CN117432647A - High-power high-pressure ratio centrifugal compressor performance test system and test method thereof - Google Patents
High-power high-pressure ratio centrifugal compressor performance test system and test method thereof Download PDFInfo
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Abstract
The invention discloses a high-power high-pressure ratio centrifugal compressor performance test system which comprises a motor dragging system, a gear accelerating transmission system, a centrifugal compression system, an air storage tank, a turbine system, a gear decelerating transmission system and a power generation system, wherein the motor dragging system is connected with the gear accelerating transmission system; the gear accelerating transmission system is connected with the centrifugal compression system; the centrifugal compression system is connected with the air storage tank; the air storage tank is connected with the turbine system; the turbine system is connected with the gear reduction transmission system; the gear reduction transmission system is connected with the power generation system; the test system of the invention can recover the energy generated in the test. The invention also discloses a testing method of the multistage centrifugal compressor, which comprises the steps of (1) pneumatic efficiency detection, (2) inter-stage cooler performance detection, (3) transmission state detection and (4) rotor rotation speed detection.
Description
Technical Field
The invention belongs to the technical field of compressors, and particularly relates to a high-power high-pressure ratio centrifugal compressor performance test system and a test method thereof.
Background
The centrifugal compressor is used as a core device in the industrial field, is a power source of a pneumatic valve, an actuating cylinder and the like, and has high running stability and reliability requirements. For different application conditions, the compressor mainly comprises a positive displacement compressor (piston compressor, oil screw compressor, oil-free screw compressor) and a centrifugal compressor. For the use condition of high pressure and low flow, the positive displacement compressor has extremely high cost performance and large market share, but the outlet pressure fluctuation is larger, and a pressure stabilizing tank is required to be arranged; for the working condition requirement of high pressure ratio and large flow, the centrifugal compressor has extremely high cost performance and has wide application in the fields of petrochemical industry, metal smelting and the like.
The performance test of the centrifugal compressor is complex, and because the outlet pressure is high, a high-speed mechanical transmission system is required to be configured, so the performance test of the high-speed mechanical transmission system and the performance test of the pneumatic performance are very important. At present, a motor is used for driving a gear box to drive a centrifugal impeller to rotate at a high speed, so that mechanical energy is converted into potential energy and internal energy of fluid, an air outlet of a compressor is connected with a surge tank through a pipeline, the surge tank is used for controlling air discharge quantity through a valve, and pressure is set in the tank.
The current testing method of the centrifugal compressor has the following problems:
(1) The centrifugal compressor has large flow, high pressure and large power, so the energy consumption of the centrifugal compressor is high, and compressed gas of the centrifugal compressor is directly emptied after passing through the surge tank at present, thereby causing great energy waste.
(2) For the multistage centrifugal compressor, the comprehensive pneumatic efficiency test is only carried out through the inlet pressure, the temperature and the outlet pressure and the temperature, and the pneumatic efficiency of the centrifugal impellers of each stage is not tested.
(3) For multistage centrifugal compressors, an inter-stage cooler is provided to improve aerodynamic efficiency, but pressure loss, cooling effect, and the like of the inter-stage cooler are not evaluated.
(4) The centrifugal compressor can generate surge when working, and the high-speed mechanical transmission system can vibrate greatly, load fluctuation is large and the like under the surge condition, so that the high-speed mechanical transmission system works abnormally.
(5) For a multistage centrifugal compressor, the rotation speeds of the impeller rotor systems are different, but the critical rotation speeds may be crossed, so that under the influence of excitation such as pressure disturbance, airflow excitation, mass unbalance and the like, the vibration of a transmission system is overlarge, and destructive loss is seriously caused.
Disclosure of Invention
The invention aims to provide a high-power high-pressure ratio centrifugal compressor performance test system and a test method thereof, which are used for solving the technical problems in the background technology.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
the high-power high-pressure ratio centrifugal compressor performance test system comprises a motor dragging system, a gear accelerating transmission system, a centrifugal compression system, an air storage tank, a turbine system, a gear reducing transmission system and a power generation system, wherein an output shaft of the motor dragging system is connected with an input shaft of the gear accelerating transmission system through a coupler; an output shaft of the gear speed increasing transmission system is connected with the centrifugal compression system; the air outlet of the centrifugal compression system is connected with the air inlet of the air storage tank; the air outlet of the air storage tank is connected with the air inlet of the turbine system; the turbine system comprises a turbine and a volute, and the turbine is directly connected with an input shaft of the gear reduction transmission system; an output shaft of the gear reduction transmission system is connected with an input shaft of the power generation system through a coupler;
the centrifugal compression system comprises a multistage centrifugal compressor; the multistage centrifugal compressor comprises a centrifugal impeller and a centrifugal volute; the centrifugal impellers are directly connected with the gear speed increasing transmission system, a plurality of centrifugal impellers are arranged, and adjacent centrifugal impellers are connected with each other through pipelines after passing through the inter-stage cooler.
Further, an air temperature sensor and an air pressure sensor are arranged on the air inlet and the air outlet of each stage of centrifugal impeller.
Further, an air temperature sensor and an air pressure sensor are arranged on the air inlet and the air outlet of each stage of centrifugal impeller.
The water inlet and the water outlet of the inter-stage cooler are provided with a water temperature sensor and a flow sensor.
A testing method of a high-power high-pressure ratio centrifugal compressor performance testing system comprises the following steps:
(1) Pneumatic efficiency detection: the pressure and the temperature of the air inlet and the air outlet of each stage of centrifugal impeller are detected through a sensor, and the pneumatic efficiency of each stage of centrifugal impeller is calculated, so that the comprehensive pneumatic efficiency is obtained.
(2) Inter-stage cooler performance detection: the pressure and the temperature of the air inlet and the air outlet of each interstage cooler are monitored through sensors, the temperature, the pressure and the flow of the air inlet and the air outlet are monitored, and the cooling heat and the pressure loss of each interstage cooler are calculated.
(3) And (3) detecting a transmission state: the running states of the gear speed-increasing transmission system and the gear speed-reducing transmission system are monitored through the state detection system, whether the running states are normal or not is judged, and the centrifugal compression system and the turbine system are adjusted according to the judging result, so that the normal running of the gear speed-increasing transmission system and the gear speed-reducing transmission system is ensured.
(4) Rotor rotation speed detection: and obtaining critical rotation speeds of centrifugal impeller rotors at all levels through rotor dynamics and vibration test results, calculating a normal rotation speed interval of the rotation speeds of the centrifugal impeller rotors, and keeping the rotation speeds of the centrifugal impeller rotors at all levels in the normal rotation speed interval.
Further, in the above (1), the specific method is as follows: the air temperature and air pressure of the air inlet and the air outlet of each stage of centrifugal impeller are detected through a sensor, the pneumatic efficiency of each stage of centrifugal impeller is calculated, and the calculation formula is as follows:
wherein:
η n -n-th stage centrifugal impeller aerodynamic efficiency;
m-medium polytropic coefficient;
k, the dielectric insulation coefficient, which can be 1.4 for air, is dimensionless;
p ni -the inlet pressure of the nth stage centrifugal impeller in Pa;
p no -the n-th stage centrifugal impeller outlet pressure in Pa;
T ni -the temperature of the nth stage centrifugal impeller in on (K)
T no -the outlet temperature of the nth stage centrifugal impeller in on (K);
according to the obtained pneumatic efficiency of each stage of centrifugal impeller, calculating the comprehensive pneumatic efficiency:
η＝η 1 ×η 2 ×···×η n
the comprehensive pneumatic efficiency of the multistage centrifugal impeller can be obtained.
Further, the method for calculating the cooling heat comprises the following steps: the flow and the water temperature of the water inlet and outlet of each inter-stage cooler are detected through a sensor, the cooling heat of each inter-stage cooler is calculated, and the calculation formula is as follows:
W＝C×m×ΔT＝(Q w ×ρ)×(WT o －WT i )
wherein:
w-cooling heat;
c-specific heat capacity of water;
m-mass of water;
delta T-water inlet and outlet temperature difference;
Q w -inlet and outlet flow rates of water;
ρ—the density of water;
WT i -water temperature at the water inlet;
WT o -water temperature at the water outlet.
Further, in the above (2), the method for calculating the cooling loss is as follows: the temperature and the pressure of the air inlet and the air outlet of each interstage cooler are detected through a sensor, and the gas pressure loss of each interstage cooler is calculated:
AP＝(AP o －AP i )
wherein:
AP-loss of gas pressure;
AP i -air outlet pressure;
AP o -inlet air pressure.
Further, in the step (3), the state monitoring system includes a PLC control system, and the PLC control system monitors the state of the gear speed increasing transmission system, determines whether the state is normal, and adjusts the operation parameters of the centrifugal compression system according to the determination result, so that the operation state of the gear speed increasing transmission system is kept normal.
Further, in the step (4), the specific method is as follows: the method comprises the steps of firstly calculating a theoretical value of a first 3 rd order critical rotation speed of each level centrifugal impeller rotor system according to rotor dynamics, then correcting by using a vibration test result to obtain an accurate value of the first 3 rd order critical rotation speed of each level centrifugal impeller rotor, and calculating a normal rotation speed interval of each level centrifugal impeller rotor according to the obtained accurate value of the critical rotation speed to keep the rotation speed of each level centrifugal impeller rotor in the normal rotation speed interval.
Further, the normal rotation speed interval of the centrifugal impeller rotors at each stage is as follows:
0.85f ns ≤N n ≤1.15f ns
wherein: f (f) ns -the nth order critical speed of the nth order centrifugal impeller rotor
Nn-n-the rotor speed of the nth stage centrifugal impeller.
Compared with the prior art, the invention has the beneficial effects that:
1. in the test system, after the compressed gas generated by the centrifugal compression system is discharged into the gas storage tank, the turbine system can convert the internal energy and potential energy of the compressed gas into mechanical energy, and the mechanical energy is converted into electric energy through the power generation system, so that energy recovery is realized, and energy waste is reduced.
2. According to the testing method, the comprehensive pneumatic efficiency of the multistage centrifugal compressor is obtained by detecting the air temperature and the air pressure of each stage of centrifugal impeller and calculating the pneumatic efficiency of each stage of centrifugal impeller, the pneumatic efficiency of the multistage centrifugal compressor can be accurately estimated, and the pneumatic performance of each stage of centrifugal impeller can be optimally matched according to the calculation result, so that the comprehensive pneumatic efficiency of the system is the highest.
3. According to the testing method, the air temperature, the air pressure and the flow of the air inlet and the air outlet of the inter-stage cooler are detected through the sensor, the cooling heat capacity of the inter-stage cooler is calculated, the water temperature and the water pressure of the air inlet and the water outlet of the inter-stage cooler are detected, the heat loss of the inter-stage cooler is calculated, the performance of the inter-stage cooler is accurately evaluated, and the optimization design of a centrifugal compressor system is facilitated.
4. According to the testing method, the state monitoring system is used for monitoring the states of the gear speed-increasing transmission system and the gear speed-reducing transmission system, abnormal operation of the transmission system caused by surge of the centrifugal compression system and the turbine system is prevented, and the normal operation of the transmission system is ensured by adjusting the operation parameters of the centrifugal compression system and the turbine system to remove asthma.
5. In the test method, the critical rotation speed of the centrifugal impeller rotors at all levels is calculated to obtain the normal rotation speed interval of the centrifugal impeller rotors at all levels, so that the normal operation of the centrifugal impeller rotors at all levels is ensured, and the stability of the system is maintained.
Drawings
FIG. 1 is a schematic diagram of a high power high pressure ratio centrifugal compressor performance test system of the present invention;
FIG. 2 is a logical block diagram of the status detection system of the present invention;
in the drawing, a motor dragging system is shown in the specification; 2-a gear speed increasing transmission system; 3-a centrifugal compression system; 4-an air storage tank; 5-turbine system; 6-a gear reduction system; 7-power generation system.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be further described in detail below by referring to the accompanying drawings and by illustrating preferred embodiments. It should be noted, however, that many of the details set forth in the description are merely provided to provide a thorough understanding of one or more aspects of the invention, and that these aspects of the invention may be practiced without these specific details.
As shown in FIG. 1, the high-power high-pressure ratio centrifugal compressor performance test system comprises a motor dragging system 1, a gear speed-increasing transmission system 2, a centrifugal compression system 3, an air storage tank 4, a turbine system 5, a gear speed-reducing transmission system 6 and a power generation system 7, wherein an output shaft of the motor dragging system 1 is connected with an input shaft of the gear speed-increasing transmission system 2 through a coupling; an output shaft of the gear speed increasing transmission system 2 is connected with the centrifugal compression system 3; the air outlet of the centrifugal compression system 3 is connected with the air inlet of the air storage tank 4; the air outlet of the air storage tank 4 is connected with the air inlet of the turbine system 5; the turbine system 5 is a turbine and comprises a turbine and a volute, and the turbine is directly connected with an input shaft of the gear reduction transmission system 6; the output shaft of the gear reduction transmission system 6 is connected with the input shaft of the power generation system 7 through a coupler.
The motor dragging system 1 drives the gear speed increasing transmission system 2 to rotate through the coupler, the gear speed increasing transmission system 2 accelerates to drive the centrifugal compression system 3 to rotate, the centrifugal compression system 3 centrifugally compresses gas and discharges the gas into the gas storage tank 4, the gas storage tank 4 stores the compressed gas and then conveys the compressed gas to the turbine system 5, the turbine system 5 converts potential energy and internal energy of the compressed gas into mechanical energy, the mechanical energy is input into the power generation system 7 after being decelerated through the gear speed increasing transmission system 6, and the power generation system 7 converts the mechanical energy into electric energy and feeds the electric energy back into the motor dragging system 1 to realize energy recovery.
The centrifugal compression system 3 comprises a multistage centrifugal compressor; the multistage centrifugal compressor comprises a centrifugal impeller and a centrifugal volute; the centrifugal impellers are provided with a plurality of air inlets and air outlets, and the air is heated and pressurized for a plurality of times through the plurality of centrifugal impellers; the adjacent centrifugal impellers are connected with each other through pipelines after passing through an inter-stage cooler, and the inter-stage cooler is provided with an air inlet and an air outlet for connecting the centrifugal impellers, and is also provided with a water inlet and a water outlet for cooling water circulation.
And air temperature sensors and air pressure sensors are arranged on the air inlet and the air outlet of each stage of centrifugal impeller and are used for monitoring the air temperature and the air pressure of the air inlet and the air outlet of each stage of centrifugal impeller.
The water inlet and the water outlet of the inter-stage cooler are provided with a water temperature sensor and a flow sensor for measuring the water temperature and the water flow of the water inlet and the water outlet of the inter-stage cooler, and the air inlet and the air outlet of the inter-stage cooler are respectively connected with the centrifugal impeller, and the air inlet and the air outlet of the centrifugal impeller are provided with a gas temperature sensor and a pressure sensor, so that the gas temperature and the gas pressure of the inlet and the outlet of the inter-stage cooler can be detected through the gas temperature sensor and the gas pressure sensor of the air inlet and the air outlet of each centrifugal impeller.
A testing method of a high-power high-pressure ratio centrifugal compressor performance testing system comprises the following steps:
(1) Pneumatic efficiency monitoring: the specific method comprises the following steps: the air temperature sensor and the air pressure sensor are used for detecting the air temperature and the air pressure of the air inlet and the air outlet of each stage of centrifugal impeller, and calculating the pneumatic efficiency of each stage of centrifugal impeller, wherein the calculation formula is as follows:
wherein:
η n -n-th stage centrifugal impeller aerodynamic efficiency;
m-medium polytropic coefficient;
k, the dielectric insulation coefficient, which can be 1.4 for air, is dimensionless;
p ni -the inlet pressure of the nth stage centrifugal impeller in Pa;
p no -the n-th stage centrifugal impeller outlet pressure in Pa;
T ni -the temperature of the nth stage centrifugal impeller in on (K)
T no -the outlet temperature of the nth stage centrifugal impeller in on (K);
according to the pneumatic efficiency of each stage of centrifugal impeller, calculating the comprehensive pneumatic efficiency:
η＝η 1 ×η 2 ×···×η n
the comprehensive pneumatic efficiency of the multistage impeller can be obtained. Through the monitoring of pressure and temperature of inlet and outlet of centrifugal impellers at each stage, the pneumatic efficiency of the centrifugal impellers at each stage is accurately calculated, and the pneumatic performance of the centrifugal impellers at each stage is optimally matched according to the test result, so that the comprehensive pneumatic efficiency of the system is highest.
(2) Inter-stage cooler performance detection: detecting the water inlet and outlet flow and the water temperature of the inter-stage cooler through a sensor, wherein the water inlet flow and the water outlet flow of the inter-stage cooler are unchanged, so that the water inlet flow of the inter-stage cooler is equal to the water outlet flow; the cooling heat of each inter-stage cooler is calculated by the following formula:
W＝C×m×ΔT＝(Q w ×ρ)×(WT o －WT i )
wherein:
w-cooling heat;
c-specific heat capacity of water;
m-mass of water;
delta T-water inlet and outlet temperature difference;
Q w -inlet and outlet flow rates of water;
ρ—the density of water;
WT i -water temperature at the water inlet;
WT o -water temperature at the water outlet.
And (3) according to the temperature, pressure and flow of the air inlet and outlet of the interstage coolers detected by the sensor, calculating the gas pressure loss of each interstage cooler:
Ap＝(Ap o －AP i )
wherein:
AP-loss of gas pressure;
Ap i -air outlet pressure;
Ap o -inlet air pressure;
the pressure loss of each interstage cooler can be obtained, and the performance of the interstage cooler is accurately estimated by cooling heat and pressure loss of the interstage cooler, so that the optimization design of the centrifugal compressor system is facilitated.
(3) And (3) transmission state monitoring: the running state of the gear speed increasing transmission system 2 is monitored through the state detection system, whether the running state is normal or not is judged, and the centrifugal compression system 3 and the turbine system 5 are adjusted according to the judging result, so that the normal running of the gear speed increasing transmission system 2 and the gear speed reducing transmission system 6 is ensured.
As shown in fig. 2, the state monitoring system includes a PLC control system, which performs state identification on the bearing temperature, the oil inlet pressure, the oil inlet temperature and the vibration condition of the gear speed increasing transmission system 2, determines whether the bearing temperature, the oil inlet pressure, the oil inlet temperature and the vibration condition are normal, if yes, keeps running, if not, adjusts the running speed, the running power and other parameters of the centrifugal compressor, and performs state monitoring on the gear speed increasing transmission system 2 until the PLC control system determines that the running state is normal.
Because the centrifugal compression system 3 can generate surge in the operation process, the gear box of the gear speed increasing transmission system 2 can vibrate and enlarge under the condition of surge, the load fluctuation is large, and the like, so that the gear speed increasing transmission system 2 works abnormally, the operation parameters of the centrifugal compression system 3 are required to be regulated to carry out asthma relief, the normal operation of the gear speed increasing transmission system 2 is further restored, and the normal operation of the gear speed increasing transmission system 2 is ensured.
In another embodiment, the condition sensing system is also capable of monitoring the operating condition of the gear reduction transmission 6 and de-energizing by changing the operating parameters of the turbine system 5, since the turbine system 5 is also subject to surge.
(4) Rotor speed monitoring: according to theory of rotor dynamics and finite element model, calculating theoretical value of 3 rd order critical rotation speed of centrifugal impeller rotor system of each stage, installing vibration sensor on each stage centrifugal impeller rotor system, vibration testing by vibration sensor, measuring vibration signals under different rotation speeds, analyzing frequency spectrum and amplitude of vibration signals on data analysis system, finding out critical rotation speed corresponding to theoretical calculation result, or finding out other critical rotation speeds existing in actual rotor system, correcting theoretical value by using vibration test result, thereby obtaining more accurate critical rotation speed value, obtaining 3 rd order accurate critical rotation speed of centrifugal impeller rotor of each stage, calculating normal rotation speed interval of centrifugal impeller rotor of each stage according to critical rotation speed, and keeping rotation speed of centrifugal impeller rotor of each stage in normal rotation speed interval.
The normal rotation speed interval is as follows:
0.85f ns ≤N n ≤1.15f ns
wherein: f (f) ns -the nth order critical rotational speed of the nth order centrifugal impeller rotor;
N n -n-th stage centrifugal impeller rotor speed.
And (3) optimally designing a rotor system of each centrifugal impeller according to the obtained correct rotating speed interval of the rotor, avoiding running near the critical rotating speed and ensuring the stability of the system.
While the invention has been described with respect to the preferred embodiments, it should be noted that modifications and adaptations to those skilled in the art may be made without departing from the principles of the present invention and are intended to be within the scope of the present invention.
Claims (10)
1. A high-power high-pressure ratio centrifugal compressor performance test system is characterized in that: the device comprises a motor dragging system, a gear accelerating transmission system, a centrifugal compression system, an air storage tank, a turbine system, a gear decelerating transmission system and a power generation system, wherein an output shaft of the motor dragging system is connected with an input shaft of the gear accelerating transmission system through a coupling; an output shaft of the gear speed increasing transmission system is connected with the centrifugal compression system; the air outlet of the centrifugal compression system is connected with the air inlet of the air storage tank; the air outlet of the air storage tank is connected with the air inlet of the turbine system; the turbine system comprises a turbine and a volute, and the turbine is directly connected with an input shaft of the gear reduction transmission system; an output shaft of the gear reduction transmission system is connected with an input shaft of the power generation system through a coupler;
the centrifugal compression system comprises a multistage centrifugal compressor; the multistage centrifugal compressor comprises a centrifugal impeller and a centrifugal volute; the centrifugal impellers are directly connected with the gear speed increasing transmission system, a plurality of centrifugal impellers are arranged, and adjacent centrifugal impellers are connected with each other through pipelines after passing through the inter-stage cooler.
2. The high power high pressure ratio centrifugal compressor performance test system of claim 1, wherein: and an air temperature sensor and an air pressure sensor are arranged on the air inlet and the air outlet of each stage of centrifugal impeller.
3. The high power high pressure ratio centrifugal compressor performance test system of claim 1, wherein: the water inlet and the water outlet of the inter-stage cooler are provided with a water temperature sensor and a flow sensor.
4. A testing method of a high power high pressure ratio centrifugal compressor performance testing system according to any one of claims 1-3, comprising the following:
(1) Pneumatic efficiency detection: the pressure and the temperature of the air inlet and the air outlet of each stage of centrifugal impeller are detected through a sensor, and the pneumatic efficiency of each stage of centrifugal impeller is calculated, so that the comprehensive pneumatic efficiency is obtained.
(2) Inter-stage cooler performance detection: the pressure and the temperature of the air inlet and the air outlet of each interstage cooler are monitored through sensors, the temperature, the pressure and the flow of the air inlet and the air outlet are monitored, and the cooling heat and the pressure loss of each interstage cooler are calculated.
(3) And (3) detecting a transmission state: the running states of the gear speed-increasing transmission system and the gear speed-reducing transmission system are monitored through the state detection system, whether the running states are normal or not is judged, and the centrifugal compression system and the turbine system are adjusted according to the judging result, so that the normal running of the gear speed-increasing transmission system and the gear speed-reducing transmission system is ensured.
(4) Rotor rotation speed detection: and obtaining critical rotation speeds of centrifugal impeller rotors at all levels through rotor dynamics and vibration test results, calculating a normal rotation speed interval of the rotation speeds of the centrifugal impeller rotors, and keeping the rotation speeds of the centrifugal impeller rotors at all levels in the normal rotation speed interval.
5. The testing method of the high-power high-pressure ratio centrifugal compressor performance testing system according to claim 4, wherein in the step (1), the specific method is as follows: the air temperature and air pressure of the air inlet and the air outlet of each stage of centrifugal impeller are detected through a sensor, the pneumatic efficiency of each stage of centrifugal impeller is calculated, and the calculation formula is as follows:
wherein:
η n -n-th stage centrifugal impeller aerodynamic efficiency;
m-medium polytropic coefficient;
k, the dielectric insulation coefficient, which can be 1.4 for air, is dimensionless;
p ni -the inlet pressure of the nth stage centrifugal impeller in Pa;
p no -the n-th stage centrifugal impeller outlet pressure in Pa;
T ni -the temperature of the nth stage centrifugal impeller in on (K)
T no -the outlet temperature of the nth stage centrifugal impeller in on (K);
according to the obtained pneumatic efficiency of each stage of centrifugal impeller, calculating the comprehensive pneumatic efficiency:
η＝η 1 ×η 2 ×···×η n
the comprehensive pneumatic efficiency of the multistage centrifugal impeller can be obtained.
6. The test method of the high-power high-pressure ratio centrifugal compressor performance test system according to claim 4, wherein in (2), the method for calculating the cooling heat is as follows: the flow and the water temperature of the water inlet and outlet of each inter-stage cooler are detected through a sensor, the cooling heat of each inter-stage cooler is calculated, and the calculation formula is as follows:
W＝C×m×ΔT＝(Q w ×ρ)×(WT o －WT i )
wherein:
w-cooling heat;
c-specific heat capacity of water;
m-mass of water;
delta T-water inlet and outlet temperature difference;
Q w -inlet and outlet flow rates of water;
ρ—the density of water;
WT i -water temperature at the water inlet;
WT o -water temperature at the water outlet.
7. The test method of the high-power high-pressure ratio centrifugal compressor performance test system according to claim 4, wherein in (2), the calculation method of the cooling loss is as follows: the temperature and the pressure of the air inlet and the air outlet of each interstage cooler are detected through a sensor, and the gas pressure loss of each interstage cooler is calculated:
AP＝(Ap o －Ap i )
wherein:
ap—gas pressure loss;
AP i -air outlet pressure;
AP o -inlet air pressure.
8. The method according to claim 4, wherein in (3), the state monitoring system comprises a PLC control system, the PLC control system monitors the state of the gear speed increasing transmission system, determines whether the gear speed increasing transmission system is normal, and adjusts the operation parameters of the centrifugal compression system according to the determination result, so that the operation state of the gear speed increasing transmission system is kept normal.
9. The testing method of the high-power high-pressure ratio centrifugal compressor performance testing system according to claim 4, wherein in the step (4), the specific method is as follows: the method comprises the steps of firstly calculating a theoretical value of a first 3 rd order critical rotation speed of each level centrifugal impeller rotor system according to rotor dynamics, then correcting by using a vibration test result to obtain an accurate value of the first 3 rd order critical rotation speed of each level centrifugal impeller rotor, and calculating a normal rotation speed interval of each level centrifugal impeller rotor according to the obtained accurate value of the critical rotation speed to keep the rotation speed of each level centrifugal impeller rotor in the normal rotation speed interval.
10. The testing method of the high-power high-pressure ratio centrifugal compressor performance testing system according to claim 9, wherein the normal rotation speed interval of the centrifugal impeller rotors of each stage is:
0.85f ns ≤N n ≤1.15f ns wherein:
f ns -the nth order critical rotational speed N of the nth order centrifugal impeller rotor n -n-th stage centrifugal impeller rotor speed.
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| CN117780614B (en) * | 2024-01-24 | 2024-05-17 | 中山清匠电器科技有限公司 | Compressor control system for portable molecular sieve oxygenerator |
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