CN114526254A - Energy consumption evaluation method and device for centrifugal compressor - Google Patents
Energy consumption evaluation method and device for centrifugal compressor Download PDFInfo
- Publication number
- CN114526254A CN114526254A CN202011319075.8A CN202011319075A CN114526254A CN 114526254 A CN114526254 A CN 114526254A CN 202011319075 A CN202011319075 A CN 202011319075A CN 114526254 A CN114526254 A CN 114526254A
- Authority
- CN
- China
- Prior art keywords
- compressor
- temperature
- determining
- polytropic exponent
- data
- 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.)
- Pending
Links
- 238000005265 energy consumption Methods 0.000 title claims abstract description 56
- 238000011156 evaluation Methods 0.000 title claims abstract description 32
- 238000000034 method Methods 0.000 claims abstract description 48
- 238000004364 calculation method Methods 0.000 claims abstract description 17
- 238000006243 chemical reaction Methods 0.000 claims description 12
- 230000005540 biological transmission Effects 0.000 claims description 8
- 230000004044 response Effects 0.000 claims description 8
- 239000007789 gas Substances 0.000 description 16
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 10
- 230000008569 process Effects 0.000 description 8
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 239000003345 natural gas Substances 0.000 description 5
- 238000012545 processing Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000012824 chemical production Methods 0.000 description 1
- 239000003546 flue gas Substances 0.000 description 1
- 235000003642 hunger Nutrition 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000037351 starvation Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P90/00—Enabling technologies with a potential contribution to greenhouse gas [GHG] emissions mitigation
- Y02P90/80—Management or planning
- Y02P90/82—Energy audits or management systems therefor
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Air Blowers (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The application relates to a method and a device for evaluating energy consumption of a centrifugal compressor, belonging to the field of energy consumption evaluation. The method comprises the following steps: determining a temperature polytropic exponent of the compressor in a preset calculation mode, wherein the temperature polytropic exponent corresponds to the temperature of the current inlet state and the temperature of the current outlet state of the compressor; determining a volume polytropic exponent of the compressor based on the temperature polytropic exponent; determining the operating power of the compressor according to the volume polytropic exponent, wherein the operating power represents the power condition of the compressor in the current operating state; and determining an energy consumption evaluation result of the compressor according to the running power. According to the assessment method, the volume polytropic exponent is determined through the temperature polytropic exponent corresponding to the current compressor, and then the power condition of the compressor in a certain running state is determined through the volume polytropic exponent.
Description
Technical Field
The application relates to the field of energy consumption evaluation, in particular to a method and a device for evaluating energy consumption of a centrifugal compressor.
Background
In the construction of a natural gas long-distance pipeline, a compressor is used as a core device, and the energy consumption cost of the compressor accounts for a large proportion of the natural gas pipeline transmission cost.
In the process of calculating the energy consumption of the compressor, four numerical values, namely the inlet pressure of the compressor, the outlet pressure of the compressor, the inlet flow of the compressor and the inlet temperature of the compressor, are required to be determined, the rotating speed of the compressor is calculated by mainly taking the temperature polytropic exponent as a parameter, so that the power of the compressor is obtained, and the specific energy consumption is calculated.
Because in the actual working process of the compressor, the temperature inside the compressor is different, heat is generated after natural gas is pressurized, the difference between the inlet temperature and the outlet temperature of the compressor is large, the energy consumption of the compressor is calculated by taking the average value of the polytropic index of the inlet temperature and the polytropic index of the outlet temperature, and the error of the energy consumption of the compressor calculated by the method is large compared with the actual energy consumption.
Disclosure of Invention
The embodiment of the application provides a method and a device for evaluating energy consumption of a centrifugal compressor, which can reduce errors of energy consumption evaluation results of the centrifugal compressor. The technical scheme is as follows:
in one aspect, a method for estimating energy consumption of a centrifugal compressor is provided, and is applied to a computer device, and the method comprises the following steps:
determining a temperature polytropic exponent of the compressor in a preset calculation mode, wherein the temperature polytropic exponent corresponds to the temperature of the current inlet state and the temperature of the current outlet state of the compressor;
determining a volume polytropic exponent for the compressor based on the temperature polytropic exponent;
determining the operating power of the compressor according to the volume polytropic exponent, wherein the operating power represents the power condition of the compressor in the current operating state;
and determining an energy consumption evaluation result of the compressor according to the running power.
In an alternative embodiment, the determining the temperature polytropic exponent of the compressor in the preset calculation manner includes:
obtaining efficiency data of a compressor, wherein the efficiency data of the compressor is the efficiency corresponding to the target flow of the compressor;
obtaining the temperature polytropic index based on the efficiency data and a temperature adiabatic coefficient, the temperature adiabatic coefficient corresponding to a temperature within the compressor.
In an alternative embodiment, the determining the operating power of the compressor based on the volume polytropic exponent comprises:
determining the running speed of the compressor according to the volume polytropic index;
and performing power conversion on the operation rotating speed to obtain the operation power of the compressor.
In an optional embodiment, said converting said operating speed to obtain said operating power of said compressor comprises:
determining candidate rotating speeds within a preset rotating speed interval range;
matching the running rotating speed with the candidate rotating speed;
and responding to the rotating speed difference between the running rotating speed and the candidate rotating speed to meet the rotating speed difference requirement, and performing power conversion on the running rotating speed to obtain the running power.
In an alternative embodiment, the determining the volume polytropic exponent of the compressor based on the temperature polytropic exponent comprises:
acquiring the inbound temperature;
determining candidate outbound temperature within a preset temperature interval range;
determining a first temperature polytropic exponent of the compressor according to the candidate rotating speed and the station entering temperature;
determining a second temperature polytropic exponent of the compressor according to the candidate rotating speed and the candidate outbound temperature;
taking the mean of the first temperature polytropic exponent and the second temperature polytropic exponent as the temperature polytropic exponent;
determining the outbound temperature according to the temperature polytropic exponent;
determining the volume polytropic exponent based on the outbound temperature in response to a temperature difference between the outbound temperature and the candidate outbound temperature meeting a temperature difference requirement.
In an alternative embodiment, the determining the volume polytropic exponent based on the outbound temperature includes:
obtaining pressure data of the compressor, the pressure data including an inlet pressure and an outlet pressure of the compressor;
determining density data of the compressor according to the inbound temperature and the outbound temperature;
determining the volume polytropic exponent from the pressure data and the density data.
In an alternative embodiment, said determining a volume polytropic exponent of said compressor based on said pressure data and said density data comprises:
determining a pressure ratio interval of the compressor under the operation state corresponding to the target flow;
acquiring current pressure ratio data of the compressor;
in response to the pressure ratio data being within a data interval range of the pressure ratio interval, determining the volume polytropic exponent from the pressure data and the density data.
In an optional embodiment, the determining the pressure ratio interval of the compressor in the operating state corresponding to the target flow rate includes:
acquiring the maximum rotating speed, the minimum rotating speed, flow data, the rotating speed of a surge working condition and the rotating speed of a stagnation working condition of the compressor;
determining a first pressure ratio according to the maximum rotating speed and the flow data;
determining a second pressure ratio according to the surge working condition rotating speed and the flow data;
determining the minimum value of the first pressure ratio and the second pressure ratio as the maximum pressure ratio of the compressor;
determining a third pressure ratio according to the minimum rotating speed and the flow data;
determining a fourth pressure ratio according to the stagnation working condition rotating speed and the flow data;
determining the largest value of the third pressure ratio and the fourth pressure ratio as the minimum pressure ratio of the press;
the range between the minimum pressure ratio and the maximum pressure ratio is taken as the pressure ratio interval.
In an alternative embodiment, the determining the operating power of the compressor according to the volume polytropic exponent further includes:
obtaining a first operation efficiency of the compressor according to the operation rotating speed;
acquiring a second operation efficiency corresponding to a transmission machine of the compressor;
acquiring a third operating efficiency corresponding to a driving machine of the compressor;
acquiring multi-variable energy head data and mass flow data of the compressor;
determining an operating power of the compressor based on the first operating efficiency, the second operating efficiency, the third operating efficiency, the multi-variable head data, and the mass flow data.
In another aspect, an apparatus for calculating and evaluating energy consumption of a centrifugal compressor is provided, and the apparatus is applied to a computer device, and comprises:
the temperature polytropic exponent determining module is used for determining a temperature polytropic exponent of the compressor in a preset calculating mode, and the temperature polytropic exponent corresponds to the temperature of the current inlet state and the temperature of the current outlet state of the compressor;
the parameter determination module is further configured to determine a volume polytropic exponent of the compressor based on the temperature polytropic exponent;
the power determining module is used for determining the operating power of the compressor according to the volume polytropic exponent, and the operating power represents the power condition of the compressor in the current operating state;
and the result determining module is used for determining the energy consumption evaluation result of the compressor according to the running power.
The technical scheme provided by the embodiment of the application brings beneficial effects that:
the method comprises the steps that the volume changeable exponent corresponding to the current flow is determined according to the current operation state of the compressor, the power condition of the compressor in the current operation state is determined according to the volume changeable exponent, the energy consumption of the compressor is evaluated according to the power condition to obtain a result, the power condition of the compressor in a certain operation state is determined according to the volume changeable exponent, the volume changeable exponent is not affected by temperature under the same flow, the value of the volume changeable exponent is fixed, the error of the energy consumption evaluation result can be reduced, and the evaluation result can be closer to the actual operation result.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a block diagram of a computer device provided in an exemplary embodiment of the present application;
FIG. 2 is a flow chart of a method for evaluating energy consumption of a centrifugal compressor provided in an exemplary embodiment of the present application;
FIG. 3 is a flow chart of energy consumption evaluation method sub-steps for a centrifugal compressor provided in an exemplary embodiment of the present application;
FIG. 4 is a flow chart of a method of determining operating power of a compressor based on a volume polytropic exponent according to an exemplary embodiment of the present application;
FIG. 5 is a flow chart of a method of determining an operating speed of a compressor based on a volume polytropic exponent according to an exemplary embodiment of the present application;
fig. 6 is a block diagram illustrating an apparatus for energy consumption evaluation of a centrifugal compressor according to an exemplary embodiment of the present application.
Detailed Description
To make the objects, technical solutions and advantages of the present application more clear, embodiments of the present application will be described in further detail below with reference to the accompanying drawings.
When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present application. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present application, as detailed in the appended claims.
In the description of the present application, it is to be understood that the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
First, in order to make the solution shown in the embodiment of the present application easy to understand, several terms and formulas appearing in the embodiment of the present application are explained below:
a centrifugal compressor: all the compressors mentioned in this application are centrifugal compressors, which are mainly used to compress gases and are key machines for compressing and transporting various gases in chemical production. The rotor comprises an impeller and a shaft, wherein the impeller is provided with blades, a balance disc and a part of shaft seal; the main body of the stator is a cylinder, and the stator also comprises a diffuser, a bend, a reflux device, a jet pipe, an exhaust pipe and other devices. The working principle of the centrifugal compressor is as follows: when the impeller rotates at a high speed, the gas is thrown into the diffuser under the action of centrifugal force along with the rotation of the impeller, a vacuum zone is formed at the impeller, and at the moment, external fresh gas enters the impeller. The impeller is continuously rotated and gas is continuously sucked and thrown out, thereby maintaining continuous flow of gas.
Energy consumption evaluation: the energy utilization condition of the compressor is simulated through simulation, the consumption of the energy consumption of the compressor is calculated, the energy efficiency index and the economic index in subsequent engineering construction are analyzed, the calculation accuracy of the energy consumption cost of the compressor is required to reach a certain standard, and the error is within an acceptable range.
Volume polytropic exponent: the calculation formula of the polytropic exponent in the polytropic process in the constant volume state is shown as the following formula I:
the formula I is as follows:
where p1 is the pressure at the compressor inlet condition, p2 is the pressure at the compressor outlet, ρ 1 is the density at the compressor inlet, ρ 2 is the density at the compressor outlet, mvRepresenting the volume polytropic exponent.
Temperature polytropic index: the calculation formula of the polytropic exponent in the polytropic process in the constant temperature state is shown as the following formula II:
the formula II is as follows:
wherein η is the polytropic efficiency of the compressor, i.e. the ratio of polytropic compression work to total power in the compressor, the polytropic efficiency of the compressor stage can reach 80-85%, kTIs the coefficient of thermal insulation of temperature, mTIs an index of temperature starvation.
Surge condition: surge is a vibration of a centrifugal compressor under an abnormal condition occurring when a flow rate is reduced to a certain extent, and the surge has a serious damage to the centrifugal compressor. When the flow rate of the centrifugal compressor is reduced to a certain value (referred to as a minimum flow rate Qmin), the centrifugal compressor cannot operate stably, the flow is pulsed, the vibration is intensified, and roar is accompanied, such unstable condition is referred to as "surge condition", and this flow rate limit Qmin is referred to as "surge flow rate".
Stagnation conditions: the stagnation state is a state in which kinetic energy is entirely converted into pressure energy. When the gas flow continues to increase to a certain maximum flow, the speed of the gas flow at the smallest cross section in the blade path will reach sonic speed, and the flow cannot be increased any more. At this time, the work of the impeller on the gas is totally used for overcoming the flow loss, the energy change is heat energy, the gas pressure is not increased, and the condition is called a stagnation condition.
Transmission efficiency: refers to the ratio of the energy output by the transmission mechanism to the energy input.
Efficiency of the drive: efficiency of the driver driving the compressor, and the typical driver of a centrifugal compressor includes one of an electric motor, a gas turbine, a steam turbine, a flue gas turbine, and a diesel engine.
Multi-energy-variable head: the energy head is a common term for axial and centrifugal compressors and refers to the difference between the energy contained in a unit mass of gas after compression by the compressor and the state before compression. The multi-energy-conversion head is a difference value between the energy contained in the gas with unit mass in the variable process after the gas is compressed by the compressor and the state before compression.
Mass flow rate: refers to the mass of fluid per unit time that the fluid passes through the effective cross-section of a closed pipe or open channel.
For example, the method for evaluating energy consumption of a centrifugal compressor according to an embodiment of the present application may be applied to a computer device, please refer to fig. 1, where fig. 1 is a block diagram of a computer device according to an exemplary embodiment of the present application, where the computer device 101 includes a processor 102 and a memory 103, where the memory 103 stores at least one instruction, and the instruction is loaded and executed by the processor 102 to implement the method for evaluating energy consumption of a centrifugal compressor according to the method embodiments of the present application.
In this application, the computer device 101 is an electronic device capable of processing data and completing calculation, the computer device 101 includes two major parts, namely a hardware system and a software system, and the computer device 101 is capable of receiving data measured by a measuring instrument on a compressor, performing sorting calculation on the data to obtain an energy consumption evaluation result of the compressor, and outputting the energy consumption evaluation result.
The Memory 103 may include a Random Access Memory (RAM) or a Read-Only Memory (Read-Only Memory). Optionally, the memory 103 includes a non-transitory computer-readable medium. The memory 103 may be used to store instructions, programs, code sets or instruction sets. The memory 103 may include a stored program area and a stored data area, wherein the stored program area may store instructions for implementing an operating system, instructions for at least one function (such as compressor power calculation, compressor energy consumption estimation result generation, etc.), instructions for implementing various method embodiments described below, and the like; the storage data area may store data and the like referred to in the following respective method embodiments.
Referring to fig. 2, an embodiment of the present application provides a method for estimating energy consumption of a centrifugal compressor, which may be applied to the computer apparatus shown above, and the method includes:
In the embodiment of the application, because the centrifugal compressor is widely applied to the construction of long-distance natural gas pipelines, certain requirements are required on the accuracy of the energy consumption evaluation of the compressor in the process of calculating and optimizing the energy consumption cost of the compressor, and the error of the centrifugal compressor needs to be controlled within a certain acceptable range.
Before calculating the energy consumption cost of the compressor, relevant parameters of the compressor need to be read, wherein the relevant parameters comprise the inlet pressure, the outlet pressure, the flow data and the inbound temperature of the compressor. Illustratively, the relevant parameters are measured by technicians on site through measuring instruments, and the data are read and recorded, wherein the measuring instruments include but are not limited to at least one of a flowmeter, a thermometer and a pressure gauge.
In the embodiment of the application, the measuring instrument can transmit the measured data to the computer device and store the data in the memory of the computer device. In one possible form, the measuring instrument is connected to the computer device directly or indirectly for data transmission. In another possible approach, the technician reads the data from the measurement instrument and records the data, and inputs the data into the computer device for storage.
In the embodiment of the application, the energy consumption evaluation mode is suitable for a centrifugal compressor, the centrifugal compressor has different stable working condition intervals under different flow rates, when the flow rate in the centrifugal compressor is reduced to a certain degree, abnormal vibration and airflow noise can be generated, the surging of the centrifugal compressor is called, and under the surging working condition, the centrifugal compressor cannot normally operate; when the pressure in the centrifugal compressor reaches the maximum value, namely the kinetic energy of the gas is completely converted into the pressure energy, the gas is in a stagnation state, and the centrifugal compressor cannot normally operate under the stagnation working condition. Therefore, after the flow data in the relevant parameters are obtained, the flow data are used as the target flow, the pressure ratio interval corresponding to the target flow in the working state is determined, the pressure ratio interval represents the inlet/outlet pressure ratio interval in which the compressor can normally work under the current flow of the compressor, and the current normal working state of the compressor is determined according to the inlet pressure and the outlet pressure in the relevant parameters.
Referring to fig. 3, the method for determining the pressure ratio interval of the compressor includes:
the maximum speed, the minimum speed, the flow data, the surge condition speed and the stagnation condition speed of the compressor are obtained, wherein the maximum speed and the minimum speed of the compressor are provided by a compressor specification. The flow data is volume flow of the compressor in an inlet state obtained by converting flow under a standard condition, and the inlet state is an inlet state under a certain entering pressure and a certain entering temperature. The conversion formula is shown as the following formula III:
the formula III is as follows:
wherein Q1For flow at the inlet of the compressor, T1Is the temperature at the inlet of the compressor, P1Is the pressure at the inlet of the compressor, Z1Is the compression factor, Q, in the import state0Is the flow under standard conditions.
The rotating speed of the surge working condition is obtained by substituting flow data into a surge curve equation of the current compressor, and the surge curve equation is shown as a formula IV:
the formula four is as follows: n ═ c0+c1Q1+c2×Q1 2
Wherein n is the rotation speed of the compressor, Q1Is the flow rate of the compressor, c0、c1And c2Are coefficients.
The rotating speed under the stagnation working condition is obtained by substituting flow data into a stagnation curve equation of the current compressor, and the stagnation curve equation is shown as a formula five:
the formula five is as follows: n ═ d0+d1Q1+d2×Q1 2
Wherein n is the rotation speed of the compressor, Q1Is the flow rate of the compressor, d0、d1And d2Are coefficients.
Determining a first pressure ratio 301 according to the maximum rotation speed and the flow data; determining a second pressure ratio 302 according to the surge condition rotating speed and flow data; and determining the minimum value of the first pressure ratio and the second pressure ratio as the maximum pressure ratio of the compressor. The pressure ratio of the compressor which can normally work under the same flow rate is always smaller than the pressure ratio corresponding to the maximum rotating speed and smaller than the pressure ratio corresponding to the rotating speed under the surge working condition.
Determining a third pressure ratio 304 from the minimum rotational speed and the flow data; determining a fourth pressure ratio 303 according to the stagnation working condition rotating speed and the flow data; and determining the largest value of the third pressure ratio and the fourth pressure ratio as the minimum pressure ratio of the compressor. The pressure ratio of the compressor capable of working normally under the same flow rate is always larger than the pressure ratio corresponding to the minimum rotating speed and larger than the pressure ratio corresponding to the rotating speed under the stagnation working condition.
The range between the minimum pressure ratio and the maximum pressure ratio is taken as a pressure ratio interval.
In the embodiment of the present application, it is required to ensure that the current pressure ratio of the compressor is within the corresponding pressure ratio interval in the operating state, so as to ensure that the compressor is normally operated. After the relevant parameters are obtained, the processor performs preset processing on the obtained relevant parameters to obtain corresponding temperature polytropic exponents, and in an example, the preset processing may be completed by one or more code modules.
Illustratively, the preset processing includes: and determining the temperature polytropic exponent of the compressor in a preset calculation mode, wherein the temperature polytropic exponent corresponds to the temperature of the current inlet state and the temperature of the current outlet state of the compressor. Illustratively, the preset calculation method includes: obtaining efficiency data of a compressor, wherein the efficiency data of the compressor is the efficiency corresponding to the target flow of the compressor; a temperature polytropic index is derived based on the efficiency data and a temperature adiabatic coefficient, wherein the temperature adiabatic coefficient corresponds to a temperature within the compressor, and in one example, the temperature polytropic index is derived from equation two.
In step 202, a volume polytropic exponent of the compressor is determined based on the temperature polytropic exponent.
Illustratively, determining the volume polytropic exponent from the temperature polytropic exponent comprises: acquiring pressure data of the compressor, wherein the pressure data comprises inlet pressure and outlet pressure of the compressor; determining density data of the compressor according to the incoming temperature and the outgoing temperature; and determining the volume polytropic exponent according to the pressure data and the density data. Wherein the outbound temperature is determined by the temperature polytropic exponent.
And step 203, determining the running power of the compressor according to the volume polytropic index, wherein the running power represents the power condition of the compressor in the current running state.
The operation power of the compressor in the current operation state is determined by the volume variable exponent, the volume variable exponent is a fixed value and cannot change according to the temperature change in the compressor in the operation state of the compressor under a certain flow, and the operation power determined by the volume variable exponent is closer to the actual operation power.
And step 204, determining an energy consumption evaluation result of the compressor according to the running power.
In the embodiment of the present application, the processor determines an energy consumption estimation result of the compressor according to the operation power determined by the volume polytropic index, wherein the energy consumption estimation result includes, but is not limited to, at least one of energy consumed by the compressor in a certain operation state, an electric power cost and an actual cost.
According to the energy consumption evaluation method of the centrifugal compressor, the power condition of the compressor in a certain operation state is determined through the volume polytropic exponent, and the volume polytropic exponent is fixed under the same flow, so that the error of an energy consumption evaluation result can be reduced, and the evaluation result can be closer to an actual operation result.
Referring to fig. 4, fig. 4 is a flowchart illustrating a method for determining an operating power of a compressor according to a volume polytropic exponent according to an embodiment of the present application. The method shown in fig. 4 may be applied in a computer device as shown in fig. 1. The method comprises the following steps:
Before calculating the energy consumption cost of the compressor, relevant parameters of the compressor need to be read, wherein the relevant parameters comprise the inlet pressure, the outlet pressure, the flow data and the inbound temperature of the compressor. Illustratively, the relevant parameters are measured by technicians on site through measuring instruments, and the data are read and recorded, wherein the measuring instruments include but are not limited to at least one of a flowmeter, a thermometer and a pressure gauge.
And 402, determining the temperature polytropic exponent of the compressor in a preset calculation mode according to the relevant parameters.
After the pressure ratio of the current inlet pressure to the current outlet pressure is ensured to be in a normal working state, the relevant parameters are subjected to preset treatment to obtain a temperature polytropic index. The method comprises the steps of acquiring efficiency data of a compressor, wherein the efficiency data of the compressor is the efficiency corresponding to the target flow of the compressor; a temperature polytropic index is derived based on the efficiency data and the temperature adiabatic coefficient.
At step 403, an outbound temperature of the compressor is determined based on the temperature polytropic exponent.
In the embodiment of the present application, the processor in the computer device obtains the relevant parameters input by the technician, or directly obtains the relevant parameters stored in the memory, processes the relevant parameters to obtain the temperature polytropic exponent, and then determines the volume polytropic exponent based on the temperature polytropic exponent. Wherein, before determining the volume polytropic exponent of the compressor based on the temperature polytropic exponent, it is desirable to determine the outlet temperature of the compressor based on the temperature polytropic exponent, comprising:
a candidate speed and a candidate temperature of the compressor are obtained, wherein the candidate speed is within a preset speed range, and the candidate temperature of the compressor is within a preset temperature range. And determining a first temperature polytropic exponent corresponding to the inlet temperature of the compressor and a second temperature polytropic exponent corresponding to the candidate outlet temperature according to the candidate rotating speed, and determining the mean value of the first temperature polytropic exponent and the second temperature polytropic exponent as the temperature polytropic exponent. And determining corresponding outlet temperature according to the temperature polytropic index, the inlet temperature, the inlet pressure and the outlet pressure in the related parameters, and schematically substituting the parameters into a formula six to obtain the outlet temperature. In response to a temperature difference between the outbound temperature and the candidate outbound temperature meeting a temperature difference requirement, a volume polytropic exponent is determined based on the outbound temperature.
Formula six:
wherein, T1For compressor approach temperature, T2For compressor outlet temperature, p1For compressor inlet pressure, p2Is the compressor outlet pressure, mTIs a temperature polytropic exponent.
At step 404, a volume polytropic exponent is determined based on the outbound temperature.
In the embodiment of the present application, the operation rotation speed of the compressor is in a positive correlation with the flow rate, that is, the larger the operation rotation speed is, the larger the flow rate of the compressor is, the more the operation power of the compressor needs to be obtained, the compressor efficiency, that is, the efficiency data in step 402, may be obtained according to the efficiency-flow characteristic equation of the compressor, so when the operation power of the compressor in the current operation state is calculated, the operation rotation speed needs to be determined first. The efficiency-flow characteristic equation is a formula seven:
the formula seven: eta0＝a0+a1Q1+a2×Q1 2
Wherein eta is0Efficiency, Q, corresponding to the volume flow at the inlet of the compressor1Is the flow rate of the compressor, a0、a1And a2Are coefficients.
In an embodiment of the present application, referring to fig. 5, a method of determining an operating speed of a compressor according to a volume polytropic exponent includes:
and determining candidate rotating speeds within a preset rotating speed interval range. Illustratively, the preset rotation speed interval range may be one or more preset selectable rotation speed intervals stored in the computer device, and the processor obtains the rotation speed interval and determines the candidate rotation speed within the preset rotation speed interval range. Optionally, the preset rotation speed interval may also be obtained by inputting by a technician. Alternatively, the candidate speed may be the current rated speed of the compressor.
And determining the outlet temperature of the compressor according to the candidate rotating speed. Illustratively, the computer device in the present application obtains the inbound temperature of the compressor, and the inbound temperature may be obtained by measuring the compressor by a measuring instrument, and then transmitted to the computer device by a direct or indirect connection manner, and stored in the memory. One or more preset temperature intervals are stored in the computer device, the preset temperature intervals can also be input by a technician, and the processor determines the candidate outbound temperature in the preset temperature intervals, for example, the candidate outbound temperature is determined to be 333K.
The processor determines a first temperature polytropic exponent of the compressor according to the candidate rotating speed and the station entering temperature, namely the temperature polytropic exponent of the inlet of the compressor in the current running state, and determines a second temperature polytropic exponent of the compressor according to the candidate rotating speed and the candidate station leaving temperature, namely the temperature of the outlet of the compressor in the current running state is assumed to be the candidate station leaving temperature, and the temperature polytropic exponent of the outlet of the compressor is calculated according to the candidate station leaving temperature. There is no particular order of acquisition of the first and second temperature polytropic exponents.
The mean value of the first temperature polytropic exponent and the second temperature polytropic exponent is taken as the temperature polytropic exponent, and the outbound temperature 501 is determined according to the temperature polytropic exponent.
And determining the running rotating speed according to the volume polytropic index and the candidate rotating speed in response to the fact that the temperature difference between the outlet temperature and the preset outlet temperature meets the temperature difference requirement. In one example, the temperature difference between the outbound temperature and the preset outbound temperature meets the temperature difference requirement, that is, if the temperature difference is less than 0.1, the operating speed is determined according to the volume polytropic index and the candidate speed; if the temperature difference is not less than 0.1, the candidate outbound temperature is updated, illustratively, the candidate outbound temperature is made equal to the outbound temperature, and a new outbound temperature is determined according to the above steps.
Illustratively, the method for obtaining the volume polytropic exponent comprises the following steps: acquiring a first pressure ratio, wherein the pressure ratio is the ratio of the pressure at an outlet to the pressure at an inlet of the compressor; obtaining a density ratio, wherein the density ratio is the ratio of the density at an outlet of the compressor to the density at an inlet of the compressor; the volume polytropic exponent is obtained as the ratio of the common logarithm of the pressure ratio to the common logarithm of the density ratio.
And step 405, determining the running speed of the compressor according to the volume polytropic index.
In the embodiment of the application, after the volume polytropic exponent is obtained, the pressure head is obtained according to the volume polytropic exponent, the obtaining mode refers to formula eight, the flow rate of the compressor in the inlet state is determined according to a pressure head-flow characteristic equation, the operating rotating speed 502 is determined according to the relationship between the flow rate and the rotating speed, and the pressure head-flow characteristic equation is formula nine:
the formula eight:
wherein H is the pressure head, mvIs a volume polytropic exponent, Z1Is the compression factor of the compressor in the inlet state, Rg is the natural gas constant, T1Is the temperature at the inlet of the compressor, p1Pressure at the inlet of the compressor, p2Is the pressure at the compressor outlet.
The formula is nine: h0＝b0+b1Q1+b2×Q1 2
Wherein H0Pressure head, Q, corresponding to the volume flow at the inlet of the compressor1Is the flow rate at the inlet of the compressor, b0、b1And b2Are coefficients.
And 406, performing power conversion on the operation rotating speed to obtain the operation power of the compressor.
The above-mentioned operation power represents the power condition in the operation state corresponding to the current flow rate of the compressor.
In the embodiment of the present application, the method for performing power conversion on the operation rotation speed to obtain the operation power of the compressor includes: matching the running rotating speed with the candidate rotating speed; and responding to the fact that the rotating speed difference between the running rotating speed and the candidate rotating speed meets the rotating speed difference requirement, and performing power conversion on the running rotating speed to obtain running power.
In one example, the difference between the operating rotation speed and the candidate rotation speed meeting the rotation speed difference requirement may be that the rotation speed difference is less than 0.1, that is, if the rotation speed difference is less than 0.1, performing power conversion on the operating rotation speed to obtain the operating power; if the over-rotation speed difference is greater than 0.1, updating the candidate rotation speed, illustratively, making the candidate rotation speed equal to the operation rotation speed, and determining a new operation rotation speed again according to the steps.
In the embodiment of the application, the flow of the compressor corresponding to the operation rotating speed is determined according to the operation rotating speed, and the efficiency of the compressor, namely the first operation efficiency, is obtained according to an efficiency-flow characteristic equation by the flow of the compressor; acquiring a second operation efficiency corresponding to a transmission machine of the compressor; acquiring a third operating efficiency corresponding to a driving machine of the compressor; acquiring multi-variable energy head data and mass flow data of the compressor. And determining the operating power of the compressor according to the first operating efficiency, the second operating efficiency, the third operating efficiency, the multi-variable energy head data and the mass flow data. The above-mentioned determination formula of the operating power is formula ten:
formula ten: w is HG/(η)CηTηD)
Wherein H is multi-variable energy head data, and the unit is kJ/kg; g is mass flow data, and the unit is kg/s; etaCA first operating efficiency; etaTA second operating efficiency; etaDThe third operating efficiency.
In the embodiment of the application, the error between the running rotating speed determined by the method for estimating the energy consumption of the compressor and the actual rotating speed is less than 0.3%, and the error between the energy consumption of the compressor and the actual energy consumption obtained by the running rotating speed is less than 0.5%.
According to the energy consumption evaluation method of the centrifugal compressor, the operation rotating speed of the compressor in a certain operation state is determined through the volume polytropic exponent, and then the operation power is determined according to the operation rotating speed.
The following are embodiments of the apparatus of the present application that may be used to perform embodiments of the method of the present application. For details which are not disclosed in the embodiments of the apparatus of the present application, reference is made to the embodiments of the method of the present application.
Referring to fig. 6, fig. 6 is a block diagram illustrating an apparatus for energy consumption evaluation of a centrifugal compressor according to an exemplary embodiment of the present application. The device for energy consumption evaluation of a centrifugal compressor can be implemented as all or part of a computer device by software, hardware or a combination of both. The device includes:
the parameter determining module 610 is configured to determine a temperature polytropic exponent of the compressor in a preset calculation manner, where the temperature polytropic exponent corresponds to a temperature of a current inlet state and a temperature of an outlet state of the compressor;
the parameter determination module 610 is further configured to determine a volume polytropic exponent of the compressor based on the temperature polytropic exponent;
a power determining module 620, configured to determine an operating power of the compressor according to the volume polytropic exponent, where the operating power represents a power condition of the compressor in a current operating state;
a result determining module 630, configured to determine an energy consumption evaluation result of the compressor according to the operating power.
In an optional embodiment, the parameter determining module 610 is further configured to obtain efficiency data of a compressor, where the compressor efficiency data is an efficiency corresponding to the target flow rate of the compressor;
obtaining the temperature polytropic index based on the efficiency data and a temperature adiabatic coefficient, the temperature adiabatic coefficient corresponding to a temperature within the compressor.
In an alternative embodiment, the power determining module 620 is further configured to determine an operating speed of the compressor according to the volume polytropic exponent;
and performing power conversion on the operation rotating speed to obtain the operation power of the compressor.
In an optional embodiment, the power determining module 620 is further configured to determine a candidate rotation speed within a preset rotation speed interval range;
matching the running rotating speed with the candidate rotating speed;
and responding to the rotating speed difference between the running rotating speed and the candidate rotating speed to meet the rotating speed difference requirement, and performing power conversion on the running rotating speed to obtain the running power.
In an optional embodiment, the parameter determining module 610 is further configured to obtain an inbound temperature;
determining candidate outbound temperature within a preset temperature interval range;
determining a first temperature polytropic exponent of the compressor according to the candidate rotating speed and the station entering temperature;
determining a second temperature polytropic exponent of the compressor according to the candidate rotating speed and the candidate outbound temperature;
taking the mean of the first temperature polytropic exponent and the second temperature polytropic exponent as the temperature polytropic exponent;
determining the outbound temperature according to the temperature polytropic exponent;
determining the volume polytropic exponent based on the outbound temperature in response to a temperature difference between the outbound temperature and the candidate outbound temperature meeting a temperature difference requirement.
In an optional embodiment, the parameter determining module 610 is further configured to obtain pressure data of the compressor, where the pressure data includes an inlet pressure and an outlet pressure of the compressor;
determining density data of the compressor according to the inbound temperature and the outbound temperature;
determining the volume polytropic exponent from the pressure data and the density data.
In an optional embodiment, the parameter determining module 610 is further configured to determine a pressure ratio interval of the compressor in an operating state corresponding to the target flow rate;
acquiring current pressure ratio data of the compressor;
in response to the pressure ratio data being within a data interval range of the pressure ratio interval, determining the volume polytropic exponent from the pressure data and the density data.
In an optional embodiment, the parameter determining module 610 is further configured to obtain a maximum rotation speed, a minimum rotation speed, flow data, a surge condition rotation speed and a stagnation condition rotation speed of the compressor;
determining a first pressure ratio according to the maximum rotating speed and the flow data;
determining a second pressure ratio according to the surge working condition rotating speed and the flow data;
determining the minimum value of the first pressure ratio and the second pressure ratio as the maximum pressure ratio of the compressor;
determining a third pressure ratio according to the minimum rotating speed and the flow data;
determining a fourth pressure ratio according to the stagnation working condition rotating speed and the flow data;
determining the largest value of the third pressure ratio and the fourth pressure ratio as the minimum pressure ratio of the press;
the range between the minimum pressure ratio and the maximum pressure ratio is taken as the pressure ratio interval.
In an alternative embodiment, the power determining module 620 is further configured to obtain a first operating efficiency of the compressor according to the operating speed;
acquiring a second operation efficiency corresponding to a transmission machine of the compressor;
acquiring a third operating efficiency corresponding to a driving machine of the compressor;
acquiring multi-variable energy head data and mass flow data of the compressor;
determining an operating power of the compressor based on the first operating efficiency, the second operating efficiency, the third operating efficiency, the multi-variable head data, and the mass flow data.
In summary, the embodiment of the device determines the power condition of the compressor in a certain operation state through the volume polytropic exponent, so that the error of the energy consumption evaluation result of the compressor can be reduced, and the evaluation result can be closer to the actual result.
Other embodiments of the present application will be apparent to those skilled in the art from consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of the invention following, in general, the principles of the application and including such departures from the present disclosure as come within known or customary practice within the art to which the invention pertains. It is intended that the specification and examples be considered as exemplary only, with a true scope and spirit of the application being indicated by the following claims.
It will be understood that the present application is not limited to the precise arrangements described above and shown in the drawings and that various modifications and changes may be made without departing from the scope thereof. The scope of the application is limited only by the appended claims.
Claims (10)
1. An energy consumption evaluation method of a centrifugal compressor, which is applied to a computer device, the method comprising:
determining a temperature polytropic exponent of the compressor in a preset calculation mode, wherein the temperature polytropic exponent corresponds to the temperature of the current inlet state and the temperature of the current outlet state of the compressor;
determining a volume polytropic exponent of the compressor based on the temperature polytropic exponent;
determining the operating power of the compressor according to the volume polytropic exponent, wherein the operating power represents the power condition of the compressor in the current operating state;
and determining an energy consumption evaluation result of the compressor according to the running power.
2. The method of claim 1, wherein the determining the temperature polytropic exponent of the compressor in a preset calculation manner comprises:
obtaining efficiency data of a compressor, wherein the efficiency data of the compressor is the efficiency corresponding to the target flow of the compressor;
obtaining the temperature polytropic index based on the efficiency data and a temperature adiabatic coefficient, the temperature adiabatic coefficient corresponding to a temperature within the compressor.
3. The method of claim 1, wherein said determining an operating power of said compressor based on said volume polytropic exponent comprises:
determining the running speed of the compressor according to the volume polytropic index;
and performing power conversion on the operation rotating speed to obtain the operation power of the compressor.
4. The method of claim 3, wherein said converting the operating speed to obtain the operating power of the compressor comprises:
determining candidate rotating speeds within a preset rotating speed interval range;
matching the operating rotation speed with the candidate rotation speed;
and responding to the rotating speed difference between the running rotating speed and the candidate rotating speed to meet the rotating speed difference requirement, and performing power conversion on the running rotating speed to obtain the running power.
5. The method of any of claims 1 to 4, wherein said determining a volume polytropic exponent of the compressor based on the temperature polytropic exponent comprises:
acquiring the inbound temperature;
determining candidate outbound temperature within a preset temperature interval range;
determining a first temperature polytropic exponent of the compressor according to the candidate rotating speed and the station entering temperature;
determining a second temperature polytropic exponent of the compressor according to the candidate rotating speed and the candidate outbound temperature;
taking the mean of the first temperature polytropic exponent and the second temperature polytropic exponent as the temperature polytropic exponent;
determining the outbound temperature according to the temperature polytropic exponent;
determining the volume polytropic exponent based on the outbound temperature in response to a temperature difference between the outbound temperature and the candidate outbound temperature meeting a temperature difference requirement.
6. The method of claim 5, wherein the determining the volume polytropic exponent based on the outbound temperature comprises:
obtaining pressure data of the compressor, the pressure data including an inlet pressure and an outlet pressure of the compressor;
determining density data of the compressor according to the inbound temperature and the outbound temperature;
determining the volume polytropic exponent from the pressure data and the density data.
7. The method of claim 6, wherein determining a volume polytropic exponent of the compressor based on the pressure data and the density data comprises:
determining a pressure ratio interval of the compressor under the operation state corresponding to the target flow;
acquiring current pressure ratio data of the compressor;
in response to the pressure ratio data being within a data interval of the pressure ratio interval, determining the volume polytropic exponent from the pressure data and the density data.
8. The method of claim 7, wherein the determining the pressure ratio interval of the compressor in the operating state corresponding to the target flow rate comprises:
acquiring the maximum rotating speed, the minimum rotating speed, flow data, the rotating speed of a surge working condition and the rotating speed of a stagnation working condition of the compressor;
determining a first pressure ratio according to the maximum rotating speed and the flow data;
determining a second pressure ratio according to the surge working condition rotating speed and the flow data;
determining the minimum value of the first pressure ratio and the second pressure ratio as the maximum pressure ratio of the compressor;
determining a third pressure ratio according to the minimum rotating speed and the flow data;
determining a fourth pressure ratio according to the stagnation working condition rotating speed and the flow data;
determining the largest value of the third pressure ratio and the fourth pressure ratio as the minimum pressure ratio of the press;
the range between the minimum pressure ratio and the maximum pressure ratio is taken as the pressure ratio interval.
9. The method of claim 8, wherein said determining an operating power of said compressor based on said volume polytropic exponent further comprises:
obtaining a first operation efficiency of the compressor according to the operation rotating speed;
acquiring a second operation efficiency corresponding to a transmission machine of the compressor;
acquiring a third operating efficiency corresponding to a driving machine of the compressor;
acquiring multi-variable energy head data and mass flow data of the compressor;
determining an operating power of the compressor based on the first operating efficiency, the second operating efficiency, the third operating efficiency, the multi-variable head data, and the mass flow data.
10. An energy consumption calculation and evaluation device of a centrifugal compressor, which is applied to computer equipment and comprises:
the temperature polytropic exponent determining module is used for determining a temperature polytropic exponent of the compressor in a preset calculating mode, and the temperature polytropic exponent corresponds to the temperature of the current inlet state and the temperature of the current outlet state of the compressor;
the parameter determination module is further configured to determine a volume polytropic exponent of the compressor based on the temperature polytropic exponent;
the power determining module is used for determining the operating power of the compressor according to the volume polytropic exponent, and the operating power represents the power condition of the compressor in the current operating state;
and the result determining module is used for determining the energy consumption evaluation result of the compressor according to the running power.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011319075.8A CN114526254A (en) | 2020-11-23 | 2020-11-23 | Energy consumption evaluation method and device for centrifugal compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011319075.8A CN114526254A (en) | 2020-11-23 | 2020-11-23 | Energy consumption evaluation method and device for centrifugal compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114526254A true CN114526254A (en) | 2022-05-24 |
Family
ID=81619219
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011319075.8A Pending CN114526254A (en) | 2020-11-23 | 2020-11-23 | Energy consumption evaluation method and device for centrifugal compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114526254A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116087613A (en) * | 2023-04-07 | 2023-05-09 | 沃德传动（天津）股份有限公司 | Reciprocating compressor energy efficiency calculation system |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0932806A (en) * | 1995-07-24 | 1997-02-04 | Ooyodo Diesel Kk | Energy saving operation diagnosis for motor-driven air compressor and energy saving operation diagnosis device |
| CN103150676A (en) * | 2013-01-21 | 2013-06-12 | 江苏大学 | Energy consumption estimation method for industrial circulating water supply pump station |
| CN104895777A (en) * | 2015-05-11 | 2015-09-09 | 中国石油天然气集团公司 | Method and device for determining dynamic mechanical efficiency of compressor |
| CN204924523U (en) * | 2015-09-24 | 2015-12-30 | 合肥科迈捷智能传感技术有限公司 | Air compressor machine energy consumption evaluation system |
| CN109921499A (en) * | 2017-12-08 | 2019-06-21 | 南京德朔实业有限公司 | Power supply device and speed regulating method for fan in power supply device |
-
2020
- 2020-11-23 CN CN202011319075.8A patent/CN114526254A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0932806A (en) * | 1995-07-24 | 1997-02-04 | Ooyodo Diesel Kk | Energy saving operation diagnosis for motor-driven air compressor and energy saving operation diagnosis device |
| CN103150676A (en) * | 2013-01-21 | 2013-06-12 | 江苏大学 | Energy consumption estimation method for industrial circulating water supply pump station |
| CN104895777A (en) * | 2015-05-11 | 2015-09-09 | 中国石油天然气集团公司 | Method and device for determining dynamic mechanical efficiency of compressor |
| CN204924523U (en) * | 2015-09-24 | 2015-12-30 | 合肥科迈捷智能传感技术有限公司 | Air compressor machine energy consumption evaluation system |
| CN109921499A (en) * | 2017-12-08 | 2019-06-21 | 南京德朔实业有限公司 | Power supply device and speed regulating method for fan in power supply device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116087613A (en) * | 2023-04-07 | 2023-05-09 | 沃德传动（天津）股份有限公司 | Reciprocating compressor energy efficiency calculation system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| RU2658869C2 (en) | Estimation of health parameters in industrial gas turbines | |
| CN106050722A (en) | General characteristic curve surge control method and system based on principle of similitude | |
| CN114912371B (en) | Digital twin body modeling system and method for running stability detection of tubular pump | |
| Gravdahl et al. | Modeling of surge in free-spool centrifugal compressors: Experimental validation | |
| CN102937104A (en) | Turbine compressor test system | |
| CN106599422B (en) | Vibration simulation analysis method and device for vane pump rotor system | |
| CN114526254A (en) | Energy consumption evaluation method and device for centrifugal compressor | |
| JP4625306B2 (en) | Fluid machinery performance diagnostic apparatus and system | |
| CN113309729B (en) | Multistage axial flow compressor test monitoring method and device | |
| US20200380180A1 (en) | Method of designing and producing a turbine | |
| CN110276115B (en) | Gas path fault diagnosis method based on gas turbine blade profile parameters | |
| JP2019522143A (en) | Adaptive surge prevention control system and method | |
| JP5653786B2 (en) | Anomaly detection device | |
| Willie | Conjugate heat transfer simulation and cooling optimization of the flow inside a screw compressor | |
| Chen et al. | Gas-path component fault diagnosis for gas turbine engine: a review | |
| CN113738688A (en) | Method and device for measuring efficiency of gas compressor, terminal and storage medium | |
| Morini et al. | Acoustic and vibrational analyses on a multi-stage compressor for unstable behavior precursor identification | |
| Ogbonnaya et al. | Gas turbine engine anomaly detection through Computer simulation technique of statistical correlation | |
| CN113761679B (en) | Method and device for predicting noise of compressor | |
| Bettocchi et al. | A multi-stage compressor test facility: uncertainty analysis and preliminary test results | |
| CN118188525A (en) | Test platform and test method for performance test and evaluation verification of centrifugal pump | |
| Pöyhönen | Variable-speed-drive-based monitoring and diagnostic methods for pump, compressor, and fan systems | |
| Rajabpour et al. | Theoretical and experimental investigation of design parameter effects on the slip phenomenon and performance of a centrifugal compressor | |
| Day Towler et al. | A novel approach to surge control: high-frequency pressure variance as an indicator of impending surge in centrifugal compressors | |
| Fakhri et al. | Stationary component optimization and the resultant improvement in the performance characteristics of a radial compressor stage |
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 |