CN105091629A - Shell and tube heat exchanger and optimization method thereof - Google Patents
Shell and tube heat exchanger and optimization method thereof Download PDFInfo
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- CN105091629A CN105091629A CN201410192397.9A CN201410192397A CN105091629A CN 105091629 A CN105091629 A CN 105091629A CN 201410192397 A CN201410192397 A CN 201410192397A CN 105091629 A CN105091629 A CN 105091629A
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Abstract
The invention relates to a shell and tube heat exchanger and an optimization method thereof. The shell and tube heat exchanger comprises a shell, a heat exchange tube, a water inlet pipe and a water outlet pipe, wherein a control system and a temperature sensor are installed on the water inlet pipe, a flowmeter, a control system, a temperature sensor and an electric valve are sequentially installed on the water outlet pipe, a spiral band equivalent to the inner diameter of the heat exchange tube is provided in the heat exchange tube, and the thickness of the spiral band is 1 to 2mm. The shell and tube heat exchanger optimized by adopting the optimization method provided by the invention has the advantage that the waste of energy of the circulating water system due to the design margin of the shell and tube heat exchanger is effectively improved.
Description
Technical field
The present invention relates to the heat exchanger in industrial circulating water system field, be related specifically to a kind of shell and tube exchanger and optimization method thereof
Background technology
Shell-and-tube heat exchanger is widely used in the fields such as oil, chemical industry, power.Due to global energy crisis, in order to energy-saving and cost-reducing, the demand of industrial heat exchanger gets more and more, and the quality requirement of heat exchanger is also more and more higher.Along with the development of modern industrial technology, new technology, new technology widely use the demand must bringing high-performance, high parameter heat exchanger.And shell and tube exchanger is as water equipment the most frequently used in industrial circulating water system, the optimization of shell and tube exchanger also can play positive meaning to the energy consumption reducing industrial circulating water system.And existing shell and tube exchanger often occurs causing because of heat exchange tube wall incrustation the phenomenon that heat transfer system declines and shell and tube exchanger design margin wastes,
Summary of the invention
Of the present inventionly be to provide a kind of shell and tube exchanger and optimization method thereof, reach the effect preventing exchanger tube wall fouling and make full use of shell and tube exchanger design margin, positive meaning is played to the energy consumption reducing industrial circulating water system.
In order to reach above object, the invention provides a kind of shell and tube exchanger, comprise housing, heat exchanger tube and water-in and water-out pipeline, described inlet channel is provided with control system and temperature sensor, described outlet conduit is provided with flowmeter, control system, temperature sensor and electrically operated valve successively, have a spiral band being equivalent to heat exchanger tube internal diameter in described heat exchanger tube, the thickness of described spiral band is 1 ~ 2mm.
Above-mentioned shell and tube exchanger inserts spiral band in heat exchanger tube can make cooling water be in turbulent condition, while enhanced heat exchange, avoids precipitation of salts thing and is detained crystallization, can prevent the formation of incrustation scale, prevent exchanger tube wall fouling.
In order to make full use of shell and tube exchanger design margin, present invention also offers a kind of optimization method for above-mentioned shell and tube exchanger.Comprise the collection of each parts data of shell and tube exchanger, data analysis and equipment optimization, by the flow in the collection of each parts data and data analysis determination shell and tube exchanger actual motion.
Further, flow Q in inflow temperature T1, leaving water temperature T2, the leaving water temperature T3 of design of heat exchanger, local annual maximum wet-bulb temperature T4, flowmeter and design heat exchange amount K1 is gathered the described collection of each parts data is comprised.For the data acquisition of T1, T2, T3 and T4 by being arranged on the temperature sensor monitors on shell and tube exchanger inlet and outlet pipe lines, flow Q monitored by the flowmeter on outlet conduit.
Further, according to GB151-1999 shell and tube exchanger national standard, shell and tube exchanger heat exchange area when design generally can leave the surplus of 10% ~ 15%.Do not have the constant prerequisite of sealing factor of fouling, water in exchanger tube wall under, when heat exchanger operates in the design water yield, leaving water temperature T2 is often lower than the leaving water temperature T3 of design.Further, when design of heat exchanger, inflow temperature designs according to the annual maximum wet-bulb temperature T4 in locality, and during actual motion, inflow temperature T1 is often lower than the annual maximum wet-bulb temperature in locality.Therefore the heat exchanger actual motion Inlet and outlet water temperature difference is often less than the Inlet and outlet water temperature difference of design, belongs to inflow-rate of water turbine and run, considerably increase the energy consumption of water pump in circulation.So be necessary to adjust the actual conditions of shell and tube exchanger in carrying out practically, determine that the step of the flow of shell and tube exchanger in actual motion is as follows:
First, compare the leaving water temperature T3 of coolant-temperature gage T2 and design of heat exchanger, as T2 < T3, control system is often crossed and is fed back signal to motor-driven valve in 5 minutes, reduces 1 ° of valve opening, continues to be adjusted to T2 >=T3, as T2 >=T3, then wouldn't controlling opening of valve;
Secondly, density × (the T2-T1) × c specific heat of water calculating actual heat exchange amount K2=Q × ρ water holds, contrast with design heat exchange amount K1, as K2 > 1.05K1, control system is often crossed and is fed back signal to motor-driven valve in 5 minutes, reduces 1 ° of valve opening, continues to be adjusted to K1 < K2≤1.05K1, during as K2≤1.05K1, then without the need to adjustment.
In formula, the density of ρ water is 1000kg/m
3.
Shell and tube exchanger after the present invention optimizes, effectively improves the waste of shell and tube exchanger design margin to circulation energy consumption.
Accompanying drawing explanation
Fig. 1 is the structural representation of shell and tube exchanger of the present invention.
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described further.
As shown in Figure 1, the invention provides a kind of shell and tube exchanger, comprise housing 1, heat exchanger tube 3 and water-in and water-out pipeline 4,5, described inlet channel 4 is provided with control system 9 and temperature sensor 7, described outlet conduit 5 is provided with successively flowmeter 8, control system 9, temperature sensor 7 and electrically operated valve 6, have a spiral band 3 being equivalent to heat exchanger tube internal diameter in described heat exchanger tube 2, the thickness of described spiral band is 1 ~ 2mm.
Embodiment: the freezing train condenser that certain coke-oven plant uses is shell and tube exchanger, the inflow temperature of design tube side cooling water is 35 DEG C, and designing coolant-temperature gage T3 is 40 DEG C, and design discharge is 50l/s.Shell side is refrigerant R22, and design condensation temperature is 65 DEG C.It is 1050kW that thermal design heat exchange amount K1 is changed in shell-tube type design.During actual motion, due to valve wide open, actual water supply is 110l/s, and inflow temperature is 30 DEG C, and leaving water temperature is 32.8 DEG C, and actual heat exchange amount is close to 1300kW.Find during maintenance that fouling of heat exchangers is serious, after pickling, inflow temperature T1 is 30 DEG C, and leaving water temperature T2 is 33.4 DEG C, and actual heat exchange amount reaches 1570kW, directly causes whole refrigeration unit condensing pressure to decline, and condensation temperature reduces, and have impact on the normal production of technique side.By this technological transformation, in heat exchanger tube 3, insert spiral band 2.Mounting temperature sensor 7 on water inlet pipe and water outlet pipe 4, access PLC control system 9; On outlet pipe, 5 install electrically operated valve 6, access PLC control system 9.Temperature sensor 7 imports temperature into PLC control system 9, and control system derives 4-20mA current signal control electrically operated valve and makes corresponding adjustment.According to T2 < T3 (33.4 DEG C < 40 DEG C), control system is often crossed and is fed back signal to electrically operated valve in 5 minutes, reduces 1 ° of valve opening, continues to be adjusted to heat exchanger leaving water temperature T2=40 DEG C.Now valve opening is 35 °, and it is 38l/s that flowmeter 8 records actual flow Q.Flowmeter 8 is accessed PLC control system 9.Density × (T2-T1) × c specific heat of water according to actual heat exchange amount K2=Q flow × ρ water holds, and contrasts with design heat exchange amount K1.Now, actual heat exchange amount K2 is 1596kW, much larger than the 1050kW of design K1.According to K2 > 1.05K1, control system is often crossed and is fed back signal to electrically operated valve in 5 minutes, reduce 1 ° of valve opening, continue to be adjusted to K1 < K2≤1.05K1. now valve opening be 27 °, now, actual leaving water temperature T2=41.9 DEG C, actual flow Q are 22l/s, and actual heat exchange amount is 1098kW.The condensing pressure temperature stabilization of freezing unit, at 65 DEG C, is produced normal.By this optimal way, this heat exchanger when normally using, cleaning frequency by original January/time, be reduced to June/time, heat exchanger water consumption is reduced to 22l/s ~ 25l/s by original 110l/s.Substantially improve the scale formation of heat exchanger, reduce the water consumption of heat exchanger.
Claims (4)
1. a shell and tube exchanger, it is characterized in that: comprise housing, heat exchanger tube and water-in and water-out pipeline, described inlet channel is provided with control system and temperature sensor, described outlet conduit is provided with flowmeter, control system, temperature sensor and electrically operated valve successively, have a spiral band being equivalent to heat exchanger tube internal diameter in described heat exchanger tube, the thickness of described spiral band is 1 ~ 2mm.
2. an optimization method for shell and tube exchanger, comprises the collection of each parts data of shell and tube exchanger, data analysis and equipment optimization, it is characterized in that, by the flow in the collection of each parts data and data analysis determination shell and tube exchanger actual motion.
3. the optimization method of shell and tube exchanger according to claim 2, it is characterized in that, described comprises the flow Q in collection inflow temperature T1, leaving water temperature T2, the leaving water temperature T3 of design of heat exchanger, local annual maximum wet-bulb temperature T4, flowmeter to the collection of each parts data and designs heat exchange amount K1.
4. the optimization method of shell and tube exchanger according to claim 2, is characterized in that, determines that the step of the flow in shell and tube exchanger actual motion is as follows:
First, compare the leaving water temperature T3 of coolant-temperature gage T2 and design of heat exchanger, as T2 < T3, control system is often crossed and is fed back signal to motor-driven valve in 5 minutes, reduces 1 ° of valve opening, continues to be adjusted to T2 >=T3, as T2 >=T3, then wouldn't controlling opening of valve;
Secondly, density × (the T2-T1) × c specific heat of water calculating actual heat exchange amount K2=Q × ρ water holds, contrast with design heat exchange amount K1, as K2 > 1.05K1, control system is often crossed and is fed back signal to motor-driven valve in 5 minutes, reduces 1 ° of valve opening, continues to be adjusted to K1 < K2≤1.05K1, during as K2≤1.05K1, then without the need to adjustment.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201410192397.9A CN105091629A (en) | 2014-05-05 | 2014-05-05 | Shell and tube heat exchanger and optimization method thereof |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410192397.9A CN105091629A (en) | 2014-05-05 | 2014-05-05 | Shell and tube heat exchanger and optimization method thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114508765A (en) * | 2022-02-16 | 2022-05-17 | 扬州金桃化工设备有限公司 | Combined high-efficiency air preheater and preheating method thereof |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2101210U (en) * | 1991-09-24 | 1992-04-08 | 上海船用柴油机研究所 | High-efficient low resistant heat exchanger |
| JP2000227031A (en) * | 1999-02-05 | 2000-08-15 | Mitsubishi Heavy Ind Ltd | Air cooler for gas turbine |
| CN101718504A (en) * | 2009-11-24 | 2010-06-02 | 上海理工大学 | Method and device for controlling flexible operation of novel heat exchanger network |
-
2014
- 2014-05-05 CN CN201410192397.9A patent/CN105091629A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2101210U (en) * | 1991-09-24 | 1992-04-08 | 上海船用柴油机研究所 | High-efficient low resistant heat exchanger |
| JP2000227031A (en) * | 1999-02-05 | 2000-08-15 | Mitsubishi Heavy Ind Ltd | Air cooler for gas turbine |
| CN101718504A (en) * | 2009-11-24 | 2010-06-02 | 上海理工大学 | Method and device for controlling flexible operation of novel heat exchanger network |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114508765A (en) * | 2022-02-16 | 2022-05-17 | 扬州金桃化工设备有限公司 | Combined high-efficiency air preheater and preheating method thereof |
| CN114508765B (en) * | 2022-02-16 | 2023-02-07 | 扬州金桃化工设备有限公司 | Combined high-efficiency air preheater and preheating method thereof |
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Address after: USB era Center No. 80 Hangzhou 310012 Zhejiang province Xihu District Pingshui Street No. 1 building 17 layer Applicant after: Zhejiang annaijie Polytron Technologies Inc Address before: 310023 Hangzhou, Zhejiang Province, Xixi Road, No. 788 Huatai Industrial Park, building 31, Applicant before: HANGZHOU ENERGY TECHNOLOGY CO., LTD. |
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Application publication date: 20151125 |
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