EP1777472A2 - Système frigorifique amélioré en expansion en plusieurs étapes - Google Patents

Système frigorifique amélioré en expansion en plusieurs étapes Download PDF

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Publication number
EP1777472A2
EP1777472A2 EP06020496A EP06020496A EP1777472A2 EP 1777472 A2 EP1777472 A2 EP 1777472A2 EP 06020496 A EP06020496 A EP 06020496A EP 06020496 A EP06020496 A EP 06020496A EP 1777472 A2 EP1777472 A2 EP 1777472A2
Authority
EP
European Patent Office
Prior art keywords
cold
under
generating fluid
compressor
cooling exchanger
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.)
Withdrawn
Application number
EP06020496A
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German (de)
English (en)
Inventor
Enzo Fornasieri
Claudio Fossati
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.)
Mondial Group Srl
Original Assignee
Mondial Group Srl
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 Mondial Group Srl filed Critical Mondial Group Srl
Publication of EP1777472A2 publication Critical patent/EP1777472A2/fr
Withdrawn legal-status Critical Current

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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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component

Definitions

  • the present invention refers to an improved refrigerating system with fractioned lamination.
  • the commercial refrigeration field particularly important given the high increase of companies linked thereto, is subjected, after years without changes, to a transition period due to the occurrence of known environmental problems, such as ozone layer reduction and greenhouse effect.
  • object of the present invention is providing an improved refrigerating system, able to improve the environmental compatibility with respect to current products.
  • Another object of the present invention is providing an improved refrigerating system which is able to use cold-generating mixtures R404A or R507 with a high efficiency increase and a reduction of the global frigorific power used with respect to similar systems belonging to the prior art.
  • COP data shown in Table 1 refer to a simple ideal thermodynamic cycle, characterised by reversible transformations, apart from iso-enthalpic lamination, which is typically irreversible, in addition to absence of overheating in steam sucked by the compressor and absence of under-cooling in liquid going out of the condenser; anyway, it can be deemed that in a real system, energy efficiency is lower for all fluids, but in about the same ratio which exists for the ideal cycle.
  • the main cause of lower performance in fluids R404A and R507 is the particular shape of the limit curve which can be seen in the diagram in FIG. 1b, which is slanted forwards and asymmetrical, different from the fluid curve shown in the diagram in FIG. 1a: such shape derives from a rather high ratio between fluid specific heat and latent vaporisation heat, and implies a low overheating value as regards compression.
  • This is the main reason why the mentioned fluids are typically used in commercial refrigeration, but such positive characteristic is accompanied by an increase of energy loss in lamination process, graphically shown by the trapezoid-like area which contains the iso-enthalpic lamination transformation.
  • the classic method for reducing lamination losses is the fractioned lamination, characteristic of the two-stage refrigerating cycle, which is typically realised by the system 20, schematically shown in FIG 2, equipped, as known, of an intermediate separator ("open flash tank") 25 arranged between a first lamination stage, comprising in line an evaporator 21 and a low-pressure compressor 23, and a second lamination stage, comprising in line a high-pressure compressor 27 and a condenser 29.
  • an intermediate separator open flash tank
  • deriving from the intermediate separator 25 the steam developed in the first lamination stage and compressing it at the condensation pressure with the high-pressure compressor 27 means avoiding the further expansion of this amount of steam up to the evaporation pressure, such operation not adding a refrigerating effect, but increasing the low-pressure compressor 23 work.
  • a two-stage refrigerating system 30, as schematically shown in FIG. 3, is preferred to such system 20, due to its simple arrangement and lower costs, such system 30 being equipped with a "compound” compressor 33 and a under-cooling exchanger 35 arranged in parallel between evaporator 31 and condenser 37; as known, a “compound” compressor is a single compressor using part of the cylinders as low pressure stage and part as high pressure stage.
  • the system 10 comprises at least one main circuit 16 of a first cold-generating fluid and at least one auxiliary circuit 18 of a second cold-generating fluid, the main circuit 16 comprising in line at least one evaporator 12, at least one compressor 15, at least one first condenser 13 and at least one under-cooling exchanger 17, and the auxiliary circuit 18 comprising in line at least one auxiliary compressor 19, at least one second condenser 14 and at least the under-cooling exchanger 17, operating as evaporator for the auxiliary circuit 18; as realised, the system 10 advantageously allows performing the fractioned lamination with reliable and low-cost technologic solutions, also for systems with small potentiality.
  • Table 2 includes the main performance data of the system 10 according to the present invention when Evap. T. of the auxiliary circuit coincides with Und. Liq. T. and percentage COP increases obtained for an ideal cycle (defined similar to the one in FIG. 1a and 1b) depending on different operating conditions, together with the percentage reduction of the sum of volumes sucked by compressors 15 and 19, with respect to sucked volume in traditional cycles.
  • the first cold-generating fluid and the second cold-generating fluid could both have mixture HFC R404A.
  • the reference to R404A is due to peculiarities of the commercial sector towards which the system 10 is mainly aimed and the obtained benefits.
  • other refrigerating agents can be used, with different benefits depending on fluid and application type.
  • Table 4 includes performance data of the system 10 operating with other refrigerating agents used for the commercial refrigeration (for Auxiliary Circuit Evaporation T. equal to Under-Cooled Liquid T.).
  • Table 4 Condensation Temperature 40°C Fluids R404A R507 R134a R290 Evaporation T. [°C] -30.00 -30.00 -30.00 Under-Cooled Liquid T.
  • the first and second condensers 13 and 14 could be integrated in a same battery 11, possibly winged, composed of separate circuits respectively for main circuit 16 and auxiliary circuit 18, cooling side; with the same refrigerating power, its exchange surface is anyway less that the one of the reference system, since heat to be globally discharges to the outside is less, due to the COP increase effect.
  • the cost of the two compressors 15, 19 can be less that the cost of the single compressor used in the conventional cycle; the auxiliary compressor 19 in fact is a compressor for medium temperature service and implies a reduced cost, above all when mass-produced components are used; for such compressor, it could be convenient, both from the energy efficiency and from the costs points of view, to use a different fluid from 404A, for example R134a.
  • thermodynamic cycle realised as an example with the system 10 according to the present invention is its applicability independently from the efficiency of basic components, which compose the system 10 itself. Therefore, developments in the components, as normally occurs for example for compressors, do not imply a smaller advantage for the proposed cycle, in percentage terms with respect to the basic cycle.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP06020496A 2005-10-18 2006-09-29 Système frigorifique amélioré en expansion en plusieurs étapes Withdrawn EP1777472A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITTO20050738 ITTO20050738A1 (it) 2005-10-18 2005-10-18 Impianto frigorifero a laminazione frazionata perfezionato

Publications (1)

Publication Number Publication Date
EP1777472A2 true EP1777472A2 (fr) 2007-04-25

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06020496A Withdrawn EP1777472A2 (fr) 2005-10-18 2006-09-29 Système frigorifique amélioré en expansion en plusieurs étapes

Country Status (2)

Country Link
EP (1) EP1777472A2 (fr)
IT (1) ITTO20050738A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3175185A1 (fr) * 2014-07-31 2017-06-07 Carrier Corporation Système de refroidissement
CN107289568A (zh) * 2017-08-18 2017-10-24 广东高而美制冷设备有限公司 一种强力制冷和快速化霜的空调热泵系统及其工作方式
CN107804142A (zh) * 2017-10-19 2018-03-16 珠海格力电器股份有限公司 一种热泵系统、电动汽车及其热泵控制方法
CN108692475A (zh) * 2018-06-08 2018-10-23 贺吉军 一种喷气增焓制冷机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107328002A (zh) * 2017-08-18 2017-11-07 广东高而美制冷设备有限公司 一种温控节流的空调热泵系统及其工作方式

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3175185A1 (fr) * 2014-07-31 2017-06-07 Carrier Corporation Système de refroidissement
CN107289568A (zh) * 2017-08-18 2017-10-24 广东高而美制冷设备有限公司 一种强力制冷和快速化霜的空调热泵系统及其工作方式
CN107804142A (zh) * 2017-10-19 2018-03-16 珠海格力电器股份有限公司 一种热泵系统、电动汽车及其热泵控制方法
CN107804142B (zh) * 2017-10-19 2023-08-08 珠海格力电器股份有限公司 一种热泵系统、电动汽车及其热泵控制方法
CN108692475A (zh) * 2018-06-08 2018-10-23 贺吉军 一种喷气增焓制冷机

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Publication number Publication date
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