CN109655102B - Method for measuring pressure and temperature loss of pipeline working medium based on hydraulic pump - Google Patents
Method for measuring pressure and temperature loss of pipeline working medium based on hydraulic pump Download PDFInfo
- Publication number
- CN109655102B CN109655102B CN201811296084.2A CN201811296084A CN109655102B CN 109655102 B CN109655102 B CN 109655102B CN 201811296084 A CN201811296084 A CN 201811296084A CN 109655102 B CN109655102 B CN 109655102B
- Authority
- CN
- China
- Prior art keywords
- turbine
- total
- pressure
- temperature
- calculating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
- G01D21/00—Measuring or testing not otherwise provided for
- G01D21/02—Measuring two or more variables by means not covered by a single other subclass
Abstract
The application provides a pressure and temperature loss measuring method of a pipeline working medium based on a hydraulic pump, which converts air pressure energy in a pipeline into mechanical energy through a turbine and measures the pressure loss and temperature loss of the pipeline working medium by measuring relevant parameters of the turbine.
Description
Technical Field
The application relates to the technical field of aviation, and particularly provides a method for measuring pressure and temperature loss of a pipeline working medium based on a hydraulic pump.
Background
In the existing pipeline pressure and temperature loss measuring method, collected pressure and temperature signals are converted into electric signals with the same frequency through a sensor, and the measured signals are processed into corresponding pressure and temperature values through a signal amplifier by utilizing a test data collection system. The measuring method has the defects that more sensors are required to be arranged on the circumferential section of the outlet of the pipeline, certain influence is caused on the flow of a pipeline system, and meanwhile, the installation of the sensors is not easy to measure for the pipeline with smaller outlet diameter or the pipeline with the diameter-variable characteristic because a certain volume space is required for installing the sensors.
Because the deviation that measurement system installation caused can cause certain influence to the data result, consequently there is the not enough of system measurement data precision unable assurance, only is fit for the great pipeline of export diameter moreover, just is not suitable for to the less pipeline of pipe diameter. In addition, in the measuring method, the sensor is sensitive to the ambient temperature, so that the service life of the sensor is influenced when the sensor is used for measuring in a high-temperature environment, and the application range is relatively narrow. When the pipeline pressure and temperature loss of different flowing media are measured, the method cannot be considered, and has certain limitation in application.
Disclosure of Invention
In order to solve at least one of the above technical problems, the present application provides a method for measuring pressure and temperature loss of a line working medium based on a hydraulic pump, comprising: connecting one end of a pipeline with an air source outlet provided with an adjustable flow valve, connecting the other end of the pipeline with a turbine, and connecting an output shaft of the turbine with a hydraulic pump; work is given to the unit mass flow rate of the turbine, the flow parameter of the adjustable flow valve, the inlet temperature of the turbine at the design point, the relative physical rotating speed of the turbine and the turbine front pressure of the turbine; acquiring inlet oil pressure, outlet oil pressure and flow of the hydraulic pump, and calculating actual output power of the hydraulic pump according to the inlet oil pressure, the outlet oil pressure and the flow; calculating a first output power of the turbine according to the actual output power; calculating a total inlet temperature of the turbine based on the first output power of the turbine; acquiring the total outlet temperature and the total outlet pressure of the hydraulic pump, and acquiring the inlet temperature, the relative physical rotating speed and the turbine front pressure of the turbine; calculating the relative conversion rotating speed of the turbine and the conversion flow of the turbine according to the inlet total temperature of the turbine; acquiring a turbine drop-out ratio array and an efficiency array under the relative conversion rotating speed of the turbine by adopting a Newton interpolation method on a turbine characteristic diagram; interpolating in the turbine falling pressure ratio array and the efficiency array to obtain the turbine falling pressure ratio and the efficiency of the turbine under the converted flow; calculating a second output power of the turbine according to the turbine pressure drop ratio and the efficiency; calculating a turbine work residual of the turbine according to the first output power and the second output power; judging whether the turbine work residual is smaller than a set threshold value or not; if the turbine work residual is smaller than the set threshold, calculating the total turbine inlet pressure of the turbine according to the total inlet temperature of the turbine; and calculating the total pressure loss of the pipeline outlet according to the total inlet pressure of the turbine and the total pressure of the air source outlet provided with the adjustable flow valve.
According to at least one embodiment of the present application, the method for measuring pressure loss and temperature loss of a pipeline working medium further comprises: if the turbine work residual is not smaller than the set threshold, recalculating the second output power of the turbine until the turbine work residual is smaller than the set threshold.
According to at least one embodiment of the present application, the method for measuring pressure loss and temperature loss of a pipeline working medium further comprises: adjusting the flow parameters of the adjustable flow valve, and repeating the steps to obtain the total temperature loss and the total pressure loss of the pipeline outlet under different flow parameters of the adjustable flow valve; and drawing curves of the total temperature loss and the total pressure loss of the pipeline outlet along with the change of the flow parameter of the adjustable flow valve according to the total temperature loss and the total pressure loss of the pipeline outlet.
According to at least one embodiment of the present application, calculating an actual output power of the hydraulic pump from the inlet oil pressure, the outlet oil pressure, and the flow rate includes: calculating the actual output power of the hydraulic pump according to the following formula:
Pd＝Wf*(Pout-Pin)*η，
wherein, PdFor actual output power, Pout is outlet oil pressure, Pin is inlet oil pressure, η is efficiency of the hydraulic pump, and Wf is flow.
According to at least one embodiment of the present application, calculating a first output power of the turbine from the actual output power comprises: the first output power of the turbine is obtained by interpolating values in a turbine map.
According to at least one embodiment of the present application, calculating a total inlet temperature of the turbine from the first output power of the turbine comprises: the total inlet temperature of the turbine is calculated according to the following formula:
Pt＝Wa*Lt，
wherein, PtFor the first output power, Wa is the flow parameter of the adjustable flow valve, LtFirst output power per unit mass flow of the turbine, CpTo a specific pressure heat capacity, Tt3Is the total inlet temperature of the turbine, pi is the turbine pressure drop ratio, etaTFor the expansion efficiency of the turbine, pt3Is the total pressure in front of the turbine, pt4Is the total post-turbine pressure. k is a constant.
According to at least one embodiment of the present application, calculating a relative scaled rotation speed of the turbine and a scaled flow rate of the turbine from a total inlet temperature of the turbine comprises: calculating a relative converted speed of the turbine according to the following formula:
wherein n _ cor is the relative conversion speed of the turbine, n _ r is the relative physical speed of the turbine, Tt3Is the total inlet temperature of the turbine;
calculating a converted flow rate for the turbine according to:
wherein Wa _ cor is the converted flow of the turbine, Wa is the flow parameter of the adjustable flow valve, Tt3Is the total inlet temperature, P, of the turbinet2Is the total pressure of the air source outlet.
According to at least one embodiment of the present application, calculating a turbine work residual of the turbine from the first output power and the second output power comprises: calculating the turbine work residual as follows:
E＝(Lt_new-Lt)/Lt，
wherein E is the turbine work residual, Lt_newSecond output power per unit mass flow of the turbine, LtIs the first output power per unit mass flow of the turbine.
According to at least one embodiment of the present application, calculating a total turbine inlet pressure of the turbine based on a total inlet temperature of the turbine comprises: calculating the total turbine inlet pressure of the turbine according to the following formula:
wherein Wa _ cor is the converted flow of the turbine, Wa is the flow parameter of the adjustable flow valve, Tt3The total inlet temperature of the turbine and the total turbine inlet pressure of the turbine.
According to at least one embodiment of the application, calculating the total temperature loss of the pipeline outlet according to the total inlet temperature of the turbine and the total outlet temperature of the air source provided with the adjustable flow valve comprises: the total temperature loss was calculated as follows:
ΔT＝T1-T2，
wherein, Delta T is total temperature loss amount, T1For total outlet temperature, T, of gas source provided with adjustable flow valve2Is the total inlet temperature of the turbine;
calculating the total pressure loss of the pipeline outlet according to the total inlet pressure of the turbine and the total outlet pressure of the air source provided with the adjustable flow valve, wherein the total pressure loss comprises the following steps: the total pressure loss was calculated as follows:
ΔP＝P1-P2，
wherein, the delta P is total pressure loss amount, P1For total pressure at the outlet of the gas source with adjustable flow valve, P2Is the total inlet pressure of the turbine.
According to the pressure loss and temperature loss measuring method of the pipeline working medium, pressure and temperature parameters of a pipeline outlet can be directly obtained without installing a pressure sensor and a temperature sensor in a pipeline, meanwhile, the efficiency of the pipeline can be obtained through calculation, the purposes of accurate data, high reliability, wide application range and capability of meeting pipeline loss tests of any pipe diameter and any trend are achieved, the operation is simple and convenient, and the practicability is good.
Drawings
FIG. 1 is a schematic structural diagram of a device for measuring pressure loss and temperature loss of a pipeline working medium according to an embodiment of the present application;
FIG. 2 is a first turbine map provided by an embodiment of the present application;
FIG. 3 is a second turbine map provided by an embodiment of the present application.
Wherein:
1. a gas source device; 2. an adjustable flow valve; 3. testing the pipeline; 4. a turbine; 5. a hydraulic pump; 6. a data acquisition device; 7. a power source.
Detailed Description
The present application will be described in further detail with reference to the following drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the relevant application and are not limiting of the application. It should be noted that, for convenience of description, only the portions related to the present application are shown in the drawings.
It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present application will be described in detail below with reference to the embodiments with reference to the attached drawings.
It should be noted that in the description of the present application, the terms of direction or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, which are merely for convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present application. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Furthermore, it should be noted that, in the description of the present application, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as being fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood by those skilled in the art as the case may be.
Fig. 1 is a schematic structural diagram of a device for measuring pressure loss and temperature loss of a pipeline working medium according to an embodiment of the present application.
As shown in fig. 1, the device includes a testing pipeline 3 connected with an air source device 1, an adjustable flow valve 2 is arranged at the joint of the air source device 1 and the testing pipeline 3, the air pressure energy in the testing pipeline 3 can be adjusted by adjusting the adjustable flow valve 2, a turbine 4 is arranged at the other end of the testing pipeline 3, an output shaft of the turbine 4 is connected with a hydraulic pump 5, a data acquisition device 6 is arranged on the hydraulic pump 5, so as to acquire the inlet oil pressure, the outlet oil pressure and the flow of the hydraulic pump, and a power supply 7 is further arranged on the data acquisition device 6 to supply power for the data acquisition device 6.
The outlet oil pressure, the inlet oil pressure, and the flow rate of the hydraulic pump 5 acquired by the data acquisition device 6 can be calculated to obtain the output power of the hydraulic pump 5, that is, the air pressure in the test line 3 can be converted into mechanical energy by the turbine 4, and the mechanical energy can be converted into hydraulic energy by the generator 5 connected to the turbine 4, so that the air pressure can be calculated by the calculated hydraulic energy.
The embodiment of the invention also provides a method for measuring the pressure loss and the temperature loss of the pipeline working medium, which specifically comprises the following steps:
and 101, connecting one end of a pipeline with an air source outlet provided with an adjustable flow valve, connecting the other end of the pipeline with a turbine, and connecting an output shaft of the turbine with a hydraulic pump.
In this embodiment, the amount of the gaseous medium in the gas source device entering the test line can be changed by adjusting the adjustable flow valve, i.e. the pressure energy in the test line is changed.
Step 102, the unit mass flow work of the turbine, the flow parameter of the adjustable flow valve, the inlet temperature of the turbine at the design point, the relative physical rotating speed of the turbine and the turbine front pressure of the turbine are given.
Step 103, acquiring the inlet oil pressure Pin, the outlet oil pressure Pout and the flow Wf of the hydraulic pump, and calculating the actual output power of the hydraulic pump according to the inlet oil pressure Pin, the outlet oil pressure Pout and the flow Wf.
In this embodiment, the actual output power of the hydraulic pump is calculated as follows:
Pd＝Wf*(Pout-Pin)*η，
wherein, PdFor actual output power, Pout is outlet oil pressure, Pin is inlet oil pressure, and η is efficiency of the hydraulic pump.
And 104, calculating the first output power of the turbine according to the actual output power.
In the present embodiment, the first output power of the hydraulic pump can be obtained according to the interpolation in the turbine characteristic diagrams given in fig. 2 and 3, based on the actual output power of the generator.
105, according to the first output power P of the turbinetCalculating the total inlet temperature T of the turbinet3。
In this embodiment, the total inlet temperature of the turbine is calculated as follows:
Pt＝Wa*Lt，
wherein, PtFor the first output power, Wa is the flow of the adjustable flow valveParameter, LtFirst output power per unit mass flow of the turbine, CpTo a specific pressure heat capacity, Tt3Is the total inlet temperature of the turbine, pi is the turbine pressure drop ratio, etaTFor the expansion efficiency of the turbine, pt3Is the total pressure in front of the turbine, pt4Is the total post-turbine pressure. k is a constant.
Step 106, acquiring the total outlet temperature T of the hydraulic pumpt2Total pressure of outlet Pt2Obtaining the inlet temperature T of the turbinet3_dRelative physical speed n _ r and turbine front pressure Pt4。
107, according to the total inlet temperature T of the turbinet3And calculating the relative conversion rotating speed n _ cor of the turbine and the conversion flow Wa _ cor of the turbine.
In this embodiment, the relative converted rotational speed of the turbine is calculated as follows:
wherein n _ cor is the relative conversion speed of the turbine, n _ r is the relative physical speed of the turbine, Tt3Is the total inlet temperature of the turbine;
the reduced flow rate of the turbine is calculated as follows:
wherein Wa _ cor is the converted flow of the turbine, Wa is the flow parameter of the adjustable flow valve, Tt3Is the total inlet temperature, P, of the turbinet2Is the total pressure of the air source outlet.
And step 108, acquiring a turbine falling pressure ratio array and an efficiency array of the turbine under the relative conversion rotating speed of the turbine by adopting a Newton interpolation method on the turbine characteristic diagram.
In the present embodiment, referring to fig. 2, a newton interpolation method is used on the first turbine characteristic diagram shown in fig. 2 to obtain a turbine pressure drop ratio array at the relative converted rotation speed of the turbine.
Continuing with FIG. 3, an efficiency array for the turbine at the relative scaled rotational speed is obtained using Newton's interpolation on the second turbine map shown in FIG. 3.
And step 109, interpolating in the turbine falling pressure ratio array and the efficiency array to obtain the turbine falling pressure ratio and the efficiency of the turbine under the converted flow.
And step 110, calculating second output power of the turbine according to the turbine pressure drop ratio and the efficiency.
In this embodiment, the second output power of the turbine is calculated as follows:
Pt＝Wa*Lt，
wherein, PtFor output power, Wa is the flow parameter of the adjustable flow valve, LtFirst output power per unit mass flow of the turbine, CpTo a specific pressure heat capacity, Tt3Is the total inlet temperature of the turbine, pi is the turbine pressure drop ratio, etaTFor the expansion efficiency of the turbine, pt3Is the total pressure in front of the turbine, pt4Is the total post-turbine pressure. k is a constant.
And step 111, calculating a turbine work residual of the turbine according to the first output power and the second output power.
In this embodiment, the turbine work residual is calculated as follows:
E＝(Lt_new-Lt)/Lt，
wherein E is the turbine work residual, Lt_newSecond output power per unit mass flow of the turbine, LtIs the first output power per unit mass flow of the turbine.
And step 111, judging whether the turbine work residual is smaller than a set threshold value.
In this embodiment, if the turbine work residual is determined to be smaller than the set threshold, step 112 is executed.
And 112, calculating the turbine inlet total pressure of the turbine according to the inlet total temperature of the turbine.
In this embodiment, the total turbine inlet pressure of the turbine is calculated as follows:
wherein Wa _ cor is the converted flow of the turbine, Wa is the flow parameter of the adjustable flow valve, Tt3The total inlet temperature of the turbine and the total turbine inlet pressure of the turbine.
And 113, calculating the total temperature loss of the pipeline outlet according to the total inlet temperature of the turbine and the total outlet temperature of the air source provided with the adjustable flow valve, and calculating the total pressure loss of the pipeline outlet according to the total inlet pressure of the turbine and the total pressure of the air source outlet provided with the adjustable flow valve.
In this embodiment, the total temperature loss amount is calculated as follows:
ΔT＝T1-T2，
wherein, Delta T is total temperature loss amount, T1For total temperature of air outlet with adjustable flow valve, T2Is the total inlet temperature of the turbine.
Calculating the total pressure loss of the pipeline outlet according to the total inlet pressure of the turbine and the total outlet pressure of the air source provided with the adjustable flow valve, and comprising the following steps of:
the total pressure loss was calculated as follows:
ΔP＝P1-P2，
wherein, the delta P is total pressure loss amount, P1For the total pressure, P, at the outlet of the gas source with the adjustable flow valve2Is the total inlet pressure of the turbine.
In some embodiments, the method for measuring pressure loss and temperature loss of a pipeline working medium further comprises the steps of:
step 201, judging whether the turbine work residual is smaller than a set threshold.
Step 202, if the turbine work residual is not less than the set threshold, recalculating the second output power of the turbine until the turbine work residual is less than the set threshold.
In the present embodiment, if the turbine work residual is not less than the set threshold, the method in the above embodiment is repeated, the second output power of the turbine is recalculated until the turbine work residual is less than the set threshold, and then step 112 and step 113 are executed.
In some embodiments, the method for measuring pressure loss and temperature loss of a pipeline working medium further comprises the steps of:
step 301, adjusting the flow parameters of the adjustable flow valve, and repeating the steps in the above embodiment to obtain the total temperature loss and the total pressure loss of the pipeline outlet under the flow parameters of different adjustable flow valves;
and step 302, drawing curves of the total temperature loss and the total pressure loss of the pipeline outlet along with the change of flow parameters of the adjustable flow valve according to the total temperature loss and the total pressure loss of the pipeline outlet.
The method for measuring the pressure loss and the temperature loss of the pipeline working medium provided by the embodiment of the present application is described below with reference to a specific calculation example.
Specifically, the example specifically comprises the following steps:
step 401, measuring an output power Pd of the hydraulic pump (Wf (Pout-Pin) · η ═ 32 kw;
in step 402, the total efficiency of the hydraulic pump is known to be 0.8, so that the input power of the hydraulic pump is 40 kw.
Step 403, 1.0047, air Gp; the line mass flow Wa was measured to be 0.5kg/s, the total temperature at the line inlet was 465K, and the turbine speed n was 100%.
In step 404, if t3 is 461K, then
And calibrating eta to 57.36% according to the turbine characteristic calibration diagram, and calibrating pi T to 3.51 according to the turbine characteristic calibration diagram.
Step 405, calculating turbine power
And (3) substituting k into 1.4 to obtain P which is 40.043KW, wherein the error is more than 1%, so that t3 needs to be reselected, and the fourth step is returned.
In step 406, if t3 is 460K, then
According to the turbine characteristics, eta is 57.531%, and pi T is 3.50.
Step 407, calculating turbine power
Where K is 1.4, P is 39.99999KW, and Δ (40-P)/40 is 2.5e-7, so t3 is assumed to be valid.
In step 408, the total loss in temperature of the line when the flow rate Wa was 0.5kg/s was found to be 5 k.
So far, the technical solutions of the present application have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present application is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the present application, and the technical scheme after the changes or substitutions will fall into the protection scope of the present application.
Claims (10)
1. A method for measuring pressure and temperature loss of a pipeline working medium based on a hydraulic pump is characterized by comprising the following steps:
connecting one end of a pipeline with an air source outlet provided with an adjustable flow valve, connecting the other end of the pipeline with a turbine, and connecting an output shaft of the turbine with a hydraulic pump;
work is given to the unit mass flow rate of the turbine, the flow parameter of the adjustable flow valve, the inlet temperature of the turbine at the design point, the relative physical rotating speed of the turbine and the turbine front pressure of the turbine;
acquiring inlet oil pressure, outlet oil pressure and flow of the hydraulic pump, and calculating actual output power of the hydraulic pump according to the inlet oil pressure, the outlet oil pressure and the flow;
calculating a first output power of the turbine according to the actual output power;
calculating a total inlet temperature of the turbine based on the first output power of the turbine;
acquiring the total outlet temperature and the total outlet pressure of the hydraulic pump, and acquiring the inlet temperature, the relative physical rotating speed and the turbine front pressure of the turbine;
calculating the relative conversion rotating speed of the turbine and the conversion flow of the turbine according to the inlet total temperature of the turbine;
acquiring a turbine drop-out ratio array and an efficiency array under the relative conversion rotating speed of the turbine by adopting a Newton interpolation method on a turbine characteristic diagram;
interpolating in the turbine falling pressure ratio array and the efficiency array to obtain the turbine falling pressure ratio and the efficiency of the turbine under the converted flow;
calculating a second output power of the turbine according to the turbine pressure drop ratio and the efficiency;
calculating a turbine work residual of the turbine according to the first output power and the second output power;
judging whether the turbine work residual is smaller than a set threshold value or not;
if the turbine work residual is smaller than the set threshold, calculating the total turbine inlet pressure of the turbine according to the total inlet temperature of the turbine;
and calculating the total temperature loss of the pipeline outlet according to the total temperature of the air source outlet provided with the adjustable flow valve and the total temperature of the inlet of the turbine, and calculating the total pressure loss of the pipeline outlet according to the total pressure of the air source outlet provided with the adjustable flow valve and the total pressure of the inlet of the turbine.
2. The method for measuring pressure and temperature loss of a line working medium based on a hydraulic pump according to claim 1, further comprising:
if the turbine work residual is not smaller than the set threshold, recalculating the second output power of the turbine until the turbine work residual is smaller than the set threshold.
3. The method for measuring pressure and temperature loss of a line working medium based on a hydraulic pump according to claim 2, further comprising:
adjusting the flow parameters of the adjustable flow valve, repeating the steps in claim 1, and obtaining the total temperature loss and the total pressure loss of the pipeline outlet under different flow parameters of the adjustable flow valve;
and drawing curves of the total temperature loss and the total pressure loss of the pipeline outlet along with the change of the flow parameter of the adjustable flow valve according to the total temperature loss and the total pressure loss of the pipeline outlet.
4. The hydraulic pump-based line working medium pressure and temperature loss measuring method according to any one of claims 1 to 3, wherein calculating the actual output power of the hydraulic pump from the inlet oil pressure, the outlet oil pressure, and the flow rate comprises:
calculating the actual output power of the hydraulic pump according to the following formula:
Pd＝Wf*(Pout-Pin)*η，
wherein, PdFor actual output power, Pout is outlet oil pressure, Pin is inlet oil pressure, η is efficiency of the hydraulic pump, and Wf is flow.
5. The method of measuring pressure and temperature loss of hydraulic pump-based line working medium according to any one of claims 1 to 3, wherein calculating a first output power of the turbine from the actual output power comprises:
the first output power of the turbine is obtained by interpolating values in a turbine map.
6. The method of any one of claims 1 to 3, wherein calculating a total inlet temperature of the turbine from the first output power of the turbine comprises:
the total inlet temperature of the turbine is calculated according to the following formula:
Pt＝Wa*Lt，
wherein, PtFor the first output power, Wa is the flow parameter of the adjustable flow valve, LtFirst output power per unit mass flow of the turbine, CpTo a specific pressure heat capacity, Tt3Is the total inlet temperature of the turbine, pi is the turbine pressure drop ratio, etaTFor the expansion efficiency of the turbine, pt3Is the total pressure in front of the turbine, pt4K is a constant for the total post-turbine pressure.
7. The method of any one of claims 1 to 3, wherein calculating a relative converted rotational speed of the turbine and a converted flow rate of the turbine based on the total inlet temperature of the turbine comprises:
calculating a relative converted speed of the turbine according to the following formula:
wherein n _ cor is the relative conversion rotating speed of the turbine, and n _ r is the relative physical rotating speed of the turbine，Tt3Is the total inlet temperature of the turbine;
calculating a converted flow rate for the turbine according to:
wherein Wa _ cor is the converted flow of the turbine, Wa is the flow parameter of the adjustable flow valve, Tt3Is the total inlet temperature, P, of the turbinet2Is the total pressure of the air source outlet.
8. The hydraulic pump-based line working medium pressure and temperature loss measurement method according to any one of claims 1 to 3, wherein calculating a turbine work residual of the turbine from the first output power and the second output power comprises:
calculating the turbine work residual as follows:
E＝(Lt_new-Lt)/Lt，
wherein E is the turbine work residual, Lt_newSecond output power per unit mass flow of the turbine, LtIs the first output power per unit mass flow of the turbine.
9. The method of any one of claims 1 to 3, wherein calculating a total turbine inlet pressure of the turbine based on the total inlet temperature of the turbine comprises:
calculating the total turbine inlet pressure of the turbine according to the following formula:
wherein Wa _ cor is the converted flow of the turbine, Wa is the flow parameter of the adjustable flow valve, Tt3The total inlet temperature of the turbine and the total turbine inlet pressure of the turbine.
10. The method for measuring pressure and temperature loss of line working medium based on hydraulic pump according to any of claims 1 to 3, wherein calculating total temperature loss of the line outlet according to total inlet temperature of the turbine and total outlet temperature of the air supply provided with a variable flow valve comprises:
the total temperature loss was calculated as follows:
ΔT＝T1-T2，
wherein, Delta T is total temperature loss amount, T1For total temperature of air outlet with adjustable flow valve, T2Is the total inlet temperature of the turbine;
calculating the total pressure loss of the pipeline outlet according to the total inlet pressure of the turbine and the total outlet pressure of the air source provided with the adjustable flow valve, wherein the total pressure loss comprises the following steps:
the total pressure loss was calculated as follows:
ΔP＝P1-P2，
wherein, the delta P is total pressure loss amount, P1For total pressure at the outlet of the gas source with adjustable flow valve, P2Is the total inlet pressure of the turbine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811296084.2A CN109655102B (en) | 2018-11-01 | 2018-11-01 | Method for measuring pressure and temperature loss of pipeline working medium based on hydraulic pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811296084.2A CN109655102B (en) | 2018-11-01 | 2018-11-01 | Method for measuring pressure and temperature loss of pipeline working medium based on hydraulic pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109655102A CN109655102A (en) | 2019-04-19 |
| CN109655102B true CN109655102B (en) | 2021-01-08 |
Family
ID=66110430
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811296084.2A Active CN109655102B (en) | 2018-11-01 | 2018-11-01 | Method for measuring pressure and temperature loss of pipeline working medium based on hydraulic pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109655102B (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1063402A2 (en) * | 1999-06-25 | 2000-12-27 | General Electric Company | Method of operation of industrial gas turbine for optimal performance |
| CN101749123A (en) * | 2008-11-28 | 2010-06-23 | 福特环球技术公司 | Method and device for evaluating exhaust gas temperature in motor vehicle |
| JP2012062833A (en) * | 2010-09-16 | 2012-03-29 | Honda Motor Co Ltd | Temperature estimation apparatus for aeroplane gas turbine engine |
| CN103267644A (en) * | 2012-06-28 | 2013-08-28 | 沈阳黎明航空发动机(集团)有限责任公司 | Engine performance simulation method |
| CN104462653A (en) * | 2014-11-10 | 2015-03-25 | 沈阳黎明航空发动机(集团)有限责任公司 | Engine simulation design method |
| CN105512429A (en) * | 2015-12-31 | 2016-04-20 | 中国航空工业集团公司沈阳发动机设计研究所 | Overall scheme computing method for three-shaft gas turbine |
| CN105930662A (en) * | 2016-04-26 | 2016-09-07 | 中国科学院工程热物理研究所 | Low-speed characteristic extrapolation method for gas compressor |
| CN107063362A (en) * | 2015-11-17 | 2017-08-18 | 通用电气公司 | The method and system measured for modified parameters |
| CN107315875A (en) * | 2017-06-26 | 2017-11-03 | 南京航空航天大学 | Separately it is vented three duct fanjet simulation models |
| CN108457750A (en) * | 2018-03-07 | 2018-08-28 | 贵州凯阳航空发动机有限公司 | A kind of aero-engine high-altitude high speed descends the acquisition methods of temperature controlling value after turbine |
-
2018
- 2018-11-01 CN CN201811296084.2A patent/CN109655102B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1063402A2 (en) * | 1999-06-25 | 2000-12-27 | General Electric Company | Method of operation of industrial gas turbine for optimal performance |
| CN101749123A (en) * | 2008-11-28 | 2010-06-23 | 福特环球技术公司 | Method and device for evaluating exhaust gas temperature in motor vehicle |
| JP2012062833A (en) * | 2010-09-16 | 2012-03-29 | Honda Motor Co Ltd | Temperature estimation apparatus for aeroplane gas turbine engine |
| CN103267644A (en) * | 2012-06-28 | 2013-08-28 | 沈阳黎明航空发动机(集团)有限责任公司 | Engine performance simulation method |
| CN104462653A (en) * | 2014-11-10 | 2015-03-25 | 沈阳黎明航空发动机(集团)有限责任公司 | Engine simulation design method |
| CN107063362A (en) * | 2015-11-17 | 2017-08-18 | 通用电气公司 | The method and system measured for modified parameters |
| CN105512429A (en) * | 2015-12-31 | 2016-04-20 | 中国航空工业集团公司沈阳发动机设计研究所 | Overall scheme computing method for three-shaft gas turbine |
| CN105930662A (en) * | 2016-04-26 | 2016-09-07 | 中国科学院工程热物理研究所 | Low-speed characteristic extrapolation method for gas compressor |
| CN107315875A (en) * | 2017-06-26 | 2017-11-03 | 南京航空航天大学 | Separately it is vented three duct fanjet simulation models |
| CN108457750A (en) * | 2018-03-07 | 2018-08-28 | 贵州凯阳航空发动机有限公司 | A kind of aero-engine high-altitude high speed descends the acquisition methods of temperature controlling value after turbine |
Non-Patent Citations (2)
| Title |
|---|
| 基于相似理论的燃气轮机建模技术研究;丁毅等;《航空动力学报》;20041031(第05期);第689-694页 * |
| 影响涡轮增压器涡轮端效率的几个因素;王华;《内燃机与配件》;20160531(第05期);第9-10页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109655102A (en) | 2019-04-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103149237B (en) | Wide-Reynolds-number-range plate-fin heat exchanger heat transfer and flow performance testing apparatus | |
| CN112067304B (en) | Method for measuring inlet flow of compressor in engine whole machine test | |
| AU7828101A (en) | System and method for direct non-intrusive measurement of corrected airflow | |
| Mohtar et al. | Describing uncertainties encountered during laboratory turbocharger compressor tests | |
| CN103842659B (en) | For determining the system and method for the fouling level of compressor | |
| CN110530597B (en) | Wind speed calibration system under low pressure | |
| CN109341771B (en) | Pressure and temperature loss measuring method of pipeline working medium based on generator | |
| Hajilouy-Benisi et al. | Empirical assessment of the performance characteristics in turbocharger turbine and compressor | |
| CN109655102B (en) | Method for measuring pressure and temperature loss of pipeline working medium based on hydraulic pump | |
| US20220205890A1 (en) | Device and method for fluid and equipment monitoring | |
| CN102997978A (en) | Ring chamber positive pressure flow detection device | |
| CN115525996B (en) | Turbine working blade flow characteristic rotation correction method and system | |
| CN109297540B (en) | Generator-based pipeline working medium pressure and temperature loss measuring device | |
| CN112013928A (en) | Gas meter temperature/pressure adaptability integrated detection device and method | |
| Toni et al. | Unsteady flow field measurements in an industrial centrifugal compressor | |
| Mersinligil et al. | A high temperature high bandwidth fast response total pressure probe for measurements in a multistage axial compressor | |
| CN111272236B (en) | Gas flow calculation method of gas laminar flow meter and gas laminar flow meter | |
| CN102384760A (en) | Novel calibrating device | |
| CN113932889A (en) | Intelligent fuel metering and correcting device based on turbine flowmeter | |
| CN109631982A (en) | The pressure and temperature of pipeline working media based on hydraulic pump loses measuring device | |
| CN117129043B (en) | Centralized monitoring system and monitoring method for high Wen Xuanjin flowmeter | |
| Kurz et al. | Site Performance Test Evaluation For Gas Turbine And Electric Motor Driven Compressors. | |
| Dielenschneider et al. | Some guidelines for the experimental characterization of turbocharger compressors | |
| Futral et al. | Instrumentation Used to Define Performance of Small Size, Low Power Gas Turbines | |
| CN113310636B (en) | Device and method for detecting internal leakage of valve of thermal power plant |
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 | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20200409 Address after: 100020 No. 1901 Motorcycle Building, 199 Chaoyang North Road, Chaoyang District, Beijing Applicant after: BEIJING QINGRUAN CHUANGXIANG INFORMATION TECHNOLOGY Co.,Ltd. Applicant after: SHENYANG AIRCRAFT DESIGN INSTITUTE, AVIATION INDUSTRY CORPORATION OF CHINA Address before: Thavorn street in Huanggu District of Shenyang city of Liaoning Province, No. 40 110035 Applicant before: SHENYANG AIRCRAFT DESIGN INSTITUTE, AVIATION INDUSTRY CORPORATION OF CHINA |
|
| TA01 | Transfer of patent application right | ||
| CB03 | Change of inventor or designer information |
Inventor after: Ma Song Inventor after: Chen Xuefang Inventor after: Li Jiyang Inventor after: Liu Fangxing Inventor after: Sun Xiaofeng Inventor before: Ma Song Inventor before: Huang Lei Inventor before: Zhang Zhiwei Inventor before: Liu Fangxing Inventor before: Li Jiyang |
|
| CB03 | Change of inventor or designer information | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20201221 Address after: Thavorn street in Huanggu District of Shenyang city of Liaoning Province, No. 40 110035 Applicant after: SHENYANG AIRCRAFT DESIGN INSTITUTE, AVIATION INDUSTRY CORPORATION OF CHINA Address before: 1901 MoMA building, 199 Chaoyang North Road, Chaoyang District, Beijing 100020 Applicant before: BEIJING QINGRUAN CHUANGXIANG INFORMATION TECHNOLOGY Co.,Ltd. Applicant before: SHENYANG AIRCRAFT DESIGN INSTITUTE, AVIATION INDUSTRY CORPORATION OF CHINA |
|
| TA01 | Transfer of patent application right | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |