JP4348424B2 - Hybrid thermoelectric supply system - Google Patents

Description

  The present invention combusts fuel by using the regenerative burner of the absorption chiller / heater as the exhaust gas of the power generation unit as combustion air, supplies the exhaust gas of the reburn burner to the regenerator, and generates the power generated by the power generation unit The present invention relates to a hybrid thermoelectric supply system configured to be used as drive power for a unit and an absorption chiller / heater.

  2. Description of the Related Art In recent years, an absorption chiller / heater that circulates cold water or hot water to a building for air conditioning in a building or the like has been attracting attention as a defluorocarbon air conditioner for reducing the global environmental load. This absorption chiller / heater uses a series of absorption cycles of an absorbing liquid (for example, an aqueous solution of lithium bromide) and a refrigerant (for example, water) to generate cold water or hot water and circulate it to a building. Yes, in the absorption cycle when supplying cold water, in the evaporator maintained in a nearly vacuum state, the refrigerant takes heat away from the water (circulated water) and evaporates, and the evaporated refrigerant is absorbed by the absorption liquid. The liquid is heated by the regenerator, and the refrigerant is separated from the absorption liquid as vapor, and the refrigerant is condensed by the condenser and sent to the evaporator again.

  Here, in the regenerator, it is necessary to give a sufficient amount of heat to separate the refrigerant from the absorbing liquid. Therefore, fuel such as city gas may be simply burned by a burner to supply heat. However, in recent years, power generation units equipped with relatively small gas turbines, gas engines, etc. A technology has been put to practical use in which the absorption liquid is heated by a regenerator with the exhaust gas of the exhaust gas to effectively use the retained heat (sensible heat) of the exhaust gas. With this technology, the power generated by the power generation unit can be used as drive power for various devices such as the power generation unit and the absorption chiller / heater, such as a pump that circulates cold / hot water to the building and a pump that circulates absorbent. .

  For example, a low temperature regenerator and a high temperature regenerator are provided as regenerators, the exhaust gas of the gas turbine power generation unit is supplied to the high temperature regenerator, and heat exchange is performed between the exhaust gas and the absorbing liquid in the high temperature regenerator. An exhaust heat effective use type absorption chiller / heater that recovers sensible heat of exhaust gas has been proposed (for example, see Patent Document 1). In addition, a technology that uses the exhaust heat of the gas turbine generator as a driving heat source for the chilled water heater and uses the generated power of the gas turbine generator as the driving power for the chilled water heater and its peripheral devices has also been put into practical use (for example, , See Patent Document 2).

  By the way, the applicant of the present application provides a reburning burner in the exhaust heat effective use type absorption chiller / heater for further effective use of the exhaust gas of the power generation unit. A system that burns fuel using residual oxygen as combustion air is being proposed and put into practical use, but the amount of fuel supplied to the power generation unit and reburn burner according to the air conditioning load of the absorption chiller / heater and the power generation requirements of the power generation unit Is required to be able to supply stable chilled water or hot water in any air conditioning load region of the absorption chiller / heater.

  Here, conventionally, as the combustion air of the reburning burner, the high-temperature exhaust gas supplied from other heat source equipment and the air supplied from a normal blower can be switched according to the air conditioning load of the absorption chiller / heater, A technique has been put to practical use in which air is supplied to the reburning burner when the air conditioning is under a low load, and high-temperature exhaust gas is supplied to the reburning burner when the air conditioning is under a high load (see, for example, Patent Document 3). However, there is no description about control in consideration of power demand.

JP-A-11-304274 Japanese Patent Laid-Open No. 2000-274861 JP 2002-195510 A

  First, in the conventional absorption chiller / heater, when the absorbent is heated by simply burning fuel with a burner in the regenerator, the temperature of the combustion air sucked into the burner is not equal to the outside air temperature, Since a part of the heat is consumed to raise the temperature of the combustion air during the combustion of the fuel in the burner, the heat efficiency is lowered accordingly. Further, the absorption chiller / heater described in Patent Document 1 only recovers the sensible heat of the exhaust gas, and in general, significant improvement in thermal efficiency cannot be expected, and oxygen remaining in the exhaust gas and unburned Gases are also released to the atmosphere at high temperatures, and improvement in combustion efficiency cannot be expected much.

  Therefore, it is conceivable to use the residual oxygen in the exhaust gas effectively by burning the fuel with the reburning burner of the absorption chiller / heater using the residual oxygen of the high-temperature exhaust gas as combustion air. However, if the fuel supply supplied to the power generation unit and the reburning burner is not properly distributed, the reburning burner will start and stop frequently and the absorption cold The chilled water outlet temperature of the water machine fluctuates and is unstable, the combustion conditions cannot be optimized without suppressing the emission of CO and NO x from the exhaust gas of the reburning burner, and the chilled water outlet temperature is stabilized. Therefore, there is a possibility that the power generated by the power generation unit cannot be maximized.

That is, by appropriately allocating the amount of fuel supplied to the power generation unit and the reburning burner according to the air conditioning load of the absorption chiller / heater and the power requirement for the power generation unit, It is required that stable cold and hot water can be supplied to the building.
The object of the present invention is to significantly improve the thermal efficiency by effectively utilizing the sensible heat and residual oxygen of the exhaust gas of the power generation unit, and to reduce the amount of fuel supplied to the power generation unit and the reburning burner to the air conditioning load of the absorption chiller / heater A hybrid thermoelectric supply system configured to appropriately distribute power based on at least one of the power requirements for the power generation unit and to supply stable cold / warm water to the building in any air conditioning load region of the absorption chiller / heater Is to provide.

The hybrid thermoelectric supply system according to claim 1 includes a power generation unit that generates power by burning gas or liquid fuel, a reburning burner that burns gas or liquid fuel using residual oxygen in the exhaust gas of the power generation unit as combustion air, Hybrid thermoelectric supply having a reburner and a regenerator that separates the refrigerant from the absorbent and an evaporator that evaporates the refrigerant, and an absorption chiller / heater that generates cold water or hot water and circulates it to the building The system is configured to supply exhaust gas from the reburning burner of the absorption chiller / heater to the regenerator and use the electric power generated by the power generation unit as drive power for the power generation unit and the absorption chiller / heater. The amount of fuel supplied to the power generation unit and the reburning burner is less than the air conditioning load of the absorption chiller / heater and the power requirement for the power generation unit. With allocating based on one, so as to maximize the originating DENDEN force of the power generating unit, it provided an integrated control device for determine the distribution amount of the fuel supply amount to the power generation unit and relapse burner, the absorption the chiller cooling water for cooling the absorbent liquid and the refrigerant is subjected supply, the integrated control unit, so as to increase the cooling water inlet temperature of the absorption chiller-heater in order to maximize the power generation power of the power generating unit It is characterized by comprising.

In this hybrid thermoelectric supply system, gas or liquid fuel is burned by the power generation unit to generate power, and the power is used as drive power for the power generation unit and the absorption chiller / heater. In an absorption chiller / heater, gas or liquid fuel is burned by the reburning burner using the residual oxygen in the exhaust gas of the power generation unit as combustion air, and the retained heat of the exhaust gas of the power generation unit and the combustion heat of the reburning burner are used as heat sources. Absorption chiller / heater is driven. That is, the exhaust gas from the reburning burner is supplied to the regenerator. In the regenerator, the absorption liquid is heated by the high-temperature exhaust gas to separate the refrigerant from the absorption liquid, and the refrigerant is condensed and then supplied to the evaporator to evaporate. In the container, the refrigerant takes heat from the water (circulated water) and evaporates to generate cold water, which is circulated and supplied to the building. When used for heating, the high-temperature refrigerant separated from the absorbing liquid is directly supplied to the regenerator so that the high-temperature refrigerant heats water (circulated water), and hot water is generated and circulated and supplied to the building. . Further, when the air conditioning load of the absorption chiller-heater is low, even to stop the fuel supply to relapse burner, but it is envisioned that more than the required amount of heating by the sensible heat of the exhaust gas of the power generation unit, integrated control device Accordingly, to prevent this, to maximize the power generation power of the generator unit, the fuel supply amount to the generator Uni Tsu preparative and relapse burner is properly distributed. Moreover, by increasing the cooling water inlet temperature of the absorption chiller / heater, the cooling performance of the absorption chiller / heater is suppressed, and even if the air conditioning load of the absorption chiller / heater is low, the amount of power generated by the power generation unit Can be maximized. In other words , even if the amount of power generated by the power generation unit is maximized, it is possible to adjust so that the cooling performance of the absorption chiller / heater is not excessively increased .

  A hybrid thermoelectric supply system according to a second aspect converts the AC power generated by the power generation unit into DC power and converts AC power supplied from an external power supply system into DC power. And a power converter having an AC power converter that converts the converted DC power into AC power having a predetermined frequency for use as the drive power. .

  In this hybrid thermoelectric supply system, AC power generated by the power generation unit is converted into DC power by a DC power conversion unit (converter) in the power conversion device, and then AC power having a predetermined frequency is converted by the AC power conversion unit (inverter). It is converted into electric power, and the AC power is supplied to various devices such as the power generation unit and the absorption chiller / heater and used as driving power. When the power generated by the power generation unit is insufficient, the AC power supplied from the external power supply system is rectified by the DC power converter (rectifier) and converted to DC power in the power converter, and then the AC power It is converted into alternating current power of a predetermined frequency by a conversion unit (inverter), and the alternating current power is supplied and used as supplementary power to various devices such as the power generation unit and the absorption chiller / heater.

  A hybrid thermoelectric supply system according to a third aspect is the invention according to the first aspect, wherein the AC power generated by the power generation unit is converted into DC power, and the AC power supplied from an external power supply system is converted into DC power. To an AC drive device having an AC power conversion unit that converts DC power converted by the DC power conversion unit into AC power having a predetermined frequency, or a DC drive device. It is characterized by supplying.

  In this hybrid thermoelectric supply system, the AC power generated by the power generation unit is converted into DC power by a DC power conversion unit (converter) in the power converter, and supplied to the AC drive device. In the AC drive device, The AC power conversion unit (inverter) converts the AC power into a predetermined frequency, or the DC power converted by the DC power conversion unit (converter) is supplied to a DC drive device and used as drive power. When the power generated by the power generation unit is insufficient, the AC power supplied from the external power supply system is rectified by the DC power converter (rectifier) and converted to DC power in the power converter, and the AC drive device In the AC drive device, the AC power conversion unit (inverter) converts the AC power into a predetermined frequency, or the DC power conversion unit (rectifier) converts the DC power to the DC drive device, Used as supplementary power.

Hybrid cogeneration system according to claim 4 is the invention of claim 2 or 3, so as to be operated with free-standing in terms of electric power without receiving power from an external power supply system, power of the power conversion equipment An integrated control device for determining the output amount is provided. As can be operated autonomously in power manner from the outside of the power supply system without receiving power supply, the power output of the power converter Ri by the integrated control device is determined. Therefore, it can be operated by electric power self-sustaining even if it can not affect the synchronization power supply from an external power supply system. In addition, about temporary excess and deficiency of the drive electric power with respect to the electric power generation amount of an electric power generation unit , a battery can be provided and it can absorb (charge, replenish) with the battery .

A hybrid thermoelectric system according to a fifth aspect is the invention according to the fourth aspect , wherein the power generation unit supplies all or part of the drive power to the power generation unit and the absorption chiller / heater device, and the integrated control device depending on the power generation capacity of the generator unit relative to the air conditioning load of formula chiller, such that the sum of the previous SL drive power is within the power generation allowance, characterized in that by Uni configured to select a device for supplying driving power It is what. In accordance with the air-conditioning load of the absorption chiller-heater is determined power generation capacity of the generator Uni Tsu bets, as the sum of the driving power supplied to the device with the power generation unit absorption chiller-heater is within the power generation allowance In addition, a device that supplies driving power is selected.

Hybrid thermoelectric system according to claim 6 is the invention of claim 4 or 5, wherein the power generating units is all or part of the drive power to the device with the power generation unit absorption chiller-heater supplies, pre Symbol integrated control device, in accordance with the power generation capacity of the generator unit relative to the air conditioning load of the absorption chiller-heater, wherein as the sum of the drive power is within the power generation allowance suppress driving power to supply feed to the device of the inverter drive system It is comprised so that it may carry out. Power generation capacity of the power generating unit in accordance with the air-conditioning load of the absorption chiller-heater is determined, as the sum of the drive power supplied to the device with the power generation unit absorption chiller-heater is within the power generation allowance inverter supplied to the device driving scheme driving power is inhibited.

According to the hybrid thermoelectric supply system of claim 1, the power generation unit burns gas or liquid fuel to generate power, and the power can be used as driving power for the power generation unit and the absorption chiller / heater. In the type chiller / heater, the reburning burner can burn the gas or liquid fuel using the remaining oxygen in the exhaust gas of the power generation unit as combustion air, and supply the high temperature exhaust gas from the reburning burner to the regenerator. In other words, since the retained heat and residual oxygen in the exhaust gas of the power generation unit can be used effectively, the thermal efficiency is greatly improved, and the amount of fuel supplied to the power generation unit and the reburning burner is reduced with the air conditioning load of the absorption chiller / heater. Proper distribution based on at least one of the power requirements for the power generation unit makes it possible to supply stable cold / hot water to the building in any air conditioning load region of the absorption chiller / heater. Also, to maximize the power generation power of the generator unit, since there is provided an integrated control device for determining the distribution amount of the fuel supply amount to the power generation unit and relapse burner, when a low air conditioning load of the absorption chiller-heater Even if the fuel supply to the reburning burner is stopped, it is assumed that the required heating amount will be exceeded due to the sensible heat of the exhaust gas of the power generation unit, but this is prevented and the generated power of the power generation unit is maximized. The fuel supply amount to the power generation unit and the reburn burner can be appropriately distributed. Further, the absorption chiller-heater is supplied with cooling water for cooling the intake Osamueki and refrigerant, the integrated control apparatus, a cooling water inlet temperature of the absorption chiller-heater of the power generated by the power generation unit to maximize since it is configured to raise and to suppress the cooling performance of the absorption chiller-heater, air-conditioning load of the absorption chiller-heater even when a low load, it is possible to maximize the power generation amount by the power generation unit.

  According to the hybrid thermoelectric supply system of claim 2, a DC power conversion unit that converts AC power generated by the power generation unit into DC power and converts AC power supplied from an external power supply system into DC power; Since the power conversion device having the AC power conversion unit that converts the converted DC power into the AC power of a predetermined frequency to be used as the driving power is provided, various devices such as the power generation unit and the absorption chiller / heater For example, AC power generated by the power generation unit can be converted into AC power of a predetermined frequency by the power conversion device and supplied, and even when the power generation power of the power generation unit is insufficient, it is supplied from an external power supply system. The AC power can be converted into AC power having a predetermined frequency and supplied by the power converter.

  According to the hybrid thermoelectric supply system of claim 3, the direct-current power conversion unit that converts alternating-current power generated by the power generation unit into direct-current power and converts alternating-current power supplied from an external power supply system into direct-current power. The power generation unit includes a power conversion device having an AC power conversion unit that converts the DC power converted by the DC power conversion unit into AC power having a predetermined frequency, or a DC drive device. The AC power generated by the power generation unit can be converted into DC power by the power converter and supplied to various AC drive devices or DC drive devices of the absorption chiller / heater. Even in this case, AC power supplied from an external power supply system can be converted into DC power by the power converter and supplied.

According to the hybrid thermoelectric supply system of claim 4, the integrated control device that determines the power output amount of the power conversion device so that the power conversion device can operate independently without receiving power supply from an external power supply system. Since it is provided, it is possible to operate independently in terms of power even when power supply from an external power supply system cannot be received.

According to the hybrid thermoelectric system of claim 5 , the power generation unit supplies all or part of the driving power to the power generation unit and the absorption chiller / heater device, and the integrated control device includes the air conditioning load of the absorption chiller / heater. depending on the power generation capacity of the power generation unit for, such that the sum of the drive power is power tolerance than the so constituted as to select a device for supplying driving power to the air conditioning load of the absorption chiller-heater depending determines the power generation capacity of the power generation units, the sum of the drive power supplied to the device with the power generation unit absorption chiller-heater is to be within the power generation allowance, the selection of equipment to supply driving power be able to.

According to the hybrid thermoelectric system of claim 6 , the power generation unit supplies all or part of the driving power to the power generation unit and the absorption chiller / heater device, and the integrated control device includes the air conditioning load of the absorption chiller / heater. depending on the power generation capacity of the power generation unit for, such that the sum of the drive power is power tolerance than the so constituted as to suppress the driving power supplied to the device of the inverter drive system, the absorption chiller machine to determine the power generation capacity of the power generating unit in accordance with the air-conditioning load of sea urchin by the sum of the drive power is within the power generation allowable amount supplied to the device with the power generation unit absorption chiller-heater, an inverter drive system The driving power supplied to the device can be suppressed.

  The hybrid thermoelectric supply system of the present embodiment burns fuel using the reburning burner of the absorption chiller / heater as the combustion unit's exhaust gas as combustion air, supplies the reburning burner's exhaust gas to the regenerator, and generates power with the power generation unit. The generated power is used as drive power for the power generation unit and the absorption chiller / heater. In particular, the amount of fuel supplied to the power generation unit and the reburning burner is determined by the air conditioning load of the absorption chiller / heater. And at least one of the power requirements for the power generation unit.

  As shown in FIG. 1, a hybrid thermoelectric supply system 1 (hereinafter referred to as a thermoelectric supply system 1) includes a gas turbine power generation unit 2 (hereinafter referred to as a power generation unit 2) that generates power by burning fuel gas (for example, city gas). ), A reburning burner 31 that burns fuel gas (for example, city gas) using the residual oxygen in the exhaust gas of the power generation unit 2 as combustion air, and an absorption liquid (for example, a lithium bromide solution) having the reburning burner 31 Absorption cold temperature having regenerators 36 and 37 for separating refrigerant (for example, water) and an evaporator 33 (see FIG. 3) for evaporating the refrigerant, and generating cold water or hot water and circulating it to a building such as a building A water machine 3 is provided, the exhaust gas from the reburning burner 31 of the absorption chiller / heater 3 is supplied to the regenerator 37, and the power generated by the power generation unit 2 is absorbed by the power generation unit 2. Those configured for use as various driving power such equipment chiller 3.

  As shown in FIGS. 1 and 2, the thermoelectric supply system 1 supplies power to various devices such as the power generation unit 2 and the absorption chiller / heater 3, and also generates the power generation unit 2 and the absorption chiller / heater 3. The power control panel 4 that is an integrated control device that controls the drive devices and the like, and a power conversion device 70, which converts high-frequency AC power generated by the power generation unit 2 into DC power. Converter 71 (DC power conversion unit), rectifier 72 (DC power conversion unit) that rectifies AC power supplied from commercial power supply 60 of the external power supply system and converts it into DC power, and the converted DC power An inverter 73 (AC power converter) that converts the AC power into a predetermined frequency (for example, 50 Hz or 60 Hz) for use as the driving power, and the AC power converted by the inverter 73 is a power generation unit. To the various devices such as the hot water 2 and the absorption chiller / heater 3.

The power generation unit 2 will be described.
As shown in FIG. 1, the power generation unit 2 includes a power generator 10, a gas turbine 11 that drives the power generator 10, a fuel gas compressor 12 that pressurizes fuel gas and supplies the fuel gas to the combustor 19 of the gas turbine 11. The control unit 13 is provided, and its power generation capacity is a comparatively small size of about 30 kw. The generator 10 is directly connected to the output shaft 14 of the gas turbine 11, and the combustion gas compressed by the fuel gas compressor 12 and the combustion air compressed by the compressor 18 are combusted by the combustor 19, and the high-temperature combustion is performed. The exhaust gas is expanded by the expander 20, and the expansion energy is taken out from the output shaft 14. As shown in FIGS. 4 and 5, an intake air adjustment valve 19 a for adjusting the amount of combustion air introduced into the combustor 19 is provided. The output shaft 14 is provided with a turbine rotational speed sensor 21 (rotary encoder) that detects the rotational speed of the gas turbine 11, and the combustor 19 is provided with a gas pressure sensor 29 that detects the gas pressure in the combustor 19. ing.

  A gas supply pipe 22 for supplying fuel gas is connected to the combustor 19. The gas supply pipe 22 is connected to the fuel gas compressor 12, a fuel gas flow rate sensor 23 for detecting the flow rate of the fuel gas, and a fuel gas flow rate. A fuel gas flow rate adjusting valve 24 for adjusting the flow rate is provided. The power generation unit 2 is also provided with a cooling fan 25 that cools the fuel gas compressor 12. The exhaust gas expanded by the expander 20 is sent to the reburning burner 31 of the absorption chiller / heater 3 through the exhaust gas duct 26, and the reburning burner 31 burns fuel gas using this exhaust gas as combustion air. The exhaust gas duct 26 is provided with an exhaust gas O2 concentration sensor 27 for detecting the O2 concentration in the exhaust gas and an exhaust gas temperature sensor 28 for detecting the temperature of the exhaust gas.

  The control unit 13 is electrically connected to the power control panel 4, and in addition to signals from the power control panel 4, the turbine speed sensor 21, the fuel gas flow sensor 23, the gas pressure sensor 29, etc. The control unit 13 controls the fuel gas compressor 12, the fuel gas flow rate adjustment valve 24, the cooling fan 25, and the like based on the input necessary signals. Necessary signals are sequentially output to the power control panel 4. FIG. 4 shows a block diagram of a control system when the power control panel 4 and the control units 13 and 32 are collectively used as the control device 80. In fact, the control device 80 is actually configured as described above. Is also possible.

The absorption chiller / heater 3 will be described.
As shown in FIGS. 1 and 4, the absorption chiller / heater 3 includes a chiller / heater body 30, a reburning burner 31, a control unit 32, and the like. Are provided with an evaporator 33, an absorber 34, a condenser 35, a low temperature regenerator 36, a high temperature regenerator 37, a low temperature heat exchanger 38, a high temperature heat exchanger 39, and the like.

  A series of absorption cycles of absorption liquid and refrigerant in the chiller / heater body 30 when chilled water is supplied from the absorption chiller / heater 3 to the building will be described. First, the evaporator 33 is maintained in a substantially vacuum state. The refrigerant is sent by the refrigerant pump 40, and in the evaporator 33, the refrigerant evaporates to become refrigerant vapor (water vapor). At this time, the circulating water for air conditioning is deprived of heat and cooled. The refrigerant vapor evaporated by the evaporator 33 is absorbed by the absorption liquid when the absorption liquid is cooled by cooling water by the absorber 34. The low concentration (for example, concentration 56%) absorption liquid which absorbed the refrigerant | coolant with the absorber 34 is sent to the low temperature regenerator 36 through the low temperature heat exchanger 38 by the 1st absorption liquid pump 41, and the low temperature heat exchanger 38 is sent. After the heat is exchanged with the absorbing liquid that circulates and heated, the refrigerant is heated by the low-temperature regenerator 36 and a part of the refrigerant is separated and recovered from the absorbing liquid.

  The slightly high concentration (for example, 58% concentration) absorption liquid from which a part of the refrigerant has been separated by the low temperature regenerator 36 is sent to the high temperature regenerator 37 through the high temperature heat exchanger 39 by the second absorption liquid pump 42. After the heat exchange with the absorbing liquid circulating in the high-temperature heat exchanger 39 and heating, the refrigerant is further heated from the high-temperature regenerator 37 and further separated and recovered from the absorbing liquid. The high-temperature regenerator 37 is introduced with high-temperature (for example, 1000 ° C.) exhaust gas from the reburn burner 31, and the absorption liquid is heated by this exhaust gas. The refrigerant separated and recovered by the low temperature regenerator 36 or the high temperature regenerator 37 is condensed by the condenser 35 and then sent to the evaporator 33 again. The refrigerant separated by the high temperature regenerator 37 is sent to the condenser 35 through the low temperature regenerator 36, and the absorption liquid is heated by the high temperature refrigerant in the low temperature regenerator 36. The high concentration (for example, 63% concentration) absorption liquid from which the refrigerant has been separated by the high temperature regenerator 37 is subjected to heat exchange between the high concentration heat exchanger 39 and the low temperature heat exchanger 38 and the intermediate concentration absorption liquid, respectively. Then, it is sprayed into the absorber 34 and absorbs the refrigerant vapor again.

  By the way, the absorption liquid passage 90 extending from the first absorption liquid pump 41 to the low-temperature heat exchanger 38 and the evaporator 33 are connected by a bypass passage 91, and a bypass valve controlled by the control device 32 is connected to the bypass passage 91. 92 is provided. On the other hand, in order to supply hot water to the building from the absorption chiller / heater 3, a refrigerant passage 93 extending from the low-temperature regenerator 36 to the condenser 35 and the evaporator 33 are connected by a cooling / heating switching passage 94. A cooling / heating switching valve 95 controlled by the control device 32 is provided in the passage 94. By opening the cooling / heating switching valve 95 and introducing a relatively high temperature (for example, 70 to 80 ° C.) refrigerant in the refrigerant passage 93 from the cooling / heating switching passage 94 to the evaporator 33, the circulating water is heated in the evaporator 33. The

  Here, as shown in FIG. 1, in the cold / hot water circulation passage connected to the cold / hot water machine body 30, cold / hot water for detecting the inlet temperature of the cold / hot water to the cold / hot water machine body 30 (absorption-type cold / hot water machine 3). An inlet temperature sensor 47, a chilled / hot water outlet temperature sensor 48 for detecting the outlet temperature of the chilled / hot water from the chiller / heater body 30 (absorption chiller / heater 3), and a chilled / hot water flow sensor 49 for detecting the flow rate of the chilled / hot water. A cold / hot water pump 51 for circulating cold / hot water is provided. A cooling water passage is connected to the chiller / heater body 30, and a cooling tower 50 is connected to the cooling water passage. The cooling tower 50 is provided with a cooling fan 50b. In the cooling water passage, the cooling water pump 50a that circulates the cooling water, and the inlet temperature of the cooling water to the chiller / heater body 30 (absorption chiller / heater 3) are provided. A cooling water inlet temperature sensor 50c for detection is provided.

  As shown in FIG. 1, a gas supply pipe 43 that supplies fuel gas is connected to the reburning burner 31, and a fuel gas flow sensor 44 that detects the flow rate of the fuel gas; A fuel gas flow rate adjustment valve 45 for adjusting the flow rate of the fuel gas is provided. Here, the exhaust gas of the gas turbine 11 is at a high temperature (for example, about 600 ° C.), a large amount of oxygen remains (for example, 18% residual oxygen concentration medicine), and unburned gas is also included. Therefore, the reburning burner 31 and the expander 20 of the gas turbine 11 are connected by the exhaust gas duct 26, and the exhaust gas duct 26 is introduced to introduce the entire amount of the exhaust gas of the power generation unit 2 into the reburning burner 31. The stored heat is effectively used to improve the thermal efficiency of the entire system.

  That is, the reburn burner 31 receives the supply of the exhaust gas and the fuel gas from the power generation unit 2, and can burn the fuel gas for reheating using the residual oxygen in the exhaust gas and the retained heat of the exhaust gas. The reburning burner 31 is provided with an intake fan 46 for introducing combustion air from the outside air, and the residual oxygen in the exhaust gas detected by the exhaust gas O2 concentration sensor 27 is less than a predetermined concentration (for example, 10%). In order to compensate for the insufficient oxygen, the combustion air can be supplied to the reburning burner 31 by driving the intake fan 46 with the power control panel 4.

  On the other hand, the exhaust gas from the reburning burner 31 is heat-exchanged with the absorbing solution in the high temperature regenerator 37 and then released to the outside air through the exhaust gas duct 52. In the exhaust gas duct 52, the exhaust gas O2 concentration sensor 53 is provided. Is provided. The absorption chiller / heater 3 including the power generation unit 2 and the reburning burner 31 is unitized so that the length of the exhaust gas duct 26 can be shortened, and heat loss of the exhaust gas of the power generation unit 2 to the outside can be suppressed as much as possible.

  The control unit 32 is electrically connected to the power control panel 4. The control unit 33 includes a signal from the power control panel 4, a cold / hot water inlet temperature sensor 47, a cold / hot water outlet temperature sensor 48, and cold / hot water. Signals from the flow sensor 49, the exhaust gas O2 sensor 53, the cooling water inlet temperature sensor 50c, and the like are input, and the control unit 32 controls the fuel gas flow control valve 45 and the refrigerant pump 40 based on the input necessary signals. The absorbent pumps 41 and 42, the cooling / heating switching valve 95, the cooling / heating water pump 51, the cooling water pump 50a, the cooling fan 50b, and the bypass valve 92 are controlled, and necessary input signals are sequentially output to the power control panel 4. To do.

Next, the power control panel 4 will be described.
As described above, the power control panel 4 has the function of supplying power to the power generation unit 2 and the absorption chiller / heater 3 and the like and the function of controlling the power generation unit 2 and the absorption chiller / heater 3 and the like. . Regarding the configuration of the power control panel 4 that supplies power to the power generation unit 2 and the absorption chiller / heater 3 and the like as a power supply device, AC power of a predetermined frequency is supplied from the power conversion device 70 to various devices (fuels) of the power generation unit 2. The gas compressor 12 and the like and the absorption chiller / heater 3 are supplied to various devices (refrigerant pump 40, absorption liquid pumps 41 and 42, etc.).

  As shown in FIG. 2, the generator 10 of the power generation unit 2 is provided with a turbine rotation speed adjuster 10 a (see FIG. 4), and the power converter 70 receives the turbine rotation received from the power control panel 4. By outputting a PWM signal corresponding to the signal of the number to the gas turbine rotation speed adjuster 10a, the gas turbine 11 can be restricted and adjusted by the rotation speed by the gas turbine rotation speed adjuster 10a. In addition, the solar cell 63 and the storage battery 64 are connected to the power converter 70 via the charge / discharge controller 62, respectively. The storage battery 64 can be charged with power from the solar battery 63 or DC power received from a commercial power source and converted by the power converter 70.

  Here, when the power generation unit 2 generates substantially the same power as the power required by the power generation unit 2 and the absorption chiller / heater 3 or the like, the power control panel 4 normally has power from the commercial power supply 60 or a storage battery. It is not necessary to receive power from 64. However, when the absorption chiller / heater 3 is started / stopped or when the rotation speed of the gas turbine 11 is controlled by the air conditioning load of the absorption chiller / heater 3, the power generation amount from the power generation unit 2 alone is insufficient. May be. In this case, with respect to the insufficient power, when the storage amount of the storage battery 64 is larger than a predetermined amount, power is supplied from the storage battery 64, and when the storage amount of the storage battery 64 is equal to or less than the predetermined amount, commercial power While replenishing power from 60, the power from the commercial power source 60 may be charged into the storage battery 64.

  Next, regarding the configuration as a control device of the power control panel 4 that controls the power generation unit 2 and the absorption chiller / heater 3 and the like, the power control panel 4 includes signals from the control units 13 and 32, the exhaust gas O2 sensor 27, 53, a signal from the exhaust gas temperature sensor 28, and the like are input. Based on these necessary signals, the power control panel 4 can directly generate the power generation unit 2 and the absorption cold temperature through the control units 13 and 32. Various devices of the water machine 3 are controlled.

  Here, in the present invention, the amount of fuel gas supplied to the gas turbine 11 and the reburning burner 31 of the power generation unit 2 by the power control panel 4 is changed to the air conditioning load of the absorption chiller / heater 3 and the power to the power generation unit 2. Appropriate distribution is made based on at least one of the requests. The appropriate distribution of the fuel supply amount is achieved by the power control panel 4 performing calculations according to the following three purposes shown in [1], [2], and [3].

[1] Suppressing fluctuations in the temperature of the cooling / heating outlet of the absorption chiller / heater 3 caused by the start / stop (start / stop) of the reburning burner 31 when the air conditioning load of the absorption chiller / heater 3 is low.
[2] Optimization of combustion conditions by suppressing emission of CO and NOx from the exhaust gas of the reburning burner 31.
[3] Maximizing the power generated by the power generation unit 2.

  [1] In order to suppress fluctuations in the temperature of the cooling / heating outlet of the absorption chiller / heater 3 caused by the start / stop (start / stop) of the reburning burner 31 when the air-conditioning load of the absorption chiller / heater 3 is low, Specifically, (1) suppressing the power generation amount of the power generation unit 2 in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3, and (2) absorbing in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3. Bypassing a part of the liquid from the bypass passage 91 to the evaporator 33, (3) suppressing the turbine rotational speed of the gas turbine 11 in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3, and (4) absorption. At least one of reducing the amount of combustion air supplied to the combustor 19 of the power generation unit 2 in accordance with a decrease in the air conditioning load of the water chiller / heater 3 is performed.

  [2] In order to suppress the emission of CO and NO x from the exhaust gas of the reburning burner 31 and optimize the combustion conditions, specifically, (1) the gas turbine 11 according to the oxygen concentration of the exhaust gas of the reburning burner 31 At least one of (2) reducing the amount of combustion air supplied to the combustor 19 of the power generation unit 2 is performed.

  [3] In order to maximize the power generated by the power generation unit 2, specifically, (1) a part of the absorbent is evaporated from the bypass passage 91 according to a decrease in the air conditioning load of the absorption chiller / heater 3. At least one of bypassing to 33 and (2) raising the cooling water inlet temperature of the absorption chiller / heater 3 is performed.

  Here, basic control of the thermoelectric supply system 1 will be described with reference to FIG. 5 and the like, and [1], [2], and [3] will be described in association with them as appropriate. In FIG. 5, [A], [B], and [C] indicate control and calculation for the power generation unit 2, and [D], [E], and [F] indicate control and calculation for the absorption chiller-heater 3. ing. These controls and calculations are performed by the integrated control panel 4 but may be performed by the control devices 13 and 32.

  First, the power generation unit 2 calculates and controls the exhaust gas temperature of the gas turbine 11, the turbine rotation speed of the gas turbine 11, and the DC voltage of the power converter 70. For the exhaust gas temperature of the gas turbine 11 and the DC voltage of the power converter 70, as shown in FIG. 5C, the flow rate of the fuel gas supplied from the fuel gas compressor 12 is used as the manipulated variable, and the gas turbine outlet The fuel flow rate request calculated by the PID control calculation from the measured value and target value (for example, 600 ° C.) of the exhaust gas temperature of the gas turbine 11 by temperature control, and the measured value and target of the DC voltage by the power converter DC voltage control From the fuel flow rate request calculated in the same way from the value (eg, 330V), the low signal is selected by the minimum signal selection circuit, the fuel request command is issued by the gas turbine fuel flow rate control, and the fuel supply according to the fuel flow rate request by the low select is performed. The fuel gas compressor 12 (in some cases, the fuel gas compressor 12 and the fuel flow rate so as to supply the quantity to the combustor 19 of the gas turbine 11. To control the Fushiben 24).

  In addition, when the DC part voltage of the power converter 70 is lower than a set voltage (for example, 290 V), power is supplied from the commercial power supply 60. Further, as shown in FIG. 5A, for the turbine speed of the gas turbine 11, the turbine speed is calculated from the target value of the turbine speed of the gas turbine 11, and the power converter 70 is controlled. The converter 71 of the power converter 70 generates a PWM signal corresponding to the turbine rotational speed and outputs the PWM signal to the turbine rotational speed adjuster 10a. The gas turbine 11 becomes the turbine rotational speed by the turbine rotational speed adjuster 10a. So that it is electrically constrained and adjusted. Further, as shown in FIG. 5B, the gas turbine intake valve opening is calculated from the target value of the gas turbine intake valve opening, and the gas turbine intake control valve 19a is controlled to be the opening, The amount of combustion air supplied to the combustor 19 is adjusted.

  For example, when the power supplied from the power conversion device 70 to the power generation unit 2 and the absorption chiller / heater 3 is increased, there is no increase in the power generation amount of the power generation unit 2 or the increase in the amount of power supply from the commercial power supply 60. Since the direct current voltage of the power conversion device 70 decreases, the fuel supply to the gas turbine 11 is increased so that the voltage does not decrease. When the voltage drop cannot be suppressed due to the increase in fuel, electric power is supplied from the commercial power source 60. Conversely, when the power supplied from the power converter 70 to the power generation unit 2 and the absorption chiller / heater 3 is decreased, the fuel is supplied to the gas turbine 11 so as to suppress an increase in the DC voltage of the power converter 70. Reduce the amount. Further, when the exhaust gas temperature at the outlet of the gas turbine 11 is decreased, the amount of fuel supplied to the gas turbine 11 is increased. Conversely, when the exhaust gas temperature at the outlet of the gas turbine 11 is increased, the gas turbine 11 is increased. Reduce the amount of fuel supplied to Here, since the fuel supply is a low select of both control outputs, a smaller fuel flow rate request is output as an operation command to the fuel gas compressor 12.

  On the other hand, the absorption chiller / heater 3 calculates and controls the chilled / hot water outlet temperature. For the cold / hot water outlet temperature, as shown in FIG. 5 [D], the measured value and the target value of the cold / hot water outlet temperature are controlled by the cold / hot water outlet temperature control, with the fuel supply amount to the reburning burner 31 being the manipulated variable. Then, the flow rate of fuel supplied to the reburning burner 31 is calculated by PID control calculation, and the fuel gas flow rate adjustment valve 45 is controlled so as to be the fuel flow rate. For example, in the case of cooling operation, when the cold / hot water outlet temperature decreases, the amount of fuel supplied to the reburning burner 31 is decreased. Conversely, when the cold / hot water outlet temperature increases, the fuel to the reburning burner 31 decreases. The fuel gas flow control valve 45 is controlled so as to increase the supply amount.

  By the way, when the cooling capacity becomes excessive due to a sudden decrease in the air conditioning load of the absorption chiller / heater 3 or the overheating of the regenerators 36 and 37, the refrigerant (water) circulating in the absorption chiller / heater 3 freezes. If there is a possibility that the outlet temperature of the cold / hot water is significantly lower than the set temperature (control temperature) (for example, 5.5 ° C.), the combustion of the reburn burner 31 is forcibly stopped and further lowered. In the case of (for example, 5.0 ° C.), the refrigerant pump 40 for spraying the refrigerant to the evaporator 33 is stopped for a certain period to suppress the cooling capacity.

  When such an on / off logic operates, the temperature of the cold / hot water outlet largely fluctuates, which causes a decrease in air conditioning performance. In particular, in this thermoelectric supply system 1, since the sensible heat of the exhaust gas of the power generation unit 2 is used in the absorption chiller / heater 3, the reburning burner 31 has excessive capacity when the air-conditioning load of the absorption chiller / heater 3 is low. Thus, not only the repeated start and stop (start / stop) of the reburn burner 31 is likely to occur frequently, but also the cold / hot water temperature control becomes unstable due to this, causing the refrigerant pump 40 to start and stop. Since it is assumed that it becomes easy, the measure [1] is effective to improve this.

  Further, with respect to changes in the combustion amount of the reburning burner 31 performed to suppress fluctuations in the temperature of the cold / hot water outlet, the flow rate of combustion exhaust gas (combustion air of high temperature and high residual oxygen) supplied from the power generation unit 2 is constant (turbine Therefore, it is difficult to keep the air ratio to the combustion of the reburning burner 31 constant. In particular, when the combustion amount of the reburning burner 31 is small (for example, when the oxygen concentration in the exhaust gas after reburning is 10% or more), it becomes difficult to suppress the emission of CO, NO x, etc. In order to improve the above, the measure [2] is effective.

  When the thermoelectric supply system 1 is regarded as a power generation facility, it is desirable to operate the power generation unit 2 with the maximum capacity regardless of the air conditioning load of the absorption chiller / heater 3 in consideration of the cost countermeasure effect of the system installation. However, when the air conditioning load of the absorption chiller / heater 3 is very low, even if the fuel supply to the reburning burner 31 is stopped, the required heating amount may be exceeded only by the sensible heat of the exhaust gas from the gas turbine 11. Since it is assumed, in order to improve this, the measure [3] is effective. FIG. 5 shows the control of [1]-(1) (2) (3) (4), [2]-(1) (2), [3]-(1) (2) and other controls. Represents the relationship between

  [1] In order to suppress fluctuations in the temperature of the cooling / heating outlet of the absorption chiller / heater 3 due to the start / stop of the reburning burner 31 when the air conditioning load of the absorption chiller / heater 3 is low. After calculating and estimating the air conditioning load from the operating state of the absorption chiller / heater 3, when the air conditioning load approaches the start / stop region of the reburn burner 31, the gas turbine 11 supplies the absorption chiller / heater 3. It is effective to cope with the problem by reducing the heat input or reducing the thermal efficiency of the absorption chiller / heater 3. In order to reduce the heat input from the power generation unit 2, it is necessary to reduce the flow rate or temperature of the exhaust gas from the gas turbine 11, which corresponds to (1) a decrease in the air conditioning load of the absorption chiller / heater 3. This can be realized by suppressing the power generation amount of the power generation unit 2, and (3) it can be realized by suppressing the turbine rotation speed of the gas turbine 11 according to a decrease in the air conditioning load of the absorption chiller / heater 3. (4) It can be realized by reducing the amount of combustion air supplied to the combustor 19 of the power generation unit 2 in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3. In order to reduce the thermal efficiency of the absorption chiller / heater 3, (2) a part of the absorbent is bypassed from the bypass passage 91 to the evaporator 33 in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3. Can be realized. However, for (2), the effect during heating operation cannot be expected from the cycle theory.

Here, specific numerical values are shown to show the effect of the above control. The equipment conditions used for the trial calculation are as follows. In the power generation unit 2, maximum power generation amount: 18.5 [kW], fuel consumption amount: 15.1 [Nm ³ / h] (13A gas, outside air temperature: 25 ° C., during maximum power generation operation), turbine rotation speed; 96000 [rpm], Combustion gas compressor power consumption: 2.0 [kW] (assumed constant), Inverter power supply amount: 22.0 [kW] (Cooled / hot water main unit + cold / hot water pump, fuel gas compressor only fed ) (Air conditioning load factor 100%), supplementary power amount: 3.5 [kW] (supplemented from commercial power, inverter power supply amount-power generation amount) In the absorption chiller-heater 3, rated refrigeration capacity: 210 [ USRT], reburn burner fuel consumption 32.2 [Nm ³ / h] (reburn burner consumption, 13A gas, outside air temperature: 25 ° C., during maximum power generation operation), chiller / heater main body + chill / hot water pump power consumption: 20 [KW] (Air-conditioning load factor 100% operation (Power is supplied from the inverter of the power converter) (proportional to the square of the air conditioning load, assuming 50% or less is constant), cooling water pump + cooling tower power consumption: 23 [kW] (operating at 100% air conditioning load factor, commercial Direct power supply from power supply) (proportional to the square of the air conditioning load, assuming 50% or less is constant).

  FIG. 6 and FIG. 7 show the fuel distribution (fuel consumption) and the power generation / reception / power supply status (power consumption) with respect to the air-conditioning load factor under the above-described equipment conditions. Here, the air conditioning load factor is a ratio with respect to the air conditioning load when the rated refrigeration capacity of the absorption chiller / heater 3 is exhibited. In the case of an absorption chiller / heater used for general air conditioning or the like, a partial load (for example, 40 In most cases, it is operated at a lower load in the intermediate period such as spring and summer.

  The air conditioning load factor-fuel consumption rate graph of FIG. 6 shows the fuel flow rate consumed by the gas turbine 11 and the reburn burner 31 and the total fuel consumption amount with respect to the air conditioning load factor. Here, in the power generation unit 2, the fuel flow rate is operated according to the power consumption of the power supply target device from the inverter 73 of the power converter 70, and the fuel consumption of the reburning burner 31 is calculated from the required fuel amount at the air conditioning load factor. It is equal to the value obtained by subtracting the fuel consumption in the power generation unit 2 (ignoring combustion loss, etc.). However, burner combustion becomes unstable in a region where the amount of fuel supplied to the reburning burner 31 is small. Here, the turndown point is 20% of the rated combustion amount, and the air conditioning load is 17.5 to 31.4%. Then, it is expected that the reburning burner 31 starts and stops frequently, and the temperature of the cold / hot water outlet becomes unstable.

  In the air conditioning load factor-power amount graph of FIG. 7, the power generation amount in the power generation unit 2, the supplementary power amount (the power amount supplemented from the commercial power supply), the inverter power supply amount (of the power conversion device 70) with respect to the air conditioning load factor. The amount of power supplied from the inverter 73 to various devices), the direct power supply power (the amount of power supplied directly from the commercial power source 60 without going through the power converter 70), and the amount of power received (the total amount of power received from the commercial power source). ing. The amount of power supplied to the inverter supplied to the chiller / heater main body 30 and the chilled / hot water pump 51 changes according to the air conditioning load factor, and the power generation unit 2 tries to generate the same amount of power as the amount of power supplied to the inverter. It becomes. However, in the high load region where the air conditioning load factor is 91% or more, the amount of power supply exceeds the maximum power generation amount, so it is necessary to replenish electric power, and in the low load region of 17.5% or less, the exhaust gas from the gas turbine 11 is required. Since it is necessary to suppress sensible heat, it is necessary to replenish electric power from the commercial power source 60 in order to suppress the generated power of the power generation unit 2. The turbine rotation speed of the gas turbine 11 is constant.

  [1] In the control for the purpose of suppressing fluctuations in the outlet temperature of the chilled / hot water of the absorption chiller / heater 3 caused by the start / stop of the reburning burner 31 when the absorption chiller / heater 3 is under low load, By suppressing the power generation amount of the power generation unit 2 in accordance with the decrease in the air conditioning load 3, the sensible heat brought by the exhaust gas of the gas turbine 11 can be suppressed. FIGS. 8 and 9 are graphs similar to those in FIGS. 6 and 7, but as shown in the air conditioning load factor-electric energy graph of FIG. 9, the power generation unit 2 in the region where the air conditioning load factor is 50% or less is shown. By suppressing the power generation amount, the flow rate of the fuel gas supplied to the combustor 19 of the gas turbine 11 is suppressed, and the combustion amount to the reburn burner 31 is increased to compensate for the suppression amount. As a result, as shown in FIG. As shown in the air conditioning load factor-fuel consumption graph, the burner start / stop region can be moved from 12.3 to 26.2% to the low load factor side.

  As a further control, by bypassing a part of the absorbing liquid from the bypass passage 91 to the evaporator 33 in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3, the start / stop region of the reburning burner 31 can be reduced. It can be expected to move to a lower load factor side. FIGS. 10 and 11 are graphs similar to those of FIGS. 6 and 7 described above, in which a bypass is added to the evaporator 33 of the absorbing liquid in addition to the suppression of the power generation amount of the power generation unit 2. By intermittently bypassing the absorbing liquid in the region where the air conditioning load factor is 40% or less, as a result, as shown in the air conditioning load factor-fuel consumption graph of FIG. It can be moved to a lower load side of 20.1%. Here, the calculation was performed by reducing the air-conditioning capacity for the same fuel amount by 20% in the region where the air-conditioning load factor is 40% or less by performing the bypass of the absorbing liquid. It should be noted that even by bypassing a part of the absorption liquid from the bypass passage 91 to the evaporator 33, frequent start / stop of the burner is suppressed, and fluctuation in the temperature of the cold / hot water outlet of the absorption chiller / heater 3 is suppressed. Is possible.

  Next, in [2] control aimed at optimizing the combustion conditions by suppressing the emission of CO and NOx in the exhaust gas of the reburning burner 31, the residual oxygen in the exhaust gas at the outlet of the absorption chiller / heater 3 It is necessary to measure the amount and maintain the combustion conditions with low CO and NO x. 12 and 13 are characteristic graphs of CO and NOX concentrations with respect to the oxygen ratio in the exhaust gas of the reburning burner 31 (estimated from the oxygen concentration in the exhaust gas at the outlet of the absorption chiller / heater). As shown in the graph of FIG. 12, since the generated concentration increases rapidly in the high oxygen region, especially for CO, and the NOx also increases in the high oxygen concentration region, the oxygen concentration is set as the combustion condition. It is desirable to control in the range of 1% to 10% (preferably 1 to 5%). Further, in order to effectively utilize the residual oxygen in the reburning burner inlet high-temperature exhaust gas, it is desirable to control the outlet oxygen concentration to be kept as low as possible. Since the combustion supply amount to the reburning burner 31 is given priority in the cold / hot water outlet temperature control, the control operation here is the exhaust gas flow rate from the gas turbine 11, that is, the turbine rotational speed of the gas turbine 11, or the power generation unit 2 It is effective to use the intake throttle (the opening degree of the intake control valve 19a) of the combustion air supplied to the combustor 19.

  Next, in [3] control aiming at maximizing the power generated by the gas turbine 11, the absorption chiller / heater particularly by the exhaust gas sensible heat of the gas turbine 11 when the absorption chiller / heater 3 has a low air conditioning load. It is necessary to consider so that 3 is not overcooled. Further, under such conditions, as shown in FIGS. 14 and 15, it is assumed that the reburning burner 31 is frequently started and stopped in which the burner starting and stopping area is 26.1 to 40%. Therefore, in accordance with a decrease in the air conditioning load of the absorption chiller / heater 3, either a part of the absorbing liquid is bypassed from the bypass passage 91 to the evaporator 33 or the cooling water inlet temperature is increased. The burner start / stop region can be moved to the lower load factor side, and overcooling of the chiller / heater 3 can be expected to be avoided.

  In order to suppress the power generation amount of the power generation unit 2 and to bypass a part of the absorption liquid from the bypass passage 91 to the evaporator 33 or raise the cooling water inlet temperature, the absorption cold temperature It is necessary to estimate the air conditioning load from the internal information of the water machine 3, the cold / hot water temperature, the cooling water temperature, and the like. This estimate is based on the calculation based on the cold / hot water outlet temperature, cold / hot water inlet temperature, and hot / cold water flow rate of the absorption chiller / heater, and the high-temperature regenerator temperature, cold / hot water outlet temperature, and chilled water inlet temperature of the absorption chiller / heater. It is effective to perform one or a combination of calculations based on the combustion amount of the reburning burner 31 of the absorption chiller / heater.

  In the calculation based on the chilled / hot water outlet temperature, the chilled / hot water inlet temperature and the chilled / hot water flow rate of the absorption chiller / heater, the amount of heat cooled (or heated) by the absorption chiller / heater 3 is directly measured. Air conditioning load estimation processing, and the calculation formula thereof is air conditioning load estimation = [(| cold hot / cold water inlet temperature−cold hot / cold water outlet temperature | ÷ rated temperature (for example, 5 ° C.)) × (cold / hot water flow rate ÷ rated flow rate (for example, 2100 USRT)). When calculating the temperature difference of the cold / hot water inlet / outlet with this calculation formula, particularly when the flow rate of the cold / hot water is small, it is necessary to consider the average time for the cold / hot water to pass through the absorption-type cold / hot water machine 3. If the average passage time Δt = (cold / hot water flow rate / rated flow rate) × rated passage time, estimated air conditioning load (t) = (| cold / hot water inlet temperature (t−Δt) −cold / hot water outlet temperature (t) | ÷ Rated temperature × (cold / hot water flow rate (t−Δt / 2) ÷ rated flow rate).

Next, the calculation based on the high-temperature regenerator temperature, the cold / hot water outlet temperature, and the cold / hot water inlet temperature of the absorption chiller / heater 3 is an empirical formula estimated from operation data measured by an air conditioning capability test or the like. During cooling, estimated air conditioning load value = (A × (high temperature regenerator temperature−cooling water inlet temperature) −B) × (cold water outlet temperature ÷ C) ^1/2. Value = D × high temperature regenerator temperature−E. A, B, C, D, and E are parameters obtained by experiments.

  Next, in the calculation based on the combustion amount of the reburning burner 31 of the absorption chiller / heater 3, the effect of the exhaust gas sensible heat of the gas turbine 11 is not taken into consideration, and therefore the load of the reburning burner 31 is estimated. . However, it is effective when the estimated value is used for suppressing fluctuations in the temperature of the chilled / hot water outlet of the absorption chiller / heater 3 caused by the start / stop of the reburning burner 31 at low load. This air conditioning load estimated value = F * reburnt fuel valve opening + G. However, this equation is a case where the relationship between the fuel valve opening and the air conditioning load is a primary linear characteristic, and F and G are parameters. The characteristic equation may be a nonlinear function or a table.

  Since all of the above air conditioning load estimated values are calculated based on instantaneous values (partly past instantaneous values), there is a possibility that they become disturbance factors due to temporary load fluctuations and measurement noise. Therefore, it is desirable to use the calculated value for the control after smoothing the estimated value by moving average calculation (about 10 to 20 minutes) or the like.

  In order to confirm the effect by the above control, the example which implemented the dynamic characteristic simulation is shown. In carrying out the simulation, a mathematical model of the gas turbine 11 and the absorption chiller / heater 3 centered on the thermal mass balance equation was used. In addition, in this calculation, confirmation of suppression of the cold / hot water exit temperature fluctuation | variation of the absorption-type cold / hot water machine 3 resulting from the start / stop of the reburning burner 31 at the time of low load was performed using suppression of the previous gas turbine electric power generation amount. Is.

  FIG. 16 is a plurality of graphs when operating with only the basic control logic with respect to changes in the air conditioning load, and FIG. 17 is a plurality of graphs when operating with the power generation amount of the power generation unit 2 being suppressed. is there. The power generation amount of the power generation unit 2 is controlled by correcting the set value of the outlet temperature control of the gas turbine 11 by the air conditioning load estimation calculation using the calculation based on the combustion amount of the reburning burner 31 of the absorption chiller / heater 3 described above. It is realized by doing. As can be seen from the plurality of graphs of FIG. 16 and FIG. 17 obtained by this simulation, in the technology of the present invention, appropriate fuel distribution is performed according to the power demand and heat demand to the thermoelectric supply system 1, and any air conditioning is performed. It is possible to provide a function capable of providing stable cold water (or hot water) in the load region.

  Here, in the present invention, as described above, the power supply amount of the fuel gas supplied to the gas turbine 11 and the reburning burner 31 of the power generation unit 2 by the power control panel 4 is set to the air conditioning load of the absorption chiller / heater 3. The power control unit 4 is configured so as to be appropriately distributed based on at least one of the power demands to the power generation unit 2. Further, [4] the power control panel 4 does not receive power supply from the external commercial power supply 60 and is independent in terms of power. Thus, the power output amount of the power conversion device 70 is determined so that it can be operated. Therefore, even when it is not possible to receive power supply from the external commercial power supply 60, it is possible to operate with power independence. The temporary excess or deficiency of the drive power with respect to the power generation amount of the power generation unit 2 can be absorbed (charged, replenished) by the storage battery 64.

  In order to realize this, the power generation unit 2 supplies all or part of the drive power to the devices of the power generation unit 2 and the absorption chiller / heater 3, and [4]-(1) the integrated control device 4 According to the power generation allowable amount of the power generation unit 2 with respect to the air conditioning load of the water chiller / heater 2, the device for supplying the drive power is selected so that the total drive power is within the power generation allowable amount, and , [4]-(2) The integrated control device 4 is configured so that the sum of the drive powers is within the allowable power generation amount according to the allowable power generation amount of the power generation unit 2 with respect to the air conditioning load of the absorption chiller / heater 3. It is comprised so that the drive electric power supplied to the apparatus (of an inverter drive system) may be suppressed. Thus, for example, as shown in FIG. 7, the amount of supplementary power (the amount of power supplemented from the commercial power supply 60 via the power converter 70, and when the air conditioning load is 17.5% or less or 91% or more, It is possible to operate as a self-supporting power generation system independent from the commercial power source 60.

As an example of the thermoelectric supply system 1 described above, the balance of the amount of heat and electric power in the thermoelectric supply system 1 including the absorption chiller / heater 3 having the capacity of 210 RT (refrigeration ton) will be described with reference to FIG. . In addition, in the following description, the ratio with respect to the maximum load of the cold or warm temperature (absorbed heat amount) of the absorption chiller / heater 3 for each value of the amount of heat and electric power is also written in parentheses.
As shown in FIG. 18, the maximum load of the absorbed heat amount in this absorption chiller / heater 3 is 386.7 kW (100%). On the other hand, when the absorption chiller / heater 3 is used alone, the amount of heat required to supply the maximum load from the absorption chiller / heater 3 is 423.1 kW (109.4%).

  On the other hand, in the thermoelectric supply system 1 in which the absorption chiller / heater 3 is combined with the power generation unit 2, the calorific value of fuel gas supplied to the combustor 19 of the gas turbine 11 is 174.9 kW (45.2%). The electric power generated by the power generation unit 2 is 150.4 kW (38.9%). Along with this exhaust gas, a fuel gas for reheating of 274.3 kW (70.9%) is supplied to the reburning burner 31, and the reburning burner 31 uses the remaining oxygen and retained heat of the exhaust gas to recharge. By doing so, the absorption heat quantity 386.7 kW (100%) in the maximum load state is supplied from the absorption chiller / heater 3.

  That is, the total calorific value of the fuel gas supplied to the thermoelectric supply system 1 is 449.2 kW (116.1%). Therefore, as compared with the case where the absorption chiller / heater 3 is used alone, the fuel gas is supplied by (116.1-109.4) = 6.7%. When a ratio (power generation efficiency) with respect to the surplus fuel gas supplied to the power generation amount 4.7% is obtained, it is 70.1%. In this thermoelectric supply system 1, when it is assumed that the thermal efficiency of the absorption chiller / heater 3 is the same as that of the conventional single use, the power generation efficiency in the power generation unit 2 is 70.1%. I mean. Considering that the power generation efficiency of a general gas turbine type power generation unit is about 10 to 20%, it can be seen that the overall heat (power generation) efficiency of the thermoelectric supply system 1 is remarkably improved.

  As described above, according to the thermoelectric supply system 1, the power generation unit 2 can burn the fuel gas to generate power, and the power can be used as driving power for the power generation unit 2 and the absorption chiller / heater 3. In the absorption chiller / heater 3, the reburning burner 31 burns fuel gas using the residual oxygen in the exhaust gas of the power generation unit 2 as combustion air, and supplies the high temperature exhaust gas from the reburning burner 31 to the regenerator. it can. That is, since the retained heat and residual oxygen of the exhaust gas of the power generation unit 2 can be used effectively, the thermal efficiency is greatly improved, and the fuel supply amount supplied to the power generation unit 2 and the reburning burner 31 is changed to the absorption chiller / heater 3. The air conditioning load is appropriately distributed based on at least one of the air conditioning load and the power requirement for the power generation unit 2, and stable cold / hot water can be supplied to the building in any air conditioning load region of the absorption chiller / heater 3.

  In order to use the converter 71 that converts AC power generated by the power generation unit 2 into DC power, the rectifier 72 that converts AC power supplied from the external commercial power 60 into DC power, and the converted DC power as drive power. Since the power conversion device 70 having the inverter 73 for converting the AC power into the predetermined frequency is provided, the AC power generated by the power generation unit 2 is supplied to various devices such as the power generation unit 2 and the absorption chiller / heater 3 in a predetermined manner. AC power having a frequency can be converted and supplied, and even when the power generated by the power generation unit 2 is insufficient, the AC power supplied from the commercial power 60 can be converted to AC power having a predetermined frequency and supplied. .

  The power generation unit 2 and the reburning burner 31 so as to suppress fluctuations in the cold / hot water outlet temperature of the absorption chilling water heater 3 due to the start / stop of the reburning burner 31 when the air conditioning load of the absorption chilling water heater 3 is low. In order to prevent overcooling by the absorption chiller / heater 3 when the air-conditioning load of the absorption chiller / heater 3 is low, the power control panel 4 for determining the distribution amount of the fuel supply amount to the There is a possibility that the start / stop of the reburning burner 31 may occur frequently. However, the power generation unit 2 is configured to suppress fluctuations in the cold / hot water outlet temperature of the absorption chiller / heater 3 caused by the start / stop of the reburning burner 31. The fuel supply amount to the reburning burner 31 can be appropriately distributed.

  In this case, the power generation amount of the power generation unit 2 is suppressed according to a decrease in the air conditioning load of the absorption chiller / heater 3, and further, the absorption liquid according to the decrease of the air conditioning load of the absorption chiller / heater 3. Is bypassed from the bypass passage 91 to the evaporator 33. Therefore, when the air conditioning load of the absorption chiller / heater 3 is low, the cooling performance of the absorption chiller / heater 3 is suppressed, and the reburn burner It is possible to prevent occurrence of frequent start / stop 31 as much as possible, and to suppress fluctuations in the cold / hot water outlet temperature.

  In addition, the power control panel 4 determines the distribution amount of the fuel supply amount to the power generation unit 2 and the reburning burner 31 so as to optimize the combustion conditions by suppressing the emission of CO and NO x of the exhaust gas of the reburning burner 31. Thus, the combustion efficiency of the reburn burner 31 can be increased. In this case, the turbine rotational speed of the gas turbine 11 is suppressed in accordance with the oxygen concentration of the exhaust gas from the reburning burner 31 so that the oxygen concentration is within a predetermined oxygen concentration range. Since the amount of combustion air supplied to 19 is reduced, the emission of CO and NO x from the exhaust gas of the reburning burner 31 can be suppressed to optimize the combustion conditions and increase the combustion efficiency.

  Moreover, since the power control panel 4 determines the distribution amount of the fuel supply amount to the power generation unit 2 and the reburning burner 31 so as to maximize the generated power of the power generation unit 2, the air conditioning load of the absorption chiller / heater 3 is determined. Is low, even if the fuel supply to the reburning burner 31 is stopped, it is assumed that the required heating amount will be exceeded due to the sensible heat of the exhaust gas of the power generation unit 2, but this is prevented and the generated power of the power generation unit 2 is prevented. Thus, the fuel supply amount to the power generation unit 2 and the reburn burner 31 can be appropriately distributed. In this case, a part of the absorption liquid is bypassed from the bypass passage 91 to the evaporator 33 in accordance with a reduction in the air conditioning load of the absorption chiller / heater 3, and further, the cooling water of the absorption chiller / heater 3 is configured. Since the inlet temperature is increased, the cooling performance of the absorption chiller / heater 3 can be suppressed, and the amount of power generated by the power generation unit can be maximized even when the air conditioning load of the absorption chiller / heater 3 is low.

  As shown in FIG. 19, this hybrid thermoelectric system 1 </ b> A includes a converter 71 </ b> A (DC power conversion unit) that converts high-frequency AC power generated by the power generation unit 2 into DC power instead of the power conversion device 70 of the first embodiment. ) And a rectifier 72A (DC power converter) that rectifies AC power supplied from the commercial power supply 60 of the external power supply system and converts it into DC power, and this converter 71A or rectifier The direct current power converted by 72A is supplied to an alternating current drive device (for example, the cold / hot water pump 51) provided with an inverter 73A that converts the direct current power into alternating current power of a predetermined frequency (for example, 50 Hz or 60 Hz) or the direct current drive device. It is composed.

  That is, the AC power generated by the power generation unit 2 can be converted into DC power by the power conversion device 70A and supplied to various AC drive devices or DC drive devices of the power generation unit 2 and the absorption chiller / heater 3. Even when the generated power of the power generation unit 2 is insufficient, the AC power supplied from the commercial power source 60 can be converted into DC power by the power converter 70A and supplied. Other configurations, operations, and effects are basically the same as those in the first embodiment.

In addition, in the said Example, you may change as follows.
1] A gas engine or a fuel cell may be applied instead of the gas turbine 11.
2] The low temperature regenerator 36 can be omitted. In this case, the heat exchanger 39 and the second absorbing liquid pump 42 are also omitted, and the absorbing liquid passage extending from the heat exchanger 38 is connected to the high temperature regenerator 36. Further, the configuration is changed as appropriate, such as by providing a bypass passage 91 so as to connect the absorbing liquid passage to the high temperature regenerator 36 and the evaporator 33.
3] An intake damper capable of adjusting the intake air flow rate to the compressor 18 of the gas turbine 11 is provided, and the exhaust gas flow rate supplied to the reburning burner 31 is changed by changing the intake air flow rate sucked into the compressor 18. Good.
4] Although the cooling operation has been mainly described in the above embodiment, the present invention (claims 1-8, 10-13, 16-20) is effective and applicable also in the heating operation.
5] In addition, various modifications can be added and implemented without departing from the spirit of the present invention.

It is a block diagram of the hybrid thermoelectric supply system which concerns on the Example of this invention. It is a partial block diagram of a hybrid thermoelectric supply system. It is a block diagram of a cold / hot water machine main body. It is a block diagram of the control system of a hybrid thermoelectric supply system. It is explanatory drawing regarding control of a hybrid thermoelectric supply system. It is a characteristic figure of an air-conditioning load factor-fuel consumption. It is a characteristic figure of an air-conditioning load factor-electric energy. It is a characteristic figure of an air-conditioning load factor-fuel consumption. It is a characteristic figure of an air-conditioning load factor-electric energy. It is a characteristic figure of an air-conditioning load factor-fuel consumption. It is a characteristic figure of an air-conditioning load factor-electric energy. It is a characteristic figure of burner exit temperature-CO concentration. It is a characteristic figure of burner exit temperature-NOX concentration. It is a characteristic figure of an air-conditioning load factor-fuel consumption. It is a characteristic figure of an air-conditioning load factor-electric energy. It is a some graph regarding an air-conditioning load. It is a several graph regarding the air-conditioning load etc. at the time of applying this invention. It is explanatory drawing of the calorie | heat amount electric power balance in a thermoelectric supply system. It is a one part block diagram of the hybrid thermoelectric supply system which concerns on Example 2. FIG.

DESCRIPTION OF SYMBOLS 1,1A Hybrid thermoelectric supply system 2 Power generation unit 3 Absorption type chiller / heater 4 Power control panel 11 Gas turbine 13, 32 Controller 31 Reburner burner 33 Evaporator 37 High temperature regenerator 70, 70A Power converter 71, 71A Converter 72, 72A Rectifier 73, 73A Inverter 91 Bypass passage

Claims (6)

A power generation unit that generates power by burning gaseous or liquid fuel, a reburning burner that burns gaseous or liquid fuel using residual oxygen in the exhaust gas of the power generation unit as combustion air, and a refrigerant from the absorbing liquid that has this reburning burner A hybrid thermoelectric supply system having a regenerator for separation and an evaporator for evaporating refrigerant, and an absorption chiller / heater that generates chilled water or hot water and circulates it to a building,
The exhaust gas of the refrigerating burner of the absorption chiller / heater is supplied to the regenerator, and the power generated by the power generation unit is configured to be used as drive power for the power generation unit and the absorption chiller / heater,
The fuel supply amount supplied to relapse burner and the power generating unit, as well as allocated based on at least one power demand for air-conditioning load and the power generation unit of the absorption chiller-heater, maximizing the generated power of the power generation unit So as to provide an integrated control device for determining a distribution amount of the fuel supply amount to the power generation unit and the reburning burner ,
Cooling water for cooling the absorption liquid and the refrigerant is supplied to the absorption chiller / heater,
The hybrid thermoelectric supply system , wherein the integrated control device is configured to increase a cooling water inlet temperature of the absorption chiller / heater to maximize the generated power of the power generation unit .   The AC power generated by the power generation unit is converted into DC power, the AC power supplied from an external power supply system is converted into DC power, and the converted DC power is used as the driving power. The hybrid thermoelectric supply system according to claim 1, further comprising: a power conversion device including an AC power conversion unit that converts AC power into a predetermined frequency for use.   The power conversion device includes a power converter having a DC power conversion unit that converts AC power generated by the power generation unit into DC power and converts AC power supplied from an external power supply system into DC power. 2. The hybrid thermoelectric supply system according to claim 1, wherein the direct-current power converted by the unit is supplied to an alternating-current drive device having an alternating-current power conversion unit that converts alternating-current power to a predetermined frequency, or a direct-current drive device. . External As operable self-supporting in terms of electric power from the power supply system without receiving power supply, according to claim 2, characterized in that a integrated control apparatus for determining the power output of the power converter or hybrid cogeneration system according to 3. The power generation unit supplies all or part of the driving power to the power generation unit and the absorption chiller / heater device ,
The integrated control device selects a device that supplies driving power according to the power generation allowable amount of the power generation unit with respect to the air conditioning load of the absorption chiller / heater so that the total driving power is within the power generation allowable amount. The hybrid thermoelectric supply system according to claim 4 , wherein the hybrid thermoelectric supply system is configured as follows . The power generation unit supplies all or part of the driving power to the power generation unit and the absorption chiller / heater device ,
The integrated control device supplies drive power to the inverter-driven device so that the sum of the drive power is within the power generation allowable amount according to the power generation allowable amount of the power generation unit with respect to the air conditioning load of the absorption chiller / heater. The hybrid thermoelectric supply system according to claim 4 , wherein the hybrid thermoelectric supply system is configured to suppress the above-described problem .