KR100634812B1 - Electric generation air condition system and the control method for the same - Google Patents

Abstract

A cogeneration system and a control method thereof are provided to improve the system efficiency with the constant heating performance according to the recovery and the supply of the waste heat. A cogeneration system comprises a heat pump-type air conditioner comprising indoor and outdoor devices(Ia,Oa); a generator(50) supplying the generation power to the heat pump-type air conditioner; a driving source(52) generating the generator; a waste heat recovery apparatus(60) recovering the waste heat of the driving source; a waste heat radiating apparatus(85) where the waste heat recovered at the waste heat recovery apparatus is radiated; a waste heat supply apparatus(80) transferring the waste heat recovered at the waste heat recovery apparatus to the heat pump-type air conditioner; a three-way valve(94) distributing the waste heat recovered at the waste heat recovery apparatus with a predetermined opening degree; and a control unit setting the initial three-way valve opening degree after the oil recovery operation when the heat pump-type air conditioner uses the waste heat of the driving source according to the three-way valve opening degree before the oil recovery operation and the load of the heat pump-type air conditioner.

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 cogeneration system according to the present invention is a power generation output, the heat pump type air conditioner is a configuration diagram when operating in a cooling cycle,

3 is a cogeneration system according to the present invention is a power generation output, the heat pump type air conditioner is a configuration diagram when operating in an outdoor high temperature heating cycle,

4 is a cogeneration system according to the present invention is a power generation output, the heat pump type air conditioner is a configuration diagram when operating in an outdoor low temperature heating cycle,

5 is a cogeneration system according to the present invention is a power generation output, the heat pump type air conditioner is a configuration diagram when operating in a double heating cycle,

6 is a cogeneration system according to the present invention is a commercial power output, the heat pump type air conditioner is a configuration diagram when operating in a cooling cycle,

7 is a commercial power output of the cogeneration system according to the present invention, the heat pump type air conditioner is a configuration diagram when operating in an outdoor high temperature heating cycle,

8 is a flow chart according to the three-way opening degree control method according to the oil recovery operation 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 device

85: waste heat radiator 94: three-way

100: refrigerant circulation flow path 110: bypass flow path

120: waste heat connection flow path

The present invention relates to a cogeneration system and a control method thereof, in particular, the three-way opening after the oil recovery operation, the three-way opening immediately before the oil recovery and the operation rate of the indoor unit in the waste heat of the drive source that the heat pump type air conditioner drives the generator. It relates to a cogeneration system and a control method thereof.

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 electric power consuming devices such as various lighting fixtures and heat pump type air conditioners 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 heat pump type 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 prior art configured as described above, the waste heat of the gas engine 10 is utilized only for hot water supply or hot water supply, and thus cannot be used in the heat pump type air conditioner 4. There is a problem in that the performance of the cogeneration system which is most needed by the user of the cogeneration system, in particular, does not maximize the heating capacity of the cogeneration system.

The present invention has been made to solve the problems of the prior art, the waste heat of the drive source is utilized to increase the heating capacity of the heat pump type air conditioner in the heating operation mode of the heat pump type air conditioner, The purpose of the present invention is to provide a heat pump type air conditioner and a cogeneration system and a control method thereof in which the efficiency thereof is maximized.

In addition, the present invention is a three-way opening degree for distributing the waste heat of the drive source after the oil recovery operation when the heat pump type air conditioner is using the waste heat of the drive source, the three-way opening degree just before the oil recovery and the heat pump type air conditioning By setting according to the operation rate of the indoor unit of the machine, not only can the heat pump type air conditioner including the three-way opening degree be stabilized quickly after the oil recovery operation of the heat pump type air conditioner, but also in terms of efficiency and reliability thereof. Another object is to provide an advantageous cogeneration system and a control method thereof.

Cogeneration system according to the present invention for solving the above problems is a heat pump type air conditioner consisting of an indoor unit and an outdoor unit; A generator for supplying generating power to the heat pump type air conditioner; A drive source for generating the generator; A waste heat recovery apparatus for recovering waste heat of the drive source; A waste heat radiating device for radiating the waste heat recovered by the waste heat recovering device; A waste heat supply device for transferring the waste heat recovered by the waste heat recovery device to the heat pump type air conditioner; A three-way stool for distributing the waste heat recovered by the waste heat recovery apparatus to a predetermined degree; The heat pump type air conditioner includes a control unit configured to set an initial three-way opening degree after the oil recovery operation when using waste heat of the driving source according to the three-way opening degree immediately before the oil recovery operation and the load of the heat pump type air conditioner. It is characterized by.

The heat pump type air conditioner includes: an outdoor unit including a compressor, a four-way valve, an outdoor heat exchanger, and an outdoor expansion valve; An indoor heat exchanger, and an indoor unit provided with an indoor expansion valve.

In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an outdoor heat exchanger, an outdoor expansion valve, an indoor expansion valve, and an indoor heat exchanger, and is then cooled to the compressor through the four-way valve. It is characterized by having a cycle.

In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an indoor heat exchanger, an indoor expansion valve, an outdoor expansion valve, and an outdoor heat exchanger, and then is circulated to the compressor through the four-way valve. It is characterized by having a high temperature heating cycle.

In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an indoor heat exchanger, an indoor expansion valve, an outdoor expansion valve, and the waste heat supply device, and then circulates to the compressor through the four-way valve. Characterized by having an outdoor low temperature heating cycle.

In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an indoor heat exchanger, an indoor expansion valve, an outdoor expansion valve, an outdoor heat exchanger, and the waste heat supply. It is characterized by having a double heating cycle circulated to the compressor through.

In addition, the control method of the cogeneration system according to the present invention for achieving the above object, the waste heat recovered from the drive source when the oil recovery operation is requested when the heat pump type air conditioner using the waste heat recovered from the drive source for driving the generator Triangular opening degree information obtaining step of obtaining the triangular opening degree information for distributing; When the oil recovery operation is completed, the initial three-way opening degree is set after the oil recovery operation when using waste heat of the driving source according to the three-way opening immediately before the oil recovery operation obtained in the first step and the load of the heat pump type air conditioner. Three-way opening degree is characterized in that consisting of the setting step.

The load of the heat pump type air conditioner is determined according to the indoor unit operation rate of the heat pump type air conditioner.

Driving ratio of the indoor unit (%) = 100 * current driving capacity of the indoor unit / total operating capacity of the indoor unit.

The initial three-way opening degree after the oil recovery operation using waste heat of the driving source in the three-way opening degree setting step may be set according to the initial three-way opening degree after the oil recovery operation using waste heat as follows.

The three-way opening after the oil recovery operation = the three-way opening degree before the oil recovery operation + the amount of the three-way opening increase, the amount of the three-way opening increase = [(90-the three-way opening before the oil recovery operation) * (100-operation rate of the indoor unit) )] / 100.

The three-way opening degree in the oil recovery operation is set to 100 so that waste heat recovered from the driving source is not distributed to the heat pump type air conditioner.

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

The cogeneration system according to the present invention may be divided into a power consumption device, a cogeneration unit for supplying generated power and waste heat to the power consumption device, and a cogeneration system control unit which controls overall operation of the cogeneration system. .

The power consumption device may be implemented in various ways, such as a heat pump type air conditioner, a refrigerator, a microwave oven, a computer, and the like.

First, the configuration of the cogeneration unit in detail, as follows.

The cogeneration unit is configured to include a generator 50 for generating power generation, a drive source 52 for driving the generator 50, and a waste heat recovery device 60 for recovering waste heat of the drive source 52. .

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.

The power generation device of the generator 50 switches the power so that any one of the power generation of the generator 50 and the commercial power (50 ') produced by the power company is output to the heat pump type air conditioner ( 51 may be output to the heat pump type 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 passage of the engine 52. The first and second exhaust gas heat exchangers 62 and 63 connected to the 54 may recover heat of the exhaust gas exhausted from the engine 52.

The waste heat recovered by the waste heat recovery device 60 may be supplied to the heat pump type air conditioner through the waste heat supply device 80 which is a heat demand destination.

The waste heat supply device 80 may be implemented in a heat exchanger method to allow the waste heat recovered by the waste heat recovery device 60 and the refrigerant of the heat pump type air conditioner to exchange heat with each other.

The waste heat supply device 80 is connected to the waste heat recovery device 60 through a waste heat recovery passage 64 for guiding a heat medium for waste heat recovery of the engine 52.

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 device 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.

In addition, the waste heat recovered by the waste heat recovery device 60 may be radiated in the air through the waste heat radiator 85.

The waste heat dissipation device 85 is connected to the heat dissipation heat exchanger 86 and the waste heat recovery passage 64 to allow the waste heat recovered by the waste heat recovery device 60 to be radiated to the atmosphere, and the waste heat recovery passage 64. The waste heat dissipation flow path 87 for guiding the inner heat medium to the heat dissipation heat exchanger 68, and the waste heat dissipation blower 88 for forcibly blowing outside air to the heat dissipation heat exchanger 86.

A waste heat distributor 94 for distributing the waste heat recovered by the waste heat recovery device 60 is disposed 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. Is installed.

The waste heat distributor 94 may be implemented in three directions to switch the flow of the heat medium in the waste heat recovery passage 64. Hereinafter, the reference number '94' is limited to three sides.

On the other hand, the cogeneration unit is provided with a suction inlet 201 and a discharge port 202 for ventilation in each of the power generation chamber 200 forming the appearance, the ventilation blower 204 in the inlet 201 of the power generation chamber 200 Is provided.

Next, a detailed description of the heat pump type air conditioner, which is one of the power consumers, is as follows.

The heat pump type air conditioner may be largely divided into an outdoor unit Oa and an indoor unit Ia, and may be configured of one outdoor unit Oa and one indoor unit Ia, and one outdoor unit Oa and a plurality of units. It is also possible to comprise a plurality of indoor units (Ia), it may be composed of a plurality of outdoor units (Oa) and a plurality of indoor units (Ia). Hereinafter, the heat pump type air conditioner according to the present embodiment will be described as limited to one outdoor unit Oa and a plurality of indoor units Ia.

The outdoor unit Oa includes a compressor 70 for circulating a refrigerant of the heat pump type air conditioner, a four-way valve 73 for switching a refrigerant flow of the heat pump type air conditioner, and the heat pump type air. An outdoor heat exchanger 75 and an outdoor expansion valve 77 in which a refrigerant of the conditioner exchanges heat with outdoor air in which the outdoor unit Oa is installed are provided.

The compressor 70 includes a compression unit having a compression chamber in which a refrigerant of the heat pump air conditioner is compressed, a motor for driving the compression unit, and an oil pump for pumping oil for lubrication and cooling of the motor and the compression unit. Is made of.

Compressor 70 provided as described above may be composed of one or more than two. Hereinafter, the two compressors 70 are configured to be limited.

The two compressors 70 are connected through a common accumulator 78 installed on the suction side where the refrigerant of the heat pump type air conditioner is sucked in.

Each indoor unit (Ia) is provided with an indoor heat exchanger (74) and an indoor expansion valve (76) in which the refrigerant of the heat pump type air conditioner exchanges heat with the indoor unit (Ia) in which the indoor unit (Ia) is installed.

The refrigerant of the heat pump type air conditioner configured as described above is circulated along the refrigerant circulation passage 100 through the indoor unit Ia and the outdoor unit Oa.

The refrigerant circulation passage 100 includes a first opening / closing valve 102 between the compressor 70 and the outdoor heat exchanger 75.

The refrigerant circulation passage 100 includes a second opening / closing valve 104 between the outdoor heat exchanger 75 and the indoor unit Ia.

The refrigerant circulation passage 100 is connected with a bypass passage 110 for guiding the refrigerant of the heat pump type air conditioner to bypass the outdoor heat exchanger 75.

The bypass flow path 110 is laminated with the refrigerant circulation flow path 100 at both sides of the outdoor heat exchanger 75, respectively.

The third opening and closing valve 112 is provided on the bypass passage 110.

In addition, the refrigerant circulation flow path 100 is connected to the waste heat connection flow path 120 for guiding the refrigerant of the heat pump type air conditioner to pass through the waste heat supply device 120.

The first waste heat opening and closing valve 122 is provided at the inlet side of the waste heat connecting passage 120, and the second waste heat opening and closing valve 124 is provided at the outlet side of the waste heat connecting passage 120.

The operation mode of the heat pump type air conditioner configured as described above is a cooling operation mode in which the indoor unit Ia is operated in a cooling cycle for supplying cold air and a heating cycle in which the indoor unit Ia supplies warm air. There is a heating operation mode.

In addition, the heating cycle of the heat pump type air conditioner includes an outdoor high temperature heating cycle that does not use waste heat of the engine 52 through the waste heat supply device 80 according to the outdoor temperature at which the outdoor unit Oa is installed. In addition, an outdoor low temperature heating cycle using waste heat of the engine 52 but not using the outdoor heat exchanger 75, and a dual heating cycle using both the waste heat of the engine 52 and the outdoor heat exchanger 75 may be used. have.

Here, since the outdoor low temperature heating cycle and the dual heating cycle can recover the waste heat of the engine 52 only when the engine 52 is operated, the heat pump type air conditioner supplies the generated power of the generator 50. Can only be implemented if received.

On the other hand, while the heat pump type air conditioner is operated in a cooling or heating operation mode, an oil recovery operation for recovering oil of the compressor 70 to the compressor 70 is performed.

In more detail, the oil of the compressor 70 is usually partially discharged together with the refrigerant of the heat pump type air conditioner when the refrigerant of the heat pump type air conditioner is discharged after being compressed by the compressor 70. It discharges and remains in the flow path through which the refrigerant | coolant of the said heat pump type air conditioner circulates, and each component part.

Therefore, the oil recovery operation allows the air conditioner to be operated in a cooling cycle for a predetermined time in order to quickly recover the oil flow path through which the refrigerant of the heat pump type air conditioner is circulated, and oil remaining in each component.

Next, the cogeneration system control unit controls the cogeneration system according to the operation mode of the heat pump type air conditioner, the operation rate of the indoor unit Ia, indoor / outdoor temperature, and the like.

In particular, the cogeneration system control unit, when the heat pump type air conditioner is supplied with the generated power of the generator 50, the waste heat recovered to the waste heat recovery device 60 is the waste heat supply device 80 or waste heat The triangular opening 94 is set between 0 and 100 so that the heat dissipation device 85 can be distributed at an optimal waste heat distribution ratio.

More specifically, the cogeneration system control unit, the cogeneration system control unit, the waste heat recovery device (when the heat pump type air conditioner does not use the waste heat recovered in the waste heat recovery device 60) The opening amount of the three-way side 94 is set to 100 so that the waste heat recovered by 60 may be radiated through the waste heat radiating device 85 in its entirety.

That is, when the heat pump type air conditioner is operated in a cooling cycle or an outdoor high temperature heating cycle, the three-way 94 opening degree is 100.

On the other hand, the cogeneration system control unit, when using the waste heat recovered by the heat pump type air conditioner to the waste heat recovery apparatus 60, the heat recovery system 60 recovers to the waste heat recovery apparatus 60 according to the load conditions of the heat pump type air conditioner The opening amount of the three-way side 94 is set between 0 and 100 so that the entire amount or part of the waste heat can be transferred to the waste heat supply device 80.

That is, the cogeneration system control unit sets the three-way side opening degree between 0 and 100 when the heat pump type air conditioner is operated by an outdoor low temperature heating cycle or a double heating cycle.

At this time, the cogeneration system control unit sets the three-way side opening degree to zero if the total amount of waste heat recovered by the waste heat recovery apparatus 60 is used in the heat pump type air conditioner.

Alternatively, the cogeneration system control unit sets the three-way side opening 94 to be greater than 0 and less than 100 if only a part of the waste heat recovered by the waste heat recovery device 60 is used in the heat pump type air conditioner.

In addition, the cogeneration system control unit, the three-way opening degree control method according to the oil recovery operation of the heat pump type air conditioner, the initial three-way (94) opening immediately after the oil recovery operation of the heat pump type air conditioner will be described later. Set according to '.

The three-way opening degree control method according to the oil recovery operation of the heat pump type air conditioner will be described with reference to FIG. 8 in particular.

When the heat pump type air conditioner is in operation (S2) and the oil recovery operation is requested (S4), first, an operation mode of the heat pump type air conditioner is determined (S6).

If the operation mode of the heat pump type air conditioner is the heating operation mode, it is determined whether the heat pump type air conditioner uses the waste heat recovered by the waste heat recovery device 60 (S8).

That is, it is determined whether the heat pump type air conditioner is operating in an outdoor high temperature heating cycle or in an outdoor low temperature heating cycle or a double heating cycle.

If the heat pump type air conditioner is operating in an outdoor low temperature heating cycle or a dual heating cycle using the waste heat of the waste heat recovery device 60, the three-way opening 94 may be obtained immediately before the oil recovery operation (S10). ).

When the three-way 94 opening degree D1 information is obtained immediately before the oil recovery operation, the oil recovery operation is performed (S12).

During the oil recovery operation, the heat pump type air conditioner is operated in a cooling cycle, so that the waste heat recovered by the waste heat recovery apparatus 60 can be radiated through the waste heat radiating device 85 in the entire amount. The triangular opening 94 is set at 100.

After the oil recovery operation is completed, before the heat pump type air conditioner is operated by returning to an outdoor low temperature heating cycle or a dual heating cycle, an initial three-way opening degree 94 is set after the oil recovery operation using the waste heat (S14).

At this time, when the heat pump type air conditioner returns to the outdoor low temperature heating cycle or the dual heating cycle with the initial three-way 94 opening D2 set to 100 after the oil recovery operation using the waste heat, the heat pump type air When the load of the conditioner is large, a large amount of time is used to stabilize the opening of the three-way side 94, and a considerable amount of waste heat recovered by the waste heat recovery device 60 while the three-way side 94 is open is stabilized. Heat dissipation through the device 85 is not good in terms of efficiency of the cogeneration system.

Alternatively, when the initial three-way 94 opening D2 after the oil recovery operation is set to the three-way 94 opening D1 immediately before the oil recovery operation when the waste heat is used, the load of the heat pump type air conditioner is small. Waste heat recovered by the waste heat recovery device 60 may be excessively supplied to the heat pump type air conditioner to damage the cogeneration system.

Therefore, the initial three-way 94 opening D2 after the oil recovery operation using the waste heat is one of the load conditions of the three-way 94 opening D1 and the air conditioner immediately before the oil recovery. In the heating operation as follows according to the operation rate of Ia), it is preferable that the initial three-way opening degree is set after the oil recovery operation.

When the waste heat is used, the initial three-way opening after the oil recovery operation = the three-way opening + the three-way opening increase immediately before the oil recovery operation,

The triangular opening degree increase = [(90-triangular opening degree just before oil return operation) * (100-operation rate of the indoor unit)] / 100,

Driving ratio of the indoor unit (%) = 100 * current driving capacity of the indoor unit / total operating capacity of the indoor unit.

After the initial three-way 94 opening D2 is set after the oil recovery operation using the waste heat, the heat pump type air conditioner returns to the outdoor low temperature heating cycle or the dual heating cycle and continues to operate (S16).

On the other hand, when the heat pump type air conditioner is in a cooling mode by a cooling cycle or a heating operation by an outdoor high temperature heating cycle, the three-way opening 94 is opened not only before the oil recovery operation but also during the oil recovery operation and after the oil recovery operation. It is set to 100 (S20).

Hereinafter, the operation of the cogeneration system configured as described above will be described in detail according to the cycle of the heat pump type air conditioner and the power output to the heat pump type air conditioner.

First, the heat pump type air conditioner is operated in a cooling cycle and described with reference to FIG. 2 at the time of generating power output. At this time, the triangular opening 94 is 100.

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), it is circulated back to the engine (52).

Since the cooling water waste heat recovered by the cooling water heat exchanger 61 is 100 in the three-way direction 94, as the heat medium on the waste heat recovery passage 64 is pumped to the heat medium circulation pump 65, the cooling water heat exchange. After passing through the air 61, the second exhaust gas heat exchanger 62, and the first exhaust gas heat exchanger 63, and then are transferred to the waste heat radiator 85 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.

In the heat pump type air conditioner, the refrigerant compressed by the compressor 70 is transferred to the outdoor heat exchanger 75 through the four-way valve 73 to condense, and is condensed by the outdoor heat exchanger 75. The refrigerant is passed through the outdoor expansion valve (77) and the indoor expansion valve (76) to the indoor heat exchanger (74) to evaporate, and the refrigerant evaporated in the indoor heat exchanger (74) again through the four-way valve (73). Circulated to the compressor (70).

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

Next, the heat pump type air conditioner is operated by an outdoor high temperature heating cycle, and will be described with reference to FIG. 3 when generating power.

At this time, the triangular opening 94 is 100.

 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 and the waste gas waste heat of the engine 52 are recovered by the waste heat recovery apparatus 60.

The waste heat recovered by the waste heat recovery device 60 is radiated through the waste heat radiator 85 because the three-way side opening 94 is 100 degrees.

In the heat pump type air conditioner, 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 condensed. Passed through the indoor expansion valve 76 and the outdoor expansion valve 77 in turn to the outdoor heat exchanger 75 and evaporated, the refrigerant evaporated in the outdoor heat exchanger 75 again through the four-way valve 73. Circulated to the compressor (70).

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

Next, the heat pump type air conditioner is operated in an outdoor low temperature heating cycle, and described with reference to FIG. 4 at the time of generating power output.

At this time, the triangular opening 94 is set to an optimum value between 0 and 100.

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.

The waste heat recovered by the waste heat recovery device 60 is transferred to the waste heat supply device 80 and the waste heat radiator 85.

In the heat pump type air conditioner, the refrigerant compressed by the compressor (70) is transferred to the indoor heat exchanger (74) via the four-way valve (73) to condense, and condensed by the indoor heat exchanger (74). The refrigerant is passed through the indoor expansion valve 76 and the outdoor expansion valve 77 to the waste heat supply device 80 in order to evaporate, and the refrigerant evaporated from the waste heat supply device 80 moves to the four-way valve 73. Through the circulation to the compressor 70 again.

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

When the heat pump type air conditioner is operated in an outdoor low temperature heating cycle as described above, since the waste heat supply device 80 instead of the outdoor heat exchanger 75 serves as an evaporator, a constant heating is always performed regardless of the outdoor temperature change. Capacity can be provided and 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, the heat pump type air conditioner is operated in a double heating cycle, and described with reference to FIG. 5 at the time of generating power output.

At this time, the triangular opening 94 is set to an optimum value between 0 and 100.

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.

The waste heat recovered by the waste heat recovery device 60 is transferred to the waste heat supply device 80 and the waste heat radiating device 85.

In the heat pump type air conditioner, the refrigerant compressed by the compressor (70) is transferred to the indoor heat exchanger (74) via the four-way valve (73) to condense, and condensed by the indoor heat exchanger (74). The refrigerant is passed through the indoor expansion valve 76 and the outdoor expansion valve 77 to the outdoor heat exchanger 75 and the waste heat supply device 80 to be evaporated, and the outdoor heat exchanger 75 and waste heat supply device. The refrigerant evaporated at 80 is circulated back to the compressor 70 through the four-way valve 73.

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

When the heat pump type air conditioner is operated in a double heating cycle as described above, the outdoor heat exchanger 75 and the waste heat supply device 80 are simultaneously used as an evaporator, thereby providing a constant heating capability regardless of the outdoor temperature change. In addition, the heating capacity and the efficiency of the cogeneration system can be improved.

Next, the heat pump type air conditioner is operated in a cooling cycle, and will be described with reference to FIG. 6 at the time of commercial power output.

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 is maintained in a stopped state, the three-way side 94 Since there is no waste heat recovery of the engine 52, the engine 52 is set to the standby state.

In the heat pump type air conditioner, the refrigerant compressed by the compressor (70) is a four-way valve (73), an outdoor heat exchanger (75), an outdoor expansion valve (77), an indoor expansion valve (76), an indoor heat exchanger. After passing through 74 and the four-way valve 73 in turn, the compressor 70 is circulated to the compressor 70, and the indoor unit Ia supplies cold air.

Next, the heat pump type air conditioner is operated by an outdoor high temperature heating cycle, and will be described with reference to FIG. 7 at the time of commercial power output.

Of course, the generator 50, the engine 52, the coolant pump 57, the heat medium circulation pump 65, and the waste heat radiating blower 88 are kept in a stopped state, and the three-way side 94 is in a standby state. Is set to.

In the heat pump type air conditioner, the refrigerant compressed by the compressor 70 is a four-way valve 73, an indoor heat exchanger 74, an indoor expansion valve 76, an outdoor expansion valve 77, an outdoor heat exchanger 75 And, after passing through the four-way valve 73 in turn circulated to the compressor 70, the indoor unit (Ia) is to supply warm air.

The cogeneration system and the control method thereof according to the present invention configured as described above may generate a generator by a driving force of a driving source, supply the generated power of the generator to a heat pump type air conditioner, and the heat pump type air conditioner. In the heating operation mode of the waste heat of the drive source is recovered and supplied to the heat pump type air conditioner to maintain the heating performance of the heat pump type air conditioner, there is an advantage that the efficiency can be maximized.

In addition, the present invention is a three-way opening degree for distributing the waste heat of the drive source after the oil recovery operation when the heat pump type air conditioner is using the waste heat of the drive source, the three-way opening degree just before oil recovery and the heat pump type air conditioning By setting according to the operation rate of the indoor unit of the machine, not only can the heat pump type air conditioner including the three-way opening degree be stabilized quickly after the oil recovery operation of the heat pump type air conditioner, but also in terms of efficiency and reliability thereof. There is an advantageous advantage.

Claims (10)

A heat pump type air conditioner comprising an indoor unit and an outdoor unit; A generator for supplying generating power to the heat pump type air conditioner; A drive source for generating the generator; A waste heat recovery apparatus for recovering waste heat of the drive source; A waste heat radiating device for radiating the waste heat recovered by the waste heat recovering device; A waste heat supply device for transferring the waste heat recovered by the waste heat recovery device to the heat pump type air conditioner; A three-way stool for distributing the waste heat recovered by the waste heat recovery apparatus to a predetermined degree; The heat pump type air conditioner is configured to include a control unit for setting the initial three-way opening after the oil recovery operation when using the waste heat of the drive source, according to the three-way opening degree just before the oil recovery operation and the load of the heat pump air conditioner. Cogeneration system characterized by the above-mentioned. The method of claim 1, The heat pump type air conditioner includes: an outdoor unit including a compressor, a four-way valve, an outdoor heat exchanger, and an outdoor expansion valve; A cogeneration system comprising an indoor heat exchanger and an indoor unit having an indoor expansion valve. The method of claim 2, In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an outdoor heat exchanger, an outdoor expansion valve, an indoor expansion valve, and an indoor heat exchanger, and is then cooled to the compressor through the four-way valve. A cogeneration system having a cycle. The method of claim 2, In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an indoor heat exchanger, an indoor expansion valve, an outdoor expansion valve, and an outdoor heat exchanger, and then is circulated to the compressor through the four-way valve. A cogeneration system having a high temperature heating cycle. The method of claim 2, In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an indoor heat exchanger, an indoor expansion valve, an outdoor expansion valve, and the waste heat supply device, and then circulates to the compressor through the four-way valve. A cogeneration system comprising an outdoor low temperature heating cycle. The method of claim 2, In the heat pump type air conditioner, the refrigerant compressed by the compressor passes through a four-way valve, an indoor heat exchanger, an indoor expansion valve, an outdoor expansion valve, an outdoor heat exchanger, and the waste heat supply. A cogeneration system, characterized in that it has a double heating cycle circulated to the compressor through. A triangular opening degree information obtaining step of acquiring trilateral opening degree information for distributing waste heat recovered from the driving source when the heat pump type air conditioner uses the waste heat recovered from the driving source for driving the generator; When the oil recovery operation is completed, the initial three-way opening degree is set after the oil recovery operation when using waste heat of the driving source according to the three-way opening immediately before the oil recovery operation obtained in the first step and the load of the heat pump type air conditioner. Control method of a cogeneration system, characterized in that consisting of three-way opening degree setting step. The method of claim 7, wherein The load of the heat pump type air conditioner is controlled according to the indoor unit operation rate of the heat pump type air conditioner. The operation rate (%) of the indoor unit = 100 * It is the current operating capacity of the indoor unit / the total operating capacity of the indoor unit. The method of claim 8, The control method of the cogeneration system, characterized in that the initial three-way opening degree after the oil recovery operation when using waste heat of the drive source in the three-way opening degree setting step is set according to the initial three-way opening degree after the oil recovery operation using the waste heat as follows. . When the waste heat is used, the triangular opening after the oil recovery operation = the trilateral opening before the oil recovery operation + the amount of trilateral opening increase, The triangular opening degree increase amount = [((trilateral opening degree before 90-oil recovery operation) * (100-operation rate of the indoor unit)] / 100. The method according to any one of claims 7 to 9, The three-way opening degree in the oil recovery operation is set to 100 so that waste heat recovered from the driving source is not distributed to the heat pump type air conditioner.

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