JP2010065989A - Tube for heat exchanger and heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tube for a heat exchanger and a heat exchanger capable of improving fracture strength with respect to flying stones or the like without causing enlargement of the tube. <P>SOLUTION: In the tube 10 for a heat exchanger, an interior of the flat tube shaped tube 10 is divided by a partition wall part 10c laid between a pair of flat wall parts 10a, 10b disposed facing a circumferential wall of the tube 10, and it has a plurality of communication passages 10d in parallel with each other. An outermost side communication passage 10e positioned in a width direction end of the tube 10 is formed in a substantially triangular shape having a vertex portion 10f with a cross section protruding toward the width direction end of the tube 10, and thickness of a wall (a thick portion 10g) in a height direction of the tube 10 in the outermost communication passage 10e is provided gradually larger toward a width direction end side of the tube 10. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a heat exchanger tube and a heat exchanger.

Conventionally, the technique of patent document 1 is known as a tube for heat exchangers and a heat exchanger (refer patent document 1).
According to the present invention, the outermost flow passages positioned at both ends in the width direction of the tube are formed in a shape such as a perfect circle without a corner or an ellipse.
Japanese Patent Laid-Open No. 11-44498

However, in the conventional invention, since the outermost flow passage is formed in a shape such as a perfect circle without a corner or an ellipse, there is a problem that the size of the tube is increased.
In addition, the impact force due to stepping stones is not necessarily input horizontally from the width direction of the tube, and may be input from diagonally downward or diagonally upward, so there is a possibility that the breaking strength against stepping stones may be insufficient. It was.

  The present invention has been made to solve the above-mentioned problems, and the object of the present invention is to provide a heat exchanger tube and a heat exchanger that can improve the breaking strength against a stepping stone without causing an increase in the size of the tube. Is to provide.

  In the first aspect of the present invention, the inside of the flat tubular tube is partitioned by a partition wall portion straddling between a pair of flat wall portions opposed to the peripheral wall of the tube, and for a heat exchanger having a plurality of flow passages side by side In the tube, the outermost flow passages positioned at both ends in the width direction of the tube are formed in a substantially triangular shape having a cross section projecting toward the end in the width direction of the tube, and the tube in the outermost flow passage The wall thickness in the height direction of the tube is increased as it goes toward the end in the width direction of the tube.

In the first aspect of the present invention, the outermost flow passages positioned at both ends in the width direction of the tube are formed in a substantially triangular shape having a vertex portion whose cross section protrudes toward the end portion in the width direction of the tube, The thickness of the wall in the height direction of the tube in the passage is increased toward the end in the width direction of the tube.
Thereby, the breaking strength with respect to a stepping stone etc. can be improved, without causing the enlargement of a tube and a heat exchanger.

  Embodiments of the present invention will be described below with reference to the drawings.

Example 1 will be described below.
FIG. 1 is a front view showing a condenser in which the heat exchanger tube of Example 1 is adopted, FIG. 2 is a cross-sectional view of the heat exchanger tube of Example 1, and FIG. 3 is a schematic diagram of the heat exchanger tube of Example 1. FIG. 4 is a diagram for explaining the operation of the first embodiment, FIG. 5 is a diagram for explaining the relationship between the set value X and the breaking strength, and FIG. 6 is a diagram for explaining the relationship between the set value X and the weight. FIG. 7 is a diagram for explaining the relationship between the set value X and the flow resistance.

First, the overall configuration will be described.
As shown in FIG. 1, a condenser 1 (corresponding to the heat exchanger in the claims) in which the heat exchanger tube 10 of the first embodiment (hereinafter referred to as tube 10) is employed is arranged at a predetermined interval on the left and right. A pair of tanks 2 and 3 and a core portion 4 arranged between the tanks 2 and 3 are provided.
The tank 2 is divided into three chambers R1, R3, R6 by four plate-shaped divider plates D1, and an input connector 5 having an input port 5a communicating with the chamber R1 is provided, while communicating with the chamber R6. The output connector 6 including the output port 6a is provided.
The tank 3 is divided into three chambers R2, R4, and R5 by four divide plates D1, and a receiver tank 9 that communicates with the chambers R4 and R5 through connecting pipes 7 and 8 is provided.

The core portion 4 includes a plurality of flat tubular tubes 10 whose both end portions are respectively inserted and fixed in the corresponding tanks 2 and 3, and corrugated plate-like fins 11 in which corrugated top portions are joined to the adjacent tubes 10. It is configured.
Further, both sides of the core portion 4 in the stacking direction are connected and reinforced by a pair of reinforcements 12 and 13 whose both ends are inserted and fixed to the corresponding tanks 2 and 3 respectively.

In addition, all the constituent members of the capacitor 1 of Example 1 are all made of aluminum, and at least one of the joint portions of the constituent members is provided with a brazing material (brazing sheet), and these are temporarily assembled. By being heat-treated with, it is integrally brazed and joined.
Depending on the internal structure of the receiver tank 9, the capacitor 1 may be mounted after heat treatment.

Next, the tube 10 will be described in detail.
As shown in FIG. 2, the outer shape of the tube 10 is formed in a flat tubular shape.
The inside of the tube 10 includes a pair of flat wall portions 10a and 10a arranged to face each other in the vertical direction, coupling wall portions 10b and 10b for connecting both ends in the width direction of the flat wall portions 10a and 10a, and flat wall portions 10a, It is partitioned by a plurality of linear partition walls 10c extending between 10a.
As a result, a plurality of flow passages 10 d are formed side by side inside the tube 10.

As shown in FIG. 3, the outermost flow passages 10 e arranged at both ends in the width direction of the tube 10 are formed in a substantially triangular shape having a vertex portion 10 f whose cross section protrudes toward the width direction portion of the tube 10. Has been.
Thereby, the thickness of the wall in the height direction of the tube 10 in the outermost flow passage 10e increases as it goes to the end portion in the width direction of the tube 10, and a thick portion 10g is formed here. .
Accordingly, the end portion in the width direction of the tube 10 has a high breaking strength against an impact force from the outside.

Further, the apex portion 10f includes an arc-shaped first arc portion 10h and an arc-shaped second arc portion 10i having a smaller curvature than the first arc portion 10h and connected to both ends of the first arc portion 10h. It is configured.
Further, the vertex portions 10k, 10m other than the vertex portion 10f are formed in an arc shape with a smaller curvature than the second arc portion 10i.
In Example 1, the curvature of the vertex portions 10k and 10m (curvature R = 0.1 mm) <the curvature of the second arc portion 10i (curvature R = 0.2 mm) <the curvature of the first arc portion 10h (curvature R = 0.7 mm), but is not limited to this.
As described above, since no sharp corner is formed in the outermost flow passage 10e, the impact force from the outside can be dispersed to avoid stress concentration on a specific part.
On the other hand, the flow passage 10d other than the outermost flow passage 10e of the tube 10 is formed in a substantially rectangular shape by the partition wall portion 10c.

Next, the operation will be described.
[Capacitor operation]
In the capacitor 1 configured as described above, the high-temperature circulation medium of about 60 ° C. flowing into the chamber R1 of the tank 2 from the engine side via the input port 5a of the input connector 5 first corresponds to each of the core portions 4. The vehicle running wind passing through the core section 4 or the forced wind and heat of a fan (not shown) while passing through the tube 10 while turning in the order of the chamber R2 of the tank 3, the chamber R3 of the tank 2, and the chamber R4 of the tank 3 through the tube 10 Replaced and cooled.

  Next, the flow medium in the chamber R4 of the tank 3 flows into the receiver tank 9 through the connection pipe 7 and is separated into gas and liquid, and then flows into the chamber R5 of the tank 3 through the connection pipe 8.

  Finally, the flow medium that has flowed into the chamber R5 of the tank 3 passes through the core portion 4 while flowing into the chamber R6 of the tank 2 via the corresponding tube 10 of the core portion 4 or a fan (not shown). After being heat-exchanged with forced air and subcooled to around 45 ° C., it is sent to the evaporator side via the output port 6a of the output connector 6 and functions as a heat exchanger.

[About stepping stones]
As described above, since the core portion 4 of the capacitor 1 needs to be communicated with the outside of the vehicle in order to allow the vehicle running wind and the forced wind of the fan to pass therethrough, the capacitor 1 is usually connected to the front portion in the engine room. It is installed.
Therefore, a stepping stone or the like may collide with the end portion in the width direction of the tube 10 of the core portion 4 while the vehicle is traveling.

At this time, as described above, the outermost flow passage 10e of the tube 10 is formed in a substantially triangular shape having an apex 10h protruding toward the end in the width direction, and further, a thick portion 10g is formed. Moreover, the breaking strength with respect to the input from the outside at the end portion in the width direction of the tube 10 can be improved, and cracking and deformation of the tube 10 due to the collision of a stepping stone or the like can be prevented.
In addition, since the outermost flow passage 10e does not have an acute corner, it is possible to disperse input from the outside and avoid stress concentration on a specific part.

  Next, based on FIG. 4, the cross section of the tube 10 of Example 1 (illustrated by a two-dot chain line) and the cross section of the tube 14 having the circular outermost flow passage 14a are compared and examined. . In addition, illustration of hatching of both the tubes 10 and 14 is omitted.

[Compact tube size]
In the tube 14, the outermost flow passage 14a has a circular shape. Therefore, in order to ensure the thickness C1 having the same thickness D1 as the width D1 in the outermost flow passage 10e of the tube 10, the tube 14 protrudes in the width direction. Length increases.
This leads to an increase in size and weight in the width direction of the tube, and an increase in size and weight in the width direction of the entire capacitor 1.
In addition, an extra thick portion 14c is formed in the partition wall portion 14b adjacent to the outermost flow passage 14a, leading to an increase in weight.

On the other hand, the tube 10 of Example 1 reduces the protruding length of the end in the width direction, that is, the width of the tube 10 while securing the thickness D1 necessary for impact resistance at the apex portion 10f. Compact and weight reduction can be realized.
Thereby, the capacitor 1 as a whole can be made compact and weight reduced.

  In addition, since the partition wall 10n (see FIG. 3) adjacent to the outermost flow passage 10e is formed in a straight line, the apex portions 10k and 10m can be effectively used as a part of the flow passage, and at the same time, the weight can be reduced. Can be planned.

[Tube breaking strength]
In the tube 14, when the thickness C1 having the same thickness as the thickness D1 in the width direction in the outermost flow passage 10a of the tube 10 is ensured, the impact force such as a stepping stone is horizontal from the width direction (illustrated by an arrow N1 in FIG. 4). When input, it is assumed that the deformation and breakage of the tube 14 can be prevented to some extent.
However, an actual impact force such as a stepping stone may be input from an oblique direction (illustrated by an arrow N2 in FIG. 4).
At this time, when the wall thickness C1 in the width direction suddenly converges to become the wall thickness C2 in the height direction like the tube 14 and is thinned, the strength may be insufficient.

On the other hand, in the tube 10 of the first embodiment, the outer flow passage 10a is formed in a substantially triangular shape and has a thick portion 10g, so that the thickness D1 in the width direction becomes the thickness D2 in the height direction. The shape converges slowly.
Thereby, even when an impact force such as a stepping stone is input from an oblique direction, the tube 10 can be well protected without insufficient strength.

[Tube dimensions]
Here, in designing the optimum shape of the tube 10, in order to satisfy the conditions (a) to (c) described below in each dimension shown in FIGS. A set value X of the following formula (1) was obtained.
(A) 2.2 <A1 / T <6.0, where T is the thickness of the partition wall 10c and A1 is the thickness of the protruding apex portion 10f on the side of the tube 10 in the width direction.
(B) When the height of the tube 10 is H and the plate thickness of the flat wall portions 10a, 10a is S, 4.6 <H / S <6.6.
(C) The plate thickness at the end in the height direction of the tube 10 at a position where the oblique side 10p of the projecting apex 10f and the hypotenuse 10p connected via the second arc 10i virtually intersect is represented by K. 1.4 <K / S <2.4

  X = (1000 × A1 × B × S) / W (1)

  However, the plate thickness at the end in the height direction of the tube 10 at the virtual intersection position of the hypotenuse 10p and the base 10q forming the apex portions 10k and 10m excluding the protruding apex portion 10f is B, and the width of the tube 10 is W. To do.

As a result, as shown in FIG. 5, when the setting value X = 2.4, a desired chipping strength (km / h) = 180 was obtained.
At this time, A1 = 0.45 to 0.55 is assumed. This value is a plate thickness necessary to prevent the tube 10 from penetrating through the end in the width direction when a sharp stepping stone or the like collides.
Further, B = 0.22 to 0.29 is assumed. This value is a plate thickness necessary for releasing stress applied to the end portion in the width direction of the tube 10 when a round stepping stone collides.
Further, S = 0.22 to 0.3 is assumed. This value is a plate thickness necessary to ensure the corrosion resistance of the tube 10.

  Here, when the set value X <2.4 is set, the chipping strength (km / h) <150, and the tube 10 may have insufficient strength. It is best to set to.

As shown in FIGS. 6 and 7, when the set value X = 2.4, the weight and the flow resistance are set to 100%, and when the set value X = 1.8, the weight is about 3%. It is possible to reduce the flow resistance by about 6%.
On the other hand, considering the manufacturing dimensional error of the tube 10 and the increase in weight and flow resistance, it is optimal to set the set value X ≦ 4.0.

  Thus, by setting each dimension of the tube 10 so as to satisfy 1.8 ≦ set value X ≦ 4.0, the optimum tube 10 can be designed easily, and the design cost can be greatly reduced.

Next, the effect will be described.
As described above, in the invention of Example 1, the inside of the flat tubular tube 10 is partitioned by the partition wall portion 10c straddling the pair of flat wall portions 10a, 10b disposed to face the peripheral wall of the tube 10, In the heat exchanger tube 10 having a plurality of flow passages 10d side by side, the outermost flow passage 10e located at both ends in the width direction of the tube 10 has an apex portion 10f whose cross section protrudes toward the end in the width direction of the tube 10 The wall of the outermost flow passage 10e in the height direction of the tube 10 (thick portion 10g) is increased in thickness toward the end of the tube 10 in the width direction.
Thereby, the breaking strength with respect to a stepping stone or the like can be improved without causing an increase in size of the tube 10 and the capacitor 1.

Further, a partition wall portion 10n formed at least between the outermost flow passage 10e and the adjacent flow passage 10d was formed linearly along the height direction of the tube 10.
Thereby, expansion of a distribution channel can be aimed at and it can prevent that tube 10 enlarges.

Further, the substantially triangular apex portions 10f, 10m, 10n of the outermost flow passage 10e are formed in an arc shape, and the protruding apex portion 10f is formed by an arc-shaped first arc portion 10h and the first arc portion 10h. The second arc portion 10i having a small curvature and connected to both ends of the first arc portion 10h, the thickness of the partition wall portion 10c is T, and the end portion in the width direction of the tube 10 of the protruding apex portion 10f When the side plate thickness is A1, 2.2 <A1 / T <6.0, the height of the tube 10 is H, and the flat wall portions 10a and 10a are S. The thickness is 4.6. <H / S <6.6, the end in the height direction of the tube 10 at a position where the oblique side 10p connected via the first arc portion 10h and the second arc portion 10i of the protruding apex portion 10f virtually intersects. When the plate thickness is K, 1.4 <K / S <2.4 is satisfied, and the top portion excluding the protruding vertex portion 10f is excluded. Where the thickness of the tube 10 at the end in the height direction of the tube 10 at the virtual crossing position of the hypotenuse 10p and the base 10q of the apex portions 10k, 10m forming the shape is B and the width of the tube 10 is W, the following equation (1) In this case, 1.8 ≦ X ≦ 4.0.
X = (1000 × A1 × B × S) / W (1)
Thereby, the optimal shape of the tube 10 can be easily designed.

Although the embodiments have been described above, the present invention is not limited to the above-described embodiments, and design changes and the like within the scope not departing from the gist of the present invention are included in the present invention.
For example, the heat exchanger in which the heat exchanger tube of the present invention is adopted is not limited to a condenser, and can be applied to a heat exchanger such as a radiator, an oil cooler, and an intercooler.
Moreover, the shape of the wall part of partition walls other than the partition wall part 10n, and the shape of the distribution | circulation channel | path 10c can be set suitably.

It is a front view which shows the capacitor | condenser by which the tube for heat exchangers of Example 1 was employ | adopted. It is a cross-sectional view of the tube for heat exchangers of Example 1. 2 is an enlarged cross-sectional view of a main part of a heat exchanger tube of Example 1. FIG. It is a figure explaining the effect | action of Example 1. FIG. It is a figure explaining the relationship between the setting value X and fracture strength. It is a figure explaining the relationship between the setting value X and weight. It is a figure explaining the relationship between the setting value X and distribution resistance.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Capacitor 2, 3 Tank 4 Core part 5 Input connector 5a Input port 6 Output connector 6a Output port 7, 8 Connection pipe 9 Receiver tank 10 Heat exchanger tube 10a Flat wall part 10b Connection part 10c Partition wall part 10d Distribution channel 10e Outer flow passages 10f, 10k, 10m, apex portion 10g, thick portion 10h, first arc portion 10i, second arc portion 10n, partition wall portion 10p, hypotenuse 10q, bottom 11 fin 12, 13 reinforcement 14 tube 14a, outermost flow passage 14b, partition wall portion 14c Thick part

Claims (4)

In the tube for a heat exchanger, the inside of the flat tubular tube is partitioned by a partition wall portion straddling between a pair of flat wall portions arranged to face the peripheral wall of the tube, and has a plurality of flow passages side by side.
The outermost flow passages located at both ends in the width direction of the tube are formed in a substantially triangular shape having a vertex part whose cross section protrudes toward the end in the width direction of the tube,
The heat exchanger tube according to claim 1, wherein the thickness of the wall in the height direction of the tube in the outermost flow passage is increased toward the end in the width direction of the tube. The heat exchanger tube according to claim 1,
A tube for a heat exchanger, characterized in that at least a partition wall portion formed between the outermost flow passage and an adjacent flow passage is formed linearly along the height direction of the tube. The heat exchanger tube according to claim 1 or 2,
Each apex portion of the substantially triangular shape of the outermost distribution passage is formed in an arc shape,
The projecting apex portion is constituted by an arc-shaped first arc portion and a second arc portion having a smaller curvature than the first arc portion and connected to both ends of the first arc portion,
When the thickness of the partition wall portion is T, and the thickness of the protruding apex portion on the side in the width direction of the tube is A1, 2.2 <A1 / T <6.0, the height of the tube is H, When the plate thickness of the flat wall portion is S, 4.6 <H / S <6.6, and the first arc portion of the protruding apex portion and the hypotenuse connected via the second arc portion are virtually intersected When the plate thickness on the side in the height direction of the tube at the position where K is taken to be K, 1.4 <K / S <2.4 is satisfied,
When the plate thickness on the side in the height direction of the tube at the hypothetical intersection of the apex portion forming the apex excluding the protruding apex portion is B and the tube width is W, the following formula (1 The heat exchanger tube is characterized in that 1.8 ≦ X ≦ 4.0.
X = (1000 × A1 × B × S) / W (1) A core portion in which a plurality of heat exchanger tubes according to any one of claims 1 to 3 are laminated in a thickness direction of the tubes;
A heat exchanger comprising a pair of tanks in which both longitudinal ends of each tube are inserted and fixed.

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