CN107076484A - 用于减少制冷剂充量的蒸发器液体预热器 - Google Patents
用于减少制冷剂充量的蒸发器液体预热器 Download PDFInfo
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Abstract
用于通过在将液体制冷剂引入到蒸发器的入口之前预加热所述液体制冷剂来减少制冷系统中的制冷剂充量的系统和方法。当制冷剂液体引入到蒸发器的入口时,制冷剂液体的一部分蒸发。该制冷剂蒸汽驱替蒸发器的入口处的制冷剂液体。随着更多的制冷剂蒸汽被引入,蒸发器内的液体量减少。热交换器安放在蒸发器的液体制冷剂入口之前,用以在制冷剂进入蒸发器时产生更多蒸汽。
Description
技术领域
本发明涉及使用压缩机、冷凝器和蒸发器的制冷系统,并且更特别地,涉及使用通过压缩机循环的挥发性制冷剂的这种系统;并且再更特别地,涉及所谓的液体过量供给型制冷系统的这种系统,但本发明也可与直接膨胀制冷系统一起使用。
背景技术
蒸汽压缩使用循环液体制冷剂作为介质,以从待冷却的空间吸收和移除热,并且随后在其它地方排出该热。所有这些系统具有压缩机、冷凝器、膨胀阀(也称为节流阀或计量装置)和蒸发器。循环制冷剂以称为饱和蒸汽的热力学状态进入压缩机,并被压缩到更高的压力,也导致更高的温度。热的、压缩的蒸汽然后处于称为过热蒸汽的热力学状态,并且处于可以通过冷却水或冷却空气而冷凝的温度和压力下。该热蒸汽被引导通过冷凝器,在那里它通过流过一个或多个用冷水或冷空气流过的盘管或管道,而被冷却和凝结成液体。在此处,循环制冷剂从系统排出热,并且排出的热被水或空气(无论哪种情况)带走。
处于被称为饱和液体的热力学状态下的冷凝的液体制冷剂接着被引导通过膨胀阀,在那里其经历压力的突然降低。该压力降低导致液体制冷剂的一部分的绝热闪蒸。绝热闪蒸的自动制冷效应将液体和蒸气制冷剂混合物的温度降低到比要致冷的封闭空间的温度更冷的状态。
然后将冷混合物引导通过蒸发器中的盘管或者管道。风扇使加温空气在封闭空间中循环穿过承载冷制冷剂液体和蒸汽混合物的盘管或者管道。该加温空气使冷制冷剂混合物的液体部分蒸发。同时,循环空气被冷却,因此将封闭空间的温度降低到期望的温度。蒸发器是循环制冷剂吸收和除去热的地方,该热随后在冷凝器中被排出,并通过在冷凝器中使用的水或空气传递到别处。为了完成制冷循环,来自蒸发器的制冷剂蒸汽再次是饱和蒸汽,并且被引导回压缩机中。
发明内容
本发明是特别地通过在液体制冷剂引入到蒸发器的入口之前预加热所述液体制冷剂而减少蒸发器中需要的制冷剂充量,从而减少制冷系统中的制冷剂充量的系统和方法。当制冷剂液体引入到蒸发器的入口时,制冷剂液体的一部分蒸发。该制冷剂蒸汽驱替蒸发器的入口处的制冷剂液体。随着更多的制冷剂蒸汽被引入,蒸发器内的液体量减少。根据本发明,热交换器安放在蒸发器的液体制冷剂入口之前。该热交换器用以在制冷剂进入蒸发器时预加热液体以产生更多蒸汽。进入蒸发器的蒸汽的增加的量(相对于现有技术的系统)驱替液体制冷剂,因此减少了蒸发器以及因此整个系统所需的制冷剂充量。根据一个实施例,可以加热液体制冷剂,以便完全蒸发5%-30%的制冷剂。根据相关实施例,液体制冷剂可以被加热,以便完全蒸发10%-30%的制冷剂、15%-30%的制冷剂、20%-30%的制冷剂、5%-10%的制冷剂、5%-15%的制冷剂或10%-20%的制冷剂。
根据另一个实施例,液体制冷剂可以被加热到在冷凝器的运行温度和蒸发器的运行温度之间的差的10%和80%之间的温度。例如,如果冷凝器在90°F下操作并且蒸发器在30°F下操作,则温度的差为60°F,并且液体制冷剂可以被加温到36°F(温度差的10%),或者被加温到78°F(所述差的80%,或被加温到在36°F和78°F之间的任何温度)。根据相关实施例,液体制冷剂可被加热到冷凝器的运行温度和蒸发器的运行温度之间的差的20%、30%、40%、50%、60%或70%的温度。
热交换器热源可以是外部能量输入,例如由制冷压缩机产生的废热,或者是内部热源,例如从制冷系统中的冷凝器排出的加温的制冷剂液体。通过使用来自冷凝器的加温液体,不会增大产生冷却所需的净能量。当到蒸发器的液体制冷剂流是其中所引入的制冷剂液体中的一部分以液态离开蒸发器的液体过量供给类型时,这种布置是优选的。
可以使用能够提高制冷剂液体的温度的任何类型的热交换器。液-液热交换器是优选的,特别是对于液体过量供给蒸发器。熔接板式热交换器,例如由阿法拉伐(AlfaLaval)制造的,特别适合于此目的。
附图说明
图1是根据本发明的实施例的制冷系统的示意图。
具体实施方式
图1示出了根据本发明的实施例的蒸发器热交换器相对于液体过量供给系统中的其它部件的管系示意图。这对于最大化制冷系统效率是优选的管系布置。该系统包括:蒸发器2a、2b,其分别包括蒸发器盘管4a、4b和除霜/乙二醇盘管6a、6b;冷凝器8;压缩机10;膨胀装置11a、11b(其可以是阀、计量孔或其它膨胀装置);和分离器容器12。前述元件可以使用标准制冷剂配管以图1所示的方式连接或根据任何标准布置连接。除霜系统18包括乙二醇箱20、乙二醇泵22、乙二醇热交换器24和乙二醇盘管6a、6b,它们也使用制冷剂配管根据图1所示的布置或者根据任何标准布置连接到彼此及连接到系统中其它元件。根据本发明,蒸发器预热器热交换器14位于蒸发器2a、2b的入口之前(上游),以在液体制冷剂引入到蒸发器的入口之前预加热所述液体制冷剂。预加热所述液体制冷剂所需的能量可以由系统内部的源(例如,离开冷凝器8的被加热的制冷剂)提供,如图1所示。还可以提供蒸发器进料泵16,以提供迫使制冷剂通过蒸发器热交换器所需的额外能量。根据一个实施例,蒸发器进料泵可以被选择和构造为将液体制冷剂的压力增大到100psi或更大,以防止过量的制冷剂在预加热时蒸发。
通过增大蒸发器入口处的液体制冷剂的温度,当制冷剂进入蒸发器时产生更多的蒸汽,从而减少了每吨制冷容量所需的制冷剂充量。根据优选实施例,在制冷剂引入到蒸发器入口之前对制冷剂预加热使得相对于不包括制冷剂预热器的相同系统,每吨制冷容量的制冷剂充量被减少10%至多达50%。其它实施例可以将每吨制冷容量的制冷剂充量减少20%、30%或40%。
传感器26a、26b可以位于所述蒸发器2a、2b的下游,在分离器12的入口的上游,以测量离开蒸发器的制冷剂的温度、压力和/或蒸气/液体比。根据替代实施例,传感器26c可以位于在分离器12的出口和压缩机10的入口之间的制冷剂管线中。传感器26a、26b和26c可以是在美国序列号14/221,694和14/705,781中公开的类型的电容传感器,这两个文献的公开内容通过引用整体并入本文。根据本发明的实施例,蒸发器预热器14可以由控制系统28控制,控制系统28可以用于手动或自动控制提供给流过预热器的制冷剂的预热量。根据优选实施例,控制系统28可以被构造为基于从所述传感器26a、26b和/或26c接收的、包括制冷剂温度、压力和/或液体/蒸汽比的数据,来控制施加到传送给蒸发器的制冷剂的预热量。
Claims (14)
1.一种液体过量供给制冷系统,包括:
制冷剂蒸发器,
制冷剂压缩机,
制冷剂冷凝器,
膨胀装置,和
制冷剂预热器,所述制冷剂预热器位于所述制冷剂蒸发器的进口之前,并且构造成在液体制冷剂进入所述蒸发器之前将所述液体制冷剂加热到所述蒸发器的工作温度和所述冷凝器的工作温度之间的差的10%至80%的温度,
其中所述预热器将制冷剂充量与制冷容量的比率降低至少10%。
2.根据权利要求1所述的制冷系统,其中所述制冷剂预热器是热交换器。
3.根据权利要求2所述的制冷系统,其中用于所述预热器热交换器的热源是来自所述制冷剂冷凝器的加温的制冷剂液体。
4.根据权利要求1所述的制冷系统,进一步包括构造成将离开所述蒸发器的液体和蒸气制冷剂分离开的分离器元件。
5.根据权利要求1所述的制冷系统,进一步包括位于所述蒸发器的上游的蒸发器进料泵。
6.根据权利要求1所述的制冷系统,进一步包括除霜系统。
7.根据权利要求1所述的制冷系统,其中所述蒸发器、压缩机、冷凝器、膨胀装置和预热器连接在制冷剂流动路径中。
8.一种制冷系统,包括:
具有入口和出口的制冷剂蒸发器,
具有入口、蒸汽出口和液体出口的液体/蒸汽分离器;
具有入口和出口的制冷剂压缩机;
具有入口和出口的制冷剂冷凝器,
具有入口和出口的膨胀装置,和
制冷剂预热器,所述制冷剂预热器具有入口和设置在所述制冷剂蒸发器的入口之前的出口;
其中所述蒸发器、分离器、压缩机、冷凝器、预热器和膨胀装置经由制冷剂管线连接在一个或多个制冷剂流动路径中。
9.根据权利要求8所述的制冷系统,其中所述系统是液体过量供给系统。
10.一种用于减少制冷系统蒸发器的制冷剂充量的方法,包括在将液体制冷剂引入到所述蒸发器的入口之前预加热所述液体制冷剂。
11.根据权利要求9所述的方法,进一步包括在所述蒸发器的入口处测量所述制冷剂的特性,并且基于所述测量的特性调节所述预加热的量。
12.根据权利要求10所述的方法,其中在将所述制冷剂引入到所述蒸发器的入口之前对所述制冷剂的所述预加热使每吨制冷容量的制冷剂充量减少10%或者更多。
13.根据权利要求12所述的方法,其中在将所述制冷剂引入到所述蒸发器的入口之前对所述制冷剂的所述预加热使每吨制冷容量的制冷剂充量减少30%或者更多。
14.根据权利要求10所述的方法,包括加热所述液体制冷剂,以转化10%至30%的制冷剂蒸汽。
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Citations (5)
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US3164973A (en) * | 1963-03-28 | 1965-01-12 | John E Watkins | Refrigerating systems |
US3664150A (en) * | 1970-12-30 | 1972-05-23 | Velt C Patterson | Hot gas refrigeration defrosting system |
US3967782A (en) * | 1968-06-03 | 1976-07-06 | Gulf & Western Metals Forming Company | Refrigeration expansion valve |
CN101984880A (zh) * | 2010-10-29 | 2011-03-16 | 浙江大学 | 基于扩散吸收式制冷的恒温恒湿系统 |
CN102865155A (zh) * | 2011-06-22 | 2013-01-09 | 曼卡车和巴士股份公司 | 用于回收热量并且将其转换成机械功率的方法和装置 |
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US5544496A (en) * | 1994-07-15 | 1996-08-13 | Delaware Capital Formation, Inc. | Refrigeration system and pump therefor |
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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
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US3164973A (en) * | 1963-03-28 | 1965-01-12 | John E Watkins | Refrigerating systems |
US3967782A (en) * | 1968-06-03 | 1976-07-06 | Gulf & Western Metals Forming Company | Refrigeration expansion valve |
US3664150A (en) * | 1970-12-30 | 1972-05-23 | Velt C Patterson | Hot gas refrigeration defrosting system |
CN101984880A (zh) * | 2010-10-29 | 2011-03-16 | 浙江大学 | 基于扩散吸收式制冷的恒温恒湿系统 |
CN102865155A (zh) * | 2011-06-22 | 2013-01-09 | 曼卡车和巴士股份公司 | 用于回收热量并且将其转换成机械功率的方法和装置 |
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