KR102048737B1 - Gas heat-pump system - Google Patents

Abstract

The present invention relates to a gas heat pump system.
The gas heat pump system of the present invention 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 configured to combust a mixer mixed with fuel and air to provide power for driving the compressor; And an oil circulation module for supplying oil to the engine, wherein the engine module comprises: a mixer which mixes the air and fuel and discharges the air to the engine; A charging means disposed between the mixer and the engine and compressing the mixer discharged from the mixer and then discharged to the engine side, wherein the oil circulation module includes an oil pan in which the oil is stored, and the oil pan. A first oil flow path for supplying the oil to the engine, a second oil flow path for supplying the oil of the oil pan to the boosting means and recovering oil from the boosting means, and recovering the oil past the boosting means And an oil tank for supplying the recovered oil to the oil pan.

Description

Gas heat pump system {Gas heat-pump system}

The present invention relates to a gas heat pump system.

The heat pump system is a system having a refrigeration cycle capable of performing cooling or heating operation, and may be linked 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 the refrigerant of the refrigerating cycle and a predetermined heat storage medium, or air conditioning for heating and cooling may be performed.

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

The heat pump system may include a gas heat pump system. Large capacity compressors are required for air conditioning in industrial or large buildings, not at home. That is, a gas heat pump system may 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 gas of high temperature and high pressure.

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

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

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

The zero governor may be understood as a device for constantly adjusting and supplying the outlet pressure regardless of the change in the magnitude or flow rate of the inlet pressure 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 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, exhaust gas may be discharged from the engine.

Korean Patent Publication 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 circulates the compressor refrigerant by using a gas engine using a house LNG or LPG as a heat source, and operates in a cooling mode in the summer and a heating mode in the winter.

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

In addition, in summer, the gas heat pump system operates in a cooling mode to lower the indoor temperature. When the outdoor temperature is a high temperature, 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 order to solve this problem, if the air is pressurized with a supercharger, such as an engine of an automobile, and the fuel is supplied while adjusting the fuel amount according to the amount of air, the supply pressure (about 2.5 kPa) in the gas fuel pipe is the boost pressure (about 30 kPa) There is also the problem of lower fuel supply.

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 charging a mixer supplied to an engine in a supercharger.

Moreover, the subject of this invention is providing the gas heat pump system which can supply oil to a supercharger with a simple structure, and can collect the supplied oil.

Another object of the present invention is to provide a gas heat pump system in which damage to a component to be supplied is prevented by cooling the oil flowing through the supercharger to prevent oxidation of the oil.

Another object of the present invention is to provide a gas heat pump system that determines whether oil is normally supplied by a supercharger and stops the engine when the oil is not normally supplied to prevent engine damage.

In order to solve the above problems, 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, and a mixer in which fuel and air are mixed to burn the air. An engine module including an engine for providing power for driving, wherein the engine module comprises: a mixer configured to mix the air and fuel and discharge the fuel to the engine side; And a charging unit disposed between the mixer and the engine to compress the mixer discharged from the mixer and discharge the mixture to the engine side, thereby improving performance of the engine.

The gas heat pump system may include an oil circulation module for supplying oil to the engine, and the oil circulation module may supply a portion of the oil to the charging means to lubricate the charging means.

In this embodiment, the oil circulation module, the oil pan in which the oil is stored, the first oil flow path for supplying the oil of the oil pan to the engine, and the oil of the oil pan to the charging means and the And a second oil flow path for recovering oil from the charging means, and an oil tank for recovering the oil passing through the charging means and supplying the recovered oil to the oil pan, thereby circulating the oil by a simple structure. It does not have to change the structure of the engine to supply oil to the charging means.

In this embodiment, the oil of the oil tank may be supplied to the oil pan by the first connecting pipe and the second connecting pipe.

The second connecting pipe is located below the first connecting pipe, and the oil in the oil tank is transferred to the oil pan through the respective connecting pipes by the difference in the oil level of the oil tank and the oil level of the oil pan. Can be supplied.

The highest height of the oil tank may be located higher than the highest height of the oil pan, and the oil pan may be located below the engine.

An oil pump may be located in the oil pan for pumping oil. The first connecting pipe may be connected to the oil pan at a higher position than the oil pump.

The oil level of the oil pan can be managed between the highest level and the lowest level. The oil pump may be installed at the same height as the lowest level.

The gas heat pump system of the present embodiment may further include a pressure equalizing tube for pressure equalization of the oil pan and the oil tank. The pressure equalizing pipe may be connected to the first oil passage and the oil recovery passage.

In the present invention, the second oil flow path may include an oil recovery flow path for recovering oil discharged from the charging means to the oil tank.

A valve may be provided in the oil return passage, and an oil bypass pipe may be connected to the valve and the second connection pipe.

The valve may be switched to the flow path in accordance with the temperature of the oil discharged from the charging means. The valve may flow oil into the oil tank when the oil discharged from the charging means has a high temperature.

In one embodiment, the valve is switched to the first state so that the oil is recovered to the oil tank when the temperature of the oil passing the charging means is higher than the reference temperature, the temperature of the oil passing the charging means is the reference temperature If less, the flow path can be switched to the second state to allow oil to flow into the oil bypass piping.

In the present invention, the gas heat pump system may further include an oil cooler for cooling oil flowing along the second oil passage before being supplied to the charging means.

For example, the oil in the oil cooler may be heat exchanged with the refrigerant flowing through the refrigerant branch pipe branched from the refrigerant pipe.

As another example, the cooling module further comprises a cooling module in which coolant flows to cool the engine, wherein the cooling module includes a supply pipe for supplying cooling water to the engine, and the cooling water in the oil cooling pipe branched from the supply pipe. And oil in the second oil passage may be heat exchanged.

According to the proposed invention, there is an advantage that the volumetric 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 supercharging means.

In addition, according to the present invention, the oil branched from the first oil passage flows along the second oil passage and is supplied to the charging means, and the oil supplied to the charging means is recovered to the oil tank through the oil recovery passage, thereby circulating oil. The structure of the module is simplified, and oil circulation is possible without changing the structure of the engine.

Further, according to the present invention, when the temperature of the oil recovered from the charging means is high, the oil is recovered to the oil tank and then supplied to the oil pan, thereby preventing damage to the charging means or the engine.

Further, according to the present invention, since the oil is cooled and then supplied to the charging means, damage to the charging means and the engine can be prevented in advance.

Further, according to the present invention, when the oil does not flow normally in the process of cooling the oil and supplying it to the charging means, by stopping the engine, it is possible to prevent damage to the engine and the charging means.

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 view showing an engine module according to a first embodiment of the present invention.
3 is a view showing an oil circulation module according to a first embodiment of the present invention.
4 is a view showing the flow of cooling water in the engine module according to the first embodiment of the present invention.
5 is a view showing the flow of oil in the oil circulation module according to the first embodiment of the present invention.
6 is a view illustrating an oil circulation module according to a second embodiment of the present invention.
7 is a cycle diagram showing the configuration of a gas heat pump system according to a third embodiment of the present invention.
8 is a view showing an engine module according to a third embodiment of the present invention.
9 is a view showing an oil circulation module according to a third embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail with reference to the accompanying drawings. In adding reference numerals to the components of each drawing, it should be noted that the same reference numerals are assigned to the same components as much as possible even though they are shown in different drawings. In addition, in describing the embodiments of the present invention, when it is determined that a detailed description of a related well-known configuration or function interferes with the understanding of the embodiments of the present invention, the detailed description thereof will be omitted.

In addition, 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 only for distinguishing the components from other components, and the nature, order or order of the components are not limited by the terms. If a component is described as being "connected", "coupled" or "connected" to another component, that component may be directly connected or connected to that other component, but between components It will be understood that may be "connected", "coupled" or "connected".

1 is a cycle diagram showing a configuration of a gas heat pump system according to a first embodiment of the present invention, Figure 2 is a view showing an engine module according to a first embodiment of the present invention. 3 is a view showing a circulation passage of oil according to the first embodiment of the present invention.

1 to 3, the gas heat pump system 10 according to an exemplary embodiment may include a plurality of components constituting a refrigerant cycle as an air conditioning module.

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

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

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

The configurations of the system shown in FIG. 1 may be disposed on the outdoor side, ie, inside the outdoor unit, except for the indoor heat exchanger 140 and the indoor expansion device 145.

When the gas heat pump system 10 is operated in a cooling operation mode, the refrigerant passing through the four sides 117 may flow to the indoor heat exchanger 140 through the outdoor heat exchanger 120. On the other hand, when the gas heat pump system 10 is operated in the heating operation mode, the refrigerant passing through the four sides 117 flows through the indoor heat exchanger 140 to the outdoor heat exchanger 120 side. Can be.

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

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

The refrigerant flowing into the outdoor heat exchanger 120 may condense by exchanging heat with outside air. One side of the outdoor heat exchanger 120 may be an outdoor fan 122 for blowing outside air.

At the outlet side of the outdoor heat exchanger 120, a main expansion device 125 may be provided to reduce the refrigerant. For example, the main expansion device 125 may include an electronic expansion valve (EEV). During the cooling operation, the main expansion device 125 is full open and does not perform the depressurization of the refrigerant.

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

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

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

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

The refrigerant in the refrigerant pipe 170 passing through the supercooled heat exchanger 130 flows to the indoor unit side, and is decompressed in the indoor expansion device 145 and then evaporated in the indoor heat exchanger 140. The indoor expansion device 145 is installed inside the indoor unit and may be configured as an electronic expansion valve (EEV).

In addition, the refrigerant evaporated in 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 may be sucked into the compressor 110. Can be.

On the other hand, the refrigerant condensed in the indoor heat exchanger 140 during the heating process may flow to the auxiliary heat exchanger (150). A refrigerant branch pipe 151 may be connected to the auxiliary heat exchanger 150.

An expansion valve 152 may be provided in a pipe located at an inlet side of the auxiliary heat exchanger 150 among the refrigerant branch pipes 151. The expansion valve 152 may reduce the pressure of the refrigerant while controlling the flow of the refrigerant.

Therefore, the auxiliary heat exchanger 150 is a heat exchanger capable of 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 flow into the gas-liquid separator 160.

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

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

The coolant pipe 360 includes a coolant pump 300 for generating a flow force of the coolant, a plurality of flow diverters 310 and 320 for changing the flow direction of the coolant, and a radiator 330 for cooling the coolant. radiator) can be installed.

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

The radiator 330 may be located at one side of the outdoor heat exchanger 120, and the coolant of the radiator 330 may exchange heat with the outside air by driving the outdoor fan 122, and may be cooled in this process. have.

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

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

The engine module may include various components for supplying a 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 a 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 having a predetermined pressure or less. It may further include.

The zero governor 230 may be understood as a device for constantly adjusting and supplying the outlet pressure 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. In addition, the mixer may be supplied to the engine 200.

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

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

On the other hand, the engine 200 applied to the gas heat pump system 10 as described above uses domestic LNG, LPG, or the like as fuel.

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

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

Accordingly, low density air is supplied to the engine 200, so that the output of the engine 200 is reduced. As a result, the output of the engine 200 cannot follow a high cooling load, and may cause a cooling failure.

To solve this problem, if the air is pressurized with a supercharger, such as an engine of an automobile, and the fuel is supplied while adjusting the fuel amount according to the air amount, the supply pressure (about 2.5 kPa) in the gas fuel pipe is lower than the boost pressure (about 30 kPa). Another problem is that fuel supply becomes difficult.

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

The charging means 400 is mixed with air and fuel in the mixer 220, and then compressed by the discharged mixer to discharge to the engine 200 side. At this time, the charging means 400 may compress the air and fuel in the mixer 220 above atmospheric pressure.

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

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

Therefore, when the charging means 400 is provided as a turbocharger, the turbocharger is connected to the exhaust manifold of the engine 200 through the exhaust pipe 191 of the engine 411 on the turbine 411 side. When the mixer is mixed with the mixer 220, the mixer 220 is rotated and pressurized (compressed), and then discharged to the intercooler 500.

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

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

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

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

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

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

On the other hand, when the mixer passes through the charging means 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 volumetric efficiency of the engine is inevitably lowered.

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

The intercooler 500 cools the high temperature and high pressure mixer discharged from the charging means 400, reduces the volume, improves the density, and discharges the mixture.

For example, the intercooler 500 may heat exchange a portion of the coolant for flowing into the mixer 200 to be supplied to the engine 200 and the engine 200.

Therefore, according to the intercooler 500, there is an advantage that can lower the temperature of the mixer supplied to the engine 200, increase the density to improve the volumetric efficiency of the engine 200.

When the charging means 400 and the intercooler 500 and the like 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 long. At this time, when there is a lot of moisture in the air, the mixer and water react to generate formic acid, which may damage the pipe, thereby causing a risk of explosion.

In the case of the present invention, when the 'stop operation command' is input from the manager to prevent this, by driving the engine 200 until the engine 200 is stopped in the closed state (closed) the control means 600, Combustion or external discharge can suppress the generation of formic acid, and can prevent risks such as pipe breakage and explosion.

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

In the supply pipe 361, a coolant pump 300 for flowing coolant may be installed.

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

That is, the coolant 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 waste heat of the engine 200 while flowing the engine 200. Recover.

In order to dissipate the turbocharger, which is the charging means 400, the cooling water pipe 360 is bypass pipe 373 which is bypassed from the outlet side pipe of the exhaust gas heat exchanger 240 in the supply pipe 361. ) May be further included.

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

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

Therefore, a part of the cooling water passing through the exhaust gas heat exchanger 240 flows directly to the engine 200, and the other part flows to the engine 200 after heat exchange with the supercharging means 400.

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

In addition, the cooling water pipe 360 may further include a first guide pipe 363 that guides the cooling water from the first flow switching unit 310 to the second flow switching unit 320.

In addition, 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 guiding cooling water from the first flow switching unit 310 to the supply pipe 361.

For example, when the temperature of the coolant passing through the engine 200 is less than the set temperature, the coolant flows to the auxiliary heat exchanger 150 or the radiator 330 to be inefficient to exchange heat. The cooling water introduced into the flow switching unit 310 may be bypassed to the supply pipe 361 through the fourth guide pipe 366.

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

Meanwhile, referring to FIG. 3, an oil pan 820 for supplying oil to the engine 200 may be provided below the engine 200. The oil pan 800 may receive the oil stored in the oil tank 810. For example, the oil pan 820 may be connected to the lower side of the engine 200.

2 is a view for easily explaining the flow of the coolant, the oil pan 800 is shown in a state in which the engine 200 is separated, in fact, as shown in Figure 3 the oil pan 800 is the engine 200 It is located underneath).

An oil pump 820 may be provided in the oil pan 800. Oil may be pumped by the oil pump 820, and the pumped oil may be recovered from the engine 200 after being supplied to the engine 200 by the first oil flow path 830.

The second oil channel 840 may branch from the first oil channel 830. The second oil passage 840 supplies oil to the turbocharger for lubrication of the rotary shaft of the turbocharger and recovers oil supplied to the turbocharger.

The second oil passage 840 may include an outlet side passage 842 of the turbocharger (or may be referred to as an oil recovery passage, hereinafter referred to as an "oil recovery passage"). The oil recovery passage 842 may be connected to the oil tank 810. That is, the oil supplied to the turbocharger may be recovered to the oil tank 810.

The first oil passage 830 and the oil recovery passage 842 may be connected by a pressure equalizing tube 832.

The pressure in the oil pan 800 and the oil tank 810 is balanced by the pressure equalizing pipe 832 so that oil is excessively supplied to the oil pan 800 so that the oil of the oil pan 800 overflows. The phenomenon can be prevented.

For example, the oil recovery flow path 842 may be provided with a T-shaped connector 844, and the oil recovery flow path 842 may be connected to the connector 844.

The oil tank 810 and the oil pan 800 may be connected by a first connection pipe 851. The first connection pipe 851 allows the oil level of the oil tank 810 and the oil level of the oil pan 800 to remain the same while the engine 200 is not operated.

In addition, the first connection pipe 851 may be connected to the oil pan 800 at a position higher than the oil pump 820.

In the present embodiment, the highest height of the oil tank 810 may be disposed to be higher than the highest height of the oil pan 800.

The oil level of the oil pan 800 may be managed between the highest level and the lowest level. Although not limited, the first connection pipe 851 may connect the oil pan 800 and the oil tank 810 at the same height as the highest level.

Therefore, when the oil level of the oil pan 800 is higher than the first connection pipe 851 in the state where the engine 200 is stopped, the oil of the oil pan 800 is increased in the first connection pipe 851. And the second connection pipe 852 may flow into the oil tank 810.

On the contrary, when the oil level of the oil tank 810 is higher than the first connection pipe 851 in the state where the engine 200 is stopped, the oil of the oil tank 810 becomes the first connection pipe 851. And the second connection pipe 852 may flow to the oil pan 800.

In this embodiment, when the engine 200 is stopped, the highest level of each of the oil pan 800 and the oil tank 810 is maintained at the same height as or similar to that of the first connection pipe 851. In order to be maintained as, the oil tank 810 may be filled with oil.

In the present embodiment, the oil pan 800, the first oil passage 830, the second oil passage 840, the oil recovery passage 842, the oil tank 810, the first connecting pipe 851, and the second The connecting pipe 852 is collectively referred to as an oil circulation module.

Meanwhile, an oil pressure switch 831 may be provided in the first oil passage 830. The oil pressure switch 831 may be used to determine whether oil is supplied to the first oil passage 830 when the oil pump 820 operates.

Although not limited, the oil pump 820 may be installed at the same position as the lowest level of oil in the oil pan 800.

Therefore, when the oil level is lower than the lowest level in the oil pan 800, the oil is not pumped by the oil pump 820.

The oil pressure switch 831 may be designed to be on or off when the oil pump 820 is operated but oil is not pumped.

Although not shown, the controller may recognize the on or off state of the oil pressure switch 831 to stop the engine 200.

Hereinafter, the operation of the gas heat pump system 10 will be described.

4 is a view showing the flow of the coolant in the engine module according to the first embodiment of the present invention, Figure 5 is a view showing the flow of oil in the oil circulation module according to the first embodiment of the present invention.

1, 4, and 5, when the gas heat pump system 10 performs a heating operation, the refrigerant may include the compressor 110, the oil separator 115, the four sides 117, and an indoor heat exchange. Gas 140 and subcooling heat exchanger (130).

In addition, the refrigerant is decompressed 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 an "evaporator."

Meanwhile, when the coolant pump 300 is driven, the coolant discharged from the coolant pump 300 flows along the supply pipe 361 and flows into the exhaust gas heat exchanger 240 to exchange heat with the exhaust gas. .

The coolant discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200, and passes through the recovery pipe 362 to the first flow switching unit 310. Inflow.

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

On the other hand, the cooling water during the heating operation may be limited to the flow to the radiator 330. In general, the heating operation is performed when the temperature of the outside air is low, so that even if the coolant is not cooled in the radiator 330, it is more likely to be cooled in the process of flowing the coolant pipe 360.

Therefore, 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 during the heating operation.

However, when the heat exchange in the auxiliary heat exchanger 150 is not required, the coolant may be introduced into the radiator 330 from the second flow switching unit 320 via the third guide pipe 365. It may be.

Next, the driving of the engine 200 will be described.

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

The mixer that has passed through the intercooler 500 is adjusted in amount through the adjusting means 600 and supplied to the engine 200 to operate the engine 200. The exhaust gas discharged from the engine 200 flows into the exhaust gas heat exchanger 240 to exchange heat with the cooling water and is discharged to the outside through the muffler 250.

By operating the oil pump 820, the oil of the oil pan 800 flows along the first oil flow path 830 to perform lubrication of the engine 200. In addition, the oil branched from the first oil passage 830 and flowing along the second oil passage 840 performs lubrication of the charging means 400.

The oil lubricating the supercharging means 400 may be recovered to the oil tank 810 after passing through the oil recovery passage 842.

Since the oil pump 820 is operated while the engine 200 is operating, the oil level of the oil pan 800 is lower than the highest level. On the other hand, the oil level of the oil tank 810 is higher than before the engine operation.

Therefore, the oil recovered to the oil tank 810 during the operation of the engine 200 is due to the difference in the height of the oil level of the oil pan 800 and the oil tank 810, the first connection pipe The oil pan 800 may be supplied to the oil pan 800 through the 851 and the second connection pipe 852.

According to the present embodiment, the volumetric efficiency is 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 supercharging means.

In addition, according to the present embodiment, since the oil is supplied to the charging means 400, there is an advantage that smooth lubrication of the charging means 400 is possible.

According to this embodiment, the oil recovered in the oil tank 810 by the height difference between the oil level of the oil pan 800 and the oil tank 810 is connected to the oil pan 800 through the connection pipes 351 and 352. Since it can be supplied to, there is an advantage that a separate oil circulation pump does not need to exist on the connection pipes (351, 352).

In addition, according to the present embodiment, since the oil passing through the charging means 400 is recovered to the oil tank 810, there is an advantage that the structure is simplified because an additional oil tank is unnecessary.

In addition, according to the present embodiment, there is an advantage that it is possible to add and form a flow path for supplying oil to the charging means 400 and the charging means 400 without changing the structure of the engine 200.

For example, a configuration for recovering oil into the oil pan 800, for example, has an advantage of not having to process holes for introducing oil.

Next, when the gas heat pump system 10 performs the cooling operation, the refrigerant is the compressor 110, the oil separator 115, the four sides 117, the outdoor heat exchanger 120, and the supercooled heat exchanger ( 130).

Then, the refrigerant is decompressed in the indoor expansion device 145, the heat exchange in the indoor heat exchanger 140 and flows back to 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."

The refrigerant passing through the four sides 117 may be introduced into the gas-liquid separator 160 to be phase-separated and then suctioned into the compressor 110. The refrigerant may be flowed by repeating the above cycle.

Meanwhile, when the coolant pump 300 is driven, the coolant discharged from the coolant pump 300 flows along the supply pipe 361 and flows into the exhaust gas heat exchanger 240 to exchange heat with the exhaust gas. . The coolant discharged from the exhaust gas heat exchanger 240 flows into the engine 200 to cool the engine 200, and passes through the recovery pipe 362 to the first flow switching unit 310. Inflow.

The coolant flow until it flows into the first flow diverter 310 is the same as the coolant flow during the heating operation.

Cooling water that has passed through the first flow diverter 310 flows into the second flow diverter 320 and flows to the radiator 330 under the control of the second flow diverter 320 to exchange heat with outside air. Can be. In addition, the coolant cooled by the radiator 330 flows into the coolant pump 300. Cooling water can be flowed through this cycle repeatedly.

On the other hand, the cooling water during the cooling operation may be limited to the flow to the auxiliary heat exchanger (150). In general, since the cooling operation is performed when the temperature of the outside air is high, endotherm of the refrigerant may not be required to secure evaporation performance. Therefore, 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 during the cooling operation.

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

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

6 is a view illustrating a circulation passage of oil according to a second embodiment of the present invention.

This embodiment is the same as in the first embodiment in other parts, except that the valve is provided in the oil return flow path. Therefore, hereinafter, only characteristic parts of the embodiment will be described.

Referring to FIG. 6, the oil return passage 842 may be provided with a valve 420.

The valve 420 may be a wax type thermostat that adjusts a flow path according to a set temperature.

For example, the valve 420 switches the flow path to the first state when the oil temperature T2 is equal to or higher than the reference temperature T1, and when the oil temperature T2 is lower than the reference temperature T1. The flow path can be switched to the second state.

An oil bypass flow path 846 may be connected to the valve 420. The oil bypass flow path 846 may be connected to the second connection pipe 852.

At this time, when the temperature of the oil passing through the charging means 400 is equal to or higher than the reference temperature, the valve 420 is switched to the first state, so that the oil is in the oil tank 810 along the oil recovery flow path 842. ) Can be recovered.

On the other hand, when the temperature of the oil passing through the charging means 400 is less than the reference temperature, the valve 420 is switched to the second state, so that the oil is connected to the second along the oil bypass flow path 846. After flowing into the pipe 852, it is supplied to the oil pan 800.

In the present embodiment, when the speed of the rotary shaft of the supercharging means 400 is a high speed, the temperature of the oil lubricated to the rotary shaft is increased. When the oil having a higher temperature is supplied directly to the oil pan 800, the oil having a higher temperature may be supplied to the engine 200 to oxidize the oil in the engine 200 and thus the oil may not function as a lubricant. In addition, when the temperature at which the temperature rises is supplied to the supercharging means 400, a problem may occur in which oil is oxidized in the supercharging means 400.

In the present embodiment, when the temperature of the oil passing through the charging means 400 is lower than the reference temperature, the oil pan 800 may be directly supplied to the oil pan 800. In this case, the amount of oil flowing from the oil tank 810 to the oil pan 800 may be reduced.

That is, in the oil tank 810, oil may be supplied to the oil pan 800 while maintaining the oil stored state and flowing along the oil bypass flow path 846. In this state in which the oil is stored in the oil tank 810, the temperature of the oil may decrease.

On the other hand, when the temperature of the oil passing through the charging means 400 is higher than the reference temperature, the oil is recovered into the oil tank 810.

Therefore, even when the temperature of the oil is higher than the reference temperature, the oil pan whose temperature is raised is not directly supplied to the oil pan 800, but is mixed with the oil stored in the oil tank 810 and the temperature is lowered. 800 may be supplied. Therefore, hot oil may be prevented from being directly supplied to the engine 200.

7 is a cycle diagram showing the configuration of a gas heat pump system according to a third embodiment of the present invention, Figure 8 is a view showing an engine module according to a third embodiment of the present invention. 9 is a view illustrating a circulation passage of oil according to a third embodiment of the present invention.

This embodiment is the same as the first embodiment in other parts, except that an oil cooler for cooling the oil is further provided. Therefore, hereinafter, only characteristic parts of the embodiment will be described.

7 to 9, the gas heat pump system 10 according to the present embodiment may further include an oil cooler 700 for cooling the oil supplied to the charging means 400.

The oil cooler 700 may exchange heat between the oil flowing through the charging means 400 and the refrigerant flowing through the refrigerant pipe 170.

The refrigerant branch pipe 151a may branch from the refrigerant pipe 170, and the auxiliary heat exchanger 150 may be connected to the refrigerant branch pipe 151a. In addition, an expansion valve 152a may be provided at an inlet side 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-side pipe of the gas-liquid separator 160.

The oil cooling pipe 153 may branch from the outlet pipe of the auxiliary heat exchanger 150 among the refrigerant branch pipes 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 the refrigerant. The flow control valve 154 may be turned on or off based on the temperature sensed by the temperature sensors 421 and 422 described later.

When the flow control valve 154 is turned on, some of the refrigerant exchanged with the coolant in the auxiliary heat exchanger 150 flows directly to the gas-liquid separator 160 without flowing the oil cooler 700, and the other Some may flow into the gas-liquid separator 160 after heat exchange with oil while flowing the oil cooler 700.

Meanwhile, a first oil sensor 421 is provided at the inlet side flow path of the charging means 400 in the second oil flow path 840, and a second temperature sensor 422 is provided at the oil recovery flow path 842. do.

The flow control valve 154 may be turned on if the on condition is satisfied.

For example, the temperature of the oil detected by the second temperature sensor 422 is greater than or equal to a reference temperature, or the difference between the temperature detected by the second temperature sensor 422 and the temperature detected by the first temperature sensor 422 is different. When the temperature difference is greater than the reference temperature, the on condition may be determined to be satisfied.

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

When the on condition of the flow control valve 154 is satisfied, the flow control valve 154 may be turned on.

When the flow control valve 154 is turned on, after the refrigerant is heat-exchanged with the coolant by the auxiliary heat exchanger 150, the refrigerant flows to the oil cooler 700 to exchange heat with the oil flowing to the turbocharger.

Since the refrigerant flowing into the auxiliary heat exchanger 150 is a refrigerant having a low pressure reduced by the expansion valve 152a, the refrigerant passing through the auxiliary heat exchanger 150 cools the oil while flowing through the oil cooler 700. You can.

According to this embodiment, since the cooled oil is supplied to the charging means, the oil is prevented from being oxidized in the charging means, and thus, the performance or the life of the charging means and the engine can be prevented from being lowered.

The controller may determine whether the stop condition of the engine 200 is satisfied based on the temperatures sensed by the temperature sensors 421 and 422.

For example, the temperature of the oil sensed by the second temperature sensor 422 is equal to or higher than the stop reference temperature or between the temperature sensed by the second temperature sensor 422 and the temperature sensed by the first temperature sensor 422. When the difference is equal to or greater than the stop reference temperature difference, it may be determined that the stop condition is satisfied.

If the oil is not circulated smoothly or is not supplied even after the oil is cooled in the oil cooler and supplied to the charging means, there is a problem that the temperature at the outlet side of the charging means is significantly increased. In this case, when the engine 200 is continuously operated, the engine 200 and the supercharging means 400 may be damaged. In this embodiment, when the stop condition of the engine 200 is satisfied, the engine 200 is satisfied. ) Can be stopped.

In another embodiment, the oil supplied to the charging means 400 may be cooled by cooling water.

For example, the oil cooling pipe may be bypassed in the supply pipe 361 to flow the oil cooler and then be laminated to the supply pipe 361.

10: gas heat pump system 110: compressor
120: outdoor heat exchanger 140: indoor heat exchanger
200: engine 400: charging means
800: oil pan 810: oil tank
820: oil pump 830: the first oil flow path
840: second oil flow path 842: oil recovery flow path
851: first connection piping 852: second connection piping

Claims (12)

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 configured to combust a mixer mixed with fuel and air to provide power for driving the compressor; And
An oil circulation module for supplying oil to the engine,
The engine module,
A mixer which mixes the air and fuel and discharges the air to the engine side;
A charging means disposed between the mixer and the engine and compressing the mixer discharged from the mixer and then discharged to the engine side;
The oil circulation module may include an oil pan in which the oil is stored;
A first oil passage for supplying oil of the oil pan to the engine,
A second oil flow path including an oil recovery flow path for supplying oil of the oil pan to the charging means and recovering oil discharged from the charging means;
An oil tank for recovering the oil past the supercharging means and for supplying the recovered oil to the oil pan,
And a pressure equalizing tube connected to the oil recovery flow path and the first oil flow path to balance the pressure between the oil pan and the oil tank. The method of claim 1,
The oil circulation module includes: a first connection pipe for connecting the oil pan and the oil tank; And
And a second connection pipe connecting the oil pan and the oil tank at a position lower than the first connection pipe. The method of claim 2,
It is provided in the oil pan further comprises an oil pump for pumping oil,
And the first connecting pipe is connected to the oil pan at a higher position than the oil pump. The method of claim 2,
The oil pan is disposed below the engine,
And the oil tank is arranged such that the highest height of the oil tank is positioned higher than the highest height of the oil pan. delete The method of claim 2,
The oil return flow path is provided with a valve,
And a gas bypass pump connected to the valve and the second connection pipe. The method of claim 6,
The valve is switched to the flow path to the first state so that the oil is recovered to the oil tank when the temperature of the oil passing the charging means is higher than the reference temperature,
If the temperature of the oil passing through the charging means is less than the reference temperature, the gas heat pump system for converting the flow path to the second state so that the oil flows to the oil bypass pipe. The method of claim 1,
And an oil cooler for allowing oil flowing along the second oil passage to be cooled before being supplied to the charging means. The method of claim 8,
The oil heat pump system in the oil cooler is the heat exchange with the refrigerant flowing through the refrigerant branch pipe branching from the refrigerant pipe. The method of claim 9,
A cooling module through which coolant flows to cool the engine;
And an intermediate heat exchanger for exchanging the refrigerant branched into the refrigerant branch pipe with the cooling water.
An oil cooling pipe is branched from the refrigerant branch pipe to an outlet pipe of the intermediate heat exchanger.
The oil cooling pipe is a gas heat pump system having a flow control valve for regulating the flow of the refrigerant. The method of claim 10,
A first temperature sensor for sensing an oil temperature at the inlet side of the charging means;
Further comprising a second temperature sensor for sensing the oil temperature of the outlet side of the charging means,
The gas heat pump system determines whether the flow control valve is on or off based on the information detected by the first temperature sensor and the second temperature sensor. The method of claim 9,
Further comprising a cooling module flowing coolant for cooling the engine,
The cooling module includes a supply pipe for supplying coolant to the engine,
The gas heat pump system in which the cooling water of the oil cooling pipe branched from the supply pipe and the oil of the second oil flow path are heat exchanged.

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