JP3627295B2 - Heat exchanger - Google Patents

Description

【００２５】
仕切り板７ａ、７ｂの効果により各流路２ａ、２ｂ、２ｃの体積流量が等しくＷとなったとすると、各流路２ａ、２ｂ、２ｃの流速Ｖは、次の数式２にて表される。
【００２６】
【数２】

【００２７】
上記数式２において、Ｘは各流路２ａ、２ｂ、２ｃの幅（図２参照）である。
また、各流路２ａ、２ｂ、２ｃの水力直径ｄは次の数式３にて表される。
【００２８】
【数３】

【００２９】
チューブ３の１つ目のブロック（チューブ３ａ〜３ｃ）と、２つ目のブロック（チューブ３ｄ〜３ｆ）と、３つ目のブロック（チューブ３ｇ〜３ｉ）に対する各流路２ａ、２ｂ、２ｃの平均通路長さをそれぞれＬ_１ 、Ｌ_２ 、Ｌ_３ としたとき、 各流路２ａ、２ｂ、２ｃの圧力損失ΔＰ_１ 、ΔＰ_２ 、ΔＰ_３ は次の数式４にて表される。
【００３０】
【数４】

【００３１】
そして、ΔＰ_１ ＝ΔＰ_２ ＝ΔＰ_３ となれば、各ブロックへの流入量はほぼ等しくなると考えられるため、各流路２ａ、２ｂ、２ｃの間隔Ａ、Ｂ、Ｃは、次の数式５を満足するような比率に設定すればよいことになる。
【００３２】
【数５】

【００３３】
なお、上述した各流路２ａ、２ｂ、２ｃの間隔Ａ、Ｂ、Ｃを決定するための計算は、入口タンク２の部分での圧力損失の差が各ブロックへの流入量の差に対する支配的要因であると考えて、入口タンク２の部分のみの圧力損失を計算しているが、その他の部分、例えば入口タンク２からチューブ３への流入損失や、チューブ３から出口タンク４への流出損失を考慮することより、各流路２ａ、２ｂ、２ｃの間隔Ａ、Ｂ、Ｃの比率をより高精度に計算できることはいうまでもない。
【００３４】
また、試作品を作り、実験結果から各流路２ａ、２ｂ、２ｃの間隔Ａ、Ｂ、Ｃの最適比率を求めることもできる。
いずれにしても、前記数式５から理解されるように、各流路２ａ、２ｂ、２ｃの間隔Ａ、Ｂ、Ｃが通路長さＬ_１ 、Ｌ_２ 、Ｌ_３ に対応した不等ピッチとなるように、仕切り板７ａ、７ｂの配設位置を設定することにより、各チューブ３への流量の均等化を大幅に改善できる。
【００３５】
なお、上述した図１、２の実施例構造では、入口タンク２内のみに仕切り板７ａ、７ｂを設置しているが、入口タンク２内でなく、出口タンク４内のみに同様の仕切り板７ａ、７ｂを設置してもよい。
また、入口タンク２内と出口タンク４内の両方に仕切り板７ａ、７ｂを設置してもよい。
【００３６】
また、上述した図１、２の実施例構造では、仕切り板７ａ、７ｂを２枚設置しているが、この仕切り板７ａ、７ｂの数をチューブ３の本数の増減等に対応して１枚のみとしたり、３枚以上としてもよい。
仕切り板７ａ、７ｂの数は、多いほど、前述したチューブ３のブロック数が増えて、１つのブロック当たりのチューブ数が減るので、各チューブ３への流体分配をより一層均等化できる。逆に、仕切り板７ａ、７ｂの数が少ないほど、各チューブ３への流体分配の均等さは低下するが、仕切り板７ａ、７ｂによる製造コストの上昇を抑制できる。このように、仕切り板７ａ、７ｂの数は目的に合わせて、容易に自由に選定することができる。
【００３７】
なお、上述した実施例では、本発明を自動車用空調装置の暖房用熱交換器に適用した例について述べたが、本発明はこれに限定されることなく、自動車のエンジン冷却用ラジエータ、自動車用空調装置の冷媒凝縮器、冷媒蒸発器等の熱交換器に適用でき、さらには自動車用以外の種々の熱交換器にも広く適用可能である。
【図面の簡単な説明】
【図１】本発明の一実施例を示す正面断面図である。
【図２】図１の熱交換器の側面断面図である。
【符号の説明】
１…入口パイプ、２…入口タンク、３、３ａ〜３ｉ…チューブ、
４…出口タンク、５…出口パイプ、７ａ、７ｂ…仕切り板。[0001]
[Industrial application fields]
The present invention relates to an improved structure for achieving a uniform temperature distribution of a heat exchange medium such as air in a heat exchanger having a large number of tubes, and is suitable for use in a heat exchanger for in-vehicle air conditioning. It is.
[0002]
[Prior art]
In recent years, in heat exchangers for in-vehicle use and the like, the demand for downsizing has increased, and it has become impossible to ensure a sufficient size of the tank portion. This tank part functions to distribute fluid to a large number of tubes and to collect fluids from a large number of tubes. Loss increases.
[0003]
As a result, when the flow rate of the fluid flowing into the heat exchanger tank is low, or when the fluid is a liquid or gas-liquid two-phase flow and is affected by gravity, the pressure loss in the tank portion A large amount of fluid flows through the tube communicating with the small part (the part close to the fluid inlet of the tank), and the flow rate of the fluid to the tube communicating with the part with a large pressure loss (the part far from the fluid inlet of the tank) is reduced. Since the flow rate is uneven between the tubes, the temperature difference of the heat exchange medium such as air that exchanges heat with the fluid flowing through the heat exchanger increases, and the temperature distribution increases. Occur. In the case of an air conditioner, this increase in temperature distribution results in variations in the temperature of air blown into the room, leading to deterioration in air conditioning feeling.
[0004]
Therefore, in Japanese Patent Application Laid-Open No. 4-155194, a multi-hole tube in which the same number of fluid passages as many tubes are formed in the inlet tank of the heat exchanger, Proposals have been made to equalize the flow rate of the fluid flowing into each of the multiple tubes by allowing the fluid to flow into each tube individually. Japanese Utility Model Laid-Open No. 61-18394 discloses a shape of an inlet tank having an air inlet and an outlet tank having an air outlet in an air inlet in a heat exchanger that cools compressed air like an intercooler of an automobile. A large number of streamlined guides having a shape that gradually decreases from one end provided with the air outlet toward the other end not provided with the inlet and outlet, and prevents the generation of vortex flow in the inlet and outlet tanks The thing which installed the board is proposed.
[0005]
[Problems to be solved by the invention]
However, in the former publication, since it is necessary to partition the inside of one multi-hole tube into a large number of passages, which is the same as the number of tubes, the multi-hole tube has a very complicated structure, and the manufacturing cost inevitably increases. . In addition, since the structure of the multi-hole tube is extremely complicated, there is a problem that variations in quality are likely to occur.
[0006]
In the latter publication, the tank shape is gradually reduced from one end where the air inlet and air outlet are provided to the other end side, so that the fluid flowing into the tank of the heat exchanger When the flow rate is low, or when the fluid is a liquid or gas-liquid two-phase flow and is affected by gravity, a large amount of fluid flows in the tube close to one end where the inlet / outlet is provided. Only a small amount of fluid flows through the tube on the other end side, and the flow rate of the fluid to each tube cannot be made uniform.
[0007]
The present invention has been made in view of the above points, and has a relatively simple configuration, and heat that can equalize the flow rate of fluid to each of a plurality of tubes regardless of the type of fluid. The purpose is to provide an exchanger.
[0008]
[Means for Solving the Problems]
In order to achieve the above object, the present invention employs the following technical means.
In invention of Claim 1, many tubes (3, 3a-3i) arranged in parallel,
An inlet tank (2) having a fluid inlet (1) and distributing fluid flowing from the fluid inlet (1) to the multiple tubes (3, 3a to 3i);
An outlet tank (4) having a fluid outlet (5) and collecting fluid from the multiple tubes (3, 3a to 3i) to flow out of the fluid outlet (5);
A partition plate (7a, 7b) installed in at least one of the inlet tank (2) and the outlet tank (4),
Due to the partition plates (7a, 7b), the flow path in the tank has a plurality of flow paths (2a, 2b, 2c) along the parallel arrangement direction (b) of the multiple tubes (3, 3a to 3i). The heat exchanger is characterized in that the pressure loss of the fluid in the plurality of flow paths (2a, 2b, 2c) is substantially equal.
[0009]
In invention of Claim 2, in the heat exchanger of Claim 1,
The fluid inlet (1) is arranged on one end side in the parallel arrangement direction (b) of the multiple tubes (3, 3a to 3i) in the inlet tank (2),
The fluid outlet (5) is arranged on one end side in the parallel arrangement direction (b) of the multiple tubes (3, 3a to 3i) in the outlet tank (4),
Average passage lengths (L _{1 to} L ₃ ) of the plurality of flow paths (2a, 2b, 2c) partitioned by the partition plates (7a, 7b) are opposed to the tubes (3a to 3c) on the one end side. The flow path (2c) facing the tubes (3g to 3i) on the other end side in the parallel arrangement direction (b) of the multiple tubes (3, 3a to 3i) rather than the flow path (2a) to be performed. It is characterized by being long.
[0010]
In invention of Claim 3, in the heat exchanger of Claim 1 or 2,
The intervals (A, B, C) of the plurality of flow paths (2a, 2b, 2c) partitioned by the partition plates (7a, 7b) are flow paths facing the tubes (3a-3c) on the one end side. The flow path (2c) facing the tube (3g-3i) on the other end side in the parallel arrangement direction (b) of the multiple tubes (3, 3a-3i) is larger than (2a). It is characterized in that the pitch is unequal.
[0011]
In invention of Claim 4, in the heat exchanger as described in any one of Claim 1 thru | or 3,
The partition plates (7a, 7b) are fitted and held in recesses (2d, 2e) provided in the tank, and are brazed.
In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of the Example description described later.
[0012]
[Effects of the invention]
According to the inventions described in claims 1 to 4, since the above technical means are provided, a partition plate for partitioning a plurality of flow paths in the tank for distributing and collecting the fluid in the heat exchanger is installed, Since the pressure loss of the fluid in the plurality of flow paths is made substantially equal, regardless of the type of fluid, the fluid flow rate to each of the multiple tubes is made uniform, and the heat exchange medium The temperature distribution can be made uniform.
[0013]
In addition, since the fluid flow rate to each tube can be made uniform with a relatively simple structure of installing a partition plate in the tank, a high-quality heat exchanger can be manufactured at low cost.
[0014]
【Example】
The present invention will be described below with reference to embodiments shown in the drawings.
1 and 2 show an embodiment of the present invention, which shows the case where the present invention is applied to a heating heat exchanger (heater core) of an automotive air conditioner. The case of water (warm water) as a circulating fluid will be described.
[0015]
Reference numeral 1 denotes an inlet pipe (fluid inlet), 2 denotes an inlet tank (upper tank) into which hot water flows from the inlet pipe 1, 3 denotes a plurality of tubes arranged in parallel, and the hot water flowing from the inlet pipe 1 is supplied to the inlet tank 2. In this way, a large number of tubes 3 are distributed. In the example of FIG. 1, nine tubes 3 a to 3 i are illustrated as the tubes 3, but a large number of about 30 tubes are provided in an actual product. In addition, the tube 3 has a flat cross section in which the length of the air (heat exchange medium) in the flow direction (see FIG. 2) is longer than the length in the direction perpendicular to the air flow direction (b) (see FIG. 1). Molded with metal.
[0016]
Since the inlet pipe 1 is arranged on one end side in the parallel arrangement direction B (left and right direction in FIG. 1) of the multiple tubes 3 in the inlet tank 2, hot water flowing from the inlet pipe 1 flows through the inlet tank 2. It flows in the tube parallel arrangement direction b.
An outlet tank (lower tank) 4 collects hot water from a large number of tubes 3 and flows out from an outlet pipe (fluid outlet) 5. The outlet pipe 5 is also disposed on one end side of the outlet tank 4 in the parallel arrangement direction B (the left-right direction in FIG. 1) of the multiple tubes 3.
[0017]
Reference numeral 6 denotes a corrugated fin, which is arranged and joined between a plurality of tubes 3. 7a and 7b are partition plates installed horizontally in the inlet tank 2, and by these two partition plates 7a and 7b, the hot water channel in the inlet tank 2 has three channels along the tube parallel arrangement direction b. It is partitioned into 2a, 2b and 2c.
The average lengths L ₁ , L ₂ and L ₃ of the _three hot water flow paths 2a, 2b and 2c partitioned by the partition plates 7a and 7b are opposed to the tubes 3a to 3c on one end side in the tube parallel arrangement direction b. The flow path 2c facing the tubes 3g to 3i on the other end side in the tube parallel arrangement direction B is longer than the flow path 2a to be performed.
[0018]
That is, the relationship L ₁ <L ₂ <L ₃ is set.
Also, intervals A, B, C (see FIG. 2) between the plurality of hot water flow paths 2a, 2b, 2c partitioned by the partition plates 7a, 7b are flow paths 2a facing the tubes 3a-3c on the one end side. Rather than unequal pitches, the flow paths 2c facing the tubes 3g to 3i on the other end side in the tube parallel arrangement direction B are larger.
[0019]
That is, the relationship of A <B <C is set.
The partition plates 7a and 7b are formed in a rectangular shape, and both end portions in the direction of arrow A are fitted and held in recesses 2d and 2e formed in the inlet tank 2 as shown in FIG. .
Each component of the heat exchanger described above is molded into a predetermined shape with a metal such as aluminum, and then temporarily assembled into the structure shown in FIGS. 1 and 2 and joined to the integrated structure by brazing in a heating furnace. It is like that.
[0020]
Next, the operation of the heat exchanger according to this embodiment in the above configuration will be described.
The hot water flowing in from the inlet pipe 1 is distributed in the inlet tank 2 to the three hot water flow paths 2a, 2b, 2c partitioned by the partition plates 7a, 7b. And the warm water distributed to the lowest warm water flow path 2a mainly flows into the tubes 3a to 3c. The warm water distributed to the intermediate warm water flow path 2b mainly flows into the tubes 3d to 3f, and the warm water distributed to the uppermost warm water flow path 2c mainly flows into the tubes 3g to 3i.
[0021]
The hot water that has flowed into each of the tubes 3a to 3i exchanges heat with air-conditioning air blown by a blower (not shown) through the corrugated fins 6 in the direction of arrow A, and radiates heat to the air-conditioning air. Therefore, the air for air conditioning is heated and becomes warm air.
The hot water that has finished heat exchange gathers in the outlet tank 4 and then flows out from the outlet pipe 5 to the outside.
[0022]
By the way, in the said heat exchange effect | action, it is desirable for the flow volume of the warm water which flows through each tube 3a-3i to make the temperature distribution of air-conditioning air uniform as much as possible. In order to equalize the hot water flow rate, the ratio of the cross-sectional areas of the three hot water flow paths 2a, 2b, 2c partitioned by the partition plates 7a, 7b, that is, the distances A, B between the flow paths 2a, 2b, 2c. , C ratio is important.
[0023]
Therefore, the concept for determining the ratio of the distances A, B, C between the flow paths 2a, 2b, 2c will be described below.
1 and 2, the two partition plates 7a and 7b are used, and a plurality of tubes 3 are connected to the tubes 3a to 3c and the tubes 3d to 3f by the partition plates 7a and 7b. Then, the case where it is divided into three blocks of the tubes 3g to 3i will be described. Generally, the fluid flowing in the flow path is subjected to the pressure loss ΔP according to the following formula 1.
[0024]
[Expression 1]

[0025]
Assuming that the volumetric flow rate of each flow path 2a, 2b, 2c is equal to W due to the effect of the partition plates 7a, 7b, the flow velocity V of each flow path 2a, 2b, 2c is expressed by the following formula 2.
[0026]
[Expression 2]

[0027]
In the above mathematical formula 2, X is the width of each flow path 2a, 2b, 2c (see FIG. 2).
Moreover, the hydraulic diameter d of each flow path 2a, 2b, 2c is represented by the following numerical formula 3.
[0028]
[Equation 3]

[0029]
The first block (tubes 3a to 3c) of the tube 3, the second block (tubes 3d to 3f), and the flow paths 2a, 2b, and 2c for the third block (tubes 3g to 3i). When the average passage lengths are L ₁ , L ₂ , and L ₃ , respectively, the pressure losses ΔP ₁ , ΔP ₂ , and ΔP ₃ of the flow paths 2 a, 2 b, and 2 c are expressed by the following Equation 4.
[0030]
[Expression 4]

[0031]
Then, if ΔP ₁ = ΔP ₂ = ΔP ₃ , the inflow amount to each block is considered to be substantially equal. Therefore, the intervals A, B, and C of the respective flow paths 2a, 2b, and 2c are expressed by the following Equation 5. It is sufficient to set the ratio to satisfy.
[0032]
[Equation 5]

[0033]
The calculation for determining the intervals A, B, and C of the flow paths 2a, 2b, and 2c described above is based on the fact that the difference in pressure loss at the inlet tank 2 is dominant over the difference in the amount of inflow into each block. The pressure loss of only the inlet tank 2 is calculated as a factor, but other parts such as the inflow loss from the inlet tank 2 to the tube 3 and the outflow loss from the tube 3 to the outlet tank 4 are calculated. Needless to say, the ratio of the intervals A, B, C between the flow paths 2a, 2b, 2c can be calculated with higher accuracy.
[0034]
It is also possible to make a prototype and obtain the optimum ratio of the intervals A, B, C between the flow paths 2a, 2b, 2c from the experimental results.
In any case, as can be understood from Equation 5, the intervals A, B, and C of the flow paths 2a, 2b, and 2c are unequal pitches corresponding to the passage lengths L ₁ , L ₂ , and L _3. Thus, by setting the arrangement positions of the partition plates 7a and 7b, the equalization of the flow rate to each tube 3 can be greatly improved.
[0035]
1 and 2, the partition plates 7a and 7b are provided only in the inlet tank 2. However, the same partition plate 7a is provided only in the outlet tank 4, not in the inlet tank 2. 7b may be installed.
Further, partition plates 7 a and 7 b may be installed in both the inlet tank 2 and the outlet tank 4.
[0036]
1 and 2, the two partition plates 7a and 7b are installed. The number of the partition plates 7a and 7b is one according to the increase / decrease in the number of the tubes 3, etc. Or 3 or more.
As the number of the partition plates 7a and 7b increases, the number of blocks of the tube 3 described above increases and the number of tubes per block decreases, so that the fluid distribution to each tube 3 can be made even more uniform. Conversely, the smaller the number of partition plates 7a and 7b, the lower the uniformity of fluid distribution to each tube 3, but it is possible to suppress an increase in manufacturing cost due to the partition plates 7a and 7b. Thus, the number of the partition plates 7a and 7b can be easily selected freely according to the purpose.
[0037]
In the above-described embodiment, the example in which the present invention is applied to a heating heat exchanger of an automotive air conditioner has been described. However, the present invention is not limited to this, and a radiator for cooling an engine of an automobile and an automobile The present invention can be applied to a heat exchanger such as a refrigerant condenser and a refrigerant evaporator of an air conditioner, and further widely applicable to various heat exchangers other than those for automobiles.
[Brief description of the drawings]
FIG. 1 is a front sectional view showing an embodiment of the present invention.
FIG. 2 is a side sectional view of the heat exchanger of FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Inlet pipe, 2 ... Inlet tank, 3, 3a-3i ... Tube,
4 ... outlet tank, 5 ... outlet pipe, 7a, 7b ... partition plate.

Claims (4)

Many tubes arranged in parallel,
An inlet tank having a fluid inlet and distributing fluid flowing from the fluid inlet to the plurality of tubes;
An outlet tank having a fluid outlet and collecting fluid from the plurality of tubes to flow out of the fluid outlet;
A partition plate installed in at least one of the inlet tank and the outlet tank,
The partition plate partitions the flow path in the tank into a plurality of flow paths along the parallel arrangement direction of the multiple tubes, and the pressure loss of the fluid in the plurality of flow paths becomes substantially equal. A heat exchanger characterized by the above. The fluid inlet is arranged on one end side in the parallel arrangement direction of the multiple tubes in the inlet tank,
The fluid outlet is arranged on one end side in the parallel arrangement direction of the multiple tubes in the outlet tank,
The average passage length of the plurality of flow paths partitioned by the partition plate is opposed to the tube on the other end side in the parallel arrangement direction of the multiple tubes rather than the flow path facing the tube on the one end side. The heat exchanger according to claim 1, wherein the flow path is longer. The interval between the plurality of flow paths partitioned by the partition plate is such that the flow path facing the tube on the other end side in the parallel arrangement direction of the multiple tubes rather than the flow path facing the tube on the one end side. The heat exchanger according to claim 1, wherein the pitches are unequal so as to be larger. The heat exchanger according to any one of claims 1 to 3, wherein the partition plate is fitted and held in a recess provided in the tank and brazed.

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