CN1158403A - 对改进的系统工作效率的反压力控制 - Google Patents

对改进的系统工作效率的反压力控制 Download PDF

Info

Publication number
CN1158403A
CN1158403A CN96121200A CN96121200A CN1158403A CN 1158403 A CN1158403 A CN 1158403A CN 96121200 A CN96121200 A CN 96121200A CN 96121200 A CN96121200 A CN 96121200A CN 1158403 A CN1158403 A CN 1158403A
Authority
CN
China
Prior art keywords
valve
pressure
saver
compressor
winding thread
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.)
Granted
Application number
CN96121200A
Other languages
English (en)
Other versions
CN1091862C (zh
Inventor
史蒂文·J·霍尔登
约翰·A·施沃雷尔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of CN1158403A publication Critical patent/CN1158403A/zh
Application granted granted Critical
Publication of CN1091862C publication Critical patent/CN1091862C/zh
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressor (AREA)

Abstract

一常闭阀位于油分离器的下游，以保证油压足以上升到能润滑压缩机。该阀响应输出与节约器之间的压差，以便在工作包络线的限定部分上形成节流。

Description

对改进的系统工作效率的反压力控制
公知的美国专利№5,170,640揭示了一种在涡旋式油分离器与聚结器之间有一阀的油分离器。这种阀受弹簧偏压而闭合。通过作用于阀上的压缩机输入压力与输出压力之间的压差来提供打开阀的偏压。因此，输出压力必须上升到能够打开阀，从而保证在向系统提供制冷剂之前能获得足够的压力以润滑压缩机。因此，有一工况范围，在此范围内阀闭合或在部分打开位置进行节流，从而降低了系统的工作效率。
本发明使用输出压力与节约器压力而不是输入压力之间的压差作为对抗弹簧偏压的打开力。对于一些节省压缩机的结构式样，其中某些轴承处于节约器压力或处于输入与输出的中间压力，或者对一压缩机喷射中间压力的油，就最小油压的需求来说，节约器压力比输入压力更重要。对于一给定的输出-输入压差，节约器压力随卸载器状态、输入压力、系统或冷凝器的过冷却、节约器效率、系统瞬变值和压缩机制造差异变化。因此，本发明能使压缩机的输出流节流，从而降低比专利5,170,640装置小的一部分工作包络线上的系统效率，选择打开偏压以保持同样最小的输出-节约器压差。如专利5,170,640的阀一样，最好是可避免阀震颤，使得在两装置中，阀仅仅在工作包络线的一部分上进行节流，而在工作包络线的其余部分上完全打开。
本发明的一个目的是在一冷却器系统的油分离器中限制反压力。
本发明的另一个目的是减少一冷却器的工作包络线中的阀必须节流的那部分。通过本发明，就能实现将在下文描述得更清楚的这些和其它目的。
基本情况是，一控制流体流动经过一油分离器进入一制冷系统的阀具有打开偏压，该偏压的大小取决于排出与节约器压力之间的压差，而且，该阀的节流发生在工作包络线有所减小的那一部分上。
图1是采用本发明的一制冷系统的示意图；
图2是图1系统的压力对焓的曲线图；
图3是图1系统的压缩机一工作包络线例子的曲线图；以及
图4是图1系统在打开位置时的阀的放大视图。
在图1中，编号10表示一采用本发明的制冷系统。通常为螺旋式压缩机但也可为涡旋式压缩机的压缩机12向在外面的油分离器14提供高压含油的制冷剂气体。阀16控制制冷剂气体通过油分离器14流到冷凝器18。液体制冷剂从冷凝器18经过膨胀阀EV19到节约器20，然后大部分制冷剂再由节约器20通过膨胀阀22和蒸发器24到压缩机12的输入口。通常向压缩机的发动机26提供呈饱和蒸汽的气体制冷剂，以冷却发动机，然后以中间阶段的压力再混入压缩过程。此外，如下面将要详细说明的那样，节约器20通过管道28与阀16相连，从而对阀16提供与节约器压力相对应的流体压力。阀23允许旁通的节约器20以另外附加的液体制冷剂冷却发动机26。节约器20可以是一个闪蒸箱式节约器也可以是一个热交换器式节约器。
在图2中，点A代表压缩机12的输入口，线A-B代表压缩的第一阶段，线B-C-J既代表通过节约器的制冷剂流冷却发动机26又代表节约器的制冷剂流重新进入压缩机12的转子的混合过程。为简单起见，图中示出一恒压过程，尽管具有节约器侧孔的螺旋式压缩机在混合过程期间压力会上升。线C-D代表压缩过程的第二阶段，其中D代表压缩机12的输出口。线D-E代表排出气体通过油分离器14和阀16的行程。线E-F代表排出气体通过冷凝器18的行程。线F-G代表经过阀19时的膨胀作用。节约器20在H提供饱和液体，在J提供饱和蒸汽。线H-I代表经过阀22时的膨胀作用。或者，这个可由一热交换器来完成，如同一绝热闪蒸箱一样，该闪蒸箱所提供的进入冷凝器的焓的下降与效率为100％的热交换器相同。如果采用一效率为100％的热交换器节约器，排出热交换器的液体会被过冷却到F’，线F’-I就代表经过阀22时的膨胀作用。对于发动机26或压缩机12需要另外冷却的时，另外的液体则通过阀23沿线F-G膨胀，这样使点J移入双相区域。线J-C既代表气体流过发动机26时吸收了热量的气体又代表重新混合进压缩过程。
在图3中，点K至R限定了压缩机12的一个作为例子的工作包络线(operatingenvelope)。如上所述，专利5,170,640中的装置的阀通过输入与输出之间的压差克服弹簧的偏压而被打开，点K-M-O-R限定的区域代表部分工作包络线，在这个区域由于阀控制流体通过油分离器而产生节流。这个节流意味着系统的损耗。
现在参阅图1至4。阀16可以象专利5,170,640装置一样位于油分离器14之内，专利5,170,640装置的阀位于涡旋式油分离器与聚结器之间。如图所示，阀16与油分离器14的输出口14-1一起作用以控制制冷剂通过油分离器14流到制冷系统10。输出口14-1与整体的活塞筒32被一环形阀座30分开，该阀座30用作空心的差动活塞阀件34的阀座。活塞筒32的一端用板40封闭，活塞筒32的径向孔33与冷凝器18流体相连。弹簧39置于内腔42内，并对一阀的差动活塞阀件34提供一底座偏压，该底座偏压等于所需的作用在油分离器14中的油槽的相对压力。板40的孔41与管道28一起使节约器20的闪蒸箱与内腔42流体连通。在使用一热交换器式节约器的情况下，管道28与热交换器的输出口相连，热交换器的输出口又与压缩机的节约器口相连，其压力为节约器压力。
开始工作时，弹簧39会对差动阀件34加偏压在其阀座30上，从而阻碍油分离器14与冷凝器18之间的流动。由于内腔42与节约器20相连，当系统10开始工作平衡时压力会上升。随着压缩机12的排出物输入到油分离器14，孔14-1的压力迅速上升，并克服弹簧39的偏压作用在差动活塞阀件34上，使差动活塞阀件34打开。在阀16的阀件34打开之前，弹簧39的偏压保证油分离器14具有足够的压力。内腔42的压力同节约器的压力，使得压差Pd-Pe由节约器的压力以及输出压力来确定。由于在工作包络线上，节约器压力的变化比输入和输出压力的多，与弹簧39的偏压相对的压差在大部分工作包络线上能够完全打开阀16。
参阅图3，本发明用节约器压力而不是用输入压力作为压差组成部分在由L-M-N-L限定的部分工作包络线上产生调节(modulation)。由此使由K-L-N-O-R-K限定的部分工作包络线不会节流，也不会形成如果使用输入压力而不是使用节约器压力所具有的附加的损耗。点N的饱和输出的压力一般比点O的低，因为点O必须被选择为最坏条件的节约器压力，即，满负荷、系统过冷却为零、100％的节约器效率、最坏条件的系统瞬变值和压缩机制造不同的最坏条件。对于一定状态的压缩机负荷、系统过冷却和节约器效率来说，恒定的输出-节约器压差(即Pd-Pe＝常数)的线L-N的斜度比恒定的输出-输入压差(即Pd-Ps＝常数)的线R-O的大或陡。
尽管举例和描述了本发明的一较佳实施例，但其它的变化对于该领域的技术人员来讲是显而易见的。例如，阀16可放置在油分离器中，也可置于其下游。因此，本发明仅限于所附权利要求书的范围。

Claims (3)

1.一种具有一工作包络线的封闭的制冷系统，包括：一压缩机(12)，一油分离器(14)，一常闭的阀(16)，一冷凝器(18)，一节约器装置(20)和一蒸发器装置(24)，阀控制装置的特征在于所述常闭阀通过管道(28)与所述节约器装置流体相连，从而节约器的压力加偏压于所述闭合的阀，压缩机的输出压力作用在所述常闭阀，以便对所述常闭阀提供一打开偏压，所述阀通过所述阀的所述工作包络线的一限定部分提供节流，使所述工作包络线的其余部分完全打开。
2.如权利要求1所述的制冷系统，其特征在于，所述节约器装置是一个闪蒸箱节约器。
3.如权利要求1所述的制冷系统，其特征在于，所述节约器装置是一个热交换器式节约器。
CN96121200A 1995-11-13 1996-11-13 封闭的制冷系统 Expired - Fee Related CN1091862C (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US08/557,390 US5603227A (en) 1995-11-13 1995-11-13 Back pressure control for improved system operative efficiency
US08/557390 1995-11-13

Publications (2)

Publication Number Publication Date
CN1158403A true CN1158403A (zh) 1997-09-03
CN1091862C CN1091862C (zh) 2002-10-02

Family

ID=24225192

Family Applications (1)

Application Number Title Priority Date Filing Date
CN96121200A Expired - Fee Related CN1091862C (zh) 1995-11-13 1996-11-13 封闭的制冷系统

Country Status (8)

Country Link
US (1) US5603227A (zh)
EP (1) EP0773415B1 (zh)
JP (1) JP2996624B2 (zh)
KR (1) KR100192626B1 (zh)
CN (1) CN1091862C (zh)
BR (1) BR9605504A (zh)
DE (1) DE69617886T2 (zh)
ES (1) ES2170219T3 (zh)

Families Citing this family (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6141950A (en) 1997-12-23 2000-11-07 Air Products And Chemicals, Inc. Integrated air separation and combustion turbine process with steam generation by indirect heat exchange with nitrogen
US6238188B1 (en) * 1998-08-17 2001-05-29 Carrier Corporation Compressor control at voltage and frequency extremes of power supply
US6116046A (en) * 1999-03-05 2000-09-12 American Standard Inc. Refrigeration chiller with assured start-up lubricant supply
US6216474B1 (en) * 1999-09-27 2001-04-17 Carrier Corporation Part load performance of variable speed screw compressor
US6349561B1 (en) 2000-02-24 2002-02-26 Visteon Global Technologies, Inc. Refrigeration circuit for vehicular air conditioning system
US6428284B1 (en) * 2000-03-16 2002-08-06 Mobile Climate Control Inc. Rotary vane compressor with economizer port for capacity control
DE04252372T1 (de) * 2003-07-18 2005-06-23 Star Refrigeration Ltd., Glasgow Verbesserte überkritische Kältekreislaufanlage
US6941769B1 (en) 2004-04-08 2005-09-13 York International Corporation Flash tank economizer refrigeration systems
JP2006207974A (ja) * 2005-01-31 2006-08-10 Sanyo Electric Co Ltd 冷凍装置及び冷蔵庫
JP2006329557A (ja) * 2005-05-27 2006-12-07 Kobe Steel Ltd スクリュ冷凍装置
US8037710B2 (en) 2005-08-22 2011-10-18 Emerson Climate Technologies, Inc. Compressor with vapor injection system
EP2078178B1 (en) * 2006-10-26 2016-05-18 Johnson Controls Technology Company Economized refrigeration system
ES2754027T3 (es) * 2007-09-24 2020-04-15 Carrier Corp Sistema de refrigerante con línea de derivación y cámara de compresión de flujo economizado dedicada
US20090241592A1 (en) * 2007-10-05 2009-10-01 Emerson Climate Technologies, Inc. Compressor assembly having electronics cooling system and method
US7895003B2 (en) 2007-10-05 2011-02-22 Emerson Climate Technologies, Inc. Vibration protection in a variable speed compressor
US8950206B2 (en) * 2007-10-05 2015-02-10 Emerson Climate Technologies, Inc. Compressor assembly having electronics cooling system and method
US20090092502A1 (en) * 2007-10-08 2009-04-09 Emerson Climate Technologies, Inc. Compressor having a power factor correction system and method
US8418483B2 (en) 2007-10-08 2013-04-16 Emerson Climate Technologies, Inc. System and method for calculating parameters for a refrigeration system with a variable speed compressor
US8539786B2 (en) 2007-10-08 2013-09-24 Emerson Climate Technologies, Inc. System and method for monitoring overheat of a compressor
US8448459B2 (en) 2007-10-08 2013-05-28 Emerson Climate Technologies, Inc. System and method for evaluating parameters for a refrigeration system with a variable speed compressor
US8459053B2 (en) 2007-10-08 2013-06-11 Emerson Climate Technologies, Inc. Variable speed compressor protection system and method
US9541907B2 (en) 2007-10-08 2017-01-10 Emerson Climate Technologies, Inc. System and method for calibrating parameters for a refrigeration system with a variable speed compressor
US20090092501A1 (en) * 2007-10-08 2009-04-09 Emerson Climate Technologies, Inc. Compressor protection system and method
JP5091015B2 (ja) * 2008-06-09 2012-12-05 荏原冷熱システム株式会社 圧縮式冷凍機
JP5306751B2 (ja) * 2008-09-12 2013-10-02 株式会社テイエルブイ 蒸気圧縮式冷凍機
US8234877B2 (en) * 2009-07-08 2012-08-07 Trane International Inc. Compressor discharge valve providing freeze and charge migration protection
ES2855008T3 (es) 2009-12-18 2021-09-23 Carrier Corp Sistema de refrigeración de transporte y métodos para el mismo para hacer frente a las condiciones dinámicas
KR20110092147A (ko) * 2010-02-08 2011-08-17 삼성전자주식회사 공기조화기 및 그 제어방법
CN102192152A (zh) * 2010-03-09 2011-09-21 上海汉钟精机股份有限公司 用于带油分半封压缩机的压力维持阀
US8931304B2 (en) 2010-07-20 2015-01-13 Hamilton Sundstrand Corporation Centrifugal compressor cooling path arrangement
FR2980564A1 (fr) * 2011-09-23 2013-03-29 Air Liquide Procede et installation de refrigeration
ITMI20130910A1 (it) * 2013-06-03 2014-12-04 Frascold S P A Dispositivo di raffreddamento per un convertitore di frequenza, gruppo convertitore di frequenza comprendente detto dispositivo di raffreddamento e impianto di refrigerazione o condizionamento comprendente detto gruppo convertitore
ES2829828T3 (es) * 2013-07-10 2021-06-02 Carrier Corp Compresor de tornillo con orificio de economizador
CN103743157B (zh) * 2014-01-09 2016-08-31 广东美的制冷设备有限公司 压缩机系统、空调器和压缩机的回油控制方法
KR101606269B1 (ko) * 2014-07-07 2016-03-24 엘지전자 주식회사 공기조화기
JP6328269B2 (ja) * 2014-11-26 2018-05-23 三菱電機株式会社 熱源側ユニットおよび冷凍サイクル装置
JP6783579B2 (ja) 2016-08-04 2020-11-11 サンデンホールディングス株式会社 スクロール圧縮機
US11206743B2 (en) 2019-07-25 2021-12-21 Emerson Climate Technolgies, Inc. Electronics enclosure with heat-transfer element

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2155051A (en) * 1937-06-03 1939-04-18 Sulzer Ag Apparatus for the compression of gases
US3827255A (en) * 1973-03-30 1974-08-06 Murray Corp Means for preventing flow of lubricant-saturated refrigerant in automotive air-conditioning systems
US4653286A (en) * 1985-12-16 1987-03-31 Carrier Corporation Discharge valve and baffle assembly for a refrigeration system
US4938029A (en) * 1989-07-03 1990-07-03 Carrier Corporation Unloading system for two-stage compressors
US5170640A (en) * 1991-03-04 1992-12-15 Carrier Corporation Oil separator
US5134856A (en) * 1991-05-21 1992-08-04 Frick Company Oil pressure maintenance for screw compressor

Also Published As

Publication number Publication date
ES2170219T3 (es) 2002-08-01
EP0773415B1 (en) 2001-12-12
BR9605504A (pt) 1998-08-11
KR970028265A (ko) 1997-06-24
CN1091862C (zh) 2002-10-02
JP2996624B2 (ja) 2000-01-11
EP0773415A3 (en) 1997-12-29
DE69617886T2 (de) 2002-07-04
EP0773415A2 (en) 1997-05-14
KR100192626B1 (ko) 1999-06-15
US5603227A (en) 1997-02-18
DE69617886D1 (de) 2002-01-24
JPH09170827A (ja) 1997-06-30

Similar Documents

Publication Publication Date Title
CN1091862C (zh) 封闭的制冷系统
CN1091510C (zh) 制冷装置的产冷量调节方法
US8181478B2 (en) Refrigeration system
JP3053379B2 (ja) 冷凍システム
US4947655A (en) Refrigeration system
KR100353784B1 (ko) 가변 속도 스크류 압축기의 개선된 부분 부하 성능
CA1296194C (en) Refrigeration system
RU2102658C1 (ru) Устройство и способ регулирования давления в транскритическом парокомпрессионном цикле
KR0173514B1 (ko) 1단 또는 다단 작동용 압축기
US4938029A (en) Unloading system for two-stage compressors
WO2004044503A2 (en) Refrigeration system with bypass subcooling and component size de-optimization
US4369633A (en) Multiple stage compressor with flash gas injection assembly
JP2008185327A (ja) 二段配置形式のオイルオーバフロー式スクリューコンプレッサを備えたｃｏ２冷凍装置
USRE30499E (en) Injection cooling of screw compressors
CA2616211A1 (en) Refrigerant system with suction line restrictor for capacity correction
KR100209036B1 (ko) 압축기 오일 레벨 제어
JP2001272122A (ja) 二段圧縮冷凍機
JPH01169278A (ja) 液体及び気体用バイパス
US6122924A (en) Hot gas compressor bypass using oil separator circuit
JP3495899B2 (ja) スクリュ冷凍機
JPH02192559A (ja) 二元冷凍機
JPH0626714A (ja) 空気調和機の冷媒回路
JPH02287058A (ja) スクリュー冷凍機
CN106403334A (zh) 能优化控制冷水机组的压力比的制冷系统
CN115164428A (zh) 风冷冷水机组系统及其控制方法

Legal Events

Date Code Title Description
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C06 Publication
PB01 Publication
C14 Grant of patent or utility model
GR01 Patent grant
C19 Lapse of patent right due to non-payment of the annual fee
CF01 Termination of patent right due to non-payment of annual fee