JP5034401B2 - Integrated heat exchanger - Google Patents
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この発明は、たとえば自動車に搭載される冷凍サイクルであるカーエアコンに好適に用いられる一体型熱交換器に関する。 The present invention relates to an integrated heat exchanger suitably used for a car air conditioner that is a refrigeration cycle mounted on an automobile, for example.
この明細書および特許請求の範囲において、各図面の上下、左右をそれぞれ上下、左右というものとする。 In the present specification and claims, the upper and lower sides and the left and right sides of each drawing are respectively referred to as the upper and lower sides and the left and right sides.
カーエアコンを構成する冷凍サイクルは、圧縮機、凝縮器、減圧器（膨張弁）および蒸発器を有しており、圧縮機により圧縮された高温高圧のガス状冷媒が凝縮器により凝縮されて液状冷媒となり、液状冷媒が膨張弁により減圧膨張させられた後、蒸発器で蒸発させられるようになっている。また、近年、冷凍サイクルの高効率化を図るために、凝縮器で凝縮された液状冷媒を、さらに凝縮温度よりも５〜１５℃程度低い温度まで過冷却する過冷却器が用いられるようになってきている。 The refrigeration cycle that constitutes a car air conditioner has a compressor, a condenser, a decompressor (expansion valve), and an evaporator. The high-temperature and high-pressure gaseous refrigerant compressed by the compressor is condensed by the condenser to be liquid. It becomes a refrigerant, and after the liquid refrigerant is decompressed and expanded by the expansion valve, it is evaporated by the evaporator. In recent years, in order to increase the efficiency of the refrigeration cycle, a supercooler that supercools the liquid refrigerant condensed in the condenser to a temperature lower by about 5 to 15 ° C. than the condensation temperature has come to be used. It is coming.
従来、凝縮器として、左右方向に間隔をおいて配置された上下方向にのびる１対のヘッダと、両ヘッダ間に上下方向に間隔をおいて並列状に配置されかつ両端部が両ヘッダにそれぞれ接続された複数の扁平状熱交換管と、隣接する熱交換管間に配置されたフィンとを備えており、第１ヘッダに、その内部に冷媒を流入させる冷媒入口が形成されるとともに、第２ヘッダに、その内部から冷媒を流出させる冷媒出口が形成され、熱交換管が幅方向に並んで形成された複数の冷媒通路を有し、両ヘッダ間に、上下に連続して並んだ複数の熱交換管からなり、かつ冷媒が同一方向に流れる１つの通路群が設けられ、冷媒入口から入口ヘッダに流入した冷媒が、全熱交換管内を通って第２ヘッダに流入するようになっているものが知られている（たとえば、特許文献１参照）。なお、特許文献１に記載されているのは、上述した凝縮器からなる凝縮部の下方に、互いに間隔をおいて配置された上下方向にのびる１対のヘッダと、両ヘッダ間に上下方向に間隔をおいて並列状に配置されかつ両端部が両ヘッダにそれぞれ接続された複数の扁平状熱交換管と、隣接する熱交換管間に配置されたフィンとを備えた過冷却部が配置されており、凝縮部の両ヘッダに、それぞれ仕切りを介して過冷却部の両ヘッダが設けられ、凝縮部における冷媒出口が形成された第１ヘッダと、このヘッダに連結された過冷却部の第１ヘッダとにまたがるように受液器が取り付けられ、凝縮部の第１ヘッダの冷媒出口から流出した冷媒が受液器を通過して過冷却部の第１ヘッダに流入するようになっている一体型熱交換器である。
Conventionally, as a condenser, a pair of headers extending in the vertical direction arranged at intervals in the left-right direction, and arranged in parallel with an interval in the vertical direction between both headers, and both end portions on both headers, respectively. A plurality of connected flat heat exchange pipes and fins disposed between adjacent heat exchange pipes, and a refrigerant inlet through which refrigerant flows into the first header is formed in the first header; Two headers are formed with a refrigerant outlet through which the refrigerant flows out from the inside, and a plurality of refrigerant passages in which the heat exchange pipes are formed side by side in the width direction. And one passage group in which the refrigerant flows in the same direction is provided, and the refrigerant that has flowed into the inlet header from the refrigerant inlet flows into the second header through the entire heat exchange pipe. What is known If, see Patent Document 1). Note that
ところで、最近では、広い車室を有する自動車が増加する傾向にある。広い車室を効率良く冷房するには、カーエアコンの性能の向上が求められ、この要求に応えるために、凝縮器においても高性能化が図られている。凝縮器の高性能化には、上下方向に並んだ熱交換管の数を増やしたり、各熱交換管の相当直径および／または各熱交換管の全冷媒通路の合計断面積を小さくすることが効果的であることが知られている。 By the way, recently, the number of automobiles having large cabins has been increasing. In order to efficiently cool a large passenger compartment, an improvement in the performance of a car air conditioner is required, and in order to meet this demand, the performance of a condenser is also improved. In order to improve the performance of the condenser, it is necessary to increase the number of heat exchange tubes arranged in the vertical direction, or to reduce the equivalent diameter of each heat exchange tube and / or the total cross-sectional area of all the refrigerant passages of each heat exchange tube. It is known to be effective.
しかしながら、上下方向に並んだ熱交換管の数を増やしたり、各熱交換管の相当直径および／または各熱交換管の全冷媒通路の合計断面積を小さくすると、各熱交換管の通路抵抗が増大して、冷媒入口から遠い位置にある熱交換管の冷媒通路内に冷媒が流入しにくくなり、その結果全熱交換管への冷媒の分流が不均一になって却って性能が低下するおそれがある。
この発明の目的は、上記問題を解決し、凝縮部の通路群を構成する全熱交換管への冷媒の分流を均一に行いうる一体型熱交換器を提供することにある。 An object of the present invention is to provide an integrated heat exchanger that can solve the above problems and can evenly distribute the refrigerant to all the heat exchange pipes that constitute the passage group of the condensing unit .
本発明は、上記目的を達成するために以下の態様からなる。 In order to achieve the above object, the present invention comprises the following aspects.
1)凝縮部と凝縮部の下方に配置された過冷却部とを備えており、凝縮部が、左右方向に間隔をおいて配置された上下方向にのびる１対のヘッダと、両ヘッダ間に上下方向に間隔をおいて並列状に配置されかつ両端部が両ヘッダにそれぞれ接続された複数の扁平状熱交換管と、隣接する熱交換管間に配置されたフィンとを備えており、凝縮部の一方のヘッダに、その内部に冷媒を流入させる冷媒入口が形成されるとともに、他方のヘッダに、その内部から冷媒を流出させる冷媒出口が形成され、凝縮部の熱交換管が幅方向に並んで形成された複数の冷媒通路を有し、凝縮部の両ヘッダ間に、上下に連続して並んだ複数の熱交換管からなり、かつ冷媒が同一方向に流れる１つの通路群が設けられ、過冷却部が、左右方向に間隔をおいて配置された上下方向にのびる１対のヘッダと、両ヘッダ間に上下方向に間隔をおいて並列状に配置されかつ両端部が両ヘッダにそれぞれ接続された複数の扁平状熱交換管と、隣接する熱交換管間に配置されたフィンとを備えており、凝縮部の両ヘッダおよび過冷却部の両ヘッダが、上下方向にのびかつ上下両端が閉鎖された左右１対のタンク内を仕切りにより仕切ることにより形成され、凝縮部の冷媒出口が形成された上記他方のヘッダと、過冷却部における凝縮部の上記他方のヘッダと同じタンクに形成されたヘッダとにまたがるように受液器が取り付けられ、凝縮部の冷媒入口から一方のヘッダに流入した冷媒が、１つの通路群を構成する全熱交換管内を通って他方のヘッダに流入し、上記他方のヘッダの冷媒出口から流出した冷媒が受液器を通過して過冷却部の上記ヘッダに流入するようになっている一体型熱交換器において、
凝縮部の冷媒入口が、上記一方のタンクヘッダの上端壁に、冷媒の流れ方向が垂直下方を向くように形成され、凝縮部の冷媒出口が、上記他方のヘッダと当該ヘッダの下方に形成された過冷却部のヘッダとの間の仕切りに形成され、冷媒入口から一方のヘッダ内に垂直下向きに流入した冷媒が、通路群を構成する全熱交換管内を通って他方のヘッダに流入し、冷媒出口から流出するようになっており、凝縮部の１つの通路群を構成する上下方向に並んだ熱交換管の数が４０以上であるとともに、上記通路群を構成する各熱交換管の相当直径が０．６ｍｍ以下である一体型熱交換器。
1) A condensing part and a supercooling part arranged below the condensing part are provided, and the condensing part is arranged between a pair of headers extending in the vertical direction and spaced apart in the left-right direction, between both headers. and vertically arranged in parallel form at intervals and a plurality of end portions are connected respectively to the two header flat heat exchange tubes, and a fin disposed between adjacent heat exchange tubes, condensed one of the header parts, together with the refrigerant inlet is formed for flowing coolant therein, the other header, the coolant outlet to flow out of the refrigerant from the inside is formed, the heat exchange tubes in the width direction of the condensation section A plurality of refrigerant passages formed side by side, a plurality of heat exchange tubes arranged continuously in the vertical direction between both headers of the condensing unit , and one passage group in which the refrigerant flows in the same direction is provided. supercooling section, they are arranged in the left-right direction at a spacing A pair of headers extending in the downward direction, a plurality of flat heat exchange tubes arranged in parallel with a space in the vertical direction between the headers, and both ends connected to the headers, and adjacent heat exchanges A fin disposed between the pipes, and the headers of the condensing part and the headers of the supercooling part extend in the vertical direction and partition the inside of a pair of left and right tanks whose upper and lower ends are closed. A liquid receiver is attached to the other header formed with the refrigerant outlet of the condensing unit and the header formed in the same tank as the other header of the condensing unit in the supercooling unit. The refrigerant flowing into the one header from the refrigerant inlet of the section flows into the other header through the total heat exchange pipe constituting one passage group, and the refrigerant flowing out from the refrigerant outlet of the other header is the liquid receiver Pass through In the integrated heat exchanger adapted to flow into the header of the subcooling section Te,
The refrigerant inlet of the condensing part is formed on the upper end wall of the one tank header so that the refrigerant flow direction is vertically downward, and the refrigerant outlet of the condensing part is formed below the other header and the header. Formed in a partition between the header of the supercooling part, and the refrigerant that has flowed vertically downward into one header from the refrigerant inlet flows into the other header through the total heat exchange pipe constituting the passage group, to flow out from the refrigerant outlet, aligned in the vertical direction constituting one passage groups of the condensation portion der
2)凝縮部の通路群を構成する各熱交換管の全冷媒通路の合計断面積が１０ｍｍ２以下である上記1)記載の一体型熱交換器。 2) The integrated heat exchanger according to 1) above, wherein the total cross-sectional area of all refrigerant passages of each heat exchange pipe constituting the passage group of the condensing unit is 10 mm 2 or less.
3)凝縮部の熱交換管が、互いに対向する１対の平坦壁と、両平坦壁の両側縁にまたがる両側壁と、両側壁間において両平坦壁にまたがるとともに長さ方向に伸びかつ相互に所定間隔をおいて設けられた複数の補強壁とを備えているとともに、内部に並列状の複数の流体通路を有しており、各補強壁が、少なくともいずれか一方の平坦壁より内方隆起状に一体成形された補強壁用凸条からなる上記1)または2)記載の一体型熱交換器。 3) The heat exchange pipes in the condensing part have a pair of flat walls facing each other, both side walls straddling both side edges of both flat walls, and span between both flat walls and extend in the longitudinal direction and mutually A plurality of reinforcing walls provided at predetermined intervals, and a plurality of parallel fluid passages in the interior, each reinforcing wall protruding upward from at least one of the flat walls The integrated heat exchanger as described in 1) or 2) above, wherein the reinforcing wall ridges are integrally molded into a shape.
4)凝縮部の熱交換管の一方の側壁が両平坦壁と一体に形成されるとともに、他方の側壁が一方の平坦壁より内方隆起状に一体成形された側壁用凸条と、他方の平坦壁より内方隆起状に一体成形された側壁用凸条とが相互に突き合わされてろう付されることにより形成され、各補強壁が、一方の平坦壁より内方隆起状に一体成形された補強壁用凸条と、他方の平坦壁より内方隆起状に一体成形された補強壁用凸条とが相互に突き合わされてろう付されることにより形成されている上記3)記載の一体型熱交換器。 4) One side wall of the heat exchange pipe of the condensing part is formed integrally with the two flat walls, and the other side wall is integrally formed in a protruding shape inward from the one flat wall, Side wall protrusions that are integrally formed in an inwardly protruding shape from a flat wall are formed by abutting each other and brazed, and each reinforcing wall is integrally formed in an inwardly protruding shape from one flat wall. One of the above-mentioned 3), wherein the reinforcing wall ridges and the reinforcing wall ridges integrally formed so as to protrude inward from the other flat wall are abutted against each other and brazed. Body heat exchanger .
5)圧縮機、上記1)〜4)のうちのいずれかに記載の一体型熱交換器、膨張弁および蒸発器を備えている冷凍サイクル。 5) A refrigeration cycle comprising a compressor , the integrated heat exchanger according to any one of 1) to 4) , an expansion valve, and an evaporator.
6)上記5)記載の冷凍サイクルをエアコンとして備えている車両。 6) A vehicle equipped with the refrigeration cycle described in 5) above as an air conditioner.
上記1)の一体型熱交換器のように、凝縮部の通路群を構成する上下方向に並んだ熱交換管の数が４０以上である場合、冷媒入口から遠い位置にある熱交換管の冷媒通路内に冷媒が流入しにくくなるが、この場合であっても、冷媒入口が、上記一方のタンクヘッダの上端壁に、冷媒の流れ方向が垂直下方を向くように形成されていると、一方のヘッダ内に流入する際の勢いにより、冷媒が一方のヘッダの下端部まで流れるので、上記通路群を構成する全熱交換管への冷媒の分流を均一に行うことができる。したがって、一体型熱交換器の性能が向上する。 When the number of heat exchange tubes arranged in the vertical direction constituting the passage group of the condensing part is 40 or more as in the integrated heat exchanger of 1) above, the refrigerant in the heat exchange tube located far from the refrigerant inlet Although it is difficult for the refrigerant to flow into the passage, even in this case, if the refrigerant inlet is formed on the upper end wall of the one tank header so that the flow direction of the refrigerant is directed vertically downward , Due to the momentum when flowing into the header, the refrigerant flows to the lower end portion of one header, so that the refrigerant can be evenly divided into all the heat exchange tubes constituting the passage group . Therefore, the performance of the integrated heat exchanger is improved.
また、凝縮部の通路群を構成する上下方向に並んだ熱交換管の数が４０以上であるとともに、同通路群を構成する各熱交換管の相当直径が０．６ｍｍ以下場合、冷媒入口から遠い位置にある熱交換管の冷媒通路内に冷媒が流入しにくくなるが、この場合であっても、冷媒入口が、上記一方のタンクヘッダの上端壁に、冷媒の流れ方向が垂直下方を向くように形成されていると、一方のヘッダ内に流入する際の勢いにより、冷媒が一方のヘッダの下端部まで流れるので、通路群を構成する全熱交換管への冷媒の分流を均一に行うことができる。したがって、一体型熱交換器の性能が向上する。 When the number of heat exchange tubes arranged in the vertical direction constituting the passage group of the condensing unit is 40 or more and the equivalent diameter of each heat exchange tube constituting the passage group is 0.6 mm or less, Although it is difficult for the refrigerant to flow into the refrigerant passage of the heat exchange pipe at a far position, even in this case, the refrigerant inlet faces the upper end wall of the one tank header, and the flow direction of the refrigerant faces vertically downward. If formed in this way, the refrigerant flows to the lower end of one header due to the momentum when flowing into one header, so that the refrigerant is evenly distributed to all the heat exchange tubes constituting the passage group. be able to. Therefore, the performance of the integrated heat exchanger is improved.
また、凝縮部の冷媒入口が、上記一方のタンクヘッダの上端壁に、冷媒の流れ方向が垂直下方を向くように形成されているので、一方のヘッダ内に流入する際の勢いにより、冷媒が、効果的に一方のヘッダの下端部まで流れることになり、その結果通路群を構成する全熱交換管への冷媒の分流を均一に行うことができる。したがって、一体型熱交換器の性能が向上する。 Further, since the refrigerant inlet of the condensing part is formed on the upper end wall of the one tank header so that the flow direction of the refrigerant faces vertically downward, the momentum of the refrigerant flows into the one header. Thus, the refrigerant effectively flows to the lower end of one header, and as a result, the refrigerant can be evenly distributed to all the heat exchange tubes constituting the passage group. Therefore, the performance of the integrated heat exchanger is improved .
上記2)の一体型熱交換器のように、凝縮部の通路群を構成する上下方向に並んだ熱交換管の数が４０以上であるとともに、同通路群を構成する各熱交換管の全冷媒通路の合計断面積が１０ｍｍ２以下である場合、冷媒入口から遠い位置にある熱交換管の冷媒通路内に冷媒が流入しにくくなるが、この場合であっても、冷媒入口が、上記一方のタンクヘッダの上端壁に、冷媒の流れ方向が垂直下方を向くように形成されいると、一方のヘッダ内に流入する際の勢いにより、冷媒が一方のヘッダの下端部まで流れるので、上端の熱交換管が属する通路群を構成する全熱交換管への冷媒の分流を均一に行うことができる。したがって、一体型熱交換器の性能が向上する。 Like the integrated heat exchanger of 2) above, the number of heat exchange tubes arranged in the vertical direction constituting the passage group of the condensing unit is 40 or more, and all the heat exchange tubes constituting the passage group are all If the total cross-sectional area of the refrigerant passage is 10 mm 2 or less, although the refrigerant is less likely to flow into the refrigerant passage of the heat exchange tubes located far from the refrigerant inlet, even in this case, the refrigerant inlet, the one If the flow direction of the refrigerant is formed on the upper end wall of the tank header so as to face vertically downward , the refrigerant flows up to the lower end of one header due to the momentum when flowing into one header. It is possible to uniformly distribute the refrigerant to all the heat exchange tubes constituting the passage group to which the heat exchange tubes belong. This improves the performance of the integrated heat exchanger.
上記4)の一体型熱交換器の熱交換管においては、通常の押出形材製熱交換管に比べて、比較的簡単に相当直径を０．６ｍｍ以下にするとともに、全冷媒通路の合計断面積を１０ｍｍ２以下にすることができる。したがって、一体型熱交換器の性能向上に効果的である。 In the heat exchange pipe of the integrated heat exchanger of the above 4) , the equivalent diameter is relatively easily reduced to 0.6 mm or less as compared with a normal heat exchanger pipe made of extruded shape, and the total interruption of all the refrigerant passages is performed. The area can be 10 mm 2 or less. Therefore, it is effective for improving the performance of the integrated heat exchanger .
以下、この発明の実施形態を、図面を参照して説明する。なお、全図面を通じて同一部分および同一物には同一符号を付して重複する説明を省略する。 Embodiments of the present invention will be described below with reference to the drawings. In addition, the same code | symbol is attached | subjected to the same part and the same thing through all drawings, and the overlapping description is abbreviate | omitted.
以下の説明において、「アルミニウム」という用語には、純アルミニウムの他にアルミニウム合金を含むものとする。 In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum.
実施形態１
この実施形態は、図１〜図６に示すものであって、この発明による熱交換器を、コンデンサの機能を有する凝縮部と、過冷却器の機能を有する過冷却部とが一体化された一体型熱交換器に適用したものである。
This embodiment is shown in FIGS. 1 to 6, and in the heat exchanger according to the present invention, a condensing part having a condenser function and a supercooling part having a supercooler function are integrated. This is applied to an integrated heat exchanger.
図１は一体型熱交換器の全体構成を示し、図２〜図６はその要部の構成を示す。 FIG. 1 shows the overall configuration of an integrated heat exchanger, and FIGS. 2 to 6 show the configuration of the main part.
図１において、一体型熱交換器(1)は、気相の冷媒を凝縮させて液相とする凝縮器の機能を有する凝縮部(2)、および凝縮部(2)で凝縮された液状冷媒を凝縮温度よりも５〜１５℃程度低い温度まで過冷却する過冷却器の機能を有する過冷却部(3)が同一垂直面内において上下に並んで設けられ、凝縮部(2)および過冷却部(3)にまたがって受液器(4)が設けられたものである。 In FIG. 1, an integrated heat exchanger (1) includes a condenser section (2) having a condenser function of condensing a gas-phase refrigerant into a liquid phase, and a liquid refrigerant condensed in the condenser section (2). A supercooling section (3) having the function of a supercooler that supercools the water to a temperature lower by about 5 to 15 ° C. than the condensation temperature is provided side by side in the same vertical plane, and the condenser section (2) and the supercooling A liquid receiver (4) is provided across the section (3).
凝縮部(2)は、左右方向に互いに間隔をおいて配置されかつ上下方向にのびる１対のアルミニウム製ヘッダ(5)(6)と、両ヘッダ(5)(6)間に上下方向に間隔をおいて並列状に配置されかつ両端部が両ヘッダ(5)(6)にそれぞれ接続された複数のアルミニウム製扁平状熱交換管(7)と、隣接する熱交換管(7)間に配置されて熱交換管(7)にろう付されたアルミニウム製コルゲートフィン(8)とを備えている。そして、全熱交換管(7)によって、上端の熱交換管(7)が属する１つの通路群(9)を構成している。この通路群(9)を構成する上下方向に並んだ熱交換管(7)の数は４０以上である。上端の熱交換管(7)の上方にはこの熱交換管(7)と間隔をおいてアルミニウム製サイドプレート(11)が配置され、サイドプレート(11)と熱交換管(7)との間にもアルミニウム製コルゲートフィン(8)が配置されてサイドプレート(11)および熱交換管(7)にろう付されている。 The condensing part (2) is vertically spaced between a pair of aluminum headers (5) and (6), which are spaced apart from each other in the left-right direction and extend vertically. Between a plurality of flat aluminum heat exchange tubes (7), which are arranged in parallel with both ends connected to both headers (5) and (6), respectively, and adjacent heat exchange tubes (7) And an aluminum corrugated fin (8) brazed to the heat exchange tube (7). The total heat exchange pipe (7) constitutes one passage group (9) to which the upper end heat exchange pipe (7) belongs. The number of heat exchange tubes (7) arranged in the vertical direction constituting the passage group (9) is 40 or more. An aluminum side plate (11) is disposed above the heat exchange pipe (7) at the upper end with a space from the heat exchange pipe (7), and is disposed between the side plate (11) and the heat exchange pipe (7). Further, an aluminum corrugated fin (8) is disposed and brazed to the side plate (11) and the heat exchange pipe (7).
過冷却部(3)は、左右方向に互いに間隔をおいて配置されかつ上下方向にのびる１対のアルミニウム製ヘッダ(12)(13)と、両ヘッダ(12)(13)間に上下方向に間隔をおいて並列状に配置されかつ両端部が両ヘッダ(12)(13)にそれぞれ接続された複数のアルミニウム製扁平状熱交換管(14)と、隣接する熱交換管(14)間に配置されて熱交換管(14)にろう付されたアルミニウム製コルゲートフィン(8)とを備えている。下端の熱交換管(14)の下方にはこの熱交換管(14)と間隔をおいてアルミニウム製サイドプレート(11)が配置され、サイドプレート(11)と熱交換管(14)との間にもアルミニウム製コルゲートフィン(8)が配置されてサイドプレート(11)および熱交換管(14)にろう付されている。 The supercooling section (3) is vertically arranged between a pair of aluminum headers (12) (13) which are spaced apart from each other in the left-right direction and extend in the up-down direction, and both headers (12) (13). Between a plurality of flat aluminum heat exchange tubes (14) arranged in parallel at intervals and having both ends connected to both headers (12) and (13), respectively, and adjacent heat exchange tubes (14) An aluminum corrugated fin (8) disposed and brazed to the heat exchange pipe (14) is provided. An aluminum side plate (11) is disposed below the heat exchange pipe (14) at the lower end with a space from the heat exchange pipe (14), and is disposed between the side plate (11) and the heat exchange pipe (14). Further, an aluminum corrugated fin (8) is disposed and brazed to the side plate (11) and the heat exchange pipe (14).
凝縮部(2)の両ヘッダ(5)(6)および過冷却部(3)の両ヘッダ(12)(13)は、上下方向にのびかつ上下両端が閉鎖された左右１対のタンク(15)(16)内を、それぞれその下部において仕切り(17)(18)により仕切ることにより形成されたものである。凝縮部(2)の右ヘッダ(6)、すなわち右側タンク(16)の上端壁(19)に冷媒入口(21)が設けられており、冷媒が、流れ方向を垂直下方に向けて凝縮部(2)の右ヘッダ(6)内に流入するようになっている。また、過冷却部(3)の右ヘッダ(13)の周壁に、冷媒を、側方に流して一体型熱交換器(1)から流出させる冷媒出口(30)が設けられている。さらに、左側のタンク(15)の仕切り(17)には、左ヘッダ(5)から冷媒を流出させる後述する冷媒出口(47)が形成されている。したがって、凝縮部(2)の左ヘッダ(5)が冷媒出口(47)を有する第１ヘッダであり、過冷却部(3)の左ヘッダ(12)が第１ヘッダである。また、凝縮部(2)の右ヘッダ(6)が第２ヘッダであり、過冷却部(3)の右ヘッダ(13)が第２ヘッダである。 The headers (5) and (6) of the condensing unit (2) and the headers (12) and (13) of the supercooling unit (3) are a pair of left and right tanks (15 ) (16) is formed by partitioning at the lower part by partitions (17) and (18), respectively. A refrigerant inlet (21) is provided in the right header (6) of the condensing unit (2), that is, the upper end wall (19) of the right tank (16), and the condensing unit (21) It flows into the right header (6) of 2). Further, a refrigerant outlet (30) is provided on the peripheral wall of the right header (13) of the supercooling section (3) to allow the refrigerant to flow laterally and out of the integrated heat exchanger (1). Further, the partition (17) of the left tank (15) is formed with a later-described refrigerant outlet (47) through which the refrigerant flows out from the left header (5). Therefore, the left header (5) of the condensing unit (2) is the first header having the refrigerant outlet (47), and the left header (12) of the supercooling unit (3) is the first header. The right header (6) of the condensing unit (2) is the second header, and the right header (13) of the supercooling unit (3) is the second header.
図２および図３に示すように、凝縮部(2)の熱交換管(7)は、互いに対向する平らな上下壁(22)(23)（１対の平坦壁）と、上下壁(22)(23)の左右両側縁どうしにまたがる左右両側壁(24)(25)と、上壁(22)の左側縁に一体に形成され、かつ左側壁(24)の外面全体を覆う被覆壁(26)と、左右両側壁(24)(25)間において上下壁(22)(23)にまたがるとともに相互に所定間隔をおいて設けられ、かつ長さ方向に伸びる複数の補強壁(27)とよりなり、内部に並列状の複数の冷媒通路(28)を有するものである。なお、図示は省略したが、全ての補強壁(27)には、隣接する流体通路(28)どうしを通じさせる複数の連通穴が、全体として平面から見て千鳥配置状となるようにあけられている。 As shown in FIGS. 2 and 3, the heat exchange pipe (7) of the condensing unit (2) includes flat upper and lower walls (22) and (23) (a pair of flat walls) facing each other, and upper and lower walls (22 ) (23) The left and right side walls (24) (25) straddling the left and right side edges of the upper wall (22) are integrally formed on the left side edge of the upper wall (22) and cover the entire outer surface of the left side wall (24) ( 26) and a plurality of reinforcing walls (27) extending between the left and right side walls (24) and (25), extending across the upper and lower walls (22) and (23) and spaced apart from each other and extending in the length direction. It has a plurality of parallel refrigerant passages (28) inside. Although not shown in the figure, all the reinforcing walls (27) are provided with a plurality of communication holes through which the adjacent fluid passages (28) pass so as to form a staggered arrangement as viewed from above. Yes.
左側壁(24)は、上壁(22)の左側縁より下方隆起状に一体成形された側壁用凸条(29)と、下壁(3)の左側縁より上方隆起状に一体成形された側壁用凸条(31)とが、先端どうしが相互に突き合わされてろう付されることにより形成されている。両側壁用凸条(29)(31)の先端部どうしは相欠き状に突き合わされている。右側壁(25)は、上下壁(22)(23)と一体に形成されている。 The left side wall (24) is integrally molded in a raised shape upward from the left side edge of the lower wall (3) and the side wall protrusion (29) integrally formed in a raised shape from the left side edge of the upper wall (22). The side wall ridges (31) are formed by brazing the tips with each other being butted together. The tip portions of the ridges for both side walls (29) and (31) are abutted in a notch shape. The right side wall (25) is formed integrally with the upper and lower walls (22) and (23).
被覆壁(26)は、上壁(22)の左側縁を左方に延長することにより形成された被覆壁形成部を折り曲げて左側壁(24)外面に沿わせることにより形成されており、その先端部が、下壁(23)の左側縁部の傾斜面(23a)に係合させられた状態で、左側壁(24)、すなわち両側壁用凸条(29)(31)の外面全体および下壁(23)の傾斜面(23a)にろう付されている。 The covering wall (26) is formed by bending a covering wall forming portion formed by extending the left side edge of the upper wall (22) to the left and along the outer surface of the left side wall (24). With the front end engaged with the inclined surface (23a) of the left edge of the lower wall (23), the left side wall (24), that is, the entire outer surface of the side wall ridges (29) (31) and It is brazed to the inclined surface (23a) of the lower wall (23).
補強壁(27)は、上壁(22)より下方隆起状に一体成形された補強壁用凸条(32)(33)と、下壁(23)より上方隆起状に一体成形された補強壁用凸条(34)(35)とが、先端どうしが相互に突き合わされてろう付されることにより形成されている。上壁(22)および下壁(23)には、それぞれ肉厚の異なる２種類の補強壁用凸条(32)(33)および(34)(35)が左右方向に交互に形成されており、上壁(22)における肉厚の厚い補強壁用凸条(32)と下壁(23)における肉厚の薄い補強壁用凸条(35)とがろう付され、上壁(22)における肉厚の薄い補強壁用凸条(33)と下壁(23)における肉厚の厚い補強壁用凸条(34)とがろう付されている。以下、上下両壁(22)(23)の肉厚の厚い補強壁用凸条(32)(34)をそれぞれ第１補強壁用凸条といい、同じく薄い補強壁用凸条(33)(35)をそれぞれ第２補強壁用凸条というものとする。上下壁(22)(23)の第１補強壁用凸条(32)(34)の先端面には、それぞれその長さ方向に伸びかつ他方の壁(23)(22)の第２補強壁用凸条(35)(33)の先端部が嵌る凹溝(36)(37)が全長にわたって形成されている。そして、上壁(22)の第１補強壁用凸条(32)の凹溝(36)内に下壁(23)の第２補強壁用凸条(35)の先端部が、下壁(23)の第１補強壁用凸条(34)の凹溝(37)内に上壁(22)の第２補強壁用凸条(33)の先端部がそれぞれ圧入された状態で、両補強壁用凸条(32)(35)および(33)(34)がろう付されている。 The reinforcing wall (27) includes a reinforcing wall projection (32) (33) integrally formed in a raised shape below the upper wall (22), and a reinforcing wall integrally formed in a raised shape above the lower wall (23). The projecting ridges (34) and (35) are formed by brazing the tips with each other being butted together. On the upper wall (22) and lower wall (23), two types of reinforcing wall projections (32) (33) and (34) (35) with different wall thicknesses are formed alternately in the left-right direction. The thick reinforcing wall ridges (32) on the upper wall (22) and the thin reinforcing wall ridges (35) on the lower wall (23) are brazed, and the upper wall (22) The thin reinforcing wall ridge (33) and the thick reinforcing wall ridge (34) on the lower wall (23) are brazed. Hereinafter, the thick reinforcing wall ridges (32) and (34) of the upper and lower walls (22) and (23) are referred to as first reinforcing wall ridges, respectively, and the thin reinforcing wall ridges (33) ( 35) shall be called the second reinforcing wall projections. The first reinforcing wall projections (32) and (34) of the upper and lower walls (22) and (23) are respectively extended in the length direction thereof, and the second reinforcing wall of the other wall (23) and (22). Concave grooves (36) and (37) into which the tips of the convex protrusions (35) and (33) are fitted are formed over the entire length. And the front-end | tip part of the 2nd reinforcement wall protruding item | line (35) of a lower wall (23) is in the recessed wall (36) of the protruding item | line (32) for 1st reinforcement wall of an upper wall (22). 23) In the state where the tip of the second reinforcing wall projection (33) of the upper wall (22) is press-fitted into the concave groove (37) of the first reinforcing wall projection (34) of 23), both reinforcements The wall ridges (32) (35) and (33) (34) are brazed.
熱交換管(7)の相当直径Ｄｈは０．６ｍｍ以下である場合がある（条件Ｘ）。ここで、相当直径とは、公知のように、複数の非円形冷媒通路を有する熱交換管(7)を、１つの管路を有する円管と見なした場合の管路の等価直径を意味するものであり、次式で定義される。 The equivalent diameter Dh of the heat exchange tube (7) may be 0.6 mm or less (Condition X). Here, the equivalent diameter means an equivalent diameter of the pipe line when the heat exchange pipe (7) having a plurality of non-circular refrigerant passages is regarded as a circular pipe having one pipe line, as is well known. Defined by the following formula.
Ｄｈ＝（４Ａｃ）／Ｐｉであり、Ａｃ：複数の通路の通路断面積の合計、Ｐｉ：複数の通路の断面内周長の合計である。 Dh = (4Ac) / Pi, where Ac is the sum of the passage cross-sectional areas of the plurality of passages, and Pi is the sum of the inner circumferential lengths of the plurality of passages.
また、各熱交換管(7)の全冷媒通路の合計断面積が１０ｍｍ２以下である場合がある（条件Ｙ）。 Moreover, the total cross-sectional area of all the refrigerant paths of each heat exchange pipe (7) may be 10 mm < 2 > or less (condition Y).
熱交換管(7)は、上記条件ＸおよびＹの両方を満たす場合と、いずれか一方を満たす場合がある。 The heat exchange tube (7) may satisfy both of the above conditions X and Y, or may satisfy either one.
凝縮部(2)の熱交換管としては、上記条件ＸおよびＹのうちの少なくともいずれか一方を満たすものであれば、図２および図３に示すものに限定されず、アルミニウム押出形材からなり、かつ幅方向に並んだ複数の冷媒通路を有するものを用いてもよい。 The heat exchange pipe of the condensing part (2) is not limited to the one shown in FIGS. 2 and 3 as long as it satisfies at least one of the above conditions X and Y, and is made of an extruded aluminum shape. And what has a plurality of refrigerant passages arranged in the width direction may be used.
過冷却部(3)の熱交換管(14)としては、凝縮部(2)の熱交換管(7)と同一構成のものを用いてもよいし、あるいは異なる構成のもの、たとえばアルミニウム押出形材製の扁平状であって、幅方向に並んだ複数の冷媒通路を有するものを用いてもよい。また、必ずしも、上記条件ＸおよびＹのうちの少なくともいずれか一方を満たしている必要もない。 As the heat exchange pipe (14) of the supercooling section (3), one having the same configuration as the heat exchange pipe (7) of the condensation section (2) may be used, or one having a different configuration, such as an aluminum extrusion type A flat shape made of a material having a plurality of refrigerant passages arranged in the width direction may be used. Further, it is not always necessary to satisfy at least one of the conditions X and Y.
受液器(4)は、左側のタンク(15)にろう付されたアルミニウム製受液器取付部材(40)に固定されている。図４に示すように、受液器取付部材(40)に、左側のタンク(15)内を凝縮部(2)の左ヘッダ(5)と過冷却部(3)の左ヘッダ(12)とに仕切る仕切り(17)が一体に形成されている。受液器取付部材(40)の右側面の前後両側縁部には、上下方向に伸びる凸部(41)がそれぞれ一体に形成されている。また、受液器取付部材(40)の右側面における両凸部(41)間の部分の下部には凹所(42)が形成されており、凹所(42)の内周面は、左側のタンク(15)の外周面に密着しうる凹円筒面状となっている。受液器取付部材(40)における凹所(42)よりも上方の部分は、左側のタンク(15)に形成された方形貫通穴(43)を通して左側のタンク(15)内に嵌め入れられる嵌入部(44)となっている。嵌入部(44)の上端周縁部に、左側のタンク(15)の内周面に当接し、かつ左側タンク(15)内を凝縮部(2)の左ヘッダ(5))と過冷却部(3)の左ヘッダ(12)とに区画する仕切り(17)が一体に形成されている。なお、凹所(42)の内周面と嵌入部(44)の下面との間の連接部分は、凹球面状となっている。そして、受液器取付部材(40)の両凸部(41)の前後方向内側面および凹所(42)の内周面が、左側タンク(15)の外周面に形成されていたろう材層を利用して左側タンク(15)外周面にろう付されるとともに、嵌入部(44)の仕切り(17)が、左側タンク(15)の内周面に形成されていたろう材層を利用して左側タンク(15)内周面にろう付されることにより、受液器取付部材(40)が左側タンク(15)に固定されている。 The liquid receiver (4) is fixed to an aluminum liquid receiver attachment member (40) brazed to the left tank (15). As shown in FIG. 4, the receiver (40) has a left tank (15) in the left header (5) of the condensing part (2) and a left header (12) of the supercooling part (3). A partition (17) for partitioning is formed integrally. Convex portions (41) extending in the vertical direction are integrally formed on both front and rear side edges of the right side surface of the receiver mounting member (40). Further, a recess (42) is formed in the lower part of the portion between the two convex portions (41) on the right side surface of the receiver mounting member (40), and the inner peripheral surface of the recess (42) is on the left side. It has a concave cylindrical surface that can be in close contact with the outer peripheral surface of the tank (15). The portion of the receiver mounting member (40) above the recess (42) is fitted into the left tank (15) through a rectangular through hole (43) formed in the left tank (15). Part (44). The upper edge of the fitting part (44) is in contact with the inner peripheral surface of the left tank (15), and the left tank (15) is filled with the left header (5) of the condenser part (2)) and the supercooling part ( A partition (17) is formed integrally with the left header (12) of 3). The connecting portion between the inner peripheral surface of the recess (42) and the lower surface of the fitting portion (44) has a concave spherical shape. Then, the brazing material layer formed on the outer peripheral surface of the left tank (15) is the inner surface in the front-rear direction of both convex portions (41) of the receiver mounting member (40) and the inner peripheral surface of the recess (42). Using the brazing material layer formed on the inner peripheral surface of the left tank (15), the partition (17) of the fitting portion (44) is brazed to the outer peripheral surface of the left tank (15). The receiver attachment member (40) is fixed to the left tank (15) by being brazed to the inner peripheral surface of the tank (15).
受液器取付部材(40)には、第１および第２の２つの流路(45)(46)が形成されている。第１流路(45)は、一端が仕切り(17)の上面に開口するとともに、他端が受液器取付部材(40)における左側タンク(15)外側に存在する部分の上面右側部分に開口している。第１流路(45)における仕切り(17)上面への開口が、凝縮部(2)の左ヘッダ(5)の冷媒出口(47)となっている。第２流路(32)は、一端が凹所(42)内周面の底部分に開口するとともに、他端が受液器取付部材(40)における左側タンク(15)外側に存在する部分の上面左側部分に開口している。第２流路(46)の上記一端開口は、左ヘッダ(2)の周壁に形成された円形貫通穴(48)を通して過冷却部(3)の左ヘッダ(12)内に連通している。また、受液器取付部材(40)の上面における第２流路(46)の上記他端開口の周囲には、上方に突出した雄パイプ部(49)が一体に形成されている。雄パイプ部(49)の外周面にはＯリング(51)が装着されている。 The liquid receiver mounting member (40) is formed with first and second flow paths (45), (46). The first flow path (45) has one end opened on the upper surface of the partition (17), and the other end opened on the upper right portion of the portion of the receiver mounting member (40) existing outside the left tank (15). is doing. The opening to the upper surface of the partition (17) in the first flow path (45) is a refrigerant outlet (47) of the left header (5) of the condensing part (2). One end of the second flow path (32) opens at the bottom of the inner peripheral surface of the recess (42), and the other end of the portion of the receiver mounting member (40) that is outside the left tank (15). Opened to the upper left part. The one end opening of the second flow path (46) communicates with the left header (12) of the supercooling section (3) through a circular through hole (48) formed in the peripheral wall of the left header (2). A male pipe portion (49) protruding upward is integrally formed around the opening of the other end of the second flow path (46) on the upper surface of the receiver mounting member (40). An O-ring (51) is mounted on the outer peripheral surface of the male pipe portion (49).
受液器(4)は上端が閉鎖されるとともに下端が開口した筒状体であり、その下端部には、一端が下端面に開口しかつ受液器取付部材(40)の第１流路(45)に通じる第１流路(52)と、一端が下端面に開口しかつ受液器取付部材(40)の第２流路(46)に通じる第２流路(53)とが形成されている。受液器(4)の下端面における第１流路(52)の開口の周囲には、下方に突出しかつ受液器取付部材(40)の第１流路(45)の上記他端開口内に挿入される雄パイプ部(54)が一体に形成されている。雄パイプ部(54)の外周面にはＯリング(55)が装着されている。受液器(4)の第２流路(53)の下端部には、受液器取付部材(40)の雄パイプ部(49)が挿入される大径部(53a)が形成されている。 The liquid receiver (4) is a cylindrical body whose upper end is closed and whose lower end is opened, and at the lower end thereof, one end opens at the lower end surface and the first flow path of the liquid receiver mounting member (40). The first flow path (52) leading to (45) and the second flow path (53) having one end opened at the lower end surface and leading to the second flow path (46) of the receiver mounting member (40) are formed. Has been. Around the opening of the first flow path (52) on the lower end surface of the liquid receiver (4), it projects downward and in the other end opening of the first flow path (45) of the liquid receiver mounting member (40). A male pipe portion (54) to be inserted into is integrally formed. An O-ring (55) is attached to the outer peripheral surface of the male pipe portion (54). A large diameter portion (53a) into which the male pipe portion (49) of the receiver mounting member (40) is inserted is formed at the lower end of the second flow path (53) of the receiver (4). .
なお、図示は省略したが、受液器(4)は複数の部材をアーク溶接などにより溶接することにより形成されたものであり、受液器(4)の内部には、冷媒から異物を除去するフィルタおよび冷媒中の水分を吸収するためのドライヤなどが配置されている。 Although not shown in the figure, the liquid receiver (4) is formed by welding a plurality of members by arc welding or the like, and the liquid receiver (4) has a foreign substance removed from the refrigerant. A filter for absorbing water in the refrigerant and a dryer for absorbing moisture in the refrigerant are disposed.
そして、受液器(4)が受液器取付部材(40)上に載せられるとともに、受液器(4)の雄パイプ部(54)が受液器取付部材(40)の第１流路(45)内に、受液器取付部材(40)の雄パイプ部(49)が受液器(4)の第２流路(53)の大径部(53a)内にそれぞれ嵌め入れられた状態で、図示しない適当なねじ手段によって、受液器(4)が受液器取付部材(40)に固定されている。 The liquid receiver (4) is placed on the liquid receiver mounting member (40), and the male pipe portion (54) of the liquid receiver (4) is the first flow path of the liquid receiver mounting member (40). In (45), the male pipe portion (49) of the receiver mounting member (40) is fitted into the large diameter portion (53a) of the second flow path (53) of the receiver (4). In this state, the liquid receiver (4) is fixed to the liquid receiver mounting member (40) by an appropriate screw means (not shown).
一体型熱交換器(1)は、圧縮機、膨張弁（減圧器）および蒸発器とともに冷凍サイクルを構成し、カーエアコンとして車両に搭載される。 The integrated heat exchanger (1) constitutes a refrigeration cycle together with a compressor, an expansion valve (decompressor), and an evaporator, and is mounted on a vehicle as a car air conditioner.
そして、圧縮機により圧縮された高温高圧のガス状冷媒が冷媒入口(21)を通って凝縮部(2)の右ヘッダ(6)内に、上方から真下に流れるように流入し、分流して凝縮部(2)の通路群(9)を構成する全熱交換管(7)の冷媒通路(28)内に流入する。全熱交換管(7)の冷媒通路(28)内に流入した冷媒は左方に流れて凝縮部(2)の左ヘッダ(5)内に流入する。そして、冷媒は全熱交換管(7)の冷媒通路(28)内を左方に流れる間に凝縮する。左ヘッダ(5)内に流入した冷媒は、冷媒出口(47)を通って左ヘッダ(5)内から流出し、受液器取付部材(40)の第１流路(45)および受液器(4)の第１流路(52)を通って受液器(4)内に流入し、ここで異物および水分が除去された後、受液器(4)の第２流路(53)および受液器取付部材(40)の第２流路(46)を通って過冷却部(3)の左ヘッダ(12)内に流入する。過冷却部(3)の左ヘッダ(12)内に流入した冷媒は、分流して過冷却部(3)の全熱交換管(14)の冷媒通路内に流入し、右方に流れて過冷却部(3)の右ヘッダ(13)内に流入する。そして、冷媒は、過冷却部(3)の全熱交換管(14)の冷媒通路内を右方に流れる間に５〜１５℃過冷却される。右ヘッダ(13)内に流入した冷媒は、冷媒出口(30)を通して一体型熱交換器(1)から流出し、膨張弁を経て蒸発器に送られる。 Then, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor flows into the right header (6) of the condensing unit (2) through the refrigerant inlet (21) so as to flow directly from above, and is divided. It flows into the refrigerant passage (28) of the total heat exchange pipe (7) constituting the passage group (9) of the condensing unit (2). The refrigerant flowing into the refrigerant passage (28) of the total heat exchange pipe (7) flows leftward and flows into the left header (5) of the condensing unit (2). The refrigerant condenses while flowing leftward in the refrigerant passage (28) of the total heat exchange pipe (7). The refrigerant flowing into the left header (5) flows out of the left header (5) through the refrigerant outlet (47), and the first flow path (45) of the receiver mounting member (40) and the receiver. It flows into the liquid receiver (4) through the first flow path (52) of (4), and after the foreign matter and moisture are removed here, the second flow path (53) of the liquid receiver (4) And flows into the left header (12) of the supercooling section (3) through the second flow path (46) of the receiver mounting member (40). The refrigerant that has flowed into the left header (12) of the supercooling section (3) is divided and flows into the refrigerant passage of the total heat exchange pipe (14) of the supercooling section (3), and flows to the right. It flows into the right header (13) of the cooling section (3). The refrigerant is supercooled at 5 to 15 ° C. while flowing right in the refrigerant passage of the total heat exchange pipe (14) of the supercooling section (3). The refrigerant flowing into the right header (13) flows out of the integrated heat exchanger (1) through the refrigerant outlet (30), and is sent to the evaporator through the expansion valve.
実施形態２
この実施形態は図５に示すものであって、この発明による熱交換器を、実施形態１と同様な一体型熱交換器に適用したものである。
This embodiment is shown in FIG. 5, and the heat exchanger according to the present invention is applied to an integrated heat exchanger similar to that of the first embodiment.
図５において、一体型熱交換器(60)の凝縮部(2)の左ヘッダ(5)における高さ方向の中程よりも下方の部分に、左ヘッダ(5)内を上下に仕切るアルミニウム製仕切り(61)が設けられており、これにより凝縮部(2)における仕切り(61)の上下両側部分に、それぞれ上下に連続して並んだ熱交換管(7)からなる通路群(62)(63)が設けられている。下側通路群(63)を構成する熱交換管(7)の本数は、上側通路群(62)を構成する熱交換管(7)の本数よりも減少している。また、各通路群(62)(63)を構成する全ての熱交換管(7)における冷媒の流れ方向が同一となっているとともに、２つの通路群(62)(63)の熱交換管(7)における冷媒の流れ方向が異なっている。そして、上端の熱交換管(7)が属する上側の通路群(62)を構成する上下方向に並んだ熱交換管(7)の数が４０以上となっている。 In FIG. 5, the left header (5) is divided into upper and lower parts in the lower part of the center of the left header (5) in the left header (5) of the condenser (2) of the integrated heat exchanger (60). A partition (61) is provided, and thereby, a passage group (62) consisting of a heat exchange pipe (7) arranged continuously in the vertical direction on both upper and lower sides of the partition (61) in the condensing part (2). 63) is provided. The number of heat exchange tubes (7) constituting the lower passage group (63) is smaller than the number of heat exchange tubes (7) constituting the upper passage group (62). Further, the flow direction of the refrigerant in all the heat exchange pipes (7) constituting each passage group (62) (63) is the same, and the heat exchange pipes of the two passage groups (62) (63) ( The refrigerant flow direction in 7) is different. The number of the heat exchange tubes (7) arranged in the vertical direction constituting the upper passage group (62) to which the heat exchange tube (7) at the upper end belongs is 40 or more.
また、凝縮部(2)の左ヘッダ(5)、すなわち左側タンク(15)の上端壁(64)に、冷媒入口(21)が設けられており、冷媒が、流れ方向を垂直下方に向けて凝縮部(2)の左ヘッダ(5)内に流入するようになっている。 In addition, a refrigerant inlet (21) is provided in the left header (5) of the condensing unit (2), that is, the upper end wall (64) of the left tank (15), and the refrigerant flows in the vertical downward direction. It flows into the left header (5) of the condensing part (2).
実施形態２の一体型熱交換器(60)において、圧縮機により圧縮された高温高圧のガス状冷媒が冷媒入口(21)を通って凝縮部(2)の左ヘッダ(5)における仕切り(61)よりも上方の部分内に、上方から真下に流れるように流入し、分流して凝縮部(2)の上側通路群(62)を構成する全熱交換管(7)の冷媒通路(28)内に流入する。上側通路群(62)を構成する全熱交換管(7)の冷媒通路(28)内に流入した冷媒は右方に流れて右ヘッダ(6)内に流入し、さらに分流して凝縮部(2)の下側通路群(63)を構成する全熱交換管(7)の冷媒通路(28)内に流入し、下側通路群(63)を構成する全熱交換管(7)の冷媒通路(28)内を左方に流れて左ヘッダ(6)における仕切り(61)よりも下方の部分内に流入する。そして、冷媒は両通路群(62)(63)の全熱交換管(7)の冷媒通路(28)内を流れる間に凝縮する。左ヘッダ(5)における仕切り(61)よりも下方の部分内に流入した冷媒は、冷媒出口(47)を通って左ヘッダ(5)内から流出する。その後、冷媒は、実施形態１の一体型熱交換器(1)の場合と同様に流れ、過冷却された後、冷媒出口(30)を通して一体型熱交換器(1)から流出し、膨張弁を経て蒸発器に送られる。 In the integrated heat exchanger (60) of the second embodiment, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor passes through the refrigerant inlet (21) and is partitioned (61 in the left header (5) of the condensing unit (2)). ) Into the upper part of the refrigerant passage (28) of the total heat exchange pipe (7) that flows into the upper part of the condenser part (2) and flows into the part above the upper part of the condenser (2). Flows in. The refrigerant that has flowed into the refrigerant passage (28) of the total heat exchange pipe (7) that constitutes the upper passage group (62) flows to the right and into the right header (6). 2) Refrigerant in the total heat exchange pipe (7) constituting the lower passage group (63) and flowing into the refrigerant passage (28) of the total heat exchange pipe (7) constituting the lower passage group (63) It flows leftward in the passage (28) and flows into a portion below the partition (61) in the left header (6). The refrigerant condenses while flowing in the refrigerant passage (28) of the total heat exchange pipe (7) of both passage groups (62) and (63). The refrigerant that has flowed into the portion below the partition (61) in the left header (5) flows out from the left header (5) through the refrigerant outlet (47). Thereafter, the refrigerant flows in the same manner as in the case of the integrated heat exchanger (1) of the first embodiment, and after being supercooled, flows out of the integrated heat exchanger (1) through the refrigerant outlet (30). And sent to the evaporator.
上記実施形態２においては、通路群の数は２つであるが、これに限定されるものではなく、３以上であってもよい。この場合、上端の熱交換管(7)が属する通路群を構成する上下方向に並んだ熱交換管(7)の数が４０以上となるとともに、凝縮部(2)の左ヘッダ(5)の冷媒出口(47)を通って左ヘッダ(5)から流出するように、左ヘッダ(5)内および右ヘッダ(6)内が適当な位置に設けられた仕切りにより適当な数に仕切られるとともに、冷媒入口(21)の位置が適宜変更される。 In the second embodiment, the number of passage groups is two. However, the number of passage groups is not limited to this, and may be three or more. In this case, the number of heat exchange pipes (7) arranged in the vertical direction constituting the passage group to which the heat exchange pipe (7) at the upper end belongs is 40 or more, and the left header (5) of the condenser (2) The left header (5) and the right header (6) are partitioned into appropriate numbers by partitions provided at appropriate positions so as to flow out from the left header (5) through the refrigerant outlet (47), The position of the refrigerant inlet (21) is appropriately changed.
実施形態３
この実施形態は図６に示すものであって、この発明による熱交換器を、過冷却器とは別体となった凝縮器に適用したものである。
This embodiment is shown in FIG. 6, and the heat exchanger according to the present invention is applied to a condenser which is a separate body from the supercooler.
図６に示す凝縮器(70)の場合、左右方向に互いに間隔をおいて配置されかつ上下方向にのびる１対のアルミニウム製ヘッダ(71)(72)は、実施形態１および２の左右のタンク(15)(16)全体によって形成されている。そして、全熱交換管(7)によって、上端の熱交換管(7)が属する１つの通路群(73)を構成している。この通路群(73)を構成する上下方向に並んだ熱交換管(7)の数は４０以上である。 In the case of the condenser (70) shown in FIG. 6, the pair of aluminum headers (71) and (72) that are spaced apart from each other in the left-right direction and extend in the vertical direction are the left and right tanks of the first and second embodiments. (15) (16) formed entirely. The total heat exchange pipe (7) constitutes one passage group (73) to which the upper end heat exchange pipe (7) belongs. The number of heat exchange tubes (7) arranged in the vertical direction constituting the passage group (73) is 40 or more.
左ヘッダ(71)、すなわち左側タンク(15)の上端壁(64)に、冷媒入口(21)が設けられており、冷媒が、流れ方向を垂直下方に向けて凝縮器(70)の左ヘッダ(71)内に流入するようになっている。 The left header (71), i.e., the upper end wall (64) of the left tank (15) is provided with a refrigerant inlet (21), and the refrigerant flows in a vertically downward direction to the left header of the condenser (70). (71) Inflows.
凝縮器(70)は、圧縮機、膨張弁（減圧器）、蒸発器および過冷却器とともに冷凍サイクルを構成し、カーエアコンとして車両に搭載される。 The condenser (70) constitutes a refrigeration cycle together with a compressor, an expansion valve (decompressor), an evaporator, and a supercooler, and is mounted on a vehicle as a car air conditioner.
そして、圧縮機により圧縮された高温高圧のガス状冷媒が冷媒入口(21)を通って左ヘッダ(71)内に、上方から真下に流れるように流入し、分流して通路群(73)を構成する全熱交換管(7)の冷媒通路(28)内に流入する。全熱交換管(7)の冷媒通路(28)内に流入した冷媒は右方に流れて右ヘッダ(72)内に流入する。そして、冷媒は全熱交換管(7)の冷媒通路(28)内を右方に流れる間に凝縮する。右ヘッダ(72)内に流入した冷媒、右ヘッダ(72)の冷媒出口(30)を通して凝縮器(70)から流出し、膨張弁を経て蒸発器に送られる。 Then, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor flows into the left header (71) through the refrigerant inlet (21) so as to flow directly from above, and is divided to pass through the passage group (73). It flows into the refrigerant passage (28) of the total heat exchange pipe (7) that constitutes it. The refrigerant flowing into the refrigerant passage (28) of the total heat exchange pipe (7) flows rightward and flows into the right header (72). The refrigerant condenses while flowing rightward in the refrigerant passage (28) of the total heat exchange pipe (7). The refrigerant flowing into the right header (72) flows out of the condenser (70) through the refrigerant outlet (30) of the right header (72), and is sent to the evaporator through the expansion valve.
上記実施形態３において、上記実施形態２の凝縮部(2)の場合と同様に、左ヘッダ(71)内および右ヘッダ(72)内が適当な位置に設けられた仕切りにより適当な数に仕切られるとともに、冷媒入口(21)および冷媒出口(30)の位置が適宜変更されることにより、全熱交換管(7)が複数の通路群に分けられていてもよい。この場合も、上端の熱交換管(7)が属する１つの通路群を構成する上下方向に並んだ熱交換管(7)の数は４０以上である。左ヘッダ(71)内および右ヘッダ(72)内が適当な位置に設けられた仕切りにより適当な数に仕切られるとともに、冷媒入口(21)の位置が適宜変更される。 In the third embodiment, as in the case of the condensing unit (2) in the second embodiment, the left header (71) and the right header (72) are partitioned into appropriate numbers by partitions provided at appropriate positions. In addition, the total heat exchange pipe (7) may be divided into a plurality of passage groups by appropriately changing the positions of the refrigerant inlet (21) and the refrigerant outlet (30). Also in this case, the number of heat exchange tubes (7) arranged in the vertical direction constituting one passage group to which the heat exchange tube (7) at the upper end belongs is 40 or more. The left header (71) and the right header (72) are partitioned into appropriate numbers by partitions provided at appropriate positions, and the position of the refrigerant inlet (21) is appropriately changed.
次に、上記実施形態３の凝縮器(70)を用いて行った実験例を、比較実験例とともに示す。 Next, an experimental example performed using the condenser (70) of the third embodiment will be described together with a comparative experimental example.
実験例
凝縮器(70)の全熱交換管(7)の数を６０、各熱交換管(7)の相当直径Ｄｈ：０．４５ｍｍ、各熱交換管(7)の全通路断面積の合計：７．３ｍｍ２とし、入口乾球温度：３５℃、平均圧力：１．５２ＭＰａ、入口過熱度：２５ｄｅｇ、出口過冷度：５ｄｅｇという条件で、風速を変化させつつ、冷媒側能力を測定した。その結果を、図７に示す。
Experimental example The number of total heat exchange tubes (7) of the condenser (70) is 60, the equivalent diameter Dh of each heat exchange tube (7) is 0.45 mm, and the total cross-sectional area of all the heat exchange tubes (7) : 7.3 mm 2 , inlet side dry bulb temperature: 35 ° C., average pressure: 1.52 MPa, inlet superheat degree: 25 deg, outlet supercooling degree: 5 deg. . The result is shown in FIG.
比較実験例
冷媒入口が、左ヘッダの周壁の上端部に設けられ、冷媒が、左側方から左ヘッダ内に流入するようになされている点を除いては、実験例で用いた凝縮器(70)と同じ構成の凝縮器を使用し、上記実験例と同じという条件で、風速を変化させつつ、冷媒側能力を測定した。その結果を、図７に示す。
Comparative Experimental Example The condenser (70) used in the experimental example, except that the refrigerant inlet is provided at the upper end of the peripheral wall of the left header and the refrigerant flows into the left header from the left side. ), The refrigerant side capacity was measured while changing the wind speed under the same conditions as in the above experimental example. The result is shown in FIG.
図７から明らかなように、実験例の凝縮器(70)の冷媒側能力は、比較実験例の凝縮器に比べて２０〜２５％程度向上している。 As is apparent from FIG. 7, the refrigerant side capacity of the condenser (70) of the experimental example is improved by about 20 to 25% compared to the condenser of the comparative experimental example.
上記３つの実施形態において、冷媒入口(21)は、ヘッダ(6)(5)(71)の上端壁(19)(64)に形成されているが、これに限定されるものではなく、上端の熱交換管(14)の上方であれば、ヘッダ(6)(5)(71)の周壁に形成されていてもよい。 In the above three embodiments, the refrigerant inlet (21) is formed in the upper end walls (19) and (64) of the headers (6), (5) and (71), but is not limited to this. As long as it is above the heat exchange pipe (14), it may be formed on the peripheral walls of the headers (6), (5) and (71).
(1)(60)：一体型熱交換器
(2)：凝縮部
(3)：過冷却部
(4)：受液器
(5)(6)：ヘッダ
(7)：熱交換管
(8)：コルゲートフィン
(9)(62)(63)：通路群
(12)(13)：ヘッダ
(14)：熱交換管
(17)(18)：仕切り
(19)(64)：上端閉鎖壁
(21)：冷媒入口
(28)：冷媒通路
(70)：凝縮器
(71)(72)：ヘッダ
(73)：通路群
(1) (60): Integrated heat exchanger
(2): Condensing part
(3): Supercooling section
(4): Liquid receiver
(5) (6): Header
(7): Heat exchange pipe
(8): Corrugated fin
(9) (62) (63): Passage group
(12) (13): Header
(14): Heat exchange pipe
(17) (18): Partition
(19) (64): Top closed wall
(21): Refrigerant inlet
(28): Refrigerant passage
(70): Condenser
(71) (72): Header
(73): Passage group
Claims (6)
凝縮部の冷媒入口が、上記一方のタンクヘッダの上端壁に、冷媒の流れ方向が垂直下方を向くように形成され、凝縮部の冷媒出口が、上記他方のヘッダと当該ヘッダの下方に形成された過冷却部のヘッダとの間の仕切りに形成され、冷媒入口から一方のヘッダ内に垂直下向きに流入した冷媒が、通路群を構成する全熱交換管内を通って他方のヘッダに流入し、冷媒出口から流出するようになっており、凝縮部の１つの通路群を構成する上下方向に並んだ熱交換管の数が４０以上であるとともに、上記通路群を構成する各熱交換管の相当直径が０．６ｍｍ以下である一体型熱交換器。 A condensing unit and a supercooling unit disposed below the condensing unit, wherein the condensing unit is arranged in a vertical direction between a pair of headers extending in the vertical direction and spaced apart in the left-right direction. A plurality of flat heat exchange pipes arranged in parallel at intervals and having both ends connected to both headers, and fins arranged between adjacent heat exchange pipes . One header is formed with a refrigerant inlet through which the refrigerant flows into the header, and the other header is formed with a refrigerant outlet through which the refrigerant flows out from the inside, and the heat exchange tubes of the condensing unit are arranged in the width direction. a plurality of coolant passages formed, between both the header of the condenser section, vertically made to a plurality of heat exchange tubes arranged continuously, and the refrigerant is one passage group is provided with flow in the same direction, over The cooling part is arranged at intervals in the left-right direction. A pair of headers extending in the direction, a plurality of flat heat exchange tubes arranged in parallel with a space in the vertical direction between the headers and having both ends connected to the headers, and adjacent heat exchange tubes The two headers of the condensing part and the headers of the supercooling part are formed by partitioning a pair of left and right tanks extending in the vertical direction and closed at the upper and lower ends with a partition. And a receiver is attached so as to straddle the other header in which the refrigerant outlet of the condensing unit is formed and the header formed in the same tank as the other header of the condensing unit in the supercooling unit. The refrigerant flowing into one header from the refrigerant inlet flows into the other header through the total heat exchange pipe constituting one passage group, and the refrigerant flowing out from the refrigerant outlet of the other header passes through the receiver. Pass In the integrated heat exchanger adapted to flow into the header of the subcooling section,
The refrigerant inlet of the condensing part is formed on the upper end wall of the one tank header so that the refrigerant flow direction is vertically downward, and the refrigerant outlet of the condensing part is formed below the other header and the header. Formed in a partition between the header of the supercooling part, and the refrigerant that has flowed vertically downward into one header from the refrigerant inlet flows into the other header through the total heat exchange pipe constituting the passage group, to flow out from the refrigerant outlet, aligned in the vertical direction constituting one passage groups of the condensation portion der number 40 or more heat exchange tubes Rutotomoni, of the heat exchange tubes which form the passage unit An integrated heat exchanger with an equivalent diameter of 0.6 mm or less .
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| JP2006252525A JP5034401B2 (en) | 2006-09-19 | 2006-09-19 | Integrated heat exchanger |
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| JP2006252525A JP5034401B2 (en) | 2006-09-19 | 2006-09-19 | Integrated heat exchanger |
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| JP5034401B2 true JP5034401B2 (en) | 2012-09-26 |
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| EP1974833A3 (en) | 2007-03-29 | 2017-06-21 | NGK Spark Plug Co., Ltd. | Ultrasonic transducer and ultrasonic apparatus having the same |
| JP5350017B2 (en) * | 2009-03-02 | 2013-11-27 | 株式会社ケーヒン・サーマル・テクノロジー | Plate for tube manufacturing |
| JP7164018B2 (en) * | 2019-03-22 | 2022-11-01 | 昭和電工マテリアルズ株式会社 | cooling structure |
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| JPH0443271A (en) * | 1990-06-11 | 1992-02-13 | Hitachi Ltd | Condenser |
| JPH0566074A (en) * | 1991-09-06 | 1993-03-19 | Hitachi Ltd | Joining method for condenser to liquid receiver |
| JP2000039290A (en) * | 1998-07-22 | 2000-02-08 | Suzuki Motor Corp | Heat exchanger |
| JP2001033121A (en) * | 1999-07-16 | 2001-02-09 | Denso Corp | Heat exchanger integrated with liquid receiver, and liquid receiver |
| JP3955766B2 (en) * | 2002-02-20 | 2007-08-08 | 昭和電工株式会社 | Heat exchanger with receiver tank, receiver tank coupling member, receiver tank assembly structure of heat exchanger, and refrigeration system |
| JP2003279275A (en) * | 2002-03-22 | 2003-10-02 | Matsushita Electric Ind Co Ltd | Heat exchanger and refrigerating cycle device using this heat exchanger |
| JP2005241237A (en) * | 2004-01-27 | 2005-09-08 | Showa Denko Kk | Condenser and heat exchanger |
| JP4759312B2 (en) * | 2004-05-10 | 2011-08-31 | 昭和電工株式会社 | Manufacturing method of heat exchanger |
| JP2006052938A (en) * | 2004-07-15 | 2006-02-23 | Showa Denko Kk | Receiver drier for refrigerating cycle and integrated heat exchanger |
| JP2006200881A (en) * | 2004-12-24 | 2006-08-03 | Showa Denko Kk | Heat exchanger |
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