KR20200044734A - A gas heat-pump system - Google Patents

Abstract

The present invention relates to a gas heat pump system which blocks mixed gas leaked from a supercharger to prevent the mixed gas from being exposed to the outside. According to embodiments of the present invention, the gas heat pump system comprises an engine module including: a mixer to mix air and fuel to discharge mixed gas to an engine side; a supercharger arranged between the mixer and the engine to compress mixed gas discharged from the mixer by rotating power of an engine or a motor and then discharge compressed mixed gas to an intake manifold side of the engine; a control means arranged between the supercharger and the engine to control an amount of compressed mixed gas supplied to the intake manifold side of the engine; a buffer tank to cover the supercharger; and a connection pipe to connect the mixer and the buffer tank. Mixed gas discharged from the connection pipe is sucked to the supercharger after flowing into the buffer tank.

Description

Gas heat pump system {A gas heat-pump system}

The present invention relates to a gas heat pump system.

The heat pump system is a system equipped with a refrigeration cycle capable of performing cooling or heating operation, and may be interlocked with a hot water supply device or an air conditioning device. That is, hot water may 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 air conditioning may be performed.

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

The heat pump system includes a gas heat pump system. A large-capacity compressor is required for air conditioning in industrial or large buildings, not for household use. That is, a gas heat pump system may be used as a system that uses a gas engine rather than an electric motor to drive a compressor for compressing a large amount of refrigerant into a gas of high temperature and high pressure.

The gas heat pump system includes an engine that generates power using a mixture of fuel and air (hereinafter, a mixer). In one example, the engine may include a cylinder supplied with the mixer and a piston movably provided within the cylinder.

The gas heat pump system includes 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 includes a zero governor for supplying fuel at a constant pressure.

The zero governor can be understood as a device that regulates and supplies the outlet pressure constant regardless of the magnitude of the inlet pressure or the change in the flow rate of the fuel. For example, the zero governor may include a nozzle unit for reducing the pressure of the fuel, a diaphragm in which the pressure reduced in the nozzle unit acts, and a valve device opened and closed by the operation of the diaphragm. .

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

In addition, when the mixer supplied to the engine is burned, exhaust gas may be discharged from the engine. The gas heat pump system further includes a muffler for reducing noise generated from the exhaust gas.

Prior literature on a conventional gas heat pump system is as follows.

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

2. Name of invention: Gas heat pump system and control method thereof

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

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

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

Accordingly, 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 cannot keep up with the high cooling load, which may cause cooling failure.

In addition, to solve this, like the engine of a vehicle, after pressurizing the air with a supercharger and supplying while adjusting the fuel amount according to the air amount, the supply pressure (about 2.5kPa) in the gas fuel pipe is the supercharge pressure (about 30kPa). There is also a problem that fuel supply becomes difficult because it is lower.

In addition, in order to improve the performance of the engine, when the mixer and the engine is provided with a supercharger, and the mixer supplied to the engine is supercharged and supplied to the engine, leakage of the mixer gas occurs due to the characteristics of the supercharger, and the leaked mixer gas While being ignited by a cause such as sparks, there was a problem that a safety problem was generated, as well as a problem that the engine performance and efficiency deteriorated according to fuel leakage.

The present invention has been proposed to solve this problem, and it is an object of the present invention to provide a gas heat pump system in which a mixer leaked from a supercharger driven for supercharging is blocked from being exposed to the outside during engine operation.

In addition, an object of the present invention is to provide a gas heat pump system capable of solving a gas leakage in a supercharger and a related problem as the mixer leaked from the supercharger is re-suctioned into the supercharger.

In addition, an object of the present invention is to provide a gas heat pump system capable of improving the performance of the engine by supercharging a mixer supplied to the engine.

In addition, an object of the present invention is to provide a gas heat pump system capable of improving the maximum power of the engine without increasing the size of the engine.

In addition, an object of the present invention is to provide a gas heat pump system capable of improving the volumetric efficiency of the engine by reducing the temperature of the mixer supplied to the engine and increasing the density.

In addition, by providing the gas heat pump system that can prevent corrosion of parts by suppressing the generation of formic acid by driving the engine until the engine stops while the inflow of the mixer is stopped at the time of engine shutdown or by exhausting the outside. It aims to do.

In addition, before starting the engine, in a state in which the fuel supply is stopped, cranking is performed to prevent abnormal combustion that may occur due to the residual mixer in the engine as the mixer existing in the engine is discharged. It is an object of the present invention to provide a gas heat pump system that can stably start the engine.

In addition, an object of the present invention is to provide a gas heat pump system equipped with a plurality of other superchargers and capable of supercharging in a wider range.

Gas heat pump system according to an embodiment of the present invention, the air conditioning module including a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and a refrigerant pipe, and a mixture of fuel and air are burned to form a compressor, It may include an engine module including an engine that provides power for driving.

In addition, the engine module, a mixer for mixing the air and fuel to discharge to the engine side, disposed between the mixer and the engine, after compressing the mixer discharged from the mixer by the rotational power of the engine or motor, the engine A supercharger discharged to the intake manifold side, a connector connecting the mixer and the supercharger, and disposed between the supercharger and the engine to control the amount of compressed mixer supplied to the intake manifold side of the engine It may include adjustment means.

In addition, the engine module includes a buffer tank covering the supercharger, a connecting pipe connecting the mixer and the buffer tank, and the mixer discharged from the connecting pipe enters the buffer tank, and then the supercharger Can be inhaled with.

In addition, the supercharger may be provided in plural, including a first supercharger and a second supercharger spaced apart from each other.

In addition, based on the flow direction of the mixer, the first supercharger may be disposed at the rear end of the second supercharger, and the internal pressure of the second supercharger may be greater than the internal pressure of the first supercharger.

According to the present invention, when the engine is operated, the mixer leaked from the supercharger driven for supercharging is blocked so as not to be exposed to the outside, and as it is re-suctioned into the supercharger, gas leakage in the supercharger and problems related thereto can be solved. There is an advantage.

In addition, as the mixer leaked from the supercharger is ignited due to a spark or the like, there is an advantage of preventing a safety accident from occurring.

In addition, 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 natural intake using a supercharger.

There is also an advantage that the engine and the entire system can be downsized.

In addition, there is an advantage that it is possible to implement a large-capacity gas engine heat pump system with a small gas engine.

In addition, there is an advantage that can increase the engine output in a gas engine heat pump (GHP) using gas fuel for the home.

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

In addition, by driving the engine until the engine stops while the inflow of the mixer is blocked, the residual mixer is burned or discharged outside to suppress the generation of formic acid, thereby preventing corrosion of parts.

In addition, before starting the engine, in a state in which the fuel supply is stopped, cranking is performed to prevent abnormal combustion that may occur due to the residual mixer in the engine as the mixer existing in the engine is discharged. There is also an advantage that the engine can be started more stably.

In addition, by providing a plurality of superchargers, there is an advantage that can be supercharged in a wider range.

1 is a cycle diagram showing the configuration of a gas heat pump system according to a first embodiment of the present invention.
2 is a cycle diagram showing the flow of refrigerant, coolant and mixed fuel during heating operation of the gas heat pump system.
3 is a cycle diagram showing the flow of refrigerant, coolant, and mixed fuel during the cooling operation of the gas heat pump system.
4 is a system diagram showing an example of an engine module applied to the gas heat pump system of the present invention.
FIG. 5 is an enlarged view of a portion of FIG. 4.
6 is a system diagram showing another example of an engine module applied to the gas heat pump system of the present invention.
7 is an enlarged view of a portion of FIG. 6.

Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. However, the spirit of the present invention is not limited to the presented embodiments, and those skilled in the art to understand the spirit of the present invention may easily propose other embodiments within the scope of the same spirit.

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

Referring to FIG. 1, the gas heat pump system 10 according to the first embodiment of the present invention includes a plurality of components constituting a refrigerant cycle as an air conditioning system. In detail, in the refrigerant cycle, the direction of the refrigerant that has passed through the compressor (110) for compressing the refrigerant and the oil separator (115) and the oil separator (115) for separating oil from the refrigerant compressed by the compressor (110). A four-sided 117 that converts is included.

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

Meanwhile, the components of the system illustrated in FIG. 1 may be disposed on the outdoor side, that is, inside the outdoor unit, except for the indoor heat exchanger 140 and the indoor expansion device 145.

In detail, when the system 10 is operated in a cooling operation mode, the refrigerant that has passed through the four sides 117 flows to the indoor heat exchanger 140 through the outdoor heat exchanger 120. On the other hand, when the system 10 is operated in a heating operation mode, the refrigerant that has passed through the four sides 117 flows to the outdoor heat exchanger 120 through the indoor heat exchanger 140.

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

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

The refrigerant flowing into the outdoor heat exchanger 120 may be condensed by exchanging heat with outside air. One side of the outdoor heat exchanger 120 includes an outdoor fan 122 that blows outside air.

On the outlet side of the outdoor heat exchanger 120, a main expansion device 125 for depressurizing the refrigerant is provided. In one example, the main expansion device 125 includes an electronic expansion valve (EVE). During the cooling operation, the main expansion device 125 is full open and does not perform a decompression action of the refrigerant.

On the outlet side of the main expansion device 125, a supercooled heat exchanger 130 for additional cooling of the refrigerant is provided. In addition, a supercooling flow path 132 is connected to the supercooling heat exchanger 130. The supercooling flow path 132 is branched from the refrigerant pipe 170 and connected to the supercooling heat exchanger 130.

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

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

The supercooling flow path 132 is connected to the gas-liquid separator 160. The refrigerant in the supercooling flow path 132 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, is depressurized in the indoor expansion device 145 and 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 flows to the auxiliary heat exchanger 150 via the four sides 117. The auxiliary heat exchanger 150 is a heat exchanger capable of exchanging heat between 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 that has passed through the auxiliary heat exchanger 150 may be introduced into the gas-liquid separator 160.

The refrigerant that has passed through the auxiliary heat exchanger 150 is gas-liquid separated from the gas-liquid separator 160, and the separated gas-phase refrigerant may be sucked into the compressor 110.

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

Meanwhile, the gas heat pump system 10 further includes a cooling water tank 305 in which cooling water for cooling the engine 200 is stored, and a cooling water pipe 360 (dotted flow path) for guiding the flow of the cooling water. The cooling water pipe 360 includes a cooling water pump 300 that generates a flow force of the cooling water, a plurality of flow switching parts 310 and 320 for switching the flow direction of the cooling water, and radiators 330 and radiators for cooling the cooling water. Can be installed.

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

The radiator 330 may be installed on one side of the outdoor heat exchanger 120, and the cooling water of the radiator 330 is heat-exchanged with the outside air by driving the outdoor fan 122, and may be cooled in this process. 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 to be described later, and the first flow switching unit 310 and the second It may be selectively flowed to the radiator 330 or the auxiliary heat exchanger 150 through the flow switching unit 320.

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

In addition, the gas heat pump system 10 includes an air filter 210 supplying purified air to the mixer 220 and a zero governor 230 for supplying fuel below a predetermined pressure. ) Is included. The zero governor can be understood as a device that regulates and supplies the outlet pressure constant regardless of the change in the inlet pressure of the fuel or the flow rate.

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, provided on the outlet side of the engine 200, the exhaust gas heat exchanger 240 and the exhaust gas heat exchanger 240 to which the exhaust gas generated after the mixer is burned is introduced ) Is provided on the outlet side of the muffler (250) for reducing the noise of the exhaust gas is further included. 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 on one side of the engine 200.

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

However, when supplying air to the engine 200 by natural intake, while supplying LNG or LPG for housing as fuel, there is a problem that the output of the engine 200 decreases due to 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 lower the temperature in 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 cannot keep up with the high cooling load, which may cause cooling failure.

In addition, to solve this, like the engine of a vehicle, after pressurizing the air with a supercharger and supplying while adjusting the fuel amount according to the air amount, the supply pressure (about 2.5kPa) in the gas fuel pipe is the supercharge pressure (about 30kPa). There is also a problem that fuel supply becomes difficult because it is lower.

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

In detail, after the air and 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 may compress the mixer received from the mixer 220 to above atmospheric pressure.

The supercharger 400 may be driven by the power of the engine 200 or an electric motor.

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

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

According to the present invention, fuel and air are mixed in the mixer 220, and after being pressurized at a high pressure in the supercharger 400, it may be 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.

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

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

In the case of the present invention, to solve this, between the supercharger 400 and the control means 600, by cooling the high-temperature high-pressure mixer discharged from the supercharger 400, to reduce the volume, improve the density After, the intercooler 500 to discharge is provided.

For example, the intercooler 500 may exchange heat with a mixture of external air or cooling water.

According to this, it is possible to lower the temperature of the mixer supplied to the engine 200 and increase the density, thereby improving the volume efficiency of the engine 200.

In addition, the engine module further includes a cooling water pump 520 for generating a flow of cooling water for cooling the intercooler 500 and a cooling water pipe 510 connected to the cooling water pump 520 and guiding the flow of cooling water. can do.

In addition, a radiator 530 is coupled to at least a portion of the cooling water pipe 510, and a fan 540 may be installed on one side of the radiator 530.

On the other hand, when the supercharger 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 lengthened. 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 piping.

In the case of the present invention, when the 'stop operation command' is input from the manager to prevent this, the engine 200 is driven until the engine 200 stops in the closed state of the regulating means 600, thereby burning the mixer. Alternatively, formic acid generation may be suppressed by external discharge, and pipe damage may be prevented.

In addition, the intercooler 500 may be made of a corrosion-resistant material (eg, STS316).

On the other hand, the cooling water pipe 360 includes a first pipe 361 extending from the cooling water tank 305 toward the engine 200. In detail, the first pipe 361 extends from the cooling water tank 305 to the exhaust gas heat exchanger 240 and the exhaust pipe heat exchanger 240 to the engine 200. The second piping portion is included. Therefore, the cooling water supplied from the cooling water tank 305 is exchanged with the exhaust gas while passing through the exhaust gas heat exchanger 240, and is introduced into the engine 200 to recover the waste heat of the engine 200. In addition, the first pipe 361 may be provided with the cooling water pump 300 that generates a flow of cooling water.

The cooling water pipe 360 further includes a second 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 further includes a third pipe 363 that guides the cooling water from the first flow conversion unit 310 to the second flow conversion unit 320.

In addition, the cooling water pipe 360 further includes a fourth pipe 364 that guides the cooling water from the second flow conversion unit 320 to the auxiliary heat exchanger 150.

The cooling water pipe 360 further includes a fifth pipe 365 that guides cooling water from the second flow conversion unit 320 to the radiator 150.

The cooling water pipe 360 further includes a sixth pipe 366 that guides the cooling water from the first flow conversion unit 310 to the first pipe 361.

For example, when the temperature of the coolant passing through the engine 200 is formed below the set temperature, the effect of exchanging heat by flowing the coolant to the auxiliary heat exchanger 150 or the radiator 330 becomes insignificant. Cooling water flowing into the flow switching unit 310 may be bypassed to the first pipe 361 through the sixth pipe 366. The sixth pipe 366 may be referred to as “bypass pipe”.

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

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

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

First, when the gas heat pump system 10 performs a heating operation, the refrigerant is the compressor 110, an oil separator 115, four sides 117, an indoor heat exchanger 140, and a supercooled heat exchanger 130 ), The pressure is reduced 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 cooling water flowing through the fourth pipe 364. The refrigerant flowing into the auxiliary heat exchanger 150 forms a low temperature and low pressure as an evaporative refrigerant, and cooling water supplied to the auxiliary heat exchanger 150 forms a high temperature by the heat of the engine 200. Therefore, the refrigerant of the auxiliary heat exchanger 150 may absorb heat from the cooling water to improve evaporation performance.

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 be repeatedly flowed.

On the other hand, when the cooling water pump 300 is driven, the cooling water discharged from the cooling water pump 300 flows into the exhaust gas heat exchanger 240 along the first pipe 361 to exchange heat with the exhaust gas. And, the cooling water discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200, and passes through the second pipe 362 to the first flow switching unit 310. Flows into

Under the control of the first flow diverter 310, the coolant that has passed through the first flow diverter 310 is directed to the second flow diverter 320 along the third 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 fourth pipe 364 and exchange heat with the refrigerant. Then, the cooling water that has passed through the auxiliary heat exchanger 150 flows into the cooling water pump 300. The coolant can flow through this cycle repeatedly.

Meanwhile, during the heating operation, the flow of cooling water to the radiator 330 may be limited. In general, the heating operation is performed when the temperature of the outside air is low, so even if the cooling water is not cooled in the radiator 330, the possibility of cooling in the process of flowing the cooling water pipe 360 increases. Therefore, during the heating operation, the first and second flow switching units 310 and 320 may be controlled so that the cooling water does not pass through the radiator 330.

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

The driving of the engine 200 will be described.

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

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

Meanwhile, when the gas heat pump system 10 performs a cooling operation, the refrigerant is the compressor 110, an oil separator 115, four sides 117, an outdoor heat exchanger 120, and a supercooling heat exchanger 130 ), And is decompressed in the indoor expansion device 145 to exchange heat 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 flow into the auxiliary heat exchanger 150 and exchange heat with cooling water flowing through the cooling water pipe 360. Then, 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 be repeatedly flowed.

Meanwhile, when the cooling water pump 300 is driven, the cooling water discharged from the cooling water pump 300 flows into the exhaust gas heat exchanger 240 and exchanges heat with the exhaust gas. Then, 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. The flow of cooling water until it flows into the first flow conversion part 310 is the same as the flow of cooling water during the heating operation.

Cooling water that has passed 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 exchange heat with outside air. Can be. Then, the cooling water cooled in the radiator 330 flows into the cooling water pump 300. The coolant can flow through this cycle repeatedly.

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

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.

Regarding the driving of the engine 200, the same operation as during the heating operation is omitted here.

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

4 is a system diagram showing an example of an engine module applied to the gas heat pump system of the present invention. FIG. 5 is an enlarged view of a portion of FIG. 4. 6 is a system diagram showing another example of an engine module applied to the gas heat pump system of the present invention. 7 is an enlarged view of a portion of FIG. 6.

4 to 7, the engine module of the present invention is provided with a supercharger 400 for supercharging the mixer supplied to the engine.

The supercharger 400 generates rotational force by the power of the engine 200 or by an electric motor, and pressurizes (compresses) the introduced gas to discharge it. In detail, the supercharger 400 serves to discharge the mixture mixed in the mixer to the intercooler 500 after being pressurized (supercharged) using the power of the engine 200 or the rotational force of an electric motor.

In the following description, the case where the impeller of the supercharger 400 rotates by receiving rotational force from a motor is described as an example, but the scope of the present invention is not limited thereto, and the supercharger rotates by receiving rotational power of the engine You may.

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

As another example, a turbo charger may be disposed between the mixer 220 and the engine 200 in place of the supercharger 400 as a supercharging means. The turbocharger uses the exhaust gas discharged from the engine 200 to rotate the turbine and pressurizes (compresses) the gas introduced by the rotational force to discharge it.

Therefore, when the supercharging means is provided as a turbocharger, the turbocharger is connected to the exhaust manifold of the engine through the exhaust pipe, rotates, and when the mixed mixer in the mixer flows in, presses (compresses) , Discharges to the intercooler 500 side.

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

On the other hand, when the turbocharger is a turbocharger as described above, heat dissipation of the turbocharger is required. For example, the turbocharger may heat dissipate while exchanging heat with cooling water.

As another example, a supercharger 400 and a turbocharger may be disposed between the mixer 220 and the engine 200 as supercharging means.

On the other hand, in order to improve the performance of the engine as described above, in the case where the mixer 220 and the engine 200 are provided with a supercharger 400 and supercharged the mixer supplied to the engine, the supercharger 400 characteristics There is a risk of leakage of the gas mixture.

In addition, as the mixed gas of the leaked gas is ignited due to a spark or the like, a safety problem occurs, and there is a problem in that engine performance and efficiency are deteriorated as gas fuel leaks.

In the case of the present invention, a separate buffer tank 710 is configured to recover the gas mixture of the micro-leakage leaked from the supercharger 400, thereby preventing the mixer from leaking to the outside. In addition, the mixer collected in the buffer tank 710 may be re-supplied to the supercharger 400 built in the buffer tank 710. Therefore, it is possible to solve the mixer leakage problem in the supercharger.

Hereinafter, the buffer tank 710 will be described in more detail.

As described above, the buffer tank 710 covers the supercharger 400. Here, 'cover' means that the supercharger 400 is accommodated in the inner space of the buffer tank 710. The buffer tank 710 forms a space 711 inside. In addition, the supercharger 400 is accommodated in the space 711.

Here, the size of the space portion 711 of the buffer tank 710 may be formed larger than the supercharger 400.

Therefore, the supercharger 400 can be accommodated in the interior of the buffer tank 710. In detail, in the state in which the supercharger 400 is accommodated inside the buffer tank 710, a flow space of the mixer may be secured in the supercharger 400.

Various shapes of the buffer tank 710 may occur, and may be particularly cylindrical.

The buffer tank 710 is connected to the mixer 220 through a connection pipe 340.

Accordingly, the mixer discharged after being mixed in the mixer 220 may be introduced into the buffer tank 710 through the connecting pipe 340.

In addition, for this purpose, the buffer tank 710 may form an inlet 712 connected to the connection pipe 340.

As described above, through the inlet 712 connected to the connection pipe 340, the mixer introduced into the buffer tank 710 is forcibly sucked into the supercharger 400.

That is, after the mixer is discharged from the mixer 220, it passes through the connecting pipe 340 and flows into the space 711 of the buffer tank 710, and then is forcedly sucked into the supercharger 400.

Then, the mixer inhaled by the supercharger 400 is compressed at high temperature and high pressure, and the compressed mixer is discharged to the engine 200 side.

In this process, a leak of the mixer occurs in the supercharger 400.

In detail, when the mixer is compressed, since the internal pressure of the supercharger 400 is greater than the internal pressure of the buffer tank 710, a leak may occur in the supercharger 400 toward the buffer tank 710 due to the pressure difference.

In the case of the present invention, the mixer leaked from the supercharger is not exposed to the outside, but is collected in the buffer tank 710. Then, the leakage mixer collected in the buffer tank 710 flows through the spacer 711 of the buffer tank 710 together with the new mixer introduced into the buffer tank 710 through the connecting pipe 340, It may be re-suctioned into the supercharger 400.

For example, the mixer that is sucked into the supercharger 400 is about 98% of the new mixer introduced into the buffer tank 710 through the connector 340 and about 2% of the mixer leaked from the supercharger 400. It can have a ratio.

Hereinafter, a description will be given of a process in which the mixer leaked from the supercharger re-suctions into the supercharger when the engine module configured as described above is operated.

First, the engine 200 is operated, and a mixer of gas fuel and air mixed in the mixer 220 is supplied to the buffer tank 710 through a connector 340.

Then, the mixer introduced into the buffer tank 710 is forcibly sucked into the supercharger 400.

The supercharger 400 rotates the impeller while rotating by the rotational power of the motor or engine. Then, as the impeller rotates, the mixer of the buffer tank 710 is sucked into the supercharger 400, and the sucked mixer is compressed.

Then, after the compressed mixer exits the supercharger 400, it is supplied to the engine 200 through a transfer pipe 350 connecting the supercharger 400 and the adjusting means 600.

At this time, the supercharger 400 may leak the mixer due to a pressure difference or the like.

In the case of the present invention, the supercharger 400 is accommodated inside the buffer tank 710. Therefore, the mixer leaked from the supercharger 400 is recovered in the space portion 711 of the buffer tank 710, The mixer of the space portion 711 may be fed back to the supercharger 400 again.

Hereinafter, the structure of the supercharger will be described.

In this embodiment, the supercharger 400, the compression chamber to form the inlet 402a to communicate with the inner space 711 of the buffer tank 710, to form a compression space 401 inside ( 402, an impeller 403 provided inside the compression chamber 402, and a rotation shaft provided outside the compression chamber 402 and penetrating the impeller 403 and the compression chamber 402 ( 404), it may include a rotating means or a motor 405 rotating by the power of the engine 200.

At this time, the buffer tank 710 may accommodate the compression chamber 402, the impeller 403, and the motor 405 in the space 711.

According to this, after the mixer is introduced into the buffer tank 710 through the connecting pipe 340, the mixer of the buffer tank 710 is sucked into the compression chamber 402 through the inlet 402a. Then, the mixer introduced is compressed while the impeller 403 rotates. Then, the compressed mixer is discharged to the outside of the compression chamber 402 through the transfer pipe 350, and is supplied to the intake manifold 201 side of the engine 200.

At this time, in the process of the mixer being compressed, leakage of the mixer may occur outside the compression chamber 402. For example, a leak of the mixer may occur through the rotating shaft 404 passing through the compression chamber 402 and the connection portion 407 of the compression chamber 402.

In the case of the present invention, the compression chamber 402, the impeller 403 and the motor 405 are accommodated inside the buffer tank 710, that is, the connection portion 407 where the mixer leaks occurs of the buffer tank 710. Since it is accommodated inside, the mixer leaked from the compression chamber 402 is recovered in the space portion 711 of the buffer tank 710, and the mixer of the space portion 711 is again compressed through the inlet portion 402a ( After re-suctioning with 402), supercharging may be performed.

In this embodiment, the compression chamber 402 may form an inlet 402a of an open shape in the axial direction of the impeller 403 to facilitate suction of the mixer. In addition, the inlet portion 402a may be formed in a direction facing the connection pipe 340 to facilitate suction of the mixer.

In addition, the compression chamber 402 may form a discharge portion 402b for discharging the compressed mixer. The discharge part 402b may be formed in the rotational direction of the impeller 403 to facilitate discharge of the compressed mixer. In addition, the discharge portion 402b may be formed in the normal direction of the outer peripheral surface of the impeller 403. In addition, the discharge portion 402b may be formed to face upward to facilitate discharge of the compressed mixer. In addition, the discharge part 402b may be formed in a direction perpendicular to the rotation axis 404.

The discharge part 402b may be connected to a transfer pipe 350 connecting the supercharger 400 and the adjusting means 600.

That is, one side of the transfer pipe 350 may be connected to the discharge portion 402b, and the other side of the transfer pipe 350 may be connected to the adjustment means 600.

Therefore, the mixer discharged to the discharge unit 402b may be supplied to the adjusting means 600 through the transfer pipe 350.

In addition, when the intercooler 500 is provided between the supercharger 400 and the adjusting means 600, the transfer pipe 350 is a first transfer pipe connecting the discharge portion 402b and the intercooler 500 351 and a second transfer pipe 352 connecting the intercooler 500 and the adjusting means 600.

In addition, one side of the first transfer pipe 351 connected to the discharge part 402b is accommodated inside the buffer tank 710 and the other side is exposed outside the buffer tank 710. That is, the first transfer pipe 351 may have a shape that penetrates the buffer tank 710.

In this embodiment, when the supercharger 400 is operated, the internal pressure of the compression chamber 402 is greater than the internal pressure of the buffer tank 710 and the connection pipe 340.

In addition, the internal pressure of the buffer tank 710 may be formed smaller than the internal pressure of the connection pipe 340 by the suction force of the supercharger 400. For example, the internal pressure P1 of the connection pipe 340 may form atmospheric pressure, and the internal pressure P2 of the buffer tank 710 may be formed smaller than atmospheric pressure by the suction force of the supercharger 400.

Therefore, the mixer of the connection pipe 340 may flow to the buffer tank 710 by a pressure difference (P1> P2).

Hereinafter, a case where a plurality of the superchargers are provided will be described.

6 to 7, the supercharger 400 may be provided in plural, including a first supercharger 410 and a second supercharger 420 spaced apart from each other.

When one supercharger 400 is disposed between the engine 200 and the mixer 220, the supercharging range is limited by the maximum rotational speed or compression capacity of the supercharger 400, and as a result, the engine ( The range of output improvement of 200) is also limited.

In the case of the present invention, a plurality of superchargers 400 are disposed between the engine 200 and the mixer 220 so as to widen the driving range of the supercharger 400 and, accordingly, to further broaden the range of engine power improvement. .

In the following description, a case in which the first supercharger 410 and the second supercharger 420 are included is described, but the scope of the present invention is not limited thereto, and the mixer 220 and the adjusting means 600 It is noted that three or more superchargers may be provided in between.

The first supercharger 410 and the second supercharger 420 may have different compression capacities or may be set to have different impeller maximum rotational speeds.

In addition, the first supercharger 410 and the second supercharger 420 may be connected in series with each other.

Accordingly, the mixer supplied from the mixer 220 passes through the first supercharger 410, the first supercharging is performed, and the second supercharger 420 makes the secondary supercharging, followed by the engine 200. Can be supplied to the side. As described above, when the mixer passes through the first supercharger 410 and the second supercharger 420, and the second stage supercharging is performed, the mixer may be supercharged at a higher pressure.

At this time, based on the flow direction of the mixer, the first supercharger 410 is disposed at the rear end of the second supercharger 420, and the internal pressure of the compression chamber of the second supercharger 420 is the first supercharger ( 410) may be formed larger than the internal pressure of the compression chamber.

In addition, the second supercharger 420 may have a larger compression capacity than the first supercharger 410. In addition, the maximum number of revolutions of the impeller compared to the first supercharger 410 may be large in the second supercharger 420.

In addition, in the present embodiment, the connection pipe 340 is a first connection pipe 341 connecting the mixer 220 and the buffer tank 710, and the discharge side of the first supercharger 410 and the A second connection pipe 342 connecting the suction side of the second supercharger 420 may be included.

In addition, at least a portion of the second connection pipe 342 may be exposed outside the buffer tank 710. That is, the second connection pipe 342 may include an exposed portion 342a exposed to the outside of the buffer tank 710.

When the exposed portion 342a is provided as described above, heat dissipation of the mixer flowing from the first supercharger 410 to the second supercharger 420 may be possible. In addition, as the volume inside the buffer tank 710 increases, a flow space of the mixer can be secured.

In the above case, when the internal pressure is compared, the internal pressure of the compression chamber of the second supercharger 420 is the largest, the internal pressure of the compression chamber of the first supercharger 410, the internal pressure of the second connector 342, The internal pressure of the 1 connection pipe 341 and the internal pressure of the buffer tank 710 may be small in size. That is, the internal pressure of the buffer tank 710 may be formed to be the smallest.

In addition, the first supercharger 410 and the second supercharger 420 are connected in parallel, the mixer mixed in the mixer 220 flows to the first supercharger 410, or the second supercharger 420 After flowing to, it may be supplied to the engine 200 side.

On the other hand, when a plurality of superchargers 400 are provided as described above, the buffer tank 710 may be separately provided in each supercharger 410 and 420.

That is, when the first supercharger 410 and the second supercharger 420 are provided between the engine and the mixer, the buffer tank 710 includes a first supercharger buffer tank and a second supercharger buffer tank. It can be provided.

On the other hand, even if a plurality of superchargers 400 are provided, only one buffer tank 710 may be provided.

That is, when the first supercharger 410 and the second supercharger 420 are provided between the engine and the mixer, the buffer tank 710 is provided as one, and therein the first supercharger 410 and the second The supercharger 420 can be accommodated.

In this case, the mixer leaked from the first supercharger 410 and the second supercharger 420 may be recovered into one buffer tank 710 and then re-suctioned into the first supercharger 410.

Hereinafter, a description will be given of a process in which a mixer leaked from a plurality of superchargers is returned to the supercharger when the engine module configured as described above is operated.

First, the engine 200 is operated, and a mixer of gas fuel and air mixed in the mixer 220 is supplied to the buffer tank 710 through the first connection pipe 341.

Then, the mixer introduced into the buffer tank 710 is forcibly sucked into the first supercharger 410.

The first supercharger 410 rotates by the rotational power of the motor or engine, and rotates the impeller. Then, as the impeller rotates, the mixer of the buffer tank 710 is sucked into the first supercharger 410, and the sucked mixer is first compressed.

Then, after the compressed mixer exits the first supercharger 410, it is delivered to the second supercharger 420 through the second connector 342.

The second supercharger 420 also rotates the impeller while rotating at a higher speed than the first supercharger 410 by the rotational power of the motor or engine. Then, as the impeller rotates, the primary compressed mixer flowing through the second connecting pipe 342 is sucked into the second supercharger 420, and the suctioned mixer is secondary compressed.

Then, the second compressed mixer in the second supercharger 420 is supplied to the engine 200 through the transfer pipe 350 connecting the second supercharger 420 and the adjusting means 600.

In detail, the mixer compressed secondarily in the second supercharger 420 is supplied to the intercooler 500 through the first transfer pipe 351 connecting the second supercharger 420 and the intercooler 500. Then, the low-temperature and high-pressure mixer passed through the intercooler 500 is supplied to the control means 600 through the second transfer pipe 352.

At this time, the first supercharger 410 and the second supercharger 420 may leak the mixer.

In the case of the present invention, the first supercharger 410 and the second supercharger 420 are accommodated inside the buffer tank 710. Therefore, the mixer leaked from the first supercharger 410 and the second supercharger 420 is recovered in the space portion 711 of the buffer tank 710, and the mixer of the space portion 711 is again the first supercharger. After re-suctioning at 410, the second supercharging may proceed while passing through the first supercharger 410 and the second supercharger 420.

On the other hand, the engine module of the present invention, before starting the engine, in a state in which the fuel supply is stopped, can be cranking (cranking) for a certain period of time.

In detail, when a 'start operation command' is input from the manager, before starting the engine, the fuel supply to the engine is stopped, the cranking is performed for a predetermined time, and then the engine is started. .

According to this, the mixer existing inside the engine can be discharged before starting the engine, the abnormal combustion that may occur due to the residual mixer in the engine can be prevented, and the engine can be started more stably.

The above description is merely illustrative of the technical idea of the present invention, and those skilled in the art to which the present invention pertains may make various modifications and variations without departing from the essential characteristics of the present invention.

Therefore, the embodiments disclosed in the present invention are not intended to limit the technical spirit of the present invention, but to explain, and the scope of the technical spirit of the present invention is not limited by these embodiments.

The scope of protection of the present invention should be interpreted by the claims below, and all technical spirits within the scope equivalent thereto should be interpreted as being included in the scope of the present invention.

10: gas heat pump system 110: compressor
120: outdoor heat exchanger 140: indoor heat exchanger
150: auxiliary heat exchanger 200: engine
240: exhaust gas heat exchanger 300: cooling water pump
400: Supercharger 500: Intercooler
600: Adjusting means 710: Buffer tank

Claims (19)

An air conditioning module including a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and a refrigerant pipe;
Comprising an engine module comprising an engine that provides power for the operation of the compressor by burning a mixture of fuel and air,
The engine module,
A mixer for mixing the air and fuel and discharging them to the engine;
A supercharger disposed between the mixer and the engine and compressing the mixer discharged from the mixer by the rotational power of the engine or motor, and then discharging it to the intake manifold side of the engine;
An adjustment means disposed between the supercharger and the engine to adjust the amount of the compressed mixer supplied to the intake manifold side of the engine;
A buffer tank covering the supercharger;
It includes a connector for connecting the mixer and the buffer tank,
The gas heat pump system characterized in that the mixer discharged from the connection pipe is introduced into the buffer tank and then sucked into the supercharger.
According to claim 1,
The supercharger is a gas heat pump system in which a mixer and an inlet to be sucked are formed, and the inlet is in communication with an internal space of the buffer tank.
According to claim 1,
The supercharger is a gas heat pump system in which a discharge portion through which a compressed mixer is discharged is formed, and the discharge portion is connected to the engine side through a transfer pipe.
According to claim 3,
The transfer pipe is a gas heat pump system at least partially disposed inside the buffer tank and penetrating the buffer tank.
According to claim 1,
The supercharger includes a connection portion through which the mixer is leaked while the first member and the second member are combined,
The buffer tank is a gas heat pump system for accommodating the connection.
According to claim 1,
The supercharger,
A compression chamber communicating with the internal space of the buffer tank;
An impeller provided inside the compression chamber;
It is provided on the outside of the compression chamber, and is connected to the impeller through a rotating shaft passing through the compression chamber, and includes a rotating means or a motor rotating by the power of the engine,
The buffer tank is a gas heat pump system for accommodating the compression chamber and the impeller and the rotating means or the motor in the interior space.
The method of claim 6,
When the supercharger works,
The internal pressure of the compression chamber is greater than the internal pressure of the buffer tank,
The gas heat pump system in which the internal pressure of the buffer tank is formed smaller than the internal pressure of the connecting pipe.
According to claim 1,
The supercharger,
A gas heat pump system provided in plurality, including a first supercharger and a second supercharger spaced apart from each other.
The method of claim 8,
The first supercharger and the second supercharger are gas heat pump systems having different compression capacities or maximum rotational speeds of the impeller.
The method of claim 8,
The first supercharger and the second supercharger are gas heat pump systems connected in series with each other.
The method of claim 10,
Based on the flow direction of the mixer, the first supercharger is disposed at a rear end of the second supercharger, and the internal pressure of the second supercharger is greater than the internal pressure of the first supercharger.
The method of claim 8,
A gas heat pump system in which the first supercharger and the second supercharger are accommodated in the buffer tank.
The method of claim 8,
The connector,
A first connector connecting the mixer and the buffer tank,
A gas heat pump system including a second connection pipe connecting the discharge side of the first supercharger and the suction side of the second supercharger.
The method of claim 13,
At least a portion of the second connection pipe is a gas heat pump system exposed to the outside of the buffer tank.
According to claim 1,
A gas heat pump system is provided between the supercharger and the adjusting means, and an intercooler for cooling the compression mixer discharged from the supercharger.
The method of claim 15,
A gas heat pump system further comprising a cooling water pump for generating a flow of cooling water for cooling the intercooler and a cooling water pipe connected to the cooling water pump and guiding the flow of cooling water.
The method of claim 16,
A gas heat pump system in which a radiator is coupled to at least a portion of the cooling water pipe, and a fan is installed at one side of the radiator.
According to claim 1,
The engine module, immediately before the engine stops operating, in the state in which the control means is closed, the gas heat pump system for performing the additional operation of the engine.
According to claim 1,
The engine module, the gas heat pump system to proceed with the cranking (cranking) in the state of stopping the fuel supply before starting the engine.

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