KR20120059031A - Air conditioner for vehicle - Google Patents

Abstract

PURPOSE: An air conditioner for an automobile is provided to reduce production cost through applying an expansion valve applied a single evaporator to a double evaporator. CONSTITUTION: An air conditioner for an automobile a compressor(100), a condenser(110), an expansion unit(120), an evaporator(130), and a connector(160). The expansion unit comprises an expansion flow passage(123) for expanding the coolant discharged from the condenser. The evaporator comprises a first evaporating part(131) and a second evaporating part(132). The first evaporating part and the second evaporating part comprise an inlet pipe(131a, 131b) and an outlet pipe(132a, 132b) respectively and flow the evaporated coolant to the compressor. The first evaporating part and the second evaporating part are located to be overlapped in the upstream and downstream of the air from a blower. The connector supplies the expanded and discharged coolant from the expansion unit to the first evaporating part and the second evaporating part respectively through furcating.

Description

Air conditioner for vehicle

The present invention relates to a vehicle air conditioner, and more particularly, to form a structure capable of branching the refrigerant in the connector installed to connect the expansion means (expansion valve) and the evaporator to branch the refrigerant discharged from the expansion means It relates to a vehicle air conditioner to be supplied to each of the first and second evaporator of the evaporator.

The vehicle air conditioner is a vehicle interior that is installed for the purpose of securing the driver's front and rear view by removing the frost from the windshield or heating in the summer or winter, or during the rain or winter season. Such an air conditioning apparatus is usually provided with a heating system and a cooling system at the same time, thereby cooling, heating, or ventilating the interior of a vehicle by selectively introducing outside air or bet, heating or cooling the air, and then blowing the air into the interior of the vehicle.

In general, the refrigeration cycle of such an air conditioning apparatus, as shown in Figure 1, a compressor (Compressor 1) for compressing and sending out the refrigerant, a condenser (Condenser) for condensing the high-pressure refrigerant from the compressor ( 2) an expansion valve 3 for condensing the liquefied refrigerant condensed in the condenser 2, and a low pressure liquid refrigerant condensed by the expansion valve 3 is blown to the vehicle interior. The evaporator 4 or the like that cools the air discharged to the room by the endothermic action of the evaporative latent heat of the refrigerant by evaporating by heat exchange with the air is connected to the refrigerant pipe 5, and the following refrigerant circulation process is performed. Cool the interior of the car through.

When the cooling switch (not shown) of the vehicle air conditioner is turned on, the compressor 1 first drives the engine power and sucks and compresses the low-temperature, low-pressure gaseous refrigerant to the condenser 2 in a high-temperature, high-pressure gas state. The condenser 2 exchanges the gaseous refrigerant with outside air to condense it into a liquid of high temperature and high pressure. Subsequently, the liquid refrigerant discharged from the condenser 2 in the state of high temperature and high pressure is rapidly expanded by the throttling action of the expansion valve 3 and is sent to the evaporator 4 in the low temperature low pressure wet state, and the evaporator 4 is The refrigerant is heat-exchanged with the air blower (not shown) blowing into the vehicle interior. Accordingly, the refrigerant is evaporated from the evaporator 4, discharged into a gas state at low temperature and low pressure, and then sucked back into the compressor 1 to recycle the refrigeration cycle as described above. In the above refrigerant circulation process, the cooling of the vehicle interior is cooled by latent heat of evaporation of the liquid refrigerant circulating in the evaporator 4 while the air blown by the blower (not shown) passes through the evaporator 4 as described above. It is made by discharging the inside of the vehicle in the cold state.

Meanwhile, a receiver dryer (not shown) is provided between the condenser 2 and the expansion valve 3 to separate the refrigerant in the gas phase and the liquid phase, so that only the liquid refrigerant can be supplied to the expansion valve 3. .

However, since the single evaporation system as described above has a limitation in improving the cooling efficiency, as shown in FIG. 2, a dual evaporation system having improved cooling efficiency through double evaporation has been developed.

The dual evaporation system shown in FIG. 2 is configured by arranging two evaporators 4a.4b side by side, wherein the refrigerant is expanded in the course of passing through one expansion valve 3a and is branched and discharged. Are supplied to the evaporators 4a and 4b.

As such, the double evaporation system uses an expansion valve 3a designed for the double evaporation system.

In addition, the dual evaporation system as described above, the first cooling the air through the first evaporator (4a) disposed upstream in the air flow direction, the second evaporator (4b) by cooling the first cooled air again cooling efficiency Will improve.

However, the above-described conventional technique is different in structure of the expansion valve 2 used in the single evaporation system of FIG. 1 and the expansion valve 3a used in the dual evaporation system of FIG. (3a) has to be designed, so there is a problem that it takes a lot of cost and development time,

In particular, since the expansion valve (3) (3a) can not be shared in a single evaporation system and a dual evaporation system, there is a problem that the cost is further increased.

An object of the present invention for solving the above problems is to form a structure capable of branching the refrigerant in the connector installed to connect the expansion means (expansion valve) and the evaporator to branch the refrigerant discharged from the expansion means of the evaporator By supplying to the first and second evaporators, respectively, the expansion valve of a single evaporation system can be applied to the dual evaporation system so that the expansion valve can be shared, thereby reducing the development period and cost, and the refrigerant in the connector. Since the branch structure is formed, it is possible to easily adjust the flow rate of the branched refrigerant and to provide a vehicle air conditioner that can simplify the piping structure.

The present invention for achieving the above object is an expansion having a compressor for sucking and compressing the refrigerant, a condenser for condensing the refrigerant compressed by the compressor, and an expansion passage therein to expand the refrigerant discharged from the condenser Means and a first evaporation unit and a second evaporation unit having inlet and outlet pipes, respectively, for supplying and evaporating the refrigerant expanded and discharged from the expansion unit to be discharged to the compressor, respectively; An evaporator disposed to overlap the upstream and downstream sides in the flow direction of air blown by the additional blower, and installed to connect the expansion means and the evaporator, and branching the refrigerant expanded and discharged from the expansion means to the first, It characterized in that it comprises a connector for supplying each of the two evaporation.

According to the present invention, the expansion is formed by forming a structure (first and second supply passages and branch passages) capable of branching the refrigerant to the first and second evaporators in a connector connecting the single expansion passage of the expansion valve and the inlet pipe of the evaporator. By diverting the refrigerant discharged from the valve to supply to the first and second evaporators of the evaporator, the expansion valve applied to a single evaporation system can be applied to the dual evaporation system, thereby making it possible to use the expansion valve in common. In addition to reducing costs, the development period can be shortened because there is no need to develop expansion valves for each evaporation system.

In addition, a refrigerant branch structure consisting of first and second supply passages and branch passages is formed in the connector to directly couple the inlet and outlet pipes of the expansion valve and the evaporator, thereby simplifying the refrigerant piping structure.

Further, by distributing a relatively large amount of refrigerant flow rate to the first evaporator portion having a large cooling load through the connector, and a relatively low amount of refrigerant flow rate to a second evaporation portion having a small cooling load, thereby improving cooling performance and efficiency. Can be maximized.

Further, after forming a refrigerant branch structure consisting of the first and second supply passages and the branch passage in the connector, by adjusting the diameter of the branch passage or by forming a flow control bar of a predetermined length in the cap, the first and second supply passages The refrigerant flow rate distributed to the (first and second evaporation units) can be easily adjusted.

1 is a configuration diagram showing a refrigeration cycle of a general vehicle air conditioner,
2 is a block diagram showing a conventional double evaporation system,
3 is a block diagram showing an air conditioner for a vehicle according to the present invention;
4 is a view showing a temperature change in the process of passing the air blown through a single blower in the order in the vehicle air conditioner according to the present invention in order,
5 is an exploded perspective view showing an evaporator, a connector, and an expansion valve in a vehicle air conditioner according to the present invention;
6 is a cross-sectional view showing a connector and an expansion valve in a vehicle air conditioner according to the present invention;
Figure 7 is a cross-sectional view showing a case in which the flow rate adjustment bar is formed on the cap of the connector in the vehicle air conditioner according to the present invention.

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

The vehicle air conditioner according to the present invention is configured by connecting the compressor 100-> condenser 110-> expansion means 120-> evaporator 130 to the refrigerant pipe 105, the evaporator 130 It is a dual evaporation system consisting of a first evaporator 131 and a second evaporator 132 separated into two evaporation zones.

The compressor 100 is driven by receiving power from a power supply source (engine or motor, etc.) to suck and compress the gaseous refrigerant discharged from the evaporator 130 and discharge the gaseous refrigerant to a condenser 110 in a gas state of high temperature and high pressure.

The condenser 110 heat-exchanges the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 100 to the outside air to condense it into a liquid of high temperature and high pressure, and discharge the same to the expansion means 120.

The expansion means 120 expands the high temperature and high pressure liquid refrigerant discharged from the condenser 110 to a low temperature low pressure liquid (wet-saturated) state, and then supplies it to the evaporator 130.

The expansion means 120, as shown in Figure 3, is formed by installing a single expansion valve 121 on the refrigerant pipe 105 for connecting the condenser 110 and the evaporator 130.

As shown in FIG. 6, the expansion valve 121 has an expansion passage 123 having an orifice 123a formed therein to expand the refrigerant supplied from the condenser 110, and the discharge valve 121 is discharged from the evaporator 130. A main body 122 having a connection passage 124 formed to supply the refrigerant to the compressor 100, a valve 125 for controlling a flow rate of the refrigerant passing through the orifice 123a of the expansion passage 123, and It consists of a shaft 127 for moving the valve 125 while moving up and down by the diaphragm 126 is displaced according to the temperature change of the refrigerant flowing in the connection passage 124.

Therefore, the diaphragm 126 is displaced in the up and down directions according to the refrigerant temperature discharged from the evaporator 130 and flows in the connection passage 124, and the shaft 127 interlocking with the diaphragm 126 is moved. The refrigerant supplied to the evaporator 130 through the expansion passage 123 by adjusting the opening degree of the orifice 123a of the expansion passage 123 by moving the valve 125 while moving up and down inside the main body 122. The flow rate will be adjusted.

As such, the expansion valve 121 is installed between the condenser 110 and the evaporator 130 to expand the condensed refrigerant so that the refrigerant can be rapidly evaporated in the evaporator 130, the expanded refrigerant is evaporator 130 ) Serves to control the flow rate of the refrigerant supplied to the evaporator 130 to be evaporated while maintaining the appropriate superheat degree.

On the other hand, a receiver dryer (not shown) is installed between the condenser 110 and the expansion means 120 to separate the refrigerant between the gas phase and the liquid phase so that only the liquid refrigerant can be supplied to the expansion means 120. desirable.

The evaporator 130 receives inlet and outlet pipes 131a and 131b and 132a and 132b so that the evaporator 130 receives and evaporates the refrigerant discharged and expanded from the expansion valve 121 and then discharges the refrigerant to the compressor 100. It is configured to include a first evaporation unit 131 and a second evaporation unit 132 having a.

Therefore, by receiving the expansion refrigerant from the expansion valve 121 to heat exchange with the air blown to the vehicle interior side through a single blower 140 to evaporate to cool the air discharged to the vehicle interior by the endothermic action by the latent heat of evaporation of the refrigerant do.

In addition, the first and second evaporators 131 and 132 preferably separate the single evaporator 130 into two evaporation regions to form the first evaporator 131 and the second evaporator 132.

In addition, the first evaporator 131 and the second evaporator 132 may be cooled in a process in which air blown by a single blower 140 sequentially passes through the first and second evaporators 131 and 132. It is arranged to overlap on the upstream and downstream sides in the flow direction of the air.

The evaporator 130, the first and second tanks 133 and 135, which are arranged side by side at a predetermined interval apart from each other, and the internal space is divided by partition walls 134 and 136, respectively,

The first and second tanks 133 and 135 are connected to each other, and the divided space in the first tank 133 and the divided space in the second tank 135 communicate with each other upstream in the air flow direction. A plurality of tubes 137 and 138 constituting the first evaporation section 131 and the second evaporation section 132;

An inlet pipe 131a and an outlet pipe 131b formed at both ends of the first tank 133 or the second tank 135 on the first evaporation unit 131;

An inlet pipe 131a and an outlet pipe 131b formed at both ends of the first tank 133 or the second tank 135 on the second evaporation part 132;

It is made of a heat radiation fin (not shown) interposed between the plurality of tubes (138).

The first evaporator 131 side tubes 137 and the second evaporator 132 side tubes 138 installed on the upstream and downstream sides of the air flow direction may be integrally formed or separated from each other. It may be formed in the form.

Meanwhile, in the drawing, the inlet and outlet pipes 131a and 131b of the first evaporator 131 are connected to both ends of the first tank 133 on the first evaporator 131 and the second evaporator The inlet and outlet pipes 132a and 132b of 132 are connected to both ends of the first tank 133 on the second evaporation unit 132 side.

At this time, the inlet pipe 131a of the first evaporator 131 and the inlet pipe 132a of the second evaporator 132 are connected to opposite directions of the first tank 133, thereby expanding the expansion valve ( After the refrigerant discharged from 121 is branched through the first and second supply passages 162 and 163 of the connector 160 to be described below, the first evaporator 131 and the second evaporator 132 are replaced. They will flow in opposite directions.

In addition, the inlet pipe 131a of the first evaporator 131 and the inlet pipe 132a of the second evaporator 132 connect the first and second supply passages 162 and 163 of the connector 160. It is connected to the expansion passage 123 of the expansion valve 121, the outlet pipe 131b of the first evaporator 131 and the outlet pipe 132b of the second evaporator 132 is joined at the end. It is formed to be connected to the connection passage 124 of the expansion valve 121 through the outlet passage 166 of the connector 160.

In addition, a baffle 139 is installed in the first tank 133 or the second tank 135, and the baffle 139 is a refrigerant flow direction of the internal spaces of the first and second tanks 133 and 135. Will be partitioned into. Therefore, the refrigerant flowing through the inlet pipes 131a and 132a of the first and second evaporators 131 and 132 flows the evaporators in a zigzag form by the baffle 139, and then the outlet pipe 131b. Is discharged through 132b.

Meanwhile, the refrigerant discharged from each of the outlet pipes 131b and 132b of the first and second evaporators 131 and 132 is joined again, and then the outlet passage 166 and the expansion valve 121 of the connector 160 are combined. The compressor flows into the compressor 100 through a connection passage 124.

In addition, in the present invention, the expansion means 120 and the evaporator 130 are installed to be connected to each other, and the branched refrigerant discharged from the expansion means 120 is branched to the first and second evaporators 131 and 132, respectively. The connector 160 for supplying is provided.

That is, the connector 160 connects the inlet pipes 131a and 132a of the expansion valve 121 to the single expansion passage 123 and the first and second evaporation parts 131 and 132 and the expansion valve ( The connection passage 124 of 121 and the outlet pipes 131b and 132b of the first and second evaporation parts 131 and 132 are connected.

The connector 160, one side is coupled to the expansion valve 121 and the other side is connected to each of the inlet and outlet pipes (131a, 131b) (132a, 132b) of the first and second evaporation parts (131, 132) Body 161 is combined,

A first supply passage formed to penetrate both sides of the body 161 to connect the single expansion passage 123 of the expansion valve 121 and the inlet pipe 131a of the first evaporator 131 to communicate with each other; 162),

A second supply passage 163 formed in the body 161 so as to be spaced apart from the first supply passage 162 at a predetermined interval and connected to the inlet pipe 132a of the second evaporator 132;

The refrigerant flowing in the first supply channel 162 is formed to connect the first supply channel 162 and the second supply channel 163 to the second supply channel 163 in the body 161. It includes a branch flow path 164 for branching a certain amount.

Here, the branch flow path 164 is drilled vertically at a predetermined depth from one end (lower end) of the body 161 to penetrate the first supply channel 162 and the second supply channel 163, thereby providing a first The supply passage 162 and the second supply passage 163 are connected in communication with each other.

At this time, the open one end (lower end) of the branch flow path 164 is closed by coupling the cap 165.

In addition, the body 161 is formed so as to penetrate both sides of the body 161 spaced apart from the first supply passage 162 by a predetermined interval, and each of the outlet pipes of the first and second evaporators 131 and 132 ( An outlet passage 166 is formed to be connected in a state in which 131b and 132b are joined.

In addition, one side of the first supply passage 162 of the body 161 and one side of the outlet passage 166 are formed with connection portions 162a and 166a to protrude from the expansion passage 123 of the expansion valve 121. It is inserted into and coupled to one side of the connection flow path 124.

The inlet pipes 131a and 132a of the first and second evaporation parts 131 and 132 are inserted into and coupled to the first and second supply passages 162 and 163 of the body 161, respectively. Each of the outlet pipes 131b and 132b of the two evaporation parts 131 and 132 is formed so that the end portions are joined to each other, and are inserted into and coupled to the outlet passage 166 of the body 161.

In addition, the first supply passage 162 is formed concentrically with the outlet of the expansion passage 123, the second supply passage 163 is spaced apart a predetermined interval below the first supply passage 162 It is formed in parallel, the branch passage 164 is formed at a right angle with respect to the first and second supply passages (162, 163).

In addition, the outlet passage 166 is formed in parallel to be spaced apart by a predetermined interval to the upper side of the first supply passage 162.

As such, the present invention provides the first and second evaporation parts to the connector 160 connecting the single expansion passage 123 of the expansion valve 121 to the inlet pipes 131a and 132a of the evaporator 130. The first and second supply passages 162 and 163 and the branch passage 164 are formed to branch the refrigerant to the 131 and 132 to branch the refrigerant discharged from the expansion valve 121 to the evaporator. By supplying to the first and second evaporators 131 and 132 of 130, respectively, the expansion valve 121 applied to a single evaporation system can be applied to the dual evaporation system, and the expansion valve 121 can be shared. Due to this, as well as the cost is reduced, there is no need to develop an expansion valve 121 for each evaporation system, thereby reducing the development period.

In addition, a refrigerant branch structure including first and second supply passages 162 and 163 and branch passages 164 is formed in the connector 160 to allow inlet and outlet pipes of the expansion valve 121 and the evaporator 130. By directly coupling the 131a and 131b and the 132a and 132b, the structure of the refrigerant pipe 105 can be simplified.

On the other hand, the air blown through the single blower 140 is sequentially passed through the first evaporator 131 and the second evaporator 132, in this case, a single blower in the air conditioning case 150 Since the hot air flows into the first evaporator 131 on the upstream side in the flow direction of the air blown by the 140, the refrigerant load is relatively large, and the second evaporator 132 on the downstream side Since the first cooled air is introduced from the first evaporator 131, the cooling load is relatively small.

That is, as shown in FIG. 4, the air before blowing from the single blower 140 and passing through the first evaporator 131 is a high temperature, and the air cooled primarily while passing through the first evaporator 131 is a medium temperature. The air cooled again while passing through the second evaporation unit 132 is changed to low temperature.

Therefore, in consideration of the characteristic that the cooling loads applied to the first and second evaporators 131 and 132 are sequentially reduced in the order that the air blown from the single blower 140 passes, the first disposed upstream in the air flow direction. Preferably, the evaporator 131 is distributed with a relatively larger amount of refrigerant than the second evaporator 132 disposed downstream.

That is, a relatively large amount of refrigerant flow rate is allocated to the first evaporation part 131 that receives a large cooling load, and a relatively low amount of refrigerant flow rate is distributed to a second evaporation part 132 that takes a small cooling load.

In the present invention, the first supply passage 162 of the connector 160 is formed concentric with the outlet of the expansion passage 123 of the expansion valve 121, the second supply passage 163 is a branch passage 164 Since the branch is formed from the first supply passage 162 through), the pressure is increased in the second supply passage 163, which is bent at a right angle than the straight first supply passage 162, causing a loss.

Accordingly, the refrigerant flow rate is increased in the first supply passage 162 of the connector 160, and the refrigerant flow rate is relatively decreased in the second supply passage 163, so that the first supply passage 162 is connected to the first supply passage 162. A relatively high refrigerant flow rate is supplied to the evaporator 131, and a relatively low refrigerant flow rate is supplied to the second evaporator 132 connected to the second supply passage 163.

In this way, a relatively large flow rate of the refrigerant is distributed to the first evaporator 131 that receives a large cooling load through the connector 160 and a relatively low refrigerant flow rate to the second evaporator 132 that takes a smaller cooling load. By distributing, it is possible to maximize the cooling performance and efficiency improvement.

In addition, when the diameter of the branch passage 164 of the connector 160 is adjusted according to the cooling load of the first and second evaporators 131 and 132, the first and second supply passages 162 and 163 are supplied through the first and second supply passages 162 and 163. The flow rate distribution of the refrigerant can be easily adjusted.

That is, when the diameter of the branch flow path 164 of the connector 160 is formed to be the same as the minimum diameter in the first and second supply flow paths 162 and 163, the second supply flow path 163 is bent at a right angle. The refrigerant distribution becomes relatively small,

When the diameter of the branch passage 164 of the connector 160 is smaller than the minimum diameter in the first and second supply passages 162 and 163, the refrigerant is distributed to the second supply passage 163 which is bent at a right angle. Will be even less,

When the diameter of the branch passage 164 of the connector 160 is formed to be larger than the minimum diameter in the first and second supply passages 162 and 163, the refrigerant of the first and second supply passages 162 and 163 is formed. The distribution may be the same, or the distribution of the refrigerant to the second supply passage 163 may be increased.

In the present invention, since the cooling load is relatively large on the first evaporator 131 and the cooling load is relatively small on the second evaporator 132, the diameter of the branch passage 164 is the first supply passage. Formed to be equal to or smaller than the minimum diameter of 162, it is preferable to supply a relatively large amount of refrigerant to the first evaporator 131 and to supply a relatively small amount of refrigerant to the second evaporator 132. Do.

In addition, as another method for adjusting the refrigerant flow rate distribution supplied to the first and second supply passages 162 and 163 of the connector 160, as illustrated in FIG. 7, the lower portion of the branch passage 164 is opened. The flow rate adjusting bar 165a is inserted into the branch flow path 164 by a predetermined length so that the refrigerant flow rate supplied to the second supply flow path 163 through the branch flow path 164 is coupled to the cap 165 coupled to the valve 165. ) May be formed.

At this time, the end portion of the flow control bar 165a which is formed to protrude a predetermined length on the upper side of the cap 165 extends to a position overlapping with the second supply passage 163 and is supplied to the second supply passage 163. By adjusting the cross-sectional area of the portion of the branch passage 164 that directly affects the flow rate, the refrigerant flow rate distribution supplied to the first and second supply passages 162 and 163 can be easily adjusted.

That is, when the cross-sectional area of the branch passage 164 connected to the inlet side of the second supply passage 163 through the flow control bar 165a of the cap 165 is reduced, the second supply passage 163 is reduced. Refrigerant flow rate to be supplied is reduced so that a relatively large refrigerant flow rate is allocated to the first supply passage 162, a relatively small refrigerant flow rate is distributed to the second supply passage (163).

On the other hand, if the flow control bar 165a is produced in advance by length, the flow rate distribution of the first and second supply passages 162 and 163 can be easily adjusted by simply replacing the cap 165.

As such, after forming the refrigerant branch structure including the first and second supply passages 162 and 163 and the branch passage 164 in the connector 160, the diameter of the branch passage 164 is adjusted or the cap is formed. By forming the flow rate adjustment bar 165a of a predetermined length in 165, the flow rate of the refrigerant distributed to the first and second supply passages 162 and 163 can be easily adjusted, and the piping structure can be simplified.

Hereinafter, the operation of the air conditioner for a vehicle according to the present invention will be described.

First, the high temperature and high pressure gaseous refrigerant compressed by the compressor 100 flows into the condenser 110.

The gaseous refrigerant introduced into the condenser 110 is condensed through heat exchange with external air, phase changes into a liquid refrigerant of high temperature and high pressure, and then flows into the expansion passage 123 of the expansion valve 121.

After the refrigerant flowing into the expansion passage 123 of the expansion valve 121 is expanded under reduced pressure in the course of passing through the expansion passage 123 to become a liquid refrigerant having a low temperature and low pressure, the first supply passage of the connector 160 ( 162).

When the refrigerant flows into the first supply passage 162 of the connector 160, a part of the refrigerant passes through the first supply passage 162 and then the first evaporation through the inlet pipe 131a of the first evaporator 131. It is supplied to the part 131, and a part passes through the branch passage 164 and the second supply passage 163 to the second evaporator 132 through the inlet pipe 132a of the second evaporator 132 side. Supplied.

In this case, the first and second evaporation parts 131 and 132 may be adjusted by adjusting the diameter of the branch flow passage 164 or adjusting the flow path cross-sectional area of the branch flow passage 164 by adjusting the length of the flow control bar 165a of the cap 165. The amount of distribution of the refrigerant supplied to the can be adjusted.

In the present invention, a relatively large refrigerant flow rate is allocated to the first evaporator 131 which takes a lot of cooling load, and a relatively small refrigerant flow rate is allocated to the second evaporator 132 that takes a small cooling load.

Subsequently, the low-temperature low-pressure liquid refrigerant supplied to the first and second evaporation parts 131 and 132 through the respective inlet pipes 131a and 132a formed in the opposite directions of the first and second evaporation parts 131 and 132 may include: , 2 evaporation parts (131, 132) to flow in the opposite direction, at this time, the tube 137, 138 of the first and second evaporation parts (131, 132) through a single blower 140 in the process of zigzag flow The heat exchanged with the air blown to the interior of the vehicle evaporates, and at the same time, the endothermic action of the refrigerant evaporates to cool the air blown into the vehicle interior.

The refrigerant evaporated while the first and second evaporators 131 and 132 flow in opposite directions to each other while being discharged through each of the outlet pipes 131b and 132b and then to the outlet passage 166 of the connector 160. Inflow,

Thereafter, the refrigerating cycle as described above is recycled while flowing into the compressor 100 through the connection passage 124 of the expansion valve 121.

100: compressor 110: condenser
120: expansion means 121: expansion valve
123: expansion passage 124: connection passage
130: evaporator 131: first evaporator
131a and 132a: inlet pipe 131b and 132b: outlet pipe
132: second evaporator 133: the first tank
134, 136: bulkhead 135: second tank
137,138: tube 139: baffle
140: blower 150: air conditioning case
160: connector 161: body
162: first supply channel 163: second supply channel
164: branching euro 165: cap
165a: flow control bar 166: outlet flow path

Claims (8)

Compressor 100 for sucking and compressing the refrigerant,
A condenser 110 for condensing the refrigerant compressed by the compressor 100,
Expansion means (120) having an expansion passage (123) therein to expand the refrigerant discharged from the condenser (110);
A first evaporation unit having inlet and outlet pipes 131a and 131b and 132a and 132b to be respectively supplied with the refrigerant discharged and expanded from the expansion means 120 and then evaporated and then discharged to the compressor 100. 131 and a second evaporator 132, the evaporator 130 is disposed so that the first, second evaporator 131, 132 overlaps the upstream, downstream side in the flow direction of air blown by the blower 140 )Wow,
The connector 160 is installed to connect the expansion means 120 and the evaporator 130, and branches the refrigerant expanded and discharged from the expansion means 120 to supply the first and second evaporators 131 and 132, respectively. Vehicle air conditioning apparatus comprising a. The method of claim 1,
The connector 160,
One side is coupled to the expansion means 120 and the other side is the body 161 is coupled to each of the inlet, outlet pipes (131a, 131b) (132a, 132b) of the first and second evaporation (131,132),
The first supply passage 162 is formed to penetrate both sides of the body 161 to connect the expansion passage 123 of the expansion means 120 and the inlet pipe 131a of the first evaporator 131 in communication. )Wow,
A second supply passage 163 formed in the body 161 so as to be spaced apart from the first supply passage 162 at a predetermined interval and connected to the inlet pipe 132a of the second evaporator 132;
The refrigerant flowing in the first supply channel 162 is formed to connect the first supply channel 162 and the second supply channel 163 to the second supply channel 163 in the body 161. A vehicle air conditioning apparatus comprising a branch passage 164 for branching a predetermined amount. The method of claim 2,
The branch flow path 164 is formed by drilling at one end of the body 161 to connect the first supply flow path 162 and the second supply flow path 163, the open one end cap 165 Vehicle air conditioner, characterized in that closed by. The method of claim 2,
The body 161 is formed to penetrate both sides of the body 161 by being spaced apart from the first supply passage 162 by a predetermined interval and each outlet pipe 131b of the first and second evaporation parts 131 and 132. The vehicle air conditioner, characterized in that the outlet passage 166 is formed to be connected in a joined state (132b). The method of claim 2,
The first supply passage 162 is formed concentric with the outlet of the expansion passage 123,
The second supply passage 163 is formed parallel to the lower side of the first supply passage 162 spaced apart at a predetermined interval,
The branch passage 164 is a vehicle air conditioning apparatus, characterized in that formed at right angles to the first, second supply passage (162, 163). The method of claim 2,
The diameter of the branch passage 164 is formed to be the same as or smaller than the minimum diameter of the first supply passage 162, the second evaporation portion 132 to take a smaller cooling load of the first, second evaporation portion (131, 132) Vehicle air conditioning apparatus characterized in that the relatively small amount of refrigerant to be distributed and supplied. The method of claim 3, wherein
The cap 165 is provided with a flow control bar 165a inserted into the branch passage 164 by a predetermined length so as to vary the refrigerant flow rate supplied to the second supply passage 163 through the branch passage 164. And a relatively small amount of refrigerant is distributed and supplied to the second evaporator 132 in which the cooling load is small among the first and second evaporators 131 and 132. The method of claim 1,
The evaporator 130,
The first and second tanks 133 and 135, which are arranged side by side at a predetermined interval apart from each other, and whose internal space is divided by the partition walls 134 and 136, respectively,
The first and second tanks 133 and 135 are connected to each other, and the divided space in the first tank 133 and the divided space in the second tank 135 communicate with each other upstream in the air flow direction. A plurality of tubes 137 and 138 constituting the first evaporation unit 131 and the second evaporation unit 132 on the downstream side;
The inlet pipe 131a and the outlet pipe 131b formed at both ends of the first tank 133 or the second tank 135 on the first evaporation unit 131;
A vehicle air conditioning apparatus comprising the inlet pipe 132a and the outlet pipe 132b formed at both ends of the first tank 133 or the second tank 135 on the second evaporation unit 132 side. .

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