JPS6346391A - Fluidized bed heat exchanger - Google Patents
Fluidized bed heat exchangerInfo
- Publication number
- JPS6346391A JPS6346391A JP19023486A JP19023486A JPS6346391A JP S6346391 A JPS6346391 A JP S6346391A JP 19023486 A JP19023486 A JP 19023486A JP 19023486 A JP19023486 A JP 19023486A JP S6346391 A JPS6346391 A JP S6346391A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- fluidized bed
- particles
- fluidized
- fluidized particles
- 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
Links
- 239000002245 particle Substances 0.000 claims abstract description 35
- 238000005219 brazing Methods 0.000 abstract description 2
- 230000003111 delayed effect Effects 0.000 abstract description 2
- 239000002826 coolant Substances 0.000 abstract 1
- 230000000717 retained effect Effects 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000011295 pitch Substances 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- PXBRQCKWGAHEHS-UHFFFAOYSA-N dichlorodifluoromethane Chemical compound FC(F)(Cl)Cl PXBRQCKWGAHEHS-UHFFFAOYSA-N 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 229920006327 polystyrene foam Polymers 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は空調用、ヒートポンプ用、あるいは産業用熱交
換器等に広く利用できる流動層熱交換器に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a fluidized bed heat exchanger that can be widely used for air conditioning, heat pumps, industrial heat exchangers, and the like.
流動層熱交換器は、従来、化学プラント用あるいは排熱
回収用等に広く用いられているがこれらは一般に流動粒
子の密度が犬きく(ρρ≠3000Kqm /m’ )
粒子径も0.3φ個以下と小さいため、圧力損失が10
0+a+Aq以上と大きく、圧力損失が5+l1lII
Aq程度のヒートポンプ用熱−交換器等のような低圧損
タイプの熱交換器には使用されていないのが実情である
。Fluidized bed heat exchangers have conventionally been widely used for chemical plants or waste heat recovery, but these generally have a high density of fluidized particles (ρρ≠3000Kqm/m').
The particle size is small, less than 0.3φ, so the pressure loss is 10
Large pressure loss of 0+a+Aq or more, 5+l1lII
The reality is that it is not used in low pressure drop type heat exchangers such as Aq heat exchangers for heat pumps.
ヒートポンプ用流動層熱交換器等の低圧損タイプとして
使用する場合、流動粒子径を決めると熱交換器のフィン
間あるいはチューブ間で粒子が安定浮遊できる最少のフ
ィン間隔あるいはチューブ間隔が存在する。When used as a low pressure drop type such as a fluidized bed heat exchanger for a heat pump, there is a minimum fin spacing or tube spacing that allows particles to be stably suspended between the fins or tubes of the heat exchanger when the diameter of the fluidized particles is determined.
即ち、流動粒子を安定浮遊させることにより低圧損で熱
伝達率を向上させるための最適値が存在する。That is, there is an optimum value for improving the heat transfer coefficient with low pressure drop by stably suspending the fluidized particles.
本発明は、ヒートポンプ用熱交換器等の低圧損タイプの
ものとして必要な低圧損で高熱伝達率を得ることができ
る流動層熱交換器を提供しようとするものである。The present invention aims to provide a fluidized bed heat exchanger that can obtain a high heat transfer coefficient with a low pressure drop necessary for a low pressure drop type heat exchanger such as a heat exchanger for a heat pump.
本発明は、上記課題を達成するため、熱交換器のまわり
に流動粒子を保持せしめてなる流動層熱交換器において
、前記流動粒子の径に対して、前記熱交換器のフィン間
隔もしくはチューブ間隔の比率を3倍以上として流動層
熱交換器を構成したものである。In order to achieve the above object, the present invention provides a fluidized bed heat exchanger in which fluidized particles are held around the heat exchanger. The fluidized bed heat exchanger is configured with a ratio of 3 times or more.
上記のようにフィン間隔もしくはチューブ間隔を流動粒
子の径の3倍以上とすることにより。By setting the fin spacing or tube spacing to three times or more the diameter of the fluidized particles as described above.
フィンあるいはチューブ表面上に空気流れ方向に沿って
できる温度境界層内に流動粒子を安定浮遊させることが
できる。Fluid particles can be stably suspended in a temperature boundary layer formed along the air flow direction on the fin or tube surface.
以下に本発明の実施例を図面に基づいて説明する。 Embodiments of the present invention will be described below based on the drawings.
第1図に冷媒(フレオン22又は12)が流れる複数本
の扁平チー−ブ3と複数枚のフィン2とをロー付あるい
は拡管により接合した流動層熱交換器を示す。FIG. 1 shows a fluidized bed heat exchanger in which a plurality of flat tubes 3 through which a refrigerant (Freon 22 or 12) flows and a plurality of fins 2 are joined by brazing or tube expansion.
第2図には複数本の扁平チー−プ3のみからなる流動層
熱交換器を示す。1は流動粒子、2はプレートフィン、
3は扁平チューブ、4は分散板、Sはプレートフィン2
の間隔又は扁平チューブ3間の最小寸法である。なお2
図示していないが、扁平チー−プ3の代りに丸形のチ−
ブを用いた熱交換器やコルゲートフィンを用いた熱交換
器にも同様に適用することができる。FIG. 2 shows a fluidized bed heat exchanger consisting only of a plurality of flat cheeps 3. 1 is a fluid particle, 2 is a plate fin,
3 is a flat tube, 4 is a distribution plate, S is a plate fin 2
or the minimum dimension between the flat tubes 3. Note 2
Although not shown, a round chip is used instead of the flat chip 3.
The present invention can be similarly applied to a heat exchanger using a fin or a heat exchanger using a corrugated fin.
また9図示のようにチューブ配列は空気流れaに対して
千鳥配列にした方が好結果が得られる。Further, better results can be obtained by arranging the tubes in a staggered arrangement with respect to the air flow a, as shown in Figure 9.
bは冷媒の流れを示している。b indicates the flow of refrigerant.
第3図は粒子径に対するフィン間隔の比率(S/粒子径
)と熱交換器の熱伝達率の関係を示す図で、S/粒子径
〈3.Oで急激に熱伝達率が低下しているが、これは粒
子に作用する空気流れの抗力が粒子の重力とバランスす
るためにピッチ間に存在し得る粒子数が急減するためで
あり、伝熱面と衝突する粒子の数は減少して着霜も早ま
る。しかし、S/粒径〉3.0を選べばこのようなこと
はなく着霜も柩端に遅延できる。FIG. 3 is a diagram showing the relationship between the ratio of the fin spacing to the particle diameter (S/particle diameter) and the heat transfer coefficient of the heat exchanger, and shows the relationship between the ratio of the fin spacing to the particle diameter (S/particle diameter) and the heat transfer coefficient of the heat exchanger. The heat transfer coefficient decreases rapidly in O, but this is because the drag force of the air flow acting on the particles is balanced with the gravity of the particles, so the number of particles that can exist between the pitches decreases rapidly, and the heat transfer rate decreases rapidly. The number of particles colliding with the surface is reduced and frost formation is accelerated. However, if S/particle size>3.0 is selected, this problem will not occur and frost formation can be delayed to the coffin ends.
第4図は所定ピッチの流動層熱交換器の熱伝達率/圧力
損失: kw/△Paと粒子径:dpの関係を粒子密度
:ρpをパラメータに示したもので粒子が流動化する適
値での熱伝達率と圧力損失している実験結果である。実
験に使用した流動粒子はポリスチレン発泡粒子又は相当
のものでρp = 500〜l O00(Kym/i)
である。なお、ヒートポンプ用熱交換器としてはkW/
ΔPa=40 (k、Il /−−℃/咽AQ)程度以
上が要求されるので、 、p=500ではdp= 1.
5以下2ρp=1000ではdp==Q、3以下の粒子
径が適当となる。Figure 4 shows the relationship between heat transfer coefficient/pressure drop: kW/△Pa and particle diameter: dp in a fluidized bed heat exchanger with a predetermined pitch, using particle density: ρp as a parameter, which is the optimum value for fluidizing the particles. The heat transfer coefficient and pressure loss are experimental results. The fluidized particles used in the experiment were polystyrene foam particles or equivalent particles, and ρp = 500 ~ l O00 (Kym/i)
It is. In addition, as a heat exchanger for a heat pump, kW/
Since ΔPa=40 (k, Il/−−℃/pharyngeal AQ) or more is required, when p=500, dp=1.
When 2ρp=1000 is 5 or less, dp==Q, and a particle size of 3 or less is appropriate.
以上のように本発明によるとフィン間隔又はチューブ間
隔を流動粒子径の3倍以上とすることにより熱交換器の
圧損を小さくシ、かつ、熱伝達率を向上させることが出
来る。As described above, according to the present invention, by setting the fin spacing or tube spacing to three times or more the diameter of the fluidized particles, it is possible to reduce the pressure drop in the heat exchanger and improve the heat transfer coefficient.
第1図はプレートフィン流動層熱交換器の構成図、第2
図は扁平チー−プ流動層熱交換器の構成図、第3図は流
動層熱交換器の熱伝達特性図、第4図は流動粒子径と熱
伝達率/圧力損失の関係を示す図である。
1・・・流動粒子、2・・・プレートフィン、3・・・
扁平チューブ、4・・・分散板、S・・・フィン間隔又
はチューブ間隔Figure 1 is a block diagram of a plate-fin fluidized bed heat exchanger, Figure 2
The figure shows the configuration of a flat cheap fluidized bed heat exchanger, Figure 3 shows the heat transfer characteristics of the fluidized bed heat exchanger, and Figure 4 shows the relationship between fluid particle diameter and heat transfer coefficient/pressure loss. be. 1...Fluid particles, 2...Plate fins, 3...
Flat tube, 4... Dispersion plate, S... Fin spacing or tube spacing
Claims (1)
熱交換器において、前記流動粒子の径に対して、前記熱
交換器のフィン間隔もしくはチューブ間隔の比率を3倍
以上としたことを特徴とする流動層熱交換器。A fluidized bed heat exchanger comprising fluidized particles held around the heat exchanger, characterized in that the ratio of the fin spacing or tube spacing of the heat exchanger to the diameter of the fluidized particles is three times or more. Fluidized bed heat exchanger.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19023486A JPS6346391A (en) | 1986-08-13 | 1986-08-13 | Fluidized bed heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19023486A JPS6346391A (en) | 1986-08-13 | 1986-08-13 | Fluidized bed heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS6346391A true JPS6346391A (en) | 1988-02-27 |
Family
ID=16254724
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19023486A Pending JPS6346391A (en) | 1986-08-13 | 1986-08-13 | Fluidized bed heat exchanger |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6346391A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102224388A (en) * | 2008-11-24 | 2011-10-19 | Rwe动力股份公司 | Indirectly heated fluidized bed dryer |
-
1986
- 1986-08-13 JP JP19023486A patent/JPS6346391A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102224388A (en) * | 2008-11-24 | 2011-10-19 | Rwe动力股份公司 | Indirectly heated fluidized bed dryer |
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