EP2916086A1 - Échangeur de chaleur et climatiseur comprenant celui-ci - Google Patents

Échangeur de chaleur et climatiseur comprenant celui-ci Download PDF

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Publication number
EP2916086A1
EP2916086A1 EP15157890.3A EP15157890A EP2916086A1 EP 2916086 A1 EP2916086 A1 EP 2916086A1 EP 15157890 A EP15157890 A EP 15157890A EP 2916086 A1 EP2916086 A1 EP 2916086A1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
circuit portions
class
circuits
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Withdrawn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
EP15157890.3A
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German (de)
English (en)
Inventor
Hiroshi Kanbara
Michiaki Nakanishi
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2916086A1 publication Critical patent/EP2916086A1/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Withdrawn legal-status Critical Current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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions

Definitions

  • the present invention relates to a heat exchanger that is suitable when R1234yf refrigerant (hydrofluoroolefin; hereinafter, also referred to simply as HFO refrigerant) having a low Global Warming Potential (GWP) is employed as a refrigerant, and to an air conditioner employing such a heat exchanger.
  • R1234yf refrigerant hydrofluoroolefin; hereinafter, also referred to simply as HFO refrigerant
  • GWP Global Warming Potential
  • R1234yf refrigerant (HFO refrigerant) is known to be a low-GWP refrigerant whose Global Warming Potential (GWP) is lower than widely employed HFC refrigerants such as R410A refrigerant, R134a refrigerant, and so forth in the related art.
  • GWP Global Warming Potential
  • Patent Literature 1 provides an invention designed to achieve a capacity equivalent to a unit employing R410A refrigerant even in the case in which HFO refrigerant is employed.
  • the fluid passage area is set so as to make refrigerant flow rates therein equal to or less than a predetermined value, or, alternatively, assuming that the inner diameter of refrigerant pipes constituting the outdoor heat exchanger is D mm, and that the number of paths thereof is P, the pipes are configured so as to satisfy the condition (3.1415 ⁇ D 2 ⁇ P)/4 ⁇ 169.3 mm 2 , so that the pressure loss at a point through which the gaseous refrigerant passes during heating will be an appropriate level of pressure loss equivalent to the case in which R410A refrigerant is employed.
  • Patent Literature 2 discloses an invention that relates to a distributor that distributes refrigerant to a plurality of heat-conducting tubes of a heat exchanger and a to refrigerator provided with that distributor, and that relates, in particular, to a distributor structure in which the number of refrigerant paths is changed in accordance with the operating conditions.
  • Patent Literature 3 discloses an invention in which, with a heat exchanger having at least two paths including N tubes divided into two sets of tubes, the amount of heat exchange is optimized by setting the ratio N1/N to 15 to 50 % when a first set of tubes includes N1 tubes between a pair of collectors and a second set of tubes includes N2 tubes between a pair of collectors.
  • Patent Literatures 1 to 3 are not designed for ensuring a high enough heat exchange performance, and therefore heating performance, by adjusting the heat transfer coefficient and pressure loss of the refrigerant by appropriately configuring the branching and collecting structure when employing a multi-circuit form, in order to compensate for the deterioration of the heating performance in the case in which HFO refrigerant is employed.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide a heat exchanger with which it is possible to ensure a high enough heat exchange performance by optimizing a heat transfer coefficient and pressure loss of a refrigerant by optimizing the configuration of branched circuits, and to provide an air conditioner employing such a heat exchanger.
  • a heat exchanger of the present invention and an air conditioner employing the same employ the following solutions.
  • a first aspect of the present invention is a heat exchanger that is a fin-tube-type heat exchanger in which HFO refrigerant is employed, and in which the refrigerant is circulated through numerous refrigerant tubes by being branched to and collected from multiple circuits, wherein a maximum number of the branched circuits among the numerous refrigerant tubes is six circuits, and, of a total number of the numerous refrigerant tubes, a proportion accounted for by a one-circuit portion and two- to four-circuit portions is set within a range from 7 to 30 % in accordance with a capacity of the heat exchanger.
  • the heat exchanger by limiting the maximum number of the branched circuits among the refrigerant tubes to six, it is possible to suppress pressure loss by ensuring a sufficient number of the branched circuits and to set the pressure loss within an appropriate range while avoiding an increase in the size of branching/collecting units, as well as the size of the heat exchanger, due to an unnecessary increase in the number of circuits.
  • the proportion accounted for by the one-circuit portion and the two- to four-circuit portions may be set within a range from 15 to 30 % in the case of a heat exchanger whose capacity is in a 2-kW to 3.6-kW class, and within a range from 7 to 15 % in the case of a heat exchanger whose capacity is above 3.6-kW class and up to 6-kW class.
  • the proportion accounted for by the one-circuit portion may be set within a range from 5 to 15 % in the case of a heat exchanger whose capacity is in a 2-kW to 3.6-kW class, and within a range from 3 to 10 % in the case of a heat exchanger whose capacity is above 3.6-kW class and up to 6-kW class.
  • the one-circuit portion because the pressure loss is increased due to an increase in the refrigerant flow rate, it is possible to suppress an increase in the pressure loss by decreasing the proportion accounted for by the one-circuit portion by a corresponding amount while keeping only the minimum number of one-circuit portion required to ensure a high enough heating performance. Therefore, it is possible to ensure a high enough heat exchange performance by appropriately setting the heat transfer coefficient and the pressure loss of the refrigerant in each case in accordance with the capacity of the heat exchanger.
  • a second aspect of the present invention is an air conditioner in which a refrigeration cycle is filled with HFO refrigerant, and in which an indoor heat exchanger constituting the refrigeration cycle is any one of the above-described heat exchangers.
  • a heat exchanger of the present invention by limiting the maximum number of branched circuits among the refrigerant tubes to six, it is possible to suppress pressure loss by ensuring a sufficient number of branched circuits and to set the pressure loss within an appropriate range while avoiding an increase in the size of branching/collecting units, as well as the size of the heat exchanger, due to an unnecessary increase in the number of circuits.
  • an air conditioner of the present invention even if HFO refrigerant, which is a low-GWP refrigerant, is employed as the refrigerant, by employing the above-described heat exchanger as an indoor heat exchanger, it is possible to enhance the heat exchange performance by maintaining a high COP by setting, both during cooling and heating, the heat transfer coefficient and the pressure loss of the refrigerant within the appropriate ranges; therefore, by suppressing the deterioration of the heating performance, it is possible to ensure substantially equivalent air conditioning performance to that of air conditioners employing R410A refrigerant.
  • Fig. 1 is an external perspective view of an air conditioner 1 according to this embodiment of the present invention
  • Fig. 2 is a schematic diagram showing an example configuration of refrigerant tube circuits of an indoor heat exchanger of an indoor unit of the air conditioner 1.
  • the air conditioner 1 is a separate-type air conditioner and is provided with an outdoor unit 2 and an indoor unit 3.
  • the outdoor unit 2 is installed at an appropriate outdoor location, and, in addition, the indoor unit 3 is installed on an indoor wall surface or the like via a mounting plate 4; the outdoor unit 2 and the outdoor unit 3 are connected by an indoor-outdoor connecting pipe 5, signal lines (not shown), and so forth to form a single unit, and the operation thereof is controlled via a remote controller 6.
  • the outdoor unit 2 accommodates outdoor equipment installed therein, such as a compressor, an outdoor heat exchanger, an outdoor blower, a four-way valve, an expansion valve, an outdoor controller, and so forth
  • the indoor unit 3 accommodates indoor equipment installed therein, such as an indoor heat exchanger, an indoor blower, an indoor controller, and so forth.
  • the compressor, the outdoor heat exchanger, the four-way valve, the expansion valve, the indoor heat exchanger, and so forth are sequentially connected by means of pipes via refrigerant pipes, including the indoor-outdoor connecting pipe 5, thereby forming a known refrigeration cycle which is a closed cycle.
  • the interior of the refrigeration cycle is filled with a required amount of R1234yf refrigerant (HFO refrigerant) which is a low-GWP refrigerant having a low Global Warming Potential (GWP).
  • HFO refrigerant R1234yf refrigerant
  • GWP Global Warming Potential
  • the indoor unit 3 takes in indoor air from an intake grill 7 that is provided at a top face thereof (and/or a front face), blows out this air into an indoor space from a vent 8 by means of the blower, after the temperature thereof is adjusted by cooling or heating the air by means of an indoor heat exchanger 9 (see Fig. 2 ), thus supplying this air for indoor air conditioning.
  • the indoor heat exchanger 9 is divided into a plurality of heat exchangers which are disposed in the indoor unit 3 in a stacked manner so as to form two layers each at the front side and the rear side thereof in the front-to-back direction.
  • This indoor heat exchanger 9 is a fin-tube-type heat exchanger constituted of numerous plate fins 10 formed of aluminum thin plates and numerous refrigerant tubes 11 formed of copper pipes, and refrigerant is circulated through the numerous refrigerant tubes 11 by being branched to and collected from multiple circuits via a plurality of branching/collecting units 12.
  • the indoor heat exchanger (heat exchanger) 9 in this embodiment is a heat exchanger 9 that is employed in a small air conditioner whose capacity is in the 2-kW to 6-kW class, and copper pipes having a diameter of 6.35 mm are employed as the refrigerant tubes 11.
  • Fig. 2 shows a 2.5-kW class heat exchanger 9 whose capacity falls within a range from 2-kW to 3.6-kW class and in which the total number of the refrigerant tubes 11 is 48. More specifically, the configuration of the heat exchanger 9 is such that the total number of refrigerant tubes 11 is 48, that, with regard to the number of branched circuits, one-circuit portions 13A have a total of six refrigerant tubes 11, four-circuit portions 13C have a total of eight refrigerant tubes 11, and six-circuit portions 13D have a total of 34 refrigerants tubes 11; and that the one-circuit portions 13A account for 13 % of the total number of refrigerant tubes 11, and the one-circuit portions 13A and the two- and four-circuit portions 13B and 13C together account for 29 % of the total number of refrigerant tubes 11.
  • the table in Fig. 3 shows example configurations (1) to (4) of the heat exchanger 9 in which the refrigerant tubes 11 are configured in a multi-circuit form.
  • the multi-circuit example (1) is a heat exchanger 9 whose configuration is such that the one-circuit portions 13A have four refrigerant tubes 11 in total, and the six-circuit portions 13D have 44 refrigerant tubes 11 in total, and that the proportion accounted for by the one-circuit portions 13A is 8 %, and the proportion accounted for by the one-circuit portions 13A and the two- and four-circuit portions 13B (not shown) and 13C is 8 %.
  • the multi-circuit example (2) is a heat exchanger 9 whose configuration is such that the one-circuit portions 13A have four refrigerant tubes 11 in total, the two-circuit portions 13B (not shown) have four refrigerant tubes 11 in total, and the six-circuit portions 13D have 40 refrigerant tubes 11 in total, and that the proportion accounted for by the one-circuit portions 13A is 8 %, and the proportion accounted for by the one-circuit portions 13A and the two- and four-circuit portions 13B and 13C is 17 %.
  • the multi-circuit example (3) is the above-described heat exchanger 9 shown in Fig. 2 as an example.
  • the multi-circuit example (4) is a heat exchanger 9 whose configuration is such that the one-circuit portions 13A have eight refrigerant tubes 11 in total, the two-circuit portions 13B have 10 refrigerant tubes 11 in total, and the six-circuit portions 13D have 30 refrigerant tubes 11 in total, and that the proportion accounted for by the one-circuit portions 13A is 17 %, and the proportion accounted for by the one-circuit portions 13A and the two- and four-circuit portions 13B and 13C is 38 %.
  • the heat exchanger 9 of above 3.6-kW class and up to 6-kW class because the amount of circulated refrigerant is increased, although it is necessary to increase the number of circuits involved, it is necessary to ensure a minimum required number of one-circuit portions in order to ensure a high enough performance during heating.
  • the number of refrigerant tubes 11 in this case is two or four, and the appropriate range of the proportion accounted for by the one-circuit portions is from 4 to 8 %.
  • the maximum number of branched circuits among the numerous refrigerant tube 11 is set at six, and, of the total number of the numerous refrigerant tubes 11, the proportion accounted for by the one-circuit portions and the two- to four-circuit portions is set within a range from 7 to 30 % in accordance with the capacity of the heat exchanger 9. By doing so, it is possible to set the heat transfer coefficient and the pressure loss of the refrigerant in optimal ranges both during cooling and heating.
  • the proportion accounted for by the one-circuit portions be set within a range from 5 to 15 %, and that the proportion accounted for by the one-circuit portions and the two- to four-circuit portions be set within a range from 15 to 30 %, and, with small air conditioners that employ heat exchangers 9 whose capacity is above 3.6-kW class and up to 6-kW class and that are driven by 200-V driving power, of the total number of the numerous refrigerant tubes 11, it is desirable that the proportion accounted for by the one-circuit portions be set within a range from 3 to 10 %, and that the proportion accounted for by the one-circuit portions and the two- to
  • the maximum number of branched circuits among the numerous refrigerant tubes 11 is set at six; of the total number of these numerous refrigerant tubes 11, the proportion accounted for by the one-circuit portions 13A and the two- and four-circuit portions 13B and 13C is set within a range from 7 to 30 % in accordance with the capacity of the heat exchanger 9.
  • the proportion accounted for by the one-circuit portions 13A and the two- and four-circuit portions 13B and 13C is set within the range from 15 to 30 % in the case of the heat exchanger 9 whose capacity is in the 2-kW to 3.6-kW class, and within the range from 7 to 15 % in the case of the heat exchanger 9 whose capacity is above 3.6-kW class and up to 6-kW class.
  • the proportion accounted for by the one-circuit portions 13A is set within the range from 5 to 15 % in the case of the heat exchanger 9 whose capacity is in the 2-kW to 3.6-kW class, and within the range from 3 to 10 % in the case of the heat exchanger 9 whose capacity is above 3.6-kW class and up to 6-kW class.
  • the one-circuit portions 13A because the pressure loss is increased, both during cooling and heating, due to an increase in the refrigerant flow rate, it is possible to suppress an increase in the pressure loss by decreasing the proportion accounted for by the one-circuit portions 13A by a corresponding amount while keeping only the minimum number of the one-circuit portions required to ensure a high enough heating performance; therefore, it is possible to ensure a high enough heat exchange performance by maintaining a high COP by appropriately setting the heat transfer coefficient and the pressure loss of the refrigerant in each case in accordance with the capacity of the heat exchanger 9.
  • the above-described heat exchanger 9 is employed as the indoor heat exchanger 9 of the air conditioner 1 constituting the refrigeration cycle filled with HFO refrigerant, even if HFO refrigerant, which is a low-GWP refrigerant, is employed as the refrigerant, by employing the above-described heat exchanger 9 as an indoor heat exchanger, it is possible to enhance the heat exchange performance by maintaining a high COP by setting, both during cooling and heating, the heat transfer coefficient and the pressure loss of the refrigerant within the appropriate ranges. Therefore, by suppressing the deterioration of the heating performance, it is possible to ensure substantially equivalent air conditioning performance to that of air conditioners employing R410A refrigerant.
  • the present invention is not limited to the invention according to the above-described embodiment, and appropriate modifications are possible within a range that does not depart from the scope thereof.
  • the air conditioner 1 in which the heat exchanger 9 is employed as the indoor heat exchanger has been described in the above-described embodiment, it is naturally permissible to employ this heat exchanger 9 as an outdoor heat exchanger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP15157890.3A 2014-03-07 2015-03-05 Échangeur de chaleur et climatiseur comprenant celui-ci Withdrawn EP2916086A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2014045131A JP6494916B2 (ja) 2014-03-07 2014-03-07 熱交換器およびそれを用いた空気調和機

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Publication Number Publication Date
EP2916086A1 true EP2916086A1 (fr) 2015-09-09

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EP15157890.3A Withdrawn EP2916086A1 (fr) 2014-03-07 2015-03-05 Échangeur de chaleur et climatiseur comprenant celui-ci

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021017210A1 (fr) * 2019-07-30 2021-02-04 广东美的制冷设备有限公司 Échangeur de chaleur intérieur et climatiseur
CN114270117A (zh) * 2019-08-22 2022-04-01 丹佛斯有限公司 制冷系统

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1686323A2 (fr) * 2005-01-31 2006-08-02 LG Electronics, Inc. Echangeur de chaleur pour un dispositif de conditionnement d'air
EP1757869A2 (fr) * 2005-08-26 2007-02-28 LS Cable Ltd. Echangeur de chaleur pour dispositif de conditionnement d'air avec différents circuits selon leurs distance au ventilateur
JP2010261683A (ja) 2009-05-11 2010-11-18 Daikin Ind Ltd 分流器及び冷凍装置
JP2011002217A (ja) 2009-05-18 2011-01-06 Panasonic Corp 冷凍装置および冷暖房装置
EP2535668A1 (fr) * 2010-02-10 2012-12-19 Mitsubishi Heavy Industries, Ltd. Récepteur réversible, et climatiseur
JP2013501909A (ja) 2009-08-12 2013-01-17 ヴァレオ システム テルミク 少なくとも１つの２ストロークサイクルを有する熱交換器、およびこのような熱交換器を含む空調ループ

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JP2002205535A (ja) * 2001-01-09 2002-07-23 Japan Climate Systems Corp 自動車用凝縮器
JP2005127529A (ja) * 2003-10-21 2005-05-19 Matsushita Electric Ind Co Ltd 熱交換器
JP2006097953A (ja) * 2004-09-29 2006-04-13 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2008121950A (ja) * 2006-11-10 2008-05-29 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2011247482A (ja) * 2010-05-27 2011-12-08 Panasonic Corp 冷凍装置および冷暖房装置
DE102010039511A1 (de) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
JP5927415B2 (ja) * 2011-04-25 2016-06-01 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
JP2012245849A (ja) * 2011-05-26 2012-12-13 Panasonic Corp 車両用空調装置
JP2013036707A (ja) * 2011-08-10 2013-02-21 Mitsubishi Electric Corp 冷凍サイクル装置
JP5909627B2 (ja) * 2011-09-16 2016-04-27 パナソニックＩｐマネジメント株式会社 空気調和機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1686323A2 (fr) * 2005-01-31 2006-08-02 LG Electronics, Inc. Echangeur de chaleur pour un dispositif de conditionnement d'air
EP1757869A2 (fr) * 2005-08-26 2007-02-28 LS Cable Ltd. Echangeur de chaleur pour dispositif de conditionnement d'air avec différents circuits selon leurs distance au ventilateur
JP2010261683A (ja) 2009-05-11 2010-11-18 Daikin Ind Ltd 分流器及び冷凍装置
JP2011002217A (ja) 2009-05-18 2011-01-06 Panasonic Corp 冷凍装置および冷暖房装置
JP2013501909A (ja) 2009-08-12 2013-01-17 ヴァレオ システム テルミク 少なくとも１つの２ストロークサイクルを有する熱交換器、およびこのような熱交換器を含む空調ループ
EP2535668A1 (fr) * 2010-02-10 2012-12-19 Mitsubishi Heavy Industries, Ltd. Récepteur réversible, et climatiseur

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021017210A1 (fr) * 2019-07-30 2021-02-04 广东美的制冷设备有限公司 Échangeur de chaleur intérieur et climatiseur
CN114270117A (zh) * 2019-08-22 2022-04-01 丹佛斯有限公司 制冷系统

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Publication number Publication date
JP6494916B2 (ja) 2019-04-03
JP2015169387A (ja) 2015-09-28

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