JP2007064518A - Cogeneration system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cogeneration system for stably and highly effectively supplying heat quantity corresponding to demand of a heat load irrespective of a degree of output of a generator. <P>SOLUTION: The cogeneration system 1 comprises a gas engine 101 for power generation for supplying power to a power load, an exhaust heat system 10 for recovering exhaust heat of the gas engine 101 for power generation and supplying to the heat load, a hot water storage system 20, a water heating system 40, and an auxiliary heat source machine 5 for supplying short heat quantity to the heat load when the heat quantity recovered by the heat exhaust system 10 runs short with respect to heat demand of the heat load. The system 1 is provided with a surplus power recovering heater 102 for converting a part of power output by the gas engine 101 for power generation into the short heat quantity and supplying to the heat exhaust system 10 when the short heat quantity does not meet a minimum output of the auxiliary heat source device. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a cogeneration system that supplies electric power generated by a heat engine or the like to an electric load and supplies exhaust heat from the heat engine or the like to the heat load.

  A first heat medium circulates between the heat and power supply means for supplying power to the power load, the heat exchanger, the heat storage tank, and the primary side pipe line of the heat and power supply means and the heat exchanger. And a second circulation path through which the second heat medium circulates between a secondary side pipe of the heat exchanger and the heat storage tank, and heat is applied from the heat storage tank to the heat load. Cogeneration systems that supply power are known.

  In such a cogeneration system, since there is a certain relationship between the electric power obtained from the combined heat and power supply means and the amount of exhaust heat from the combined heat and power supply means, the two cannot be increased or decreased independently. On the other hand, since the electric power demand and the heat demand increase and decrease separately, if the operation is performed according to the electric power demand, the heat supply becomes excessive, and if the operation is performed according to the heat demand, the electric power supply may be excessive.

Therefore, the cogeneration system currently in practical use is equipped with an auxiliary heat source and a surplus power recovery heater. The auxiliary heat source is attached to a pipe that sends the second heat medium from the heat storage tank to the heat load. When the demand for the heat load cannot be covered by the amount of exhaust heat from the heat and power supply means, the second heat medium is supplied. It is a heater that compensates for the heat quantity that is deficient by heating. The surplus power recovery heater is a heater that is attached to the front side of the heat exchanger in the first circulation path and heats the first heat medium with surplus power, and converts the surplus power into heat to generate heat. Heat is supplied to the load (Patent Documents 1 to 3).
JP 2003-21392 A JP 2004-257364 A JP 2005-009456 A

  Normally, a combustor that uses gas or kerosene as fuel is used as the auxiliary heat source. Since it is displayed as a number with the ability to perform No. 1, it is also called the lowest number.) There is a problem that combustion below cannot be performed. This is because if the output is reduced, the combustion becomes unstable and disappears. Therefore, there is a problem that the auxiliary heat source device cannot be operated when the insufficient heat quantity is less than the minimum output of the auxiliary heat source device.

If the auxiliary heat source device is operated intermittently, this problem can be solved easily, but there is a problem that it is difficult to use because the temperature of the second heat medium sent from the cogeneration system to the heat load fluctuates. In addition, if the intermittent operation is carried out, the can body of the auxiliary heat source device repeatedly rises and falls, and part of the combustion heat of the fuel is consumed for raising the temperature of the can body of the auxiliary heat source device. There is a problem that the thermal efficiency of the is reduced.

  Further, when the amount of exhaust heat from the heat engine is reduced, there is a problem that the temperature of the first heat medium flowing into the primary side pipe of the heat exchanger is lowered. When the temperature of the first heat medium decreases, the temperature of the second heat medium flowing out from the secondary side pipe of the heat exchanger (exhaust heat recovery temperature) decreases. 2 heat medium may not be supplied.

  The present invention has been made to solve such a problem, and provides a cogeneration system capable of stably and efficiently supplying the amount of heat according to the demand of the heat load regardless of the output level of the generator. The purpose is to do.

  A first configuration of a cogeneration system according to the present invention includes a cogeneration unit that generates electric power and heat, a heat recovery supply system that recovers exhaust heat of the cogeneration unit and supplies it to an external heat load, and In a cogeneration system having an auxiliary heat source device that supplies a deficient amount of heat to the heat load when the amount of heat supplied by the heat recovery and supply system is insufficient with respect to the heat demand of the heat load, the cogeneration unit outputs An electrothermal converter that converts a part of electric power into heat and supplies it to the heat recovery and supply system; and when the insufficient heat is less than the minimum output of the auxiliary heat source device, the output of the cogeneration means increases the output While increasing the exhaust heat of the combined heat and power means, the increase in output of the combined heat and power means is input to the electrothermal conversion device and converted into the amount of heat, so that the insufficient heat amount Characterized in that it comprises a; controller to compensate.

  According to this configuration, since the shortage of heat that is less than the minimum output of the auxiliary heat source device is supplemented by the power output from the combined heat and power supply means, the amount of heat according to the heat demand can be stably supplied without excess or deficiency. Moreover, since the intermittent operation of the auxiliary heat source device can be avoided, the overall efficiency of the cogeneration system is improved. Here, the combined heat and power means means a device that generates electric power and generates waste heat as a by-product, and includes not only a heat engine driven generator but also an electrochemical combined heat and power means such as a fuel cell. It is a waste.

  A second configuration of the cogeneration system according to the present invention includes a cogeneration unit that generates electric power and heat, a heat recovery supply system that recovers exhaust heat of the cogeneration unit and supplies the exhaust heat to an external heat load, In a cogeneration system having an auxiliary heat source device that supplies a deficient amount of heat to the heat load when the amount of heat supplied by the heat recovery and supply system is insufficient with respect to the heat demand of the heat load, the cogeneration unit outputs An electrothermal converter for converting a part of electric power into heat and supplying the heat recovery and supply system; and a fuel consumption when the insufficient heat is supplied by operation of the auxiliary heat source device; and the combined heat and power for the insufficient heat Compared to the increase in exhaust heat due to the increase in the output of the means and the amount of fuel consumed when the electric power for the increase in the output of the combined heat and power supply means is covered by the amount of heat obtained by converting the electric heat conversion device, When the person is smaller than the former, the output of the combined heat and power supply means is increased, and the increase in the output of the combined heat and power supply means is input to the electric heat conversion device and converted into heat, thereby compensating for the insufficient heat quantity An apparatus.

  According to this configuration, the shortage of heat is covered by either the operation of the auxiliary heat source device or the increase in the output of the combined heat and power supply means, which reduces the fuel consumption, so that the overall efficiency of the cogeneration system is further improved.

  A third configuration of the cogeneration system according to the present invention is the first or second configuration, wherein the heat recovery and supply system includes a heat exchanger, a heat storage tank, the thermoelectric supply unit, and the heat exchanger. The first heat medium circulates between the primary side pipes and the second heat medium circulates between the secondary side pipes of the heat exchanger and the heat storage tank. A second circulation path and a heat supply pipe for sending the second heat medium from the heat storage tank to the heat load; and the electrothermal conversion device includes the first heat in the first circulation path. It is an electric heater that heats the medium.

  This configuration also compensates for the shortage of heat that is less than the minimum output of the auxiliary heat source device with the power output by the combined heat and power supply means, so that the amount of heat according to the heat demand can be stably supplied without excess or deficiency.

  According to a fourth configuration of the cogeneration system of the present invention, in the first or second configuration, the heat recovery supply system includes a heat exchanger, a heat storage tank, the combined heat and power supply unit, and the heat exchanger. The first heat medium circulates between the primary side pipes and the second heat medium circulates between the secondary side pipes of the heat exchanger and the heat storage tank. A second circulation path, and a heat supply pipe for sending the second heat medium from the heat storage tank to the thermal load, and the electrothermal conversion device includes the second circulation path in the second circulation path. It is an electric heater that heats the heat medium.

  According to this configuration, since the second heat medium is directly heated by the electric heater in the second circulation path without going through the first heat medium and the heat exchanger, the loss in the heat transfer path is reduced. Therefore, the overall efficiency of the cogeneration system is further improved.

  A fifth configuration of the cogeneration system according to the present invention is the first or second configuration, wherein the heat recovery and supply system includes a heat exchanger, a heat storage tank, the thermoelectric supply unit, and the heat exchanger. The first heat medium circulates between the primary side pipes, and the second heat medium circulates between the secondary side pipes of the heat exchanger and the heat storage tank. And a heat supply pipe that sends the second heat medium from the heat storage tank to the heat load, and the electrothermal converter is configured to supply the second heat in the heat supply pipe. It is an electric heater that heats the medium.

  Also in this configuration, since the second heat medium is directly heated by the electric heater in the heat supply pipe without going through the first heat medium and the heat exchanger, the loss in the heat transfer path is reduced. Therefore, the overall efficiency of the cogeneration system is further improved.

  According to a sixth configuration of the cogeneration system according to the present invention, in the third to fifth configurations, the temperature of the first heat medium at the inlet of the primary side pipe line of the heat exchanger is changed. A flow rate adjusting means for increasing or decreasing the flow rate of the first heat medium in the first circulation path is provided.

  According to this configuration, since the flow rate of the first heat medium is increased or decreased according to the temperature of the first heat medium, the temperature of the first heat medium flowing into the primary side pipe inlet of the heat exchanger. Can be kept in the desired range. Therefore, the temperature (exhaust heat recovery temperature) of the second heat medium at the secondary side pipe outlet of the heat exchanger can be maintained within a desired range regardless of increase or decrease of the exhaust heat of the combined heat and power supply means.

  According to a seventh configuration of the cogeneration system according to the present invention, in the third to fifth configurations, the temperature of the first heat medium at the inlet of the primary side pipe line of the heat exchanger is changed. A flow rate adjusting means for increasing or decreasing the flow rate of the second heat medium in the second circulation path is provided.

  According to this configuration, since the flow rate of the second heat medium is increased or decreased according to the temperature of the first heat medium, the temperature of the first heat medium flowing into the primary side pipe inlet of the heat exchanger. Can be kept in the desired range. Therefore, the temperature (exhaust heat recovery temperature) of the second heat medium at the secondary side pipe outlet of the heat exchanger can be maintained within a desired range regardless of increase or decrease of the exhaust heat of the combined heat and power supply means.

  According to an eighth configuration of the cogeneration system of the present invention, in the seventh configuration, the thermoelectric generator is configured according to the temperature of the first heat medium at the inlet of the primary side conduit of the heat exchanger. The temperature control means includes target temperature increase / decrease means for increasing / decreasing the control target temperature of the first heat medium at the inlet of the combined supply means, and the flow rate adjusting means controls the temperature of the first heat medium at the inlet of the heat / electric supply means. The flow rate of the second heat medium in the second circulation path is increased or decreased according to the level with respect to the target temperature.

  This configuration also increases or decreases the flow rate of the second heat medium according to the temperature of the first heat medium, so that the temperature of the first heat medium flowing into the primary side pipe inlet of the heat exchanger is desired. Can be kept in the range. Therefore, the temperature (exhaust heat recovery temperature) of the second heat medium at the secondary side pipe outlet of the heat exchanger can be maintained within a desired range regardless of increase or decrease of the exhaust heat of the combined heat and power supply means.

  A ninth configuration of the cogeneration system according to the present invention includes a cogeneration means for generating electric power and heat, a heat exchanger, a heat storage tank, the cogeneration means, and a primary side pipe of the heat exchanger. A first circulation path through which the first heat medium circulates, and a second circulation path through which the second heat medium circulates between the secondary pipe line of the heat exchanger and the heat storage tank, In the cogeneration system for supplying heat to the heat load from the heat storage tank, the first circulation according to the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger A flow rate adjusting means for increasing or decreasing the flow rate of the first heat medium in the passage is provided.

  According to this configuration, since the flow rate of the first heat medium is increased or decreased according to the temperature of the first heat medium, the temperature of the first heat medium flowing into the primary side pipe inlet of the heat exchanger. Can be kept in the desired range. Therefore, the temperature of the second heat medium (exhaust heat recovery temperature) at the secondary side pipe outlet of the heat exchanger can be maintained at a desired value regardless of the increase or decrease of the exhaust heat of the combined heat and power supply means.

  A tenth configuration of a cogeneration system according to the present invention includes a cogeneration means for generating electric power and heat, a heat exchanger, a heat storage tank, the cogeneration means, and a primary side pipe of the heat exchanger. A first circulation path through which the first heat medium circulates, and a second circulation path through which the second heat medium circulates between the secondary pipe line of the heat exchanger and the heat storage tank, In the cogeneration system for supplying heat to the heat load from the heat storage tank, the second circulation according to the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger A flow rate adjusting means for increasing or decreasing the flow rate of the second heat medium in the passage is provided.

  According to this configuration, since the flow rate of the second heat medium is increased or decreased according to the temperature of the first heat medium, the temperature of the first heat medium flowing into the primary side pipe inlet of the heat exchanger. Can be kept in the desired range. Therefore, the temperature (exhaust heat recovery temperature) of the second heat medium at the secondary side pipe outlet of the heat exchanger can be maintained within a desired range regardless of increase or decrease of the exhaust heat of the combined heat and power supply means.

  According to an eleventh configuration of the cogeneration system according to the present invention, in the tenth configuration, the thermoelectric power is generated according to the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger. The temperature control means includes target temperature increase / decrease means for increasing / decreasing the control target temperature of the first heat medium at the inlet of the combined supply means, and the flow rate adjusting means controls the temperature of the first heat medium at the inlet of the heat / electric supply means. The flow rate of the second heat medium in the second circulation path is increased or decreased according to the level with respect to the target temperature.

  This configuration also increases or decreases the flow rate of the second heat medium according to the temperature of the first heat medium, so that the temperature of the first heat medium flowing into the primary side pipe inlet of the heat exchanger is desired. Can be kept in the range. Therefore, the temperature (exhaust heat recovery temperature) of the second heat medium at the secondary side pipe outlet of the heat exchanger can be maintained within a desired range regardless of increase or decrease of the exhaust heat of the combined heat and power supply means.

  As described above, according to the present invention, it is possible to provide an efficient cogeneration system that can supply the amount of heat required by the thermal load without excess or deficiency.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

  FIG. 1 is a piping system diagram of a cogeneration system according to an embodiment of the present invention. A cogeneration system 1 shown in FIG. 1 is a system that collects exhaust heat from a combined heat and power supply means and supplies it to a heating system and a hot water supply system. The hot water storage tank 2, a hot water storage heat exchanger 3, a heating low temperature heat exchanger 4, It is comprised from the auxiliary heat source machine 5, the heating high temperature heat exchanger 6, and the other apparatus mentioned later. The cogeneration system 1 is controlled by a control computer (not shown). In addition, the cogeneration system 1 includes other devices, pipe systems, valves, and the like, but descriptions of devices that are not necessary for the description of the present invention are omitted.

  The cogeneration system 1 is roughly divided into five systems, that is, an exhaust heat system 10, a hot water storage system 20, a heating system 30, a hot water supply system 40, and a water supply system 50. Hereinafter, constituent devices and their functions will be described for each system.

[Exhaust heat system]
The exhaust heat system 10 passes high-temperature cooling water returning from the power generation gas engine 101 to the primary side pipe 3 a of the hot water storage heat exchanger 3, and then the primary side pipe of the heating low-temperature heat exchanger 4. By passing water through the passage 4a, the exhaust heat of the power generation gas engine 101 is supplied to the hot water storage system 20 and the heating system 30, and the cooling water which has become low temperature by releasing the exhaust heat is sent to the power generation gas engine 101. It is a piping system.

  The exhaust heat system 10 includes a heat exchange inlet thermistor 102, a surplus power recovery heater 103, an intermediate thermistor 104, a heat exchange outlet thermistor 105, a cooling water tank 106, a cooling water pump 107, and a cooling water proportional valve 108, and a power generation gas engine. 101 → Primary side pipe 3a of hot water storage heat exchanger 3 → Primary side pipe 4a of heating low-temperature heat exchanger 4 → Cooling water tank 106 → Cooling water pump 107 → Cooling water proportional valve 108 → Power generation gas engine 101 The cooling water circulation path (first circulation path) is formed.

  The heat exchange inlet thermistor 102 is a sensor that detects the temperature of the high-temperature cooling water that has absorbed the exhaust heat of the power generation gas engine 101 and returned to the exhaust heat system 10.

  The surplus power recovery heater 103 is used when there is a surplus in the power generation capacity of the power generation gas engine 101 and when the amount of exhaust heat recovered from the power generation gas engine 101 does not satisfy the demand of the heating system 30 and the hot water supply system 40. A heater that converts a part of electric power generated by the power generation gas engine 101 into heat and heats the cooling water, and is provided between the heat exchange inlet thermistor 102 and the primary side pipe 3 a of the hot water storage heat exchanger 3. It is done.

  The intermediate thermistor 104 is a temperature sensor that detects the temperature of the cooling water at the outlet of the primary side pipe 3 a of the hot water storage heat exchanger 3.

  The heat exchange outlet thermistor 105 is a temperature sensor that detects the temperature of the cooling water at the outlet of the primary side pipe 4 a of the heating low-temperature heat exchanger 4.

  The cooling water tank 106 receives water from the water supply system 50, replenishes the cooling water evaporated in the middle of the cooling water circulation path, and keeps the cooling water level within a certain range.

  The cooling water pump 107 is a pump that pressurizes the cooling water and circulates it in the cooling water circulation path.

  The cooling water proportional valve 108 is a valve on the downstream side of the cooling water pump 107 and adjusts the flow rate of the cooling water flowing through the cooling water circulation path.

[Hot water storage system]
The hot water storage system 20 passes the low temperature hot water extracted from the lower part of the hot water storage tank 2 through the secondary side pipe 3b of the hot water storage heat exchanger 3 and heats it with the heat supplied from the exhaust heat system 10, This is a piping system that returns to the upper part of the hot water storage tank 2.

  The hot water storage system 20 includes a circulation proportional valve 201, a circulation pump 202, and a hot water storage thermistor 203. The hot water storage tank 2 → the circulation proportional valve 201 → the secondary pipe 3b of the hot water storage heat exchanger 3 → the circulation pump 202 → the hot water storage tank. Two hot water circulation paths (second circulation paths) are formed.

  The circulation proportional valve 201 is located between the lower part of the hot water storage tank 2 and the inlet of the secondary side pipe 3b of the hot water storage heat exchanger 3, and adjusts the flow rate of hot water flowing through the hot water circulation path.

  The circulation pump 202 is a pressure feeding means that pressurizes hot water discharged from the outlet of the secondary side pipe 3 b of the hot water storage heat exchanger 3 and pumps the hot water to the upper part of the hot water storage tank 2.

  The hot water storage thermistor 203 is a temperature sensor that is attached to the body of the hot water storage tank 2 and detects the temperature of the hot water in the hot water storage tank 2.

  The lower part of the hot water storage tank 2 is connected to the water supply system 50, and the water supply pressure of the water supply system 50 is balanced with the pressure of the hot water inside the hot water storage tank 2. That is, if the water pressure in the hot water storage tank 2 is at a predetermined level, the water supply is stopped, the hot water in the hot water storage tank 2 is consumed, and water supply is performed when the water pressure decreases.

[Heating system]
The heating system 30 passes low-temperature heating water (heating heating medium) returning from a heater (not shown) (for example, a fan coil unit or a floor heating unit) to the secondary side pipe 4 b of the heating low-temperature heat exchanger 4. Water is absorbed from the exhaust heat system 10, and further, water is passed through the secondary side pipe 6 b of the heating high-temperature heat exchanger 6 to absorb heat from the hot water supply system 40. This is a piping system that is sent to a heater.

  The heating system 30 includes a heating water return port 301, a heating water tank 302, a return circuit 303, a heating water pump 304, a heating water thermistor 305, and a heating outlet 306. The secondary side pipe 4b of the exchanger 4 → the secondary side pipe 6b of the heating high-temperature heat exchanger 6 → the heating water tank 302 → the heating water pump 304 → the heating outlet 306 → the heating water circulation path of the heater is formed. .

  The heating water return port 301 is a port into which low-temperature heating water returning from the heater flows.

  The heating water tank 302 is downstream of the secondary side pipe 6b of the heating high-temperature heat exchanger 6, receives water from the water supply system 50, replenishes the heating water evaporated in the middle of the heating water circulation path, This tank keeps the heating water level within a certain range.

  In order to prevent an excessive load from being generated in the heating water pump 304 when the heating water flow path inside the heater is closed, the return circuit 303 supplies the heating water from the heating outlet 306 side to the heating high temperature heat exchanger. 6 is a pipe system that returns to the secondary side pipe line 6b side.

  The heating water pump 304 is a pump that circulates heating water in the heating water circulation path.

  The heating water thermistor 305 is a temperature sensor that detects the temperature of the heating water downstream of the heating water pump 304.

  The heating outlet 306 is a port through which heated water having a high temperature is sent to the heater.

[Hot water system]
The hot water supply system 40 is a piping system that sends hot water supplied from the hot water storage system 20 to a heat load. Here, the heat load includes the heating system 30 and a curan / shower head (not shown) or a heat exchanger for reheating the bathtub. There are two types of heat loads: one that consumes only heat, such as a heat exchanger for bathing, and one that does not consume the heat medium (in this case, hot water), and one that consumes a heat medium, such as a currant showerhead. is there. The hot water supplied from the hot water storage system 20 to the hot water supply system 40 passes through the auxiliary heat source unit 5 and then enters the primary side 6a of the heating high temperature heat exchanger 6 to supply heat to the heating system 30, and the other It is divided into a flow toward a heat load (not shown).

  The hot water supply system 40 includes a BU water amount sensor 401, a BU entry thermistor 402, a BU exit thermistor 403, and a heating valve 404.

  The BU water amount sensor 401 is a sensor that detects the flow rate of hot water flowing into the hot water supply system 40 from the hot water storage system 20.

  The BU entry thermistor 402 is a temperature sensor that detects the temperature of hot water flowing into the auxiliary heat source unit 5.

  The BU outlet thermistor 403 is a temperature sensor that detects the temperature of hot water flowing out from the auxiliary heat source unit 5.

  The heating valve 404 is a valve that adjusts the flow rate of hot water flowing into the primary side pipe 6 a of the heating high-temperature heat exchanger 6.

  The hot water that has flowed into the primary side pipe 6 a of the heating high temperature heat exchanger 6 and heated to the heating system 30 and has become low temperature passes through the heating valve 404 and then passes through the secondary side pipe of the hot water storage heat exchanger 3. It returns to the hot water storage system 20 at a position intermediate between the passage 3 b and the circulation pump 202.

  In addition, the auxiliary heat source unit 5 supplies the hot water when the temperature of the hot water supplied from the hot water storage system 20 to the hot water supply system 40 (temperature detected by the BU input thermistor 402) is lower than the temperature required by the heat load. It is a backup heat source to heat.

[Water supply system]
The water supply system 50 is a piping system that supplies water supplied from unshown tap water to the exhaust heat system 10, the hot water storage system 20, the heating system 30, and the hot water supply system 40.

  The water supply system 50 includes a water supply port 501, a makeup water closing valve 502, and a pressure reducing valve 503.

  The water supply port 501 is a port for receiving tap water from tap water (not shown).

  The makeup water closing valve 502 is a valve that closes the supply of water to the exhaust heat system 10 and the heating system 30, that is, the supplementation of the cooling water in the cooling water tank 106 and the supplementation of the heating water in the heating water tank 302.

  The pressure reducing valve 503 is a valve that adjusts the supply water pressure.

Next, the operation of the cogeneration system 1 will be described. As described above, the auxiliary heat source unit 5 heats the hot water when the temperature of the hot water supplied from the hot water storage system 20 is lower than the temperature required by the heat load. There is. This is because if the amount of fuel supplied to the combustor is reduced, stable combustion cannot be performed and there is a risk that the fuel will disappear. Here, the lower limit of the heat generation amount of the auxiliary heat source unit 5, that is, the minimum heat generation amount is set to Q _low . The minimum heat generation amount Q _low is a specific amount of the auxiliary heat source unit 5. Further, assuming that the flow rate of hot water detected by the BU water amount sensor 401 is F, the temperature of hot water required by the thermal load is T _d , and the temperature of hot water detected by the BU inlet thermistor 402 is T _s , the auxiliary heat source unit 5 The amount of heat Q to be compensated by combustion is given by the following equation. Where C is the specific heat of water.

Q = CF (T _d −T _s ) (Formula 1)

If Q ≧ Q _low , the auxiliary heat source unit 5 can be continuously burned. Therefore, the auxiliary heat source unit 5 is ignited to warm hot water. In this case, the hot water temperature detected by the BU outlet thermistor 403 is fed back to the auxiliary heat source unit 5. That is, the amount of heat generated by the auxiliary heat source unit 5 is adjusted so that the temperature of the hot water detected by the BU outlet thermistor 403 becomes _Td .

When Q <Q _low , the auxiliary heat source unit 5 cannot be combusted, and therefore, heating by the surplus power recovery heater 103 is performed instead of heating by the auxiliary heat source unit 5. That is, according to the magnitude of Q, the output of the power generation gas engine 101 is increased to increase the amount of exhaust heat, and the increase in the output of the power generation gas engine 101 is supplied to the surplus power recovery heater 103 to convert it into heat. The cooling water flowing into the primary side pipe line 3a of the hot water storage heat exchanger 3 is heated. In this case, the temperature of hot water detected by the BU outlet thermistor 403 is fed back to the power generation gas engine 101 and the surplus power recovery heater 103. That is, the outputs of the power generation gas engine 101 and the surplus power recovery heater 103 are adjusted so that the temperature of the hot water detected by the BU output thermistor 403 becomes _Td .

In addition, even when Q ≧ Q _low , it is preferable to obtain the heat quantity Q by increasing the output of the power generation gas engine 101 and energizing the surplus power recovery heater 103 rather than burning the auxiliary heat source unit 5. Consumption may be reduced. In such a case, the auxiliary heat source unit 5 is stopped, the output of the power generation gas engine 101 is increased, and the surplus power recovery heater 103 is energized to increase the amount of exhaust heat Q due to the output increase of the power generation gas engine 101. The total amount Q ′ + Q ″ of the amount of heat Q ″ obtained by energizing the surplus power recovery heater 103 with the power for the output increase may be equal to Q.

The comparison of the amount of fuel consumption may be performed according to the following procedure.
(1) Power generation efficiency of the power generation gas engine 101 (output power / fuel heat generation amount) η _G , conversion efficiency of the surplus power recovery heater 103 (output heat amount / input power) η _H , exhaust heat efficiency of the power generation gas engine 101 ( Waste heat amount / heat generation amount of fuel) η _E , recovery efficiency of hot water storage heat exchanger 3 (heat amount recovered by hot water storage heat exchanger 3 and flowing into hot water storage system 20 / heat amount flowing into exhaust heat system 10) η _R and auxiliary The thermal efficiency (output heat amount / fuel heat generation amount) η _B of the heat source unit 5 is calculated by experiment or calculation, and is stored in the computer for control of the cogeneration system 1. These efficiencies are not necessarily constants. . For example, it may vary depending on the amount of heat Q. In such a case, it is stored in the computer in the form of a numerical table or an approximate expression showing the relationship between the heat quantity Q and the efficiency.

(2) While increasing the output of the power generation gas engine 101, the surplus power recovery heater 103 is energized to obtain the efficiency η _B ′ when obtaining the heat quantity Q according to the following equation.

η _B '= (η _G η _H + η _E ) η _R (Formula 2)

(3) In the computer, eta if _B and eta _{B 'compares} eta _B'> eta _B, is better to give the quantity Q by power generation gas engine 101 surplus power recovery heater 103, less fuel consumption Therefore, it is selected that the output of the power generation gas engine 101 is increased and the surplus power recovery heater 103 is energized to obtain the heat quantity Q. On the contrary, if η _B ′ ≦ η _B , it is selected to obtain the heat quantity Q by the combustion of the auxiliary heat source unit 5.

  In the present embodiment, the surplus power recovery heater 103 is attached to the exhaust heat system 10, but it may be attached to the hot water storage system 20 or the hot water supply system 40. That is, a pipe line between the hot water storage heat exchanger 3 of the hot water storage system 20 and the circulation pump 202, a pipe line between the BU inlet thermistor 402 and the auxiliary heat source machine 5 of the hot water supply system 40, or the auxiliary heat source machine 5 and the BU outlet thermistor. A surplus power recovery heater 103 may be attached to the pipe line 403 to directly heat the hot water in the hot water storage system 20 and the hot water supply system 40.

  When the power generation gas engine 101 is operated at a low output, the temperature of the cooling water returning from the power generation gas engine 101 to the exhaust heat system 10 decreases. When the temperature of the cooling water is lowered, the hot water in the hot water storage system 20 cannot be sufficiently heated in the hot water storage heat exchanger 3. When the temperature of the cooling water becomes lower than the temperature of the hot water in the hot water storage system 20, heat flows from the hot water storage system 20 to the exhaust heat system 10 in the hot water storage heat exchanger 3.

  Therefore, when the temperature of the high-temperature cooling water that has returned to the exhaust heat system 10 after absorbing the exhaust heat of the power generation gas engine 101 (temperature detected by the heat exchange inlet thermistor 102) decreases, the cooling water proportional valve 108 is throttled. Thus, the flow rate of the cooling water circulating between the power generation gas engine 101 and the exhaust heat system 10 is reduced, and the temperature of the cooling water returning from the power generation gas engine 101 to the exhaust heat system 10 is increased. Conversely, when the detected temperature of the heat exchange inlet thermistor 102 rises, the cooling water proportional valve 108 is opened to increase the flow rate of the cooling water circulating between the power generation gas engine 101 and the exhaust heat system 10 to generate the power generation gas. The temperature of the cooling water returning to the exhaust heat system 10 from the engine 101 is lowered.

  In place of the heat exchange inlet thermistor 102, a temperature sensor is provided at the cooling water outlet of the power generation gas engine 101, and the cooling water proportional valve 108 is opened and closed based on the cooling water temperature at the cooling water outlet. Good.

  Instead of providing the cooling water proportional valve 108, the cooling water pump 107 may be a variable flow rate type pump, and the flow rate of the cooling water pump 107 may be decreased when the temperature of the cooling water is lowered.

  Alternatively, as shown in FIG. 2, the exhaust heat system 10 includes a bypass pipe 109 with a valve that bypasses the cooling water tank 106, and when the temperature of the cooling water is high, the valve is closed to control the flow rate of the cooling water. When the temperature of the cooling water is low, the valve may be opened to reduce the flow rate.

  Further, the hot water flowing through the hot water storage system 20 (second circulation path) flows in accordance with the temperature of the high-temperature cooling water that has returned to the exhaust heat system 10 by absorbing the exhaust heat from the power generation gas engine 101. The flow rate of hot water may be increased or decreased. For example, the control target temperature of the heat exchange outlet thermistor 105 is raised or lowered according to the detected temperature level of the heat exchange inlet thermistor 102, and the detected temperature of the heat exchange outlet thermistor 105 with respect to the control target temperature is raised or lowered. Then, the flow rate of hot water flowing through the hot water circulation path (second circulation path) of the hot water storage system 20 is increased or decreased by opening and closing the circulation proportional valve 201. That is, if the detected temperature of the heat exchange outlet thermistor 105 becomes higher than the control target temperature, the circulation proportional valve 201 is opened in proportion to the difference, and the detected temperature of the heat exchange outlet thermistor 105 becomes higher than the control target temperature. If it becomes lower, the circulation proportional valve 201 is closed in proportion to the difference.

  FIG. 3 is a flowchart showing a control program for increasing / decreasing the control target temperature of the heat exchange outlet thermistor 105 in accordance with the detected temperature of the heat exchange inlet thermistor 102. Hereinafter, this program will be described with reference to step numbers.

(Step 1) It is determined whether the exhaust heat recovery operation is in progress and whether the cooling water pump 107 is operating. If the cooling water pump 107 is in operation, the process proceeds to step 2.

(Step 2) comparing the detected temperature T of the heat交入port thermistor 102, the upper limit value _{T max} and the lower limit value _{T min} of the detected temperature T. If T _min > T or T _max <T, the process proceeds to step 3, and if T _min ≦ T ≦ T _max , the process returns to the top of step 1. That is, the detected temperature T is, if within the range between the upper limit value T _max and the lower limit value T _min, changes the control target temperature of the heat交出port thermistor 105 is not performed, make changes if out of range. Moreover, it is good also as conditions for the change of control target temperature that the state of _Tmin > T or _Tmax <T is detected continuously more than predetermined time. This is because if the control target temperature is changed with respect to temporary fluctuations in the detected temperature T due to disturbance or the like, the control may be unstable.

The upper limit value T _max and the lower limit value T _min are constants determined by the design conditions of the hot water storage heat exchanger 3 and the power generation gas engine 101. For example, the upper limit value T _max is a constant determined by the limit of overheating of the power generation gas engine 101, and the lower limit value T _min is a constant determined by the lower limit of the exhaust heat recovery temperature of the hot water storage heat exchanger 3.

(Step 3) The control target temperature _{T C} of heat交出port thermistor 105 changes according to the following equation (3) and (4). However, T C _'is a control target temperature after the change, TC is a control target temperature before the change. K (k> 0) is a proportional constant.

When T _min > T T _C ′ = T _C + k (T _min −T) Equation (3)
In the case of T _max <T, T _C ′ = T _C −k (T _max −T) Equation (4)

Thus, when the detected temperature T of the heat交入port thermistor 102 is less than the lower limit _{T min,} control target temperature _{T C} of heat交出port thermistor 105 increases. When the control target temperature T _C of heat交出port thermistor 105 increases, the opening degree of the circulating proportional valve 201 becomes small, since the hot water flow rate through the hot water storage system 20 is decreased, the exhaust heat system 10 in the hot water storage heat exchanger 3 The amount of heat flowing to the hot water storage system 20 decreases, and as a result, the detected temperature T of the heat exchange inlet thermistor 102 increases.

On the other hand, the detected temperature T of the heat交入port thermistor 102 exceeds the upper limit value _{T max,} the control target temperature _{T C} of heat交出port thermistor 105 is low. When the control target temperature T _C of heat交出port thermistor 105 is low, the opening degree of the circulating proportional valve 201 is increased, since the hot water flow rate through the hot water storage system 20 is increased, the exhaust heat system 10 in the hot water storage heat exchanger 3 The amount of heat flowing to the hot water storage system 20 increases, and as a result, the detected temperature T of the heat exchange inlet thermistor 102 decreases.

It is a piping system diagram of a cogeneration system concerning an example of the present invention. It is a piping system diagram which shows the modification of the said cogeneration system. It is a flowchart which shows the control program of the said cogeneration system.

Explanation of symbols

1 Cogeneration system 2 Hot water storage tank (heat storage tank)
DESCRIPTION OF SYMBOLS 3 Hot water storage heat exchanger 4 Heating low temperature heat exchanger 5 Auxiliary heat source machine 6 Heating high temperature heat exchanger 10 Waste heat system 20 Hot water storage system 30 Heating system 40 Hot water supply system 50 Water supply system 101 Power generation gas engine 102 Heat entrance inlet thermistor 103 Surplus power Recovery heater (electrothermal converter)
104 Intermediate thermistor 105 Heat exchange outlet thermistor 106 Cooling water tank 107 Cooling water pump 108 Cooling water proportional valve 109 Bypass pipe 201 with valve Circulating proportional valve
202 Circulation Pump 203 Hot Water Storage Thermistor 301 Heating Water Return Port 302 Heating Water Tank 303 Return Circuit 304 Heating Water Pump 305 Heating Water Thermistor 306 Heating Outlet Port 401 BU Water Quantity Sensor 402 BU Input Thermistor 403 BU Outlet Thermistor 404 Heating Valve 501 Water Supply Port 502 Replenishment Water stop valve 503 Pressure reducing valve

Claims (11)

A cogeneration means for generating electric power and heat;
A heat recovery and supply system for recovering exhaust heat of the cogeneration means and supplying it to an external heat load;
In a cogeneration system having an auxiliary heat source device that supplies a shortage of heat to the heat load when the amount of heat supplied by the heat recovery supply system is insufficient with respect to the heat demand of the heat load,
An electrothermal conversion device for converting a part of electric power output from the cogeneration means into heat and supplying the heat recovery supply system;
And when the insufficient heat quantity is less than the minimum output of the auxiliary heat source device, the exhaust heat of the combined heat and power supply means is increased by increasing the output of the combined heat and power supply means, and the increased output of the combined heat and power supply means is A control device that compensates for the shortage of heat by inputting it into a converter and converting it into heat;
Cogeneration system characterized by having A cogeneration means for generating electric power and heat;
A heat recovery and supply system for recovering exhaust heat of the cogeneration means and supplying it to an external heat load;
In a cogeneration system having an auxiliary heat source device that supplies a shortage of heat to the heat load when the amount of heat supplied by the heat recovery supply system is insufficient with respect to the heat demand of the heat load,
An electrothermal conversion device for converting a part of electric power output from the cogeneration means into heat and supplying the heat recovery supply system;
And the amount of fuel consumed when the amount of insufficient heat is covered by the operation of the auxiliary heat source device, the amount of exhaust heat due to the increase in output of the heat and power supply means, and the amount of power corresponding to the increase in output of the heat and power supply means. Compared to the amount of fuel consumed when the amount of heat obtained by conversion by the electrothermal conversion device is covered, if the latter is smaller than the former, the output of the cogeneration means is increased and the output of the cogeneration means is increased. A controller that compensates for the shortage of heat by inputting the amount into the electrothermal converter and converting it into heat;
Cogeneration system characterized by comprising. The heat recovery supply system includes:
Heat exchanger;
Heat storage tank;
A first circulation path through which a first heat medium circulates between the cogeneration means and the primary pipe of the heat exchanger;
A second circulation path through which a second heat medium circulates between a secondary side pipe of the heat exchanger and the heat storage tank;
And a heat supply line for delivering the second heat medium from the heat storage tank to the heat load;
With
The electrothermal converter is
The cogeneration system according to claim 1, wherein the cogeneration system is an electric heater that heats the first heat medium in the first circulation path. The heat recovery supply system includes:
Heat exchanger;
Heat storage tank;
A first circulation path through which a first heat medium circulates between the cogeneration means and the primary pipe of the heat exchanger;
A second circulation path through which a second heat medium circulates between a secondary side pipe of the heat exchanger and the heat storage tank;
And a heat supply line for delivering the second heat medium from the heat storage tank to the heat load;
With
The electrothermal converter is
The cogeneration system according to claim 1, wherein the cogeneration system is an electric heater that heats the second heat medium in the second circulation path. The heat recovery supply system includes:
Heat exchanger;
Heat storage tank;
A first circulation path through which a first heat medium circulates between the cogeneration means and the primary pipe of the heat exchanger;
A second circulation path through which a second heat medium circulates between a secondary side pipe of the heat exchanger and the heat storage tank;
And a heat supply line for delivering the second heat medium from the heat storage tank to the heat load;
With
The cogeneration system according to claim 1 or 2, wherein the electrothermal converter is an electric heater that heats the second heat medium in the heat supply pipe. Flow rate adjusting means for increasing or decreasing the flow rate of the first heat medium in the first circulation path according to the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger. The cogeneration system according to any one of claims 3 to 5, further comprising: Flow rate adjusting means for increasing or decreasing the flow rate of the second heat medium in the second circulation path according to the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger. The cogeneration system according to any one of claims 3 to 5, further comprising: A target temperature increase / decrease for increasing / decreasing the control target temperature of the first heat medium at the inlet of the cogeneration means according to the level of the temperature of the first heat medium at the inlet of the primary side conduit of the heat exchanger. With means,
The flow rate adjusting means is
The flow rate of the second heat medium in the second circulation path is increased or decreased according to the level of the temperature of the first heat medium at the inlet of the cogeneration means with respect to the control target temperature. The cogeneration system according to claim 7. A cogeneration means for generating electric power and heat;
A heat exchanger,
A heat storage tank,
A first circulation path through which a first heat medium circulates between the cogeneration means and the primary side pipe of the heat exchanger;
A cogeneration system that has a second circulation path through which a second heat medium circulates between a secondary side pipe of the heat exchanger and the heat storage tank, and supplies heat to the heat load from the heat storage tank In the system,
The first circulation path is:
Flow rate adjusting means for increasing or decreasing the flow rate of the first heat medium in the first circulation path according to the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger. A cogeneration system characterized by comprising. A cogeneration means for generating electric power and heat;
A heat exchanger,
A heat storage tank,
A first circulation path through which a first heat medium circulates between the cogeneration means and the primary side pipe of the heat exchanger;
A cogeneration system that has a second circulation path through which a second heat medium circulates between a secondary side pipe of the heat exchanger and the heat storage tank, and supplies heat to the heat load from the heat storage tank In the system,
The second circulation path is configured so that the temperature of the first heat medium at the inlet of the primary side pipe of the heat exchanger varies depending on the temperature of the first heat medium. A cogeneration system comprising flow rate adjusting means for increasing or decreasing the flow rate. A target temperature increase / decrease for increasing / decreasing the control target temperature of the first heat medium at the inlet of the cogeneration means according to the level of the temperature of the first heat medium at the inlet of the primary side conduit of the heat exchanger. With means,
The flow rate adjusting means is
The flow rate of the second heat medium in the second circulation path is increased or decreased according to the level of the temperature of the first heat medium at the inlet of the cogeneration means with respect to the control target temperature. The cogeneration system according to claim 10.

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