CN114165303A - Operation method of low-load flexibly-operated cogeneration steam turbine generator unit - Google Patents
Operation method of low-load flexibly-operated cogeneration steam turbine generator unit Download PDFInfo
- Publication number
- CN114165303A CN114165303A CN202210127166.4A CN202210127166A CN114165303A CN 114165303 A CN114165303 A CN 114165303A CN 202210127166 A CN202210127166 A CN 202210127166A CN 114165303 A CN114165303 A CN 114165303A
- Authority
- CN
- China
- Prior art keywords
- low
- pressure cylinder
- isolation valve
- medium
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- 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
-
- 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
-
- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
-
- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
-
- 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]
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses an operation method of a heat and power cogeneration turbo generator set with low load and flexible operation, which can effectively inhibit the efficiency reduction of a low-pressure cylinder when in the operation under a condensing working condition, can raise the operation back pressure of the low-pressure cylinder when in the operation under a heating working condition, and can meet the requirement of waste steam waste heat recovery for a heating system. Adopting asymmetrical three-low pressure cylinder technology, namely a large low pressure cylinder, a medium low pressure cylinder and a small low pressure cylinder; a non-traditional shafting arrangement scheme of the steam turbine generator unit is adopted, and a high-power clutch or a quick detachable/detachable coupling is adopted in a matching manner; the four working modes of three-low-pressure cylinder operation, double-low-pressure cylinder operation, single-low-pressure cylinder operation or zero-low-pressure cylinder operation can be selectively realized when the steam turbine unit operates under the condensing working condition; when the steam turbine generator set system runs under a low load condition in the operation of a heat supply working condition, the unit volume flow of dead steam in the running low-pressure cylinder is improved by cutting off part of the low-pressure cylinder, and the requirement of the heat supply system is met.
Description
Technical Field
The invention relates to an operation method of a steam turbine generator unit, in particular to an operation method of a combined heat and power steam turbine generator unit with low load and flexible operation.
Background
At present, low-carbon economy and clean energy technology are rapidly developed, the energy utilization side needs the turbo generator unit to operate flexibly with the load as low as possible on one hand, and needs the turbo generator unit to recover and utilize waste steam waste heat as much as possible on the other hand; however, the low-load flexible operation of the steam turbine generator unit requires 10kPa.a or lower back pressure to reduce the damage of water erosion, flutter and other phenomena to the last-stage blade of the low-pressure cylinder, and the waste heat utilization of the exhaust steam requires 30Pa.a or higher back pressure, so that the temperature of the exhaust steam can be used for heat supply; because the safe operation backpressure value of the low-pressure cylinder of the steam turbine generator unit is approximately in direct proportion to the steam inlet quantity of the low-pressure cylinder and is approximately in inverse proportion to the power generation load of the steam turbine generator unit, the traditional steam turbine generator unit system is difficult to reconcile the contradiction between flexible low-load power generation and high-backpressure exhaust steam waste heat utilization; when the steam inlet quantity of a low-pressure cylinder of the traditional steam turbine generator unit is lower than 30%, the down slip of the thermoelectric conversion efficiency is serious, and the last-stage blade in the low-pressure cylinder is easily damaged by water erosion, flutter and the like, so that how to solve the problem is a difficult problem in the field; in addition, how to safely raise the back pressure of the low-pressure cylinder when the steam turbine generator unit system runs at low load so as to recover the waste heat of the exhaust steam for heat supply is another difficult problem to be solved.
Disclosure of Invention
The invention provides a running method of a heat and power cogeneration steam turbine generator unit with low-load flexible running, which can effectively reduce the efficiency loss of a low-pressure cylinder when the low-power cogeneration steam turbine generator unit runs under a condensing working condition, and can ensure that the low-pressure cylinder keeps higher running back pressure when the low-power cogeneration steam turbine generator unit runs under a heating working condition so as to meet the requirement of recovering waste heat of exhaust steam for a heating system.
The invention solves the technical problems by the following technical scheme:
the general concept of the invention is: the method is characterized in that an asymmetrical three-low-pressure-cylinder technology is adopted, and a large low-pressure cylinder, a medium low-pressure cylinder and a small low-pressure cylinder are configured according to rated power, wherein the last-stage blade of the large low-pressure cylinder is longer and is suitable for the utilization of waste steam waste heat of low back pressure of 0-30kPa.a, the small low-pressure cylinder is shorter and has high rigidity and strength and can adapt to a wide back pressure range of 0-70kPa.a, the adaptability of the back pressure range of the medium low-pressure cylinder and the low-pressure cylinder is between the large low-pressure cylinder and the small low-pressure cylinder, and different back pressure adaptation capacities are realized, so that the waste steam of the three low-pressure cylinders can form cascade heating on heat supply network water in a heating system; the generator and the three low-pressure cylinders are respectively arranged at two ends of a shaft system of the turbo generator set, and the rotating shafts of the three low-pressure cylinders are connected by adopting a high-power clutch or a coupling capable of being quickly disassembled/assembled; when the steam turbine generator set operates under the condensing working condition, three working modes of three-low-pressure-cylinder operation, double-low-pressure-cylinder operation or single-low-pressure-cylinder operation can be selectively realized; when the steam turbine generator set system operates under the heat supply working condition and runs under the low electric load, the volume flow of dead steam in the rest running low-pressure cylinders can be improved by stopping the running part of the low-pressure cylinders, so that the high back pressure can be maintained, and the requirement of a heat supply system can be met; each low-pressure cylinder is provided with a double-function heat exchanger, cooling water flows in parallel in the non-heating period, heating water flows in series in the heating period, and heating network water flows in series in the heating period and the non-heating period, and the two working conditions are switched through a valve on a pipeline.
A running method of a low-load flexibly running cogeneration turbogenerator unit comprises a generator, a high-pressure cylinder, a medium-pressure cylinder, a large low-pressure cylinder, a medium-low pressure cylinder, a small low-pressure cylinder, a first clutch, a second clutch, a condenser circulating cooling water path and a heat supply network circulating water path, wherein a condenser circulating cooling water path water filter, a condenser circulating water cooling device, a circulating water pump and a fourteenth isolating valve are arranged in series in the condenser circulating cooling water path, a heat supply network circulating water pump, a heat consumer, a heat supply network circulating water path water filter, a heat supply network water high-temperature heater and a tenth isolating valve are arranged in series in the heat supply network circulating water path, a large low-pressure cylinder double-function heat exchanger is arranged on the large low-pressure cylinder, a medium-low pressure cylinder double-function heat exchanger is arranged on the medium-low pressure cylinder, a small low-pressure cylinder double-function heat exchanger is arranged on the small low-pressure cylinder, a steam input pipe of the medium-low pressure cylinder, the steam input pipe of the small low pressure cylinder is provided with a seventh isolating valve, the high pressure cylinder, the medium pressure cylinder, the large low pressure cylinder, the medium and low pressure cylinders and the small low pressure cylinder are coaxially arranged, a first clutch is arranged on a connecting shaft between the large low pressure cylinder and the medium and low pressure cylinder, and a second clutch is arranged on the connecting shaft between the medium and low pressure cylinder and the small low pressure cylinder; the heat exchange water end of the large low-pressure cylinder dual-function heat exchanger, the heat exchange water end of the medium-low pressure cylinder dual-function heat exchanger and the heat exchange water end of the small low-pressure cylinder dual-function heat exchanger are sequentially connected in series and then are connected into a heat supply network circulating water path; the heat exchange water end of the large low-pressure cylinder dual-function heat exchanger, the heat exchange water end of the medium-low pressure cylinder dual-function heat exchanger and the heat exchange water end of the small low-pressure cylinder dual-function heat exchanger are respectively connected into a condenser circulating cooling water path in parallel; the third isolating valve, the sixth isolating valve, the ninth isolating valve, the tenth isolating valve and the thirteenth isolating valve form a first group of valve groups, the first isolating valve, the eleventh isolating valve, the twelfth isolating valve, the fourteenth isolating valve, the fifteenth isolating valve and the sixteenth isolating valve form a second group of valve groups, the first group of valve groups and the second group of valve groups are switched in an opening and closing mode, and heat exchange water ends of the double-function heat exchanger with the large, medium and small low pressure cylinders are connected into a heat supply network circulating water path or a condenser circulating cooling water path, and the heat exchange water system is characterized by comprising the following steps of:
if the system runs under the high-electric load under the condensing working condition, the first clutch and the second clutch are both in a connected state; the heat supply network circulating water pump is stopped; closing the third isolation valve, the sixth isolation valve, the ninth isolation valve, the tenth isolation valve and the thirteenth isolation valve, and disconnecting the heat supply network circulating water path from the system; operating a circulating water pump, and opening a first isolation valve, a second isolation valve, a fourth isolation valve, a fifth isolation valve, a seventh isolation valve, an eighth isolation valve, an eleventh isolation valve, a twelfth isolation valve, a fourteenth isolation valve, a fifteenth isolation valve and a sixteenth isolation valve to enable the large low-pressure cylinder dual-function heat exchanger, the medium-low pressure cylinder dual-function heat exchanger and the small low-pressure cylinder dual-function heat exchanger to work in parallel in a circulating cooling water path of the condenser, wherein the large low-pressure cylinder, the medium-low pressure cylinder and the small low-pressure cylinder are maintained to operate under the same back pressure;
if the system is required to operate under medium electric load under the condensing working condition, disconnecting the second clutch, closing the seventh isolating valve and stopping the small low-pressure cylinder from the system; the large low-pressure cylinder and the medium-low pressure cylinder of the steam turbine keep running;
if the system is required to operate under a low electric load under the condensing working condition, disconnecting the first clutch and the second clutch, closing the fourth isolating valve and the seventh isolating valve, stopping the operation of the medium-low pressure cylinder and the small low pressure cylinder from the system, and keeping the operation of the large low pressure cylinder;
if the system runs under the heat supply working condition and the electric load is high, the first clutch and the second clutch are both in a connection state; stopping the circulating water pump; closing the eleventh isolating valve, the twelfth isolating valve, the thirteenth isolating valve, the fourteenth isolating valve, the fifteenth isolating valve, the sixteenth isolating valve and the first isolating valve, and disconnecting the condenser circulating cooling water path from the system; operating a heat supply network circulating water pump, and opening a second isolation valve, a third isolation valve, a fourth isolation valve, a fifth isolation valve, a sixth isolation valve, a seventh isolation valve, an eighth isolation valve, a ninth isolation valve and a tenth isolation valve to enable water in a heat supply network circulating water path to sequentially flow through a large and low pressure cylinder dual-function heat exchanger, a medium and low pressure cylinder dual-function heat exchanger, a small and low pressure cylinder dual-function heat exchanger and a heat supply network water high-temperature heater to be heated in a stepped manner, wherein the large and low pressure cylinder works at low back pressure, the medium and low pressure cylinder works at medium back pressure, and the small and low pressure cylinder works at high back pressure;
if the system operates under the heat supply working condition and is required to have medium electric load, disconnecting the second clutch, closing the seventh isolating valve, stopping the small low-pressure cylinder, enabling the large low-pressure cylinder to be in a low back pressure operation state, and enabling the medium and low-pressure cylinders to be in a medium back pressure operation state; the heat supply network circulating water sequentially flows through the large low-pressure cylinder dual-function heat exchanger and the medium low-pressure cylinder dual-function heat exchanger, is heated by the two-stage cascade, does not absorb heat when passing through the small low-pressure cylinder dual-function heat exchanger, and finally is heated to the required temperature by the heat supply network water high-temperature heater to supply heat for heat users;
if the system operates under the heat supply working condition and is required to have low electric load, disconnecting the first clutch and the second clutch, closing the fourth isolating valve and the seventh isolating valve, stopping the operation of the medium-low pressure cylinder and the small low pressure cylinder, and enabling the large low pressure cylinder to operate at low back pressure; the circulating water of the heat supply network flows through the double-function heat exchanger of the large low-pressure cylinder and is heated by the first stage, the circulating water of the heat supply network does not absorb heat when flowing through the double-function heat exchanger of the medium-low pressure cylinder and the double-function heat exchanger of the small low-pressure cylinder, and finally is heated to the required temperature by the high-temperature heater of the water of the heat supply network to supply heat for a heat user.
According to the invention, the low-pressure cylinders in the running state can obtain a high-proportion steam inlet amount under different power generation loads by controlling the number of the low-pressure cylinders in parallel running, so that the requirement of the overall deep peak shaving of the steam turbine generator unit is met, and the low-load running is more efficient and safer; the low-pressure cylinders in the running state can obtain a high-proportion steam inlet amount under different power generation loads by controlling the quantity of the low-pressure cylinders in parallel running, so that the low-pressure cylinders can keep high running back pressure, the waste steam and waste heat can be utilized, and the steam turbine generator set can also fully utilize the waste steam and waste heat to supply heat while flexibly running under the low power load.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Detailed Description
The invention is described in detail below with reference to the accompanying drawings:
a running method of a low-load flexibly running cogeneration turbogenerator unit comprises a generator 1, a high-pressure cylinder 2, an intermediate-pressure cylinder 3, a large low-pressure cylinder 4, a medium low-pressure cylinder 5, a small low-pressure cylinder 6, a first clutch 8, a second clutch 9, a condenser circulating cooling water circuit 22 and a heat supply network circulating water circuit 15, wherein a condenser circulating cooling water circuit water filter 20, a condenser circulating water cooling device 21, a circulating water pump 23 and a fourteenth isolating valve D14 are arranged in series in the condenser circulating cooling water circuit 22, a heat supply network circulating water pump 7, a heat user 13, a heat supply network circulating water circuit water filter 14, a heat supply network water high-temperature heater 16 and a tenth isolating valve D10 are arranged in series in the heat supply network circulating water circuit 15, a large low-pressure cylinder dual-function heat exchanger 10 is arranged on the large low-pressure cylinder 4, a medium low-pressure cylinder and low-pressure cylinder dual-function heat exchanger 11 is arranged on the medium low-pressure cylinder 5, a small low-pressure cylinder 6 is provided with a small low-pressure cylinder dual-function heat exchanger 12, a fourth isolation valve D4 is arranged on a steam input pipe of the medium and low pressure cylinder 5, a seventh isolation valve D7 is arranged on a steam input pipe of the small low pressure cylinder 6, the high pressure cylinder 2, the medium pressure cylinder 3, the large low pressure cylinder 4, the medium and low pressure cylinder 5 and the small low pressure cylinder 6 are coaxially arranged, a first clutch 8 is arranged on a connecting shaft between the large low pressure cylinder 4 and the medium and low pressure cylinder 5, and a second clutch 9 is arranged on a connecting shaft between the medium and low pressure cylinder 5 and the small low pressure cylinder 6; the heat exchange water end of the large low-pressure cylinder dual-function heat exchanger 10, the heat exchange water end of the medium-low pressure cylinder dual-function heat exchanger 11 and the heat exchange water end of the small low-pressure cylinder dual-function heat exchanger 12 are sequentially connected in series and then are connected into a heat supply network circulating water path 15; the heat exchange water end of the large low-pressure cylinder dual-function heat exchanger 10, the heat exchange water end of the medium-low pressure cylinder dual-function heat exchanger 11 and the heat exchange water end of the small low-pressure cylinder dual-function heat exchanger 12 are connected in parallel and then are connected into a condenser circulating cooling water path 22; the third isolation valve D3, the sixth isolation valve D6, the ninth isolation valve D9, the tenth isolation valve D10 and the thirteenth isolation valve D13 form a first group of valve groups, the first isolation valve D1, the eleventh isolation valve D11, the twelfth isolation valve D12, the fourteenth isolation valve D14, the fifteenth isolation valve D15 and the sixteenth isolation valve D16 form a second group of valve groups, and the opening and closing switching of the first group of valve groups and the second group of valve groups is used for switching the heat exchange water ends of the double-function heat exchanger with the large, medium and small low pressure cylinders into the hot network circulating water circuit 15 or into the condenser circulating cooling water circuit 22, and the method is characterized by comprising the following steps:
if the system runs under the high electric load under the condensing working condition, the first clutch 8 and the second clutch 9 are both in a connection state; the heat supply network circulating water pump 7 is shut down, the third isolation valve D3, the sixth isolation valve D6, the ninth isolation valve D9, the tenth isolation valve D10 and the thirteenth isolation valve D13 are closed, and the heat supply network circulating water circuit 15 is disconnected from the system; the circulating water pump 23 is operated, a first isolation valve D1, a second isolation valve D2, a fourth isolation valve D4, a fifth isolation valve D5, a seventh isolation valve D7, an eighth isolation valve D8, an eleventh isolation valve D11, a twelfth isolation valve D12, a fourteenth isolation valve D14, a fifteenth isolation valve D15 and a sixteenth isolation valve D16 are opened, so that the large low-pressure cylinder dual-function heat exchanger 10, the medium-low pressure cylinder dual-function heat exchanger 11 and the small low-pressure cylinder dual-function heat exchanger 12 work in parallel in the condenser circulating cooling water circuit 22, and the large low-pressure cylinder 4, the medium-low pressure cylinder 5 and the small low-pressure cylinder 6 maintain the same back pressure operation;
if the system is required to operate under medium electric load under the condensing working condition, the total steam inlet quantity of the steam turbine generator set and the steam quantity discharged by the medium pressure cylinder 3 are necessarily reduced, and in order to reduce the efficiency loss of the low pressure cylinder, the second clutch 9 is disconnected, the seventh isolating valve D7 is closed, and the small low pressure cylinder 6 is shut down from the system; the large low pressure cylinder 4 and the medium low pressure cylinder 5 of the steam turbine can operate to maintain a high proportion of steam inlet amount, and the operation efficiency of the large low pressure cylinder and the medium low pressure cylinder can be maintained at a high level;
if the system is required to operate under a low electric load in a condensing working condition, disconnecting the first clutch 8 and the second clutch 9, closing the fourth isolation valve D4 and the seventh isolation valve D7, and stopping the medium-low pressure cylinder 5 and the small-low pressure cylinder 6 from the system; the only large and low pressure cylinder 4 which is left to operate can obtain a higher proportion of steam inlet quantity, the operation efficiency of the large and low pressure cylinder can be maintained at a higher level, and the problems that the water erosion, the flutter and the like which occur at the last stage blade in the cylinder affect the safety and the service life of equipment under a small steam inlet quantity can be effectively avoided;
if the system runs under the heat supply working condition and the electric load is high, the first clutch 8 and the second clutch 9 are both in a connection state; the circulating water pump 23 is stopped, the first isolation valve D1, the eleventh isolation valve D11, the twelfth isolation valve D12, the thirteenth isolation valve D13, the fourteenth isolation valve D14, the fifteenth isolation valve D15 and the sixteenth isolation valve D16 are closed, and the condenser circulating cooling water circuit 22 is disconnected from the system; the heat supply network circulating water pump 7 is operated, a second isolation valve D2, a third isolation valve D3, a fourth isolation valve D4, a fifth isolation valve D5, a sixth isolation valve D6, a seventh isolation valve D7, an eighth isolation valve D8, a ninth isolation valve D9 and a tenth isolation valve D10 are opened, so that water in the heat supply network circulating water path 15 sequentially flows through the large and low pressure cylinder dual-function heat exchanger 10, the medium and low pressure cylinder dual-function heat exchanger 11, the small low pressure cylinder dual-function heat exchanger 12 and the heat supply network water high-temperature heater 16 and is heated in a stepped mode, at the moment, the large and low pressure cylinder 4 works in low back pressure, the medium and low pressure cylinder 5 works in medium back pressure, and the small low pressure cylinder 6 works in high back pressure;
if the system is operated in a heating working condition and is required to have medium electric load, the second clutch 9 is disconnected, the seventh isolating valve D7 is closed, and the small low-pressure cylinder 6 is shut down, so that the power generation load is reduced, more importantly, the exhaust steam of the medium-pressure cylinder 3 is intensively supplied to the large low-pressure cylinder 4 and the medium-low pressure cylinder 5, so that the large low-pressure cylinder 4 and the medium-low pressure cylinder 5 can obtain a high-proportion steam inlet amount, and a high-level back pressure is maintained, so that the requirement for secondary heating of heat supply network water is met; the circulating water of the heat supply network sequentially flows through the large low-pressure cylinder double-function heat exchanger 10 and the middle low-pressure cylinder double-function heat exchanger 11, is heated by the second-level cascade, does not absorb heat when passing through the small low-pressure cylinder double-function heat exchanger 12, and finally is heated to the required temperature by the heat supply network water high-temperature heater 16 to supply heat for a heat user 13;
if the system is operated in a heating working condition and low electric load is required, the first clutch 8 and the second clutch 9 are disconnected, the fourth isolation valve D4 and the seventh isolation valve D7 are closed, and the medium-low pressure cylinder 5 and the small low pressure cylinder 6 are stopped, so that the power generation load is reduced, and more importantly, the exhaust steam of the medium-low pressure cylinder 3 is intensively supplied to the large low pressure cylinder 4 to obtain a high-proportion steam inlet amount, so that a high-level back pressure is maintained to meet the requirement of primary heating of heat supply network water; the circulating water of the heat supply network flows through the large low-pressure cylinder dual-function heat exchanger 10 and is heated by a first stage, the circulating water of the heat supply network does not absorb heat when passing through the medium and low-pressure cylinder dual-function heat exchanger 11 and the small low-pressure cylinder dual-function heat exchanger 12, and finally the circulating water of the heat supply network is heated to the required temperature by the high-temperature heater 16 of the water of the heat supply network to supply heat for a heat user 13.
Claims (1)
1. A running method of a low-load flexibly-running cogeneration turbo generator set comprises a generator (1), a high-pressure cylinder (2), an intermediate-pressure cylinder (3), a large low-pressure cylinder (4), a medium-low pressure cylinder (5), a small low-pressure cylinder (6), a first clutch (8), a second clutch (9), a condenser circulating cooling water circuit (22) and a heat supply network circulating water circuit (15), wherein a condenser circulating cooling water circuit water filter (20), a condenser circulating water cooling device (21), a circulating water pump (23) and a fourteenth isolating valve (D14) are arranged in the condenser circulating cooling water circuit (22) in series, a heat supply network circulating water pump (7), a heat consumer (13), a heat supply network circulating water circuit water filter (14), a heat supply network water high-temperature heater (16) and a tenth isolating valve (D10) are arranged in the heat supply network circulating water circuit (15) in series, and on the large low-pressure cylinder (4), the double-function heat exchanger is provided with a large low-pressure cylinder double-function heat exchanger (10), a medium and low-pressure cylinder double-function heat exchanger (11) is arranged on a medium and low-pressure cylinder (5), a small low-pressure cylinder double-function heat exchanger (12) is arranged on a small low-pressure cylinder (6), a fourth isolation valve (D4) is arranged on a steam input pipe of the medium and low-pressure cylinder (5), a seventh isolation valve (D7) is arranged on the steam input pipe of the small low-pressure cylinder (6), a high-pressure cylinder (2), a medium-pressure cylinder (3), a large low-pressure cylinder (4), the medium and low-pressure cylinder (5) and the small low-pressure cylinder (6) are coaxially arranged, a first clutch (8) is arranged on a connecting shaft between the large low-pressure cylinder (4) and the medium and low-pressure cylinder (5), and a second clutch (9) is arranged on the connecting shaft between the medium and low-pressure cylinder (5) and the small low-pressure cylinder (6); the heat exchange water end of the large low-pressure cylinder dual-function heat exchanger (10), the heat exchange water end of the medium-low pressure cylinder dual-function heat exchanger (11) and the heat exchange water end of the small low-pressure cylinder dual-function heat exchanger (12) are sequentially connected in series and then are connected into a heat supply network circulating water path (15); the heat exchange water end of the large low-pressure cylinder dual-function heat exchanger (10), the heat exchange water end of the medium-low pressure cylinder dual-function heat exchanger (11) and the heat exchange water end of the small low-pressure cylinder dual-function heat exchanger (12) are respectively connected into a condenser circulating cooling water channel (22) in parallel; the third isolation valve (D3), the sixth isolation valve (D6), the ninth isolation valve (D9), the tenth isolation valve (D10), the thirteenth isolation valve (D13) constitute a first group of valve groups, the first isolation valve (D1), the eleventh isolation valve (D11), the twelfth isolation valve (D12), the fourteenth isolation valve (D14), the fifteenth isolation valve (D15), the sixteenth isolation valve (D16) constitute a second group of valve groups, the opening and closing of the first group of valve groups and the second group of valve groups are switched, and heat exchange water ends of the double-function heat exchangers of the large, medium and small low pressure cylinders are connected into a heat supply network circulating water channel (15) or into a condenser circulating cooling water channel (22), and the heat exchange water system is characterized by comprising the following steps:
if the system runs under the high-electric load under the condensing working condition, the first clutch (8) and the second clutch (9) are both in a connection state; the heat supply network circulating water pump (7) is stopped; closing the third (D3), sixth (D6), ninth (D9), tenth (D10) and thirteenth (D13) isolation valves and disconnecting the heat network circulation water circuit (15) from the system; the method comprises the steps of operating a circulating water pump (23), opening a first isolation valve (D1), a second isolation valve (D2), a fourth isolation valve (D4), a fifth isolation valve (D5), a seventh isolation valve (D7), an eighth isolation valve (D8), an eleventh isolation valve (D11), a twelfth isolation valve (D12), a fourteenth isolation valve (D14), a fifteenth isolation valve (D15) and a sixteenth isolation valve (D16), enabling a large low-pressure cylinder dual-function heat exchanger (10), a medium-low pressure cylinder dual-function heat exchanger (11) and a small low-pressure cylinder dual-function heat exchanger (12) to work in parallel in a condenser circulating cooling water circuit (22), and enabling a large low-pressure cylinder (4), a medium-low pressure cylinder (5) and a small low-pressure cylinder (6) to operate under the same backpressure;
if the system is required to run under medium electric load under the condensing working condition, disconnecting the second clutch (9), closing the seventh isolating valve (D7) and stopping the small low-pressure cylinder (6) from the system; the large and low pressure cylinders (4) and the medium and low pressure cylinders (5) of the steam turbine keep running;
if the system is required to operate under low electric load under the condensing working condition, disconnecting the first clutch (8) and the second clutch (9), closing the fourth isolation valve (D4) and the seventh isolation valve (D7), stopping the medium and low pressure cylinders (5) and the small and low pressure cylinders (6) from the system, and keeping the large and low pressure cylinders (4) to operate;
if the system runs under the heat supply working condition and the electric load is high, the first clutch (8) and the second clutch (9) are both in a connection state; the water circulation pump (23) is shut down; closing an eleventh isolation valve (D11), a twelfth isolation valve (D12), a thirteenth isolation valve (D13), a fourteenth isolation valve (D14), a fifteenth isolation valve (D15), a sixteenth isolation valve (D16) and a first isolation valve (D1) to disconnect the condenser recirculating cooling water circuit (22) from the system; the method comprises the steps of operating a heat supply network circulating water pump (7), opening a second isolation valve (D2), a third isolation valve (D3), a fourth isolation valve (D4), a fifth isolation valve (D5), a sixth isolation valve (D6), a seventh isolation valve (D7), an eighth isolation valve (D8), a ninth isolation valve (D9) and a tenth isolation valve (D10), enabling water in a heat supply network circulating water path (15) to sequentially flow through a large low pressure cylinder double-function heat exchanger (10), a medium and low pressure cylinder double-function heat exchanger (11), a small low pressure cylinder double-function heat exchanger (12) and a heat supply network water high-temperature heater (16) and be heated in a stepped mode, a large low pressure cylinder (4) works in low back pressure, a medium and low pressure cylinder (5) works in medium back pressure, and a small low pressure cylinder (6) works in high back pressure;
if the system is operated under the heating working condition and is required to have medium electric load, disconnecting the second clutch (9), closing the seventh isolating valve (D7), stopping the small and low pressure cylinders (6), enabling the large and low pressure cylinders (4) to be in a low back pressure operation state, and enabling the medium and low pressure cylinders (5) to be in a medium back pressure operation state; the heat supply network circulating water sequentially flows through the large and low pressure cylinder double-function heat exchanger (10) and the middle and low pressure cylinder double-function heat exchanger (11), is heated by the two-stage cascade, does not absorb heat when passing through the small and low pressure cylinder double-function heat exchanger (12), and finally is heated to the required temperature by the heat supply network water high-temperature heater (16) to supply heat for a heat user (13);
if the system is operated in a heating working condition and low electric load is required, disconnecting the first clutch (8) and the second clutch (9), closing the fourth isolation valve (D4) and the seventh isolation valve (D7), stopping the operation of the medium and low pressure cylinders (5) and the small and low pressure cylinders (6), and enabling the large and low pressure cylinders (4) to be operated at low back pressure; the circulating water of the heat supply network flows through the large low-pressure cylinder dual-function heat exchanger (10) and is heated by the first stage, the circulating water of the heat supply network does not absorb heat when flowing through the medium and low-pressure cylinder dual-function heat exchanger (11) and the small low-pressure cylinder dual-function heat exchanger (12), and finally the circulating water of the heat supply network is heated to the required temperature by the high-temperature water heater (16) of the heat supply network to supply heat for a heat user (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210127166.4A CN114165303B (en) | 2022-02-11 | 2022-02-11 | Low-load flexible-operation cogeneration steam turbine generator unit operation method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210127166.4A CN114165303B (en) | 2022-02-11 | 2022-02-11 | Low-load flexible-operation cogeneration steam turbine generator unit operation method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114165303A true CN114165303A (en) | 2022-03-11 |
| CN114165303B CN114165303B (en) | 2022-05-10 |
Family
ID=80489697
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210127166.4A Active CN114165303B (en) | 2022-02-11 | 2022-02-11 | Low-load flexible-operation cogeneration steam turbine generator unit operation method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114165303B (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB190776A (en) * | 1921-09-21 | 1922-12-21 | Charles Algernon Parsons | Improvements in and relating to multiple unit steam turbine installations |
| EP2942495A1 (en) * | 2014-05-08 | 2015-11-11 | Alstom Technology Ltd | Coal fired oxy plant with heat integration |
| CN106401657A (en) * | 2016-11-27 | 2017-02-15 | 冯伟忠 | Coaxially arranged steam turbine optimizing configuration system and method |
| CN207598299U (en) * | 2017-11-15 | 2018-07-10 | 西安西热节能技术有限公司 | A kind of zero output operating system of more low pressure (LP) cylinder steam turbine underload unilateral side low pressure (LP) cylinder |
-
2022
- 2022-02-11 CN CN202210127166.4A patent/CN114165303B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB190776A (en) * | 1921-09-21 | 1922-12-21 | Charles Algernon Parsons | Improvements in and relating to multiple unit steam turbine installations |
| EP2942495A1 (en) * | 2014-05-08 | 2015-11-11 | Alstom Technology Ltd | Coal fired oxy plant with heat integration |
| CN106401657A (en) * | 2016-11-27 | 2017-02-15 | 冯伟忠 | Coaxially arranged steam turbine optimizing configuration system and method |
| CN207598299U (en) * | 2017-11-15 | 2018-07-10 | 西安西热节能技术有限公司 | A kind of zero output operating system of more low pressure (LP) cylinder steam turbine underload unilateral side low pressure (LP) cylinder |
Non-Patent Citations (1)
| Title |
|---|
| 钟史明等: "N200―12.75/535/535型三缸三排汽汽轮机组供热改造成热电两用机", 《区域供热》 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114165303B (en) | 2022-05-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109826681B (en) | Industrial heating system for gas-steam combined cycle unit steam extraction integration and operation method thereof | |
| CN109855147B (en) | Combined cycle device based on heat supply and power peak regulation coupling and operation method thereof | |
| CN107939460B (en) | Expansion unit for high-power-level compressed air energy storage system | |
| CN109854316B (en) | Combined cycle heat supply and power peak regulation coupling system based on energy cascade utilization and operation method thereof | |
| CN111365748B (en) | Heat supply method and heat supply system of cogeneration unit | |
| CN109869784B (en) | Combined cycle device for steam extraction integration and heat accumulation peak shaving coupling and operation method thereof | |
| CN114165303B (en) | Low-load flexible-operation cogeneration steam turbine generator unit operation method | |
| CN210088955U (en) | Combined cycle device for steam extraction integration and heat storage peak regulation coupling | |
| CN109763869B (en) | Heat accumulation coupling steam extraction integrated system for cascade utilization of combined cycle energy and operation method thereof | |
| CN116557094A (en) | Thermoelectric cooperative system integrating compressed air energy storage and operation method | |
| CN114000928B (en) | Tandem peak cooling and waste heat recovery turbo generator set | |
| CN217001983U (en) | Combined heat and power turbogenerator unit system capable of fully utilizing waste heat of exhaust steam under low load | |
| CN217001982U (en) | Turbogenerator set system capable of flexibly operating at low load | |
| CN110056402B (en) | Steam complementary energy utilization coupling steam extraction heat supply system and adjusting method | |
| CN212027896U (en) | High-pressure injection type thermoelectric decoupling heat supply system | |
| CN210663026U (en) | Novel heating system | |
| CN112432219A (en) | Double-cold-source efficient heating system suitable for large four-exhaust steam turbine unit | |
| CN110230521B (en) | Cascade heating system for heat pump by cutting off steam inlet coupling of low-pressure cylinder of thermoelectric unit and adjusting method | |
| CN210087417U (en) | Thermoelectric unit cuts off low pressure jar steam admission coupling heat pump step heating system | |
| CN113883576A (en) | Efficient and flexible heat supply and power generation system capable of realizing energy gradient recycling | |
| CN113027553A (en) | System for improving unit operation economy and flexibility | |
| CN114635797A (en) | Control system for inlet air temperature of gas turbine | |
| CN206190331U (en) | Coaxial steam turbine optimizing configuration system who arranges | |
| CN213450523U (en) | Steam extraction reverse cooling device of steam turbine under zero-power working condition of low-pressure cylinder | |
| CN219995950U (en) | Cooling water circulation system based on operation under pure condensation high back pressure working condition |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |