CN111797518 B CN 111797518B CN 202010578495 A CN202010578495 A CN 202010578495A CN 111797518 B CN111797518 B CN 111797518B
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Abstract
The invention discloses a load solving method under compressor low-frequency torque compensation, which is used for calculating each operating frequency point f under a non-torque compensation state i Compressor load M of i Then at the frequency f of the loading torque compensation i Within the range of (2), each vibration maximum frequency point f is calculated j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij Fitting each frequency point f by MATLAB fitting tool i Moment compensation coefficient lambda of ij Establishing 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 compressor low-frequency torque compensation, and particularly relates to a load solving method under compressor low-frequency torque compensation.
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.
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 purpose, the invention provides a load solving method under compressor low-frequency torque compensation, which is characterized by comprising the following steps of:
(1) Calculating each operating frequency point f under the state of no moment compensation i Load M of compressor i ；
M i ＝M di -M gi
Wherein i represents the number of operating frequency points of the compressor, M di For compressor operating frequency f i Instantaneous drive torque, M gi For compressor operating frequency f i Resistance moment in time;
(2) Establishing a library function of the moment compensation coefficient;
(2.1) calculating the maximum frequency f of each vibration j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij ；
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 f j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij Equal to the compressor at each frequency point f i Lower moment compensating loadThe ratio of the load to the moment-free compensation load, i.e.:
λ ij ＝M' i /M i ＝x' i /x i (1)
wherein, M' i For each operating frequency point f in the state of moment compensation i Compressor load of (M) i For each operating frequency point f in the state of no moment compensation i Compressor load of (x' i Operating frequency points f for a compressor distribution system in the absence of moment compensation i Response of (a), x i Representing each operating frequency point f of the compressor piping system in the state of moment compensation i The response of (c);
(2.2) setting the frequency f of the load moment compensation i The range of (A) is 10 Hz-40 Hz; at f i In the value range of (c), the frequency point f is calculated according to the formula (1) i Moment compensation coefficient lambda of ij ；
(2.3) fitting each frequency point f by MATLAB fitting tool i Moment compensation coefficient lambda of ij Establishing a library function of the moment compensation coefficient;
λ ij ＝F n (f i ,f j ) (2)
wherein f is i 、f j ∈[10Hz,40Hz]，F n () The library function is represented, specifically as: when f is j Equal to a fixed frequency f 1 * When, lambda ij ＝F 1 (f i ) (ii) a When f is j Equal to a fixed frequency
When, lambda ij ＝F 2 (f i ) (ii) a By analogy, when f j Is equal to a fixed frequency->
When, lambda ij ＝F n (f i ) (ii) a Wherein +>
Vibration of piping system for compressorThe value of the maximum frequency point;
(3) Calling a library function of a moment compensation coefficient, and calculating the load M of the compressor under the low-frequency torque compensation i '；
M' i ＝M i *λ ij (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 compensation i Compressor load M of i Then at the frequency f of the loading torque compensation i Within the range of (2), each vibration maximum frequency point f is calculated j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij Fitting each frequency point f by MATLAB fitting tool i Moment compensation coefficient lambda of ij Establishing 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 many times and matched with the compressor, the problem that the traditional compressor load excitation solving method needs to test for many 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 moment compensation coefficient function 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 formula i The rotational inertia moment is calculated, namely, each operating frequency point f under the state of no moment compensation is calculated i Load M of compressor i ；
M i ＝M di -M gi
Wherein i represents the number of operating frequency points of the compressor, M di For compressor operating frequency f i Moment of time drive, M gi For compressor operating frequency f i Resistance moment in time;
s2, establishing a library function of the moment compensation coefficient;
s2.1, calculating each vibration maximum frequency point f j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij ；
Since the compressor distribution pipe system can be approximately considered as a linear system, according to the characteristics of the linear system, when the compressor distribution pipe system is at the point f of maximum vibration frequency j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij Equal to the compressor at each frequency point f i The ratio of the lower moment-compensated load to the no moment-compensated load, i.e.:
λ ij ＝M' i /M i ＝x' i /x i (1)
wherein, M' i For each operating frequency point f in the state of moment compensation i Compressor load of (M) i For each operating frequency point f in the state of no moment compensation i Compressor load of (x' i Operating frequency points f for a compressor distribution system in the absence of moment compensation i Response of (a), x i Representing each operating frequency point f of the compressor piping system in the state of moment compensation i The 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 compensation i The range of (A) is 10 Hz-40 Hz; at f i In the value range of (2), the frequency point f is calculated according to the formula (1) i Moment compensation coefficient lambda of ij ；
S2.3, compensation factor lambda due to moment ij Is at the point f of maximum frequency of vibration j Related, so that if the point of maximum frequency of vibration changes, the compensation factor λ ij The change will occur, i.e. the point f of maximum frequency of vibration j Determining that the compressor is at each operating frequency point f i Moment compensation coefficient lambda of ij It was also determined that, therefore, each frequency point f was fitted by a MATLAB fitting tool i Moment compensation coefficient lambda of ij Establishing a library function of the moment compensation coefficient;
λ ij ＝F n (f i ,f j ) (2)
wherein f is i 、f j ∈[10Hz,40Hz]，F n () The library function is represented, specifically as: when f is j Equal to a fixed frequency f 1 * When is lambda ij ＝F 1 (f i ) (ii) a When f is j Equal to a fixed frequency
When is lambda ij ＝F 2 (f i ) (ii) a By analogy, when f j Is equal to a fixed frequency->
When is lambda ij ＝F n (f i ) (ii) a Wherein +>
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 compensation i '；
M' i ＝M i *λ ij (3)
Examples of the invention
In the present embodiment, the response obtained by the vibration test is stress, and f is obtained separately j ＝f 1 * ＝25Hz、
And stress data of the pipeline under the state of moment compensation and no moment compensation are available, namely n =2.
It should be noted that the range of the optimal frequency point for 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 is j ＝f 1 * And when the frequency is 25Hz, solving to obtain torque compensation coefficient data points at 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.
λ ij ＝-7.5E-06f i 4 +7.5E-04f i 3 -2.3E-02f i 2 +2.3E-01f i +0.19(f j ＝25Hz)
When in use
Then, the moment compensation coefficient data points under each operating frequency point of the compressor are obtained by solving, and the data points are subjected to quasi-function fitting, and the fitting result is as followsAs shown in fig. 3.
λ ij ＝1.01E-05f i 4 -9.6E-04f i 3 +3.5E-02f i 2 -6.2E-01f+4.5(f j ＝30Hz)
The piping system of the compressor is [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 f j =23Hz, when the vibration maximum frequency point is at lambda ij There is no corresponding f in the function library j At this time, f can be selected to be away j λ corresponding to the vibration maximum frequency point of =23Hz ij Instead, therefore, we are at λ ij The following functions are selected from the function library:
λ ij ＝-7.5E-06f i 4 +7.5E-04f i 3 -2.3E-02f i 2 +2.3E-01f i +0.19(f j ＝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 compensation i Compressor load M of i ；
M i ＝M di -M gi
Wherein i represents the number of operating frequency points of the compressor, M di To compressThe machine operating frequency is f i Moment of time drive, M gi For compressor operating frequency f i Resistance moment in time;
(2) Establishing a library function of the moment compensation coefficient;
(2.1) establishing and calculating each vibration maximum frequency point f j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij A 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 f j At each frequency point f of compressor operation i Moment compensation coefficient lambda of ij Equal to the compressor at each frequency point f i The ratio of the lower moment-compensated load to the moment-less compensated load, i.e.:
λ ij ＝M′ i /M i ＝x′ i /x i (1)
wherein, M' i For each operating frequency point f in the state of moment compensation i Compressor load of (M) i For each operating frequency point f in the state of no moment compensation i Compressor load of x' i Operating frequency points f for a compressor distribution system in the absence of moment compensation i Response of (c), x i Representing each operating frequency point f of the compressor piping system in the state of moment compensation i The response of (c);
(2.2) setting the frequency f of the load moment compensation i The range of (A) is 10 Hz-40 Hz; at f i In the value range of (c), the frequency point f is calculated according to the formula (1) i Moment compensation coefficient lambda of ij ；
(2.2) fitting each frequency point f by MATLAB fitting tool i Moment compensation coefficient lambda of ij Establishing a library function of the moment compensation coefficient;
λ ij ＝F n (f i ,f j ) (2)
wherein, f i 、f j ∈[10Hz,40Hz]，F n () The library function is represented, specifically as: when f is j Equal to a fixed frequency f 1 * When, lambda ij ＝F 1 (f i ) (ii) a When f is j Equal to a fixed frequency
When is lambda ij ＝F 2 (f i ) (ii) a By analogy, when f j Is equal to a fixed frequency->
When is lambda ij ＝F n (f i ) (ii) a Wherein it is present>
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 ＝M i *λ ij (3)。
2. Load solving method at low frequency torque compensation of a compressor, according to claim 1, characterized in that said λ ij If 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 vibration j Corresponding lambda ij Instead.
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