201038902 四、 指定代表圖·· (一） 本案指定代表圖為：第（1)圖。 (二） 本代表圖之元件符號簡單説明： 11〜第一波形板材， 12〜第二波形板材； 13〜平板狀板材； 14〜間隔保持板材； 20〜單位結構元件； 31〜波形流道（第一流道）； 32〜直行流道（第二流道）； 101〜全熱交換元件。 五、 本案若有化學式時，請揭示最能顯示發明特徵的化學式： 無0 六、發明說明： 【發明所屬之技術領域】 件’其在積層板材之間 ’分別使空氣等之第一 間進行全熱交換。 本發明疋關於一種全熱交換元 父叉形成的第一流道及第二流道上 流體及第二流體流過，在兩流體之 【先前技術】 專利文獻1所揭示， 兩個流體之隔間元件 在此種全熱交換元件中，過去如 一般設有間隔保持元件，以保持隔開 201038902 與此隔間元件之間的間隔。隔間元件具有透溼性，以此作 為媒介’在兩個流體之間同時進行顯熱（溫度）和潛熱（溼度） 的熱交換。在此種全熱交換元件中，以流體之全熱交換為 目的’所以’元件被要求提供很大的熱交換量。全熱交換 疋件相較於一般熱交換器（僅進行顯熱的交換），只有潛熱 之交換熱量的熱交換量增加，效果增高。 王熱交換元件有直父流型和逆流型2種。直交流型於 0 理論上之單位體積之熱交換量比逆流型少，但不需要逆流 型在結構中所必須具備的集箱（用來分割進行全熱交換之 兩流體並將其導入全熱交換元件流道的部分），所以，具備 組合至裝置中之實際體積小而且元件本身之加工也很容易 等優點。 為了增加此種直交流型全熱交換元件之熱交換量，過 去如專利文獻2所揭示，有藉由形成波紋鰭板而具備鰭板 功能以增加熱交換量的例子。不過，此例子為了提高性能， 〇 流道内之鶴板之面積如專利文獻2所揭示，藉由變化韓板 2折疊來增加，但這樣會因為鰭板本身之體積而使流道變 窄，於是導致流體通過時之壓力損失增大。又，籍板具有 顯熱父換之效果’但沒有潛熱交換之效果，簡直可以說由 於鰭板和隔間元件的接觸而使潛熱之交換面積減少。於 是’就全熱交換元件而言，特別是藉由鰭板提高熱交換量 之效果有其限制。 對於此4了增加熱父換量而進行之形狀設計如專 利文獻3至5所揭示，提出一種發明，其中，藉由設置突 201038902 起等來取代鰭板來改變流動形況，以改善隔間元件表面之 熱傳導率而增加熱交換量。 再者如專利文獻6至8所揭示，提出一種發明，其 中，藉由流道形狀之變更來增加每單位體積之傳熱面積， 以增加熱交換量。 專利文獻1 :特開平4-24492號公報 專利文獻2 :實開平1-178471號公報 專利文獻3 :實開平3-21 670號公報 專利文獻4 :特許第3805665號公報 專利文獻5 :特開2008-232592號公報 專利文獻6 :實昭開58-165476號公報 專利文獻7 :特許第3546 574號公報 專利文獻8 :實開平5-52567號公報 【發明内容】 【發明所欲解決的課題】 的叩，有關 • ’ q ▼千之改善，狩别 在換氣用全熱交換元件中，多為管路相對於流體之流量 小直徑且管路内之雷諾數比其他熱交換器小（大 100〜1000)的層流狀態，又’在此區域内，使流體之流動 身變化來引起熱傳導率改善的效果报小。所以，鰭板、 起等特別是在低雷諾數之區域中，盘並g 興其說是能改善熱傳 率’不如說導致壓力損失增加的問顳#士 ,^ 门喊更大。壓力損失之: 加在增大將流體傳送至全熱交換元件之動201038902 IV. Designation of Representative Representatives (1) The representative representative of the case is: (1). (b) A simple description of the symbol of the representative figure: 11~ first corrugated sheet, 12~ second corrugated sheet; 13~ flat sheet; 14~ interval holding sheet; 20~ unit structural element; 31~ waveform flow path ( First flow path); 32~ straight flow path (second flow path); 101~ full heat exchange element. 5. If there is a chemical formula in this case, please disclose the chemical formula that best shows the characteristics of the invention: None. 6. Description of the invention: [Technical field of invention] The piece 'between laminated sheets' allows the first room of air, etc. Full heat exchange. The present invention relates to a fluid flow and a second fluid flow in a first flow path and a second flow path formed by a full heat exchange element parent fork, in the two fluids. [Prior Art] Patent Document 1 discloses a two fluid compartment element. In such a total heat exchange element, spacer retaining elements have been provided in the past to maintain the spacing between 201038902 and the compartment elements. The compartment element is moisture permeable as a medium' heat exchange between sensible heat (temperature) and latent heat (humidity) simultaneously between the two fluids. In such a total heat exchange element, the element is required to provide a large amount of heat exchange for the purpose of total heat exchange of the fluid. The total heat exchange element is compared with the general heat exchanger (only sensible heat exchange), and only the heat exchange amount of the latent heat exchange heat is increased, and the effect is increased. The king heat exchange element has two types: a straight parent flow type and a counter flow type. The direct AC type has a theoretical heat exchange capacity per unit volume of less than the counterflow type, but does not require a counterflow type of headers that must be provided in the structure (to separate the two fluids for total heat exchange and introduce them into full heat) The part of the flow path of the component is exchanged, so that the actual volume combined into the device is small and the processing of the component itself is easy. In order to increase the amount of heat exchange of such a direct current type total heat exchange element, as disclosed in Patent Document 2, there has been an example in which a fin function is provided by forming a corrugated fin to increase the amount of heat exchange. However, in order to improve the performance of this example, the area of the crane plate in the choke channel is as disclosed in Patent Document 2, and is increased by changing the folding of the Korean plate 2, but the flow path is narrowed due to the volume of the fin itself, so The pressure loss caused by the passage of fluid increases. Moreover, the board has the effect of changing the heat father', but there is no effect of latent heat exchange, and it can be said that the exchange area of latent heat is reduced by the contact of the fins and the compartment elements. Thus, there is a limit to the effect of increasing the amount of heat exchange by the fins in terms of the total heat exchange element. For the shape design in which the heat master shift is increased, as disclosed in Patent Documents 3 to 5, an invention is proposed in which the flow state is changed by setting the protrusion 201038902 and the like to replace the fin to improve the compartment. The heat transfer rate of the surface of the component increases the amount of heat exchange. Further, as disclosed in Patent Documents 6 to 8, an invention is proposed in which a heat transfer area per unit volume is increased by a change in the shape of a flow path to increase the amount of heat exchange. [Patent Document 1] Japanese Laid-Open Patent Publication No. Hei No. Hei. No. Hei. No. Hei. No. Hei. No. Hei. Japanese Unexamined Patent Publication No. Hei. No. Hei. No. Hei. No. Hei. No. Hei. No. Hei. No. Hei.叩 有关 有关 ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换 换The laminar flow state of ~1000), and in this region, the effect of changing the flow body of the fluid to cause an improvement in thermal conductivity is small. Therefore, fins, lifting, etc., especially in the area of low Reynolds number, it is said that it can improve the heat transfer rate. It is better to say that the pressure loss is increased. Pressure loss: added to increase the flow of fluid to the full heat exchange element
切刀裝置之消耗J 201038902 量的理由下，宜不存在。 所以，宜有另一種方法爽辦心—抑 沄采增加母單位面積之傳熱面 積。不過，在這個增加傳熱面積的方法中，過去的發明也 有以下的問題。第8圖為概略刮面圖，表示死水域在流道 中發生的狀態。過去，在為了辦力會 社馬了增加傳熱面積而形成的流道 的凹凸形狀中’有時會在四邱F祕众 θ隹凹邛^域發生死水域（流體不沿著 ΟThe reason for the consumption of the cutter device is J 201038902, which should not exist. Therefore, there is another way to do it – to increase the heat transfer area of the parent unit area. However, in this method of increasing the heat transfer area, the past invention has the following problems. Figure 8 is a schematic plan view showing the state of the dead water in the flow path. In the past, in the concavo-convex shape of the flow path formed to increase the heat transfer area for the purpose of the meeting, the dead waters sometimes occur in the area of the four-storied F secret θ ( 流体 (the fluid does not follow the Ο
隔間元件表面流動而產生滞留跡雖然、在表面上好像增加 了傳熱面積，實際上有時反而傳熱面積減少。 方面近年來在組合全熱交換元件的機械設計 中為了配合各種技術課題，要求對於全熱交換元件之外 徑尺寸不Μ限制而能自由決定。相對於此，在專利文獻 4及5 +有-㈣材料⑽成同—形狀再將對其進行積層 的方法纟此方法中，當需要變更全熱交換元件之外形尺 寸時，需要再次製作壓鑄模，所以較難配合。 再者’在上述專利文獻6至8所揭示之企圖增加每單 位面積之傳熱面積的範例中，兩個流體通過之流道形狀完 全不同，所以，等流量流過時之壓力損失也跟著大大不同。 在此情況下，若針對換氣用熱交換器之全熱交換元件等之 類的溫度不同之同種流體的熱交換來設計出的元件，多為 兩個流體以近乎等流量流過的情況，於是，當進行組合元 件之機械設計時，兩流道之流體用動力裝置之規格也可能 必須分開設計，事情變得更加繁瑣。所以，宜盡量使進行 熱交換之兩個流體之流道有相同之壓力損失，再者，宜具 有相同形狀或近似形狀。 5 201038902 本發明為鑑於上述情況所創作之發明，目的在得到一 種全熱交換元件，其可在不使用會阻礙流動之鰭板、突起 等也不產生死水域的情況下，增加每單位面積之傳熱面 積，而且進行顯熱（溫度）和潛熱（溼度）之熱交換的兩個流 體流過且交又之兩個方向的流道為相同壓力損失之相同形 狀再者本發明之目的在得到一種可輕易進行外形尺寸 之變更的全熱交換元件。 【用以解決課題的手段】 為解決上述課題並達成目的，本發明之全熱交換元件 在積層板材之間交叉形成的第一流道及第二流道上分別 使第-流體及第二流體流過，在兩流體之間交換顯熱及潛 …其特徵在於.上述第一流道為矩形剖面之波形流道， 其形成方式為，形狀為朝向流體前進方向且在積層方向產 生振幅之波形並具有透溼性的第一波形板材與波形以與此 第一波形板材約略相同之週期產生振幅並具有透溼性的第 二波形板材相隔既定之間隔並重疊，再藉由密閉元件密閉 流體之前進方向兩側部位，上述第二流道為約略三角形剖 面之直行流道，其形成方式為，在上述第一波形板材與上 述第二波形板材中任一者之波形面上密合並重疊具有透溼 性之平板狀板材’再使其位於兩板材之間。 【發明效果】 根據本發明之全熱交換元件，所使用之板材之近乎所 有面之兩面使不同之流體通過，又，流道形狀也為難以產 生死水域之形狀，所以，約略全為有效之傳熱面積，於是 201038902 能增加每單位體積之 量。又，•教m 增加元件之熱交換 篁又田熱父換量和過去一樣好 件之體積，進而有助p 羡好時，反而有可能縮小元 二波來;、’、又，第一波形板材、第 不僅可交換顯教，介 有透漫性之材料’藉此’ 熱交換量的效果。#潛熱達到可增加全熱交換之The surface of the compartment element flows to generate a stagnation trace. Although the heat transfer area is increased on the surface, the heat transfer area may actually decrease. In recent years, in order to cope with various technical problems in the mechanical design of a combined total heat exchange element, it is required to be freely determined not to limit the size of the total heat exchange element. On the other hand, in Patent Documents 4 and 5 +, there is a method in which - (4) material (10) is laminated and then laminated, and in this method, when it is necessary to change the size of the entire heat exchange element, it is necessary to reproduce the die casting mold. So it is more difficult to cooperate. Further, in the example disclosed in the above-mentioned Patent Documents 6 to 8, in an attempt to increase the heat transfer area per unit area, the flow paths through which the two fluids pass are completely different, so that the pressure loss when the flow rate flows is greatly different. . In this case, if the element is designed for heat exchange of the same type of fluid having a different temperature such as a total heat exchange element of the heat exchanger for ventilation, etc., it is often the case that two fluids flow at nearly equal flow rates. Therefore, when the mechanical design of the combined components is performed, the specifications of the fluid power devices of the two flow paths may have to be separately designed, and things become more complicated. Therefore, it is preferable to make the flow paths of the two fluids subjected to heat exchange have the same pressure loss, and it is preferable to have the same shape or approximate shape. 5 201038902 The present invention has been made in view of the above circumstances, and an object of the invention is to provide a total heat exchange element which can increase the area per unit without using fins, protrusions, etc. which hinder flow, and no dead water. The heat transfer area, and the two fluids that perform heat exchange between sensible heat (temperature) and latent heat (humidity) flow and the flow paths in the two directions are the same shape of the same pressure loss, and the object of the present invention is obtained. A full heat exchange element that can easily change the external dimensions. [Means for Solving the Problems] In order to solve the above problems and achieve the object, the total heat exchange element of the present invention allows the first fluid and the second fluid to flow through the first flow path and the second flow path which are formed between the laminated sheets. The sensible heat and the latent exchange between the two fluids are characterized in that the first flow passage is a waveform flow passage of a rectangular cross section, and is formed in a shape that is a waveform that is oriented toward the forward direction of the fluid and that generates an amplitude in the laminating direction. The wet first corrugated sheet and the waveform are generated at intervals approximately the same period as the first corrugated sheet, and the second corrugated sheet having a moisture permeability is spaced apart from each other by a predetermined interval, and then the fluid is sealed by the sealing member. a side portion, wherein the second flow path is a straight flow path having a substantially triangular cross section, and is formed by densely overlapping and superimposing a wave surface of the first wave plate and the second wave plate The flat sheet is then placed between the two sheets. [Effect of the Invention] According to the total heat exchange element of the present invention, the surfaces of almost all the faces of the plate used allow different fluids to pass, and the shape of the flow path is also difficult to produce a shape of dead water, so that it is approximately all effective. The heat transfer area, then 201038902 can increase the amount per unit volume. Also, • teach m to increase the heat exchange of components, and the heat of the field is as good as the volume of the past, which in turn helps p. When it is good, it may reduce the two waves; and, again, the first waveform The plate, the first can not only exchange the teaching, but also the translucent material 'by this' the effect of heat exchange. #潜热达到 Increases the total heat exchange
【實施方式】 之實施 以下根據圖面詳細說明本發明之全熱交換元件 型態。此外，本實施型態不能限定本發明。 第1實施型態. 第1圖為本發明第1實施型態之全熱交換元件的立體 圖。為了明確地說明，使用圖令所記載之座標轴輔助性地 j明方向，但此點並不能限定本發明。本實施型態之全熱 又換TL件1G1之構成方式為，形成流道之複數個單位結構 Ο，件2G每旋轉9G度就積層__次，如此積層複數層。Μ 單位結構件20由形狀為2片波形且具有透溼性之波形板 材（第一波形板材11及第二波形板材2)與i片具有透溼性 平板狀板材13所構成。如此，由3片板材所構成之單位 結構元件20積層複數層，再使丨片平板狀板材13增加至 積層方向端部，於是完成全熱交換元件101。 首先’就第1圖中最上端之單位結構元件20來進行說 明。第一波形板材11及第二波形板材1 2形成呈約略正方 形且以相同週期振動之振幅的波形，從其中一邊朝向相向 7 201038902 之-邊(朝向γ軸方向)沿著其厚度方向(積層方向：z軸方 向）凹折成剖面為鑛齒形之狀態而形成約略波形。以此種方 式形成之第—波形板材11及第二波形板材12沿著積層方 向（Z軸方向）間隔既定之距離（流道高度）而配置。第一波 形板材11及第二波形板材12之大小加工成投影至平面之 形狀與平板狀板材13 一致的大小。 在第一波形板材11及第二波形板材12之間，流道之 寬度方向兩端部(X轴方向兩端部)為了保持兩者之間的距 離且為了密閉兩者之間的兩端部，夾持有沿著波形以鑛齒 狀凹折之間隔保持元件141隔保持㈣14為了不使流 過之流體（在本例中為空氣）茂漏，以氣密狀態固著於第一 波形板材11及第二波形板材12上。如此，第一波形板材 11及第二波形板材12藉由間隔保持元件14橫跨流道方向 之全長以密閉作為流道之兩側部的部分，藉此，内部形成 矩形剖面之波形流道（第一流道）31。 於第一波形板材11及第二波形板材12之積層方向之 上下重疊平板狀板材13(上側之1片平板狀板材13作為上 述增加的那1片）。波形板材U，12之波形之頂點（稜線） 與平板狀板材13以氣密狀態固著，以不使流過之流體洩 漏。藉此，在第一波形板材11、第二波形板材12及平板 狀板材1 3之間形成約略三角形剖面之直行流道（第二流 道）32。 如上所述’在單位結構元件20上，形成剖面為矩形、 對著流體之前進方向且沿著積層方向具有振幅的波形流道 201038902 31及與此波形流道31垂直、剖面為約略三角形且不迁迴 曲折而從人"直接到出口的直行流道32。另外，以此種方 式構成之單位結構元件2。在波之方向相互交又之狀態 下每旋轉9G度就積層—次，如此積層複數層。在第】圖 之範例中，沿著積層方向（z轴方向）積層3個單位结構元 件20 〇 、第2圖為用來說明流經各段單位結構元件2〇之流道之 〇流體方向的立體圖。在第2圖中，為了避免麻煩而省略符 號之記述，但其實是和第1圖相同之結構。從第2圖之右 侧々著X軸方向流動的第一流體A如圖中一點鏈線箭頭所 示’從下方流過第i及第3段之直行流道32和第2段之波 形流道3卜另一方面’從第2圖之左側沿著γ軸方向流動 的第二流體B從下方流過第i及第3段之波形流道31和第 2段之直行流道32。亦即，進行顯熱和潛熱之熱交換的第 —流體A與第二流體B同時通過波形流道31及直行流道 〇 32這兩種不同之流道。另外，第-流體A與第二流體b將 第一波形板材π、第二波形板材12及平板狀板材13作為 具有透溼性之媒介來進行熱交換。如此，進行熱交換之流 體所流過之兩個方向之流道皆由波形流道31及直行流道 32這兩種流道形成且為相同形狀，所以，兩個方向產生幾 乎相同之壓力損失。 第9圖為立體圖，表示習知之全熱交換元件之一例， 以作為比較。第9圖之全熱交換元件2〇1為交互積層平板 狀之隔間元件213與剖面整形為波紋鰭板之間隔保持元件 9 201038902 (波紋鑛板)211而構成。積層方法為，使！片隔間元件213[Embodiment] The following describes the full heat exchange element type of the present invention in detail based on the drawings. Further, the present embodiment does not limit the present invention. First Embodiment. Fig. 1 is a perspective view showing a total heat exchange element according to a first embodiment of the present invention. For the sake of clarity, the coordinate axes described in the drawings are used to assist the direction, but this is not intended to limit the invention. The full-heat and TL-changing 1G1 of this embodiment is formed by forming a plurality of unit structures 流 of the flow path, and the member 2G is laminated __ times every 9 G of rotation, thus stacking a plurality of layers.单位 The unit structural member 20 is composed of a corrugated sheet material (first corrugated sheet material 11 and second corrugated sheet material 2) having a shape of two sheets and having moisture permeability, and an i-sheet having a moisture-permeable flat sheet material 13. In this manner, the unit structural member 20 composed of three sheets is laminated with a plurality of layers, and the sheet-like sheet member 13 is increased to the end portion in the lamination direction, whereby the total heat exchange element 101 is completed. First, the description will be made on the uppermost unit structural element 20 in Fig. 1. The first corrugated sheet material 11 and the second corrugated sheet material 12 form a waveform having an amplitude of approximately square and vibrating at the same period, from one side toward the opposite side of the phase 7 201038902 (toward the γ-axis direction) along the thickness direction thereof (the lamination direction) : z-axis direction) The concave shape is a state in which the cross section is a mineral tooth shape to form an approximate waveform. The first corrugated sheet material 11 and the second corrugated sheet material 12 formed in this manner are arranged at a predetermined distance (flow path height) along the lamination direction (Z-axis direction). The first corrugated sheet material 11 and the second corrugated sheet material 12 are sized to have a shape projected into a plane conforming to the flat sheet material 13. Between the first corrugated sheet 11 and the second corrugated sheet 12, both ends in the width direction of the flow path (both end portions in the X-axis direction) are for keeping the distance therebetween and sealing both ends of the gap between the two. Holding the gap between the retaining elements 141 at intervals along the waveform in the shape of a tooth-toothed recess (4) 14 in order to prevent the fluid flowing through (in this case, air) from leaking, and fixed to the first corrugated sheet in an airtight state. 11 and the second corrugated sheet 12. In this manner, the first corrugated sheet material 11 and the second corrugated sheet material 12 are sealed as a portion of both sides of the flow path by the entire length of the spacer member 14 across the flow path direction, thereby forming a waveform flow path having a rectangular cross section therein ( The first flow path) 31. The flat plate material 13 is overlapped on the upper and lower sides in the stacking direction of the first corrugated sheet 11 and the second corrugated sheet 12 (one sheet-like sheet material 13 on the upper side is added as the above-mentioned sheet). The apex (ridge line) of the waveform of the corrugated sheets U, 12 and the flat sheet 13 are fixed in an airtight state so as not to leak the fluid flowing therethrough. Thereby, a straight flow path (second flow path) 32 having a substantially triangular cross section is formed between the first corrugated sheet material 11, the second corrugated sheet material 12, and the flat sheet material 13. As described above, 'on the unit structural element 20, a waveform flow path 201038902 31 having a rectangular cross section, a forward direction toward the fluid, and an amplitude along the lamination direction is formed, and is perpendicular to the waveform flow path 31, and the cross section is approximately triangular and not Move back to the twists and turns straight from the person " direct to the exit 32. Further, the unit structural element 2 is constructed in this manner. In the state where the directions of the waves intersect each other, the layer is laminated every 9 degrees, and thus a plurality of layers are laminated. In the example of the first figure, three unit structural elements 20 积 are stacked along the lamination direction (z-axis direction), and the second figure is used to explain the direction of the turbulent flow of the flow path flowing through the respective unit structural elements 2〇. Stereo picture. In Fig. 2, the description of the symbol is omitted in order to avoid trouble, but it is actually the same structure as Fig. 1. The first fluid A flowing in the X-axis direction from the right side of Fig. 2 flows through the flow paths of the straight flow path 32 and the second stage of the i-th and third stages from below as indicated by the one-point chain arrow On the other hand, the second fluid B flowing in the γ-axis direction from the left side of the second figure flows through the waveform flow path 31 of the i-th and third stages and the straight flow path 32 of the second stage from below. That is, the first fluid A and the second fluid B which perform heat exchange between sensible heat and latent heat simultaneously pass through the two different flow paths of the waveform flow path 31 and the straight flow path 〇 32. Further, the first fluid A and the second fluid b exchange heat of the first corrugated sheet π, the second corrugated sheet 12, and the flat sheet 13 as a medium having moisture permeability. In this way, the flow paths in the two directions through which the fluid for heat exchange flows are formed by the two flow paths of the waveform flow path 31 and the straight flow path 32, and have the same shape, so that the two directions produce almost the same pressure loss. . Fig. 9 is a perspective view showing an example of a conventional total heat exchange element for comparison. The total heat exchange element 2〇1 of Fig. 9 is an inter-separated flat member 213 and a spacer holding member 9 201038902 (corrugated ore plate) 211 which is cross-sectionally shaped into a corrugated fin. The layering method is to make! Tablet compartment element 213
和1片間隔保持元件211如第9圖所示，使波形凸部接觸， 製作出以重疊接人古Α π A 〇D 接0方式來固疋之單位結構元件220，使此 單位結構元件220呈隔間元件213和間隔保持元件211交 替之狀態，並使間隔保持元件211之波形開口部之開口方 又之角度乂互積層（在第9圖之範例中，積層了 6個單位結構元件22G)。另外，從第9圖右側沿著X軸方 向流動之第-流體A與從第9圖左侧沿著γ軸方向流動之 第：机體B如圖中—點鏈線箭頭所示，形成每隔—層便相 互乂叉之全熱交換元件2〇1。如此，當使兩種流體通過時， 可將隔間7L件213作為媒介’在兩流體之間進行熱交換。 ▲本實施型態之第一波形板材第二波形板材匕為 …、乂換¥之媒介’相當於帛9圖之習知例之隔間元件2】3。 _本實施型態之全熱交換元件之最大特徵為，元件内之 間隔保持元件以外之粦車@ π μ 什乂外之幾乎所有之壁面並非如鰭板般之間接 傳熱面，而是流過在其兩面為不同之受熱交 傳熱面’所以，不會浪費材料，可加大元件之每單位= 之傳熱面積。由於藉由將鰭板本身所儲存的熱給予直接傳 熱面來傳熱’所以’有助於熱交換之面積不是韓板表面積 的100%，而是使用視鰭板形狀、周圍狀況等而定的鰭板效 率，僅藉由鰭板表面積X鰭板效率和所給予的量產生影 響不過，與兩面不同之受熱交換流體接觸的直接傳熱面 之表面積有助於100%熱交換。 此外，上述熱交換是有關於顯熱，至於潛熱，轉板幾 10 201038902 乎不會產生影響（亦即，鰭板效㈣）。或者可以說，籍板 和直接傳熱面接觸而導致直接傳熱面減少的效果，因此， 潛熱交換量減少。於是，可以說盡量增大直接傳熱面會比 較不浪費材料。 若要不浪費材料，不僅僅是可以提供較便宜的元件， 為了不浪費而使提供相同性能之平板量減少，使每單位體 積之空間體積（流體可流過之體積）更大或使與流體接觸之 0 面積亦比使用鰭板時少，對於從流體通過時之壓力損失這 一點來看也是有利的。 本實施型態之第一波形板材11、第二波形板材12及 平板狀板材13為了進行顯熱和潛熱之交換，使用具有透溼 性之材料。又，在換氣用全熱交換元件中，也同時要求確 保氣體遮蔽性和安全性之阻燃性，使受熱交換流體不混合 在一起°再者’當在客廳等生命存在之空間進行換氣時使 用本實施型態時’會具體要求揮發性有機化合物（VOCs)散 © 發量較少’並要求不會散發出使人不愉快之臭氣且材料強 度要耐得住元件加工時及使用時之壓力。所以，波形板材 11、第二波形板材丨2及平板狀板材13使用滿足以上特徵 之材料。 這些板材之厚度若薄—點，則有助於溫度、溼度之通 透，而且單位結構元件2〇之其中一積層高度可變小，以同 樣ν度進行更多積層，如此效果更佳。不過，當厚度太薄 時，也可能會有材料強度無法承受加工等壞處，視其與加 工法等之間之調整而定。—般而言，常使用2〇〜120"之材 201038902 料。又，在全熱交換元件中， 層而採用多層結構，亦可以八=述質’不採用單 ㈣在第口，材料散方式具備上述性質(例如透 料之結構等情況為何，若丄層等)不過“隔間材 實施型態之元件。滿足上述之性質’則可使用用本 當使用含有具氣體遮蔽性且具水溶性及潮解性之驗金 屬鹽及驗土金屬鹽之枯料 M 第—波形板材U、第二波形 ^及平板狀板材13之材料時，這㈣劑藉由自行吸 /作用將水分儲存於元件中 潘摇仟〒间時’藉由融入該水中，藥 换 來不添加藥劑之部分’於是，原本會有需要且 殘留在隔間元件中之藥劑量減少的問題發生 r之結構中，隔間元件以外之部分之比例比習知之2 :透=及二吏用相同材料時，可確保比習知結構有更高 之透屋性及潛熱交換量。 之平實：型態之單位結構元件20形成約略正方形 之千板狀，但亦可形成平 〈第！實施例〉 料A長杨之平板狀。 依照如下之方式，絮作ψ笙！ m α 全熱交換元件1G1 本實施型態之 (PVA)等^ Γ " m之紙上’將水溶性高分子物質聚乙烯醇 劑之二及二然後混合具有水溶性及吸㈣用且作為藥 t及作為阻燃劑之氨基磺酸胍 用藥液’於單面塗佈此藥液產生特殊加工紙 加工之特殊加工紙產 指痕並加卫成波形，㈣切割成- 12 201038902 片120inm之方形紙張，重疊此種方形紙張，使用滾筒塗層 設備將聚_乙稀乳膠塗佈接合至經過波形加工之紙張之 摺痕頂部。 此時，安排夾具等設備’波形之高度設定為17_， 從波形之頂部至頂部之長度設定為115腿。接著，配合第 一波形板材1 2之波形之表面形狀而從厚度約i · 2μ之厚紙 切出之間隔保持元件14透過第二波形板材12之端部重疊 於其上，藉由刷毛來塗佈相同之聚醋酸乙烯乳膠，配合與 第二波形板材12之波形之前進方向平行的兩邊進行接合。 然後，在間隔保持元件14之上側端面塗佈乳膠後，作 為第一波形板材Η，使與第二波形板材12之厚度一樣為 ΙΟΟβπι之特殊加工紙配合間隔保持元件之波形並貼附於其 上。為了使第一波形板材11和第二波形板材12之積層方 向之距離為而決定出間隔保持元件14之高度（寬 度）。 準備好複數個以此方式製作出來之單位結構元件2〇， 母旋轉9G度就積層1片，得到第1圖之全熱交換元件101。 〈比較例〉 另一方面’為了和本實施型態之全熱交換元件101作 比較，製作出第9圖所示之全熱交換元件201。此時，間 隔保持元件（波紋鰭板）211之波形形狀與上述實施例之第 波形板材11及第二波形板材12之波形形狀相同。亦即， 間隔保持疋件211之波形之高度設定為1. 7nm，從波形之 頂部道頂部之長度設定為11 .5mm ° 13 201038902 〈比較〉 針對上述第1實施例、比較例分別積層相同層數時之 直接傳熱面積之大小進行比較之後，得到下表。在習知例 中，直接傳熱面積僅為平板狀之隔間元件213之面積，相 對於此，f 1實施例之形狀使得平板狀板材及波形板材之 面積為直接傳熱面積，所以，本實施型態之全熱交換元件 101可使相同體積之直接傳熱面積變得非常大。 [表1] 直接傳熱面積（將比較例設定為η 為1實施例 1.37 ' 比較例〈波紋鰭板〉 1.0 _ 製作本實施型態之全熱交換元件101時需要注意的 是，即使從表面上看起來為直接傳熱面積較大之結構，也 有可能隨著流道内之流體之流動方向而使實際之傳熱面積 減少而無法得到之前所期待之效果。此點尤其在矩形剖面 之波形流道中特別顯著，例如，當加高波形流道之流道高 度時，若加得太高，如第3圖所示，會有流體僅流入上面 之波形與下面之波形之間所產生之直線流道的現象發生。 在此種情況下，實際上會變成壁面與欲進行熱交換之流體 (邊乎都流入直線流道）之間所產生之循環流動之死水域D1 產生隔熱作用的狀況，所以，無法達到作為傳熱面積之效 果。若為了防止此點而使波形流道間之距離比波形板材之 波形高度短，上面之波形板材之頂部與下面之波形板材之 頂部相互嵌合，於是不會產生直線流道，結果可抑制死水 域之發生而得到想要的效果。 14 201038902 又，在波形流道之彎曲部分，隨著流量及波形形狀等 而使流體偏離原路，形成死水域。第4圖為波形板材之頂 部較為尖銳之矩形剖面所形成之波形流道剖面，第5圖為 波形板材頂部具有曲率時之矩形剖面所形成之波形流道剖 面，此為兩流道中流過相同流量時之流體(在此情況下為空 氣）流動的模擬情況。在第4圖所示之情況下，產生流體頂 部之下游侧壁面偏離原路而形成之流體循環區域(亦即死 Ο ❹ 水域D2)。於是，與此死水域的接觸之壁面表面上為直接 傳熱面’但實際上幾乎無助於傳熱。如此，當死水域D2發 生時，產生熱交換量之下降及壓力損失之上升等不想要之 效果。 針對此點之改善方法如t ς 如弟5圖所不，使波形流道之彎 曲部分亦即包含波形板材之 啊<•頂部的凹折部之形狀如第1實 施型態所示，不形成平S 4 凹折之形狀而形成具有適當曲率 之彎曲面。 又，波形板材之形狀只1且 ，、要是波形’任何形狀皆無所謂， 不過，以正弦波或三角波夕犯山α 円及之形狀為宜。也可為矩形波，但 當採用矩形波時，平板妝 板材與波形板材之間的接觸面積 變大，有可能導致性能下降 卜降’又，經過波形流道之流體以 與矩形波之起始部相撞之 形狀〜過，所以，也有壓力損失 上升之虞。 、 又’當對波形之頂部轴1 Ρ賦予曲率時，可提供一種壓力損 失較低之全熱交換元件。 ,. 错由減少壓力損失，可減少對欲 組合之機器之流體動力 置之輪入，也有助於減少機器之 15 201038902 能量化。 第2實施型態. 第6圖為本發明第2實施型態之全熱交換元件的立體 圖。在本實施型態之全熱交換元件1〇2中，第一波形板材 11及第二波形板材12之波形之頂部附近之凹折部之形狀 如第5圖所示，為當流體通過時不會形成死水域之既定曲 率之圓滑彎曲形狀。又，在本實施型態之全熱交換元件1〇2 中，在第一波形板材11與第二波形板材12之間，將波形 流道31沿著流道寬度方向分割為複數個，並且，設置使兩 板材11，12相互支持的複數個隔壁24。其他方面之結構 則和第1實施型態相同。 在本實施型態中，由於設置複數個隔壁24，第一波形 板材11和第二波形板材12藉由狹窄間隔相互支持所以， 增加了兩板材11，12的保持點，也使製作過程中之單位結 構元件20及整個全熱交換元件⑽之結構強度變大，於^ 得以提高it件之加X性及使用性。㈣，也有助於防止進 行熱交換之兩個流體之間的洩漏。 再者，生產時之優點包括，藉由複數個隔壁24隔開， 所以可在事先設計外形尺寸較大之元件時切割出任意大小 之相似形，藉此，可得到任意外形尺寸之全熱交換元件。 因此’可在不變更模具等之情況下進行外形尺寸之變更。 ^ 點有助於生產效率之A大提高及產品設計自^度 尚。 第3實施型態. 16 201038902 第7圖為本發明第3實施型態之全熱交換元件的立體 圖。在本實施型態之全熱交換元件103中，有設置於波形 流道31内且將該波形流道31沿著流道寬度方向分割成複 數個的隔壁，隔壁之流道寬度方向厚度每隔既定片數而變 大。換言之，厚度較小之隔壁24d與厚度較大之隔壁24a 根據既定順序來設置。在本實施型態中，厚度較小之隔壁 24d與厚度較大之隔壁24a交互設置。其他方面之結構則 Q 和第2實施型態相同。 在第2實施型態之範例中，藉由以任意尺寸來切割， 可得任意外形尺寸之元件，然而，所得到之元件之端部視 隔壁之位置與切割位置之間的關係而定，有可能導致很多 浪費的部分。在此種情況下，為了防止流體進入元件之端 部之部分而洩漏至其他流體之流道，必須組合可封閉寬度 比過去寬之部分的結構物，不過，其寬度尺寸必須決定元 件之切割位置，所以結構物之設計與準備變得困難。因此， 〇 對切割位置賦予限制，不過，若切割隔壁之較厚部分之中 心，切割後之元件可成為其端部沒有浪費部分之相似形元 件。 【產業上可利性】 如上所述，本發明之全熱交換元件適用於在兩個流體 間進行顯熱和潛熱交換之板材積層型全熱交換元件，尤其 適用於用來組合至換氣裝置、空調機内並進行空氣對空氣 之全熱交換的全熱交換元件。 17 201038902 【圖式簡單說明】 第 1圖 為本發明第 1 實 圖 〇 第 2圖 為用來說明 流 經 體 方 向 的立 體圖。 第 3圖 為模式圖， 表 示 致 死 水域變 多的範例。 第 4囷 為模式圖， 表 示 死 水域 變多 的範例。 第 5圖 為模式圖， 表 示 曲 會 導 致死水域消失的 範 例 第 6圖 為本發明第 2 實 圖。 施型態之全熱矣換元件的立體 各段單位結構元件之流道之流 波形流道之流道高度過高會導 波形板材之頂部被凹摺會導致 波形板材之頂部以適當曲率彎 〇 施型態之全熱交換 狭疋件的立體 第7圖為本發明第3實施型態之全熱交換元件的立體 第8圖為流動不沿著波形壁面時的流動棋式圖。 第9圖為用來比較之習知全熱交換元件的立體圖 【主要元件符號說明】 11〜第一波形板材； 12〜第二波形板材； 〜平板狀板材； 14〜間隔保持板材； 201038902 20〜單位結構元件； 24, 24a，24b~ 隔壁； 3卜波形流道（第一流道）； 32〜直行流道（第二流道）； 101，102，103〜全熱交換元件； 201〜全熱交換元件； 211〜間隔保持元件； 213~隔間元件； ❹ 220〜單位結構元件； A〜第一流體； B〜第二流體； DO, Dl，D2〜死水域。 〇 19As shown in FIG. 9, the one-piece spacer member 211 is brought into contact with the convex portion of the waveform, and a unit structural member 220 is formed which is fixed by overlapping the πA 〇A and the 0D, and the unit structural member 220 is fixed. In a state in which the compartment member 213 and the spacer member 211 are alternated, and the opening of the waveform opening portion of the spacer member 211 is angled to each other (in the example of FIG. 9, 6 unit structural members 22G are laminated) ). Further, the first fluid A flowing in the X-axis direction from the right side of the ninth diagram and the first fluid body B flowing in the γ-axis direction from the left side of the ninth graph are formed as shown by the dotted line arrow in the figure. The entire heat exchange element 2〇1 is separated from each other by the interlayer. Thus, when the two fluids are passed, the compartment 7L member 213 can be used as a medium to exchange heat between the two fluids. ▲ The first corrugated sheet of the first embodiment of the present invention is a medium ... 乂 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 The most characteristic feature of the full heat exchange element of this embodiment is that almost all the wall surfaces other than the spacers other than the spacers in the components are not connected to the heat transfer surface like a fin, but flow The heat transfer surface is different on both sides of the heat transfer surface. Therefore, the material is not wasted, and the heat transfer area per unit of the component can be increased. Since the heat stored by the fin itself is given to the direct heat transfer surface, the heat transfer area is not 100% of the surface area of the Korean plate, but is determined by the shape of the fin, the surrounding condition, and the like. The fin efficiency is only affected by the fin surface area X fin efficiency and the amount imparted. However, the surface area of the direct heat transfer surface in contact with the heated exchange fluid on both sides contributes to 100% heat exchange. In addition, the above heat exchange is related to sensible heat, as for latent heat, the transfer plate does not affect (ie, fin effect (4)). Or it can be said that the contact between the plate and the direct heat transfer surface results in a reduction in the direct heat transfer surface, and therefore, the amount of latent heat exchange is reduced. Therefore, it can be said that increasing the direct heat transfer surface as much as possible will waste material. If you don't waste material, you can not only provide cheaper components, but also reduce the amount of flat plates that provide the same performance without wasting, so that the volume of space per unit volume (the volume through which fluid can flow) is larger or the fluid is made The area of contact 0 is also less than when fins are used, and is also advantageous in view of the pressure loss from the passage of the fluid. In the present embodiment, the first corrugated sheet 11, the second corrugated sheet 12, and the flat sheet 13 are made of a material having moisture permeability for the exchange of sensible heat and latent heat. In addition, in the total heat exchange element for ventilation, it is also required to ensure the flame retardancy of the gas shielding property and the safety, so that the heat exchange fluid is not mixed together, and then the air is ventilated in a living space such as a living room. When using this embodiment, the specific requirements of volatile organic compounds (VOCs) are required to be less, and it is required that the unpleasant odor will not be emitted and the strength of the material should be able to withstand the processing and use of the components. The pressure. Therefore, the corrugated sheet 11, the second corrugated sheet 2, and the flat sheet 13 are made of materials satisfying the above characteristics. If the thickness of these sheets is thin, the temperature is favorable for the penetration of temperature and humidity, and the height of one of the unit structural elements 2 可变 is small, and more layers are laminated with the same ν degree, so that the effect is better. However, when the thickness is too thin, there may be cases where the material strength cannot withstand processing and the like, depending on the adjustment between the processing method and the like. In general, 2〇~120" material 201038902 is often used. Further, in the total heat exchange element, the layer has a multilayer structure, and it is also possible to use the above-mentioned properties in the material dispersion mode (for example, the structure of the material to be permeable, etc. However, "the components of the compartments are of a type that meets the above properties" can be used with the use of a metal salt containing a gas-shielding, water-soluble and deliquescent metal salt and a soil-measuring metal salt. - When the material of the corrugated sheet U, the second waveform ^ and the flat sheet 13 is used, the (four) agent stores the moisture in the component by self-priming/acting, and when the pan is shaken, the drug is exchanged. Adding the portion of the drug', then, in the structure where there is a problem that the amount of the drug remaining in the compartment element is reduced, the ratio of the portion other than the compartment component is the same as that of the conventional 2: transparent and the second In the case of materials, it is ensured that there is a higher permeability and latent heat exchange capacity than the conventional structure. The level: the unit structure element 20 of the form forms a roughly square shape, but can also form a flat embodiment. Material A Chang Yang's tablet According to the following method, floculation m! m α full heat exchange element 1G1 This embodiment type (PVA), etc. ^ Γ " m paper on the 'water-soluble polymer substance polyvinyl alcohol agent two and two Then, mixing the water-soluble and absorbing (four) medicinal sulfamate as a medicine t and as a flame retardant, the special processing paper processed by the single-side coating of the medicinal liquid to produce a special processing paper is produced and added. Waveform, (4) Cut into - 12 201038902 Pieces of 120inm square paper, overlap the square paper, use the roller coating equipment to apply the poly-ethylene latex coating to the top of the crease of the wave-processed paper. At this time, arrange the fixture The height of the waveform of the device is set to 17_, and the length from the top to the top of the waveform is set to 115. Then, the interval of the surface of the waveform of the first corrugated sheet 12 is cut out from the thick paper having a thickness of about i · 2 μ. The holding member 14 is superposed on the end portion of the second corrugated sheet 12, and the same polyvinyl acetate latex is applied by the bristles to engage with the two sides parallel to the forward direction of the second corrugated sheet 12. Then, after the latex is coated on the upper end surface of the spacer member 14, as a first corrugated sheet, a special processing paper having the same thickness as the second corrugated sheet 12 is placed in a space of the spacer member and attached thereto. The height (width) of the spacer member 14 is determined in order to set the distance between the first wave plate 11 and the second wave plate 12 in the lamination direction. A plurality of unit structural members 2 manufactured in this manner are prepared, When the mother rotates 9 G degrees, one sheet is laminated to obtain the total heat exchange element 101 of Fig. 1. <Comparative Example> On the other hand, in order to compare with the total heat exchange element 101 of the present embodiment, the same is shown in Fig. 9. The total heat exchange element 201. At this time, the waveform shape of the spacer member (corrugated fin) 211 is the same as that of the first wave plate 11 and the second wave plate 12 of the above embodiment. That is, the height of the waveform of the spacer 211 is set to 1. 7 nm, and the length from the top of the top of the waveform is set to 11.5 mm ° 13 201038902 <Comparative> The same layer is laminated for the first embodiment and the comparative example described above. After comparing the magnitudes of the direct heat transfer areas for several hours, the following table was obtained. In the conventional example, the direct heat transfer area is only the area of the flat-shaped spacer element 213. In contrast, the shape of the f 1 embodiment is such that the area of the flat plate material and the corrugated plate material is the direct heat transfer area. The implementation of the full heat exchange element 101 allows the direct heat transfer area of the same volume to be made very large. [Table 1] Direct heat transfer area (Comparative example is set to η is 1 Example 1.37 'Comparative example <Corrugated fin plate> 1.0 _ When manufacturing the entire heat exchange element 101 of the present embodiment, it is noted that even from the surface The structure which appears to have a large direct heat transfer area may also reduce the actual heat transfer area with the flow direction of the fluid in the flow channel, and the previously expected effect cannot be obtained. This is especially the waveform flow in the rectangular profile. Especially significant in the channel, for example, when the height of the channel of the waveform channel is increased, if it is added too high, as shown in Fig. 3, there will be a straight flow between the waveform flowing into the upper surface and the waveform below. In this case, it is actually a situation in which the dead water D1 of the circulating flow generated between the wall and the fluid to be exchanged for heat (which flows into the straight flow path) is insulated. Therefore, the effect as a heat transfer area cannot be achieved. If the distance between the waveform channels is shorter than the waveform height of the corrugated sheet in order to prevent this, the top and bottom of the corrugated sheet above When the tops of the materials are fitted to each other, a straight flow path is not generated, and as a result, the occurrence of dead water can be suppressed to obtain a desired effect. 14 201038902 Further, in the curved portion of the waveform flow path, the flow rate and the waveform shape are used. The fluid deviates from the original path to form dead water. Figure 4 is the waveform flow path section formed by the sharp rectangular section at the top of the corrugated plate, and the fifth figure shows the waveform flow path profile formed by the rectangular section with the curvature at the top of the corrugated plate. This is a simulation of the flow of fluid (in this case, air) flowing through the same flow in the two flow paths. In the case shown in Fig. 4, the fluid formed by the downstream side wall surface of the fluid top is deviated from the original path. The circulation area (that is, the dead water D water area D2). Therefore, the surface of the wall contacting the dead water area is a direct heat transfer surface' but it practically does not contribute to heat transfer. Thus, when the dead water D2 occurs, heat is generated. Undesirable effects such as a decrease in the amount of exchange and an increase in pressure loss. For the improvement of this point, for example, t ς, as shown in Figure 5, the curved portion of the waveform flow path contains the wave. The shape of the concave portion of the top plate is as shown in the first embodiment, and the curved surface having the appropriate curvature is formed without forming the shape of the flat S 4 concave fold. Moreover, the shape of the corrugated plate material is only 1 and If the waveform 'any shape does not matter, however, it is suitable for the shape of a sine wave or a triangular wave. It can also be a rectangular wave, but when a rectangular wave is used, the contact between the flat plate and the corrugated plate As the area becomes larger, there is a possibility that the performance is degraded. In addition, the fluid passing through the waveform flow path collides with the initial portion of the rectangular wave. Therefore, there is also a rise in pressure loss. The top shaft 1 Ρ provides a full heat exchange element with a low pressure loss when imparting curvature. . . . by reducing the pressure loss, reducing the fluid power of the machine to be combined, and helping to reduce the machine. 15 201038902 Energyization. Second Embodiment. Fig. 6 is a perspective view showing a total heat exchange element according to a second embodiment of the present invention. In the total heat exchange element 1〇2 of the present embodiment, the shape of the concave portion near the top of the waveform of the first wave plate 11 and the second wave plate 12 is as shown in FIG. 5, and is not when the fluid passes. It will form a rounded curved shape with a given curvature of the dead water. Further, in the total heat exchange element 1A2 of the present embodiment, the waveform flow path 31 is divided into a plurality of the flow path 31 along the flow path width direction between the first corrugated plate 11 and the second corrugated plate 12, and A plurality of partition walls 24 are provided which support the two sheets 11, 12 to each other. The structure of the other aspects is the same as that of the first embodiment. In the present embodiment, since the plurality of partition walls 24 are provided, the first corrugated sheet material 11 and the second corrugated sheet material 12 are mutually supported by the narrow intervals, so that the holding points of the two sheets 11 and 12 are increased, and the manufacturing process is also performed. The structural strength of the unit structural element 20 and the entire total heat exchange element (10) is increased, so that the X-addability and usability of the IT member can be improved. (iv) It also helps to prevent leakage between the two fluids that exchange heat. Furthermore, the advantages in production include that the plurality of partition walls 24 are separated, so that a similar shape of any size can be cut when a component having a large outer shape is designed in advance, thereby obtaining a total heat exchange of any outer shape. element. Therefore, the external dimensions can be changed without changing the mold or the like. ^ Points contribute to the improvement of production efficiency and product design. Third Embodiment. 16 201038902 FIG. 7 is a perspective view of a total heat exchange element according to a third embodiment of the present invention. In the total heat exchange element 103 of the present embodiment, a partition wall is provided in the wave flow path 31 and divided into a plurality of the flow path 31 along the flow path width direction, and the thickness of the partition wall in the flow path width direction is every It becomes larger in a given number of sheets. In other words, the partition wall 24d having a small thickness and the partition wall 24a having a large thickness are provided in accordance with a predetermined order. In the present embodiment, the partition wall 24d having a small thickness is alternately disposed with the partition wall 24a having a larger thickness. The structure of the other aspects is the same as the second embodiment. In the example of the second embodiment, an element of any outer shape can be obtained by cutting in an arbitrary size. However, the end of the obtained element depends on the relationship between the position of the partition wall and the cutting position, and It can lead to a lot of wasted parts. In this case, in order to prevent fluid from entering the end portion of the element and leaking to the flow path of other fluids, it is necessary to combine a structure that can enclose a portion wider than the past, but the width dimension must determine the cutting position of the element. Therefore, the design and preparation of the structure becomes difficult. Therefore, 〇 imposes a restriction on the cutting position, but if the center of the thick portion of the partition wall is cut, the cut component can be a similar shaped element whose end portion is not wasted. [Industrial Applicability] As described above, the total heat exchange element of the present invention is suitable for a plate-stacked type full heat exchange element for performing sensible heat and latent heat exchange between two fluids, and is particularly suitable for combination to a ventilator A total heat exchange element for air-to-air heat exchange in the air conditioner. 17 201038902 [Simple description of the diagram] Fig. 1 is the first diagram of the present invention. Fig. 2 is a perspective view for explaining the direction of the flow. Figure 3 is a pattern diagram showing an example of a large number of dead waters. The fourth is a pattern diagram showing an example of a large number of dead waters. Fig. 5 is a pattern diagram showing a pattern in which the dead water is disappeared. Fig. 6 is a second diagram of the present invention. The flow path of the flow path of the three-dimensional unit of the full-heat 矣 change element of the embodiment is too high, and the top of the wavy plate is concavely folded, which causes the top of the slab to bend with an appropriate curvature. Fig. 7 is a perspective view of the total heat exchange element of the third embodiment of the present invention. Fig. 8 is a flow diagram of the flow of the entire heat exchange element according to the third embodiment of the present invention. Figure 9 is a perspective view of a conventional full heat exchange element for comparison [main component symbol description] 11 to first wave plate; 12 to second wave plate; ~ flat plate; 14 to spacer plate; 201038902 20~ unit structure Components; 24, 24a, 24b~ partition wall; 3 wave waveform channel (first channel); 32~ straight channel (second channel); 101, 102, 103~ total heat exchange element; 201~ total heat exchange element 211~ spacer holding element; 213~ compartment element; ❹ 220~ unit structural element; A~ first fluid; B~ second fluid; DO, Dl, D2~ dead water. 〇 19