JPH08131754A - Heat exchanger for dehumidifying compressed air - Google Patents
Heat exchanger for dehumidifying compressed airInfo
- Publication number
- JPH08131754A JPH08131754A JP6298758A JP29875894A JPH08131754A JP H08131754 A JPH08131754 A JP H08131754A JP 6298758 A JP6298758 A JP 6298758A JP 29875894 A JP29875894 A JP 29875894A JP H08131754 A JPH08131754 A JP H08131754A
- Authority
- JP
- Japan
- Prior art keywords
- air
- compressed air
- passage
- heat exchanger
- outlet
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
- F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
- F28D7/085—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Drying Of Gases (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、圧縮空気除湿装置に関
するものであり、特に、除湿能力の高い圧縮空気除湿用
熱交換器に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressed air dehumidifying device, and more particularly to a compressed air dehumidifying heat exchanger having a high dehumidifying capacity.
【０００２】[0002]
【従来技術】この種の熱交換器は、例えば、特開平５−
９６１２２号公報や実開平６−３１８２３号公報に開示
されている。前者には、空気入口と出口とを有する圧力
容器内を、予冷室と冷却室とに分画し、これら両室の外
傍に圧縮空気の流れ方向を反転させる方向変換通路を設
けて、予冷室と冷却室とにおいて互いに熱交換する気体
が、相互に向流状態で流れるようにして、熱交換効率を
向上させ、圧縮空気の乾燥度を高める装置が開示されて
いる。2. Description of the Related Art A heat exchanger of this type is disclosed in, for example, Japanese Unexamined Patent Publication No.
It is disclosed in Japanese Patent No. 96122 and Japanese Utility Model Laid-Open No. 6-31823. In the former, the inside of a pressure vessel having an air inlet and an outlet is divided into a precooling chamber and a cooling chamber, and a direction changing passage for reversing the flow direction of the compressed air is provided on the outer side of these chambers for precooling. An apparatus is disclosed in which gases that exchange heat with each other in a chamber and a cooling chamber flow countercurrently to each other to improve heat exchange efficiency and improve the dryness of compressed air.
【０００３】一方、後者の公報には、上記冷却室に相当
する除湿用熱交換器として、空気流路に冷凍機の蒸発器
と伝熱フィンを収納し、通路形成板（邪魔板）を空気流
路の内周面から蒸発器に向けて交互に延設することによ
り、熱交換器内に一連の蛇行流路を形成し、最も出口側
の通路形成板を空気流路の内周面下部から上方に延びる
ように形成して、気流の方向をドレンの流下方向と分離
することにより、凝縮水が、気流中に巻き込まれて、供
給空気中に移行するのを防止し、乾燥度を高める装置が
開示されている。On the other hand, in the latter publication, as a dehumidifying heat exchanger corresponding to the cooling chamber, an evaporator of a refrigerator and heat transfer fins are housed in an air flow path, and a passage forming plate (baffle plate) is used as air. By alternately extending from the inner peripheral surface of the flow path toward the evaporator, a series of meandering flow paths are formed in the heat exchanger, and the passage forming plate on the most outlet side is located below the inner peripheral surface of the air flow path. It is formed so as to extend upward from the air flow direction and separates the direction of the air flow from the down flow direction of the drain, so that condensed water is prevented from being entrained in the air flow and being transferred into the supply air, thereby improving the dryness. A device is disclosed.
【０００４】これらの従来装置は、上述のように、熱交
換効率の向上やドレンの巻き込み防止によって乾燥度を
向上させるものであるから、これらの不具合が解消さ
れ、或いは、飽和点に到達すれば、その到達乾燥度は、
装着されている冷凍機の冷却能力によって自ずから定ま
り、それ以上に乾燥させることは、不可能である。As described above, these conventional devices improve the heat exchange efficiency and prevent the entrainment of the drain to improve the dryness. Therefore, if these problems are eliminated or the saturation point is reached, , Its ultimate dryness is
It is naturally determined by the cooling capacity of the attached refrigerator, and further drying is impossible.
【０００５】[0005]
【発明の目的】本発明の目的は、このような圧縮空気除
湿用熱交換器において、装置の大型化や構成の複雑化を
伴うことなく、除湿能力を高めることを第一の目的とす
るものであって、特に、上述の従来装置と異なり、圧縮
空気自体の圧力を利用して、装備する冷却器の能力以上
に一段と圧縮空気を冷却除湿して、その乾燥度を高める
ことの出来る圧縮空気除湿装置を開示することにある。An object of the present invention is to increase the dehumidifying ability of such a heat exchanger for dehumidifying compressed air without increasing the size of the apparatus or complicating the structure. In particular, unlike the above-mentioned conventional device, the compressed air can be used to further cool and dehumidify the compressed air by using the pressure of the compressed air itself and further dehumidify the compressed air more than the capacity of the cooler to be equipped. Disclosed is a dehumidifying device.
【０００６】[0006]
【発明の構成】本発明の第一の要旨は、圧縮空気の入口
と出口とを有する圧力容器内の空気流路に冷凍機の冷却
器（蒸発器）を収納して成る空気冷却流路を備えた圧縮
空気除湿用熱交換器において、前記空気冷却流路の途中
に圧縮空気の流れを遮るように設けられた気流遮断板に
よって該空気冷却流路を狭隘化する絞り口を形成したこ
とを特徴とする圧縮空気除湿用熱交換器にある。気流遮
断板によって設けられた気流の絞り口は、空気冷却流路
の内壁面と気流遮断板の端縁との間隙で構成されてもよ
いし、又、気流遮断板に穿設した開口によって構成され
ていてもよい。The first gist of the present invention is to provide an air cooling flow path in which a cooler (evaporator) of a refrigerator is housed in an air flow path inside a pressure vessel having an inlet and an outlet for compressed air. In the heat exchanger for compressed air dehumidification provided, a throttle opening for narrowing the air cooling passage is formed by an airflow blocking plate provided in the middle of the air cooling passage so as to block the flow of compressed air. It is a characteristic heat exchanger for dehumidifying compressed air. The airflow restricting port provided by the airflow blocking plate may be formed by a gap between the inner wall surface of the air cooling channel and the edge of the airflow blocking plate, or by an opening formed in the airflow blocking plate. It may have been done.
【０００７】圧縮空気は、空気冷却流路を流下するに伴
い、その行程に略比例して次第に温度を下げて行き、水
分を冷却器に結露として排出しながら絞り口に到達す
る。そして、該絞り口を通過する際に、若干減圧される
と共に断熱膨張することによって、圧縮空気自体の内部
エネルギーが消費され、圧縮空気は、急激に温度低下す
る。これによって、更に、圧縮空気の露点は低下し、生
じた凝結水は、出口に至るまでに残された冷却器表面に
結露して、ドレンとして排除される。As the compressed air flows down through the air cooling flow path, the temperature of the compressed air gradually decreases in proportion to the stroke of the compressed air and reaches the throttle port while discharging moisture as dew condensation to the cooler. Then, when passing through the throttle opening, the internal energy of the compressed air itself is consumed by being slightly decompressed and adiabatically expanded, and the temperature of the compressed air sharply drops. As a result, the dew point of the compressed air is further lowered, and the generated condensed water is condensed on the surface of the cooler left by the time it reaches the outlet and is removed as drain.
【０００８】本発明の第二の要旨は、圧縮空気の入口と
出口とを有する圧力容器内の空気流路に冷凍機による冷
却器を収納すると共に該空気流路を囲む内壁面から該空
気流路を横断する方向に複数の邪魔板を交互に反対方向
に延設することにより、該空気流路の入口から出口に向
かって蛇行する空気冷却流路を形成して成る圧縮空気除
湿用熱交換器において、前記複数の邪魔板と前記空気流
路内壁面との間に形成される複数の圧縮空気の通過間隙
のうち前記空気冷却流路の出口側近くに位置する一つの
通過間隙の面積を他の通過間隙の面積より狭くすること
により形成した絞り口を有することを特徴とする圧縮空
気除湿用熱交換器にある。A second aspect of the present invention is to store a cooler by a refrigerator in an air flow passage in a pressure vessel having an inlet and an outlet for compressed air, and to supply the air flow from an inner wall surface surrounding the air flow passage. A heat exchange for decompressing compressed air, which is formed by alternately extending a plurality of baffle plates in a direction traversing a path to form an air cooling flow path meandering from an inlet to an outlet of the air flow path. In the container, the area of one passage gap located near the outlet side of the air cooling passage out of the passage gaps of the plurality of compressed air formed between the plurality of baffle plates and the inner wall surface of the air passage. The heat exchanger for dehumidifying compressed air is characterized in that it has a throttle port formed by narrowing the area of other passage gaps.
【０００９】この発明にかかる熱交換器は、前記第一要
旨において用いられた気流遮断板の代わりに、熱交換効
率の向上を目的として冷却器と圧縮空気との接触行程を
長くするために設けた邪魔板のうち、空気冷却流路の出
口に近い位置に設けられた任意の１枚を用いて、この邪
魔板と空気冷却流路内壁面との間の間隙の面積を狭くし
て絞り口を形成したものである。したがって、特別な部
材を必要とせず、邪魔板の１枚を、若干大きくして、取
り付ければよいので、製造上において、殆ど新規な負担
を要せず、しかも、得られる圧縮空気の乾燥度向上効果
は絶大である。The heat exchanger according to the present invention is provided, instead of the airflow blocking plate used in the first aspect, for extending the contact stroke between the cooler and the compressed air for the purpose of improving the heat exchange efficiency. Among the baffle plates, an arbitrary one provided near the outlet of the air cooling channel is used to reduce the area of the gap between the baffle plate and the inner wall surface of the air cooling channel to reduce the aperture. Is formed. Therefore, since no special member is required and one baffle plate can be attached to a slightly larger size, almost no new load is required in manufacturing, and the dryness of the obtained compressed air is improved. The effect is tremendous.
【００１０】本願発明において、絞り口を設ける位置
は、出口との間に若干の空気冷却領域を残している位置
に設けることが望ましい。これは、絞り口が、空気冷却
流路の出口を兼ねているか、若しくは、出口に極めて近
く、空気冷却領域（換言すれば、冷却器との接触域）が
残されていない場合、気流中に生じた凝縮水分は、ドレ
ンとして捕捉される機会が極めて僅かになり、大部分の
凝結水分は、そのまま気流と共に、供給空気側に移行し
てしまう虞れがあるからである。又、絞り口を空気冷却
流路の入口に近い位置に設けた場合、圧縮空気は、その
位置では、未だ、冷却器能力に基づく到達限度には程遠
い高温であるため、本願の目的である冷却器能力以上の
冷却効果は望めない。In the present invention, it is desirable that the throttle opening is provided at a position where a slight air cooling region is left between the throttle opening and the outlet. This is because if the throttle port also serves as the outlet of the air cooling flow path or is very close to the outlet and no air cooling region (in other words, contact region with the cooler) is left, This is because the condensed water generated has a very small chance of being captured as drain, and most of the condensed water may be transferred to the supply air side together with the airflow. Further, when the throttle opening is provided at a position close to the inlet of the air cooling flow path, the compressed air at that position is still at a high temperature far from the reaching limit based on the cooler capacity. The cooling effect beyond the capacity of the vessel cannot be expected.
【００１１】したがって、第二要旨に規定される熱交換
器の場合ならば、出口との間に空気冷却領域を残してい
る位置に設けられた邪魔板であって、なお且つ、該出口
に最も近い位置にある邪魔板と、空気冷却流路内壁との
間隙によって絞り口を構成することが、最も冷却効果が
高い。絞り口の面積は、圧力損失とも関連するので、一
概に規定することは困難であるが、本願発明者による実
験では、空気冷却流路を通過する圧縮空気の流速が、お
よそ７〜１０ｍ／ｓのとき、絞り口の有効面積を２０〜
５０％狭くすると、絞り口を通過する流速は、他の部分
の平均流速に比して、２５〜１００％近く増加し、最高
２℃程度の露点温度低下を示した。Therefore, in the case of the heat exchanger defined in the second aspect, the baffle plate is provided at a position leaving an air cooling region between the heat exchanger and the heat exchanger, and is most close to the outlet. The cooling effect is highest when the aperture is formed by the gap between the baffle plate located close to the inner wall of the air cooling channel. The area of the throttle opening is also related to the pressure loss, so it is difficult to unconditionally define it. However, in the experiment by the inventor of the present application, the flow velocity of the compressed air passing through the air cooling passage is approximately 7 to 10 m / s. , The effective area of the aperture is 20 ~
When the width was narrowed by 50%, the flow velocity passing through the restrictor increased by 25 to 100% as compared with the average flow velocity of other portions, and the maximum dew point temperature decrease was about 2 ° C.
【００１２】絞り口の面積は、空気冷却流路の他の部分
の有効通過断面積のおよそ８０〜５０％の範囲の面積に
設定すれば、圧縮空気圧源の元圧を増加させる事なく、
同等の能力仕様の圧縮空気除湿用熱交換器において、
１.５〜２℃の露点温度低下を発生させることが出来
る。但し、温度低下の割合と、絞り口の面積の狭隘化の
程度とは、必ずしも、比例するものではなく、熱交換器
の形状、仕様、絞り口の形状、位置等によって、異なる
ことは、いうまでもない。以下に、本願発明の好適な一
実施例を掲げて、より詳細に説明する。If the area of the throttle opening is set to an area in the range of about 80 to 50% of the effective passage sectional area of the other part of the air cooling flow passage, the source pressure of the compressed air pressure source is not increased,
In a heat exchanger for compressed air dehumidification with equivalent capacity specifications,
A dew point temperature drop of 1.5-2 ° C can be generated. However, the rate of decrease in temperature and the degree of narrowing of the area of the throttle opening are not necessarily proportional, but differ depending on the shape of the heat exchanger, the specifications, the shape of the throttle opening, the position, etc. There is no end. Hereinafter, a preferred embodiment of the present invention will be described in more detail.
【００１３】[0013]
【実施例】図１〜２は、本願熱交換器の１実施例を示す
ものである。熱交換器１は、圧縮空気の入口３ａと出口
３ｂとを左右両端付近に有する横長円筒形の圧力容器２
を有する。この圧力容器２内は、圧力容器２の左右の鏡
板２ａ，ｂとの間に若干の間隔をおいて設けられた仕切
板１１、１２によって、円筒形空間１０と、該円筒形空
間１０の左右に出口側チャンバー１３ｂ、入口側チャン
バー１３ａとが、夫々画成されている。この円筒形空間
内を長手方向に沿って、更に仕切板で分画することによ
り、最上部に第１変向流路４が画成されている。これ
は、図１において圧力容器１の右端付近から導入される
圧縮空気を左端付近に導いて流れ方向を変えるための流
路である。1 and 2 show one embodiment of the heat exchanger of the present invention. The heat exchanger 1 has a horizontally long cylindrical pressure vessel 2 having inlets 3a and outlets 3b of compressed air near the left and right ends.
Have. The interior of the pressure vessel 2 is divided into a cylindrical space 10 and left and right sides of the cylindrical space 10 by partition plates 11 and 12 provided at a slight interval between the left and right end plates 2a and 2b of the pressure vessel 2. An outlet side chamber 13b and an inlet side chamber 13a are defined therein. By partitioning the inside of this cylindrical space along the longitudinal direction with a partition plate, the first turning flow path 4 is defined at the uppermost portion. This is a flow path for guiding the compressed air introduced from near the right end of the pressure vessel 1 to the vicinity of the left end in FIG. 1 to change the flow direction.
【００１４】この第１変向流路４の下方に隣接して、直
方形の予冷流路５が画成されている。予冷流路の左端付
近の天井面には、第１変向流路４と通じる連通口４ａが
設けられている。この予冷流路５内を左右方向に貫通し
て、多数の熱良導性伝熱パイプから成る再熱流路６が設
けられており、該流路６の左右開口端６ａ、６ａ、…
は、両チャンバー１３ａ，ｂに開口している。予冷流路
５内は、底面及び天井面から再熱流路６に向けて交互
に、バッフルプレート７、７、…が、延設されることに
より圧縮空気が蛇行して流れるようになっている。A rectangular precooling channel 5 is defined below and adjacent to the first turning channel 4. On the ceiling surface near the left end of the precooling passage, a communication port 4a communicating with the first turning passage 4 is provided. A reheat passage 6 composed of a large number of heat-conducting heat transfer pipes is provided penetrating the inside of the precooling passage 5 in the left-right direction, and the left-right open ends 6a, 6a, ... Of the passage 6 are provided.
Are open to both chambers 13a and 13b. In the pre-cooling channel 5, baffle plates 7, 7, ... Are alternately extended from the bottom surface and the ceiling surface toward the reheating channel 6, whereby compressed air meanders and flows.
【００１５】予冷流路５の下方には、若干の空間から成
る第２変向流路８を隔てて、空気冷却流路１５が設けら
れている。第２変向流路８は、図１における左右の仕切
板１１、１２の方向は除いて、図１における前後の水平
方向（換言すれば、図２において左右方向）は、大部分
円筒形空間１０内に開放されている。この第２変向流路
と、予冷流路５とは、予冷流路の右端付近の床面に設け
られた出口開口５ａを通して連通している。予冷流路５
の下方に画成された空気冷却流路１５内には、冷凍機
（図示せず）の蒸発管１６ａと該蒸発管が貫通する多数
の伝熱フィン１６ｂ、…から成る空気冷却器１６が、収
納されている。Below the pre-cooling flow path 5, an air cooling flow path 15 is provided with a second diverting flow path 8 consisting of a small space separated. The second diverting flow path 8 is mostly a cylindrical space in the front-rear horizontal direction (in other words, the left-right direction in FIG. 2) in FIG. 1 except the directions of the left and right partition plates 11 and 12. It is open within 10. The second diversion flow path and the precooling flow path 5 communicate with each other through an outlet opening 5a provided on the floor near the right end of the precooling flow path. Precooling channel 5
An air cooler 16 including an evaporator pipe 16a of a refrigerator (not shown) and a large number of heat transfer fins 16b penetrating the evaporator pipe is provided in an air cooling passage 15 defined below It is stored.
【００１６】この空気冷却器１６には、空気冷却流路１
５の床面と天井面から、夫々邪魔板（バッフルプレー
ト）１７、１７、…が、冷却器１６の方向に延設される
ことによって、該流路１５を流れる圧縮空気が上下に蛇
行し、圧縮空気と冷却器との接触効率が高まるように、
配設されている。勿論、各邪魔板と流路１５の内壁面と
のなす、気流の通過間隙は、通過抵抗に実質的に差が生
じないように設けられる。空気冷却流路１５は、図２に
おいて、仕切板１１に近接した位置における左右側面
に、一対の流入口１５ａ、１５ａが開口すると共に、該
流路１５の右端は、仕切板１２に開口する流出口１５ｂ
を介して、入口側チャンバー１３ａに連通している。３
ｃはドレン排出口である。The air cooler 16 includes an air cooling passage 1
Baffle plates (baffle plates) 17, 17, ... Are respectively extended from the floor surface and the ceiling surface of 5 toward the cooler 16, so that the compressed air flowing in the flow path 15 meanders up and down. To improve the contact efficiency between the compressed air and the cooler,
It is arranged. Of course, the air flow passage gaps formed by the respective baffle plates and the inner wall surface of the flow path 15 are provided so that there is substantially no difference in passage resistance. The air cooling flow path 15 has a pair of inflow ports 15a, 15a opened on the left and right side surfaces at a position close to the partition plate 11 in FIG. 2, and the right end of the flow path 15 is a flow path opened to the partition plate 12. Exit 15b
Via the inlet side chamber 13a. Three
c is a drain discharge port.
【００１７】このような圧縮空気の除湿用熱交換器１に
おいて、空気冷却流路１５の流出口１５ｂとの間に、実
質的に空気を冷却除湿することが出来る空気冷却領域
（換言すれば、冷却器１６の流出口付近の一部分１６
ｃ）を挟んで位置する邪魔板１７ａを、気流遮蔽板とし
て、気流の通過間隙を狭めるために、他の邪魔板１７、
…によりも、空気冷却流路１５の内壁面側に一層突出し
て設けてある。これによって、邪魔板１７ａの下端縁と
冷却流路内壁面とが囲む間隙の面積は、他の邪魔板１
７、…と内壁面との間隙の面積に比べて、約１／２近く
絞られた絞り口Ｓを構成して成るものである。In such a heat exchanger 1 for dehumidifying compressed air, an air cooling region (in other words, a space for cooling and dehumidifying air) can be provided between the outlet 15b of the air cooling passage 15 and the air outlet 15b. Part 16 near the outlet of the cooler 16
The baffle plates 17a located with the c) interposed therebetween are used as airflow shield plates to reduce the airflow passage gap.
Also, it is provided so as to further project to the inner wall surface side of the air cooling flow path 15. As a result, the area of the gap surrounded by the lower end edge of the baffle plate 17a and the inner wall surface of the cooling passage is different from that of the other baffle plate 1.
.. and the inner wall surface, the aperture S is narrowed down by about ½ compared to the area of the gap between the inner wall surface.
【００１８】[0018]
【作用】上記実施例にかかる熱交換器１は、入口３ａか
ら導入された湿った圧縮空気が、第１変向流路４を通っ
て連通口４ａから予冷流路５に入り、再熱流路６中を流
れる、空気冷却流路１５からの乾燥圧縮空気と向流状態
で熱交換して、予冷され出口開口５ａから、空気冷却流
路１５の外傍を通って流入口１５ａに至り、ここから、
空気冷却流路１５内に入る。空気冷却流路中において、
冷却器１６と熱交換して冷却され、上下に蛇行しながら
流出口１５ｂに向かう。In the heat exchanger 1 according to the above-described embodiment, the moist compressed air introduced from the inlet 3a passes through the first diverting passage 4 and enters the precooling passage 5 from the communicating opening 4a to reheat the passage. 6 heat-exchanges with the dry compressed air from the air cooling flow passage 15 in a counterflow state, is pre-cooled, passes through the outer side of the air cooling flow passage 15 to the inflow port 15a, From
It enters the air cooling flow path 15. In the air cooling channel,
It is cooled by exchanging heat with the cooler 16, and meanders up and down toward the outlet 15b.
【００１９】圧縮空気の温度は、流出口１５ｂに近づく
にしたがって、低下するが、絞り口Ｓを通過する際に、
流速を速めると共に、断熱膨張することによって、急激
な温度低下を生じ、発生した凝縮水は、流出口側に残さ
れた冷却器の一部１６ｃによって、冷却され捕捉され
る。かくして、空気冷却流路１５を出た圧縮空気は、従
来と同能力仕様の熱交換器に比べて、一層乾燥度の高い
空気となり、再熱流路において、再熱されて更に相対湿
度が低下した乾燥圧縮空気として、出口３ｂから供給さ
れる。The temperature of the compressed air decreases as it approaches the outlet 15b, but when passing through the throttle S,
A rapid decrease in temperature is caused by increasing the flow velocity and adiabatic expansion, and the generated condensed water is cooled and captured by the part 16c of the cooler left on the outlet side. Thus, the compressed air flowing out from the air cooling flow path 15 becomes air having a higher degree of dryness than the conventional heat exchanger having the same capacity specifications, and is reheated in the reheating flow path to further lower the relative humidity. It is supplied from the outlet 3b as dry compressed air.
【００２０】上記実施例では、気流遮断板として、邪魔
板を利用して、絞り口を形成した例を示したが、これ
は、例えば、図３〜４において、上記実施例と全く同様
に構成した空気冷却流路２５内に、邪魔板２７、２７、
…を設けて、圧縮空気が蛇行して冷却器２６を流れるよ
うにした熱交換器において、空気冷却流路２５の流出口
２５ｂに近い位置において、空気冷却流路を遮断するよ
うに、絞り口としての複数のスリット３１、３１、…が
穿設されている気流遮断板３０を、任意の邪魔板２７ａ
の下端縁から隣の邪魔板２７ｂに、水平に架設したもの
でもよい。In the above embodiment, an example in which the baffle plate is used as the air flow blocking plate to form the aperture is shown, but this has the same structure as that of the above embodiment in FIGS. Baffle plates 27, 27,
In the heat exchanger in which the compressed air meanders and flows through the cooler 26, a throttle opening is provided at a position near the outlet 25b of the air cooling passage 25 so as to block the air cooling passage. The airflow blocking plate 30 having a plurality of slits 31, 31, ...
It may be horizontally installed from the lower end edge to the adjacent baffle plate 27b.
【００２１】この場合、気流遮断板３０の下流に、冷却
器（空気冷却領域）２６ａが、残存していることが、凝
縮水の供給側への巻き上げ移行現象が起こらないので、
好ましい。又、スリットの方向は、伝熱フィン２６ｂの
配列方向と直交するように取り付けるのが望ましい。ス
リットの総面積は、他の邪魔板２７、…と、空気冷却流
路の内壁面との間隙とによって規定される流路の開口面
積のおよそ２０〜５０％減に設定しておけば、１.５〜
２℃の露点温度低下が得られる。In this case, the fact that the cooler (air cooling region) 26a remains downstream of the airflow blocking plate 30 does not cause the phenomenon of hoisting and transfer of condensed water to the supply side.
preferable. Further, it is desirable that the slits are attached so as to be orthogonal to the arrangement direction of the heat transfer fins 26b. If the total area of the slits is set to be about 20 to 50% less than the opening area of the flow passage defined by the other baffle plates 27, ... And the gap between the inner wall surface of the air cooling flow passage, 1 .5
A dew point temperature drop of 2 ° C is obtained.
【００２２】[0022]
【効果】本願熱交換器は、圧縮空気の圧力を、供給圧に
殆ど影響しないごく僅かだけ利用することによって、圧
縮空気を断熱膨張させて、圧縮空気の温度低下を発生さ
せるものであり、又、これを実現する装置としては、邪
魔板を僅かに延長して設けることで、その目的を十分に
達成する事ができる。従って、装置の大型化や、コスト
アップを伴う事なく、圧縮空気除湿熱交換器の能力を一
段と高めることに成功したものである。このことは、同
時に、従来より一段下の能力仕様の冷凍機によって、従
来の圧縮空気除湿装置が実現できることを意味するもの
で、大幅なコストダウン効果と小型化効果とがある。[Effect] The heat exchanger of the present application adiabatically expands the compressed air by utilizing the pressure of the compressed air in a very small amount that hardly affects the supply pressure, and causes the temperature of the compressed air to decrease. As a device for achieving this, the object can be sufficiently achieved by providing the baffle plate by slightly extending it. Therefore, the capacity of the compressed air dehumidifying heat exchanger has been further improved without increasing the size of the apparatus and increasing the cost. This means that at the same time, the conventional compressed air dehumidifying device can be realized by the refrigerator having the capacity specification one step lower than that of the conventional one, which has a significant cost reduction effect and miniaturization effect.
【図１】本願発明の一実施例を示す説明図である。FIG. 1 is an explanatory diagram showing an embodiment of the present invention.
【図２】図１のＡ−Ａ断面説明図である。2 is a cross-sectional view taken along the line AA of FIG.
【図３】本願発明の他の実施例の要部を示す説明図であ
る。FIG. 3 is an explanatory diagram showing a main part of another embodiment of the present invention.
【図４】図３の気流遮断板３０の平面方向から見た説明
図である。FIG. 4 is an explanatory view of the airflow blocking plate 30 of FIG. 3 as seen from the plane direction.
１ 圧縮空気用熱交換器 ２ 圧力容器 ４ 第１変向流路 ５ 予冷流路 ６ 再熱流路 ８ 第２変向流路 １５ 空気冷却流路 １５ａ 流入口 １６ 冷却器 １７ 邪魔板 １７ａ、３０ 気流遮断板 Ｓ 絞り口 DESCRIPTION OF SYMBOLS 1 Heat exchanger for compressed air 2 Pressure vessel 4 1st turning flow path 5 Precooling flow path 6 Reheating flow path 8 2nd turning flow path 15 Air cooling flow path 15a Inlet 16 Cooler 17 Baffle plate 17a, 30 Air flow Blocking plate S Squeezing port
Claims (4)
内の空気流路に冷凍機による冷却器を収納して成る空気
冷却流路を備えた圧縮空気除湿用熱交換器において、前
記空気冷却流路の途中に圧縮空気の流れを遮るように設
けられた気流遮断板によって該空気冷却流路を狭隘化す
る絞り口を形成したことを特徴とする圧縮空気除湿用熱
交換器。1. A compressed air dehumidifying heat exchanger having an air cooling flow path formed by accommodating a cooler by a refrigerator in an air flow path inside a pressure vessel having an inlet and an outlet for compressed air. A heat exchanger for decompressing compressed air, characterized in that an airflow blocking plate provided so as to block the flow of compressed air is provided in the middle of the cooling flow passage to form a throttle port for narrowing the air cooling flow passage.
って構成されている請求項１の熱交換器。2. The heat exchanger according to claim 1, wherein the throttle opening is formed by an opening formed in the airflow blocking plate.
内の空気流路に冷凍機による冷却器を収納すると共に該
空気流路を囲む内壁面から該空気流路を横断する方向に
複数の邪魔板を交互に反対方向に延設することにより、
該空気流路の入口から出口に向かって蛇行する空気冷却
流路を形成して成る圧縮空気除湿用熱交換器において、
前記複数の邪魔板と前記空気流路内壁面との間に形成さ
れる複数の圧縮空気の通過間隙のうち前記空気冷却流路
の出口側近くに位置する一つの通過間隙の面積を他の通
過間隙の面積より狭くすることにより形成した絞り口を
有することを特徴とする圧縮空気除湿用熱交換器。3. A cooler by a refrigerator is housed in an air passage in a pressure vessel having an inlet and an outlet for compressed air, and a plurality of compressors are arranged in a direction traversing the air passage from an inner wall surface surrounding the air passage. By alternately extending baffle plates in the opposite direction,
In a heat exchanger for decompressing compressed air, which comprises an air cooling flow passage meandering from an inlet of the air flow passage toward an outlet thereof,
Among the passage gaps of the plurality of compressed air formed between the plurality of baffle plates and the inner wall surface of the air passage, the area of one passage gap located near the outlet side of the air cooling passage passes through the other passage area. A heat exchanger for dehumidifying compressed air, having a throttle port formed by making the area smaller than the gap.
気冷却領域を残して設けられた邪魔板であって、且つ、
該出口に最も近い位置にある邪魔板と、空気冷却流路内
壁との間隙によって構成されている請求項３の熱交換
器。4. A baffle plate, wherein the throttle port is provided so as to leave an air cooling region between it and the outlet of the air cooling channel, and
The heat exchanger according to claim 3, which is constituted by a gap between the baffle plate located closest to the outlet and the inner wall of the air cooling passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6298758A JP3021298B2 (en) | 1994-11-07 | 1994-11-07 | Heat exchanger for compressed air dehumidification |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6298758A JP3021298B2 (en) | 1994-11-07 | 1994-11-07 | Heat exchanger for compressed air dehumidification |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08131754A true JPH08131754A (en) | 1996-05-28 |
| JP3021298B2 JP3021298B2 (en) | 2000-03-15 |
Family
ID=17863854
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6298758A Expired - Fee Related JP3021298B2 (en) | 1994-11-07 | 1994-11-07 | Heat exchanger for compressed air dehumidification |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3021298B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2430898A (en) * | 2005-10-06 | 2007-04-11 | Teng-Fu Chen | Air barrel of air compressor |
| CN105020944A (en) * | 2014-04-25 | 2015-11-04 | 重庆美的通用制冷设备有限公司 | Water chilling unit and heat exchanger thereof |
| JP2016203064A (en) * | 2015-04-17 | 2016-12-08 | オリオン機械株式会社 | Compressed air dehumidification device |
| JP2017181024A (en) * | 2014-09-09 | 2017-10-05 | 有限会社泰栄産業 | Compressed air cooling method and compressed air cooling device |
| CN108413783A (en) * | 2017-02-10 | 2018-08-17 | 中国石化工程建设有限公司 | A kind of and tower function heat exchanger |
| CN109758882A (en) * | 2019-03-04 | 2019-05-17 | 张君宇 | A kind of tunnel oven discharged gas fume reheating takes off white system and treatment process |
| KR20200015521A (en) | 2017-06-08 | 2020-02-12 | 에스엠시 가부시키가이샤 | Dehumidification system provided with a heat exchanger for compressed air, the dehumidification unit using the heat exchanger, and the dehumidification unit |
| CN116123896A (en) * | 2023-02-09 | 2023-05-16 | 唐山市宝凯科技有限公司 | Efficient heat exchanger |
-
1994
- 1994-11-07 JP JP6298758A patent/JP3021298B2/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2430898A (en) * | 2005-10-06 | 2007-04-11 | Teng-Fu Chen | Air barrel of air compressor |
| CN105020944A (en) * | 2014-04-25 | 2015-11-04 | 重庆美的通用制冷设备有限公司 | Water chilling unit and heat exchanger thereof |
| CN105020944B (en) * | 2014-04-25 | 2019-08-30 | 重庆美的通用制冷设备有限公司 | Water cooler and its heat exchanger |
| JP2017181024A (en) * | 2014-09-09 | 2017-10-05 | 有限会社泰栄産業 | Compressed air cooling method and compressed air cooling device |
| JP2016203064A (en) * | 2015-04-17 | 2016-12-08 | オリオン機械株式会社 | Compressed air dehumidification device |
| CN108413783A (en) * | 2017-02-10 | 2018-08-17 | 中国石化工程建设有限公司 | A kind of and tower function heat exchanger |
| CN108413783B (en) * | 2017-02-10 | 2019-11-22 | 中国石化工程建设有限公司 | A kind of and tower function heat exchanger |
| KR20200015521A (en) | 2017-06-08 | 2020-02-12 | 에스엠시 가부시키가이샤 | Dehumidification system provided with a heat exchanger for compressed air, the dehumidification unit using the heat exchanger, and the dehumidification unit |
| US11135548B2 (en) | 2017-06-08 | 2021-10-05 | Smc Corporation | Compressed-air heat exchanger, dehumidification unit using heat exchanger, and dehumidification system provided with dehumidification unit |
| CN109758882A (en) * | 2019-03-04 | 2019-05-17 | 张君宇 | A kind of tunnel oven discharged gas fume reheating takes off white system and treatment process |
| CN116123896A (en) * | 2023-02-09 | 2023-05-16 | 唐山市宝凯科技有限公司 | Efficient heat exchanger |
| CN116123896B (en) * | 2023-02-09 | 2024-01-19 | 唐山市宝凯科技有限公司 | Efficient heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3021298B2 (en) | 2000-03-15 |
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