KR102333763B1 - Cogeneration unit and system having the same - Google Patents

Abstract

The present invention relates to a cogeneration unit and a cogeneration system. A cogeneration unit according to an embodiment of the present invention includes an engine that drives a generator and generates heat, a radiator that radiates heat generated in the engine, a hot water heat exchanger that transfers heat generated in the engine to a hot water supply unit, and a heating medium A heat medium circulation passage connecting the engine, the radiator and the hot water heat exchanger to circulate the engine, the hot water heat exchanger and the radiator, and a flow regulator for controlling the flow of the heat medium flowing through the heat medium circulation passage. Based on the operation mode according to the amount of hot water supply, and a control unit that controls the flow regulator to vary the flow rate of the thermal medium bypassed to the engine. Accordingly, it is possible to flexibly vary the amount of hot water supplied.

Description

Cogeneration unit and system including same

The present invention relates to a cogeneration unit and a system including the same, and more particularly, to a cogeneration unit and a system including the same, capable of efficiently varying the amount of hot water supplied.

In general, a cogeneration system refers to a system that simultaneously produces power and heat from a single energy source.

For example, the combined heat and power generation system generates electric power by driving a generator and uses heat generated when the generator is driven. The heat generated from the heat source is provided to the heat demanders such as the hot water supply unit.

On the other hand, in the cogeneration system, when the coolant for cooling the engine is used as a hot water supply heat source such as a hot water supply unit, when the temperature of the coolant drops below a predetermined temperature, the usable efficiency of the engine decreases, , the heating of the hot water supply unit is stopped even when there is a request for hot water supply.

In particular, since the conventional cogeneration system transfers heat to the hot water supply unit regardless of the hot water supply requirement, there is a risk of causing user inconvenience due to a decrease in engine performance and a decrease in the hot water supply temperature.

That is, in the conventional cogeneration system, there is a problem in that the amount of hot water supplied cannot be flexibly changed according to the user's hot water supply requirement, and thus the cogeneration system cannot be efficiently operated in response to the user's request.

It is an object of the present invention to provide a cogeneration unit and a system including the same, which can efficiently vary the amount of hot water supplied.

Another object of the present invention is to provide a cogeneration unit capable of rapidly changing the temperature of cooling water in order to vary the amount of heat supplied by hot water, and a system including the same.

Another object of the present invention is to provide a cogeneration unit capable of varying the amount of hot water supplied by a user's setting and a system including the same.

In order to achieve the above object, a cogeneration unit according to an embodiment of the present invention includes an engine that drives a generator and generates heat, a radiator that radiates heat generated in the engine, and a hot water supply unit for heat generated by the engine. A hot water heat exchanger that transmits, a heat medium circulation passage connecting the engine, the radiator and the hot water heat exchanger so that the heat medium circulates between the engine, the hot water heat exchanger and the radiator, and a flow regulator that regulates the flow of the heat medium flowing through the heat medium circulation passage; Based on the operation mode according to, by controlling the flow regulator, includes a control unit for varying the flow rate of the heat medium bypassed to the engine.

In order to achieve the above object, the cogeneration system according to an embodiment of the present invention includes a hot water supply unit that generates power and heat, and receives the heat generated from the cogeneration unit and the cogeneration unit for supplying power and heat and , The combined heat and power unit includes an engine that drives a generator and generates heat, a radiator that radiates heat generated from the engine, a hot water heat exchanger that transfers heat generated from the engine to a hot water supply unit, a heat medium engine, and a hot water heat exchanger and a heat medium circulation passage connecting the engine, the radiator, and the hot water heat exchanger to circulate the radiator, a flow regulator for controlling the flow of the heat medium flowing through the heat medium circulation passage, and a flow controller based on the operation mode according to the amount of hot water supply, It includes a control unit for varying the flow rate of the heating medium bypassed to the engine.

The combined heat and power unit according to the embodiment of the present invention can flexibly vary the amount of hot water supplied by adjusting the flow rate of the heat medium bypassed to the engine without additional configuration or complicated piping heat connection.

In addition, the cogeneration unit applies a heating medium to a radiator when there is no user's demand for hot water, and while preventing overheating of the engine, increases power generation efficiency, and when there is a user's demand for hot water, the heating medium is applied as a hot water heat exchanger, Even if the power generation efficiency is lowered, since the amount of hot water heat is increased, it is possible to efficiently control the system in consideration of power generation efficiency and hot water heat amount.

In addition, since the cogeneration unit only changes the flow of the heating medium, it is possible to maintain the total amount of power generation even when the power generation efficiency is lowered.

In addition, the cogeneration unit may vary the flow of the heating medium through the flow regulator, and the flow regulator may be configured as a three-way valve, thereby reducing manufacturing costs for regulating the amount of hot water supply.

In addition, in the cogeneration unit, since the heating medium is directly introduced into the hot water supply passage through the first and second flow controllers in the hot water supply mode, it is possible to realize a rapid hot water supply mode.

In addition, the cogeneration unit may include a mode setting unit, and the user can change the amount of heat supplied through the mode setting unit, thereby improving user convenience.

In addition, since the cogeneration unit senses the temperature of the heating medium through the temperature sensor and calculates the amount of hot water supplied based on the temperature of the heating medium, it is possible to accurately control the amount of hot water supplied, and to stably maintain the hot water outlet temperature.

In addition, since the combined heat and power unit performs a stabilization state check before the operation mode is performed, based on the engine rotation speed change, the suction pressure change, the temperature of the heating medium, and the operation mode maintenance time, the stability of the system is improved.

In addition, since the cogeneration unit recovers not only engine heat but also exhaust gas heat and supplies it to a heat demanding destination, energy efficiency is maximized.

The combined heat and power generation system according to the embodiment of the present invention can flexibly vary the amount of hot water supplied by adjusting the flow rate of the heat medium bypassed to the engine without additional configuration or complicated piping heat connection.

1 is a schematic diagram of a cogeneration system according to an embodiment of the present invention.
2 is a control block diagram of a cogeneration system according to an embodiment of the present invention.
3A to 3C are views illustrating a change in the flow rate of a heat medium according to a change in the operation mode of the cogeneration unit of FIG. 1 .
FIG. 4 is a diagram illustrating a change in the flow rate of a heat medium according to a change in the operation mode of the cogeneration unit of FIG. 1 .
FIG. 5A is a diagram illustrating a change in the amount of hot water supplied according to a change in the operation mode of the cogeneration unit of FIG. 1 .
FIG. 5B is a view illustrating a change in a temperature of a heating medium and a change in a temperature of hot water supply according to a change in the operation mode of the cogeneration unit of FIG. 1 .
6 is a diagram referred to in the description of power generation efficiency.
7A to 7C are diagrams referred to in the description of the present invention.
8 is a flowchart illustrating a method of operating a cogeneration unit according to an embodiment of the present invention.
9 is a flowchart illustrating the stabilization state inspection method of FIG. 8 .

Hereinafter, the present invention will be described in more detail with reference to the drawings.

The suffixes "module" and "part" for the components used in the following description are given simply in consideration of the ease of writing the present specification, and do not give a particularly important meaning or role by themselves. Accordingly, the terms “module” and “unit” may be used interchangeably.

Terms including an ordinal number, such as first, second, etc., may be used to describe various elements, but the elements are not limited by the terms. The above terms are used only for the purpose of distinguishing one component from another.

In the present application, terms such as "comprises" or "have" are intended to designate that a feature, number, step, operation, component, part, or combination thereof described in the specification exists, but one or more other features It is to be understood that it does not preclude the existence of, or addition of, elements, numbers, steps, operations, components, parts, or combinations thereof.

1 is a schematic diagram of a cogeneration system according to an embodiment of the present invention, and FIG. 2 is a control block diagram of a cogeneration system according to an embodiment of the present invention.

Referring to the drawings, the cogeneration system 1 according to an embodiment of the present invention may include a cogeneration unit 10 and a heat demander.

The cogeneration unit 10 may generate power and heat through fuel, supply the generated power to lighting or home appliances that are power consuming devices, and transmit the generated heat to a heat demanding device.

The heat demander may be a hot water supply unit 60 that receives heat generated from the engine 14 and supplies hot water into the building, or an air conditioner that receives heat generated from the engine 14 and air-conditions the inside of the building. . Hereinafter, it will be described that the heat demand destination in this embodiment is the hot water supply unit 60 .

The cogeneration unit 10 includes an engine 14 , a generator 100 connected from the engine 14 to generate electric power, and a hot water supply heat exchanger 16 connected to a hot water supply unit 60 and a water circulation passage 18 . ), a radiator 320 for dissipating heat generated by the engine, and an engine 14, a hot water heat exchanger ( 16) and the heat medium circulation passage 40 connecting the radiator 320, and the flow regulators for controlling the flow of the heat medium flowing through the heat medium circulation passage 40 (25a, 25b, hereinafter referred to as 25 if there is no need for distinction) and a temperature sensor 27 for measuring the temperature of the heating medium, and a heating medium pump 33 for pumping the heating medium.

The engine 14 may be driven by fossil fuels such as gas or petroleum to drive the generator 100 and generate heat.

The engine 14 may be connected to the intake line 20 and the exhaust line 30 to generate power by combustion of the mixture. The mixer supplied to the engine 14 through the mixer intake line 24 may be discharged as exhaust gas through the exhaust line 30 after combustion in the engine 14 .

The engine 14 includes a cylinder head 14b in which the mixture burns, an intake manifold 14a for flowing the mixture into the cylinder head 14b, and an exhaust manifold for flowing the burned exhaust gas to the exhaust line 30 . A fold 14c may be included.

The intake line 20 may introduce a mixture in which fuel is mixed with air. The intake line 20 may take in air and fuel, mix the air and fuel, and then supply it to the intake compressor 300 and the engine 14 . The fuel may include landfill gas as well as fossil fuels such as gas or petroleum.

The intake line 20 may be connected to external air, a fuel storage (not shown), an intake manifold 14a of the engine 14 and the intake compressor 300 .

For example, the intake line 20 is connected to an air intake line 21 through which air is introduced, a fuel intake line 22 through which fuel is introduced, an air intake line 21 and a fuel intake line 22 . It may include a mixer 23 for mixing air and fuel, and a mixer intake line 24 connected to the mixer 23 to supply the mixer to the engine 14 . According to an embodiment, the air intake line 21 , the fuel intake line 22 , and the mixer intake line 24 excluding the mixer 23 may be referred to as an intake line 20 .

The air intake line 21 may allow air to flow. One end of the air intake line 21 may be connected to outside air, and the other end may be connected to the mixer 23 . An air filter 41a for purifying the intake air and a silencer (not shown) may be disposed in the air intake line 21 .

The fuel intake line 22 may allow fuel to flow. One end of the fuel intake line 22 may be connected to a fuel reservoir (not shown), and the other end may be connected to the mixer 23 .

The mixer 23 may be connected to the fuel intake line 22 , the air intake line 21 , and the mixer intake line 24 . The mixer 23 may mix air and fuel in appropriate proportions and provide the mixed mixer to the mixer intake line 24 .

The mixer intake line 24 may provide the mixer mixed in the mixer 23 to the intake manifold 14a of the engine 14 . The mixer intake line 24 may have one end connected to the mixer 23 and the other end connected to the intake manifold 14a of the engine 14 .

The intake compressor 300 may compress the mixture supplied to the intake line 20 and provide it to the engine 14 .

The intake compressor 300 may compress the mixer flowing through the mixer intake line 24 to a constant pressure. The intake compressor 300 may be connected to the intake line 24 . Specifically, the intake compressor 300 may be connected to the mixer intake line 24 between the intake manifold 14a of the engine 14 and the mixer 23 .

The intake compressor 300 may be operated by a separate power source other than exhaust gas, or may be rotated by exhaust gas discharged to the exhaust line 30 to compress the mixture supplied to the intake line 20 . Hereinafter, the intake compressor 300 will be described on the assumption that the exhaust gas is operated as a power source. When the intake compressor 300 is operated by exhaust gas, there is an advantage of saving energy because there is no need to supply separate energy to the intake compressor 300 .

The intake compressor 300 may include a turbocharger, and the turbocharger may compress the mixer through the turbocharger in a state where air and fuel are mixed. In this case, there is an advantage in that the power generation output is improved while the fuel is stably supplied without a separate fuel pressurization device and a regulator.

On the other hand, when the intake compressor 300 is used, the temperature and pressure of the mixer flowing into the engine 14 become very high, and there is a risk of explosion when the high-temperature and high-pressure mixer flows out to the outside, and the engine 14 ), since the amount of fuel is relatively small when inflowing, the output may be reduced.

Accordingly, the cogeneration unit 10 of the present invention may further include a cooler 50 for cooling the mixture compressed in the intake compressor 300 . The cooler 50 may provide the engine 14 by cooling the mixture compressed in the intake compressor 300 .

The cooler 50 may provide the engine 14 by cooling the mixture compressed in the intake compressor 300 .

The cooler 50 includes a cooler radiator 52 for exchanging the refrigerant with outside air, a cooler heat exchanger 51 for exchanging refrigerant with a mixer flowing through the mixer intake line 24, and a refrigerant in which the refrigerant flows, and heat exchange with the cooler A cooler circulation flow path 53 circulating between the unit 51 and the cooler radiator 52 may be included.

When the mixer compressed by the cooler 50 is cooled, the temperature of the mixer is lowered and the volume is small, so that the amount of fuel supplied to the engine 14 is increased to improve power generation efficiency, and the mixer explodes when leaking There are advantages to avoiding

The generator 100 has a rotor connected to the output shaft of the engine 14 to produce power when the output shaft rotates, and through the generated power, it can be supplied to power consuming devices such as lighting or home appliances in a building in which the cogeneration generator is installed. have.

The hot water supply unit 60 is connected to a water pipe or hot water pipe in the building, and the hot water supply tank 12 in which the hot water is accommodated, and the hot water supply heat exchange so that the hot water supply circulates between the hot water heat exchanger 16 and the hot water tank 12 . It may include a water circulation passage 18 connecting the unit 16 and the hot water supply tank 12 . The hot water supply unit 60 may further include a temperature controller for controlling the temperature of the hot water supply tank 12 .

The hot water heat exchanger 16 may transmit heat generated by the engine 14 to the hot water supply unit 60 . Specifically, the heat medium on the heat medium circulation passage 40 may recover heat generated in the engine 14 and transmit it to the hot water heat exchanger 16 . At this time, the hot water heat exchanger 16 transfers heat generated in the engine 14 to the hot water supply unit 60 through heat exchange with the water circulation passage 18 .

On the other hand, the cogeneration unit 10 of the present invention generates heat together with electric power during its operation, and is preferably operated when the hot water supply load from the hot water supply unit 60 and the electric power load of the electric power consuming device are together. However, in order to protect the engine 14 when there is a power load and no hot water supply load, it is necessary to recover heat from the engine 14 and radiate heat to the outside. there is

Accordingly, the cogeneration unit 10 of the present invention may further include a radiator 320 for dissipating heat generated by the engine. In this case, the radiator 320 may include heat dissipation passages 19a and 19b through which the heat medium passes, hereinafter referred to as 19 when no distinction is required.

The radiator 320 may be water-cooled by cooling water such as water for heat transferred from the heating medium, and may be cooled by air-cooling by air, which will be described below as being cooled by air-cooling. To this end, the radiator 320 may further include a heat dissipation fan.

The heat medium circulation passage 40 may connect the engine 14, the hot water heat exchanger 16, and the radiator 320 so that the heat medium circulates through the engine 14, the hot water heat exchanger 16, and the radiator 320. .

The heat medium on the heat medium circulation passage 40 may recover heat generated in the engine 14 and transmit it to the hot water supply unit 60 . To this end, the heat medium circulation passage 40 includes a heat medium supply passage 11, a bypass passage 17, hot water supply passages 15a and 15b (referred to as 15 when there is no need for a distinction below), and a heat medium recovery passage 26. and a heat dissipation flow path 19 .

On the other hand, in the cogeneration unit 10 of the present invention, it is possible to recover the heat of the engine 14, that is, the heat of the engine body, while the heating medium passes directly through the engine 14, and includes a separate engine cooling heat exchanger. , it is also possible to recover the heat transferred to the engine cooling heat exchanger while the heating medium passes through the engine 14 and the engine cooling heat exchanger. Also, hereinafter, the heating medium may mean cooling water.

The heat medium circulation passage 40 is passed to the engine 14 through the heat medium supply passage 11 through the bypass passage 17 and/or the hot water supply passage 15 after the heat medium passes through the engine 14 . It may be formed in a cycle.

In addition, the heat medium on the hot water supply passage 15 can be recovered to the engine 14 through the heat radiation passage 19 by a flow regulator 25 to be described later.

More specifically, the heat medium supply passage 11 may be disposed at one end of the engine 14 to supply heat generated by the engine 14 . The hot water supply passage 15 may branch at the first branch point of the heat medium supply passage 11 to transmit heat generated in the engine 14 to the hot water heat exchanger 16 . The bypass flow path 17 may be branched at the first branch point so that the heat medium on the heat medium supply flow path is bypassed to the engine 14 . The heat dissipation flow path 19 may branch at the second branch point of the hot water supply flow path 15 to transfer heat generated by the engine 14 to the radiator 320 .

The hot water supply passage 15 may include a first hot water supply passage 15a and a second hot water supply passage 15b. The first hot water supply passage 15a may be connected to the first branch point to guide the heating medium to the second branch point. The second hot water supply flow path 15b may connect the second branch point and the bypass flow path 17 .

The heat dissipation flow path 19 includes a heat dissipation suction flow path 19a for sucking the heat medium on the hot water supply flow path 15 , in particular, the first hot water supply flow path 15a to the radiator 320 , and discharges the heat medium sucked into the radiator 320 . It may include a heat dissipation discharge flow path (19b) for

The heat radiation suction passage 19a may be connected to the second branch point to guide the heat medium on the first hot water supply passage 15a to the radiator 320 . The heat dissipation discharge flow path 19b may connect the radiator 320 and the bypass flow path 17 .

The flow regulator 25 may be disposed in the heat medium circulation passage 40 to control the flow of the heat medium. The flow regulator 25 may include a first flow regulator 25a and a second flow regulator 25b.

The first flow regulator 25a is disposed at the first branch point so that the heating medium on the heating medium supply flow path 40 selectively flows into either the bypass flow path 17 or the hot water supply flow path 19, or the heating medium bypasses It is possible to control the flow of the heating medium so as to simultaneously flow into the flow passage 17 and the hot water supply passage 19 .

The second flow regulator 25b is disposed at the second branch point so that the heating medium on the hot water supply flow path 19 selectively flows into either the heat dissipation flow path 19 or the hot water supply flow path 15 , or the heat medium flows through the heat dissipation flow path 19 ) and the flow of the heating medium can be controlled to flow simultaneously to the hot water supply passage 15 .

Specifically, the heating medium supply passage 11 may be connected to one end of the engine 14 and extend to the first flow regulator 25a. The first hot water supply passage 15a may be connected to the first flow regulator 25a to guide the heating medium on the heating medium supply passage 11 to the second flow regulator 25b. The second hot water supply flow path 15b may have one end connected to the second flow regulator 25b and the other end coupled to the bypass flow path 17 .

The heat radiation suction passage 19a may be connected to the second flow regulator 25b to guide the heat medium on the first hot water supply passage 15a to the radiator 320 . One end of the heat dissipation discharge flow path 19b may be connected to the radiator 320 , and the other end may be laminated to the bypass flow path 17 .

Meanwhile, the bypass flow path 17 may have one end connected to the first flow regulator 25a and the other end coupled to the second hot water supply flow path 15b and the heat dissipation discharge flow path 19b.

The heat medium recovery passage 26 may be connected to a junction where the bypass passage 17 , the heat radiation discharge passage 19b , and the second hot water supply passage 15b are laminated, and extend to the engine 14 .

Meanwhile, in FIG. 1 , the junction of the heat dissipation discharge flow path 19b and the bypass flow path 17 and the junction of the second hot water supply flow path 15b and the bypass flow path 17 are different from each other, but heat dissipation Since the heating medium on the discharge passage 19b, the heating medium on the bypass passage 17, and the heating medium on the second hot water supply passage 15b are applied to the engine 14 through the heating medium recovery passage 26, the heat radiation discharge passage 19b , the junction of the bypass flow path 17 and the second hot water supply flow path 15b may be shown at the same location.

The first flow regulator 25a may have a three-way valve, so that the heating medium on the heating medium supply flow path 11 flows to the bypass flow path 17 and/or the first hot water supply flow path 15a according to the operation mode. .

The second flow regulator 25b may have a three-way valve to allow the heat medium on the second hot water supply passage 15a to flow to the heat radiation suction passage 19a and/or the second hot water supply passage 15b according to the operation mode. have.

When the flow regulator 25 is configured as a three-way valve, the manufacturing cost can be reduced.

Meanwhile, the combined heat and power generation system 1 of the present invention may include a sensing unit 270 for sensing the temperature of a heating medium or water supply or sensing a flow rate of a heating medium on the heating medium circulation passage 40 .

The sensing unit 270 may include a first temperature sensor 27 , a second temperature sensor 28 , and a third temperature sensor 29 .

The first temperature sensor 27 may be disposed in the heat medium circulation passage 40 to measure the temperature of the heat medium on the heat medium circulation passage 40 . More preferably, the first temperature sensor 27 is disposed in the heat medium recovery passage 26 , and can measure the temperature of the heat medium recovered by the engine 14 .

The second temperature sensor 28 may be disposed on the water circulation passage 18 . More preferably, the second temperature sensor 28 is disposed at the water inlet of the hot water supply tank 12 and can measure the temperature of the water obtained into the hot water supply tank 12 .

The third temperature sensor 29 may be disposed on the water circulation passage 18 . More preferably, the third temperature sensor 29 is disposed at the water outlet of the hot water supply tank 12 to measure the temperature of water discharged from the hot water supply tank 12 .

The controller 240 may calculate the amount of heat supplied by the hot water supply tank 12 through the second temperature sensor 28 and the third temperature sensor 29 . For example, the control unit 240 may control the hot water supply of the hot water supply tank 12 through a calorific formula based on the temperature of the water supplied to the hot water supply tank 12 and the water outlet temperature of the water discharged from the hot water supply tank 12 . The amount of heat can be calculated.

Meanwhile, the controller 240 may set the operation mode according to the amount of heat supplied, and the amount of heat may be derived through the temperature of the heat medium on the heat medium circulation passage 40 sensed by the first temperature sensor 27 .

For example, through the control unit 240, the second temperature sensor 28, and the third temperature sensor 29, the amount of heat supplied in the hot water supply tank 12 is calculated, and at this time, the amount of hot water supplied by the first temperature sensor 27 is detected. By measuring the temperature, the relationship between the temperature of the heating medium sensed by the first temperature sensor 27 and the amount of heat supplied may be converted into a database. The controller 240 may calculate the amount of heat supplied through the temperature of the first temperature sensor 27 based on the database DB.

On the other hand, in the cogeneration system 1 of the present invention, since the first temperature sensor 27 is disposed on the heat medium recovery passage 26 , the bypass passage 17 , the heat dissipation passage 19 and the hot water supply passage 15 ) The manufacturing cost is reduced compared to the case of arranging each temperature sensor in each. In addition, since the first temperature sensor 27 is disposed on the heat medium recovery passage 26 , it is possible to measure the temperature of all the heat medium flowing on the heat medium circulation passage 40 . In addition, the combined heat and power system 1 measures the temperature of the entire heating medium, so that the temperature change due to a sudden change in flow rate is small, and thus provides accuracy and reliability of measuring the amount of hot water supply.

The sensing unit 270 may include a flow rate sensor 28 that measures the flow rate of the heating medium. The flow rate sensor 28 is disposed on the heat medium circulation passage 40 , and can measure the heat medium flow rate on the heat medium circulation passage 40 . The control unit 240 controls the degree of opening and closing of the flow controller 25 based on the flow rate sensed by the flow rate sensor 28 to enable more accurate flow rate control.

The mode setting unit 230 may receive a user's driving mode setting command. The operation mode may be set according to the amount of heat supplied by hot water. For example, the operation mode may be divided into a hot water supply non-use mode having a minimum amount of hot water supply and a hot water supply use mode having a hot water supply heat amount greater than a minimum value. The hot water supply use mode may be divided into a first operation mode, a second operation mode that outputs a greater amount of hot water supply than the first operation mode, and a third operation mode that outputs a greater amount of hot water supply than the second operation mode according to the amount of hot water supplied. .

The mode setting unit 230 may be disposed in the cogeneration unit 10 or may be disposed in the hot water supply tank 12 . Alternatively, they may be respectively disposed in the cogeneration unit 10 and the hot water supply tank 12 .

At least one pump 33 may be installed on the heat medium circulation passage 40 to circulate the heat medium. The pump 33 may be disposed in the heat medium recovery flow path 26 of the heat medium circulation flow path 40 , and a first temperature sensor 27 may be disposed at the heat medium inlet of the pump 33 .

Meanwhile, the cogeneration system 1 of the present invention may further include an exhaust gas heat exchanger 13 disposed in the heat medium circulation passage 40 to exchange exhaust gas heat discharged from the engine 14 .

The exhaust gas heat exchanger 13 may exchange heat between the exhaust gas passing through the exhaust line 30 and the heat medium circulating in the heat medium circulation passage 40 . The exhaust gas heat exchanger 13 may transfer exhaust gas thermal energy of the exhaust line 30 to the heat medium circulation passage 40 . Accordingly, the combined heat and power generation system 1 of the present invention recovers not only engine heat but also exhaust gas heat and supplies it to a heat demanding destination, thereby maximizing energy efficiency.

3A to 3C and 4 are views illustrating a change in the flow rate of a heat medium according to a change in the operation mode of the cogeneration unit of FIG. 1 .

In more detail, FIGS. 3A to 3C are diagrams illustrating a change in the flow rate of the thermal medium of the cogeneration unit 10 in the hot water supply mode, and FIG. 4 is a diagram illustrating the change in the flow rate of the thermal medium in the hot water supply non-use mode.

3A, the control unit 240 bypasses the first heat medium flow rate to the engine in the first hot water supply mode to control the heat medium on the heat medium circulation passage 40 to be the first heat medium temperature. can

Specifically, in the first hot water supply mode, the control unit 240 controls the first flow regulator 25a so that the heat medium on the heat medium supply passage 11 is directed to the bypass passage 17 and the first hot water supply passage 15a. They can be controlled to flow at the same time.

The control unit 240 controls the first flow regulator 25a to control the first heat medium flow rate to flow in the bypass flow path 17 , and control so that the first hot water supply flow rate flows through the first hot water supply flow path 15a . can do. For example, the control unit 240 controls 30% of the total heat medium flow rate on the heat medium supply flow path 11 to flow to the bypass flow path 17 , and the remaining 70% flows to the first hot water supply flow path 15a . can be controlled to

The control unit 240 selectively opens and closes the second flow controller 25b in the first hot water supply mode, so that the entire heat medium (first hot water supply flow rate) on the first hot water supply passage 15a is transferred to the second hot water supply passage 15b. flow can be controlled.

The heat medium on the second hot water supply passage 15b and the heat medium on the bypass passage 17 may be laminated and introduced into the heat medium recovery passage 26 . At this time, the heat medium temperature on the heat medium recovery passage 26 may be the first heat medium temperature.

On the other hand, the hot water heat exchanger 16 can exchange heat between the heat medium on the second hot water supply passage 15b and the heat medium on the water circulation passage 18 . The heat medium on the second hot water supply passage 15b transmits thermal energy to the water circulation passage 18 , and the hot water supply tank 12 can output the first hot water supply heat amount.

In FIG. 3B , the control unit 240 bypasses the second heat medium flow rate, which is smaller than the first heat medium flow rate, to the engine 14 in the second hot water supply mode, so that the heat medium on the heat medium circulation passage 40 is higher than the first heat medium temperature. It can control so that it may become a low 2nd heating medium temperature.

Specifically, in the second hot water supply mode, the control unit 240 controls the first flow regulator 25 so that a second heat medium flow rate smaller than the first heat medium flow rate flows in the bypass flow path 17 , The second hot water supply flow rate greater than the first hot water supply flow rate may be controlled to flow through the first hot water supply flow path 15a. For example, the control unit 240 controls 15% of the total heat medium flow rate on the heat medium supply flow path 11 to flow to the bypass flow path 17, and the remaining 85% flows to the first hot water supply flow path 15a. can be controlled to

The control unit 240 may selectively open and close the second flow controller 25b to control the entire heat medium (second hot water supply flow rate) on the first hot water supply passage 15a to flow through the second hot water supply passage 15b. .

The heat medium on the second hot water supply passage 15b and the heat medium on the bypass passage 17 may be laminated and introduced into the heat medium recovery passage 26 . At this time, in the second hot water supply mode, since the amount of the heat medium that has passed through the hot water supply heat exchanger 16 is greater than the amount of the heat medium that has passed through the hot water heat exchanger 16 in the first hot water supply mode, the heat medium recovery passage 26 . The heating medium temperature of the phase may be a second heating medium temperature smaller than the first heating medium temperature.

On the other hand, the hot water heat exchanger 16 can exchange heat between the heat medium on the second hot water supply passage 15b and the heat medium on the water circulation passage 18 . Since more heat energy is transmitted to the hot water heat exchanger 16 than in the first hot water supply mode, the hot water tank 12 may output a second hot water supply heat quantity greater than the first hot water supply heat quantity.

In FIG. 3C , the control unit 240 sends all of the heat medium on the heat medium supply passage 11 to the hot water supply heat exchanger 16 in the third hot water supply mode, so that the heat medium on the heat medium circulation passage 40 becomes the third heat medium temperature. can be controlled The third hot water supply mode can be called the maximum hot water supply mode.

Specifically, the control unit 240 may selectively open and close the first flow regulator 25a in the third hot water supply mode to control that the heat medium on the heat medium supply passage 11 does not flow into the bypass flow passage 17 . . At this time, the flow rate of the third heat medium may flow through the first hot water supply passage 15a.

That is, the third heat medium flow rate may be the total flow rate flowing through the heat medium supply passage 11 . For example, the controller 240 may control the total flow rate (100%) flowing through the heat medium supply passage 11 to flow in the first hot water supply passage 15a.

The control unit 240 may selectively open and close the second flow regulator 25b so that all of the heat medium flow rate (the third hot water supply flow rate) on the first hot water supply passage 15a flows to the second hot water supply passage 15b. have.

The heat medium on the second hot water supply passage 15b may flow into the heat medium recovery passage 26 . At this time, in the third hot water supply mode, since the amount of the heat medium that has passed through the hot water supply heat exchanger 16 is greater than the amount of the heat medium that has passed through the hot water heat exchanger 16 in the second hot water supply mode, the heat medium recovery flow path 26 . The temperature of the heating medium of the phase may be a temperature of the third heating medium that is smaller than the temperature of the second heating medium

On the other hand, the hot water heat exchanger 16 can exchange heat between the heat medium on the second hot water supply passage 15b and the heat medium on the water circulation passage 18 . Since more heat energy is transmitted to the hot water heat exchanger 16 than in the second hot water supply mode, the hot water supply tank 12 can output a third hot water supply heat quantity greater than the second hot water supply heat quantity.

On the other hand, in the above example, the flow rate of the heat medium flowing through the bypass flow path 17 is an example for matching the temperature of the heat medium flowing through the heat medium recovery flow path 26 to the preset heat medium temperature, and the present invention is 30%, It is not bound to a flow rate, such as 15% or 0% . That is, in the cogeneration unit 10 of the present invention, the flow rate of the heating medium bypassed to the engine 14 can be adjusted so that the temperature of the heating medium on the heating medium recovery passage 26 becomes a preset heating medium temperature according to the amount of heat supplied. .

In addition, as described above, in the cogeneration unit 10 of the present invention, since the bypass flow path 17 is directly connected to the heat medium supply flow path 11 through the first flow regulator 25a, the engine 14 It has the advantage of being able to quickly respond to changes in the hot water supply mode by quickly changing the flow rate of the thermal medium bypassed by the

In addition, there is an advantage that the flow rate of the heating medium can be flexibly varied by using the first flow regulator 25a and the second flow regulator 25b without a complicated additional configuration.

In FIG. 4 , the controller 240 controls the flow regulator 25 in the hot water supply non-use mode so that the heat medium on the heat medium circulation passage 40 passes through the radiator 320 and the hot water heat exchanger 16 at the same time. can do.

Specifically, in the hot water supply non-use mode, the control unit 240 controls the fourth heat medium flow rate to flow in the bypass flow path 17 by adjusting the first flow controller 25a, and the fourth hot water supply flow rate is the first hot water supply flow rate. It can be controlled to flow in the flow path (15a). For example, the control unit 240 controls 30% of the total heat medium flow rate on the heat medium supply flow path 11 to flow to the bypass flow path 17 , and the remaining 70% flows to the first hot water supply flow path 15a . can be controlled to

In the hot water supply non-use mode, the control unit 240 may control the second flow regulator 25b to flow the heat medium on the heat medium supply passage 11 to the heat radiation passage 19 and the hot water supply passage 15 at the same time. have. For example, the control unit 240 controls 80% of the total flow rate of the heat medium on the first hot water supply passage 15a to flow to the heat dissipation passage 19, and the remaining 20% flows to the second hot water supply passage 15a. can be controlled to

On the other hand, the hot water heat exchanger 16 can exchange heat between the heat medium on the second hot water supply passage 15b and the heat medium on the water circulation passage 18 . The heat medium on the second hot water supply passage 15b transmits thermal energy to the water circulation passage 18 , and the hot water supply tank 12 can output the minimum amount of hot water supply heat.

The cogeneration unit 10 of the present invention controls the minimum hot water supply heat amount to be supplied to the hot water supply unit 60 by adjusting the second flow regulator 25b in the hot water supply non-use mode, so that the hot water supply mode is changed from the hot water supply non-use mode In time, it is possible to quickly reach the target hot water calorie.

FIG. 5A is a view showing a change in the amount of heat supplied according to the operation mode change of the cogeneration unit of FIG. 1 , and FIG. 5B is a heat medium temperature change and hot water supply according to the operation mode change of the cogeneration unit of FIG. 1 . It is a figure which shows the temperature change.

Referring to the drawings, in FIG. 5A , as the engine rotation speed increases, the thermal energy generated in the engine 14 increases. As the engine rotation speed increases, the thermal energy transferred to the hot water heat exchanger 16 increases. can do.

In addition, since the hot water heat exchanger 16 transfers thermal energy to the hot water supply unit 60 , as the engine rotation speed increases, the amount of heat in the hot water supply may increase. On the other hand, the amount of heat supplied by the hot water supply may converge to a certain amount of heat in the hot water supply as the engine rotation speed increases.

The converged amount of hot water supply may be the maximum amount of hot water supply that can be output in the corresponding operation mode, and the operation mode may be set based on the maximum amount of hot water supply. Hereinafter, for convenience of description, the maximum amount of hot water supply and the amount of hot water supply may be used interchangeably. Also, likewise, in FIG. 5B, the minimum heating medium temperature and the heating medium temperature may be used interchangeably. In addition, in FIG. 5B , the maximum hot water temperature and the hot water temperature may be used interchangeably.

The controller 240 may control the flow controller 25 so that the hot water supply unit 60 outputs the first hot water supply heat amount H2 in the first hot water supply mode (mode 1).

Specifically, the controller 240 may adjust the flow controller 25 so that the temperature of the heat medium on the heat medium circulation passage 40 becomes the first heat medium temperature T2 corresponding to the first hot water supply heat H2.

To this end, the control unit 240 controls the first flow regulator 25a to control the first heat medium flow rate among the total heat medium flow rates on the heat medium supply flow path 15a to flow to the bypass flow path 17, By adjusting the second flow regulator 25b, the first hot water supply flow rate can be controlled to flow through the second hot water supply flow path 15b.

The hot water supply heat exchanger 16 can exchange heat between the first hot water supply flow rate and the water circulation passage 18 . At this time, the hot water supply temperature from which the hot water supply tank 12 is discharged may be the first hot water supply temperature T5.

The control unit 240, in the second hot water supply mode (mode 2), the hot water supply unit 60 can control the flow regulator 25 to output the second hot water supply heat amount (H3) greater than the first hot water supply heat amount (H2) have.

Specifically, the controller 240 may adjust the flow controller 25 so that the temperature of the heat medium on the heat medium circulation passage 40 becomes the second heat medium temperature T1 corresponding to the second hot water supply heat amount H3 . Since the second hot water supply heat amount H3 is larger than the first hot water supply heat amount H2, it is preferable that the second heat medium temperature T1 is smaller than the first heat medium temperature T1.

To this end, the control unit 240 controls the first flow regulator 25a to set a second heat medium flow rate smaller than the first heat medium flow rate among the total heat medium flow rates on the heat medium supply flow path 15a, the bypass flow path 17 . It is possible to control the flow to flow in the , and by adjusting the second flow regulator 25b, a second hot water supply flow rate greater than the first hot water supply flow rate can be controlled to flow in the second hot water supply flow passage 15b.

The hot water supply heat exchanger 16 can exchange heat between the second hot water supply flow rate and the water circulation passage 18 . Since the second hot water supply flow rate is greater than the first hot water supply flow rate, the hot water supply temperature from the hot water supply tank 12 may be the second hot water supply temperature T6 which is greater than the first hot water supply temperature T5.

6 is a diagram referred to in the description of power generation efficiency, and FIGS. 7A to 7C are diagrams referred to in the description of the present invention.

Referring to the drawings, in FIG. 6 , in the combined heat and power generation system 1 , the amount of heat supplied from hot water may gradually increase from the time t1 when the operation mode is changed from the first operation mode to the second operation mode.

As the hot water supply heat amount increases from H4 to H5, the hot water supply flow rate flowing through the hot water supply passage 15 may be increased. In addition, as the hot water supply flow rate increases, the heat medium flow rate bypassed to the engine 14 may be reduced.

Accordingly, the temperature of the heating medium sensed in the heating medium circulation passage 26 may be decreased from T8 to T7 as the amount of heat supplied increases.

On the other hand, as the temperature of the heating medium decreases, friction between the cylinder and the engine oil inside the engine 14 increases, so that the fuel consumption of the engine 14 may increase. As fuel consumption increases, power generation efficiency may decrease.

In FIG. 6 , as the amount of heat supplied from hot water is increased, the temperature of the heating medium is gradually decreased, and thus, the power generation efficiency may be decreased from P1 to P2.

In FIG. 7A , S610 represents the power generation efficiency according to the engine speed in the first hot water supply mode, and FIG. S630 represents the power generation efficiency according to the engine speed in the second hot water supply mode.

In the first hot water supply mode, the heat medium temperature on the heat medium recovery passage 26 may be the first heat medium temperature. In addition, in the second hot water supply mode, the temperature of the heating medium on the heating medium recovery passage 26 may be a second heating medium temperature smaller than the first heating medium temperature.

Since the temperature of the first heating medium is greater than the temperature of the second heating medium, the power generation efficiency P5 in the first hot water supply mode may be greater than the power generation efficiency P4 in the second hot water supply mode.

For example, in FIG. 7B , when the heat medium temperature on the heat medium recovery passage 26 is 30 degrees, the hot water supply unit 60 may output a hot water supply heat amount of 51Kw, and in this case, the power generation efficiency may be 30.7.

In addition, in FIG. 7C , when the temperature of the heat medium on the heat medium recovery passage 26 is 25 degrees, the hot water supply unit 60 may output a hot water supply heat amount of 55Kw, and at this time, the power generation efficiency may be slightly lowered to 30.2. .

The combined heat and power generation system 1 of the present invention can efficiently operate the system in consideration of a situation in which power generation efficiency is required to be high and a situation in which hot water supply heat quantity is required.

That is, the combined heat and power generation system 1 of the present invention can increase power generation efficiency while preventing overheating of the engine 14 by applying a heating medium to the radiator 320 when there is no user's request for hot water. In addition, when there is a user's request for hot water, the heat medium may be applied to the hot water heat exchanger 16 to increase the hot water heat quantity even if the power generation efficiency is lowered.

On the other hand, since the cogeneration system 1 of the present invention performs the hot water supply mode by changing only the flow of the heat medium, even when the power generation efficiency is lowered, the total amount of power generation can be maintained.

8 is a flowchart illustrating an operation method of a cogeneration unit according to an embodiment of the present invention, and FIG. 9 is a flowchart illustrating the stabilization state inspection method of FIG. 8 .

Referring to the drawings, the mode setting unit 230 may receive a user's driving mode setting command. The controller 240 may check the driving mode (S810).

The operation mode may be divided into a hot water supply non-use mode in which the amount of hot water supply is minimum and a hot water supply mode in which the hot water supply heat amount is greater than a minimum value. The hot water supply mode may be divided into a first operation mode, a second operation mode that outputs a greater amount of hot water supply than the first operation mode, and a third operation mode that outputs a greater amount of hot water supply than the second operation mode according to the amount of hot water supplied.

The controller 240 may calculate whether the checked operation mode corresponds to the hot water supply mode (S830).

When the checked operation mode is the hot water supply non-use mode, the control unit 240 adjusts the first flow controller 25a and the second flow controller 25b so that the heat medium on the heat medium supply flow path is changed to the bypass flow path 17, It can be controlled so that it flows through the hot water supply flow path 15 and the heat radiation flow path 19 .

When the checked operation mode is the hot water supply mode, the controller 240 may perform a system stability test (S850).

First, the control unit 240 may perform an engine rotation speed variation width test ( S910 ). The controller 240 may calculate that the engine rotation speed variation range is normal when the engine speed variation range is within a preset engine speed variation range. For example, when the engine rotation speed is within 30 rpm, the controller 240 may calculate that the engine rotation speed fluctuation range is normal.

The controller 240 may perform a suction pressure fluctuation range test (S930). To this end, the cogeneration unit 10 may further include a manifold absolute pressure (MAP) sensor in the intake manifold 14a of the engine 14 .

When the suction pressure fluctuation range is within a preset suction pressure fluctuation range, the controller 240 may calculate that the suction pressure fluctuation range is normal. For example, when the suction pressure variation range is within 10MAP, the controller 240 may calculate that the suction pressure variation range is normal.

The controller 240 may perform a thermal medium temperature test (S950). The controller 240 may calculate that the heat medium temperature is normal when the heat medium temperature measured in the heat medium recovery passage 26 is equal to or greater than a preset temperature.

The heating medium temperature may be set differently depending on the operation mode. For example, in the hot water supply non-use mode, the reference heating medium temperature may be 70 degrees. Also, in the first hot water supply mode, the reference heating medium temperature may be 30 degrees.

When the first hot water supply mode setting command is received in the hot water supply non-use mode, the controller 240 may calculate that the thermal medium temperature is normal if the thermal medium temperature measured by the temperature sensor 27 is 70 degrees or more.

The controller 240 may perform a driving mode maintenance time test (S970). The controller 240 may control the flow rate when the operation mode maintenance time is equal to or greater than the preset operation mode maintenance time. For example, when a mode setting command is not received from the mode setting unit 230 for 5 minutes, the controller 240 may control the flow controller 25 .

Meanwhile, if any one of steps S910 to S970 does not satisfy a preset condition, the controller 240 may output the error without entering the flow rate control step.

The cogeneration system 1 of the present invention has the advantage of improving the stability of the system and stably supplying hot water because the stabilization state inspection is performed before performing the hot water supply mode.

The controller 240 may control the flow regulator 25 according to the hot water supply mode after the stabilization state test (S870).

The control unit 240 controls the first flow regulator 25a according to the hot water supply mode to flow the thermal medium on the thermal medium supply passage 15a to the bypass passage 17 and/or the first hot water supply passage 15a. can be controlled to In addition, the control unit 240 may selectively open and close the second flow regulator 25b to control the heating medium on the heating medium supply passage 15a to flow into the second hot water supply passage 15b.

As the flow rate of the heat medium on the heat medium circulation passage 40 changes, the flow rate of the heat medium passing through the hot water heat exchanger 16 may vary, so that the amount of heat of hot water supply may be varied.

The accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and the technical spirit disclosed herein is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and scope of the present invention It should be understood to include water or substitutes.

Likewise, although acts are depicted in the drawings in a particular order, it should not be construed that such acts must be performed in that particular order or sequential order shown, or that all depicted acts must be performed in order to achieve desirable results. . In certain cases, multitasking and parallel processing may be advantageous.

In addition, although preferred embodiments of the present invention have been illustrated and described above, the present invention is not limited to the specific embodiments described above, and the technical field to which the present invention belongs without departing from the gist of the present invention as claimed in the claims In addition, various modifications are possible by those of ordinary skill in the art, and these modifications should not be individually understood from the technical spirit or perspective of the present invention.

14: engine
15: hot water euro
16: hot water heat exchanger
17: Bypass Euro
19: heat dissipation flow path
25a: first flow regulator
25b: second flow regulator
40: heat medium circulation flow path
240: control unit
320: radiator

Claims (10)

an engine that drives the generator and generates heat;
a heating medium supply passage disposed at one end of the engine and through which a heating medium heated by heat generated in the engine flows;
a heating medium recovery passage disposed at the other end of the engine so that the heating medium flows into the engine;
a radiator for dissipating heat generated by the engine through the heating medium;
a hot water heat exchanger for transferring the heat generated by the engine to the hot water supply unit through the heating medium;
a first flow regulator connected to the heating medium supply passage and transferring the heating medium introduced through the heating medium supply passage to at least one of the heating medium recovery passage, the radiator, and the hot water heat exchanger;
Among the heating media introduced into the first flow regulator, the remaining heating media except for the heating medium transferred to the heating medium recovery passage is introduced, and the heating medium introduced from the first flow regulator is transferred to at least one of the radiator and the hot water heat exchanger. 2 flow regulator; and
A control unit configured to control the first flow regulator and the second flow regulator based on a set value related to heat transferred between the hot water supply heat exchanger and the hot water supply unit, which is set according to a user input,
The set value is a cogeneration unit, characterized in that it is a target value for the amount of heat supplied by the hot water supply unit. According to claim 1,
Further comprising a mode setting unit for receiving the user input,
The control unit is
Based on the user input received through the mode setting unit, the cogeneration unit, characterized in that for determining the set value related to the heat. delete According to claim 1,
Further comprising a bypass passage connecting the first flow regulator and the heat medium recovery passage,
The control unit is
According to the user input, as the target value for the amount of hot water supply increases, the first flow regulator is controlled such that the flow rate of the heating medium transferred to the bypass passage decreases. 5. The method of claim 4,
The control unit is
When the target value for the hot water heat quantity is set to the maximum value according to the user input,
controlling the first flow regulator so that the heating medium is not transferred to the bypass passage,
Cogeneration unit, characterized in that controlling the second flow regulator so that the heat medium is not transferred to the radiator. 5. The method of claim 4,
The control unit is
According to the user input, when the target value for the amount of hot water supply is not set, controlling the second flow regulator so that at least a portion of the heating medium is transferred to the radiator,
According to the user input, when a target value for the amount of hot water supply is set, the second flow regulator is controlled so that the heating medium is not transferred to the radiator. 5. The method of claim 4,
It is disposed in the heating medium recovery passage, further comprising a temperature sensor for detecting the temperature of the heating medium,
The control unit is
and controlling the first flow controller and the second flow controller so that the temperature of the heating medium detected through the temperature sensor matches the temperature corresponding to the set value. 5. The method of claim 4,
a first temperature sensor for detecting a temperature of water flowing into the hot water supply unit; and
Further comprising a second temperature sensor for detecting the temperature of the water discharged from the hot water supply unit,
The control unit is
Calculate the amount of heat supplied by the hot water supply unit based on the values detected by the first temperature sensor and the second temperature sensor, respectively;
The combined heat and power unit according to claim 1, wherein the first flow regulator and the second flow regulator are controlled so that the calculated hot water supply heat amount and a target value for the hot water supply heat amount match. 5. The method of claim 4,
a hot water supply passage for transferring at least a portion of the heating medium introduced into the second flow controller to the hot water supply heat exchanger and transferring the heating medium discharged from the hot water supply heat exchanger to the heating medium recovery passage; and
Among the heating media introduced to the second flow regulator, the heat medium other than the heating medium transferred to the hot water supply heat exchanger is transferred to the radiator, and a heat radiation passage for transferring the heating medium discharged from the radiator to the heating medium recovery passage.
The second flow regulator includes, among the heating media introduced to the first flow regulator, other heating media except for the heating media flowing through the bypass passage, and transfers the heating media introduced from the first flow regulator to the radiator and the hot water supply. Cogeneration unit, characterized in that the transfer to at least one of the heat exchangers. a cogeneration unit that generates power and heat and supplies the power and heat; and
and a hot water supply unit receiving heat generated from the cogeneration unit,
The combined heat and power unit,
an engine that drives the generator and generates heat;
a heating medium supply passage disposed at one end of the engine and through which a heating medium heated by heat generated in the engine flows;
a heating medium recovery passage disposed at the other end of the engine so that the heating medium flows into the engine;
a radiator for dissipating heat generated by the engine through the heating medium;
a hot water heat exchanger for transferring heat generated in the engine to the hot water supply unit through the heating medium;
a first flow regulator connected to the heating medium supply passage and transferring the heating medium introduced through the heating medium supply passage to at least one of the heating medium recovery passage, the radiator, and the hot water heat exchanger;
Among the heating media introduced into the first flow regulator, the remaining heating media except for the heating medium transferred to the heating medium recovery passage is introduced, and the heating medium introduced from the first flow regulator is transferred to at least one of the radiator and the hot water heat exchanger. 2 flow regulator; and
A control unit configured to control the first flow regulator and the second flow regulator based on a set value related to heat transferred between the hot water supply heat exchanger and the hot water supply unit, which is set according to a user input,
The set value is a cogeneration system, characterized in that it is a target value for the amount of heat supplied by the hot water supply unit.

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