EP2321593B1 - Verbesserter betrieb eines kühlsystems - Google Patents

Verbesserter betrieb eines kühlsystems Download PDF

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Publication number
EP2321593B1
EP2321593B1 EP09805559.3A EP09805559A EP2321593B1 EP 2321593 B1 EP2321593 B1 EP 2321593B1 EP 09805559 A EP09805559 A EP 09805559A EP 2321593 B1 EP2321593 B1 EP 2321593B1
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EP
European Patent Office
Prior art keywords
refrigerant
economizer
cylinder module
module
valve
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.)
Not-in-force
Application number
EP09805559.3A
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English (en)
French (fr)
Other versions
EP2321593A4 (de
EP2321593A2 (de
Inventor
Alexander Lifson
Michael F. Taras
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
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Filing date
Publication date
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Publication of EP2321593A2 publication Critical patent/EP2321593A2/de
Publication of EP2321593A4 publication Critical patent/EP2321593A4/de
Application granted granted Critical
Publication of EP2321593B1 publication Critical patent/EP2321593B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air

Definitions

  • the present invention relates to a refrigerant system having an economizer module and a reciprocating compressor. More particularly, the present invention relates to a method and system for operating the refrigerant system in various modes of loading and unloading.
  • suction pressure (P3) and discharge pressure (P4) of economizer cylinder module 32 may not be included in refrigerant system 10. Pressures (P3) and (P4) may be less significant than suction pressure (P1) and discharge pressure (P2) of main cylinder module 30, which are used to analyze conditions at evaporator 22.
  • refrigerant system 110 includes connector refrigerant line 170 located between main refrigerant line 142c and economizer refrigerant line 144b, and third valve 172 installed in connector refrigerant line 170.
  • valves 124, 126 and 172 have variable openings such that refrigerant system 110 has additional flexibility to position valves 124, 126 and 172 at an intermediate position between fully open and fully closed.
  • Refrigerant system 110 is able to operate in eight different operating modes, based on a position of valves 124, 126 and 172.
  • the operating modes are generally ordered from highest to lowest cooling capacity. For purposes of the description below, a higher level of unloading corresponds to a lower cooling capacity.
  • Four of the eight operating modes shown in Table 2 for refrigerant system 110 are feasible in refrigerant system 10 of FIG. 1 .
  • system 110 provides even greater flexibility and control for unloading, as compared to refrigerant system 10 of FIG. 1 .
  • system 110 also provides for greater cooling capacity than system 10 when the economizer cycle is not being used.
  • main cylinder module 130 Due to a limited capacity of main cylinder module 130, less cooling is provided in evaporator 122 in this mode, as compared to a mode in which all refrigerant from economizer refrigerant line 144b were flowing through economizer cylinder module 130.
  • first valve 124 is open, and second valve 126 and third valve 172 are closed.
  • This operating mode was also feasible in refrigerant system 10 and was described above as mid-level unloading in Table 1.
  • the economizer cycle is blocked in operating mode four. Because valve 172 is closed and economizer cylinder module 132 is thus not used, operating mode four provides less cooling as compared to operating mode two (i.e. full loading without economizer), and is therefore designated as an unloading mode. Additional unloading may be accomplished by partially closing first valve 124.
  • Operating modes seven and eight are not common; if refrigerant system 110 operates in either of these modes, typically it is temporary operating mode and is used to avoid shutting down refrigerant system 110. Either of modes seven and eight may be adjusted to mid-level unloading or even a low level unloading by only partially closing one of the valves designated as being closed in Table 2. For example, if valve 124 is partially closed in either operating mode seven or eight, system 110 may operate between a low and mid-level unloading, depending on a specific position of valve 124.
  • refrigerant system 110 provides superior flexibility during unloading, as well as the feasibility to achieve a greater cooling capacity when the economizer module is not being used.
  • refrigerant system 110 includes both valves 124 and 126 in combination with connector refrigerant line 170 and valve 172.
  • valve 124 or valve 126 may be eliminated.
  • economizer module 18 and 118 is a heat exchanger.
  • FIG. 3 is an alternative example in which economizer module 218 is a flash tank.
  • the refrigerant exiting the high pressure heat exchanger is split into two refrigerant streams prior to entering the economizer heat exchanger.
  • the single refrigerant stream from the high pressure heat exchanger passes through expansion device 219, where it is partially expanded to an intermediate pressure and temperature.
  • the refrigerant entering flash tank 218 is usually in a two-phase thermodynamic state.
  • float flow control device 221 is configured to open when a liquid level in the flash tank reaches a predetermined level or provide a certain restriction to a refrigerant flow to maintain a desired refrigerant level.
  • the refrigerant exiting flash tank 218 through refrigerant line 244 has low vapor and high liquid content, which enhances cooling capacity in the evaporator.
  • the refrigerant system and operating method described herein may easily be implemented into existing refrigerant systems.
  • the refrigerant systems may include supermarket refrigerant systems, container refrigerant systems, truck/trailer refrigerant systems, rooftop air conditioning and heat pump refrigerant systems, and residential air conditioning refrigerant systems.
  • the valves may be installed in existing refrigerant lines, and in some cases, a connector refrigerant line may also be added between the economizer refrigerant line and the main refrigerant line.
  • the valves and connector refrigerant line described herein may also be incorporated into the design of new refrigerant systems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Claims (9)

  1. Kühlsystem (110), Folgendes umfassend:
    einen Hochdruckwärmetauscher (114), der dazu konfiguriert ist, Wärme von einem Kühlmittel zu absorbieren, wenn das Kühlmittel durch den Hochdruckwärmetauscher läuft;
    ein Economizer-Modul (118), das dazu konfiguriert ist, eine erste Kühlmittelströmung (142a) und eine zweite Kühlmittelströmung (144a) aufzunehmen, die von dem Kühlmittel abgeleitet sind, das den Hochdruckwärmetauscher verlässt;
    einen Verdampfer (122), der dazu konfiguriert ist, die erste Kühlmittelströmung zu verdampfen;
    eine erste Kühlmittelleitung (142c), die sich von dem Verdampfer erstreckt und dazu konfiguriert ist, die erste Kühlmittelströmung aufzunehmen;
    eine zweite Kühlmittelleitung (144b), die sich von dem Economizer-Modul erstreckt und dazu konfiguriert ist, die zweite Kühlmittelströmung aufzunehmen; gekennzeichnet durch
    einen sich hin- und herbewegenden Kompressor (112), der Folgendes umfasst:
    ein Hauptzylindermodul (130), das einen ersten Einlass (134) aufweist, der mit der ersten Kühlmittelleitung verbunden und dazu konfiguriert ist, die erste Kühlmittelströmung aufzunehmen, die erste Kühlmittelströmung durch das Hauptzylindermodul zu leiten und die erste Kühlmittelströmung von dem Kompressor über einen ersten Auslass (138) abzugeben; und
    ein Economizer-Zylindermodul (132), das einen zweiten Einlass (136) aufweist, der mit der zweiten Kühlmittelleitung verbunden und dazu konfiguriert ist, die zweite Kühlmittelströmung aufzunehmen, die zweite Kühlmittelströmung durch das Economizer-Zylindermodul zu leiten und die zweite Kühlmittelströmung von dem Kompressor über einen zweiten Auslass (140), der von dem ersten Auslass getrennt ist, abzugeben; und
    eine Steuerung (128) zum Steuern von Strömen mindestens einer der ersten Kühlmittelströmung und der zweiten Kühlmittelströmung;
    ein erstes Ventil (124) in der ersten Kühlmittelleitung zwischen dem Verdampfer und dem sich hin- und herbewegenden Kompressor, um Strömen der ersten Kühlmittelströmung in den sich hin- und herbewegenden Kompressor zu steuern;
    ein zweites Ventil (126) in der zweiten Kühlmittelleitung zwischen dem Economizer-Modul und dem sich hin- und herbewegenden Kompressor, um Strömen der zweiten Kühlmittelströmung in den sich hin- und herbewegenden Kompressor zu steuern;
    eine Kühlmittelverbindungsleitung (170) zwischen der ersten Kühlmittelleitung (142c) und der zweiten Kühlmittelleitung (144b), die dazu konfiguriert ist, mindestens eines von Umleiten der ersten Kühlmittelströmung (142c) in das Economizer-Zylindermodul (132) und Umleiten der zweiten Kühlmittelströmung (144b) in das Hauptzylindermodul (130) durchzuführen; und
    ein Ventil (172) in der Kühlmittelverbindungsleitung, um mindestens eine der Umleitung der ersten Kühlmittelströmung in das Economizer-Zylindermodul und der Umleitung der zweiten Kühlmittelströmung in das Hauptzylindermodul zu steuern;
    wobei das Ventil in der Kühlmittelverbindungsleitung sich stromabwärts des Ventils (126) in der zweiten Kühlmittelleitung (144b) und stromaufwärts des Ventils (124) in der ersten Kühlmittelleitung (142c) befindet.
  2. Kühlsystem nach Anspruch 1, wobei die Steuerung dazu konfiguriert ist, das Ventil in der zweiten Kühlmittelleitung mindestens teilweise zu schließen und das Ventil in der Kühlmittelverbindungsleitung mindestens teilweise zu öffnen, sodass mindestens ein Abschnitt der ersten Kühlmittelströmung durch die zweite Kühlmittelleitung und durch das Economizer-Zylindermodul strömt.
  3. Kühlsystem nach Anspruch 1, wobei die Steuerung dazu konfiguriert ist, das Ventil in der ersten Kühlmittelleitung mindestens teilweise zu schließen, sodass die erste Kühlmittelströmung durch die zweite Kühlmittelleitung und durch das Economizer-Zylindermodul strömt.
  4. Kühlsystem nach Anspruch 1, wobei die Steuerung dazu konfiguriert ist, die Ventile in der ersten und der zweiten Kühlmittelleitung mindestens teilweise zu öffnen und das Ventil in der Kühlmittelverbindungsleitung mindestens teilweise zu öffnen, sodass ein Abschnitt der zweiten Kühlmittelströmung durch die erste Kühlmittelleitung und durch das Hauptzylindermodul strömt.
  5. Verfahren zum Betreiben eines Kühlsystems (110) nach Anspruch 1, das dazu konfiguriert ist, Kühlung unter Verwendung eines Kühlmittels bereitzustellen, und einen Hochdruckwärmetauscher (114), ein Economizer-Modul (118), einen Verdampfer (122) und einen sich hin- und herbewegenden Kompressor (112) beinhaltet, der ein Hauptzylindermodul (130) mit einem ersten Einlass (134) und einem ersten Auslass (138) und ein Economizer-Zylindermodul (132) mit einem zweiten Einlass (136) und einem zweiten Auslass (140) aufweist, wobei das Hauptzylindermodul und das Economizer-Zylindermodul getrennte Einlass- und Auslassströmungen aufweisen, wobei das Kühlsystem Folgendes umfasst:
    eine erste Kühlmittelleitung (142c), die den Verdampfer mit dem ersten Einlass des Hauptzylindermoduls des sich hin- und herbewegenden Kompressors verbindet; und
    eine zweite Kühlmittelleitung (144b), die das Economizer-Modul mit dem zweiten Einlass des Economizer-Zylindermoduls verbindet;
    eine Kühlmittelverbindungsleitung (170) zwischen der ersten Kühlmittelleitung und der zweiten Kühlmittelleitung;
    ein Ventil (172) in der Kühlmittelverbindungsleitung;
    ein erstes Ventil (124) in der ersten Kühlmittelleitung; und
    ein zweites Ventil (126) in der zweiten Kühlmittelleitung, wobei sich das Ventil in der Kühlmittelverbindungsleitung stromabwärts des zweiten Ventils und stromaufwärts des ersten Ventils befindet, wobei das Verfahren Folgendes umfasst:
    Strömen des Kühlmittels durch den Hochdruckwärmetauscher, das Economizer-Modul, den Verdampfer und mindestens einen des Hauptzylindermoduls und des Economizer-Zylindermoduls, wobei sich das Kühlmittel, das das Economizer-Modul verlässt, in einer Hauptkühlmittelströmung (142b) und einer Economizerkühlmittelströmung (144b) befindet und wobei die Hauptkühlmittelströmung durch den Verdampfer strömt;
    Steuern eines Stroms des Kühlmittels in das Hauptzylindermodul des sich hin- und herbewegenden Kompressors mindestens teilweise als eine Funktion eines Betriebsmodus des Kühlsystems; und
    Steuern eines Stroms von Kühlmittel in das Economizer-Zylindermodul des sich hin- und herbewegenden Kompressors mindestens teilweise als eine Funktion des Betriebsmodus;
    wobei das Steuern eines Stroms des Kühlmittels in das Hauptzylindermodul Folgendes beinhaltet:
    Verhindern, dass die Hauptkühlmittelströmung (142c), die den Verdampfer verlässt, in das Hauptzylindermodul eindringt; und
    Leiten der Hauptkühlmittelströmung, die den Verdampfer verlässt, durch das Economizer-Zylindermodul.
  6. Verfahren nach Anspruch 5, wobei der Betriebsmodus eine Funktion mindestens eines einer Umgebungslufttemperatur (AT; 160), einer Soll-Lufttemperatur (SPT; 162), eines Drucks (P1; P3; P5; 152; 156; 159) an einem Einlass des sich hin- und herbewegenden Kompressors und eines Drucks (P2; P4; 154; 158) an einem Auslass des sich hin- und herbewegenden Kompressors ist.
  7. Verfahren nach Anspruch 5, wobei das Steuern eines Stroms des Kühlmittels in das Economizer-Zylindermodul das Verhindern, dass die Economizerkühlmittelströmung, die das Economizer-Modul verlässt, in das Economizer-Zylindermodul eindringt, beinhaltet.
  8. Verfahren nach Anspruch 7, ferner Folgendes umfassend:
    Leiten mindestens eines Abschnitts der Hauptkühlmittelströmung, die den Verdampfer verlässt, durch das Economizer-Zylindermodul.
  9. Verfahren nach Anspruch 7, ferner Folgendes umfassend:
    Leiten der Economizerkühlmittelströmung, die das Economizer-Modul verlässt, durch das Hauptzylindermodul.
EP09805559.3A 2008-08-07 2009-08-06 Verbesserter betrieb eines kühlsystems Not-in-force EP2321593B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US8700808P 2008-08-07 2008-08-07
PCT/US2009/052995 WO2010017384A2 (en) 2008-08-07 2009-08-06 Improved operation of a refrigerant system

Publications (3)

Publication Number Publication Date
EP2321593A2 EP2321593A2 (de) 2011-05-18
EP2321593A4 EP2321593A4 (de) 2014-05-28
EP2321593B1 true EP2321593B1 (de) 2019-06-19

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EP09805559.3A Not-in-force EP2321593B1 (de) 2008-08-07 2009-08-06 Verbesserter betrieb eines kühlsystems

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EP (1) EP2321593B1 (de)
WO (1) WO2010017384A2 (de)

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JP2012233676A (ja) * 2011-04-21 2012-11-29 Denso Corp ヒートポンプサイクル
US8876650B2 (en) 2012-03-30 2014-11-04 Hamilton Sundstrand Corporation Aircraft accessory drive multiple speed transmission
CN103471275B (zh) * 2013-08-30 2017-12-19 青岛海信日立空调系统有限公司 补气增焓的空调循环系统及其控制方法
US9581985B2 (en) 2014-02-21 2017-02-28 Johnson Controls Technology Company Systems and methods for auto-commissioning and self-diagnostics
KR102240070B1 (ko) * 2014-03-20 2021-04-13 엘지전자 주식회사 공기조화기 및 그 제어방법
US9835347B2 (en) 2014-12-08 2017-12-05 Johnson Controls Technology Company State-based control in an air handling unit
DE102017115623A1 (de) * 2016-07-13 2018-01-18 Trane International Inc. Variable Economizereinspritzposition

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Also Published As

Publication number Publication date
EP2321593A4 (de) 2014-05-28
US20110138827A1 (en) 2011-06-16
WO2010017384A3 (en) 2010-05-14
WO2010017384A2 (en) 2010-02-11
EP2321593A2 (de) 2011-05-18

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