Patent Description:
The gradual depletion of fossil fuels, which is the most widely used energy source, has led to the interest in alternative energy that can be continuously renewed by using infinite natural energy such as the sun, wind, waves, biological organisms and their waste. Further, most of all, clean energy causing little pollution unlike fossil fuels that have been used before is required. In particular, as the environmental problems such as environmental pollution and climate change conventions became social concerns in the <NUM>, the importance of these has become even more important.

Among the alternative energy projects, the power generation project using landfill gas (LFG) is the most applied field of landfill gas energy conversion projects. The composition of landfill gas, which is the raw material of such a system, is mainly composed of <NUM>-<NUM>% methane (CH4), <NUM>-<NUM>% carbon dioxide (CO2), and trace amounts of N2, O2. Since landfill gas has a heating value of about <NUM>,<NUM> to <NUM>,<NUM> kcal/m3 based on <NUM>% of methane content, it is the most important material of landfill gas recycling project and used as the fuel of gas engine driving.

Gas engines using landfill gas may be classified into a dedicated engine and a dual fuel engine. Since the dual fuel engine uses the existing diesel engine intactly, the retrofit is easy and the flammable limit is wide, so that stable operation can be achieved even with changes in fuel composition. The dedicated engine has an advantage in that only gas is used as fuel, but it has difficulty in operating in a place where gas component is severely changed because the heating value of fuel must be somewhat high and the gas component must be uniform. In order to maximize the fuel conversion efficiency of the engine in the operating range in which combustion stability is ensured, precise control of each component according to the characteristics of the fuel-air mixture is required.

In particular, when the concentration of the gaseous fuel is lean, there is a problem that power generation is difficult due to poor ignition, and in the case of the gas, when the combustion is performed by a natural aspirated engine, there is a limit in improving the output due to the low supply pressure.

In order to solve the shortcomings of the natural aspirated engine, the prior art includes a compressor connected to the shaft of the engine by a belt, so that intake pressure of the engine can be enhanced, and the efficiency of the engine can be improved.

However, when the compressor is connected to the engine by a belt as in the prior art, there is problem of noise and large space occupancy, and there is disadvantage that the compression ratio of the compressor cannot be precisely controlled due to the connection to the shaft of the engine by the belt.

Relevant prior art can be found in <CIT>. Additional reference is made to the following prior art documents: <CIT>, <CIT>, <CIT> and <CIT>.

The present invention has been made in view of the above problems, and provides a cogeneration system having improved stability while improving the output of an engine.

The present invention further provides a cogeneration system for reducing the volume of a product, and preventing the leakage of a mixed gas, by configuring a mixer gas for supplying gas and an intake compressor for compressing the mixer gas as a single module.

The present invention further provides a cogeneration system for using a motor-type intake compressor which allows precise compression ratio control and preventing the mixed gas from burning when an electric leakage occurs in an electric line controlling a motor.

The present invention further provides a cogeneration system for disposing a mixer for mixing gas and air in between the motor and the impeller of the intake compressor.

The present invention further provides a cogeneration system for disposing a mixer for mixing gas and air in between the motor and the impeller of the intake compressor, and disposing the motor in the upper stream from which air flows.

In accordance with an aspect of the present invention, we describe a cogeneration pipe comprising: an intake pipe one end of which communicating with outside air and another end of which being connected to an engine, the intake pipe having a motor accommodating part, a mixer accommodating part and an impeller accommodating part; a mixer disposed in the mixer accommodating part of the intake pipe to supply gas into the intake pipe; and an intake compressor for compressing a mixed gas which is a mixture of the air and the gas; wherein the intake compressor comprises: a motor disposed in the motor accommodating part of the intake pipe; and a compressor impeller disposed in the impeller accommodating part of the intake pipe and rotated by the motor to compress the mixed gas, wherein the mixer is positioned between the motor and the compressor impeller in the intake pipe, and wherein the motor is disposed upstream of the mixer, wherein the mixer comprises: an acceleration unit for reducing a cross-sectional area of the mixer accommodating part while progressing toward the compressor impeller from the motor; and a spray unit having a smaller cross-sectional area than the acceleration unit and provided with a spray hole connected to a gas intake pipe of the intake pipe, wherein the intake compressor further comprises a shaft connecting the motor and the compressor impeller, wherein the spray unit and the acceleration unit are disposed to surround the shaft, wherein the spray unit is disposed closer to the compressor impeller than the acceleration unit.

Preferred embodiments are defined in the dependent claims <NUM> to <NUM>.

The mixer is disposed between the motor and the compressor impeller in the intake pipe.

The mixer includes an acceleration unit for reducing a cross-sectional area of the air intake pipe while progressing toward the compressor impeller from the motor, and a spray unit which has a smaller cross-sectional area than the acceleration unit, and is provided with a spray hole connected to the gas intake pipe.

The spray unit is disposed closer to the compressor impeller than the acceleration unit.

The cogeneration system further includes a shaft connecting the motor and the compressor impeller, and the spray unit and the acceleration unit are disposed to surround the shaft.

The compressor impeller may further include a first compressor impeller connected to the motor by a shaft, a second compressor impeller, and a clutch for connecting or disconnecting power of the first compressor impeller to the second compressor impeller.

The cogeneration system may further include a cooler for cooling the mixed gas compressed in the intake compressor.

In accordance with another aspect of the present invention, a cogeneration system includes an intake pipe having one end which communicates with the outside air and having the other end which is connected to an engine, a mixer disposed in the intake pipe to supply gas into the intake pipe, and an intake compressor for compressing a mixed gas which is a mixture of the air and the gas, wherein the intake compressor includes a motor disposed in the intake pipe; and a compressor impeller which is disposed in the intake pipe, and rotates by the motor to compress the mixed gas, wherein the mixer is positioned between the motor and the compressor impeller.

The motor is disposed upstream of the mixer.

The intake pipe includes: a motor accommodating part in which the motor is disposed; a mixer accommodating part in which the mixer is disposed; and an impeller accommodating part in which the compressor impeller is positioned.

The mixer accommodating part is positioned between the motor accommodating part and the impeller accommodating part.

The mixer includes: an acceleration unit for reducing a cross-sectional area of the mixer accommodating part while progressing toward the compressor impeller from the motor; and a spray unit which has a smaller cross-sectional area than the acceleration unit, and is provided with a spray hole connected to the gas intake pipe.

The compressor impeller includes: a first compressor impeller connected to the motor by a shaft; a second compressor impeller; and a clutch for connecting or disconnecting power of the first compressor impeller to the second compressor impeller.

The cogeneration system further includes a cooler for cooling the mixed gas compressed in the intake compressor, and the cooler is positioned in the intake pipe between the engine and the compressor impeller.

The cogeneration system further includes a generator for generating power by a power of the engine.

The cogeneration system further includes a hot water storage tank for storing heat medium recovering heat generated by the engine.

The first compressor impeller is disposed closer to the motor than the second compressor impeller, and the mixer is positioned between the first compressor impeller and the motor.

The above and other objects, features and advantages of the present invention will be more apparent from the following detailed description in conjunction with the accompanying drawings, in which:.

Exemplary embodiments of the present invention are described with reference to the accompanying drawings in detail. The same reference numbers are used throughout the drawings to refer to the same or like parts. Detailed descriptions of well-known functions and structures incorporated herein may be omitted to avoid obscuring the subject matter of the present invention.

<FIG> is a schematic diagram of a cogeneration system according to an embodiment of the present invention.

Referring to <FIG>, the cogeneration system of the present embodiment generates power may include a power generation unit <NUM> for generating power and dissipating heat generated during power generation, an air conditioner for cooling and heating indoor air, a hot water storage tank <NUM>, a distribution unit <NUM> for guiding the heat of the power generation unit <NUM> to any one of the air conditioner and the hot water storage tank <NUM>. Part of the power generated by the power generation unit <NUM> may be supplied to the air conditioner.

The power generation unit <NUM> may generate power and heat, supply the generated power to lighting or home appliances, which is power consumption devices, and transfer the generated heat to the hot water storage tank <NUM> or the air conditioner.

The power generation unit <NUM> may include an engine <NUM>, a generator <NUM> connected to the engine <NUM> to generate power, a hot water supply heat exchanger <NUM> connected to the hot water storage tank <NUM> through a hot water supply circulation flow path <NUM>, and a heat medium flow path <NUM> which recovers at least one heat of the engine <NUM> and the generator <NUM> and transfers the recovered heat to the hot water supply heat exchanger <NUM>.

In addition, the power generation unit <NUM> may include an intake pipe <NUM> through which a gas mixed with air flows in, a mixer <NUM> which is disposed in the intake pipe and supplies gas into the intake pipe, an intake compressor for compressing a mixed gas supplied to the intake pipe <NUM>, an exhaust pipe <NUM> which is connected to the engine <NUM> and exhausts an exhaust gas, a return pipe <NUM> for recirculating a part of the exhaust gas flowing into the exhaust pipe <NUM> to the intake pipe <NUM>, and a catalyst module <NUM> for oxidizing/deoxidizing harmful components in the exhaust gas to be harmless.

The engine <NUM> is connected to the intake pipe <NUM> and the exhaust pipe <NUM> to generate power due to the combustion of the mixed gas. The mixed gas supplied to the engine <NUM> through the intake pipe <NUM> is discharged as exhaust gas through the exhaust pipe <NUM> after combustion in the engine <NUM>.

The engine <NUM> may include a cylinder head 14b in which the mixed gas is combusted, an intake manifold 14a for flowing the mixed gas into the cylinder head 14b, and an exhaust manifold 14c for flowing the combusted exhaust gas to the exhaust pipe <NUM>.

A gas mixed with the air flows into the intake pipe <NUM>. The intake pipe <NUM> intakes air and gas to mix air and gas, and then supplies them to the intake compressor and the engine <NUM>. The gas may include various combustible materials, and preferably, include landfill gas.

The intake pipe <NUM> is connected to outside air, a gas storage (not shown), the intake manifold 14a of the engine <NUM>, and the intake compressor.

For example, the intake pipe <NUM> includes an air intake pipe <NUM> into which air is introduced, a gas intake pipe <NUM> into which gas is introduced, and a mixed gas intake pipe <NUM> for supplying air supplied from the air intake pipe <NUM> and the mixed gas supplied from the gas intake pipe <NUM> to engine <NUM>.

The air intake pipe <NUM> flows air. One end of the air intake pipe <NUM> is connected to the outside air and the other end is connected to the gas intake pipe <NUM> and the mixed gas intake pipe <NUM>. An air filter 41a for purifying the intaken air, a silencer <NUM>, and the like may be disposed in the air intake pipe <NUM>.

Gas flows in the gas intake pipe <NUM>. One end of the gas intake pipe <NUM> is connected to the gas storage and the other end is connected to the air intake pipe <NUM>.

The mixer <NUM> is disposed in the intake pipe <NUM> to mix air and gas at an appropriate ratio, and provides the mixed gas to the mixed gas intake pipe <NUM>. The mixer <NUM> may be connected to the gas intake pipe <NUM> and the air intake pipe <NUM>. Specifically, the mixer <NUM> may allow the gas to be naturally dispersed in the air due to the pressure difference between the gas intake pipe <NUM> and the air intake pipe <NUM>. More specifically, the mixer <NUM> may be an spray hole 342a which communicates with the gas intake pipe <NUM>, and is disposed in the air intake pipe <NUM>.

The mixed gas intake pipe <NUM> provides the mixed gas mixed by the mixer <NUM> to the intake manifold 14a of the engine <NUM>. One end of the mixed gas intake pipe <NUM> is connected to the air intake pipe <NUM>, and the other end is connected to the intake manifold 14a of the engine <NUM>.

The embodiment may further include a generator <NUM> which is connected to an output shaft of the engine <NUM> and generates power when the output shaft rotates, and supplies the generated power through a power line.

A heat medium that recovered the heat of a driving source of the power generator <NUM> passes through the heat medium flow path <NUM>. The heat medium flow path <NUM> transfers the heat of the engine or the generator <NUM> to a cooling cycle of the air conditioner or the hot water supply circulation flow path <NUM> of the hot water storage tank <NUM> through the heat medium. For example, a heat recovery unit (not shown) for recovering heat of the engine <NUM> or the generator <NUM> may be disposed in the heat medium flow path <NUM>. Obviously, the heat medium flow path <NUM> may recover the heat of the engine <NUM>, the generator <NUM>, and the exhaust pipe.

Specifically, the heat medium flow path <NUM> may include an engine, a heat medium outflow path 11b through which the heat medium that heat exchanged with the generator <NUM> flows out, and a heat medium inflow path 11a through which the heat medium discharged from the distribution unit <NUM> flows back into the engine and the generator <NUM>. Here, water may be used as the heat medium.

The hot water supply heat exchanger <NUM> heat-exchanges between the heat medium circulating the heat medium flow path <NUM> and the heat medium circulating the hot water supply circulation flow path <NUM>. The hot water supply heat exchanger <NUM> transfers the thermal energy of the heat medium flow path <NUM> to the hot water supply circulation flow path <NUM>. A second refrigerant flows in the hot water supply circulation flow path <NUM>.

In addition, the power generation unit <NUM> may further include a heat dissipation unit <NUM> which is connected to the hot water storage tank <NUM> through a heat dissipation flow path <NUM> and dissipates the heat of water in the hot water storage tank <NUM>. The water in the hot water storage tank <NUM> is provided to a place which requires hot water, but is cooled by the heat dissipation unit <NUM> and used as the cooling water of the hot water supply heat exchanger <NUM>.

The intake compressor compresses the mixed gas supplied to the intake pipe <NUM> and provides to the engine <NUM>.

Hereinafter, a cooling cycle of an air conditioner constituting a part of the cogeneration system of the present embodiment will be described.

The cooling cycle of the present embodiment includes a compressor <NUM>, an expansion mechanism, an outdoor heat exchanger <NUM>, and an indoor heat exchanger <NUM>.

The compressor <NUM> compresses the refrigerant and endows a circulation force so that the refrigerant can circulate a cooling cycle. Meanwhile, in the present embodiment, it may be connected to the generator <NUM> by a power line to receive power from the generator <NUM>. In addition, an accumulator <NUM> for accumulating liquid refrigerant is connected to an inlet pipe through which the refrigerant of the compressor <NUM> flows in.

The expansion mechanism expands the refrigerant, before the refrigerant is evaporated while passing through the heat exchanger, and is formed of an electronic expansion valve such as EEV. A single expansion mechanism may be provided to be able to expand the refrigerant in the cooling operation and the heating operation respectively.

However, the present embodiment may include a first expansion valve <NUM> which expands the refrigerant introduced into the outdoor heat exchanger <NUM> during the heating operation, and a second expansion valve <NUM> which expands the refrigerant introduced into the indoor heat exchanger <NUM> during the cooling operation.

Meanwhile, the cooling cycle of the present invention further includes an outdoor heat exchanger <NUM>, an indoor heat exchanger <NUM>, a compressor <NUM>, and a four-way valve <NUM> connected between expansion devices so as to change the flow of the refrigerant according to the cooling and heating.

In the outdoor heat exchanger <NUM>, the refrigerant flows and is condensed/evaporated while exchanging heat with outdoor air blown by a blower (not shown). Furthermore, in the present embodiment, defrosting may be achieved by absorbing the heat of the heat medium flowing through the heat medium flow path <NUM> described above.

In the indoor heat exchanger <NUM>, the refrigerant flows and is condensed/evaporated while exchanging heat with indoor air blown by the blower (not shown).

The distribution unit <NUM> controls the direction of the refrigerant flowed through the heat medium flow path <NUM>. The distribution unit <NUM> allows the heat medium flowing through the heat medium flow path <NUM> to heat exchange with a first refrigerant of the air conditioner among the hot water storage tank <NUM> and the air conditioner during the defrosting operation or the heating operation, and allows the heat medium flowing through the heat medium flow path <NUM> to heat exchange with a second refrigerant of the hot water storage tank <NUM> among the hot water storage tank <NUM> and the air conditioner during the cooling operation.

Specifically, the distribution unit <NUM> allows the heat medium flowing through the heat medium flow path <NUM> to heat exchange with the first refrigerant flowing through a refrigerant cycle of the air conditioner, during the defrosting operation or the heating operation, and allows the heat medium flowing through the heat medium flow path <NUM> to heat exchange with the second refrigerant flowing through the hot water circulation flow path <NUM> during the cooling operation.

For example, the distribution unit <NUM> includes an air conditioning heat exchanger <NUM> for exchanging heat of the heat medium and the first refrigerant, and a three-way valve <NUM> for guiding the heat medium passed through the driving source of the generator <NUM> to the hot water supply heat exchanger <NUM> of the hot water storage tank <NUM> during the cooling operation, and guiding the heat medium passed through the driving source of the generator <NUM> to the air conditioning heat exchanger <NUM> during the defrosting operation or the heating operation. The distribution unit <NUM> may include a plurality of distribution pipes.

A pump <NUM> for compressing the heat medium may be further disposed in the heat medium flow path 11b. The heat medium compressed by the pump <NUM> is supplied to the three-way valve <NUM>. The pump <NUM> and the three-way valve <NUM> are connected by a fifth distribution pipe <NUM>.

The three-way valve <NUM> is connected to the heat medium outflow path 11b, the air conditioning heat exchanger <NUM>, and the hot water supply heat exchanger <NUM>. The three-way valve <NUM> is connected to the pump <NUM>, the air conditioning heat exchanger <NUM>, and the hot water supply heat exchanger <NUM>.

The three-way valve <NUM> and the air conditioning heat exchanger <NUM> are connected by a first distribution pipe <NUM>, the air conditioning heat exchanger <NUM> and the hot water supply heat exchanger <NUM> are connected by a second distribution pipe <NUM>, and the hot water supply heat exchanger <NUM> and the three-way valve <NUM> are connected by a third distribution pipe <NUM>. The second distribution pipe <NUM> and the heat medium flow path <NUM> are connected by a fourth distribution pipe <NUM>. Specifically, the fourth distribution pipe <NUM> connects the heat medium inflow path 11a and the second distribution pipe <NUM>.

The air conditioning heat exchanger <NUM> exchanges heat between the heat medium flowing through the first distribution pipe <NUM> and the first refrigerant bypassed in the cooling cycle.

The distribution unit <NUM> further includes a bypass pipe <NUM>. The bypass pipe <NUM> bypasses the outdoor heat exchanger <NUM> of the air conditioner and guides the expanded refrigerant to the air conditioning heat exchanger <NUM>, during the defrosting operation or the heating operation.

The air conditioning heat exchanger <NUM> is connected to the bypass pipe <NUM>. The air conditioning heat exchanger <NUM> exchanges heat between the heat medium flowing through the first distribution pipe <NUM> and the first refrigerant flowing through the bypass pipe <NUM>.

One end of the bypass pipe <NUM> is connected between the expansion device of the air conditioner and the outdoor heat exchanger <NUM>, and the other end of the bypass pipe <NUM> is connected between the outdoor heat exchanger <NUM> and the compressor <NUM> of the air conditioner. Specifically, one end of the bypass pipe <NUM> is connected to an outdoor unit inlet pipe <NUM> connecting the first expansion valve <NUM> of the air conditioner, and the other end of the bypass pipe <NUM> is connected to an outdoor unit outlet pipe <NUM> connecting the outdoor heat exchanger <NUM> and the four-way valve <NUM>.

The bypass pipe <NUM> may further include an intermittent valve <NUM> that is closed during the cooling operation, and is opened during the defrosting operation or the heating operation. The intermittent valve <NUM> is opened during the defrosting operation or the heating operation so that the first refrigerant expanded in the first expansion valve <NUM> flows to the air conditioning heat exchanger <NUM> through the bypass pipe <NUM>. The intermittent valve <NUM> is closed during the cooling operation so that the refrigerant expanded in the first expansion valve <NUM> cannot flow into the bypass pipe <NUM> but flows to the outdoor heat exchanger <NUM>. The intermittent valve <NUM> is disposed between the air conditioning heat exchanger <NUM> and the outdoor unit inlet pipe <NUM> in the bypass pipe <NUM>.

In addition, the bypass pipe <NUM> may further include a check valve <NUM> that restricts the inflow of the first refrigerant evaporated from the outdoor heat exchanger <NUM> of the air conditioner into the air conditioning heat exchanger <NUM> during the cooling operation. The check valve <NUM> passes the first refrigerant passed through the air conditioning heat exchanger <NUM> during the heating operation or the defrosting operation. Therefore, the first refrigerant passed through the check valve <NUM> flows to the refrigerant cycle. The check valve <NUM> is disposed between the air conditioning heat exchanger <NUM> and the outdoor unit outlet pipe <NUM> in the bypass pipe <NUM>.

The outdoor unit inlet pipe <NUM> may further include an adjustment valve <NUM> that is opened during the cooling operation or the heating operation, and is closed during the defrosting operation. The adjustment valve <NUM> is opened during the cooling operation or the heating operation to allow the first refrigerant expanded in the first expansion valve <NUM> to flow into the outdoor heat exchanger <NUM>, and is closed during the defrosting operation to prevent the first refrigerant expanded in the first expansion valve from flowing to the outdoor heat exchanger <NUM>. The adjustment valve <NUM> is disposed between a connection point of the bypass pipe <NUM> and the outdoor heat exchanger <NUM> in the outdoor inlet pipe.

The distribution unit <NUM> is preferably positioned in a separate cabinet from the driving source of the generator <NUM>.

The distribution unit <NUM> may further include a controller for controlling the three-way valve <NUM> and an air conditioner described later.

The controller controls the three-way valve <NUM> to guides the heat medium passed through the driving source of the generator <NUM> to the hot water supply heat exchanger <NUM> of the hot water storage tank <NUM> during the cooling operation and the heating operation, and guide the heat medium passed through the driving source of the generator <NUM> to the air conditioning heat exchanger <NUM> during the defrosting operation or the heating operation.

In addition, the controller (not shown) determines whether to perform the defrosting operation by determining the condition to be implanted in the outdoor heat exchanger <NUM> during the heating operation. The controller may determine the defrost condition based on the outdoor temperature, or the like.

Accordingly, since the embodiment evaporates the expanded refrigerant of the air conditioner by using the waste heat of the engine or the generator <NUM> absorbed by the heat medium during the defrosting operation, and supplies the refrigerant to the outdoor heat exchanger <NUM>, there is an advantage that a heating operation can be performed even when the outdoor heat exchanger <NUM> is landed, and an advantage of transferring the waste heat of the engine or generator <NUM> absorbed by the heat medium during the cooling operation to the hot water storage tank <NUM>.

Hereinafter, the compressor module <NUM> including the intake compressor and the mixer <NUM> will be described in detail with reference to <FIG>.

<FIG> is a diagram illustrating a part of a power generation unit of the cogeneration system of <FIG>.

In the intake compressor using a motor <NUM>, since the motor <NUM> uses electricity, there is a problem that the mixed gas is combusted when a spark occurs in the motor <NUM> and an electric line connected to the motor <NUM>. In order to solve this problem, if air is compressed through the intake compressor before the gas is mixed, the pressure of air becomes high, and thus the gas becomes difficult to be mixed due to the pressure difference. In this case, there is a problem that a separate compressor is required because the gas must be pressurized separately.

In addition, the mixer <NUM> is disposed in the air intake pipe <NUM>, and thus if the mixer <NUM> is disposed elsewhere, there is a problem that the pipe is extended, and must be disposed before the intake compressor in order to mix the gas.

In order to solve the above-described problems and reduce a space occupied by the mixer <NUM>, the present invention implemented the intake compressor and the mixer <NUM> as a single module.

The intake compressor compresses the mixed gas flowing through the mixed gas intake pipe <NUM> with a constant pressure. The intake compressor may be operated by a separate power source.

Specifically, the intake compressor may include a motor <NUM>, a compressor impeller <NUM>, and a shaft <NUM>.

The motor <NUM> generates power by electric energy. The motor <NUM> is disposed in the intake pipe <NUM>. Since the electric line is connected to the motor <NUM>, in order to prevent combustion of the mixed gas, the motor <NUM> may be disposed in the air intake pipe <NUM> in which the mixed gas does not flow.

The compressor impeller <NUM> is rotated by the motor <NUM> to compress and discharge the intake mixed gas. The compressor impeller <NUM> is axially connected to the motor <NUM> by a shaft <NUM>. The compressor impeller <NUM> is disposed in the intake pipe.

Specifically, the compressor impeller <NUM> may be disposed in the mixed gas intake pipe <NUM> through which the mixer flows. The compressor impeller <NUM> sucks and compresses a mixed gas in which the air of the air intake pipe <NUM> and the gas of the gas intake pipe <NUM> are mixed, and discharges the mixed gas to the mixed gas intake pipe <NUM> connected to the engine. The mixed gas intake pipe <NUM> may be an area positioned downstream from the mixer <NUM> or/and the gas intake pipe <NUM> of the intake pipe <NUM>.

When the compressor impeller <NUM> is disposed in the mixed gas intake pipe <NUM>, the fuel can be stably supplied without a separate fuel pressurizing apparatus and a regulator, and the gas in the gas intake pipe <NUM> can be stably sucked.

The shaft <NUM> is extended along the longitudinal direction of the intake pipe <NUM>. The motor <NUM> and the compressor impeller <NUM> are rotated about the shaft <NUM>. The shaft <NUM> spaces the motor <NUM> from the compressor impeller <NUM>.

The mixer <NUM> is disposed between the motor <NUM> and the compressor impeller <NUM> in the air intake pipe <NUM>. The motor <NUM> is disposed upstream of the mixer <NUM>, and the mixer <NUM> is disposed upstream of the compressor impeller <NUM>. Here, the upstream means the upstream side based on the flow direction of the air or the mixed gas. In addition, the upstream means a portion relatively adjacent to a portion communicating with the outside air in the intake pipe <NUM>.

When the mixer <NUM> is disposed between the motor <NUM> and the compressor impeller <NUM> in the air intake pipe <NUM>, the motor <NUM> is disposed upstream of the mixer <NUM>, so that gas is not mixed in the air flowing around the motor <NUM>. Thus, there is no risk that the mixed gas is combusted due to the spark of the motor <NUM> and the electric line connected to the motor <NUM>.

In addition, since the mixer <NUM> is disposed upstream of the compressor impeller <NUM> to mix air and gas before being compressed by the intake compressor, the gas can be naturally mixed without compressing the gas.

The mixer <NUM> may have a structure in which gas is dispersed into the air due to a pressure difference between the gas intake pipe <NUM> and the air intake pipe <NUM> without a separate energy source. The mixer <NUM> may have a structure that lowers the pressure of the air intake pipe <NUM> than the gas intake pipe <NUM>.

According to the invention, the mixer <NUM> includes an acceleration unit <NUM> and a spray unit <NUM>. The acceleration unit <NUM> lowers the compression by accelerating the air in the air intake pipe <NUM>. The acceleration unit <NUM> has a structure in which the cross-sectional area of the air intake pipe <NUM> is reduced as it progresses toward the compressor impeller <NUM> from the motor <NUM>.

The acceleration unit <NUM> may protrude from the inner surface of the air intake pipe <NUM> toward the center of the air intake pipe <NUM>. Here, the cross-sectional area of the air intake pipe <NUM> means the internal area of the air intake pipe <NUM>, based on the cross section that crosses the longitudinal direction of the air intake pipe <NUM>.

Specifically, the acceleration unit <NUM> may have a ring shape, and may have a structure in which an inner diameter decreases while progressing toward the compressor impeller <NUM> from the motor <NUM>. Alternatively, the acceleration unit <NUM> may be disposed above and below the air intake pipe <NUM>, and may have a structure of being inclined upward while progressing toward the compressor impeller <NUM> from the motor <NUM>.

The spray unit <NUM> is a place where the gas of the gas intake pipe <NUM> flows into the air intake pipe <NUM> by the pressure of the air which passed the acceleration unit <NUM>. The spray unit <NUM> may maintain the speed of the air accelerated in the acceleration unit <NUM>.

In detail, the spray unit <NUM> may have a cross-sectional area smaller than the average cross-sectional area of the acceleration unit <NUM>, or may have a cross-sectional area equal to the minimum cross-sectional area of the acceleration unit <NUM>. Here, the cross-sectional area of the spray unit <NUM> means the internal area of the air intake pipe <NUM> excluding the spray unit <NUM>, on the cross section that crosses the longitudinal direction of the air intake pipe <NUM>, and the cross-sectional area of the acceleration unit <NUM> means an inner area of the air intake pipe <NUM> excluding the acceleration unit <NUM>, on the cross section that crosses the longitudinal direction of the air intake pipe <NUM>.

More specifically, the cross-sectional area of the spray unit <NUM> may be uniform along the longitudinal direction of the air intake pipe <NUM> or may be reduced, but it is preferable that the cross-sectional area of the spray unit <NUM> is uniform so as to uniformly suck the gas from the gas intake pipe <NUM>.

For example, the spray unit <NUM> may have a ring shape having a constant internal diameter, or may be a bar disposed above and below the air intake pipe <NUM>. Preferably, the spray unit <NUM> and the acceleration unit <NUM> have a ring shape disposed to surround the shaft <NUM>.

The spray unit <NUM> may be provided with a spray hole 342a connected to the gas intake pipe. The spray hole 342a sprays gas from the spray unit <NUM> toward the center of the mixer accommodating part 21b. The spray hole 342a may be formed to be penetrated at the spray unit <NUM>. The spray unit <NUM> is disposed downstream of the acceleration unit <NUM>. According to the invention, the spray unit <NUM> is disposed closer to the compressor impeller <NUM> than the acceleration unit <NUM>.

In other words, the compressor module <NUM> may include the mixer <NUM> and a compressor housing 21a, 21b, 24a in which the intake compressor is disposed. The compressor housing 21a, 21b, 24a may form part of the intake pipe and may define a separate space.

The compressor housing 21a, 21b, 24a may include a motor accommodating part 21a in which the motor <NUM> is disposed, a mixer accommodating part 21b in which the mixer <NUM> is disposed, and an impeller accommodating part 24a in which the compressor impeller <NUM> is positioned. The mixer accommodating part 21b is positioned between the motor accommodating part 21a and the impeller accommodating part 24a. The motor accommodating part 21a is disposed upstream of the mixer accommodating part 21b. The shaft <NUM> penetrates through the mixer accommodating part 21b to connect the motor <NUM> and the compressor impeller <NUM>.

One end of the motor accommodating part 21a is connected to the air intake pipe <NUM>, and the other end of the motor accommodating part 21a is connected to the mixer accommodating part 21b. One end of the mixer accommodating part 21b is connected to the motor accommodating part 21a, and the other end of the mixer accommodating part 21b is connected to the impeller accommodating part 24a. The gas intake pipe <NUM> is connected to the mixer accommodating part 21b. The suction side of the impeller accommodating part 24a is connected to the mixer accommodating part 21b, and the discharge side of the impeller accommodating part 24a is connected to the engine <NUM>.

The air sucked into the motor accommodating part 21a is accelerated in the mixer accommodating part 21b and mixed with the gas. The mixed gas of the mixer accommodating part 21b is compressed and discharged from the impeller accommodating part 24a. The impeller accommodating part 24a may be connected to a cooler <NUM>. The discharge side of the impeller accommodating part 24a is connected to the mixed gas intake pipe <NUM>. Specifically, the impeller accommodating part 24a is connected to the intake manifold 14a of the engine <NUM> by the mixed gas intake pipe <NUM>.

Here, the mixer <NUM> may include an acceleration unit <NUM> which reduces the cross-sectional area of the mixer accommodating part 21b while progressing toward the compressor impeller <NUM> from the motor <NUM>, and a spray unit <NUM> having a smaller cross-sectional area than the acceleration unit unit <NUM> and having a spray hole 342a connected to the gas intake pipe.

The present invention includes the intake compressor that compresses the mixed gas, and compresses the mixed gas through the intake compressor and supplies the mixer <NUM> to the engine <NUM>, thereby improving the power generation output and improving the efficiency. Further, since the mixed gas is compressed through the intake compressor in the state where the air and the gas are mixed, there is an advantage in that the power generation output is improved while stably supplying fuel without a separate fuel pressurizing device and a regulator.

When the intake compressor is used, the temperature and pressure of the mixed gas flowing to the engine <NUM> become very high. Thus, there is a risk of explosion when such a high temperature and pressure mixed gas flows out to the outside, and the amount of gas becomes relatively smaller when flowing to the engine <NUM>, so that the output may be reduced.

Therefore, the embodiment may further include a cooler <NUM> for cooling the mixed gas compressed by the intake compressor. The cooler <NUM> cools the mixed gas compressed by the intake compressor and provides the mixed gas to the engine <NUM>.

The cooler <NUM> may be disposed between the engine <NUM> and the compressor impeller <NUM> in the mixed gas intake pipe <NUM>. In detail, the cooler <NUM> may include a radiator <NUM> for exchanging heat between the refrigerant and an outside air, an internal heat exchanger <NUM> for exchanging heat between the mixed gas flowing through the mixed gas intake pipe <NUM> and the refrigerant, and a circulation flow path <NUM> which refrigerant flows therein and circulates between the internal heat exchanger <NUM> and the radiator <NUM>. The radiator <NUM> may further include a fan <NUM> that provides air flow to the radiator <NUM>.

When the mixed gas compressed by the cooler <NUM> is cooled, the temperature of the mixed gas is lowered and the volume is reduced. Thus, there is an advantage in that the power generation efficiency can be improved by increasing the amount of fuel supplied to the engine <NUM>, and explosion can be prevented when the mixed gas is leaked.

When the exhaust gas is discharged through the exhaust pipe <NUM>, air pollution is generated due to harmful substances such as nitrogen oxides.

The return pipe <NUM> supplies a part of the exhaust gas discharged through the exhaust pipe <NUM> back to the engine <NUM> so that uncombusted combustion products are re-combusted in the engine and the amount of exhaust gas discharged through the exhaust pipe <NUM> is reduced. Therefore, the combustion efficiency and reliability of the engine are improved, and volatile organic compounds discharged through the exhaust gas can be reduced.

Specifically, the return pipe <NUM> recirculates a part of the exhaust gas flowing into the exhaust pipe <NUM> to the intake pipe <NUM>. The return pipe <NUM> recirculates the exhaust gas by the pressure difference from the exhaust pipe <NUM> which has a relatively high pressure due to the exhaust pressure of the engine to the intake pipe <NUM> which has the same pressure as the outside air.

When the exhaust gas is re-circulated to the intake pipe <NUM> due to the pressure difference, there is an advantage in that a separate compressor <NUM>, a controller for control, or the like is unnecessary.

The catalyst module <NUM> oxidizes/deoxidizes harmful components in the exhaust gas to be harmless. The catalyst module <NUM> is an apparatus that is disposed in the exhaust pipe <NUM>, and oxidizes/deoxidizes harmful CO(carbon monoxide), HC (hydrocarbon), and NOX(nitrogen oxide) in the exhaust gas passing through the catalyst module <NUM> into carbon dioxide(CO2), H2O(water), and N2(nitrogen) which are harmless to the human body.

The catalyst module <NUM> has a pellet type and a monolith type in terms of a structure, and has two types of an oxidation catalytic converter and a three-way catalytic converter in terms of function.

First, the oxidation catalytic converter finely and evenly coats (deposit) a precious metal of palladium (Pd) or palladium + platinum (Pt), which catalyzes the surface of granular alumina called catalytic pellets, on wash and serves to make carbon monoxide and hydrocarbon in the exhaust gas into carbon dioxide and water.

The three-way catalytic converter uses precious metal, such as platinum + rhodium (Rh) or platinum + rhodium + palladium, which performs catalysis, and serves to reduce carbon monoxide, hydrocarbons, and nitrogen oxides in the exhaust gas. Three-way catalytic converter is currently the most used because it has a high efficiency of over <NUM>% at high temperature.

A part of the exhaust gas which passed through the catalyst module <NUM> is re-circulated to the intake pipe <NUM> through the return pipe <NUM>. Therefore, the catalyst module <NUM> primarily reduces harmful substances in the exhaust gas, and secondly, reduces the amount of the exhaust gas by the return pipe <NUM> to reduce the discharge amount of harmful substances.

The embodiment may further include an exhaust gas heat exchanger <NUM> for cooling the exhaust gas. The exhaust gas heat exchanger <NUM> radiates heat of the exhaust gas to lower the temperature of the exhaust gas provided to the return pipe <NUM>.

Therefore, when the temperature of the exhaust gas is lowered by the exhaust gas heat exchanger <NUM>, there is an advantage in that the temperature of the mixed gas in the intake pipe <NUM> is increased by the exhaust gas re-circulated to the intake pipe <NUM> to prevent spontaneous combustion.

For example, as shown in <FIG>, the exhaust gas heat exchanger <NUM> may radiate heat of the exhaust gas while transferring heat of the exhaust gas to the hot water storage tank <NUM>. Specifically, the exhaust gas heat exchanger <NUM> is disposed in the heat medium flow path <NUM> and the exhaust pipe <NUM>. The heat of the exhaust gas is transferred to the hot water supply heat exchanger <NUM> through the heat medium flow path <NUM>, and the heat transferred to the hot water supply heat exchanger <NUM> is transferred to the hot water storage tank <NUM> through the hot water circulation flow path <NUM>.

Therefore, when the exhaust gas heat exchanger <NUM> is connected to the heat medium flow path <NUM>, the heat of the exhaust gas can be reused to heat the hot water storage tank <NUM> without wasting heat by dissipating heat to the outside.

For another example, although not shown in the drawing, the exhaust gas heat exchanger <NUM> may have a structure for exchanging heat between the outside air and the exhaust gas through a heat transfer medium.

A part of the exhaust gas that passed through the catalyst module <NUM> and the exhaust gas heat exchanger <NUM> is re-circulated to the intake pipe <NUM> through the return pipe <NUM> due to the pressure difference between the exhaust pipe <NUM> and the intake pipe <NUM>.

Thus, the return pipe <NUM> is disposed downstream of the catalyst module <NUM> and the exhaust gas heat exchanger <NUM> in the exhaust pipe <NUM>.

The exhaust pipe <NUM> may include a first exhaust pipe <NUM> connecting the engine and the catalyst module <NUM>, a second exhaust pipe <NUM> connecting the catalyst module <NUM> and the exhaust gas heat exchanger <NUM>, and a third exhaust pipe connecting the exhaust gas heat exchanger <NUM> and the outside air. One end of the return pipe <NUM> is connected to the third exhaust pipe to remove harmful components, and the exhaust gas having a lowered temperature is re-circulated to the intake pipe <NUM>, and the re-circulated exhaust gas is provided to the engine <NUM>.

The other end of the return pipe <NUM> may be connected upstream of the intake compressor in the intake pipe <NUM>. Therefore, the exhaust gas re-circulated through the return pipe <NUM> may be compressed with the gas and the air and supplied to the engine <NUM>. More specifically, the other end of the return pipe <NUM> is preferably connected to the air intake pipe <NUM>. That is, the other end of the return pipe <NUM> is connected between the mixer <NUM> and the air filter 41a in the air intake pipe <NUM>.

The exhaust pipe <NUM> may be provided with a sound reduction box <NUM> to reduce the exhaust noise. The sound reduction box <NUM> may be positioned downstream from the catalyst module <NUM>, the exhaust gas heat exchanger <NUM>, and a branch point of the return piping <NUM> in the exhaust pipe <NUM>. Specifically, the sound reduction box <NUM> may be disposed in the third exhaust pipe.

<FIG> is a diagram illustrating the flow of a heat medium and a refrigerant during a heating operation of the cogeneration system of <FIG>.

Referring to <FIG>, first, the circulation process of the heat medium will be described.

The heat medium absorbs waste heat while passing through the engine and the generator <NUM>, and is supplied to the distribution unit <NUM> through the heat medium flow path 11b.

The heat medium supplied to the distribution unit <NUM> passes through the hot water supply heat exchanger <NUM> or the air conditioning heat exchanger <NUM> according to the operation state by the distribution unit <NUM>, and flows back into the power generation unit <NUM> through the heat medium inflow path 11a. The heat medium introduced through the heat medium inflow path 11a is circulated back to the engine and the generator <NUM>, and absorbs waste heat.

Specifically, the heat medium supplied to the distribution unit <NUM> is pressurized by the pump <NUM> and flows into the three-way valve <NUM> during the heating operation, and the heat medium introduced into the three-way valve <NUM> is introduced into the air conditioning heat exchanger <NUM> through the first distribution pipe <NUM>. However, since the first refrigerant is not supplied to the air conditioning heat exchanger <NUM>, heat exchange does not occur between the heat medium and the first refrigerant. The heat medium passed through the air conditioning heat exchanger <NUM> passes through the fourth distribution pipe <NUM> and flows into the heat medium inflow path 11a.

For another example, the heat medium supplied to the distribution unit <NUM> is pressurized by the pump <NUM> and flows into the three-way valve <NUM> during the heating operation, and the heat medium introduced into the three-way valve <NUM> is introduced into the hot water supply heat exchanger <NUM> through the third distribution pipe <NUM>. The heat medium supplied to the hot water supply heat exchanger <NUM> may exchange heat with the second refrigerant in the hot water circulation flow path <NUM>, and supply heat to the hot water storage tank <NUM>.

Hereinafter, the circulation process of the first refrigerant of the cooling cycle of the air conditioner will be described.

In the heating operation, the outdoor heat exchanger <NUM> serves as an evaporator, and the indoor heat exchanger <NUM> serves as a condenser.

The first refrigerant of high temperature and high pressure discharged from the compressor <NUM> is introduced into the indoor heat exchanger <NUM> via the four-way valve <NUM>.

The first refrigerant introduced into the indoor heat exchanger <NUM> is condensed by exchanging heat with the indoor air. The condensed first refrigerant is throttled by the first expansion valve <NUM>.

The controller <NUM> controls to close the intermittent valve <NUM> and to open the adjustment valve <NUM>.

The first refrigerant passed through the first expansion valve <NUM> cannot flow into the bypass pipe <NUM> as the intermittent valve <NUM>, <NUM> is closed, but flows into the outdoor heat exchanger <NUM> to be evaporated.

The first refrigerant passed through the outdoor heat exchanger <NUM> flows into the accumulator via the four-way valve <NUM>. The first refrigerant introduced into the accumulator from the four-way valve <NUM> flows into the compressor <NUM>.

<FIG> is a diagram illustrating the flow of a heat medium and a refrigerant during a cooling operation of the cogeneration system of <FIG>.

Referring to <FIG>, the heat medium supplied to the distribution unit <NUM> is pressurized by the pump <NUM> and flows into the three-way valve <NUM> during the cooling operation, and the heat medium introduced into the three-way valve <NUM> flows into the hot water supply heat exchanger <NUM> through the third distribution pipe <NUM>. The heat medium supplied to the hot water supply heat exchanger <NUM> may exchange heat with the second refrigerant in the hot water circulation flow path <NUM>, and supply heat to the hot water storage tank <NUM>.

In the cooling operation, the outdoor heat exchanger <NUM> serves as a condenser and the indoor heat exchanger <NUM> serves as an evaporator.

The first refrigerant of high temperature and high pressure discharged from the compressor <NUM> is introduced into the outdoor heat exchanger <NUM> via the four-way valve <NUM>.

The first refrigerant introduced into the outdoor heat exchanger <NUM> is condensed by exchanging heat with outdoor air. The condensed first refrigerant is throttled in the second expansion valve <NUM>.

The refrigerant flowing from the four-way valve <NUM> to the outdoor heat exchanger <NUM> has a limit in flowing into the bypass pipe <NUM> due to the check valve <NUM>.

The first refrigerant passed through the outdoor heat exchanger <NUM> flows into the indoor heat exchanger <NUM>. The first refrigerant introduced into the indoor heat exchanger <NUM> is evaporated while exchanging heat with the indoor air.

The first refrigerant introduced into the indoor heat exchanger <NUM> flows into the accumulator via the four-way valve <NUM>. The first refrigerant introduced into the accumulator from the four-way valve <NUM> flows into the compressor <NUM>.

<FIG> is a diagram illustrating the flow of a heat medium and a refrigerant during a defrost operation of the cogeneration system of <FIG>.

Referring to <FIG>, the heat medium supplied to the distribution unit <NUM> is pressurized by the pump <NUM> and flows into the three-way valve <NUM> during the heating operation, and the heat medium introduced into the three-way valve <NUM> is introduced into the air conditioning heat exchanger <NUM> through the first distribution pipe <NUM>. The heat medium supplied to the air conditioning heat exchanger <NUM> exchanges heat with the first refrigerant flowing through the bypass pipe <NUM>. The heat medium supplied to the air conditioning heat exchanger <NUM> transfers heat to the first refrigerant flowing through the bypass pipe <NUM>.

At this time, the air conditioning heat exchanger <NUM> serves as an evaporator.

In the defrosting operation, the air conditioning heat exchanger <NUM> serves as an evaporator, and the indoor heat exchanger <NUM> serves as a condenser.

The controller <NUM> controls to open the intermittent valve <NUM> and to close the adjustment valve <NUM>.

The first refrigerant passed through the first expansion valve <NUM> flows into the bypass pipe <NUM> as the intermittent valve <NUM>, <NUM> is opened, and does not flow into the outdoor heat exchanger <NUM>.

The first refrigerant supplied to the bypass pipe <NUM> is evaporated by heat exchange with the heat medium in the air conditioning heat exchanger <NUM>.

The first refrigerant passed through the air conditioning heat exchanger is introduced into the accumulator via the four-way valve <NUM>. The first refrigerant introduced into the accumulator from the four-way valve <NUM> flows into the compressor <NUM>.

Therefore, even if the frost is generated in the outdoor heat exchanger <NUM>, heat operation can be performed using the waste heat of the engine or generator <NUM>.

<FIG> is a diagram illustrating the flow of a heat medium and a refrigerant during a defrost operation of a cogeneration system according to another embodiment of the present invention.

<FIG> is different from <FIG> in that the intermittent valve and the adjustment valve are changed to a first flow control valve 470a and a second flow control valve 570a, respectively.

The first flow control valve 470a and the second flow control valve 570a may adjust flow rates of the heat medium and the first refrigerant flowing through the bypass pipe and an outdoor unit inlet pipe. When the first flow control valve 470a and the second flow control valve 570a control the flow rate, the amount of the inflow of the first refrigerant expanded in the first expansion valve into the air conditioning heat exchanger and/or the outdoor heat exchanger may be adjusted within a range where the outdoor heat exchanger is not frosted.

The first refrigerant expanded in the first expansion valve may flow into the air conditioning heat exchanger and/or the outdoor heat exchanger according to the opening degree of the first flow control valve 470a and the second flow control valve 570a.

<FIG> is a diagram illustrating a part of a power generation unit according to another embodiment of the present invention.

In comparison with the embodiment of <FIG>, a compressor module 300B of another embodiment has a difference in that a plurality of compressor impellers <NUM> are provided. Hereinafter, it will be described with a focus on the difference from the embodiment of <FIG> and the configuration not specially described is regarded as the same as the embodiment of <FIG>.

The plurality of compressor impellers <NUM> of another embodiment may be disposed in series. In detail, the compressor impeller <NUM> may include a first compressor impeller <NUM> connected to the motor <NUM> by the shaft <NUM>, and a second compressor impeller <NUM>.

The second compressor impeller <NUM> may be rotated together with or separately from the first compressor impeller <NUM>. Specifically, the second compressor impeller <NUM> may be rotated by receiving the rotational force of the first compressor impeller <NUM>.

Specifically, the embodiment may further include a clutch <NUM> connecting or disconnecting the power of the first compressor impeller <NUM> to the second compressor impeller <NUM>. One side of the clutch <NUM> is contacted or non-contacted with the second compressor impeller <NUM>, and the other end of the clutch <NUM> is fixed to a transmission shaft <NUM> connected to the first compressor impeller <NUM>.

The first compressor impeller <NUM> is disposed closer to the motor <NUM> than the second compressor impeller <NUM>, and the mixer <NUM> is positioned between the first compressor impeller <NUM> and the motor <NUM>.

The compressor impeller <NUM> may not be driven, only the first compressor impeller <NUM> may be driven, or the first compressor impeller <NUM> and the second compressor impeller <NUM> may be driven according to the required output of the engine. Therefore, the pressure of the mixed gas may be variously adjusted according to the engine output.

In addition, the compression ratio of the first compressor impeller <NUM> and the compression ratio of the second compressor impeller <NUM> may be different from each other or the same.

In this case, the impeller accommodating part 24a includes a first impeller accommodating part 24b for accommodating the first compressor impeller <NUM> and a second impeller accommodating part 24c for accommodating the second compressor impeller <NUM>.

In comparison with the embodiment of <FIG>, a compressor module 300C of another embodiment has a difference in that a plurality of compressor modules <NUM> are provided. Hereinafter, it will be described with a focus on the difference from the embodiment of <FIG> and the configuration not specially described is regarded as the same as the embodiment of <FIG>.

A plurality of compressor modules <NUM> of another embodiment may be provided in parallel. Specifically, the compressor module <NUM> includes a first compressor module <NUM>-<NUM> and a second compressor module <NUM>-<NUM>, the first compressor module <NUM>-<NUM> is connected to a first air intake pipe <NUM>-<NUM>, and the second compressor module <NUM>-<NUM> is connected to a second air intake pipe <NUM>-<NUM>. One end of the first air intake pipe <NUM>-<NUM> and one end of the second air intake pipe <NUM>-<NUM> are connected to the outside air. The gas intake pipe <NUM> is connected to the mixer <NUM> of the first compressor module <NUM>-<NUM> and the second compressor module <NUM>-<NUM>.

The first compressor module <NUM>-<NUM> and the second compressor module <NUM>-<NUM> are connected to the mixed gas intake pipe <NUM>. The mixed gas intake pipe <NUM> may include a main pipe <NUM> having one end connected to the engine <NUM>, a first branch pipe <NUM> having one end which is connected to the main pipe <NUM> and the other end which is connected to the first compressor module <NUM>-<NUM>, and a second branch pipe <NUM> having one end which is connected to the main pipe <NUM> and the other end which is connected to the first compressor module <NUM>-<NUM>. The first branch pipe <NUM> and the second branch pipe <NUM> may be provided with a check valve 241a, 242a to prevent the back flow of the mixed gas.

A single compressor module <NUM> is driven at a low engine load, and two compressor modules <NUM> are driven at a high load to improve the engine output. In consideration of the durability of the compressor module <NUM> according to the operation of each compressor module <NUM>, the durability of the compressor module <NUM> can be improved through a sequential control based on the operating time, and normal operation can be achieved even in case of failure of a single compressor module <NUM>. The first compressor module <NUM>-<NUM> and a compression ratio of the first compressor module <NUM>-<NUM> may be different from each other or the same.

According to the cogeneration system of the present invention, there are one or more of the following effects.

First, since the intake compressor for compressing the mixed gas is provided so that the mixed gas is compressed and supplied to the engine, the power generation output is improved and the efficiency is improved.

Second, since the mixed gas is compressed through the intake compressor in a state where air and gas are mixed, there is an advantage in that the power generation output is improved while stably supplying fuel without a separate fuel pressurization apparatus and a regulator.

Third, since the mixer for supplying gas and the intake compressor for compressing the mixed gas are configured as a single module, there is an advantage of reducing the volume of the product and preventing leakage of the mixed gas.

Fourth, since a motor-type intake compressor is used and a plurality of impellers are connected in parallel or in series, there is an advantage in that precise compression ratio control can be achieved.

Fifth, by disposing the impeller in a place in which the mixed gas flows and by disposing the motor in a place in which the air flows, when the fuel smoothly introduced in the mixer and a short circuit occurs in the electric line controlling the motor, there is an advantage of preventing the mixed gas from combusting.

Sixth, since the mixed gas is compressed through the intake compressor and then cooled again, there is an advantage of improving power generation efficiency by increasing the amount of fuel supplied to the engine, and preventing explosion of the mixed gas in case of leakage.

The effects of the present invention are not limited to the above-mentioned effects, and other effects not mentioned will be clearly understood by those skilled in the art from the description of the claims.

Claim 1:
A cogeneration system comprising:
an intake pipe (<NUM>) one end of which communicating with outside air and another end of which being connected to an engine (<NUM>), the intake pipe (<NUM>) having a motor accommodating part, a mixer accommodating part and an impeller accommodating part;
a mixer (<NUM>) disposed in the mixer accommodating part of the intake pipe (<NUM>) to supply gas into the intake pipe; and
an intake compressor (<NUM>) for compressing a mixed gas which is a mixture of the air and the gas;
wherein the intake compressor (<NUM>) comprises:
a motor (<NUM>) disposed in the motor accommodating part of the intake pipe (<NUM>); and
a compressor impeller (<NUM>) disposed in the impeller accommodating part of the intake pipe (<NUM>) and rotated by the motor (<NUM>) to compress the mixed gas, wherein the mixer (<NUM>) is positioned between the motor (<NUM>) and the compressor impeller (<NUM>) in the intake pipe (<NUM>), and wherein the motor (<NUM>) is disposed upstream of the mixer (<NUM>),
wherein the mixer (<NUM>) comprises:
an acceleration unit (<NUM>) for reducing a cross-sectional area of the mixer accommodating part while progressing toward the compressor impeller (<NUM>) from the motor (<NUM>); and
a spray unit (<NUM>) having a smaller cross-sectional area than the acceleration unit (<NUM>) and provided with a spray hole (342a) connected to a gas intake pipe (<NUM>) of the intake pipe (<NUM>),
wherein the intake compressor (<NUM>) further comprises a shaft (<NUM>) connecting the motor (<NUM>) and the compressor impeller (<NUM>),
wherein the spray unit (<NUM>) and the acceleration unit (<NUM>) are disposed to surround the shaft (<NUM>),
wherein the spray unit (<NUM>) is disposed closer to the compressor impeller (<NUM>) than the acceleration unit (<NUM>).