CN111912640A - EGR cooler heat exchange performance experiment system and application method thereof - Google Patents
EGR cooler heat exchange performance experiment system and application method thereof Download PDFInfo
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- KZHJGOXRZJKJNY-UHFFFAOYSA-N dioxosilane;oxo(oxoalumanyloxy)alumane Chemical compound O=[Si]=O.O=[Si]=O.O=[Al]O[Al]=O.O=[Al]O[Al]=O.O=[Al]O[Al]=O KZHJGOXRZJKJNY-UHFFFAOYSA-N 0.000 description 1
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- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
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- Y02T10/12—Improving ICE efficiencies
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Abstract
The invention discloses an EGR cooler heat exchange performance experiment system and an application method thereof, and belongs to the technical field of EGR cooling tests. It includes: the main conveying pipeline is a closed loop circulation loop; the EGR cooler is arranged on the main conveying pipeline; the upstream of the EGR cooler is provided with a heat exchange front end pressure measuring point and a heat exchange front end temperature measuring point, and the downstream of the EGR cooler is provided with a heat exchange rear end pressure measuring point and a heat exchange rear end temperature measuring point; the circulating pump is arranged on the main conveying pipeline; the mass flow controller is arranged on the main conveying pipeline; a high-temperature heating unit and a low-temperature heating unit provided in parallel. The pressure, flow and temperature parameters can be respectively measured and controlled, meanwhile, closed-loop gas-liquid circuit circulation is adopted, and the stability of the pressure and flow after the temperature of gas-liquid changes can be effectively improved by combining with valve body control; adopt the heating gas liquid route, can effectively simulate experiment inlet air temperature to two heating system of high low temperature can directly switch the air supply when carrying out the thermal shock experiment, and the experiment gas temperature switches faster, control is more accurate.
Description
Technical Field
The invention relates to the technical field of EGR cooling tests, in particular to an EGR cooler heat exchange performance experiment system and an application method thereof.
Background
EGR generally refers to an exhaust gas recirculation system. The EGR cooler system of the automobile reduces the combustion temperature of the mixed gas in the cylinder by introducing waste gas to absorb and improve the condition of high temperature oxygen enrichment, thereby effectively inhibiting the NO of the automobile exhaustXFinally, the pollution to the atmosphere is reduced.
The heat exchange performance experiment table of the automobile EGR cooler is mainly used for heat exchange performance experiment, cold and hot shock test and boiling experiment in an EGR cooling module, so that the heat exchange performance of the EGR cooling module of an automobile is examined, experimental data are provided for the design of the cooler, and the quality of a welding line of the cooler and the quality of a pipe of the cooler can be tested by using alternating temperature. However, in the prior art, the heat exchange performance experiment table for the EGR cooler is difficult to realize in the same experiment system, flexible switching measurement and control are performed on a gas-liquid heat exchange experiment and a high-low temperature gas thermal shock experiment, and functional integrity and flexibility are poor; meanwhile, the problem of inaccurate experimental result caused by single adjustment means of parameters such as gas-liquid pressure, flow, temperature and the like due to poor stability of the internal pressure of the system exists, and the reliability and controllability are low.
In view of the above-mentioned prior art, the applicant of the present invention has made a lot of repeated and useful researches, and the final products have achieved effective results and have formed the technical solutions to be described below.
Disclosure of Invention
Therefore, the invention provides an EGR cooler heat exchange performance experiment system and an application method thereof, aiming at solving the problem that in the prior art, an experiment table aiming at the heat exchange performance of an EGR cooler is difficult to realize in the same experiment system, and the flexible switching measurement and control aiming at a gas-liquid heat exchange experiment and a high-low temperature gas thermal shock experiment are difficult to realize; and the problem that the experimental result is inaccurate because the pressure stability in the system is poor and the adjustment means for the parameters is single.
In order to achieve the above purpose, the invention provides the following technical scheme:
EGR cooler heat transfer performance experimental system includes:
a main conveying pipeline; the main conveying pipeline is a closed loop circulation loop; the main conveying pipelines of the closed loop circulation are respectively provided with at least one pipeline inlet end and at least one pipeline outlet end; and
a heat exchange experimental part; the heat exchange experimental part is an EGR cooler which is arranged on the main conveying pipeline of the closed-loop circulation; the upstream position of the EGR cooler corresponding to the total conveying pipeline along the internal flow direction is respectively provided with a heat exchange front end pressure measuring point and a heat exchange front end temperature measuring point, and the downstream position of the EGR cooler corresponding to the total conveying pipeline along the internal flow direction is respectively provided with a heat exchange rear end pressure measuring point and a heat exchange rear end temperature measuring point; the heat exchange front end pressure measuring point and the heat exchange rear end pressure measuring point are respectively provided with a pressure sensor, and the heat exchange front end temperature measuring point and the heat exchange rear end temperature measuring point are respectively provided with a temperature sensor; and
the circulating pump is a variable-frequency circulating pump; the variable-frequency circulating pump is arranged on the main conveying pipeline; and
the mass flow controller is arranged on the main conveying pipeline and is positioned at the downstream position of the pipeline inlet end corresponding to the flow direction in the main conveying pipeline; and
the high-temperature heating part is arranged on the main conveying pipeline and is positioned between the pipeline inlet end and the heat exchange experimental part, and the high-temperature heating part comprises a high-temperature heater and a first flow dividing valve; the high-temperature heater and the first flow dividing valve are arranged on the main conveying pipeline; and
a low-temperature heating section; the pipeline of the low-temperature heating part and the total conveying pipeline of the high-temperature heating part are arranged in parallel; and the low-temperature heating part includes a low-temperature heater and a second dividing valve.
On the basis of the technical scheme, the invention can be further improved as follows:
as a modified scheme of the invention, a pipeline between the pipeline inlet end and the main conveying pipeline is provided with a pressure increasing valve;
and a pressure relief valve is arranged on the pipeline between the main conveying pipeline and the pipeline outlet end.
As an improved scheme of the invention, the output ends of the pressure sensors of the heat exchange front end pressure measuring point and the heat exchange rear end pressure measuring point are electrically connected with a first PID control module; the output end of the first PID control module is electrically connected with the circulating pump, the booster valve and the pressure relief valve respectively.
As the improvement scheme of the invention, the mass flow controller is provided with a mass flow sensor, a second PID control module and a mass flow regulating valve;
the output end of the mass flow sensor is electrically connected with the input end of the second PID control module, and the output end of the second PID control module is electrically connected with the input end of the mass flow regulating valve.
As a development of the invention, the main supply line has a bypass line;
the two ends of the pipeline of the bypass pipeline are respectively and correspondingly arranged at the downstream position of the pipeline inlet end and the upstream position of the pipeline outlet end corresponding to the flow direction in the main conveying pipeline one by one; and the bypass pipeline is provided with a bypass valve, and the bypass valve is electrically connected with the output end of the second PID control module.
As the improvement scheme of the invention, the high-temperature heater is provided with a heating cavity, a plurality of baffle plates are arranged in the heating cavity, and a preset passage is reserved among the baffle plates.
As an improved scheme of the invention, the pressure measuring point at the front end of the heat exchange is positioned at the common downstream position of the high-temperature heater and the low-temperature heater corresponding to the flowing direction in the main conveying pipeline.
As an improved scheme of the invention, a liquid storage tank is arranged in the main conveying pipeline, and a float gauge and a thermometer are respectively arranged in the liquid storage tank.
As a modified scheme of the invention, the high-temperature heater is distributed with at least three thermocouples;
the low-temperature heater is distributed with at least two thermocouples.
The method for applying the EGR cooler heat exchange performance experiment system comprises the following steps:
s1: introducing gas or liquid into the main conveying pipeline through the pipeline inlet end, and enabling the pressure and the flow of the gas or liquid to reach the set range; starting a first flow dividing valve and a high-temperature heater of the high-temperature heating part;
recording the pressure and temperature detected by a heat exchange front end pressure measuring point and a heat exchange front end temperature measuring point, and recording the mass flow detected by a mass flow controller before an experiment;
s2: starting a heat exchange experimental part, recording the pressure and the temperature detected by a heat exchange rear end pressure measuring point and a heat exchange rear end temperature measuring point after a preset time, and recording the mass flow detected by a mass flow controller after an experiment;
s3: judging the heat exchange performance of the heat exchange experimental part according to the temperature difference detected by the heat exchange rear end temperature measuring point and the heat exchange front end temperature measuring point; calculating the pressure difference generated after the temperature changes according to the difference detected by the pressure measuring point at the rear end of the heat exchange and the pressure measuring point at the front end of the heat exchange; calculating the mass flow difference generated in the system after the temperature changes through the difference detected by the mass flow controller before and after the experiment;
s4: when the pressure difference is small, the pressure is adjusted by a variable-frequency circulating pump, and when the pressure difference is large, the pressure is increased by inflating a pressure increasing valve or is released by releasing the pressure by a pressure releasing valve; when the mass flow difference is small, the mass flow controller is used for adjusting, and when the mass flow difference is large, the bypass valve is opened and closed for adjusting;
s5: when a thermal shock experiment is carried out on the heat exchange experimental piece, the first flow dividing valve and the high-temperature heater of the high-temperature heating part and the second flow dividing valve and the low-temperature heater of the low-temperature heating part are respectively and alternately opened, and gas and liquid at different temperatures are rapidly and alternately switched.
The invention has the following advantages:
1. according to the scheme, the whole system adopts a plurality of PID closed-loop control loops to respectively measure and control pressure, flow and temperature parameters, and meanwhile, a closed-loop gas-liquid path circulating system is adopted, and the stability of the pressure and flow of the gas-liquid after the temperature of the gas-liquid changes can be effectively improved by combining with valve body control; adopt special heating gas liquid route, can effectively simulate experiment inlet air temperature to two heating system of high low temperature also can be when carrying out thermal shock experiment direct switch air supply, and experiment gas temperature switches faster, control is more accurate.
2. The gas is heated by adopting a resistance heating mode, the temperature control precision is high, the gas adopts an internal circulation mode, the impurities in the pipeline are few, the pipeline is free of corrosion, and the service life of the equipment is long.
3. By adopting two heating systems with high and low temperatures, the air source can be directly switched during thermal shock experiments, and the experimental gas temperature is switched more quickly and controlled more accurately.
4. The pressure is crossed low and can carry out the tonifying qi pressure boost with compressed air introduction system through the pressure-increasing valve, and the too high accessible relief valve of pressure carries out the exhaust and reduces system pressure to guarantee system pressure's relatively stable. The mass flow controller and the bypass valve act together to control the gas flow accurately and stably.
5. The gas circuit of the whole system adopts a closed loop, and the pressure is stable and easy to control; no excess gas emission, no pollution, energy conservation and environmental protection.
Drawings
In order to clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the technical solutions in the prior art will be briefly introduced, and the structures, the proportions, the sizes, and the like shown in the specification are only used for matching with the contents disclosed in the specification, so that those skilled in the art can understand and read the modifications of any structures, the changes of the proportion relationships, or the adjustments of the sizes, without affecting the functions and the achievable purposes of the present invention, and still fall within the scope of the technical contents disclosed in the present invention.
Fig. 1 is a schematic diagram of the overall system principle provided by the embodiment of the present invention.
In the drawings, the components represented by the respective reference numerals are listed below:
the system comprises a main conveying pipeline 1, a pipeline inlet end 11, a pipeline outlet end 12, a heat exchange front end pressure measuring point 13, a heat exchange rear end pressure measuring point 14, a heat exchange front end temperature measuring point 15, a heat exchange rear end temperature measuring point 16, a bypass pipeline 17, a circulating pump 2, a booster valve 3, a pressure release valve 4, a mass flow controller 5, a bypass valve 6, a high-temperature heating part 7, a first flow dividing valve 71, a high-temperature heater 72, a low-temperature heating part 8, a second flow dividing valve 81, a low-temperature heater 82 and a heat exchange experimental part 9.
Detailed Description
The present invention is described in terms of particular embodiments, other advantages and features of the invention will become apparent to those skilled in the art from the following disclosure, and it is to be understood that the described embodiments are merely exemplary of the invention and that it is not intended to limit the invention to the particular embodiments disclosed. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the present specification, the terms "upper", "lower", "left", "right" and "middle" are used for clarity of description only, and are not used to limit the scope of the present invention, and the relative relationship between the terms and the relative positions may be changed or adjusted without substantial technical change.
As shown in fig. 1, the invention provides an experimental system for heat exchange performance of an EGR cooler, which comprises a main conveying pipeline 1, a circulating pump 2, a pressure increasing valve 3, a pressure reducing valve 4, a mass flow controller 5, a bypass valve 6, a high-temperature heating part 7, a low-temperature heating part 8 and a heat exchange experimental part 9, wherein the experimental system is used for measuring and controlling pressure, flow and temperature parameters by adopting a plurality of PID closed-loop control loops, and can effectively improve the pressure and flow stability of gas and liquid after the temperature of the gas and liquid changes by adopting a closed-loop gas-liquid circuit circulating system and combining with valve body control; adopt special heating gas liquid route, can effectively simulate experiment inlet air temperature to two heating system of high low temperature also can be when carrying out thermal shock experiment direct switch air supply, and experiment gas temperature switches faster, control is more accurate. The whole system has no emission of redundant gas, no pollution, energy conservation and environmental protection. The specific settings are as follows: example 1
The main conveying pipeline 1 is a gas flow and pressure control loop, a gas path formed by the main conveying pipeline 1 adopts closed-loop circulation, and the heat exchange experimental part 9 is arranged on the main conveying pipeline 1 in the closed-loop circulation. The main conveying pipeline 1 is respectively provided with at least one pipeline inlet end 11 and at least one pipeline outlet end 12, and gas is introduced into or discharged from the main conveying pipeline 1 through the pipeline inlet end 11 and the pipeline outlet end 12 in a matching mode.
Total conveying pipeline 1 is equipped with circulating pump 2, circulating pump 2 adopts high temperature resistant frequency conversion circulating pump 2 for as the power supply of gas in total conveying pipeline 1 through high temperature resistant frequency conversion circulating pump 2, simultaneously because gas pressure and flow all receive temperature variation's influence, consequently gaseous after the heat transfer of heat transfer experiment piece 9, guarantee that gas pressure can be adjusted through frequency conversion circulating pump 2 in the pressure range of allowwing.
Preferably, a pressure increasing valve 3 is arranged on the pipeline between the pipeline inlet end 11 and the main conveying pipeline 1, and a pressure reducing valve 4 is arranged on the pipeline between the main conveying pipeline 1 and the pipeline outlet end 12, so that on the basis that pipeline closure can be guaranteed, the pressure increasing valve 3 and the pressure reducing valve 4 can adjust the pressure in the main conveying pipeline 1 when the pressure in the main conveying pipeline 1 is out of an allowable pressure range, and when the pressure in the main conveying pipeline 1 is too low, compressed air can be introduced into the main conveying pipeline 1 through the pressure increasing valve 3 to supplement air and increase pressure; when the pressure in the main conveying pipeline 1 is too high, the pressure in the main conveying pipeline 1 can be reduced by exhausting through the pressure release valve 4, so that the pressure in the main conveying pipeline 1 can be always kept in an allowable pressure range, the pressure of the whole system is ensured to be relatively stable, and the system can run safely and stably.
Specifically, a heat exchange front end pressure measuring point 13 and a heat exchange front end temperature measuring point 15 are respectively arranged at the upstream position of the main conveying pipeline 1 corresponding to the heat exchange experimental part 9 along the gas flowing direction, and a heat exchange rear end pressure measuring point 14 and a heat exchange rear end temperature measuring point 16 are respectively arranged at the downstream position corresponding to the heat exchange experimental part 9; the heat exchange front end pressure measuring point 13 and the heat exchange rear end pressure measuring point 14 are respectively provided with a pressure sensor, and the heat exchange front end temperature measuring point 15 and the heat exchange rear end temperature measuring point 16 are respectively provided with a temperature sensor, so that the temperature value and the temperature difference value of the front end and the rear end of the heat exchange experimental part 9, and the pressure value and the pressure difference value which change along with the temperature value are effectively monitored, and the temperature and the pressure are more accurately measured and controlled.
More specifically, the output ends of the pressure sensors of the heat exchange front-end pressure measurement point 13 and the heat exchange rear-end pressure measurement point 14 are electrically connected with a first PID control module, the output end of the first PID control module is respectively connected with the circulating pump 2, the booster valve 3 and the pressure release valve 4, so as to realize instant feedback control of the pressure in the main conveying pipeline 1, automatically adjust the pressure deviation amount caused by temperature change through the circulating pump 2, the booster valve 3 or the pressure release valve 4, and ensure that the pressure can fluctuate within a set range.
Preferably, the main conveying pipeline 1 is further provided with a pressure gauge, and the pressure gauge is arranged at a position downstream of the pipeline inlet end 11 corresponding to the gas flow in the main conveying pipeline 1 and used for feeding back the pressure in the main conveying pipeline 1 at the pipeline inlet end 11 in real time through the pressure gauge so as to judge whether the pressure is in a stable range.
The total conveying pipeline 1 is provided with a mass flow controller 5, the mass flow controller 5 is arranged at the downstream position of a pipeline inlet end 11 corresponding to gas flowing in the total conveying pipeline 1 and used for measuring the flow in the total conveying pipeline 1 at the pipeline inlet end 11 after heat exchange through the mass flow controller 5, and the mass flow controller can be used for adjusting when the deviation between the measured flow and the initial set flow is small.
Specifically, the mass flow controller 5 has a mass flow sensor, a second PID control module, and a mass flow control valve, wherein an output end of the mass flow sensor is electrically connected to an input end of the second PID control module, an output end of the second PID control module is electrically connected to an input end of the mass flow control valve, and the second PID control module controls the mass flow control valve to perform flow adjustment by comparing the flow detected by the mass flow sensor with an input predetermined flow range.
Preferably, the main conveying line 1 also has a bypass line 17; the two ends of the bypass pipeline 17 are respectively and correspondingly arranged at the downstream position of the pipeline inlet end 11 and the upstream position of the pipeline outlet end 12 corresponding to the gas flowing in the main conveying pipeline 1, the bypass pipeline 17 is provided with a bypass valve 6, the bypass valve 6 is electrically connected with the output end of the second PID control module, and the second PID control module is used for controlling the bypass valve 6 to effectively balance the flow difference when the range deviation between the flow detected by the mass flow sensor and the input set flow is large, so that the flow is ensured to fluctuate within the set range.
In order to ensure that the temperature of the gas detected by the heat exchange experimental part 9 is closer to the temperature of the mixed gas, a high-temperature heating part 7 is arranged between the pipeline inlet end 11 and the heat exchange experimental part 9 of the main conveying pipeline 1 and is used for heating the gas before passing through the heat exchange experimental part 9; specifically, the high-temperature heating part 7 includes a high-temperature heater 72, the high-temperature heater 72 adopts a resistance heating mode, the high-temperature heater 72 has a heating cavity, a plurality of blocking plates are arranged in the heating cavity, and a predetermined passage is reserved between the blocking plates, so that after compressed air enters from the periphery of the heating cavity, the compressed air can be preheated through heat conduction of a pipeline; after entering the heating cavity, the air flowing resistance can be increased through the baffle plate, the heat exchange time is prolonged, and the air inlet temperature of the heat exchange experimental part 9 is ensured to reach 500-900 ℃.
It should be noted that the materials of all the parts between the pipeline inlet end 11 and the heat exchange test piece 9 are matched with the pressure and the maximum temperature of 1000 ℃.
Preferably, at least three thermocouples distributed in a multipoint dispersed manner are uniformly arranged in the heating cavity, so that the temperature uniformity in the heating cavity is guaranteed to +/-3 ℃ through multipoint detection temperature calibration, and the uniformity of the detection temperature is improved.
Preferably, the heat exchange front end pressure measurement point 13 is located at a downstream position of the high temperature heater 72 corresponding to the gas flowing direction, and since the pressure of the heated compressed air with a certain flow rate can be increased, the pressure sensor arranged at the heat exchange front end pressure measurement point 13 can detect the test pressure and the pressure difference more accurately.
The input end of the resistance heating sheet of the high-temperature heater 72 is electrically connected with a third PID control module, the input end of the third PID control module is electrically connected with at least three thermocouples respectively, and the third PID control module is used for automatically controlling the temperature of the high-temperature heating part 7, so that the heating power of the high-temperature heater 72 is 60-80KW, the preset heating temperature can be effectively reached, and the heating rate and the constant temperature precision are ensured.
Example 2
In embodiment 2, the same reference numerals are given to the same components as those in embodiment 1, and the same description is omitted, but embodiment 2 differs from embodiment 1 in that the main transfer line 1 is a liquid flow rate and pressure control circuit, and the main transfer line 1 forms a liquid path and adopts a closed loop cycle.
Preferably, a liquid storage tank is arranged in the main conveying pipeline 1, a float level meter and a thermometer are respectively arranged in the liquid storage tank, the float level meter and the thermometer can be electrically connected with an external digital display device in a non-limiting mode, the liquid level change in the liquid storage tank is detected in real time through the float level meter, and the liquid temperature change in the liquid storage tank is detected in real time through the thermometer.
Example 3
In embodiment 3, the same reference numerals are given to the same structures as those in embodiment 1-2, and the same description is omitted, and embodiment 3 is modified from embodiment 1 or 2, and a low-temperature heating part 8 is further provided in the total conveying pipe 1; the pipeline in which the low-temperature heating unit 8 is located is provided in parallel with the main delivery pipeline 1 in which the high-temperature heating unit 7 is located.
Specifically, the low-temperature heating part 8 includes a second shunt valve 81 and a low-temperature heater 82, and the high-temperature heating part 7 further includes a first shunt valve 71, so that the first shunt valve 71 and the second shunt valve 81 are matched to realize rapid start switching control of high-temperature and low-temperature heating, and experimental requirements are met.
The low-temperature heater 82 adopts a resistance heating mode, and the low-temperature heater 82 is uniformly provided with at least two thermocouples which are distributed in a multi-point dispersing mode, so that the temperature equalization of the low-temperature heater 82 is guaranteed to be +/-3 ℃ through multi-point detection temperature calibration, and the uniformity of the detection temperature is improved.
Preferably, the heat exchange front end pressure measurement point 13 is located at a common downstream position of the high temperature heater 72 and the low temperature heater 82 corresponding to the gas flowing direction, and since the pressure of the compressed air with a certain flow rate is increased after the compressed air is heated, the heat exchange front end pressure measurement point 13 can detect the test pressure and the pressure difference more accurately.
The input end of the resistance heating sheet of the low-temperature heater 82 is electrically connected with a fourth PID control module, the input end of the fourth PID control module is electrically connected with at least two thermocouples respectively, and the fourth PID control module is used for automatically controlling the temperature of the low-temperature heating part 8, so that the heating power of the low-temperature heater 82 is 10-15KW, the preset heating temperature can be effectively reached within 130-180 ℃, and the heating rate and the constant temperature precision are guaranteed. This low-temperature heating part 8 is used only during thermal shock tests, i.e. by rapid alternating switching of hot and cold liquids, the adaptability of the heat exchange test piece 9 to sharp changes in ambient temperature is examined.
According to the experimental requirement, the high temperature heater 72 and the low temperature heater 82 can be selected from but not limited to iron-chromium-aluminum because the highest temperature of HRE alloy in iron-chromium-aluminum used in the atmosphere can reach 1400 ℃. The resistivity of the iron-chromium-aluminum alloy is high, and a large-size alloy material can be selected when the element is designed; and the allowable use temperature is high, the surface load of the element can be higher, and the temperature rising rate is high. The Al2O3 oxide film generated on the surface of the iron-chromium-aluminum alloy has compact structure and good adhesion performance with a substrate, and is not easy to scatter and fall to cause pollution; in addition, the resistivity and the melting point of Al2O3 are high, and the factors determine that the Al2O3 oxidation film has excellent oxidation resistance; has good corrosion resistance to sulfur-containing atmosphere and surface pollution by sulfur-containing substances.
The high-temperature heater 72 and the low-temperature heater 82 are also provided with heat insulation layers; the material of the protective layer can be selected from but not limited to a polycrystalline mullite special-shaped piece, the thermal capacity is low, the thermal conductivity is low, the thermal shock resistance is good, the size is accurate, and the hot surface of thermal equipment in various industries is specially treated and replaces imported refractory materials.
The application method of the EGR cooler heat exchange performance experiment system comprises the following steps:
s1: introducing gas or liquid into the main conveying pipeline 1 through the pipeline inlet end 11, and enabling the pressure and the flow of the gas or liquid to reach set ranges; the first flow dividing valve 71 and the high temperature heater 72 of the high temperature heating portion 7 are started;
and recording the pressure and the temperature detected by the heat exchange front end pressure measuring point 13 and the heat exchange front end temperature measuring point 15, and recording the mass flow detected by the mass flow controller 5 before the experiment.
S2: and starting the heat exchange experimental part 9, recording the pressure and the temperature detected by the heat exchange rear end pressure measuring point 14 and the heat exchange rear end temperature measuring point 16 after a preset time, and recording the mass flow detected by the mass flow controller 5 after the experiment.
S3: judging the heat exchange performance of the heat exchange experimental part 9 according to the temperature difference detected by the heat exchange rear end temperature measuring point 16 and the heat exchange front end temperature measuring point 15; calculating the pressure difference generated after the temperature changes according to the difference detected by the heat exchange rear end pressure measuring point 14 and the heat exchange front end pressure measuring point 13; the difference in mass flow rate generated in the system after the temperature change is calculated from the difference detected by the mass flow controller 5 before and after the experiment.
S4: when the pressure difference is small, the variable-frequency circulating pump 2 is used for adjusting, and when the pressure difference is large, the booster valve 3 is used for inflating and boosting or the pressure relief valve 4 is used for relieving pressure; when the mass flow difference is small, the mass flow controller 5 is used for adjusting, and when the mass flow difference is large, the bypass valve 6 is opened and closed for adjusting.
S5: when a thermal shock experiment is performed on the heat exchange experimental part 9, the first flow dividing valve 71 and the high temperature heater 72 of the high temperature heating part 7 and the second flow dividing valve 81 and the low temperature heater 82 of the low temperature heating part 8 are respectively and alternately opened, so that the gas and liquid with different temperatures can be rapidly and alternately switched.
Although the invention has been described in detail above with reference to a general description and specific examples, it will be apparent to one skilled in the art that modifications or improvements may be made thereto based on the invention. Accordingly, such modifications and improvements are intended to be within the scope of the invention as claimed.
Claims (10)
- EGR cooler heat exchange performance experimental system, its characterized in that includes:a main conveying pipeline; the main conveying pipeline is a closed loop circulation loop; the main conveying pipelines of the closed loop circulation are respectively provided with at least one pipeline inlet end and at least one pipeline outlet end; anda heat exchange experimental part; the heat exchange experimental part is an EGR cooler which is arranged on the main conveying pipeline of the closed-loop circulation; the upstream position of the EGR cooler corresponding to the total conveying pipeline along the internal flow direction is respectively provided with a heat exchange front end pressure measuring point and a heat exchange front end temperature measuring point, and the downstream position of the EGR cooler corresponding to the total conveying pipeline along the internal flow direction is respectively provided with a heat exchange rear end pressure measuring point and a heat exchange rear end temperature measuring point; the heat exchange front end pressure measuring point and the heat exchange rear end pressure measuring point are respectively provided with a pressure sensor, and the heat exchange front end temperature measuring point and the heat exchange rear end temperature measuring point are respectively provided with a temperature sensor; andthe circulating pump is a variable-frequency circulating pump; the variable-frequency circulating pump is arranged on the main conveying pipeline; andthe mass flow controller is arranged on the main conveying pipeline and is positioned at the downstream position of the pipeline inlet end corresponding to the flow direction in the main conveying pipeline; andthe high-temperature heating part is arranged on the main conveying pipeline and is positioned between the pipeline inlet end and the heat exchange experimental part, and the high-temperature heating part comprises a high-temperature heater and a first flow dividing valve; the high-temperature heater and the first flow dividing valve are arranged on the main conveying pipeline; anda low-temperature heating section; the pipeline of the low-temperature heating part and the total conveying pipeline of the high-temperature heating part are arranged in parallel; and the low-temperature heating part includes a low-temperature heater and a second dividing valve.
- 2. The experimental system for heat exchange performance of an EGR cooler according to claim 1, wherein a pressure increasing valve is arranged on a pipeline between the pipeline inlet end and the main conveying pipeline;and a pressure relief valve is arranged on the pipeline between the main conveying pipeline and the pipeline outlet end.
- 3. The experimental system for the heat exchange performance of the EGR cooler according to claim 2, wherein the output ends of the pressure sensors of the heat exchange front end pressure measurement point and the heat exchange rear end pressure measurement point are electrically connected with a first PID control module; the output end of the first PID control module is electrically connected with the circulating pump, the booster valve and the pressure relief valve respectively.
- 4. The EGR cooler heat exchange performance testing system of claim 3, wherein the mass flow controller has a mass flow sensor, a second PID control module, and a mass flow control valve;the output end of the mass flow sensor is electrically connected with the input end of the second PID control module, and the output end of the second PID control module is electrically connected with the input end of the mass flow regulating valve.
- 5. The EGR cooler heat exchange performance testing system of claim 4, wherein the main transfer line has a bypass line;the two ends of the pipeline of the bypass pipeline are respectively and correspondingly arranged at the downstream position of the pipeline inlet end and the upstream position of the pipeline outlet end corresponding to the flow direction in the main conveying pipeline one by one; and the bypass pipeline is provided with a bypass valve, and the bypass valve is electrically connected with the output end of the second PID control module.
- 6. The experimental system for heat exchange performance of an EGR cooler according to claim 1, wherein the high temperature heater has a heating chamber, the heating chamber has a plurality of baffle plates therein, and predetermined passages are left between the plurality of baffle plates.
- 7. The experimental system for heat exchange performance of the EGR cooler according to claim 1, wherein the heat exchange front end pressure measurement point is located at a common downstream position of the high-temperature heater and the low-temperature heater corresponding to the flow direction in the main conveying pipeline.
- 8. The experimental system for heat exchange performance of an EGR cooler according to claim 1, characterized in that a liquid storage tank is arranged in the main conveying pipeline, and a float gauge and a thermometer are respectively arranged in the liquid storage tank.
- 9. The experimental system for heat exchange performance of the EGR cooler according to claim 1, wherein the high temperature heater is distributed with at least three thermocouples;the low-temperature heater is distributed with at least two thermocouples.
- 10. A method of using a system for testing heat exchange performance of an EGR cooler according to any of claims 5-9, comprising the steps of:s1: introducing gas or liquid into the main conveying pipeline through the pipeline inlet end, and enabling the pressure and the flow of the gas or liquid to reach the set range; starting a first flow dividing valve and a high-temperature heater of the high-temperature heating part;recording the pressure and temperature detected by a heat exchange front end pressure measuring point and a heat exchange front end temperature measuring point, and recording the mass flow detected by a mass flow controller before an experiment;s2: starting a heat exchange experimental part, recording the pressure and the temperature detected by a heat exchange rear end pressure measuring point and a heat exchange rear end temperature measuring point after a preset time, and recording the mass flow detected by a mass flow controller after an experiment;s3: judging the heat exchange performance of the heat exchange experimental part according to the temperature difference detected by the heat exchange rear end temperature measuring point and the heat exchange front end temperature measuring point; calculating the pressure difference generated after the temperature changes according to the difference detected by the pressure measuring point at the rear end of the heat exchange and the pressure measuring point at the front end of the heat exchange; calculating the mass flow difference generated in the system after the temperature changes through the difference detected by the mass flow controller before and after the experiment;s4: when the pressure difference is small, the pressure is adjusted by a variable-frequency circulating pump, and when the pressure difference is large, the pressure is increased by inflating a pressure increasing valve or is released by releasing the pressure by a pressure releasing valve; when the mass flow difference is small, the mass flow controller is used for adjusting, and when the mass flow difference is large, the bypass valve is opened and closed for adjusting;s5: when a thermal shock experiment is carried out on the heat exchange experimental piece, the first flow dividing valve and the high-temperature heater of the high-temperature heating part and the second flow dividing valve and the low-temperature heater of the low-temperature heating part are respectively and alternately opened, and gas and liquid at different temperatures are rapidly and alternately switched.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113589682A (en) * | 2021-09-28 | 2021-11-02 | 南方电网调峰调频发电有限公司 | Main transformer cooler switching method and system |
| CN114517986A (en) * | 2022-01-28 | 2022-05-20 | 大族激光科技产业集团股份有限公司 | Load adjusting device |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20120024232A (en) * | 2010-09-06 | 2012-03-14 | 재단법인 부산테크노파크 | Performance test facilities of heat exchanger for high temperature and pressure |
| CN203101080U (en) * | 2013-01-28 | 2013-07-31 | 临海市伟达汽车部件有限公司 | EGR cooling device performance test analysis system |
| CN206726063U (en) * | 2017-03-31 | 2017-12-08 | 北京金风慧能技术有限公司 | The pressure control device and cooling device of cooling device |
| CN107462390A (en) * | 2016-06-06 | 2017-12-12 | 苏州中尧节能环保设备有限公司 | A kind of dual flow path Multifunctional mobile and heat exchange test device |
| CN110057863A (en) * | 2019-05-07 | 2019-07-26 | 西安交通大学 | A kind of high-temperature high-flow rate gas fluid interchange experimental provision and experimental method |
| CN210923044U (en) * | 2019-12-06 | 2020-07-03 | 中国航空综合技术研究所 | Verification test device for aviation fuel-air radiator temperature alternating circulation rack |
-
2020
- 2020-07-14 CN CN202010675226.7A patent/CN111912640B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20120024232A (en) * | 2010-09-06 | 2012-03-14 | 재단법인 부산테크노파크 | Performance test facilities of heat exchanger for high temperature and pressure |
| CN203101080U (en) * | 2013-01-28 | 2013-07-31 | 临海市伟达汽车部件有限公司 | EGR cooling device performance test analysis system |
| CN107462390A (en) * | 2016-06-06 | 2017-12-12 | 苏州中尧节能环保设备有限公司 | A kind of dual flow path Multifunctional mobile and heat exchange test device |
| CN206726063U (en) * | 2017-03-31 | 2017-12-08 | 北京金风慧能技术有限公司 | The pressure control device and cooling device of cooling device |
| CN110057863A (en) * | 2019-05-07 | 2019-07-26 | 西安交通大学 | A kind of high-temperature high-flow rate gas fluid interchange experimental provision and experimental method |
| CN210923044U (en) * | 2019-12-06 | 2020-07-03 | 中国航空综合技术研究所 | Verification test device for aviation fuel-air radiator temperature alternating circulation rack |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113589682A (en) * | 2021-09-28 | 2021-11-02 | 南方电网调峰调频发电有限公司 | Main transformer cooler switching method and system |
| CN114517986A (en) * | 2022-01-28 | 2022-05-20 | 大族激光科技产业集团股份有限公司 | Load adjusting device |
| CN114517986B (en) * | 2022-01-28 | 2024-05-03 | 大族激光科技产业集团股份有限公司 | Load adjusting device |
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