KR100712854B1 - Cogeneration System and Control Method - Google Patents

Abstract

The cogeneration system and the control method thereof according to the present invention include a heat medium replenishment mode function for causing the heat medium of the waste heat recovery device to be cycled for a predetermined time so that the heat medium of the waste heat recovery device may be degassed when the heat medium of the waste heat recovery device is replenished. As a result, the air in the waste heat recovery device can be easily removed.

Cogeneration Systems, Engines, Generators, Power Generation, Commercial Power, Power Changers, Air Conditioners

Description

Cogeneration system and control method {Electric generation air condition system and the Control method for the Same}

1 is a configuration diagram of a cogeneration system according to the prior art,

2 is a configuration diagram when the cogeneration system according to the present invention is a power generation output, the air conditioner is in the cooling operation mode,

3 is a configuration diagram when the cogeneration system according to the present invention is a power generation output, the air conditioner is the outdoor high temperature heating operation mode,

4 is a configuration diagram when the cogeneration system according to the present invention is a power generation output, the air conditioner is the outdoor low temperature heating operation mode,

5 is a configuration when the cogeneration system according to the present invention is a commercial power output, the air conditioner in the cooling operation mode,

6 is a commercial power output of the cogeneration system according to the present invention, the configuration when the air conditioner in the heating operation mode,

7 is a heat medium supplement mode block diagram of a cogeneration system according to the present invention,

8 is a schematic view in the heat medium supplement mode according to the first embodiment of the cogeneration system according to the present invention,

9 is a flow chart of the heat medium supplement mode according to the second embodiment of the cogeneration system according to the present invention,

10 is a schematic view in the heat medium supplement mode according to the second embodiment of the cogeneration system according to the present invention,

11 is a flow chart of the heat medium supplement mode according to the second embodiment of the cogeneration system according to the present invention.

<Explanation of symbols on main parts of the drawings>

50: generator 51: power switching device

52: drive source 55: engine cooling device

60: waste heat recovery device 70: compressor

73: four-way valve 74: indoor heat exchanger

75: outdoor heat exchanger 76: indoor expansion valve

77: outdoor expansion valve 80: waste heat supply heat exchanger

85: waste heat radiator 94: three-way

100: damper for heating 104: damper for cooling

142: heat medium supplement mode switch

The present invention relates to a cogeneration system and a control method thereof, and more particularly, to a cogeneration system including a heat medium replenishment mode function for causing a heat medium of the waste heat recovery device to be circulated for a predetermined time for degassing after refilling the heat medium of the waste heat recovery device. It is about a method.

Cogeneration systems, commonly referred to as cogeneration systems, are systems that produce power and heat simultaneously from a single energy source.

The cogeneration system can recover waste heat of exhaust gas or cooling water generated by power generation by driving a gas engine or turbine, and can increase the overall thermal efficiency by 70-80%. In particular, it is a high-efficiency energy utilization method that utilizes the waste heat recovered in particular for heating, cooling, and hot water supply.

1 is a block diagram of a cogeneration system according to the prior art.

In the conventional cogeneration system, as shown in FIG. 1, a generator 2 for generating electric power and a driving source 10 such as a gas engine for driving heat of the generator 2 and generating heat, hereinafter referred to as a 'gas engine' ), A waste heat recovery apparatus 20 for recovering waste heat generated by the gas engine 10, and a heat demand unit 30 for utilizing waste heat of the waste heat recovery apparatus 20 to supply hot water or the like to radiate heat to the outside. It is configured to include).

The generated electric power generated by the generator 2 is supplied to a power consuming device such as various lighting fixtures or an air conditioner 4 in the home.

The generator 2 and the gas engine 10 are installed in an engine room E of a chassis (not shown) formed separately from the heat demand 30.

The air conditioner 4 includes an indoor unit 3 and an outdoor unit 5.

The waste heat recovery apparatus 20 includes an exhaust gas heat exchanger 22 which takes heat of exhaust gas discharged from the gas engine 10, and a cooling water heat exchanger that takes heat of cooling water cooling the gas engine 10 ( 24).

The exhaust gas heat exchanger 22 is connected to the heat demand 30 and the first heat supply line 23, and the waste heat taken from the exhaust gas of the gas engine 10 is the first heat supply line 23. It is transmitted to the heat demand 30 through.

The cooling water heat exchanger 24 is connected to the heat demand 30 and the second heat supply line 25, and heat taken from the cooling water cooling the gas engine 10 is transferred to the second heat supply line 25. It is transmitted to the heat demand 30 through.

However, in the cogeneration system according to the related art configured as described above, since the heat medium of the waste heat recovery apparatus 20 is partially evaporated in the process of recovering the waste heat of the engine 10, the waste heat recovery apparatus 20 In this case, air flows into the first and second heat supply lines 23 and 25 to reduce the flow rate of the heat medium of the waste heat recovery device 20, and it is difficult to control the heat quantity of the recovered waste heat. have.

In addition, the cogeneration system according to the prior art as described above, because the waste heat of the gas engine 10 is not used in the air conditioner 4 is used only in hot water supply, etc., there is a problem that the efficiency is not maximized. .

The present invention has been made to solve the above problems of the prior art, and after refilling the heat medium of the waste heat recovery apparatus, the heat medium of the waste heat recovery apparatus is circulated for a predetermined time while the driving source for driving the generator is stopped, the waste heat It is an object of the present invention to provide a cogeneration system and a control method thereof in which air in a recovery device is sufficiently drained.

In addition, an object of the present invention is to provide a cogeneration system and a method of controlling the waste heat of the drive source is utilized to increase the heating performance of the air conditioner in the heating operation mode of the air conditioner to maximize its efficiency.

Cogeneration system according to the present invention for solving the above problems is a power consumer; A generator for supplying generated power to the power consumer; A drive source for generating the generator; A waste heat recovery apparatus for recovering waste heat of the drive source; An expansion tank connected to the waste heat recovery device; When the heat medium replenishment of the waste heat recovery device is characterized in that it comprises a heat medium replenishment mode device for degassing while the heat medium of the waste heat recovery device is circulated.

The heat medium supplement mode device may include a heat medium supplement mode switch for generating a heat medium supplement mode request signal.

The cogeneration system may further include a power switching device for outputting any one of generated power and commercial power of the generator.

The cogeneration system includes: a waste heat supply heat exchanger configured to transfer waste heat recovered by the waste heat recovery device to the air conditioner; A waste heat radiating device for radiating the waste heat recovered by the waste heat recovering device; The three-way valve for distributing the waste heat recovered by the waste heat recovery device to the waste heat supply heat exchanger or waste heat radiating device is further included.

In addition, the cogeneration system according to the present invention for achieving the above object, the heat medium replenishing step of replenishing the heat medium of the waste heat recovery apparatus for recovering the waste heat of the drive source for driving the generator; After the heat medium replenishment, the heat medium in the waste heat recovery device is circulated, characterized in that it comprises a heat medium degassing step to remove the air.

The heating medium replenishing step is characterized in that the drive source is stopped.

The heat medium degassing step may be performed according to whether or not the heat medium degassing mode request signal is input.

The heat medium degassing step is characterized in that it is carried out during a predetermined heat medium degassing time.

In the heat medium degassing step, the heat medium of the waste heat recovery device passes through both the waste heat radiating device and the waste heat supply heat exchanger.

When the generated power of the generator is used during the heat medium degassing step, the driving source, the generator, the waste heat radiator, the ventilation blower, and the air conditioner are controlled in an operating state, and the air conditioner, which is a power consumption device, is stopped. It is characterized by being controlled.

When the commercial power is used during the heat medium degassing step, the driving source, the generator, the waste heat radiator, the ventilation blower, and the air conditioner, which is a power consuming device, are controlled in a stopped state.

Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. 2 to 8.

In the cogeneration system according to the present invention, the cogeneration unit includes a generator (50) for generating power generation, a drive source (52) for driving the generator (50), and waste heat recovery for recovering waste heat of the drive source (52). Device 60 and an air conditioner, which is one of the power consumer devices.

The generator 50 is any one of an alternator and a direct current generator, the rotor is connected to the output shaft of the drive source 60 to produce power when the output shaft rotates.

Power generation device and commercial power (50 ') of the generator 50, the power switching device for switching the power so that any one of the generated power and commercial power (50') of the generator 50 is output to the air conditioner ( 51 may be output to the air conditioner.

The power switching device 51 is a power generation switchgear (GCB) 51a that regulates the generated power output of the generator 50, and a commercial power switchgear (MCB) 51b that controls the output of the commercial power 50 '. It consists of.

The driving source 52 may be implemented as a fuel cell or various devices such as an engine and a turbine that are operated by using a fuel such as gas or oil. ).

The engine 52 is provided with a fuel supply passage 53 through which fuel is supplied to a combustion chamber provided therein, and an exhaust passage 54 through which exhaust gas is exhausted from the combustion chamber.

In addition, the engine 52 may be easily broken when the engine 52 is overheated, its life may be shortened, and the output of the engine may be reduced, and the reliability of the engine 52 may be degraded. The engine cooler 55 is provided to allow the engine 52 to operate within an appropriate temperature range.

The engine cooler 55 includes a coolant circulation flow path 56 for guiding the coolant to circulate between the engine 52 and the coolant heat exchanger 61, which will be described later, among the waste heat recovery device 60, and the coolant circulation flow path. And a coolant pump 57 installed on the pump 56 to pump the coolant.

The waste heat recovery device 60 is connected to the cooling water circulation passage 56 to extract the heat of the cooling water that has become a high temperature after cooling the engine 52 and the exhaust pipe of the engine 52. The first and second exhaust gas heat exchangers 62 and 63 may be connected to the furnace 54 to recover the heat of the exhaust gas exhausted from the engine 52.

In particular, the waste heat recovery device 60 may be provided to selectively recover the waste gas waste heat of the engine 52 according to the operation mode of the air conditioner.

That is, the exhaust gas heat exchanger 62 is provided on the exhaust passage 54 to recover the waste gas waste heat of the engine 52, and the exhaust gas heat exchanger 62 inlet is provided on the exhaust passage 54. A heating damper 100 is provided at the side to open and close the exhaust passage 54.

In addition, a waste heat discharge passage 102 is connected to the exhaust passage 54 so that the exhaust gas waste heat of the engine 52 bypasses the second exhaust gas heat exchanger 63 and is immediately discharged to the outside.

The waste heat dissipation passage 102 is provided with a cooling damper 104 for opening and closing the waste heat dissipation passage 102.

Cooling / heating dampers 100 and 104 provided as described above are operated in an open mode or a closed mode according to the power output through the power switching device 51 and the operation mode of the air conditioner, respectively.

The waste heat recovered by the waste heat recovery device 60 may be supplied to some of the power consumer devices through the waste heat supply heat exchanger 80, which is a heat demand source, or may be radiated in the air through the waste heat radiator 85.

The waste heat supply heat exchanger (80) absorbs the heat recovered in at least one of the cooling water heat exchanger (61) and the first and second exhaust gas heat exchangers (62, 63), and the cooling water heat exchanger (61). And the first and second exhaust gas heat exchangers 62 and 63 and a waste heat recovery passage 64 for guiding a heat medium (for example, using an antifreeze) for waste heat recovery.

That is, the waste heat recovery passage (64) is a heat medium in the waste heat recovery passage (64), wherein the cooling water heat exchanger (61), the second exhaust gas heat exchanger (63), the first exhaust gas heat exchanger (62), and the Waste heat supply heat exchanger 80 may be provided to circulate in turn.

The waste heat recovery passage 64 is provided with a heat medium circulation pump 65 which performs a pumping function so that the heat medium in the waste heat recovery passage 64 can be circulated.

The heat medium circulation pump 65 may be driven by receiving generated power or commercial power of the generator 50 through the power conversion device 51, or may be driven by being supplied with commercial power connected separately.

In addition, the waste heat recovery passage (64) is connected to an expansion tank (66) for discharging gas in the waste heat recovery passage (64) to an inlet side of the heat medium circulation pump (65).

The waste heat dissipation device 85 includes a heat dissipation heat exchanger 86 for discharging waste heat recovered from the cooling water heat exchanger 61, the first and second exhaust gas heat exchangers 62, 63, and the waste heat. The waste heat dissipation passage 87 is connected to the recovery passage 64 to guide the heat medium in the waste heat recovery passage 64 to the heat dissipation heat exchanger 68.

In addition, the waste heat radiating device 85 includes a waste heat radiating blower 88 for forcibly blowing outside air to the heat radiating heat exchanger 86 in order to maximize heat radiation.

The three-way side 94 for switching the flow of the heat medium is installed at any one of the two points of the junction where the waste heat radiating passage 87 and the waste heat recovery passage 64 are interconnected.

The air conditioner may be composed of one outdoor unit (Oa) and one indoor unit (Ia), may be composed of one outdoor unit (Oa) and a plurality of indoor units (Ia), a plurality of outdoor units (Oa) It is also possible to be composed of a plurality of indoor unit (Ia). Hereinafter, the air conditioner according to the present embodiment will be described as being limited to a plurality of outdoor units Oa and a plurality of indoor units Ia.

Each outdoor unit (Oa) is provided with a compressor 70, a four-way valve 73, an outdoor heat exchanger 75, an outdoor expansion valve 77 which is a drive unit for circulating the refrigerant of the air conditioner.

The compressor 70 may be composed of one or more than two plural to each outdoor unit Oa. Hereinafter, only two compressors 70 are configured for each outdoor unit Oa.

The two compressors 70 installed in the respective outdoor units Oa are connected through a common accumulator 78 installed at a suction side on which a refrigerant, which is a heat medium of the air conditioner, is sucked.

Each indoor unit Ia is provided with the indoor heat exchanger 74 and the indoor expansion valve 76.

The air conditioner and the waste heat supply heat exchanger 80 configured as described above are connected through a refrigerant circulation passage 79 so that refrigerant for cooling / heating action of the air conditioner can be circulated.

A first opening / closing valve 81 which is a valve for heating operation so that the refrigerant flows into the waste heat supply heat exchanger 80 or is blocked at the inlet side of the waste heat supply heat exchanger 80 in the refrigerant circulation passage 79. Is provided.

In addition, the refrigerant circulation passage 79 includes a first check valve 91 at the outlet side of the waste heat supply heat exchanger 80 to block the refrigerant from flowing back to the waste heat supply heat exchanger 80.

In addition, a waste heat supply heat exchanger bypass connecting the inlet side and the outlet side of the waste heat supply heat exchanger 80 to allow the refrigerant to bypass the waste heat supply heat exchanger 80 in the refrigerant circulation passage 79. The flow path 95 is provided.

The waste heat supply heat exchanger bypass passage 95 is provided with a second check valve 92 such that refrigerant flows only from the outlet side of the waste heat supply heat exchanger 80 to the inlet side of the waste heat supply heat exchanger 80. .

In addition, the refrigerant circulation passage 79 includes a second opening / closing valve 82 at one side of the outdoor heat exchanger 75 so that the refrigerant may be introduced into or blocked by the outdoor heat exchanger 75.

In addition, the refrigerant circulation passage 79 includes a third check valve 93 at the other side of the outdoor heat exchanger 75 to block the refrigerant from flowing back from the indoor unit Ia to the outdoor heat exchanger 75. do.

In addition, the refrigerant circulation passage 79 is provided with an outdoor heat exchanger bypass passage 90 connecting one side and the other side of the outdoor heat exchanger 75 so that the refrigerant bypasses the outdoor heat exchanger 75. .

At the inlet side of the outdoor heat exchanger bypass flow path 90, the outdoor expansion valve 77 is provided.

At the outlet side of the outdoor heat exchanger bypass flow path 90, a third open / close valve 83 capable of opening and closing the outdoor heat exchanger bypass flow path 90 is provided.

The outdoor heat exchanger bypass flow path 90 may be connected to the other side of the outdoor heat exchanger 75 through an outdoor heat exchanger connection flow path 96.

The outdoor heat exchanger connection flow path 96 is provided with a fourth open / close valve 84 for opening and closing the outdoor heat exchanger connection flow path 96.

The operation mode of the air conditioner configured as described above includes a cooling operation mode in which the indoor unit Ia supplies cold air, and a heating operation mode in which the indoor unit Ia supplies warm air.

The heating operation mode of the air conditioner is an outdoor high temperature heating operation mode in which the waste heat of the engine 52 is not used through the waste heat supply heat exchanger 80 according to the outdoor temperature at which the outdoor unit Oa is installed. And, through the waste heat supply heat exchanger 80 may be divided into the outdoor low temperature heating operation mode using the waste heat of the engine (52).

The outdoor low temperature heating operation mode is possible to recover the waste heat of the engine 52 when the engine 52 is operated, and thus can be implemented only when the air conditioner receives the generated power of the generator 50.

The cogeneration system configured as described above may be divided into a cogeneration unit for generating the generator 50 and an air conditioner that is the power consuming device.

The cogeneration unit includes a power generation chamber or main unit 110 including the generator 50, the engine 52, the engine cooling device 55, and the waste heat recovery device 60, and the waste heat supply heat exchanger 80. ) And the waste heat radiator 85 may be divided into the sub unit 120 installed.

The main unit 110 is provided with a main unit controller 112 and a ventilation blower 112 for ventilation of the main unit 110.

The sub unit 120 includes a sub unit controller 114 connected to the main unit controller 112.

Meanwhile, in the cogeneration system according to the present invention, at least one of the plurality of indoor units (Ia) is requested to operate for the purpose of supplementing the heat medium of the waste heat recovery apparatus 60 or checking the cogeneration system during the cogeneration system operation. Even if it is further comprises a soft stop device for the soft stop mode for the cogeneration system to stop or pause after the compressor 70 deceleration of the air conditioner. That is, the soft stop mode allows the operation request of the indoor unit Ia to be limited or waited while the cogeneration system is in soft stop.

The soft stop device includes a soft stop switch 130 for generating the soft stop mode request signal or generating a soft stop mote release signal according to an operator's operation of the cogeneration system.

In the cogeneration system according to the present invention, particularly, as shown in FIGS. 7 to 11, when the heat medium of the waste heat recovery device 60 is replenished, the heat medium of the waste heat recovery device 60 includes the waste heat recovery device ( The heat medium supplementation mode device for the heat medium supplement mode for degassing the waste heat supply heat exchanger 80 and the waste heat supply heat exchanger 80 and the waste heat cycle 85 for a predetermined time is further included.

The heat medium supplement mode device includes a heat medium supplement mode switch 142 that generates the heat medium supplement mode request signal.

The heat medium supplement mode switch 142 may be installed in the main unit 110 or the sub unit 120 to be operated by the driver of the cogeneration system.

The signal of the heat medium supplement mode switch 142 is a cogeneration system such as the main unit controller 112 or the sub unit controller 114 such that the cogeneration system can be controlled to the heat medium supplement mode when the heat medium supplement mode request signal is generated. It is preferably delivered to the controller 144.

In addition, the heat medium supplement mode device may include a heat medium supplement mode display 146 to inform the plurality of indoor unit Ia users that the cogeneration system is operating in the heat medium supplement mode.

The heat medium replenishment mode implemented as described above, when the cogeneration system is operated during the operation of the cogeneration system, a safety accident occurs, and the cogeneration system is preferably performed in a soft stop state.

Referring to the control method of the cogeneration system according to the present invention configured as described above, as follows.

When the driving request signal of the air conditioner is input while the engine 52 and the air conditioner are stopped, the first mode is determined according to the operation mode of the air conditioner and whether the generator 50 outputs the generated power. The third check valves 91 to 93, the three-way valve 94, the first to fourth open / close valves 81 to 84, and the cooling / heating dampers 100 and 104 are set.

When the setting step according to the operation mode of the air conditioner is finished, any one of the generated power and the commercial power 50 'of the generator 50 is output to the air conditioner according to whether the generated power of the generator 50 is output. do.

In this case, the power switching device 51 is controlled according to the operation mode of the air conditioner and the load of the air conditioner, or the generated power of the generator 50 preset for the initial operation of the air conditioner or Commercial power 50 'can be output.

When the generated power 50 'of the generator 50 is output to the air conditioner, the engine 52 is operated and the coolant pump 57 and the coolant pump 57 are generated by the generated power of the generator 50. It is preferable that the heat medium circulation pump 65, the waste heat radiation blower 88, and the ventilation blower 112 are driven.

On the other hand, when the commercial power 50 'is output to the air conditioner, the generator 50 and the engine 52, the coolant pump 57, the heat medium circulation pump 65, the waste heat radiating blower ( 88 and the ventilation blower 112 are preferably kept stationary.

When any one of the generated power and the commercial power (50 ') of the generator 50 is output to the air conditioner through the above process, the air conditioner supplies the power output through the power switching device 51 It is operated by receiving and performing cooling / heating function.

At this time, even if at least one of the plurality of indoor units Ia continues to request operation during the operation of the cogeneration system, the cogeneration system is soft for checking the heat medium replenishment mode or the cogeneration system of the waste heat recovery apparatus described later. Can be stopped.

On the other hand, if the plurality of indoor units Ia do not all request driving during the operation of the cogeneration system, that is, when all of the plurality of indoor units Ia are stopped, an operation stop request signal of the air conditioner is input to the air. The outdoor unit Oa of the conditioner is stopped, and the cogeneration system is stopped.

The operation of the cogeneration system configured and operated as described above will be described in detail according to the operation mode of the air conditioner and the power output to the air conditioner.

First, the operation mode of the air conditioner is a cooling operation mode, and when the generation power output is described with reference to FIG.

When the generator 50 is generated by the driving force of the engine 52, the engine 52 is operated at an appropriate temperature by the engine cooling device 55. That is, as the coolant on the coolant circulation passage 56 is pumped by the coolant pump 57, the heat of the engine 52 is absorbed by the coolant, and the coolant that absorbs the heat of the engine 52 is After the heat is released from the coolant heat exchanger 61, the water is circulated back to the engine 52.

The coolant waste heat recovered by the coolant heat exchanger 61 is pumped into the heat medium circulation pump 65 as the heat medium on the waste heat recovery passage 64 is pumped to the coolant heat exchanger 61 and the second exhaust gas heat exchanger. And after passing through the first exhaust gas heat exchanger 63, the waste heat radiator 85 is transferred through the three-way side 94.

The coolant waste heat transferred to the waste heat radiator 85 is radiated to the outside by the waste heat radiator 85.

Part of the exhaust gas waste heat of the engine 52 is immediately discharged to the outside through the waste heat discharge passage 102, and the rest is recovered through the second exhaust gas heat exchanger 63, and together with the cooling water waste heat. The heat is radiated from the waste heat radiator 85.

In the air conditioner, the refrigerant compressed by the compressor 70 passes through the four-way valve 73 to the outdoor heat exchanger 75 to condense, and the refrigerant condensed by the outdoor heat exchanger 75 expands indoors. Passed through the valve 76 to the indoor heat exchanger 74 and evaporated, the refrigerant evaporated in the indoor heat exchanger 74 is circulated back through the four-way valve 73 to the compressor 70.

Then, the refrigerant in the air conditioner absorbs the indoor air heat from the indoor heat exchanger 74 and evaporates, thereby cooling the room.

Next, the operation mode of the air conditioner is the outdoor high temperature heating operation mode, and when described with reference to FIG.

 The engine 52 is operated at an appropriate temperature by the engine cooling device 55, and the generator 50 generates power generated by the driving force of the engine 52.

After the waste water waste heat and part of the waste gas waste heat of the engine 52 are recovered by the waste heat recovery device 60, the waste heat heat dissipation device 85 is radiated, and the waste gas waste heat of the engine 52 is exhausted. A part is discharged directly through the waste heat discharge passageway 102.

The refrigerant compressed by the compressor 70 is transferred to the indoor heat exchanger 74 through the four-way valve 73 to condense, and the refrigerant condensed by the indoor heat exchanger 74 is outdoors with the indoor expansion valve 76. Passed through the expansion valve 77 to the outdoor heat exchanger 75 in order to evaporate, the refrigerant evaporated in the outdoor heat exchanger 75 passes through the waste heat supply heat exchanger 80 and the four-way valve 73 in turn. Afterwards it is circulated to the compressor 70 again.

At this time, since the waste heat recovered by the waste heat recovery device 60 is not transmitted to the waste heat supply heat exchanger 80, the refrigerant evaporated in the outdoor heat exchanger 75 is designed in the refrigerant circulation passage 79. Due to the nature, the waste heat supply heat exchanger 80 passes through, but does not evaporate from the waste heat supply heat exchanger 80.

In such a heating operation mode, since the refrigerant of the air conditioner is condensed by dissipating heat from the indoor heat exchanger 74, the room may be heated.

Next, the air conditioner is the outdoor low-temperature heating operation mode, and when described with reference to Figure 4 when generating power output. At this time, the first opening / closing valve 81 which is the valve for heating operation is set in an on state so that the refrigerant in the refrigerant circulation flow path 79 passes through the waste heat supply heat exchanger 80.

The engine 52 is operated at an appropriate temperature by the engine cooling device 55, and the generator 50 generates power generated by the driving force of the engine 52.

The waste water waste heat of the engine 52 and the waste gas waste heat of the engine 52 are sequentially recovered through the waste heat recovery device 60. At least a part of the waste heat recovered by the waste heat recovery device 60 is transferred to the waste heat supply heat exchanger 80, and the surplus waste heat remaining after being transferred to the waste heat supply heat exchanger 80 passes through the waste heat radiator 85. Heat dissipation through.

In the air conditioner, the refrigerant compressed by the compressor (70) passes through the four-way valve (73) to the indoor heat exchanger (74) to condense, and the refrigerant condensed in the indoor heat exchanger (74) is Passed through the indoor expansion valve 76 and the outdoor expansion valve 77 in order to the waste heat supply heat exchanger 80 and evaporated, the refrigerant evaporated in the waste heat supply heat exchanger 80 through the four-way valve 73. It is circulated to the compressor 70 again.

Then, since the refrigerant of the air conditioner is condensed by dissipating heat from the indoor heat exchanger 74, the room may be heated.

In the outdoor low temperature heating operation mode as described above, since the waste heat supply heat exchanger 80 instead of the outdoor heat exchanger 75 serves as an evaporator, it is possible to always provide a constant heating capacity regardless of the outdoor temperature change. The compressor 70 can be operated without difficulty.

In addition, since the waste heat of the engine 52 is used, power consumption may be minimized when the operating capacity of the compressor 70 is reduced.

Next, when the air conditioner is in the cooling operation mode and is described with reference to FIG. 5 at the time of commercial power output, it is as follows.

At this time, the generator 50, the engine 52, the coolant pump 57, the heat medium circulation pump 65, and the waste heat radiating blower 88 are maintained in a stopped state.

The first opening / closing valve 81, which is the valve for heating operation, is set to an off state so that the refrigerant in the refrigerant circulation flow path 79 does not pass through the waste heat supply heat exchanger 80.

In the air conditioner, the refrigerant compressed by the compressor (70) passes through a four-way valve (73), an outdoor heat exchanger (75), an indoor expansion valve (76), an indoor heat exchanger (74), and a four-way valve (73). After being circulated to the compressor 70, the indoor unit Ia supplies cold air.

Next, the air conditioner is a heating operation mode, and will be described with reference to FIG. 6 when outputting commercial power.

At this time, the generator 50, the engine 52, the coolant pump 57, the heat medium circulation pump 65, and the waste heat radiating blower 88 are maintained in a stopped state.

At this time, the first opening / closing valve 81, which is the valve for heating operation, is set in an on state so that the refrigerant in the refrigerant circulation flow path 79 passes through the waste heat supply heat exchanger 80.

The air conditioner, the refrigerant compressed by the compressor 70, the four-way valve 73 and the indoor heat exchanger 74, the indoor expansion valve 76, outdoor expansion valve 77, outdoor heat exchanger 75, waste heat After passing through the supply heat exchanger 80 and the four-way valve 73 in turn, the indoor unit Ia supplies warm air while being circulated to the compressor 70.

Here, since the waste heat recovered by the waste heat recovery device 60 is not transmitted to the waste heat supply heat exchanger 80, the refrigerant passes through the waste heat supply heat exchanger 80 due to the design characteristics of the refrigerant circulation flow path 79. However, it is not evaporated in the waste heat supply heat exchanger (80).

Hereinafter, the operation of the cogeneration system according to the heat medium replenishment mode of the waste heat recovery apparatus will be described.

8 is a schematic view of the heat medium supplement mode according to the first embodiment of the cogeneration system according to the present invention, Figure 9 is a flow chart of the heat medium supplement mode according to the first embodiment of the cogeneration system according to the present invention.

In the heat medium supplement mode according to the first embodiment of the cogeneration system illustrated in FIGS. 8 and 9, the cogeneration system is a state in which at least the engine 52 of the soft stop or the cogeneration system is stopped. The heat medium of the waste heat recovery apparatus 60 may be replenished to the heat medium circulation passage 64.

At this time, when the cogeneration system is not in the soft stop state, the coolant circulation pump 57, the heat medium circulation pump 65, and the waste heat radiating blower 88 are preferably kept in a stopped state.

And the air conditioner is preferably at least the compressor 70 when the heating operation mode is stopped. For reference, the air conditioner does not pass through the waste heat supply heat exchanger 80 in the cooling operation mode, and thus may be operated by being supplied with commercial power 50 ′ through the power switching device 51. The compressor 70 may be stopped. Hereinafter, the air conditioner in the heat medium replenishing mode will be described as being limited to remain unconditionally regardless of the operation mode.

After the heat medium replenishment step is completed as described above, when the heat medium replenishment mode switch 142 is pressed for a few seconds (for example, 5 seconds) or longer, a heat medium replenishment mode request signal is input to the heat medium circulation pump 65. Commercial power is output.

At this time, since the generator 50 and the engine 52 are kept in a stopped state, it is preferable that the heating medium refill mode setting step is performed as follows.

That is, the heating damper 100 is set in the closed mode and the cooling damper 104 is set in the open mode.

The three-way side 94 is controlled at a predetermined opening degree (for example, 50) such that the heat medium of the waste heat recovery device 60 passes through both the waste heat supply heat exchanger 80 and the waste heat heat dissipation device 85.

The cooling water circulation pump 57, waste heat radiation blower 88 and the ventilation blower 114 is preferably maintained in a stopped state.

When the heat medium refilling mode setting step is completed as described above, the heat medium circulation pump 65 is driven for a preset heat medium degassing time (eg, 30 minutes).

Then, while the heat medium of the waste heat recovery device 60 circulates through the waste heat recovery device 60, the waste heat supply heat exchanger 80, and the waste heat radiator 85, the air in the heat medium circulation flow path 64 Fall out through the expansion tank (66).

The predetermined heat medium degassing time of the heat medium circulation pump 65 is a time at which air in the heat medium circulation flow path 64 can be sufficiently drained, and varies depending on the length of the heat medium circulation flow path 64 and the like.

When the heat medium degassing step is completed, after the heat medium circulation pump 65 is stopped, the heat medium refilling mode ends.

After the heat medium replenishment mode is finished as described above, the cogeneration system is operated in response to an operation request of at least one of the plurality of indoor units Ia.

10 is a schematic diagram of a heat medium supplement mode according to a second embodiment of a cogeneration system according to the present invention, and FIG. 11 is a flow chart of a heat medium supplement mode according to a second embodiment of a cogeneration system according to the present invention.

In the heat medium supplement mode according to the first embodiment of the cogeneration system illustrated in FIGS. 10 and 11, in the cogeneration system, at least the engine 52 of the soft stop or the cogeneration system is stopped, the waste heat. The heat medium of the recovery device 60 may be replenished in the heat medium circulation passage 64.

At this time, when the cogeneration system is not in the soft stop state, the cooling water circulation pump 57, the heat medium circulation pump 65, the waste heat radiating blower 88, and the compressor 70 of the air conditioner It is preferred to remain stationary.

After the heat medium replenishment step is completed as described above, when the heat medium replenishment mode switch 142 is pressed for a few seconds (for example, 5 seconds) or longer, a heat medium replenishment mode request signal is input to the heat medium circulation pump 65. The generated power of the generator 50 is output.

At this time, it is preferable that the generator 50 and the engine 52 have a heat medium refilling mode setting step as follows.

That is, the heating damper 100 is set in the closed mode and the cooling damper 104 is set in the open mode.

The three-way side 94 is controlled at a predetermined opening degree (for example, 50) such that the heat medium of the waste heat recovery device 60 passes through both the waste heat supply heat exchanger 80 and the waste heat heat dissipation device 85.

The cooling water circulation pump 57, waste heat radiation blower 88, and ventilation blower 114 are driven.

When the heat medium refilling mode setting step is completed as described above, the heat medium circulation pump 65 is driven for a preset heat medium degassing time (eg, 30 minutes).

Then, while the heat medium of the waste heat recovery device 60 circulates through the waste heat recovery device 60, the waste heat supply heat exchanger 80, and the waste heat radiator 85, the air in the heat medium circulation flow path 64 Fall out through the expansion tank (66).

When the heat medium degassing step is completed, after the heat medium circulation pump 65 is stopped, the heat medium refilling mode ends.

The cogeneration system and the control method according to the present invention configured as described above, the heat medium to circulate the heat medium of the waste heat recovery apparatus for a predetermined time so that the heat medium of the waste heat recovery apparatus can be degassed when the heat medium of the waste heat recovery apparatus is replenished By including the replenishment mode function, there is an advantage that can easily remove the air in the waste heat recovery apparatus.

In addition, the present invention has the advantage that the heat medium supplement mode function is operated in a switch mode by the cogeneration system operator, so that the heat medium supplement mode function can be easily selected.

In addition, the present invention generates a generator by the driving force of the drive source to supply the generated power of the generator to the air conditioner, and in addition to the waste heat of the drive source in the heating operation mode of the air conditioner to supply to the air conditioner By keeping the heating performance of the air conditioner constant, there is an advantage that the efficiency can be maximized.

In addition, according to the present invention, according to the operation mode and load conditions of the air conditioner, the system operating efficiency can be improved because the power for the operating efficiency of the cogeneration system among the generated power and commercial power is output to the air conditioner. As a result, the operating cost of the system can be reduced.

Claims (11)

A power consumer; A generator for supplying generated power to the power consumer; A drive source for generating the generator; A waste heat recovery apparatus for recovering waste heat of the drive source; An expansion tank connected to the waste heat recovery device; And a heat medium replenishment mode device configured to degas as the heat medium of the waste heat recovery device is circulated when the heat medium of the waste heat recovery device is replenished. The method of claim 1, The heat medium supplement mode device, the cogeneration system characterized in that it comprises a heat medium supplement mode switch for generating a heat medium supplement mode request signal. The method according to claim 1 or 2, The cogeneration system further comprises a power switching device for outputting any one of the generated power and commercial power of the generator. The method according to claim 1 or 2, The cogeneration system includes: a waste heat supply heat exchanger configured to transfer waste heat recovered by the waste heat recovery device to the air conditioner; A waste heat radiating device for radiating the waste heat recovered by the waste heat recovering device; Cogeneration system characterized in that it further comprises three sides for distributing the waste heat recovered by the waste heat recovery device to the waste heat supply heat exchanger or waste heat radiator. A heat medium replenishing step of replenishing a heat medium of a waste heat recovery apparatus for recovering waste heat of a drive source for driving a generator; And a heat medium degassing step in which air is discharged while the heat medium in the waste heat recovery device is circulated after the heat medium replenishment. The method of claim 5, The heating medium replenishing step is a control method of a cogeneration system, characterized in that carried out in the drive source stopped state. The method of claim 5, The heat medium degassing step, the control method of the cogeneration system, characterized in that carried out according to whether the heat medium degassing mode request signal input. The method of claim 5, The heat medium degassing step is a control method of a cogeneration system, characterized in that carried out during a predetermined heat medium degassing time. The method of claim 5, And the heat medium of the waste heat recovery device passes through both the waste heat radiating device and the waste heat supply heat exchanger during the heat medium degassing step. The method according to any one of claims 5 to 9, When the generated power of the generator is used during the heat medium degassing step, the driving source, the generator, the waste heat radiator, the ventilation blower, and the air conditioner are controlled in an operating state, and the air conditioner, which is a power consumption device, is stopped. Control method of a cogeneration system, characterized in that the control. The method according to any one of claims 5 to 9, When the commercial power is used during the heat medium degassing step, the cogeneration system, characterized in that the drive source, the generator, the waste heat radiator, the ventilation blower, the air conditioner which is a power consumption device is controlled in a stopped state. .

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