KR100352876B1 - Plate for heat exchanger having enhanced evaporating performance and heat exchanger using it - Google Patents

Abstract

The present invention relates to a plate for a laminated heat exchanger and a heat exchanger using the same, and aims to increase the refrigerant fluidity, achieve the miniaturization of the heat exchanger, achieve an optimum heat exchange performance, and improve durability.

According to the present invention, the beads 25 formed in the heat exchange part 23 of the plate are regularly arranged. Among these beads, the ratio S / L of the area S formed by the center line connecting two adjacent rows of beads in the width direction to the width of the heat exchanger portion is 0.89 mm ≤ S / L ≤ 1.5 mm. The flow path spacing Gs between the refrigerant discharge side flange 29 of the heat exchange part and the beads adjacent in the width direction is 0.15 mm ≤ Gs ≤ 1.6 mm. A plurality of beads are formed on the bottom extension of the partition bead 24 that splits the heat exchange part left and right, and two beads adjacent to the partition bead are formed larger than the other beads. Reinforcing beads 28 are formed in both corners of the U-turn part 27 in a diagonal direction. In the manifold plate on the blank plate side, the length and width of the refrigerant inlet side first slot 22a are shorter than others. Three vertical beads 26 are formed in the lower portion of the cup 21 connected to the semi-circular manifold 131, and both of these vertical bead outer passages are blocked.

Description

Plate for heat exchanger with improved heat exchange performance and heat exchanger using same {PLATE FOR HEAT EXCHANGER HAVING ENHANCED EVAPORATING PERFORMANCE AND HEAT EXCHANGER USING IT}

The present invention relates to a laminated heat exchanger plate having improved heat exchange performance constituting a heat exchanger used in an automobile air conditioner, and a heat exchanger using the same. In particular, the present invention prevents the flow of refrigerant and improves the turbulence effect of the refrigerant. The heat exchange performance can be improved by improving the efficiency of the heat exchanger, and the heat exchanger can be miniaturized by having a certain rule in the arrangement relationship between the width of the plate and the bead, and the curved flow portion of the high pressure refrigerant in the flat tube composed of two plates The present invention relates to a plate for a laminated heat exchanger and a heat exchanger using the same, which has improved heat exchange performance, which can improve assembly and durability by securing adhesive rigidity.

The heat exchanger is a device configured to exchange heat between the refrigerant and the outside air by providing a passage through which the refrigerant flows, and is used in various air conditioners, and in particular, a laminated heat exchanger is mainly used in an automobile air conditioner.

15 to 17, the stacked heat exchanger has a pair of cups 911 and 911 having a slot 912 at the top thereof, and a plurality of beads in a central portion communicating with the pair of cups 911 and 911. 915 are projected into the inner surface by the embossing process, and the two-piece tank plate 91 formed with the U-turn 919 at the lower end is joined to each other by a partition bead 917 formed vertically in the center of the pair of tanks. (93,93) and a group of flat tubes (90) having a U-shaped passage as a whole, a group of pins (94) stacked between the flat tubes (90), the group of flat tubes (90) and the pin (94) It comprises two end plates 95 and 95 installed on their outermost side for reinforcement of the group. In addition, the tank 93 of any one of the two flat tubes 90 and 90 according to a predetermined flow path among the flat tube 90 groups has a manifold connected to a refrigerant inlet pipe (not shown) and a refrigerant discharge pipe (not shown). 96 are projected respectively. For example, in an air conditioner employing an evaporator as the heat exchanger, a refrigerant flows into a tank 93 of the refrigerant inlet tube 90 through a manifold 96 through an expansion valve (not shown) and a refrigerant inlet tube. When the refrigerant flows through the slots 912 into the tanks 93 of the adjacent flat tube 90, the tank 93 of the adjacent flat tube 90 and the tank 93 of the manifold tube 90. Heat exchange with the refrigerant and the blowing air in the process of flowing the refrigerant through the U-shaped passage to the other tank 93 group of each tube 90, and then again through the process as described above to the manifold on the refrigerant discharge pipe side The refrigerant flows into the tank 93 connected to the 96, and the refrigerant is discharged to the compressor through the manifold 96 and the refrigerant discharge pipe. The heat exchanged refrigerant is evaporated and supplied to the compressor in a gaseous state. On the other hand, in the case of the two-tank plate, except that two cups (911,911) in the upper portion, a pair of cups are formed in the lower portion, except that the rest of the configuration and operation is the same as the above-described 1-tank plate all 1-tank for convenience Only the plate will be described by way of example.

The performance of the evaporator that heats the blower air with the refrigerant and provides it to the vehicle interior depends on the value of the product of the heat transfer rate and the area, and mediates the group of fins 94 that are stacked between the groups of flat tubes 90 where low temperature refrigerant flows. This is caused by the heat exchange between the cold heat of the refrigerant and the high heat of the blowing air. That is, in order for the refrigerant to evaporate, an external heat having a larger amount of heat than that of the heat medium is required, and in order to increase the evaporation effect of the heat medium, the heat exchange area of the plate 91 in contact with the fin 94 is increased, and at the same time, the heat transfer rate is increased. It should be elevated. However, the heat exchanger used for automobile air conditioner is required to be miniaturized due to its high heat exchange performance in terms of weight reduction, noise reduction, air volume increase, and securing of vehicle mounting. it's difficult.

In order to solve this problem, a method of lowering the height of the fin 94 and increasing the density of the fin 94 has been proposed, but this method has a problem of drainage of condensate from the heat exchanger, pressure drop in the blower air, and air volume. In some cases, the heat exchange performance may be lowered due to the problem of reduction.

In addition, the factors influencing the heat exchange performance, the number, size, shape, arrangement or spacing of the beads 915 formed in the plate 91 has a large effect on the flow path area of the refrigerant. Crazy That is, in the case of a heat exchanger having a large capacity, the influence of the arrangement of the beads 915 may be somewhat small, but in the compact heat exchanger having a small width of the plate 91, the influence of the beads 915 is large. That is, when the size of the beads 915 is greater than a certain proportional value compared to the width of the plate 91 and the arrangement of the beads 915 is not dense, the flow resistance of the refrigerant is small but the refrigerant flows and the beads 915 By reducing the turbulent flow effect of the refrigerant, and also the thermal contact rate with the fin 94 can be reduced heat exchange efficiency. In addition, when the size of the beads 915 is larger than the width of the plate 91 and the arrangement of the beads 915 is dense, the evaporation effect of the refrigerant is greatly reduced because the flow resistance of the refrigerant is large. In this case, it may be considered to reduce the size of the beads, but it is not possible to make the size of the beads below a predetermined size, which is impossible due to manufacturing technology, and there are limitations due to the problem of bonding between the two plates.

The plate 91 is generally formed by cladding a brazing sheet, and as described above, a pair of cups 911 and 911, a heat exchanger 913 in which a plurality of beads 915 are formed, and a partition bead ( 917 and a U-turn 919. The flat tube 90 is formed by the joining of two plates 91 and 91, and the flat tube 90 has a pair of tanks 93 in which a pair of cups 911 and 911 are joined. Therefore, during the flow of the refrigerant from one tank 93 of the flat tube 90 to the other tank 93, the refrigerant passes through the U-turn part 919, while the refrigerant passes through the U-turn part 919. Because of the flow of the curve, the flow direction of the refrigerant is changed from the bottom to the opposite direction. Therefore, a relatively large pressure is applied to the U-turn portion 919 as compared to other flow path portions of the flat tube 90. However, only the beads 915 and 915 corresponding to each other of the two plates 91 and 91 are joined to the U-turn part 919 and the partition bead 917 formed vertically in the center extends to the lower end of the U-turn part 919. The U-turn portion 919 region is relatively weaker than the region where the partition bead 917 is located because it is not. Therefore, the beads 915 and 915 bonded to each other may be separated by the high flow pressure of the refrigerant. When the beads 915 in the U-turn 919 region are separated in this way, the high flow pressure of the refrigerant cannot be dispersed, and the flanges 916 and 916 are joined directly to each other in the U-turn 919 region to form the edges of the flat tube 90. By acting on the flange, the flanges 916 and 916 can be opened without overcoming the high pressure, and the refrigerant may leak.

This phenomenon in the U-turn portion 919 can be seen well through FIGS. 22 to 25. 22 to 25 are recently printed by measuring in 1997 using a CFD software called Fluent (Fluent) the refrigerant flow distribution is shown by installing the evaporator to which the plate is applied in a bottom mounting method.

The problem that results from the refrigerant flow distribution results is that the flow of the refrigerant is biased on the outer plate side. In other words, if the refrigerant flows to the plate outer side without uniformly distributed throughout the plate, the heat exchange efficiency of the entire evaporator formed by stacking a plurality of plates is severely affected. As described above, the U-turn portion 919 has a relatively large pressure than the other flow path portion, the vertically formed compartment bead 917 does not extend to the lower end of the U-turn portion 919 (see Fig. 16) fragile Therefore, the refrigerant flow pressure acts on the flange 916 forming the edge of the flat tube 90 in the U-turn 919 region. Therefore, as shown in red in FIGS. 22 to 25, the flow of the coolant is distributed to the coolant inlet side of the partition bead 917 and the flange 916 forming the edge of the plate, resulting in uneven coolant flow distribution. will be.

Meanwhile, the manifolds 96 protruding from one of the tanks 93 of the flat tubes 90 connected to the refrigerant inlet pipe and the refrigerant discharge pipe of the heat exchanger are in the form of pipes by joining two plates having a semicircular manifold. Is done.

When the heat exchanger is installed in the vehicle air conditioner, the tank 93 group faces upwardly (ie, the refrigerant inlet pipe and the refrigerant discharge pipe face upward), and the tank 93 faces downward. Bottom mounting (bottom mounting) is used, there is a slight difference in the characteristics of the heat exchange capacity, such as the evaporator installation method, the number of tubes 90, the location of the refrigerant inlet pipe and the refrigerant discharge pipe. Indeed, this difference can seriously affect the performance of a car air conditioner.

For example, the 24-row evaporator refers to an evaporator in which 24 pairs of plates 91, that is, 24 tubes 90 are stacked. In addition, a 24-column 4 / 7-4 / 7 pass evaporator means that 24 tubes 90 are stacked, and the arrangement of the tubes 90 is connected to four pairs of plates 91-refrigerant inlet pipes. 1 pair of manifold plates 91 (i.e. manifold tube 90)-7 pairs of plates 91, 4 pairs of plates 91-1 pair of manifold plates 91 to which refrigerant discharge conduits are connected ( That is, the evaporator is arranged in the order of the manifold tube (90)-seven pairs of plates (91). Then, the reinforcing end plates 95 are respectively installed on the outermost sides of the plates 91 or the outermost groups of the fin 94 groups, and the plates 91 (cups of the cups are blocked to serve as baffles). The plate blocking the refrigerant from flowing to the adjacent plate) is called a blank plate (ie, the "-" mark in 4 / 7-4 / 7 passes means that the end plate of 4/7 is the blank plate).

The following Table 1 shows the performance data according to the top mounting and bottom mounting installation method of the compact evaporator, and the evaporators composed of the paths shown in Table 1 are installed by the bottom mounting and top mounting installation method. Compared to the bottom mounting and top mounting, there is a difference of approximately 9%. This performance data is typically tested on an evaporator calorimeter held by a heat exchanger manufacturer to determine heat exchanger performance.

Bottom mounting Top mounting pass Q (kcal / h) Δpa (mmAq) ΔPr (kg / ㎠) Calories Q (kcal / h) Δpa (mmAq) ΔPr (kg / ㎠) 13-13A company 4,049 8.68 0.33 3,715 9.28 0.27 5-7-10B company 4,190 13.42 0.51 4,351 13.75 0.53 4 / 7-4 / 7 4,238 9.55 0.40 4,056 10.41 0.37 3 / 8-4 / 7 4,091 9.70 0.37 4,140 10.02 0.37

As described above, the performance difference of the "air conditioner test stand" is that the inventors have the same structure as the actual vehicle air conditioner for the purpose of developing the air conditioner and the heat exchanger unit by adjusting the flow rate of the refrigerant, the refrigerant pressure, the temperature, and the like. By using the experimental apparatus "to take a front temperature distribution using an infrared camera at about 1 meter away from the front of the evaporator, it was possible to confirm the degree of flow uniformity of the refrigerant as shown in Figures 18 to 21.

That is, in the case of the 24-row 4 / 7-4 / 7-pass evaporator, the refrigerant flows more toward the blank plate after the refrigerant flows into the refrigerant inlet manifold tube 90 in the top mounting method (see FIG. 19). As a result, the refrigerant does not flow well toward the end plate 95, and thus the refrigerant flow distribution is uneven throughout the evaporator. Accordingly, the cooling performance is lowered, and the difference in the refrigerant flow distribution according to the two installation methods is large.

In addition, as shown in FIG. 20 and FIG. 21, in the case of the 24-row type 3 / 8-4 / 7 pass evaporator, two installed by the bottom mounting method (see FIG. 20) and the top mounting method (see FIG. 21), respectively. It can be seen that the difference in refrigerant flow distribution in the case is very large.

As such, if the refrigerant flow distribution is uneven and the difference in the refrigerant flow distribution according to the bottom mounting installation method and the top mounting installation method is large, one evaporator cannot be selectively installed by the top mounting or bottom mounting installation method. Therefore, it is necessary to manufacture a heat exchanger having a separate specification separately according to the installation method, which hinders the common use of the heat exchanger, and also increases the productivity and reduce the manufacturing cost.

In addition, if the refrigerant flow distribution is uneven, the heat exchange performance is reduced, the cooling effect of the interior of the car is reduced, causing discomfort to the passengers.

As described above, the reason that the refrigerant flowing into the refrigerant inlet side manifold tube 90 flows more toward the blank plate than the end plate 95 side is because of the two manifold plates 91 and 91 on the refrigerant inlet side. No slot is formed in the slot 912 of the refrigerant inlet pipe side cup 911 of the manifold plate 91 side of the end plate 95, and the refrigerant inlet pipe side cup 911 of the manifold plate 91 of the blank plate side. This is because the burring portion is formed in the slot 912 of the.

The burring part prevents a poor bonding between the plates 91 when the plates 91 are stacked, and prevents the plates 91 from falling to one side when moving for brazing in the stacked state, but as described above. A flat plate 91 stacked outside the manifold plate 91 on the end plate 95 side has a burring portion inserted into the slot 912 of the manifold plate 91 and a blank plate side manifold plate ( The slot 912 of the 91 is provided with a burring portion inserted into the slot 912 of the flat plate 91 and joined to the slot 912. The slot 912 is introduced into the tank 93 of the manifold tube 90 through the refrigerant inlet tube. When the coolant flows toward the blank plate, the burring portion of the manifold plate 91 on the blank plate side is formed in the flow direction of the coolant so that the coolant can easily flow. have. On the other hand, when the refrigerant flows toward the end plate 95, the burring portion of the flat plate 91 stacked outside the manifold plate 91 on the end plate 95 side slot 912 of the manifold plate 91. ) Is projected into the cup 911 in a direction opposite to the flow direction of the refrigerant, so that the resistance is flowed by the burring portion of the flat plate 91, so that the end plate 95 is relatively closer to the blank plate side. A small amount of refrigerant will flow.

Therefore, the flow rate of the refrigerant flowing toward the blank plate is greater than the refrigerant flowing toward the end plate 95 so that evenly distributed refrigerant does not occur throughout the evaporator. As such, a difference in the refrigerant flow distribution causes cooling performance to decrease. In addition, the refrigerant flow distribution difference is increased according to the top mounting method and the bottom mounting method.

The present invention has been made in view of the above-described conventional problems, and an object thereof is to improve heat exchange performance by increasing refrigerant flowability.

Another object of the present invention is to evenly distribute the flow of the refrigerant, so that even when the air volume increases or decreases to feel almost uniform temperature so that the driver or passengers feel cool and comfortable.

It is still another object of the present invention to achieve an optimal heat exchange performance while miniaturizing the heat exchanger by having a predetermined rule in the relationship between the width of the plate and the bead arrangement.

Another object of the present invention is to improve the durability of the heat exchanger.

1 is a schematic front view showing an example of a stacked heat exchanger according to the present invention.

2 is a schematic perspective view showing an example of a stacked heat exchanger according to the present invention.

3 is a front view showing a heat exchange plate according to the present invention.

4 is a partially enlarged cross-sectional view illustrating a state in which heat exchange plates are bonded to each other to form a flat tube.

5 is a partially enlarged front view showing a refrigerant inflow side of the heat exchange parts constituting the heat exchange plate according to the present invention.

6 is a partial front view showing the refrigerant discharge side of the heat exchange part constituting the heat exchange plate according to the present invention.

7 is a graph showing heat exchange performance according to a set ratio between an area S formed by two bead rows of a heat exchange plate according to the present invention and a length L in a width direction of the plate.

8 is an exploded perspective view showing the main portion of a heat exchanger using a manifold plate according to the present invention.

9 is a perspective view showing a main portion of a heat exchanger using a manifold plate according to the present invention.

10 is a plan sectional view of FIG.

FIG. 11 is a front cross-sectional view of FIG. 9.

12 is an example of a heat exchanger using a manifold plate according to the present invention, in which a 24-row type 3 / 8-4 / 7 pass evaporator is installed in a bottom mounting method and a refrigerant flow distribution thereof is photographed by an infrared camera. to be.

13 is an example of a heat exchanger using a manifold plate according to the present invention, in which a 24-row type 3 / 8-4 / 7 pass evaporator is installed in a top mounting method and a refrigerant flow distribution thereof is photographed by an infrared camera. to be.

14 is a front view showing another example of the manifold plate according to the present invention.

15 is a front view showing an example of a conventional general laminated heat exchanger.

16 is a front view illustrating an example of a conventional general heat exchange plate.

17 is an exploded perspective view illustrating a state in which two conventional heat exchange plates are joined to form a flat tube.

18 is an example of a heat exchanger using a conventional manifold plate, a 24-row type 4 / 7-4 / 7 pass evaporator is installed in a bottom mounting method, and a refrigerant flow distribution thereof is photographed by an infrared camera.

19 is an example of a heat exchanger using a conventional manifold plate, and a 24-row type 4 / 7-4 / 7 pass evaporator is installed in a top mounting method, and a refrigerant flow distribution thereof is photographed by an infrared camera.

20 is another example of a heat exchanger using a conventional manifold plate, a 24-row type 3 / 8-4 / 7 pass evaporator is installed in a bottom mounting method, and a refrigerant flow distribution thereof is photographed by an infrared camera.

21 is another example of a heat exchanger using a conventional manifold plate, a 24-row type 3 / 8-4 / 7 pass evaporator is installed in a top mounting method, and a refrigerant flow distribution thereof is photographed by an infrared camera.

22 is an analysis diagram of a refrigerant flow distribution shown in a plate by installing an evaporator to which a conventional plate is applied by a bottom mounting method.

FIG. 23 is an enlarged view of the inlet of the plate in FIG. 22.

24 is an enlarged view of the heat exchanger of the plate in FIG. 22.

FIG. 25 is an enlarged view of the U turn portion of the plate in FIG. 22.

<Explanation of symbols for the main parts of the drawings>

1, 1a: tube, 2, 2a, 2b: plate,

4: pin, 5: end plate,

6: refrigerant inlet pipe, 7: refrigerant discharge pipe,

11: tank, 13: manifold,

21: cup, 22, 22a, 22b: slot,

23: heat exchanger, 24: compartment bead,

25: bead, 26: vertical bead,

27: U turn part, 28: reinforcement bead,

29: flange, 131: semi-circular manifold,

221: burring part

In order to achieve the above object, the present invention is formed side by side with a pair of cups each having a slot, and a partition bead and the plurality of cups by the partition bead vertically formed in the center and a plurality of By having a heat exchange portion formed by the embossing of the beads, beads having the same shape as the beads, U-turn portion formed by the partition bead, and a flange formed at the same height as the beads along an edge, In the laminated heat exchanger plate, in which a pair of tanks are formed when two are joined to each other, and a flat tube having a U-shaped passageway communicating with the pair of tanks as a whole, the beads are arranged to form a lattice in an oblique direction. Center line connecting the bead rows arranged in a line in the width direction, The ratio (S / L) of the area and the heat exchange section width which forms the center line connecting the bead column adjacent to the bottom characterized in that the 0.89mm≤S / L≤1.5mm. Due to the regular arrangement of the beads and the ratio (S / L), the fluidity and turbulence effect of the refrigerant may be improved, thereby increasing heat exchange efficiency.

Among the beads of the U-turn part, at least three beads are sequentially arranged in a predetermined arrangement below the partition beads, and two beads adjacent to the partition beads among the beads are larger in size than other beads. In addition, it is preferable that a slotted reinforcement bead is further formed at both corners of the U-turn part in a diagonal direction in the refrigerant flow direction. In this way, two of the three beads placed on the lower side of the partition bead are formed larger than the other beads, and further reinforcement beads are formed to join the two plates to form a flat tube in the U-turn portion where high pressure is applied. Rigidity that can withstand high pressure is secured and durability can be improved.

Further, it is preferable that the flow path interval Gs between the refrigerant flow-out flange of the plate and the beads adjacent in the width direction is 0.15 mm ≤ Gs ≤ 1.6 mm. If the flow path interval Gs is set in such a range, good refrigerant fluidity can be obtained by dispersing the refrigerant such that beads adjacent to the flange in the width direction do not flow into the refrigerant outflow flange.

In addition, the present invention is a laminated heat exchanger using the plate, a plurality of flat tubes formed by joining a pair of plates, a plurality of fins stacked between them, and the flat tubes and the outermost thereof It characterized in that it comprises two end plates are stacked.

In addition, the present invention, a pair of cups are formed side by side at the top and has a semi-circular manifold extending from one side of the cup and connected to the refrigerant inlet pipe, the slots are formed in each of the two cups in turn and the refrigerant A heat exchanger plate having a burring portion outwardly along an edge of a blank plate side slot of an inflow pipe side, wherein the length and width of the slot formed on the blank plate side of the refrigerant inlet pipe side and shorter than the length and width of another slot It features.

According to the present invention, it is preferable that the length x width of the blank plate side slot on the refrigerant inlet pipe side is 15 mm x 9 mm, and the length x width of the other slots is 16.6 mm x 10.8 mm. In addition, three vertical beads are formed in the lower portion of the cup connected to the semi-circular manifold, and the flow path between the two vertical beads on both sides of the vertical beads and the flange and the partition bead is preferably blocked.

As such, when the length and width of the refrigerant inlet pipe side slot in the manifold plate are shorter than the length and width of the other slots, the refrigerant flows more toward the end plate than the blank plate side in the heat exchanger. In reality, the burring portion formed in the small size slot is formed in the direction of refrigerant flow unlike other slots, so that the flow resistance of the refrigerant flowing toward the blank plate decreases, and consequently, The flow rates of the refrigerant flowing toward the blank plate are balanced with each other, so that the entire refrigerant distribution of the heat exchanger is uniform. Accordingly, even if the heat exchanger is installed in any of the bottom mounting method and the top mounting method, there is no difference in the refrigerant flow distribution.

In addition, the present invention is a laminated heat exchanger to which the manifold plate is applied, a plurality of pairs of plates, a second manifold plate on the end plate side to which the refrigerant inlet pipe is connected, and a first manifold plate on the blank plate side, many pairs Plates, one pair of manifold plates to which the refrigerant discharge pipes are connected, and a plurality of pairs of plates are arranged in this order, and the outermost side is reinforced by two end plates, and the first slot toward the refrigerant inlet pipe of the first manifold plate. The burring portion protrudes outwardly and is inserted into a slot of a plate stacked outside the first manifold plate, and is joined to the second slot of the refrigerant inlet pipe side of the second manifold plate. The burring part of the plate to be stacked on the plate is inserted and joined to each other, and the bar and the length and width of the first slot and the first slot The length and width of the burring part formed in the direction of an adjacent plate to be inserted into slotted, characterized in that is less than the length and width of the second slotted.

Other features and advantages of the present invention will become more apparent from the following detailed description based on the accompanying drawings.

As shown in FIGS. 1 and 2, the heat exchanger according to the invention comprises a plurality of flat tubes 1 of aluminum alloy, each of which has two plates 2 (see FIG. 3). ) Is made by brazing bonding. The flat tube 1 has a pair of tanks 11 and 11 at the upper end or the lower end, or a pair of tanks at the upper and lower ends, respectively, but only the number of tanks 11 is different and the rest of the structure is the same. Only the one having a pair of tanks in the upper end is shown and described here.

The fins 4 are sequentially stacked between the flat tubes 1, and on the outermost side thereof are reinforced with two end plates 5, 5. As shown in FIG. 3, the flat tubes 1 are formed by joining two plates 2 and 2 to each other, and among the flat tubes 1, a refrigerant inlet pipe 6 connected to an expansion valve (not shown). And two flat tubes having a manifold 13 (see FIG. 2) to which a refrigerant discharge pipe 7 connected to a compressor (not shown) are connected, respectively. The manifold tube 1a is referred to by a different designation, and the plates constituting the manifold tube 1a (see FIGS. 8 and 9) are also labeled with different reference numerals for convenience in the first and the first. The two manifold plates 2a and 2b are called.

As shown in FIG. 3, the plate 2 forming the flat tube 1 has a pair of cups 21 and 21 at its upper end, and slots 22 are formed in the cups 21, respectively. It is. Therefore, when the two plates 2 and 2 are joined, the tanks 11 are formed by the two cups 21 correspondingly joined to each other, and the flat tubes 1 are sequentially stacked, and thus, through the slots 22. The tanks 11 may communicate with each other.

Under the cups 21 of the plate 2, a bead 24 is formed perpendicularly to the center, and the heat exchanger 23 has a plurality of beads 25 formed on both sides of the bead 24. ) The partition bead 24 does not extend completely to the lower end of the plate 2 but extends leaving some lower end of the plate 2. For example, the compartment beads 24 extend about 1/8 of the length of the plate 2. In addition, the lower portion of the heat exchange part 23, that is, the lower portion of the compartment bead 24, is formed of the U-turn part 27 so that the refrigerant flows (see FIGS. 5 and 6) by turning down the compartment bead 24. A plurality of beads 25 are formed in a predetermined arrangement in the same arrangement as the beads 25.

The beads 25 may be simply formed to protrude to the inner surface by an embossing molding method, have a circular or elliptical cross section, and are preferably lattice-arranged regularly in an oblique direction to improve flowability and turbulence of the refrigerant. . In addition, the periphery of the edge of the plate 2 is preferably formed of a flange 29 having the same projected height as the beads 25. Thus, when the two plates 2 and 2 are in contact with each other, the flanges 29 and 29, the beads 25 and 25 and the partition beads 24 and 24 corresponding to each other in the two plates 2 and 2 are in contact with each other. When the brazing process is in contact with each other, the flat tube 1 may be formed by joining portions in contact with each other. The flat tube 1 is a half space of the heat exchangers 23 centered on one tank 11 (refrigerant inlet side tank 11) and joined compartment beads 24 of the flat tube 1. (Refrigerant inlet side passage), space between U-turn portions 27, the other half space (refrigerant outlet side passage) of the heat exchangers 23 around the compartment beads 24, and the other tank 11 (Refrigerant outflow side tank 11) passes in order to have a U-shaped passageway as a whole. That is, the partition beads 24 joined to each other serve as a partition wall, thereby forming a U-shaped passage as a whole. The compartment beads 24 and the beads 25 also serve to increase the mechanical strength of the plate 2.

The tips of the beads 25 are shown in FIG. 4 so that the joining state of the two plates 2 and 2 can be maintained satisfactorily by joining the partition beads 24 and 24 and the beads 25 and 25 corresponding to each other. It is preferable to make it flat, and although not shown, otherwise, one of the beads 25 corresponding to each other has a hole formed so that the tip of the other bead 25 is inserted into this hole and brazed. The two beads 25 and 25 may be joined together. The coolant flows through the flow paths formed by the beads 25 and 25 bonded in this way, and since the beads 25 are regularly lattice-arranged, turbulence flows when the coolant passes between the beads 25. And it flows.

According to the present invention, in order to improve the bonding strength of the U-turn part 27, since the flow direction of the coolant is changed to the U-turn part 27, the flow direction of the coolant is large, as shown in FIG. In the position of the lower end extension line of the partition bead 24 in the area (27), a plurality of (preferably three) beads 25 are formed so as to form a predetermined arrangement with the other beads 25 in turn. Among the beads 25 positioned on the bottom extension of the partition beads 24, two beads 25 adjacent to the partition beads 24 are preferably larger than the other beads 25. The remaining (preferably one) beads 25 are preferably formed in the same manner as the other beads 25 formed in the region other than the extension line of the partition beads 24. In addition, at both corners of the U-turn part 27, slotted reinforcement beads in a diagonal direction in the refrigerant flow direction can reduce the flow resistance and pressure of the refrigerant flowing in the U-turn part 27 and guide the flow of the refrigerant well. It is preferable that 28 are each formed further.

As shown in FIGS. 5 and 6, the plate 2 includes two centerlines C1 and C2 and a flange 29 connecting two adjacent bead rows in the width direction formed on either side of the partition bead 24. Optimum heat exchange efficiency can be obtained by determining a predetermined ratio with respect to the area formed by the partition beads 24 and the width direction length L of the plate 2. That is, when the center line C1 connecting one bead row and the center line C2 connecting the bead row adjacent to the upper or lower portion of the bead row are connected, the area S of the quadrangle S is divided by the partition bead 24 and the flange 29. ) Is compartmentalized. The area S is calculated as the area S of the bottom surface of the plate 2 without considering the areas of the beads 25 constituting the bead row. Experimental results show that the optimum heat exchange efficiency can be obtained by appropriately setting the ratio between the area S and the width direction length L of the plate 2. That is, the area S and the plate (in the relationship between setting the width direction length L of the plate 2 to 60 mm and setting the area S formed by the center line C1 and the center line C2 to 76.2 mm 2. It can be seen that the ratio (S / L) of the width L in the width direction 2) is 1.27 mm, and the ratio shows the optimum heat exchange efficiency. As can be seen from the graph of Fig. 7, it can be seen that even when the ratio (S / L) is in the range of 0.89 mm &lt; S / L &lt; 1.5 mm, good heat exchange efficiency can be obtained. The above ratio (S / L) does not take into account the external environment, and may change, for example, in consideration of the temperature of the air, the performance of the refrigeration cycle, or other environment, and thus the ratio (S / L) It is preferable not to fix X to 1.27 mm exactly but to set appropriately in the range of 0.89 mm ≤ S / L ≤ 1.5 mm.

When the ratio S / L is smaller than 0.89 mm, the flow resistance of the refrigerant is large, so that the internal pressure of the flat tube 1 is increased, thereby decreasing the fluidity of the refrigerant and deteriorating heat exchange efficiency. Because of this, the refrigerant is completely evaporated and cannot be supplied to the compressor in a gaseous state, and the liquid refrigerant is supplied to some compressors to damage the compressor. On the contrary, when the ratio S / L is larger than 1.5 mm, the flow resistance of the refrigerant decreases, so that the flowability of the refrigerant is good, but the turbulence effect caused by the beads 25 is reduced, so that the heat exchange efficiency is lowered. As a result.

The following Table 2 compares the performance of the heat exchanger to which the plate 2 according to the present invention and the heat exchanger to which the conventional plate 2 is applied through the calorimeter measurement data.

Tank section up (top mounting) Tank section downward (bottom mounting) Rate (S / L) Calories (kcal / h) Pressure (kg / ㎠) Calories (kcal / h) Pressure (kg / ㎠) Example (1.27mm) 4.238 0.40 4.056 0.37 Comparative Example (1.66mm) 4.049 0.33 3.715 0.27

According to Table 2, in the case of the heat exchanger (example) in which the above-mentioned ratio (S / L) is applied to the plate 2 according to the present invention by 1.27 mm, the ratio (S / L) of the conventional plate 2 is 1.66 mm. It can be seen that better performance is achieved regardless of the mounting method of the heat exchanger than the applied heat exchanger (comparative example).

Refrigerant fluidity in the tank 11 is also an important factor because the influence of the fluidity of the refrigerant on the heat exchange efficiency is significant, but the refrigerant fluidity in the plate 2 greatly affects the heat exchange efficiency. Therefore, although only the ratio (S / L) has a great influence on the heat exchange efficiency, it is shown and described here, but in addition to the height of the beads 25, and thus the volume relationship can also be considered by the ratio (S / L) Accordingly, the height and volume relationship of these beads 25 should also be included in the scope of the present invention.

In addition, although the experiment was explained above by limiting the width direction length L of the plate 2 to 60 mm, in the present invention, the width direction length L in the range of 45 mm to 63 mm is not limited to the length L. All may be applied to the plate (2) having. That is, in the case of the plate 2 having the short width direction L, the area occupied by the beads 25 is reduced, and conversely, in the case of the plate 2 having the long width direction L, the beads 25 are reduced. By increasing the area they occupy, it is possible to achieve the intention of the present invention.

On the other hand, as shown in Fig. 6, since the flow direction of the refrigerant is changed when the refrigerant flows through the U-turn portion 27, the flange 29 of the side (refrigerant outlet side) in which the flow direction of the plate 2 is changed by centrifugal force. As the refrigerant is biased and flows toward the refrigerant, the refrigerant does not flow evenly inside the plate 2, thereby degrading heat exchange efficiency. As described above, it is well understood that the refrigerant flow is biased by centrifugal force by the results of FIGS. 22 to 25 for the conventional plate described above.

In view of the above, in the present invention, in order to prevent the drift of the refrigerant, the refrigerant outlet side flange 29 of the plate 2 and the beads 25 adjacent to the flange 29 in the width direction (preferably a heat exchanger) The flow path gap Gs between the 23 and the beads 25 located at the boundary between the U-turns 27 is limited to a predetermined range, that is, the refrigerant 25 is adjacent to the flange 29 toward the refrigerant. Is guided to the center of the U-shaped passage without biasing toward the flange 29. The flow path spacing Gs is preferably 0.15 mm?

Meanwhile, in the heat exchanger, the refrigerant is introduced through the refrigerant inlet pipe 6 connected to the expansion valve and the refrigerant is discharged through the refrigerant discharge pipe 7 connected to the compressor, as shown in FIGS. 8 to 11. When refrigerant flows into the tank 11 of the manifold tube 1a (refrigerant inlet side) through the refrigerant inlet pipe 6, the adjacent flat tube is formed through the first slot 22a formed in the tank 11. Refrigerant flows to (1) and the refrigerant flows to the other tank 11 group through the U-shaped passages of the manifold tube 1a and the flat tubes 1 as described above, and thus the other tank ( 11) The refrigerant introduced into the group is likewise flowed into the adjacent tank 11 through the slots 22, and again through the U-shaped passages. The refrigerant discharge pipe 7 of the manifold tube 1a on the refrigerant discharge pipe 7 side. Flows into the tank (11) connected to the manifold (13) and cold It is supplied to the compressor via the discharge pipe 7.

As described above, in the conventional heat exchanger, when the refrigerant flows into the tank of the manifold tube of the refrigerant inlet pipe side, the refrigerant flows more toward the blank plate than the end plate side, causing uneven distribution of the refrigerant. The reason is that, among the two manifold plates constituting the refrigerant inlet tube side manifold tube, a burring portion is not formed in the slot of the refrigerant inlet tube side cup of the end plate side manifold plate, and the refrigerant inlet tube side of the manifold plate of the blank plate side is not provided. It is because the burring part is formed in the slot of a cup. As such, the unevenness of the refrigerant flow distribution becomes larger according to the top mounting installation method and the bottom mounting installation method.

In the present invention, a uniform refrigerant flow distribution can be obtained by improving the structure of the first manifold plate 2a, which is a blank plate side plate, among the plates constituting the refrigerant inlet pipe 6 side manifold tube 1a.

1, 2, and 8 to 11, the manifold tube (1a) is connected to the refrigerant inlet pipe (6) from one tank 11 to communicate with the inside of one tank (11) It has an extended protruding manifold 13 in the form of a circular pipe, and the manifold 13 is connected to the refrigerant inlet pipe 6 by brazing so that the refrigerant inlet pipe 6 and the manifold tube 1a can be connected. Can be. The manifolds 13 of the manifold tubes 1a may be formed by joining the first manifold plate 2a and the second manifold plate 2b with the semicircular manifold 131 to each other.

As shown in Fig. 10, the first manifold plate 2a is located on the blank plate side (arrow A direction), and the second manifold plate 2b is on the end plate 5 side (arrow B direction). Defined as being located.

A burring portion 221 protrudes outward along the edge of the first slot 22a formed in the cup 21 on the refrigerant inlet pipe 6 of the first manifold plate 2a. The burring portion 221 is inserted into the slot 22 of the plate 2 stacked adjacent to the outside of the first manifold plate 2a. Also, unlike the first slot 22a of the first manifold plate 2a, a burring portion is not formed in the second slot 22b formed on the refrigerant inlet pipe 6 side of the second manifold plate 2b. The burring part 221 formed in the slot 22 of the plate 2 joined to the outer side of the 2nd manifold plate 2b is inserted and joined.

According to the present invention, as shown in FIGS. 8, 10, and 11, the length and width of the first slot 22a and the plate 2 laminated outside the first manifold plate 2a are provided. The length and width of the slot 22 formed to insert the burring portion 221 formed in the first slot 22a is the length of the second slot 22b formed in the second manifold plate 2b and Shorter than width The length x width of the second slot 22b is 16.6 mm x 10.8 mm, and the length x width of the slot 22 into which the first slot 22a and the burring portion 221 are inserted and joined is 15 mm x 9 mm. It is preferable. Of course, the first slot 22a formed on the first manifold plate 2a and the plate 2 stacked on the outer side of the first manifold plate 2a are combined with the first slot 22a. It is preferable that the sizes of the slots 22 formed on the plate 2 other than the slot 22 are all the same as the size of the second slot 22b.

As described above, when the size of the first slot 22a is smaller than the size of the second slot 22b, the coolant inlet pipe 6 of the manifold tube 1a is provided through the coolant inlet pipe 6. When the refrigerant flows into the side tank 11, the refrigerant flows toward the end plate 5 through the second slot 22b, which is relatively large, and is smaller than the second slot 22b. The coolant also flows toward the blank plate through the one slot 22a. At this time, although the size of the second slot 22b is larger than that of the first slot 22a, the refrigerant flows more toward the end plate 5, but in reality, the second manifold plate 2b is used. The flow rate of the refrigerant is reduced by flow resistance by the burring portion 221 formed on the plate 2 stacked on the outer side of the second manifold plate 2b and inserted into the second slot 22b of the second manifold plate 2b. Therefore, the flow rate of the refrigerant flowing toward the end plate 5 and the flow rate of the refrigerant flowing toward the blank plate are balanced with each other, so that the overall refrigerant distribution of the heat exchanger is uniform, and any of the installation methods of the bottom mounting and top mounting installation methods Even if it is installed, the refrigerant flow distribution does not differ. 12 and 13, the refrigerant flow distribution is installed in accordance with the bottom mounting installation method and the top mounting installation method of the heat exchanger consisting of 3 / 8-4 / 7 array to install the infrared camera at the front 1 meter point The temperature distribution was used to confirm the results.

Then, if a uniform refrigerant flow distribution can be obtained, the burring portion 221 is not formed along the edge of the blank plate side slot 22 on the refrigerant inlet pipe 6 side as in the prior art, and this refrigerant inlet pipe 6 The length and width of the blank plate side slot 22 on the side of) may be formed shorter than the length and width of the slot 22 side slot 22.

Meanwhile, in the manifold tube 1a to which the manifold plates 2a and 2b having such a structure are applied, when the refrigerant flows into the tank 11, the manifold plates 2a and 2b flow toward the adjacent tanks 11 through the first slots 22a. Differences may arise in the flow distribution of the refrigerant and the refrigerant flowing from the tank 11 on the refrigerant inlet pipe 6 side of the manifold tube 1a toward the heat exchange unit 23. That is, there is a fear that the refrigerant flows more toward the heat exchange unit 23.

Under each cup 21 of the plates 2a and 2b, three vertical beads 26, 26 and 26 are generally inward as shown in FIG. 3 so that the refrigerant flows from the tank 11 toward the heat exchanger 23. The flow path is formed by protruding into the shape. In the present invention, as shown in FIG. 14, the structure of the three vertical beads 26, 26, 26 formed under the cup 21 connected to the semicircular manifold 131 is shown. The uniformity of the refrigerant flow distribution is achieved by changing. That is, of the three vertical beads 26, 26, 26 formed at the bottom of the cup 21 connected to the semicircular manifold 131, the flow path between the two vertical beads 26, 26 and the flange 29 is blocked. The flow distribution of the coolant flowing toward the heat exchanger 23 through the flow path between the vertical beads 26 and the coolant flowing toward the adjacent tanks 11 through the slots 22, 22a and 22b is uniform. . Therefore, the heat exchange performance is further increased because the flow of the refrigerant is more evenly distributed.

Effects of the heat exchanger plate 2 and the laminated heat exchanger plate 2 having improved heat exchange performance according to the present invention are as follows.

First, an area formed by two center lines C1 and C2 connecting adjacent bead rows arranged in a straight line in the width direction of the plate 2 on the refrigerant inlet side or the refrigerant outlet side of the heat exchange unit 23 ( Flowing between the beads 25 by arranging the beads 25 so that the ratio S / L of S) to the widthwise length L of the plate 2 is in the range of 0.89 mm S / L ≤ 1.5 mm As the refrigerant fluidity is improved and turbulent flow of the refrigerant is well induced, the optimum heat exchange efficiency can be achieved.

Second, by setting the flow path interval Gs between the refrigerant outlet side flange 29 of the plate 2 and the beads 25 adjacent in the width direction so as to be in the range of 0.15 mm? As the coolant flows toward the outlet side flange 29 and can be evenly dispersed by the beads 25 adjacent to the flange 29, good refrigerant fluidity can be obtained, thereby further increasing heat exchange efficiency.

Third, when the refrigerant flows toward the end plate 5 through the second slot 22b, the flow resistance is caused by the burring portion 221 of the plate 2 stacked on the outside of the second manifold plate 2b. In consideration of the above, the size of the first slot 22a of the first manifold plate 2a, which is formed for the refrigerant flow on the blank plate side, is relatively smaller than that of the second slot (2b) of the second manifold plate 2b. Since the refrigerant is uniformly flowed to the end plate 5 and the blank plate by reducing the size of 22b), there is almost no difference in the refrigerant flow distribution even if the heat exchanger is installed by any of the top mounting method and the bottom mounting method. The heat exchange performance can be improved, and the heat exchanger can be used in common, so that the standard of the heat exchanger can be excluded according to the installation method.

Fourth, two vertical beads (26, 26) on both sides of the three vertical beads (26, 26, 26) formed in the lower portion of the cup (21) connected to the semi-circular manifold (131), partition bead (24) and flange Refrigerant flows through the slots 22a and 22b to the adjacent tanks 11 and through the flow path between the vertical beads 26 from the tank 11 on the manifold 13 side. By uniformizing the flow distribution of the refrigerant flowing toward the portion 23, the refrigerant flow distribution can be made more uniform, so that the heat exchange performance is further improved.

Fifth, the size of the two beads (25, 25) placed adjacent to the partition bead 24 on the lower extension of the partition bead (24) larger than the other beads (25) U-turn portion that a relatively large pressure acts ( 27 is reinforced to improve durability of the flat tube 1, and thus, two plates 2 and 2 constituting the flat tube 1 are not separated, thereby preventing the leakage of the refrigerant.

Sixth, the slot-type reinforcement beads 28 are formed at both corners of the U-turn part 27 in the diagonal direction in the refrigerant flow direction, thereby further reinforcing the U-turn part 27 to flat tube 1 and manifold tube 1a. ) Durability is further improved, and the flow of the refrigerant is smoothly guided by the reinforcing beads 28 to reduce the flow resistance of the refrigerant, thereby improving the fluidity of the refrigerant, thereby further increasing heat exchange performance. .

Claims (10)

(Single correction) A pair of cups formed side by side at the top and each slot having a slot and a partition bead vertically formed in the center are partitioned from the pair of cups and a plurality of beads are used for embossing. When the two are joined to each other by having a heat exchanger formed by the formed, beads having the same shape as the beads and a U-turn formed by the partition bead, and a flange formed at the same height as the beads along an edge thereof, In the laminated heat exchanger plate forming a flat tube having a pair of tanks and having a U-shaped passage that communicates with the pair of tanks as a whole, The beads are arranged regularly so as to form a grid in an oblique direction, The ratio (S / L) between the area formed by the center line connecting the bead rows arranged in a straight line in the width direction and the center line connecting the bead rows adjacent to the upper or lower portion of the beads and the width of the heat exchanger portion is 0.89. Laminated heat exchanger plate with improved heat exchange performance, characterized in that mm≤S / L≤1.5mm. The plate type heat exchanger plate of claim 1, wherein a flow path gap Gs between the refrigerant discharge side flange of the heat exchange part and the beads adjacent in the width direction is 0.15 mm ≤ Gs ≤ 1.6 mm. The bead according to claim 1 or 2, wherein a plurality of beads are formed at predetermined intervals on a lower extension line of the partition bead among the beads of the U-turn portion, and two of the beads adjacent to the partition bead are different from each other. It is formed larger in size, and both sides of the U-turn portion of the laminated heat exchanger plate is improved heat exchange performance, characterized in that the slot type reinforcement beads are further formed in the diagonal direction of the refrigerant flow direction. A pair of cups formed side by side at the top and each slot having a slot, and partitioned with the pair of cups by partition beads vertically formed at the center, and a plurality of beads formed by embossing, The bead of the same type as the beads and the U-turn portion formed by the partition bead, and has a flange formed at the same height as the beads along the edge, so that when the two are bonded to each other a pair of tanks In the laminated heat exchanger plate which is formed and forms a flat tube having a U-shaped passage communicating with a pair of tanks as a whole, The flow path gap (Gs) between the refrigerant discharge side flange of the heat exchange part and the beads adjacent in the width direction is 0.15 mm ≤ Gs ≤ 1.6 mm. A pair of cups formed side by side at the top and each slot having a slot, a semi-circular manifold extending from one cup and joined to the refrigerant inlet pipe, and an outer side along the edge of the blank plate side slot on the refrigerant inlet pipe side. Burr portion protruded toward the side, a partition bead vertically formed in the center and the heat exchanger is partitioned with the pair of cups and formed with a plurality of beads, beads formed in the same shape as the beads and the partition beads By having a U-turn portion formed by and a flange formed along the edge and the same height as the beads, when the two are joined to each other, a pair of tanks are formed and a U-shaped passageway in communication with the pair of tanks as a whole In the plate for laminated heat exchanger forming a manifold tube, The length and width of the slot on the blank plate side of the refrigerant inlet pipe side is shorter than the length and width of the other slot, characterized in that the heat exchanger plate with improved heat exchange performance. 6. The heat exchange performance of claim 5, wherein the length × width of the blank plate side slot on the refrigerant inlet pipe side is approximately 15 mm × 9 mm, and the length × width of the other slots is approximately 16.6 mm × 10.8 mm. Laminated heat exchanger plate. 7. The three vertical beads of claim 5 or 6 are formed at predetermined intervals so as to form a flow passage through the heat exchange portion at a lower portion of the cup connected to the semi-circular manifold, and two vertical ones of both of the three vertical beads are formed. A plate for laminated heat exchangers having improved heat exchange performance, characterized in that the flow path between the beads, the compartment beads, and the flange is blocked. (Single correction) The length X width of the blank plate side slot on the refrigerant inlet tube side is approximately 15 mm x 9 mm, and the length x width of the other slots is approximately 16.6 mm x 10.8 mm, and the blank plate Laminated heat exchanger plate with improved heat exchange performance, characterized in that no burring portion is formed outward along the edge of the side slot. A pair of cups formed at an upper end portion, a heat exchanger partitioned with the pair of cups by a partition bead formed perpendicularly to the center, and having a plurality of beads formed thereon, and beads having the same shape as the beads A plurality of flat tubes in which two plates having a U-turn portion formed by the partition beads and a flange formed along the edge and flush with the beads are joined to each other; A plurality of pins stacked between them formed by joining a pair of plates; And a flat heat exchanger and two end plates stacked on the outermost side thereof. The beads are arranged regularly so as to form a grid in an oblique direction, The ratio (S / L) between the area formed by the center line connecting the bead rows arranged in a straight line in the width direction and the center line connecting the bead rows adjacent to the upper or lower portion of the beads and the width of the heat exchanger portion is 0.89. Multilayer heat exchanger, characterized in that mm≤S / L≤1.5mm. (Once corrected) Multiple pairs of plates, blank plate side manifold plate to which refrigerant inlet pipe is connected and second manifold plate to end plate, multiple pair of plates, one pair of manifold plate to which refrigerant outlet pipe is connected The outermost side is reinforced by the two end plates, and a burring portion protrudes outward from the first slot toward the refrigerant inlet pipe of the first manifold plate, thereby forming the first manifold plate. In the stack type heat exchanger which is inserted into the slot of the plate to be laminated to the outside and joined, the burring portion of the plate to be laminated to the outside of the second manifold plate is inserted into the second slot of the refrigerant inlet pipe side of the second manifold plate. , The length and width of the first slot, and the length and width of the slot of the adjacent plate to which the burring portion formed outwardly formed in the first slot is bonded, is shorter than the length and width of the second slot Stacked heat exchanger.