CN111365748B - Heat supply method and heat supply system of cogeneration unit - Google Patents
Heat supply method and heat supply system of cogeneration unit Download PDFInfo
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- CN111365748B CN111365748B CN202010159328.3A CN202010159328A CN111365748B CN 111365748 B CN111365748 B CN 111365748B CN 202010159328 A CN202010159328 A CN 202010159328A CN 111365748 B CN111365748 B CN 111365748B
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- 238000000034 method Methods 0.000 title claims abstract description 31
- 238000010438 heat treatment Methods 0.000 claims abstract description 121
- 238000005338 heat storage Methods 0.000 claims abstract description 80
- 238000004519 manufacturing process Methods 0.000 claims abstract description 31
- 230000005611 electricity Effects 0.000 claims abstract description 26
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 459
- 238000001816 cooling Methods 0.000 claims description 143
- 238000004891 communication Methods 0.000 claims description 19
- 230000009467 reduction Effects 0.000 claims description 18
- 239000000203 mixture Substances 0.000 claims description 12
- 239000007788 liquid Substances 0.000 claims description 10
- 230000020169 heat generation Effects 0.000 claims description 7
- 238000010521 absorption reaction Methods 0.000 claims description 4
- 239000007789 gas Substances 0.000 description 87
- 239000000498 cooling water Substances 0.000 description 55
- 238000005086 pumping Methods 0.000 description 35
- 238000010248 power generation Methods 0.000 description 24
- 230000001105 regulatory effect Effects 0.000 description 22
- 230000033228 biological regulation Effects 0.000 description 17
- 238000000605 extraction Methods 0.000 description 12
- 238000007599 discharging Methods 0.000 description 10
- 239000002918 waste heat Substances 0.000 description 8
- 239000008400 supply water Substances 0.000 description 7
- 230000003139 buffering effect Effects 0.000 description 6
- 238000009833 condensation Methods 0.000 description 6
- 230000005494 condensation Effects 0.000 description 6
- 238000011144 upstream manufacturing Methods 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 239000003245 coal Substances 0.000 description 4
- 239000002699 waste material Substances 0.000 description 4
- 238000007664 blowing Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000004064 recycling Methods 0.000 description 2
- 230000001172 regenerating effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D3/00—Hot-water central heating systems
- F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
- F24D3/1058—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system disposition of pipes and pipe connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D11/00—Central heating systems using heat accumulated in storage masses
- F24D11/002—Central heating systems using heat accumulated in storage masses water heating system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D19/00—Details
- F24D19/10—Arrangement or mounting of control or safety devices
- F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
- F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
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- Thermal Sciences (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention relates to the technical field of turbo-generator units, and particularly provides a heat supply method and a heat supply system of a cogeneration unit, which solve the problem that the heat load demand and the electric load peak shaving are difficult to schedule at the same time in a heating period. The heat supply method and the heat supply system can adopt a high-backpressure heat storage mode when the heat load demand is low and the electric load demand is high, adopt a high-backpressure heat release mode when the heat load demand and the electric load demand are both high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, adopt a low-pressure cylinder near-zero output heat storage mode when the electric load demand and the heat load demand are both low, and adopt a low-pressure cylinder near-zero output heat release mode when the electric load demand is low, the heat load demand is high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand.
Description
Technical Field
The invention relates to the technical field of steam turbine generator units, in particular to a heat supply method and a heat supply system of a cogeneration unit.
Background
In the 'three north' area of China, because the coal-fired thermoelectric ratio is high, the peak-shaving power supply construction condition is insufficient, in addition, the unit also needs to undertake the heat supply task in winter, and the peak shaving of the electric load of the unit is difficult in the heating period in winter, so that the problem of wind power wind abandon of the power grid is serious. The cogeneration unit is used as an important town construction industry and plays an important role in replacing the shutdown of a coal-fired heating small boiler to treat the environmental pollution. However, in a conventional cogeneration unit, extraction of steam discharged from a steam turbine intermediate pressure cylinder is usually adopted to heat a heat supply network for supplying water for supplying heat, and a large amount of high-grade steam which can be originally used for power generation is directly used for supplying heat in the heat supply production process, so that energy quality waste exists. The high back pressure heat supply technology can effectively utilize the waste heat of the steam exhausted from the low pressure cylinder of the steam turbine set for heat supply, can fully utilize high-grade steam for power generation, can improve the power generation output of the set in the heat supply state, and can change the waste steam of the set into valuable, thereby reducing the coal consumption of the set for heat supply and power generation and gaining more and more attention of thermal power plants.
The cogeneration unit is the most main heating source in winter in northern cities, and in order to meet the rapidly increasing heating demand of the cities, the power generation load of the cogeneration unit is often in a high-load operation state, so that the abnormal difficulty of peak shaving of a power grid is caused. In order to relieve the increasing peak-valley contradiction of the power grid and ensure the safe operation of the power grid, the government successively establishes and issues 'power auxiliary service market operation rules', provides a paid peak regulation method, solves the current power peak regulation difficulty and promotes the consumption of clean energy. Under the drive of the policy of peak regulation by compensation, more and more cogeneration units participate in the team of peak regulation by compensation, which provides great challenge to the cogeneration units on how to solve the demand difference of heat supply and power generation in different time periods, and provides higher requirements on the flexible operation of heat and power under the heat supply working condition of the cogeneration units.
Aiming at the large contradiction between the heat load demand and the electric load peak regulation of the cogeneration unit in the heating period, the traditional steam extraction and heat supply unit has the defect that the low-pressure cylinder steam extraction cold source loss cannot be fully utilized when the medium-pressure cylinder steam extraction and heat supply is adopted. This presents a greater challenge to how to increase the flexibility of the unit load peak shaving during the unit heating period and the unit heating economy.
Disclosure of Invention
Technical problem to be solved
The invention aims to provide a heat supply method and a heat supply system of a cogeneration unit, which solve the problem that the heat load demand and the electric load peak shaving are difficult to schedule at the same time in the heating period.
(II) technical scheme
In order to achieve the purpose, the invention adopts the main technical scheme that:
the invention provides a heat supply method of a cogeneration unit on one hand, which comprises the following steps: when the heat load demand is low and the electric load demand is high, a high back pressure heat storage mode is adopted; when the heat load demand and the electric load demand are both high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, a high back pressure heat release mode is adopted; when the electric load demand and the heat load demand are both low, a low-pressure cylinder near-zero-output heat storage mode is adopted; when the electric load demand is low, the heat load demand is high, and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, a low-pressure cylinder near-zero-output heat release mode is adopted; the high back pressure heat storage mode is as follows: the steam exhaust of the intermediate pressure cylinder enters the low pressure cylinder to do work, the formed steam exhaust of the low pressure cylinder heats the return water of the heat supply network, and one part of the heated return water of the heat supply network enters the heat reservoir and then enables the heat reservoir to store heat in one of the following two modes: the first heat storage mode: part of the heated return water of the heat supply network is directly stored in the heat reservoir as high-temperature heat supply network water, and meanwhile, the low-temperature heat supply network water in the heat reservoir and the return water of the heat supply network entering the heat reservoir with the same flow rate leaves the heat reservoir to be continuously circulated and heated by the low-pressure cylinder exhaust steam; a second heat storage mode: one part of heated return water of the heat supply network releases heat to a heat absorption and release medium in the heat reservoir, and the return water leaves the heat reservoir after releasing the heat to continue to circulate and be heated by the low-pressure cylinder exhaust steam; the high back pressure heat release pattern is: all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder to do work, the exhaust steam of the formed low pressure cylinder heats the return water of the first part of the heat supply network, and the return water of the second part of the heat supply network enters the heat reservoir and then the heat reservoir releases heat in one of the following two ways: the first heat release mode matched with the first heat storage mode: the second part of heat supply network backwater is stored in the heat reservoir as low-temperature heat supply network water, and the high-temperature heat supply network water in the heat reservoir is output to the heat reservoir; a second heat release mode matched with the second heat storage mode: the second part of return water of the heat supply network flows through a heat-absorbing and heat-releasing medium of the heat reservoir and is heated and then output to the heat reservoir; the low-pressure cylinder near-zero-output heat storage mode is as follows: the low pressure cylinder is cooled after the steam exhaust of the first part intermediate pressure cylinder is subjected to temperature and pressure reduction, the formed low pressure cylinder steam exhaust uses cooling tower circulating water/air cooling island to be cooled and recovered, the steam exhaust of the second part intermediate pressure cylinder heats the return water of the heat supply network, and one part of the heated return water of the heat supply network enters the heat reservoir and then enables the heat reservoir to store heat in one of the following two ways: the first heat storage mode: one part of the heated return water of the heat supply network is directly stored in the heat reservoir as high-temperature heat supply network water, and meanwhile, the low-temperature heat supply network water in the heat reservoir and the flow of the return water of the heat supply network entering the heat reservoir are equal to that of the return water of the heat supply network stored in the heat reservoir, leave the heat reservoir and are continuously circulated and heated by the exhaust steam of the second part of the intermediate pressure cylinder; the second heat storage mode: one part of the heated return water of the heat supply network releases heat to a heat absorption and release medium in the heat reservoir, and the heat is continuously circulated and heated by the steam exhaust of the second part of the intermediate pressure cylinder after the heat is released; the low-pressure cylinder near-zero output heat release mode is as follows: the method comprises the following steps that after the steam exhaust of the first part of intermediate pressure cylinders is subjected to temperature reduction and pressure reduction, the low pressure cylinders are cooled, the formed low pressure cylinder steam exhaust uses circulating water/an air cooling island of a cooling tower to be cooled and recovered, the steam exhaust of the second part of intermediate pressure cylinders heats the return water of the first part of heat supply network, and the return water of the second part of heat supply network enters the heat reservoir to enable the heat reservoir to release heat in one of the following two ways: a first heat release mode matched with the first heat storage mode: the second part of heat supply network backwater is stored in the heat reservoir as low-temperature heat supply network water, and the high-temperature heat supply network water in the heat reservoir is output to the heat reservoir; a second heat release mode matched with the second heat storage mode: the second part of return water of the heat supply network flows through the heat-absorbing and heat-releasing medium of the heat reservoir and is heated and then output to the heat reservoir.
According to the invention, in the high back pressure heat storage mode: if the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is lower than the set temperature, the return water of the heat supply network is continuously heated by utilizing the exhaust steam of a part of intermediate pressure cylinders of the cogeneration unit and/or the exhaust steam of the intermediate pressure cylinders of the adjacent cogeneration unit; in high back pressure heat release mode: if the temperature of the first part of return water of the heat supply network heated by the low-pressure cylinder is lower than the set temperature, continuously heating the first part of return water of the heat supply network by using the steam discharged by the intermediate pressure cylinder of the adjacent cogeneration unit; if the temperature of the high-temperature heat supply network water output by the heat reservoir is lower than the set temperature or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir is lower than the set temperature, continuously heating the second part of heat supply network backwater by utilizing the steam exhausted by the intermediate pressure cylinder of the adjacent cogeneration unit; low cylinder near zero force heat release mode: if the temperature of the high-temperature heat supply network water output by the heat reservoir is lower than the set temperature or the temperature of the second part of heat supply network backwater heated by the heat-absorbing and heat-releasing medium in the heat reservoir is lower than the set temperature, the second part of intermediate pressure cylinder exhaust steam is utilized to continuously heat the high-temperature heat supply network water/the heated second part of heat supply network backwater; and if the heat of the steam discharged by the second part of intermediate pressure cylinders is lower than the heat of heating the first part of return water of the heat supply network or the first part of return water of the heat supply network and the high-temperature return water of the heat supply network/the heated second part of return water of the heat supply network to a set temperature, simultaneously or subsequently heating the first part of return water of the heat supply network or the first part of return water of the heat supply network and the high-temperature return water of the heat supply network/the heated second part of return water of the heat supply network by using the steam discharged by the intermediate pressure cylinders of the adjacent cogeneration units.
According to the invention, when the cogeneration unit is a wet cooling unit or an indirect air cooling unit, the low-pressure cylinder exhaust steam heating heat supply network backwater and the low-pressure cylinder exhaust steam are cooled in the condenser by using circulating water of the cooling tower; in the high back pressure heat storage mode and the high back pressure heat release mode: the mixture of the non-condensable gas and part of the steam in the condenser is extracted by a vacuum pump, the non-condensable gas and part of the steam extracted from the condenser are selectively condensed, and condensed water is sent back to the condenser; in the low-pressure cylinder near-zero output heat storage mode and the low-pressure cylinder near-zero output heat release mode: the vacuum environment in the condenser is kept through the vacuum pump and the auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, noncondensable gas and part of steam extracted from the condenser are condensed, and condensed water is sent back to the condenser.
According to the invention, when the cogeneration unit is a direct air cooling unit, the exhaust steam of the low-pressure cylinder is cached by the exhaust device and then enters the condenser to heat the return water of the heating network or enters the air cooling island; in the high back pressure heat storage mode and the high back pressure heat release mode: the method comprises the following steps of (1) extracting a mixture of non-condensable gas and part of steam in a condenser through a vacuum pump, optionally condensing the non-condensable gas and part of the steam extracted from the condenser, and sending condensed water to a steam exhaust device; in the low-pressure cylinder near-zero output heat storage mode and the low-pressure cylinder near-zero output heat release mode: the working pressure of the air cooling island is reduced through the suction of the vacuum pump and the auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, non-condensable gas and part of steam extracted from the air cooling island are condensed, and condensed water is sent to the steam exhaust device.
According to the invention, when the heat load demand and the electric load demand are both high and the electricity production quantity and the heat production quantity of the unit are matched with the corresponding demands, a conventional high back pressure mode is adopted; when the electric load demand is low, the heat load demand is high, and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional low-pressure cylinder near-zero output mode is adopted; the conventional high back pressure mode is: all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder to do work, the formed exhaust steam of the low pressure cylinder heats the return water of the heat supply network, and if the temperature of the return water of the heat supply network heated by the exhaust steam of the low pressure cylinder is lower than the set temperature, the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit is used for continuously heating the return water of the heat supply network; the conventional low-pressure cylinder near-zero force mode is as follows: and the steam exhausted by the intermediate pressure cylinders of the second part heats the return water of the heat supply network, and if the heat of the steam exhausted by the intermediate pressure cylinders of the second part is lower than the heat for heating the return water of the heat supply network to a set temperature, the steam exhausted by the intermediate pressure cylinders of adjacent cogeneration units is used for heating the return water of the heat supply network simultaneously or subsequently.
According to the invention, when the cogeneration unit is a wet cooling unit or an indirect air cooling unit, the low-pressure cylinder exhaust steam heating heat supply network backwater and the low-pressure cylinder exhaust steam are cooled in the condenser by using circulating water of the cooling tower; in the conventional high back pressure mode: the mixture of the non-condensable gas and part of the steam in the condenser is extracted by a vacuum pump, the non-condensable gas and part of the steam extracted from the condenser are selectively condensed, and condensed water is sent back to the condenser; in the conventional low-pressure cylinder near-zero force mode: the vacuum environment in the condenser is kept through the vacuum pump and the auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, non-condensable gas and part of steam extracted from the condenser are condensed, and condensed water is sent back to the condenser; when the cogeneration unit is a direct air cooling unit, the low-pressure cylinder exhaust steam is cached by an exhaust device and then enters a condenser to heat a heating network to return water or enters an air cooling island; in the conventional high back pressure mode: the method comprises the following steps of (1) extracting a mixture of non-condensable gas and part of steam in a condenser through a vacuum pump, optionally condensing the non-condensable gas and part of the steam extracted from the condenser, and sending condensed water to a steam exhaust device; in the conventional low-pressure cylinder near-zero force mode: the working pressure of the air cooling island is reduced through the suction of the vacuum pump and the auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, non-condensable gas and part of steam extracted from the air cooling island are condensed, and condensed water is sent to the steam exhaust device.
The invention provides a heating system of the cogeneration unit, which is used for the heating method of the cogeneration unit, and comprises a medium pressure cylinder, a low pressure cylinder, a condenser, a heat supply network heater, a cooling tower, a heat reservoir and a controller; the steam outlet of the intermediate pressure cylinder is selectively and directly communicated with the steam inlet of the low pressure cylinder or communicated with the low pressure cylinder through a temperature and pressure reducing device; the steam outlet of the intermediate pressure cylinder is selectively communicated with the hot side inlet of the heat supply network heater; the steam exhaust port of the low pressure cylinder is communicated with the hot side inlet of the condenser; a cold side inlet of the condenser is selectively communicated with a heat supply network return pipe and an outlet of the cooling tower; a cold side outlet of the condenser is selectively communicated with an inlet of the cooling tower and a cold side inlet of the heat supply network heater; a cold side inlet and a cold side outlet of the heat reservoir are selectively communicated with a heat supply network return pipe and a cold side inlet of the condenser; the hot side inlet and outlet of the heat reservoir are selectively communicated with the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and the heat supply network water supply pipe; the cold side inlet of the heat supply network heater is also selectively communicated with a heat supply network water return pipe; the outlet of the cold side of the heat supply network heater is communicated with a heat supply network water supply pipe; the controller controls the steam outlet of the intermediate pressure cylinder to be selectively communicated with the steam inlet of the low pressure cylinder directly or through a temperature and pressure reducing device, controls the steam outlet of the intermediate pressure cylinder to be selectively communicated with the hot side inlet of the heat supply network heater, controls the cold side inlet of the condenser to be selectively communicated with the hot side return pipe and the outlet of the cooling tower, controls the cold side outlet of the condenser to be selectively communicated with the inlet of the cooling tower and the cold side inlet of the heat supply network heater, controls the cold side inlet and outlet of the heat reservoir to be selectively communicated with the hot side return pipe and the cold side inlet of the condenser, and controls the hot side inlet and outlet of the heat reservoir to be selectively communicated with the cold side outlet of the condenser and the cold side inlet of the heat supply network heater, and the selective communication between the cold side outlet of the heat supply network heater and the heat supply network water supply pipe is controlled.
According to the invention, the hot side inlet of the heat supply network heater is also selectively communicated with the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit; the heating system of the cogeneration unit also comprises a vacuum pump, a steam cooler and an auxiliary vacuumizing device; the inlet of the auxiliary vacuumizing device is communicated with the condenser; the outlet of the auxiliary vacuumizing device is communicated with the hot side inlet of the steam cooler; a hot-side gas outlet of the steam cooler is communicated with an inlet of a vacuum pump; a hot-side liquid outlet of the steam cooler is selectively communicated with the condenser; an auxiliary vacuum pumping device bypass is also provided which can be switched on and off for selectively short-circuiting the auxiliary vacuum pumping device.
The invention further provides a heating system of the cogeneration unit, which is used for any one of the heating methods of the cogeneration unit, and comprises a medium pressure cylinder, a low pressure cylinder, a condenser, a heating network heater, an air cooling island, a heat reservoir, a steam exhaust device and a controller; the steam outlet of the intermediate pressure cylinder is selectively and directly communicated with the steam inlet of the low pressure cylinder or communicated with the low pressure cylinder through a temperature and pressure reducing device; the steam outlet of the intermediate pressure cylinder is selectively communicated with the hot side inlet of the heat supply network heater; the steam outlet of the low pressure cylinder is communicated with the upper part of the steam exhaust device; the upper part of the steam exhaust device is also selectively communicated with a hot side inlet of the condenser and an inlet of the air cooling island; a cold side inlet of the condenser is communicated with a heat supply network water return pipe; a cold side outlet of the condenser is communicated with a cold side inlet of the heat supply network heater; a cold side inlet and a cold side outlet of the heat reservoir are selectively communicated with a heat supply network return pipe and a cold side inlet of the condenser; the hot side inlet and outlet of the heat reservoir are selectively communicated with the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and the heat supply network water supply pipe; the outlet of the cold side of the heat supply network heater is communicated with a heat supply network water supply pipe; the controller controls the steam outlet of the intermediate pressure cylinder to be selectively communicated with the steam inlet of the low pressure cylinder directly or through a temperature and pressure reducing device, controls the steam outlet of the intermediate pressure cylinder to be selectively communicated with the hot side inlet of the heat supply network heater, controls the upper part of the steam exhaust device to be selectively communicated with the hot side inlet of the condenser and the inlet of the air cooling island, controls the cold side inlet and outlet of the heat reservoir to be selectively communicated with the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and the heat supply network pipe.
According to the invention, the hot side inlet of the heat supply network heater is also selectively communicated with the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit; the heating system of the cogeneration unit also comprises a vacuum pump, a steam cooler and an auxiliary vacuumizing device; the inlet of the auxiliary vacuumizing device is selectively communicated with the air cooling island and the condenser; the outlet of the auxiliary vacuumizing device is communicated with the hot side inlet of the steam cooler; a hot-side gas outlet of the steam cooler is communicated with an inlet of a vacuum pump; the hot-side liquid outlet of the steam cooler is selectively communicated with the lower part of the steam exhaust device; an auxiliary vacuum pumping device bypass is also provided which can be switched on and off for selectively short-circuiting the auxiliary vacuum pumping device.
(III) advantageous effects
The invention has the beneficial effects that:
the heat supply method and the heat supply system can perform a high-pressure back-pressure heat supply mode and a low-pressure cylinder near-zero output heat supply mode, on one hand, the heat supply capacity of the unit can be effectively improved by adopting the high-back-pressure heat supply mode under the same input heat quantity, the generated output of the low-pressure cylinder in a heat supply state can be increased, the cold source loss of the unit is reduced, the heat supply economical efficiency of the unit is improved, and on the other hand, the heat supply capacity of the unit can be improved by adopting the low-pressure cylinder near-zero output heat supply mode, the generated energy of steam in the low-pressure cylinder can be greatly reduced, the thermoelectric output proportion of the. On the basis, through the arrangement of the heat reservoir, the high-backpressure heat storage and heat release mode and the low-pressure cylinder near-zero output heat storage and heat release mode can be increased on the basis of the conventional high-backpressure mode and the conventional low-pressure cylinder near-zero output mode, the contradiction that the thermal load demand of the unit and the electric load peak regulation of the power grid are difficult to schedule at the same time in the heating period can be relieved, the unit can adapt to the deep peak regulation demand of the power grid in the heating period, the peak regulation flexibility of the unit is improved, and the unit competitiveness of a power plant is increased. In addition, the heat reservoir can fully utilize the outstanding advantages of good heat supply index economy and low heat supply and power generation coal consumption of a high back pressure heat supply mode and a low-pressure cylinder near-zero output heat supply mode, and the peak regulation capacity of the unit is expanded while the heat supply economy of the whole plant can be improved in multiple time periods.
Drawings
Fig. 1 is a schematic structural view of an embodiment of a heating system according to the present invention, wherein the unit is a wet cooling unit or an indirect air cooling unit;
fig. 2-7 are schematic views of different modes of the heating method according to the present invention when applying an embodiment of the heating system of fig. 1, and only the conducting paths are shown in fig. 2-7;
FIG. 8 is a schematic structural view of another embodiment of the heating system of the present invention, wherein the unit is a direct air-cooling unit;
fig. 9-14 are schematic diagrams of different modes of the heating method of the present invention when one embodiment of the heating system in fig. 8 is applied, and only the conducting path is shown in fig. 9-14.
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1: a high pressure cylinder; 2: an intermediate pressure cylinder; 3: a low pressure cylinder; 4: a generator; 5: a cooling tower; 6: a condenser; 7: a heat supply network water return pump; 8: a heat supply network heater; 9: a heat reservoir; 10: an auxiliary vacuum-pumping device; 11: a steam cooler; 12: a vacuum pump; 13: a temperature and pressure reducing device; 14: a flow measuring device; 15: a butterfly valve; 16: the middle pressure cylinder exhausts steam to the low pressure cylinder and enters the flow control valve; 17: the intermediate pressure cylinder exhausts steam to a heating network heater valve; 18: a bypass valve of the auxiliary vacuum pumping device; 19: condensing water of the steam cooler to a condenser valve; 20: a cooling tower circulating water inlet valve; 21: a water outlet valve for circulating water of the cooling tower; 22: a condenser heat supply network backwater outlet valve; 23: a condenser heat supply network backwater inlet valve; 24: a cold side inlet and outlet reversing valve of the heat reservoir; 25: a change valve is arranged at the inlet and the outlet of the hot side of the first heat reservoir; 26: a change valve is arranged at the inlet and the outlet of the hot side of the second heat reservoir; 27: a heat supply network water return pipe; 28: a heat supply network water supply pipe; 29: a noncondensable gas discharge pipe; 30: a cooling water inlet pipe; 31: a cooling water outlet pipe; 32: a desuperheating water line; 33: an air cooling island; 34: a steam exhaust device; 35: an air cooling island vacuum pumping valve; 36: a steam inlet valve of the condenser; 37: a pipeline (between a hot side inlet of the heat supply network heater and a steam outlet of a medium pressure cylinder of an adjacent cogeneration unit); 38: a heat supply network backwater bypass valve; 39: an air cooling island steam inlet valve; 40: the adjacent machine intermediate pressure cylinder exhausts steam to a heating network heater valve; 41: a condenser vacuum valve; 42: the steam cooler condenses water to the exhaust valve.
Detailed Description
For the purpose of better explaining the present invention and to facilitate understanding, the present invention will be described in detail by way of specific embodiments with reference to the accompanying drawings.
Example one
Referring to fig. 1, the present embodiment provides a heating system of a cogeneration unit, in which a turbine regenerative steam extraction system and a condensing/water supply system are omitted in fig. 1, and other auxiliary devices are omitted in the heating system, and only a system description of main devices is given. The heating system mainly comprises a high-pressure cylinder 1, a medium-pressure cylinder 2, a low-pressure cylinder 3, a generator 4, a cooling tower 5, a condenser 6, a heat supply network water return pump 7, a heat supply network heater 8, a heat reservoir 9, an auxiliary vacuumizing device 10, a steam cooler 11, a vacuum pump 12 and a controller. The heating system of the present embodiment is suitable for both the wet cooling unit and the indirect air cooling unit because of the use of the cooling tower 5.
The steam outlet of the high pressure cylinder 1 is communicated with the steam inlet of the intermediate pressure cylinder 2.
The steam outlet of the intermediate pressure cylinder 2 is selectively communicated with the steam inlet of the low pressure cylinder 3 directly or through a temperature and pressure reducing device 13. Specifically, the steam outlet of the intermediate pressure cylinder 2 is communicated with the steam inlet of the low pressure cylinder 3 through two branches, a butterfly valve 15 is arranged on one branch, and a steam inlet flow regulating valve 16, the temperature and pressure reducing device 13 and a flow measuring device 14 for exhausting steam from the intermediate pressure cylinder to the low pressure cylinder are sequentially arranged on the other branch along the direction far away from the intermediate pressure cylinder 2. When the butterfly valve 15 is opened and the steam exhaust of the intermediate pressure cylinder is closed to the steam inlet flow regulating valve 16 of the low pressure cylinder, the steam exhaust port of the intermediate pressure cylinder 2 is directly communicated with the steam inlet of the low pressure cylinder 3 through the branch where the butterfly valve 15 is located, and the steam exhaust of the intermediate pressure cylinder directly enters the low pressure cylinder 3; when the butterfly valve 15 is closed and the steam inlet flow regulating valve 16 of the middle pressure cylinder is opened when the steam exhaust of the middle pressure cylinder reaches the low pressure cylinder, the steam exhaust of the middle pressure cylinder 2 is communicated with the steam inlet of the low pressure cylinder 3 through the branch where the temperature and pressure reducing device 13 is located, and the steam exhaust of the middle pressure cylinder is subjected to temperature and pressure reduction through the temperature and pressure reducing device 13 to form cooling steam to enter the low pressure cylinder 3. Wherein, the inlet of the desuperheating water of the desuperheating and pressure reducing device 13 is connected with a desuperheating water pipeline 32, and can receive the desuperheating water, and the desuperheating water is mixed with the steam exhaust of the intermediate pressure cylinder, and the steam exhaust of the intermediate pressure cylinder is desuperheated and reduced in pressure. The desuperheating water line 32 may be connected to a condensate system to employ condensate as the desuperheating water.
The high pressure cylinder 1, the intermediate pressure cylinder 2 and the low pressure cylinder 3 are connected with the generator 4, and steam entering the high pressure cylinder 1, the intermediate pressure cylinder 2 and the low pressure cylinder 3 does work to supply the generator 4 to generate electricity.
The steam outlet of the intermediate pressure cylinder 2 is selectively communicated with the hot side inlet of the heating network heater 8 through a pipeline and a valve 17 of the intermediate pressure cylinder on the pipeline for exhausting steam to the heating network heater.
The hot side inlet of the heating network heater 8 is selectively communicated with the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit through a pipeline 37 and the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit on the pipeline 37 to a heating network heater valve 40.
The condenser 6 adopts a high-back-pressure condenser which can adapt to the passing of circulating water of a heat supply network and the passing of circulating water of a main machine.
And a hot side inlet of the condenser 6 is communicated with a steam exhaust port of the low-pressure cylinder 3 through a pipeline.
The cold side inlet of the condenser 6 is selectively communicated with a heat supply network return pipe 27 through a pipeline and a condenser heat supply network return water inlet valve 23 on the pipeline.
The heat reservoir 9 may be a volumetric heat reservoir or contain a heat absorbing and releasing medium. The length of the heat storage time and the amount of the stored heat are determined by the capacity of the heat storage device/the capacity of the heat absorbing and releasing medium, the larger the capacity of the heat storage device/the larger the capacity of the heat absorbing and releasing medium and the stronger the heat absorbing capacity, and the longer the heat storage time, the more the stored heat. The length of the heat release time and the amount of heat released are determined by the capacity of the heat storage device/the capacity of the heat absorbing and releasing medium, and the larger the capacity of the heat storage device/the larger the capacity of the heat absorbing and releasing medium and the stronger the heat release capacity, the longer the heat release time, the more the amount of heat released.
The inlet and outlet of the cold side of the heat reservoir 9 are selectively communicated with the heat supply network return pipe 27 and the inlet of the cold side of the condenser 6. Specifically, the downstream end of the heat supply network water return pipe 27 and the upstream end of a pipeline connected between the heat supply network water return pipe 27 and the cold side inlet of the condenser 6 are communicated with the cold side inlet and outlet of the heat reservoir 9 through the same pipeline, and the pipeline is provided with a heat reservoir cold side inlet and outlet direction changing valve 24, so that the heat reservoir cold side inlet and outlet direction changing valve 24 controls the communication between the heat supply network water return pipe 27 and the cold side inlet of the condenser 6 and the cold side inlet and outlet of the heat reservoir 9.
The cold side inlet of the condenser 6 is also selectively communicated with the outlet of the cooling tower 5 through a pipeline and a cooling tower circulating water inlet valve 20 on the pipeline.
The outlet of the cold side of the condenser 6 is selectively communicated with the inlet of the cooling tower 5 through a pipeline and a cooling tower circulating water outlet valve 21 on the pipeline.
The cold side outlet of the condenser 6 is selectively communicated with the cold side inlet of the heat supply network heater 8 through a pipeline and a condenser heat supply network backwater outlet valve 22 on the pipeline, and a heat supply network backwater pump 7 is further arranged on the pipeline.
The cold side inlet of the heat network heater 8 is optionally in communication with a heat network return 27. Specifically, a pipeline is connected between the downstream of the heat reservoir cold side inlet/outlet direction changing valve 24 and the upstream of the condenser heat supply network backwater outlet valve 22, and a heat supply network backwater bypass valve 38 is arranged on the pipeline to control whether the heat supply network backwater directly moves forward to the heat supply network heater 8 without passing through the condenser 6.
The cold side outlet of the heating network heater 8 is in communication with a heating network water supply pipe 28 via piping.
And a hot side inlet and a hot side outlet of the heat reservoir 9 are selectively communicated with a cold side outlet of the condenser 6, a cold side inlet of the heat supply network heater 8, a cold side outlet of the heat supply network heater 8 and a heat supply network water supply pipe 28. Specifically, the inlet and outlet of the hot side of the heat reservoir 9 are communicated with the pipeline between the outlet of the cold side of the condenser 6 and the inlet of the cold side of the heat supply network heater 8 through a pipeline with a first heat reservoir hot side inlet and outlet direction changing valve 25, and the communication position is located at the downstream of the condenser heat supply network backwater outlet valve 22 and the heat supply network backwater pump 7. Meanwhile, the inlet and outlet of the hot side of the heat reservoir 9 are communicated with the pipeline between the outlet of the cold side of the heat supply network heater 8 and the water supply pipe 28 of the heat supply network through the pipeline with the change valve 26 of the inlet and outlet of the hot side of the second heat reservoir.
The inlet of the auxiliary vacuumizing device 10 is communicated with the condenser 6 through a pipeline, the outlet of the auxiliary vacuumizing device 10 is communicated with the hot-side inlet of the steam cooler 11 through a pipeline, and the hot-side gas outlet of the steam cooler 11 is communicated with the inlet of the vacuum pump 12 through a pipeline, so that the auxiliary vacuumizing device 10, the steam cooler 11 and the vacuum pump 12 are sequentially communicated along the direction far away from the condenser 6. The outlet of the vacuum pump is connected to a non-condensable gas discharge pipe 29. Wherein, the vacuum pump 12 is a water ring vacuum pump.
The cold side inlet of the steam cooler 11 is connected with a cooling water inlet pipe 30, and the cold side outlet is connected with a cooling water outlet pipe 31.
And the hot side liquid outlet of the steam cooler 11 is selectively communicated with the condenser 6. Specifically, a hot-side liquid outlet of the steam cooler 11 is communicated with the condenser 6 through a pipeline, and a steam cooler condensed water to condenser valve 19 is arranged on the pipeline to control the communication between the hot-side liquid outlet of the steam cooler 11 and the condenser 6.
At the same time, an auxiliary vacuum pump bypass which can be switched on and off is provided for selectively short-circuiting the auxiliary vacuum pump 10. One end of the auxiliary vacuumizing device bypass is connected to the upstream of the auxiliary vacuumizing device 10, the other end of the auxiliary vacuumizing device bypass is connected to the downstream of the auxiliary vacuumizing device 10, and an auxiliary vacuumizing device bypass valve 18 is arranged on the auxiliary vacuumizing device bypass and used for controlling the auxiliary vacuumizing device bypass to be switched on and off.
The controller is in communication with the valves and the electrical control equipment to control the operation of the valves and the operation of the electrical control equipment.
The heat supply method of the cogeneration unit executed by the heat supply system is introduced as follows, and the heat supply method at least comprises six heat supply modes, namely a conventional high back pressure mode, a high back pressure heat storage mode, a high back pressure heat release mode, a conventional low pressure cylinder near zero output mode, a low pressure cylinder near zero output heat storage mode and a low pressure cylinder near zero output heat release mode.
Wherein, the high back pressure mode (including the conventional high back pressure mode, the high back pressure heat storage mode and the high back pressure heat release mode) refers to: the heat supply network backwater is adopted to replace unit circulating water and is used for absorbing the exhaust waste heat of the low-pressure cylinder, the exhaust back pressure of the low-pressure cylinder of the heat supply steam turbine generator unit is properly increased during heat supply operation, and the heat supply network backwater can reach higher outlet water temperature after absorbing the exhaust waste heat of the low-pressure cylinder.
The low-pressure cylinder near-zero output mode (including a conventional low-pressure cylinder near-zero output mode, a low-pressure cylinder near-zero output heat storage mode and a low-pressure cylinder near-zero output heat release mode) refers to: compared with the traditional method for extracting partial exhaust steam of the intermediate pressure cylinder for heating, the method breaks through the minimum steam inlet amount designed by the low pressure cylinder, only a small amount of cooled intermediate pressure cylinder steam (cooling steam for short) is introduced into the low pressure cylinder, the work of the cooling steam is almost zero when the cooling steam passes through the low pressure cylinder, the heat supply steam extraction amount of the unit is increased, and the flexibility of the output ratio between the heat supply amount of the unit and the generated energy is improved.
The following modes take the heat load demand of an external heat user and the height of the electric load demand of the unit of the power grid as the standard for selecting the application mode. When the unit is in the high back pressure heat supply mode, a large amount of exhaust steam waste heat is used for heating after steam works through the high, medium and low pressure cylinders, and at the moment, as much steam as possible in the unit is subjected to the three cylinders to do work to generate electricity, so that the unit can provide large electric load and large heat load in the high back pressure heat supply mode, but the generated energy and the heat supply amount of the unit in the high back pressure heat supply mode are proportionally generated, the heat supply amount of the unit is large when the generated energy of the unit is large in the mode, and the heat supply amount of the unit is small when the generated energy of the unit is small. In the low-pressure cylinder near-zero output heat supply mode, most of the medium-pressure cylinder exhaust steam does not work through the low-pressure cylinder any more, but directly enters the heat supply network heater to heat the return water of the heat supply network, so that the low-pressure cylinder power generation output of the unit is reduced, therefore, the unit in the mode has smaller power generation amount and larger heat supply amount, but the power generation amount and the heat supply amount of the low-pressure cylinder near-zero output heat supply mode unit are also proportionally produced, in the mode, the heat supply amount of the unit is large when the power generation amount of the unit is large, and the heat supply amount of the unit is small when the power generation amount of the unit is small. The magnitude of the heat load demand of the external heat consumer is determined by the influence of the local weather environment temperature and the like, and the magnitude of the unit electric load is determined by the power grid dispatching adjustment. The generating capacity of the unit and the heat supply output of the unit are different along with the selection mode of the heat supply mode, but the electric quantity output of the heat output is synchronous, and the modes are different only in the heat and electricity output proportion. When the demand of the heat load of an external heat user and the demand of the power generation load of the unit by power grid dispatching correspond to the thermoelectric output proportion when the unit selects a corresponding heat supply mode, the required heat and the required electric quantity are simultaneously produced without breaking the production mode of thermoelectric cooperative output of the unit; when the demand of the heat load of the external heat user and the demand of the power grid dispatching on the generating load of the unit exceed the corresponding relation of the thermoelectric output proportion of the unit in different heat supply modes, and in order to more fully utilize the waste heat of the unit and reduce the loss of a cold source of the unit, the demand contradiction between the demand of the heat load of the external user and the demand of the power grid dispatching on the electric load is relieved and solved by utilizing a heat storage system (comprising a heat storage device and corresponding pipelines). It will also be appreciated that the levels of thermal and electrical load demands referred to herein are a set of relative concepts, with the "high" and "low" limits being imposed in practice by the modes of generation and supply of heat that the unit can achieve.
Generally speaking, in the invention, when the electric load demand is low and the heat load demand is high and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional low-pressure cylinder near-zero output mode is adopted; when the heat load demand and the electric load demand are high and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional high back pressure mode is adopted; when the heat load demand is low and the electric load demand is high, a high back pressure heat storage mode is adopted; when the heat load demand and the electric load demand are both high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, a high back pressure heat release mode is adopted; when the electric load demand and the heat load demand are both low, a low-pressure cylinder near-zero-output heat storage mode is adopted; and when the electric load demand is low, the heat load demand is high, and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, adopting a low-pressure cylinder near-zero output heat release mode. In order to make the above "high" and "low" of the thermal load demand and the electrical load demand more definite, the following judgment equation is used as a reference:
the steam turbine generator unit is characterized in that under the condition of steam input heat with the same parameters: when the unit adopts a conventional high-backpressure heat supply mode, the heat load output of the unit is A, and the electric load output of the unit is B; when the unit adopts a conventional low-pressure cylinder near-zero output heat supply mode, the heat load output of the unit is C, and the electric load output of the unit is D; and satisfies A < C, B > D, A ÷ B < C ÷ D.
When the ratio of the heat load demand to the electric load demand is A/B, adopting a conventional high-back-pressure heat supply mode;
when the proportion of the thermal load demand to the electrical load demand is C/D, adopting a conventional low-pressure cylinder near-zero-output heat supply mode;
when the electric load demand is greater than D and the ratio of the heat load demand to the electric load demand is less than A/B, adopting a high-back-pressure heat storage mode;
when the electric load demand is greater than D and the ratio of the heat load demand to the electric load demand is greater than A/B but less than C/D, adopting a high back pressure heat release mode;
when the electric load demand is D and the ratio of the heat load demand to the electric load demand is less than C/D, adopting a low-pressure cylinder near-zero-output heat storage mode;
when the electric load demand is D and the ratio of the heat load demand to the electric load demand is greater than C/D, adopting a low-pressure cylinder near-zero output heat release mode;
wherein, the parameter A, B, C, D has different values according to different units and different working conditions.
Referring to fig. 2, when both the thermal and electrical load demands are high and the electricity and heat production of the unit match the respective demands, a conventional high back pressure mode is employed. The conventional high back pressure mode is:
the controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the condenser heat supply network backwater outlet valve 22 and the condenser heat supply network backwater inlet valve 23 to be opened. The controller controls the steam inlet flow regulating valve 16 of the middle-pressure cylinder, the steam outlet heat supply network heater valve 17 of the middle-pressure cylinder, the cooling tower circulating water inlet valve 20, the cooling tower circulating water outlet valve 21, the heat reservoir cold side inlet and outlet direction changing valve 24, the first heat reservoir hot side inlet and outlet direction changing valve 25, the second heat reservoir hot side inlet and outlet direction changing valve 26 and the heat supply network water return bypass valve 38 to be closed. Therefore, all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder 3 to do work, and the formed exhaust steam of the low pressure cylinder enters the condenser 6. The return water of the heat supply network sent from the return water pipe 27 of the heat supply network also enters the condenser 6, and the exhaust steam of the low-pressure cylinder heats the return water of the heat supply network in the condenser 6.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is equal to the set temperature, the controller controls the valve 40 of the heat supply network heater to close when the exhaust steam of the intermediate pressure cylinder of the adjacent machine flows, the return water of the heat supply network is sent to the water supply pipe 28 of the heat supply network through the heat supply network heater 8 and is used as the water supply of the heat supply network, and the return water of the heat supply network only passes through the heat supply network heater 8 and is not heated by the heat supply network heater.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is lower than the set temperature, the controller controls the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit to open the valve 40 of the heat supply network heater, the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit is introduced into the heat supply network heater 8, the return water of the heat supply network is continuously heated in the heat supply network heater 8 by utilizing the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit, and the return water of the heat supply network heated by the heat supply network heater 8 is sent to the water supply pipe 28 of the heat supply network to be used as.
Meanwhile, the controller controls the vacuum pump 12 to start, and non-condensable gas and part of steam in the condenser 6 are pumped out through the auxiliary vacuumizing device bypass, the steam cooler 11 and the vacuum pump 12, so that the vacuum environment in the condenser 6 is maintained. The controller can control the steam cooler 11 to receive cooling water sent by the cooling water inlet pipe 30, and simultaneously open the condensed water of the steam cooler to the condenser valve 19. The cooling water exchanges heat with the non-condensing gas and the steam, the non-condensing gas and the steam are condensed to form condensed water and the non-condensing gas, the condensed water is sent back to the condenser 6 and is discharged from a hot side outlet of the condenser 6 together with the condensed water formed by the low-pressure cylinder steam discharge, the cooling water is discharged through a cooling water outlet pipe 31 after being heated, and the non-condensing gas enters the vacuum pump 12 and then enters a non-condensing gas discharge pipe 29. Of course, it is also possible to simply pass the noncondensable gas and vapor through the vapor cooler 11 into the vacuum pump 12 without introducing cooling water.
Therefore, the conventional high back pressure mode can not only fully utilize the waste steam waste heat of the unit for heating to improve the heating economy of the unit, but also enable the steam which needs to be extracted from part of the exhausted steam of the middle pressure cylinder to continue to work in the low pressure cylinder for generating power, thereby improving the peak regulation capacity of the power grid dispatching on the upper limit of the generated power of the unit in the heating state of the unit. When the demand of the power grid on the unit electrical load is low in the heat supply period and the demand of the heat grid on the unit thermal load is high, a part of steam in the unit low-pressure cylinder always needs to flow to do work to generate power when the conventional high-backpressure mode is adopted, so that the generating load of the unit in the conventional high-backpressure mode cannot be too low, and in order to enable the unit to meet the load requirement of power grid scheduling on the deep peak regulation lower limit of the generating load of the unit, the heat supply running state of the unit with small generating output and large heat supply load can be realized by adopting the near-zero output mode of the conventional low-pressure cylinder. That is, when the demand of the electrical load is low and the demand of the thermal load is high and the generated electricity and the generated heat of the unit are matched with the corresponding demands, referring to fig. 3, a normal low-pressure cylinder near-zero output mode is adopted.
The conventional low-pressure cylinder near-zero force mode is as follows:
the controller controls the steam inlet flow regulating valve 16 of the middle pressure cylinder for discharging steam to the low pressure cylinder, the steam heater valve 17 of the middle pressure cylinder for discharging steam to the heat supply network, the condensed water condenser valve 19 of the steam cooler, the circulating water inlet valve 20 of the cooling tower, the circulating water outlet valve 21 of the cooling tower and the return water bypass valve 38 of the heat supply network to be opened. The controller controls the steam cooler 11 to be started and the temperature and pressure reducing device 13 to be started. The controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the condenser heat supply network backwater outlet valve 22, the condenser heat supply network backwater inlet valve 23, the heat reservoir cold side inlet and outlet direction changing valve 24, the first heat reservoir hot side inlet and outlet direction changing valve 25 and the second heat reservoir hot side inlet and outlet direction changing valve 26 to be closed. Thereby, the intermediate pressure cylinder exhaust steam is divided into two parts. The first part of the intermediate pressure cylinder exhaust steam is cooled after being subjected to temperature reduction and pressure reduction, enters the low pressure cylinder 3, the formed low pressure cylinder exhaust steam enters the condenser 6, the cooling tower circulating water also enters the condenser 6 and is heated by the low pressure cylinder exhaust steam, and the heated cooling tower circulating water returns to the cooling tower 5. The second part of the intermediate pressure cylinder exhaust steam enters the heat supply network heater 8, the heat supply network return water sent by the heat supply network return water pipe 27 enters the heat supply network heater 8 to be heated by the intermediate pressure cylinder exhaust steam, and the heat supply network return water is formed after heating and is sent to the heat supply network water supply pipe 28.
If the heat of the steam exhausted by the second part of the intermediate pressure cylinders is equal to the heat of the return water of the heat supply network heated to the set temperature, the controller controls the steam exhausted by the intermediate pressure cylinders of the adjacent machines to close the heater valve 40 of the heat supply network. The return water of the heat supply network is heated only by the exhaust steam of the medium pressure cylinder of the same unit.
If the heat of the steam exhaust of the intermediate pressure cylinder in the second part is lower than the heat for heating the return water of the heat supply network to the set temperature, the controller controls the steam exhaust of the intermediate pressure cylinder in the adjacent machine to open the valve 40 of the heater of the heat supply network, and the steam exhaust of the intermediate pressure cylinder in the adjacent machine is introduced into the heater 8 of the heat supply network, so that the steam exhaust of the intermediate pressure cylinder in the adjacent cogeneration unit and the steam exhaust of the intermediate pressure cylinder in the second part of the same machine set are simultaneously or subsequently utilized to heat the return water of the heat supply network (in the heater 8 of the heat supply network, the steam exhaust of the intermediate pressure cylinder in the same machine.
Meanwhile, the controller controls the vacuum pump 12 and the auxiliary vacuum pumping device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, so that non-condensable gas and part of steam in the condenser 6 are pumped out, and the vacuum environment in the condenser 6 is maintained. Meanwhile, the controller controls the steam cooler 11 to be started, non-condensing gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water in the steam cooler 11 to form condensing water and non-condensing gas, the condensing water is sent back to the condenser 6, the condensing water formed by the condensing water and low-pressure cylinder exhaust steam is discharged from a hot side outlet of the condenser 6 together, the cooling water is heated and then discharged through a cooling water outlet pipe 31, and the non-condensing gas enters the vacuum pump 12 and then enters a non-condensing gas discharge pipe 29. Wherein the cooling water can be obtained from an open water system in a factory.
In this embodiment, in order to prevent the low pressure cylinder from exhausting and blowing overheated when the low pressure cylinder only maintains small flow cooling steam during the low pressure cylinder near zero output heat supply, two improvements are made, firstly, the small flow cooling steam entering the low pressure cylinder is desuperheated through a desuperheating and depressurizing device before entering the low pressure cylinder, a desuperheating water source can be obtained from condensed water, the steam flow before desuperheating is realized by adjusting a medium pressure exhaust steam to a low pressure cylinder steam inlet flow regulating valve 16, and a flow measuring device 14 is additionally arranged for accurately measuring the cooling steam entering the low pressure cylinder. And secondly, the low-pressure cylinder exhaust steam needs to maintain ultralow back pressure operation, an auxiliary vacuumizing device 10 (a roots vacuum pump can be adopted as the auxiliary vacuumizing device) is additionally arranged on the basis of a vacuum pump 12 in order to realize the ultralow back pressure operation of the low-pressure cylinder, a steam cooler 11 is additionally arranged on an outlet pipeline of the auxiliary vacuumizing device 10 in order to reduce the temperature of an inlet medium of the original vacuum pump 12, and after a mixture of non-condensed gas and steam is cooled by the steam cooler 11, the steam in the mixture is cooled and condensed by the steam cooler, and is recycled to a large turbine condensed water system through a steam cooler condensed water drain valve 19 and a condenser, so that the effective recycling of working media is realized. Meanwhile, the temperature of the non-condensable gas cooled by the steam cooler 11 is reduced, and the working output of the vacuum pump 12 is improved. Meanwhile, the auxiliary vacuum pump bypass valve 18 is additionally arranged, so that the auxiliary vacuum pumping device 10 can be flexibly put into use, and the auxiliary vacuum pumping device bypass valve 18 can be opened to recover to the original vacuum pump vacuum pumping operation mode in the non-heating period.
Although the heating economy of the conventional high back pressure mode and the conventional low pressure cylinder near-zero output mode is greatly improved in the power generation output and the heating capacity of the unit compared with the traditional steam extraction heating, and the heating flexibility of the conventional low pressure cylinder near-zero output mode is also improved compared with the traditional steam extraction heating, the heat supply and the power generation of the unit are still simultaneously output in the conventional high back pressure mode and the conventional low pressure cylinder near-zero output mode, and the deep peak regulation control of the power grid to the unit in the heating period is not facilitated. Therefore, in the embodiment, by additionally arranging the heat storage device, the contradiction of the thermoelectric requirements of the unit in different time is solved within a certain time, and the thermoelectric decoupling of the whole plant is realized.
When the thermal load demand is low and the electrical load demand is high, a high back pressure heat storage mode is employed. Referring to fig. 4, the high back pressure heat storage mode is:
the controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the condenser heat supply network backwater outlet valve 22 and the condenser heat supply network backwater inlet valve 23 to be opened. The controller controls a cold side inlet and outlet valve 24 of the heat reservoir and a hot side inlet and outlet direction changing valve 25 of the first heat reservoir so that the direction in which the cold side inlet and outlet of the heat reservoir are used as outlets and the hot side inlet and outlet of the heat reservoir are used as inlets is opened. The controller controls the steam discharged by the medium pressure cylinder to close the steam inlet flow regulating valve 16 of the low pressure cylinder, the cooling tower circulating water inlet valve 20, the cooling tower circulating water outlet valve 21, the heat side inlet and outlet diversion valve 26 of the second heat reservoir and the heat supply network water return bypass valve 38. Therefore, the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder 3 to do work, and the formed exhaust steam of the low pressure cylinder enters the condenser 6. The return water of the heat supply network with the flow rate of A + B also enters the condenser 6, and the exhaust steam of the low-pressure cylinder heats the return water of the heat supply network with the flow rate of A + B in the condenser 6. The heated return water of the heat supply network is divided into two parts, the heated return water of the first part with the flow rate of A enters the heat supply network heater 8, and the heated return water of the second part with the flow rate of B enters the heat reservoir 9. In this embodiment, the heat reservoir 9 is a volumetric heat reservoir, and then the second part of the return water of the heat supply network with the flow rate B enters the heat reservoir 9 to be directly stored in the heat reservoir 9 as high-temperature heat supply network water, and the low-temperature heat supply network water with the corresponding flow rate B in the heat reservoir 9 leaves the heat reservoir 9 to be continuously heated by the low-pressure cylinder exhaust steam, so that the heat reservoir stores heat. Of course, in other embodiments, if there is a heat absorbing and releasing medium in the heat reservoir 9, the second part of the return water from the heat supply network with the flow rate B enters the heat reservoir 9 to release heat to the heat absorbing and releasing medium in the heat reservoir 9, and then the second part of the return water from the heat supply network leaves the heat reservoir 9 to continue to circulate and be heated by the low-pressure cylinder exhaust steam, so that the heat reservoir stores heat.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is equal to the set temperature, the controller controls the valve 17 of the steam exhaust to the heat supply network heater of the intermediate pressure cylinder and the valve 40 of the steam exhaust to the heat supply network heater of the adjacent machine to be closed, all the exhaust steam of the intermediate pressure cylinder enters the low-pressure cylinder 3, and the part (namely, the first part of return water of the heat supply network) of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder, which does not enter the heat reservoir, is used as supply water of the heat supply network and sent to a supply water pipe 28 of the heat supply network through the.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is lower than the set temperature, the controller controls one or two of the valve 17 of the intermediate pressure cylinder exhaust steam to the heat supply network heater and the valve 40 of the adjacent intermediate pressure cylinder exhaust steam to the heat supply network heater to be opened (the unopened valve is closed), and then the exhaust steam of a part of intermediate pressure cylinders of the same unit and/or the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit is introduced into the heat supply network heater 8 to continuously heat the return water of the heat supply network. At this time, the first part of the returned heat supply network water reheated by the heat supply network heater 8 is discharged and sent to the heat supply network water supply pipe 28 as the heat supply network water supply.
Meanwhile, the controller controls the vacuum pump 12 and the auxiliary vacuum pumping device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, so that non-condensable gas and part of steam in the condenser 6 are pumped out, and the vacuum environment in the condenser 6 is maintained. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 19 of the condenser is opened, non-condensed gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6, the condensed water formed by the condensed water and low-pressure cylinder exhaust steam is exhausted from the hot side outlet of the condenser 6 together, the cooling water is heated and then exhausted through the cooling water outlet pipe 31, and the non-condensed gas enters the vacuum pump 12 and then enters the non-condensed gas exhaust pipe 29. Wherein the cooling water can be obtained from an open water system in a factory.
And when the heat load demand and the electric load demand are both high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, adopting a high back pressure heat release mode. Referring to fig. 5, the high back pressure heat release pattern is:
the controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the condenser heat supply network backwater outlet valve 22 and the condenser heat supply network backwater inlet valve 23 to be opened. The controller controls the heat reservoir cold side inlet and outlet direction changing valve 24 to open the heat reservoir cold side inlet and outlet as the inlet direction. The controller controls the steam exhaust of the intermediate pressure cylinder to the low pressure cylinder to enter the steam flow regulating valve 16, the steam exhaust of the intermediate pressure cylinder to the heat supply network heater valve 17, the cooling tower circulating water inlet valve 20, the cooling tower circulating water outlet valve 21, the heat reservoir cold side inlet and outlet diversion valve 24 and the heat supply network backwater bypass valve 38 to be closed. Therefore, all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder 3 to do work, and the formed exhaust steam of the low pressure cylinder enters the condenser 6. The return water of the heat supply network sent by the return water pipe 27 of the heat supply network is divided into two parts, the first part of the return water of the heat supply network with the flow rate of E enters the condenser 6, the low-pressure cylinder exhaust steam heats the first part of the return water of the heat supply network in the condenser 6, the second part of the return water of the heat supply network with the flow rate of F enters the heat reservoir 9 and then is stored in the heat reservoir 9 as low-temperature heat supply network water, and meanwhile, the high-temperature heat supply network water with the flow rate of F is output to the heat reservoir 9. Herein, the "high temperature network water" and the "low temperature network water" are a set of relative concepts, and are not limited to specific temperatures. Of course, when the heat reservoir 9 has the heat-absorbing and heat-releasing medium, the second part of the return water of the heat supply network with the flow rate F flows through the heat-absorbing and heat-releasing medium of the heat reservoir 9 to be heated and then is output to the heat reservoir 9.
If the temperature of the first part of return water of the heat supply network heated by the low-pressure cylinder 3 is equal to the set temperature and the temperature of the high-temperature water of the heat supply network output by the heat reservoir 9 is equal to the set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of return water of the heat supply network heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is equal to the set temperature, the controller controls the valve 40 of the heat supply network heater to be closed by the cylinder in the adjacent machine, the first part of return water of the heat supply network passes through the heat supply network heater 8 but is not heated, and simultaneously the controller controls the valve 25 of the inlet and outlet of the hot side of the first heat reservoir to be closed and the valve 26 of the inlet and outlet of the hot side of the second heat reservoir to be opened in the direction that the inlet and outlet of the hot side of the heat reservoir is used as an outlet, so that the, the flow rate of the water supplied by the heat supply network is E + F.
If the temperature of the first part of return water of the heat supply network heated by the low-pressure cylinder 3 is lower than the set temperature, the controller controls the steam exhaust of the intermediate pressure cylinder of the adjacent machine to open the valve 40 of the heater of the heat supply network, and the steam exhaust of the intermediate pressure cylinder of the adjacent machine is led into the heater 8 of the heat supply network, so that the first part of return water of the heat supply network is continuously heated in the heater 8 of the heat supply network. Meanwhile, if the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is equal to a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is equal to the set temperature, the controller controls the closing of the inlet/outlet valve 25 at the hot side of the first heat reservoir and opens the inlet/outlet valve 26 at the hot side of the second heat reservoir in the direction in which the inlet/outlet at the hot side of the heat reservoir serves as an outlet, and at this time, the high-temperature heat supply network water output by the heat reservoir 9, the second part of heat supply network backwater heated and the first part of heat supply network backwater heated by the heat. If the temperature of the high-temperature heat supply network water output by the heat reservoir 9 and the heat reservoir 9 is lower than a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is lower than the set temperature, the controller controls the closing of the inlet and outlet valve 26 at the hot side of the second heat reservoir and opens the inlet and outlet valve 25 at the hot side of the first heat reservoir in the direction that the inlet and outlet at the hot side of the heat reservoir are used as outlets, at this time, the high-temperature heat supply network water output by the heat reservoir 9 and the second part of heat supply network backwater heated are heated by the exhaust steam of the intermediate pressure cylinder of the adjacent machine through the heat supply network heater 8, and the first part of heat supply network backwater and.
Meanwhile, the controller controls the vacuum pump 12 and the auxiliary vacuum pumping device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, so that non-condensable gas and part of steam in the condenser 6 are pumped out, and the vacuum environment in the condenser 6 is maintained. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 19 of the condenser is opened, non-condensed gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6, the condensed water formed by the condensed water and low-pressure cylinder exhaust steam is exhausted from the hot side outlet of the condenser 6 together, the cooling water is heated and then exhausted through the cooling water outlet pipe 31, and the non-condensed gas enters the vacuum pump 12 and then enters the non-condensed gas exhaust pipe 29. Wherein the cooling water can be obtained from an open water system in a factory.
The comprehensive utilization of the high-backpressure heat storage mode and the high-backpressure heat release mode ensures that when the heat required by an external heat user in unit time is low, the heat generated by the unit is temporarily stored in the heat storage 9; when the heat required by the external heat consumer increases in unit time and the unit is limited by power generation and cannot generate enough heat in time, the heat stored in the heat reservoir 9 is released to the heat consumer, so that the contradiction between the heat production of the unit and the time requirement of the heat consumer is relieved.
And when the electric load demand and the heat load demand are both low, a low-pressure cylinder near-zero-output heat storage mode is adopted. Referring to fig. 6, the low-pressure cylinder near-zero output heat storage mode is as follows:
the controller controls the steam inlet flow regulating valve 16 of the middle pressure cylinder for discharging steam to the low pressure cylinder, the steam inlet flow regulating valve 17 of the middle pressure cylinder for discharging steam to the heat supply network heater, the cooling tower circulating water inlet valve 20, the cooling tower circulating water outlet valve 21 and the heat supply network water return bypass valve 38 to be opened. The controller controls the temperature and pressure reducing device 13 to start. The controller controls and controls the heat reservoir cold side inlet and outlet direction changing valve 24 and the second heat reservoir hot side inlet and outlet direction changing valve 26 to enable the direction that the heat reservoir cold side inlet and outlet are an outlet and the heat reservoir hot side inlet and outlet are an inlet to be opened. The controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the condenser heat supply network backwater outlet valve 22, the condenser heat supply network backwater inlet valve 23, the first heat reservoir hot side inlet and outlet diversion valve 25 and the adjacent machine intermediate pressure cylinder steam exhaust to heat supply network heater valve 40 to be closed. Thereby, the intermediate pressure cylinder exhaust steam is divided into two parts. The first part of the intermediate pressure cylinder exhaust steam is cooled after being subjected to temperature reduction and pressure reduction, the low pressure cylinder exhaust steam enters the low pressure cylinder 3, the formed low pressure cylinder exhaust steam enters the condenser 6, the cooling tower circulating water enters the condenser 6 to absorb the heat of the low pressure cylinder exhaust steam, and the heated cooling tower circulating water returns to the cooling tower 5. The second part of the intermediate pressure cylinder exhaust steam enters the heat supply network heater 8, and the heat supply network return water sent by the heat supply network return pipe 27 completely enters the heat supply network heater 8 and is heated by the second part of the intermediate pressure cylinder exhaust steam. The first portion of the heated return water from the heat supply network having a flow rate C is discharged as supply water from the heat supply network supply pipe 28. And the heated second part of the return water of the heat supply network with the flow of D enters the heat reservoir to release heat, and then continuously and circularly enters the heat supply network heater 8 to be heated by the exhaust steam of the second part of the intermediate pressure cylinder, so that the heat reservoir stores heat. If the heat reservoir 9 is a volumetric heat reservoir, the second part of return water of the heat supply network with the flow rate of D enters the heat reservoir to be directly stored in the heat reservoir as high-temperature heat supply network water, and the part of the low-temperature heat supply network water stored in the heat reservoir 9 with the flow rate of D leaves the heat reservoir to be continuously circulated and heated by the exhaust steam of the medium pressure cylinder in the second part; if the heat reservoir 9 has a heat-absorbing and heat-releasing medium, the second part of return water of the heat supply network with the flow rate of D flows through the heat-absorbing and heat-releasing medium after entering the heat reservoir 9, releases heat to the heat-absorbing and heat-releasing medium in the heat reservoir, and continues to be circularly heated by the second part of intermediate pressure cylinder exhaust steam after releasing heat.
The controller controls the vacuum pump 12 and the auxiliary vacuumizing device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, non-condensable gas and part of steam in the condenser 6 are pumped out, and the vacuum environment in the condenser 6 is kept. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 19 of the condenser is opened, non-condensed gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6, the heated cooling water is discharged out of the steam cooler 11, and the non-condensed gas continuously enters the vacuum pump 12 and is finally discharged to the non-condensed gas discharge pipe 29.
And when the electric load demand is low, the heat load demand is high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, adopting a low-pressure cylinder near-zero-output heat release mode. Referring to fig. 7, the low-pressure cylinder near-zero output heat release mode is as follows:
the controller controls the steam inlet flow regulating valve 16 of the middle pressure cylinder for discharging steam to the low pressure cylinder, the steam heater valve 17 of the middle pressure cylinder for discharging steam to the heat supply network, the condensed water condenser valve 19 of the steam cooler, the circulating water inlet valve 20 of the cooling tower, the circulating water outlet valve 21 of the cooling tower and the return water bypass valve 38 of the heat supply network to be opened. The controller controls the temperature and pressure reducing device 13 to start. The controller controls the heat reservoir cold side inlet and outlet direction changing valve 24 to be opened in the direction that the heat reservoir cold side inlet and outlet is used as an inlet. The controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the condenser heat supply network backwater outlet valve 22 and the condenser heat supply network backwater inlet valve 23 to be closed. Thereby, the intermediate pressure cylinder exhaust steam is divided into two parts. The first part of the intermediate pressure cylinder exhaust steam is cooled after being subjected to temperature reduction and pressure reduction, the low pressure cylinder exhaust steam enters the low pressure cylinder 3, the formed low pressure cylinder exhaust steam enters the condenser 6, the cooling tower circulating water enters the condenser 6 to cool the low pressure cylinder exhaust steam, and the cooling tower circulating water after absorbing heat returns to the cooling tower 5. The second part of the intermediate pressure cylinder exhaust steam enters the heat supply network heater 8, the heat supply network return water with the flow of G + H sent by the heat supply network return pipe 27 is divided into two parts, the first part of the heat supply network return water with the flow of H enters the heat supply network heater 8 and is heated by the intermediate pressure cylinder exhaust steam, and the second part of the heat supply network return water with the flow of G enters the heat reservoir 9. When the heat reservoir 9 is a volumetric heat reservoir, the second part of the return water of the heat supply network with the flow rate of G is stored in the heat reservoir 9 as low-temperature heat supply network water, and the high-temperature heat supply network water with the corresponding flow rate of G in the heat reservoir 9 leaves the heat reservoir 9, so that heat release of the heat reservoir is completed. When the heat reservoir 9 includes the heat absorbing and releasing medium, the second part of the return water of the heat supply network with the flow rate G flows through the heat absorbing and releasing medium of the heat reservoir 9 to be heated and then is output to the heat reservoir 9.
If the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is equal to a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is equal to the set temperature, the controller controls the hot-side inlet/outlet direction changing valve 25 of the first heat reservoir to be closed and controls the hot-side inlet/outlet direction changing valve 26 of the second heat reservoir to be opened in a direction in which the hot-side inlet/outlet of the heat reservoir serves as an outlet, at this time, the high-temperature heat supply network water output by the heat reservoir 9/the heated second part of heat supply network backwater and the first part of heat supply network backwater discharged from the heat network heater 8 are jointly used as heat supply network water to.
If the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is lower than a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network return water heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is lower than the set temperature, the controller controls the heat side inlet/outlet direction changing valve 26 of the second heat reservoir to be closed and controls the heat side inlet/outlet direction changing valve 25 of the first heat reservoir to open the direction in which the heat side inlet/outlet of the heat reservoir serves as an outlet, and at this time, the high-temperature heat supply network water output by the heat reservoir 9/the heated second part of heat supply network return water enters the heat supply network.
If the heat of the second part of the intermediate pressure cylinder exhaust steam is equal to the heat for heating the first part of the return water of the heat supply network (under the condition that only the first part of the return water of the heat supply network enters the heat supply network heater 8) or the first part of the return water of the heat supply network and the second part of the return water of the heat supply network heated by the heat reservoir (under the condition that the second part of the return water of the heat supply network heated by the heat reservoir 9 also enters the heat supply network heater 8) to the set temperature, the controller controls the valve 40 of the intermediate pressure cylinder exhaust steam of the adjacent machine to the heat supply network heater to be closed.
If the heat quantity of the steam discharged by the pressure cylinder in the second part is lower than the heat quantity for heating the first part of return water of the heat supply network (under the condition that only the first part of return water of the heat supply network enters the heat supply network heater 8) or the first part of return water of the heat supply network and the second part of return water of the heat supply network heated by the heat reservoir (under the condition that the high-temperature return water of the heat supply network output by the heat reservoir 9/the heated second part of return water of the heat supply network also enters the heat supply network heater 8) to the set temperature, the controller controls the steam exhaust of the intermediate pressure cylinder of the adjacent machine to open the valve 40 of the heating network heater, the steam exhaust of the intermediate pressure cylinder of the adjacent machine is led into the heating network heater 8, and simultaneously with or subsequently to the steam discharge of the intermediate pressure cylinder in the second part of the same machine (in the heat supply network heater 8, the steam discharge of the intermediate pressure cylinder in the same machine set and the adjacent machine can be mixed firstly and then heat supply can be carried out, and heat can also be supplied in sequence) heating the return water of the first part of the heat supply network or the return water of the first part of the heat supply network and the return water of the second part of the heat supply network.
The controller controls the vacuum pump 12 and the auxiliary vacuumizing device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, non-condensable gas and part of steam in the condenser 6 are pumped out, and the vacuum environment in the condenser 6 is kept. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 19 of the condenser is opened, non-condensed gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6, the heated cooling water is discharged out of the steam cooler 11, and the non-condensed gas continuously enters the vacuum pump 12 and is finally sent to the non-condensed gas discharge pipe 29.
Example two
Referring to fig. 8, the present embodiment provides a heating system of a cogeneration unit, in fig. 8, a turbine regenerative steam extraction system and a condensing/water supply system are omitted, and other auxiliary devices are also omitted in the heating system, and only the main device is described systematically. The heating system mainly comprises a high-pressure cylinder 1, a medium-pressure cylinder 2, a low-pressure cylinder 3, a generator 4, a condenser 6, a heat supply network water return pump 7, a heat supply network heater 8, a heat reservoir 9, an auxiliary vacuumizing device 10, a steam cooler 11, a vacuum pump 12, an air cooling island 33, a steam exhaust device 34 and a controller. The heating system of the present embodiment is suitable for a direct air-cooling unit because the air-cooling island 33 is used.
The steam outlet of the high pressure cylinder 1 is communicated with the steam inlet of the intermediate pressure cylinder 2.
The steam outlet of the intermediate pressure cylinder 2 is selectively communicated with the steam inlet of the low pressure cylinder 3 directly or through a temperature and pressure reducing device 13. Specifically, the steam outlet of the intermediate pressure cylinder 2 is communicated with the steam inlet of the low pressure cylinder 3 through two branches, a butterfly valve 15 is arranged on one branch, and a steam inlet flow regulating valve 16, the temperature and pressure reducing device 13 and a flow measuring device 14 for exhausting steam from the intermediate pressure cylinder to the low pressure cylinder are sequentially arranged on the other branch along the direction far away from the intermediate pressure cylinder 2. When the butterfly valve 15 is opened and the steam exhaust of the intermediate pressure cylinder is closed to the steam inlet flow regulating valve 16 of the low pressure cylinder, the steam exhaust port of the intermediate pressure cylinder 2 is directly communicated with the steam inlet of the low pressure cylinder 3 through the branch where the butterfly valve 15 is located, and the steam exhaust of the intermediate pressure cylinder directly enters the low pressure cylinder 3; when the butterfly valve 15 is closed and the steam inlet flow regulating valve 16 of the middle pressure cylinder is opened when the steam exhaust of the middle pressure cylinder reaches the low pressure cylinder, the steam exhaust of the middle pressure cylinder 2 is communicated with the steam inlet of the low pressure cylinder 3 through the branch where the temperature and pressure reducing device 13 is located, and the steam exhaust of the middle pressure cylinder is subjected to temperature and pressure reduction through the temperature and pressure reducing device 13 to form cooling steam to enter the low pressure cylinder 3. Wherein, the inlet of the desuperheating water of the desuperheating and pressure reducing device 13 is connected with a desuperheating water pipeline 32, and can receive the desuperheating water, and the desuperheating water is mixed with the steam exhaust of the intermediate pressure cylinder, and the steam exhaust of the intermediate pressure cylinder is desuperheated and reduced in pressure. The desuperheating water line 32 may be connected to a condensate system to employ condensate as the desuperheating water.
The high pressure cylinder 1, the intermediate pressure cylinder 2 and the low pressure cylinder 3 are connected with the generator 4, and steam entering the high pressure cylinder 1, the intermediate pressure cylinder 2 and the low pressure cylinder 3 does work to supply the generator 4 to generate electricity.
The steam outlet of the intermediate pressure cylinder 2 is also selectively communicated with the hot side inlet of the heating network heater 8 through a pipeline and a valve 17 of the intermediate pressure cylinder on the pipeline for exhausting steam to the heating network heater.
The hot side inlet of the heating network heater 8 is also selectively communicated with the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit through a pipeline 37 and the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit on the pipeline to the heating network heater valve 40. The steam outlet of the low pressure cylinder 3 is communicated with the upper part of the steam exhaust device 34 through a pipeline.
The condenser 6 adopts a high back pressure condenser.
The hot side inlet of the condenser 6 is selectively communicated with the upper part of the exhaust device 34 through a pipeline and a condenser steam inlet valve 36 on the pipeline.
And a cold side inlet of the condenser 6 is communicated with a heat supply network water return pipe 27 through a pipeline.
The heat reservoir 9 may be a volumetric heat reservoir or contain a heat absorbing and releasing medium. The length of the heat storage time and the amount of the stored heat are determined by the capacity of the heat storage device/the capacity of the heat absorbing and releasing medium, the larger the capacity of the heat storage device/the larger the capacity of the heat absorbing and releasing medium and the stronger the heat absorbing capacity, and the longer the heat storage time, the more the stored heat. The length of the heat release time and the amount of heat released are determined by the capacity of the heat storage device/the capacity of the heat absorbing and releasing medium, and the larger the capacity of the heat storage device/the larger the capacity of the heat absorbing and releasing medium and the stronger the heat release capacity, the longer the heat release time, the more the amount of heat released.
The inlet and outlet of the cold side of the heat reservoir 9 are selectively communicated with the heat supply network return pipe 27 and the inlet of the cold side of the condenser 6. Specifically, the downstream end of the heat supply network water return pipe 27 and the upstream end of a pipeline connected between the heat supply network water return pipe 27 and the cold side inlet of the condenser 6 are communicated with the cold side inlet and outlet of the heat reservoir 9 through the same pipeline, and the pipeline is provided with a heat reservoir cold side inlet and outlet direction changing valve 24, so that the heat reservoir cold side inlet and outlet direction changing valve 24 controls the communication between the heat supply network water return pipe 27 and the cold side inlet of the condenser 6 and the cold side inlet and outlet of the heat reservoir 9.
The upper part of the steam exhaust device 34 and the inlet of the air cooling island 33 are selectively communicated with an air cooling island steam inlet valve 39 on the pipeline.
The outlet of the cold side of the condenser 6 is also communicated with the inlet of the cold side of the heat supply network heater 8 through a pipeline, and the pipeline is also provided with a heat supply network water return pump 7.
The cold side outlet of the heating network heater 8 is in communication with a heating network water supply pipe 28 via piping.
And a hot side inlet and a hot side outlet of the heat reservoir 9 are selectively communicated with a cold side outlet of the condenser 6, a cold side inlet of the heat supply network heater 8, a cold side outlet of the heat supply network heater 8 and a heat supply network water supply pipe 28. Specifically, the hot side inlet and outlet of the heat reservoir 9 are communicated with a pipeline between the cold side outlet of the condenser 6 and the cold side inlet of the heat supply network heater 8 through a pipeline with a first heat reservoir hot side inlet and outlet direction changing valve 25, and the communication position is located at the downstream of the heat supply network water return pump 7. Meanwhile, the inlet and outlet of the hot side of the heat reservoir 9 are communicated with the pipeline between the outlet of the cold side of the heat supply network heater 8 and the water supply pipe 28 of the heat supply network through the pipeline with the change valve 26 of the inlet and outlet of the hot side of the second heat reservoir.
The inlet of the auxiliary vacuum pumping device 10 is selectively communicated with the condenser 6. Specifically, the inlet of the auxiliary vacuum pumping device 10 is communicated with the condenser 6 through a pipeline, and a condenser vacuum pumping valve 41 is arranged on the pipeline.
The inlet of the auxiliary vacuum 10 is in selective communication with the air cooling island 33 via a conduit and an air cooling island vacuum valve 35 on the conduit.
An outlet of the auxiliary vacuumizing device 10 is communicated with a hot-side inlet of the steam cooler 11 through a pipeline, and a hot-side gas outlet of the steam cooler 11 is communicated with an inlet of the vacuum pump 12 through a pipeline, so that the auxiliary vacuumizing device 10, the steam cooler 11 and the vacuum pump 12 are sequentially communicated in the direction away from the condenser 6. The outlet of the vacuum pump 12 is connected to a noncondensable gas discharge pipe 29. Wherein, the vacuum pump 12 is a water ring vacuum pump.
The cold side inlet of the steam cooler 11 is connected with a cooling water inlet pipe 30, and the cold side outlet is connected with a cooling water outlet pipe 31.
While the hot side liquid outlet of the steam cooler 11 is in selective communication with the lower part of the exhaust 34. Specifically, the hot side liquid outlet of the steam cooler 11 communicates with the lower portion of the exhaust device 34 through a pipeline, and the steam cooler condensate is provided on the pipeline to the exhaust device valve 42 to control the communication between the hot side liquid outlet of the steam cooler 11 and the lower portion of the exhaust device 34.
At the same time, an auxiliary vacuum pump bypass which can be switched on and off is provided for selectively short-circuiting the auxiliary vacuum pump 10. One end of the auxiliary vacuumizing device bypass is connected to the upstream of the auxiliary vacuumizing device 10, the other end of the auxiliary vacuumizing device bypass is connected to the downstream of the auxiliary vacuumizing device 10, and an auxiliary vacuumizing device bypass valve 18 is arranged on the auxiliary vacuumizing device bypass and used for controlling the auxiliary vacuumizing device bypass to be switched on and off. Just as the auxiliary vacuum bypass is used to short-circuit the auxiliary vacuum 10, the upstream end of the auxiliary vacuum bypass is optionally connected to the condenser 6 and the air cooling island 33, and downstream to the hot side inlet of the steam cooler 11.
The controller is in communication with the valves and the electrical control equipment to control the operation of the valves and the operation of the electrical control equipment.
The heat supply method of the cogeneration unit executed by the heat supply system is introduced as follows, and the heat supply method at least comprises six heat supply modes, namely a conventional high back pressure mode, a high back pressure heat storage mode, a high back pressure heat release mode, a conventional low pressure cylinder near zero output mode, a low pressure cylinder near zero output heat storage mode and a low pressure cylinder near zero output heat release mode.
The definitions of the high back pressure mode and the low cylinder near-zero output mode and the high/low standard of the thermal/electrical load demand are given in the first embodiment, and are not described again.
And when the heat load demand and the electric load demand are high and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional high back pressure mode is adopted. Referring to fig. 9, the conventional high back pressure mode is:
the controller controls the butterfly valve 15, the auxiliary vacuum pumping device bypass valve 18, the condenser steam inlet valve 36 and the condenser vacuum pumping valve 41 to be opened. The controller controls the steam exhaust to low-pressure cylinder steam inlet flow regulating valve 16 of the intermediate pressure cylinder, the steam exhaust to heat supply network heater valve 17 of the intermediate pressure cylinder, the heat reservoir cold side inlet and outlet direction changing valve 24, the first heat reservoir hot side inlet and outlet direction changing valve 25, the second heat reservoir hot side inlet and outlet direction changing valve 26, the air cooling island vacuum pumping valve 35, the heat supply network water return bypass valve 38 and the air cooling island steam inlet valve 39 to be closed. Therefore, all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder 3 to do work, the formed exhaust steam of the low pressure cylinder enters the exhaust device 34 for buffering, and then enters the condenser 6 from the exhaust device 34. The return water of the heat supply network sent from the return water pipe 27 of the heat supply network also enters the condenser 6, and the exhaust steam of the low-pressure cylinder heats the return water of the heat supply network in the condenser 6.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is equal to the set temperature, the controller controls the valve 40 of the heat supply network heater to close when the exhaust steam of the intermediate pressure cylinder of the adjacent machine flows, the return water of the heat supply network is sent to the water supply pipe 28 of the heat supply network through the heat supply network heater 8 and is used as the water supply of the heat supply network, and the return water of the heat supply network only passes through the heat supply network heater 8 and is not heated by the heat supply network heater.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is lower than the set temperature, the controller controls the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit to open the valve 40 of the heat supply network heater, the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit is introduced into the heat supply network heater 8, the return water of the heat supply network is continuously heated in the heat supply network heater 8 by utilizing the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit, and the return water of the heat supply network heated by the heat supply network heater 8 is sent to the water supply pipe 28 of the heat supply network to be used as.
Meanwhile, the controller controls the vacuum pump 12 to start, and non-condensable gas and part of steam in the condenser 6 are pumped out through the auxiliary vacuumizing device bypass, the steam cooler 11 and the vacuum pump 12, so that the vacuum environment in the condenser 6 is maintained. The controller controls the steam cooler 11 to receive the cooling water from the cooling water inlet pipe 30 and simultaneously opens the steam cooler condensate to the steam exhaust valve 42. The cooling water exchanges heat with the non-condensing gas and part of steam, the non-condensing gas and part of steam are condensed to form condensing water and non-condensing gas, the condensing water is sent back to the condenser 6 and is discharged from a hot side outlet of the condenser 6 together with the condensing water formed by low-pressure cylinder steam discharge, the cooling water is heated and then is discharged through a cooling water outlet pipe 31, and the non-condensing gas enters the vacuum pump 12 and then enters a non-condensing gas discharge pipe 29. Of course, it is also possible to let only the non-condensable gases and part of the steam simply pass through the steam cooler 11 into the vacuum pump 12 without introducing cooling water.
Therefore, the conventional high back pressure mode can not only fully utilize the waste steam waste heat of the unit for heating to improve the heating economy of the unit, but also enable the steam which needs to be extracted from part of the exhausted steam of the middle pressure cylinder to continue to work in the low pressure cylinder for generating power, thereby improving the peak regulation capacity of the power grid dispatching on the upper limit of the generated power of the unit in the heating state of the unit. When the demand of the power grid on the unit electrical load is low in the heat supply period and the demand of the heat grid on the unit thermal load is high, a part of steam in the unit low-pressure cylinder always needs to flow to do work to generate power when the conventional high-backpressure mode is adopted, so that the generating load of the unit in the conventional high-backpressure mode cannot be too low, and in order to enable the unit to meet the load requirement of power grid scheduling on the deep peak regulation lower limit of the generating load of the unit, the heat supply running state of the unit with small generating output and large heat supply load can be realized by adopting the near-zero output mode of the conventional low-pressure cylinder. Namely, when the electric load demand is low, the heat load demand is high, and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional low-pressure cylinder near-zero output mode is adopted.
Referring to fig. 10, the near-zero force mode of the conventional low pressure cylinder is:
the controller controls the steam exhaust of the intermediate pressure cylinder to the low pressure cylinder to enter the steam flow regulating valve 16, the steam exhaust of the intermediate pressure cylinder to the heating network heater valve 17, the air cooling island vacuum pumping valve 35, the air cooling island steam inlet valve 39 and the steam cooler condensed water to steam exhaust device valve 42 to be opened. The controller controls the steam cooler 11 to be started and the temperature and pressure reducing device 13 to be started. The controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the heat reservoir cold side inlet and outlet direction changing valve 24, the first heat reservoir hot side inlet and outlet direction changing valve 25, the second heat reservoir hot side inlet and outlet direction changing valve 26, the condenser steam inlet valve 36 and the condenser vacuumizing valve 41 to be closed. Thereby, the intermediate pressure cylinder exhaust steam is divided into two parts. The first part of the intermediate pressure cylinder exhausts steam, after temperature and pressure reduction, the low pressure cylinder 3 cools the low pressure cylinder, and the formed low pressure cylinder exhausts steam enters the steam exhaust device 34 for buffering and then enters the air cooling island 33 from the steam exhaust device 34. The second part of the intermediate pressure cylinder exhaust steam enters the heat supply network heater 8, the heat supply network return water sent from the heat supply network return water pipe 27 enters the heat supply network heater 8 through the condenser 6 and is heated by the intermediate pressure cylinder exhaust steam, and after heating, the heat supply network supply water is formed and sent to the heat supply network water supply pipe 28. The return water of the heat supply network is not heated when passing through the condenser 6, but enters the heat supply network heater 8 only by the path of the condenser 6. Of course, in another system embodiment of the present invention, a condenser bypass may be provided, and the condenser 6 may be connected by turning on the condenser bypass when the condenser 6 does not have the heating function.
If the heat of the steam exhausted by the second part of the intermediate pressure cylinders is equal to the heat of the return water of the heat supply network heated to the set temperature, the controller controls the steam exhausted by the intermediate pressure cylinders of the adjacent machines to close the heater valve 40 of the heat supply network. The return water of the heat supply network is heated only by the exhaust steam of the medium pressure cylinder of the same unit.
If the heat of the steam exhaust of the intermediate pressure cylinder in the second part is lower than the heat for heating the return water of the heat supply network to the set temperature, the controller controls the steam exhaust of the intermediate pressure cylinder in the adjacent machine to open the valve 40 of the heater of the heat supply network, and the steam exhaust of the intermediate pressure cylinder in the adjacent machine is introduced into the heater 8 of the heat supply network, so that the steam exhaust of the intermediate pressure cylinder in the adjacent cogeneration unit and the steam exhaust of the intermediate pressure cylinder in the second part of the same machine set are simultaneously or subsequently utilized to heat the return water of the heat supply network (in the heater 8 of the heat supply network, the steam exhaust of the intermediate pressure cylinder in the same machine.
Meanwhile, the controller controls the vacuum pump 12 and the auxiliary vacuum pumping device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, non-condensable gas and part of steam in the air cooling island 33 are pumped out, and the working pressure of the air cooling island 33 is reduced. And simultaneously, the controller controls the steam cooler 11 to be started, the non-condensation gas and part of steam extracted from the air cooling island 33 exchange heat with cooling water in the steam cooler 11 to form condensation water and non-condensation gas, the condensation water is sent to a steam discharging device 34, the cooling water is heated and then discharged through a cooling water outlet pipe 31, and the non-condensation gas enters the vacuum pump 12 and then enters a non-condensation gas discharging pipe 29. Wherein the cooling water can be obtained from an open water system in a factory.
In this embodiment, in order to prevent the low pressure cylinder from exhausting and blowing overheated when the low pressure cylinder only maintains small flow cooling steam during the low pressure cylinder near zero output heat supply, two improvements are made, firstly, the small flow cooling steam entering the low pressure cylinder is desuperheated through a desuperheating and depressurizing device before entering the low pressure cylinder, a desuperheating water source can be obtained from condensed water, the steam flow before desuperheating is realized by adjusting a medium pressure exhaust steam to a low pressure cylinder steam inlet flow regulating valve 16, and a flow measuring device 14 is additionally arranged for accurately measuring the cooling steam entering the low pressure cylinder. Secondly, the low-pressure cylinder exhaust needs to maintain ultralow back pressure operation, an auxiliary vacuumizing device 10 (a roots vacuum pump can be adopted as the auxiliary vacuumizing device) is additionally arranged on the basis of a vacuum pump 12 in order to realize the ultralow back pressure operation of the low-pressure cylinder, a steam cooler 11 is additionally arranged on an outlet pipeline of the auxiliary vacuumizing device 10 in order to reduce the temperature of an inlet medium of an original vacuum pump 12, and after a mixture of non-condensed gas and steam is cooled by the steam cooler 11, the steam in the mixture is cooled and condensed by the steam cooler, and then the condensed water passes through a steam cooler valve 42 and a condenser to be recycled to a large turbine condensed water system, so that the effective recycling of working media is realized. Meanwhile, the temperature of the non-condensable gas cooled by the steam cooler 11 is reduced, and the working output of the vacuum pump 12 is improved. Meanwhile, the auxiliary vacuum pump bypass valve 18 is additionally arranged, so that the auxiliary vacuum pumping device 10 can be flexibly put into use, and the auxiliary vacuum pumping device bypass valve 18 can be opened to recover to the original vacuum pump vacuum pumping operation mode in the non-heating period.
Although the heating economy of the conventional high back pressure mode and the conventional low pressure cylinder near-zero output mode is greatly improved in the power generation output and the heating capacity of the unit compared with the traditional steam extraction heating, and the heating flexibility of the conventional low pressure cylinder near-zero output mode is also improved compared with the traditional steam extraction heating, the heat supply and the power generation of the unit are still simultaneously output in the conventional high back pressure mode and the conventional low pressure cylinder near-zero output mode, and the deep peak regulation control of the power grid to the unit in the heating period is not facilitated. Therefore, in the embodiment, by additionally arranging the heat storage device, the contradiction of the thermoelectric requirements of the unit in different time is solved within a certain time, and the thermoelectric decoupling of the whole plant is realized.
When the thermal load demand is low and the electrical load demand is high, a high back pressure heat storage mode is employed. Referring to fig. 11, the high back pressure heat storage mode is:
the controller controls the butterfly valve 15, the auxiliary vacuum pumping device bypass valve 18, the condenser steam inlet valve 36 and the condenser vacuum pumping valve 41 to be opened. The controller controls a cold side inlet and outlet valve 24 of the heat reservoir and a hot side inlet and outlet direction changing valve 25 of the first heat reservoir so that the direction in which the cold side inlet and outlet of the heat reservoir are used as outlets and the hot side inlet and outlet of the heat reservoir are used as inlets is opened. The controller controls the steam exhaust of the intermediate pressure cylinder to close the steam inlet flow regulating valve 16 of the low pressure cylinder, the hot side inlet and outlet diversion valve 26 of the second heat reservoir, the vacuum pumping valve 35 of the air cooling island and the steam inlet valve 39 of the air cooling island. Therefore, the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder 3 to do work, the formed exhaust steam of the low pressure cylinder enters the exhaust device 34 for buffering, and then enters the condenser 6 from the exhaust device 34. The return water of the heat supply network with the flow rate of A + B also enters the condenser 6, and the exhaust steam of the low-pressure cylinder heats the return water of the heat supply network with the flow rate of A + B in the condenser 6. The heated return water of the heat supply network is divided into two parts, the heated return water of the first part with the flow rate of A enters the heat supply network heater 8, and the heated return water of the second part with the flow rate of B enters the heat reservoir 9. In this embodiment, the heat reservoir 9 is a volumetric heat reservoir, and then the second part of the return water of the heat supply network with the flow rate of B enters the heat reservoir 9 to be directly stored in the heat reservoir 9 as high-temperature heat supply network water, and the low-temperature heat supply network water with the corresponding flow rate of B in the heat reservoir 9 leaves the heat reservoir 9 to be continuously heated by the low-pressure cylinder exhaust steam, so that the heat reservoir 9 stores heat; of course, in other embodiments, if there is a heat absorbing and releasing medium in the heat reservoir 9, a second portion of the return water from the heat supply network with the flow rate B enters the heat reservoir 9 to release heat to the heat absorbing and releasing medium in the heat reservoir 9, and then the second portion of the return water from the heat supply network continues to be circulated and heated by the exhaust steam of the low pressure cylinder, so that the heat reservoir 9 stores heat.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is equal to the set temperature, the controller controls the valve 17 of the steam exhaust to the heat supply network heater of the intermediate pressure cylinder and the valve 40 of the steam exhaust to the heat supply network heater of the adjacent machine to be closed, all the exhaust steam of the intermediate pressure cylinder enters the low-pressure cylinder 3, and the part (namely, the first part of return water of the heat supply network) of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder, which does not enter the heat reservoir, is used as supply water of the heat supply network and sent to a supply water pipe 28 of the heat supply network through the.
If the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is lower than the set temperature, the controller controls one or two of the valve 17 of the intermediate pressure cylinder exhaust steam to the heat supply network heater and the valve 40 of the adjacent intermediate pressure cylinder exhaust steam to the heat supply network heater to be opened (the unopened valve is closed), and then the exhaust steam of a part of intermediate pressure cylinders of the same unit and/or the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit is introduced into the heat supply network heater 8 to continuously heat the return water of the heat supply network. At this time, the first part of the returned heat supply network water reheated by the heat supply network heater 8 is discharged and sent to the heat supply network water supply pipe 28 as the heat supply network water supply.
Meanwhile, the controller controls the vacuum pump 12 and the auxiliary vacuum pumping device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, so that non-condensable gas and part of steam in the condenser 6 are pumped out, and the vacuum environment in the condenser 6 is maintained. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 42 of the steam exhaust device is opened, non-condensed gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6, the condensed water formed by the condensed water and low-pressure cylinder exhaust steam is exhausted from the hot side outlet of the condenser 6 together, the cooling water is heated and then exhausted through the cooling water outlet pipe 31, and the non-condensed gas enters the vacuum pump 12 and then enters the non-condensed gas exhaust pipe 29. Wherein the cooling water can be obtained from an open water system in a factory.
And when the heat load demand and the electric load demand are both high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, adopting a high back pressure heat release mode. Referring to fig. 12, the high back pressure heat release pattern is:
the controller controls the butterfly valve 15, the auxiliary vacuum pumping device bypass valve 18, the condenser steam inlet valve 36 and the condenser vacuum pumping valve 41 to be opened. The controller controls the heat reservoir cold side inlet and outlet direction changing valve 24 to open the heat reservoir cold side inlet and outlet as the inlet direction. The controller controls the steam exhaust of the intermediate pressure cylinder to the low pressure cylinder to enter the steam flow regulating valve 16, the steam exhaust of the intermediate pressure cylinder to the heating network heater valve 17, the air cooling island vacuum pumping valve 35 and the air cooling island steam inlet valve 39 to be closed. Therefore, all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder 3 to do work, the formed exhaust steam of the low pressure cylinder enters the exhaust device 34 for buffering, and then enters the condenser 6 from the exhaust device 34. The return water of the heat supply network with the flow rate of E + F is sent by the return water pipe 27 of the heat supply network and divided into two parts, the first part of the return water of the heat supply network with the flow rate of E enters the condenser 6, the low-pressure cylinder exhaust steam heats the first part of the return water of the heat supply network in the condenser 6, the second part of the return water of the heat supply network with the flow rate of F enters the heat reservoir 9 and is stored in the heat reservoir 9 as low-temperature heat supply network water, and the high-temperature heat supply network water with the corresponding flow rate of F in the heat reservoir 9 is output to the. Of course, when the heat reservoir 9 has the heat-absorbing and heat-releasing medium, the second part of the return water of the heat supply network with the flow rate F flows through the heat-absorbing and heat-releasing medium of the heat reservoir 9 to be heated and then is output to the heat reservoir 9.
If the temperature of the first part of return water of the heat supply network heated by the low-pressure cylinder 3 is equal to the set temperature and the temperature of the second part of return water of the heat supply network heated by the heat reservoir 9 is equal to the set temperature, the controller controls the steam exhaust of the adjacent intermediate pressure cylinder to close the valve 40 of the heat supply network heater, the first part of return water of the heat supply network passes through the heat supply network heater 8 but is not heated, and simultaneously the controller controls the closing of the inlet and outlet valve 25 at the hot side of the first heat reservoir and opens the inlet and outlet valve 26 at the hot side of the second heat reservoir in the direction that the inlet and outlet at the hot side of the heat reservoir are used as outlets, so that the second part of return water of the heat supply network after heat release by the heat reservoir 9 and the first part of return water of the heat supply network passing through the heat supply network heater 8.
If the temperature of the first part of return water of the heat supply network heated by the low-pressure cylinder 3 is lower than the set temperature, the controller controls the steam exhaust of the intermediate pressure cylinder of the adjacent machine to open the valve 40 of the heater of the heat supply network, and the steam exhaust of the intermediate pressure cylinder of the adjacent machine is led into the heater 8 of the heat supply network, so that the first part of return water of the heat supply network is continuously heated in the heater 8 of the heat supply network. Meanwhile, if the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is equal to a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is equal to the set temperature, the controller controls the closing of the inlet/outlet valve 25 at the hot side of the first heat reservoir and opens the inlet/outlet valve 26 at the hot side of the second heat reservoir in the direction in which the inlet/outlet at the hot side of the heat reservoir serves as an outlet, and at this time, the high-temperature heat supply network water output by the heat reservoir 9, the second part of heat supply network backwater heated and the first part of heat supply network backwater heated by the heat. If the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is lower than a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is lower than the set temperature, the controller controls the closing of the hot-side inlet/outlet valve 26 of the second heat reservoir and opens the hot-side inlet/outlet valve 25 of the first heat reservoir in the direction that the hot-side inlet/outlet of the heat reservoir serves as an outlet, at this time, the high-temperature heat supply network water output by the heat reservoir 9/the heated second part of heat supply network backwater is heated by the exhaust steam of the intermediate pressure cylinder of the adjacent machine through the heat supply network heater 8, and the first part of heat supply network backwater and the second part of heat.
Meanwhile, the controller controls the vacuum pump 12 to start, and non-condensable gas and part of steam in the condenser 6 are pumped out, so that the vacuum environment in the condenser 6 is maintained. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 42 of the steam exhaust device is opened, non-condensed gas and part of steam which are extracted from the condenser 6 exchange heat with cooling water which is sent in by the cooling water inlet pipe 30 in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6 and is discharged from a hot side outlet of the condenser 6 together with the condensed water which is formed by low-pressure cylinder exhaust, the cooling water is heated and then discharged through the cooling water outlet pipe 31, and the non-condensed gas enters the vacuum pump 12 and then enters the non-condensed gas discharge pipe 29. Wherein the cooling water can be obtained from an open water system in a factory.
The comprehensive utilization of the high-backpressure heat storage mode and the high-backpressure heat release mode ensures that when the heat required by an external heat user in unit time is low, the heat generated by the unit is temporarily stored in the heat storage 9; when the heat required by the external heat consumer increases in unit time and the unit is limited by power generation and cannot generate enough heat in time, the heat stored in the heat reservoir 9 is released to the heat consumer, so that the contradiction between the heat production of the unit and the time requirement of the heat consumer is relieved.
And when the electric load demand and the heat load demand are both low, a low-pressure cylinder near-zero-output heat storage mode is adopted. Referring to fig. 13, the low-pressure cylinder near-zero output heat storage mode is as follows:
the controller controls the steam exhaust of the intermediate pressure cylinder to the low pressure cylinder to enter the steam flow regulating valve 16, the steam exhaust of the intermediate pressure cylinder to the heating network heater valve 17, the air cooling island vacuum pumping valve 35 and the air cooling island steam inlet valve 39 to be opened. The controller controls the temperature and pressure reducing device 13 to start. The controller controls the heat reservoir cold side inlet and outlet direction changing valve 24 and the second heat reservoir hot side inlet and outlet direction changing valve 26 to enable the direction that the heat reservoir cold side inlet and outlet are an outlet and the direction that the heat reservoir hot side inlet and outlet are an inlet to be opened. The controller controls the butterfly valve 15, the auxiliary vacuumizing device bypass valve 18, the inlet and outlet direction changing valve 25 at the hot side of the first heat reservoir, the steam inlet valve 36 of the condenser, the valve 40 for exhausting steam to the heat supply network heater of the adjacent machine and the vacuumizing valve 41 of the condenser to be closed. Thereby, the intermediate pressure cylinder exhaust steam is divided into two parts. The first part of the intermediate pressure cylinder exhausts steam, the temperature and the pressure are reduced, the low pressure cylinder 3 cools the low pressure cylinder, the formed low pressure cylinder exhausts steam enters the steam exhaust device 34 for buffering, and then the low pressure cylinder exhausts steam from the steam exhaust device 34 to enter the air cooling island. The second part of the intermediate pressure cylinder exhaust steam enters the heat supply network heater 8, and the heat supply network return water sent by the heat supply network return pipe 27 completely enters the heat supply network heater 8 and is heated by the second part of the intermediate pressure cylinder exhaust steam. The first portion of the heated return water from the heat supply network having a flow rate C is discharged as supply water from the heat supply network supply pipe 28. And the heated second part of the return water of the heat supply network with the flow of D enters the heat reservoir 9 to release heat, and then continuously and circularly enters the heat supply network heater 8 to be heated by the exhaust steam of the second part of the intermediate pressure cylinder, so that the heat reservoir 9 stores heat. If the heat reservoir 9 is a volumetric heat reservoir, the second part of return water of the heat supply network with the flow rate of D enters the heat reservoir to be directly stored in the heat reservoir as high-temperature heat supply network water, and the part of the low-temperature heat supply network water stored in the heat reservoir 9 with the flow rate of D leaves the heat reservoir to be continuously circulated and heated by the exhaust steam of the medium pressure cylinder in the second part; if the heat reservoir 9 has a heat-absorbing and heat-releasing medium, the second part of return water of the heat supply network with the flow rate of D flows through the heat-absorbing and heat-releasing medium after entering the heat reservoir 9, releases heat to the heat-absorbing and heat-releasing medium in the heat reservoir, and continues to be circularly heated by the second part of intermediate pressure cylinder exhaust steam after releasing heat.
The controller controls the vacuum pump 12 and the auxiliary vacuumizing device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, non-condensable gas and part of steam in the air cooling island 33 are pumped out, and the working pressure of the air cooling island 33 is reduced. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the steam exhaust device valve 42 is opened, the non-condensable gas extracted from the air cooling island 33 and part of steam exchange heat with the cooling water sent from the cooling water inlet pipe 30 in the steam cooler 11 to form condensed water and non-condensable gas, the condensed water is sent to the steam exhaust device, the heated cooling water is discharged out of the steam cooler 11 to the cooling water exhaust pipe 31, and the non-condensable gas continuously enters the vacuum pump 12 and is finally discharged to the non-condensable gas discharge pipe 29.
And when the electric load demand is low, the heat load demand is high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, adopting a low-pressure cylinder near-zero-output heat release mode. Referring to fig. 14, the low-pressure cylinder near-zero output heat release mode is as follows:
the controller controls the steam exhaust of the intermediate pressure cylinder to the low pressure cylinder to enter the steam flow regulating valve 16, the steam exhaust of the intermediate pressure cylinder to the heating network heater valve 17, the air cooling island vacuum pumping valve 35 and the air cooling island steam inlet valve 39 to be opened. The controller controls the temperature and pressure reducing device 13 to start. The controller controls the heat reservoir cold side inlet and outlet direction changing valve 24 to be opened in the direction that the heat reservoir cold side inlet and outlet is used as an inlet. The controller controls the butterfly valve 15, the auxiliary vacuum pumping device bypass valve 18, the condenser steam inlet valve 36 and the condenser vacuum pumping valve 41 to be closed. Thereby, the intermediate pressure cylinder exhaust steam is divided into two parts. The first part of the intermediate pressure cylinder exhausts steam, after temperature and pressure reduction, the low pressure cylinder 3 cools the low pressure cylinder, and the formed low pressure cylinder exhausts steam enters the steam exhaust device 34 for buffering and then enters the air cooling island 33 from the steam exhaust device 34. The second part of the intermediate pressure cylinder exhaust steam enters the heat supply network heater 8, the heat supply network return water with the flow of G + H sent by the heat supply network return pipe 27 is divided into two parts, the first part of the heat supply network return water with the flow of H enters the heat supply network heater 8 and is heated by the intermediate pressure cylinder exhaust steam, and the second part of the heat supply network return water with the flow of G enters the heat reservoir 9. When the heat reservoir 9 is a volumetric heat reservoir, the second part of the return water of the heat supply network with the flow rate of G is stored in the heat reservoir 9 as low-temperature heat supply network water, and the high-temperature heat supply network water with the flow rate of G corresponding to the heat reservoir 9 in the heat reservoir 9 leaves the heat reservoir 9, so that heat release of the heat reservoir is completed. When the heat reservoir 9 includes the heat absorbing and releasing medium, the second part of the return water of the heat supply network with the flow rate G flows through the heat absorbing and releasing medium of the heat reservoir 9 to be heated and then is output to the heat reservoir 9.
If the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is equal to a set temperature (in the case that the heat reservoir 9 is a volume heat reservoir) or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 (in the case that the heat reservoir 9 has the heat absorbing and releasing medium) is equal to the set temperature, the controller controls the hot-side inlet/outlet direction changing valve 25 of the first heat reservoir to be closed and controls the hot-side inlet/outlet direction changing valve 26 of the second heat reservoir to be opened in a direction in which the hot-side inlet/outlet of the heat reservoir serves as an outlet, at this time, the high-temperature heat supply network water output by the heat reservoir 9/the heated second part of heat supply network backwater and the first part of heat supply network backwater discharged from the heat network heater 8 are jointly used as heat supply network water to.
If the temperature of the high-temperature heat supply network water output by the heat reservoir 9 is lower than the set temperature or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir 9 is lower than the set temperature, the controller controls the inlet and outlet direction changing valve 26 of the hot side of the second heat reservoir to be closed and controls the inlet and outlet direction changing valve 25 of the hot side of the first heat reservoir to open in the direction that the inlet and outlet of the hot side of the heat reservoir is used as an outlet, and at the moment, the high-temperature heat supply network water output by the heat reservoir 9/the heated second part of heat supply network backwater enter the heat supply network heater 8.
If the heat of the steam exhausted by the pressure cylinder in the second part is equal to the heat which enables the first part of return water of the heat supply network (under the condition that only the first part of return water of the heat supply network enters the heat supply network heater 8) or the first part of return water of the heat supply network and the second part of return water of the heat supply network heated by the heat reservoir (under the condition that the heat reservoir 9 outputs high-temperature return water of the heat supply network/the heated second part of return water of the heat supply network also enters the heat supply network heater 8) to be heated to the set temperature, the controller controls the valve 40 of the pressure cylinder steam exhausted by the pressure cylinder in the adjacent machine to be closed until.
If the heat quantity of the second part of intermediate pressure cylinder exhaust steam is lower than the heat quantity for heating the first part of return water of the heat supply network (under the condition that only the first part of return water of the heat supply network enters the heat supply network heater 8) or the first part of return water of the heat supply network and the second part of return water of the heat supply network heated by the heat reservoir (under the condition that the second part of return water of the heat supply network heated by the heat reservoir 9 also enters the heat supply network heater 8) to the set temperature, the controller controls the valve 40 of the intermediate pressure cylinder exhaust steam to be opened of the adjacent machine, the exhaust steam of the intermediate pressure cylinder of the adjacent machine is introduced into the heat supply network heater 8, and the exhaust steam of the intermediate pressure cylinder of the same machine set and the adjacent machine can be mixed firstly and then used for supplying heat or can be used for supplying heat in sequence in the heat supply network heater 8 to heat the first part of return water of the heat supply network or the return water of the first part.
The controller controls the vacuum pump 12 and the auxiliary vacuumizing device 10 connected in series between the vacuum pump 12 and the condenser 6 to be started, non-condensable gas and part of steam in the air cooling island 33 are pumped out, and the working pressure of the air cooling island 33 is reduced. Meanwhile, the controller controls the steam cooler 11 to be started and controls the steam cooler to condense water until the valve 42 of the steam exhaust device is opened, non-condensed gas extracted from the air cooling island 33 and part of steam exchange heat with cooling water sent from the cooling water inlet pipe 30 in the steam cooler 11 to form condensed water and non-condensed gas, the condensed water is sent back to the condenser 6, the heated cooling water is exhausted from the steam cooler 11 to form the cooling water outlet pipe 31, and the non-condensed gas continuously enters the vacuum pump 12 and is finally sent to the non-condensed gas exhaust pipe 29.
In summary, the heating system and the heating method of the first and second embodiments have the following advantages:
under the same input heat, a turbo generator unit adopts a high-backpressure heat supply mode (comprising a conventional high-backpressure mode, a high-backpressure heat storage mode and a high-backpressure heat release mode) to effectively improve the heat supply capacity of the unit, increase the low-pressure cylinder power generation output in a heat supply state, reduce the loss of a cold source of the unit and improve the heat supply economy of the unit;
secondly, the unit in the heating period adopts a low-pressure cylinder near-zero-output heating mode (comprising a conventional low-pressure cylinder near-zero-output mode, a low-pressure cylinder near-zero-output heat storage mode and a low-pressure cylinder near-zero-output heat release mode), so that the heating capacity of the unit can be improved, the power generation amount of steam in the low-pressure cylinder can be greatly reduced, the thermoelectric output proportion of the unit is improved, and the peak regulation capacity and the heating economy of the heating unit are improved;
thirdly, low-grade exhaust steam of the steam turbine is recycled by adopting a high-backpressure condenser and used for supplying heat, so that the waste heat utilization rate of a power plant is improved, the generating output of a unit is improved, the coal consumption of the unit for heat supply and power generation is reduced, and the heat supply economical efficiency of the whole plant is improved;
fourthly, adjusting the opening of a butterfly valve by additionally arranging a steam inlet cooling steam pipeline (namely a pipeline which is provided with a temperature and pressure reducing device and is communicated with a steam outlet of the intermediate pressure cylinder and a steam inlet of the low pressure cylinder) of the low pressure cylinder of the steam turbine, expanding the heating steam extraction amount of the unit, increasing the heat supply load of the unit, reducing the power generation output of the unit, expanding the thermoelectric ratio of the unit and improving the heat supply flexibility of the unit;
fifthly, a temperature and pressure reducing device and a steam discharging flow regulating valve of a medium pressure cylinder to the low pressure cylinder are additionally arranged on a steam inlet cooling steam pipeline of the low pressure cylinder, so that the steam inlet temperature of the low pressure cylinder is reduced, the flow of cooling steam entering the low pressure cylinder is controlled, the steam discharging temperature of the low pressure cylinder of the unit is controlled within a reasonable range, and the running safety of the unit in a low pressure cylinder near-zero output mode is improved;
sixth, through the design of additionally arranging a heat reservoir, corresponding pipelines, valves and the like, a high-backpressure heat storage and heat release mode and a low-pressure cylinder near-zero output heat storage and heat release mode can be added on the basis of a conventional high-backpressure mode and a conventional low-pressure cylinder near-zero output mode, the contradiction that the thermal load demand of a unit in a heating period and the peak shaving of the electric load of an electric network are difficult to dispatch at the same time can be relieved, the unit can adapt to the deep peak shaving demand of the electric network in the heating period, the peak shaving flexibility of the unit is improved, and the competitiveness of a power plant unit is improved. In addition, the heat reservoir can fully utilize the outstanding advantages of good heat supply index economy and low heat supply and power generation coal consumption of a high back pressure heat supply mode and a low-pressure cylinder near-zero output heat supply mode, and the peak regulation capacity of the unit is expanded while the heat supply economy of the whole plant can be improved in multiple time periods.
Seventh, through additionally arranging an auxiliary vacuumizing device, a steam cooler, corresponding pipelines, valves and other designs, the working capacity of the original vacuum pump is improved, so that the exhaust back pressure of a low-pressure cylinder of the unit under the flow of cooling steam is reduced, the exhaust steam of the low-pressure cylinder is prevented from being overheated, and the running safety of the unit under a near-zero output mode of the low-pressure cylinder is ensured;
eighth, through addding the little flow cooling steam pipeline of intermediate pressure jar, install the temperature reduction pressure relief device additional and control the temperature that the cooling steam got into the low pressure jar, increase auxiliary evacuating device and steam cooler and improve former vacuum pump work and exert oneself in addition, reduce unit low pressure jar exhaust steam backpressure, and then realize that the low pressure jar is close to zero and exert oneself the heat supply, improve the unit thermal power ratio by a wide margin, promote unit heat supply flexibility.
The above description is only a preferred embodiment of the present invention, and for those skilled in the art, the present invention should not be limited by the description of the present invention, which should be interpreted as a limitation.
Claims (9)
1. A heat supply method of a cogeneration unit is characterized by comprising the following steps:
when the heat load demand is low and the electric load demand is high, a high back pressure heat storage mode is adopted;
when the heat load demand and the electric load demand are both high and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, a high back pressure heat release mode is adopted;
when the electric load demand and the heat load demand are both low, a low-pressure cylinder near-zero-output heat storage mode is adopted;
when the electric load demand is low, the heat load demand is high, and the heat load demand is higher than the heat production quantity matched with the electricity production quantity of the unit according to the electric load demand, a low-pressure cylinder near-zero-output heat release mode is adopted;
the high back pressure heat storage mode is as follows:
the steam exhaust of the intermediate pressure cylinder enters the low pressure cylinder to do work, the formed steam exhaust of the low pressure cylinder heats the return water of the heat supply network, and one part of the heated return water of the heat supply network enters the heat reservoir and then enables the heat reservoir to store heat in one of the following two modes:
the first heat storage mode: part of the heated return water of the heat supply network is directly stored in the heat reservoir as high-temperature heat supply network water, and meanwhile, low-temperature heat supply network water in the heat reservoir and the flow of the return water of the heat supply network entering the heat reservoir and having the same flow as the return water of the heat supply network stored in the heat reservoir leave the heat reservoir to be continuously circulated and heated by the exhaust steam of the low-pressure cylinder;
a second heat storage mode: one part of the heated return water of the heat supply network releases heat to a heat absorption and release medium in the heat reservoir, and the return water leaves the heat reservoir after releasing the heat to continue to circulate and be heated by low-pressure cylinder exhaust steam;
the high back pressure heat release mode is as follows:
all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder to do work, the exhaust steam of the formed low pressure cylinder heats the return water of the first part of the heat supply network, and the return water of the second part of the heat supply network enters the heat reservoir and then the heat reservoir releases heat in one of the following two ways:
a first heat release mode matched with the first heat storage mode: the second part of heat supply network backwater is stored in the heat reservoir as low-temperature heat supply network water, and the high-temperature heat supply network water in the heat reservoir is output to the heat reservoir;
a second heat release mode matched with the second heat storage mode: the second part of return water of the heat supply network flows through the heat-absorbing and heat-releasing medium of the heat reservoir and is heated and then output to the heat reservoir;
the low-pressure cylinder heat storage mode with near-zero output is as follows:
the low pressure cylinder is cooled after the steam exhaust of the first part intermediate pressure cylinder is subjected to temperature and pressure reduction, the formed low pressure cylinder steam exhaust uses cooling tower circulating water/air cooling island to be cooled and recovered, the steam exhaust of the second part intermediate pressure cylinder heats the return water of the heat supply network, and one part of the heated return water of the heat supply network enters the heat reservoir and then enables the heat reservoir to store heat in one of the following two ways:
the first heat storage mode: one part of the heated return water of the heat supply network is directly stored in the heat reservoir as high-temperature heat supply network water, and meanwhile, low-temperature heat supply network water with the same flow as the return water of the heat supply network entering the heat reservoir and stored in the heat reservoir leaves the heat reservoir to be continuously circulated and heated by the exhaust steam of a second part of intermediate pressure cylinders;
the second heat storage mode: one part of the heated return water of the heat supply network releases heat to a heat absorption and release medium in the heat reservoir, and the heat is continuously circulated and heated by the exhaust steam of the second part of the intermediate pressure cylinder after the heat is released;
the low-pressure cylinder near-zero output heat release mode is as follows:
the method comprises the following steps that after the steam exhaust of the first part of intermediate pressure cylinders is subjected to temperature reduction and pressure reduction, the low pressure cylinders are cooled, the formed low pressure cylinder steam exhaust uses circulating water/an air cooling island of a cooling tower to be cooled and recovered, the steam exhaust of the second part of intermediate pressure cylinders heats the return water of the first part of heat supply network, and the return water of the second part of heat supply network enters the heat reservoir to enable the heat reservoir to release heat in one of the following two ways:
a first heat release means matched to the first heat storage means: the second part of heat supply network backwater is stored in the heat reservoir as low-temperature heat supply network water, and the high-temperature heat supply network water in the heat reservoir is output to the heat reservoir;
a second heat release means matched to the second heat storage means: the second part of return water of the heat supply network flows through the heat-absorbing and heat-releasing medium of the heat reservoir and is heated and then output to the heat reservoir;
in the high back pressure heat storage mode:
if the temperature of the return water of the heat supply network heated by the exhaust steam of the low-pressure cylinder is lower than the set temperature, the return water of the heat supply network is continuously heated by utilizing the exhaust steam of a part of intermediate pressure cylinders of the cogeneration unit and/or the exhaust steam of the intermediate pressure cylinders of the adjacent cogeneration unit;
in the high back pressure heat release mode:
if the temperature of the first part of return water of the heat supply network heated by the low-pressure cylinder is lower than the set temperature, continuously heating the first part of return water of the heat supply network by using the steam discharged by the intermediate pressure cylinder of the adjacent cogeneration unit;
if the temperature of the high-temperature heat supply network water output by the heat reservoir is lower than a set temperature or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir is lower than the set temperature, continuously heating the high-temperature heat supply network water/the second part of heat supply network backwater by utilizing the steam exhausted by the intermediate pressure cylinder of the adjacent cogeneration unit;
in the low-pressure cylinder near-zero force heat release mode:
if the temperature of the high-temperature heat supply network water output by the heat reservoir is lower than a set temperature or the temperature of the second part of heat supply network backwater heated by the heat absorbing and releasing medium in the heat reservoir is lower than the set temperature, utilizing the steam exhausted by the second part of intermediate pressure cylinder to continuously heat the high-temperature heat supply network water/the heated second part of heat supply network backwater;
and if the heat of the steam discharged by the second part of intermediate pressure cylinders is lower than the heat of heating the first part of return water of the heat supply network or the first part of return water of the heat supply network and the high-temperature return water of the heat supply network output by the heat reservoir to a set temperature, heating the first part of return water of the heat supply network or the first part of return water of the heat supply network and the high-temperature return water of the heat supply network or the heated second part of return water of the heat supply network by using the steam discharged by the intermediate pressure cylinders of the adjacent cogeneration units at the same time or later.
2. The cogeneration unit heating method according to claim 1,
when the cogeneration unit is a wet cooling unit or an indirect air cooling unit, the low-pressure cylinder exhaust steam heats the return water of the heat supply network and the low-pressure cylinder exhaust steam is cooled in a condenser by using the circulating water of the cooling tower;
in the high back pressure heat storage mode and the high back pressure heat release mode:
extracting a mixture of non-condensable gas and part of steam in the condenser through a vacuum pump, selectively condensing the non-condensable gas and part of steam extracted from the condenser, and feeding condensed water back to the condenser;
in the low-pressure cylinder near-zero-output heat storage mode and the low-pressure cylinder near-zero-output heat release mode:
the vacuum environment in the condenser is maintained through a vacuum pump and an auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, non-condensable gas and part of steam extracted from the condenser are condensed, and condensed water is sent back to the condenser.
3. The cogeneration unit heating method according to claim 1,
when the cogeneration unit is a direct air cooling unit, the exhausted steam of the low pressure cylinder is cached by the steam exhausting device and then enters the condenser to heat the backwater of the heat supply network or enters the air cooling island;
in the high back pressure heat storage mode and the high back pressure heat release mode:
the mixture of the non-condensable gas and part of the steam in the condenser is extracted through a vacuum pump, the non-condensable gas and part of the steam extracted from the condenser are selectively condensed, and condensed water is sent to the steam exhaust device;
in the low-pressure cylinder near-zero-output heat storage mode and the low-pressure cylinder near-zero-output heat release mode:
the working pressure of the air cooling island is reduced through the suction of a vacuum pump and an auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, noncondensable gas and part of steam extracted from the air cooling island are condensed, and condensed water is sent to the steam exhaust device.
4. The cogeneration unit heating method according to claim 1,
when the heat load demand and the electric load demand are high and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional high back pressure mode is adopted;
when the electric load demand is low, the heat load demand is high, and the electricity generation quantity and the heat generation quantity of the unit are matched with the corresponding demands, a conventional low-pressure cylinder near-zero output mode is adopted;
the conventional high back pressure mode is:
all the exhaust steam of the intermediate pressure cylinder enters the low pressure cylinder to do work, the formed exhaust steam of the low pressure cylinder heats the return water of the heat supply network, and if the temperature of the return water of the heat supply network heated by the exhaust steam of the low pressure cylinder is lower than the set temperature, the exhaust steam of the intermediate pressure cylinder of the adjacent cogeneration unit is used for continuously heating the return water of the heat supply network;
the conventional low-pressure cylinder near-zero force mode is as follows:
the first part of the medium pressure cylinder exhausts steam, after temperature and pressure reduction, the low pressure cylinder cools the low pressure cylinder, the formed low pressure cylinder exhausts steam is cooled and recovered by using circulating water/air cooling island of a cooling tower, and the second part of the medium pressure cylinder exhausts steam to heat a heat supply network to return water.
5. The cogeneration unit heating method according to claim 4,
when the cogeneration unit is a wet cooling unit or an indirect air cooling unit, the low-pressure cylinder exhaust steam heats the return water of the heat supply network and the low-pressure cylinder exhaust steam is cooled in a condenser by using the circulating water of the cooling tower;
in the conventional high back pressure mode: the mixture of the non-condensable gas and the steam in the condenser is extracted through a vacuum pump, the non-condensable gas and part of the steam extracted from the condenser are selectively condensed, and condensed water is sent back to the condenser;
in the conventional low-pressure cylinder near-zero force mode: maintaining a vacuum environment in the condenser through a vacuum pump and an auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, condensing non-condensable gas and part of steam extracted from the condenser, and sending condensed water back to the condenser;
when the cogeneration unit is a direct air cooling unit, the exhausted steam of the low pressure cylinder is cached by the steam exhausting device and then enters the condenser to heat the backwater of the heat supply network or enters the air cooling island;
in the conventional high back pressure mode: the mixture of the non-condensable gas and part of the steam in the condenser is extracted through a vacuum pump, the non-condensable gas and part of the steam extracted from the condenser are selectively condensed, and condensed water is sent to the steam exhaust device;
in the conventional low-pressure cylinder near-zero force mode: the working pressure of the air cooling island is reduced through the suction of a vacuum pump and an auxiliary vacuumizing device connected in series between the vacuum pump and the condenser, meanwhile, noncondensable gas and part of steam extracted from the air cooling island are condensed, and condensed water is sent to the steam exhaust device.
6. A cogeneration unit heating system for use in the cogeneration unit heating method of any one of claims 1 to 5, comprising an intermediate pressure cylinder, a low pressure cylinder, a condenser, a heat supply network heater, a cooling tower, a heat reservoir, and a controller;
the steam outlet of the intermediate pressure cylinder is selectively communicated with the steam inlet of the low pressure cylinder directly or through a temperature and pressure reducing device;
the steam outlet of the intermediate pressure cylinder is selectively communicated with the hot side inlet of the heat supply network heater;
the steam exhaust port of the low pressure cylinder is communicated with the hot side inlet of the condenser;
a cold side inlet of the condenser is selectively communicated with a heat supply network water return pipe and an outlet of the cooling tower;
a cold side outlet of the condenser is selectively communicated with an inlet of the cooling tower and a cold side inlet of the heat supply network heater;
the inlet and the outlet of the cold side of the heat reservoir are selectively communicated with a heat supply network return pipe and the inlet of the cold side of the condenser;
the hot side inlet and outlet of the heat reservoir are selectively communicated with the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and a heat supply network water supply pipe;
the cold side inlet of the heat supply network heater is also selectively communicated with the heat supply network water return pipe;
a cold side outlet of the heat supply network heater is communicated with the heat supply network water supply pipe;
the controller controls the steam outlet of the intermediate pressure cylinder to be selectively communicated with the steam inlet of the low pressure cylinder directly or through a temperature and pressure reducing device, controls the steam outlet of the intermediate pressure cylinder to be selectively communicated with the hot side inlet of the heat supply network heater, controls the cold side inlet of the condenser to be selectively communicated with the hot network water return pipe and the outlet of the cooling tower, controls the cold side outlet of the condenser to be selectively communicated with the inlet of the cooling tower and the cold side inlet of the heat supply network heater, controls the cold side inlet and outlet of the heat reservoir to be selectively communicated with the hot network water return pipe and the cold side inlet of the condenser, and controls the hot side inlet and outlet of the heat reservoir to be selectively communicated with the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and the heat supply pipe, controlling selectable communication between a cold side inlet of the heat net heater and the heat net return pipe.
7. Cogeneration unit heating system according to claim 6,
the hot side inlet of the heat supply network heater is also selectively communicated with the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit;
the heating system of the cogeneration unit further comprises a vacuum pump, a steam cooler and an auxiliary vacuumizing device;
the inlet of the auxiliary vacuumizing device is communicated with the condenser;
the outlet of the auxiliary vacuumizing device is communicated with the hot side inlet of the steam cooler;
a hot-side gas outlet of the steam cooler is communicated with an inlet of the vacuum pump;
a hot-side liquid outlet of the steam cooler is selectively communicated with the condenser;
an auxiliary vacuum bypass is also provided which can be switched on and off for selectively short-circuiting the auxiliary vacuum.
8. A cogeneration unit heating system for use in the cogeneration unit heating method of any one of claims 1 to 5, comprising an intermediate pressure cylinder, a low pressure cylinder, a condenser, a heat supply network heater, an air cooling island, a heat reservoir, a steam exhaust device, and a controller;
the steam outlet of the intermediate pressure cylinder is selectively communicated with the steam inlet of the low pressure cylinder directly or through a temperature and pressure reducing device;
the steam outlet of the intermediate pressure cylinder is selectively communicated with the hot side inlet of the heat supply network heater;
the steam outlet of the low pressure cylinder is communicated with the upper part of the steam exhaust device;
the upper part of the steam exhaust device is also selectively communicated with a hot side inlet of the condenser and an inlet of the air cooling island;
a cold side inlet of the condenser is communicated with a heat supply network water return pipe;
a cold side outlet of the condenser is communicated with a cold side inlet of the heat supply network heater;
a cold side inlet and a cold side outlet of the heat reservoir are selectively communicated with the heat supply network water return pipe and a cold side inlet of the condenser;
the hot side inlet and outlet of the heat reservoir are selectively communicated with the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and a heat supply network water supply pipe;
a cold side outlet of the heat supply network heater is communicated with the heat supply network water supply pipe;
the controller controls the steam exhaust port of the intermediate pressure cylinder to be selectively communicated with the steam inlet of the low pressure cylinder directly or through a temperature and pressure reducing device, controls the selective communication between the steam exhaust port of the intermediate pressure cylinder and the hot side inlet of the heat supply network heater, controls the selective communication between the upper part of the steam exhaust device and the hot side inlet of the condenser and the inlet of the air cooling island, controls the selective communication between the cold side inlet and outlet of the heat reservoir and the cold side inlet of the heat supply network water return pipe and the condenser, and controls the selective communication between the hot side inlet and outlet of the heat reservoir and the cold side outlet of the condenser, the cold side inlet of the heat supply network heater, the cold side outlet of the heat supply network heater and the heat supply pipe.
9. Cogeneration unit heating system according to claim 8,
the hot side inlet of the heat supply network heater is also selectively communicated with the steam outlet of the intermediate pressure cylinder of the adjacent cogeneration unit;
the heating system of the cogeneration unit further comprises a vacuum pump, a steam cooler and an auxiliary vacuumizing device;
the inlet of the auxiliary vacuumizing device is selectively communicated with the air cooling island and the condenser;
the outlet of the auxiliary vacuumizing device is communicated with the hot side inlet of the steam cooler;
a hot-side gas outlet of the steam cooler is communicated with an inlet of the vacuum pump;
the hot-side liquid outlet of the steam cooler is selectively communicated with the lower part of the steam exhaust device;
an auxiliary vacuum bypass is also provided which can be switched on and off for selectively short-circuiting the auxiliary vacuum.
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| CN112611010B (en) * | 2020-11-30 | 2022-06-28 | 华北电力大学 | Adjusting method of flexible adjusting system for power generation load of multi-heat-source cogeneration unit |
| CN112963210A (en) * | 2021-03-17 | 2021-06-15 | 国网天津市电力公司电力科学研究院 | Comprehensive control device with thermoelectric balance capability |
| CN114165826B (en) * | 2022-02-11 | 2022-05-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | Steam extraction and heat supply operation method of cogeneration unit under low heat load |
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