CN1246594A - High-effecient heat load regulator and its application - Google Patents
High-effecient heat load regulator and its application Download PDFInfo
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Abstract
The present invention relates to a heat energy storage and regulation equipment. Said efficient heat load regulator with two-phase heat supply unit and external heater has a volume heat-storing and -releasing intensity that is 8-9 times higher than that of heat accumulator. If it is used for boiler set, the installed capacity can be decreased by 30% or more and boiler set can stably work with a thermal efficiency increased by over 15%. If it is used for electric generator set, the load disturbance is smaller.
Description
" high-effecient heat load regulator and application " of the present invention relates to the application that a kind of heat energy stores adjusting device.
It is to adopt storage heater that boiler unit heat energy is regulated comparatively ideal mode, and the storage heater structure has accumulation of heat loop and heat supplying loop.(Fig. 1) [practical power-saving technology, Shanghai science tech publishing house, 1993.447] connect formation accumulation of heat loop, main steam loop (3) by the built-in carbonated drink heater of hot water storage tank (1) (2) through accumulation of heat steam-return line (5); Hot water storage tank (1) is connected main steam loop (3) through steam-water separator (4) and is constituted heat supplying loop, main steam pipe road pressure is higher than hot water storage tank pressure during accumulation of heat, steam enters built-in steam water heater of water tank and the exchange of the water heat of mixing, produce the full Heshui of setting pressure, hot water storage tank pressure is higher than the steam supply pipe network during heat release, and flash-off steam is discharged into steam supply pipe.Its shortcoming is to hold steam bleeding latent heat, does not utilize sensible heat, and sensible heat quantity is far longer than the latent heat of vaporization, so volume energy density is too low, the accumulation of heat heat release can only realize under higher operating pressure.
" high-effecient heat load regulator and application " of the present invention purpose is: by storing and discharging the volume calorific intensity that the latent heat of vaporization of working medium and sensible heat improve the heat load adjustment device, the boiler unit that is used for the fluctuating load operation can reduce installed capacity and guarantee 24 hours load operations of stabilizing the economy of unit, is used for cogeneration units and can guarantees that electric heating compares balance.
The present invention is achieved in that half of algebraical sum of the absolute value that adopts a high-effecient heat load regulator, this device thermic load per hour to equal actual load and average load difference, and the rich benefit of holding of loading in satisfied 24 hours is owed needs.Steam more than needed is in the accumulation of heat control valve enters external heating oxygen-eliminating device, and the external heating oxygen-eliminating device of the water inlet bottom delivery port that additional water pipe is connected external heating oxygen-eliminating device enters hot water storage tank formation accumulation of heat loop through the accumulation of heat water valve.Injection well downhole flow regulator is through the heat supply control valve in the hot water storage tank, and atomizer is connected in heat supply transfer valve and the external flash vessel, and the flash distillation steam supply pipe volleys the Pump Suction Nozzle formation through the connection of flash distillation pressure regulator valve and volleys flash distillation low pressure heat supplying loop.External flash vessel top vapour communicating pipe is connected live steam pipe through the vapour pressure transfer valve, external flash vessel bottom delivery port inserts the heat supply water pipe through the hot water transfer valve and constitutes the liquid phase heat supplying loop, the accumulation of heat loop, volley flash distillation low pressure heat supplying loop, the liquid phase heat supplying loop constitutes high-effecient heat load regulator jointly, the boiler installed capacity is determined (conventional method is to determine installed capacity according to the peak-peak load) by 24 hourly averages load when being used for the boiler unit of fluctuating load operation, boiler can keep economic load stable operation in 24 hours, when being higher than the boiler installed capacity with the vapour load, when doing the work jet through steam injector, main steam inhaling steam ports generation negative pressure, the high-temperature water of hot water storage tank enters an external flash vessel and under low pressure produces steam and enter and mix with main steam in the steam injector, surplus hot water after the flash distillation that stores in another external flash vessel, under the main steam back pressure as boiler feedwater, two external flash vessel alternations, one in an outer heat supply water is outer for steam, uses until exhausted until the accumulation of heat high-temperature water.Steam more than needed enters in the external heater when being lower than the boiler installed capacity with the vapour load, mixing the accumulation of heat water that produces setup parameter with make-up water sends in the water storage box standby, during accumulation of heat owing to adopt full make-up water, the moisturizing dissolved oxygen must be removed, external heater has the deoxygenation function, when being used for the thermoelectric cold cogeneration unit from the saturated vapor of boiler, total flow equals boiler rating and adds that replenishing evaporation capacity replenishes the heating load that evaporation capacity derives from hot water storage tank, there is the evaporation capacity of accumulation of heat water concurrent heating to be divided into two-way, one the tunnel through the superheated steam control valve, superheater enters steam turbine, its steam flow equals 24 hourly average flows (also equaling the specified throttle flow of boiler installed capacity and steam turbine), another road enters steam through the saturated vapor bypass valve and volleys pump, its flow is determined according to (heating demand-steam turbine steam discharge load), steam volleys and enters steam-distributing pipe pump discharge steam enters the back pressure vapor mixing of high-low pressure steam blender and steam turbine through saturated steam pipe after, its accumulation of heat is the same with the heating boiler unit with heat release loop and operating mode, the generating set installed capacity is determined by 24 little mean heat fluxs, because boiler can keep economic load stable operation in 24 hours, the steam turbine evaporation capacity for engine is guaranteed, because the rich benefit effect of owing of holding of high-effecient heat load regulator, the steam turbine steam discharge can all effectively utilize, obviously electric heating is very littler than the fluctuation that is balance, and the device operating pressure all can be realized steady operation below 16.17MPa.
The present invention and existing heat energy regulation technology--the comparison advantage of-storage heater is:
In conjunction with the accompanying drawings and embodiments the present invention is described as follows:
| Project name | The present invention | Storage heater |
| Volume calorific intensity kilojoule/cubic meter | 1336-2500 (1.27MPa) | 167-251 (1.27MPa) |
| Heat-supplying mode | The heat supply of low pressure flash high temperature water-supply two-phase | The heat supply of high pressure flash vapour phase |
| The heat absorption mode | The low temperature moisturizing | Saturation water |
| Total efficiency improves | ＞15％ | Uncertain |
| Thermoelectric balancing the load | Fine | Can't guarantee |
(Fig. 1) be total binding figure of storage heater
(Fig. 1): hot water storage tank (1), built-in carbonated drink add hot charging value (2), main steam loop (3), steam control valve (4), steam-water separator (5).
(Fig. 2) be the total binding figures of apparatus of the present invention when being used for boiler heat supplying
(Fig. 2): accumulation of heat water dispenser (1), hot water storage tank (2), heating demand control valve (3), hot water transfer valve group (4), heat supply transfer valve group (5), the external flash vessel of bottom delivery port (6) (7), flash distillation transfer valve group (8), main steam pipe (9), steam volley pump (10), flash distillation pressure regulator valve (11), flash distillation steam supply pipe (12), vapour pressure transfer valve (13), vapour pressure transfer valve (13), steam-distributing pipe (14), accumulation of heat control valve (15), external heating oxygen-eliminating device device (16), direct feed water valve (17), heat exchanger (18), accumulation of heat water valve (19), heat accumulation pipe (20), heat supply water pipe (21), steam (22) more than needed.
(Fig. 3) be the total binding figures of apparatus of the present invention when being used for cogeneration units
(Fig. 3): accumulation of heat water dispenser (1), hot water storage tank (2), heating demand control valve (3), hot water transfer valve group (4), heat supply transfer valve group (5), the bottom external flash vessel of delivery port (6) (7), flash distillation transfer valve group (8), saturated steam pipe (9), steam volleys pump (10), flash distillation pressure regulator valve (11), flash distillation steam supply pipe (12), vapour pressure transfer valve (13), vapour pressure transfer valve (13), steam-distributing pipe (14), accumulation of heat control valve (15), external heating oxygen-eliminating device device (16), direct feed water valve (17), heat exchanger (18), accumulation of heat water valve (19), heat accumulation pipe (20), heat supply water pipe (21), steam (22) more than needed, superheated steam control valve (23) superheater (24), saturated vapor bypass valve (25), heat supply reject steam pipe (26), high-low pressure steam blender (27), back pressure steam (28), heat supply control valve (29) steam turbine (30) saturated vapor (31)
Below in conjunction with (Fig. 2) detailed structure and the working condition when illustrating that apparatus of the present invention are used for boiler heat supplying.
Steam (22) more than needed is in accumulation of heat control valve (15) enters external heating oxygen-eliminating device (16), additional water pipe is connected the water inlet of external heating oxygen-eliminating device (16), external heating oxygen-eliminating device bottom delivery port is when accumulation of heat water valve (19) enters hot water storage tank (2) and constitutes the accumulation of heat loop works: accumulation of heat control valve (15) was opened to external heating oxygen-eliminating device steam supply in steam distribution pipe pressure higher (the external heat load is lower) time, simultaneously inside after softening water, because soft water dissolved oxygen content height, so it must be again the moisturizing oxygen-eliminating device at the external heating oxygen-eliminating device of when heating deoxygenation external heat exchanger (storage heater adopts built-in heat exchange mode) that in fact is high-effecient heat load regulator that the system of bringing into can produce oxygen corrosion.Its operating pressure will be determined according to accumulation of heat pressure.Another effect of external heating oxygen-eliminating device is directly to supply deaerated water to boiler, the interior accumulation of heat water dispenser of hot water storage tank (2) (1) atomizer in heating demand control valve (3) heat supply transfer valve (5) and external flash vessel (7) is connected, flash distillation steam supply pipe (12) volleys pump (10) suction inlet formation through flash distillation pressure regulator valve (11) connection and volleys flash distillation low pressure heat supplying loop, it mainly acts on: when main steam produces negative pressure at the steam suction inlet as the work jet when volleying pump (10), flash distillation pressure regulator valve (11) can be delivered to negative pressure external flash vessel after opening, at this moment the process control valve under pressure promotes of the high-temperature heat accumulation water in the hot water storage tank enters and is ejected into space in the external flash vessel (7) in the atomizer, the latent heat of vaporization becomes steam and enters under volleying and volley pump (10) and mix back output with main steam, volleys the Pump Suction Nozzle low-pressure designs and is＞0.098MPa.External flash vessel (7) top vapour communicating pipe is connected live steam pipe (9) through vapour pressure transfer valve (13), external flash vessel (7) bottom delivery port (6) inserts heat supply water pipe (21) through hot water transfer valve (4) and constitutes the liquid phase heat supplying loop, the operating pressure of external flash vessel is with to volley PIP close, surplus coolant-temperature gage is the saturation temperature of flashing pressure correspondence, its effect be vapour pressure be left water be in supercooled state can cavitation when boiler pumping high-temperature water is done feedwater, can realize reliable liquid phase heat supply, the device parallel connection is provided with two external flash vessels (7), volleying under the negative pressure of generation outwards flash distillation steam supply at the next external flash vessel of the switching of each transfer valve group (7), another external flash vessel (7) is outside hot-water supply under back pressure, realize the heat supply of vapour-liquid two-phase, for each transfer valve group of reliably working adopts automatic valve, the accumulation of heat loop volleys flash distillation low pressure heat supplying loop liquid phase heat supplying loop and constitutes high-effecient heat load regulator integral body jointly.
The present invention is further described for embodiment by being used for the boiler heat supplying unit: 1. basic parameter:
Boiler working pressure-52.92[MPa]
Evaporation capacity-400 ton (8 hours) greater than nominal output
Evaporation capacity-440 ton (16 hours) less than nominal output
Saturated-steam temperature-243.04C saturated vapor enthalpy-669.02. boiler machine kludge capacity is determined: (determining by 24 hourly averages load)
D0=(400+440)/24==35 ton/hour 3. regenerative loads determine: the absolute value of actual load and average load difference by the hour
Half of algebraical sum determined, (pressing superheated steam calculates)
In Dc=(DC1+DC2) * 0.5 formula: DC-regenerative load ton (24 hours)
DC1-is higher than the amount of the owing algebraical sum absolute value of average load
DC1=400-35*8=120 ton/H
DC2-is lower than the surplus algebraical sum absolute value of average load
DC2=|440-35*16|=120 ton/H
DC=(120+120) * 0.5=120 ton (24 hours) the 4. volume V 0 of hot water storage tank is determined (pressing saturated vapor determines)
Accumulation of heat pressure (setting)-1.27MPa regenerator temperature 194.13C
Accumulation of heat water enthalpy 197.3
Volume calorific intensity Q=120*1000*669.0/406.89=197301.48
KcaL/M35. the operating mode of external flash vessel is determined: the interior accumulation of heat water of hot water storage tank (2) is through distributor (1) heating demand control valve (3), interior the atomizer connection of heat supply transfer valve (5) and external flash vessel (7), when needing concurrent heating per hour the flow from hot water storage tank be 50.85 tons/H.The flash-off steam flow that produces is 1.25 tons/H, by flash distillation steam supply pipe (12), flash distillation pressure regulator valve (11) enters to volley in the pump (10) with after mixing from the about 50 tons/H of boiler saturated vapor and externally carries, external flash vessel (7) top vapour communicating pipe is connected live steam pipe (9) through vapour pressure transfer valve (13), external flash vessel (7) bottom delivery port (6) inserts heat supply water pipe (21) through hot water transfer valve (4) and constitutes the liquid phase heat supplying loop, surplus discharge is 50 tons/H pressure 0.98MPa, back pressure was＞1.164MPa (18KGf/CM2) when temperature 183.2C. carried surplus water, purpose is to guarantee that surplus water has certain degree of supercooling, when pumping, ward off and exempt from cavitation, in order to guarantee continuous operation, parallel connection is provided with two external flash vessels (7), volleying under the negative pressure of generation outwards flash distillation steam supply at the next external flash vessel of the control of each transfer valve group (7), when being elevated to certain water level, surplus water stops into accumulation of heat water, change over to and under back pressure, outwards supply surplus water, another replaces into accumulation of heat water flash distillation steam supply, realize the heat supply of vapour-liquid two-phase, the purpose of flash distillation is promptly to increase the steam supply, also make the cold cooling of the suitable mistake of accumulation of heat water satisfy the requirement of economizer inlet water temperature, ward off cavitation when exempting from pumping simultaneously.Each operational factor gathers as follows:
The average heat supply of external flash vessel is exerted oneself: DS=DC1/8=120/8=15 ton/hour (i=669.KCAL/KG) mean heat flux DS*1000*669.0=15*1000*669.0=10035000Kcal/H flashing pressure (setting)-0.98MPa saturation temperature 183.2C (principle of flashing pressure setting is that its saturation temperature is lower than boiler saturation temperature 60C, as the temperature rise of economizer) saturation water enthalpy 185.6Kcal/KG saturated vapor enthalpy 663.9Kcal/kg is according to balance having: GS*i '+Gq*i "=10035000 Kcal/H
GS+Gq=50.85 KG/H group of solving an equation: (50850-Gq) * i '+Gq*i "=10035000
(50850-Gq)*185.6+Gq*663.9＝10035000
Gq＝＝1250?????KG/H
In the GS==49600 KG/H formula: the surplus water KG/H of GS--Gq--flash-off steam KG/H
Maximum boiler feed capacity=35+ (15-1.25)=48.75 ton/H
The GS=49.6 ton can satisfy feedwater and surplus is arranged, and does not need the oxygen-eliminating device moisturizing, and it is steam-water separator than the influence that boiler rating increases boiler that the total evaporation of accumulation of heat water concurrent heating is arranged; Safety valve, stop valve need not have other adverse effect outward by strengthening load setting.6. external deaerating heater operational factor divides accumulation of heat and two kinds of operating modes of heat release to determine.
During accumulation of heat; Steam (22) (about 8652.93KG/H flow) more than needed is in accumulation of heat control valve (15) enters external heating oxygen-eliminating device (16), its operational factor is: 60.43 tons/H of operating pressure 1.27MPa hot water temperature 194.13C deaerated water output wherein 35 tons/H (112C) does boiler feedwater, and 25.43 tons/H (194.13C) makes accumulation of heat water and enter hot water storage tank (2) through accumulation of heat water valve (19).During heat supply such as accumulation of heat water can to satisfy the external deaerating heater of boiler feedwater out of service.
Operational factor result of calculation is as follows:
Operating pressure 1.27MPa hot water temperature 194.13C
Deaerated water output=35+ (V0/16)=35+ (406.89/16)=60.43 ton/H deoxygenation thermic load is:
Qxr＝(DC2/16)*1000*(663.9-20)＝(120/16)*663.9*1000
=4979250 KCAl/H (Qxr-regenerative load)
Qgs＝35000*[(197.3+20)/2+3]＝3907750KCAl/H
(Qgs-boiler feedwater thermic load)
Qy＝Qxr+Qgs＝4979350+3907750＝8881100KCAl/H
35 tons/H of boiler feedwater flow
Boiler feed temperature Tx=112C (need not improve feed temperature because thermic load is low
Be used to heat the 20C moisturizing, cooling desuperheat during output).
Accumulation of heat discharge=25.43M3/H heat accumulating water temperature degree=194.13C
During heat release: but maximum confluent is 48.75 tons/H because the per hour heat supply water yield of storage heater is Gxr=50.86 ton/H boiler, can satisfy the boiler feedwater needs, and external heating oxygen-eliminating device can stop moisturizing.7. load regulation rate:
Qmax＝(35000+15000)*663.9＝33195000
Qmin＝35000*663.9-4979250＝18257250
Q0??＝35000*663.9＝23236500
Kqx?＝Qmax-Q0/Q0
＝33195000-23236500/23236500＝+0.4285
Kqn?＝Qmin-Q0/Q0
＝18257250-23236500/23236500＝-0.2143
Qmax-maximum heating load KCAL/H Qmin-minimum thermal load KCAL/H
Q0-rated heat input, rated heat load KCAL/H Kqx-overload factor
Kqn-underload coefficient
Kgx in short period; Kgn can also increase by big radian.8. operating pressure can be below 16.71MPa.
Owing to adopted high-effecient heat load regulator of the present invention, boiler can be pressed rated load stable operation in 24 hours, and can satisfy long-time excess load and the boiler operatiopn of underload heat supply needs and render a service and to improve more than 15%, because existing apparatus is to determine installed capacity according to peak load, its load is 1.4285 times of average load, and the present invention can examine and subtract an installed capacity 42.85% less.
The structure and the application feature of apparatus of the present invention are described below in conjunction with (Fig. 3) and the embodiment that is used for cogeneration of heat and power.
Equal boiler rating from saturated vapor (30) total flow of boiler when being used for cogeneration units and add additional evaporation capacity, additional evaporation capacity derives from the heating load of hot water storage tank, and it is steam-water separator than the influence that boiler rating increases boiler that the total evaporation of accumulation of heat water concurrent heating is arranged; Safety valve; Stop valve does not have other adverse effect outward by strengthening load setting.Total flow is divided into two-way, one the tunnel enters its steam flow of steam turbine (31) through superheated steam control valve (23) superheater (24) equals 24 hourly average flows (also equaling the specified throttle flow of boiler installed capacity and steam turbine), another road enters steam through saturated vapor bypass valve (25) and volleys pump (10), its flow is determined according to (heating demand-steam turbine steam discharge load), steam volleys pump (10) outlet steam and enter steam-distributing pipe (14) after saturated steam pipe (26) enters high-low pressure steam blender (27) and the back pressure steam (28) of steam turbine mixes, steam (22) more than needed is in accumulation of heat control valve (15) enters external heating oxygen-eliminating device (16), additional water pipe is connected the water inlet of external heating oxygen-eliminating device (16), external heating oxygen-eliminating device (16) bottom delivery port is divided into two-way, water loop that goes out through cooling heat exchanger (18) is arranged, one without cooling the water loop that goes out enter hot water storage tank (2) through accumulation of heat water valve (19) and constitute the accumulation of heat loop, during work: accumulation of heat control valve (15) is opened to the simultaneously inside after softening water of external heating oxygen-eliminating device steam supply when steam distribution pipe pressure higher (the external heat load is lower), because soft water dissolved oxygen content height, so the system of bringing into can produce oxygen corrosion must be in the deoxygenation of when heating, in fact external heating oxygen-eliminating device promptly is the external heater (storage heater adopts built-in heat exchange mode) of high-effecient heat load regulator, it is again the moisturizing oxygen-eliminating device, its operating pressure will be determined according to accumulation of heat pressure, another effect of external heating oxygen-eliminating device is directly to supply deaerated water to boiler, the interior accumulation of heat water dispenser of hot water storage tank (2) (1) atomizer in heating demand control valve (3) heat supply transfer valve (5) and external flash vessel (7) is connected, flash distillation steam supply pipe (12) is connected through flash distillation pressure regulator valve (11) and is volleyed pump (10) suction inlet, constitute and volley flash distillation low pressure heat supplying loop, it mainly acts on: when main steam produces negative pressure at the steam suction inlet as the work jet when volleying pump (10), flash distillation pressure regulator valve (11) can be delivered to negative pressure external flash vessel after opening, at this moment the process control valve under pressure promotes of the high-temperature heat accumulation water in the hot water storage tank enters and is ejected into space in the external flash vessel (7) in the atomizer, the latent heat of vaporization becomes steam and enters under volleying and volley pump (10) and mix back output with main steam, volleying the Pump Suction Nozzle low-pressure designs is＞0.098MPa, external flash vessel (7) top vapour communicating pipe is connected live steam pipe (9) through vapour pressure transfer valve (13), external flash vessel (7) bottom delivery port (6) inserts heat supply water pipe (21) through hot water transfer valve (4) and constitutes the liquid phase heat supplying loop, the operating pressure of external flash vessel is with to volley PIP close, surplus coolant-temperature gage is the saturation temperature of flashing pressure correspondence, its effect be vapour pressure be left water be in supercooled state can cavitation when boiler pumping high-temperature water is done feedwater, can realize reliable liquid phase heat supply, the device parallel connection is provided with two external flash vessels (7), volleying under the negative pressure of generation outwards flash distillation steam supply at the next external flash vessel of the switching of each transfer valve group (7), another external flash vessel (7) is outside hot-water supply under back pressure, realize the heat supply of vapour-liquid two-phase, for each transfer valve group of reliably working adopts automatic valve, the accumulation of heat loop, volley flash distillation low pressure heat supplying loop liquid phase heat supplying loop and constitute high-effecient heat load regulator integral body jointly, device by above-mentioned principle setting can guarantee steam turbine running at full capacity in 24 hours, and thermoelectric load fluctuation seldom.
The present invention is further described for embodiment by being used for thermoelectric heat supply unit: 1. basic parameter:
Boiler working pressure-52.92[MPa] (＜16.17MPa chooses)
Evaporation capacity-400 ton (8 hours) greater than nominal output
Evaporation capacity-440 ton (16 hours) less than nominal output
Saturated-steam temperature-243.04C saturated vapor enthalpy-669.0
Superheat steam temperature-400C superheated steam enthalpy-769.7
Back pressure steam pressure 1.27MPa temperature 220C
Back pressure steam enthalpy 682.2KcaL/KG
Electric load Qd=769.7-682.2=87.5 KCAL/KG2. installation load is determined: (determining by 24 hourly averages load)
The boiler installation: D0=(400+440)/24=35 ton/hour
Generate output: (87.5*35000)/860=3567 KW.H
Heat supply high load capacity: 15000*669+ (35000*682.2)=33915500 KCAL/H
Heat supply underload: 35000*682.2-(QC/16)=18160163 KCAL/H3. regenerative load is determined: accumulation of heat pressure (setting)-1.27MPa
Regenerator temperature 194.13C
Accumulation of heat water enthalpy 197.3
DP=(400+440)/24=35 ton/time DP-average output
DC-accumulation of heat volume [cubic meter]
Dc＝(DP-440/16)*1000*682.2*16/197.3
=7500*682.2*16/197.3=414.9[cubic meter] (accumulation of heat in 16 hours)
The average heat supply of the 4. external flash vessel of QC=414.9*1000*197.3=81859770 KCAL (16 hours) is exerted oneself:
QC/8＝81859770/8.0＝10232471???KCAL/H
Flashing pressure (setting)-0.98MPa saturation temperature 183.2C
Saturation water enthalpy 185.6Kcal/KG saturated vapor enthalpy 663.9Kcal/kg
According to balance having: GS*i '+Gq*i "=10232471Kcal/H
The group 413.3/8=51.66KG/H solve an equation: (51660-Gq) * i '+Gq*i "=10232471
(51660-Gq)*185.6+Gq*663.9＝10232471
Gq＝＝1347KG/H
In the GS==50312KG/H formula: the surplus water KG/H of GS--Gq--flash-off steam KG/H
Maximum boiler feed capacity=35+ (15-1.26)=48.74 ton/H
The GS=50.312 ton can satisfy feedwater and surplus is arranged, and does not need the oxygen-eliminating device moisturizing, and it is steam-water separator than the influence that boiler rating increases boiler that the total evaporation of accumulation of heat water concurrent heating is arranged; Safety valve, stop valve need do not have other adverse effect outward by strengthening load setting.5. external deaerating heater operational factor divides accumulation of heat and two kinds of operating modes of heat release to determine.
During accumulation of heat: steam (22) (7500KG/H more than needed, 679.6KCAL/KG) in accumulation of heat control valve (15) enters external heating oxygen-eliminating device (16), its operational factor is: 60.93 tons/H of operating pressure 1.27MPa hot water temperature 194.13C deaerated water output wherein 35 tons/H (112C) does boiler feedwater, 25.93 ton/H (194.13C) makes accumulation of heat water and enters hot water storage tank (2) through accumulation of heat water valve (19), need to replenish 20C soft water flow 48808.0KG/H, during heat supply such as accumulation of heat water can satisfy boiler feedwater, external deaerating heater is out of service, and operational factor result of calculation is as follows:
Operating pressure 1.27MPa hot water temperature 194.13C
Deaerated water output=35+ (V0/16)=35+ (414.9/16)=60.93 ton/H
Qxr＝81859770/16
=5116235KCAl/H (Qxr-regenerative load)
Qy＝35000*[(197.3+20)/2+3]＝3907750
(Qy-deoxygenation thermic load)
According to balance having:
GBs*20+GBq*i″gr＝5116235+3907750＝9023985
KCAL/H
GBs+GBq＝60930KG/H
(60930-GBq)*20+GBq*663.9＝9023985KCAL/H
Steam consumption per hour during GBq=12122 KG/H GBq-accumulation of heat
GBs=60930-12122=48808 KG/H GBs-is rate of water make-up per hour
When the result gathers following underload: 35 tons/H of boiler feedwater flow boiler feed temperature Tx=112C (because thermic load low need not improve feed temperature be used to heat the 20C moisturizing, cooling desuperheat during output).During accumulation of heat discharge=25.93 ton/H heat accumulating water temperature degree=194.13C high load capacity: because the accumulation of heat moisturizing can be satisfied the boiler feedwater needs, external heating oxygen-eliminating device can stop moisturizing.6. load regulation rate:
Qmax＝35000*682.2+15000*669.0＝33915500
Qmin＝35000*669.0-5116235＝18298765
Q0??＝35000*669.0＝23415000
Kqx?＝Qmax-Q0/Q0
＝33915500-23415000/23415000＝+0.44845
Kqn?＝Qmin-Q0/Q0
＝18298765-23415000/23415000＝-0.2185
Qmax-maximum heating load KCAL/H Qmin-minimum thermal load KCAL/H
Q0-rated heat input, rated heat load KCAL/H Kqx-overload factor
Kqn-underload coefficient
Claims (8)
1. energy regulating device, particularly high-effecient heat load regulator has accumulation of heat loop and heat supplying loop, it is characterized in that: steam (22) more than needed is in accumulation of heat control valve (15) enters external heating oxygen-eliminating device (16), the external heating oxygen-eliminating device of the water inlet bottom delivery port that additional water pipe is connected external heating oxygen-eliminating device (16) enters hot water storage tank (2) formation accumulation of heat loop through accumulation of heat water valve (19), distributor (1) atomizer in heating demand control valve (3) heat supply transfer valve (5) and external flash vessel (7) is connected in the hot water storage tank, the flash distillation steam supply pipe volleys pump (10) suction inlet formation through flash distillation transfer valve (8) flash distillation pressure regulator valve (11) connection steam and volleys flash distillation vapour phase heat supplying loop, (when being used for the thermoelectric cold cogeneration unit, the formation that volleys flash distillation vapour phase heat supplying loop is that the saturated vapor from boiler is divided into two-way, one the tunnel enters steam turbine (31) through superheated steam control valve (23) superheater (24), another road enters steam through saturated vapor bypass valve (25) and volleys pump (10), steam volleys pump discharge steam and enter steam-distributing pipe (14) after saturated steam pipe (26) enters high-low pressure steam mixer (27) and the back pressure steam (28) of steam turbine mixes), external flash vessel top vapour communicating pipe is connected live steam pipe (9) through vapour pressure transfer valve (13), external flash vessel bottom delivery port (6) inserts heat supply water pipe (21) through hot water transfer valve (4) and constitutes the liquid phase heat supplying loop, the accumulation of heat loop, volley the flash-off steam heat supplying loop, the liquid phase heat supplying loop constitutes high-effecient heat load regulator jointly.
2. high-effecient heat load regulator is characterized in that two external flash vessels (7) deployment in parallel in the claim 1.
3. high-effecient heat load regulator is characterized in that transfer valve (4) in the claim 1; (5) (8); (13) be the threeway automatic valve.
In the claim 1 high-effecient heat load regulator it is characterized in that external heating oxygen-eliminating device (16) have one through cooling heat exchanger (18) go out water loop, one without cooling go out water loop.
5. high-effecient heat load regulator is characterized in that it is the Laval nozzle structure that steam volleys pump (10) high-low pressure steam mixer (27) in the claim 1.
6. high-effecient heat load regulator is characterised in that the thermic load of its hot water storage tank (2) when being used for the boiler heat supplying unit per hour equals half of actual load and average load difference absolute value algebraical sum among the claim 1-5, satisfies the rich benefit of holding of 24 hours loads and owes needs.
7. the saturated vapor (31) from boiler when high-effecient heat load regulator is characterized in that being used for cogeneration units among the claim 1-6 is divided into two-way, one the tunnel enters its steam flow of steam turbine (30) through superheated steam control valve (23) superheater (24) equals 24 hourly average flows (also equaling the specified throttle flow of boiler installed capacity and steam turbine), another road enters steam through saturated vapor bypass valve (25) and volleys pump (10), its flow determines that according to (heating demand-steam turbine steam discharge load) steam volleys pump (10) outlet steam and enter steam-distributing pipe (14) after saturated steam pipe (26) enters high-low pressure steam blender (27) and the back pressure steam (28) of steam turbine mixes.
8. high-effecient heat load regulator among the claim 1-7, operating pressure is less than 16.17MPa when it is characterized in that being used for boiler and thermoelectric cold cogeneration unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB981182089A CN1143978C (en) | 1998-08-30 | 1998-08-30 | High-effecient heat load regulator and its application |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB981182089A CN1143978C (en) | 1998-08-30 | 1998-08-30 | High-effecient heat load regulator and its application |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1246594A true CN1246594A (en) | 2000-03-08 |
| CN1143978C CN1143978C (en) | 2004-03-31 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB981182089A Expired - Fee Related CN1143978C (en) | 1998-08-30 | 1998-08-30 | High-effecient heat load regulator and its application |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1143978C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100392231C (en) * | 2003-09-18 | 2008-06-04 | 松下电器产业株式会社 | Cogeneration system |
| CN102927549A (en) * | 2012-11-02 | 2013-02-13 | 张家港市威孚热能科技有限公司 | Self-heat-accumulating type electrical heating pressure variable steam boiler device |
| CN104048286A (en) * | 2014-06-25 | 2014-09-17 | 付红萍 | Steam heat accumulator system |
| CN105547010A (en) * | 2016-02-03 | 2016-05-04 | 浙江省特种设备检验研究院 | Thermal load adjusting device suitable for organic heat carrier boiler shaping energy efficiency test |
| CN112460668A (en) * | 2020-12-01 | 2021-03-09 | 福建晋江热电有限公司 | Undisturbed heat storage system and method for peak valley filling of back pressure type heat supply unit |
| CN114251640A (en) * | 2020-09-22 | 2022-03-29 | 广东美的环境电器制造有限公司 | Heating method and device for steam generator, steam appliance and storage medium |
-
1998
- 1998-08-30 CN CNB981182089A patent/CN1143978C/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100392231C (en) * | 2003-09-18 | 2008-06-04 | 松下电器产业株式会社 | Cogeneration system |
| CN102927549A (en) * | 2012-11-02 | 2013-02-13 | 张家港市威孚热能科技有限公司 | Self-heat-accumulating type electrical heating pressure variable steam boiler device |
| CN102927549B (en) * | 2012-11-02 | 2014-08-13 | 张家港市威孚热能科技有限公司 | Self-heat-accumulating type electrical heating pressure variable steam boiler device |
| CN104048286A (en) * | 2014-06-25 | 2014-09-17 | 付红萍 | Steam heat accumulator system |
| CN105547010A (en) * | 2016-02-03 | 2016-05-04 | 浙江省特种设备检验研究院 | Thermal load adjusting device suitable for organic heat carrier boiler shaping energy efficiency test |
| CN105547010B (en) * | 2016-02-03 | 2017-07-11 | 浙江省特种设备检验研究院 | Suitable for the heat load adjusting device of boiler of organic heat carrier sizing efficiency test |
| CN114251640A (en) * | 2020-09-22 | 2022-03-29 | 广东美的环境电器制造有限公司 | Heating method and device for steam generator, steam appliance and storage medium |
| CN114251640B (en) * | 2020-09-22 | 2023-09-12 | 广东美的环境电器制造有限公司 | Heating method and device for steam generating device, steam appliance and storage medium |
| CN112460668A (en) * | 2020-12-01 | 2021-03-09 | 福建晋江热电有限公司 | Undisturbed heat storage system and method for peak valley filling of back pressure type heat supply unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1143978C (en) | 2004-03-31 |
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