CN1193200C - 一种制冷***用转子压缩-膨胀机 - Google Patents
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Abstract
一种制冷***用转子压缩-膨胀机,其工作腔由内转子与外转子组成,内转子驱动外转子运动,外转子安装在一个筒形壳体内,压缩机与膨胀机的内转子安装在同一轴上,进、排气孔设在筒体或端盖上,压缩机与膨胀机的内外转子径向尺寸相同,轴向尺寸根据压缩机与膨胀机的容量特性或优化设计确定,压缩机可根据需要设计成一级压缩或两级压缩。整个压缩机-膨胀机结构加工、安装工艺简单、结构紧凑,同时该结构力平衡性能好,能够承受高压,满足二氧化碳两级压缩、一级膨胀的制冷***的要求,提高二氧化碳跨临界制冷循环的热力性能。
Description
一、技术领域
本发明涉及一种高效空调与制冷***,特别涉及一种制冷***用转子压缩-膨胀机。
二、背景技术
二氧化碳作为制冷剂使用的历史已有100多年,曾用于船用冷冻装置、制冰以及其他食品冷冻装置,还包括空调***。二十世纪八十年代,挪威的Lorentzen和Pettersen等研制了利用二氧化碳为工质的汽车空调器样机,并开展了一系列研究,再次引起人们对二氧化碳作为制冷工质的兴趣。
二氧化碳作为制冷剂其优点在于,曾经作为制冷剂使用较长时间,无毒,没有可燃性(事实上是性能优良的灭火剂),价格便宜、来源丰富、无须回收,能与普通润滑油相溶,容积制冷量约是氟利昂22的5倍,因此,相同制冷量时,压缩机的气缸容积减小很多,而且压缩比小。二氧化碳作为制冷剂的缺点是***的工作压力高,最高压力达到10Mpa(100bar),甚至更高。由于二氧化碳的临界温度低,因此,制冷循环采用跨临界制冷循环(trans-critical cycle)。目前关于二氧化碳制冷剂的研究主要集中在采用跨临界制冷循环的汽车空调***(顾兆林,压缩式制冷技术的新进展-制冷工质的环境效应及其特点,流体机械,Vol.29(10),2001)。
由于二氧化碳跨临界制冷***中冷却器与蒸发器之间的压力差很大,可以利用一个膨胀机回收其压力能,进一步提高制冷性能,例如相同的蒸发温度下,两级压缩、一级膨胀的***其性能COP达到3.97,高于现有氟利昂22的COP(3.88),而两级压缩直接膨胀的***其性能COP只有2.89(M.S.Zhu,L.Shi,Researches on the CO2 transcritical R/AC/HP systems inChina,Proceedings of the 5th IIR-Gustav Lorentzen conference on naturalworking fluids at Guangzhou,China,September 17-20,2002)
将二氧化碳两级压缩、一级膨胀的***推向实用,关键是压缩机与膨胀机的结构问题,一般的方案可以是往复式压缩机与往复式膨胀机,也可以有采用涡旋式压缩机与涡旋式膨胀机,但上述两种结构方案整体结构与技术要求均比较复杂,工程应用难度很大,必须有新的压缩机与膨胀机的一体化结构,才能解决目前的二氧化碳两级压缩、一级膨胀制冷***的关键问题
三、发明内容
本发明的目的在于克服压缩机与膨胀机的一体化结构的不足之处,提出了一种二氧化碳两级压缩、一级膨胀制冷***用转子压缩-膨胀机。
为达到上述目的,本发明采用的技术方案是:包括与电机相连接的旋转轴,在旋转轴上依次设置有左端盖、左隔板、右隔板和右端盖,其特点是,在旋转轴上的左端盖、左隔板、右隔板和右端盖之间还设置有花瓣形内转子和外转子,左端盖与内转子、外转子、左隔板以及I级筒体共同组成了一级压缩机,左隔板与内转子、外转子、右隔板以及II级筒体共同构成了二级压缩机,右隔板、内转子、外转子、右端盖以及膨胀机筒体共同构成了膨胀机,内转子与外转子啮合且构成了吸气区和排气区,吸气区和排气区分别与一级压缩机、二级压缩机和膨胀机的吸气孔和排气孔相连通,且在左端盖上开设有一级压缩机的吸气孔和排气孔,一级压缩机的吸气孔经管道与蒸发器的出口相连通,一级压缩机的排气孔经管道与中间冷却器的进气端相连通,中间冷却器的排气端经管道与二级压缩机的吸气孔相连通,二级压缩机的排气孔经管道与冷却器的进气端相连通,冷却器的排出端经管道与膨胀机的吸入孔相连通,膨胀机的排出孔经管道与中间冷却器另一进气端相连通,中间冷却器另一排气端经管道与蒸发器的吸入口相连通。
本发明的另一特点是:内转子型线由短幅外摆线的等距线构成,外转子由三段圆弧构成;一级压缩机、二级压缩机和膨胀机的径向尺寸相同、轴向尺寸不同;一级压缩机的吸气孔、排气孔分别设置在左端盖上;二级压缩机的吸气孔、排气孔分别设置在左隔板和右隔板上;膨胀机的吸入孔和排出孔分别设置在端盖右隔板和端盖右端盖上。
由于本发明采用压缩机与膨胀机同轴安装,径向尺寸一致,主要零部件相同,因此,整个压缩机-膨胀机结构加工、安装工艺简单、结构紧凑,同时该结构力平衡性能好,能够承受高压,很好地满足了二氧化碳两级压缩、一级膨胀的制冷***的要求。
四、附图说明
图1是本发明制冷***的流程原理图;
图2是本发明两级压缩、一级膨胀的结构原理图;
图3是本发明内外转子啮合形成的工作腔以及进气区、排气区的结构示意图。
五、具体实施方式
下面结合附图对本发明的结构原理和工作原理作进一步详细说明。
参见图1,2,本发明包括与电机1相连接的旋转轴15,在旋转轴15上依次设置有左端盖18、左隔板17、右隔板19和右端盖20,在旋转轴15上的左端盖18、左隔板17、右隔板19和右端盖20之间还设置有花瓣形内转子11和外转子12,左端盖18与内转子11、外转子12、左隔板17以及I级筒体16共同组成了一级压缩机21,左隔板17与内转子11、外转子12、右隔板19以及II级筒体24共同构成了二级压缩机22,右隔板19、内转子11、外转子12、右端盖20以及膨胀机筒体25共同构成了膨胀机23,内转子11与外转子12啮合且构成了吸气区13和排气区14,吸气区13和排气区14分别与一级压缩机21、二级压缩机22和膨胀机23的吸气孔和排气孔连通,一级压缩机21的吸气孔2经管道与蒸发器10的出口相连通,一级压缩机21的排气孔3经管道与中间冷却器4一进气端相连通,中间冷却器4一排气端经管道与二级压缩机22级的吸气孔5相连通,二级压缩机22的排气孔6经管道与冷却器7进气端相连通,冷却器7排出端经管道与膨胀机23的吸入孔8相连通,膨胀机23的排出孔9经管道与中间冷却器4另一进口相连通,中间冷却器4另一排出口经管道与蒸发器10的吸入口相连通。
参见图2,本发明径向尺寸相同、不同轴向尺寸的一级压缩机21、二级压缩机22和膨胀机23,它们的内转子11共同安装在旋转轴15上,旋转轴15与电机1相连接,而外转子12分别封装在I级筒体16、II级筒体21和膨胀机筒体22内,端部有左端盖18,一级压缩机21的吸气孔2、排气孔3分别设置在左端盖18上,二级压缩机22的吸气孔5、排气孔6分别设置在左隔板17和右隔板19上,膨胀机23的吸入孔8和排出孔9分别设置在右隔板19和右端盖20上。
参见图3,本发明的内转子11为花瓣形,内转子11与外转子12啮合,构成工作腔以及吸气区13与排气区14,内转子11型线由短幅外摆线的等距线构成,外转子12由三段圆弧构成。
本发明的工作原理如下:内转子11与外转子12啮合,装在I级筒体16、II级筒体24和膨胀机筒体25内、并与左隔板17、右隔板19、右端盖20和左端盖18相互固定连接共同构成一级压缩机21、二级压缩机22和膨胀机24,内转子11与旋转轴15及电机1相连,电机1驱动内转子11转动,内转子11带动外转子12转动,完成一级压缩机21和二级压缩机22的吸气-压缩-排气的连续过程;膨胀机23的作功通过旋转轴15传递给一级压缩机21和二级压缩机22,减少电机1驱动功率。
一级压缩机21、二级压缩机22和膨胀机23组合在一起,控制整个制冷***工质的流动,实现制冷目的。具体的工质流动过程如下:蒸发器10的低温低压蒸汽,经管道与吸气孔2被一级压缩机21吸入,经过压缩,温度与压力升高,由一级压缩机21的排气孔3经管道进入中间冷却器4冷却,冷却后的气体经管道与二级压缩机22的吸气孔5被二级压缩机22吸入,再次经过压缩,变成高压气体,由二级压缩机22的排气孔6经管道进入冷却器7冷却,变成高压液体,高压液体由冷却器7排出端经管道与膨胀机23的吸入孔8相连进入膨胀机23膨胀作功,变成中间温度、压力的气液两相混合物由膨胀机23的排出孔9经管道与中间冷却器4的另一进气端进入中间冷却器4,并冷却一级压缩机21的排气,气液两相混合物的液相在进一步降低压力后,经管道进入蒸发器10,吸收热量成为低温低压蒸汽。
一级压缩机21与二级压缩机22压缩需要的动力一部分来自膨胀机23的膨胀功,其余由电机1输入。
Claims (6)
1、一种制冷***用转子压缩-膨胀机,包括与电机[1]相连接的旋转轴[15],在旋转轴[15]上依次设置有左端盖[18]、左隔板[17]、右隔板[19]和右端盖[20],其特征在于:在旋转轴[15]上的左端盖[18]、左隔板[17]、右隔板[19]和右端盖[20]之间还设置有花瓣形内转子[11]和外转子[12],左端盖[18]与内转子[11]、外转子[12]、左隔板[17]以及I级筒体[16]共同组成了一级压缩机[21],左隔板[17]与内转子[11]、外转子[12]、右隔板[19]以及II级筒体[24]共同构成了二级压缩机[22],右隔板[19]、内转子[11]、外转子[12]、右端盖[20]以及膨胀机筒体[25]共同构成了膨胀机[23],内转子[11]与外转子[12]啮合且构成了吸气区[13]和排气区[14],吸气区[13]和排气区[14]分别与一级压缩机[21]、二级压缩机[22]和膨胀机[23]的吸气孔和排气孔相连通,且在左端盖[18]上开设有一级压缩机[21]的吸气孔[2]和排气孔[3],一级压缩机[21]的吸气孔[2]经管道与蒸发器[10]的出口相连通,一级压缩机[21]的排气孔[3]经管道与中间冷却器[4]的进气端相连通,中间冷却器[4]的排气端经管道与二级压缩机[22]的吸气孔[5]相连通,二级压缩机[22]的排气孔[6]经管道与冷却器[7]的进气端相连通,冷却器[7]的排出端经管道与膨胀机[23]的吸入孔[8]相连通,膨胀机[23]的排出孔[9]经管道与中间冷却器[4]另一进气端相连通,中间冷却器[4]另一排气端经管道与蒸发器[10]的吸入口相连通。
2、根据权利要求1所述的制冷***用转子压缩-膨胀机,其特征在于:所说的内转子[11]型线由短幅外摆线的等距线构成,外转子[12]由三段圆弧构成。
3、根据权利要求1所述的制冷***用转子压缩-膨胀机,其特征在于:所说的一级压缩机[21]、二级压缩机[22]和膨胀机[23]的径向尺寸相同、轴向尺寸不同。
4、根据权利要求1所述的制冷***用转子压缩-膨胀机,其特征在于:所说的一级压缩机[21]的吸气孔[2]、排气孔[3]分别设置在左端盖[18]上。
5、根据权利要求1所述的制冷***用转子压缩-膨胀机,其特征在于:所说的二级压缩机[22]的吸气孔[5]、排气孔[6]分别设置在左隔板[17]和右隔板[19]上。
6、根据权利要求1所述的制冷***用转子压缩-膨胀机,其特征在于:所说的膨胀机[23]的吸入孔[8]和排出孔[9]分别设置在端盖右隔板[19]和端盖右端盖[20]上。
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CNB021455244A CN1193200C (zh) | 2002-12-16 | 2002-12-16 | 一种制冷***用转子压缩-膨胀机 |
KR1020057001677A KR100677513B1 (ko) | 2002-12-16 | 2003-04-25 | 냉동시스템 및 그 압축기 |
AU2003222502A AU2003222502A1 (en) | 2002-12-16 | 2003-04-25 | Refrigeration system and compressor thereof |
PCT/KR2003/000846 WO2004055451A1 (en) | 2002-12-16 | 2003-04-25 | Refrigeration system and compressor thereof |
US10/539,053 US20060123838A1 (en) | 2002-12-16 | 2003-04-25 | Refrigeration system and compressor thereof |
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CNB021455244A CN1193200C (zh) | 2002-12-16 | 2002-12-16 | 一种制冷***用转子压缩-膨胀机 |
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CN1193200C true CN1193200C (zh) | 2005-03-16 |
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US (1) | US20060123838A1 (zh) |
KR (1) | KR100677513B1 (zh) |
CN (1) | CN1193200C (zh) |
AU (1) | AU2003222502A1 (zh) |
WO (1) | WO2004055451A1 (zh) |
Cited By (1)
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CN101893349A (zh) * | 2010-06-25 | 2010-11-24 | 蔡茂林 | 双缸往复式压力能回收热泵机构 |
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KR101128791B1 (ko) * | 2004-10-14 | 2012-03-26 | 엘지전자 주식회사 | 기어타입 압축기 |
EP1853856A1 (en) | 2005-02-18 | 2007-11-14 | Carrier Corporation | Co2-refrigeration device with heat reclaim |
CN1307394C (zh) * | 2005-05-23 | 2007-03-28 | 西安交通大学 | 一种压缩-膨胀机的制备方法 |
AT504564B1 (de) * | 2006-11-23 | 2008-09-15 | Stojec Mario Paul | Wärmepumpe |
KR100858431B1 (ko) * | 2007-06-22 | 2008-09-16 | 주식회사 대우일렉트로닉스 | 냉장고의 냉동 시스템 및 제어방법 |
JP4422208B2 (ja) * | 2007-11-21 | 2010-02-24 | パナソニック株式会社 | 膨張機一体型圧縮機 |
CN101251310B (zh) * | 2008-03-07 | 2010-06-02 | 西安交通大学流体机械及压缩机国家工程研究中心 | 用于制冷循环的膨胀机 |
CN103615824B (zh) * | 2013-12-06 | 2016-08-17 | 东南大学常州研究院 | 一种基于膨胀功回收驱动的多温区冷量获取方法及装置 |
CN103868266B (zh) * | 2014-03-23 | 2016-05-18 | 龚炳新 | 新型节能制冷设备 |
BE1021899B1 (nl) * | 2014-05-19 | 2016-01-25 | Atlas Copco Airpower, Naamloze Vennootschap | Inrichting voor het comprimeren en het expanderen van gassen en werkwijze voor het regelen van de druk in twee netten met een verschillend nominaal drukniveau |
CN107313819A (zh) * | 2017-05-18 | 2017-11-03 | 天津大学 | 一种集成热泵和发电功能的新型热能利用*** |
CN107387169A (zh) * | 2017-08-16 | 2017-11-24 | 无锡锡压压缩机有限公司 | 一种两级螺杆膨胀机级间加热结构 |
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-
2002
- 2002-12-16 CN CNB021455244A patent/CN1193200C/zh not_active Expired - Fee Related
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2003
- 2003-04-25 AU AU2003222502A patent/AU2003222502A1/en not_active Abandoned
- 2003-04-25 WO PCT/KR2003/000846 patent/WO2004055451A1/en not_active Application Discontinuation
- 2003-04-25 KR KR1020057001677A patent/KR100677513B1/ko not_active IP Right Cessation
- 2003-04-25 US US10/539,053 patent/US20060123838A1/en not_active Abandoned
Cited By (1)
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CN101893349A (zh) * | 2010-06-25 | 2010-11-24 | 蔡茂林 | 双缸往复式压力能回收热泵机构 |
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US20060123838A1 (en) | 2006-06-15 |
CN1417478A (zh) | 2003-05-14 |
AU2003222502A1 (en) | 2004-07-09 |
KR20050034725A (ko) | 2005-04-14 |
KR100677513B1 (ko) | 2007-02-02 |
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