KR101993724B1 - A gas heat-pump system - Google Patents

Abstract

The present invention relates to a gas heat pump system.
A gas heat pump system according to an embodiment of the present invention includes a compressor, an outdoor heat exchanger, an expansion device, an air conditioning module including an indoor heat exchanger and a refrigerant pipe, and a mixer in which fuel and air are mixed, The engine module includes a mixer that mixes and discharges the air and the fuel, and a supercharger that compresses the mixed air discharged from the mixer, An intercooler for receiving the compressed air from the supercharging means and cooling it by a heat exchange system to increase the density thereof and discharging the mixed air; And an intake manifold for introducing the mixer supplied from the regulating means, wherein the first mixer of the intake manifold, The inlet and the discharge port of the first mixer control means is directly connected.

Description

A gas heat-pump system

The present invention relates to a gas heat pump system.

The heat pump system is a system equipped with a refrigeration cycle capable of performing cooling or heating operation, and can be interlocked with a hot water supply device or a cooling / heating device. That is, hot water can be produced using a heat source obtained by heat exchange between a refrigerant in a refrigeration cycle and a predetermined heat storage medium, or air conditioning for cooling and heating can be performed.

The refrigeration cycle includes a compressor for compressing the refrigerant, a condenser for condensing the refrigerant compressed in the compressor, an expansion device for decompressing the refrigerant condensed in the condenser, and an evaporator for evaporating the decompressed refrigerant.

The heat pump system includes a gas heat pump system. Large-capacity compressors are required for air conditioning in industrial buildings and large buildings, not for home use. That is, a gas heat pump system can be used as a system using a gas engine instead of an electric motor to drive a compressor for compressing a large amount of refrigerant into a high-temperature and high-pressure gas.

The gas heat pump system includes an engine that generates power by using a mixture of fuel and air (hereinafter referred to as a mixer). As an example, the engine may include a cylinder to which the mixer is fed, and a piston that is movably provided in the cylinder.

The gas heat pump system includes an air supply device for supplying a mixer to the engine, and a mixer for mixing the fuel supply device and the air and the fuel.

The air supply device may include an air filter for purifying the air. The fuel supply apparatus includes a zero governor for supplying fuel with a constant pressure.

The zero governor can be understood as an apparatus for regulating and supplying the outlet pressure uniformly, without regard to the change in the magnitude of the inlet pressure or the flow rate of the fuel). For example, the zero governor may include a nozzle unit for reducing the pressure of the fuel, a diaphragm acting on the reduced pressure in the nozzle unit, and a valve device opened and closed by the operation of the diagram .

The air passing through the air filter and the fuel discharged from the zero governor may be mixed in the mixer (mixer) and supplied to the engine.

When the mixer supplied to the engine is burned, the exhaust gas can be discharged from the engine. The gas heat pump system further includes a muffler for reducing noise generated in the exhaust gas.

The prior art related to the conventional gas heat pump system is as follows.

1. Registration number (Registration date): 10-1341533 (December 9, 2013)

2. Title of the invention: Gas heat pump system and its control method

The conventional gas heat pump uses a gas engine that uses a residential LNG or LPG as a heat source to circulate the compressor refrigerant, operates in a cooling mode in summer, and operates in a heating mode in winter.

However, there is a problem that when the gas is supplied to the gas engine by the natural intake method and the LNG or LPG for the housing is supplied by the fuel, the output of the gas engine is reduced due to the low supply pressure (1 to 2.5 kPa).

Also, in summer, the gas heat pump system operates in the cooling mode to lower the indoor temperature. When the outdoor temperature is high, the hot air is supplied to the gas engine due to the high temperature.

As a result, low-density air is supplied to the gas engine, thereby reducing the output of the gas engine. As a result, the output of the gas engine can not keep up with the high cooling load, which may cause the cooling failure.

In order to solve this problem, when the supply pressure (about 2.5 kPa) of the gaseous fuel is supplied to the supercharging pressure (about 30 kPa) by supplying air while adjusting the amount of fuel according to the amount of air after the air is pressurized with a supercharger, The fuel supply becomes difficult.

Meanwhile, when components such as a mixer, a supercharging unit, an intercooler, a control unit, and the like are additionally provided, the components are fixed to the structure separated from the engine. Thus, the piping must be connected to the intake manifold of the engine and the exhaust manifold, There is a problem that the total length of the guide member becomes longer.

In addition, since the length of the piping is long to make the structure complicated and the fastening members for fixing the respective components are separately provided, the structure becomes more complicated and the area occupied by the respective components becomes larger, There was also a problem.

When the components such as the mixer, the supercharging means, the intercooler, and the adjusting means are fixed to the structure separate from the engine, the engine and the respective components do not vibrate in the same direction and vibrate in the opposite direction, There is a problem that the connection portion of the connection pipe and the pipe is broken by the vibration of the pipe.

Further, when the flow length of the mixer becomes long due to the mixing of fuel and air, the risk of explosion increases.

In addition, when the mixer, the supercharging unit, the intercooler, the adjusting unit, and the like are additionally provided for compressing the fuel-air mixture and supplying the mixture to the engine, the flow path of the air- So that the flow resistance of the mixer is inevitably increased. Therefore, it is necessary to change the shape and arrangement of the intake manifold and the adjusting means so that the flow resistance of the mixer can be minimized.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a gas heat pump system in which the performance of an engine can be improved by supercharging a mixer supplied to an engine.

Another object of the present invention is to provide a gas heat pump system which can improve the maximum output of the engine without increasing the size of the engine.

Another object of the present invention is to provide a gas heat pump system in which the intercooler is mounted to lower the temperature of the mixer supplied to the engine and increase the density to improve the volume efficiency of the engine.

It is another object of the present invention to provide a gas heat pump system in which an intake manifold is directly connected to an outlet of an adjusting means so that the adjusting means can be fixed to the intake manifold, do.

Further, even if the shape of the flow path through which the mixer flows becomes complicated, the length of the flow path through which the mixer flows is minimized, and the design is made so that the direction of the mixer in the intercooler and the direction in which the mixer flows in the intake manifold are smoothly connected. And it is an object of the present invention to provide a gas heat pump system capable of minimizing the resistance.

It is another object of the present invention to provide a gas heat pump system in which components such as a supercharging means, an intercooler, and a control means are fixed to an engine, not a separate structure separated from an engine, do.

Further, as each of the parts is fixed to the engine, the interval between the adjusting means and the intake manifold, the supercharging means and the exhaust manifold, the interval between the intercooler and the supercharging means and the adjusting means can be reduced to reduce the length of the entire piping, And to provide a gas heat pump system capable of reducing the amount of heat generated by the heat pump.

In addition, since parts such as the supercharging unit, the intercooler, and the adjusting unit are fixed to the engine, it is possible to prevent a relative motion phenomenon in which components such as the supercharging unit, the intercooler, It is possible to reduce the vibration applied to the piping and the connecting portion and to prevent the phenomenon that the piping and various connection portions are loosened or broken by the vibration, thereby providing a gas heat pump system which can enhance the durability and prevent the safety accident .

Another object of the present invention is to provide a gas heat pump system in which the adjustment means is directly connected to the intake manifold, so that the supply amount of the mixer can be adjusted more precisely.

Another object of the present invention is to provide a gas heat pump system in which a pipe connecting the air filter and the mixer is formed in a straight line to minimize the suction resistance of air.

In addition, an oil supply line may be installed so that a part of the oil used in the engine passes through the rotary shaft of the supercharger, so that the lubrication to the supercharger can proceed without a separate oil supply device, and the oil passing through the supercharger can pass through the engine oil cooler And it is an object of the present invention to provide a gas heat pump system capable of preventing the temperature of the oil supplied to the supercharger from rising, thereby preventing oil carbonization and damage to the turbocharger.

A gas heat pump system capable of preventing safety accidents such as corrosion and explosion by driving the engine until the engine stops when the mixer is stopped and the residual mixer is burnt or discharged outside to suppress the formation of formic acid And to provide the above objects.

A gas heat pump system according to an embodiment of the present invention includes a compressor, an outdoor heat exchanger, an expansion device, an air conditioning module including an indoor heat exchanger and a refrigerant pipe, and a mixer in which fuel and air are mixed, The engine module includes a mixer for mixing and discharging the air and the fuel, a supercharging unit for supplying compressed air to the mixer discharged from the mixer, An intercooler supplied with the mixed fuel compressed by the supercharging means, cooled by a heat exchange system to increase its density, and then discharged; and a control unit for controlling the amount of mixed fuel discharged from the intercooler, And an intake manifold for introducing the mixture supplied from the regulating means, wherein the first mixer oil of the intake manifold The inlet and the first mixer outlet of the adjusting means are directly connected.

Further, the supercharging means is formed adjacent to an exhaust manifold formed on the first surface of the engine, and the regulating means is disposed adjacent to the intake manifold formed on the second surface of the engine opposite to the first surface And the intercooler may be fixed to the first surface and the third surface in a direction intersecting the second surface.

Further, the intercooler may be arranged above the supercharging means or the adjusting means.

In addition, the intercooler may be formed with a downwardly inclined discharge pipe for discharging the mixer toward the intake manifold.

Between the discharge pipe and the second mixer inlet of the regulating means, a connecting pipe for guiding the flow of the mixer from the upper side to the lower side may be provided.

Also, the mixer discharge port of the regulating means is formed to face downward, and the mixer inlet of the intake manifold may be formed to face upward.

The intake manifold may include a main portion for guiding the mixer introduced in the downward direction of the mixer inlet in the horizontal direction and a mixer for guiding the mixer guided in the horizontal direction in the vertical direction, And may include a plurality of branching sections for supplying the plurality of branching sections.

In addition, the intake manifold may be disposed so as to be flush with the second surface of the engine.

The engine module may further include an exhaust gas heat exchanger for exchanging heat between the exhaust gas passing through the supercharging means and the cooling water.

Further, the mixer may be fixed to the intercooler.

The engine module may further include an air filter for purifying the outside air,

At least a part of the air pipe connecting the air filter and the mixer may be formed in a straight line.

In addition, the air filter and the mixer may be fixed to the same height.

Further, a cooling water pump for generating a flow of cooling water for cooling the engine and a cooling module connected to the cooling water pump and including a cooling water pipe for guiding the flow of the cooling water may be included.

According to the present invention, there is an advantage that a mixture of fuel and air supplied to the gas engine can be supplied to the engine at a higher pressure than the natural intake by using supercharging means to improve the volume efficiency.

In addition, there is an advantage that the engine and the entire system can be downsized.

In addition, there is an advantage that a compact gas engine can realize a large-capacity gas engine heat pump system.

In addition, there is an advantage that the gas engine heat pump (GHP) using the residential gas fuel can raise the engine output.

There is also an advantage that the temperature of the mixer supplied to the engine can be lowered and the density can be increased to improve the volume efficiency of the engine.

Further, since the outlet of the adjusting means and the intake manifold are directly connected, the adjusting means can be fixed to the intake manifold, and the structure can be made compact, so that the intake resistance can be reduced.

Further, even if the shape of the flow path through which the mixer flows becomes complicated, the length of the flow path through which the mixer flows is minimized, and the design is made so that the direction of the mixer in the intercooler and the direction in which the mixer flows in the intake manifold are smoothly connected. There is also an advantage of minimizing the resistance.

Also, there is an advantage that components such as the supercharging means, the intercooler, the adjusting means and the like can be fixed to the engine itself, not the separate structure separated from the engine, so that the structure for fixing the respective components can be omitted.

Further, as each of the parts is fixed to the engine, the interval between the adjusting means and the intake manifold, the supercharging means and the exhaust manifold, the interval between the intercooler and the supercharging means and the adjusting means can be reduced to reduce the length of the entire piping, There is also an advantage to reduce.

In addition, since parts such as the supercharging unit, the intercooler, and the adjusting unit are fixed to the engine, it is possible to prevent a relative motion phenomenon in which components such as the supercharging unit, the intercooler, It is possible to reduce the vibration applied to the piping and the connecting portion and prevent the phenomenon that the piping and various connecting portions are loosened or broken by the vibration, thereby enhancing the durability and preventing safety accidents.

Further, there is an advantage that the adjustment means can be directly connected to the intake manifold, so that the supply amount adjustment of a more precise mixer can be achieved.

In addition, the piping connecting the air filter and the mixer is formed as a straight line, thereby minimizing the suction resistance of the air.

In addition, an oil supply line may be installed so that a part of the oil used in the engine passes through the rotary shaft of the supercharger, so that the lubrication to the supercharger can proceed without a separate oil supply device, and the oil passing through the supercharger can pass through the engine oil cooler As a result, the temperature of the oil supplied to the turbocharger is prevented from rising, and the oil carbonization and the damage of the supercharger can be prevented.

In addition, there is an advantage that a safety accident such as corrosion and explosion of components can be prevented by driving the engine until the engine stops when the mixture is stopped from flowing, and by suppressing the generation of formic acid by burning or discharging the residual mixer to the outside.

1 is a cycle diagram showing a configuration of a gas heat pump system according to a first embodiment of the present invention.
2 is a cycle diagram showing the flow of refrigerant, cooling water, and mixed fuel during the heating operation of the gas heat pump system.
3 is a cycle diagram showing the flow of refrigerant, cooling water and mixed fuel in the cooling operation of the gas heat pump system.
4 is a system diagram showing an example of an engine module which is a part of the present invention.
5 is a perspective view of an engine module, which is a component of the present invention, viewed from an intake manifold direction.
FIG. 6 shows the flow of air in the engine module shown in FIG.
7 is an exploded perspective view of an engine module which is a part of the present invention.
8 is a diagram showing the configuration of an engine module without the conventional supercharging capability.
FIG. 9 is a view showing a configuration of an engine module having a supercharging function according to the present invention.
10 is a perspective view of an engine module provided with a cooling water pump.

Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. It is to be understood, however, that the spirit of the invention is not limited to the embodiments shown and that those skilled in the art, upon reading and understanding the spirit of the invention, may easily suggest other embodiments within the scope of the same concept.

1 is a cycle diagram showing the configuration of a gas heat pump system according to an embodiment of the present invention.

Referring to Fig. 1, the gas heat pump system 10 according to the first embodiment of the present invention includes a plurality of components constituting a refrigerant cycle as an air conditioning system. The refrigerant cycle includes a compressor 110 for compressing the refrigerant, an oil separator 115 for separating the oil in the refrigerant compressed by the compressor 110, and an oil separator 115 And the four sides 117 for switching.

The gas heat pump system (10) further includes an outdoor heat exchanger (120) and an indoor heat exchanger (140). The outdoor heat exchanger 120 may be disposed inside an outdoor unit disposed on the outdoor side, and the indoor heat exchanger 140 may be disposed inside an indoor unit disposed on the indoor side. The refrigerant passing through the four sides 117 flows into the outdoor heat exchanger 120 or the indoor heat exchanger 140.

On the other hand, the configurations of the system shown in Fig. 1 can be disposed on the outdoor side, i.e., inside the outdoor unit, except for the indoor heat exchanger 140 and the indoor expansion unit 145. [

More specifically, when the system 10 is operated in the cooling operation mode, the refrigerant passing through the four sides 117 flows to the indoor heat exchanger 140 side via the outdoor heat exchanger 120. On the other hand, when the system 10 is operated in the heating operation mode, the refrigerant passing through the four sides 117 flows to the outdoor heat exchanger 120 side via the indoor heat exchanger 140.

The system 10 further includes a refrigerant pipe 170 (solid line flow path) for connecting the compressor 110, the outdoor heat exchanger 120, and the indoor heat exchanger 140 to guide the flow of the refrigerant.

The configuration of the system 10 will be described with reference to a cooling operation mode.

The refrigerant that has flowed to the outdoor heat exchanger 120 can be condensed by heat exchange with the outside air. One side of the outdoor heat exchanger (120) includes an outdoor fan (122) for blowing outdoor air.

At the outlet side of the outdoor heat exchanger (120), a main expansion device (125) for depressurizing the refrigerant is provided. For example, the main expansion device 125 includes an electronic expansion valve (EEV). During the cooling operation, the main expansion device 125 is fully opened and does not perform the depressurizing action of the refrigerant.

On the outlet side of the main expansion device (125), there is provided a supercooling heat exchanger (130) for further cooling the refrigerant. A supercooling flow path 132 is connected to the supercooling heat exchanger 130. The supercooling flow path 132 is branched from the refrigerant pipe 170 and connected to the supercooling heat exchanger 130.

The supercooling flow path 132 is provided with a supercooling expansion device 135. The refrigerant flowing through the supercooling passage 132 may be decompressed while passing through the supercooling expansion device 135.

In the supercooling heat exchanger 130, heat exchange may be performed between the refrigerant of the refrigerant pipe 170 and the refrigerant of the supercooling flow path 132. In the heat exchange process, the refrigerant in the refrigerant pipe 170 is subcooled, and the refrigerant in the supercooling passage 132 absorbs heat.

The supercooling flow path (132) is connected to the gas-liquid separator (160). The refrigerant in the supercooling flow path 132, which is heat-exchanged in the supercooling heat exchanger 130, may be introduced into the gas-liquid separator 160.

The refrigerant in the refrigerant pipe 170 that has passed through the supercooling heat exchanger 130 flows to the indoor unit side and is decompressed in the indoor expansion unit 145 and evaporated in the indoor heat exchanger 140. The indoor expansion device 145 may be installed inside the indoor unit and may include an electronic expansion valve (EEV).

The refrigerant evaporated in the indoor heat exchanger (140) flows to the auxiliary heat exchanger (150) via the four sides (117). The auxiliary heat exchanger (150) is a heat exchanger capable of performing heat exchange between the evaporated low-pressure refrigerant and the high-temperature cooling water, for example, a plate heat exchanger may be included.

Since the refrigerant evaporated in the indoor heat exchanger (140) can be absorbed while passing through the auxiliary heat exchanger (150), the evaporation efficiency can be improved. The refrigerant passing through the auxiliary heat exchanger (150) may be introduced into the gas-liquid separator (160).

The refrigerant having passed through the auxiliary heat exchanger 150 is separated from the gas-liquid separator 160 by the gas-liquid separator 160, and the separated gaseous refrigerant can be sucked into the compressor 110.

The refrigerant vaporized in the indoor heat exchanger 140 may flow into the gas-liquid separator 160 immediately after passing through the four sides 117. The separated gaseous refrigerant may be sucked into the compressor 110 .

The gas heat pump system 10 further includes a cooling water tank 305 for storing cooling water for cooling the engine 200 and a cooling water pipe 360 for guiding the flow of the cooling water. The cooling water pipe 360 is provided with a cooling water pump 300 for generating the flow of the cooling water, a plurality of flow switching units 310 and 320 for switching the flow direction of the cooling water, and a radiator 330 for cooling the cooling water. Can be installed.

The plurality of flow switching units 310 and 320 include a first flow switching unit 310 and a second flow switching unit 320. For example, the first flow switching unit 310 and the second flow switching unit 320 may include a three-way valve.

The radiator 330 may be installed at one side of the outdoor heat exchanger 120. The cooling water of the radiator 330 is heat-exchanged with the outside air by driving the outdoor fan 122, have.

When the cooling water pump 300 is driven, the cooling water stored in the cooling water tank 305 passes through the engine 200 and the exhaust gas heat exchanger 240, which will be described later, The refrigerant can be selectively flowed to the radiator 330 or the auxiliary heat exchanger 150 through the flow switching unit 320.

The gas heat pump system 10 includes an engine 200 generating power for driving the compressor 110 and a mixer 220 disposed at an inlet side of the engine 200 to supply mixed fuel do.

The gas heat pump system 10 includes an air filter 210 for supplying purified air to the mixer 220 and a zero governor 230 for supplying fuel below a predetermined pressure ). The zero governor can be understood as a device for regulating and supplying the outlet pressure uniformly regardless of the change in the magnitude or the flow rate of the inlet pressure of the fuel.

The air passing through the air filter 210 and the fuel discharged from the zero governor 230 are mixed in the mixer 220 to form a mixer. The mixer may be supplied to the engine 200.

The gas heat pump system 10 includes an exhaust gas heat exchanger 240 and an exhaust gas heat exchanger 240, which are provided at the outlet side of the engine 200 and into which exhaust gas is introduced after the mixture is combusted, And a muffler 250 for reducing the noise of the exhaust gas. In the exhaust gas heat exchanger 240, heat exchange can be performed between the cooling water and the exhaust gas.

An oil tank 205 for supplying oil to the engine 200 may be provided at one side of the engine 200.

Meanwhile, as described above, the engine 200 applied to the gas heat pump system 10 uses household LNG, LPG, or the like as fuel.

However, there is a problem that the output of the engine 200 is reduced due to the low supply pressure (1 to 2.5 kPa) when supplying the residential LNG or LPG as fuel while supplying air to the engine 200 by the natural intake system .

In summer, the gas heat pump system 10 operates in a cooling mode to lower the temperature of the room. When the outdoor temperature is high, high temperature air is supplied to the engine 200 due to the high temperature.

Accordingly, low-density air is supplied to the engine 200, and the output of the engine 200 is reduced. As a result, the output of the engine 200 can not keep up with the high cooling load, which may cause the cooling failure.

In order to solve this problem, when the supply pressure (about 2.5 kPa) of the gaseous fuel is supplied to the supercharging pressure (about 30 kPa) by supplying air while adjusting the amount of fuel according to the amount of air after the air is pressurized with a supercharger, The fuel supply becomes difficult.

In the case of the present invention, the supercharging means 400 and the adjusting means 600 are provided between the mixer 220 and the engine 200 in order to solve such a problem.

In detail, the supercharging means 400 compresses the discharged air-fuel mixture and discharges the air-fuel mixture to the engine 200 after the air and the fuel are mixed in the mixer 220. At this time, the supercharger 400 can compress the air and the fuel to atmospheric pressure or higher in the mixer 220.

For example, the supercharging means 400 is provided as a turbocharger driven by the exhaust gas of the engine 200.

As another example, the supercharging means 400 may be provided as a supercharger driven by the power of the engine 200 or an electric motor.

The regulating means 600 is disposed between the supercharging means 400 and the engine 200 to regulate the amount of the compressed mixture supplied to the engine 200.

For example, the control means 600 may be a valve using an electronic throttle control (ETC) method.

According to the present invention, fuel and air are mixed in the mixer 220, pressurized in the supercharging means 400 at a high pressure, and then supplied to the engine 200. Also, the amount of the high-pressure mixer (air + fuel) supplied to the engine 200 through the regulating means 600 may be precisely controlled.

Therefore, the efficiency of the engine 200 can be improved. Further, the maximum output amount of the engine 200 can be increased without increasing the size of the engine 200. [ That is, the output of a large engine can be realized with a small engine.

On the other hand, when the mixer passes through the supercharging means 400 as described above, the pressure and the temperature of the mixer rise. In this case, the density of the mixer sucked into the engine 200 is reduced, and the volume efficiency of the engine is inevitably lowered.

In order to solve this problem, in order to solve this problem, a high-temperature high-pressure mixer discharged from the supercharging means 400 is cooled between the supercharging means 400 and the regulating means 600 to reduce the volume and improve the density And an intercooler 500 for discharging the air.

For example, the intercooler 500 can heat-exchange external air or cooling water with the mixer.

According to this, there is an advantage that the volume efficiency of the engine 200 can be improved by lowering the temperature of the mixer supplied to the engine 200 and increasing the density.

If the supercharging unit 400 and the intercooler 500 are provided between the mixer 220 and the engine 200 as described above, the length of the flow path in which the mixer stays is inevitably long. At this time, if there is a large amount of water in the air, the mixer reacts with water to generate formic acid, thereby damaging the piping, thereby causing explosion.

The engine 200 is driven from the closed state of the control means 600 to the stop of the engine 200 so that the mixture is burned Or can be discharged to the outside to suppress formation of formic acid, and it is possible to prevent danger such as pipe breakage and explosion.

Further, the intercooler 500 may be made of a corrosion-resistant material (for example, STS 316).

The cooling water pipe 360 includes a first pipe 361 extending from the cooling water tank 305 toward the engine 200. In detail, the first pipe 361 includes a first pipe portion extending from the cooling water tank 305 to the exhaust gas heat exchanger 240 and a second pipe portion extending from the exhaust gas heat exchanger 240 to the engine 200 And a second piping section. The cooling water supplied from the cooling water tank 305 is heat-exchanged with the exhaust gas through the exhaust gas heat exchanger 240 and flows into the engine 200 to recover the waste heat of the engine 200. The cooling water pump 300 for generating a flow of cooling water may be installed in the first pipe 361.

The cooling water pipe 360 further includes a second pipe 362 for guiding cooling water that has passed through the engine 200 to the first flow switching unit 310.

The cooling water pipe 360 further includes a third pipe 363 for guiding cooling water from the first flow switching unit 310 to the second flow switching unit 320.

The cooling water pipe 360 further includes a fourth pipe 364 for guiding the cooling water from the second flow switching unit 320 to the auxiliary heat exchanger 150.

The cooling water pipe 360 further includes a fifth pipe 365 for guiding cooling water from the second flow switching unit 320 to the radiator 150.

The cooling water pipe 360 further includes a sixth pipe 366 for guiding cooling water from the first flow switching unit 310 to the first pipe 361.

For example, when the temperature of the cooling water passing through the engine 200 is lower than the set temperature, the cooling water flows to the auxiliary heat exchanger 150 or the radiator 330 to reduce the effect of heat exchange, The cooling water flowing into the flow switching unit 310 can be bypassed to the first pipe 361 through the sixth pipe 366. The sixth pipe 366 may be referred to as "bypass pipe ".

The gas heat pump system 10 may further include a cooling water temperature sensor 290 disposed at the outlet of the engine 200 for sensing the temperature of the cooling water passing through the engine 200.

Hereinafter, the operation of the refrigerant, the cooling water and the mixed fuel according to the operation mode of the gas heat pump system 10 according to the first embodiment of the present invention will be described.

2 is a cycle diagram showing the flow of refrigerant, cooling water, and mixed fuel during the heating operation of the gas heat pump system.

When the gas heat pump system 10 performs the heating operation, the refrigerant passes through the compressor 110, the oil separator 115, the four sides 117, the indoor heat exchanger 140, and the supercool heat exchanger 130 The refrigerant is decompressed in the main expansion device 125 and heat-exchanged in the outdoor heat exchanger 120, and then flows into the four sides 117 again. Here, the indoor heat exchanger 140 may function as a "condenser" and the outdoor heat exchanger 120 may function as an "evaporator. &Quot;

The refrigerant that has passed through the four sides 117 flows into the auxiliary heat exchanger 150 and can be heat-exchanged with the cooling water flowing through the fourth pipe 364. [ The coolant flowing into the auxiliary heat exchanger 150 forms a low temperature and a low pressure as evaporative coolant and the coolant supplied to the auxiliary heat exchanger 150 forms a high temperature by the heat of the engine 200. Therefore, the refrigerant of the auxiliary heat exchanger (150) absorbs heat from the cooling water, and the evaporation performance can be improved.

The refrigerant heat-exchanged in the auxiliary heat exchanger (150) flows into the gas-liquid separator (160), is phase-separated and then sucked into the compressor (110). The refrigerant can be repeatedly cycled through the above cycle.

Meanwhile, when the cooling water pump 300 is driven, the cooling water discharged from the cooling water pump 300 flows into the exhaust gas heat exchanger 240 along the first pipe 361 and is heat-exchanged with the exhaust gas. The cooling water discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200 and flows into the first flow switching unit 310 via the second pipe 362, Lt; / RTI >

The cooling water flowing through the first flow switching unit 310 is directed to the second flow switching unit 320 along the third pipe 363 under the control of the first flow switching unit 310. [ The cooling water passing through the second flow switching unit 320 flows into the auxiliary heat exchanger 150 via the fourth pipe 364 and can be heat-exchanged with the refrigerant. The cooling water passing through the auxiliary heat exchanger (150) flows into the cooling water pump (300). The cooling water can be circulated by repeating this cycle.

On the other hand, the flow of cooling water to the radiator 330 during heating operation can be restricted. Generally, since the heating operation is performed when the temperature of the outside air is low, there is a high possibility that the cooling water is cooled in the process of flowing through the cooling water pipe 360 even if the cooling water is not cooled by the radiator 330. Accordingly, the first and second flow switching units 310 and 320 can be controlled so that the cooling water does not pass through the radiator 330 during the heating operation.

However, when the heat exchange in the auxiliary heat exchanger 150 is not required, the cooling water may flow from the second flow switching unit 320 to the radiator 330 via the fifth pipe 365 have.

The driving of the engine 200 will be described.

The air filtered by the air filter 210 and the fuel regulated through the zero governor 230 are mixed in the mixer 220. The mixer mixed in the mixer 220 is pressurized by the supercharger 400, and the pressurized mixer is cooled in the intercooler 500 to improve the density. The amount of the mixed gas passing through the intercooler 500 is adjusted through the adjusting means 600 and supplied to the engine 200 to drive the engine 200. The exhaust gas discharged from the engine 200 flows into the exhaust gas heat exchanger 240, exchanges heat with the cooling water, and is discharged to the outside through the muffler 250.

3 is a cycle diagram showing the flow of refrigerant, cooling water and mixed fuel in the cooling operation of the gas heat pump system.

When the gas heat pump system 10 performs the cooling operation, the refrigerant passes through the compressor 110, the oil separator 115, the four sides 117, the outdoor heat exchanger 120, and the supercool heat exchanger 130 The refrigerant is depressurized in the indoor expansion device 145 and is heat-exchanged in the indoor heat exchanger 140 and flows into the four sides 117 again. Here, the outdoor heat exchanger 120 may function as a "condenser" and the indoor heat exchanger 120 may function as an "evaporator. &Quot;

The refrigerant passing through the four sides 117 flows into the auxiliary heat exchanger 150 and can be heat-exchanged with the cooling water flowing through the cooling water pipe 360. The refrigerant heat-exchanged in the auxiliary heat exchanger (150) flows into the gas-liquid separator (160), is phase-separated and then sucked into the compressor (110). The refrigerant can be repeatedly cycled through the above cycle.

On the other hand, when the coolant pump 300 is driven, the coolant discharged from the coolant pump 300 flows into the exhaust gas heat exchanger 240 and is heat-exchanged with the exhaust gas. The cooling water discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200 and flow into the first flow switching unit 310. The coolant flow until the coolant flows into the first flow switching unit 310 is the same as the coolant flow during the heating operation.

The cooling water that has passed through the first flow switching unit 310 flows into the second flow switching unit 320 and flows to the radiator 330 under the control of the second flow switching unit 320, . The cooling water cooled by the radiator (330) flows into the cooling water pump (300). The cooling water can be circulated by repeating this cycle.

On the other hand, the flow of cooling water to the auxiliary heat exchanger (150) during the cooling operation can be restricted. Generally, since the cooling operation is performed when the temperature of the outside air is high, heat absorption of the evaporation refrigerant for securing the evaporation performance may not be required. Therefore, the first and second flow switching units 310 and 320 can be controlled so that the cooling water does not pass through the auxiliary heat exchanger 150 during the cooling operation.

However, when it is necessary to perform heat exchange in the auxiliary heat exchanger 150, the cooling water may flow into the auxiliary heat exchanger 150 via the second flow switching unit 320.

The operation of the engine 200 is the same as that in the heating operation, and thus a detailed description thereof will be omitted.

4 is a system diagram showing an example of an engine module which is a part of the present invention.

Referring to FIG. 4, the supercharging means 400 may be provided with a turbocharger.

The turbo charger rotates the turbine 411 using the exhaust gas discharged from the engine 200, presses (compresses) the introduced gas by the rotational force, and discharges the gas.

Therefore, when the supercharging means 400 is provided as a turbocharger, the turbine 411 side is connected to the exhaust manifold of the engine 200 through the exhaust pipe 191 and rotated, (Compressed), the mixture is discharged to the intercooler 500 side.

Further, the rotating shaft of the turbocharger may be supplied with oil from the engine 200 side for the purpose of lubrication or the like.

1 to 3, the engine module includes an oil tank 205 provided outside the engine 200 for storing oil, and an oil tank 205 for storing the oil in the oil tank 205, An oil pump 207 for supplying the oil collected in the oil pan (not shown) inside the engine 200 to the oil tank 205, And an oil supply pipe (not shown) connected to the oil pump 207 and supplying at least a part of the oil sent to the oil pump 207 to the supercharging means 400.

That is, when the engine 200 is operating, a part of the oil circulated by the oil pump constitutes an additional flow path by the supercharging means 400.

As described above, the oil supplied to the supercharging means 400 can be recovered to the oil tank outside the engine 200 after passing through the rotary shaft of the supercharging means 400 (the power transmission shaft connecting the turbine and the compressor).

In this embodiment, the temperature sensor can be attached to the point where the oil is introduced into the supercharging means 400 and the point where the oil is discharged from the supercharging means 400, respectively.

Further, after the change in the temperature of the oil is sensed through the temperature sensor, when the excessive oil temperature rises, the oil used in the supercharging means 400 is cooled by utilizing the oil cooler (not shown). Therefore, breakage of the supercharging means 400 due to high temperature oil can be prevented, and oil carbonization can be prevented.

On the other hand, when the supercharging means 400 is a turbocharger, it is necessary to heat the turbocharger. For example, the turbocharger can be heat-exchanged while performing heat exchange with the cooling water.

The cooling water pipe 360 may include a first cooling water pipe 360a and a second cooling water pipe 360b for the heat dissipation of the turbocharger.

Specifically, the first cooling water pipe 360a is disposed between the exhaust gas heat exchanger 240 and the engine 200, and guides the cooling water passed through the exhaust gas heat exchanger 240 to the engine 200 side.

As another example, the first cooling water pipe 360a may include the cooling water pipe before passing through the exhaust gas heat exchanger 240. [ That is, the first cooling water pipe 360a may refer to a cooling water pipe between the cooling water pump 300 and the engine 200. [

The second cooling water pipe 360b is branched at the first cooling water pipe 360a so that at least a part of the cooling water flowing through the first cooling water pipe 360a is heat-exchanged with the supercharging means 400. [ The cooling water flowing into the second cooling water pipe 360a flows to the engine 200 after passing through the supercharging means 400. [

At this time, the second cooling water pipe 360b is branched from the first cooling water pipe 360a before the supercharging means 400, passes through the supercharging means 400, and then flows through the first cooling water pipe 360a And may be supplied to the engine 200.

Meanwhile, the supercharging means 400 may be a supercharger.

The supercharger generates a rotational force by the power or electric motor of the engine 200, and pressurizes (compresses) the introduced gas and discharges it. Therefore, when the supercharger 400 is provided as a supercharger, the supercharger pressurizes (supercharges) the mixer mixed in the mixer using the power of the engine 200 or the rotational force of the electric motor, 500).

Generally, the supercharger stably operates in the low rotation range, and there is a tendency that the output is lost in the high rotation range. Therefore, a supercharger or a turbocharger can be selected and used as the supercharging means 400 in accordance with the operation conditions of the engine and the required output conditions.

On the other hand, when the supercharger 400 is a supercharger as described above, since the heat dissipation problem is not as pronounced as in the turbocharger, it is not necessary to additionally provide a cooling water pipe for cooling the supercharging means 400. Accordingly, the structure of the flow path is simplified, the space utilization is improved, and there is an advantage that the flow path can be downsized.

Hereinafter, the structure of the 'engine module' which is the main component of the present invention will be described in more detail.

5 is a perspective view of an engine module, which is a component of the present invention, viewed from an intake manifold direction. FIG. 6 is a view showing the flow of air in the engine module shown in FIG. 5. FIG. And Fig. 7 is an exploded perspective view of an engine module which is a part of the present invention.

Generally, components such as the mixer 220, the supercharging unit 400, the adjusting unit 600, and the intercooler 500, which are provided for compressing the fuel-air mixture and supplying the mixture to the engine, In this case, since the piping is connected to the intake manifold 260 of the engine 200 and the exhaust manifold 270, the entire length of the piping is increased.

In addition, since the length of the piping is long to make the structure complicated and the fastening members for fixing the respective components are separately provided, the structure becomes more complicated and the area occupied by the respective components becomes larger, .

When the components such as the mixer 220, the supercharging unit 400, the adjusting unit 600 and the intercooler 500 are fixed to a separate structure from the engine 200, when the engine 200 is operated, And the respective components do not vibrate in the same direction but vibrate in a relatively opposite direction, so that the connecting parts of the connecting pipe and the pipe are damaged due to the vibration of the engine 200, and the like.

Further, when the flow length of the mixer in which the fuel and the air are mixed is long, the risk of explosion increases.

In order to solve this problem, at least one of the components of the mixer 220, the supercharging unit 400, the adjusting unit 600, and the intercooler 500 is directly fixed to the engine 200 in the present invention.

At this time, only a selected one of the mixer 220, the supercharging means 400, the adjusting means 600 and the intercooler 500 can be directly fixed to the engine 200, and the mixer 220, the supercharging means 400, (600), and the intercooler (500) may be fixed directly to the engine (200).

As described above, when the mixer 220, the supercharging unit 400, the adjusting unit 600, and the intercooler 500 are fixed to the engine 200, the following advantages are obtained.

The structure for fixing the components such as the mixer 220, the supercharging unit 400, the adjusting unit 600, and the intercooler 500 can be omitted, which is advantageous in that the structure is simplified. It also has the advantage of lowering cost by lowering fixed parts.

As the components such as the mixer 220, the supercharging means 400, the adjusting means 600 and the intercooler 500 are fixed to the engine 200, the adjusting means 600 and the intake manifold 260, The interval between the exhaust manifold 400, the exhaust manifold 270, the intercooler 500, the supercharging means 400, and the regulating means 600 can be reduced to reduce the length of the entire piping and the flow path, There are advantages.

The components such as the mixer 220, the supercharging unit 400, the adjusting unit 600 and the intercooler 500 are fixed to the engine 200 so that the mixer 220, 400, the adjusting means 600, the intercooler 500 and the like are vibrated in the same direction, the vibration applied to the piping and the connecting portion can be reduced, and the piping and various connecting portions can be vibrated It is possible to prevent a phenomenon such as loosening or breakage caused by the above-mentioned problems, thereby enhancing durability and preventing safety accidents.

5 to 7, a mixer inlet port 261 of the intake manifold 260 and a mixer outlet port (not shown) of the control means 600 can be directly connected, May be fixed to the engine 200 through the intake manifold 260. [

At this time, the mixer discharge port (not shown) may mean an outlet formed in the discharge part 620 to be described later.

The supercharging means 400 is formed adjacent to an exhaust manifold 270 formed on a first surface (right side of FIG. 7) of the engine 200, (Left side in FIG. 7) of the engine 200 opposite to the side of the intake manifold 260. The intercooler 500 is formed so as to intersect the first and second surfaces (The front surface with reference to Fig. 7).

The supercharging means 400 that is powered by the exhaust manifold 270 can be disposed adjacent to the exhaust manifold 270 and can be disposed between the exhaust manifold 270 and the supercharging means 400 The length of the exhaust gas supply passage can be minimized, and the supercharging means 400 can maximally recover the power energy of the exhaust gas.

Further, the adjusting means 600 for adjusting and supplying the mixer to the intake manifold 260 may also be disposed adjacent to the intake manifold 260. Therefore, the amount of the mixer supplied to the intake manifold 260 can be adjusted more precisely.

An intercooler 500 fixed between the supercharging means 400 fixed on both sides of the exhaust manifold 270 and the adjusting means 600 fixed on the intake manifold 260 side is connected to the exhaust manifold 270 and the intake manifold 260 so that the distance between the intercooler 500 and the supercharging means 400 and the distance between the intercooler 500 and the control means 600 can be kept to a minimum. Thus, the length of the flow path through which the mixer flows can be minimized.

7) is provided on the upper surface (upper part of Fig. 7) of the engine 200, since maintenance of the engine oil, spark plug, valve clearance and the like is required through the upper surface Do not install any parts.

Hereinafter, with reference to the drawings, the shape and structure of the intake manifold and the adjusting means will be described in more detail.

8 is a diagram showing the configuration of an engine module without the conventional supercharging capability. 9 is a diagram showing the configuration of an engine module having a supercharging function according to the present invention.

Referring to FIG. 8, since the conventional engine module has no supercharging capability, various components for supercharging, for example, the supercharging unit 400, the intercooler 500, and a separate component for connecting them are mounted . 8 (a) is a view showing the conventional engine module as viewed from the intake manifold side, and FIG. 8 (b) is a view as viewed from the upper side.

In this case, when the filtered air is supplied through the air filter 210 disposed at one side of the engine 200, air flows into the mixer 220 through the pipe 215. Thereafter, the air and the fuel are mixed in the mixer 220, and the mixer is supplied to the intake manifold 260 via the adjusting means 600.

At this time, the flow length of the air and the mixer is short and the direction of the flow path can be formed in a straight line, so that the supply of the mixer to the intake manifold 260 can be performed with the flow resistance minimized. The direction in which the inlet of the intake manifold 260 is viewed may be directed toward the air filter 210 to minimize the length of the flow path.

However, in the state where the intake manifold is disposed as shown in FIG. 8, when components such as the supercharging unit 400 and the intercooler 500 are additionally disposed for the supercharging function, The flow distance of the mixer discharged from the disposed supercharging means must be long and the flow path must be formed to bypass the engine 200, which causes a problem of increased flow resistance.

In the case of the present invention, the shape and structure of the adjusting means 600 and the intake manifold 260 are changed in order to solve this problem.

9, it can be seen that the shape of the intake manifold 260 and the arrangement structure of the adjusting means 600 are changed on the basis of the conventional art.

9 (a) is a view showing the engine module according to the present invention as viewed from the intake manifold side, and FIG. 9 (b) is a view as viewed from the upper side.

9A, an intake manifold 260 is disposed in parallel with a side wall (second side) of the engine 200, and a direction of a mixer inlet 261 of the intake manifold 260 Is directed toward the side of the intercooler 500 while facing the opposite direction of the air filter 210.

Also, it can be confirmed that the direction in which the mixer is introduced into the mixer inlet port 261 of the intake manifold 260 is formed so as to be directed downward from the upper side. (See arrows in Fig. 9)

That is, conventionally, the direction in which the mixer is introduced into the intake manifold 260 is horizontally arranged from left to right with reference to FIG. 8 (a), whereas in the present invention, the mixer flows into the intake manifold 260 9A may be formed so as to be vertically downward with respect to FIG. 9A or downwardly inclined from the right side to the left side.

The distance between the intercooler 500 and the intake manifold 260 may be reduced when the arrangement of the intake manifold 260 is changed.

In addition, the mixer discharged downward from the intercooler 500 disposed on the upper side can be introduced into the intake manifold 260 formed to face upward, so that the flow of the mixer smoothly proceeds, and the flow resistance of the mixer There is an advantage that can be minimized.

In addition, in the case of the present invention, the intake manifold 260 takes the form of a flat box as a whole, and is disposed in parallel with the side wall (second surface) of the engine 200, thereby reducing the volume of the engine module.

9 (b), it can be seen that the height of the intake manifold 260 protruding outside the side wall (second surface) of the engine 200 is reduced compared to the conventional one (see FIG. 8).

In addition, the direction of discharging purified air of the air filter 210 is also reversed.

Specifically, in the conventional air filter, a direction in which purified air is discharged is directed toward the intake manifold side. On the other hand, in the present invention, the discharge direction of the purified air in the air filter 210 is toward the exhaust manifold side As shown in FIG.

Accordingly, air can be smoothly supplied to the mixer 220 disposed adjacent to the exhaust manifold 270. Also, the supply of the mixer can be smoothly performed by the supercharger 400 disposed adjacent to the mixer 220 and the exhaust manifold 270.

The intake manifold 260 includes a main portion 262 for horizontally guiding the mixer introduced downward through the mixer inlet 261 and a main portion 262 for communicating with the main portion 262 in the horizontal direction And a plurality of branch portions 263 for guiding the guided mixer upward and supplying the guided mixer into the engine 200.

Therefore, the mixer, which is inclined downwardly through the mixer inlet 261 of the intake manifold 260, flows in the horizontal direction while passing through the main portion 262, And flows into the cylinder of the engine 200 after flowing to the upper side while passing through the branching section 263.

When the shape and the arrangement direction of the intake manifold 260 are changed and the arrangement structure of the adjustment means 600 is changed as described above, the outlet side of the intercooler 500 and the inlet side of the intake manifold 260 The spacing between the sides can be minimized.

In addition, the interval between the intercooler 500 and the supercharging unit 400 can be minimized, and the interval between the supercharging unit 400 and the exhaust manifold 270 and the mixer 220 can be minimized.

Further, the mixer discharge direction of the intercooler 500 and the mixer inlet direction of the intake manifold 260 may be the same or similar to each other so that the mixer can be formed as straight as possible in the flow path, It is possible to flow quickly without loss in a state where resistance (intake resistance) is minimized.

In addition, on the flow path of the mixer, the adjustment means 600 were arranged in a direction parallel to the flow path so that the adjustment means 600 did not affect the flow of the mixer.

That is, in the case of the present invention, when the supercharging means 400 and the intercooler 500 are added to the engine module, the outlet of the air filter 210 is formed on the exhaust manifold side, 210 and the pipe 215 connecting the mixer 220 are formed as straight as possible. And formed as horizontally as possible. The distance between the mixer 220 and the supercharging unit 400 is minimized and the supercharging unit 400 is directly connected to the exhaust manifold 270. The intercooler 500 disposed between the supercharging means 400 and the adjusting means 600 is disposed at an optimal position based on the flow of the mixer. In detail, the intercooler 500 is disposed on the other side connecting the surface on which the exhaust manifold 270 is fixed and the surface on which the intake manifold 260 is fixed.

At this time, the intake side of the intake manifold 260 and the exhaust side of the exhaust manifold 270 are both formed near the surface where the intercooler 500 is disposed.

The inlet side of the intake manifold 260 is formed at the portion closest to the outlet side of the intercooler 500 and the shape and arrangement direction of the intake manifold 260 are thereby changed to set the inlet direction of the mixer to the condition Respectively. Also, the adjusting means 600 is disposed on the flow path of the mixer that flows from the intercooler 500 to the intake manifold 260.

According to the above description, the flow paths of the air and the mixer can be smoothly formed as a whole by drawing a U-shape from the exhaust manifold side toward the intake manifold side, thereby minimizing the length of the flow path and making it structurally compact And has the advantage of reducing flow resistance.

Hereinafter, the supercharging means and the intercooler constituting the 'engine module' will be described with reference to FIG. 5 to FIG.

In the following description, the case where the supercharging means 400 is provided as a 'turbocharger' will be described as an example, but the scope of the present invention is not limited thereto, As shown in FIG.

The turbocharger 400 includes a turbine chamber 410 that receives the exhaust gas and rotates the turbine 411 (see FIG. 4) provided inside the turbine chamber 410, And a rotary shaft for transmitting the rotational force of the turbine chamber 410 to the compression chamber 420. In addition, the compression chamber 420 may include an impeller which is connected to the rotation shaft and compresses the mixer introduced into the compression chamber 420 while rotating.

Accordingly, the exhaust gas discharged from the exhaust manifold 270 directly flows into the turbine chamber 410 to rotate the turbine, and the rotational force is transmitted to the compression chamber 420 through the rotation shaft. The mixer supplied from the mixer 220 is compressed by the impeller rotating and connected to the rotating shaft 430 while passing through the inside of the compression chamber 420 and then discharged through the discharge pipe 401 (420).

As described above, the compression mixer discharged to the outside of the compression chamber 420 flows to the intercooler 500 to improve the density.

For example, the intercooler 500 may include a body 510, which is open at both sides, and a space for heat exchange between the cooling water supplied from the outside and the compressed mixer, An inlet 520 formed at one side of the main body 510 and formed with an inlet pipe 521 connected to the outlet of the supercharging means 400 and an inlet 520 formed at the other side of the body 510, And a discharge unit 530 having a discharge pipe 531 connected to the inlet side.

At this time, the discharge pipe 401 of the compression chamber 420 may be directly connected to the inlet pipe 521 of the intercooler 500.

Alternatively, the discharge pipe 401 of the compression chamber 420 and the inlet pipe 521 of the intercooler 500 may be connected to each other through the bent first connection pipe 810.

In detail, the intercooler 500 may be connected through a first connection pipe 810 bent in a U-shape or a J-shape.

The discharge pipe 531 of the intercooler 500 may be inclined downwardly to discharge the mixer toward the intake manifold 260. The discharge pipe 531 may be connected to the inlet of the adjusting means 600, (Not shown).

As another example, the discharge pipe 531 of the intercooler 500 may be connected to the inlet 610 of the regulating means 600 through a second connecting pipe 820 having a curved shape.

In detail, the second connection pipe 820 is formed to be inclined downward from the side of the intercooler 500 toward the regulating means 600, and can be bent into a shape of 'A'.

As another example, the second connection pipe 820 may be formed in a straight line. To this end, the discharge pipe 531 of the intercooler 500 and the inlet 610 of the adjusting means 600 may be formed facing each other at the same angle.

In this case, the intake resistance of the mixer flowing into the regulating means 600 can be minimized.

7) of the regulating unit 600 may be directly connected to the mixer inlet 261 (see FIG. 7) of the intake manifold 260. As shown in FIG.

When the adjusting means 600 and the intake manifold 260 are directly connected as described above, the piping for connecting them can be omitted, which simplifies the structure and can shorten the flow path of the mixer.

Meanwhile, the mixer 220 may be fixed to the intercooler 500.

For this purpose, the inlet 520 of the intercooler 500 may be formed with a mixer coupling part 560 to which the mixer 220 is fastened.

The mixer coupling part 560 may be formed as a single body with the inlet part 520 and has a hollow shape so as to be discharged to the supercharger 400 after the mixer having passed through the mixer 220 is introduced.

Accordingly, the mixer discharged from the mixer 220 passes through the hollow 561 of the mixer coupling part 560, and then passes through the third pipe ('830' in FIG. 7) To the supercharging means (400). According to this, not only the mixer 220 can be fixed to the engine 200, but also the alignment of the mixer 220 can be facilitated.

The engine module may further include an air filter 210 for purifying the outside air and at least a portion of the air pipe 215 connecting the air filter 210 and the mixer 220 may be formed in a straight line. have.

When the air pipe 215 is formed in a straight line as described above, the fluidity of the air can be improved. That is, in the straight section, the air flows smoothly, and the air supply to the mixer 220 can be facilitated.

In addition, a part of the air pipe 215 may be formed as a curved line.

In addition, the air filter 210 and the mixer 220 may be fixed at the same height.

As described above, when the air filter 210 and the mixer 220 are fixed at the same height, airflow can be smoothly performed, and the air supply to the mixer 220 can be more easily performed.

According to the present invention, the air sucking resistance of the mixer 220 can be minimized by forming the air pipe 215 connecting the air filter 210 and the mixer 220 horizontally and linearly.

10 is a perspective view of an engine module provided with a cooling water pump.

Referring to FIG. 10, the engine module further includes an exhaust gas heat exchanger 240 for exchanging heat between the exhaust gas passing through the supercharging means 400 and the cooling water.

At this time, the exhaust gas heat exchanger 240 may be fixed directly to the engine 200. In detail, the exhaust gas heat exchanger 240 may be fixed directly to the exhaust manifold 270 of the engine 200. At this time, a fixing means such as a clamp for fixing the exhaust gas heat exchanger 240 to the exhaust manifold 270 may be separately provided.

The exhaust gas discharged from the exhaust manifold 270 first flows through the turbine chamber 410 of the supercharging means 400 and rotates the turbine 411 and the exhaust gas discharged from the turbine chamber 410 As the gas passes through the exhaust gas heat exchanger 240, heat exchange with the cooling water can proceed.

The exhaust gas that has passed through the exhaust gas heat exchanger 240 is in a state in which its temperature is lowered through heat radiation and is discharged to the atmosphere through the muffler. On the other hand, the cooling water passed through the exhaust gas heat exchanger 240 is in a state of improved temperature through heat absorption and is recovered to the cooling water tank through the exhaust manifold 270 and the radiator.

At this time, the exhaust gas heat exchanger 240 and the turbine chamber 410 of the supercharging unit 400 may be directly connected without any piping. That is, the first outlet (not shown) of the turbine chamber 410 and the exhaust gas inlet 241 (see FIG. 11) of the exhaust gas heat exchanger 240 can be directly connected.

For example, the first exhaust port (not shown) and the exhaust gas inlet 241 form a flange 413 extending outward along the circumference. In a state where the flange 413 is in contact with the exhaust port, So that they can be interconnected.

Hereinafter, the flow of the cooling water will be described in detail with reference to FIG.

First, when the cooling water pump 300 is driven, the cooling water stored in the cooling water tank passes through the exhaust gas heat exchanger 240 and the primary heat exchange proceeds. Thereafter, while passing through the exhaust manifold 270, It proceeds. The temperature of the exhaust gas of the exhaust manifold 270 and the exhaust gas heat exchanger 240 can be lowered as the cooling water flows as described above. On the other hand, the cooling water heated while passing through the exhaust manifold 270 can be recovered to the cooling water tank after the temperature passes through the radiator.

In addition, some of the cooling water that has passed through the exhaust gas heat exchanger 240 may be branched to cool the supercharging means 400 while passing through the supercharging means 400, and the cooling water passing through the supercharging means 400 may also be cooled After passing through the radiator, the temperature is lowered and can be returned to the cooling water tank again.

The radiator may be installed on one side of the outdoor heat exchanger, and the cooling water of the radiator may be cooled by the heat exchange with the outside air by driving the outdoor fan.

The overall operation of the engine module will now be described with reference to FIG.

First, the purified air passing through the air filter 210 and the fuel (LNG) passing through the zero governor are mixed in the mixer 220.

The mixed mixer (air and LNG) mixed in the mixer 220 is discharged from the mixer 220 and then passes through the mixer coupling part 560 of the intercooler 500 to which the mixer 220 is fixed, 3 pipe 830 and into the supercharging means 400. [

At this time, the supercharging means 400 is coupled to the exhaust manifold 270 of the engine 200, the supercharging means 400 is powered by the exhaust gas of the engine 200 and rotates, The mixture introduced into the supercharging means 400 is compressed to high temperature and high pressure.

Thereafter, the mixer compressed by the supercharging means 400 flows to the intercooler 500 side through the discharge pipe 401 and the bent first connection pipe 810.

The compressed mixture is introduced through the first connection pipe 810 connected to the discharge pipe 401 and the inflow pipe 521 connected to the first connection pipe 810, The mixture introduced into the mixing chamber 510 is cooled while its heat is being exchanged with the cooling water passing through the body 510, and the density thereof is improved.

Thereafter, the mixer having the increased density is discharged to the outside of the intercooler 500 through the discharge portion 530 and the discharge pipe 531, and is discharged through the second connection pipe 820 connected to the discharge pipe 531, ).

In the adjusting means 600, the amount of the mixer introduced from the intercooler 500 is adjusted, the engine 200 is discharged, and the adjusted amount of the mixer is introduced through the intake manifold 260 of the engine 200.

At this time, the adjusting means 600 can be fixed to the intake manifold 260 while the outlet of the adjusting means 600 is directly connected to the inlet of the intake manifold 260, so that the structure becomes compact, There is also an advantage that this can be reduced.

In addition, even if the shape of the flow path through which the mixer flows becomes complicated, the length of the flow path through which the mixer flows can be minimized and the length of the flow path of the mixer of the intake manifold 260 and the control means 600, So that the flow resistance of the mixer can be minimized.

Meanwhile, when the mixer flows into the engine 200 through the intake manifold 260 as described above, the combustion progresses inside the engine 200, and power for driving the compressor is generated.

Meanwhile, the exhaust gas generated in the combustion process is discharged to the outside of the engine 200 through the exhaust manifold 270.

The supercharging means 400 is connected to the exhaust manifold 270 and the exhaust gas discharged from the exhaust manifold 270 is supplied to the supercharging means 400 to rotate the turbine of the supercharging means 400. Accordingly, the supercharger 400 can compress the mixer introduced from the mixer 220 side.

On the other hand, the exhaust gas that has passed through the supercharging unit 400 passes through the exhaust gas heat exchanger 240, and heat exchange with the cooling water provided by the cooling water pump 300 proceeds. The exhaust gas having undergone the heat exchange as described above is supplied to the outlet side of the exhaust gas heat exchanger 240 and passes through a muffler 250 for reducing the noise of the exhaust gas and is then discharged to the outside.

On the other hand, the cooling water having been heat-exchanged in the exhaust gas heat exchanger 240 after being sent out from the cooling water pump 300 is supplied to the exhaust manifold 270 through a separate pipe and passes through the exhaust manifold 270 After the cooling water exits the engine 200, the cooling water is recovered to the cooling water tank connected to the cooling water pump 300 through the radiator.

Part of the cooling water that has been heat-exchanged in the exhaust gas heat exchanger 240 after being discharged from the cooling water pump 300 is branched through a separate connection pipe 350 before flowing into the exhaust manifold 270 The cooling water having undergone the heat exchange while passing through the supercharging means 400 passes through the exhaust manifold 270 and the radiator and is then recovered to the cooling water tank connected to the cooling water pump 300 .

The components such as the supercharging unit 400, the intercooler 500 and the adjusting unit 600 are fixed to the engine 200 itself not in a separate structure separate from the engine 200, There is also an advantage in that the structure for fixing the parts can be omitted.

As the components are fixed to the engine 200, the control means 600 and the intake manifold 260, the supercharging means 400 and the exhaust manifold 270, the intercooler 5600 and the supercharging means 400, The length of the entire piping can be reduced, and the area occupied by the piping can be reduced.

The components such as the supercharging unit 400, the intercooler 500 and the adjusting unit 600 are fixed to the engine 200 so that the supercharger 400, the intercooler 500, It is possible to prevent the relative vibration phenomenon in which components such as the compressor 600 and the engine 200 move in mutually opposite directions, thereby reducing the vibration applied to the piping and the connecting portion, and the piping and various connecting portions are loosened It is possible to prevent a phenomenon such as breakage or damage, thereby enhancing durability and preventing safety accidents.

10: Gas heat pump system 110: Compressor
120: outdoor heat exchanger 140: indoor heat exchanger
150: auxiliary heat exchanger 200: engine
240: Exhaust gas heat exchanger 260: Intake manifold
300: coolant pump 400: supercharging means
500: intercooler 600: adjusting means

Claims (15)

An air conditioning module including a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and a refrigerant pipe; And
And an engine for combusting a mixture of fuel and air to provide power for operation of the compressor,
The engine module includes:
A mixer for mixing and discharging the air and the fuel;
A supercharging unit that receives the compressed air discharged from the mixer, compresses the compressed air, and discharges the compressed air;
An intercooler supplied with the compressed air from the supercharging means, cooled by a heat exchange system to increase its density, and then discharged;
Adjusting means for adjusting the amount of the mixed air discharged from the intercooler and supplying the mixed air to the engine;
An intake manifold for introducing the mixer supplied from the regulating means; And
An air filter for purifying the outside air,
The first mixer inlet of the intake manifold and the first mixer outlet of the controller are directly connected,
Wherein at least a part of the air pipe connecting the air filter and the mixer is formed in a straight line, and the air filter and the mixer are fixed to the same height.
The method according to claim 1,
Wherein the supercharging means is formed adjacent to an exhaust manifold formed on a first surface of the engine,
Wherein the adjusting means is formed adjacent to an intake manifold formed on the second surface of the engine opposite the first surface,
Wherein the intercooler is fixed to a third surface in a direction intersecting the first surface and the second surface.
3. The method of claim 2,
In the intercooler,
Wherein the gas heat pump system is disposed above the supercharging means or the regulating means.
The method of claim 3,
Wherein the intercooler has a downwardly sloping discharge pipe for discharging the mixer toward the intake manifold.
5. The method of claim 4,
Wherein a connection pipe for connecting the discharge pipe and the second mixer inlet of the regulating means is provided for guiding the flow of the mixer from the upper side to the lower side.
6. The method of claim 5,
Wherein the mixer discharge port of the adjusting means is formed to face downward, and the mixer inlet of the intake manifold is formed to face upward.
The method according to claim 6,
The intake manifold includes:
A main part for horizontally guiding the mixer introduced downward from the mixer inlet;
And a plurality of branch portions communicating with the main portion and guiding the mixer guided in the horizontal direction vertically upward to supply the mixture to the engine.
8. The method of claim 7,
Wherein the intake manifold is disposed so as to stand upright in parallel with the second surface of the engine.
The method according to claim 1,
Wherein the engine module further comprises an exhaust gas heat exchanger for exchanging heat between the exhaust gas passing through the supercharging means and the cooling water.
The method according to claim 1,
Wherein the mixer is fixed to the intercooler.
delete delete The method according to claim 1,
Wherein the supercharging means comprises:
And a turbocharger driven by the exhaust gas of the engine.
The method according to claim 1,
Wherein said fuel is domestic LNG or LPG.
The method according to claim 1,
A cooling water pump for generating a flow of cooling water for cooling the engine, and a cooling module connected to the cooling water pump and including a cooling water pipe for guiding the flow of the cooling water.

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