JP2003139479A - Heat pump type heat exchanger core - Google Patents
Heat pump type heat exchanger coreInfo
- Publication number
- JP2003139479A JP2003139479A JP2001333755A JP2001333755A JP2003139479A JP 2003139479 A JP2003139479 A JP 2003139479A JP 2001333755 A JP2001333755 A JP 2001333755A JP 2001333755 A JP2001333755 A JP 2001333755A JP 2003139479 A JP2003139479 A JP 2003139479A
- Authority
- JP
- Japan
- Prior art keywords
- region
- refrigerant
- heat exchanger
- tube
- exchanger core
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ヒートポンプ型の
空調用熱交換器コアに関し、特に送風量を大きくするこ
とが困難な室内機のものに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump type air conditioner heat exchanger core, and more particularly to an indoor unit in which it is difficult to increase the amount of air blown.
【０００２】[0002]
【従来の技術】ヒートポンプ型熱交換器コアは、夏期に
おいては室内機が蒸発器として用いられ、冬季において
は凝縮器として用いられる。室内機は、コンパクトで熱
交換性能が良いと共に、ファン等に基づく騒音の低減が
求められていた。特に冬期における暖房能力の高いもの
が要求され且つ、シンプルで製造し易く安価なものが求
めれ、それらの各要素は互いに矛盾する要求であった。2. Description of the Related Art A heat pump type heat exchanger core uses an indoor unit as an evaporator in summer and a condenser in winter. The indoor unit is required to be compact and have good heat exchange performance, and to reduce noise due to a fan or the like. In particular, there is a demand for a high heating capacity in the winter season, and a simple, easy-to-manufacture and inexpensive one is required, and these respective elements are in conflict with each other.
【０００３】従来の室内機としての熱交換器コアは、一
例として図４に示すものが存在した。この熱交換器コア
は、図示しないケーシング形状に合わせて、２列チュー
ブの複数の熱交換器コアが配置されると共に、空気流入
側にさらに１列のコアを重ね合わせたものである。そし
てそれらの内部に図示しないファンを設け、空気流８を
各コアの外周側から内側に流通させて、チューブ内を流
通する冷媒との間に熱交換を行うものである。夫々のコ
アには多数のプレートフィンが並列され、その表面に
は、境界層の発達を阻止する多数のスリットまたはルー
バあるいは波形曲折部が設けられていた。このようなチ
ューブは、通常７mm程度の外直径を有するものが一般的
である。As a conventional heat exchanger core as an indoor unit, there is one shown in FIG. 4 as an example. In this heat exchanger core, a plurality of heat exchanger cores of two rows of tubes are arranged according to a casing shape (not shown), and one row of cores is further stacked on the air inflow side. Then, a fan (not shown) is provided inside them to allow the airflow 8 to flow from the outer peripheral side of each core to the inside so as to exchange heat with the refrigerant flowing in the tubes. A large number of plate fins were arranged in parallel in each core, and a large number of slits or louvers or corrugated bends were provided on the surface thereof to prevent the development of the boundary layer. Such a tube generally has an outer diameter of about 7 mm.
【０００４】[0004]
【発明が解決しようとする課題】図４に示すような従来
型の熱交換器コアは、本体熱交換器に別に制作した複数
のサブコア10を付加しており、その取付け及びパイプの
連結その他が面倒であり、部品点数が多くなりコスト高
とならざるを得ず、これが最大の問題であった。また、
部分的にサブコア10を重ね合わせた部分においては、流
通抵抗が増大し、期待した程の熱交換性能の向上は得ら
れなかった。なお、高性能化のためにチューブの直径を
５mm程とし、チューブの列ピッチ及び段ピッチを小さく
したものも提案されていた。しかしながら、それを用い
て３列チューブのコアを構成すると、空気の流通抵抗が
高くなる欠点があった。そこで、コアに用いる多数のプ
レートフィンをフラットなものとする提案もなされてい
た。しかしながら、その場合にはフラットなるが故の問
題が生じ、フィン表面で境界層が発達し、コストに見合
うほど熱交換性能が向上しなかった。In the conventional heat exchanger core as shown in FIG. 4, a plurality of sub-cores 10 which are separately manufactured are added to the main body heat exchanger. This was a hassle, and the number of parts increased, which inevitably resulted in high costs, and this was the biggest problem. Also,
In the portion where the sub-cores 10 were partially overlapped, the flow resistance increased, and the expected improvement in heat exchange performance was not obtained. In order to improve performance, a tube having a diameter of about 5 mm and a reduced row pitch and row pitch of tubes has been proposed. However, if the core of a three-row tube is constructed by using it, there is a drawback that the flow resistance of air becomes high. Therefore, it has been proposed to make many plate fins used for the core flat. However, in that case, a problem due to the flatness occurred, a boundary layer developed on the fin surface, and the heat exchange performance was not improved enough to meet the cost.
【０００５】また、性能向上のために外径７mmのチュー
ブを用い、全体を３列化した熱交換器コアを用いると、
凝縮性能は２列の場合の約３０％上昇するが、材料投入
量が５割増大してしまう。さらに空気抵抗はほぼ５割程
度増加してしまい、量産品として合理的な範囲の室内機
に事実上、使用することができない。即ち、現在広く用
いられている熱交換器コアをそのまま、チューブ列を３
列化した場合、その性能を向上させることが難しいとこ
ろまできている。そこで本発明は、係る問題点を解決す
ることを課題とする。Further, in order to improve the performance, if a tube having an outer diameter of 7 mm is used and a heat exchanger core having three rows is used,
The condensing performance is increased by about 30% as compared with the case of the two rows, but the material input amount is increased by 50%. Further, the air resistance increases by about 50%, so that it cannot be practically used in an indoor unit within a reasonable range as a mass-produced product. That is, the heat exchanger core that is widely used at present is used as it is, and the tube row is
When lined up, it is difficult to improve its performance. Then, this invention makes it a subject to solve such a problem.
【０００６】[0006]
【課題を解決するための手段】請求項１に記載の本発明
は、小隙を有して並列された細長い多数のプレートフィ
ン(1) と、そのチューブ挿通孔(2) に挿通されたチュー
ブ(3) とを有するヒートポンプ型熱交換器コアにおい
て、前記プレートフィン(1) は、幅方向に第１領域(4)
と第２領域(5) と第３領域(6) とに３等分されており、
夫々の領域にチューブ挿通孔(2) が等間隔に設けられる
と共に、隣接する領域のチューブ挿通孔(2) は互いに半
ピッチ長手方向に位置ずれして千鳥に形成され、少なく
とも前記第１領域(4) にはそのチューブ挿通孔(2) 間
に、ルーバまたは台形のスリット(7) が切り起こされ或
いは、波形に曲折形成され、少なくとも第３領域(6) に
はそれらが存在しないフラット面が形成され、空気流
(8) が前記第１領域(4) から第３領域(6) に流通するよ
うに構成されたことを特徴とするヒートポンプ型熱交換
器コアである。According to the present invention as set forth in claim 1, a large number of elongated plate fins (1) arranged side by side with a small gap and a tube inserted into a tube insertion hole (2) thereof. (3) In the heat pump type heat exchanger core having, the plate fin (1) has a first region (4) in the width direction.
Is divided into three areas, the second area (5) and the third area (6),
The tube insertion holes (2) are provided at equal intervals in each area, and the tube insertion holes (2) in the adjacent areas are staggered with respect to each other in the longitudinal direction by a half pitch, and at least the first area ( 4) A louver or trapezoidal slit (7) is cut or raised between the tube insertion holes (2) or bent in a corrugated form, and there is a flat surface where they do not exist at least in the third region (6). Formed and air flow
(8) is a heat pump type heat exchanger core characterized in that it is configured to flow from the first region (4) to the third region (6).
【０００７】請求項２に記載の本発明は、請求項１にお
いて、夫々の領域における各チューブ(3) は、互いに連
結されて蛇行状となる複数のグループの冷媒流路を有
し、凝縮器として用いる場合では、先ず第３領域(6) の
前記複数のグループの冷媒流路に冷媒が同時に並列的に
供給され、次いで、第２領域(5) の前記複数のグループ
の冷媒流路に冷媒が同時に並列的に供給され、次いで、
第１領域(4) の一部おける前記グループの冷媒流路に冷
媒が供給され、その冷媒出口が第１領域(4) の他部にお
けるグループの冷媒流路に供給されて、その他部の冷媒
流路で冷媒を過冷却する過冷却部(9) が設けられたヒー
トポンプ型熱交換器コアである。According to a second aspect of the present invention, in the first aspect, each tube (3) in each region has a plurality of groups of refrigerant flow passages connected to each other to form a meandering shape, and a condenser is provided. In such a case, first, the refrigerant is simultaneously supplied in parallel to the plurality of groups of refrigerant passages in the third region (6), and then the refrigerant is supplied to the plurality of groups of refrigerant passages in the second region (5). Are fed simultaneously in parallel, then
Refrigerant is supplied to the group of refrigerant channels in a part of the first region (4), and its refrigerant outlet is supplied to the group of refrigerant channels in the other part of the first region (4), and the refrigerant of the other part is supplied. A heat pump type heat exchanger core provided with a supercooling section (9) for supercooling a refrigerant in a flow path.
【０００８】請求項３に記載の本発明は、請求項１また
は請求項２において、前記チューブ(3) の外直径が４mm
〜６mmであり、プレートフィン(1) の長手方向における
チューブ挿通孔(2) のピッチＰ1 が１５mm〜１９mmであ
り、幅方向におけるチューブ挿通孔(2) のピッチＰ2 が
８mm〜１５mmであるヒートポンプ型熱交換器コアであ
る。According to a third aspect of the present invention, in the first or second aspect, the outer diameter of the tube (3) is 4 mm.
The pitch P 1 of the tube insertion holes (2) in the longitudinal direction of the plate fin (1) is 15 mm to 19 mm, and the pitch P 2 of the tube insertion holes (2) in the width direction is 8 mm to 15 mm. It is a heat pump type heat exchanger core.
【０００９】[0009]
【発明の実施の形態】次に、図面に基づいて本発明のヒ
ートポンプ型熱交換器コアの実施の形態につき説明す
る。図１は本発明の熱交換器コアに用いるプレートフィ
ン１の要部平面図及びそのＢ−Ｂ矢視断面略図である。
そして図２はそのプレートフィン１を多数用いて熱交換
器コアを構成した側面図であり、凝縮器としての冷媒の
流れを示す。また、図３は同蒸発器としての冷媒の流れ
を示すものである。BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of a heat pump type heat exchanger core of the present invention will be described with reference to the drawings. FIG. 1 is a plan view of a main part of a plate fin 1 used in a heat exchanger core of the present invention and a schematic cross-sectional view taken along the line BB.
FIG. 2 is a side view showing a heat exchanger core formed by using a large number of the plate fins 1 and shows the flow of refrigerant as a condenser. Further, FIG. 3 shows the flow of the refrigerant as the evaporator.
【００１０】この熱交換器コアは、小隙を有して並列さ
れた図１に示す細長い多数のプレートフィン１と、その
チューブ挿通孔２に挿通された多数のチューブ３（図
２）とを有するものである。そして本発明の主たる特徴
はプレートフィン１にあり、図１の如く幅方向に第１領
域４と第２領域５と第３領域６とに３等分されている。
そして、夫々の領域にチューブ挿通孔２が等間隔に穿設
されると共に、隣接するチューブ挿通孔２は互いに半ピ
ッチ長手方向に位置ずれして千鳥状に配置されている。This heat exchanger core comprises a large number of elongated plate fins 1 shown in FIG. 1 arranged side by side with a small gap, and a large number of tubes 3 (FIG. 2) inserted into their tube insertion holes 2. I have. The main feature of the present invention resides in the plate fin 1, which is divided into the first region 4, the second region 5, and the third region 6 in the width direction as shown in FIG.
The tube insertion holes 2 are formed at equal intervals in the respective areas, and the adjacent tube insertion holes 2 are arranged in a zigzag pattern with their positions displaced from each other in the half pitch longitudinal direction.
【００１１】なお、チューブ挿通孔２の孔縁部は図示し
ないバーリング加工が形成され、平面に対して僅かにチ
ューブ挿通孔２の軸線方向に立ち上げられている。この
チューブ挿通孔２の内直径は４mm〜６mm程度である。ま
た、プレートフィン１の長手方向におけるチューブ挿通
孔２のピッチＰ1 は１５mm〜１９mm程度である。さらに
幅方向におけるチューブ挿通孔２のピッチＰ2 が８mm〜
１５mm程度である。A burring process (not shown) is formed on the hole edge portion of the tube insertion hole 2 and is slightly raised in the axial direction of the tube insertion hole 2 with respect to the plane. The inner diameter of the tube insertion hole 2 is about 4 mm to 6 mm. The pitch P 1 of the tube insertion holes 2 in the longitudinal direction of the plate fin 1 is about 15 mm to 19 mm. Further, the pitch P 2 of the tube insertion holes 2 in the width direction is 8 mm ~
It is about 15 mm.
【００１２】次に、この例では第１領域４及び第２領域
５に台形状に切り起こし形成されたスリット７が各チュ
ーブ挿通孔２間に配置されている。なお、このスリット
７の代わりに傾斜して切り起こされるルーバを設けても
よい。或いは、各チューブ挿通孔２間に三角波状の波形
を、空気流通方向に波が進行するように、曲折形成して
もよい。そして第３領域６には、それらが全く存在しな
いフラット面が形成されている。なお、必要に応じ第２
領域５もスリット７の存在しないフラット面とすること
ができる。或いは、第２領域５のうち空気流８の流入側
のみのスリット７を残し、その下流側のスリット７を取
り除くこともできる。Next, in this example, slits 7 formed by cutting and raising trapezoids in the first region 4 and the second region 5 are arranged between the tube insertion holes 2. Instead of the slit 7, a louver that is inclined and cut and raised may be provided. Alternatively, a triangular waveform may be bent between the tube insertion holes 2 so that the wave travels in the air flow direction. Then, in the third region 6, a flat surface is formed in which they do not exist at all. In addition, if necessary, the second
The region 5 can also be a flat surface without the slit 7. Alternatively, it is possible to leave the slit 7 only on the inflow side of the air flow 8 in the second region 5 and remove the slit 7 on the downstream side.
【００１３】このように少なくとも第３領域６をフラッ
トな面とし、なおかつそこにチューブ挿通孔２を設ける
ことにより、空気側流通抵抗の増大を抑え、空気の流通
を円滑にして、チューブ挿通孔２に挿通されるチューブ
内の冷媒との熱交換を促進させることができる。As described above, at least the third region 6 has a flat surface, and the tube insertion hole 2 is provided therein, so that the increase of the air side flow resistance is suppressed, the air flow is made smooth, and the tube insertion hole 2 is formed. It is possible to promote heat exchange with the refrigerant in the tube inserted into the tube.
【００１４】このようにしてなるプレートフィン１は、
小隙を有して互いに平行に多数並列され、整合する夫々
のチューブ挿通孔２にＵ字状のチューブ３が図２の如く
挿入され、各チューブ３間が短いＵ字状の接続管11によ
り接続され、それにより蛇行状の冷媒流路が複数形成さ
れる。第３領域６においては、４つのグループの冷媒流
路が長手方向に離間して配置され、第２領域５において
も４つの冷媒流路が同様に配置されている。また、第１
領域４においては６つの冷媒流路のグループが存在す
る。そして第３領域６の各冷媒流路のグループの端は、
第２領域５のそれに連結され、さらに第２領域５の各グ
ループの端は第１領域４の図において上方に位置する二
つの冷媒流路に連結され、さらにそれらの端が分岐・合
流管12を介し第１領域４の下部の二つの冷媒流路に連通
する。そして、それらの端が分岐・合流管12に接続され
ている。そして空気流８は、常に第１領域４側から第３
領域６側に流通する。The plate fin 1 thus constructed is
A large number of U-shaped tubes 3 are arranged in parallel with each other with a small gap, and U-shaped tubes 3 are inserted into the matching tube insertion holes 2 as shown in FIG. These are connected, and thereby a plurality of meandering coolant flow paths are formed. In the third region 6, four groups of refrigerant channels are arranged in the longitudinal direction at a distance from each other, and also in the second area 5, four refrigerant channels are similarly arranged. Also, the first
In region 4, there are six groups of coolant channels. And the ends of the groups of the respective refrigerant channels in the third region 6 are
It is connected to that of the second region 5, and the ends of each group of the second region 5 are connected to the two refrigerant flow paths located above in the drawing of the first region 4, and the ends thereof are further branched / merged. To communicate with the two refrigerant passages below the first region 4. Then, their ends are connected to the branch / merge pipe 12. And, the air flow 8 is always from the first region 4 side to the third region
It is distributed to the area 6 side.
【００１５】図２はこの熱交換器コアを凝縮器として用
いる場合の冷媒13の流れを示すものであり、右端中央か
ら分岐・合流管12に流入する冷媒13は二つに分岐される
と共に、さらに第２段目の分岐・合流管12を介して分岐
され、第３領域６の四つの冷媒流路に同時に供給され
る。そして夫々の第３領域６の冷媒流路の端部が第２領
域５に流入し、さらにその端部が第１領域４の上半部の
冷媒流路を介し分岐・合流管12によって合流して、下半
部の第１領域４の二つの冷媒流路を流通し、それが最終
の分岐・合流管12を介して蒸発器側に導かれる。そして
この例では、第１領域４の下半分が過冷却部９を構成す
る。即ち、第１領域４の上半部の冷媒流路で完全に凝縮
した冷媒13が過冷却部９においてさらに冷却される。FIG. 2 shows the flow of the refrigerant 13 when the heat exchanger core is used as a condenser. The refrigerant 13 flowing into the branch / merge pipe 12 from the center of the right end is branched into two. Further, it is branched through the second-stage branch / merge pipe 12, and is simultaneously supplied to the four refrigerant passages in the third region 6. Then, the ends of the refrigerant channels of the respective third regions 6 flow into the second region 5, and the ends thereof are joined by the branch / merge pipe 12 via the refrigerant channels of the upper half of the first region 4. Then, it flows through the two refrigerant flow paths in the first region 4 in the lower half part, and is guided to the evaporator side through the final branching / merging pipe 12. In this example, the lower half of the first area 4 constitutes the supercooling section 9. That is, the refrigerant 13 completely condensed in the upper half of the first region 4 is further cooled in the supercooling section 9.
【００１６】次に、図３は本発明の熱交換器コアを蒸発
器として用いる場合の冷媒13の流れであり、前記図２の
冷媒13の流れとは全く逆となる。Next, FIG. 3 shows the flow of the refrigerant 13 when the heat exchanger core of the present invention is used as an evaporator, which is completely opposite to the flow of the refrigerant 13 shown in FIG.
【００１７】[0017]
【実施例】本発明の熱交換器コアに用いるプレートフィ
ン１として、図１においてピッチＰ1 を１７mmとしピッ
チＰ2 を１０mmとし、第１領域４，第２領域５の各チュ
ーブ挿通孔２間にスリット７を切り起こし形成する。ま
た、チューブ挿通孔２の内直径を５mmとする。上記のよ
うなプレートフィン１を用いた本発明の熱交換器コア
は、従来の７mmチューブ（ピッチＰ1 ：２１mm，ピッチ
Ｐ2 ：１２．７mm）の２列品に対し、同一の前面面積に
おいて、凝縮性能で２６％上昇（空気抵抗４％増加）
し、特に暖房能力の高いことが判った。そして、冷房能
力である蒸発性能で４％上昇（空気抵抗３％上昇）した
ことが判った。また、比較のため第３領域６にもスリッ
ト７を配置すると、空気抵抗が２０％程度まで上昇し、
空気流８の円滑な流通が困難となることが判った。EXAMPLE As the plate fin 1 used in the heat exchanger core of the present invention, in FIG. 1, the pitch P 1 is 17 mm, the pitch P 2 is 10 mm, and the space between the tube insertion holes 2 in the first region 4 and the second region 5 is The slit 7 is cut and raised to form. The inner diameter of the tube insertion hole 2 is 5 mm. The heat exchanger core of the present invention using the plate fins 1 as described above has the same front surface area as the conventional two-row product of 7 mm tubes (pitch P 1 : 21 mm, pitch P 2 : 12.7 mm). 26% increase in condensation performance (4% increase in air resistance)
However, it turned out that the heating capacity was particularly high. It was found that the evaporation performance, which is the cooling capacity, increased by 4% (air resistance increased by 3%). Further, when the slit 7 is arranged in the third region 6 for comparison, the air resistance is increased to about 20%,
It has been found that smooth flow of the air stream 8 becomes difficult.
【００１８】さらに図４に示すように、７mmチューブを
用い２列タイプのコアにサブコア10を付加したものに比
較した場合、本発明の方が凝縮性能で７〜８％上昇し
（空気抵抗１％上昇）、蒸発性能で４〜５％上昇（空気
抵抗同等）を得た。このときの本実施例の材料投入量
は、図４のそれ以下であった。また、このときの空気側
熱伝達率も１９％向上し、空気側熱伝達率と外表面伝熱
面積の積は４６％向上しており、ポテンシャルの高い熱
交換器であることが確認できた。Further, as shown in FIG. 4, when compared with a two-row type core with a sub-core 10 using a 7 mm tube, the present invention increases the condensation performance by 7 to 8% (air resistance 1 % Increase) and a 4-5% increase in evaporation performance (equivalent to air resistance). The amount of material input in this example at this time was less than that in FIG. Further, the air-side heat transfer coefficient at this time was also improved by 19%, and the product of the air-side heat transfer coefficient and the outer surface heat transfer area was improved by 46%, confirming that the heat exchanger has a high potential. .
【００１９】さらにプレートフィンの材料１ｋｇ当たり
の凝縮性能は、図４のそれが1.14ｋｗ／ｋｇであり、本
発明のそれは1.23ｋｗ／ｋｇであった。また、蒸発性能
の場合には同0.92ｋｗ／ｋｇであるのに対し、本発明の
蒸発性能は0.96ｋｗ／ｋｇであった。しかも本発明のコ
アは、細長い単体のプレートのみを用いれば足り、部品
点数が極めて少なく組立てが簡単で製造コストの安いも
のを提供することができる。次に、図１において、スリ
ット７の代わりに波形曲折部を設けたプレートフィンを
製作し、同様の実験を行なったところ、図１の場合のプ
レートフィンと略同一の凝縮性能および蒸発性能の結果
が得られた。Further, the condensing performance per 1 kg of material of the plate fin was 1.14 kw / kg in FIG. 4 and 1.23 kw / kg in the present invention. Further, in the case of the evaporation performance, the same was 0.92 kw / kg, whereas the evaporation performance of the present invention was 0.96 kw / kg. Moreover, the core of the present invention can be provided by using only an elongated single plate, which has a very small number of parts, is easy to assemble, and has a low manufacturing cost. Next, in FIG. 1, a plate fin provided with a corrugated bent portion instead of the slit 7 was manufactured, and the same experiment was performed. was gotten.
【００２０】次に、第２領域５のスリット７のうち、下
流側のものをフラットとした、プレートフィンを作成
し、同様の実験を行なったところ、図１の場合のプレー
トフィンと略同一の凝縮性能および蒸発性能の結果が得
られた。次に、チューブの直径を５．５mmとして、ピッ
チＰ1 を１８mm，ピッチＰ2 を１２mm、第３領域６のみ
フラットとし、同様の実験をしたが、直径５mmのチュー
ブと略同一の凝縮性能および蒸発性能の結果が得られ
た。さらにチューブの直径を４．５mmとして、ピッチＰ
1 を１４mm，ピッチＰ2 を９mm、第３領域６のみフラッ
トとし、同様の実験をしたが、直径５mmのチューブと略
同一の凝縮性能および蒸発性能の結果が得られた。その
結果、チューブ直径が４〜６mmで、ピッチＰ1 が１５mm
〜１９mm、ピッチＰ2 が８mm〜１５mmの範囲では、従来
のものに比し性能の向上が期待できる。Next, when a plate fin was prepared in which the slits 7 in the second region 5 were flat on the downstream side, and a similar experiment was conducted, it was found that the plate fin was substantially the same as the plate fin in the case of FIG. The results of condensation performance and evaporation performance were obtained. Next, the tube diameter was set to 5.5 mm, the pitch P 1 was set to 18 mm, the pitch P 2 was set to 12 mm, and only the third region 6 was flat, and the same experiment was carried out. Evaporation performance results were obtained. Furthermore, the tube diameter is 4.5 mm and the pitch P is
The same experiment was conducted with 1 being 14 mm, the pitch P 2 being 9 mm, and only the third region 6 being flat, but the same condensation and evaporation results as the tube having a diameter of 5 mm were obtained. As a result, the tube diameter is 4 to 6 mm and the pitch P 1 is 15 mm.
～19Mm, in the range of the pitch P 2 is 8Mm～15mm, improvement in comparison with the conventional performance can be expected.
【００２１】[0021]
【発明の作用・効果】請求項１に記載の本発明によれ
ば、少なくとも第１領域４にはそのチューブ挿通孔２間
に、ルーバまたはスリット７が切り起こしまたは波形に
曲折されているため、フィン表面の境界層の発達を阻止
して熱交換を促進する。そして少なくとも第３領域６に
はそれらが存在しないフラット面が形成されているた
め、空気側圧力損失を低下し、空気の流通を促進して熱
交換性能を向上し得る。According to the present invention as set forth in claim 1, since the louver or slit 7 is cut and raised or bent in a corrugated shape at least in the first region 4 between the tube insertion holes 2 thereof, Prevents the development of a boundary layer on the fin surface to promote heat exchange. Since at least the third region 6 is formed with a flat surface without them, the pressure loss on the air side can be reduced, the circulation of air can be promoted, and the heat exchange performance can be improved.
【００２２】請求項２に記載の本発明によれば、第３領
域６及び第２領域５を流通した冷媒がスリット等を有し
て最も熱交換性能の高い第１領域４の一部領域において
先ず冷却され、さらに第１領域４の他部において冷媒が
過冷却される構造を有するから、特に凝縮器として用い
る場合、その凝縮性能を向上できる。請求項３に記載の
本発明によれば、チューブ３の直径及びプレートフィン
１のチューブ挿通孔２の各ピッチを所定の範囲にするこ
とにより、熱交換器の単位重量当たりの凝縮性能及び蒸
発性能を、従来のそれに比べて向上することが可能とな
る。According to the second aspect of the present invention, the refrigerant flowing through the third region 6 and the second region 5 has slits or the like and is in a partial region of the first region 4 having the highest heat exchange performance. Since it has a structure in which it is first cooled and then the refrigerant is supercooled in the other part of the first region 4, the condensing performance can be improved especially when it is used as a condenser. According to the present invention as set forth in claim 3, by setting the diameter of the tube 3 and the pitch of the tube insertion holes 2 of the plate fin 1 within a predetermined range, the condensation performance and the evaporation performance per unit weight of the heat exchanger can be improved. Can be improved as compared with the conventional one.
【図１】本発明の熱交換器コアに用いるプレートフィン
１の要部平面図及びそのＢ−Ｂ矢視断面略図。FIG. 1 is a plan view of a main part of a plate fin 1 used in a heat exchanger core of the present invention and a schematic cross-sectional view taken along the line BB thereof.
【図２】本発明の熱交換器コアを凝縮器として用いる場
合の冷媒13の流通説明図。FIG. 2 is an explanatory view of the flow of the refrigerant 13 when the heat exchanger core of the present invention is used as a condenser.
【図３】本発明の熱交換器コアを蒸発器として用いる場
合の冷媒13の流通説明図。FIG. 3 is an explanatory view of circulation of a refrigerant 13 when the heat exchanger core of the present invention is used as an evaporator.
【図４】従来型熱交換器コアの一例を示す側面図。FIG. 4 is a side view showing an example of a conventional heat exchanger core.
１ プレートフィン ２ チューブ挿通孔 ３ チューブ ４ 第１領域 ５ 第２領域 ６ 第３領域 ７ スリット ８ 空気流 ９ 過冷却部 10 サブコア 11 接続管 12 分岐・合流管 13 冷媒 1 plate fin 2 Tube insertion hole 3 tubes 4 First area 5 Second area 6 third area 7 slits 8 air flow 9 Supercooling section 10 sub-core 11 Connection tube 12 branches / merging pipes 13 Refrigerant
フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ２５Ｂ 39/04 Ｆ２５Ｂ 39/04 Ｙ Continuation of front page (51) Int.Cl. 7 Identification code FI theme code (reference) F25B 39/04 F25B 39/04 Y
Claims (3)
レートフィン(1) と、そのチューブ挿通孔(2) に挿通さ
れたチューブ(3) とを有するヒートポンプ型熱交換器コ
アにおいて、 前記プレートフィン(1) は、幅方向に第１領域(4) と第
２領域(5) と第３領域(6) とに３等分されており、夫々
の領域にチューブ挿通孔(2) が等間隔に設けられると共
に、隣接する領域のチューブ挿通孔(2) は互いに半ピッ
チ長手方向に位置ずれして千鳥に形成され、 少なくとも前記第１領域(4) にはそのチューブ挿通孔
(2) 間に、ルーバまたは台形のスリット(7) が切り起こ
され或いは、波形に曲折形成され、少なくとも第３領域
(6) にはそれらが存在しないフラット面が形成され、 空気流(8) が前記第１領域(4) から第３領域(6) に流通
するように構成されたことを特徴とするヒートポンプ型
熱交換器コア。1. A heat pump type heat exchanger core comprising a large number of elongated plate fins (1) arranged in parallel with a small gap and a tube (3) inserted into a tube insertion hole (2) thereof. The plate fin (1) is divided into a first region (4), a second region (5) and a third region (6) in the width direction, and the tube insertion hole (2) is formed in each region. Are provided at equal intervals, and the tube insertion holes (2) in the adjacent areas are staggered to be displaced from each other in the longitudinal direction by a half pitch, and the tube insertion holes (2) are formed at least in the first area (4).
A louver or a trapezoidal slit (7) is cut or raised between (2) or bent in a corrugated manner, and at least the third region is formed.
The heat pump type is characterized in that a flat surface is formed in (6) without them, and the air flow (8) is configured to flow from the first region (4) to the third region (6). Heat exchanger core.
て蛇行状となる複数のグループの冷媒流路を有し、 凝縮器として用いる場合では、先ず第３領域(6) の前記
複数のグループの冷媒流路に冷媒が同時に並列的に供給
され、 次いで、第２領域(5) の前記複数のグループの冷媒流路
に冷媒が同時に並列的に供給され、 次いで、第１領域(4) の一部おける前記グループの冷媒
流路に冷媒が供給され、その冷媒出口が第１領域(4) の
他部におけるグループの冷媒流路に供給されて、その他
部の冷媒流路で冷媒を過冷却する過冷却部(9) が設けら
れたヒートポンプ型熱交換器コア。2. The tube according to claim 1, wherein each tube (3) in each region has a plurality of groups of refrigerant flow passages which are connected to each other to form a meandering shape. The refrigerant is simultaneously supplied in parallel to the plurality of groups of refrigerant channels of the region (6), and then the refrigerant is simultaneously supplied to the plurality of groups of refrigerant channels of the second region (5) in parallel, Then, the refrigerant is supplied to the refrigerant flow paths of the group in a part of the first region (4), and the refrigerant outlet is supplied to the refrigerant flow paths of the group in the other part of the first region (4), and the other part is supplied. A heat pump type heat exchanger core provided with a supercooling section (9) for supercooling the refrigerant in the refrigerant flow path.
トフィン(1) の長手方向におけるチューブ挿通孔(2) の
ピッチＰ1 が１５mm〜１９mmであり、幅方向におけるチ
ューブ挿通孔(2) のピッチＰ2 が８mm〜１５mmであるヒ
ートポンプ型熱交換器コア。3. The tube according to claim 1 or 2, wherein the tube (3) has an outer diameter of 4 mm to 6 mm, and the pitch P 1 of the tube insertion holes (2) in the longitudinal direction of the plate fin (1) is 15 mm. A heat pump type heat exchanger core having a width of ˜19 mm and a pitch P 2 of the tube insertion holes (2) in the width direction of 8 mm to 15 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001333755A JP2003139479A (en) | 2001-10-31 | 2001-10-31 | Heat pump type heat exchanger core |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001333755A JP2003139479A (en) | 2001-10-31 | 2001-10-31 | Heat pump type heat exchanger core |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003139479A true JP2003139479A (en) | 2003-05-14 |
Family
ID=19148972
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001333755A Pending JP2003139479A (en) | 2001-10-31 | 2001-10-31 | Heat pump type heat exchanger core |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003139479A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005282918A (en) * | 2004-03-29 | 2005-10-13 | Daikin Ind Ltd | Heat exchanger |
| JP2013011369A (en) * | 2011-06-28 | 2013-01-17 | Mitsubishi Electric Corp | Fin tube heat exchanger, and refrigeration cycle apparatus using the same |
| CN102997503A (en) * | 2012-12-13 | 2013-03-27 | Tcl空调器(中山)有限公司 | Heat exchanger and heat pump outdoor unit and heat pump air conditioner using same |
| US9593886B2 (en) | 2008-08-07 | 2017-03-14 | Sanden Holdings Corporation | Heat exchanger and heat pump device using the same |
-
2001
- 2001-10-31 JP JP2001333755A patent/JP2003139479A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005282918A (en) * | 2004-03-29 | 2005-10-13 | Daikin Ind Ltd | Heat exchanger |
| US9593886B2 (en) | 2008-08-07 | 2017-03-14 | Sanden Holdings Corporation | Heat exchanger and heat pump device using the same |
| JP2013011369A (en) * | 2011-06-28 | 2013-01-17 | Mitsubishi Electric Corp | Fin tube heat exchanger, and refrigeration cycle apparatus using the same |
| CN102997503A (en) * | 2012-12-13 | 2013-03-27 | Tcl空调器(中山)有限公司 | Heat exchanger and heat pump outdoor unit and heat pump air conditioner using same |
| CN102997503B (en) * | 2012-12-13 | 2016-02-03 | Tcl空调器(中山)有限公司 | Heat exchanger and use heat-pump-type off-premises station and the heat pump air conditioner of this heat exchanger |
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