JP5948158B2 - LPI vehicle heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger for an LPI vehicle, and more specifically, for an LPI vehicle that causes the refrigerant circulating in the air conditioner system and the LPG fuel returned from the engine to exchange heat with each other to cool the LPG fuel. It relates to a heat exchanger.

  In general, an LPI (Liquid Petroleum Injection: LPG injection device) engine is different from a mechanical LPG fuel injection method that relies on the pressure of a bomb, and a fuel pump is provided in the bomb. LPG fuel is liquefied at high pressure (5 to 15 bar) by a pump. The liquid fuel is injected into the cylinder using an injector, thereby driving the engine.

  Since such an LPI engine injects liquid fuel, no components such as a vaporizer or a mixer are required. Instead, a high-pressure injector, a fuel pump provided in the cylinder, a fuel supply line, an LPI dedicated electronic control unit (ECU), and a regulator unit for adjusting the fuel pressure are additionally required.

  Such an electronic control unit of an LPI engine receives input signals from various sensors, determines the state of the engine, and controls a fuel pump, an injector, and an ignition coil in order to improve the optimal air-fuel ratio and engine performance.

  Then, the fuel pump is controlled according to the amount of fuel required by the engine to supply liquid fuel to the engine, and the LPI injector sequentially injects fuel into the cylinder to achieve an optimum air-fuel ratio.

However, in a vehicle to which the conventional LPI system is applied, since the high-temperature return fuel is returned from the engine to the cylinder, the temperature of the LPG fuel in the cylinder rises, thereby causing a phenomenon that the internal pressure of the cylinder increases. It has occurred. In particular, when the internal pressure of the cylinder is higher than the filling pressure at the filling station, there is a problem that the LPG fuel is not filled into the cylinder.
(For example, see Patent Document 1)

  In order to lower the temperature of the fuel returned from the engine, another fuel cooling device must be installed on the return line, which increases the manufacturing and installation costs, and restricts the installation space in the narrow engine room. There was also a problem such as that occurred.

JP 2008-267190 A

  The present invention has been made in view of the above points, and an object of the present invention is to perform mutual heat exchange between the refrigerant circulating in the air conditioner system and the LPG fuel returned to the cylinder from the engine. An object of the present invention is to provide an LPI vehicle heat exchanger that lowers the temperature of the LPG fuel and then flows into the cylinder to prevent an increase in the internal pressure of the cylinder.

  In addition, heat exchange is performed between the refrigerant and the LPG fuel, and at the same time, heat exchange is performed between the medium-temperature and high-pressure liquid refrigerant supplied from the condenser and the low-temperature and low-pressure gas refrigerant supplied from the evaporator. An object of the present invention is to provide an LPI vehicular heat exchanger that improves the cooling efficiency of the refrigerant.

  Thereby, the fall of an air-conditioner system performance can be prevented and a cooling performance can be improved.

  To achieve the above object, an LPI vehicle heat exchanger according to an embodiment of the present invention is an LPI vehicle heat exchanger for cooling high-temperature LPG fuel returned from an engine in an LPI vehicle using LPG fuel. A plurality of plates are stacked to form first, second, and third connection channels, and the first, second, and third working fluids flow into the first, second, and third connection channels, respectively. The first, second, and third working fluids supplied to the first, second, and third connection channels are exchanged while passing through the first, second, and third connection channels. A heat dissipating part that circulates without being mixed with each other, and is formed on one surface of the heat dissipating part, and is connected to the first, second, and third connecting flow paths, respectively, and the first, second, and third working fluids Are supplied to the first, second and third connecting flow paths, respectively, Corresponding to the first, second, and third inlets, formed on the other surface of the heat radiating portion, respectively, connected to the first, second, and third connecting flow paths, respectively, the first, second, and third It is characterized by including the 1st, 2nd, 3rd discharge port which discharges working fluid from the 1st, 2nd, 3rd connection channel, respectively.

  The first working fluid is LPG fuel returned from the engine, the second working fluid is a medium-temperature and high-pressure liquid refrigerant supplied from a condenser of an air conditioner system, and the third working fluid is an evaporator. A low-temperature and low-pressure gaseous refrigerant supplied from

  The first inlet may be formed at one corner on one surface of the heat radiating portion, and the first outlet may be formed at a corner facing the first inlet on a diagonal direction on the other surface of the heat radiating portion. It is characterized by.

  The second inlet is formed on one surface of the heat radiating portion at a corner opposite to the longitudinal direction of the first inlet, and the second outlet is formed on the other surface of the heat radiating portion of the second inlet. It can be formed at opposite corners in the width direction.

  The third inflow port is formed on one surface of the heat radiating portion and spaced apart from the first inflow port in the longitudinal direction, and the third discharge port is formed on the other surface of the heat radiating portion on the width of the third inflow port. It can be formed on the opposite side of the direction.

  The LPG fuel circulates through the first inlet, the first connection channel, and the first outlet, and the low-temperature and low-pressure gas refrigerant passes through the second inlet, the second connection channel, and the second outlet. The medium-temperature and high-pressure liquid refrigerant circulates through the third inflow port, the third connection channel, and the third discharge port.

  The first connection channel is located in a central portion inside the heat radiating unit, and the second connection channel is disposed adjacent to the first connection channel at an upper part of the heat radiating unit. The third connection channel is located above the second connection channel at the top of the heat dissipating unit, and at the bottom of the heat dissipating unit. It can be formed between the first connection channel and the second connection channel.

  The low-temperature and low-pressure gas refrigerant and the medium-temperature and high-pressure liquid refrigerant can flow in opposite directions in the second connection channel and the third connection channel.

  The first inlet may be connected to an engine, the second inlet may be connected to a condenser of an air conditioner system, and the third inlet may be connected to an evaporator of an air conditioner system.

  The first outlet is connected to a cylinder in which LPG fuel is returned and stored, the second outlet is connected to a compressor of the air conditioner system, and the third outlet can be connected to an expansion valve of the air conditioner system. Features.

  The heat dissipation part is a plate-type heat dissipation part in which a plurality of plates are stacked.

  The heat exchanger for an LPI vehicle according to an embodiment of the present invention exchanges heat between the refrigerant circulating in the air conditioner system and the LPG fuel returned to the cylinder, lowers the temperature of the LPG fuel, and then flows into the cylinder 5 Therefore, an increase in the internal pressure of the cylinder 5 can be prevented.

  In addition, the medium temperature and high pressure liquid refrigerant supplied from the condenser and the low temperature and low pressure gas refrigerant supplied from the evaporator are exchanged with each other using the subcooling effect of the refrigerant, improving the cooling efficiency of the refrigerant. can do.

  In addition, since the refrigerant is supercooled and the LPG fuel is simultaneously cooled in a narrow engine room, space utilization can be improved and the layout can be simplified.

It is a lineblock diagram of an air-conditioning system to which a heat exchanger for LPI vehicles concerning an embodiment of the present invention is applied. It is a front perspective view of the heat exchanger for LPI vehicles concerning the embodiment of the present invention. It is a back perspective view of the heat exchanger for LPI vehicles concerning an embodiment of the present invention. It is sectional drawing along the AA line of FIG. It is sectional drawing along the BB line of FIG. It is sectional drawing along CC line of FIG. It is an operation state figure of the heat exchanger for LPI vehicles concerning an embodiment of the present invention.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

  Prior to this, the embodiment described in the present specification and the configuration shown in the drawings are only the most preferred embodiment of the present invention, and do not represent all the technical ideas of the present invention. It should be understood that there are various equivalents and variations that can be substituted at the time of filing.

  FIG. 1 is a configuration diagram of an air conditioner system to which an LPI vehicle heat exchanger according to an embodiment of the present invention is applied. FIGS. 2 and 3 are diagrams of an LPI vehicle heat exchanger according to an embodiment of the present invention. 4 is a front perspective view and a rear perspective view, FIG. 4 is a cross-sectional view taken along line AA in FIG. 2, and FIG. 5 is a cross-sectional view taken along line BB in FIG. These are sectional drawings along the CC line of FIG.

  Referring to these drawings, an LPI vehicle heat exchanger 100 according to an embodiment of the present invention mutually exchanges heat between the refrigerant circulating in the air conditioner system and the LPG fuel returned to the cylinder 5 from the engine 3. Thus, after the temperature of the LPG fuel is lowered, it is caused to flow into the cylinder 5. Accordingly, the heat exchanger 100 has a structure capable of preventing the internal pressure of the cylinder from increasing.

  In addition, heat exchange is performed between the refrigerant and the LPG fuel, and at the same time, heat exchange is performed between the medium-temperature and high-pressure liquid refrigerant supplied from the condenser 20 and the low-temperature and low-pressure gas refrigerant supplied from the evaporator 40, thereby Use the effect to improve the cooling efficiency of the refrigerant. As a result, the heat exchanger 100 has a structure that prevents the performance of the air conditioner system from being lowered and improves the cooling performance.

  Here, as shown in FIG. 1, an LPI vehicle heat exchanger 100 according to an embodiment of the present invention includes a compressor 10 that compresses a refrigerant, and a condensation that receives and condenses the refrigerant compressed from the compressor 10. Used in an air conditioner system that includes an evaporator 20, an expansion valve 30 that expands the liquid refrigerant condensed by the condenser 20, and an evaporator 40 that evaporates the refrigerant expanded by the expansion valve 30 by heat exchange with air. .

  Here, the heat exchanger 100 cools the high-temperature LPG fuel returned from the engine 3 in the LPI vehicle using the LPG fuel by heat exchange with the refrigerant.

  To this end, the LPI vehicle heat exchanger 100 according to the embodiment of the present invention includes a heat radiating portion 110, a plurality of inlets 120, and a plurality of outlets 130, as shown in FIGS. This will be described in more detail below for each configuration.

  First, the heat radiating part 110 is formed by laminating a plurality of plates 111, and a plurality of connection channels 140 are formed between adjacent plates 111. The plurality of working fluids exchange heat with each other while passing through the plurality of connection channels 140.

  The heat dissipating part 110 configured as described above is formed as a plate type (or “plate type”) heat dissipating part in which a plurality of plates 111 are stacked.

  Here, the plurality of working fluids include LPG fuel returned from the engine 3, medium temperature and high pressure liquid refrigerant supplied from the condenser 20 of the air conditioner system, and low temperature and low pressure gas refrigerant supplied from the evaporator 40. Including.

  In the present embodiment, the plurality of inlets 120 are formed on one surface of the heat radiating unit 110, and the plurality of working fluids flow into the heat radiating unit 110 through the plurality of inlets 120. . The plurality of inlets 120 are connected to the plurality of connection channels 140.

  The plurality of outlets 130 correspond to the plurality of inlets 120 and are formed on the other surface of the heat radiating unit 110. The plurality of working fluids flowing through the heat radiating unit 110 are discharged through the plurality of discharge ports 130. The plurality of outlets 130 are connected to the plurality of connection channels 140.

  Here, the plurality of inlets 120 include first, second, and third inlets 121, 123, and 125 that are formed on one surface of the heat dissipating unit 110 so as to be spaced apart from each other in the longitudinal direction.

  The plurality of discharge ports 130 correspond to the first, second, and third inflow ports 121, 123, and 125, respectively, and are formed on the other surface of the heat radiating unit 110 to be separated from each other. 2 and third discharge ports 131, 133, 135. The first, second, and third discharge ports 131, 133, and 135 are connected to the first, second, and third inlet ports 121, 123, and 125 through the plurality of connection channels 140, respectively.

  In the present embodiment, the first inlet 121 is formed at one corner on one surface of the heat radiating part 110, and the first outlet 131 is formed on the other surface of the heat radiating part 110. Are formed at corners facing diagonally.

  The second inflow port 123 is formed on one surface of the heat radiating unit 110 at a corner opposite to the longitudinal direction of the first inflow port 121, and the second discharge port 133 is formed on the other surface of the heat radiating unit 110. The second inflow port 123 is formed at the opposite corner in the width direction.

  The third inlet 125 is formed on one surface of the heat radiating part 110 and is spaced apart from the first inlet 121 in the longitudinal direction, and the third outlet 135 is formed on the other surface of the heat radiating part 110. The third inlet 125 is formed on the opposite side in the width direction.

  Here, the LPG fuel circulates through the first inlet 121 and the first outlet 131, and the low-temperature and low-pressure gas refrigerant circulates through the second inlet 123 and the second outlet 133, The medium temperature and high pressure liquid refrigerant circulates through the third inlet 125 and the third outlet 135.

  That is, the first outlet 131 is interconnected to the cylinder 5 where LPG fuel is returned and stored, and the second outlet 133 is interconnected to the compressor 10 of the air conditioner system and passes through the heat radiating unit 110. A low-pressure gaseous refrigerant is supplied to the compressor 10.

  The third discharge port 135 is interconnected with the expansion valve 30 of the air conditioner system, and supplies the medium temperature and high pressure liquid refrigerant that has passed through the heat radiating unit 110 to the expansion valve 30.

  On the other hand, a connection port (not shown) can be attached to each of the inflow port 120 and the discharge port 130, and the air conditioner system, the engine 3 and the cylinder 5 are connected via a connection hose or a connection pipe attached to the connection port. Can be connected to each other.

  In the present embodiment, the plurality of connection channels 140 include first, second, and third connection channels 141, 143, and 145, which will be described in more detail below.

  First, as shown in FIG. 4, the first connection channel 141 is configured such that the LPG fuel that has flowed in through the first inlet 121 moves, and is located in the center of the heat radiating unit 110. To position.

  In the present embodiment, as shown in FIG. 5, the second connection channel 143 is disposed adjacent to the first connection channel 141 in the upper part of the heat radiating unit 110 and in the lower part of the heat radiating unit 110. It is formed apart from the first connection channel 141. The second connection channel 143 at the upper part of the heat radiating unit 110 and the second connection channel 143 at the lower part of the heat radiating unit 110 are connected inside the heat radiating unit 110 and flowed in through the second inlet 123. The low-temperature and low-pressure gaseous refrigerant that moves moves in the second connection channel 143.

  That is, the LPG fuel passing through the first connection channel 141 is cooled by heat exchange with a low-temperature and low-pressure gas refrigerant flowing through the second connection channel 143 located adjacent to the top of the first connection channel 141. The

  As shown in FIG. 6, the third connection channel 145 is positioned above the second connection channel 143 above the heat dissipating unit 110, and the first connection flow is positioned below the heat dissipating unit 110. A path 141 is formed between the second connection channel 143. The third connection channel 145 in the upper part of the heat radiating unit 110 and the third connection channel 145 in the lower part of the heat radiating unit 110 are connected inside the heat radiating unit 110 and flow in via the third inlet 125. The medium-temperature and high-pressure liquid refrigerant that moves moves in the third connection channel 145.

  That is, the second connection channel 143 interconnects the upper part of the first connection channel 141 and the lower part of the third connection channel 145 located below the heat dissipation unit 110 in the heat dissipation unit 110. Formed as follows.

  As a result, the low-temperature and low-pressure gaseous refrigerant passing through the second connection channel 143 is heat-exchanged with the LPG fuel passing through the first connection channel 141 at the upper part of the heat dissipation unit 110, and at the lower part of the heat dissipation unit 110. Heat exchange with the medium-temperature and high-pressure liquid refrigerant passing through the third connection channel 145 is performed.

  Therefore, the LPG fuel and the medium temperature / high pressure liquid refrigerant are cooled by heat exchange with the low temperature / low pressure gas refrigerant.

  Since the second inlet 123 and the third inlet 125 are formed in opposite directions on one surface of the heat radiating part 110, the low-temperature and low-pressure gas refrigerant and the medium-temperature and high-pressure liquid refrigerant are connected to the second connection channel 143. And flow in opposite directions within the third connection channel 145.

  Thereby, the heat exchange efficiency between the low-temperature and low-pressure gas refrigerant and the medium-temperature and high-pressure liquid refrigerant is improved.

  Further, the non-condensed gas refrigerant contained in the medium-temperature and high-pressure liquid refrigerant passing through the third connection channel 145 is condensed by heat exchange with the low-temperature and low-pressure gas refrigerant passing through the second connection channel 143. As a result, the efficiency of the air conditioner system is prevented from decreasing due to the non-condensable gas refrigerant, and the expansion efficiency of the expansion valve 30 is increased.

  Hereinafter, the operation and action of the heat exchanger 100 for an LPI vehicle according to the embodiment of the present invention configured as described above will be described in detail.

  FIG. 7 is a use state diagram of the heat exchanger for an LPI vehicle according to the embodiment of the present invention.

  First, as shown in FIG. 7 (S1), the high-temperature LPG fuel returned from the engine 3 flows in through the first inflow port 121 and passes through the first connection flow path 141, and the first exhaust. The gas is discharged to the cylinder 5 through the outlet 131.

  The low-temperature and low-pressure gaseous refrigerant supplied from the evaporator 40 flows in through the second inlet 123 and passes through the second connection channel 143 as shown in (S2) of FIG. It is discharged to the compressor 10 through the outlet 133.

  Here, the LPG fuel moves in the first connection channel 141, and the low-temperature and low-pressure gaseous refrigerant is a second connection channel 143 located above the heat dissipation part 110 and above the first connection channel 141. Move in. Therefore, the LPG fuel is cooled while exchanging heat with a low-temperature and low-pressure gaseous refrigerant.

  Then, the medium-temperature and high-pressure liquid refrigerant supplied from the condenser 20 flows in through the third inlet 125 and passes through the third connection channel 145 as shown in (S3) of FIG. 3 is discharged to the expansion valve 30 through the discharge port 135.

  At this time, the low-temperature and low-pressure gas refrigerant moves in the second connection channel 143 in the upper part of the heat dissipating unit 110, and the medium-temperature and high-pressure liquid refrigerant moves in the third connection channel 143. It moves in the channel 145. The low-temperature and low-pressure gas refrigerant flows in the opposite direction to the medium-temperature and high-pressure liquid refrigerant. Therefore, the medium temperature and high pressure liquid refrigerant exchanges heat with the low temperature and low pressure gas refrigerant.

  Since the medium temperature and high pressure liquid refrigerant passes through the third connection channel 145 located above the second connection channel 143 above the heat radiating unit 110, the medium temperature and high pressure liquid refrigerant has a low temperature in the engine room. It prevents the direct transmission to the low-pressure gas refrigerant and prevents the temperature of the gas refrigerant from rising.

  Thereby, the fall of the cooling performance of the air-conditioning system by the temperature rise of gaseous refrigerant can be prevented beforehand.

  In the lower part of the heat radiating unit 110, the medium-temperature and high-pressure liquid refrigerant passes through the third connection channel 145 disposed at the lower part of the first connection channel 141. Therefore, the LPG fuel that passes through the first connection channel 141 is prevented from being overcooled during heat exchange with the low-temperature and low-pressure gaseous refrigerant, and the LPG fuel is cooled to an appropriate level.

  Thus, the LPG fuel cooled to an appropriate level of temperature is supplied to the cylinder 5 through the first exhaust port 131.

  Therefore, the heat exchanger 100 heat-exchanges the high-temperature LPG fuel returned from the engine 3 with the low-temperature and low-pressure gas refrigerant and the medium-temperature and high-pressure liquid refrigerant, and after cooling to an appropriate level, Supplied. Accordingly, it is possible to prevent the LPG fuel in a high temperature state from flowing into the cylinder 5 and increasing the internal pressure of the cylinder 5.

  On the other hand, the non-condensed gas refrigerant contained in the medium-temperature and high-pressure liquid refrigerant passing through the third connection channel 145 is condensed by heat exchange with the low-temperature and low-pressure gas refrigerant passing through the second connection channel 143. Is done. Therefore, it is possible to prevent the efficiency of the air conditioner system from decreasing due to the non-condensable gas refrigerant and to increase the expansion efficiency of the expansion valve 30.

  Therefore, the LPI vehicle heat exchanger 100 according to the embodiment of the present invention reduces the temperature of the LPG fuel by exchanging heat between the refrigerant circulating in the air conditioner system and the LPG fuel returned to the cylinder 5. Then, it flows into the cylinder 5. Therefore, it is possible to prevent the internal pressure of the cylinder 5 from increasing.

  Further, by preventing the internal pressure of the cylinder 5 from increasing, fuel can be smoothly injected into the cylinder 5 at the time of fuel filling, and the merchantability can be improved.

  Furthermore, the LPI vehicle heat exchanger 100 according to the embodiment of the present invention exchanges heat between the medium-temperature and high-pressure liquid refrigerant supplied from the condenser 20 and the low-temperature and low-pressure gas refrigerant supplied from the evaporator 40. In this case, it is possible to improve the cooling efficiency of the refrigerant by utilizing the cooling effect of the refrigerant, to prevent the performance of the air conditioner system from being lowered, and to improve the cooling performance.

  Further, by simultaneously performing cooling of the refrigerant and cooling of the LPG fuel in a narrow engine room, it is possible to improve space utilization and simplify the layout.

  As described above, the present invention has been described with reference to the embodiments and the drawings. However, the present invention is not limited thereto, and any person having ordinary knowledge in the technical field to which the present invention belongs can be used. Various modifications and variations are possible within the technical idea and the technical scope.

  The present invention can be applied to the field of heat exchangers for LPI vehicles.

3: Engine 5: Cylinder 10: Compressor 20: Condenser 30: Expansion valve 40: Evaporator 100: Heat exchanger for LPI vehicle 110: Heat radiation part 111: Plate 120: Inlet 121, 123, 125: First, Second and third inlets 130: outlets 131, 133, 135: first, second, and third outlets 140: connection channels 141, 143, and 145: first, second, and third connection channels

Claims (10)

In an LPI vehicle heat exchanger for cooling high temperature LPG fuel returned from an engine in an LPI vehicle using LPG fuel,
In the heat radiating part formed by laminating a plurality of plates , the first, second and third connection flow paths are formed,
First front Symbol on a surface of the heat radiating portion, the second, first that will be connected respectively to the third connecting flow path, the second, third inlet port is spaced apart from each
Other surface before Symbol first the heat radiating portion, the second, first that will be connected respectively to the third connecting flow path, the second, third outlet is spaced apart from each
High-temperature LPG fuel returned from the engine flows in through the first inlet, passes through the first connection channel, and is discharged into the cylinder through the first outlet.
A low-temperature and low-pressure gaseous refrigerant supplied from an evaporator of a vehicle air conditioner flows in through the second inlet, passes through the second connection channel, and is discharged to the compressor through the second outlet. And
Medium temperature and high pressure liquid refrigerant supplied from a condenser of the vehicle air conditioner flows in through the third inlet, passes through the third connection channel, and passes through the third outlet to the expansion valve. Discharged,
LPG fuel in the high temperature state, the low temperature the each first low-pressure gas refrigerant and intermediate temperature high pressure liquid refrigerant, a second, mutual heat exchange is performed while passing through the third connecting channel, wherein the Turkey Heat exchanger for LPI vehicles.   The first inlet is formed at one corner on one surface of the heat radiating portion, and the first outlet is formed at a corner facing the first inlet on a diagonal direction on the other surface of the heat radiating portion. The heat exchanger for an LPI vehicle according to claim 1.   The second inlet is formed on one surface of the heat radiating portion at a corner opposite to the longitudinal direction of the first inlet, and the second outlet is formed on the other surface of the heat radiating portion of the second inlet. The LPI vehicle heat exchanger according to claim 1, wherein the LPI vehicle heat exchanger is formed at a corner opposite to the width direction.   The third inflow port is formed on one surface of the heat radiating portion and spaced apart from the first inflow port in the longitudinal direction, and the third discharge port is formed on the other surface of the heat radiating portion on the width of the third inflow port. The LPI vehicle heat exchanger according to claim 1, wherein the heat exchanger is formed on an opposite side of the direction.   The LPG fuel circulates through the first inlet, the first connection channel, and the first outlet, and the low-temperature and low-pressure gas refrigerant passes through the second inlet, the second connection channel, and the second outlet. 2. The LPI vehicle heat exchanger according to claim 1, wherein the medium-temperature and high-pressure liquid refrigerant circulates through the third inflow port, the third connection flow path, and the third exhaust port. . The first connection channel is located in a central part inside the heat dissipation part,
The second connection channel is disposed adjacent to the first connection channel in the upper part of the heat dissipation part, and is formed separately from the first connection channel in the lower part of the heat dissipation part, and
The third connection channel is located above the second connection channel above the heat dissipating unit, and is formed between the first connection channel and the second connection channel below the heat dissipating unit. The LPI vehicle heat exchanger according to claim 5 , wherein the heat exchanger is for LPI vehicles. 6. The heat exchanger for an LPI vehicle according to claim 5 , wherein the low-temperature and low-pressure gas refrigerant and the medium-temperature and high-pressure liquid refrigerant flow in opposite directions in the second connection channel and the third connection channel. .   The first inlet is connected to an engine, the second inlet is connected to a condenser of an air conditioner system, and the third inlet is connected to an evaporator of the air conditioner system. The heat exchanger for LPI vehicles described in 2.   The first outlet is connected to a cylinder in which LPG fuel is returned and stored, the second outlet is connected to a compressor of an air conditioner system, and the third outlet is connected to an expansion valve of the air conditioner system. The heat exchanger for LPI vehicles according to claim 1 characterized by things.   The LPI vehicle heat exchanger according to claim 1, wherein the heat dissipating unit is a plate heat dissipating unit in which a plurality of plates are stacked.

Images