KR102036817B1 - Cogeneration unit and system having the same - Google Patents

Abstract

The present invention relates to a cogeneration unit and a cogeneration system. The cogeneration unit according to the embodiment of the present invention includes an engine for driving a generator and generating heat, a radiator for radiating heat generated from the engine, a hot water heat exchanger for transferring heat generated from the engine to a hot water supply unit, and a heat medium On the basis of the heat medium circulation passage connecting the engine, the radiator and the hot water supply heat exchanger so as to circulate the engine, the hot water heat exchanger and the radiator, the flow regulator for controlling the flow of the heat medium flowing through the heat medium circulation passage, And a control unit for controlling the flow regulator to vary the flow rate of the heat medium bypassed to the engine. As a result, the calorific value of the hot water supply can be flexibly changed.

Description

Cogeneration unit and a system including the same {COGENERATION UNIT AND SYSTEM HAVING THE 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, which can efficiently vary the amount of hot water supply.

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

For example, a cogeneration system generates power by driving a generator and uses heat generated when the generator is driven. The power generated by the generator is supplied to lighting or various electric devices in a building where the generator is installed. The heat generated from the water is supplied to the heat demand such as the hot water supply unit.

On the other hand, in the cogeneration system, when the cooling water 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 cooling water falls below a predetermined temperature, the available efficiency of the engine is lowered, and due to the reduced available efficiency, The heating of the hot water supply unit is stopped even when there is a demand for hot water supply.

In particular, the conventional cogeneration system transmits heat to the hot water supply unit irrespective of the hot water supply demand, which may cause user inconvenience due to a decrease in engine performance and a decrease in the hot water supply temperature.

That is, the conventional cogeneration system has a problem in that it is not possible to flexibly change the amount of hot water supply according to the user's hot water demand, and therefore, the cogeneration system may not operate efficiently in response to the user's needs.

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

Another object of the present invention is to provide a cogeneration unit and a system including the same, which can quickly change the cooling water temperature in order to vary the amount of hot water supply.

Still another object of the present invention is to provide a cogeneration unit and a system including the same, which may vary the amount of hot water supply by a user's setting.

In order to achieve the above object, the cogeneration unit according to an embodiment of the present invention, an engine for driving a generator to generate heat, a radiator for radiating heat generated from the engine, and heat generated from the engine to the hot water supply unit A hot water heat exchanger to transmit, a heat medium circulation passage connecting the engine, the radiator and the hot water heat exchanger so that the heat medium circulates the engine, the hot water heat exchanger and the radiator, a flow regulator for controlling the flow of the heat medium flowing through the heat medium circulation passage, On the basis of the operation mode according to the control unit, the flow controller includes a control unit for varying the flow rate of the heat medium bypassed to the engine.

In order to achieve the above object, a cogeneration system according to an embodiment of the present invention includes a cogeneration unit for generating power and heat, and a hot water supply unit receiving heat generated from a cogeneration unit and a cogeneration unit. The cogeneration unit includes an engine for driving a generator and generating heat, a radiator for radiating heat generated from the engine, a hot water heat exchanger for transferring heat generated from the engine to the hot water supply unit, and a heat medium engine, a hot water heat exchanger. And a flow regulator for controlling the flow of the heat medium flowing through the heat medium circulation flow path, the heat medium circulation flow path connecting the engine, the radiator, and the hot water heat exchanger to circulate the radiator; And a control unit for varying the flow rate of the heat medium bypassed to the engine.

The cogeneration unit according to the embodiment of the present invention can flexibly vary the amount of hot water supply by adjusting the flow rate of the heat medium to be bypassed to the engine without any additional configuration or complicated piping heat.

In addition, the cogeneration unit applies a heat medium to a heat radiator when there is no user's demand for hot water, prevents overheating of the engine, and improves power generation efficiency. Even if the power generation efficiency is lowered, the hot water supply amount is increased, so that efficient system control in consideration of the power generation efficiency and the hot water supply amount is possible.

In addition, since the cogeneration unit changes only the flow of the heat medium, the total power generation amount can be maintained even when the power generation efficiency is lowered.

In addition, the cogeneration unit may vary the flow of the heat medium through the flow regulator, and the flow regulator may be configured as a three-way valve, thereby reducing the manufacturing cost for hot water supply calorie control.

Further, in the cogeneration unit, the heat medium flows directly into the hot water supply flow path through the first flow controller and the second flow regulator in the hot water supply mode, thereby enabling rapid hot water supply mode to be realized.

In addition, the cogeneration unit may include a mode setting unit, and the user may change the amount of hot water supply through the mode setting unit, thereby improving user convenience.

In addition, the cogeneration unit detects the temperature of the heat medium through the temperature sensor and calculates the amount of hot water supply heat based on the temperature of the heat medium, thereby enabling accurate control of the hot water amount of heat supply and stably maintaining the hot water output temperature.

In addition, the cogeneration unit performs the stabilization state check on the basis of the engine speed change, the intake pressure change, the temperature of the heating medium and the operation mode holding time before performing the operation mode, thereby improving the stability of the system.

In addition, the cogeneration unit recovers not only the engine heat but also the exhaust gas heat and supplies it to the heat demand, thereby maximizing energy efficiency.

The cogeneration system according to the embodiment of the present invention can flexibly vary the amount of hot water supply by adjusting the flow rate of the heat medium bypassed to the engine, without any additional configuration or complicated piping cracking.

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 diagrams showing changes in the flow rate of the heat medium according to the operation mode change of the cogeneration unit of FIG. 1.
FIG. 4 is a diagram showing a change in the flow rate of the heat medium according to the operation mode change of the cogeneration unit of FIG. 1.
5: A is a figure which shows the change in hot water calorie | heat amount according to the operation mode change of the cogeneration unit of FIG.
FIG. 5B is a diagram showing a heat medium temperature change and a hot water temperature change according to a change in an operation mode of the cogeneration unit of FIG. 1.
6 is a diagram referred to for describing power generation efficiency.
7A to 7C are views 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.
FIG. 9 is a flowchart illustrating the stabilization state inspection method of FIG. 8.

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

The suffixes "module" and "unit" for components used in the following description are merely given in consideration of ease of preparation of the present specification, and do not impart any particular meaning or role by themselves. Therefore, the "module" and "unit" may be used interchangeably.

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

In this application, the terms "comprises" or "having" are intended to indicate that there is a feature, number, step, operation, component, part, or combination thereof described in the specification, and one or more other features. It is to be understood that the present invention does not exclude, in advance, the existence or the possibility of adding 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 the embodiment of the present invention may include a cogeneration unit 10 and a heat source.

The cogeneration unit 10 may generate power and heat through fuel, supply the generated power to a lighting or home appliance, which is a power consuming device, and transfer the generated heat to a heat demander.

The heat demand may be a hot water supply unit 60 that receives the heat generated by the engine 14 and supplies hot water into the building, or an air conditioner that receives the heat generated by the engine 14 to air condition the interior of the building. . Hereinafter, the heat demand destination in the present embodiment will be described as the hot water supply unit 60.

The cogeneration unit 10 includes an engine 14, a generator 100 connected to the engine 14 to generate electric power, and a hot water heat exchanger 16 connected to the hot water supply unit 60 and the water circulation passage 18. ), A heat radiator 320 for radiating heat generated from the engine, and an engine 14 and a hot water heat exchanger to transfer the heat generated from the engine 14 to the hot water supply heat exchanger 16 and the radiator 320. 16) and the heat medium circulation flow path 40 which connects the radiator 320, and the flow regulators 25a, 25b which control the flow of the heat medium flowing through the heat medium circulation flow path 40 (25 if there is no need for division) And a temperature sensor 27 for measuring the temperature of the heat medium, and a heat medium pump 33 for pumping the heat medium.

The engine 14 may be driven by a fossil fuel 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 mixer. 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 mixer burns, an intake manifold 14a for flowing the mixer into the cylinder head 14b, and an exhaust manifold for flowing the burned exhaust gas to the exhaust line 30. It may include a fold 14c.

Intake line 20 may be introduced into the mixer is a mixture of fuel and air. The intake line 20 may intake air and fuel, mix air and fuel, and then supply the intake compressor 300 and the engine 14. The fuel may include landfill gas as well as fossil fuel such as gas or petroleum.

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

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

The air intake line 21 can flow air. One end of the air intake line 21 may be connected to the outside air, and the other end thereof may be connected to the mixer 23. The air intake line 21 may include an air filter 41a for purifying the intaken air, a silencer, and the like.

The fuel intake line 22 can flow fuel. 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 at an appropriate ratio and provide the mixed mixer to the mixer intake line 24.

The mixer intake line 24 may provide a 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 mixer supplied to the intake line 20 and provide it to the engine 14.

The intake compressor 300 can 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 the exhaust gas, or may be rotated by the exhaust gas discharged to the exhaust line 30 to compress the mixer supplied to the intake line 20. Hereinafter, the intake compressor 300 will be described on the premise that the exhaust gas is operated as a power source. When the intake compressor 300 is operated by the exhaust gas, energy is saved because there is no need to supply additional energy to the intake compressor 300.

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

On the other hand, in the case of using the intake compressor 300, the temperature and pressure of the mixer flowing to the engine 14 becomes very high, there is a fear of explosion when such a high temperature and high pressure mixer is leaked to the outside, the engine 14 As the amount of fuel is relatively small at the time of inflow, output may be lowered.

Therefore, the cogeneration unit 10 of the present invention may further include a cooler 50 for cooling the mixer compressed by the intake compressor 300. The cooler 50 may cool the mixer compressed by the intake compressor 300 and provide it to the engine 14.

The cooler 50 may cool the mixer compressed by the intake compressor 300 and provide it to the engine 14.

The cooler 50 includes a cooler radiator 52 for exchanging heat between the outside air and the refrigerant, a cooler heat exchanger 51 for exchanging the refrigerant and the refrigerant flowing through the mixer intake line 24, and a refrigerant therein, and the cooler heat exchanger. It may include a cooler circulation passage 53 for circulating between the unit 51 and the cooler radiator 52.

When the mixer compressed by the cooler 50 is cooled, the temperature of the mixer is lowered and the volume is reduced, thereby increasing the amount of fuel supplied to the engine 14, improving the power generation efficiency, and exploding when the mixer leaks. There is an advantage that can be prevented.

Generator 100, the rotor is connected to the output shaft of the engine 14, when the output shaft rotates to produce power, and through the generated power can be supplied to the power consumption devices such as lighting or home appliances in the 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 heat exchanger 12 accommodates the hot water supply therein, and the hot water supply water circulates between the hot water supply heat exchanger 16 and the hot water supply tank 12. It may include a water circulation passage 18 connecting the group 16 and the hot water tank 12. The hot water supply unit 60 may further include a temperature controller for controlling the temperature of the hot water tank 12.

The hot water supply heat exchanger 16 can transfer the heat generated by the engine 14 to the hot water supply unit 60. Specifically, the heat medium on the heat medium circulation passage 40 can recover heat generated by the engine 14 and transfer it to the hot water heat exchanger 16. At this time, the hot water supply heat exchanger 16 transfers the heat generated by 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 the electric power during its operation, and is preferably operated when the hot water load from the hot water supply unit 60 and the electric power load of the power consuming device are together. However, even if only one of the power load and the hot water load is operated, when there is a power load and no hot water load, in order to protect the engine 14, it is necessary to recover heat from the engine 14 and radiate it to the outside. There is.

Therefore, the cogeneration unit 10 of the present invention may further include a radiator 320 for radiating heat generated from the engine. At this time, the radiator 320 may include heat dissipation passages 19a and 19b through which the heat medium passes, hereinafter referred to as 19 when there is no need for division.

The radiator 320 may be cooled by water with a cooling water such as water or the like, and may be cooled by air, or may be cooled by air. To this end, the radiator 320 may further include a heat radiating fan.

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

The heat medium on the heat medium circulation channel 40 can recover heat generated by the engine 14 and transfer it to the hot water supply unit 60. For this purpose, the heat medium circulation flow path 40 includes the heat medium supply flow path 11, the bypass flow path 17, the hot water supply flow paths 15a and 15b (15 if no need for division), and the heat medium recovery flow path 26. And a heat dissipation passage 19.

On the other hand, the cogeneration unit 10 of the present invention can also recover heat of the engine 14, that is, the heat of the engine body, while the heat 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 heat medium passes through the engine 14 and the engine cooling heat exchanger. In addition, below, the heat medium may mean cooling water.

After the heat medium passes through the engine 14, the heat medium circulation flow path 40 passes through the bypass flow path 17 and / or the hot water supply flow path 15 to the engine 14 through the heat medium supply flow path 11. It may be formed to be circulated.

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

In more detail, the heat medium supply flow path 11 is arrange | positioned at the one end of the engine 14, and can supply the heat which the engine 14 generate | occur | produced. The hot water flow passage 15 is branched at the first branch point of the heat medium supply flow passage 11, and can transfer heat generated by 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 passage 19 may branch from the second branch point of the hot water flow passage 15 to transfer heat generated by the engine 14 to the radiator 320.

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

The heat dissipation flow path 19 discharges the 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 flow path 15a with the heat dissipator 320, and the heat medium sucked into the heat dissipator 320. The heat dissipation discharge passage 19b may be included.

The heat dissipation suction passage 19a is connected to the second branch point, and can guide the heat medium on the first hot water flow passage 15a to the radiator 320. The heat dissipation discharge passage 19b may connect the radiator 320 and the bypass passage 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 to allow the heat medium on the heat medium supply flow path 40 to selectively flow into either the bypass flow path 17 or the hot water supply flow path 19, or the heat medium is bypassed. The flow of the heat medium can be adjusted to flow simultaneously into the flow path 17 and the hot water supply flow path 19.

The second flow regulator 25b is disposed at the second branch point to allow the heat medium on the hot water flow passage 19 to selectively flow into either the heat dissipation flow passage 19 or the hot water flow passage 15, or the heat medium flows through the heat dissipation flow passage 19. ) And the flow of the heat medium can be adjusted to flow simultaneously into the hot water supply passage (15).

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

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

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

The heat medium recovery flow path 26 may be connected to a lamination point where the bypass flow path 17, the heat dissipation discharge flow path 19b, and the second hot water supply flow path 15b are laminated, and may extend to the engine 14.

In FIG. 1, although the positions of the lamination points of the heat dissipation discharge flow path 19b and the bypass flow path 17 and the lamination points of the second hot water supply flow path 15b and the bypass flow path 17 are shown to be different, The heat medium on the discharge flow path 19b, the heat medium on the bypass flow path 17, and the heat medium on the second hot water flow path 15b are applied to the engine 14 through the heat medium recovery flow path 26, so that the heat dissipation discharge flow path 19b is provided. The mating points of the bypass flow passage 17 and the second hot water flow passage 15b may be disposed at the same position.

The first flow regulator 25a may include a three-way valve to allow the heat medium on the heat medium supply flow path 11 to flow into the bypass flow path 17 and / or the first hot water flow path 15a according to the operation mode. .

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

If the flow regulator 25 is composed of a three-way valve, the manufacturing cost can be reduced.

On the other hand, the cogeneration system 1 of the present invention may include a sensing unit 270 for sensing the temperature of the heat medium or water supply, or the heat medium flow rate on the heat medium circulation passage 40.

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

The 1st temperature sensor 27 is arrange | positioned in the heat medium circulation flow path 40, and can measure the heat medium temperature on the heat medium circulation flow path 40. FIG. More preferably, the 1st temperature sensor 27 is arrange | positioned at the heat medium collect | recovery flow path 26, and can measure the temperature of the heat medium collect | recovered by the engine 14. As shown in FIG.

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

The third temperature sensor 29 may be disposed on the water circulation passage 18. More preferably, the 3rd temperature sensor 29 is arrange | positioned at the water outlet of the hot water supply tank 12, and can measure the temperature of the water discharged | emitted from the hot water supply tank 12. FIG.

The control unit 240 may calculate the amount of heat of hot water supply of the hot water tank 12 through the second temperature sensor 28 and the third temperature sensor 29. For example, the control unit 240 supplies the hot water in the hot water tank 12 through a calorie formula based on the water inlet temperature of the water received in the hot water tank 12 and the water temperature of the water discharged from the hot water tank 12. Calorie can be calculated.

Meanwhile, the controller 240 may set an operation mode according to the amount of hot water supply, and the amount of hot water supply may be derived through the temperature of the heat medium on the heat medium circulation channel 40 detected 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 calorific value of the hot water supply of the hot water tank 12 is calculated, and at this time, the first temperature sensor 27 is detected. By measuring the temperature it is possible to database the relationship between the heat medium temperature detected by the first temperature sensor 27 and the hot water supply calorific value. The controller 240 may calculate the hot water supply amount of heat 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 flow path 26, the bypass flow path 17, the heat dissipation flow path 19, and the hot water supply flow path 15 are provided. The manufacturing cost is reduced compared to the case where the temperature sensors are arranged in the respective chambers. Moreover, since the 1st temperature sensor 27 is arrange | positioned on the heat medium collect | recovery flow path 26, the temperature of the whole heat medium flowing on the heat medium circulation flow path 40 can be measured. In addition, the cogeneration system 1 measures the temperature of the entire heating medium, so that the temperature change due to the rapid flow rate change is small, thereby providing the accuracy and reliability of the hot water supply calorie measurement.

The detection unit 270 may include a flow rate sensor 28 that measures the flow rate of the heat medium. The flow rate sensor 28 is arrange | positioned on the heat medium circulation flow path 40, and can measure the heat medium flow volume on the heat medium circulation flow path 40. FIG. The control unit 240 controls the opening and closing degree of the flow regulator 25 based on the flow rate detected by the flow sensor 28, so that more precise flow rate control is possible.

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 hot water supply. For example, the operation mode may be divided into a hot water supply unused mode in which the hot water supply amount of heat is minimum and a hot water use mode in which the hot water supply amount of heat is greater than the minimum value. The hot water supply mode may be divided into a first operation mode, a second operation mode for outputting a hot water supply amount greater than the first operation mode, and a third operation mode for outputting a hot water amount value greater than the second operation mode. .

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

At least one pump 33 may be provided 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 the first temperature sensor 27 may be disposed at the heat medium inlet of the pump 33.

On the other hand, 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 and exchanging exhaust gas heat discharged from the engine 14.

The exhaust gas heat exchanger 13 may heat exchange between the exhaust gas passing through the exhaust line 30 and the heat medium circulating through the heat medium circulation flow path 40. The exhaust gas heat exchanger 13 may transfer the exhaust gas thermal energy of the exhaust line 30 to the heat medium circulation passage 40. Accordingly, the cogeneration system 1 of the present invention recovers not only engine heat but also exhaust gas heat, and supplies the heat to the heat demand, thereby maximizing energy efficiency.

3A to 3C and FIG. 4 are diagrams showing changes in the flow rate of the heat medium according to the operation mode change of the cogeneration unit of FIG. 1.

More specifically, FIGS. 3A to 3C are diagrams showing the flow rate change of the heat medium of the cogeneration unit 10 in the hot water supply mode, and FIG. 4 is a diagram showing the flow rate change of the heat medium in the hot water non-use mode.

Referring to the drawings, in FIG. 3A, the controller 240 controls the heat medium on the heat medium circulation passage 40 to be the first heat medium temperature by bypassing the first heat medium flow rate to the engine in the first hot water supply mode. Can be.

Specifically, the control unit 240 adjusts the first flow regulator 25a in the first hot water supply mode, so that the heat medium on the heat medium supply flow path 11 passes through the bypass flow path 17 and the first hot water flow path 15a. It 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 into the bypass flow path 17, and to control the first hot water flow rate to flow into the first hot water flow path 15a. can do. For example, the control part 240 controls 30% of the total heat medium flow volume on the heat medium supply flow path 11 to flow to a bypass flow path 17, and flows the remaining 70% to the 1st hot water supply flow path 15a. Can be controlled.

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

The heat medium on the second hot water flow path 15b and the heat medium on the bypass flow path 17 may be laminated and flow into the heat medium recovery flow path 26. In this case, the heat medium temperature on the heat medium recovery passage 26 may be a first heat medium temperature.

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

In FIG. 3B, the control unit 240 bypasses the second heat medium flow rate less 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 lower than the first heat medium temperature. It can be controlled so as to become a low second heat medium temperature.

Specifically, in the second hot water supply mode, the controller 240 controls the first flow regulator 25 to control the flow rate of the second heat medium smaller than the first heat medium flow rate to the bypass flow path 17. The second hot water flow rate more than the first hot water flow rate can be controlled to flow in the first hot water flow passage 15a. For example, the control part 240 controls 15% of the total heat medium flow volume on the heat medium supply flow path 11 to flow to a bypass flow path 17, and flows the remaining 85% to the 1st hot water supply flow path 15a. Can be controlled.

The control unit 240 can selectively open and close the second flow regulator 25b to control the entire heating medium (second hot water supply flow rate) on the first hot water flow passage 15a to flow in the second hot water flow passage 15b. .

The heat medium on the second hot water flow path 15b and the heat medium on the bypass flow path 17 may be laminated and flow into the heat medium recovery flow path 26. At this time, since the amount of the heat medium passing through the hot water supply heat exchanger 16 in the second hot water supply mode is greater than the amount of the heat medium passing through the hot water heat exchanger 16 in the first hot water supply mode, the heat medium recovery flow path 26 The heat medium temperature of the phase may be a second heat medium temperature less than the first heat medium temperature.

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

In FIG. 3C, in the third hot water supply mode, the controller 240 sends all of the heat medium on the heat medium supply flow path 11 to the hot water heat exchanger 16 so that the heat medium on the heat medium circulation flow path 40 becomes the third heat medium temperature. Can be controlled. The third hot water supply mode may be referred to as a maximum hot water supply mode.

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

That is, the third heat medium flow rate may be the total flow rate flowing through the heat medium supply flow path 11. For example, the control part 240 can control so that the total flow volume (100%) which flows through the heat medium supply flow path 11 may flow into the 1st hot water supply flow path 15a.

The control unit 240 selectively opens and closes the second flow regulator 25b to control the flow of the entire heat medium flow rate (third hot water flow rate) on the first hot water flow passage 15a to flow into the second hot water flow passage 15b. have.

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

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

On the other hand, in the above-described 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 predetermined heat medium temperature. It is not bound to the flow rate ratio, such as 15% and 0%. That is, the cogeneration unit 10 of the present invention can adjust the flow rate of the heat medium bypassed to the engine 14 so that the heat medium temperature on the heat medium recovery flow path 26 becomes a predetermined heat medium temperature according to the amount of hot water supply. .

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 The flow rate of the heat medium to be bypassed quickly can be changed quickly, and the hot water mode can be quickly changed.

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

In FIG. 4, the control unit 240 controls the flow regulator 25 in the hot water supply unused mode so that the heat medium on the heat medium circulation passage 40 passes simultaneously through the radiator 320 and the hot water heat exchanger 16. can do.

Specifically, in the hot water supply unused mode, the control unit 240 controls the first flow regulator 25a to control the fourth heat medium flow rate to flow into the bypass flow path 17, and the fourth hot water flow rate flows the first hot water supply. It can be controlled to flow in the flow path 15a. For example, the control part 240 controls 30% of the total heat medium flow volume on the heat medium supply flow path 11 to flow to a bypass flow path 17, and flows the remaining 70% to the 1st hot water supply flow path 15a. Can be controlled.

In the hot water supply unused mode, the controller 240 may control the second flow regulator 25b so that the heat medium on the heat medium supply flow passage 11 flows simultaneously into the heat dissipation flow passage 19 and the hot water flow passage 15. have. For example, the control part 240 controls 80% of all the heat medium flow rates on the 1st hot water flow channel 15a to flow to the heat dissipation flow path 19, and flows the remaining 20% to the 2nd hot water flow channel 15a. Can be controlled.

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

Since the cogeneration unit 10 of the present invention controls the minimum hot water supply amount to be supplied to the hot water supply unit 60 by adjusting the second flow controller 25b in the hot water non-use mode, the hot water generation mode is changed from the hot water non-use mode to the hot water mode. At the time, the target hot water calorie can be reached quickly.

FIG. 5A is a diagram illustrating a change in hot water supply quantity according to the operation mode change of the cogeneration unit of FIG. 1, and FIG. 5B is a heat medium temperature change and a hot water supply according to an operation mode change of the cogeneration unit of FIG. 1. It is a figure which shows a temperature change.

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

In addition, since the hot water heat exchanger 16 transfers heat energy to the hot water supply unit 60, the hot water heat amount may increase as the engine speed increases. On the other hand, the hot water supply calorie can converge to the constant hot water supply calorie as the engine speed increases.

The amount of hot water that is converged may be referred to as the maximum amount of hot water that can be output in the operation mode, and the operation mode may be set based on the maximum amount of hot water. Hereinafter, for the convenience of explanation, the maximum hot water amount and the hot water amount may be used in combination. Likewise, in Fig. 5B, the minimum heat medium temperature and the heat medium temperature may be used interchangeably. In addition, in FIG. 5B, the maximum hot water temperature and the hot water temperature may be used in combination.

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

Specifically, the control unit 240 may adjust the flow regulator 25 so that the temperature of the heat medium on the heat medium circulation flow path 40 becomes the first heat medium temperature T2 corresponding to the first hot water supply heat amount H2.

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

The hot water supply heat exchanger 16 may heat exchange between the first hot water flow rate and the water circulation flow path 18. At this time, the hot water supply temperature that the hot water supply tank 12 withdraws may be the first hot water temperature (T5).

In the second hot water supply mode (mode 2), the controller 240 may control the flow regulator 25 to output the second hot water supply H3 greater than the first hot water supply H2. have.

Specifically, the control unit 240 may adjust the flow regulator 25 so that the heat medium temperature on the heat medium circulation flow path 40 is the second heat medium temperature T1 corresponding to the second hot water supply calorie H3. Since the 2nd hot water supply heat H3 is larger than the 1st hot water supply heat amount H2, it is preferable that 2nd heat medium temperature T1 is smaller than 1st heat medium temperature T1.

To this end, the control unit 240 adjusts the first flow regulator 25a so that the second flow medium flow rate smaller than the first heat medium flow rate among all the heat medium flow rates on the heat medium supply flow path 15a is obtained. It controls so that it may flow in, and it may control so that the 2nd hot water flow volume which is larger than a 1st hot water flow volume may flow in the 2nd hot water flow channel 15b by adjusting the 2nd flow regulator 25b.

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

6 is a diagram referred to for 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, the cogeneration system 1 may gradually increase the amount of hot water supply 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 amount increases from H4 to H5, the hot water flow rate flowing through the hot water flow passage 15 may increase. Also, as the hot water supply flow rate is increased, the heat medium flow rate bypassed to the engine 14 can be reduced.

Therefore, the heat medium temperature sensed in the heat medium circulation flow path 26 can be reduced from T8 to T7 as the hot water calorific value increases.

On the other hand, as the heat medium temperature decreases, friction between the cylinders inside the engine 14 and engine oil, etc. 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 hot water supply calorie is increased, the heat medium temperature is gradually reduced, and thus the power generation efficiency can be reduced from P1 to P2.

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

In the first hot water mode, the heat medium temperature on the heat medium recovery passage 26 may be a first heat medium temperature. In the second hot water mode, the heat medium temperature on the heat medium recovery flow path 26 may be a second heat medium temperature smaller than the first heat medium temperature.

Since the first heat medium temperature is greater than the second heat medium temperature, 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 mode.

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

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

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

That is, the cogeneration system 1 of the present invention can increase power generation efficiency while preventing overheating of the engine 14 by applying a heat medium to the radiator 320 when there is no user's demand for hot water. In addition, when the user demands hot water, the heat medium is applied to the hot water supply heat exchanger 16, so that the amount of hot water supply heat can be increased even if the power generation efficiency is lowered.

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

FIG. 8 is a flowchart showing a method of operating a cogeneration unit according to an embodiment of the present invention, and FIG. 9 is a flowchart showing a method of checking a stabilized state 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 an operation mode (S810).

The operation mode may be divided into a hot water supply unused mode in which the hot water heating amount is minimum and a hot water supply mode in which the hot water heating amount is larger than the minimum value. The hot water supply mode may be divided into a first operation mode, a second operation mode for outputting a greater amount of hot water than the first operation mode, and a third operation mode for outputting a greater amount of hot water than the second operation mode.

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

The controller 240 adjusts the first flow regulator 25a and the second flow regulator 25b when the checked operation mode is the hot water non-use mode, so that the heat medium on the heat medium supply flow path is the bypass flow path 17, It can control so that it may flow in the hot water supply flow path 15 and the heat dissipation flow path 19.

If the checked operation mode is the hot water mode, the controller 240 may perform a system steady state test (S850).

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

The controller 240 may perform a suction pressure fluctuation test (S930). To this end, the cogeneration unit 10 may further include a map (Manifold Absolute Pressure (MAP)) sensor on the intake manifold 14a of the engine 14.

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

The controller 240 may perform a heat medium temperature test (S950). The controller 240 may calculate that the heat medium temperature is normal when the heat medium temperature measured by the heat medium recovery flow path 26 is equal to or higher than a predetermined temperature.

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

The controller 240 may calculate that the heat medium temperature is normal when the heat medium temperature measured by the temperature sensor 27 is 70 degrees or more when the first hot water mode setting command is received in the hot water non-use mode.

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

On the other hand, if any one of the steps of S910 to S970 does not satisfy the predetermined condition, the controller 240 may output the error without entering the flow control step.

Since the cogeneration system 1 of the present invention performs a check of the stabilization state before performing the hot water supply mode, there is an advantage in that the stability of the system can be improved and the hot water supply can be stably supplied.

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

The control part 240 adjusts the 1st flow regulator 25a according to a hot water supply mode, and flows the heat medium on the heat medium supply flow path 15a to the bypass flow path 17 and / or the 1st hot water flow path 15a. Can be controlled. Moreover, the control part 240 can open and close the 2nd flow regulator 25b selectively, and can control the heat medium on the heat medium supply flow path 15a to flow in the 2nd hot water supply flow path 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 supply heat exchanger 16 is variable, so that the amount of hot water supply heat can be varied.

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

Likewise, although the operations are depicted in the drawings in a specific order, it should not be understood that such operations must be performed in the specific order or sequential order shown in order to obtain desirable results, or that all illustrated operations must be performed. . In certain cases, multitasking and parallel processing may be advantageous.

In addition, although the preferred embodiment of the present invention has been shown and described above, the present invention is not limited to the specific embodiments described above, but the technical field to which the invention belongs without departing from the spirit of the invention claimed in the claims. Of course, various modifications can be made by those skilled in the art, and these modifications should not be individually understood from the technical spirit or the prospect of the present invention.

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

Claims (11)

An engine for driving a generator and generating heat;
A heat medium supply flow path disposed at one end of the engine and heated by heat generated in the engine to flow the heat medium discharged from the engine;
A heat medium recovery flow path disposed at the other end of the engine such that the heat medium discharged from the engine flows into the engine;
A radiator for radiating heat generated by the engine through the heat medium;
Hot water heat exchanger for transferring the heat generated from the engine through the heat medium to the hot water supply unit;
A first flow regulator connected to the heat medium supply passage and discharging the heat medium flowing through the heat medium supply passage to at least one of the heat medium recovery passage, the radiator, and the hot water supply heat exchanger;
A bypass flow path connecting the first flow regulator and the heat medium recovery flow path;
Of the heat medium flowing into the first flow regulator, the remaining heat medium except for the heat medium discharged through the bypass flow path is introduced, and the heat medium flowing from the first flow regulator is discharged to at least one of the radiator and the hot water supply heat exchanger. A second flow regulator;
A hot water flow passage configured to transfer at least a portion of the heat medium discharged from the second flow controller to the hot water supply heat exchanger, and to transfer the heat medium discharged from the hot water heat exchanger to the heat medium recovery flow path;
A heat dissipation flow path which transfers the remaining heat medium except the heat medium transferred to the hot water heat exchanger to the radiator among the heat medium discharged from the second flow regulator, and transfers the heat medium discharged from the radiator to the heat medium recovery flow path; And
And a control unit for controlling the first flow regulator and the second flow regulator based on an operation mode according to a hot water supply quantity. delete delete delete The method of claim 1,
The control unit,
In hot water nonuse mode,
At least a part of the heat medium introduced from the heat medium supply passage is discharged to the bypass flow path, and the first flow regulator is controlled to discharge the remaining heat medium except the heat medium discharged to the bypass flow path to the second flow regulator. ,
At least a portion of the heat medium introduced from the first flow regulator is discharged to the radiator, and the heat flow cogeneration is controlled so that the remaining heat medium except the heat medium discharged to the radiator is discharged to the hot water supply heat exchanger. Power generation unit. The method of claim 1,
The control unit,
In the first hot water mode, the temperature of the heat medium flowing through the heat medium recovery flow path becomes the first heat medium temperature,
Controlling the first flow regulator to discharge the heat medium at the first flow rate from the heat medium supplied from the heat medium supply flow path to the bypass flow path, and to discharge the remainder except the heat medium at the first flow rate to the second flow regulator. Cogeneration unit characterized in that. The method of claim 6,
The control unit,
In the second hot water mode, the temperature of the heat medium flowing through the heat medium recovery flow path is a second heat medium temperature lower than the first heat medium temperature,
In the heat medium flowing from the heat medium supply flow path, the heat medium having a second flow rate less than the first flow rate is discharged to the bypass flow path, and the remaining fluid except the heat medium at the second flow rate is discharged to the second flow regulator. Cogeneration unit characterized in that for controlling the flow regulator. The method of claim 1,
The control unit,
Cogeneration unit characterized in that for performing the stabilization state check, based on the rotation speed fluctuation range, the suction pressure change, the temperature of the heat medium and the operation mode holding time before the operation mode. The method of claim 1,
A heat medium pump for pumping the heat medium such that the heat medium flowing through the heat medium recovery passage flows into the engine; And
And an exhaust gas heat exchanger disposed in the heat medium recovery flow path and performing heat exchange between the exhaust gas discharged from the engine and the heat medium flowing through the heat medium recovery flow path. The method of claim 1,
And a temperature sensor disposed in the heat medium recovery flow path and measuring a temperature of the heat medium flowing through the heat medium recovery flow path. A cogeneration unit that generates power and heat and supplies the power and heat; And
It includes a hot water supply unit for receiving the heat generated from the cogeneration unit,
The cogeneration unit,
An engine for driving a generator and generating heat;
A heat medium supply flow path disposed at one end of the engine and heated by heat generated in the engine to flow the heat medium discharged from the engine;
A heat medium recovery flow path disposed at the other end of the engine such that the heat medium discharged from the engine flows into the engine;
A radiator for radiating heat generated by the engine through the heat medium;
Hot water heat exchanger for transferring the heat generated from the engine through the heat medium to the hot water supply unit;
A first flow regulator connected to the heat medium supply passage and discharging the heat medium flowing through the heat medium supply passage to at least one of the heat medium recovery passage, the radiator, and the hot water supply heat exchanger;
A bypass flow path connecting the first flow regulator and the heat medium recovery flow path;
Of the heat medium flowing into the first flow regulator, the remaining heat medium except for the heat medium discharged through the bypass flow path is introduced, and the heat medium flowing from the first flow regulator is discharged to at least one of the radiator and the hot water supply heat exchanger. A second flow regulator;
A hot water flow passage configured to transfer at least a portion of the heat medium discharged from the second flow controller to the hot water supply heat exchanger, and to transfer the heat medium discharged from the hot water heat exchanger to the heat medium recovery flow path;
A heat dissipation flow path which transfers the remaining heat medium except the heat medium transferred to the hot water heat exchanger to the radiator among the heat medium discharged from the second flow controller, and transfers the heat medium discharged from the radiator to the heat medium recovery flow path; And
And a control unit for controlling the first flow regulator and the second flow regulator based on an operation mode according to a hot water supply quantity.

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