KR101982587B1 - Evaporator - Google Patents

Abstract

The present invention relates to an evaporator, and more particularly to an evaporator in which the flow of refrigerant is composed of a two-row tube and the flow of the refrigerant is six passes, wherein the number of the rear tubes of the sixth and fifth passes is the same, The tube is formed so as to be equal to or less than 1/3 of the total number of the rear heating tubes to increase the pressure drop on the refrigerant side in the sixth pass as the superheating portion so as to lower the refrigerant temperature of the superheating portion and thereby improve the performance and the temperature distribution. .

Description

Evaporator {Evaporator}

The present invention relates to an evaporator, and more particularly to an evaporator in which the flow of refrigerant is composed of a two-row tube and the flow of the refrigerant is six passes, wherein the number of the rear tubes of the sixth and fifth passes is the same, The tube is formed so as to be equal to or less than 1/3 of the total number of the rear heating tubes to increase the pressure drop on the refrigerant side in the sixth pass as the superheating portion so as to lower the refrigerant temperature of the superheating portion and thereby improve the performance and the temperature distribution. .

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 weather or winter season by cooling or heating the interior of the automobile in the summer or winter season, Such an air conditioner usually has 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 interior of the automobile to cool,

A typical refrigeration cycle of such an air conditioner is composed of an evaporator for absorbing heat from the surroundings, a compressor for compressing the refrigerant, a condenser for releasing heat to the surroundings, and an expansion valve for expanding the refrigerant. In the cooling system, the gaseous refrigerant flowing into the compressor from the evaporator is compressed to a high temperature and a high pressure in the compressor, and the refrigerant in the gaseous state in the condensed state is discharged while being liquefied while passing through the condenser, The refrigerant passes through the expansion valve again to become a low-temperature and low-pressure humidified vapor state, and then flows into the evaporator again to vaporize and absorb the heat of vaporization from the surroundings, thereby cooling the surrounding air and thereby cooling the interior of the vehicle.

As a representative heat exchanger used in such a cooling system, there have been a lot of studies for more effectively exchanging heat between the air outside the heat exchanger and the heat exchange medium inside the heat exchanger, that is, the refrigerant. The most direct effect of indoor cooling is manifested by evaporator efficiency, and various structural research and development have been conducted to improve the heat exchange efficiency of the evaporator.

Japanese Patent Laid-Open Publication No. 2005-0104072 (published on November 11, 2005, entitled: Heat Exchanger) discloses an evaporator that improves heat exchange performance by minimizing pressure loss due to flow resistance of refrigerant flowing through an inlet pipe.

As another example, Figure 1 is a perspective view of a conventional evaporator and a heat exchange medium flow schematic.

The conventional evaporator as shown in FIG. 1 and FIG. 2 has at least one compartment formed by the partition 11 and is spaced apart from the partition by a predetermined distance, and an inlet pipe 30 and an outlet pipe 40 are formed respectively A first header tank (10) and a second header tank (20); A baffle 12 provided in the first header tank 10 or the second header tank 20 to regulate the flow of the heat exchange medium; A plurality of tubes connected to the first header tank and the second header tank and forming a first row communicating with the inlet pipe and a second row communicating with the outlet pipe, 50); A communicating portion 13 communicating a predetermined region of the first and second rows in the first header tank 10; And a plurality of pins (60) stacked between the tubes (50); And the second electrode is formed.

The evaporator is formed such that the baffle extends over the first and second rows in the width direction of the first header tank or the second header tank.

FIG. 3 is a schematic view of the heat exchange medium flow of the evaporator shown in FIG. 1, showing an example having six passes.

3, the heat exchange medium flowing into the first header tank through the inlet pipe moves in the longitudinal direction of the first header tank to a region where the first baffle of the first row is formed, The heat exchanging medium flowing into the second header tank flows through the first column tube into the second header tank and flows into the second header tank through the second header tank, (Second pass) through the first column tube (U-turn) and flows into the second header tank again through the first column tube (third pass) and flows through the first header tube Is moved to the second header tank of the second row and flows into the first header tank through the second row of tubes (fourth pass), to the region where the first baffle of the second row is formed, in the longitudinal direction of the first header tank Through the second column tube while moving, It flows into the further tank (fifth pass), is turned U- is again introduced into the first header tank through the second column tube and is discharged through the outlet pipe.

However, in the evaporator as shown in Figs. 1 to 3, since the temperature of the region adjacent to the outlet side (the region indicated by S) is increased and the temperature of the air passing through the region differs from the temperature of the air passing through the other region There is a problem.

That is, the temperature distribution of the air passing through the entire evaporator can be made non-uniform, and the cooling comfort of the user can be lowered.

Accordingly, development of an evaporator capable of improving the uniformity of the entire temperature while increasing the heat exchange efficiency has been demanded.

Korean Patent Publication No. 2005-0104072 (published on November 11, 2005, entitled: Heat Exchanger)

It is an object of the present invention to provide an evaporator in which the flow of refrigerant is composed of a two-row tube and the flow of the refrigerant is six passes, and the number of the rear tubes of the sixth pass and the fifth pass is The sixth pass tube is formed so as to be equal to or less than 1/3 of the total number of the rear heat pipes to increase the pressure drop on the refrigerant side in the sixth pass which is the overheat section to lower the refrigerant temperature of the superheat section, And to provide an evaporator capable of improving the temperature distribution.

The evaporator of the present invention includes an upper tank (110) and a lower tank (120) partitioned by a partition (130) into an inner space and a rear row in the air flow direction and spaced apart from each other by a predetermined distance. A plurality of tubes 200 arranged in two rows in which the both ends of the heat exchange medium are fixed to the divided spaces of the upper tank 110 and the lower tank 120, respectively; A pin (300) interposed between the tubes (200); A first heat transfer baffle 411 and a first heat transfer baffle 412 provided in the upper and lower tanks 110, respectively; A second electrothermal heating baffle 421 and a second rear heating baffle 422 provided in the heat and the subsequent heat of the lower tank 120; An inlet pipe (500) formed in the heat of the upper tank (110) or the lower tank (120); And an outlet pipe (600) formed at a rear row of the upper tank (110) or the lower tank (120); Wherein the evaporator 1 is connected to the upper tank 110 or the lower tank 120 through a tube 200 in the rear row, The heat exchanging medium of the upper tank 110 or the lower tank 120 flows through the tube 200 of the rear heat to the upper tank 110 Or the number of the rear tubes 200 of the fifth pass P5 which is introduced into the lower tank 120 and then passes through the sixth pass P6 is the same.

The evaporator 1 is characterized in that the tube of the sixth pass P6 forms 13 to 31% of the total number of the rear heating tubes 200.

The evaporator may include a first path P1 through which the heat exchange medium introduced from the inlet pipe 500 flows into the upper tank 110 or the lower tank 120 through the heat transfer tube 200, The heat exchanging medium passing through the first pass P1 flows into the upper tank 110 or the lower tank 120 through the heat transfer tube 200. In this case, And the number of tubes (200) of the second path (P2) and the fifth path (P5) are formed to be the same.

The evaporator 1 is further provided with a third path P3 through which the heat exchange medium passing through the second path P2 flows into the upper tank 110 or the lower tank 120 via the heat transfer tube 200 The heat exchange medium passing through the third pass P3 passes through the communication hole formed on the partition 210 of the lower tank 120 through the rear heating tube 200, The fourth passage P4 flowing into the upper tank 110 or the lower tank 120 is 1/3 or more of the number of the rear tubes 200. [

The evaporator 1 is characterized in that the tube 200 is an extruded tube 200 having a plurality of partitions 210 and the tube 200 has a hydraulic diameter Dh of 0.5 to 3.0 mm .
Further, the upper tank 110 and the lower tank 120 are divided into a front space and a rear space in the air flow direction by the partition 130, and are spaced apart from each other by a predetermined distance. A plurality of tubes 200 arranged in two rows in which the both ends of the heat exchange medium are fixed to the divided spaces of the upper tank 110 and the lower tank 120, respectively; A pin (300) interposed between the tubes (200); A first heat transfer baffle 411 and a first heat transfer baffle 412 provided in the upper and lower tanks 110, respectively; A second electrothermal heating baffle 421 and a second rear heating baffle 422 provided in the heat and the subsequent heat of the lower tank 120; An inlet pipe (500) formed in the heat of the upper tank (110) or the lower tank (120); And an outlet pipe (600) formed at a rear row of the upper tank (110) or the lower tank (120); Wherein the evaporator 1 has a heat exchanging medium that has passed through the heat transfer tube 200 in the upper tank 110 or the lower tank 110. [ A fifth path P5 in which the heat exchange medium having passed through the fourth path P4 flows into the upper tank 110 or the lower tank 120, And a sixth passage P6 through which the heat exchange medium having passed through the second passage P5 is discharged to the outlet pipe 600 through the upper tank 110 or the lower tank 120, The number of tubes 200 in the rear row is larger than the number of tubes 200 in the rear row forming the fifth pass P5 and the sixth pass P6, (200) and the number of tubes (200) in the rear row forming the sixth pass (P6) are equal to each other.

The evaporator of the present invention is composed of two rows of tubes, and the flow of the refrigerant is six passes. The evaporator of the sixth and seventh passes has the same number of the tubes of the fifth pass, The temperature of the refrigerant in the sixth pass is increased to lower the temperature of the refrigerant in the superheating portion, thereby improving the performance and the temperature distribution.

In detail, the conventional six-pass evaporator is constituted by equally dividing the number of tubes of each pass. In order to solve the problem that the area of the sixth pass, which is an exit-side pass, is overheated and the cooling performance is lowered, The number of tubes in the sixth pass is limited to 1/3 or less in order to increase the pressure drop on the refrigerant side of the sixth pass, so that the temperature of the refrigerant in the superheat can be lowered.

At this time, the number of tubes of the first pass, the second pass, the fifth pass, and the sixth pass may be made the same, and the performance may be further improved.

In addition, the present invention can further improve the synergistic effect of the evaporator performance by limiting the hydraulic diameter (Dh) of the tube to 0.5 to 3.0 mm with the tube being an extruded tube composed of a plurality of partition walls.

1 and 2 are a perspective view and an exploded perspective view of a conventional evaporator;
3 is a flow chart illustrating the flow of refrigerant in the evaporator of FIG.
4 is a partially exploded perspective view showing an evaporator according to the present invention.
FIG. 5 is a schematic view showing the flow of refrigerant in the evaporator of FIG. 4;
Figure 6 is a front view of Figure 5;
7 is a table comparing the cooling performance according to the number of tubes in the fifth pass and the sixth pass.
8 is a schematic diagram illustrating the flow of refrigerant in an evaporator of yet another embodiment.
9 is a partially exploded perspective view showing an evaporator of still another embodiment.
10 is a PH diagram showing characteristics of a superheating part of a conventional evaporator and an evaporator of the present invention.
11 is a perspective view and a cross-sectional view of a tube of an evaporator according to the present invention.
12 is a graph showing performance according to the tube ratio of the sixth pass relative to the total number of tubes and the hydraulic diameter of the tube in the evaporator according to the present invention.
13 is a graph showing the difference in surface temperature distribution according to the tube ratio of the sixth pass relative to the total number of tubes and the hydraulic diameter of the tube in the evaporator according to the present invention.

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

The evaporator 1 of the present invention includes an upper tank 110, a lower tank 120, a tube 200, a fin 300, a first heat transfer baffle 411, a first heat transfer baffle 412, A second rear baffle 422, an inlet pipe 500, and an outlet pipe 600.

The upper tank 110 and the lower tank 120 are spaced apart from each other by a predetermined distance and may be formed by a combination of a header and a tank.

At this time, the header has a dividing section 130 dividing into two spaces long in the longitudinal direction in the central region, and the inner space is divided into the heat transfer and the heat transfer in the air flow direction, and the upper tank 110 and the lower tank 120 And the refrigerant of the heat transferring and the heat of the rear heating are communicated with each other.

The tube 200 is configured such that both ends thereof are fixed to the divided spaces of the upper tank 110 and the lower tank 120 so that the refrigerant flows together with the upper tank 110 and the lower tank 120, .

In the present invention, the heat transfer tube 200 is located on the rear side in the drawing, and the refrigerant flowing in the inlet pipe 500 formed in the heat of the upper tank 110 or the lower tank 120 flows, The refrigerant which has passed through the heat transfer tube 200 flows into the heat transfer tube 200 through the communication hole and flows into the upper tank 110 or the lower heat transfer tube 120 And is discharged to the outlet pipe 600 formed in the outlet pipe.

The first heat transfer baffle 411 and the first heat transfer baffle 412 are provided for the heat transfer and the post heat of the upper tank 110 to control the flow of the refrigerant, (422) is provided for the heat transfer and the post heat of the lower tank (120) to control the flow of the refrigerant.

At this time, the evaporator 1 of the present invention is configured such that the refrigerant flow is divided into six passes by the first heat conductive baffle 411, the first heat conductive baffle 412, the second heat conductive baffle 421 and the second heat conductive baffle 422 FIG. 5 shows six passes when the inlet pipe 500 is formed in the upper tank 110 and the outlet pipe 600 is formed in the rear row of the upper tank 110, 8 shows six passes when the inlet pipe 500 is formed in the heat transfer of the lower tank 120 and the outlet pipe 600 is formed in the downstream of the lower tank 120.

As shown in FIGS. 5 and 8, the evaporator 1 having six passes has an overheating phenomenon in which the temperature of the refrigerant at the outlet pipe 600 is higher than that of the other refrigerant. By reducing the number of the tubes 200 located in the sixth pass P6, which is the closest path, to be 1/3 or less of the number of the rear tubes 200 and reducing the number of the tubes 200 adjacent to the outlet, The pressure drop can be increased and the temperature of the superheating portion can be further lowered in accordance with the PH line characteristic as shown in Fig.

That is, in the evaporator 1 of the present invention, the pressure drop in the superheating section corresponding to the outlet side from the PH diagram is increased, and the temperature of the refrigerant passing through the evaporator 1 is increased from the existing two- By making the temperature range from 2 to 4 DEG C at 8 DEG C, the overall temperature distribution is improved.

The evaporator 1 of the present invention may be constructed such that the heat exchange medium flowing into the upper tank 110 or the lower tank 120 through the tube 200 of the rear heat is discharged to the outlet pipe 600 The tube 200 of the path P6 forms 13 to 31% of the total number of the rear heating tubes 200. The basis for this numerical value will be described below based on FIGS. 11 and 12 .

The following description will be made on the basis of the embodiment shown in Fig.

5, the refrigerant introduced into the upper tank 110 through the inlet pipe 500 flows through the upper tank 110 to the region where the first 1-1 baffle 411 of the heat is formed, The heat exchanging medium flowing into the lower tank 120 flows into the second-1 baffle 120 through the heat transfer tube 200 while being moved in the longitudinal direction of the second tank 120, (Second path P2) through the heat transfer tube 200 while moving in the longitudinal direction of the lower tank 120 to the region where the heat transfer tube 200 through the upper tank 120 and the lower tank 120 through the communication part 140 formed in the partition 130 of the lower tank 120 And then flows into the upper tank 110 through the rear tube 200 (the fourth pass P4) to the region where the 1-2 th baffle 412 of the rear row is formed, (Fifth pass P5) and flows through the rear tube 200 to the upper tank 110 through the rear tube 200 while moving in the longitudinal direction of the upper tank 110 And is discharged through the outlet pipe 600.

9, the evaporator 1 of the present invention differs from the evaporator of the first embodiment in that the positions of the first heat conductive baffle 411, the first heat conductive baffle 412, the second heat conductive baffle 421 and the second heat conductive baffle 422 are different, The number of tubes of the first to sixth passes P1 to P6 can be adjusted.

5, the fourth pass P4: the fifth pass P5: the sixth pass P6, the fourth pass P4, the fifth pass P5, the sixth pass P6, = 7: 4: 4.

The evaporator 1 according to the present invention includes a first path P1 through which the heat exchange medium introduced from the inlet pipe 500 flows into the upper tank 110 or the lower tank 120 through the heat transfer tube 200, The number of the tubes 200 of the sixth pass P6 is the same and the heat exchange medium passing through the first pass P1 passes through the heat transfer tube 200 to the upper tank 110 or the lower tank 120 It is preferable that the number of the second paths P2 and the number of the tubes 200 of the fifth path P5 are the same.

5, the evaporator 1 of the present invention is arranged such that the first heat transfer baffle 411 and the first heat transfer baffle 412 are positioned in a straight line in the air flow direction, And the number of the tubes 200 of the sixth pass P6 may be the same, and the second heating baffle 421 and the second rear heating baffle 422 may be formed so as to be aligned in parallel in the air flow direction The number of the second passes P2 and the number of the fifth passes P5 tubes 200 may be the same.

FIG. 7 is a table comparing the cooling performances according to the number of tubes 200 constituting the fifth and sixth passes P5 and P6. Through this table, the fifth pass P5 and sixth When the number of passes P6 is the same, the cooling performance is greatly improved compared to the conventional one.

7, the first pass P1: the second pass P2: the third pass P3: the fourth pass P4: the second pass P2: the third pass P3: the fourth pass P4 ) Shows the performance when the performance in the case of the fifth path P5: sixth path P6 = 10: 10: 10: 10: 10: 10 is assumed as 100%. In the fifth path P5, And the sixth pass P6 and the tubes 200 of the first pass P1 and the second pass P2 are equal to eight, the effect is 102%.

That is, in the evaporator 1 of the present invention, the number of the tubes 200 in the sixth pass P6 is 13 to 31%, and the number of the rear tubes 200 in the fifth pass P5 and the sixth pass P6 Is the same, the cooling performance improvement effect is the best compared with the conventional one.

However, the present invention can reduce the number of tubes 200 of the sixth pass P6, which have a difference in temperature distribution, from that of the prior art to increase the effect of improving the refrigerant distribution and increase the refrigerant pressure drop of the sixth pass P6 It is preferable that the fourth path P4 at this time is 1/3 or more of the number of the four rear heating tubes 200. [

The first pass P1 = the sixth pass P6, the second pass P2, the fifth pass P5, the second pass P2, The number of the first passes P1 is 8, the number of the second passes P2 is 8, and the number of the first pass P1 is 8, And the number of the first passes P1 is equal to or less than 13 to 31% of the total number of the tubes 200. The number of the first passes P1 is equal to the number of the second passes P2, And the third path P3 may be 1/3 or more.

As another example, in the evaporator 1 of the present invention, the first pass P1 may be 9, the second pass P2 may be 9, the third pass P3 may be 12, and any modification may be made under the above- Is possible.

Further, the evaporator 1 of the present invention was tested to find the conditions with improved temperature distribution and improved performance compared to the existing one. As a result, a suitable path for the 6-pass and a hydraulic diameter of the tube 200 were set.

It is preferable that the tube 200 is an extrusion tube 200 having a plurality of partitions 210 and the hydraulic diameter Dh of the tube 200 is 0.5 to 3.0 mm.

Here, the hydraulic diameter of the tube 200 is such that the hydraulic diameter Dh = 4 占 ㅧ area / reception length for one channel divided by the partition 210 in the tube 200 of Fig. 10, Sectional area of the flow path 200, and the reception length means the circumferential length of the flow path.

12, in the evaporator 1 of the present invention, the range of the sixth pass P6 in which the existing performance dash predominates is in the range of 13 to 31% of the number of the rear heating tubes 200 or the total area of the rear heating tubes 200, The larger Dh = 0.5 ~ 3.0mm is suitable.

13, the pass ratio satisfying the temperature target of 5 ° C or less is also in the range of the sixth pass P6, which is superior to the existing performance, in the number of the rear heating tubes 200 or 13 to 31% And the hydraulic diameter tends to be higher as the diameter is smaller. Therefore, in consideration of the mass production of the holes of the tube 200, it is preferable that Dh = 0.5 to 3.0 mm as described above.

As a result, the evaporator 1 of the present invention reduces the number of the rear tubes 200 corresponding to the sixth pass P6 adjacent to the outlet pipe 600 for reducing the pressure, The tube 200 of the first pass P1 constitutes 13 to 31% of the number of the heat-transfer tubes 200 and the tube 200 of the sixth pass P6 constitutes 13 to 31% of the number of the heat- 13 to 31%.

Accordingly, the evaporator 1 of the present invention can lower the temperature of the refrigerant in the superheating portion, thereby improving the performance and the temperature distribution.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. It goes without saying that various modifications can be made.

1: Evaporator
110: upper tank 120: lower tank
130: partitioning part 140:
200: tube 210: partition wall
300: pin
411: 1-1 Baffle 412: 1-2 Baffle
421: 2-1 baffle 422: 2-2 baffle
500: inlet pipe
600: outlet pipe
P1 to P6: First to sixth passes

Claims (5)

An upper tank 110 and a lower tank 120 partitioned by the partitioning unit 130 into an electric heat and a rear heat in an air flow direction and spaced apart from each other by a predetermined distance; A plurality of tubes 200 arranged in two rows in which the both ends of the heat exchange medium are fixed to the divided spaces of the upper tank 110 and the lower tank 120, respectively; A pin (300) interposed between the tubes (200); A first heat transfer baffle 411 and a first heat transfer baffle 412 provided in the upper and lower tanks 110, respectively; A second electrothermal heating baffle 421 and a second rear heating baffle 422 provided in the heat and the subsequent heat of the lower tank 120; An inlet pipe (500) formed in the heat of the upper tank (110) or the lower tank (120); And an outlet pipe (600) formed at a rear row of the upper tank (110) or the lower tank (120); And the flow of the heat exchange medium is divided into six passes. In the evaporator 1,
The evaporator 1 includes a fourth passage P4 through which the heat exchange medium having passed through the heat transfer tube 200 flows into the upper tank 110 or the lower tank 120 and a fourth passage P4 through which the heat exchange medium passes through the fourth passage P4, The fifth path P5 through which the medium flows into the upper tank 110 or the lower tank 120 and the heat exchange medium which has passed through the fifth path P5 pass through the upper tank 110 or the lower tank 120, And a sixth path P6 discharged to the pipe 600. The number of the tubes 200 forming the fourth path P4 is greater than the number of the tubes P5 and P6, The number of the tubes 200 forming the fifth pass P5 and the number of the tubes 200 forming the sixth pass P6 are larger than the number of the tubes 200 forming the fifth pass P5, Respectively,
Characterized in that the number of trailing tubes forming the sixth pass (P6) is 13 to 31% of the number of tubes (200) of the total trailing heat.
delete The method according to claim 1,
The evaporator 1 includes a first path P1 through which the heat exchange medium introduced from the inlet pipe 500 flows into the upper tank 110 or the lower tank 120 through the heat transfer tube 200, The number of tubes 200 forming the path P6 is formed to be the same,
A second path P2 and a fifth path P5 through which the heat exchange medium passing through the first path P1 flows into the upper tank 110 or the lower tank 120 through the heat transfer tube 200 And the number of the tubes (200) is made equal.
The method of claim 3,
The evaporator 1 forms a third path P3 through which the heat exchange medium passing through the second path P2 flows into the upper tank 110 or the lower tank 120 through the heat transfer tube 200 The number of heat transfer tubes 200 is 1/3 or more of the total heat transfer tubes 200,
The heat exchange medium passing through the third path P3 flows through the fourth pass P4 which is introduced into the upper tank 110 or the lower tank 120 through the communication hole formed on the partition 210 of the lower tank 120, ) Is 1/3 or more of the total number of tubes (200) in the subsequent row.
The method according to claim 1,
In the evaporator 1, the tube 200 is an extrusion tube 200 having a plurality of partitions 210,
And the hydraulic diameter (Dh) of the tube (200) is 0.5 to 3.0 mm.

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