CN112459984B - Performance test calculation method for isothermal compressor - Google Patents
Performance test calculation method for isothermal compressor Download PDFInfo
- Publication number
- CN112459984B CN112459984B CN202011271517.6A CN202011271517A CN112459984B CN 112459984 B CN112459984 B CN 112459984B CN 202011271517 A CN202011271517 A CN 202011271517A CN 112459984 B CN112459984 B CN 112459984B
- Authority
- CN
- China
- Prior art keywords
- stage
- inlet
- parameters
- temperature
- water
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
- F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
- F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/064—Cooling by a cooling jacket in the pump casing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B51/00—Testing machines, pumps, or pumping installations
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention provides a performance test calculation method for an isothermal compressor, which comprises the following steps: step one, collecting parameters of an isothermal compressor: step two, calculating process multivariable preliminary determination: step 201, acquiring pressure and temperature parameters of inlet and outlet of each stage in a design state; step 202, calculating multiple variables at each level of the design state: step 203, preliminarily determining the multivariable of each stage of the test state: making the test state multi-variable at each level equal to the design state multi-variable at each level; step three, preliminary calculation of test data: step four, data comparison and correlation coefficient selection iterative computation: comparing the complete machine power N obtained by calculation in the step three with the actually measured power N, calculating a relevant power adjustment coefficient, and recalculating multiple variables at each stage: and (3) redetermining the multiple variables of each stage of the test state: making the multi-variables of each stage in the test state equal to the multi-variables of each stage obtained by recalculation; repeatedly iterating the calculation of the third step and the calculation of the fourth step; and step five, calculating the related characteristic parameters.
Description
Technical Field
The invention belongs to the field of compressors, relates to an isothermal compressor, and particularly relates to a performance test calculation method for the isothermal compressor.
Background
Isothermal compressors with built-in coolers are widely used in the industrial fields of air separation and the like. The built-in cooler enables the high-temperature gas after each stage of compression to be cooled immediately in time and then enter the next stage for compression again. The overall energy consumption of the unit is lower than that of other types of compressor units with the same scale, and the overall occupied area is also smaller than that of other types of compressor units with the same scale. However, the application of the built-in cooler, especially the use of a special gas distributor for gas distribution in order to ensure that the high-temperature gas can be sufficiently cooled, increases the nonuniformity of the high-temperature gas flow at the outlet of the previous stage and the low-temperature gas flow at the inlet of the subsequent stage of the built-in cooler, especially the nonuniformity of the temperature field, and brings certain difficulties to the performance test and evaluation of the unit. Especially, quantitative and accurate evaluation of performance test and analysis of all levels is difficult to achieve.
At present, in the test analysis of the isothermal centrifugal compressor, test points are arranged at an inlet and an outlet of each stage of the compressor according to the JB/T3165 standard to obtain pressure and temperature parameters of the inlet and the outlet of each stage of the compressor, a flow meter arranged on a test pipeline obtains flow measurement parameters of the flow meter, and the measurement parameters are calculated and analyzed by combining related environmental medium parameters and unit operation characteristic parameters through the principle of a thermal balance method to obtain the overall thermal performance of the compressor and the thermal performance of each stage.
Due to the structural limitation of the isothermal compressor, the temperature testing precision of the inlet and the outlet of each stage is difficult to guarantee. The inlet and the outlet of the compressor complete machine are connected with the test pipeline, pressure and temperature measuring points can be arranged according to the test standard requirements strictly, and related pressure and temperature parameters can be obtained accurately. The compressor flow measurement is arranged on the relevant test pipeline, and the flow parameters can be accurately obtained. The difficulty in measuring the pressure and temperature parameters between compressor stages (namely the relevant parameters of the inlet and the outlet of the built-in cooler) is high. In contrast, the pressure field is relatively stable, and accurate pressure measurement parameters can be obtained by increasing the number of measuring points for averaging or seeking a stable flow area for arranging the measuring points. For the inter-stage temperature measurement, the applicant also tries to obtain temperature parameters by increasing the number of measuring points for averaging and seeking for arranging measuring points in a stable flow region in the previous research process, and carries out analysis and calculation according to the calculation method recommended by JB/T3165. The obtained result often has great deviation from the design concept and the theoretical principle, and sometimes even has the conclusion of violating the thermodynamic principle. The test of the isothermal compressor is caused, and the applicant can only give qualitative analysis conclusion in the early research process, and hardly gives quantitative conclusion.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide a performance test calculation method for an isothermal compressor, which aims at the test difficulty brought by the characteristics of the isothermal compressor structure and solves the technical problem that the accurate quantitative test result is difficult to give out by aiming at the characteristics of the isothermal compressor structure in the prior art.
In order to solve the technical problems, the invention adopts the following technical scheme:
a performance test calculation method for an isothermal compressor, wherein the isothermal compressor is provided with a built-in cooler, comprises the following steps:
step one, collecting parameters of an isothermal compressor:
the parameters comprise:
environmental parameters: including atmospheric pressure and atmospheric temperature;
flow parameters: including mass flow rate;
and (3) inlet parameters of each stage: including stage inlet pressures and stage inlet temperatures;
exit parameters at each level: including stage outlet pressures;
parameters of each stage of cooler: the method comprises the steps of feeding water mass flow of each stage of cooler, feeding water temperature of each stage of cooler and discharging water temperature of each stage of cooler;
compressor related parameters: including compressor speed and compressor power;
preparing parameters at the early stage: including adiabatic index, gas constant and cooling water specific heat;
step two, preliminary determination of multiple variables in the calculation process:
step 201, checking design parameters corresponding to the test working condition points of the isothermal compressor, and acquiring the inlet and outlet pressure and temperature parameters of each stage in a design state, namely:
including at least a design secondary inlet pressure P2j', design second level inlet temperature T2j', design second level outlet pressure P2C' and design State Secondary Outlet temperature T2C’;
Step 202, calculating multiple variables at each level of the design state:
Step 203, preliminarily determining the multivariable of each stage of the test state:
making the test state multi-variable at each level equal to the design state multi-variable at each level;
step three, preliminary calculation of test data:
in the formula:
k is the adiabatic index;
r is a gas constant;
Qmis the mass flow rate;
T2jcalculating for the second stage inlet temperature:
P2jis the second inlet pressure;
P2Ca secondary outlet pressure;
σ2is a test state secondary multivariable;
step four, data comparison and correlation coefficient selection iterative computation:
the total machine power N obtained by the calculation of the step threeMeterComparing with the measured power N, calculating a relevant power adjustment coefficient, and recalculating multiple variables at each stage:
in the formula:
T2j meter 2Is a two-stage inlet temperatureRecalculating the result;
T2C meter 2Recalculating the results for the secondary outlet temperature;
and (3) redetermining the multiple variables of each stage of the test state:
making the multi-variables of each stage in the test state equal to the multi-variables of each stage obtained by recalculation;
substituting the calculated inlet and outlet temperature parameter values of each stage into the corresponding calculation formula of the third step for recalculation, and repeatedly iterating the calculation of the third step and the calculation of the fourth step until the complete machine power N obtained by calculationMeterIs equal to the measured power N;
calculating related characteristic parameters;
the related characteristic parameters comprise inlet volume flow of each stage, pressure ratio of each stage, efficiency of each stage and power of each stage.
The invention also has the following technical characteristics:
the isothermal compressor is a four-stage isothermal compressor, three built-in coolers are arranged in the compressor, the four-stage isothermal compressor is divided into a first-stage cooler, a second-stage cooler, a third-stage cooler and a fourth-stage cooler, and the three built-in coolers are divided into a first-stage cooler, a second-stage cooler and a third-stage cooler; the method is characterized by comprising the following steps:
step one, collecting parameters of an isothermal compressor:
the parameters comprise:
environmental parameters: including atmospheric pressure Pa and atmospheric temperature Ta;
flow parameters: including mass flow rate Qm;
Primary inlet parameters: including a primary inlet pressure P1jAnd primary inlet temperature T1j;
Primary outlet parameters: including a primary outlet pressure P1C;
Primary cooler parameters: comprises a primary cooler water inlet mass flow q1m waterFirst-stage cooler inlet water temperature T1j WaterAnd the outlet water temperature T of the primary cooler1C water;
Secondary import parameters: comprises thatSecondary inlet pressure P2j;
Secondary outlet parameters: including a secondary outlet pressure P2C;
Secondary cooler parameters: comprises a secondary cooler water inlet mass flow q2m waterWater inlet temperature T of secondary cooler2j waterAnd the outlet water temperature T of the secondary cooler2C water;
Three-level import parameters: including three inlet pressures P3j;
And (3) three-level outlet parameters: three stage outlet pressure P3C;
Parameters of the tertiary cooler: water inlet mass flow q of three-stage cooler3m waterWater inlet temperature T of three coolers3j WaterAnd the outlet water temperature T of the three-stage cooler3C water;
Four-stage inlet parameters: including four stages of inlet pressure P4j;
Four-stage outlet parameters: four stage outlet pressure P4CAnd a fourth stage outlet temperature T4C;
Compressor related parameters: the compressor speed N and the compressor power N;
preparing parameters at the early stage: adiabatic index k, gas constant R and specific heat of cooling water Cp water;
Step two, calculating process multivariable preliminary determination:
step 201, checking design parameters corresponding to the test working condition points of the isothermal compressor, and acquiring the inlet and outlet pressure and temperature parameters of each stage in a design state, namely:
design primary inlet pressure P1j', design first-level inlet temperature T1j', design first stage outlet pressure P1C' and design State first order Outlet temperature T1C’;
Design second order inlet pressure P2j', design second level inlet temperature T2j', design second level outlet pressure P2C' and design State Secondary Outlet temperature T2C’;
Design state three-stage inlet pressure P3j' design state three-level inlet temperature T3j', design three-stage outlet pressure P3C' and design three stage exit temperature T3C’;
Design state four stage inlet pressure P4j', design four-stage inlet temperature T4j', design four stage outlet pressure P4C' and design State four stage Outlet temperature T4C’;
Step 202, calculating multiple variables at each level of the design state:
Step 203, preliminarily determining the multivariable of each stage of the test state:
order:
first-order multivariable sigma of test state1=σ1';
Test state two-stage multivariable sigma2=σ'2;
Three-stage multivariable sigma of test state3=σ'3;
Test state four-stage multivariable sigma4=σ'4;
Step three, preliminary calculation of test data:
and (3) calculating the power of the whole machine: n is a radical ofMeter=N1 meter+N2 meter+N3 meter+N4 meter;
In the formula:
Q1the heat of a first-stage built-in cooler;
Q2the heat of a secondary built-in cooler;
Q3the heat of a three-stage built-in cooler is adopted;
step four, data comparison and correlation coefficient selection iterative computation:
the total machine power N obtained by the calculation of the step threeMeterComparing the four-level outlet temperature T with the actually measured power N, and calculating the four-level outlet temperature T obtained in the step three4C meterAnd actually measuring the four-stage outlet temperature T4CComparing, calculating the related power adjustment coefficient, and recalculating the multi-variables at each stage:
in the formula:
T1C meter 2Recalculating the results for the primary outlet temperature;
T2j meter 2Recalculating the results for the secondary inlet temperature;
T2C meter 2Recalculating the results for the secondary outlet temperature;
T3j meter 2Recalculating results for the third level inlet temperature;
T3C meter 2Recalculating results for the tertiary outlet temperatures;
T4j meter 2Recalculating the results for the four stage inlet temperature;
T4C meter 2Recalculating the results for the four stage outlet temperature;
λ1the value range of the coefficient is 0.95-1.05;
λ2the value range of the coefficient is 0.95-1.05;
λ3the value range of the coefficient is 0.95-1.05;
λ4the value range of the coefficient is 0.95-1.05;
and (3) redetermining the multiple variables of each stage of the test state:
order:
first-order multivariable sigma of test state1=σ1 meter;
Test state two-stage multivariable sigma2=σ2 meter;
Three-stage multivariable sigma of test state3=σ3 meter;
Test state four-stage multivariable sigma4=σ4 meter;
And calculating the inlet and outlet temperature parameter values T of each level1C meter 2、T2j meter 2、T2C meter 2、T3j meter 2、T3C meter 2And T4j meter 2Substituting into the corresponding calculation formula in the third step for recalculation, and repeating the iteration of the calculation in the third step and the calculation in the fourth step until the complete machine power N obtained by calculationMeterEqual to the measured power N and calculating the obtained four-stage outlet temperature T4C meterAnd actually measuring the four-stage outlet temperature T4C;
Step five, calculating related characteristic parameters:
in the formula:
ρ1is the first level inlet density;
ρ2the second level inlet density;
ρ3the density is three-level inlet density;
ρ4is a four-stage inlet density.
Compared with the prior art, the invention has the following technical effects:
the test calculation method disclosed by the invention has the advantages that (I) the obtained superposition calculation result is compared and analyzed with the tested model level complete machine result, the parameters are basically consistent, the data deviation is within the range allowed by the calculation error, the result accuracy is high, and the quantitative test of the isothermal compressor is realized.
(II) the test calculation method can be applied to the test and field test analysis and evaluation of the isothermal compressor with the built-in cooler and the analysis and treatment of the auxiliary relevant operation problems.
(III) the test calculation method of the invention obtains the complete machine thermodynamic performance of the isothermal compressor and the thermodynamic performance parameters of all stages by combining the thermodynamic correlation principle and the compressor characteristics through experimental tests, substituting the calculation parameters for the relevant temperature parameters with high measurement difficulty through theoretical reasoning and iterative calculation.
The present invention will be explained in further detail with reference to examples.
Detailed Description
It is to be understood that all devices and components of the present invention, unless otherwise specified, are intended to be within the scope of the present invention, as defined in the appended claims.
It should be noted that the types, units and acquisition modes of the parameters collected by the isothermal compressor in the present invention are as follows:
environmental parameters:
pa- -atmospheric pressure in kPa (measured value);
ta- -atmospheric temperature in K (measured);
flow parameters:
Qm-mass flow in kg/s (measured value);
primary inlet parameters:
P1j-primary inlet pressure in Pa (taking inlet test pressure transmitter average);
T1j-primary inlet temperature in K (taking inlet test temperature transmitter average);
primary outlet parameters:
P1C-primary outlet pressure in Pa (take-off test pressure transmitter mean);
primary cooler parameters:
q1m water-primary cooler inlet water mass flow in kg/s (measured value);
T1j Water-primary cooler inlet water temperature in K (measured value);
T1C water-primary cooler exit water temperature in K (measured value);
secondary import parameters:
P2j-secondary inlet pressure in Pa (taking inlet test pressure transmitter mean);
secondary outlet parameters:
P2C-secondary outlet pressure in Pa (take-off test pressure transmitter mean);
secondary cooler parameters:
q2m water-mass flow of the secondary cooler inlet water in kg/s (measured);
T2j water-secondary cooler inlet water temperature in K (measured value);
T2C water-secondary cooler effluent temperature in K (measured value);
three-level import parameters:
P3j-tertiary inlet pressure in Pa (taking inlet test pressure transmitter average);
and (3) three-level outlet parameters:
P3C-a tertiary outlet pressure in Pa (take-off test pressure transmitter mean);
parameters of the tertiary cooler:
q3m water-mass flow of water entering the tertiary cooler in kg/s (measured);
T3j Water-the tri-cooler inlet water temperature in K (measured value);
T3C water-the outlet water temperature of the tertiary cooler in K (measured value);
four-stage inlet parameters: in the relevant characteristic parameter
P4j-four levels of inlet pressure in Pa (taking inlet test pressure transducer mean);
four-stage outlet parameters:
P4C-a quaternary outlet pressure in Pa (take-off test pressure transmitter mean);
T4C-four levels of outlet temperature in K (take-off test temperature transmitter mean);
compressor related parameters:
n-compressor speed in r/min (measured);
n- -compressor power in kW (measured);
preparing parameters at the early stage:
k — adiabatic index, unit 1, (air k 1.4);
r-gas constant, in J/(kg · K) (air R288.3);
Cpwater (W)Specific heat of cooling water, in J/(kg. DEG C.) (selected).
In the isothermal compressor-related characteristic parameters according to the present invention, the units of the parameters are as follows:
primary inlet volume flow Q1vVolume flow Q of secondary inlet2vThree-stage inlet volume flow Q3vAnd four stages of inlet volume flow Q4vAll units of (are m)3/min;
Primary power N1Second order power N2Three-stage power N3And four levels of power N4The units of (A) are all kW.
The present invention is not limited to the following embodiments, and all equivalent changes based on the technical solutions of the present invention fall within the protection scope of the present invention.
Example 1:
according to the technical scheme, the performance test calculation method of the isothermal compressor is provided in the embodiment, the compressor is a four-stage isothermal compressor, three built-in coolers are arranged in the compressor, the four-stage isothermal compressor is divided into a first-stage cooler, a second-stage cooler, a third-stage cooler and a fourth-stage cooler, and the three built-in coolers are divided into a first-stage cooler, a second-stage cooler and a third-stage cooler; the method comprises the following steps:
step one, collecting parameters of an isothermal compressor:
the parameters comprise:
environmental parameters: including atmospheric pressure Pa and atmospheric temperature Ta;
flow parameters: including mass flow rate Qm;
Primary inlet parameters: including a primary inlet pressure P1jAnd primary inlet temperature T1j;
Primary outlet parameters: including a primary outlet pressure P1C;
Primary cooler parameters: comprises a primary cooler water inlet mass flow q1m waterFirst-stage cooler inlet water temperature T1j WaterAnd the outlet water temperature T of the primary cooler1C water;
Secondary import parameters: including a secondary inlet pressure P2j;
Secondary outlet parameters: including a secondary outlet pressure P2C;
Secondary cooler parameters: comprises a secondary cooler water inlet mass flow q2m waterAnd the water inlet temperature T of the secondary cooler2j waterAnd the outlet water temperature T of the secondary cooler2C water;
Three-level import parameters: including three inlet pressures P3j;
And (3) three-level outlet parameters: three stage outlet pressure P3C;
Parameters of the tertiary cooler: water inlet mass flow q of three-stage cooler3m waterWater inlet temperature T of three coolers3j WaterAnd the outlet water temperature T of the three-stage cooler3C water;
Four-stage inlet parameters: including four stages of inlet pressure P4j;
Four-stage outlet parameters: four-stage outlet pressure P4CAnd a fourth stage outlet temperature T4C;
Compressor related parameters: the compressor speed N and the compressor power N;
preparing parameters at the early stage: adiabatic index k, gas constant R and specific heat of cooling water Cp water;
Step two, calculating process multivariable preliminary determination:
step 201, checking design parameters corresponding to the test working condition points of the isothermal compressor, and acquiring the inlet and outlet pressure and temperature parameters of each stage in a design state, namely:
design primary inlet pressure P1j', design first-level inlet temperature T1j', design first stage outlet pressure P1C' and design State first order Outlet temperature T1C’;
Design second stage inlet pressure P2j', design second level inlet temperature T2j', design second level outlet pressure P2C' and design State Secondary Outlet temperature T2C’;
Design state three-stage inlet pressure P3j' design state three-level inlet temperature T3j', design three-stage outlet pressure P3C' and design three stage exit temperature T3C’;
Design state four stage inlet pressure P4j', design four-stage inlet temperature T4j', design four stage outlet pressure P4C' and design State four stage Outlet temperature T4C’;
Step 202, calculating multiple variables at each level of the design state:
Step 203, preliminarily determining the multivariable of each stage of the test state:
order:
first-order multivariable sigma of test state1=σ1';
Test state two-stage multivariable sigma2=σ'2;
Three-stage multivariable sigma of test state3=σ'3;
Test state four-stage multivariable sigma4=σ'4;
Step three, preliminary calculation of test data:
and (3) calculating the power of the whole machine: n is a radical ofMeter=N1 meter+N2 meter+N3 meter+N4 meter;
In the formula:
Q1the heat of a first-stage built-in cooler;
Q2the heat of a secondary built-in cooler;
Q3the heat of a three-stage built-in cooler is adopted;
step four, data comparison and correlation coefficient selection iterative computation:
the total machine power N obtained by the calculation of the step threeMeterComparing the four-level outlet temperature T with the actually measured power N, and calculating the four-level outlet temperature T obtained in the step three4C meterAnd actually measuring the four-stage outlet temperature T4CComparing, calculating the related power adjustment coefficient, and recalculating the multi-variables at each stage:
in the formula:
T1C meter 2Recalculating the results for the primary outlet temperature;
T2j meter 2Recalculating the results for the secondary inlet temperature;
T2C meter 2Recalculating the results for the secondary outlet temperature;
T3j meter 2Recalculating results for the third level inlet temperature;
T3C meter 2Recalculating results for the tertiary outlet temperatures;
T4j meter 2Recalculating the results for the four stage inlet temperature;
T4C meter 2Recalculating the results for the four stage outlet temperature;
λ1the value range of the coefficient is 0.95-1.05;
λ2the value range of the coefficient is 0.95-1.05;
λ3the value range of the coefficient is 0.95-1.05;
λ4the value range of the coefficient is 0.95-1.05;
and (3) redetermining the multiple variables of each stage of the test state:
order:
first-order multivariable sigma of test state1=σ1 meter;
Test state two-stage multivariable sigma2=σ2 meter;
Three-stage multivariable sigma of test state3=σ3 meter;
Test state four-stage multivariable sigma4=σ4 meter;
And calculating the inlet and outlet temperature parameter values T of each level1C meter 2、T2j meter 2、T2C meter 2、T3j meter 2、T3C meter 2And T4j meter 2Substituting into the corresponding calculation formula in the third step for recalculation, and repeating the iteration of the calculation in the third step and the calculation in the fourth step until the complete machine power N obtained by calculationMeterIs equal to the actually measured power N and calculates the obtained four-stage outlet temperature T4C meterAnd actually measuring the four-stage outlet temperature T4C;
Step five, calculating related characteristic parameters:
in the formula:
ρ1is the first level inlet density;
ρ2the second level inlet density;
ρ3the density is three-level inlet density;
ρ4is a four-stage inlet density.
Application example:
the isothermal compressor in the application example is an isothermal centrifugal compressor unit which operates on site, the compressor is a four-stage isothermal compressor, three built-in coolers are arranged in the compressor, the four-stage isothermal compressor is divided into a first-stage cooler, a second-stage cooler, a third-stage cooler and a fourth-stage cooler, and the three built-in coolers are divided into a first-stage cooler, a second-stage cooler and a third-stage cooler. The design parameters are shown in table 1.
TABLE 1 design parameters for isothermal compressors
The application example adopts the performance test calculation method of the isothermal compressor in the embodiment 1 to calculate.
In this application example, the parameters of the isothermal compressor collected according to the method of step one of example 1 are shown in table 2.
TABLE 2 parameters collected
In this application example, the relevant characteristic parameters obtained by the method of step five in example 1 are shown in table 3.
TABLE 3 relevant characteristic parameters
The performance test calculation method of the isothermal compressor, provided by the invention, has the advantages that the superposed calculation result is compared and analyzed with the tested model level complete machine result, the parameters are basically consistent, the data deviation is very small, and the very small deviation is caused by calculation errors.
Claims (2)
1. A performance test calculation method for an isothermal compressor, wherein the isothermal compressor is provided with a built-in cooler, is characterized by comprising the following steps:
step one, collecting parameters of an isothermal compressor:
the parameters comprise:
environmental parameters: including atmospheric pressure and atmospheric temperature;
flow parameters: including mass flow rate;
and (3) inlet parameters of each stage: including stage inlet pressures and stage inlet temperatures;
exit parameters at each level: including stage outlet pressures;
parameters of each stage of cooler: the method comprises the steps of feeding water mass flow of each stage of cooler, feeding water temperature of each stage of cooler and discharging water temperature of each stage of cooler;
compressor related parameters: including compressor speed and compressor power;
preparing parameters at the early stage: including adiabatic index, gas constant and cooling water specific heat;
step two, calculating process multivariable preliminary determination:
step 201, checking design parameters corresponding to the test working condition points of the isothermal compressor, and acquiring the inlet and outlet pressure and temperature parameters of each stage in a design state, namely:
including at least a design secondary inlet pressure P2j', design second level inlet temperature T2j', design second level outlet pressure P2C' and design State Secondary Outlet temperature T2C’;
Step 202, calculating multiple variables at each level of the design state:
Step 203, preliminarily determining the multivariable of each stage of the test state:
making the test state multi-variable at each level equal to the design state multi-variable at each level;
step three, preliminary calculation of test data:
in the formula:
k is the adiabatic index;
r is a gas constant;
Qmis the mass flow rate;
T2jcalculating for the second stage inlet temperature:
P2jis the second inlet pressure;
P2Ca secondary outlet pressure;
σ2is a test state secondary multivariable;
step four, data comparison and correlation coefficient selection iterative computation:
the total machine power N obtained by the calculation of the step threeMeterComparing with the measured power N, calculating a relevant power adjustment coefficient, and recalculating multiple variables at each stage:
in the formula:
T2j meter 2Recalculating the results for the secondary inlet temperature;
T2C meter 2Recalculating the results for the secondary outlet temperature;
and (3) redetermining the multiple variables of each stage of the test state:
making the multi-variables of each stage in the test state equal to the multi-variables of each stage obtained by recalculation;
substituting the calculated inlet and outlet temperature parameter values of each stage into the corresponding calculation formula of the third step for recalculation, and repeatedly iterating the calculation of the third step and the calculation of the fourth step until the complete machine power N obtained by calculationMeterIs equal to the measured power N;
calculating related characteristic parameters;
the related characteristic parameters comprise inlet volume flow of each stage, pressure ratio of each stage, efficiency of each stage and power of each stage.
2. The isothermal compressor performance test calculation method according to claim 1, wherein the isothermal compressor is a four-stage isothermal compressor, three internal coolers are arranged in the compressor, the four-stage isothermal compressor is divided into a first-stage cooler, a second-stage cooler, a third-stage cooler and a fourth-stage cooler, and the three internal coolers are divided into a first-stage cooler, a second-stage cooler and a third-stage cooler; the method is characterized by comprising the following steps:
step one, collecting parameters of an isothermal compressor:
the parameters comprise:
environmental parameters: including atmospheric pressure Pa and atmospheric temperature Ta;
flow parameters: including mass flow rate Qm;
Primary inlet parameters: including a primary inlet pressure P1jAnd primary inlet temperature T1j;
Primary outlet parameters: including a primary outlet pressure P1C;
Primary cooler parameters: comprises a primary cooler water inlet mass flow q1m waterFirst-stage cooler water inlet temperature T1j WaterAnd the outlet water temperature T of the primary cooler1C water;
Secondary import parameters: including a secondary inlet pressure P2j;
Secondary outlet parameters: including a secondary outlet pressure P2C;
Secondary cooler parameters: comprises a secondary cooler water inlet mass flow q2m waterWater inlet temperature T of secondary cooler2j waterAnd the outlet water temperature T of the secondary cooler2C water;
Three-level import parameters: including three inlet pressures P3j;
And (3) three-level outlet parameters: three stage outlet pressure P3C;
Parameters of the tertiary cooler: water inlet mass flow q of three-stage cooler3m waterCooling by threeTemperature T of inlet water of device3j WaterAnd the outlet water temperature T of the three-stage cooler3C water;
Four-stage inlet parameters: involving four levels of inlet pressure P4j;
Four-stage outlet parameters: four-stage outlet pressure P4CAnd a fourth stage outlet temperature T4C;
Compressor related parameters: the compressor speed N and the compressor power N;
preparing parameters at the early stage: adiabatic index k, gas constant R and specific heat of cooling water Cp water;
Step two, calculating process multivariable preliminary determination:
step 201, checking design parameters corresponding to the test working condition points of the isothermal compressor, and acquiring the inlet and outlet pressure and temperature parameters of each stage in a design state, namely:
design primary inlet pressure P1j', design first-level inlet temperature T1j', design first stage outlet pressure P1C' and design State first order Outlet temperature T1C’;
Design second stage inlet pressure P2j', design second level inlet temperature T2j', design second level outlet pressure P2C' and design State Secondary Outlet temperature T2C’;
Design state three-stage inlet pressure P3j' design state three-level inlet temperature T3j', design three-stage outlet pressure P3C' and design three stage exit temperature T3C’;
Design state four stage inlet pressure P4j', design four-stage inlet temperature T4j', design four stage outlet pressure P4C' and design State four stage Outlet temperature T4C’;
Step 202, calculating multiple variables at each level of the design state:
Step 203, preliminarily determining the multivariable of each stage of the test state:
order:
first-order multivariable sigma of test state1=σ’1;
Test state two-stage multivariable sigma2=σ'2;
Three-stage multivariable sigma of test state3=σ'3;
Test state four-stage multivariable sigma4=σ'4;
Step three, preliminary calculation of test data:
and (3) calculating the power of the whole machine: n is a radical ofMeter=N1 meter+N2 meter+N3 meter+N4 meter;
In the formula:
Q1the heat of a first-stage built-in cooler;
Q2the heat of a secondary built-in cooler;
Q3the heat of a three-stage built-in cooler is adopted;
step four, data comparison and correlation coefficient selection iterative computation:
the total machine power N obtained by the calculation of the step threeMeterComparing the four-level outlet temperature T with the actually measured power N, and calculating the four-level outlet temperature T obtained in the step three4C meterAnd actually measuring the four-stage outlet temperature T4CComparing, calculating the related power adjustment coefficient, and recalculating the multi-variables at each stage:
in the formula:
T1C meter 2Recalculating the results for the primary outlet temperature;
T2j meter 2Recalculating the results for the secondary inlet temperature;
T2C meter 2Recalculating the results for the secondary outlet temperature;
T3j meter 2Recalculating results for the third level inlet temperature;
T3C meter 2Recalculating results for the tertiary outlet temperatures;
T4j meter 2Recalculating the results for the four stage inlet temperature;
T4C meter 2Recalculating the results for the four stage outlet temperature;
λ1the value range of the coefficient is 0.95-1.05;
λ2the value range of the coefficient is 0.95-1.05;
λ3the value range of the coefficient is 0.95-1.05;
λ4the value range of the coefficient is 0.95-1.05;
and (3) redetermining the multiple variables of each stage of the test state:
order:
first-order multivariable sigma of test state1=σ1 meter;
Test state two-stage multivariable sigma2=σ2 meter;
Three-stage multivariable sigma of test state3=σ3 meter;
Test state four-stage multivariable sigma4=σ4 meter;
And calculating the inlet and outlet temperature parameter values T of each level1C meter 2、T2j meter 2、T2C meter 2、T3j meter 2、T3C meter 2And T4j meter 2Substituting into the corresponding calculation formula in the third step for recalculation, and reversing the calculations in the third step and the fourth stepRepeating the iteration till the obtained overall power N is calculatedMeterIs equal to the actually measured power N and calculates the obtained four-stage outlet temperature T4C meterAnd actually measuring the four-stage outlet temperature T4C;
Step five, calculating related characteristic parameters:
in the formula:
ρ1is the first level inlet density;
ρ2the second level inlet density;
ρ3the density is three-level inlet density;
ρ4is a four-stage inlet density.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN202011271517.6A CN112459984B (en) | 2020-11-13 | 2020-11-13 | Performance test calculation method for isothermal compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN202011271517.6A CN112459984B (en) | 2020-11-13 | 2020-11-13 | Performance test calculation method for isothermal compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
CN112459984A CN112459984A (en) | 2021-03-09 |
CN112459984B true CN112459984B (en) | 2022-05-03 |
Family
ID=74836902
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN202011271517.6A Active CN112459984B (en) | 2020-11-13 | 2020-11-13 | Performance test calculation method for isothermal compressor |
Country Status (1)
Country | Link |
---|---|
CN (1) | CN112459984B (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN116087613B (en) * | 2023-04-07 | 2023-06-30 | 沃德传动(天津)股份有限公司 | Reciprocating compressor energy efficiency calculation system |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN202228310U (en) * | 2011-09-07 | 2012-05-23 | 中国科学院工程热物理研究所 | Air compressor set for recycling and storing interstage cooling heat |
TW201224289A (en) * | 2010-12-06 | 2012-06-16 | China Steel Corp | On-line monitor method of multi-stage compressor |
CN102900660A (en) * | 2012-10-26 | 2013-01-30 | 西南石油大学 | Test method for testing terminal efficiency of integral reciprocating natural gas compressor unit |
TW201321604A (en) * | 2011-09-29 | 2013-06-01 | Gen Electric | Gas density sensor package for measuring polytropic efficiency of a charge gas compressor |
CN103867446A (en) * | 2012-12-07 | 2014-06-18 | 三星泰科威株式会社 | Method for anti-surge controlling of multi-stage compressing system |
WO2016147134A1 (en) * | 2015-03-18 | 2016-09-22 | University Of The Western Cape | Multistage metal hydride hydrogen compressor |
CN109058088A (en) * | 2018-07-09 | 2018-12-21 | 北京博华信智科技股份有限公司 | A kind of reciprocating compressor discharge capacity tolerance control method based on temperature and pressure ratio |
CN111164312A (en) * | 2017-10-31 | 2020-05-15 | 克里奥斯塔股份有限公司 | Method for controlling outlet pressure of compressor |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111914362B (en) * | 2020-07-22 | 2022-09-20 | 中国航发沈阳发动机研究所 | Self-adaptive method for turbofan engine model in research and development stage |
-
2020
- 2020-11-13 CN CN202011271517.6A patent/CN112459984B/en active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TW201224289A (en) * | 2010-12-06 | 2012-06-16 | China Steel Corp | On-line monitor method of multi-stage compressor |
CN202228310U (en) * | 2011-09-07 | 2012-05-23 | 中国科学院工程热物理研究所 | Air compressor set for recycling and storing interstage cooling heat |
TW201321604A (en) * | 2011-09-29 | 2013-06-01 | Gen Electric | Gas density sensor package for measuring polytropic efficiency of a charge gas compressor |
CN102900660A (en) * | 2012-10-26 | 2013-01-30 | 西南石油大学 | Test method for testing terminal efficiency of integral reciprocating natural gas compressor unit |
CN103867446A (en) * | 2012-12-07 | 2014-06-18 | 三星泰科威株式会社 | Method for anti-surge controlling of multi-stage compressing system |
WO2016147134A1 (en) * | 2015-03-18 | 2016-09-22 | University Of The Western Cape | Multistage metal hydride hydrogen compressor |
CN111164312A (en) * | 2017-10-31 | 2020-05-15 | 克里奥斯塔股份有限公司 | Method for controlling outlet pressure of compressor |
CN109058088A (en) * | 2018-07-09 | 2018-12-21 | 北京博华信智科技股份有限公司 | A kind of reciprocating compressor discharge capacity tolerance control method based on temperature and pressure ratio |
Also Published As
Publication number | Publication date |
---|---|
CN112459984A (en) | 2021-03-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN111503025B (en) | Low-pressure-ratio axial flow compressor model level performance calculation method | |
CN112459984B (en) | Performance test calculation method for isothermal compressor | |
CN107014240B (en) | A kind of cooling tower cooling efficiency monitoring method and system | |
WO2006123090A2 (en) | Analysis method | |
CN107255652A (en) | The heat exchanger performance testing device tested under low temperature in the range of large Reynold number | |
Zilio et al. | An assessment of heat transfer through fins in a fin-and-tube gas cooler for transcritical carbon dioxide cycles | |
CN110489706B (en) | Simplified calculation method for energy efficiency index EEI of plate heat exchanger | |
CN108458888B (en) | Performance testing device for low-temperature heat exchanger with temperature range below K | |
CN105865661B (en) | Positive displacement enthalpy-increasing compressor refrigeration capacity test device and test method | |
CN104361147A (en) | Design method of counter flow cooling tower | |
CN115292946B (en) | High-pressure turbine efficiency evaluation method and device based on variable specific heat calculation | |
CN108595813B (en) | A kind of CO2 gas cooler optimum design method based on optimum quality flow velocity | |
CN111380775A (en) | Device and method for detecting static evaporation rate of gas cylinder | |
CN110702175B (en) | Online soft measurement device and method for main steam flow of steam turbine of thermal power plant | |
CN104361148A (en) | Design method of transverse flow type cooling tower | |
CN108953204A (en) | Pipeline compressor performance test method and system | |
CN113959730A (en) | Method for determining exhaust enthalpy of steam turbine | |
CN107664653A (en) | Heat exchanger condensation heat transfer experiment test platform and method of testing | |
CN115274154A (en) | Thermal and hydraulic comprehensive experiment system and method for small helium-xenon cooling reactor | |
CN109884426B (en) | Method for obtaining environmental control system cooling tower energy efficiency evolution characteristic along with operation age | |
CN207439979U (en) | Heat exchanger condensation heat transfer experiment test platform | |
CN112446003A (en) | Method for accurately evaluating steam turbine set steam leakage amount based on characteristic flow area | |
CN114996864B (en) | Method for calculating length-diameter ratio of flow and throttle pipe in refrigeration cycle loop | |
Vidović et al. | Steady state analysis and modeling of the gas metering and pressure reduction station using the electrical analogy | |
CN204944707U (en) | The system that heat interchanger heat exchange measures accuracy of measurement is improved under micro-temperature difference condition |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PB01 | Publication | ||
PB01 | Publication | ||
SE01 | Entry into force of request for substantive examination | ||
SE01 | Entry into force of request for substantive examination | ||
GR01 | Patent grant | ||
GR01 | Patent grant |