JP2006336873A - Heat exchanging tube and heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanging tube having sufficient pressure resistant strength and small passage resistance while keeping light weight, and improving heat exchanging performance. <P>SOLUTION: This heat exchanging tube is applied to a header type heat exchanger. This heat exchanging tube is constituted to satisfy relationships of W=6 to 18 mm, Ac/At×100=50 to 70%, and P/L×100=350 to 450%, where " W" is a width of a tube main body 61, "Ac" is a total cross-sectional area of a refrigerant passages 65, "At" is a total cross-sectional area of the tube main body 61 (including the refrigerant passages), "L" is an external perimeter of the tube main body 61, and "P" is a total inner perimeter of the refrigerant passages 65. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger such as a condenser and an evaporator in a refrigeration cycle such as an automobile air conditioner, a home air conditioner, a refrigerator, and an electronic device cooler, and a tube for the heat exchanger.

  Conventionally, as a condenser in a refrigeration cycle of an automotive air conditioner, as shown in Patent Document 1 below, a heat exchanger called a multi-flow type is often employed.

  In this heat exchanger, a plurality of heat exchanger tubes that are connected in communication with both headers at both ends are arranged in parallel in the vertical direction between a pair of vertical headers, and a partition member provided in the header Thus, a plurality of heat exchanger tubes are divided to form a plurality of paths. The gas refrigerant flowing in from the refrigerant inlet of the header is circulated through each path in order to be condensed and liquefied, and flows out from the refrigerant outlet of the header.

The size of such a heat exchanger is determined by the required heat dissipation performance, the size of the installation space, and the like. For example, a flat tube having a width of about 20 mm is generally used as the heat exchanger tube. in use.
International Publication No. WO02 / 42706

  The heat exchanger is mainly mounted on a vehicle such as an automobile or a truck. In such a vehicle, in recent years, for the purpose of improving fuel consumption and reducing harmful exhaust gases (CO2, NOX), There is a strong demand for weight reduction. For this reason, weight reduction of all automobile parts is calculated | required and the said heat exchanger is no exception.

  Under these circumstances, to reduce the weight of the heat exchanger, set the tube height low, set the outer wall thickness of the tube thin, or set the fin between the tubes thin. A method etc. can be considered.

  However, these weight reduction methods are approaching the limit, and if the weight reduction is promoted based on these methods, the original performance of the heat exchanger is reduced. For example, when the tube height is set low, the cross-sectional area of the refrigerant passage in the tube is reduced, the passage resistance is increased, the inner peripheral length of the refrigerant passage is shortened, and the heat dissipation performance is lowered. Further, when the wall thickness of the tube outer peripheral wall is set to be thin, the pressure resistance is lowered. Further, if the fin is set thin, the temperature difference between the fin in contact with the tube and the fin central portion becomes large, and the heat dissipation performance is lowered.

  This invention eliminates the above-mentioned problems of the prior art, can achieve sufficient pressure resistance while achieving weight reduction, and can further reduce passage resistance and improve heat exchange performance. An object is to provide a tube and a heat exchanger.

  The inventor diligently analyzed the configuration of a heat exchanger tube such as a condenser in detail from all angles, and further repeated detailed experimental research based on the analysis result. And as a heat exchanger, the optimum condition which can achieve the said objective was discovered, and it came to make this invention.

  That is, the gist of the first invention is as follows.

(1) In the heat exchanger tube in which a plurality of refrigerant passages extending in the tube length direction are formed in parallel in the tube width direction in a flat tube body having a predetermined length,
The tube body width is “W”, the refrigerant passage total cross-sectional area is “Ac”, the tube main body cross-sectional area (including the refrigerant passage portion) is “At”, and the tube main body outer perimeter is “ When “L” and the total inner perimeter of the refrigerant passage are “P”, the following relational expressions (A) to (C):
W = 6-18mm ... (I)
Ac / At × 100 = 50 to 70 (%) (B)
P / L × 100 = 350 to 450 (%) (C)
A tube for a heat exchanger, characterized in that

  Hereinafter, the heat exchanger tube of the invention described in the same paragraph 1 (first invention) is a multiflow type heat exchanger used as a condenser or the like in a refrigeration cycle of an automotive air conditioner, as shown in FIGS. 1 and 2. Applicable.

  In this heat exchanger, a plurality of heat exchanger tubes (60) are connected in parallel between a pair of headers (50) and (50) extending in the vertical direction, with both ends communicating with both headers (50) and (50). The fins (51) are disposed between the tubes (60) and outside the outermost tube (60), and the side plates (52) are disposed outside the outermost fins (51). Be placed. Moreover, the heat exchange tube (60) is divided by the partition member (53) provided in the header (50) (50), and a plurality of paths (C1) to (C3) are formed. And the gas refrigerant which flowed in from the refrigerant inlet (50a) of the header upper part distribute | circulates each path | pass (C1)-(C3) in order, and is condensed and liquefied by the heat exchange with external air at the time of the distribution | circulation, (50b).

  The tube (60) in this heat exchanger is constituted by an extruded tube made of an extruded product of aluminum (or an alloy thereof).

  As shown in FIGS. 3 and 4, the heat exchanger tube (60) has a flat tube body (61) having a height (H) smaller than a width (W).

  The tube body (61) includes an outer peripheral wall (63) and a partition wall (64) formed integrally with the outer peripheral wall (63). The partition wall (64) is continuously formed in the tube length direction so as to be bridged between the upper wall and the lower wall of the outer peripheral wall (63). A plurality of refrigerant passages (65) having a rectangular cross section extending along the tube length direction are partitioned by the partition walls (64) inside the outer peripheral wall (63) of the tube main body (61). They are formed in parallel in the width direction.

  Here, in the heat exchanger tube (60) of the present invention, it is necessary to establish the above relational expressions (A) to (C).

  Relational expression (A) specifies the tube width (W), and it is necessary to set the tube width (W) to 6 to 18 mm. That is, when the tube width (W) is too wide (over 18 mm), there is a risk that the weight will increase and it may be difficult to achieve the initial purpose. Conversely, when the width (W) is too narrow (less than 6 mm), the refrigerant passage (65) cannot be secured to a sufficient size, the refrigerant passage resistance increases, and the inner periphery of the refrigerant passage (65). If the length is reduced, the heat dissipation performance is lowered, and it may be difficult to obtain sufficient heat exchange performance. The tube width (W) is preferably set to 6 to 14 mm, and more preferably 7 to 12 mm.

  The relational expression (b) specifies the relationship between the total cross-sectional area (Ac) of the refrigerant passage (65) and the total cross-sectional area (At) including the refrigerant passage portion of the tube body (61). / At "× 100 needs to be set to 50 to 70 (%), preferably 55 to 65 (%). That is, if “Ac / At” is too small (less than 50%), the passage resistance of the refrigerant increases, pressure loss increases, and the tube weight may increase. Conversely, when “Ac / At” is too large (when it exceeds 70%), the flow path cross-sectional area increases, the flow rate of the refrigerant in the tube decreases, and the heat transfer rate may decrease.

  The relational expression (c) specifies the relationship between the outer perimeter (L) of the tube main body (61) and the total inner perimeter (P) of the refrigerant passage (65), and “P / L” × 100 needs to be set to 350 to 450 (%), more preferably 360 to 420 (%). That is, when “P / L” is too small (less than 350%), the heat transfer property is lowered and sufficient heat performance as a heat exchanger cannot be obtained. On the other hand, if “P / L” is too large (over 450%), for example, when the tube is made of an aluminum extrusion molded product, a dense shape is required for the extrusion mold, which may make it difficult to manufacture the tube. There is. Furthermore, even if a three-dimensional shape processing method or a method of forming communication holes (refrigerant passages) by roll forming or the like, the mold may have a dense shape and it may be difficult to manufacture the tube.

  In the heat exchanger having the heat exchanger tube of the first invention, since it has the configuration described in the same paragraph (1), it is possible to obtain sufficient pressure resistance while achieving weight reduction, The passage resistance can be reduced, and the heat exchange performance can be improved.

  On the other hand, in this 1st invention, it is preferable to employ | adopt the structure as described in the following (2)-(7) items.

(2) The following relational expression (d):
P / W × 100 = 750-850 (%) (D)
The tube for a heat exchanger according to the preceding item (1), which is configured so that

  The same item (2) specifies the relationship between the total inner peripheral length (P) of the tube body (61) and the tube width (W), and “P / W × 100” is set to 750 to 850 (%). It is preferable to set to. That is, when this “P / W” deviates from the above specified value, it is not possible to obtain a good passage shape, and there is a risk that the heat exchange performance may be lowered due to an increase in passage resistance or a decrease in heat conductivity. .

(3) When the number of the refrigerant passages is “N”, the following relational expression (e):
N / W = 3-4 (pieces / mm) (e)
3. The heat exchanger tube according to the preceding item 1 or 2, wherein the tube is configured so that

  The item (3) specifies the relationship between the number (N) of the refrigerant passages (65) and the tube width (W), and sets “N / W” to 3 to 4 (pieces / mm). Is good. That is, when this “N / W” is too small (less than 3 / mm), the number of widths of the partition wall (64) may be reduced and the pressure resistance may be lowered. On the other hand, when “N / W” is too large (in the case of more than 4 / mm), the width of the passage (65) becomes small, and the heat exchange performance may be deteriorated due to an increase in passage resistance.

(4) When the height of the tube body is “H”, the following relational expression (f):
H = 0.5-1.5mm (F)
4. The heat exchanger tube according to any one of the preceding items 1 to 3, wherein

  The item (4) specifies the tube height (H), and it is desirable to set the tube height (H) to 0.5 to 1.5 mm. In other words, if the tube height (H) is too high (over 1.5 mm), the tube size increases, resulting in an increase in weight, which may make it difficult to achieve the initial purpose. Conversely, when the tube height (H) is too low (less than 0.5 mm), the refrigerant passage (65) cannot be secured to a sufficient size, the refrigerant passage resistance increases, and the refrigerant passage (65 ), The heat dissipation performance decreases, and it may be difficult to obtain sufficient heat exchange performance.

  In addition, in order to set the tube height (H) to less than 0.5 mm, the thickness of the outer peripheral wall (63) of the tube main body (61) is made thin so as to secure the size of the refrigerant passage (65). Then, the pressure resistance of the outer peripheral wall (63), and thus the pressure resistance of the entire tube may be reduced.

(5) When the thickness of the partition wall between adjacent refrigerant passages in the tube body is “Ta”, the following relational expression (g):
Ta = 50-80 μm (G)
5. The heat exchanger tube according to any one of the preceding items 1 to 4, wherein the tube is configured so that

  The same item (5) specifies the thickness (Ta) of the partition wall (64) between adjacent refrigerant passages in the tube body (61), and the partition wall thickness (Ta) is set to 50 to 80 μm. Is more preferable. That is, when the thickness (Ta) is too thin (less than 50 μm), the strength of the partition wall (64) is lowered, and it may be difficult to obtain sufficient pressure resistance. Conversely, if the partition wall thickness (Ta) is too thick (over 80 μm), the refrigerant passage (65) cannot be secured to a sufficient size, and the refrigerant passage resistance increases and the heat exchange performance may be reduced. There is.

(6) When the thickness of the outer peripheral wall in the tube body is “Tb”, the following relational expression (h):
Tb = 80 to 250 μm (H)
6. The heat exchanger tube according to any one of the preceding items 1 to 5, wherein

  The item (6) specifies the thickness (Tb) of the outer peripheral wall (63) of the tube body (61), and it is even more preferable to set the outer peripheral wall thickness (Tb) to 80 to 250 μm. . That is, when the thickness (Tb) is too thin (less than 80 μm), the strength of the outer peripheral wall (63) is lowered, and it may be difficult to obtain sufficient pressure resistance. On the other hand, if the outer peripheral wall thickness (Tb) is too thick (over 250 μm), the refrigerant passage (65) cannot be secured to a sufficient size, and the refrigerant passage lowers and the heat exchange performance may deteriorate. There is.

  (7) The heat exchanger tube according to any one of the preceding items 1 to 6, wherein the refrigerant passage has a substantially rectangular cross section.

  In the item (7), since the refrigerant passage (65) is formed in a substantially rectangular (quadrangle) cross section, the inner peripheral length of the refrigerant passage (65) and the refrigerant are compared with, for example, a circular cross section. A large passage cross-sectional area can be secured. For this reason, in the configuration described in the paragraph (7), the heat radiation resistance can be increased, the passage resistance can be decreased, and the heat exchange performance can be further improved.

  The preferred configurations of the preceding items (2) to (7) can be applied to the second to fourth inventions described later, respectively, and exhibit the same effects as described above.

  In order to achieve the above object, the second invention has the following structure.

(8) In a heat exchanger tube in which a plurality of refrigerant passages extending in the tube length direction are formed in parallel in the tube width direction in a flat tube body having a predetermined length,
The tube body width is “W”, the tube body height is “H”, the partition wall thickness between adjacent refrigerant passages in the tube body is “Ta”, and the outer peripheral wall thickness in the tube body is “ When “Tb” is assumed, the following relational expressions (A) (F) (G) (G):
W = 6-18mm ... (I)
H = 0.5-1.5mm (F)
Ta = 50-80 μm (G)
Tb = 80 to 250 μm (H)
A tube for a heat exchanger, characterized in that

  When applied to a heat exchanger, the heat exchanger tube of the invention described in (8) of the same paragraph (8) obtains sufficient pressure resistance while reducing the weight as in the first invention. In addition, the passage resistance can be reduced and the heat exchange performance can be improved.

  In order to achieve the above object, the third invention is summarized as follows.

(9) In a heat exchanger in which a plurality of heat exchanger tubes that are connected to both headers in communication with each other between a pair of headers are arranged in parallel in the header length direction,
The tube for heat exchanger is formed in a flat tube body having a predetermined length, and a plurality of refrigerant passages extending in the tube length direction are arranged in parallel in the tube width direction.
The tube body width is “W”, the refrigerant passage total cross-sectional area is “Ac”, the tube main body cross-sectional area (including the refrigerant passage portion) is “At”, and the tube main body outer perimeter is “ L "and the total inner perimeter of the refrigerant passage is" P ",
When the thickness of the partition wall between adjacent refrigerant passages in the tube main body is “Ta”, the following relational expressions (A) to (C):
W = 6-18mm ... (I)
Ac / At × 100 = 50 to 70 (%) (B)
P / L × 100 = 350 to 450 (%) (C)
It is comprised so that may be materialized, The heat exchanger characterized by the above-mentioned.

  Since the invention (third invention) described in the same item (9) specifies a heat exchanger using the heat exchanger tube of the first invention, it is sufficient to reduce the weight in the same manner as described above. In addition to achieving high pressure resistance, the passage resistance can be reduced and the heat exchange performance can be improved.

  In order to achieve the above object, the fourth invention has the following structure.

(10) In a heat exchanger in which a plurality of heat exchanger tubes that are connected to both headers in communication with each other between a pair of headers are arranged in parallel in the header length direction.
The tube for heat exchanger is formed in a flat tube body having a predetermined length, a plurality of refrigerant passages having a rectangular cross section extending in the tube length direction, arranged in parallel in the tube width direction,
The tube body width is “W”, the tube body height is “H”, the partition wall thickness between adjacent refrigerant passages in the tube body is “Ta”, and the outer peripheral wall thickness in the tube body is “ When “Tb” is assumed, the following relational expressions (A) (F) (G) (G):
W = 6-18mm ... (I)
H = 0.5-1.5mm (F)
Ta = 50-80 μm (G)
Tb = 80 to 250 μm (H)
It is comprised so that may be materialized, The heat exchanger characterized by the above-mentioned.

  The invention (fourth invention) described in the same item (10) specifies a heat exchanger using the heat exchanger tube of the second invention, and thus, as in the above, it is sufficient to reduce the weight while sufficiently reducing the weight. In addition to achieving high pressure resistance, the passage resistance can be reduced and the heat exchange performance can be improved.

  In the second to fourth inventions, the preferable range of the tube width (W) is 6 to 14 mm as in the first invention.

  According to the present invention, it is possible to obtain sufficient pressure resistance while achieving weight reduction, and further, it is possible to reduce the passage resistance and improve the heat exchange performance.

  Examples of the invention will be described below.

<Example 1>
A heat exchanger tube was produced according to the above embodiment (FIGS. 3 and 4). At this time, as shown in Table 1 above, the total cross-sectional area (Ac) of the refrigerant passage is 5.29 mm ² , the total cross-sectional area (At) of the tube body is 8.92 mm ² , and the total inner peripheral length (P) of the refrigerant passage 64.1 mm, the outer perimeter (L) of the tube body is 17.3 mm, the total cross-sectional area (Ac / At) of the refrigerant passage relative to the total cross-sectional area of the tube main body is 59%, and the refrigerant passage relative to the outer perimeter of the tube main body The total inner perimeter (P / L) is 371%, the number of refrigerant passages (N) is 28, the tube height (H) is 1.15 mm, the tube width (W) is 8 mm, and the refrigerant passage relative to the tube width is The total inner perimeter (P / W) is 801%, the number of passages (N / W) relative to the tube width is 3.50 / mm, the partition wall thickness (Ta) of the tube body is 0.06 mm, and the outer wall thickness (Tb) ) Was adjusted to 0.1 mm.

  Furthermore, using the heat exchanger tube, a heat exchanger as shown in FIG. 1 was produced.

<Example 2>
As shown in the above table 1, the "Ac" 8.36Mm ^2, the "At" 13.5 mm ^2, the "P" 101.2Mm, the "L" 25.3 mm, the "Ac / At" 62% , "P / L" 400%, "N" 44, "H" 1.15mm, "W" 12mm, "P / W" 843%, "N / W" 3.67 / Mm, “Ta” was adjusted to 0.06 mm, and “Tb” was adjusted to 0.1 mm, a heat exchanger tube was prepared in the same manner as described above, and a heat exchanger was similarly prepared.

<Example 3>
As shown in Table 1 above, “Ac” is 11.3 mm ² , “At” is 18.1 mm ² , “P” is 131.8 mm, “L” is 33.3 mm, and “Ac / At” is 63%. , "P / L" 396%, "N" 57, "H" 1.15mm, "W" 16mm, "P / W" 824%, "N / W" 3.56 / Mm, “Ta” was adjusted to 0.06 mm, and “Tb” was adjusted to 0.1 mm, a heat exchanger tube was prepared in the same manner as described above, and a heat exchanger was similarly prepared.

<Comparative Example 1>
As shown in Table 1 above, “Ac” is 22 mm ² , “At” is 46.1 mm ² , “P” is 55 mm, “L” is 35.4 mm, “Ac / At” is 48%, “P / “L” is 155%, “N” is 4 pieces, “H” is 3 mm, “W” is 16 mm, “P / W” is 344%, “N / W” is 0.25 piece / mm, “Ta” Was adjusted to 0.5 mm, and “Tb” was adjusted to 0.5 mm, and a heat exchanger tube was produced in the same manner as described above.

<Comparative Example 2>
As shown in Table 1 above, “Ac” is 7.15 mm ² , “At” is 18.1 mm ² , “P” is 74.7 mm, “L” is 32.1 mm, and “Ac / At” is 40%. , "P / L" 233%, "N" 28, "H" 1.15mm, "W" 16mm, "P / W" 467%, "N / W" 1.75 / Mm, “Ta” was adjusted to 0.14 mm, and “Tb” was adjusted to 0.2 mm, a heat exchanger tube was prepared in the same manner as described above, and a heat exchanger was similarly prepared.

<Comparative Example 3>
As shown in the above table 1, the "Ac" 4.16 mm ^2, the "At" 18.1 mm ^2, the "P" 59.8Mm, the "L" 32.1 mm, "Ac / At" 23% , 186% "P / L", 26 "N", 1.15mm "H", 8mm "W", 748% "P / W", 3.25 "N / W" / Mm, “Ta” was adjusted to 0.1 mm, and “Tb” was adjusted to 0.1 mm to produce a heat exchanger tube in the same manner as described above, and a heat exchanger was produced in the same manner.

<Comparative Example 4>
As shown in Table 1 above, “Ac” is 6.05 mm ² , “At” is 18.1 mm ² , “P” is 73.3 mm, “L” is 32.1 mm, and “Ac / At” is 33%. , "P / L" 228%, "N" 32, "H" 1.15mm, "W" 8mm, "P / W" 916%, "N / W" 4.00 / Mm, “Ta” was adjusted to 0.03 mm, and “Tb” was adjusted to 0.1 mm, a heat exchanger tube was prepared in the same manner as described above, and a heat exchanger was similarly prepared.

<Evaluation test on weight>
The weight (kg) of each heat exchanger of the above-mentioned examples and comparative examples was measured, and as shown in the graph of FIG. 5, each weight and the target ideal heat exchanger weight (thick line in the graph). The values shown in FIG.

  As is apparent from the graph, it can be seen that the heat exchangers of the example and the comparative examples 3 and 4 can be suppressed within the target weight and are lightweight. On the other hand, the heat exchangers of Comparative Examples 1 and 2 having a large tube width exceeded the target weight.

<Evaluation test for pressure resistance>
A destructive test was performed on each heat exchanger of the above Examples and Comparative Examples, and a destructive pressure (MPa) was measured. Then, as shown in the graph of FIG. 6, each burst pressure was compared with the required ideal heat exchanger burst pressure (value indicated by the bold line in the graph).

  As is clear from the graph, the heat exchangers of Examples and Comparative Examples 1 to 3 having a thick partition wall thickness (Ta) were higher than the required breaking pressure and had sufficient pressure resistance. On the other hand, the heat exchanger of Comparative Example 4 having a thin partition wall thickness (Ta) did not reach the required breaking pressure.

<Evaluation test for heat dissipation>
The amount of heat release (kW) in each heat exchanger of the above Examples and Comparative Examples was measured. Then, as shown in the graph of FIG. 7, each heat release amount was compared with the target ideal heat exchanger heat release amount (value indicated by a thick line in the graph).

  As is apparent from the graph, the heat exchangers of the example and the comparative example 2 had a sufficient heat dissipation performance, more than the target heat dissipation amount. Furthermore, the heat exchangers of Comparative Examples 3 and 4 were slightly less than the target heat release. On the other hand, the heat exchanger of Comparative Example 1 having an excessively high tube height (H) was considerably smaller than the target heat radiation amount.

<Evaluation test for refrigerant passage resistance>
Refrigerant passage resistance in each heat exchanger of the above-mentioned examples and comparative examples was measured. Then, as shown in the graph of FIG. 8, each passage resistance was compared with the passage resistance of the ideal ideal heat exchanger (value indicated by a thick line in the graph).

  As is clear from the graph, the heat exchangers of Examples and Comparative Examples 1, 2, and 4 were able to be suppressed within the target passage resistance, and the passage resistance was low. In contrast, the heat exchanger of Comparative Example 3 exceeded the target passage resistance.

  <Comprehensive evaluation>

  In each heat exchanger of the said Example and a comparative example, the result of each evaluation test of the said weight, pressure | voltage resistance, heat dissipation, and passage resistance is put together in the above Table 2, and is shown. In the table, heat exchangers that have achieved the targets of each evaluation test are marked with “○”, and those that did not reach the target slightly, but with a heat exchanger of a practical level, marked with “△”. The “×” mark is given to heat exchangers that are difficult to put into practical use.

  As is clear from Table 2 above, the heat exchangers of Examples 1 to 3 that satisfy the gist of the present invention obtained good results in all evaluations. On the other hand, the heat exchangers of Comparative Examples 1 to 4 that depart from the gist of the present invention were unsatisfactory in any evaluation.

It is a front view which shows the heat exchanger relevant to this invention. It is a perspective view which decomposes | disassembles and shows the tube connection part periphery of the header in the heat exchanger relevant to this invention. It is a perspective view which shows the tube for heat exchangers relevant to this invention. It is sectional drawing which shows the tube for heat exchangers relevant to this invention. It is a graph which shows the relationship with the target weight in the heat exchanger of an Example and a comparative example. It is a graph which shows the relationship with the request | requirement pressure | voltage resistance in the heat exchanger of an Example and a comparative example. It is a graph which shows the relationship with the target heat dissipation performance in the heat exchanger of an Example and a comparative example. It is a graph which shows the relationship with the target channel | path resistance in the heat exchanger of an Example and a comparative example.

Explanation of symbols

60 ... Tube for heat exchanger 61 ... Tube body 63 ... Outer wall 64 ... Partition wall 65 ... Refrigerant passage H ... Tube height Ta ... Partition wall thickness Tb ... Outer wall thickness W ... Tube width

Claims (10)

In a heat exchanger tube in which a plurality of refrigerant passages extending in the tube length direction are formed in parallel in the tube width direction in a flat tube body having a predetermined length,
The tube body width is “W”, the refrigerant passage total cross-sectional area is “Ac”, the tube main body cross-sectional area (including the refrigerant passage portion) is “At”, and the tube main body outer perimeter is “ When “L” and the total inner perimeter of the refrigerant passage are “P”, the following relational expressions (A) to (C):
W = 6-18mm ... (I)
Ac / At × 100 = 50 to 70 (%) (B)
P / L × 100 = 350 to 450 (%) (C)
A tube for a heat exchanger, characterized in that The following relational expression (d):
P / W × 100 = 750-850 (%) (D)
The heat exchanger tube according to claim 1, wherein the heat exchanger tube is configured so that When the number of the refrigerant passages is “N”, the following relational expression (e):
N / W = 3-4 (e)
The heat exchanger tube according to claim 1, wherein: When the height of the tube body is “H”, the following relational expression (f):
H = 0.5-1.5mm (F)
The heat exchanger tube according to claim 1, wherein the heat exchanger tube is configured so that When the thickness of the partition wall between adjacent refrigerant passages in the tube body is “Ta”, the following relational expression (g):
Ta = 50-80 μm (G)
The heat exchanger tube according to claim 1, wherein the heat exchanger tube is configured so that When the thickness of the outer peripheral wall of the tube body is “Tb”, the following relational expression (h):
Tb = 80 to 250 μm (H)
The heat exchanger tube according to claim 1, wherein the heat exchanger tube is configured so that   The heat exchanger tube according to claim 1, wherein the refrigerant passage has a substantially rectangular cross section. In a heat exchanger tube in which a plurality of refrigerant passages extending in the tube length direction are formed in parallel in the tube width direction in a flat tube body having a predetermined length,
The tube body width is “W”, the tube body height is “H”, the partition wall thickness between adjacent refrigerant passages in the tube body is “Ta”, and the outer peripheral wall thickness in the tube body is “ When “Tb” is assumed, the following relational expressions (A) (F) (G) (G):
W = 6-18mm ... (I)
H = 0.5-1.5mm (F)
Ta = 50-80 μm (G)
Tb = 80 to 250 μm (H)
A tube for a heat exchanger, characterized in that In a heat exchanger in which a plurality of heat exchanger tubes that are connected to both headers in communication between both headers are arranged in parallel in the header length direction between a pair of headers,
The tube for heat exchanger is formed in a flat tube body having a predetermined length, and a plurality of refrigerant passages extending in the tube length direction are arranged in parallel in the tube width direction.
The tube body width is “W”, the refrigerant passage total cross-sectional area is “Ac”, the tube main body cross-sectional area (including the refrigerant passage portion) is “At”, and the tube main body outer perimeter is “ L "and the total inner perimeter of the refrigerant passage is" P ",
When the thickness of the partition wall between adjacent refrigerant passages in the tube main body is “Ta”, the following relational expressions (A) to (C):
W = 6-18mm ... (I)
Ac / At × 100 = 50 to 70 (%) (B)
P / L × 100 = 350 to 450 (%) (C)
It is comprised so that may be materialized, The heat exchanger characterized by the above-mentioned. In a heat exchanger in which a plurality of heat exchanger tubes that are connected to both headers in communication between both headers are arranged in parallel in the header length direction between a pair of headers,
The tube for heat exchanger is formed in a flat tube body having a predetermined length, and a plurality of refrigerant passages extending in the tube length direction are arranged in parallel in the tube width direction.
The tube body width is “W”, the tube body height is “H”, the partition wall thickness between adjacent refrigerant passages in the tube body is “Ta”, and the outer peripheral wall thickness in the tube body is “ When “Tb” is assumed, the following relational expressions (A) (F) (G) (G):
W = 6-18mm ... (I)
H = 0.5-1.5mm (F)
Ta = 50-80 μm (G)
Tb = 80 to 250 μm (H)
It is comprised so that may be materialized, The heat exchanger characterized by the above-mentioned.

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