JPH0366593B2 - - Google Patents
Info
- Publication number
- JPH0366593B2 JPH0366593B2 JP57194119A JP19411982A JPH0366593B2 JP H0366593 B2 JPH0366593 B2 JP H0366593B2 JP 57194119 A JP57194119 A JP 57194119A JP 19411982 A JP19411982 A JP 19411982A JP H0366593 B2 JPH0366593 B2 JP H0366593B2
- Authority
- JP
- Japan
- Prior art keywords
- heat exchange
- heat exchanger
- air flow
- cylindrical
- exchange device
- 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.)
- Expired - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
-
- 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
- F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
- F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
-
- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
- F28D9/0018—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form without any annular circulation of the heat exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1032—Desiccant wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/104—Heat exchanger wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1048—Geometric details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1052—Rotary wheel comprising a non-axial air flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1068—Rotary wheel comprising one rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1084—Rotary wheel comprising two flow rotor segments
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明は回転式空調換気扇等に用いる熱交換装
置の改良に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to improvements in heat exchange devices used in rotary air conditioning ventilation fans and the like.
従来例の構成とその問題点
従来の全熱交換方式には、ロータへの蓄熱およ
び蓄湿を利用した蓄熱回転式と、仕切板を介して
全熱交換さす静止透過式の２方式がある。蓄熱回
転式はロータの蓄熱容量が少ないため、通常約15
回転／分程度のロータの回転数が必要となる。こ
のため回転にともなう摺動音が発生しやすい。ま
た、ロータへの顕熱蓄熱や水分の吸着熱や脱着熱
の影響により、エレメントへの水分の有効吸着量
が減少するという欠点がある。Conventional Structure and Problems There are two types of conventional total heat exchange systems: a heat storage rotation type that utilizes heat and moisture stored in a rotor, and a static transmission type that performs total heat exchange through a partition plate. The heat storage rotary type has a small heat storage capacity of the rotor, so it is usually about 15
A rotational speed of the rotor on the order of revolutions per minute is required. Therefore, sliding noise is likely to occur due to rotation. Furthermore, there is a drawback that the effective amount of moisture adsorption to the element is reduced due to the effects of sensible heat storage in the rotor and heat of adsorption and desorption of moisture.
一方、静止−透過式では顕熱交換および潜熱交
換は仕切板中の熱伝導機構および透湿現象のみに
よつて行なわれるので、一般的に全熱交換効率は
低い。 On the other hand, in the static-permeation type, sensible heat exchange and latent heat exchange are performed only by the heat conduction mechanism in the partition plate and the moisture permeation phenomenon, so the total heat exchange efficiency is generally low.
発明の目的
従来よりも高効率で、しかも回転数が従来の蓄
熱回転式に比べ少なくてすむため、摺動音が低い
という特徴をもつた蓄熱透過回転式熱交換装置な
るものを提供するものである。OBJECT OF THE INVENTION It is an object of the present invention to provide a heat storage transmission rotary heat exchange device that is more efficient than conventional heat exchangers and has a lower rotational speed than conventional heat storage rotary heat exchangers, and thus has low sliding noise. be.
発明の構成
透湿性をもつた隔壁を間隔を置いて円周方向に
複数層重ね合わせ、一次気流と二次気流とをこれ
ら各層間を交互に通るように形成した円筒状ロー
タを構成要素とし、これを回転させることによ
り、これら一次気流と二次気流を周期的に入れ換
えて前記隔壁間の各層を通すことを繰返す全熱交
換方式を採用することにより、エレメントへの蓄
積顕熱や水分の吸脱着にともなつてエレメントの
表面で発生する熱を、ロータの回転のみで他方へ
移動させるのでなく、そのある程度の部分を隔壁
中の熱伝導により他方へ移動させることができる
ので、従来の回転式全熱交換装置に比べ、回転速
度を落すことが出来、摺動落を減ずることが出来
る。また、エレメントへの水分の有効吸着量が増
大するので熱交換効率が高くなる。また、この構
成では従来の静止透過式全熱交換法に比べ、熱交
換機構に蓄熱、蓄湿機構が加わるので、より効率
を高くすることが可能である。Structure of the Invention The component is a cylindrical rotor in which a plurality of layers of moisture-permeable partition walls are stacked circumferentially at intervals, and primary airflow and secondary airflow are formed to pass alternately between these layers, By rotating this, a total heat exchange method is adopted in which the primary airflow and secondary airflow are periodically exchanged and passed through each layer between the partition walls, thereby absorbing sensible heat accumulated in the element and moisture. The heat generated on the surface of the element during attachment and detachment is not transferred to the other side only by the rotation of the rotor, but a certain amount of it can be transferred to the other side by heat conduction in the partition wall, which is different from the conventional rotary type. Compared to a total heat exchange device, the rotation speed can be lowered and sliding drop can be reduced. Furthermore, since the effective amount of moisture adsorbed to the element increases, the heat exchange efficiency increases. In addition, in this configuration, compared to the conventional static permeation type total heat exchange method, a heat storage and moisture storage mechanism is added to the heat exchange mechanism, so it is possible to further increase efficiency.
実施例の説明
以下本発明の実施例を図にもとづいて説明す
る。第１図は本発明の熱交換方式を実現するため
の実施例の円筒形ロータの部分的な概略外観と、
関連する気体の流出入経路を示した図である。図
中１は円筒形のロータ、２はその内円筒部分で後
で説明するように気流通路入換部がついている。
３は両気流を分離するセパレータである。この構
造のロータ１の場合、セパレータ３の一方側から
ロータ１に入つた気流はセパレータ３の同一側か
らロータ１を出る。DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on the drawings. FIG. 1 shows a partial schematic appearance of a cylindrical rotor according to an embodiment for realizing the heat exchange method of the present invention,
FIG. 3 is a diagram showing related gas inflow and outflow paths. In the figure, reference numeral 1 indicates a cylindrical rotor, and reference numeral 2 indicates an inner cylindrical portion of the rotor, which is provided with an air flow passage switching section as will be explained later.
3 is a separator that separates both air flows. In the case of the rotor 1 having this structure, airflow entering the rotor 1 from one side of the separator 3 exits the rotor 1 from the same side of the separator 3.
このロータ１は第２図に示すように、筒軸方向
に貫通する通路を有する第１のエレメント４と、
これに直角な半径方向に気流が出入する内円筒部
の２つの開口部間を連通する通路を有する第２の
エレメント５を隔壁６を介して、円周方向に互い
に積層させた構成をしている。 As shown in FIG. 2, this rotor 1 includes a first element 4 having a passage passing through in the axial direction of the cylinder;
A second element 5 having a passage communicating between two openings of the inner cylindrical part through which air flows in and out in a radial direction perpendicular to this is laminated on each other in the circumferential direction via a partition wall 6. There is.
第３図はこのようなロータ１を構成するエレメ
ントの実施例で、基本素子７，８の一対を交互に
積重ねてロータ１を構成している。この場合、基
本素子７および８はクラフト紙の表面に吸湿剤と
してLiClを塗布したものである。この基本素子７
の気流流路は筒軸方向に貫通しており、基本素子
８の気流通路は内円筒側入口の一方より入り、内
円筒側の他方の出口より出る構造になつている。 FIG. 3 shows an example of elements constituting such a rotor 1, in which a pair of basic elements 7 and 8 are stacked alternately to constitute the rotor 1. In this case, the basic elements 7 and 8 are made of kraft paper coated with LiCl as a moisture absorbent. This basic element 7
The air flow path penetrates in the axial direction of the cylinder, and the air flow path of the basic element 8 enters from one of the inlets on the inner cylinder side and exits from the other outlet on the inner cylinder side.
第４図はロータ１を構成している基本素子の他
の実施例である。この場合、基本素子９の隔壁６
間の間隔は半径方向で異なるが、基本素子１０の
通路間隔は一定であるので、基本素子１０内の通
路の抵抗は基本素子８の場合より小さいという特
徴がある。 FIG. 4 shows another embodiment of the basic elements constituting the rotor 1. In FIG. In this case, the partition wall 6 of the basic element 9
Although the spacing between them varies in the radial direction, the passage spacing of the basic element 10 is constant, so that the resistance of the passages in the basic element 10 is characteristically smaller than in the case of the basic element 8.
第５図はこのような円筒形ロータ１を使つた場
合の本実施例の熱交換器の断面模式図で、熱交換
器内の気流の流れを模式的に示したものである。 FIG. 5 is a schematic cross-sectional view of the heat exchanger of this embodiment using such a cylindrical rotor 1, and schematically shows the flow of air within the heat exchanger.
図中１１，１２はロータ１に入る両気流の通路
を分けるセパレータである。これは１枚の仕切板
１５の中央部を軸として両端を180°ひねつたもの
を用いているが他の構成であつてもよい。１３，
１４は内円筒側気流通路の出入口に設けられた気
流通路入換部で、基本的には第６図のような構造
をもつたもので、そのx1，x2間に相当するもので
ある。図中x1，x2間で両気流の通路を分ける仕切
板１５が180°回転しているため、この部分で仕切
板１５の両側の気流の通路が互いに入換わるよう
になつている。このような構造において、熱交換
時に筒軸を中心にして回転するものは、ロータ１
とロータ１と一体構造になつている仕切部１６の
みで、セパレータ１１，１２や気流通路入換部１
３，１４は固定されているので動かない。 In the figure, numerals 11 and 12 are separators that separate the paths of both air flows entering the rotor 1. This uses a single partition plate 15 whose both ends are twisted 180 degrees around the central part of the partition plate 15, but other configurations may be used. 13,
Reference numeral 14 denotes an air flow passage switching section provided at the entrance and exit of the inner cylinder side air flow passage, which basically has the structure as shown in Fig. 6, and corresponds to the area between x 1 and x 2 . . In the figure, the partition plate 15 that separates the air flow paths between x 1 and x 2 is rotated by 180 degrees, so that the air flow paths on both sides of the partition plate 15 switch places at this portion. In such a structure, the rotor 1 rotates around the cylinder axis during heat exchange.
Only the partition part 16, which is integrated with the rotor 1, separates the separators 11, 12 and the air flow passage switching part 1.
3 and 14 are fixed and do not move.
両気流間の熱交換は、第２図における第１のエ
レメント４と第２のエレメント５の間の隔壁６を
通して全熱交換が行なわれるだけでなく、ロータ
１の回転により、例えば第５図に示すように、図
中ロータ１の上面部では第１のエレメント４には
気流Ｂ、第２のエレメント５には気流Ａが流れて
いるが、下面部では第１のエレメント４には気流
Ａ、第２のエレメント５には気流Ｂというよう
に、互いに入換わることを繰返すことにより、エ
レメントに蓄熱、蓄湿された顕熱と水分が他方の
気流中に移行することにより全熱交換が行なわれ
る。 The heat exchange between the two air streams not only takes place through the partition wall 6 between the first element 4 and the second element 5 in FIG. 2, but also by the rotation of the rotor 1, for example, As shown in the figure, on the upper surface of the rotor 1, airflow B flows through the first element 4 and airflow A flows through the second element 5, but on the lower surface, airflow A flows through the first element 4, and airflow A flows through the first element 4. The second element 5 has airflow B, and by repeatedly exchanging each other, the sensible heat and moisture stored in the element transfer to the other airflow, thereby performing total heat exchange. .
従来の蓄熱回転式の全熱交換器と比べて、この
方式の利点はエレメントへの水分の吸着および脱
着にともなう吸着熱も脱着熱、あるいは高温気流
中の顕熱をロータの回転だけによらず、第１のエ
レメント４と第２のエレメント５間の隔壁６を通
して大部分移行させることができるため、エレメ
ントの水分の有効吸着量を多くとることができ効
率を高くできる。また隔壁６を通しての顕熱移行
によりロータ１が静止していてもエレメントの蓄
熱容量が飽和に達しないため、従来の回転式に比
べロータの回転速度を遅くすることができる。従
来の蓄熱回転式の最適回転数は15回転／分前後で
あるが、実験結果によると新方式では１回転／分
前後が最適であることがわかつた。このことは新
方式が従来の回転式に比べ回転にともなう摺動音
が小さくなる原因である。また、この方式は従来
の静止透過式に比べても高効率のデータが得られ
ている。これは全熱交換機構が静止透過式では伝
導と透過のみであるが、新方式ではこれらに蓄湿
の両機構が加わつてくるためと考えられる。 Compared to conventional heat storage rotary type total heat exchangers, the advantage of this method is that the adsorption heat associated with adsorption and desorption of moisture on the element is also converted into desorption heat, or the sensible heat in the high-temperature air flow is not only generated by the rotation of the rotor. Since most of the water can be transferred through the partition wall 6 between the first element 4 and the second element 5, the effective amount of moisture adsorbed by the element can be increased and efficiency can be increased. Furthermore, the heat storage capacity of the element does not reach saturation even when the rotor 1 is stationary due to sensible heat transfer through the partition wall 6, so the rotational speed of the rotor can be lowered compared to the conventional rotary type. The optimal rotation speed for conventional heat storage rotary systems is around 15 revolutions per minute, but experimental results show that the optimal rotation speed for the new system is around 1 revolution per minute. This is the reason why the new system produces less sliding noise due to rotation than the conventional rotary system. Furthermore, this method can obtain data with higher efficiency than the conventional static transmission method. This is thought to be because the total heat exchange mechanism is only conduction and permeation in the static permeation type, but in the new type, both moisture storage mechanisms are added to these.
第７図は本発明の熱交換方式を実現するための
他の実施例の円筒形ロータの概略外観と関連する
気体の流出入経路を示した図である。この実施例
の場合、ロータ１７は第８図に示すように筒軸方
向の一端側２３と他端側に近い内円筒側に開口部
２４をもつた第１のエレメント１８と、これとは
逆に筒軸方向の他端側２５とそれと反対側の内円
筒側に開口部２６をもつた第２のエレメント１９
を隔壁２０を介して円周方向に互いに積層させた
構成をしている。第９図はこの場合のロータ１７
を構成するエレメントの実施例で、基本素子２
１，２２一対を交互に積重ねてロータ１７を構成
している。この場合の基本素子２１，２２も前記
実施例と同様、クラフト紙に吸湿剤としてLiClを
塗布したものである。このような基本素子２１，
２２を積層したロータでは、内部の気流の流れは
内部で90°方向転換するようになつており、この
両通路とも風路抵抗が同一になるという特徴をも
つている。両気流通路間の風圧が等しくなるの
で、伝熱・透過による熱交換率が向上する。 FIG. 7 is a diagram showing a schematic appearance of a cylindrical rotor according to another embodiment for realizing the heat exchange method of the present invention and related gas inflow and outflow paths. In this embodiment, as shown in FIG. 8, the rotor 17 includes a first element 18 having an opening 23 on one end side 23 in the cylinder axis direction and an opening 24 on the inner cylinder side near the other end; a second element 19 having an opening 26 at the other end 25 in the cylinder axis direction and at the inner cylinder side opposite thereto;
are stacked on each other in the circumferential direction with partition walls 20 in between. Figure 9 shows the rotor 17 in this case.
This is an example of the elements constituting the basic element 2.
The rotor 17 is constructed by stacking pairs of rotors 1 and 22 alternately. The basic elements 21 and 22 in this case are also made of kraft paper coated with LiCl as a moisture absorbent, as in the previous embodiment. Such a basic element 21,
In the rotor in which 22 are laminated, the direction of the internal airflow is changed by 90 degrees internally, and both passages have the same air path resistance. Since the wind pressure between both air flow passages becomes equal, the heat exchange rate due to heat transfer and permeation is improved.
第１０図はこの例のロータ１７を使つた場合の
熱交換器の断面模式図で熱交換器内の気流の流れ
を模式化したものである。この例のような場合で
も、熱交換機構は前記ロータ１の気流通路の場合
の熱交換機構と同様である。 FIG. 10 is a schematic cross-sectional view of a heat exchanger using the rotor 17 of this example, which schematically shows the flow of air within the heat exchanger. Even in a case like this example, the heat exchange mechanism is the same as the heat exchange mechanism in the case of the airflow passage of the rotor 1.
第１１図は第５図の熱交換器を使い、35℃、60
％、25℃、50％風量２m3／minの両気流間の熱交
換効率をロータの回転数を変化させてとつたデー
タである。図中Ａは全熱交換効率、Ｂは顕熱交換
効率、Ｃは潜熱交換効率である。このデータから
分かるように、ロータの回転数を変化させること
により、顕熱交換効率と潜熱交換効率中にしめる
割合を変化させることができるので、より高度な
空調に対応できる可能性を有していることを示し
ている。なお、第１２図は比較のため従来の蓄熱
回転式の場合の同様の実験データを示したもの
で、エレメントとしてはコルゲート加工したクラ
フト紙をロータ状にまいた構造である。この場合
は、データを示すようにロータの回転数が変化し
ても、顕熱交換効率と潜熱交換効率の全熱交換効
率中にしめる割合は、第１１図の蓄熱透過式程に
は変化しないことがわかる。 Figure 11 shows the heat exchanger shown in Figure 5 used at 35℃ and 60℃.
%, 25°C, 50% air flow rate of 2 m 3 /min, heat exchange efficiency between both air flows was obtained by changing the rotational speed of the rotor. In the figure, A is the total heat exchange efficiency, B is the sensible heat exchange efficiency, and C is the latent heat exchange efficiency. As can be seen from this data, by changing the rotation speed of the rotor, it is possible to change the proportion of sensible heat exchange efficiency and latent heat exchange efficiency, which has the potential to support more advanced air conditioning. It is shown that. For comparison, FIG. 12 shows similar experimental data in the case of a conventional heat storage rotary type, and the elements have a structure in which corrugated kraft paper is spread in the shape of a rotor. In this case, even if the rotation speed of the rotor changes as shown in the data, the ratio of sensible heat exchange efficiency and latent heat exchange efficiency to the total heat exchange efficiency will not change as much as the heat storage transmission equation shown in Figure 11. I understand.
発明の効果
以上のごとく本発明の熱交換装置では全熱交換
効率を従来法より相当高くできる。また、回転数
制御により顕熱交換効率と潜熱交換効率の比率を
変化さすことができる。このような特徴をもつた
本発明の熱交換装置を空調機に使用することによ
り大きな省エネルギー効果が期待できる。Effects of the Invention As described above, in the heat exchange device of the present invention, the total heat exchange efficiency can be considerably higher than that of the conventional method. Furthermore, the ratio between sensible heat exchange efficiency and latent heat exchange efficiency can be changed by controlling the rotation speed. By using the heat exchange device of the present invention having such characteristics in an air conditioner, a large energy saving effect can be expected.
また本発明では中空部があるので、外周を用い
ることなく、円筒の端面と中空部間で熱交換気流
を流すことができ、取付面積が小さくてよい。な
お、円筒中央部は熱交換の有効面積が小さいの
で、この部分を除いても同じ外形の円柱状のもの
に比べて、熱交換機能が損なわれることはない。 Further, since the present invention has a hollow portion, a heat exchange airflow can flow between the end face of the cylinder and the hollow portion without using the outer periphery, and the installation area may be small. In addition, since the effective area for heat exchange is small in the central part of the cylinder, even if this part is removed, the heat exchange function will not be impaired compared to a cylinder having the same external shape.
第１図は本発明の熱交換装置を実現するための
一実施例の円筒形ロータの部分的概略説明図、第
２図は第１図の部分的な詳細図、第３図は前記ロ
ータを構成する基本素子の斜視図、第４図は基本
素子の他の実施例の斜視図、第５図は本発明の一
実施例の熱交換装置の断面模式図、第６図は気流
通路入換部の斜視図、第７図は本発明の他の実施
例の円筒形ロータの部分的概略説明図、第８図は
第７図のロータの部分的詳細図、第９図は前記ロ
ータを構成する基本素子の斜視図、第１０図は本
発明の異なる実施例の熱交換装置の断面模式図、
第１１図は第５図の熱交換装置を使い両気流間の
熱交換効率を示す図、第１２図は第１１図に示す
データと比較するための従来の蓄熱回転式の熱交
換効率を示す図である。
１……ロータ、２……内円筒部分、３……セパ
レータ、４，５……エレメント、６……隔壁、７
〜１０……基本素子、１１，１２……セパレー
タ、１３，１４……気流通路入換部。
FIG. 1 is a partial schematic explanatory diagram of a cylindrical rotor according to an embodiment for realizing the heat exchange device of the present invention, FIG. 2 is a partial detailed diagram of FIG. 1, and FIG. FIG. 4 is a perspective view of another embodiment of the basic element, FIG. 5 is a cross-sectional schematic diagram of a heat exchange device according to an embodiment of the present invention, and FIG. 6 is an air flow passage exchange FIG. 7 is a partial schematic illustration of a cylindrical rotor according to another embodiment of the present invention, FIG. 8 is a partial detailed view of the rotor of FIG. 7, and FIG. 9 is a configuration of the rotor. FIG. 10 is a schematic cross-sectional view of a heat exchange device according to a different embodiment of the present invention.
Figure 11 shows the heat exchange efficiency between both air streams using the heat exchange device shown in Figure 5, and Figure 12 shows the heat exchange efficiency of the conventional heat storage rotary type for comparison with the data shown in Figure 11. It is a diagram. DESCRIPTION OF SYMBOLS 1... Rotor, 2... Inner cylindrical part, 3... Separator, 4, 5... Element, 6... Partition wall, 7
~10... Basic element, 11, 12... Separator, 13, 14... Air flow passage switching section.
Claims (1)
メントを交互に積層して中空の円筒を形成し、前
記第１、第２のエレメント間に存在する隔壁は伝
熱性を有しかつ透湿性であり、前記一方のエレメ
ントに一次気流通路、他方のエレメントを二次気
流通路とし、前記円筒状熱交換器を回転させるこ
とによつて前記一次気流と二次気流の通路を周期
的に入れ換え、前記円筒状熱交換器の中空部の少
なくとも一端に気流通路入換部を設けた熱交換装
置。 ２ 第１のエレメントは円筒軸方向に気流の通過
孔を有し、前記第２のエレメントは前記中空部に
対して複数の開口を有し、一方の開口部から他方
の開口部へ気流を通過可能にした特許請求の範囲
第１項記載の熱交換装置。 ３ 第１のエレメントは円筒状熱交換器の一端か
ら軸方向通路を介して中空部へ通じ、前記第２の
エレメントは前記円筒状熱交換器の他端から軸方
向通路を介して前記中空部へ抜ける通路を有する
特許請求の範囲第１項記載の熱交換装置。 ４ 円筒状熱交換器の直径方向にセパレータを介
在させ、前記円筒状熱交換器および中空部を２分
する特許請求の範囲第２項または第３項記載の熱
交換装置。 ５ 気流通路入換部は、伸縮自在の平板の中央線
を円筒状熱交換器の軸と一致させ両端を180°ひね
つた形状である特許請求の範囲第１項記載の熱交
換装置。[Claims] 1. A hollow cylinder is formed by alternately stacking first and second elements having heat storage and moisture storage properties, and a partition wall existing between the first and second elements has heat conductivity. and is moisture permeable, one element has a primary air flow passage and the other element has a secondary air flow passage, and by rotating the cylindrical heat exchanger, the passage for the primary air flow and the secondary air flow is formed. A heat exchange device in which the cylindrical heat exchanger is periodically replaced, and an airflow passage switching part is provided at at least one end of the hollow part of the cylindrical heat exchanger. 2 The first element has an airflow passage hole in the cylindrical axial direction, and the second element has a plurality of openings with respect to the hollow part, and the airflow passes from one opening to the other opening. A heat exchange device according to claim 1, which enables the heat exchange device according to claim 1. 3 The first element communicates from one end of the cylindrical heat exchanger to the hollow part via an axial passage, and the second element communicates from the other end of the cylindrical heat exchanger to the hollow part via an axial passage. 2. The heat exchange device according to claim 1, further comprising a passage leading to the heat exchanger. 4. The heat exchange device according to claim 2 or 3, wherein a separator is interposed in the diametrical direction of the cylindrical heat exchanger to divide the cylindrical heat exchanger and the hollow portion into two. 5. The heat exchange device according to claim 1, wherein the air flow passage switching section has a shape in which the center line of a stretchable flat plate is aligned with the axis of the cylindrical heat exchanger, and both ends are twisted by 180 degrees.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57194119A JPS5984091A (en) | 1982-11-04 | 1982-11-04 | Heat exchanger |
| EP83903413A EP0127683B1 (en) | 1982-11-04 | 1983-11-02 | Heat exchanger |
| DE8383903413T DE3371247D1 (en) | 1982-11-04 | 1983-11-02 | Heat exchanger |
| PCT/JP1983/000392 WO1984001817A1 (en) | 1982-11-04 | 1983-11-02 | Heat exchanger |
| US06/629,844 US4574872A (en) | 1982-11-04 | 1983-11-02 | Heat exchanger apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57194119A JPS5984091A (en) | 1982-11-04 | 1982-11-04 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5984091A JPS5984091A (en) | 1984-05-15 |
| JPH0366593B2 true JPH0366593B2 (en) | 1991-10-17 |
Family
ID=16319227
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57194119A Granted JPS5984091A (en) | 1982-11-04 | 1982-11-04 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5984091A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5662545B1 (en) * | 2013-11-13 | 2015-01-28 | 多田 禮子 | High performance total heat exchanger |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS527185B2 (en) * | 1972-09-14 | 1977-02-28 |
-
1982
- 1982-11-04 JP JP57194119A patent/JPS5984091A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5984091A (en) | 1984-05-15 |
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