CONDENSER FOR VEHICLE

Abstract

A condenser for a vehicle is used in an air conditioning having an expansion valve, an evaporator, and a compressor, is provided between the compressor and the expansion valve, and circulates coolant supplied from a radiator so as to condense refrigerant supplied from the compressor through heat-exchange with the coolant and the refrigerant. The condenser may include a main heat-radiating portion connected to the radiator to circulate coolant, and adapted to circulate refrigerant from the compressor to condense the refrigerant through heat-exchange with the coolant, a receiver-drier portion integrally formed with the main heat-radiating portion to receive the condensed refrigerant perform gas-liquid separation and moisture removal of the refrigerant, and an overcooling heat-radiating portion circulating low temperature and low pressure gas refrigerant supplied from the evaporator, and overcooling the refrigerant supplied from the receiver-drier portion through heat-exchange with the low temperature and low pressure gas refrigerant.

Description

CROSS-REFERENCE TO RELATED APPLICATION

The present application claims priority of Korean Patent Application Number 10-2011-0131299 filed Dec. 8, 2011, the entire contents of which application is incorporated herein for all purposes by this reference.

BACKGROUND OF INVENTION

1. Field of Invention

The present invention relates to a condenser for a vehicle. More particularly, the present invention relates to a condenser for a vehicle that is stacked-plate type in which a receiver-drier is integrally formed and that is water-cooled type in which a refrigerant is condensed by using a coolant.

2. Description of Related Art

Generally, an air conditioning for a vehicle maintains suitable cabin temperature regardless of ambient temperature and realizes comfortable indoor environment.

Such an air conditioning includes a compressor compressing a refrigerant, a condenser condensing and liquefying the refrigerant compressed by the compressor, an expansion valve quickly expanding the refrigerant condensed and liquefied by the condenser, and an evaporator evaporating the refrigerant expanded by the expansion valve and cooling air which is supplied to the cabin in which the air conditioning is installed by using evaporation latent heat.

Herein, the condenser cools compressed gas refrigerant of high temperature/pressure by using an outside air flowing into the vehicle when running and condenses it into liquid refrigerant of low temperature.

Such a condenser is generally connected through a pipe to a receiver-drier which is provided for improving condensing efficiency through gas-liquid separation and removing moisture in the refrigerant.

An air-cooled condenser which heat-exchanges with the outside air is mainly used for the condenser for the vehicle. Since such an air-cooled condenser has pin-tube structures, entire size of the condenser may be increased so as to improve cooling performance. Therefore, the air-cooled condenser may be hard to be installed in a small engine compartment.

In order to solve such a problem, a water-cooled condenser which uses coolant as refrigerant is applied to the vehicle.

However, the water-cooled condenser, compared with the air-cooled condenser, has lower condensing temperature of the refrigerant by about 5-15° C., and accordingly difference between the condensing temperature and the ambient temperature is small. Therefore, condensing efficiency may be deteriorated due to small sub-cool effect, and accordingly cooling efficiency may also be deteriorated.

In addition, size of a radiator or capacity of a cooling fan may be increased so as to increase condensing efficiency or cooling efficiency of the water-cooled condenser for the vehicle. Therefore, cost and weight may increase and connections between the receiver-drier and the condenser may be complex.

The above information disclosed in this Background section is only for enhancement of understanding of the background of the invention and therefore it may contain information that does not form the prior art that is already known in this country to a person of ordinary skill in the art.

The information disclosed in this Background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.

SUMMARY OF INVENTION

Various aspects of the present invention provide for a condenser for a vehicle having advantages of being integrally formed with a receiver-drier and stacking a plurality of plates.

According to the condenser for the vehicle, dead volume of the receiver-drier may be minimized and heat-radiating area may be increased. Therefore, cooling efficiency may be improved.

In addition, the condenser separates refrigerant into gas refrigerant and liquid refrigerant and condenses the gas refrigerant and the liquid refrigerant by using coolant, and the condensed refrigerant is overcooled by low temperature and low pressure gas refrigerant supplied from an evaporator through heat-exchange therebetween. Since additional components for overcooling the condensed refrigerant can be omitted, the number of components may be reduced, connections may be simplified, and cost and weight may be reduced.

Various aspects of the present invention provide for a condenser for a vehicle used in an air conditioning having an expansion valve, an evaporator, and a compressor, is provided between the compressor and the expansion valve, and circulates coolant supplied from a radiator so as to condense refrigerant supplied from the compressor through heat-exchange with the coolant and the refrigerant.

The condenser may include a main heat-radiating portion formed by stacking a plurality of plates, connected to the radiator so as to circulate the coolant, and adapted to circulate the refrigerant supplied from the compressor so as to condense the refrigerant through heat-exchange with the coolant and the refrigerant, a receiver-drier portion integrally formed with the main heat-radiating portion so as to receive the condensed refrigerant from the main heat-radiating portion and to perform gas-liquid separation and moisture removal of the refrigerant, and connected to the main heat-radiating portion, and an overcooling heat-radiating portion integrally formed at a lower portion of the main heat-radiating portion, circulating low temperature and low pressure gas refrigerant supplied from the evaporator, and overcooling the refrigerant supplied from the receiver-drier portion through heat-exchange with the low temperature and low pressure gas refrigerant.

The main heat-radiating portion may include a first refrigerant line formed at a middle portion in the main heat-radiating portion along a length direction, the refrigerant flowing into an end portion of the main heat-radiating portion passing through the first refrigerant line, a gas-liquid separating portion formed at the other end portion in the main heat-radiating portion, connected to the first refrigerant line, and adapted to separate the refrigerant flowing therein through the first refrigerant line into gas refrigerant and liquid refrigerant, at least one second refrigerant line formed above the first refrigerant line so as for the light gas refrigerant separated at the gas-liquid separating portion to flow therein, and at least one third refrigerant line formed below the first refrigerant line so as for the heavy liquid refrigerant separated at the gas-liquid separating portion to flow therein.

The gas-liquid separating portion may be connected to the second and third refrigerant lines close to an upper portion and a lower portion of the gas-liquid separating portion among the second and third refrigerant lines, and may not be connected to the other second and third refrigerant lines by the plates.

The main heat-radiating portion may cause the coolant and the refrigerant to exchange heat with each other by means of counterflow of the coolant and the refrigerant.

The main heat-radiating portion may further include a first connecting line formed at an upper portion of the main heat-radiating portion so as to be connected with the second refrigerant line, and a second connecting line formed at a lower portion of the main heat-radiating portion so as to be connected with the third refrigerant line, wherein the main heat-radiating portion supplies the condensed refrigerant to the receiver-drier portion through the first connecting line and the second connecting line.

The overcooling heat-radiating portion may cause the low temperature and low pressure gas refrigerant and the refrigerant supplied from the receiver-drier portion to exchange heat with each other by means of counterflow of the low temperature and low pressure gas refrigerant and the refrigerant.

The overcooling heat-radiating portion may be connected to the receiver-drier portion through a third connecting line, and the refrigerant in which gas-liquid separation and moisture removal is performed at the receiver-drier portion may flow into the overcooling heat-radiating portion through the third connecting line.

The overcooling heat-radiating portion may include a refrigerant line in which the refrigerant supplied from the receiver-drier portion through the third connecting line flows, and a gas refrigerant line formed alternately with the refrigerant line, the low temperature and low pressure gas refrigerant supplied from the evaporator flowing in the gas refrigerant line, wherein the overcooling heat-radiating portion is adapted to overcool the condensed refrigerant flowing in the refrigerant line through heat-exchange with the gas refrigerant flowing in the gas refrigerant line.

A heat-isolating portion for preventing heat-exchange with the refrigerant passing through the main heat-radiating portion and the overcooled refrigerant passing through the overcooling heat-radiating portion may be formed between the main heat-radiating portion and the overcooling heat-radiating portion.

The heat-isolating portion may receive nitrogen therein easily through a plurality of brazing holes formed along a length direction thereof between the main heat-radiating portion and the overcooling heat-radiating portion in a case of welding.

The condenser may further include an upper and lower covers mounted respectively on an upper surface and a lower surface of the main heat-radiating portion, the receiver-drier portion and the overcooling heat-radiating portion.

The upper cover may be provided with a coolant outlet formed at an end portion thereof and adapted to discharge the coolant from the main heat-radiating portion, a coolant inlet formed at the other end portion thereof and connected to the radiator so as to receive the coolant from the radiator, and a refrigerant inlet formed at the end portion thereof and connected to the compressor so as to receive the refrigerant from the compressor.

The lower cover may be provided with a refrigerant outlet formed at the end portion thereof corresponding to the refrigerant inlet and connected to the expansion valve, a gas refrigerant inlet formed at the end portion thereof and connected to the evaporator, and a gas refrigerant outlet formed at the other end portion thereof and connected to the compressor.

An end portion of the plates forming the second refrigerant line may be bent so as to form a wall.

The third refrigerant line may not be directly communicated with the coolant inlet by the top plate among the plates forming the third refrigerant line.

The receiver-drier portion may be provided with a space formed therein, and an insertion hole may be formed at the lower cover corresponding to the space.

A desiccant may be inserted in the space through the insertion hole.

A fixing cap for preventing escape of the desiccant inserted in the space and for preventing leakage of the refrigerant supplied to the receiver-drier portion may be mounted at the insertion hole.

The radiator may be connected to a reserve tank and a cooling fan may be provided at a rear portion of the radiator.

The condenser may further include a heat exchanger formed by stacking a plurality of plates.

The methods and apparatuses of the present invention have other features and advantages which will be apparent from or are set forth in more detail in the accompanying drawings, which are incorporated herein, and the following Detailed Description, which together serve to explain certain principles of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of an exemplary air conditioning of a vehicle to including an exemplary condenser according to the present invention.

FIG. 2 is a perspective view of an exemplary condenser for a vehicle according to the present invention.

FIG. 3 is a cross-sectional view taken along a line A-A in FIG. 2.

FIG. 4 is a cross-sectional view taken along a line B-B in FIG. 2.

DETAILED DESCRIPTION

Reference will now be made in detail to various embodiments of the present invention(s), examples of which are illustrated in the accompanying drawings and described below. While the invention(s) will be described in conjunction with exemplary embodiments, it will be understood that present description is not intended to limit the invention(s) to those exemplary embodiments. On the contrary, the invention(s) is/are intended to cover not only the exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the invention as defined by the appended claims.

Exemplary embodiments and drawings disclosed in this specification represent only a few exemplary embodiments of the present invention and do not represent all the spirit of the present invention. So, it is to be understood that various equivalents and variation can exist at the filing date of the present application.

FIG. 1 is a schematic diagram of an air conditioning of a vehicle to which a condenser according to various embodiments of the present invention is applied; FIG. 2 is a perspective view of a condenser for a vehicle according to various embodiments of the present invention; FIG. 3 is a cross-sectional view taken along a line A-A in FIG. 2; and FIG. 4 is a cross-sectional view taken along a line B-B in FIG. 2.

Referring to the drawings, a condenser 100 for a vehicle according to various embodiments of the present invention is used in an air conditioning which includes an expansion valve 101 for expanding a liquid refrigerant, an evaporator 103 for evaporating the refrigerant expanded by the expansion valve 101 through heat-exchange with an air, and a compressor 105 for receiving from the evaporator 103 and compressing a gaseous refrigerant.

That is, the condenser 100 is provided between the compressor 105 and the expansion valve 101, and is configured to circulate a coolant supplied from a radiator 107 and to condense the refrigerant supplied from the compressor 105 through heat-exchange with the coolant.

The radiator 107 is connected to a reserve tank 108, and a cooling fan 109 is provided at a rear portion of the radiator 107.

In the condenser 100 for the vehicle according to various embodiments of the present invention, a receiver-drier is integrally provided and a plurality of plates is stacked. The condenser 100 for the vehicle separates the refrigerant into and condenses gas refrigerant and liquid refrigerant by using the coolant, and overcools the condensed refrigerant through heat-exchange with low temperature and low pressure gas refrigerant supplied from the evaporator 103. Since additional components for overcooling the condensed refrigerant can be omitted, the number of components may be reduced, connections may be simplified, and cost and weight may be reduced. In addition, since dead volume of the receiver-drier can be minimized and heat-radiating area may be increased, cooling efficiency may be improved according to the condenser 100 for the vehicle.

For these purposes, the condenser 100 for the vehicle according to various embodiments of the present invention, as shown in FIG. 2 to FIG. 4, includes a main heat-radiating portion 110, a receiver-drier portion 130 and a overcooling heat-radiating portion 140, and these components will be described in detail.

Herein, an upper cover 111 and a lower cover 113 are mounted respectively at upper and lower portions of the condenser 100 for the vehicle, and the main heat-radiating portion 110, the receiver-drier portion 130 and the overcooling heat-radiating portion 140 are disposed between the upper and lower covers 111 and 113.

The main heat-radiating portion 110 is formed by stacking a plurality of plates 115.

The main heat-radiating portion 110 is connected to the radiator 107 so as to circulate the coolant, and circulates the refrigerant supplied from the compressor 105 so as to condense the refrigerant through heat-exchange with the coolant.

Herein, the main heat-radiating portion 110 is adapted to perform heat-exchange by means of counterflow of the coolant and the refrigerant.

That is, the plurality of plates 115 is stacked in the main heat-radiating portion 110 refrigerant lines 117 and coolant lines 119 are alternately formed between the plurality of plates 115. Since the refrigerant passes through the refrigerant line 117 and the coolant passes through the coolant line 119, the refrigerant and the coolant are not mixed with each other and flow to opposite directions, as shown in FIG. 3 and FIG. 4. At this process, heat-exchange of the refrigerant and the coolant occurs.

The main heat-radiating portion 110, as shown in FIG. 3, includes a first refrigerant line 117a, a second refrigerant line 117b, a third refrigerant line 117c and a gas-liquid separating portion 118.

The plurality of the first refrigerant lines 117a is formed at a middle portion in the main heat-radiating portion 110 along a length direction. The refrigerant supplied to an end portion of the main heat-radiating portion 110 flows in the first refrigerant line 117a.

The gas-liquid separating portion 118 is formed at the other end portion in the main heat-radiating portion 110 and is connected to the first refrigerant line 117a. The gas-liquid separating portion 118 is adapted to separate the refrigerant flowing in the first refrigerant line 117a into the gas refrigerant and the liquid refrigerant by gravity.

If the refrigerant in which the gas refrigerant and the liquid refrigerant are mixed flows into the gas-liquid separating portion 118, the gas-liquid separating portion 118 separates the refrigerant into the gas refrigerant and the liquid refrigerant by gravity difference between the gas refrigerant and the liquid refrigerant. At this time, the light gas refrigerant is positioned at an upper portion of the gas-liquid separating portion 118 and the heavy liquid refrigerant is positioned at a lower portion of the gas-liquid separating portion 118.

According to various embodiments, a plurality of the second refrigerant lines 117b is formed above the first refrigerant line 117a. The light gas refrigerant separated at the gas-liquid separating portion 118 flows in the second refrigerant line 117b.

The second refrigerant line 117b, when the gas refrigerant separated at the gas-liquid separating portion 118 flows therein, is adapted to perform heat-exchange with the gas refrigerant and the coolant so as to condense the gas refrigerant again.

In addition, a plurality of third refrigerant lines 117c is formed below the first refrigerant line 117a. The heavy liquid refrigerant separated at the gas-liquid separating portion 118 flows in the third refrigerant line 117c.

The third refrigerant line 117c, when the liquid refrigerant separated at the gas-liquid separating portion 118 flows therein, is adapted to perform heat-exchange with the liquid refrigerant and the coolant so as to condense the liquid refrigerant.

Herein, the gas-liquid separating portion 118 is connected respectively to the second and third refrigerant lines 117b and 117c close to upper and lower portions of the gas-liquid separating portion 118 among the plurality of second refrigerant lines 117b and third refrigerant lines 117c, and is not connected to other second and third refrigerant lines 117b and 117c by the plates 115.

That is, the plates 115 are adapted to close the upper and lower portions of the gas-liquid separating portion 118 such that the gas refrigerant and the liquid refrigerant does not flow into the second and third refrigerant lines 117b and 117c other than the second and third refrigerant lines 117b and 117c close to upper and lower portions of the gas-liquid separating portion 118.

According to various embodiments, a coolant outlet 123 is formed at an end portion of the upper cover 111 and a coolant inlet 121 is formed at the other end portion of the upper cover 111. The coolant inlet 121 and the coolant outlet 123 are connected to the main heat-radiating portion 110. Therefore, the coolant is supplied to the main heat-radiating portion 110 from the radiator 107 through the coolant inlet 121, and the coolant passing through the main heat-radiating portion 110 is exhausted from the main heat-radiating portion 110 through the coolant outlet 123.

In addition, a refrigerant inlet 125 through which the refrigerant is supplied from the compressor 105 is formed at the end portion of the upper cover 111.

That is, since the refrigerant inlet 125 is formed at an opposite side to the coolant inlet 121 and is formed at the same side as the coolant outlet 123, the coolant and the refrigerant flow in the opposite directions according to various embodiments.

Herein, an end portion of each plate 115 forming the second refrigerant line 117b is bent so as to form a wall 122. The end portion of each plate 115 is an end portion disposed close to the refrigerant inlet 125.

The wall 122 is adapted to prevent the refrigerant supplied through the refrigerant inlet 125 from flowing into the second refrigerant line 117b formed at an upper portion of the main heat-radiating portion 110.

In addition, the third refrigerant line 117c is not directly communicated with the refrigerant inlet 125 by the top plate 115 among the plates 115 forming the third refrigerant line 117c.

Therefore, the refrigerant supplied through the refrigerant inlet 125 is prevented from flowing directly into the third refrigerant line 117c by the top plate 115 among the plates 115 forming the third refrigerant line 117c and flows into the first refrigerant line 117a.

According to various embodiments, the receiver-drier portion 130 is adapted to receive the condensed refrigerant from the main heat-radiating portion 110 and to perform gas-liquid separation and moisture removal of the refrigerant. The receiver-drier portion 130 is integrally formed at the other end of the main heat-radiating portion 110 and is connected to the main heat-radiating portion 110.

The refrigerant flowing in the main heat-radiating portion 110 is separated into the gas refrigerant and the liquid refrigerant at the gas-liquid separating portion 118, and the gas refrigerant and the liquid refrigerant flow respectively through the second and third refrigerant lines 117b and 117c so as to exchange heat with the coolant and to be condensed.

After that, the condensed refrigerant is discharged to the receiver-drier portion 130 through a first connecting line 126 formed at the upper portion of the main heat-radiating portion 110 and connected to the second refrigerant line 117b and a second connecting line 123 formed at the lower portion of the main heat-radiating portion 110 and connected to the third refrigerant line 117c.

Since the receiver-drier portion 130 uses a receiver-drier having the same shape as the condenser 100, dead volume thereof may be minimized and additional connecting pipes may be removed, compared with a conventional receiver-drier of cylindrical shape.

According to various embodiments, a space 131 is formed in the receiver-drier portion 130, and an insertion hole 133 is formed at the lower cover 113 corresponding to the space 131.

A desiccant 135 is inserted in the space 131 through the insertion hole 133 and removes moisture in the refrigerant condensed at the main heat-radiating portion 110.

The desiccant 135 can be replaced through the insertion hole 133 according to replacement period. That is, the desiccant 135 is replaceably mounted in the receiver-drier portion 130.

Meanwhile, a filter is integrally formed with the desiccant 135, and the filter removes foreign materials contained in the refrigerant supplied to the receiver-drier portion 130.

That is, the receiver-drier portion 130 removes the moisture remaining in the refrigerant by the desiccant 135 and filters the foreign materials contained in the refrigerant by the filter. Therefore, it is prevented for the foreign materials remaining in the refrigerant from flowing into the expansion valve 101.

Accordingly, it is prevented for the foreign materials remaining in the refrigerant from blocking the expansion valve 101.

A fixing cap 137 for preventing escape of the desiccant 135 inserted in the space 131 and for preventing leakage of the refrigerant supplied to the receiver-drier portion 130 is mounted at the insertion hole 133.

In addition, the overcooling heat-radiating portion 140 is integrally formed at a lower portion of the main heat-radiating portion 110.

The low temperature and low pressure gas refrigerant supplied from the evaporator 103 flows in the overcooling heat-radiating portion 140. The low temperature and low pressure gas refrigerant passing through the overcooling heat-radiating portion 140 overcools the refrigerant through heat-exchange with the refrigerant supplied from the receiver-drier portion 130.

Herein, the overcooling heat-radiating portion 140 is adapted to perform heat-exchange by means of counterflow of the low temperature and low pressure gas refrigerant and the refrigerant supplied from the receiver-drier portion 130.

According to various embodiments, the overcooling heat-radiating portion 140 is connected to the receiver-drier portion 130 through a third connecting line 128. The overcooling heat-radiating portion 140 is adapted to receive the refrigerant in which gas-liquid separation and moisture removal is performed from the receiver-drier portion 130.

The refrigerant lines 117 and gas refrigerant lines 141 are alternately formed in the overcooling heat-radiating portion 140. Therefore, the refrigerant supplied from the receiver-drier portion 130 to the overcooling heat-radiating portion 140 through the third connecting line 128 flows in the refrigerant line 117, and the low temperature and low pressure gas refrigerant supplied from the evaporator 103 flows in the gas refrigerant line 141. At this process, heat-exchange of the condensed refrigerant and the gas refrigerant occurs.

That is, the plurality of plates 115 is stacked in the overcooling heat-radiating portion 140, and the refrigerant lines 117 and the gas refrigerant lines 141 are formed between the plurality of plates 115. Since the condensed refrigerant passing through the receiver-drier portion 130 flows in the refrigerant line 117 and the low temperature and low pressure gas refrigerant flows in the gas refrigerant line 141, the condensed refrigerant and the low temperature and low pressure gas refrigerant, as shown in FIG. 3 and FIG. 4, flows in opposite directions. At this process, heat-exchange of the condensed refrigerant and the low temperature and low pressure gas refrigerant occurs.

Herein, a refrigerant outlet 129 is formed at an end portion of the lower cover 113 corresponding to the refrigerant inlet 125. The refrigerant outlet 129 is connected to the expansion valve 101.

In addition, a gas refrigerant inlet 143 is formed at the end portion of the lower cover 113 and a gas refrigerant outlet 145 is formed at the other end portion of the lower cover 113. The gas refrigerant inlet 143 is connected to the evaporator 103 and the gas refrigerant outlet 145 is connected to the compressor 105.

Meanwhile, the receiver-drier portion 130 is integrally formed at the other end of the main heat-radiating portion 110 and the overcooling heat-radiating portion 140. The receiver-drier portion 130 is not fluidly connected to the main heat-radiating portion 110 and the overcooling heat-radiating portion 140 at positions other than the first and second and the third connecting lines 126, 127, and 128. Therefore, the refrigerant cannot flow into the receiver-drier portion 130 through the positions other than the first and second and the third connecting lines 126, 127, and 128.

According to various embodiments, a heat-isolating portion 150 for preventing heat-exchange of the refrigerant flowing in the main heat-radiating portion 110 and the overcooled refrigerant flowing in the overcooling heat-radiating portion 140 is formed between the main heat-radiating portion 110 and the overcooling heat-radiating portion 140.

The heat-isolating portion 150 may be adapted to receive nitrogen easily through a plurality of brazing holes 151 formed when stacking the plurality of plates 115 in a case of welding.

The brazing holes 151 are formed in order to reduce welding inferiority rate by exhausting gas occurring when the plurality of plates 115 are stacked and to easily insert the nitrogen into the heat-isolating portion 150.

The brazing holes 151 are closed after the nitrogen for forming the heat-isolating portion 150 is inserted.

As mentioned above, a condenser 100 according to various embodiments of the present invention includes heat exchanger in which a plurality of plates 115 is stacked.

The coolant cooled at the radiator 107 flows into the main heat-radiating portion 110 through the coolant inlet 121.

The coolant circulates along the coolant lines 119 formed between the plurality of plates 115 in the main heat-radiating portion 110. After that, the coolant is exhausted from the condenser 100 through the coolant outlet 123 and is supplied to the radiator 107 again.

At this time, the refrigerant is supplied from the compressor 105 to the main heat-radiating portion 110 through the refrigerant inlet 125, and flows to gas-liquid separating portion 118 along the first refrigerant line 117a among the refrigerant lines 117 formed alternately with the coolant lines 119.

The refrigerant is separated into the gas refrigerant and the liquid refrigerant at the gas-liquid separating portion 118, and the gas refrigerant and the liquid refrigerant flow respectively in the second refrigerant line 117b and the third refrigerant line 117c and exchange heat with the coolant.

At this time, the gas refrigerant and the liquid refrigerant separated at the gas-liquid separating portion 117 flow in opposite direction to the coolant flowing along the coolant line 119 and exchange heat with the coolant.

In addition, the condensed refrigerant cooled at the main heat-radiating portion 110 flows to the receiver-drier portion 130 through the first connecting line 126 and the second connecting line 127.

The condensed refrigerant circulates in the receiver-drier portion 130. At this time, gas-liquid separation is performed and the moisture in the refrigerant is removed by the desiccant 135. After that, the condensed refrigerant flows to the overcooling heat-radiating portion 140 through the third connecting line 128.

The refrigerant flowing into the overcooling heat-radiating portion 140 circulates in the overcooling heat-radiating portion 140 along the refrigerant line 117.

At this time, the low temperature and low pressure gas refrigerant supplied from the evaporator 103 flows into the overcooling heat-radiating portion 140 through the gas refrigerant inlet 143.

The gas refrigerant flowing into the overcooling heat-radiating portion 140 flows along the gas refrigerant line 141 in an opposite direction to the refrigerant flowing along the refrigerant line 117.

Therefore, the refrigerant passing through the main heat-radiating portion 110 and the receiver-drier portion 130 is overcooled through heat-exchange with the gas refrigerant flowing into the overcooling heat-radiating portion 140.

That is, the refrigerant flowing into the overcooling heat-radiating portion 140 flows in the opposite direction to the gas refrigerant and is overcooled through heat-exchange with the gas refrigerant. After that, the overcooled refrigerant is supplied to the expansion valve 101 through the refrigerant outlet 129.

Meanwhile, the gas refrigerant flowing into the overcooling heat-radiating portion 140 through the gas refrigerant inlet 143, after exchanging heat with the refrigerant flowing along the refrigerant line 117, is supplied to the compressor 105 through the gas refrigerant outlet 145.

Since the receiver-drier portion 130 is integrally formed with the main heat-radiating portion 110 and the overcooling heat-radiating portion 140, additional connection pipes for connecting the receiver-drier portion 130 to the main heat-radiating portion 110 and the overcooling heat-radiating portion 140 can be removed. In addition, since receiver-drier of the receiver-drier portion 130 has the same shape as the condenser 100, dead volume can be minimized.

In addition, the heat-isolating portion 150 prevents heat-exchange between the main heat-radiating portion 110 and the overcooling heat-radiating portion 140. Therefore, condensing efficiency and cooling efficiency of the condenser 100 may be improved.

It is exemplified but is not limited to that the main heat-radiating portion 110, the receiver-drier portion 130, and the overcooling heat-radiating portion 140 are formed by stacking the plurality of plates 115 between the upper and lower covers 111 and 113. The plurality of plates 115 without the upper and lower covers 111 and 113 can form the main heat-radiating portion 110, the receiver-drier portion 130, and the overcooling heat-radiating portion 140.

The condenser 100 for the vehicle according to various embodiments of the present invention is integrally formed with the receiver-drier, is formed by stacking the plurality of plates, and is adapted to separate the refrigerant the gas refrigerant and the liquid refrigerant and to condense the gas refrigerant and the liquid refrigerant. In addition, the condenser 100 is adapted to overcool the condensed refrigerant through heat-exchange with the low temperature and low pressure gas refrigerant supplied from the evaporator 103. Therefore, the number of components may be reduced and connections therebetween may be simplified. In addition, cost and weight may be reduced.

Since the refrigerant condensed at the main heat-radiating portion 110 can be overcooled through heat-exchange with the low temperature and low pressure gas refrigerant at the overcooling heat-radiating portion 140, additional components or pipes necessary for overcooling the refrigerant may be removed. Therefore, additional cost may not be consumed.

The condenser 100 separates the refrigerant flowing in the main heat-radiating portion 110 into the gas refrigerant and the liquid refrigerant at the gas-liquid separating portion 118. The gas refrigerant and the liquid refrigerant exchange heat with the coolant and are condensed, respectively. Therefore, heat-exchanging efficiency may be improved.

Since the receiver-drier is integrally formed with heat-radiating portions 110 and 140, dead volume in the condenser 100 may be reduced. Therefore, heat-radiating area of the condenser 100 may be increased and condensing efficiency and cooling efficiency may be improved without increasing the size of the condenser 100. Therefore, marketability may be improved.

For convenience in explanation and accurate definition in the appended claims, the terms upper or lower, front or rear, inside or outside, and etc. are used to describe features of the exemplary embodiments with reference to the positions of such features as displayed in the figures.

The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. They are not intended to be exhaustive or to limit the invention to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teachings. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and their practical application, to thereby enable others skilled in the art to make and utilize various exemplary embodiments of the present invention, as well as various alternatives and modifications thereof. It is intended that the scope of the invention be defined by the Claims appended hereto and their equivalents.

Claims

1. A condenser for a vehicle which is used in an air conditioning having an expansion valve, an evaporator, and a compressor, is provided between the compressor and the expansion valve, and circulates coolant supplied from a radiator to condense refrigerant supplied from the compressor through heat-exchange with the coolant and the refrigerant, the condenser comprising:

a main heat-radiating portion including a stacked a plurality of plates, connected to the radiator to circulate the coolant, and adapted to circulate the refrigerant supplied from the compressor to condense the refrigerant through heat-exchange with the coolant and the refrigerant;

a receiver-drier portion integrally formed with the main heat-radiating portion to receive the condensed refrigerant from the main heat-radiating portion and to perform gas-liquid separation and moisture removal of the refrigerant, and connected to the main heat-radiating portion; and

an overcooling heat-radiating portion integrally formed at a lower portion of the main heat-radiating portion, circulating low temperature and low pressure gas refrigerant supplied from the evaporator, and overcooling the refrigerant supplied from the receiver-drier portion through heat-exchange with the low temperature and low pressure gas refrigerant;

wherein the main heat-radiating portion includes: a first refrigerant line formed at a middle portion in the main heat-radiating portion along a length direction, the refrigerant flowing into an end portion of the main heat-radiating portion passing through the first refrigerant line; a gas-liquid separating portion formed at the other end portion in the main heat-radiating portion, connected to the first refrigerant line, and adapted to separate the refrigerant flowing therein through the first refrigerant line into gas refrigerant and liquid refrigerant; at least one second refrigerant line formed above the first refrigerant line for the light gas refrigerant separated at the gas-liquid separating portion to flow therein; and at least one third refrigerant line formed below the first refrigerant line for the heavy liquid refrigerant separated at the gas-liquid separating portion to flow therein.

2. The condenser of claim 1, wherein the gas-liquid separating portion is connected to the second and third refrigerant lines close to an upper portion and a lower portion of the gas-liquid separating portion among the second and third refrigerant lines, and is not connected to the other second and third refrigerant lines by the plates.

3. The condenser of claim 1, wherein the main heat-radiating portion causes the coolant and the refrigerant to exchange heat with each other by means of counterflow of the coolant and the refrigerant.

4. The condenser of claim 1, wherein the main heat-radiating portion further comprises a first connecting line formed at an upper portion of the main heat-radiating portion to be connected with the second refrigerant line, and a second connecting line formed at a lower portion of the main heat-radiating portion to be connected with the third refrigerant line, and

the main heat-radiating portion supplies the condensed refrigerant to the receiver-drier portion through the first connecting line and the second connecting line.

5. The condenser of claim 1, wherein the overcooling heat-radiating portion causes the low temperature and low pressure gas refrigerant and the refrigerant supplied from the receiver-drier portion to exchange heat with each other by means of counterflow of the low temperature and low pressure gas refrigerant and the refrigerant.

6. The condenser of claim 1, wherein the overcooling heat-radiating portion is connected to the receiver-drier portion through a third connecting line, and the refrigerant in which gas-liquid separation and moisture removal is performed at the receiver-drier portion flows into the overcooling heat-radiating portion through the third connecting line.

7. The condenser of claim 6, wherein the overcooling heat-radiating portion comprises:

a refrigerant line in which the refrigerant supplied from the receiver-drier portion through the third connecting line flows; and

a gas refrigerant line formed alternately with the refrigerant line, the low temperature and low pressure gas refrigerant supplied from the evaporator flowing in the gas refrigerant line, and

wherein the overcooling heat-radiating portion is adapted to overcool the condensed refrigerant flowing in the refrigerant line through heat-exchange with the gas refrigerant flowing in the gas refrigerant line.

8. The condenser of claim 1, wherein a heat-isolating portion for preventing heat-exchange with the refrigerant passing through the main heat-radiating portion and the overcooled refrigerant passing through the overcooling heat-radiating portion is formed between the main heat-radiating portion and the overcooling heat-radiating portion.

9. The condenser of claim 8, wherein the heat-isolating portion receives nitrogen therein easily through a plurality of brazing holes formed along a length direction thereof between the main heat-radiating portion and the overcooling heat-radiating portion in a case of welding.

10. The condenser of claim 1, further comprising an upper and lower covers mounted respectively on an upper surface and a lower surface of the main heat-radiating portion, the receiver-drier portion and the overcooling heat-radiating portion.

11. The condenser of claim 10, wherein the upper cover is provided with a coolant outlet formed at an end portion thereof and adapted to discharge the coolant from the main heat-radiating portion, a coolant inlet formed at the other end portion thereof and connected to the radiator to receive the coolant from the radiator, and a refrigerant inlet formed at the end portion thereof and connected to the compressor to receive the refrigerant from the compressor.

12. The condenser of claim 10, wherein the lower cover is provided with a refrigerant outlet formed at the end portion thereof corresponding to the refrigerant inlet and connected to the expansion valve, a gas refrigerant inlet formed at the end portion thereof and connected to the evaporator, and a gas refrigerant outlet formed at the other end portion thereof and connected to the compressor.

13. The condenser of claim 10, wherein an end portion of the plates forming the second refrigerant line is bent to form a wall.

14. The condenser of claim 10, wherein the third refrigerant line is not directly communicated with the coolant inlet by the top plate among the plates forming the third refrigerant line.

15. The condenser of claim 1, wherein the receiver-drier portion is provided with a space formed therein, and an insertion hole is formed at the lower cover corresponding to the space.

16. The condenser of claim 15, wherein a desiccant is inserted in the space through the insertion hole.

17. The condenser of claim 16, wherein a fixing cap for preventing escape of the desiccant inserted in the space and for preventing leakage of the refrigerant supplied to the receiver-drier portion is mounted at the insertion hole.

18. The condenser of claim 1, wherein the radiator is connected to a reserve tank and a cooling fan is provided at a rear portion of the radiator.

19. The condenser of claim 1, comprising a heat exchanger formed by stacking a plurality of plates.