EP0409000B1 - A dual-operation mode air conditioning apparatus - Google Patents

A dual-operation mode air conditioning apparatus Download PDF

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Publication number
EP0409000B1
EP0409000B1 EP90112829A EP90112829A EP0409000B1 EP 0409000 B1 EP0409000 B1 EP 0409000B1 EP 90112829 A EP90112829 A EP 90112829A EP 90112829 A EP90112829 A EP 90112829A EP 0409000 B1 EP0409000 B1 EP 0409000B1
Authority
EP
European Patent Office
Prior art keywords
line
heat exchanger
heating mode
flexible line
cooling mode
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.)
Expired - Lifetime
Application number
EP90112829A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0409000A1 (en
Inventor
Giovanni Redaelli
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.)
Delchi Carrier SpA
Original Assignee
Delchi Carrier SpA
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 Delchi Carrier SpA filed Critical Delchi Carrier SpA
Publication of EP0409000A1 publication Critical patent/EP0409000A1/en
Application granted granted Critical
Publication of EP0409000B1 publication Critical patent/EP0409000B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25B41/40—Fluid line arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/007—Compression machines, plants or systems with reversible cycle not otherwise provided for three pipes connecting the outdoor side to the indoor side with multiple indoor units

Definitions

  • This invention relates to an air-conditioner refrigerating apparatus comprising two separate units intended, the one for installation within a room to be air conditioned and the other for outdoor installation.
  • the invention relates to an air-conditioner refrigerating apparatus having dual operation mode features, i.e. a cooling mode and a heating mode by reversal of the thermal fluid flow, according to the precharacterizing part of Claim 1 (see DE-A-2 826 813 and US-A-2 388 314).
  • Apparatus of this general type have been known and used especially as portable air conditioners, that is air conditioners for non-permanent installation. In this case, much valued is indeed the possibility they afford of installing them without bores having to be provided through the window panes, it being sufficient that a window be kept ajar or that a cutout be formed in the window frame and/or jamb for the connection element.
  • connection element is provided, in fact, in the form of a thick flattened cable. It has an outer sleeve enclosing the electrical connections (three electrical cables), the two-way refrigerating liquid lines (two lines), and usually a drain line for taking to the outdoor heat exchanger the condensation water which forms over the indoor heat exchanger during operation in the cooling mode.
  • the direction of flow of the thermal fluid is just reversed.
  • the flow direction is from the compressor to the outdoor heat exchanger (which then operates as the system condenser), the expansion device, in indoor heat exchanger (which operates then as the evaporator), and back to the compressor;
  • the flow direction is from the compressor to the indoor heat exchanger (then operating as the system condenser) to the expansion device, the outdoor heat exchanger (then operating as the evaporator), and back to the compressor.
  • connection ducts comprise three flexible lines within the connection element, namely a main flexible line for the thermal fluid to flow between the outdoor heat exchanger and the compressor in either directions, a heating mode flexible line for conveying the thermal fluid flow from the indoor heat exchanger to the outdoor heat exchanger during operation in the heating mode, and a cooling mode flexible line for conveying the thermal fluid flow from the outdoor heat exchanger to the indoor heat exchanger during operation in the cooling mode.
  • the main flexible line is located adjacent to the heating mode flexible line and at a spacing from the cooling mode flexible line.
  • the flexible connection element comprises a sleeve defining two separate longitudinal cavities, with the main and heating mode flexible lines housed within one of the cavities and the cooling mode flexible line housed in the other of said cavities.
  • a refrigerating apparatus for air conditioning being of a type which can operate in a dual mode (i.e , either in the cooling or heating modes).
  • the apparatus 1 comprises an indoor unit 2, an outdoor unit 3, and a flexible connection element 4 extending between the indoor unit 2 and the outdoor unit 3.
  • the indoor unit 2 comprises an indoor heat exchanger 5 having conventional air forcing means, only shown schematically at 6 in the drawings, associated therewith.
  • the indoor unit 2 further comprises a compressor 7 and a change-over valve 8, as well as a line 9 between the change-over valve 8 and the indoor heat exchanger 5, a line 10 between the indoor heat exchanger 5 and the connection element 4, a line 11 between the change-over valve 8 and an intake port 12 of the compressor 7, a line 13 between the change-over valve 8 and a delivery port 14 of the compressor 7, and a line 15 between the change-over valve 8 and the connection element 4.
  • the outdoor unit 3 comprises an outdoor heat exchanger 16, having conventional air forcing means associated therewith, as only shown schematically at 17 in the drawings.
  • the outdoor unit 3 also comprises two lines 18 and 19 extending between the outdoor heat exchanger 16 and the connection element 4.
  • the line 10 in the indoor unit 2 and line 18 in the outdoor unit 3, leading to the connection element 4, are both split, the former into two sub-lines 20 and 21 and the latter into two sub-lines 22 and 23.
  • the sub-line 21 includes a one-way valve 24 which only allows the thermal fluid to flow toward the line 10
  • the sub-line 22 includes a one-way valve 25 which only allows the thermal fluid to flow toward the line 18.
  • connection element 4 comprises a sleeve or outer sheath 26 having two longitudinal cavities 27 and 28 defined therein which are separated by a partition 29.
  • connection element 4 further comprises a main flexible line or duct 32 connected, at one end, to the line 15 of the indoor unit 2, and at the other end, to the line 19 going to the outdoor unit 3; a heating mode flexible line or duct 33 connected, at one end, to the sub-line 20 of the indoor unit 2, and at the other end, to the sub-line 22 of the outdoor unit 3; and a cooling mode flexible line or duct 34 connected, at one end, to the sub-line 21 of the indoor unit 2, and at the other end, to the sub-line 23 of the outdoor unit 3.
  • the main flexible line 32 is formed essentially by a pipe positioned inside the cavity 27 in the sleeve 26; the heating mode flexible line 33 consists instead of at least one capillary tube, preferably two capillary tubes placed in parallel with each other within the cavity 27, and therefore at a location substantially adjacent to the main line 32.
  • the cooling mode flexible line 34 also consists of at least one capillary tube, preferably two capillary tubes in parallel, positioned inside the cavity 28, that is at a location substantially removed from the main flexible line 32.
  • the switching or change-over valve 8 When the apparatus is operated as a cooler, i.e. in the cooling mode, the switching or change-over valve 8 is set to communicate the line 13 to the line 15, and the line 9 to the line 11. In this way, the following circuit is established for the thermal fluid in this order: compressor 7, line 13, line 15, main flexible line 32, line 19, outdoor heat exchanger 16, line 18, sub-line 23, cooling mode flexible line 34, sub-line 21, line 10, indoor heat exchanger 5, line 9, line 11, compressor 7.
  • the one-way valve 25 in the sub-line 22 will cut off the heating mode flexible line 33.
  • the thermal fluid undergoes the following thermodynamic cycle in the cooling mode.
  • the thermal fluid will enter at dry saturated steam conditions at a temperature T1 (point A in Figure 4) and be compressed iso-entropically up to a temperature T4 (segment AB). Under this condition of superheated steam (point B), the thermal fluid will flow through the lines 13 and 15, the main flexible line 32, and line 19 to the outdoor heat exchanger 16.
  • the thermal fluid will give forth heat to the surroundings, to be cooled and liquefied; more specifically, vapor phase cooling would initially (segment BC) take place from temperature T4 down to temperature T3, followed by a gradual iso-thermobaric change of state at temperature T3 (segment CD), and finally by further liquid phase cooling (referred to as subcooling) from temperature T3 to temperature T2 (segment DE).
  • segment BC vapor phase cooling
  • the thermal fluid therefore, will leave the outdoor heat exchanger 16 in a liquid state subcooled to temperature T2 (point E) and flow through the lines 18 and 23 to the cooling mode flexible line 34.
  • This line 34 provides a choke, and accordingly, will serve as an expansion device wherein the thermal fluid undergoes iso-enthalpic expansion (segment EF) and be cooled down to temperature T1 and partly evaporated.
  • segment EF iso-enthalpic expansion
  • the thermal fluid will take in heat from the space to be cooled and undergo a gradual iso-thermobaric change of state (segment FA) to a condition of dry saturated steam at temperature T1 (point A). It is in this condition that the thermal fluid will flow through lines 9 and 11 to compressor 7.
  • the expansion device rather than being comprised of the capillary tubes of the cooling mode flexible line 34, were comprised of a conventional expansion valve provided on the outdoor unit 3 (e.g , on sub-line 23) or on the indoor unit 2 (e.g., on sub-line 21).
  • the expansion device incorporated to the indoor unit 2 within the cooling mode flexible line 34 there would still be thermal fluid under condition E; in the other case, within the cooling mode flexible line 34 there would be fluid under condition F, i.e. at a lower temperature T1 than temperature T2, which would aggravate the problems due to transfer of heat between lines 32 and 34.
  • the advantage may therefore be appreciated of having heat transfer between the main flexible line 32 and the cooling mode flexible line 34 prevented, which is accomplished, according to the invention, by placing the former inside the cavity 27 of sleeve 26 and the latter inside the cavity 28 of sleeve 26, that is separated by the partition 29.
  • the switching of change-over valve 8 is set to communicate line 13 with line 9, and line 15 with line 11.
  • the following circuit path is established for the thermal fluid: compressor 7, line 13, line 9, indoor heat exchanger 5, line 10, sub-line 20, heating mode flexible line 33, sub-line 22, line 18, outdoor heat exchanger 16, line 19, main flexible line 32, line 15, line 11, compressor 7.
  • the one-way valve 24 will cut off the cooling mode flexible line 34.
  • the thermal fluid undergoes the following thermodynamic cycle in the heating mode.
  • the thermal fluid will enter a condition of dry saturated steam at temperature T1 (point A) and be compressed iso-enthropically to temperature T4 (segment AB). Under this superheated steam condition (point B), the thermal fluid flows through the lines 13 and 9 to the indoor heat exchanger 5.
  • the thermal fluid will transfer heat iso-barically to the space to be heated, and hence be cooled and liquefied; specifically, vapor phase cooling (segment BC) will first take place from temperature T4 down to temperature T3, followed by a gradual iso-thermobaric change of state at temperature T3 (segment CD), and finally by further liquid phase cooling (subcooling) from temperature T3 to temperature T2 (segment DE).
  • vapor phase cooling (segment BC) will first take place from temperature T4 down to temperature T3, followed by a gradual iso-thermobaric change of state at temperature T3 (segment CD), and finally by further liquid phase cooling (subcooling) from temperature T3 to temperature T2 (segment DE).
  • the thermal fluid then exits the indoor heat exchanger 5 in a condition of subcooled liquid at temperature T2 (point E), and flows through the lines 10 and 20 to the heating mode flexible line 33.
  • This line 33 provides a choke, and accordingly, will function as an expansion device whereby the thermal fluid, in flowing through it, undergoes iso-enthalpic expansion (segment EF) and cooling to temperature T1 while evaporating in part.
  • segment EF iso-enthalpic expansion
  • T1 iso-enthalpic expansion
  • the thermal fluid will take in heat from the surroundings and undergo a gradual iso-thermobaric change of state (segment FA) to the condition of dry saturated steam at temperature T1 (point A). It is in this condition that the thermal fluid flows then through the line 19, main flexible line 32, line 15, and line 11 to the compressor 7.
  • the main flexible line will contain dry saturated steam at temperature T1 (point A), and the heating mode flexible line 33 contain liquid at temperature T2 (point E). It should be also noted that the amount of heat delivered to the space being heated is directly proportional to the length of segment BG.
  • the expansion device instead of comprising the capillary tubes of the heating mode flexible line 33, consists of a traditional expansion valve incorporated to the outdoor unit 3 (e.g. to line 18) or to the indoor unit 2 (e.g. to sub-line 21).
  • the expansion device at the outdoor unit 3 inside the heating mode flexible line 33 there would be present thermal fluid under condition E all the same; in the other case, inside the heating mode flexible line 33 there would be present fluid under condition F, that is at the same temperature T1 as that of the fluid within the main flexible line 32, thereby any transfer of heat between the lines 32 and 33 would be prevented.
  • the interior wall of cavity 27 is formed with ribs 35. These hold the line 32 suspended and prevent full contact of the line 32 with the sleeve 26, thereby preventing direct thermal exchange therebetween such as would harm the benefit from arranging the line 33 within the same cavity 27.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP90112829A 1989-07-18 1990-07-05 A dual-operation mode air conditioning apparatus Expired - Lifetime EP0409000B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT8921212A IT1231284B (it) 1989-07-18 1989-07-18 Apparecchiatura per il condizionamento dell'aria, a duplice possibilita' di funzionamento.
IT2121289 1989-07-18

Publications (2)

Publication Number Publication Date
EP0409000A1 EP0409000A1 (en) 1991-01-23
EP0409000B1 true EP0409000B1 (en) 1994-02-02

Family

ID=11178457

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90112829A Expired - Lifetime EP0409000B1 (en) 1989-07-18 1990-07-05 A dual-operation mode air conditioning apparatus

Country Status (3)

Country Link
EP (1) EP0409000B1 (it)
ES (1) ES2050889T3 (it)
IT (1) IT1231284B (it)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8290722B2 (en) 2006-12-20 2012-10-16 Carrier Corporation Method for determining refrigerant charge
US9568226B2 (en) 2006-12-20 2017-02-14 Carrier Corporation Refrigerant charge indication

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2349192A (en) * 1991-07-05 1993-02-11 Maskinfabrikken Derby A/S Heat pumping system with flow restricting tube in inner cavity of suction conduit
CN1110394A (zh) * 1994-04-04 1995-10-18 吉阿明 空气能8字循环空调机-微分冷谷管应用
JP3540075B2 (ja) * 1995-12-11 2004-07-07 松下電器産業株式会社 空気調和機
KR100593084B1 (ko) * 2004-02-16 2006-06-26 엘지전자 주식회사 에어컨 실외기의 흡입관 구조
US7472557B2 (en) 2004-12-27 2009-01-06 Carrier Corporation Automatic refrigerant charging apparatus
US7552596B2 (en) 2004-12-27 2009-06-30 Carrier Corporation Dual thermochromic liquid crystal temperature sensing for refrigerant charge indication
US7712319B2 (en) 2004-12-27 2010-05-11 Carrier Corporation Refrigerant charge adequacy gauge
US7610765B2 (en) 2004-12-27 2009-11-03 Carrier Corporation Refrigerant charge status indication method and device
US7419192B2 (en) 2005-07-13 2008-09-02 Carrier Corporation Braze-free connector utilizing a sealant coated ferrule
US9759465B2 (en) 2011-12-27 2017-09-12 Carrier Corporation Air conditioner self-charging and charge monitoring system
WO2024175373A1 (de) * 2023-02-21 2024-08-29 Schweitzer Project S.P.A. Traverse, anschlusssäule und anlage zum anschluss eines kühlgeräts an einem waterloop-system und verkaufsraum mit einer solchen anlage

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2388314A (en) * 1942-02-14 1945-11-06 Westinghouse Electric Corp Air conditioning apparatus
US2760354A (en) * 1953-12-09 1956-08-28 Lawrence P Brady Portable air conditioning unit
US2708835A (en) * 1954-01-18 1955-05-24 Joseph G Nigro Mobile and portable air conditioner
US3611743A (en) * 1969-11-19 1971-10-12 Anthony J Manganaro Room air conditioner
US4057975A (en) * 1976-09-07 1977-11-15 Carrier Corporation Heat pump system
DE2826813A1 (de) * 1978-06-19 1979-12-20 Braun Ag Nach dem waermepumpe-prinzip arbeitende klimaanlage
DE3477417D1 (en) * 1983-08-02 1989-04-27 Ronald Hallett Pipe freezing device
KR900001896B1 (ko) * 1984-05-23 1990-03-26 미쓰비시전기주식회사 히트펌프식 냉난방장치

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8290722B2 (en) 2006-12-20 2012-10-16 Carrier Corporation Method for determining refrigerant charge
US9568226B2 (en) 2006-12-20 2017-02-14 Carrier Corporation Refrigerant charge indication

Also Published As

Publication number Publication date
IT8921212A0 (it) 1989-07-18
ES2050889T3 (es) 1994-06-01
IT1231284B (it) 1991-11-28
EP0409000A1 (en) 1991-01-23

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