CN106537077B - 热交换器芯体 - Google Patents
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- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
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Abstract
在波纹散热片型热交换器中,使百叶板的切开立起方向仅向一个方向倾斜地形成,相对于现有型散热片使传热性能得到提升。满足H>Qup/(Qup‑1)×ΔH的式子。在此,H是热交换器的芯体高度,Qup是通风部中的单向百叶板散热片和转向百叶板散热片的每1山的热交换量之比,ΔH是从转向百叶板散热片变更为单向百叶板散热片所引起的热交换器芯体的传热降低区域的增量。
Description
技术领域
背景技术
波纹散热片型热交换器是如下装置:大量扁平管和波纹散热片交替地并列,使第1流体在管内流通,并使第2流体在管的外面侧以及波纹散热片流通。
第2流体主要是空气等气体。
在这样的波纹散热片型热交换器中,当前实际应用的散热片是,在中间配置转向百叶板,在其两侧,将倾斜的朝向彼此为反向的百叶板切开立起。
接下来,给出将百叶板的朝向限定在一个方向的波纹散热片型热交换器,作为下述专利文献1。
在该热交换器中,与空气流的流入方向成锐角的角度的单向百叶板在该芯体宽度的全长的整个范围内切开立起而形成。根据该发明,对于在芯体宽度全长的整个范围内向一个方向切开立起的散热片,指摘出该芯体的上端部以及下端部的空气流停滞这一现象。
为此,该发明配置隔离构件,该隔离构件在配置于芯体的上下的罐与散热片的端部之间形成空隙部。于是,由于该空隙部的存在,散热片内的空气流的停滞消失,能大幅降低通风阻力。
现有技术文献
专利文献
专利文献1:JP特开2006-266574号公报
发明内容
发明要解决的课题
但是,根据本发明的发明者的流体分析、实验等研讨,明确了在由向一个方向切开立起的波纹散热片构成的芯体中,在调整其芯体高度、芯体宽度以及切开立起角度之后,热交换性能才会相比由现有型散热片构成的芯体有提升。
本发明基于相关的见解而开发。
用于解决课题的手段
权利要求1记载的本发明是一种热交换器芯体,在该热交换器芯体中,大量波纹散热片(以下称作单向散热片)和大量扁平管交替并列,其中,在该大量波纹散热片中,在流体所流通的散热片的宽度方向上并列地将全部百叶板向同一方向倾斜地切开立起加工,所述热交换器芯体的特征在于,芯体的高度H(mm)、流体的主要的流动方向的百叶板切开立起宽度W(mm)、和百叶板切开立起角度θ被设定为满足下述不等式(1):
H>Qup/(Qup-1)×ΔH (1)
Qup=Qup(W,θ)=α(W)+β(W,θ)+1 (2)
α(W)=η/(W-η) (3)
β(W,θ)=ξ/(W·tan22θ-ξ) (4)
ΔH=ΔH(W,θ)=j·W(sinθ+k·sin2θ) (5)
η=0.3553 (mm)
ξ=0.5447 (mm)
j=0.1419
k=4.2789。
发明的效果
在本发明中,芯体的高度H(mm)、流体的主要的流动方向的百叶板切开立起宽度W(mm)、以及百叶板切开立起角度θ满足权利要求1的不等式(1),由于芯体的高度H为H>Qup/(Qup-1)×ΔH,因此与现有型散热片相比,热交换性能更高。
具体地,在图6的W-H曲线上,在各百叶板的切开立起角度θ下,有超过将所描绘的各点连起来的曲线的范围的芯体H的高度。另外,在此,百叶板切开立起宽度W在图3中是指将单向百叶板进行切开立起的范围。
以下记述能得到效果的理由。
单向散热片相对于现有的转向百叶板散热片有缺点以及优点,缺点是通风降低区域(传热降低区域)的增加ΔH,优点是通风部中的传热的提升(比)Qup。
在此,用于使优点超过缺点的条件是
Qup×(H-ΔH)/H>1,
若将该不等式变形,则成为
H>Qup/(Qup-1)×ΔH。
附图说明
图1是对本发明的散热片所引起的空气流和现有型热交换器的散热片所引起的空气流进行比较的说明图。
图2(A)是表示本发明的空气流的流通状态的说明图,图2(B)是表示现有型热交换器的空气流的流通状态的说明图。
图3(A)是本发明的热交换器芯体的百叶板的切开立起说明图,图3(B)是现有型热交换器芯体的百叶板的切开立起说明图。
图4是在横轴取百叶板切开立起宽度W且在纵轴取本发明的芯体与现有型芯体中的主要的传热区域(通风部)的传热率之比的实验数据。
图5是在横轴取百叶板切开立起宽度W且在纵轴表征本发明的芯体相对于现有型芯体的传热降低区域(通风降低区域)的增量ΔH的曲线图。
图6是在横轴取百叶板切开立起宽度W且在纵轴表征相对于现有型芯体具有本发明的芯体的效果的芯体高度的下限的曲线图。
图7是在横轴取百叶板切开立起宽度W且在纵轴取本发明的热交换器芯体与现有型热交换器芯体的热交换量的比率的曲线图。
具体实施方式
接下来基于附图来说明本发明的实施方式。
图1~图3分别表征本发明的热交换器芯体与当前正实际应用化的现有型热交换器芯体的比较。
图1是该热交换器芯体的纵截面说明图。另外,图2(A)示出本发明的百叶板所引起的空气的流通路,图2(B)示出现有型芯体的空气的流通路。并且,图3(A)、图3(B)是表示各个百叶板的切开立起状态的说明图。
本发明的热交换器芯体将扁平管和波纹散热片交替并列来形成芯体。并且,在该示例中,在上下配置一对罐3,扁平管的两端贯通于该罐3。在图1中,芯体高度H是上下一对罐3间的分离距离(一对罐3间的空间部高度)。该芯体的百叶板切开立起宽度W比图3的芯体宽度要短散热片的平坦部长度的量。
在该示例中,如图2(A)、图3(A)所示那样,对波纹散热片,仅单向散热片倾斜地在百叶板切开立起宽度W的范围内被等间隔地切开立起。另外,在百叶板切开立起宽度W的两侧,存在平坦部6d,在该平坦部6d形成半百叶板6c。该半百叶板6c的宽度是其以外的百叶板6的宽度的一半。
并且,如图2(A)所示那样,空气流1若流入到单向散热片7就被引导到该单向散热片的各百叶板6,该单向的流路4从上游侧到下游侧形成为倾斜的带状。
与此相对,现有型散热片8如图2(B)、图3(B)所示那样,在散热片的宽度方向中央具有转向百叶板6b,在其两侧并列有改变了百叶板的朝向的百叶板6a。在该转向百叶板6b的两侧将半百叶板切开立起。
并且,若空气流1流入到现有型散热片8就会如图2(B)所示那样使现有型散热片的流路5形成为山形。
如此,作为本发明的对象的单向散热片7和现有型散热片8的流路分别如单向散热片的流路4以及现有型散热片的流路5那样完全不同。
这是基于本发明的单向散热片7与现有型散热片8的结构状况的差异。并且,出现以下的差异。
首先,在单向散热片7中,相比于现有型散热片8能实现更多的百叶板6的切开立起。这是因为,能取代现有型散热片8的转向百叶板6b来将单向百叶板切开立起。由于这一点,本发明的芯体提升了传热率。
其次,难以通过转向百叶板6b使空气流1完全转向,在现有型散热片8中,会紧挨转向部下游后产生滞留域,但在本发明中消除了这一问题。也由于这一点,传热率得以提升。
在图1中,从左侧流入的空气流1在单向散热片7中在该实效芯体高度H1的范围内在热交换器芯体2内倾斜地流通。
与此相对,在现有型散热片8的情况下,在现有型的实效芯体高度H2的范围内在热交换器芯体2内如山形的虚线那样流通。如从图1所明确的那样,相比本发明的单向散热片的实效芯体高度H1,现有型的实效芯体高度H2更高。为此,在图1中,在本发明中,由于设为单向散热片,从而出现通风降低区域的增加ΔH。并且,在该ΔH的区域中,传热率降低。
为此,首先,本发明的发明者以实验来求得图1中的单向散热片的实效芯体高度H1下的传热率,作为相对于现有型散热片8的比。图4是该实验数据,在横轴取百叶板切开立起宽度W,在纵轴取传热率的比率。然后,在百叶板角度为20度、30度、40度下尝试各个实验。
如从图4所明确的那样,不管何种角度,在实效芯体高度H1的范围内,都示出了比现有型百叶板的传热率高的传热率的比率。
另外,图7表示百叶板切开立起宽度W和芯体整体的热交换量的比率。
若对这些数据进行回归分析,则得到
Qup=Qup(W,θ)=α(W)+β(W,θ)+1。
在此,α(W)=η/(W-η),η=0.3553(mm)。并且,β(W,θ)=ξ/(W·tan22θ-ξ),ξ=0.5447(mm)。
α(W)表征百叶板片数增加的效果,β(W,θ)表征转向部下游滞留域消失的效果。
另外,Qup=(通风部中的单向散热片每1山的热交换量)/(通风部中的现有型散热片每1山的热交换量)。
接下来,本发明的发明者如图1所示那样,以实验确认由于设为单向散热片而相对于现有型的实效高度H2所损失的区域ΔH。这是图5。在图5中,横轴是芯体的百叶板切开立起宽度W,纵轴是设为单向百叶板而带来的传热降低区域的增量ΔH,各自的单位是mm。
然后,以数值计算所获得的流线为基础,在各百叶板角度θ下进行回归分析,得到回归式(5)
ΔH=ΔH(W,θ)=j·W·(sinθ+k·sin2θ)
(j=0.1419,k=4.2789)。
在此,若将单向百叶板的优点和缺点与现有型散热片比较考虑,则表征其效果的范围是Qup×(H-ΔH)/H>1。
然后,若将该式变形,则成为H>Qup/(Qup-1)×ΔH。
在图6中示出根据该不等式求得的具有单向百叶板的效果的芯体高度的下限(曲线a3~c3)。
作为一例,在百叶板角度20度的情况下,相对于百叶板切开立起宽度W的该下限的值位于a3的曲线上。
只要是该下限值以上的芯体高度,就能得到比现有型的芯体高的热交换性能。
百叶板角度30度以及40度的情况也是同样。
因此,单向百叶板的热交换器芯体只要被设定成使该H、W和θ满足式(1)H>Qup/(Qup-1)×ΔH即可。
另外,本发明是根据以下研究探讨而得到的:百叶板切开立起宽度W为6~46mm,百叶板切开立起角度θ为20度~35度,百叶板间距为0.5~1.5mm,散热片间距为2~5mm,将流体设为空气流,将该芯体前面流速设为2~8m/s。
并且,更优选的适用条件是:百叶板切开立起宽度W为6~26mm,百叶板切开立起角度θ为20度~30度,百叶板间距为0.5~1.0mm,散热片间距为2~3mm,流体为空气流,该芯体前面流速为4~8m/s。
标号的说明
1 空气流
1a 空气流
2 热交换器芯体
3 罐
4 单向散热片的流路
5 现有型散热片的流路
6 百叶板
6a 百叶板
6b 转向百叶板
6c 半百叶板
6d 平坦部
7 单向散热片
8 现有型散热片
H 芯体高度
W 百叶板切开立起宽度
θ 百叶板切开立起角度
Claims (1)
1.一种热交换器芯体,在该热交换器芯体中,在流体所流通的散热片的宽度方向上并列地将全部百叶板向同一方向倾斜地切开立起加工的大量波纹散热片即单向百叶板散热片和大量扁平管交替并列,所述热交换器芯体的特征在于,
在该芯体的两端配置贯通了所述扁平管的两端的一对罐,
芯体的高度H、流体的主要的流动方向的百叶板切开立起宽度W、和百叶板切开立起角度θ被设定为满足下述不等式(1),其中,该芯体的高度H是一对罐间的分离距离,即一对罐间的空间部距离:
H>Qup/(Qup-1)×ΔH (1)
Qup=Qup(W,θ)=α(W)+β(W,θ)+1 (2)
α(W)=η/(W-η) (3)
β(W,θ)=ξ/(W·tan22θ-ξ) (4)
ΔH=ΔH(W,θ)=j·W(sinθ+k·sin2θ) (5)
η=0.3553(mm)
ξ=0.5447(mm)
j=0.1419
k=4.2789,
其中,芯体的高度H和百叶板切开立起宽度W的单位为mm,
相对于在流体所流通的散热片的宽度方向上在中间配置转向百叶板并在该转向百叶板的两侧将百叶板向相反方向倾斜地切开立起加工的转向百叶板散热片,
ΔH是所述单向百叶板散热片的热交换器芯体相对于所述转向百叶板散热片的热交换器芯体的传热降低区域的增量,
Qup是通风部中的所述单向百叶板散热片每1山的热交换量与通风部中的所述转向百叶板散热片每1山的热交换量之比。
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