WO2018159605A1

WO2018159605A1 - Heat-exchange member

Info

Publication number: WO2018159605A1
Application number: PCT/JP2018/007241
Authority: WO
Inventors: 光太郎渡邊; 喜多　晃一; 俊彦幸
Original assignee: 三菱マテリアル株式会社
Priority date: 2017-02-28
Filing date: 2018-02-27
Publication date: 2018-09-07
Also published as: JP2018141615A; TW201834760A

Abstract

This heat-exchange member is characterized by the following: comprising tubes through which a heat-exchange fluid flows and which are disposed so as to be mutually parallel, and fins which are disposed between adjacent tubes; and the fins being configured by packing coil-bodies, formed by rolling a metal wire material into coils, between the tubes which are disposed so as to be mutually parallel.

Description

Heat exchange member

The present invention relates to a heat exchange member that includes a tube portion in which a heat exchange fluid is circulated and a fin portion disposed between the tube portions.
This application claims priority based on Japanese Patent Application No. 2017-037452 for which it applied to Japan on February 28, 2017, and uses the content here.

Conventionally, as a heat exchange member such as a radiator, as shown in Patent Document 1, for example, flat tubes are arranged in parallel by bending the flat tubes so as to meander, and between these adjacent flat tubes, There has been proposed a corrugated fin provided with a fin portion.

In the heat exchange member described above, a coolant (heat exchange fluid) is circulated inside the flat tube, and a heat medium such as air is passed through the fin portion composed of the corrugated fins, so It has a configuration for heat exchange.

JP 2012-096264 A

By the way, in the heat exchange member described in Patent Document 1, a plate-like corrugated fin is disposed as a fin portion between adjacent flat tubes. However, since the specific surface area of the fin portion is small, the fin portion is The contact area with the passing heat medium was insufficient, and heat exchange could not be performed efficiently between the heat medium and the heat exchange fluid.
When the pitch of the corrugated fins is narrowed to increase the specific surface area, the pressure loss of the heat medium that passes through the fin part increases, that is, the load for feeding the heat medium to the fin part increases and the entire device becomes The energy efficiency could be degraded.

The present invention has been made against the background as described above, and the contact area between the heat medium passing through the fin portion and the fin portion is large, and the pressure loss of the heat medium passing through the fin portion is small. It aims at providing the heat exchange member excellent in the heat exchange characteristic.

In order to solve such problems and achieve the above-mentioned object, a heat exchange member according to one aspect of the present invention includes a tubular body portion that is arranged so that a heat exchange fluid is circulated therein and arranged in parallel. A fin portion disposed between adjacent tube portions, wherein the fin portions are metal wire rods between the tube portions disposed in parallel. It is characterized by being comprised by being filled with the coil body which wound this in coil shape.

According to the heat exchange member having this configuration, the fin portion is configured by filling a coil body in which a metal wire is wound in a coil shape between tube portions arranged in parallel. The specific surface area of the part increases, and the contact area between the fin part and the heat medium is ensured. In addition, since a coil body in which a metal wire is wound in a coil shape is used, the hole diameter is sufficiently large, and the flow of the heat medium passing through the fin portion is not greatly hindered compared to a general corrugated fin. The pressure loss of the heat medium passing through the fin portion can be suppressed. Therefore, it is possible to provide a heat exchange member having excellent heat exchange characteristics.

In the heat exchange member according to one aspect of the present invention, the fin portion preferably includes a plate-shaped fin body and the coil body.
In this case, since the plate-like fin body is disposed between the adjacent tubular body portions and the coil body is filled, the coil body is in contact with the plate-like fin body and the tubular body portion. Thus, heat transfer between the tube portion and the fin portion is promoted. Therefore, it is possible to further improve the heat exchange characteristics.

In the heat exchange member according to one aspect of the present invention, it is preferable that the porosity of the fin portion is in the range of 40% to 90%.
In this case, since the porosity of the fin portion is 40% or more, it is possible to reliably prevent an excessive pressure loss of the heat medium passing through the fin portion.
On the other hand, since the porosity of the fin portion is 90% or less, a contact area with the heat medium passing through the fin portion is ensured, and excellent heat exchange characteristics are obtained.

In the heat exchange member according to one aspect of the present invention, it is preferable that the specific surface area of the fin portion is in a range of 300 m ² / m ³ or more and 25000 m ² / m ³ or less.
In this case, since the specific surface area of the fin portion is 300 m ² / m ³ or more, a contact area with the heat medium passing through the fin portion is ensured, and excellent heat exchange characteristics are obtained.
On the other hand, since the specific surface area of the fin portion is 25000 m ² / m ³ or less, it is possible to reliably prevent an excessive pressure loss of the heat medium passing through the fin portion.

ADVANTAGE OF THE INVENTION According to this invention, the contact area of the heat medium which passes a fin part and a fin part is large, the pressure loss of the heat medium which passes a fin part is small, and the heat exchange member excellent in the heat exchange characteristic is provided. be able to.

It is explanatory drawing of the heat exchange member which is one Embodiment of this invention. It is an expansion explanatory view of the fin part of the heat exchange member shown in FIG. It is a side view of the coil body used with the heat exchange member shown in FIG.1 and FIG.2. It is a front view of the coil body used with the heat exchange member shown in FIG.1 and FIG.2. It is a flowchart of the manufacturing method of the heat exchange member shown in FIG.1 and FIG.2. It is expansion explanatory drawing of the heat exchange member which is other embodiment of this invention. It is expansion explanatory drawing of the heat exchange member which is other embodiment of this invention. It is expansion explanatory drawing of the heat exchange member which is other embodiment of this invention. It is expansion explanatory drawing of the heat exchange member which is other embodiment of this invention. It is expansion explanatory drawing of the heat exchange member which is other embodiment of this invention. It is explanatory drawing of the heat exchange member which is other embodiment of this invention.

Hereinafter, a heat exchange member according to an embodiment of the present invention will be described with reference to the accompanying drawings.

As shown in FIG. 1, the heat exchange member 10 according to the present embodiment has a heat exchange fluid circulated therein and a tube portion 11 disposed so as to be parallel to each other and between adjacent tube portions 11. The fin part 12 arrange | positioned by these.

The tube part 11 is comprised with the metal with favorable heat conductivity, for example, copper or copper alloy, aluminum, or aluminum alloy. In this embodiment, it is comprised, for example with aluminum.
In the present embodiment, as shown in FIG. 1, a plurality of tube parts 11 are arranged in parallel, and end portions thereof are respectively connected to headers 15.
In the present embodiment, the thickness of the tube body portion 11 is in the range of 0.5 mm or more and 30 mm or less, and the width of the tube body portion 11 is in the range of 5 mm or more and 50 mm or less. The thickness of the tube part 11 is preferably in the range of 0.6 mm to 2.5 mm, and the width of the tube part 11 is preferably in the range of 8 mm to 35 mm. There is no limit.

As shown in FIG. 2, the fin portion 12 is configured by filling a coil body 20 in which a metal wire is wound in a coil shape between adjacent tube body portions 11.
In the present embodiment, as shown in FIG. 2, the coil body 20 is such that the length direction of the coil body 20 is along the width direction of the tube body portion 11, that is, the end surface of the coil body 20 passes through the fin portion 12. It is filled so as to face the passing direction of the heating medium.

As shown in FIGS. 3A and 3B, the coil body 20 has a structure in which a metal wire is wound in a coil shape. The coil body 20 is made of a metal having good thermal conductivity, such as copper or a copper alloy, aluminum or an aluminum alloy. In the present embodiment, the coil body 20 is made of aluminum or an aluminum alloy, like the tube body portion 11.

The diameter r of the metal wire constituting the coil body 20 is preferably in the range of 0.1 mm to 3 mm. The diameter r of the metal wire constituting the coil body 20 is more preferably in the range of 0.1 mm or more and 2 mm or less, but is not limited thereto.
Here, the diameter r is a value calculated based on the cross-sectional area A of each wire, and is defined by the following equation assuming that it is a perfect circle regardless of the cross-sectional shape.
r = (A / π) ^1/2 × 2

The winding pitch P of the metal wire wound around the coil body 20 is set within a range of r to 10 × r with respect to the diameter r of the metal wire. The winding pitch P of the metal wire is preferably set within the range of 3 × r to 4 × r with respect to the diameter r of the metal wire, but is not limited thereto.
The winding diameter R of the coil body 20 is set within a range of 3 × r to 1000 × r. The winding diameter R of the coil body 20 is preferably set within a range of 2 × r to 10 × r, but is not limited thereto.
The length L of the coil body 20 is the same as the width of the tube body portion 11.

In the fin part 12 comprised as mentioned above, the porosity of the fin part 12 is made into the range of 40% or more and 90% or less.
The specific surface area of the fin portion 12 is in the range of 300 m ² / m ³ or more and 25000 m ² / m ³ or less.

Hereinafter, a method for manufacturing the heat exchange member 10 according to the present embodiment having the above-described configuration will be described with reference to the flowchart of FIG.

(Tube body forming step S01)
First, the aluminum alloy tube bodies 11 described above are arranged in parallel, and the ends thereof are connected to the headers 15 respectively.

(Coil body filling step S02)
Next, the coil body 20 is filled between the pipe body portions 11 arranged so as to be arranged in parallel. In the present embodiment, the coil body 20 having a length equivalent to the width of the tube body portion 11 is formed so that the length direction of the coil body 20 is aligned with the width direction of the tube body portion 11. Fill in between.

(Jointing step S03)
Next, the coil body 20 and the tube body portion 11 filled between the tube body portions 11 arranged so as to be arranged in parallel are joined. In this embodiment, the coil body 20 and the tube part 11 are joined by sintering.
In this embodiment, since the tube part 11 and the coil body 20 are comprised with aluminum or aluminum alloy, it is preferable to implement sintering in an inert gas atmosphere or a vacuum atmosphere.
Although there are no particular limitations on the conditions of the joining step S03, it is preferable that the sintering temperature is in the range of 500 ° C. to 650 ° C., and the holding time at the sintering temperature is in the range of 5 min to 300 min. As the atmosphere in the bonding step S03, an inert gas such as nitrogen gas or argon gas may be used. The atmosphere in the bonding step S03 may be a vacuum atmosphere of 100 Pa or less.

The heat exchange member 10 which is this embodiment is manufactured by the above processes.
In this heat exchange member 10, a heat exchange fluid is circulated inside the tube body portion 11, and a heat medium such as air is sent to the fin portion 12, and the heat medium and the tube body that pass through the fin portion 12. Heat exchange is performed with the heat exchange fluid flowing through the section 11.

According to the heat exchange member 10 of the present embodiment configured as described above, the fin portion 12 is arranged so that the tube portions 11 through which the heat exchange fluid flows are arranged in parallel, and adjacent tubes. Since the coil body 20 in which the metal wire is wound in a coil shape is filled between the body parts 11, the specific surface area of the fin part 12 through which the heat medium passes increases, and the fin part 12 and the heat A high contact area with the medium is ensured.

As shown in FIG. 3A and FIG. 3B, the coil body 20 is formed with many gaps when viewed from the side surface side and the end surface side, so that the flow of the heat medium passing through the fin portion 12 is not greatly hindered. The pressure loss can be suppressed.
In particular, in this embodiment, the length direction of the coil body 20 is along the width direction of the tube body portion 11, that is, the end surface of the coil body 20 faces the passage direction of the heat medium passing through the fin portion 12. Therefore, the coil body 20 is arranged so as to be largely opened with respect to the flow direction of the heat medium passing through the fin portion 12, and the pressure loss of the heat medium can be suppressed.

As described above, in the heat exchange member 10 according to the present embodiment, the contact area with the heat medium is ensured in the fin portion 12 and the pressure loss of the heat medium is suppressed low. Heat exchange can be efficiently performed between the passing heat medium and the heat exchange fluid flowing through the inside of the tube body part 11.

In the heat exchange member 10 according to the present embodiment, since the porosity of the fin portion 12 is 40% or more, it is possible to reliably prevent an excessive pressure loss of the heat medium passing through the fin portion 12. On the other hand, since the porosity of the fin portion 12 is 90% or less, a contact area with the heat medium passing through the fin portion 12 is ensured, and excellent heat exchange characteristics are obtained.
In order to further reduce the pressure loss of the heat medium passing through the fin portion 12, the upper limit of the porosity of the fin portion 12 is preferably 90% or less. On the other hand, in order to further ensure the contact area with the heat medium passing through the fin portion 12, the lower limit of the porosity of the fin portion 12 is preferably 40% or more.
In order to ensure particularly excellent heat exchange characteristics and pressure loss characteristics, the porosity of the fin portion 12 is preferably 50% or more and 88% or less.

In the heat exchange member 10 according to the present embodiment, since the specific surface area of the fin portion 12 is 300 m ² / m ³ or more, the contact area with the heat medium passing through the fin portion 12 is ensured, and excellent heat Exchange characteristics are obtained. On the other hand, since the 12 specific surface area of the fin portion is 25000 m ² / m ³ or less, it is possible to reliably prevent an excessive pressure loss of the heat medium passing through the fin portion 12.
In order to further secure the contact area with the heat medium passing through the fin portion 12, the upper limit of the specific surface area of the fin portion 12 is preferably 25000 m ² / m ³ or less. On the other hand, in order to further reduce the pressure loss of the heat medium passing through the fin portion 12, the lower limit of the specific surface area of the fin portion 12 is preferably set to 300 m ² / m ³ or more.
In order to ensure particularly excellent heat exchange characteristics and pressure loss characteristics, the specific surface area of the fin portion 12 is preferably 500 m ² / m ³ or more and 20000 m ² / m ³ or less.

As mentioned above, although embodiment of this invention was described, this invention is not limited to this, It can change suitably in the range which does not deviate from the technical idea of the invention.
For example, in the present embodiment, the tubular body portion and the coil body have been described as being composed of aluminum or an aluminum alloy. However, the present invention is not limited to this and is composed of other metals such as copper or a copper alloy. Alternatively, the tube part and the coil body may be made of different metals.

The arrangement of the coil bodies 20 filled between the pipe body portions 11 arranged so as to be arranged in parallel is not limited to that shown in FIG. 2. For example, as shown in FIG. The coil body 20 may be filled so that the vertical direction is along the extending direction of the tubular body portion 11.
As shown in FIG. 6, the length of the coil body 20 may be the same as the interval between the tube body parts 11, and the coil body 20 may be filled so that the end surface of the coil body 20 faces the tube body part 11 side.
In the heat exchange member 10 shown in FIGS. 5 and 6, the side surface of the coil body 20 is opposed to the passing direction of the heat medium passing through the fin portion 12, so the winding pitch P of the coil body 20 is adjusted. By doing so, it is preferable to keep the pressure loss of the heat medium small.
As shown in FIG. 7, the coil body 20 may be filled non-oriented (randomly) between the tubular body portions 11 arranged so as to be arranged in parallel.

As shown in FIG. 8, corrugated fins are arranged as plate-like fin bodies 13 between the tube bodies 11 arranged so as to be arranged in parallel, and the coil bodies 20 are non-oriented (randomly) between the fin bodies 13. It may be filled.
As shown in FIG. 9, a plurality of plate-like fin bodies 13 are arranged between the tubular body portions 11 arranged so as to be arranged in parallel, and the coil bodies 20 are aligned in a space partitioned by the fin bodies 13. And may be filled.
As shown in FIGS. 8 and 9, when the plate-like fin body 13 is arranged between the pipe body portions 11 arranged so as to be arranged in parallel, the coil body 20 has the plate-like fin body 13 and the pipe body. It will be in contact with the part 11 and heat is transferred between the tube part 11 and the fin part 12 well. Therefore, it is possible to further improve the heat exchange characteristics.

In the present embodiment, the tubular body portion 11 and the coil body 20 have been described as being joined by sintering. However, the present invention is not limited to this, and may be joined using a brazing material or the like.
In the present embodiment, a description has been given of a case where a plurality of tubular body portions 11 are arranged in parallel. However, the present invention is not limited to this, and the tubular body portion 11 is bent so as to meander as shown in FIG. And the tube part 11 may be arranged in parallel.
In this embodiment, the coil body having a substantially cylindrical shape has been described as an example. However, the present invention is not limited to this, and the coil body may have a polygonal cross section, and the winding diameter R is long. The coil body may be configured to change in the vertical direction.
In addition, the shapes of the coil bodies used need not all be the same, and a plurality of shapes may be used as long as a predetermined condition is satisfied in various forms defined in this patent.

Hereinafter, the results of a confirmation experiment conducted to confirm the effect of the present invention will be described.

A flat tube (width: 30 mm, thickness: 2 mm) made of aluminum (purity 99% by mass or more) was prepared, the flat tube was bent so as to meander, and a tubular body portion arranged in parallel was formed. . In addition, the center space | interval of the tube part was 15 mm.
And the coil body shown in Table 1 was filled between the tube parts arranged so as to be arranged in parallel. The coil body was made of aluminum (purity 99% by mass or more).
In Examples 41 to 47 of the present invention, corrugated fins (thickness: 0.5 mm, fin shape: triangular wave shape) made of aluminum (purity 99% by mass or more) are provided between the tube parts arranged in parallel. , Fin spacing: 15 mm), and coil bodies were filled between the corrugated fins.
Then, as shown below, sintering was performed at 650 ° C. for 60 minutes in an inert gas atmosphere (Ar gas atmosphere) in a state where the coil bodies were filled in the fin grooves.
In the comparative example, only the above-mentioned corrugated fin was arrange | positioned without filling a coil body between the tubular-body parts arrange | positioned so that it might be arranged in parallel.

In Examples 1 to 7 of the present invention, as shown in FIG. 2, the coil body was filled so that the length direction of the coil body was along the width direction of the tube body portion.
In Inventive Examples 11 to 17, as shown in FIG. 5, the coil body was filled so that the length direction of the coil body was along the extending direction of the tube portion.
In Inventive Examples 21 to 27, as shown in FIG. 6, the coil body was filled so that the end face of the coil body faced the tube body side.

In Invention Examples 31 to 38, as shown in FIG. 7, the coil bodies were filled non-oriented (randomly).
In Examples 41 to 47 of the present invention, as shown in FIG. 8, corrugated fins were arranged, and coil bodies were filled non-oriented (randomly) between the corrugated fins.

The porosity, specific surface area, pressure loss, and heat exchange characteristics of the heat exchange member obtained as described above were evaluated as follows. The evaluation results are shown in Table 1.

(Porosity)
The porosity ε is obtained by the following formula.
ε = {1− (Vp + Vc) / V × 100 (%)
Vp is the volume of the corrugated fin, Vc is the volume of the entire coil (= total coil mass / metal density), and V is the volume of the entire fin including the metal part and the space part.

(Specific surface area)
The specific surface area of the fin portion was measured using a krypton test gas with a BET method specific surface area measurement device (Tristar II 3020 series manufactured by Shimadzu Corporation).

(Pressure loss)
The above-described heat exchange member is fitted into a cooling performance measuring apparatus in which a heat medium (air) flows in one direction, and air at 30 ° C. is flowed at 100 L / min (constant) to the fin portion, The outlet differential pressure was measured.

(Heat exchange characteristics)
Using a cooling performance measuring device in which a heat medium (air) flows in one direction, 80 ° C. ethylene glycol was circulated at 1 L / min as a heat exchange fluid through the tube portion of the heat exchange member. A heat medium (air) at 30 ° C. was flowed through the fin portion at 100 L / min (constant), and the temperature change of the heat exchange fluid was measured. In addition, it becomes the heat exchange member excellent in the heat exchange characteristic with this large temperature change.

In the comparative example in which the coil body was not filled between adjacent tube parts, the temperature change was as small as 6.1 ° C., and the heat exchange characteristics were insufficient. It is estimated that the contact area between the heat medium and the fin portion was small.

On the other hand, in the present invention example in which the fin portion is formed by filling the coil body between the tube portions arranged in parallel, the specific surface area is large and the pressure loss of the heat medium is small. And had excellent heat exchange characteristics.
In particular, Invention Example 2-6 in which the porosity of the fin portion is within the range of 40% to 90% and the specific surface area of the fin portion is within the range of 300 m ² / m ^{3 to} 25000 m ² / m ^3. , 12-16, 22-26, 32-36, 42-46 were more excellent in heat exchange characteristics.

From the above, according to the present invention, the contact area between the fin and the heat medium passing through the fin portion is large, the pressure loss of the heat medium passing through the fin portion is small, and the heat exchanging characteristics are excellent. It was confirmed that an exchange member could be provided.

DESCRIPTION OF SYMBOLS 10 Heat exchange member 11 Tube part 12 Fin part 13 Fin body 20 Coil body

Claims

A heat exchanging member comprising a tube portion disposed so that heat exchange fluid is circulated therein and arranged in parallel, and a fin portion disposed between the adjacent tube portions,
The said fin part is comprised by filling the coil body which wound the metal wire in the coil shape between the said tube part arrange | positioned so that it may parallel, The heat exchange member characterized by the above-mentioned.
The heat exchange member according to claim 1, wherein the fin portion includes a plate-like fin body and the coil body.
The heat exchange member according to claim 1 or 2, wherein a porosity of the fin portion is 40% or more and 90% or less.
The heat exchange member according to any one of claims 1 to 3, wherein a specific surface area of the fin portion is 300 m 2 / m 3 or more and 25000 m 2 / m 3 or less.