JP2018124034A - Tube for heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a tube for a heat exchanger which can surely improve heat exchange efficiency.SOLUTION: A tube for a heat exchanger comprises: a cylindrical member 10 in which a refrigerant passage 40 in which a refrigerant flows is formed, and whose cross section shape is formed into a flat shape extending along an air flow direction; and inner fins 12 arranged in the cylindrical member 10, and partitioning the refrigerant passage 40 into a plurality of fine flow passages 4. A communication part 6 in which a plurality of clearances 5 for making the adjacent fine flow passages 4 communicate with each other is arranged at a part of the cylindrical member 10 in a longitudinal direction, and in the communication part 6, a passage cross section area of the clearance 5 at a downstream side of the air flow direction is larger than a passage cross section area of the clearance 5 at an upstream side of the air flow direction.SELECTED DRAWING: Figure 5

Description

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

  Conventionally, in a tube for a heat exchanger such as a refrigerant condenser, a technique has been disclosed in which an inner fin is accommodated inside and a plurality of communication holes are provided in the inner fin (see, for example, Patent Document 1).

  In the heat exchanger tube described in Patent Document 1, the gas-phase refrigerant flowing in the refrigerant passage on the upstream side of the air flow in the tube has a large temperature difference from the outside air, and thus condenses early and becomes a liquid-phase refrigerant. And this liquid phase refrigerant | coolant can move to the refrigerant path of the adjacent air flow downstream via a communicating hole. For this reason, since the refrigerant can be agitated in the refrigerant passages on the upstream and downstream sides of the air flow in the tube to make the liquid density uniform, the heat exchange efficiency can be improved.

JP 2003-238776 A

  By the way, in the tube of the refrigerant condenser, the dryness of the refrigerant is not constant in the width direction (air flow direction). That is, in the refrigerant passage on the upstream side of the air flow, the dryness of the refrigerant is 0 (liquid refrigerant), but in the refrigerant passage on the downstream side of the airflow, the dryness of the refrigerant increases toward the downstream side of the airflow.

  However, in the prior art described in Patent Document 1, it is not considered that the dryness of the refrigerant is not constant in the width direction of the tube, so the refrigerant stirring effect by the communication holes of the inner fin is not optimally exhibited, The heat exchange efficiency may not be improved.

  An object of this invention is to provide the tube for heat exchangers which can improve heat exchange efficiency reliably in view of the said point.

  In order to achieve the above-mentioned object, the heat exchange tube according to claim 1 is a flat shape in which a heat medium flow path (40) through which a heat medium flows is formed and a cross-sectional shape extends along the flow direction of the external fluid. A cylindrical member (10) formed in a shape, and an inner fin (12) that is provided inside the cylindrical member and partitions the heat medium flow path into a plurality of narrow flow paths (4), the length of the cylindrical member A part of the direction is provided with a communication part (6) in which a plurality of communication passages (5, 65) for communicating adjacent narrow channels are formed, and in the communication part, the downstream side in the flow direction of the external fluid. The passage sectional area in the communication passage is larger than the passage sectional area in the communication passage on the upstream side in the flow direction of the external fluid.

  According to this, the cross-sectional area of the communication passage (5, 65) on the downstream side of the external fluid flow is larger than the cross-sectional area of the communication passage (5, 65) on the upstream side of the external fluid flow. (10) The cross-sectional area of the passage can be increased as the communication passages (5, 65) in the downstream portion of the external fluid flow where the dryness increases. For this reason, the heat medium stirring effect by providing a communicating path (5, 65) in the cylindrical member (10) of the tube for heat exchangers can be exhibited optimally, and heat exchange efficiency can be improved reliably. it can.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a perspective view which shows the refrigerant condenser in 1st Embodiment. It is a disassembled perspective view which shows the principal part of the refrigerant condenser in 1st Embodiment. It is a top view which shows the tube which concerns on 1st Embodiment. It is IV-IV sectional drawing of FIG. It is VV sectional drawing of FIG. It is VI-VI sectional drawing of FIG. It is sectional drawing which shows the cross section orthogonal to the air flow direction of the tube which concerns on 2nd Embodiment. It is a disassembled perspective view which shows the tube which concerns on 3rd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
1st Embodiment of this invention is described based on FIGS. This embodiment demonstrates the example which applied the tube for heat exchangers which concerns on this invention to the tube of the refrigerant | coolant condenser in the refrigerating cycle of a vehicle air conditioner.

  As shown in FIG. 1, the refrigerant condenser includes a core portion 2 in which a plurality of tubes 1 through which refrigerant passes and outer fins 20 are alternately stacked. The core unit 2 is a heat exchange unit that exchanges heat between the refrigerant and air (outside air). Note that the refrigerant of the present embodiment corresponds to the heat medium of the present invention, and the air of the present embodiment corresponds to the external fluid of the present invention.

  The refrigerant condenser includes a header tank 3 connected to both ends of the tube 1 in the longitudinal direction, and a side plate 25 that is a reinforcing member disposed on the outer side of the core portion 2 in the stacking direction of the tubes 1. I have. One header tank 3 is provided with an inflow portion 31 through which refrigerant discharged from a compressor (not shown) flows into the one header tank 3. The other header tank 3 is provided with an outflow portion 32 through which refrigerant flows out from the other header tank 3.

  As shown in FIG. 2, the tube 1 includes a cylindrical member 10 in which a cross section of the flow path perpendicular to the direction in which the refrigerant flows is formed in a flat shape, and an inner fin 12 disposed inside the cylindrical member 10. I have. Details of the tubular member 10 and the inner fin 12 will be described later.

  The header tank 3 is configured by integrating a core plate 32 to which the tubular member 10 is joined and a tank main body 33 that forms a tank internal space together with the core plate 32. The core plate 32 has an insertion hole 320 into which the cylindrical member 10 is inserted.

  The core plate 32 is formed of a clad material in which a sacrificial corrosion layer made of an alloy containing zinc or the like is coated on the surface of a core material made of aluminum (the surface on the outer side of the header tank 3). The tank body 33 is formed of a clad material in which a brazing material is coated on both surfaces of an aluminum core material.

  As shown in FIGS. 3 and 4, the cylindrical member 10 has a refrigerant flow path 40 through which a refrigerant flows. The tubular member 10 is formed in a flat shape in which a cross-sectional shape orthogonal to the longitudinal direction (refrigerant flow direction) extends along the air flow direction. The cylindrical member 10 has two flat surfaces 11p that face each other with the refrigerant flow path 40 interposed therebetween.

  The inner fin 12 partitions the refrigerant flow path 40 in the tubular member 10 into a plurality of narrow flow paths 4. The inner fin 12 is formed by bending the belt-shaped first plate member 100 into a wave shape.

  More specifically, the inner fin 12 is formed in a wave shape by rolling the first plate member 100. The wave-like top portions 14 of the inner fins 12 are respectively joined to the inner surface of the flat surface 11p in the tubular member 10. A flat portion 15 is provided at one end in the width direction of the inner fin 12. The first plate-like member 100 is a clad material in which both surfaces of an aluminum core material are covered with an inner fin brazing material.

  The “width direction” in the present embodiment is a longitudinal direction in a cross section perpendicular to the refrigerant flow direction of the tube 1 (tubular member 10), and coincides with the air flow direction in the refrigerant condenser.

  Here, the cylindrical member 10 is formed by bending a substantially central portion in the width direction of the band-shaped second plate-shaped member 200. In the second plate-like member 200, the surface of the aluminum core material, that is, the outer surface of the tubular member 10 is covered with a brazing material containing zinc. The brazing material containing zinc exhibits a sacrificial corrosion action on the core material.

  The cylindrical member 10 includes the two flat surfaces 11p, the curved end portion 11a, and the crimping portion 11b described above. The curved end portion 11a is disposed at one end portion in the width direction of the tubular member 10 and is formed by curving the second plate-shaped member 200 in a substantially arc shape. The two flat surfaces 11p are each connected to the curved end portion 11a and arranged to face each other. The crimping part 11b is arrange | positioned in the cylindrical member 10 on the opposite side to the curved edge part 11a.

  The one end portion 11e of the second plate member 200 is bent so as to sandwich the other end portion 11f of the second plate member 200 and the end portion 15a of the flat portion 15 of the inner fin 12. A portion 11b is formed. That is, the caulking portion 11b bends the one end portion 11e in the width direction of the second plate member 200, and the other end portion 11f in the width direction of the second plate member 200, and one end portion in the width direction of the inner fin 12. It is formed by caulking both ends of (the end portion 15a of the flat portion 15).

  By the way, as shown in FIG. 3 and FIG. 5, a communication part 6 is provided in a part of the tubular member 10 in the tube 1 in the longitudinal direction so that adjacent narrow channels 4 communicate with each other. In the communication part 6, a gap 5 is formed between the top part 14 of the inner fin 12 and the inner side surface of the flat surface 11 p of the tubular member 10. Adjacent narrow channels 4 communicate with each other through the gap 5. Therefore, the clearance gap 5 of this embodiment comprises the communicating path of this invention. And since the refrigerant | coolant in the some narrow flow path 4 is stirred via these some clearance gap 5, the heat exchange efficiency in the tube 1 is improved.

  In the tubular member 10, the gap 5 is not provided in a portion other than the communication portion 6. That is, the general part 7 where the adjacent narrow flow paths 4 are independent from each other is provided in a part other than the communication part 6 in the tubular member 10. In the present embodiment, the tubular member 10 is provided with a plurality (specifically, five) communication portions 6. In the tubular member 10, the general portion 7 is disposed between the plurality of communicating portions 6.

  Here, the direction orthogonal to both the longitudinal direction of the cylindrical member 10 and the air flow direction is defined as the height direction. The length in the height direction of the gap 5 is defined as a gap height H. In the present embodiment, the height direction is parallel to the stacking direction of the tubes 1.

  Moreover, the site | part which comprises the communication part 6 among the inner fins 12 is called the communication part formation part 60. FIG. The communication portion forming portion 60 has a shorter length in the height direction than other portions of the inner fin 12.

  As shown in FIG. 5, in the communicating portion 6, the gap height H in the gap 5 on the downstream side in the air flow direction is larger than the gap height H in the gap 5 on the upstream side in the air flow direction. In other words, in the communication part 6, the gap height H is larger in the gap 5 on the downstream side of the air flow. Therefore, in the communication portion 6, the passage cross-sectional area in the refrigerant passage (communication passage) formed by the gap 5 on the downstream side in the air flow direction is the refrigerant passage (communication passage) formed by the gap 5 on the upstream side in the air flow direction. It is larger than the cross-sectional area of the passage.

  As shown in FIG. 6, in the cross section orthogonal to the air flow direction of the cylindrical member 10, the communication part 6 and the general part 7 are smoothly connected. That is, in the communication portion 6, the inner fin 12 is formed such that the gap height H of the gap 5 gradually decreases as the top portions 14 at both ends in the tube longitudinal direction approach the general portion 7.

  In other words, the communication part 6 has the inclined part 61 in which the gap height H of the gap 5 gradually decreases as it approaches the general part 7 in the cross section orthogonal to the air flow direction. The inclined portions 61 are provided at both ends of the communicating portion 6 in the tube longitudinal direction. In the cylindrical member 10 shown in FIG. 6, a portion between two broken lines is the communication portion 6, and a portion outside each broken line is the general portion 7.

  The inner fin 12 of the present embodiment is formed by adding a pressing process in a roller forming process for bending the first plate-like member 100 into a wave shape. Specifically, a part of the inner fins 12 formed in a corrugated shape is gradually crushed by applying a pressing process while the first plate-shaped member 100 is subjected to a roller process and bent into a corrugated shape, so that the tube An inclined portion 61 on one side in the longitudinal direction (left side in FIG. 6) is formed.

  And the communicating part formation part 60 is formed by pressing the 1st plate-shaped member 100 by predetermined reference time and predetermined press force during a roller shaping | molding process. Then, by finishing the press work, the length in the height direction of the first plate-like member 100 is gradually increased, and the inclined portion 61 on the other side in the tube longitudinal direction (the right side in FIG. 6) is formed.

  As described above, in the tube 1 of the present embodiment, in the communication portion 6, the passage cross-sectional area in the refrigerant passage (communication passage) formed by the gap 5 on the downstream side of the air flow is changed by the gap 5 on the upstream side of the air flow. It is larger than the cross-sectional area of the formed refrigerant passage. According to this, the passage cross-sectional area can be increased as the refrigerant passage in the downstream portion of the air fluid flow where the dryness increases in the tubular member 10. For this reason, since the refrigerant | coolant stirring effect by providing the clearance gap 5 in the cylindrical member 10 of the tube 1 can be exhibited optimally, heat exchange efficiency can be improved reliably.

  Moreover, in this embodiment, the communication part 6 is formed by adding a press process during the roller formation process of the 1st plate-shaped member 100 which comprises the inner fin 12. As shown in FIG. According to this, compared with the case where a press process is provided separately from a roller shaping | molding process, a manufacturing man-hour can be reduced. For this reason, the communication part 6 can be provided in the tube 1, suppressing the deterioration of productivity.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. This 2nd Embodiment differs in the structure of the communication part 6 of the cylindrical member 10 compared with the said 1st Embodiment.

  As shown in FIG. 7, in this embodiment, in the cross section orthogonal to the air flow direction of the cylindrical member 10, the communication portion 6 and the general portion 7 are connected by a wall portion 62 orthogonal to the tube longitudinal direction. . That is, in the communication part 6, the top part 14 of the tube longitudinal direction both ends of the inner fin 12 is bent so as to be orthogonal to the tube longitudinal direction. In the cylindrical member 10 shown in FIG. 7, a portion between two broken lines is the communication portion 6, and a portion outside each broken line is the general portion 7.

  The inner fin 12 according to the present embodiment performs a pressing process in which a part of the first plate-like member 100 bent into a wave shape is subjected to a pressing process after the roller forming step of bending the first plate-like member 100 into a wave shape. It is formed by. That is, after the first plate-like member 100 is subjected to roller processing and bent into a wave shape, a part of the first plate-like member 100 bent into a wave shape is pressed so that a part of the inner fin 12 is pressed. It is crushed and the communication part formation part 60 is formed. At this time, in the inner fin 12, the communication part forming part 60 and other parts are linearly connected like a rising of a rectangular wave.

  Other configurations are the same as those of the first embodiment. Therefore, according to this embodiment, the same effect as that of the first embodiment can be obtained.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. The third embodiment is different from the first embodiment in the configuration of the tube 1.

  As shown in FIG. 8, in the communication portion 6 of the tube 1, the inner fin 12 is formed with a through hole 65 that allows the narrow channels 4 on both sides of the inner fin 12 to communicate with each other. In the present embodiment, the through hole 65 is provided in the top portion 14 of the inner fin 12. Further, the through hole 65 is formed in a circular shape.

  Adjacent narrow channels 4 communicate with each other through the through hole 65. Therefore, the through hole 65 of the present embodiment constitutes the communication path of the present invention.

  In the communication part 6, the size of the through hole 65 formed on the downstream side in the air flow direction is larger than the size of the through hole 65 formed on the upstream side in the air flow direction. That is, in the communication part 6, the hole diameter is larger in the through hole 65 on the downstream side of the air flow. Therefore, in the communication portion 6, the passage cross-sectional area of the refrigerant passage (communication passage) formed by the through hole 65 on the downstream side in the air flow direction is the refrigerant passage (communication passage) formed by the through hole 65 on the upstream side in the air flow direction. ) Is larger than the cross-sectional area of the passage.

  As described above, in the tube 1 of the present embodiment, the passage cross-sectional area of the through hole 65 on the downstream side of the air flow is set larger than the cross sectional area of the through hole 65 on the upstream side of the air flow in the communication portion 6. Yes. According to this, since the passage cross-sectional area can be increased as the refrigerant passage in the downstream portion of the air fluid flow where the dryness increases in the tubular member 10, the same effect as in the first embodiment can be obtained. Can do.

  By the way, since the top part 14 of the inner fin 12 is joined to the inner side surface of the cylindrical member 10, it does not contribute to the increase of the heat exchange area. On the other hand, in this embodiment, since the through-hole 65 is formed in the top part 14 which does not contribute to the increase in the heat exchange area in the inner fin 12, it suppresses that a heat exchange area reduces by the through-hole 65. it can. For this reason, heat exchange efficiency can be improved effectively.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows, for example, within a range not departing from the gist of the present invention.

  (1) In the first and second embodiments described above, the example in which the tubular member 10 of the tube 1 is configured to have the crimped portion 11b at one end in the width direction has been described. It is not limited to. For example, you may comprise the cylindrical member 10 so that it may not have the crimp part 11b by extrusion molding.

  (2) In the third embodiment, the example in which the circular through hole 65 is formed in the top portion 14 of the inner fin 12 has been described. However, the configuration of the through hole 65 is not limited to this. For example, the through hole 65 may be formed in a flat plate portion (inclined surface) that connects the adjacent top portions 14 of the inner fin 12. Further, the through hole 65 may be formed in a polygonal shape such as an elliptical shape or a quadrangular shape.

4 Narrow channel 5 Gap (Communication path)
6 Communication portion 10 Tubular member 12 Inner fin 40 Refrigerant flow path (heat medium flow path)

Claims (4)

A tubular member (10) formed in a flat shape with a cross-sectional shape extending along the flow direction of the external fluid, while forming a heat medium flow path (40) through which the heat medium flows,
An inner fin (12) provided inside the cylindrical member and partitioning the heat medium flow path into a plurality of narrow flow paths (4),
A communication portion (6) in which a plurality of communication passages (5, 65) for communicating the adjacent narrow flow paths are formed is provided in a part of the cylindrical member in the longitudinal direction,
In the communication portion, the heat exchanger tube has a passage cross-sectional area in the communication passage on the downstream side in the flow direction of the external fluid larger than a cross-sectional area in the communication passage on the upstream side in the flow direction of the external fluid. The cylindrical member has two flat surfaces (11p) facing each other across the heat medium flow path,
The inner fin is formed in a wave shape,
The wave-like tops (14) of the inner fins are respectively joined to the inner surfaces of the two flat surfaces of the cylindrical member,
In the communication portion, a gap (5) is formed between the top portion of the inner fin and the inner surface of the flat surface of the cylindrical member,
The communication path is constituted by the gap,
The direction perpendicular to both the longitudinal direction of the cylindrical member and the flow direction of the external fluid is the height direction,
When the length of the gap in the height direction is the gap height (H),
2. The heat exchanger according to claim 1, wherein, in the communication portion, the gap height in the gap on the downstream side in the flow direction of the external fluid is larger than the gap height in the gap on the upstream side in the flow direction of the external fluid. tube. The cylindrical member has two flat surfaces (11p) facing each other across the heat medium flow path,
The inner fin is formed in a wave shape,
The wave-like tops (14) of the inner fins are respectively joined to the inner surfaces of the two flat surfaces of the cylindrical member,
In the communication portion, the inner fin is formed with a through hole (65) for communicating the narrow channels on both sides of the inner fin.
The communication path is constituted by the through hole,
The size of the through hole formed on the downstream side in the flow direction of the external fluid in the communication portion is larger than the size of the through hole formed on the upstream side in the flow direction of the external fluid. Tube for heat exchanger.   The heat exchanger tube according to claim 3, wherein the through hole is formed in the top portion of the inner fin.

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