KR101104278B1 - Plate for heat exchanger - Google Patents

Abstract

The present invention relates to a plate for a heat exchanger, and more particularly, to form a bead of the neck bead portion asymmetrically, the beads on the flow path are formed in a streamlined and the same number in a zigzag arrangement to uniformly distribute the refrigerant flowing in the tank to each tube The present invention relates to a heat exchanger plate which is more advantageous for thinner and smaller heat exchanger by increasing heat dissipation and heat exchange efficiency by uniformly improving refrigerant flow distribution and reducing pressure drop on the refrigerant side.

Accordingly, in the present invention, the tank 140 provided at the end side in communication with the internal flow path 102 and both sides facing each other to turbulize the refrigerant flowing in the flow path 102 through the tank 140 are joined to each other. Neck beads having a plurality of passages 106b formed on the inlet and outlet sides of the flow path 102 and partitioned into one or more second beads 106a In the heat exchanger plate constituting the tube (100) consisting of 106, the first bead 105 is arranged in a zigzag array of rows of the same number each other, the second bead (106a) is the flow path ( 102, characterized in that formed asymmetrically arranged on the basis of the center line (C).

Heat exchanger, evaporator, plate, tube, neck bead, flow path, bead

Description

Plate for heat exchanger

1 is an overall perspective view showing a conventional heat exchanger (evaporator),

Figure 2 is a perspective view showing the separated state of the tube in a conventional heat exchanger,

3 is a view showing the top of the plate in FIG.

4 is a view showing the refrigerant flow distribution for the plate of FIG.

5 is a perspective view showing the separated state of the tube in the heat exchanger according to the present invention,

6 is a view showing the top of the plate in FIG.

7 is a graph showing the heat radiation performance and the refrigerant pressure drop amount with respect to the ratio of the width and length of the first bead;

8 is a view showing the refrigerant flow distribution for the plate of FIG.

9 is a view showing another form of the first and second beads formed on the plate in the heat exchanger according to the present invention;

10 is a view showing a symmetrical configuration of each of the first and second beads formed on the inlet and outlet sides of the plate in the heat exchanger according to the present invention.

Description of the Related Art [0002]

1: evaporator 2: inlet pipe

3: outlet pipe 10,100: tube

20, 20a: manifold tube 30: end plate

40,140: Tank 50: Heat dissipation fin

101: plate 102: euro

103: compartment bead 104: cup

105: first bead 106: neck bead part

106a: second bead 106b: passageway

The present invention relates to a plate for a heat exchanger, and more particularly, to form a bead of the neck bead portion asymmetrically, the beads on the flow path are formed in a streamlined and the same number in a zigzag arrangement to uniformly distribute the refrigerant flowing in the tank to each tube The present invention relates to a heat exchanger plate which is more advantageous for thinner and smaller heat exchanger by increasing heat dissipation and heat exchange efficiency by uniformly improving refrigerant flow distribution and reducing pressure drop on the refrigerant side.

The heat exchanger has a flow path through which a heat exchange medium can flow, so that the heat exchange medium and the outside air can be exchanged. It is used in various air-conditioning apparatuses. Many different formats are used.

In addition, an evaporator using a refrigerant as a heat exchange medium in the heat exchanger is formed by joining two tank plates each having a pair of cups formed at one end and a U-shaped flow path by a partition bead therein. 1 tank type formed by alternately stacking the field and the heat radiation fins,

A two tank type formed by alternately stacking tubes and heat dissipation fins formed by joining two tank plates each having cups formed at upper and lower ends thereof,

A four tank formed by alternately stacking tubes and heat dissipation fins formed by joining two four tank plates each having two flow paths separated from each other by an inner compartment bead and a pair of cups formed at both upper and lower ends. Type and the like.

Hereinafter, in the present invention, one tank type heat exchanger will be described as an example.

As shown in FIGS. 1 to 3, the heat exchanger 1 includes two plates 11 having a pair of cups 14 side by side formed with slots 14a formed at upper or upper and lower ends, respectively. And a pair of tanks 40 are formed by the cups 14 joined to each other, and the inside of the partition bead 13 formed by a predetermined length vertically between the pair of tanks 40. A plurality of U-shaped flow paths 12 communicating with the pair of tanks 40 are formed around the tube 10 and the heat dissipation fins 50 stacked between the tubes 10. And two end plates 30 installed at the outermost parts thereof for reinforcement of the tubes 10 and the heat dissipation fins 50.

In addition, a plurality of first beads 15 protrude inwardly and are joined to both sides of the plate 11 facing each other in order to turbulize the refrigerant flowing in the flow path 12 of the tube 10.

In addition, the neck bead portion having a plurality of passages 16b partitioned into a plurality of second beads 16a so that refrigerant is evenly distributed to the passages 12 at the inlet and outlet sides of the passages 12 of the respective tubes 10. 16 is formed.

In addition, since the double head plate is the same as the migraine plate 11 except that two cups are further formed at the lower end, only the migraine plate 11 having two cups 14 formed at the top for convenience will be described below. do.

In addition, among the tubes 10, the manifold tube 20 protruding the inlet manifold 21 toward one side of the tank 40 so as to be connected to the inlet pipe 2 to introduce the refrigerant, and the outlet A manifold tube 20a is also used in which the outlet side manifold 21a protrudes to one side of the tank 40 so as to be connected to the pipe 3 to discharge the refrigerant.

The manifolds 21 and 21a are formed in the shape of a circular pipe by contacting two manifold plates having semi-circular manifolds 21 and 21a with each other. The manifolds 21 and 21a thus formed are The manifold (21) (21a) and the inlet pipe (2) and the outlet pipe (3) can be joined to each other by combining with the inlet pipe (2) and the outlet pipe (3) by the brazing material of the ring shape and then brazing. .

In addition, the manifold tubes 20 and 20a have the same configuration as the tube 10 except for the manifolds 21 and 21a.

As described above, the refrigerant flow in the configured heat exchanger 1 will be described with reference to FIG. 1 as follows.

Prior to the description, in the tank 40 where the inlet and outlet side manifolds 21 and 21a of the refrigerant are formed, a baffle 60 for partitioning the refrigerant flowing into and the refrigerant flowing out is formed therein.

Thus, the pair of tanks 40 are divided into an inlet side 4 through which the refrigerant is introduced and an outlet side 5 through which the refrigerant is discharged, based on the baffle 60. 40 denotes " A " and " B " in the figure, and when the outlet 40 tank 40 through which the refrigerant is discharged is " C ", " D "

The refrigerant flowing through the inlet manifold 21 is evenly distributed to the "A" side of the tank 40 and then flows along the "U" -shaped flow path 12 of the tubes 10 and 20 to be adjacent. It flows into the "B" side of the other tank 40 and continues to the "C" side of the same tank 40, and flows again along the "U" -shaped flow path 12 of the tubes 10, 20a and exits The manifold 21a is introduced to the "D" side of the tank 40 is formed to be the final discharge.

The heat exchanger 1 exchanges heat with the air blown through the tubes 10, 20 and 20a in the process of introducing and discharging the refrigerant circulating in the cooling system along the refrigerant line to evaporate the refrigerant. The endothermic action by the latent heat of evaporation is to cool the air blown to the interior of the vehicle.

Recently, the trend of heat exchanger (1) development is thinner and smaller, so the heat exchanger (1) structure and performance must satisfy the high efficiency, low refrigerant side pressure drop. In particular, in the case of the refrigerant pressure drop, when the heat exchanger 1 becomes thinner and manufactured with the plate 11 having a conventional shape, a high refrigerant pressure drop occurs, thereby increasing the work of the compressor (not shown) and decreasing the system efficiency. There is a problem.

That is, in the related art, in order to promote the heat transfer performance and secure the durability of the heat exchanger 1 as described above, the first bead 15 is formed at regular intervals along the inner flow path 12 to be bonded to each other. In addition, in order to ensure uniform distribution and durability of the refrigerant stored in the tank 40 to the flow path 12, the neck bead part 16 having the second bead 16a formed at equal intervals is provided.

However, when the second bead 16a formed in the first bead 15 and the neck bead portion 16 is formed at equal intervals and symmetrically, as in the conventional plate 11, the refrigerant flows as shown in FIG. 4. Since the distribution is uneven, the heat dissipation amount and heat exchange efficiency are lowered, and accordingly, there are many difficulties in thinning and miniaturizing the heat exchanger 1.

That is, referring to FIG. 4, red is a portion where the flow rate of the refrigerant is high and the flow rate is high, and blue is a portion where the flow rate of the refrigerant is slow and the flow rate is low.

Therefore, when the plate 11 is viewed as a whole, there is a problem in that the central portion in the width (left and right) direction has a small flow rate and the flow rate is biased to both sides, and the central portion of the neck bead portion 16 has a large flow rate. As it flows away from both sides, the flow rate is lowered and the flow rate decreases.

In addition, when viewed from the length (up, down) direction of the plate 11, the farther away from the neck bead portion 16 there is a problem that the flow rate flows more and is also biased.

As such, it can be seen that the conventional plate 11 has a non-uniform refrigerant flow distribution of up, down, left and right as a whole.

An object of the present invention for solving the above-mentioned problems is that the second bead formed in the neck bead portion of the plate is asymmetrical with respect to the center line of the flow path and at the same time the first bead formed along the flow path is streamlined By forming the same number of rows arranged in a zigzag pattern, the coolant in the tank is uniformly distributed / inflowed into the flow path of each tube to uniformly improve the coolant flow distribution and reduce the pressure drop on the coolant side to increase heat dissipation and heat exchange. It is an object of the present invention to provide a plate for a heat exchanger having improved efficiency and more advantageous for thinning and miniaturizing a heat exchanger.

The present invention for achieving the above object is a tank provided on the end side in communication with the flow path therein, and a plurality of agents in which both sides facing each other in order to turbulence the refrigerant flowing in the flow path through the tank are bonded to each other In the heat exchanger plate comprising a bead and a tube formed on the inlet and outlet sides of the flow path and partitioned into one or more second beads and having a neck bead having a plurality of passages, the first bead is the same number. Each row formed of the plurality of rows is repeatedly arranged in a zigzag pattern, and the plurality of second beads are formed in an asymmetrical number with respect to the center line of the flow path, and each second bead is aligned with the first row of the first beads. The separation distance is formed non-uniformly, and the minimum separation distance between the second bead and the first bead with the smaller number of second beads relative to the center line Claim 2 is characterized in that the bead be formed smaller than the minimum separation distance between the large side of the second bead and the first bead.

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

The same parts as in the prior art will be described with reference to the drawings and the same reference numerals, and repeated description thereof will be omitted.

5 is a perspective view showing the separated state of the tube in the heat exchanger according to the present invention, Figure 6 is a view showing the upper portion of the plate in Figure 5, Figure 7 is a heat radiation performance against the ratio of the width and length of the first bead And a graph showing a refrigerant-side pressure drop amount, FIG. 8 is a diagram illustrating a distribution of refrigerant flow for the plate of FIG. 6, and FIG. FIG. 10 is a view showing a symmetrical configuration of first and second beads formed on the inlet and outlet sides of the plate in the heat exchanger according to the present invention.

First, the present invention will be found in advance that the same applies to the heat exchanger of the 1 tank type, 2 tank type, 4 tank type, and will be described for the 1 tank type for convenience.

As shown, the heat exchanger 1 according to the present invention is formed by joining two plates 101 having a pair of cups 104 formed in parallel with each other at the upper end and cups 104 joined together. A pair of tanks 140 are formed therebetween, and a pair of tanks 140 are communicated with the partition bead 103 formed therebetween vertically between the pair of tanks 140 by a predetermined length. The tube 100 is formed of a plurality of "U" -shaped flow path 102 to be stacked,

A heat dissipation fin 50 interposed in a bent form between the tubes 100 to widen the heat transfer area to promote heat exchange;

In order to reinforce the tube 100 and the heat dissipation fins 50, two end plates 30 are installed on the outermost side thereof.

In addition, among the tubes 100, a manifold tube 20 protruding from the inlet manifold 21 to one side of the tank 140 to be connected to the inlet pipe 2 to introduce the refrigerant, and the outlet pipe A manifold tube 20a is also used in which the outlet side manifold 21a protrudes to one side of the tank 140 so as to be connected to (3) to discharge the refrigerant.

Here, the manifold tubes 20 and 20a have the same configuration as the tube 100 except for the inlet and outlet side manifolds 21 and 21a protruding to one side.

In addition, a baffle 60 is formed in one tank 140 in which the inlet and outlet side manifolds 21 and 21a are formed to partition the refrigerant flowing in and the refrigerant flowing out.

The plurality of tubes 100 stacked by the baffle 60 are divided into an inlet side 4 through which the refrigerant is introduced and an outlet side 5 through which the refrigerant is discharged.

Therefore, the refrigerant flowing into the inlet pipe 2 flows along the “U” -shaped flow path 102 of the inlet side 4 tubes 20 and 100 separated by the baffle 60, and then the outlet side ( 5) and then flows along the "U" -shaped flow path 102 of the outlet side 5 tubes 20a and 100 and is then discharged through the outlet pipe 3. Of course, the refrigerant cools the outside air by heat exchange with the outside air in the course of sequentially flowing the inlet and outlet side 4 and 5 tubes 100.

In the heat exchanger 1, the neck bead portion 106 having a plurality of passages 106b partitioned into a plurality of second beads 106a at the inlet and outlet sides of the flow path 102 of the tubes 100. Is formed.

Here, the second bead (106a) is asymmetrically with respect to the center line (C) of the flow path 102 so that the refrigerant stored in the tank 140 can be uniformly distributed into the flow path (102). Array is formed.

That is, the second bead 106a is formed asymmetrically in number, spacing, or shape with respect to the center line C of the flow path 102.

FIG. 6 is a view illustrating an example of a plate in which the second bead is formed asymmetrically. The second bead 106a is formed on one side and the other side is based on the center line C of the flow path 102. One second bead 106a is formed. In addition, it can be seen that the second bead 106a is formed asymmetrically with respect to the spacing and shape therebetween.

Of course, the second bead 106a is asymmetrically formed in the number, spacing, or shape of the second bead, but is not necessarily limited thereto, and at least one or more of the number, spacing, and shape may be formed asymmetrically.

In addition, each of the second beads 106a is formed in a non-uniform spaced apart distance (L1, L2, L3) from the first row of the first bead 105, that is, at least one of the second bead (106a) It is preferable to form the above nonuniformly.

On the other hand, the second bead 106a formed asymmetrically has the second bead 106a and the first bead 105 having the smaller number of second beads 106a with respect to the center line C of the flow path 102. The minimum separation distance between the two is smaller than the minimum separation distance between the second bead 106a and the first bead 105 having the larger number of second beads 106a. In other words, it is preferable to form the beads 106a having the smaller number on the basis of the center line C of the flow path 102 longer or larger than the larger ones. Therefore, as the number of beads 106a is small, the size thereof is made long or large so that the refrigerant in the tank 140 is uniformly distributed to the flow path 102.

That is, each of the second beads 106a of the neck bead portion 106 is gradually increased in shape and size from one side to the other side, and at least one second bead 106a and at least one first. Beads 105 are arranged on the same line.

In addition, a plurality of first beads 105 are formed by joining side surfaces of a pair of plates 101 facing each other to turbulent refrigerant flowing in the flow path 102 of the respective tubes 100. .

That is, the first bead 105 is formed to protrude inwardly by the embossing molding method along the flow path 102 of the plate 101, and is arranged in a grid in a diagonal direction so as to improve the fluidity of the refrigerant and induce turbulent flow. . Thus, the first beads 105 formed on the pair of plates 101 are bonded by brazing in contact with each other.

In addition, the first bead 105 is arranged in a predetermined distance from each other, the columns formed in the same number to be uniform in the flow distribution of the refrigerant, it is preferable to be arranged repeatedly in a zigzag.

In addition, the first bead 105 is preferably formed in a streamline so as to reduce the amount of pressure drop on the refrigerant side.

That is, as the first bead 105 is streamlined, the pressure drop in the refrigerant side decreases, so that a large pressure does not occur at a stagnation point in the refrigerant inflow direction of the first bead 105 and the streamlined surface of the first bead 105 is reduced. It will flow smoothly along.

Accordingly, the first bead 105 according to the present invention is formed in a streamline to reduce the pressure of the tip in the direction in which the refrigerant flows, to improve the nonuniformity of the refrigerant flow distribution and to improve the heat transfer performance, the first bead 105 The ratio (W / L) of the width (W) and the length (L) of is limited, as shown in the graph shown in FIG.

The smaller the ratio W / L of the width W and the length L of the first bead 105, the lower the pressure drop on the refrigerant side, which is advantageous, while the heat dissipation performance is lowered (approximately 2-3%). ,

In addition, the larger the ratio (W / L) of the width (W) and the length (L), the heat dissipation performance is slightly increased and advantageous, while the pressure drop on the refrigerant side increases, resulting in uneven flow distribution of the refrigerant.

Therefore, in the present invention, it is preferable that the ratio (W / L) of the width W and the length L of the first bead 105 satisfies the following formula, 0.3 ≦ W / L ≦ 0.9, which is an appropriate range.

As described above, the flow distribution of the refrigerant according to the arrangement of the first bead 105 and the second bead 106a is shown in FIG. 8, and as shown, the conventional first bead 15 and the second bead It can be seen that the flow distribution of the refrigerant is improved more uniformly than when the structure 16a is configured at equal intervals and symmetry with respect to the centerline C of the flow path 12. In other words, the plate 101 as a whole, the speed difference in the width (left, right) direction and the length (up, down) direction of the flow path 102 can be seen that a uniform flow rate flows.

9 is a view showing another form of the first and second beads formed on the plate in the heat exchanger according to the present invention, and as shown, the number of the first beads 105 and the second beads 106a described above is increased. In other words, the first bead 105 is formed in each row three, and the second bead 106a is formed four.

Even in this case, the second bead 106a of the neck bead part 106 is formed asymmetrically with respect to the centerline C of the flow path 102, and the first bead 105 is formed in a streamline shape and is the same. Each column formed by the number is repeatedly arranged in a zigzag pattern.

On the other hand, in the above, although the second bead 106a of the neck bead portion 106 formed on the inlet and the outlet side of the "U" -shaped flow path 102 are formed in the same shape, as shown in FIG. You may. Moreover, the shape of the pair of cups 104 can also be comprised circularly.

As described above, in the present invention, regardless of the number of the first bead 105 and the second bead 106a, the second bead 106a of the neck bead portion 106 is the centerline C of the flow path 102. The first bead 105 is formed in a streamlined shape, and the same beads are repeatedly arranged in a zigzag pattern, so that the flow distribution of the coolant is uniform and the pressure drop on the coolant side is reduced to increase heat dissipation. And the heat exchange efficiency is improved to be more advantageous for thinning, miniaturization of the heat exchanger.

As described above, in the present invention, only the application of the arrangement form of the first bead 105 and the second bead 106a to the heat exchanger 1 of the one tank type has been described, but the present invention is not limited thereto. The first bead 105 and the second bead 106a may be variously modified within the scope of the present invention, and the same effect may be obtained even when the same structure is applied to a two tank or four tank type heat exchanger. Of course.

According to the present invention, the second bead formed in the neck bead portion of the plate is formed asymmetrically with respect to the center line of the flow path and at the same time the first bead formed along the flow path is formed in the same number of each By arranging the heat in a zigzag arrangement, the coolant in the tank is uniformly distributed / introduced into the flow path of each tube to uniformly improve the coolant flow distribution, reduce the pressure drop on the coolant side, increase heat dissipation, heat exchange efficiency, and heat exchanger. It is more advantageous for thinning and miniaturization of the battery.

Claims (6)

A plurality of tanks 140 provided at the end side in communication with the internal flow path 102 and both sides facing each other for turbulence of the refrigerant flowing in the flow path 102 through the tank 140 are bonded to each other and arranged. The first bead 105 and the neck bead portion 106 formed on the inlet and outlet sides of the flow passage 102 and partitioned into a plurality of second beads 106a are provided with a plurality of passages 106b. In the heat exchanger plate constituting the configured tube 100, The first bead 105, each row formed in the same number is repeatedly arranged in a zigzag pattern, The plurality of second beads 106a are asymmetrically arranged in number with respect to the centerline C of the flow path 102, and each second bead 106a is formed of the first bead 105. The distances L1, L2, and L3 from the first row are formed non-uniformly, and the second bead 106a and the first bead 105 having the smaller number of the second beads 106a based on the centerline C are formed. And a minimum separation distance between the plurality of second beads (106a) is smaller than the minimum separation distance between the second bead (106a) and the first bead (105). delete The method of claim 1, The second bead (106a) is a heat exchanger plate, characterized in that the gap between each asymmetric. The method of claim 1, The second bead (106a) is a heat exchanger plate, characterized in that the asymmetrical shape. delete The method of claim 1, The first bead 105 is made of a streamline, the ratio (W / L) of the width (W) and the length (L) satisfies the following equation, 0.3 ≤ W / L ≤ 0.9 .

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