EP2321593B1 - Fonctionnement amélioré d'un système de réfrigération - Google Patents

Fonctionnement amélioré d'un système de réfrigération 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
Authority
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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German (de)
English (en)
Other versions
EP2321593A2 (fr
EP2321593A4 (fr
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
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP2321593A2 publication Critical patent/EP2321593A2/fr
Publication of EP2321593A4 publication Critical patent/EP2321593A4/fr
Application granted granted Critical
Publication of EP2321593B1 publication Critical patent/EP2321593B1/fr
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. Système de réfrigération (110) comprenant :
    un échangeur de chaleur haute pression (114) configuré pour absorber la chaleur du réfrigérant lorsque le réfrigérant passe à travers l'échangeur de chaleur haute pression ;
    un module économiseur (118) configuré pour recevoir un premier flux de réfrigérant (142a) et un second flux de réfrigérant (144a) dérivé du réfrigérant sortant de l'échangeur de chaleur haute pression ;
    un évaporateur (122) configuré pour évaporer le premier flux de réfrigérant ;
    une première conduite de réfrigérant (142c) s'étendant depuis l'évaporateur et configurée pour recevoir le premier flux de réfrigérant ;
    une seconde conduite de réfrigérant (144b) s'étendant depuis le module économiseur et configurée pour recevoir le second flux de réfrigérant ; caractérisé par un compresseur alternatif (112) comprenant :
    un module de cylindre principal (130) ayant une première entrée (134) raccordée à la première conduite de réfrigérant et configurée pour recevoir le premier flux de réfrigérant, diriger le premier flux de réfrigérant à travers le module de cylindre principal et faire sortir le premier flux de réfrigérant du compresseur par l'intermédiaire d'une première sortie (138) ; et
    un module de cylindre économiseur (132) ayant une seconde entrée (136) raccordée à la seconde conduite de réfrigérant et configurée pour recevoir le second flux de réfrigérant, diriger le second flux de réfrigérant à travers le module de cylindre économiseur et faire sortir le second flux de réfrigérant du compresseur par l'intermédiaire d'une seconde sortie (140) séparée de la première sortie ; et
    un dispositif de commande (128) pour commander le débit d'au moins l'un parmi le premier flux de réfrigérant et le second flux de réfrigérant ;
    une première vanne (124) dans la première conduite de réfrigérant entre l'évaporateur et le compresseur alternatif, pour commander le débit du premier flux de réfrigérant dans le compresseur alternatif ;
    une seconde vanne (126) dans la seconde conduite de réfrigérant entre le module économiseur et le compresseur alternatif, pour commander le débit du second flux de réfrigérant dans le compresseur alternatif ;
    une conduite de réfrigérant à connecteur (170) entre la première conduite de réfrigérant (142c) et la seconde conduite de réfrigérant (144b) et configurée pour effectuer au moins l'un parmi le contournement du premier flux de réfrigérant (142c) dans le module de cylindre économiseur (132) et le contournement du second flux de réfrigérant (144b) dans le module de cylindre principal (130) ; et
    une vanne (172) dans la conduite de réfrigérant à connecteur pour commander au moins l'un parmi le contournement du premier flux de réfrigérant dans le module de cylindre économiseur et le contournement du second flux de réfrigérant dans le module de cylindre principal ;
    dans lequel la vanne dans la conduite de réfrigérant à connecteur est située en aval de la vanne (126) dans la seconde conduite de réfrigérant (144b) et en amont de la vanne (124) dans la première conduite de réfrigérant (142c).
  2. Système de réfrigération selon la revendication 1, dans lequel le dispositif de commande est configuré pour fermer au moins partiellement la vanne dans la seconde conduite de réfrigérant et pour ouvrir au moins partiellement la vanne dans la conduite de réfrigérant à connecteur de sorte qu'au moins une partie du premier flux de réfrigérant s'écoule à travers la seconde conduite de réfrigérant et à travers le module de cylindre économiseur.
  3. Système de réfrigération selon la revendication 1, dans lequel le dispositif de commande est configuré pour fermer au moins partiellement la vanne dans la première conduite de réfrigérant de sorte que le premier flux de réfrigérant s'écoule à travers la seconde conduite de réfrigérant et à travers le module de cylindre économiseur.
  4. Système de réfrigération selon la revendication 1, dans lequel le dispositif de commande est configuré pour ouvrir au moins partiellement les vannes dans les première et seconde conduites de réfrigérant et pour ouvrir au moins partiellement la vanne dans la conduite de réfrigérant à connecteur de sorte qu'une partie du second flux de réfrigérant s'écoule à travers la première conduite de réfrigérant et à travers le module de cylindre principal.
  5. Procédé de fonctionnement d'un système de réfrigération (110) selon la revendication 1 configuré pour assurer un refroidissement en utilisant un réfrigérant et comportant un échangeur de chaleur haute pression (114), un module économiseur (118), un évaporateur (122) et un compresseur alternatif (112) ayant un module de cylindre principal (130) avec une première entrée (134) et une première sortie (138) et un module de cylindre économiseur (132) avec une seconde entrée (136) et une seconde sortie (140), dans lequel le module de cylindre principal et le module de cylindre économiseur ont des flux d'entrée et de sortie séparés, dans lequel le système de réfrigération comprend :
    une première conduite de réfrigérant (142c) raccordant l'évaporateur à la première entrée du module de cylindre principal du compresseur alternatif ; et
    une seconde conduite de réfrigérant (144b) raccordant le module économiseur à la seconde entrée du module de cylindre économiseur ;
    une conduite de réfrigérant à connecteur (170) entre la première conduite de réfrigérant et la seconde conduite de réfrigérant ;
    une vanne (172) dans la conduite de réfrigérant à connecteur ;
    une première vanne (124) dans la première conduite de réfrigérant ; et
    une seconde vanne (126) dans la seconde conduite de réfrigérant, dans lequel la vanne dans la conduite de réfrigérant à connecteur est située en aval de la seconde vanne et en amont de la première vanne, le procédé comprenant :
    l'écoulement du réfrigérant à travers l'échangeur de chaleur haute pression, le module économiseur, l'évaporateur et au moins l'un parmi le module de cylindre principal et le module de cylindre économiseur, dans lequel le réfrigérant sortant du module économiseur se trouve dans un flux de réfrigérant principal (142b) et un flux de réfrigérant économiseur (144b), et le flux de réfrigérant principal s'écoule à travers l'évaporateur ;
    la commande d'un flux du réfrigérant dans le module de cylindre principal du compresseur alternatif au moins en partie en fonction d'un mode de fonctionnement du système de réfrigération ; et
    la commande d'un flux de réfrigérant dans le module de cylindre économiseur du compresseur alternatif au moins en partie en fonction du mode de fonctionnement ;
    dans lequel la commande d'un flux du réfrigérant dans le module de cylindre principal comporte :
    le fait d'empêcher le flux de réfrigérant principal (142c) sortant de l'évaporateur d'entrer dans le module de cylindre principal ; et
    le fait de diriger le flux de réfrigérant principal sortant de l'évaporateur à travers le module de cylindre économiseur.
  6. Procédé selon la revendication 5, dans lequel le mode de fonctionnement dépend d'au moins l'une parmi une température de l'air ambiant (AT ; 160), une température de l'air de point de consigne (SPT ; 162), une pression (P1 ; P3 ; P5 ; 152 ; 156 ; 159) au niveau d'une entrée du compresseur alternatif et une pression (P2 ; P4 ; 154 ; 158) au niveau d'une sortie du compresseur alternatif.
  7. Procédé selon la revendication 5, dans lequel la commande d'un flux du réfrigérant dans le module de cylindre économiseur comporte le fait d'empêcher le flux de réfrigérant économiseur sortant du module économiseur d'entrer dans le module de cylindre économiseur.
  8. Procédé selon la revendication 7, comprenant en outre :
    le fait de diriger au moins une partie du flux de réfrigérant principal sortant de l'évaporateur à travers le module de cylindre économiseur.
  9. Procédé selon la revendication 7, comprenant en outre :
    le fait de diriger le flux de réfrigérant économiseur sortant du module économiseur à travers le module de cylindre principal.
EP09805559.3A 2008-08-07 2009-08-06 Fonctionnement amélioré d'un système de réfrigération Not-in-force EP2321593B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US8700808P 2008-08-07 2008-08-07
PCT/US2009/052995 WO2010017384A2 (fr) 2008-08-07 2009-08-06 Fonctionnement amélioré d'un système de réfrigération

Publications (3)

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EP2321593A2 EP2321593A2 (fr) 2011-05-18
EP2321593A4 EP2321593A4 (fr) 2014-05-28
EP2321593B1 true EP2321593B1 (fr) 2019-06-19

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EP09805559.3A Not-in-force EP2321593B1 (fr) 2008-08-07 2009-08-06 Fonctionnement amélioré d'un système de réfrigération

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US (1) US20110138827A1 (fr)
EP (1) EP2321593B1 (fr)
WO (1) WO2010017384A2 (fr)

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

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