CN202182663U - Sub-control phase-change heat exchange system based on two-stage vapor-liquid heat exchanger - Google Patents
Sub-control phase-change heat exchange system based on two-stage vapor-liquid heat exchanger Download PDFInfo
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- CN202182663U CN202182663U CN2011202225478U CN201120222547U CN202182663U CN 202182663 U CN202182663 U CN 202182663U CN 2011202225478 U CN2011202225478 U CN 2011202225478U CN 201120222547 U CN201120222547 U CN 201120222547U CN 202182663 U CN202182663 U CN 202182663U
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- 238000004781 supercooling Methods 0.000 claims abstract description 21
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- 238000012544 monitoring process Methods 0.000 claims description 12
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- 230000007704 transition Effects 0.000 abstract description 4
- 230000001105 regulatory effect Effects 0.000 abstract description 2
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- 238000005516 engineering process Methods 0.000 description 8
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- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 5
- 239000003546 flue gas Substances 0.000 description 5
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- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 238000005260 corrosion Methods 0.000 description 3
- 230000007797 corrosion Effects 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 239000002918 waste heat Substances 0.000 description 3
- 229910021529 ammonia Inorganic materials 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
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Abstract
The utility model relates to a divide accuse phase transition heat transfer system based on two-stage vapour liquid heat exchanger. The system comprises a heat source heat exchanger (2), a cold source heat exchanger (20) and a low-temperature liquid tank (23), and also comprises a high-temperature heat exchanger (14), a low-temperature heat exchanger (22) and a high-temperature liquid tank (8); a heat source steam main pipe at the top of the heat source heat exchanger (2) is divided into two branch pipes after passing through a heat source steam exhaust regulating valve (16), the two branch pipes are respectively communicated with an upper header and a lower header of a cold source heat exchanger (20), and control systems are respectively arranged on the branch pipes; the low-temperature liquid tank (23) is communicated with the high-temperature heat exchanger (14) through a condensate liquid pipeline, the bottom of the high-temperature heat exchanger (14) is communicated with the high-temperature liquid tank (8) through a condensate liquid pipeline, and the condensate liquid pipeline at the bottom of the high-temperature liquid tank (8) is respectively communicated with the low-temperature heat exchanger (22) and the heat source heat exchanger (2). Through the utility model discloses a device has solved the overheated and the supercooling phenomenon of steam and condensate, and heat exchange efficiency further improves.
Description
Technical field
The utility model relates to the controlled augmentation of heat transfer technical field of safety, and particularly, the utility model relates to a kind of branch control phase-change heat-exchange system based on the two-stage vapour-liquid heat exchanger.
Background technology
Aspect flue gas waste heat recovery utilizes, control the corrosion of fume side heating surface and tie grey speed through different phase-change heat-exchange technical schemes, obtain effect preferably.Divide control phase-change heat-exchange technology through to low-temperature receiver heat exchange and the independent respectively control of thermal source heat exchange, realized the reliability and the precision of higher heat exchange control, improved the benefit of waste heat recovery, also make the adaptability of system applies be greatly improved.
Because the influence of flow resistance; The pressure phase transition of low-temperature receiver heat exchanger condensation must be lower than the pressure phase transition of thermal source heat exchanger evaporation, thereby the saturation temperature of the saturated evaporated liquor of temperature relatively hot source heat exchanger of the saturated condensate liquid of low-temperature receiver heat exchanger condensation certainly exists degree of supercooling.Because steam in low-temperature receiver heat exchanger condensation process, can produce liquid film at wall, the thermal resistance of liquid film makes condensate liquid produce cold can't avoiding.In addition; Because the difficult parameters such as heat exchanger area, the coefficient of heat transfer and heat transfer temperature difference under the design conditions are to adapt under the variable working condition and the actual transformation heat of Various Seasonal; The influence of factor such as level fluctuation in addition, thereby the phase-change heat-exchange process is always supervened the situation that condensate liquid is crossed the cold-peace steam superheating; The existence of supercooled liquid and overheated vapour can reduce the exchange capability of heat of phase-change heat-exchanger; Simultaneously; Also can make evaporation and heat-exchange basifacial wall surface temperature be lower than mean temperature because the existence of Natural Circulation, supercooled liquid get into the thermal source heat exchanger, safe clearance is not enough; Be easy to produce local cold end corrosion, the life-span of reducing equipment.
Because the restriction in apparatus arrangement space and equipment are installed the disunity of absolute altitude; Cause liquid level and heat exchange control disunity in the phase-change heat-exchange system; Tradition phase-change heat-exchange system is for improving difficult adaptation of difficulty that the equipment integration is had; In an application item, often need to overlap independently the phase-change heat-exchange device works alone separately more.This not only causes utilization rate of equipment and installations to reduce, and makes that also the redundancy of control system is lower; Not only the equipment total cost is higher, also makes the reliability of system reduce.
The utility model content
The purpose of the utility model is to provide a kind of branch control phase-change heat-exchange system based on the two-stage vapour-liquid heat exchanger.
Branch control phase-change heat-exchange system according to the utility model based on the two-stage vapour-liquid heat exchanger; This system comprises thermal source heat exchanger 2, low-temperature receiver heat exchanger 20 and low temperature liquid case 23; It is characterized in that; Said thermal source heat exchanger 2 is interconnected to form through steam pipe and condensate line with cold source heat exchanger 20 and divides control phase-change heat-exchange loop, on this loop, is provided with its barometric damper controlled and flow control valve
Said system also comprises high-temperature heat-exchanging 14, cryogenic heat exchanger 22 and high temperature liquid case 8;
The female pipe of the thermal source steam at said thermal source heat exchanger 2 tops is divided into two arms behind thermal source steam discharge control valve 16; Wherein the first steam pipe arm is communicated with through the upper collecting chamber of high-temperature heat-exchanging 14 with low-temperature receiver heat exchanger 20; And low-temperature receiver admission control valve 17 is set between high-temperature heat-exchanging 14 and low-temperature receiver heat exchanger 20; The second steam pipe arm be communicated with the next part case of low-temperature receiver heat exchanger 20 through low temperature liquid case 23 and cryogenic heat exchanger 22, and before low temperature liquid case 23, bypass steam flow control valve 18 is set;
Said low temperature liquid case 23 is communicated with high-temperature heat-exchanging 14 through the condensate liquid pipeline; Described high-temperature heat-exchanging 14 bottoms are communicated with high temperature liquid case 8 through the condensate liquid pipeline; The condensate liquid pipeline of high temperature liquid case 8 bottoms is divided into two arms, and wherein the first condenser pipe arm is communicated with cryogenic heat exchanger 22, and recirculation control valve 27 is set on this branch road; The second condenser pipe arm is communicated with the next part case of thermal source heat exchanger 2, and the logical liquid valve 1 of thermal source is set on this branch road.
Said thermal source heat exchanger 2 and low-temperature receiver heat exchanger 20 be two or more than,
Take parallel connection setting between said two or the above thermal source heat exchanger 2, and on this parallel condensing pipe arm, be provided with the logical liquid valve 1 of thermal source, on this parallel connection steam pipe arm, be provided with isolating valve;
Take parallel connection setting between said two or the above low-temperature receiver heat exchanger 20, and on this parallel connection steam pipe arm and this parallel condensing pipe arm, be respectively equipped with isolating valve.
Between the parallelly connected steam pipe arm isolating valve of said low-temperature receiver heat exchanger 20 and the low-temperature receiver admission control valve 17 exhaust-valve 19 is set, is used to discharge intrasystem on-condensible gas;
On the condensate liquid pipeline circulating pump 26 is set between said low temperature liquid case 23 and the high-temperature heat-exchanging 14;
On the female pipe of the condensate line of said high temperature liquid case 8 bottoms booster 5 is set;
Said high temperature liquid case 8 set inside high temperature liquid case heaters 7 are used to heat the condensate liquid in the high temperature liquid case 8, to reduce its degree of supercooling;
Said cryogenic heat exchanger 22 is provided with make-up valve 21, is used in system, adding circulation fluid working medium;
Said cryogenic heat exchanger 22 inside are provided with low temperature liquid case heater 24, are used to heat the condensate liquid in the low temperature liquid case 23, to reduce its degree of supercooling.
The intrafascicular evaporated liquor temperature sensor 3 that is provided with of the endothermic tube of said thermal source heat exchanger 2 is used for measuring and monitors thermal source heat exchanger temperature inside separately;
Between the upper collecting chamber of said thermal source heat exchanger 2 and the next part case evaporated liquor liquid level sensor 4 is set, is used to measure and monitors the inner liquid level of thermal source heat exchanger separately;
Between isolating valve and the thermal source steam discharge control valve 16 thermal source steam pressure sensor 15 is set on the said thermal source heat exchanger 2 parallelly connected steam pipe arms, is used to measure the steam pressure in the female pipe of monitoring thermal source steam;
High temperature liquid oven temperature, degree sensor 6 and high temperature liquid case liquid level sensor 9 are set on the said high temperature liquid case 8, are respectively applied for temperature and the liquid level measured in the monitoring high temperature liquid case 8;
Low temperature liquid oven temperature, degree sensor 25 is set on the said low temperature liquid case 23, is used to measure monitoring low temperature liquid case 23.
The branch control phase-change heat-exchange system's operating mode based on the two-stage vapour-liquid heat exchanger of the utility model may further comprise the steps:
Through thermal source heat exchanger 2 from external heat source absorption of fluids heat; Make its inner liquid be evaporated to steam, this steam is divided into two-way at least behind thermal source steam discharge control valve 16, wherein one the tunnel gets into high-temperature heat-exchanging 14; Carry out heat exchange with the condensate liquid that gets into high-temperature heat-exchanging 14 from low temperature liquid case 23; With the degree of superheat of reduction steam and the degree of supercooling of condensate liquid, the steam after heat exchange gets into low-temperature receiver heat exchanger 20 and is condensed into condensate liquid, simultaneously heat is discharged to the external source fluid; Other one road steam gets into the next part case of low-temperature receiver heat exchanger 20 through bypass steam flow control valve 18, low temperature liquid case 23 and low temperature heat exchanger 22; Be advanced into the condensate liquid generation heat exchange that gets into low temperature liquid casees 23 with the low temperature heat exchanger 22 of passing through down in the process of next part case on this steam; Heat is emitted in the condensation of part steam, has reduced the degree of supercooling of condensate liquid simultaneously; The part that this steam does not condense gets into the 20 back condensations of low-temperature receiver heat exchanger and emits heat, with the degree of supercooling of continuation reduction condensate liquid,
Saidly get into the condensate liquid degree of supercooling that obtains after the condensate heat exchange of high-temperature heat-exchangings 14 from low temperature liquid case 23 and reduce; This condensate liquid is divided into two-way behind high temperature liquid case 8; Wherein one the tunnel get into thermal source heat exchanger 2 the next part case, other one the tunnel gets into low temperature heat exchangers 22 through recirculation control valve 27.
Thermal source heat exchanger 2 steam that the absorption heat produces from the outside through parallel connection is two-way; Two-way steam is incorporated in the female pipe of steam pipe behind the arm isolating valve; Through 16 controls of thermal source steam discharge control valve; The low-temperature receiver admission control valve 17 and 18 controls of bypass steam flow control valve that are provided with through the steam pipe arm through aforementioned steam branch pipe respectively then are in the low-temperature receiver heat exchanger 20 of entering parallel connection
Condensate liquid in the high temperature liquid case 8 through logical liquid valve 1 control of thermal source, gets into the thermal source heat exchanger 2 of parallel connection through a condensate liquid branch road, and condensate liquid through 27 controls of recirculation control valve, gets into low temperature heat exchanger 22 through another branch road.
Said high-temperature heat exchanger 14 is direct contact heat exchanger or surface-type heat exchanger.
The aperture control method of the logical liquid valve 1 of said thermal source is:
The aperture of the logical liquid valve 1 of thermal source is controlled according to the measuring-signal of evaporated liquor liquid level sensor 4; When the liquid level that records when evaporated liquor liquid level sensor 4 is higher than evaporated liquor liquid level setting value; The logical liquid valve of thermal source turns down, on the contrary open big, to keep the consistent of this liquid level and this setting value.
The control method of the aperture of thermal source steam discharge control valve 16 is:
The aperture of thermal source steam discharge control valve 16 is carried out Comprehensive Control according to the measurement signal value of thermal source steam pressure sensor 15 and evaporated liquor temperature sensor 3; After the control system carries out comprehensive computing to measurement signal value; Output is to the aperture control instruction of thermal source steam discharge control valve 16, consistent with the setting value that keeps this measurement signal value and control system;
When the deviation of this measurement signal value of this measurement signal value and respective settings value during greater than the deviation setting value; Forbid that with sending booster 5 circulating pumps 26 start the instruction of operation, standard-sized sheet recirculation control valve 27, the logical liquid valve 1 of thermal source, the water of system all is discharged into low temperature liquid case 23.
When the steam pressure of thermal source steam pressure sensor 15 measurements and the setting value generation deviation of thermal source steam pressure, then control the aperture of the corresponding adjusting barometric damper of system, should move deviation to correct, measured value and setting value are consistent.
The aperture control method of low-temperature receiver admission control valve 17 and bypass steam flow control valve 18 is:
The aperture of low-temperature receiver admission control valve 17 and bypass steam flow control valve 18 is controlled through the measuring-signal of low temperature liquid oven temperature, degree sensor 25;
When the measured value of low temperature liquid oven temperature, degree sensor 25 is lower than low temperature liquid case 23 desired temperatures; The aperture of low-temperature receiver admission control valve 17 reduces; The aperture of the steam flow of bypass simultaneously control valve 18 is opened greatly; So that more thermal source steam and condensate liquid generation countercurrent flow, the temperature of raising condensate liquid, the degree of supercooling of reduction condensate liquid;
The deviate that is lower than low temperature liquid case 23 desired temperatures when the measured value of low temperature liquid oven temperature, degree sensor 25 will be sent alarm signal greater than setting value for the moment, and prompting starts low temperature liquid case heater 24 to reduce this deviation; When this deviate further is increased to greater than setting value two, sends and forbid that circulating pump 26 starts the instruction of operation.
The control method of recirculation control valve 27 apertures is:
The liquid level signal that the aperture of recirculation control valve 27 is measured through high temperature liquid case liquid level sensor 9 is controlled, to keep high temperature liquid case 8 level gauging values consistent with high temperature liquid case 8 liquid level setting values one;
When high temperature liquid case level gauging value is lower than high temperature liquid case liquid level setting value for the moment, the aperture of recirculation control valve 27 is opened greatly, otherwise turns down, and when the measured value of high temperature liquid case liquid level sensor 9 is lower than setting value two, forbids that with sending booster 5 starts the instruction that moves;
The deviate that is lower than high temperature liquid oven temperature, degree setting value when the measured value of high temperature liquid oven temperature, degree sensor 6 will be sent alarm signal greater than setting value for the moment, and prompting starts high temperature liquid case heater 7 to reduce this deviation; When this deviate further was increased to greater than setting value two, the instruction with sending standard-sized sheet recirculation control valve 27 all was discharged into low temperature liquid case 23 with water.
According to the utility model with the specific embodiment, the forming and working method is of the utility model based on the branch control phase-change heat-exchange system of two-stage vapour-liquid heat exchanger:
The thermal source heat exchanger package is composed in parallel by a plurality of thermal source heat exchangers; Compose in parallel by two thermal source heat exchangers 2 like thermal source heat exchanger package among Fig. 1; Two thermal source heat exchangers 2 are connected with the logical liquid valve 1 of thermal source respectively at lower collecting box; Export upper header separately and be connected with steam shut-off valve (not shown) respectively, close logical liquid valve of thermal source heat exchanger thermal source separately and shut-off valve and can make this thermal source heat exchanger from the thermal source heat exchanger package, isolate.
The thermal source heat exchanger absorbs the heat of thermal source heat release fluid flue gas (heat source fluid also can be production technology tail gas etc.) from the outside; (the internal system cycle fluid is a water to make its inner evaporated liquor; Also can use freon, ammonia etc.) be evaporated to steam; The steam that each thermal source heat exchanger produces is divided into two-way through compiling the female pipe of entering thermal source steam behind the aforementioned steam shut-off valve again after being installed in the thermal source steam discharge control valve 16 on the female pipe of this thermal source steam.
This thermal source steam wherein one the tunnel gets into low temperature liquid case 23 behind bypass steam flow control valve 18; Get into low temperature heat exchanger 22 and low-temperature receiver heat exchanger 20 lower collecting box successively by connecting line afterwards; This steam is at the heat transferred low-temperature receiver heat recipient fluid of low-temperature receiver heat exchanger 20 with release; Be condensed into condensate liquid simultaneously, return successively again by aforementioned connecting line from low-temperature receiver heat exchanger 20 lower collecting box then and get into low temperature heat exchanger 22 and low temperature liquid case 23.The aforementioned steam that behind bypass steam flow control valve 18, gets into low temperature liquid case 23; By low temperature liquid case 23 in low-temperature receiver heat exchanger 20 flow process; Carrying out heat exchange with aforementioned condensate liquid always; Steam is cooled and part is condensed, and emits the aforementioned condensate liquid of heat simultaneously, has reduced the degree of supercooling of condensate liquid.
Another road of this thermal source steam behind the thermal source steam discharge control valve 16 gets into high-temperature heat exchanger 14 and carries out heat exchange.High-temperature heat exchanger 14 can also can be surface-type heat exchanger for direct contact heat exchanger, and the steam after high-temperature heat exchanger 14 heat exchange has reduced the degree of superheat, behind the low-temperature receiver admission control valve 17 of flowing through again, gets into the upper header of low-temperature receiver heat exchanger 20.
This steam with the heat transferred low-temperature receiver heat recipient fluid that discharges, is condensed into condensate liquid at low-temperature receiver heat exchanger 20 simultaneously, gets into low temperature heat exchanger 22 and low temperature liquid case 23 from low-temperature receiver heat exchanger 20 lower collecting box successively by aforementioned connecting line then.This condensate liquid is at low-temperature receiver heat exchanger 20, low temperature heat exchanger 22 and flow in the connecting line and equipment of low temperature liquid case 23; Can get into the steam heat-exchanging of low-temperature receiver heat exchanger 20 with the aforementioned bypass steam flow control valve 18 of flowing through, low temperature liquid case 23, low temperature heat exchanger 22 backs; Through this countercurrent flow process, condensate liquid has reduced degree of supercooling.
The condensate liquid that flows out from low temperature liquid case 23 gets into high-temperature heat exchanger 14 after circulating pump 26 boosts, with the steam heat-exchanging of aforementioned entering high-temperature heat exchanger 14, reduced degree of supercooling through this condensate liquid of heat exchange, gets into high temperature liquid case 8 afterwards.
The condensate liquid that flows out from high temperature liquid case 8 is divided into two-way after booster 5 boosts.Wherein one the tunnel turn back to low temperature liquid case 23 through recirculation control valve 27, low temperature heat exchanger 22 successively; Another road gets into the lower collecting box of the thermal source heat exchanger 2 of two parallel connections respectively via the logical liquid valve 1 of thermal source, at thermal source heat exchanger heat absorption becoming evaporated liquor.This evaporated liquor heat absorption evaporation back gets into thermal source heat exchanger upper header and begins new heat transfer cycle.
The advantage of the utility model is:
The utility model will evaporate the independent separately respectively control of phase transition parameter of heat absorption and condensation heat release.Connecting line and equipment between evaporative phase-change equipment and the condensation phase transformation equipment have adopted the control valve isolation, and do not have the disturbing influence of miscellaneous equipment between evaporative phase-change equipment and the control valve, divide the control more reliable performance.
The utility model adopts the combination of multi-parameter to implement polynary, multi-level control, and controlled parameter does not receive that the Cooling and Heat Source parameter distribution is inhomogeneity to be influenced, and uniformity is better.Because control characteristic is better, control accuracy and reliability are higher.Phase-change heat-exchange saturation temperature fluctuating range is little in the thermal source heat exchanger, the fluctuation time short, can significantly reduce the cold end corrosion probability of thermal source heat exchanger tube.
The utility model reduces condensate liquid degree of supercooling and steam superheat through high low temperature two-stage heat exchanger, makes heat exchange efficiency be improved, and the wall temperature up and down of thermal source heat exchanger is uniformity more, and security and economy are better.
The branch control phase-change heat-exchange technology of the utility model is through device packets, substep control; Can break away from the restriction of installing space and absolute altitude; More convenient combination and layout of carrying out heat transmission equipment, the integration of system is higher, and cost that can be lower improves the redundancy of utilization rate of equipment and installations and control system.
Because the heat transfer technology of the utility model can be controlled the heat exchanger tube wall temperature more accurately, more evenly, reliably; Not only improved the life-span of heat exchange equipment; Also comparable other technology reduces heat exchanger tube wall temperature safe clearance; The reduction of flue gas exhaust gas temperature is more, reclaim more heats, higher energy-saving and emission-reduction benefit is arranged.
The utility model can be regardless of season through the intelligentized grouping of heat exchanger, substep control, multiple security monitoring measure and assistant heating measure etc., starts to the stoppage in transit overall process from unit and carries out flue gas waste heat recovery utilization efficiently.
Description of drawings
Fig. 1 is the branch control phase-change heat-exchange system schematic of the utility model based on the two-stage vapour-liquid heat exchanger.
The accompanying drawing sign
1, the logical liquid valve 2 of thermal source, thermal source heat exchanger 3, evaporated liquor temperature sensor
4, evaporated liquor liquid level sensor 5, booster 6, high temperature liquid oven temperature, degree sensor
7, high temperature liquid case heater 8, high temperature liquid case 9, high temperature liquid case liquid level sensor
14, high-temperature heat exchanger 15, thermal source steam pressure sensor 16, thermal source steam discharge control valve
17, low-temperature receiver admission control valve 18, bypass steam flow control valve 19, exhaust-valve
20, low-temperature receiver heat exchanger 21, make-up valve 22, low temperature heat exchanger
23, low temperature liquid case 24, low temperature liquid case heater 25, low temperature liquid oven temperature, degree sensor
26, circulating pump 27, recirculation control valve
The specific embodiment
Below in conjunction with Fig. 1 system's composition, the course of work and the characteristic of the branch control phase-change heat-exchange technology of the utility model are further explained:
The thermal source heat exchanger package is composed in parallel by a plurality of thermal source heat exchangers; Compose in parallel by two thermal source heat exchangers 2 like thermal source heat exchanger package among Fig. 1; Two thermal source heat exchangers 2 are connected with the logical liquid valve 1 of thermal source respectively at lower collecting box; Export upper header separately and be connected with steam shut-off valve (not shown) respectively, close logical liquid valve of thermal source heat exchanger thermal source separately and shut-off valve and can make this thermal source heat exchanger from the thermal source heat exchanger package, isolate.
The thermal source heat exchanger absorbs the heat of thermal source heat release fluid flue gas (heat source fluid also can be production technology tail gas etc.) from the outside; (the internal system cycle fluid is a water to make its inner evaporated liquor; Also can use freon, ammonia etc.) be evaporated to steam; The steam that each thermal source heat exchanger produces is divided into two-way through compiling the female pipe of entering thermal source steam behind the aforementioned steam shut-off valve again after being installed in the thermal source steam discharge control valve 16 on the female pipe of this thermal source steam.
This thermal source steam wherein one the tunnel gets into low temperature liquid case 23 behind bypass steam flow control valve 18; Get into low temperature heat exchanger 22 and low-temperature receiver heat exchanger 20 lower collecting box successively by connecting line afterwards; This steam is at the heat transferred low-temperature receiver heat recipient fluid of low-temperature receiver heat exchanger 20 with release; Be condensed into condensate liquid simultaneously, return successively again by aforementioned connecting line from low-temperature receiver heat exchanger 20 lower collecting box then and get into low temperature heat exchanger 22 and low temperature liquid case 23.The aforementioned steam that behind bypass steam flow control valve 18, gets into low temperature liquid case 23; By low temperature liquid case 23 in low-temperature receiver heat exchanger 20 flow process; Carrying out heat exchange with aforementioned condensate liquid always; Steam is cooled and part is condensed, and emits the aforementioned condensate liquid of heat simultaneously, has reduced the degree of supercooling of condensate liquid.
Another road of this thermal source steam behind the thermal source steam discharge control valve 16 gets into high-temperature heat exchanger 14 and carries out heat exchange.High-temperature heat exchanger 14 can also can be surface-type heat exchanger for direct contact heat exchanger, and the steam after high-temperature heat exchanger 14 heat exchange has reduced the degree of superheat, behind the low-temperature receiver admission control valve 17 of flowing through again, gets into the upper header of low-temperature receiver heat exchanger 20.
This steam with the heat transferred low-temperature receiver heat recipient fluid that discharges, is condensed into condensate liquid at low-temperature receiver heat exchanger 20 simultaneously, gets into low temperature heat exchanger 22 and low temperature liquid case 23 from low-temperature receiver heat exchanger 20 lower collecting box successively by aforementioned connecting line then.This condensate liquid is at low-temperature receiver heat exchanger 20, low temperature heat exchanger 22 and flow in the connecting line and equipment of low temperature liquid case 23; Can get into the steam heat-exchanging of low-temperature receiver heat exchanger 20 with the aforementioned bypass steam flow control valve 18 of flowing through, low temperature liquid case 23, low temperature heat exchanger 22 backs; Through this countercurrent flow process, condensate liquid has reduced degree of supercooling.
The condensate liquid that flows out from low temperature liquid case 23 gets into high-temperature heat exchanger 14 after circulating pump 26 boosts, with the steam heat-exchanging of aforementioned entering high-temperature heat exchanger 14, reduced degree of supercooling through this condensate liquid of heat exchange, gets into high temperature liquid case 8 afterwards.
The condensate liquid that flows out from high temperature liquid case 8 is divided into two-way after booster 5 boosts.Wherein one the tunnel turn back to low temperature liquid case 23 through recirculation control valve 27, low temperature heat exchanger 22 successively; Another road gets into the lower collecting box of the thermal source heat exchanger 2 of two parallel connections respectively via the logical liquid valve 1 of thermal source, at thermal source heat exchanger heat absorption becoming evaporated liquor.This evaporated liquor heat absorption evaporation back gets into thermal source heat exchanger upper header and begins new heat transfer cycle.
Aforementioned low-temperature receiver heat exchanger 20 can constitute the low-temperature receiver heat exchanger package by the many groups of heat exchanger grouping parallel connections of installing the entry and exit separation valve door additional, and the per minute group of parallel connection all can make it to isolate with common header system through closing the entry and exit separation valve door.
Evaporated liquor temperature sensor 3 is installed on the thermal source heat exchanger, is used for measuring monitoring thermal source heat exchanger temperature inside separately.
Evaporated liquor liquid level sensor 4 is installed on the thermal source heat exchanger 2, is used to measure monitor the inner liquid level of thermal source heat exchanger separately.
Thermal source steam pressure sensor 15 is installed on the female pipe of thermal source steam before the thermal source steam discharge control valve 16, is used to measure the steam pressure in the female pipe of monitoring thermal source steam.
High temperature liquid oven temperature, degree sensor 6 and high temperature liquid case liquid level sensor 9 are installed on the high temperature liquid case 8, are respectively applied for temperature and the liquid level measured in the monitoring high temperature liquid case 8; Be installed in high temperature liquid case heater 7 on the high temperature liquid case 8 and can be used for condensate temperatures in the high temperature liquid case 8 and cross when low, heat this condensate liquid to reduce its degree of supercooling.
Low temperature liquid oven temperature, degree sensor 25 and low temperature liquid case heater 24 are installed on the low temperature liquid case 23, are respectively applied for temperature and the condensate temperature in low temperature liquid case 23 measured in the monitoring low temperature liquid case 23 and cross when hanging down, heat this condensate liquid to reduce its degree of supercooling.
The heat exchanger that exhaust-valve 19 is installed in low-temperature receiver admission control valve 17 and low-temperature receiver heat exchanger 20 divides into groups to be used to discharge intrasystem on-condensible gas on the female pipe of steam between the inlet separation valve door.
Make-up valve 21 is installed on the low temperature liquid case heater 24, is used in system, adding and replenishment cycles liquid working medium.
The operation control course of work and the characteristic of system are:
The aperture of the logical liquid valve 1 of thermal source can be controlled according to the measuring-signal of evaporated liquor liquid level sensor 4 respectively; When the liquid level that records when the evaporated liquor liquid level sensor is higher than evaporated liquor liquid level setting value; The logical liquid valve of thermal source turns down, on the contrary open big, to keep the consistent of this liquid level and this setting value.
The aperture of thermal source steam discharge control valve 16 can be carried out Comprehensive Control according to the measuring-signal of thermal source steam pressure sensor 15 and evaporated liquor temperature sensor 3; After the control system carried out comprehensive computing to measuring-signal, output was to the aperture control instruction of thermal source steam discharge control valve 16.The measuring-signal of evaporated liquor temperature sensor compares; Smaller value of the two or mean value are as being controlled parameter; Control computing with the setting value of thermal source evaporated liquor temperature; The output signal of result of calculation controls to adjust the aperture of thermal source steam discharge control valve 16, is controlled the consistent of parameter and this thermal source evaporated liquor desired temperature to keep this.
If this deviation of being controlled parameter and this thermal source evaporated liquor desired temperature is during greater than setting value, forbid that with sending circulating pump 26 starts the instruction that liquid valve 1 is led in operation, standard-sized sheet recirculation control valve 27, thermal source, the water of system all is discharged into low temperature liquid case 23.
When the steam pressure of thermal source steam pressure sensor 15 measurements and the setting value generation deviation of thermal source steam pressure, then control the aperture of the corresponding adjusting barometric damper of system, should move deviation to correct, measured value and setting value are consistent.
The aperture of low-temperature receiver admission control valve 17 and bypass steam flow control valve 18 is controlled according to the measuring-signal of low temperature liquid oven temperature, degree sensor 25; When the measured value of low temperature liquid oven temperature, degree sensor 25 is lower than low temperature liquid oven temperature, degree setting value; The aperture of low-temperature receiver admission control valve 17 reduces, and the aperture of the steam flow of bypass simultaneously control valve 18 is opened greatly, so that more thermal source steam and condensate liquid generation countercurrent flow; Improve the temperature of condensate liquid, reduce the degree of supercooling of condensate liquid.
The deviate that is lower than low temperature liquid oven temperature, degree setting value when the measured value of low temperature liquid oven temperature, degree sensor 25 will be sent alarm signal greater than setting value for the moment, and whether prompting drops into low temperature liquid case heater 24 to reduce this deviation; When this deviate further is increased to greater than setting value two, forbid that with sending circulating pump 26 starts the instruction of operation.
The liquid level signal that the aperture of recirculation control valve 27 is measured according to high temperature liquid case liquid level sensor 9 is controlled, to keep the consistent of high temperature liquid case level gauging value and high temperature liquid case liquid level setting value one.When high temperature liquid case level gauging value is lower than high temperature liquid case liquid level setting value for the moment, the aperture of recirculation control valve 27 is opened greatly, otherwise turns down.When the measured value of high temperature liquid case liquid level sensor 9 is lower than setting value two, forbid that with sending booster 5 starts the instruction of operation.
The deviate that is lower than high temperature liquid oven temperature, degree setting value when the measured value of high temperature liquid oven temperature, degree sensor 6 will be sent alarm signal greater than setting value for the moment, and whether prompting drops into high temperature liquid case heater 7 to reduce this deviation; When this deviate further was increased to greater than setting value two, the instruction with sending standard-sized sheet recirculation control valve 27 all was discharged into low temperature liquid case 23 with water.
The outlet conduit of circulating pump 26 can be provided with control valve, with convenient balance of regulating circulating fluid flow rate, and the flexibility of increase system design.Low temperature liquid case 23 can be provided with liquid level gauge, with the liquid level in the monitoring low temperature liquid case 23, and when this liquid level is lower than setting value, forbids the startup operation of circulating pump 26.
Claims (4)
1. branch control phase-change heat-exchange system based on the two-stage vapour-liquid heat exchanger; This system comprises thermal source heat exchanger (2), low-temperature receiver heat exchanger (20) and low temperature liquid case (23); It is characterized in that said system also comprises high-temperature heat-exchanging (14), cryogenic heat exchanger (22) and high temperature liquid case (8);
The female pipe of the thermal source steam at said thermal source heat exchanger (2) top is divided into two arms behind thermal source steam discharge control valve (16); Wherein the first steam pipe arm is communicated with through the upper collecting chamber of high-temperature heat-exchanging (14) with low-temperature receiver heat exchanger (20); And between high-temperature heat-exchanging (14) and low-temperature receiver heat exchanger (20), low-temperature receiver admission control valve (17) is set; The second steam pipe arm be communicated with the next part case of low-temperature receiver heat exchanger (20) through low temperature liquid case (23) and cryogenic heat exchanger (22), and at the preceding bypass steam flow control valve (18) that is provided with of low temperature liquid case (23);
Said low temperature liquid case (23) is communicated with high-temperature heat-exchanging (14) through the condensate liquid pipeline; Described high-temperature heat-exchanging (14) bottom is communicated with high temperature liquid case (8) through the condensate liquid pipeline; The condensate liquid pipeline of high temperature liquid case (8) bottom is divided into two arms, and wherein the first condenser pipe arm is communicated with cryogenic heat exchanger (22), and recirculation control valve (27) is set on this branch road; The second condenser pipe arm is communicated with the next part case of thermal source heat exchanger (2), and the logical liquid valve (1) of thermal source is set on this branch road.
2. the branch control phase-change heat-exchange system based on the two-stage vapour-liquid heat exchanger according to claim 1 is characterized in that, said thermal source heat exchanger (2) and low-temperature receiver heat exchanger (20) be respectively two or more than,
Take parallel connection setting between said two or the above thermal source heat exchanger (2), and on this parallel condensing pipe arm, be provided with logical liquid valve (1) of thermal source and isolating valve, on this parallel connection steam pipe arm, be provided with isolating valve;
Take parallel connection setting between said two or the above low-temperature receiver heat exchanger (20), and on this parallel connection steam pipe arm and this parallel condensing pipe arm, be respectively equipped with isolating valve.
3. the branch control phase-change heat-exchange system based on the two-stage vapour-liquid heat exchanger according to claim 1 is characterized in that,
Between the parallelly connected steam pipe arm isolating valve of said low-temperature receiver heat exchanger (20) and the low-temperature receiver admission control valve (17) exhaust-valve (19) is set, is used to discharge intrasystem on-condensible gas;
On the condensate liquid pipeline circulating pump (26) is set between said low temperature liquid case (23) and the high-temperature heat-exchanging (14);
On the female pipe of the condensate line of said high temperature liquid case (8) bottom booster (5) is set;
Said high temperature liquid case (8) set inside high temperature liquid case heater (7) is used to heat the condensate liquid in the high temperature liquid case (8), to reduce its degree of supercooling;
Said cryogenic heat exchanger (22) is provided with make-up valve (21), is used in system, adding circulation fluid working medium;
Said cryogenic heat exchanger (22) inside is provided with low temperature liquid case heater (24), is used to heat the condensate liquid in the low temperature liquid case (23), to reduce its degree of supercooling.
4. the branch control phase-change heat-exchange system based on the two-stage vapour-liquid heat exchanger according to claim 1 is characterized in that,
The intrafascicular evaporated liquor temperature sensor (3) that is provided with of the endothermic tube of said thermal source heat exchanger (2) is used for measuring and monitors thermal source heat exchanger temperature inside separately;
Said thermal source heat exchanger (2) is provided with evaporated liquor liquid level sensor (4); The upper end of said evaporated liquor liquid level sensor (4) is connected with the upper collecting chamber of thermal source heat exchanger (2); The lower end of evaporated liquor liquid level sensor (4) is connected the lower end of liquid level sensor (4) with the next part case, be used to measure monitor the inner liquid level of thermal source heat exchanger separately;
Between isolating valve and the thermal source steam discharge control valve (16) thermal source steam pressure sensor (15) is set on the parallelly connected steam pipe arm of said thermal source heat exchanger (2), is used to measure the steam pressure in the female pipe of monitoring thermal source steam;
High temperature liquid oven temperature, degree sensor (6) and high temperature liquid case liquid level sensor (9) are set on the said high temperature liquid case (8), are respectively applied for temperature and the liquid level measured in the monitoring high temperature liquid case (8);
Low temperature liquid oven temperature, degree sensor (25) is set on the said low temperature liquid case (23), is used to measure monitoring low temperature liquid case (23).
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| CN2011202225478U CN202182663U (en) | 2011-06-28 | 2011-06-28 | Sub-control phase-change heat exchange system based on two-stage vapor-liquid heat exchanger |
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| CN2011202225478U CN202182663U (en) | 2011-06-28 | 2011-06-28 | Sub-control phase-change heat exchange system based on two-stage vapor-liquid heat exchanger |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102200403A (en) * | 2011-06-28 | 2011-09-28 | 北京圆能工业技术有限公司 | Branch-control and phase-change heat exchange system and method based on two-stage steam-liquid heat exchanger |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102200403A (en) * | 2011-06-28 | 2011-09-28 | 北京圆能工业技术有限公司 | Branch-control and phase-change heat exchange system and method based on two-stage steam-liquid heat exchanger |
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