KR102216716B1 - Gas heat-pump system - Google Patents

Abstract

The gas heat pump system of the present invention comprises: an air conditioning module including a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and a refrigerant pipe; An engine module including an engine that provides power for driving the compressor by combusting a mixture of fuel and air; And a cooling module through which coolant for cooling the engine flows.
The engine module includes: a supercharging means for compressing a mixture of air and fuel and then discharging the mixture to the engine; And an intercooler disposed between the engine and the supercharging means, and cooling the mixer compressed by the supercharging means, wherein the cooling module comprises: an intercooler side pipe through which coolant to be supplied to the intercooler flows, and the intercooler side A cooling water heat exchanger connected to a pipe, and the refrigerant pipe includes a suction pipe connected to a suction side of the compressor and passing through the cooling water heat exchanger, wherein the refrigerant of the suction pipe and the cooling water of the intercooler side pipe heat exchange do.

Description

Gas heat-pump system

The present invention relates to a gas heat pump system.

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

The refrigeration cycle may include a compressor for compressing the refrigerant, a condenser for condensing the refrigerant compressed by the compressor, an expansion device for decompressing the refrigerant condensed by the condenser, and an evaporator for evaporating the reduced refrigerant.

The heat pump system may include a gas heat pump system. A large-capacity compressor is required for air conditioning in industrial or large buildings, not for home use. That is, a gas heat pump system may be used as a system using a gas engine rather than 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 may include an engine that generates power 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 supplied, and a piston provided to be movable within the cylinder.

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

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

The zero governor may be understood as a device that constantly adjusts and supplies an outlet pressure regardless of a change in the inlet pressure or flow rate of the fuel. For example, the zero governor may include a nozzle unit for reducing a pressure of fuel, a diaphragm acting on a pressure reduced by the nozzle unit, and a valve device that is opened and closed by an operation of the diaphragm. .

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.

In addition, when the mixer supplied to the engine is combusted, exhaust gas may be discharged from the engine.

Prior literature: Korean Patent Publication No. 10-2013-0021377,

Prior literature discloses a cooling device for an engine exhaust gas recirculation circuit.

In the case of the prior literature, a high-temperature loop for cooling an engine and a low-temperature loop in which a fluid for heat exchange with an intercooler through which air passing through an air supply circuit of the engine flows flows may be included.

The high temperature loop is configured independently of the low temperature loop, and each of the high temperature loop and the low temperature loop includes a pump.

According to such prior literature, since two flow paths for flowing fluid for cooling are independently configured, there is a disadvantage that a pump for fluid flow must exist in each flow path, and fluid flow in each flow path must be controlled. There are drawbacks.

In addition, when each flow path is configured separately, a radiator must be present in each flow path, and a fan for blowing air to each radiator must be present, and thus there is a disadvantage in that it is structurally complicated and the volume of the cooling device is increased.

An object of the present invention is to provide a gas heat pump system capable of cooling an intercooler using coolant for cooling an engine.

Further, an object of the present invention is to provide a gas heat pump system in which the cooling performance of an intercooler is improved.

Further, an object of the present invention is to provide a gas heat pump system in which the cooling performance of an engine is improved.

The gas heat pump system of the present invention for solving the above problems includes: an air conditioning module including a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and a refrigerant pipe; An engine module including an engine that provides power for driving the compressor by combusting a mixture of fuel and air; And a cooling module through which coolant for cooling the engine flows.

The engine module includes: a supercharging means for compressing a mixture of air and fuel and then discharging the mixture to the engine; And an intercooler disposed between the engine and the supercharging means and cooling a mixer compressed by the supercharging means, wherein the cooling module includes: an intercooler side pipe through which coolant to be supplied to the intercooler flows, and the intercooler side A cooling water heat exchanger connected to a pipe, and the refrigerant pipe includes a suction pipe connected to a suction side of the compressor and passing through the cooling water heat exchanger, wherein the refrigerant of the suction pipe and the cooling water of the intercooler side pipe heat exchange As a result, the cooling performance of the intercooler can be improved.

The gas heat pump system may further include a gas-liquid separator for separating gas and liquid. The suction side pipe may be an outlet side pipe of the gas-liquid separator.

The cooling module may further include an engine-side pipe branching from the intercooler-side pipe. The intercooler side pipe includes an inlet pipe located at an inlet side of the intercooler and an outlet pipe located at an outlet side of the intercooler, and the inlet pipe and the engine side pipe may be connected to a flow control valve. have.

The outlet pipe may be connected to a downstream side of the flow control valve from the engine pipe.

The engine module may further include an exhaust gas heat exchanger through which exhaust gas exhausted from the engine is introduced. The engine-side pipe may be connected to the engine after passing through the exhaust gas heat exchanger.

The engine-side pipe may further include a bypass pipe branched from the outlet pipe of the exhaust gas heat exchanger and connected to the outlet pipe of the exhaust gas heat exchanger after passing through the supercharge means.

According to the proposed invention, since the intercooler can be cooled using coolant for cooling the engine, there is an advantage that a coolant flow path separate from a cooling water flow path for engine cooling is unnecessary. Accordingly, there is an advantage of not only being able to flow coolant to the intercooler side but also to the engine side by using one coolant pump.

In addition, since an additional cooling water pump, a radiator, and a fan for heat dissipation are unnecessary, the structure of the entire system is simplified and the volume is reduced.

In addition, since the coolant for flowing to the intercooler is heat-exchanged with the low-temperature refrigerant, the cooling performance of the mixer in the intercooler is improved.

In addition, since the coolant to be supplied to the exhaust gas heat exchanger is supplied to the exhaust gas heat exchanger in a state that is combined with the coolant that has passed through the intercooler having a relatively low temperature, there is an advantage of improving the heat exchange performance of the exhaust gas heat exchanger and the cooling performance of the engine. .

1 is a cycle diagram showing the configuration of a gas heat pump system according to an embodiment of the present invention.
2 is a view showing an engine module according to an embodiment of the present invention.
3 is a cycle diagram illustrating flows of refrigerant, coolant, and mixed fuel during a heating operation of a gas heat pump system according to an embodiment of the present invention.
4 is a cycle diagram showing flows of refrigerant, coolant, and mixed fuel during cooling operation of the gas heat pump system according to an embodiment of the present invention.
5 is a view showing the flow of coolant in the engine module according to an embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail through exemplary drawings. In adding reference numerals to elements of each drawing, it should be noted that the same elements are assigned the same numerals as possible even if they are indicated on different drawings. In addition, in describing an embodiment of the present invention, if it is determined that a detailed description of a related known configuration or function interferes with the understanding of the embodiment of the present invention, the detailed description thereof will be omitted.

In addition, in describing the constituent elements of the embodiment of the present invention, terms such as first, second, A, B, (a), (b) may be used. These terms are only used to distinguish the component from other components, and the nature, order, or order of the component is not limited by the term. When a component is described as being "connected", "coupled" or "connected" to another component, that component may be directly connected or connected to that other component, but another component between each component It should be understood that may be “connected”, “coupled” or “connected”.

1 is a cycle diagram showing the configuration of a gas heat pump system according to an embodiment of the present invention, and FIG. 2 is a view showing an engine module according to an embodiment of the present invention.

1 and 2, the gas heat pump system 10 according to an embodiment of the present invention may include a plurality of components constituting a refrigerant cycle as an air conditioning module.

For example, the air conditioning module includes a compressor 110 for compressing a refrigerant, an oil separator 115 for separating oil from the refrigerant compressed by the compressor 110, and a refrigerant that has passed through the oil separator 115. It may include a four-way side 117 to change the direction.

The gas heat pump system 10 may further include an outdoor heat exchanger 120 and an indoor heat exchanger 140.

The outdoor heat exchanger 120 may be disposed inside an outdoor unit disposed at an outdoor side, and the indoor heat exchanger 140 may be disposed inside an indoor unit disposed at an indoor side. The refrigerant passing through the four sides 117 may flow to the outdoor heat exchanger 120 or the indoor heat exchanger 140.

Components of the system shown in FIG. 1 may be disposed outside the indoor heat exchanger 140 and the indoor expansion device 145, that is, inside the outdoor unit.

When the gas heat pump system 10 is operated in the cooling operation mode, the refrigerant passing through the four sides 117 may flow toward the indoor heat exchanger 140 through the outdoor heat exchanger 120. On the other hand, when the gas heat pump system 10 is operated in the heating operation mode, the refrigerant that has passed through the four sides 117 may flow toward the outdoor heat exchanger 120 through the indoor heat exchanger 140. I can.

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

The configuration of the gas heat pump system 10 will be described based on the cooling operation mode.

The refrigerant flowing through the outdoor heat exchanger 120 may be condensed by heat exchange with outside air. An outdoor fan 122 for blowing outside air may be disposed on one side of the outdoor heat exchanger 120.

A main expansion device 125 for depressurizing a refrigerant may be provided at an outlet side of the outdoor heat exchanger 120. For example, the main expansion device 125 may include an electronic expansion valve (EV). During the cooling operation, the main expansion device 125 is fully open and does not decompress the refrigerant.

At the outlet side of the main expansion device 125, a subcooling heat exchanger 130 for additionally cooling the refrigerant may be provided. In addition, a subcooling flow path 132 may be connected to the subcooling heat exchanger 130. The subcooling passage 132 may be branched from the refrigerant pipe 170 and connected to the subcooling heat exchanger 130.

In addition, a supercooling expansion device 135 may be installed in the subcooling passage 132. The refrigerant flowing through the subcooling passage 132 may be depressurized while passing through the supercooling expansion device 135.

In the subcooling heat exchanger 130, heat exchange may be performed between the refrigerant in the refrigerant pipe 170 and the refrigerant in the subcooling passage 132. During the heat exchange process, the refrigerant in the refrigerant pipe 170 is supercooled, and the refrigerant in the subcooling passage 132 absorbs heat.

The supercooling flow path 132 may be connected to the gas-liquid separator 160. The refrigerant in the subcooling passage 132 heat-exchanged in the subcooling heat exchanger 130 may flow into the gas-liquid separator 160.

The refrigerant in the refrigerant pipe 170 that has passed through the subcooling heat exchanger 130 flows toward the indoor unit, is depressurized in the indoor expansion device 145 and then evaporated in the indoor heat exchanger 140. The indoor expansion device 145 is installed inside the indoor unit and may be configured with an electronic expansion valve (EEV).

The refrigerant evaporated from the indoor heat exchanger 140 may flow 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 high-temperature cooling water, and may include, for example, a plate heat exchanger.

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

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

In addition, the refrigerant evaporated from the indoor heat exchanger 140 may be directly introduced into the gas-liquid separator 160 after passing through the four sides 117, and the separated gaseous refrigerant may be sucked into the compressor 110. I can.

Meanwhile, the gas heat pump system 10 may further include a coolant tank 305 storing coolant for cooling the engine 200 and a coolant pipe 360 (dotted line) for guiding the flow of the coolant. .

In the cooling water pipe 360, a cooling water pump 300 for generating a flow force of the cooling water, a plurality of flow conversion units 310 and 320 for changing the flow direction of the cooling water, and a radiator 330 for cooling the cooling water. radiator) can be installed.

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

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

When the coolant pump 300 is driven, the coolant stored in the coolant tank 305 passes through the engine 200 and the exhaust gas heat exchanger 240 to be described later, and the first flow conversion unit 310 and the second It may selectively flow to the radiator 330 or the auxiliary heat exchanger 150 through the flow conversion unit 320.

The gas heat pump system 10 may further include an engine module including an engine 200 that generates power for driving the compressor 110.

The engine module may include various components for supplying the engine 200 and the mixed fuel to the engine 200.

The gas heat pump system 10 may further include a mixer 220 disposed at an inlet side of the engine 200 to supply mixed fuel.

In addition, 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. ) May be further included.

The zero governor 230 may be understood as a device that constantly adjusts and supplies an outlet pressure regardless of a change in the inlet pressure or flow rate 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. In addition, the mixer may be supplied to the engine 200.

In addition, the gas heat pump system 10 is provided on the outlet side of the engine 200, the exhaust gas heat exchanger 240 and the exhaust gas heat exchanger 240 into which the exhaust gas generated after the mixer is burned is introduced. ) May further include a muffler 250 provided on the outlet side of the exhaust gas to reduce noise of exhaust gas.

In the exhaust gas heat exchanger 240, heat exchange may be performed between cooling water and exhaust gas.

In addition, an oil tank 205 for supplying oil to the engine 200 may be provided at one side of the engine 200.

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

However, when air is supplied to the engine 200 in a naturally aspirated manner and when LNG or LPG for residential use is supplied as fuel, there is a problem that the output of the engine 200 decreases due to a low supply pressure (1 to 2.5 kPa). .

In addition, in the summer, the gas heat pump system 10 operates in a cooling mode to reduce the indoor temperature. 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 cannot keep up with the high cooling load, which may cause a cooling failure.

To solve this problem, like the engine of a car, if air is pressurized by a supercharger and then supplied while adjusting the amount of fuel according to the amount of air, the supply pressure (about 2.5 kPa) in the pipe of gas fuel is lower than the boost pressure (about 30 kPa). There is also a problem that fuel supply becomes difficult.

In the case of the present invention, in order to solve such a problem, the gas heat pump system 10 further includes a supercharge means 400 and a control means 600 disposed between the mixer 220 and the engine 200 can do.

After the air and fuel are mixed in the mixer 220, the supercharging means 400 compresses the discharged mixer and discharges it to the engine 200. In this case, the supercharging means 400 may compress air and fuel in the mixer 220 to at least atmospheric pressure.

As an example, the supercharging means 400 may be configured as a turbo charger driven by exhaust gas of the engine 200.

The turbocharger rotates the turbine 411 by using the exhaust gas discharged from the engine 200, and pressurizes (compresses) the gas introduced by the rotational force and discharges it.

Accordingly, when the supercharge means 400 is provided as a turbocharger, the turbocharger is connected to the exhaust manifold of the engine 200 through the exhaust pipe 191 of the engine 200 at the side of the turbine 411 When the mixer 220 flows in, the mixer 220 is pressurized (compressed) and then discharged to the intercooler 500 side.

In addition, the rotation shaft of the turbocharger may be supplied with oil from the engine 200 for purposes such as lubrication.

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

In addition, the adjusting means 600 is disposed between the supercharging means 400 and the engine 200 to adjust the amount of the compressed mixer supplied to the engine 200.

For example, the control means 600 may be provided with a valve to which an electronic throttle control (ETC) method is applied.

According to the present invention, fuel and air are mixed in the mixer 220 and pressurized to a high pressure in the supercharging means 400, and then supplied to the engine 200.

In addition, the amount of the high-pressure mixer (air + fuel) supplied to the engine 200 through the adjusting means 600 may be precisely controlled.

Accordingly, the efficiency of the engine 200 may be improved. In addition, it is possible to increase the maximum output amount of the engine 200 without increasing the size of the engine 200. In other words, the output of a large engine can be realized with a small engine.

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

In the case of the present invention, in order to solve this, the gas heat pump system 10 may further include an intercooler 500 disposed between the supercharging means 400 and the adjusting means 600.

The intercooler 500 cools the high-temperature and high-pressure mixer discharged from the supercharging means 400 to reduce the volume and increase the density, and then discharge it.

As an example, the intercooler 500 may heat-exchange a mixer to be supplied to the engine 200 and a part of coolant to flow to the engine 200.

Accordingly, according to the intercooler 500, there is an advantage of lowering the temperature of the mixer supplied to the engine 200 and increasing the density, thereby improving the volumetric efficiency of the engine 200.

As described above, if the supercharge means 400 and the intercooler 500 are provided between the mixer 220 and the engine 200, the length of the flow path in which the mixer stays is inevitably longer. At this time, if there is a lot of moisture in the air, the mixer and water react to generate formic acid, which can damage the pipe, and there is a risk of explosion.

In the case of the present invention, when a'operation stop command' is input from an administrator to prevent this, the engine 200 is driven until the engine 200 is stopped in the state where the adjusting means 600 is closed, and the mixer is It can be burned or discharged to the outside to suppress the generation of formic acid, and can prevent the risk of pipe damage and explosion.

The cooling water pipe 360 may include a supply pipe 361 extending from the cooling water tank 305 toward the engine 200.

A cooling water pump 300 for flowing cooling water may be installed in the supply pipe 361.

The first branch pipe 371 and the second branch pipe 372 may branch from the supply pipe 361.

In addition, the flow of cooling water in the first branch pipe 371 and the second branch pipe 372 may be controlled by a flow control valve 322. For example, the flow control valve 322 may be a three way valve.

Although not limited, the flow control valve 322 may be connected to the supply pipe 361, and the first branch pipe 371 and the second branch pipe 372 may be connected to the flow control valve 322. have.

As another example, the flow control valve 332 may be installed in each of the first branch pipe 371 and the second branch pipe 372.

The flow rate of the coolant flowing to the first branch pipe 371 and the second branch pipe 372 may be adjusted by the flow control valve 322. For example, cooling water may flow to each of the first branch pipe 371 and the second branch pipe 372, or to any one of the first branch pipe 371 and the second branch pipe 372. have.

The first branch pipe 371 may extend to the engine 200 through the exhaust gas heat exchanger 240.

That is, the cooling water flowing through the first branch pipe 371 is heat-exchanged with the exhaust gas discharged from the engine 200 in the exhaust gas heat exchanger 240 and flows through the engine 200 while the engine 200 The waste heat of is recovered. The first branch pipe 371 may be referred to as an engine side pipe.

The second branch pipe 372 may pass through the intercooler 500. The second branch pipe 372 passing through the intercooler 500 may be connected to the first branch pipe 371, for example. The second branch pipe 372 may be referred to as an intercooler side pipe. A pipe located at the inlet side of the intercooler 500 in the second branch pipe 372 is referred to as an inlet pipe 372a, and a pipe positioned at the outlet side of the intercooler 500 is an outlet pipe 372b. It can be called this. The outlet pipe 372b may be connected to a downstream side of the flow control valve 322 among the first branch pipes 372.

In this case, the second branch pipe 372 may be connected to a pipe at the inlet side of the exhaust gas heat exchanger 240 among the first branch pipes 372.

Therefore, the cooling water branched from the supply pipe 361 to the second branch pipe 372 flows through the intercooler 500 and exchanges heat with the mixer, and then flows to the inlet pipe of the exhaust gas heat exchanger 240. I can.

At this time, in order to reduce the temperature of the cooling water branched from the supply pipe 361 to the second branch pipe 372, the cooling water flowing through the second branch pipe 372 exchanges heat with the refrigerant in the refrigerant pipe 170 Can be.

For example, the gas heat pump system 10 may further include a cooling water heat exchanger 152. The cooling water heat exchanger 152 may be, for example, a plate heat exchanger.

Among the second branch pipes 372, a pipe at the inlet side of the intercooler 500 may pass through the cooling water heat exchanger 152.

The cooling water flowing through the cooling water heat exchanger 152 may be heat-exchanged with a refrigerant to be sucked into the compressor 110, for example.

For example, the suction side pipe (or the outlet side pipe of the gas-liquid separator 160) 171 of the compressor 110 may pass through the cooling water heat exchanger 152.

The refrigerant discharged from the gas-liquid separator 160 may be sucked into the compressor 110 after heat exchange with the coolant while flowing through the coolant heat exchanger 152.

On the other hand, the coolant branched from the supply pipe 361 to the second branch pipe 372 may flow to the intercooler 500 after heat exchange with the refrigerant while flowing through the coolant heat exchanger 152.

Since the temperature of the refrigerant discharged from the gas-liquid separator 160 is considerably lower than the temperature of the cooling water flowing into the cooling water heat exchanger 152, the temperature may decrease while the cooling water flows through the cooling water heat exchanger 152. have.

Accordingly, according to the present embodiment, the cooling water branched from the supply pipe 361 to the second branch pipe 372 flows through the cooling water heat exchanger 152 while the temperature is lowered to the intercooler 500. Since it flows, there is an advantage in that the cooling performance of the mixer in the intercooler 500 can be shaped.

In addition, since the refrigerant is absorbed while passing through the cooling water heat exchanger 152, the temperature supplied to the compressor is increased in the cooling mode, thereby stabilizing the refrigerant system.

In addition, even if the temperature of the cooling water increases while passing through the intercooler 500, the temperature T1 of the cooling water is lower than the temperature T2 of the cooling water of the supply pipe 361.

This is because the temperature of the cooling water supplied to the intercooler 500 is lowered by the cooling water heat exchanger 152 described above.

The cooling water discharged from the intercooler 500 is combined with the cooling water branched through the first branch pipe 371.

Since the temperature T1 of the cooling water discharged from the intercooler 500 is lower than the temperature T2 of the cooling water of the supply pipe 361, the temperature T3 of the cooling water supplied to the exhaust gas heat exchanger 240 ( The temperature of the coolant in a state in which the coolant branched to the first branch pipe 371 and the coolant discharged from the intercooler 500 are combined) is lower than the temperature T2 of the coolant of the supply pipe 361.

Accordingly, according to the present embodiment, since the coolant whose temperature is lowered passes through the exhaust gas heat exchanger 240 and the engine 200, there is an advantage in that the cooling efficiency of the engine 200 is improved.

For heat dissipation of the turbocharger, which is the supercharge means 400, the cooling water pipe 360 is a bypass pipe bypassed from the outlet side pipe of the exhaust gas heat exchanger 240 among the first branch pipes 371 It may further include (373).

The bypass pipe 373 may be supplied to the outlet side pipe of the exhaust gas heat exchanger 240 after heat exchange with the supercharging means 400.

That is, one end of the bypass pipe 373 is connected to the pipe at the outlet side of the exhaust gas heat exchanger 240, and the other end is connected to the pipe at the outlet side of the exhaust gas heat exchanger 240 at a position spaced apart from the one end. Can be connected.

Accordingly, a part of the coolant that has passed through the exhaust gas heat exchanger 240 flows directly to the engine 200, and another part flows to the engine 200 after heat exchange with the supercharging means 400.

The cooling water pipe 360 may further include a recovery pipe 362 that guides the cooling water passing through the engine 200 to the first flow conversion unit 310.

In addition, the cooling water pipe 360 may further include a first guide pipe 363 for guiding the cooling water from the first flow conversion part 310 to the second flow conversion part 320.

In addition, the cooling water pipe 360 may further include a second guide pipe 364 for guiding the cooling water from the second flow conversion unit 320 to the auxiliary heat exchanger 150.

The cooling water pipe 360 may further include a third guide pipe 365 for guiding the cooling water from the second flow conversion unit 320 to the radiator 150.

The cooling water pipe 360 may further include a fourth guide pipe 366 for guiding the cooling water from the first flow conversion unit 310 to the supply pipe 361.

For example, when the temperature of the coolant that has passed through the engine 200 is less than the set temperature, the first heat exchange effect by flowing the coolant to the auxiliary heat exchanger 150 or the radiator 330 becomes insignificant. The cooling water introduced into the flow conversion unit 310 may be bypassed to the supply pipe 361 through the fourth guide pipe 366.

The gas heat pump system 10 may further include a coolant temperature sensor 290 installed at an outlet side of the engine 200 to detect a temperature of coolant that has passed through the engine 200.

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

3 is a cycle diagram showing flows of refrigerant, coolant, and mixed fuel during a heating operation of a gas heat pump system according to an embodiment of the present invention, and FIG. 4 is a diagram of a gas heat pump system according to an embodiment of the present invention. A cycle diagram showing flows of refrigerant, coolant, and mixed fuel during cooling operation, and FIG. 5 is a view showing the flow of coolant in the engine module according to an embodiment of the present invention.

First, referring to FIGS. 3 and 5, when the gas heat pump system 10 performs a heating operation, the refrigerant is the compressor 110, the oil separator 115, the four sides 117, and the indoor heat exchanger. (140) and the subcooled heat exchanger (130). Then, the refrigerant is depressurized in the main expansion device 125 and heat-exchanged in the outdoor heat exchanger 120, and then flows back into the four sides 117. Here, the indoor heat exchanger 140 may function as a "condenser" and the outdoor heat exchanger 120 may function as a "evaporator".

The refrigerant passing through the four sides 117 may flow into the auxiliary heat exchanger 150 and exchange heat with the coolant flowing through the second guide pipe 364.

The refrigerant flowing into the auxiliary heat exchanger 150 is an evaporating refrigerant and forms a low temperature and low pressure, and the coolant supplied to the auxiliary heat exchanger 150 forms a high temperature by the heat of the engine 200. Accordingly, the refrigerant of the auxiliary heat exchanger 150 absorbs heat from the cooling water, thereby improving evaporation performance.

The refrigerant heat-exchanged in the auxiliary heat exchanger 150 may flow into the gas-liquid separator 160 and phase-separate, and then may be sucked into the compressor 110. The refrigerant may flow through repeated cycles described above.

On the other hand, when the cooling water pump 300 is driven, the cooling water discharged from the cooling water pump 300 flows along the supply pipe 361 and then the first branch pipe 371 by the flow control valve 322. ) And the second branch pipe 372 to flow.

The refrigerant branched through the first branch pipe 371 flows into the exhaust gas heat exchanger 240 to heat exchange with the exhaust gas. In addition, the coolant discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200, and passes through the recovery pipe 362 to the first flow conversion unit 310. Flow in.

Under the control of the first flow conversion unit 310, the coolant passing through the first flow conversion unit 310 flows toward the second flow conversion unit 320 along the first guide pipe 363. . In addition, the cooling water that has passed through the second flow conversion unit 320 may be introduced into the auxiliary heat exchanger 150 via the second guide pipe 364 to exchange heat with the refrigerant. In addition, the cooling water passing through the auxiliary heat exchanger 150 may be introduced into the cooling water pump 300. The cooling water can be flowed repeatedly in this cycle.

On the other hand, the cooling water branched into the second branch pipe 372 is heat-exchanged with the refrigerant while passing through the cooling water heat exchanger 152. Further, the cooling water that has passed through the cooling water heat exchanger 152 is heat-exchanged with the mixer while passing through the intercooler 500. And, finally, the cooling water flows to the first branch pipe 371.

Meanwhile, during the heating operation, the flow of cooling water to the radiator 330 may be limited. In general, since the heating operation is performed when the temperature of the outside air is low, even if the cooling water is not cooled in the radiator 330, there is a high possibility that the cooling water is cooled during the flow of the cooling water pipe 360.

Accordingly, the first and second flow conversion units 310 and 320 may be controlled so that the coolant does not pass through the radiator 330 during heating operation.

However, when heat exchange in the auxiliary heat exchanger 150 is not required, cooling water is introduced into the radiator 330 from the second flow conversion unit 320 through the third guide pipe 365. May be.

Next, driving of the engine 200 will be described.

The air filtered by the air filter 210 and the fuel pressure-controlled through the zero governor 230 are mixed in the mixer 220. The mixer mixed in the mixer 220 is pressurized by the supercharging means 400, and the pressurized mixer is cooled by the intercooler 500 to improve density.

The amount of the mixer passing through the intercooler 500 is adjusted through the adjusting means 600 and supplied to the engine 200 to drive the engine 200. Further, the exhaust gas discharged from the engine 200 flows into the exhaust gas heat exchanger 240 to exchange heat with the coolant, and is discharged to the outside through the muffler 250.

Next, referring to FIG. 4, on the other hand, when the gas heat pump system 10 performs a cooling operation, the refrigerant is the compressor 110, the oil separator 115, the four sides 117, and the outdoor heat exchanger. 120 and the subcooling heat exchanger 130.

Then, the refrigerant is depressurized in the indoor expansion device 145, heat exchanged in the indoor heat exchanger 140, and flows back into the four sides 117. Here, the outdoor heat exchanger 120 may function as a "condenser" and the indoor heat exchanger 120 may function as a "evaporator".

The refrigerant passing through the four sides 117 may be introduced into the auxiliary heat exchanger 150 and exchanged with the coolant flowing through the cooling water pipe 360. In addition, the refrigerant heat-exchanged in the auxiliary heat exchanger 150 may be introduced into the gas-liquid separator 160 and phase-separated, and then sucked into the compressor 110. The refrigerant may flow through repeated cycles described above.

On the other hand, when the cooling water pump 300 is driven, the cooling water discharged from the cooling water pump 300 flows along the supply pipe 361 and then the first branch pipe 371 by the flow control valve 322. ) And the second branch pipe 372 to flow.

The refrigerant branched through the first branch pipe 371 flows into the exhaust gas heat exchanger 240 to heat exchange with the exhaust gas. In addition, the coolant discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200, and passes through the recovery pipe 362 to the first flow conversion unit 310. Flow in.

The flow of cooling water until flowing into the first flow conversion unit 310 is the same as the flow of cooling water during the heating operation.

The coolant passing through the first flow conversion unit 310 flows into the second flow conversion unit 320 and flows to the radiator 330 under the control of the second flow conversion unit 320 to heat exchange with outside air. Can be. In addition, the cooling water cooled by the radiator 330 is introduced into the cooling water pump 300. The cooling water can be flowed repeatedly in this cycle.

Meanwhile, during the cooling operation, the flow of cooling water to the auxiliary heat exchanger 150 may be restricted. In general, since the cooling operation is performed when the temperature of the outside air is high, endothermic heat of the evaporating refrigerant for securing the evaporation performance may not be required. Accordingly, the first and second flow conversion units 310 and 320 may be controlled so that the cooling water does not pass through the auxiliary heat exchanger 150 during cooling operation.

However, when heat exchange in the auxiliary heat exchanger 150 is required, cooling water may be introduced into the auxiliary heat exchanger 150 via the second flow conversion unit 320.

In relation to the driving of the engine 200, since it is the same as the operation during the heating operation, a detailed description thereof will be omitted.

According to the proposed embodiment, since the intercooler can be cooled using coolant for cooling the engine, there is an advantage that a coolant flow path separate from a cooling water flow path for engine cooling is unnecessary. Accordingly, there is an advantage of not only being able to flow coolant to the intercooler side but also to the engine side by using one coolant pump.

In addition, since the coolant for flowing to the intercooler is heat-exchanged with the low-temperature refrigerant, the cooling performance of the mixer in the intercooler is improved.

In addition, since the coolant to be supplied to the exhaust gas heat exchanger is supplied to the exhaust gas heat exchanger in a state that is combined with the coolant that has passed through the intercooler having a relatively low temperature, there is an advantage of improving the heat exchange performance of the exhaust gas heat exchanger and the cooling performance of the engine. .

10: gas heat pump system 110: compressor
120: outdoor heat exchanger 140: indoor heat exchanger
150: auxiliary heat exchanger 152: cooling water heat exchanger
200: engine 240: exhaust gas heat exchanger
300: coolant pump 322: flow control valve
361: supply pipe 362: return pipe
371: first branch piping 372: second branch piping
400: supercharge means 500: intercooler
600: adjustment means

Claims (6)

An air conditioning module including a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and a refrigerant pipe;
An engine module including an engine that provides power for driving the compressor by combusting a mixture of fuel and air; And
And a cooling module through which coolant for cooling the engine flows,
The engine module,
A supercharging means for compressing a mixture of air and fuel and discharging it to the engine; And
An intercooler disposed between the engine and the supercharging means, and cooling the mixer compressed by the supercharging means,
The cooling module includes an intercooler side pipe through which cooling water to be supplied to the intercooler flows,
A cooling water heat exchanger connected to the intercooler side pipe,
The refrigerant pipe is connected to the suction side of the compressor and includes a suction side pipe passing through the cooling water heat exchanger,
A gas heat pump system in which refrigerant in the suction side pipe and coolant in the intercooler side pipe heat exchange. The method of claim 1,
Further comprising a gas-liquid separator for separating gas and liquid,
The suction side pipe is a gas heat pump system that is an outlet pipe of the gas-liquid separator. The method of claim 1,
The cooling module further includes an engine-side pipe branching from the intercooler-side pipe,
The intercooler-side pipe includes an inlet-side pipe positioned at an inlet side of the intercooler, and an outlet-side pipe positioned at an outlet side of the intercooler,
The gas heat pump system wherein the inlet pipe and the engine pipe are connected to a flow control valve. The method of claim 3,
The outlet pipe is a gas heat pump system connected to a downstream side of the flow control valve from the engine pipe. The method of claim 3,
Further comprising an exhaust gas heat exchanger into which the exhaust gas exhausted from the engine is introduced,
The engine-side pipe is connected to the engine after passing through the exhaust gas heat exchanger. The method of claim 5,
The gas heat pump system further comprises a bypass pipe branched from the outlet pipe of the exhaust gas heat exchanger among the engine pipes and connected to the outlet pipe of the exhaust gas heat exchanger after passing through the supercharge means.

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