KR102004480B1 - 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 burns a mixture of fuel and air to provide power for operation of the compressor; And an oil circulation module for supplying oil to the engine, wherein the engine module comprises: a mixer for mixing the air and fuel and discharging the mixture to the engine side; A supercharger disposed between the mixer and the engine for compressing the mixer discharged from the mixer and discharging the mixed gas to the engine; And an intercooler disposed between the engine and the supercharging means for cooling the mixer compressed by the supercharging means, wherein the oil circulation module comprises: an oil pan in which the oil is stored; And a second oil passage for supplying the oil of the oil pan to the supercharging means, wherein oil flowing through the second oil passage is branched from the refrigerant branched from the refrigerant pipe And is heat-exchanged with the refrigerant flowing in the branch piping.

Description

[0001] Gas heat pump system [0002]

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 may include 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 may include 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 may include an engine that generates power using a mixture of fuel and air (hereinafter referred to as a mixer). In one example, the engine may include a cylinder to which the mixer is fed and a piston that is provided movably within the cylinder.

The gas heat pump system may further include 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. And, the fuel supply apparatus may include a zero governor for supplying fuel of 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). In one example, the zero governor may include a nozzle unit for reducing the pressure of the fuel, a diaphragm to which the reduced pressure is applied in the nozzle unit, and a valve unit to be opened and closed by the 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.

When the mixer supplied to the engine is burned, the exhaust gas can be discharged from the engine.

Korean Patent Registration No. 10-1341533, which is a prior art document, discloses a gas heat pump system and a control method thereof.

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.

An object of the present invention is to provide a gas heat pump system in which the performance of an engine can be improved by supercharging a supercharging device supplied to an engine with a supercharging device.

Another object of the present invention is to provide a gas heat pump system in which damage to a supplied component is prevented by preventing oil from being oxidized by cooling the oil flowing through the supercharging device.

Another object of the present invention is to provide a gas heat pump system capable of cooling oil with a simple structure.

According to an aspect of the present invention, there is provided a gas heat pump system including 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 burns a mixture of fuel and air to provide power for operation of the compressor; And an oil circulation module for supplying oil to the engine.

In this embodiment, the engine module includes: a mixer that mixes the air and the fuel and discharges the mixture to the engine; A supercharger disposed between the mixer and the engine for compressing the mixer discharged from the mixer and discharging the mixed gas to the engine; And an intercooler which is disposed between the engine and the supercharging means and cools the mixer compressed by the supercharging means.

Further, in the present embodiment, the oil circulation module includes an oil pan in which the oil is stored, a first oil channel for supplying the oil of the oil pan to the engine, and a second oil channel for supplying the oil of the oil pan to the supercharging means And a second oil passage for supplying oil.

In order to cool the oil flowing through the second oil passage, the oil may be heat-exchanged with the refrigerant flowing in the refrigerant branch pipe branched from the refrigerant pipe.

The gas heat pump system of the present embodiment may further include an oil cooler for exchanging the refrigerant branched to the refrigerant branch pipe with a refrigerant flowing along the second oil channel.

Alternatively, in the present embodiment, the refrigerant branched to the refrigerant branch pipe can cool the oil indirectly by cooling the supercharging means.

The gas heat pump system according to the present embodiment further includes a cooling module in which cooling water for cooling the engine flows and an intermediate heat exchanger for exchanging the refrigerant branched to the refrigerant branch pipe with the cooling water, The inlet pipe of the intermediate heat exchanger is provided with an expansion valve for regulating the flow of the refrigerant and expanding the refrigerant. The refrigerant passing through the intermediate heat exchanger can be heat-exchanged with the oil of the supercharging means.

The second oil passage is provided with an oil temperature sensor for sensing the temperature of the oil discharged from the supercharging means. The expansion valve may be turned on when the temperature sensed by the oil temperature sensor is equal to or higher than a reference temperature.

As another example, the gas heat pump system of the present embodiment may further include a cooling module in which cooling water for cooling the engine flows, and an intermediate heat exchanger for exchanging the refrigerant branched from the refrigerant branch pipe with the cooling water , An oil cooling pipe is branched to the outlet pipe of the intermediate heat exchanger in the refrigerant branch pipe, and the oil cooling pipe is provided with a flow control valve for regulating the refrigerant flow.

The second oil passage is provided with an oil temperature sensor for sensing the temperature of the oil discharged from the supercharging means. The flow control valve can be controlled according to a result of comparison between the temperature sensed by the oil temperature sensor and the reference temperature have.
According to another aspect, a gas heat pump system 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 burns a mixture of fuel and air to provide power for operation of the compressor; An oil circulation module for supplying oil to the engine; A cooling module through which cooling water for cooling the engine flows; And an auxiliary heat exchanger for exchanging heat between the refrigerant flowing into the refrigerant branch pipe branched from the refrigerant pipe and the cooling water.
Wherein the engine module includes: a mixer for mixing the air and the fuel and discharging the mixture to the engine; A supercharger disposed between the mixer and the engine for compressing the mixer discharged from the mixer and discharging the mixed gas to the engine; And an intercooler disposed between the engine and the supercharging means, the supercharger cooling the mixer compressed by the supercharging means.
The oil circulation module includes an oil pan for storing the oil, a first oil channel for supplying the oil of the oil pan to the engine, and a second oil channel for supplying the oil of the oil pan by the supercharging means. And the oil flowing through the second oil passage is heat-exchanged in the refrigerant branch pipe with the refrigerant flowing in the auxiliary heat exchanger.

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

Further, by cooling the oil supplied as the supercharging means through the oil cooler, the performance and life of the supercharging means and the engine can be prevented from deteriorating.

Further, since the refrigerant is heat-exchanged with the oil of the supercharging means and is supplied to the compressor after the heat is absorbed, the heating performance can be improved.

1 is a cycle diagram showing a 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 showing the flow of refrigerant, cooling water, and mixed fuel in a heating operation of a gas heat pump system according to an embodiment of the present invention.
4 is a cycle diagram showing the flow of refrigerant, cooling water, and mixed fuel in a cooling operation of a gas heat pump system according to an embodiment of the present invention.
5 is a view showing the flow of cooling water and oil in an engine module according to an embodiment of the present invention.
6 is a view showing an engine module according to another embodiment of the present invention.
7 is a cycle diagram showing a configuration of a gas heat pump system according to another embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that, in adding reference numerals to the constituent elements of the drawings, the same constituent elements are denoted by the same reference numerals whenever possible, even if they are shown in different drawings. In the following description of the embodiments of the present invention, a detailed description of known functions and configurations incorporated herein will be omitted when it may make the difference that the embodiments of the present invention are not conclusive.

In describing the components of the embodiment of the present invention, terms such as first, second, A, B, (a), and (b) may be used. These terms are intended to distinguish the constituent elements from other constituent elements, and the terms do not limit the nature, order or order of the constituent elements. When a component is described as being "connected", "coupled", or "connected" to another component, the component may be directly connected or connected to the other component, Quot; may be "connected," "coupled," or "connected. &Quot;

FIG. 1 is a cycle diagram showing a 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.

Referring to FIGS. 1 and 2, a 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 refrigerant compressed in the compressor 110, And may include four sides 117 for switching directions.

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 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 can flow to the outdoor heat exchanger 120 or the indoor heat exchanger 140.

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. [

When the gas heat pump system 10 is operated in the cooling operation mode, the refrigerant passing through the four sides 117 can flow to the indoor heat exchanger 140 side via 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 passing through the four sides 117 flows into the outdoor heat exchanger 120 through the indoor heat exchanger 140 .

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

Hereinafter, the configuration of the gas heat pump 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. An outdoor fan (122) for blowing outdoor air may be disposed at one side of the outdoor heat exchanger (120).

A main expansion device 125 for reducing the pressure of the refrigerant may be provided at the outlet side of the outdoor heat exchanger 120. For example, the main expansion device 125 may include 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, a supercooling heat exchanger 130 for further cooling the refrigerant may be provided. The supercooling heat exchanger 130 may be connected to the supercooling flow path 132. The supercooling flow path 132 may be branched from the refrigerant pipe 170 and connected to the supercooling heat exchanger 130.

The supercooling flow path 132 may be 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 may be 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 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 .

Meanwhile, in the heating process, the refrigerant condensed in the indoor heat exchanger 140 may flow into the auxiliary heat exchanger 150 (or the intermediate heat exchanger). The refrigerant branch pipe 151 may be connected to the auxiliary heat exchanger 150.

An expansion valve 152 may be installed in the piping located at the inlet side of the auxiliary heat exchanger 150 in the refrigerant branch pipe 151. The expansion valve 152 can reduce the pressure of the refrigerant while controlling the flow of the refrigerant.

Accordingly, the auxiliary heat exchanger 150 is a heat exchanger capable of performing heat exchange between the low-pressure refrigerant and the high-temperature cooling water, and may include, for example, a plate heat exchanger.

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 gas heat pump system 10 may further include a cooling water tank 305 for storing cooling water for cooling the engine 200 and a cooling water pipe 360 for flowing the cooling water .

The cooling water pipe 360 is provided with a cooling water pump 300 for generating the flow of cooling water, a plurality of flow switching parts 310 and 320 for switching the flow direction of the cooling water, and a radiator 330, radiator) may be installed.

The plurality of flow switching units 310 and 320 may 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 located 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 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 mixed fuel to the engine 200 and 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.

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 230 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 an outlet side of the engine 200 and through which exhaust gas generated 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.

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 follow the high cooling load, which may cause a cooling failure.

In order to solve this problem, when the air is supplied by adjusting the amount of fuel according to the amount of air after pressurizing the air with a supercharger as in an automobile engine, the supply pressure (about 2.5 kPa) in the gas fuel pipe is lower than the boost pressure There is a problem that fuel supply becomes difficult.

The gas heat pump system 10 further includes a supercharging means 400 and an adjusting means 600 disposed between the mixer 220 and the engine 200 can do.

After the air and the fuel are mixed in the mixer 220, the supercharger 400 compresses the discharged mixer and discharges it to the engine 200 side. 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 may be a turbocharger driven by the exhaust gas of the engine 200.

The turbocharger 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.

The turbine 411 is connected to the exhaust manifold of the engine 200 through the exhaust pipe 191 of the engine 200 when the supercharging means 400 is provided as a turbocharger, When the mixed gas is introduced into the mixer 220, the mixed gas is pressurized (compressed) and then discharged to the intercooler 500 side.

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 and can be supplied to the engine 200 after being pressurized by the supercharging means 400 at a high pressure.

Also, the amount of the high-pressure mixer (air + fuel) supplied to the engine 200 through the regulating unit 600 may be precisely controlled.

Therefore, the efficiency of the engine 200 can be improved. In addition, the maximum output 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 supercharger 400 as described above, the pressure and the temperature of the mixer increase. 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.

The gas heat pump system 10 may further include an intercooler 500 disposed between the supercharging means 400 and the regulating means 600 to solve the above problem.

The intercooler (500) cools the high-temperature high-pressure mixer discharged from the supercharging means (400), reduces the volume, increases the density, and discharges it.

For example, the intercooler 500 may exchange heat between a mixer to be supplied to the engine 200 and a part of cooling water to flow to the engine 200.

Therefore, according to the intercooler 500, the temperature of the mixer supplied to the engine 200 can be lowered and the density can be increased, thereby improving the volume efficiency of the engine 200.

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 prolonged. 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 to stop the operation of the mixer 600. In this case, It is possible to suppress the formation of formic acid by burning or externally discharging, and it is possible to prevent the danger such as breakage and explosion of piping.

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

The supply pipe 361 may be provided with a cooling water pump 300 for flowing cooling water.

The supply pipe 361 may extend to the engine 200 through the exhaust gas heat exchanger 240.

That is, the cooling water flowing through the supply pipe 361 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, Lt; / RTI >

The cooling water pipe 360 is connected to the bypass pipe 373 bypassed from the outlet pipe of the exhaust gas heat exchanger 240 among the supply pipe 361 for radiating heat from the turbocharger, ). ≪ / RTI >

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

Therefore, a portion of the cooling water passing through the exhaust gas heat exchanger 240 flows directly to the engine 200, and the other portion of the cooling water 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 for guiding cooling water that has passed through the engine 200 to the first flow switching unit 310.

The cooling water pipe 360 may further include a first guide 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 may further include a second guide pipe 364 for guiding cooling water from the second flow switching unit 320 to the auxiliary heat exchanger 150.

The cooling water pipe 360 may further include a third guide pipe 365 for guiding cooling water from the second flow switching unit 320 to the radiator 330.

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

For example, when the temperature of the cooling water that has passed through the engine 200 is less than the predetermined 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 supply pipe 361 through the fourth guide pipe 366. [

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

An oil pan 820 for supplying oil to the engine 200 may be provided at one side of the engine 200 and the oil pan 800 may supply oil stored in the oil tank 810 Can receive.

The oil pan 800 may include an oil pump 820. The oil pumped by the oil pump 820 may be recovered from the engine 200 after being supplied to the engine 200 by the first oil passage 830.

The second oil passage 840 may be branched from the first oil passage 830. [ The second oil passage 840 supplies oil to the turbocharger for lubrication of the rotary shaft of the turbocharger and recovers oil from the turbocharger.

Although not limited, the outlet-side oil passage 842 of the turbocharger in the second oil passage 840 may be connected to the oil tank 810.

When the speed of the rotary shaft of the turbo choker is high, the temperature of the oil lubricated by the rotary shaft becomes high, and oil may be oxidized. The lubricating performance of the engine 200 and the turbocharger deteriorates and the performance and life of the engine 200 and the turbocharger are reduced.

Accordingly, the gas heat pump system 10 of the present invention may further include an oil cooler 700 for cooling the oil supplied to the turbocharger to limit the temperature rise of the oil.

The oil cooler 700 exchanges heat between the oil flowing into the turbocharger and the refrigerant flowing through the refrigerant pipe 170.

For example, refrigerant flowing through the refrigerant branch pipe 151 and oil flowing through the second oil channel 840 may be heat-exchanged by the oil cooler 700.

At this time, the refrigerant in the refrigerant branch pipe 151 is heat-exchanged with the cooling water by the auxiliary heat exchanger 150, and then flows to the oil cooler 700 and is heat-exchanged with the oil flowing into the turbocharger. Then, the refrigerant heat-exchanged with the oil may flow to the gas-liquid separator 160.

An oil temperature sensor 710 for detecting the temperature of the oil discharged from the turbocharger may be provided at the outlet-side oil passage 842 of the turbocharger in the second oil passage 840.

When the temperature sensed by the oil temperature sensor 710 becomes equal to or higher than the reference temperature, the refrigerant flows to the refrigerant branch pipe 151 by the expansion valve 152 provided in the refrigerant branch pipe 151, The refrigerant can be decompressed by the heat exchanger 152.

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

3 and 5, 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 supercooling heat exchanger (130).

Then, the refrigerant is decompressed in the main expansion device 125, 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;

Meanwhile, when the cooling water pump 300 is driven, the cooling water discharged from the cooling water pump 300 flows along the supply pipe 361, 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 flows into the first flow switching unit 310 via the return pipe 362 ≪ / RTI >

Under the control of the first flow switching unit 310, the cooling water flowing through the first flow switching unit 310 flows toward the second flow switching unit 320 along the first guide pipe 363 . The cooling water passing through the second flow switching unit 320 flows into the auxiliary heat exchanger 150 via the second guide pipe 364 and can be heat-exchanged with the refrigerant. The cooling water passing through the auxiliary heat exchanger (150) may be introduced 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.

When the heat exchange in the auxiliary heat exchanger 150 is not required, the cooling water flows from the second flow switching unit 320 to the radiator 330 via the third guide pipe 365 It is possible.

Next, 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 by the intercooler 500 to improve the density.

The amount of the mixer having passed 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.

The oil of the oil pan 800 flows along the first oil passage 830 by the operation of the oil pump 820 to perform the lubrication of the engine 200. The oil that is branched from the first oil passage 840 and flows along the second oil passage 840 performs lubrication of the turbocharger.

In the oil temperature sensor 710, the temperature of the oil discharged from the turbocharger is periodically or continuously sensed. When the sensed temperature of the oil reaches a reference temperature or more, the expansion valve 152 may be opened.

When the expansion valve 152 is opened, a part of the refrigerant passing through the supercooling heat exchanger 130 is branched into the refrigerant branch pipe 151 and flows into the auxiliary heat exchanger 150, Exchanged with the cooling water flowing through the heat exchanger 364.

The refrigerant introduced into the auxiliary heat exchanger 150 is a low-temperature refrigerant decompressed by the expansion valve 152. The cooling water supplied to the auxiliary heat exchanger 150 is heated to a high temperature by the heat of the engine 200 to be. Therefore, the refrigerant of the auxiliary heat exchanger (150) can absorb heat from the cooling water.

The refrigerant heat-exchanged in the auxiliary heat exchanger 150 flows to the oil cooler 700 and is heat-exchanged with the oil supplied to the supercharging unit 400. The refrigerant then flows into the gas-liquid separator 160 to be phase- (Not shown). The refrigerant can be repeatedly cycled through the above cycle.

In this embodiment, since the refrigerant passing through the auxiliary heat exchanger 150 is further heat-absorbed while being heat-exchanged with the oil in the oil cooler 700, the heating performance can be improved.

As another example, when the temperature of the oil detected by the oil temperature sensor 710 is lower than the reference temperature, the opening degree of the expansion valve 152 is increased Can be varied.

For example, when the heating operation is started, the expansion valve 152 may be opened at the first opening degree, and if the temperature of the oil detected by the oil temperature sensor 710 is higher than the reference temperature, Can be changed to a second opening degree smaller than the first opening degree.

Referring to FIG. 4, when the gas heat pump system 10 performs the cooling operation, the refrigerant flows into the compressor 110, the oil separator 115, the four sides 117, the outdoor heat exchanger 120 ) And a supercooling heat exchanger (130).

Then, the refrigerant is decompressed in the indoor expansion device 145, heat-exchanged in the indoor heat exchanger 140, and then introduced 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 an "evaporator. &Quot;

The refrigerant passing through the four sides 117 flows into the gas-liquid separator 160, is phase-separated, and then is 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 along the supply pipe 361, 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 flows into the first flow switching unit 310 via the return pipe 362 ≪ / RTI >

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 refrigerant may not be required for securing the evaporation performance. 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.

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

Further, by cooling the oil supplied as the supercharging means through the oil cooler, the performance and life of the supercharging means and the engine can be prevented from deteriorating.

6 is a view showing an engine module according to another embodiment of the present invention.

This embodiment is identical to the previous embodiment in other respects except that the refrigerant indirectly cools the oil by directly cooling the turbocharger. Therefore, only the characteristic parts of the present embodiment will be described below.

Referring to FIG. 6, in the case of the present embodiment, the oil cooler is omitted, and the refrigerant in the refrigerant branch pipe 151a can cool the turbocharger itself.

When the refrigerant in the refrigerant branch pipe 151a cools the turbocharger itself, the oil supplied to the turbocharger can be indirectly cooled by the refrigerant.

In this embodiment, the oil of the turbocharger can be cooled by the cooling water flowing through the bypass pipe 373 described in the previous embodiment and the refrigerant flowing through the refrigerant branch pipe 151a.

Alternatively, the bypass pipe 373 may be omitted, and the turbocharger may be cooled only by the refrigerant flowing along the refrigerant branch pipe 151a.

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

The present embodiment differs from the previous embodiment in that the oil cooling pipe is branched from the outlet pipe of the auxiliary heat exchanger and connected to the oil cooler. Therefore, only the characteristic parts of the present embodiment will be described below.

Referring to FIG. 7, the refrigerant branch pipe 151a is branched from the refrigerant pipe 170, and the auxiliary heat exchanger 150 is connected to the refrigerant branch pipe 151a. An expansion valve 152a is provided in the inlet pipe of the auxiliary heat exchanger 150 in the refrigerant branch pipe 151a.

The refrigerant branch pipe 151a may be connected to the gas-liquid separator 160 or the inlet pipe of the gas-liquid separator 160.

The oil cooling pipe 153 may be branched from the outlet pipe of the auxiliary heat exchanger 150 of the refrigerant branch pipe 151a. The oil cooling pipe 153 may be connected to the oil cooler 700.

The oil cooling pipe 153 may be provided with a flow control valve 154 for controlling the flow of refrigerant. The flow control valve 154 may be turned on when the temperature of the oil detected by the oil sensor 710 is equal to or higher than the reference temperature.

According to the present embodiment, at the start of the heating operation, the expansion valve 152a may be turned on and the flow control valve 154 may be turned off. In this case, the refrigerant heat-exchanged with the cooling water in the auxiliary heat exchanger (150) can flow directly to the gas-liquid separator (160) without flowing through the oil cooler (700).

If the temperature of the oil detected by the oil sensor 710 is higher than the reference temperature, the flow control valve 154 may be turned on.

Then, some of the refrigerant heat-exchanged with the cooling water in the auxiliary heat exchanger 150 flows into the gas-liquid separator 160 without flowing through the oil cooler 700, and another part of the refrigerant flows through the oil cooler 700 Liquid separator 160 after exchanging heat with the oil.

In the present specification, a configuration for supplying and circulating oil to the engine and the turbocharger may be referred to as an oil circulation module. For example, the oil circulation module may include a first oil passage, a second oil passage, an oil pan, and an oil tank.

10: Gas heat pump system 110: Compressor
120: outdoor heat exchanger 140: indoor heat exchanger
150: auxiliary heat exchanger 151: refrigerant branch piping
152: Expansion valve
200: engine 240: exhaust gas heat exchanger
400: supercharging means 700: oil cooler
700: Oil temperature sensor 830: First oil path
840: the second oil passage

Claims (10)

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 burns a mixture of fuel and air to provide power for operation of the compressor;
An oil circulation module for supplying oil to the engine;
A cooling module through which cooling water for cooling the engine flows; And
And an auxiliary heat exchanger for exchanging heat between the refrigerant flowing into the refrigerant branch pipe branched from the refrigerant pipe and the cooling water,
The engine module includes:
A mixer for mixing the air and the fuel and discharging the mixture to the engine side;
A supercharger disposed between the mixer and the engine for compressing the mixer discharged from the mixer and discharging the mixed gas to the engine; And
And an intercooler which is disposed between the engine and the supercharging means and cools the mixer compressed by the supercharging means,
The oil circulation module includes an oil pan in which the oil is stored,
A first oil passage for supplying the oil of the oil pan to the engine,
And a second oil passage for supplying the oil of the oil pan to the supercharging means,
And the oil flowing through the second oil passage is heat-exchanged with the refrigerant flowing in the auxiliary heat exchanger in the refrigerant branch pipe. The method according to claim 1,
And an oil cooler for exchanging the refrigerant branched to the refrigerant branch pipe with a refrigerant flowing along the second oil channel. The method according to claim 1,
And the refrigerant branched to the refrigerant branch pipe indirectly cools the oil by cooling the supercharging means. The method according to claim 2 or 3,
And an expansion valve for controlling the flow of the refrigerant and expanding the refrigerant is provided in the inlet pipe of the auxiliary heat exchanger in the refrigerant branch pipe. 5. The method of claim 4,
Wherein the second oil passage is provided with an oil temperature sensor for sensing the temperature of the oil discharged from the supercharging means,
Wherein the expansion valve is turned on when the temperature sensed by the oil temperature sensor is equal to or higher than a reference temperature. The method according to claim 1,
An oil cooling pipe is branched from the refrigerant branch pipe to an outlet side pipe of the auxiliary heat exchanger,
Wherein the oil cooling pipe is provided with a flow control valve for controlling the flow of refrigerant. The method according to claim 6,
And an oil cooler for exchanging the refrigerant branched to the oil cooling pipe with a refrigerant flowing along the second oil passage. The method according to claim 6,
And the refrigerant branched to the oil cooling pipe indirectly cools the oil by cooling the supercharging means. 9. The method according to claim 7 or 8,
Wherein the second oil passage is provided with an oil temperature sensor for sensing the temperature of the oil discharged from the supercharging means,
Wherein the flow control valve is controlled according to a result of comparison between a temperature sensed by the oil temperature sensor and a reference temperature. 10. The method of claim 9,
Further comprising an expansion valve provided on an outlet side pipe of the auxiliary heat exchanger in the refrigerant branch pipe,
The flow control valve is turned on when the heating operation is started, and the flow control valve is turned on when the temperature sensed by the oil temperature sensor during the heating operation is equal to or higher than the reference temperature.

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