KR20060085448A - Heat exchanger - Google Patents

Abstract

The present invention relates to a heat exchanger, and more particularly, by communicating a pair of cups in a predetermined region of the central portion of the heat exchanger to communicate with the inlet and outlet heat exchangers, as well as by making the flow direction of the refrigerant flowing therein the same. The present invention relates to a heat exchanger that is more advantageous in miniaturization by reducing the amount of refrigerant deflection and the pressure drop on the refrigerant side, as well as uniformizing the surface temperature distribution of the heat exchanger, improving heat exchange performance, and facilitating forward arrangement of inlet and outlet pipes.

In the present invention, a pair of plates 111 are bonded to each other to form two independent flow paths 114 with partition beads 113 therebetween, and the upper and lower ends communicate with each of the flow paths 114. A pair of cups (112) are formed side by side and a plurality of tubes (110) laminated to bond the pair of cups 112 to form the upper and lower tanks (101) (102); Inlet and outlet pipes 150 and 151 which are respectively installed at both ends of any one of the upper and lower tanks 101 and 102 to introduce and discharge refrigerants; In the laminated tube 110, the inlet-side heat exchanger 103 communicating with the inlet pipe 150 and the outlet-side heat exchanger 104 communicating with the outlet pipe 151 communicate with each other, Communication in which each tank 101 of the inlet and outlet side heat exchanger 103 and 104 provided with the inlet and outlet pipes 150 and 151 communicates 10 to 50% of the total size with the same flow direction. Means 140; The heat exchange areas (106, 107) partitioning the inlet and outlet side heat exchange parts (103, 104) into a plurality of heat exchange areas (105 to 108), and communicating with the communication means (140) so that some of them overlap each other. It characterized in that it comprises a blank plate 111a installed by closing one cup (112a) positioned in a diagonal direction with the communication means 140 therebetween.

Heat exchanger, evaporator, tube, plate, communication path, blank plate

Description

Heat exchanger

1 is a perspective view showing a conventional heat exchanger,

2 is a view showing a refrigerant flow of a conventional heat exchanger,

3 is a perspective view of a heat exchanger according to a first embodiment of the present invention;

4 is a front view showing a heat exchanger according to the first embodiment of the present invention;

5 is a perspective view illustrating a state in which a general tube is disassembled in a heat exchanger according to a first embodiment of the present invention;

6 is a perspective view illustrating a state in which a tube formed with a communication path is disassembled in a heat exchanger according to a first embodiment of the present invention;

7 is a perspective view illustrating a state in which the blank plate is disassembled in the heat exchanger according to the first embodiment of the present invention;

8 is a graph showing the heat dissipation amount and the refrigerant pressure drop amount according to the ratio of the number of communication tube tubes to the total number of tube columns in the heat exchanger according to the first embodiment of the present invention;

9 is a view showing a refrigerant flow of the heat exchanger according to the first embodiment of the present invention,

10 is a view showing the refrigerant flow distribution in the heat exchanger according to the first embodiment of the present invention;                 

11 is a perspective view showing a heat exchanger according to a second embodiment of the present invention;

12 is a perspective view of a heat exchanger according to a third embodiment of the present invention;

FIG. 13 is a perspective view illustrating a state in which a tube in which a communication passage is formed at an upper end and a bypass passage is formed at a lower end in a heat exchanger according to a third embodiment of the present invention.

<Description of Signs of Major Parts of Drawings>

100: heat exchanger 101: upper tank

102: lower tank 103: inlet side heat exchanger

104: outlet side heat exchanger 105 to 108 first to fourth heat exchange zone

110: tube 111: plate

111a: blank plate 112, 112a: cup

112b: Allocation Hall

113: compartment bead 114: euro

115: first bead 116: neck bead part

116a: second bead 116b: passage

120: heat sink fin 130: end plate

140: communication means 141: communication path

145: bypass passage

150: inlet pipe 151: outlet pipe

The present invention relates to a heat exchanger, and more particularly, by communicating a pair of cups in a predetermined region of the central portion of the heat exchanger to communicate with the inlet and outlet heat exchangers, as well as by making the flow direction of the refrigerant flowing therein the same. The present invention relates to a heat exchanger that is more advantageous in miniaturization by reducing the amount of refrigerant deflection and the pressure drop on the refrigerant side, as well as uniformizing the surface temperature distribution of the heat exchanger, improving heat exchange performance, and facilitating forward arrangement of inlet and outlet pipes.

The heat exchanger has a flow path through which a heat exchange medium flows, and is used to heat exchange the heat exchange medium and the outside air. The heat exchanger is used in various air-conditioning apparatuses. .

Among the heat exchangers, the evaporator is classified according to the structural type of the refrigerant passage, such as a serpentine type in which a single extruded tube is bent in multiple stages, a laminate type in which a dimple-shaped plate is laminated, and a plurality of extruded tubes. The multiple extruder tube type evaporator used is introduced.

Japanese Utility Model Laid-Open No. 7-12778 is disclosed as an example of such a conventional evaporator, and briefly described with reference to FIG. 1, the evaporator 1 has a plate 11 having a pair of cups 12 formed at the top and bottom thereof. It is made by stacking a plurality of tubes 10 formed by joining two pieces.

In addition, by stacking a plurality of tubes 10, tanks 2 and 3 are formed at upper and lower sides, and inlet and outlet pipes 4 and 5 are provided at one side to allow the refrigerant to be introduced / exhausted. .

Therefore, the inlet side heat exchanger 20a is configured at the side communicating with the inlet pipe 4, and the outlet side heat exchanger 20b is configured at the side communicating with the outlet pipe 5.

In addition, communication portions 25 are provided on opposite sides of the inlet and outlet pipes 4 and 5 so as to allow the inlet and outlet side heat exchangers 20a and 20b to communicate with each other.

Meanwhile, partition walls 26 are formed in parallel in the upper tank 2 so as to partition the inlet and outlet side heat exchange parts 20a and 20b into a plurality of heat exchange areas 21 to 24. Between the (10) is interposed a heat radiation fin (15) to promote heat exchange.

The refrigerant flow of the evaporator 1 will be described with reference to FIG. 2 as follows.

The refrigerant flowing into the upper tank 2 of the inlet heat exchanger 20a through the inlet pipe 4 is lowered in the first heat exchange area 21 partitioned by the partition wall 26 to lower the tank 3. And the refrigerant moved to the lower tank (3) is returned here and then rises in the second heat exchange zone (22) to move to the upper tank (2).

The refrigerant passing through the inlet side heat exchanger 20a flows into the upper tank 2 of the outlet side heat exchanger 20b through the communication unit 25.

The refrigerant flowing into the upper tank 2 of the outlet side heat exchanger 20b is lowered in the third heat exchange zone 23 partitioned by the partition wall 26 to move to the lower tank 3, and the lower tank ( The refrigerant moved to 3) is returned from the fourth heat exchange zone 24, and then moves to the upper tank 2, and is discharged through the outlet pipe (5).                         

Meanwhile, the first heat exchange region 21 is a region in which the coolant in the upper tank 2 descends along the tube 10 and moves to the lower tank 3. Gravity acts to increase the amount of refrigerant flowing into each tube 10 at the beginning of the direction of the refrigerant, and the amount of refrigerant flowing into the tube 10 gradually decreases toward the second half.

The second heat exchange region 22 is a region where the refrigerant in the lower tank 3 introduced from the first heat exchange region 21 rises along the tube 10 and moves to the upper tank 2. The inertial force acts on the refrigerant flowing inside) so that the amount of refrigerant flowing into each tube 10 at the beginning of the refrigerant direction decreases and the amount of refrigerant flowing into the tube 10 gradually increases toward the second half.

In the third heat exchange zone 23, the refrigerant of the upper tank 2 introduced from the second heat exchange zone 22 via the communication unit 25 descends along the tube 10 and moves to the lower tank 3. As a region, gravity acts on the refrigerant flowing in the upper tank 2, so that the amount of refrigerant flowing into each tube 10 increases at the beginning of the refrigerant direction, and the amount of refrigerant flowing into the tube 10 gradually increases toward the latter half. Will be less.

The fourth heat exchange region 24 is a region where the refrigerant in the lower tank 3 introduced from the third heat exchange region 23 rises along the tube 10 and moves to the upper tank 2. The inertial force acts on the refrigerant flowing inside) so that the amount of refrigerant flowing into each tube 10 at the beginning of the refrigerant direction decreases and the amount of refrigerant flowing into the tube 10 gradually increases toward the second half.                         

Therefore, the surface temperature difference of the evaporator 1 is severely generated by the deflection of the refrigerant, which is more severely generated when the amount of refrigerant flows or the air passing through the evaporator 1 is low in air volume, that is, the inlet and outlet sides. In the heat exchange parts 20a and 20b, the supercooling section and the superheating section are respectively generated on the tube 10 side through which a large amount of refrigerant flows and the tube 10 side through which a small amount of refrigerant flows.

In the flow path configuration as described above, the subcooling section and the superheating section are generated at a position substantially similar to the inlet side heat exchanger 20a and the outlet side heat exchanger 20b, and the subcooled section of the outlet side heat exchanger 20b. Most of the air passing through passes through the supercooling section of the inlet side heat exchanger 20a, and most of the air passing through the overheating section of the outlet side heat exchanger 20b passes through the superheated section of the inlet side heat exchanger 20a. Therefore, the air passing between the entire tubes 10 does not have a uniform heat exchange, so that a difference in temperature distribution of the discharged air occurs, and of course, icing on the surface of the evaporator 1 in the subcooling section. The air conditioner system becomes unstable, such as problems, and in the overheating section, the cooling and dehumidification of the discharged air is not performed normally. There is a problem offensive.

In addition, the refrigerant pressure drop is increased by the communication unit 25 separately provided at one end of the tank 2 so as to communicate the inlet side heat exchanger 20a and the outlet side heat exchanger 20b, thereby reducing the heat exchange performance. Not only that, but also a lot of obstacles to downsizing.

In addition, since both the inlet and outlet pipes 4 and 5 are arranged on one side of the evaporator 1, there is also a problem that the front and rear of the inlet and outlet pipes 4 and 5 are difficult to arrange.

An object of the present invention for solving the above problems is to communicate a pair of cups in a predetermined region of the central portion of the heat exchanger to communicate with the inlet and outlet side heat exchanger as well as the same flow direction of the refrigerant flowing therein By reducing the pressure of the refrigerant, the pressure drop on the refrigerant side, and the heat exchanger of the inlet and outlet side to complement each other, it is more advantageous for miniaturization, uniformity of the surface temperature distribution of the heat exchanger, and improved heat exchange performance. It is to provide a heat exchanger that can be easily disposed in the front of the outlet pipe.

Another object is to provide a heat exchanger that can obtain an optimal heat dissipation by configuring the ratio of the communication means (communication path) to the total size of the heat exchanger within 10 to 50%.

In order to achieve the above object, in the present invention, a pair of plates are bonded to each other to form two independent flow paths having partition beads therebetween, and a pair of cups communicating with each of the flow paths at the upper and lower ends are arranged side by side. A plurality of tubes are formed to form a plurality of upper and lower tanks by bonding the pair of cups; Inlet and outlet pipes installed at both ends of any one of the upper and lower tanks to introduce and discharge refrigerant; Inlet and outlet side in which the inlet and outlet pipes are installed so that the flow direction of the refrigerant flowing through each of the same through the inlet-side heat exchanger communicating with the inlet pipe and the outlet-side heat exchanger communicating with the outlet pipe Communicating means for communicating each tank of the heat exchange part with an area of 10 to 50% of the total size; The heat exchanger is divided into a plurality of heat exchange zones, and the heat exchange zones communicating with the communication means include a blank plate provided by closing one cup in a diagonal direction with the communication means interposed therebetween to partially overlap each other. Characterized in that comprises a.

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

3 is a perspective view showing a heat exchanger according to a first embodiment of the present invention, Figure 4 is a front view showing a heat exchanger according to a first embodiment of the present invention, Figure 5 is a heat exchanger according to a first embodiment of the present invention 6 is a perspective view illustrating a state in which a general tube is disassembled, FIG. 6 is a perspective view illustrating a state in which a communication path is formed in a heat exchanger according to a first embodiment of the present invention, and FIG. 7 is a first embodiment of the present invention. 8 is a perspective view illustrating a state in which a blank plate is disassembled in a heat exchanger according to an embodiment, and FIG. 8 is a graph showing a heat dissipation amount and a refrigerant pressure drop amount according to a ratio of communication means to a total size in a heat exchanger according to a first embodiment of the present invention. 9 is a view showing the refrigerant flow of the heat exchanger according to the first embodiment of the present invention, Figure 10 is a refrigerant flow in the heat exchanger according to the first embodiment of the present invention It is a figure which shows a distribution.

As shown, the heat exchanger 100 according to the first embodiment of the present invention is formed by stacking a plurality of tubes 110 having a flow path 114 to allow the refrigerant to flow therein.

The tube 110 is formed by bonding a pair of plates 111 to each other, there are two flow paths 114 that are independent on both sides of the partition bead 113 formed perpendicularly to the center therebetween. At the upper and lower ends, a pair of cups 112 communicating with the flow paths 114 are formed to protrude side by side.

In addition, the tube 110 is formed by joining and stacking a pair of cups 112 to each other, the tanks 101 and 102 are formed at the upper and lower portions by the bonded pair of cups 112.

Meanwhile, a neck bead part 116 having a plurality of passages 116b partitioned into at least one second bead 116a is formed at each of the flow paths 114 of the tubes 110. It is made to flow evenly distributed into the flow path (114).

In addition, in the pair of plates 111 constituting the tube 110, a plurality of first beads 115 are formed to protrude inwardly by an embossing molding method along the flow path 114, and the fluidity of the refrigerant is increased. The grid is arranged regularly in diagonal direction to induce improvement and turbulence. In addition, the partition beads 113 and the first beads 115 formed on the pair of plates 111 are joined by brazing in contact with each other.

Meanwhile, the heat dissipation fins 120 are interposed between the stacked tubes 110 to promote heat exchange, and the outermost end plates of the heat dissipation fins 120 are reinforced to reinforce the plurality of tubes 110 and the heat dissipation fins 120. 130 is installed.                     

In addition, inlet and outlet pipes 150 and 151 are installed at both ends of any one of the upper and lower tanks 101 and 102 to allow the refrigerant to flow in and out. Hereinafter, in the present invention, a case in which the inlet and outlet pipes 150 and 151 are installed in the upper tank 101 will be described.

In addition, an inlet heat exchanger 103 is formed at a rear side of the laminated tube 110 in communication with the inlet pipe 150, and an outlet side heat exchanger 104 is provided at a front side in communication with the outlet pipe 151. Is composed.

In addition, the inlet and outlet pipes 150 and 151 are provided with the inlet and outlet pipes 150 and 151 so that the inlet heat exchanger 103 and the outlet side heat exchanger 104 communicate with each other. Communication means 140 which communicates each tank 101 of the side heat exchange part 103,104 by a predetermined area is provided.

That is, the inlet and outlet side heat exchangers 103 and 104 are cooled down by the compartment of the blank plate 111a to be described below from the upper tank 101 and returned from the lower tank 102 again. It has a refrigerant flow direction rising to the tank 101 side.

Therefore, the refrigerant flows from the upper tank 101 to the lower tank 102 on the inlet pipe 150 side based on the blank plate 111a at both the inlet and outlet side heat exchanger 103 and 104. On the 151 side, the refrigerant has the same refrigerant flow structure ascending from the lower tank 102 to the upper tank 101.

On the other hand, the communication means 140 is formed so as to communicate an area of 10 to 50% of the total size of the tank 101 to the upper tank 101 of the inlet and outlet side heat exchanger 103 (104). desirable. That is, the number of the tube 110 in which the communication means 140 is formed is comprised within 10 to 50% of the number of the entire tubes 110.

8 is a graph showing a heat dissipation amount and a refrigerant pressure drop amount according to a ratio of the number of communication path tube rows to the total number of tube rows in the heat exchanger according to the first embodiment of the present invention. It is understood that the ratio of 10% to 50% is an optimal value. If it is less than 10%, there is a problem that the amount of pressure drop in the refrigerant increases and at the same time, the amount of heat dissipation decreases. If the amount is less than 50%, the refrigerant flow path group of the outlet heat exchange part 104 provided with the outlet pipe 151 decreases. There is a problem that the amount of pressure drop in the refrigerant is increased and thus the amount of heat radiation is lowered.

Here, the communication means 140 is a pair of the tube 110 corresponding to the area of the 10 to 50% of the total tube 110 stacked between the inlet, outlet pipes 150, 151 It is formed by forming a communication path 141 communicating the cup 112 with each other, the communication path 141 is formed on the upper end of the tube (110).

On the other hand, in consideration of the refrigerant pressure drop and the amount of heat dissipation, the number of tube rows in which the communication path 141 is formed is more preferably 20 to 40% of the total number of tube rows of the heat exchanger 100.

In addition, the communication means 140 is preferably formed in an approximately intermediate region of the heat exchanger 100, and the number of the tubes 110 in which the communication path 141, which is the communication means 140, is formed is a distribution of refrigerant. And it may be set to the appropriate number in consideration of the pressure-side pressure drop amount or the heat exchange performance.                     

In addition, the communication paths 141 may all have the same size, but may be formed in different sizes, and the communication paths 141 may be formed in one row or several rows in the middle without being continuously formed. The communication path 141 may be closed to partially form only a necessary portion.

The heat exchange zones 106 and 107 which divide the inlet and outlet side heat exchangers 103 and 104 into a plurality of heat exchange zones 105 to 108 but communicate with the communication means 140 are partially overlapped with each other. The blank plate 111a is installed to be able to.

The blank plate 111a is installed at both sides thereof with the communication means 140 interposed therebetween, and one cup 112a positioned diagonally to each other is closed.

Thus, the inlet and outlet side heat exchanger 103 and 104 are partitioned into first, second, third and fourth heat exchanger regions 105 to 108 by the blank plate 111a, where the blank plate 111a is used. The area of the first heat exchange region 105 and the fourth heat exchange region 108 in the diagonal direction with the gap between them is the same, and the second heat exchange region 106 and the third heat exchange communicate with the communication means 140. The area of the region 107 is the same, and the second and third heat exchange regions 106 and 107 are partially overlapped with each other by the communication means 140.

Hereinafter, the refrigerant flow of the heat exchanger 100 according to the first embodiment of the present invention will be described with reference to FIG. 9.

First, the refrigerant introduced through the inlet pipe 150 flows back from the first heat exchange region 105 of the inlet side heat exchanger 103 to the second heat exchange region 106, and then the communication means 140. After moving to the outlet side heat exchanger 104 through this time, the flow returns from the third heat exchange region 107 to the fourth heat exchange region 108 and is discharged to the outlet pipe 151.

In more detail, the refrigerant introduced into the upper tank 101 of the first heat exchange region 105 through the inlet pipe 150 is lowered along the tube 110 to move to the lower tank 102 and the lower tank. The refrigerant moved to 102 flows into the lower tank 102 of the second heat exchange region 106.

The refrigerant that has moved to the lower tank 102 of the second heat exchange zone 106 this time rises along the tube 110 to move to the upper tank 101 to complete the heat exchange at the inlet side heat exchanger 103. do.

Subsequently, the refrigerant transferred to the upper tank 101 of the second heat exchange zone 106 is transferred to the third heat exchange zone 107 through a communication path 141 formed at an upper end of the tube 110 that is the communication means 140. It moves to the upper tank 101 of).

The refrigerant moved to the upper tank 101 of the third heat exchange zone 107 is lowered along the tube 110 to move to the lower tank 102, and the refrigerant moved to the lower tank 102 is the fourth heat exchange zone. It flows into the lower tank 102 of 108.

The refrigerant that has moved to the lower tank 102 of the fourth heat exchange region 108 is now risen along the tube 110 and moved to the upper tank 101 to complete the heat exchange at the outlet side heat exchanger 104. After it is discharged through the outlet pipe 151.                     

As described above, although the heat exchanger 100 of the present invention is also affected by gravity and inertial force during the flow of the refrigerant as shown in FIG. 10, the refrigerant flow direction of the inlet heat exchanger 103 and the outlet heat exchanger 104 is shown. Because of the same, that is, in the first heat exchange zone 105 and the third heat exchange zone 107 corresponding to each other in the flow direction of air, gravity acts on the refrigerant descending along the tube 110 as well as mutual heat exchange. The area is different, and in the second heat exchange area 106 and the fourth heat exchange area 108, both inertial forces act on the refrigerant rising along the tube 110 and the mutual heat exchange areas are different.

In addition, in the second heat exchange area 106, the refrigerant rising up along the tube 110 is biased toward the end of the tank 101, 102 to change the biasing direction toward the communication means 140 to bias the refrigerant. To reduce the amount of refrigerant to flow as uniformly as possible through each tube (110). That is, in the second heat exchange region 106, the amount of refrigerant flowing through the tube 110 increases gradually toward the ends of the tanks 101 and 102 by inertial force, but the communication means 140 is connected to the heat exchanger 100. By installing in the intermediate region, the direction of the refrigerant biased toward the ends of the tanks 101 and 102 is changed to the communication means 140 side.

Therefore, the air passing through the subcooling section of the outlet side heat exchange part 104 is allowed to pass through the overheating section of the inlet side heat exchange part 103 to the maximum, and the air passing through the superheating section of the outlet side heat exchange part 104 is the inlet. By allowing the subcooling section of the side heat exchanger 103 to pass as much as possible, the inlet and outlet side heat exchanger 103 and 104 have a complementary heat exchange effect, and thus the surface temperature difference decreases, thereby reducing the overall heat exchanger 100. The surface temperature distribution becomes uniform.

In addition, by forming the communication means 140 in a predetermined region between the inlet and outlet pipes 150 and 151, the amount of pressure drop on the refrigerant side can be reduced, and at the same time, the heat exchange performance is also improved, which is more advantageous for miniaturization. It is possible to install the inlet and outlet pipes 150 and 151 on both ends of the upper tank 101 by the flow path configuration, so that the front and rear pipes of the inlet and outlet pipes 150 and 151 can be easily disposed.

FIG. 11 is a perspective view illustrating a heat exchanger according to a second embodiment of the present invention, and description thereof will be omitted if only the parts different from the first embodiment are described.

As shown, the second embodiment has the same configuration as the first embodiment described above, but at least one of the upper and lower tanks 101 and 102 to promote the evaporation of the refrigerant to improve the heat exchange performance. The distribution hole 112b is formed in which the passage cross-sectional area of the inside is reduced.

Here, the distribution hole 112b is formed at the top cup 112 side of the tube 110 on which the communication means 140 is formed, and is formed at the outlet side heat exchanger 104 rather than the inlet side heat exchanger 103. It is preferable. Of course, a plurality of distribution holes 112b may be formed at various positions of the inlet and outlet side heat exchangers 103 and 104.

Therefore, when moving from the inlet side heat exchanger 103 to the outlet side heat exchanger 104 through the communication means 140, some of the refrigerant passes through the distribution hole 112b. It can improve heat exchange performance by promoting evaporation.

12 is a perspective view showing a heat exchanger according to a third embodiment of the present invention, Figure 12 is an exploded state of the tube formed in the communication path at the top and the bypass passage at the bottom in the heat exchanger according to the third embodiment of the present invention It is a perspective view which shows, and repeating description is abbreviate | omitted if only a part different from the above-mentioned 2nd Example is demonstrated.

As shown, the third embodiment has the same configuration as the above-described second embodiment, except that a part of the refrigerant returned from the lower tank 102 of the inlet side heat exchanger 103 receives the outlet side heat exchanger ( In order to bypass the lower tank 102 of the 104, the at least one tube 110 is formed with a bypass passage 145 in which a pair of cups 112 in communication with each other are connected to each other. will be.

Therefore, when the flow rate of the refrigerant flowing through the heat exchanger 100 is small, a portion of the refrigerant flowing through the inlet side heat exchanger 103 is bypassed directly to the outlet side heat exchanger 104 through the bypass passage 145. It is possible to improve the outlet air temperature distribution.

According to the present invention described above, the pair of cups in a certain region of the central portion of the heat exchanger to communicate with each other, the communication between the inlet and outlet side heat exchanger, as well as to make the flow direction of the refrigerant flowing therein, the deflection of the refrigerant And it is more advantageous for miniaturization by reducing the pressure drop of the refrigerant side and the heat exchanger of the inlet and outlet side to complement each other, the surface temperature distribution of the heat exchanger is uniform, the heat exchange performance is also improved.                     

The optimum heat dissipation amount can be obtained by configuring the ratio of the communication means (communication path) to the total size of the heat exchanger within 10 to 50%.

In addition, the inlet and outlet pipes can be provided at both end portions of the upper tank by the flow path configuration, so that the front and rear pipes can be easily disposed.

In addition, by forming a distribution hole with a reduced passage cross-sectional area inside the tank, the refrigerant passing through the distribution hole is atomized to promote evaporation and to improve heat exchange performance.

Also, by forming a bypass passage to bypass a portion of the refrigerant returned from the inlet side heat exchanger to the outlet side heat exchanger, when the flow rate of the refrigerant flowing through the heat exchanger is small, some of the refrigerant flowing through the inlet side heat exchanger exits. The bypass air temperature distribution is improved by bypassing directly to the side heat exchanger.

Claims (7)

A pair of plates 111 are joined to each other to form two independent flow paths 114 having partition beads 113 therebetween, and a pair of cups communicating with each of the flow paths 114 at upper and lower ends thereof. 112 is formed side by side and a plurality of tubes 110 are laminated to form the upper and lower tanks 101 and 102 by bonding the pair of cups 112; Inlet and outlet pipes 150 and 151 which are respectively installed at both ends of any one of the upper and lower tanks 101 and 102 to introduce and discharge refrigerants; In the laminated tube 110, the inlet-side heat exchanger 103 communicating with the inlet pipe 150 and the outlet-side heat exchanger 104 communicating with the outlet pipe 151 communicate with each other, Communication in which each tank 101 of the inlet and outlet side heat exchanger 103 and 104 provided with the inlet and outlet pipes 150 and 151 communicates 10 to 50% of the total size with the same flow direction. Means 140; The heat exchange areas (106, 107) partitioning the inlet and outlet side heat exchange parts (103, 104) into a plurality of heat exchange areas (105 to 108), and communicating with the communication means (140) so that some of them overlap each other. Blank plate 111a installed by closing one cup 112a positioned diagonally to each other with the communication means 140 therebetween. Heat exchanger comprising a. The method of claim 1, The communication means 140 is a communication between the pair of cups 112 to the tube 110 corresponding to the region of the tube 110 stacked between the inlet, outlet pipes 150, 151 mutually A heat exchanger, characterized by forming a communication path (141). The method of claim 2, The number of tube rows in which the communication path 141 is formed is 20 to 40% of the total number of tube rows of the heat exchanger (100). The method of claim 2, The communication means 140 is a heat exchanger, characterized in that formed in the middle region of the heat exchanger (100). The method of claim 1, At least one of the upper and lower tanks (101) (102) is a heat exchanger, characterized in that the distribution hole (112b) is reduced to reduce the cross-sectional area of the passage. The method of claim 5, wherein The distribution hole (112b) is a heat exchanger, characterized in that formed on the cup 112 side of the tube 110, the communication means 140 is formed. The method of claim 1, At least one tube 110 has a pair of cups 112 at a region side in which the refrigerant returns so that a part of the refrigerant returned from the inlet side heat exchanger 103 can be bypassed to the outlet side heat exchanger 104. Heat exchanger characterized in that the bypass passage (145) for communicating with each other is formed.

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