KR101276220B1 - Dual Air Conditioner for Vehicle - Google Patents

Abstract

The present invention relates to a vehicle dual air conditioner, and more particularly, by installing the rear side high temperature pipe connected to the rear expansion valve of the rear air conditioner so as to branch directly from the expansion part of the double tube internal heat exchanger of the front air conditioner, By eliminating the separate connector for branching the high temperature pipe from the front air conditioner, it reduces the number of parts and simplifies the manufacturing process, and also improves the refrigerant flow by reducing the piping work and route route and reduces the material cost and work process. The present invention relates to a dual air conditioner for a vehicle that can be shortened.

Description

Dual air conditioner for vehicle

The present invention relates to a vehicle dual air conditioner, and more particularly, a vehicle dual air conditioner installed so as to branch directly from the expansion portion of the double tube internal heat exchanger of the front air conditioner to the rear side high temperature pipe connected to the rear expansion valve of the rear air conditioner. Relates to a device.

Background Art [0002] A vehicle air conditioner is an automobile interior product installed for the purpose of enabling a driver to secure front and rear vision by removing air from the windshield during rainy or winter or by cooling or heating the interior of the automobile in the summer or winter season. Such an air conditioning apparatus is usually equipped with a heating system and a cooling system at the same time so that the outside air or the inside is selectively introduced to heat or cool the air and then air is blown into the inside of the vehicle to cool,

In the air conditioner, a small passenger car having a small indoor space has a so-called single air conditioner having one evaporator in the engine room at the front side of the vehicle. In order to provide a sufficient air conditioning environment to the rear of the vehicle, as shown in FIG. 1, the front air conditioner 10 installed at the engine room side and having the front evaporator 14, and the rear evaporator 22 installed at the rear side of the vehicle. Applying a dual air conditioning device consisting of a rear air conditioning device 20 having a.

The dual air conditioner including the front air conditioner 10 and the rear air conditioner 20 may operate the front evaporator 14 and the rear evaporator 22 simultaneously or separately, and the front evaporator 14 and The rear evaporator 22 forms a refrigeration cycle in which the refrigerant is circulated through the one compressor 11 and the condenser 12.

1 is a view showing a state in which a conventional dual air conditioner is installed in a vehicle, Figure 2 is a block diagram showing a conventional dual air conditioner, Figure 3 is a refrigerant from the front air conditioner to the rear air conditioner in the conventional dual air conditioner It is a perspective view which shows the part to branch.

As illustrated, first, the front air conditioner 10 includes a compressor 11 for sucking and compressing a refrigerant, a condenser 12 for condensing a high temperature and high pressure refrigerant sent from the compressor 11, and the condenser ( 12, the front expansion valve 13 for throttling the refrigerant condensed and liquefied, and the low-temperature low-pressure liquid refrigerant throttled by the front expansion valve 13 exchanges heat with the air blown to the vehicle interior to evaporate the refrigerant. It is configured by connecting the front evaporator 14 for cooling the air discharged to the room by the endothermic action by the latent heat of evaporation by the pipe 16, to cool the front seat of the vehicle.

In addition, the front side low temperature pipe 16a connecting the front evaporator 14 and the compressor 11 and the front side high temperature pipes 16b and 16c connecting the condenser 12 and the front expansion valve 13 are specified. A double tube internal heat exchanger 15 is installed to configure a section in a double tube structure to mutually heat-exchange the refrigerant flowing through each pipe.

Here, the double tube type internal heat exchanger 15 exchanges heat between the high temperature and high pressure liquid refrigerant before being throttled by the front expansion valve 13 and the low temperature and low pressure gas phase refrigerant discharged from the front evaporator 14 to thereby exchange the front evaporator ( 14) stabilizes the flow of the refrigerant flowing into the front, reduces the refrigerant pressure drop in the front evaporator (14), the refrigerant is completely set to vaporize to prevent the compressor inflow of the liquid refrigerant is a relatively high temperature front evaporator It is possible to reduce the overheating region (not shown) of (14).

Therefore, since the specific volume of the refrigerant flowing into the front evaporator 14 is reduced, the refrigerant pressure drop in the front evaporator 14 is reduced, so that the refrigerant flow in each cooling tube in the front evaporator 14 can be stabilized. Since the refrigerant flowing into (11) can be superheated after being discharged from the front evaporator 14, the superheated area of the front evaporator 14, which is a factor of lowering the cooling performance of the air conditioner, can be reduced because the temperature is relatively high. The cooling efficiency of the air conditioner can be greatly increased. As a result, the compressor 11, the condenser 12 and the front evaporator 14 can be made efficient, contributing to the high efficiency and miniaturization of the air conditioning apparatus.

The rear air conditioner 20 is configured to branch refrigerant from the condenser 12 of the front air conditioner 10 toward the front expansion valve 13 to the rear high temperature pipe 23 to throttle the branched refrigerant. An expansion valve 21 and a rear evaporator 22 for evaporating the refrigerant flowing from the rear expansion valve 21 and then joining the refrigerant from the front evaporator 14 to the compressor 11. The rear seats are cooled.

As such, the front air conditioner 10 having the front expansion valve 13 and the front evaporator 14 and the rear air conditioner 20 having the rear expansion valve 21 and the rear evaporator 22 include one compressor. A refrigeration cycle using 11 and one condenser 12 in common is formed.

Hereinafter, a refrigerant circulation process of the dual air conditioner will be described.

First, when a cooling switch (not shown) is turned on, first, the compressor 11 drives by the power of the engine to suck and compress the low-temperature low-pressure gaseous refrigerant to the condenser 12 in a gas state of high temperature and high pressure. The condenser 12 exchanges the gaseous refrigerant with outside air to condense it into a liquid of high temperature and high pressure. Subsequently, the liquid refrigerant sent out from the condenser 12 in a state of high temperature and high pressure passes through the external appearance 15b of the double tube internal heat exchanger 15.

Subsequently, some of the refrigerant that has passed through the exterior 15b of the double tube internal heat exchanger 15 flows into the front expansion valve 13 through the front hot pipe 16c and expands to the front evaporator 14. Is introduced and evaporated by heat exchange with air blown to the front seat side of the vehicle interior, and the rest is introduced into the rear expansion valve 21 through the rear high temperature pipe 23 branched from the front high temperature pipe 16c. After inflated, it is introduced into the rear evaporator 22 and evaporated by heat exchange with air blown to the rear seat side of the vehicle interior.

In the above process, the cooling is performed on the front and rear seats of the vehicle interior, respectively. That is, the air blown by the blower (not shown) is discharged to the vehicle interior while cooled by the latent heat of evaporation of the liquid refrigerant circulating in the evaporators 14 and 22 while passing through the evaporators 14 and 22. By doing so.

Subsequently, the low-temperature low-pressure gaseous refrigerant discharged after evaporation from the front evaporator 14 and the low-temperature low-pressure gas phase refrigerant discharged after the evaporation from the rear evaporator 22 are combined, and then the double tube internal heat exchanger 15 Pass through the inner tube (15a).

At this time, the low-temperature low-pressure gas phase refrigerant passing through the inner tube 15a of the double tube internal heat exchanger 15 exchanges heat with the high temperature and high pressure liquid refrigerant passing through the exterior 15b of the double tube internal heat exchanger 15, and then again. It is sucked into the compressor 11 and recycles the refrigerating cycle as described above.

2 and 3, the rear air conditioner 20 branches the refrigerant circulating through the front air conditioner 10 to circulate the refrigerant through the rear expansion valve 21 and the rear evaporator 22. That is, the rear expansion valve 21 is branched by branching the rear high temperature pipe 23 from the front high temperature pipe 16c connecting the exterior 15b and the front expansion valve 13 of the double tube internal heat exchanger 15. And the refrigerant is circulated to the rear evaporator 22.

In this case, in order to connect the front high temperature pipe 16c and the rear high temperature pipe 23, a separate connector 30 is used as shown in FIGS. 4 and 5, and is manufactured in the following process.

4 is divided into the front hot pipe 16c and welded to both ends of the connector 30, the rear hot pipe 23 is welded to the connector 30 in a perpendicular direction,

5 shows the front hot pipe 16c passing through the connector 30, and the rear hot pipe 23 is welded to the connector 30 at right angles. At this time, a hole must be formed in the front high temperature pipe 16c penetrating the inside of the connector 30.

However, in the related art, in order to branch the refrigerant circulating in the front air conditioning apparatus 10 and circulate it to the rear air conditioning apparatus 20, the rear side high temperature pipe 23 is used in the front side by using the connector 30. Since the high temperature pipe 16c needs to be connected, there is a problem in that the number of parts increases and the manufacturing process also increases.

In addition, when the distance between the double tube internal heat exchanger 15 and the front expansion valve 13 is short, the piping work of the front high temperature pipe 16c and the rear high temperature pipe 23 is complicated, and the pipe route Also complicated, refrigerant flow is disadvantageous.

In addition, since the rear high temperature pipe 23 branches in the direction perpendicular to the connector 30, refrigerant flow is disadvantageous.

An object of the present invention for solving the above problems is to install the rear high temperature pipe connected to the rear expansion valve of the rear air conditioner so as to branch directly from the expansion portion of the double tube internal heat exchanger of the front air conditioner, thereby By eliminating separate connectors for branching from the front air conditioning unit, it is possible to reduce the number of parts and simplify the manufacturing process, and to improve refrigerant flow, reduce material costs, and shorten the work process by simplifying piping and piping routes. The present invention provides a dual vehicle air conditioner.

The present invention for achieving the above object is a compressor for sucking and compressing a refrigerant, a condenser for condensing the refrigerant compressed in the compressor, a front expansion valve for condensing the refrigerant condensed in the condenser, and the front expansion valve Each pipe flows with a double pipe structure consisting of a front section of the front evaporator for evaporating the refrigerant flowing from, and a front section of the low temperature pipe connecting the front evaporator and the compressor and the front high temperature pipe connecting the condenser and the front expansion valve. A front air conditioner including a double tube internal heat exchanger configured to mutually heat-exchange the refrigerant, and cooling the front seat of the vehicle; The rear expansion valve for branching the refrigerant to the front expansion valve from the condenser to the rear high-temperature pipe and condenses the branched refrigerant, and after the refrigerant flowing from the rear expansion valve is evaporated, the refrigerant from the front evaporator to the compressor is joined. And a rear air conditioner configured to cool a rear seat of the vehicle, wherein the rear high temperature pipe is branched directly while being connected to one side of the double-tubular internal heat exchanger. It is characterized in that it is formed to be connected to the valve.

According to the present invention, the rear side hot pipe connected to the rear expansion valve of the rear air conditioner is installed so as to branch directly from the expansion part of the double tube type internal heat exchanger of the front air conditioner, so that the rear side hot pipe is separated from the front air conditioner. The connector can be deleted, thereby reducing the number of parts and simplifying the manufacturing process, and can simplify the piping work irrespective of the distance between the double tube internal heat exchanger and the front expansion valve.

In addition, by simplifying the route of the rear high-temperature pipe, it is possible to improve the refrigerant flow, reduce the material cost and shorten the work process.

Further, by directly branching the rear high temperature pipe from the expansion part of the external appearance of the double tube internal heat exchanger, the pressure loss of the refrigerant is minimized when the refrigerant flowing in the external appearance is distributed to the rear high temperature pipe, thereby improving the refrigerant flow. .

In addition, by installing a pipe having a diameter larger than that of the double tube internal heat exchanger and less disturbance of fluid flow due to the inner tube, the refrigerant flow is smoother to the high temperature and high pressure pipe.

The flow rate of the refrigerant distributed to each pipe can be easily adjusted by adjusting the inclination angles or diameters of the front high temperature pipe and the rear high temperature pipe connected in the circumferential direction or the longitudinal direction to the expansion pipe part of the external appearance.

1 is a view showing a state where a conventional dual air conditioner is installed in a vehicle,
2 is a block diagram showing a conventional dual air conditioner,
3 is a perspective view showing a part of the refrigerant branched from the front air conditioner to the rear air conditioner in the conventional dual air conditioner,
4 and 5 are perspective views showing a case where the front high temperature pipe and the rear high temperature pipe are coupled by a connector in a conventional dual air conditioner;
6 is a configuration diagram showing a vehicle dual air conditioning apparatus according to the present invention,
7 is a perspective view showing a portion of the refrigerant branched from the front air conditioner to the rear air conditioner in the vehicle dual air conditioner according to the present invention,
8 is a cross-sectional view taken along the line AA of FIG.
9 is a cross-sectional view showing the double tube internal heat exchanger of FIG.
10 is a partial cross-sectional view showing the flow direction of the refrigerant in the double tube internal heat exchanger of FIG.
11 is a perspective view showing another embodiment as a part of the refrigerant branched from the front air conditioner to the rear air conditioner in the vehicle dual air conditioner according to the present invention,
12 is a cross-sectional view showing the double tube internal heat exchanger of FIG.
FIG. 13 is an enlarged cross-sectional view illustrating one expanding tube of FIG. 12;
14 is an enlarged cross-sectional view illustrating another embodiment of FIG. 13.

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

The vehicle dual air conditioner 100 according to the present invention includes a front air conditioner 200 installed at an engine room side of a vehicle and a rear branch installed at a rear side of the vehicle by branching a refrigerant circulating through the front air conditioner 200. It is composed of an air conditioning apparatus (300).

First, the front air conditioner 200, the compressor 210-> condenser 220-> double tube internal heat exchanger 250-> front expansion valve 230-> front evaporator 240 pipe (P) It is configured by connecting.

The compressor 210 drives and receives power from a power supply source (engine or motor) to suck and compress the low-temperature low-pressure gaseous refrigerant discharged from the front evaporator 240 to condense the gas into a high-temperature, high-pressure gas state. 220).

The condenser 220 heat-exchanges the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 210 to the outside air to condense it into a high-temperature, high-pressure liquid, and discharge the same to the front expansion valve 230.

The expansion valve 230 expands rapidly the high-temperature and high-pressure liquid refrigerant discharged from the condenser 220 by throttling to be sent to the front evaporator 240 in a low temperature low pressure wet state.

The front evaporator 240 exchanges the low pressure liquid refrigerant throttled by the front expansion valve 230 with the air blown to the inside of the vehicle to evaporate the air to be discharged to the room by the endothermic action of the latent heat of evaporation of the refrigerant. To cool.

Subsequently, the low-temperature low-pressure gaseous refrigerant evaporated in the front evaporator 240 is again sucked into the compressor 210 to recycle the cycle as described above.

In addition, in the refrigerant circulation process as described above, the cooling of the vehicle interior is a liquid refrigerant that circulates inside the front evaporator 240 while the air blown by a blower (not shown) of the vehicle air conditioner passes through the front evaporator 240. It is made by being discharged to the interior of the vehicle in a state of being cooled by the latent heat of evaporation.

The double tube internal heat exchanger 250 is a front side cold pipe P3 connecting the front evaporator 240 and the compressor 210 and a front side connecting the condenser 220 and the front expansion valve 230. Specific sections of the high-temperature pipes P1 and P2 are formed in a double pipe structure to mutually heat exchange the refrigerant flowing through each pipe.

The double tube internal heat exchanger 250 includes an inner tube 251 formed in a specific section of the front side cold pipe P3 connecting the front evaporator 240 and the compressor 210, and an outer circumferential surface of the inner tube 251. It consists of an appearance 252 is coupled to a double pipe structure.

That is, as shown in FIGS. 9 and 10, the double tube internal heat exchanger 250 forms a spiral protrusion 251 a and a recess 251 b in any one of the inner tube 251 and the exterior 252. A first refrigerant passage R1 is formed inside the inner tube 251, and a second refrigerant passage R2 is formed between the inner tube 251 and the exterior 252.

Here, the first refrigerant flow path R1 is a flow path through which refrigerant (gas refrigerant) discharged from the front evaporator 240 and the rear evaporator 320 merges and flows, and the second refrigerant flow path R2 is the condenser. It is a flow path through which the refrigerant (liquid refrigerant) discharged from 220 flows.

In the drawing, a spiral protrusion 251a and a recess 251b are formed on the outer circumferential surface of the inner tube 251, and the outer tube 252 is formed by a circular pipe, thereby combining the inner tube 251 with a double tube structure. It is shown.

At this time, the spiral protrusion 251a of the inner tube 251 is in close contact with the inner circumferential surface of the outer tube 252, so that the second refrigerant passage R2 formed between the inner tube 251 and the outer tube 252 is in a spiral shape. Will be formed.

In addition, both ends of the protruding portion 251a and the concave portion 251b formed on the outer circumferential surface of the inner tube 251 are terminated in the expansion pipe 253 formed at both ends of the outer appearance 252 which will be described later.

On the other hand, both ends of the outer appearance 252 is sealed with the outer peripheral surface of the front side cold pipe (P3) by a method such as welding.

In addition, expansion pipes 253 are formed at both ends of the exterior 252, and at one side expansion pipe 253, the front side high temperature pipe P1 connected to the condenser 220 is joined by welding, and the other expansion pipe portion 253. The front side high temperature pipe P2 connected to the front expansion valve 230 is welded to 253.

As such, the expansion pipes 253 are formed at both ends of the exterior 252 to enlarge the refrigerant passage (the flow path cross-sectional area), so that the refrigerant flows into the exterior 252 or when the refrigerant is discharged from the exterior 252. Minimize pressure loss.

The rear air conditioner 300 branches the high temperature and high pressure refrigerant from the condenser 220 toward the front expansion valve 230 to the rear side high temperature pipe P4 to throttle the branched refrigerant. And a rear evaporator 320 for evaporating the low temperature and low pressure refrigerant flowing from the rear expansion valve 310 and then joining the refrigerant from the front evaporator 240 to the compressor 210 to the rear seat of the vehicle. Cooled.

That is, the refrigerant before branching into the front expansion valve 230 of the front air conditioner 200 through the rear high-temperature pipe (P4) branched refrigerant to the rear expansion valve 310 and the rear evaporator 320 Cycles).

In addition, the rear cold pipe (P5) connected to the outlet side of the rear evaporator 320 is connected to the front cold pipe (P3) before passing through the double-tubular internal heat exchanger (250) in the front evaporator (240). The refrigerant after evaporating from the rear evaporator 320 is combined with the refrigerant flowing through the front low temperature pipe P3 after evaporating from the front evaporator 240.

In addition, the rear high temperature pipe (P4) is connected to one side of the double-tubular internal heat exchanger 250 is directly branched is formed to be connected to the rear expansion valve (310).

Therefore, in the process of flowing the refrigerant discharged from the condenser 220 of the front air conditioner 200 to the front expansion valve 230 through the exterior 252 of the double-tube internal heat exchanger 250, the exterior 252 Some of the refrigerant flowing through the branch is branched directly to the rear high-temperature pipe (P4) to flow to the rear expansion valve (310).

In addition, the rear high temperature pipe P4 is welded to and connected to an expansion pipe portion 253 of the exterior 252 to which the front high temperature pipe P2 connected to the front expansion valve 230 is connected. That is, the rear side high temperature pipe P4 is connected to the expansion part 253 of the exterior 252, so that the refrigerant having passed through the second refrigerant flow path R2 in the exterior 252 passes through the rear side high temperature pipe P4. When distributed to P4), the pressure loss of the refrigerant is minimized to improve the refrigerant flow.

In addition, the flow rates of the refrigerants respectively distributed through the front high temperature pipe P2 and the rear high temperature pipe P4 connected to the expansion pipe 253 of the exterior 252 may be adjusted through various embodiments below. have.

In the first embodiment, as shown in FIG. 8, the front hot pipe P2 and the rear hot pipe P4 respectively connected to the expansion pipe 253 of the exterior 252 have a circumference of the expansion pipe 253. Are connected at regular intervals in the direction of each other.

At this time, the front side high temperature pipe P2 is inclined at a predetermined angle θ1 in a downward direction (gravity direction) to one side (left side) based on the vertical center line C of the expansion pipe 253, and the other side (right side). ), The rear high temperature pipe P4 is inclined at a predetermined angle θ2 in the downward direction (gravity direction).

Here, the inclination angle θ1 of the front high temperature pipe P2 is smaller than the inclination angle θ2 of the rear high temperature pipe P4 based on the vertical center line C of the expansion pipe 253. Do.

That is, since the front high temperature pipe P2 connected to the expansion pipe 253 is inclined closer to the vertical side than the rear high temperature pipe P4, the influence of gravity is increased, and thus the appearance 252 Refrigerant introduced into the expansion unit 253 through the second refrigerant passage (R2) in the) is relatively more refrigerant is distributed to the front high-temperature pipe (P2) by gravity (self-weight).

Typically, since the front evaporator 240 of the front air conditioner 200 has a larger capacity than the rear evaporator 320 of the rear air conditioner 300, the front high temperature pipe for supplying a refrigerant to the front evaporator 240 side ( By installing P2) closer to the vertical, relatively more refrigerant is supplied to the front evaporator 240 side.

As described above, the refrigerant distributed to each of the pipes P2 and P4 by adjusting the inclination angles of the front high temperature pipe P2 and the rear high temperature pipe P4 connected to the expansion pipe 253 of the external appearance 252. The flow rate can be adjusted.

In the second embodiment, as shown in FIGS. 11 to 13, the front side high temperature pipe P2 and the rear side high temperature pipe P4 respectively connected to the expansion part 253 of the external appearance 252 have the expansion part 253. Are connected at regular intervals in the longitudinal direction.

At this time, the front high temperature pipe (P2) and the rear high temperature pipe (P4) is connected perpendicularly to the lower direction (gravity direction) of the expansion pipe 253.

In addition, in the embodiment of FIGS. 11 to 13, since both the front high temperature pipe P2 and the rear high temperature pipe P4 are connected to the expansion pipe 253 perpendicularly to each of the pipes P2 and P4. The diameters D1 and D2 are adjusted to adjust the flow rates of the refrigerant distributed to each of the pipes P2 and P4.

Here, the diameter (D1) of the front hot pipe (P2) is formed larger than the diameter (D2) of the rear hot pipe (P4) to supply more refrigerant to the front evaporator 240 side having a larger capacity. It is preferable.

In addition, since the front high temperature pipe (P2) and the rear high temperature pipe (P4) is connected to be spaced apart at regular intervals in the longitudinal direction of the expansion pipe 253, the front high temperature pipe (P2) and the rear high temperature It is preferable that the length L2 of the expansion pipe part 253 to which the pipe P4 is connected is larger than the length L1 of the expansion pipe part 253 to which the said front side high temperature pipe P1 is connected.

In the third embodiment, as shown in Fig. 14, the front side high temperature pipe P2 and the rear side high temperature pipe P4 respectively connected to the expansion portion 253 of the outer appearance 252 are refrigerant within the expansion portion 253. It is connected at regular intervals from each other in the flow direction.

In this case, the front high temperature pipe (P2) and the rear high temperature pipe (P4) is connected in a vertical direction to the lower direction (gravity direction) of the expansion pipe 253 is formed with the same diameter, respectively.

In addition, in the embodiment of FIG. 14, since both the front high temperature pipe P2 and the rear high temperature pipe P4 are vertically connected to the expansion pipe 253 and are formed to have the same diameter, respectively, the expansion pipe ( The flow rate of the refrigerant distributed to each of the pipes P2 and P4 is adjusted by changing the arrangement order of the front side hot pipes P2 and the rear side hot pipes P4 connected along the refrigerant flow direction 253.

Here, the front side hot pipe P2 is further flowed up in the refrigerant flow direction in the expansion pipe 253 of the rear side hot pipe P4 so as to supply more refrigerant to the front evaporator 240 having a larger capacity. It is preferable to arrange | position to the side.

That is, the refrigerant flowing into the expansion pipe 253 through the second refrigerant flow path R2 in the exterior 252 is relatively more refrigerant into the front high temperature pipe P2 disposed upstream of the refrigerant flow direction. Will be distributed.

As such, even if the diameters of the front high temperature pipe P2 and the rear high temperature pipe P4 connected to the expansion pipe portion 253 of the exterior 252 are equal to each other, the respective pipes P2, According to the arrangement order of P4) it is possible to adjust the flow rate of the refrigerant distributed to each pipe (P2, P4).

On the other hand, since the front high temperature pipe (P2) and the rear high temperature pipe (P4) is connected to be spaced apart from each other in the refrigerant flow direction of the expansion pipe 253, the front high temperature pipe (P2) and the rear side It is preferable that the length L2 of the expansion pipe portion 253 to which the high temperature pipe P4 is connected is larger than the length L1 of the expansion pipe portion 253 to which the front high temperature pipe P1 is connected.

As described above, the present invention installs the rear high temperature pipe P4 so as to be directly connected to the expansion part 253 of the exterior 252 of the double tube internal heat exchanger 250, thereby branching the rear high temperature pipe as in the prior art. The separate connector 30 can be deleted to thereby reduce the number of parts and simplify the manufacturing process, irrespective of the distance between the double tube internal heat exchanger 250 and the front expansion valve 230, piping work Can be easily done.

In addition, by simplifying the route of the rear high-temperature pipe (P4) it can improve the refrigerant flow, reduce the material cost and shorten the work process.

Hereinafter, the operation of the vehicle dual air conditioning apparatus 100 according to the present invention will be described.

First, the high temperature and high pressure gaseous refrigerant compressed and discharged from the compressor 210 is introduced into the condenser 220, and the gaseous refrigerant introduced into the condenser 220 is condensed through heat exchange with external air. After the phase change to the liquid refrigerant, it is introduced into one side expansion portion 253 of the outer appearance 252 of the double-tubular internal heat exchanger (250).

The high temperature and high pressure refrigerant introduced into the expansion part 253 of the exterior 252 flows from the front evaporator 240 and the rear evaporator 320 in the process of flowing the second refrigerant flow path R2 in the exterior 252. After the mutual heat exchange with the low-temperature low-pressure refrigerant flowing through the first refrigerant flow path (R1) in the inner pipe 251, the front high temperature pipe (P2) and the rear high temperature connected to the other expansion pipe portion 253 The pipes P4 are respectively distributed.

Here, the refrigerant distributed into the front high temperature pipe (P2) is introduced into the front expansion valve 230 and expanded under reduced pressure to become a low-temperature low-pressure atomization state is introduced into the front evaporator 240, the front evaporator 240 The refrigerant introduced into e) heat exchanges with the air blown to the front seat side of the vehicle to evaporate and cools the air blown to the front seat side of the vehicle by the endothermic action by the latent heat of evaporation of the refrigerant.

In addition, the refrigerant distributed into the rear high temperature pipe P4 flows into the rear expansion valve 310 and expands under reduced pressure to become a low temperature low pressure atomization state and flows into the rear evaporator 320, and the rear evaporator 320. The refrigerant introduced into the evaporator exchanges heat with the air blown to the rear seat side of the vehicle to evaporate and cools the air blown to the rear seat side of the vehicle by the endothermic action by the latent heat of evaporation of the refrigerant.

Subsequently, the low temperature low pressure gas phase refrigerant discharged after the evaporation from the front evaporator 240 and the low temperature low pressure gas phase refrigerant discharged after the evaporation from the rear evaporator 320 are respectively the front low temperature pipe P3 and the rear low temperature. After joining through the pipe (P5), it passes through the first refrigerant flow path (R1) in the inner tube 251 of the double-tubular internal heat exchanger (250).

At this time, the low-temperature low-pressure gas phase refrigerant passing through the first refrigerant passage R1 in the inner tube 251 of the double-tubular internal heat exchanger 250 has a high temperature and high pressure passing through the second refrigerant passage R2 in the exterior 252. After exchanging heat with the liquid refrigerant, it is again sucked into the compressor 210 to recycle the refrigeration cycle as described above.

100: dual air conditioner 200: front air conditioner
210: compressor 220: condenser
230: front expansion valve 240: front evaporator
250: double tube internal heat exchanger 251: inner tube
252: appearance 253: expansion tube
300: rear air conditioner
310: rear expansion valve 320: rear evaporator
P1, P2: Front high temperature pipe P3: Front low temperature pipe
P4: Rear high temperature pipe P5: Rear low temperature pipe

Claims (12)

A compressor 210 for sucking and compressing refrigerant, a condenser 220 for condensing the refrigerant compressed by the compressor 210, a front expansion valve 230 for throttling the refrigerant condensed in the condenser 220, The front evaporator 240 for evaporating the refrigerant flowing from the front expansion valve 230, the front side low temperature pipe (P3) connecting the front evaporator 240 and the compressor 210 and the condenser 220 and the front It comprises a double pipe type internal heat exchanger 250 for heat-exchanging the refrigerant flowing through each pipe by configuring a specific section of the front high-temperature pipe (P1, P2) connecting the expansion valve 230 to each other, the front of the vehicle Front air conditioning device 200 for cooling the seat;
The rear expansion valve 310 for branching the refrigerant from the condenser 220 to the front expansion valve 230 to the rear high-temperature pipe (P4) to throttle the branched refrigerant, and is introduced from the rear expansion valve (310) And a rear air conditioner (300) configured to join the refrigerant from the front evaporator (240) to the compressor (210) after evaporating the refrigerant; In the air conditioning apparatus,
The rear high-temperature pipe (P4) is connected to one side of the double tube type internal heat exchanger (250) is directly branched vehicle dual air conditioning apparatus, characterized in that formed to be connected to the rear expansion valve (310). The method of claim 1,
The double tube internal heat exchanger 250 includes an inner tube 251 formed in a specific section of the front side cold pipe P3 connecting the front evaporator 240 and the compressor 210, and an outer circumferential surface of the inner tube 251. In addition to the double pipe structure in the expansion pipe portion 253 is formed on both ends, one expansion pipe portion 253 is connected to the front high-temperature pipe (P1) connected to the condenser 220, the other expansion pipe portion 253 to the front It consists of an exterior 252 to which the front high-temperature pipe (P2) connected to the expansion valve 230 is connected,
The rear side high temperature pipe (P4) is connected to the expansion pipe portion 253 of the exterior 252 to which the front side high temperature pipe (P2) connected to the front expansion valve (230) is connected. Device. 3. The method of claim 2,
The front high temperature pipe P2 and the rear high temperature pipe P4 respectively connected to the expansion pipe 253 of the exterior 252 are spaced apart from each other by a predetermined interval in the circumferential direction of the expansion pipe 253. Dual air conditioning apparatus for a vehicle, characterized in that. The method of claim 3, wherein
The front side high temperature pipe P2 is inclined at a predetermined angle θ1 on one side with respect to the vertical center line C of the expansion pipe 253, and the rear side high temperature pipe P4 is at a constant angle θ2 on the other side. The inclined connection, the dual air conditioner for a vehicle, characterized in that for controlling the flow rate of the refrigerant distributed to each pipe (P2, P4) by adjusting the inclination angle of each pipe (P2, P4). The method of claim 4, wherein
The inclination angle θ1 of the front high temperature pipe P2 is smaller than the inclination angle θ2 of the rear high temperature pipe P4. 3. The method of claim 2,
The front high temperature pipe P2 and the rear high temperature pipe P4 respectively connected to the expansion pipe 253 of the exterior 252 are spaced apart from each other at regular intervals in the longitudinal direction of the expansion pipe 253. And adjusting the diameters D1 and D2 of the pipes P2 and P4 to adjust the flow rate of the refrigerant distributed to each pipe P2 and P4. The method according to claim 6,
A diameter D1 of the front side high temperature pipe P2 is larger than a diameter D2 of the rear side high temperature pipe P4. The method according to claim 6,
The length L2 of the expansion pipe 253 to which the front high temperature pipe P2 and the rear high temperature pipe P4 is connected is the length of the expansion pipe 253 to which the front high temperature pipe P1 is connected. Dual air conditioning apparatus for a vehicle, characterized in that greater than (L1). 3. The method of claim 2,
The front high temperature pipe P2 and the rear high temperature pipe P4 respectively connected to the expansion pipe 253 of the exterior 252 are spaced apart from each other by a predetermined distance in the refrigerant flow direction in the expansion pipe 253. The flow rate of the refrigerant distributed to each of the pipes P2 and P4 is adjusted by changing the arrangement order of the respective pipes P2 and P4 connected along the refrigerant flow direction in the expansion pipe 253. Dual air conditioning system for vehicles. The method of claim 9,
And said front side high temperature pipe (P2) is connected to the refrigerant flow direction upstream in said expansion pipe section (253) rather than said rear side high temperature pipe (P4). 3. The method of claim 2,
The double tube internal heat exchanger 250 forms a helical protrusion 251a and a recess 251b in any one of the inner tube 251 and the outer tube 252, and a first inside the inner tube 251. And a second refrigerant passage (R2) is formed between the inner tube (251) and the exterior (252). The method of claim 11,
The first refrigerant flow path R1 is a flow path through which the refrigerant discharged from the front evaporator 240 and the rear evaporator 320 joins and flows.
The second refrigerant passage (R2) is a vehicle dual air conditioning apparatus, characterized in that the flow path for the refrigerant discharged from the condenser 220 flows.

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