WO2015037214A1 - 熱交換器及び空気調和機 - Google Patents
熱交換器及び空気調和機 Download PDFInfo
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- WO2015037214A1 WO2015037214A1 PCT/JP2014/004579 JP2014004579W WO2015037214A1 WO 2015037214 A1 WO2015037214 A1 WO 2015037214A1 JP 2014004579 W JP2014004579 W JP 2014004579W WO 2015037214 A1 WO2015037214 A1 WO 2015037214A1
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- Prior art keywords
- heat exchange
- main
- heat exchanger
- refrigerant
- communication space
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
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- 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
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- 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
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/04—Fastening; Joining by brazing
Definitions
- the refrigerant flowing into the downstream main heat exchange region has a higher ratio of gas refrigerant in the whole than the refrigerant flowing into the upstream auxiliary heat exchange region.
- At least one heat exchanger unit (30) divided into heat exchange regions (35, 37) (37, 135, 235) (335, 337, 365, 367) is provided, and when functioning as an evaporator, a plurality of the heat exchange regions (35, 37) (37,135,235) (335,337,365,367) are connected in series, and the heat exchanger exchanges heat between the refrigerant flowing through the flat tube (31) and air, and each of the heat exchange regions (35,37) (37,135,235) (335,337,365,367) Is further divided into a plurality of heat exchanging portions arranged vertically, and the first and second header collecting pipes (40, 70) (340, 345, 370, 380), a communication space communicating with the plurality of flat tubes (31) is formed for each of the heat exchange sections, and the two are connected to each other when the heat exchanger functions as an evaporator.
- the seventh invention of the present disclosure is directed to the air conditioner (10), and the refrigerant circuit (20) provided with the heat exchanger (23) according to any one of the first to sixth aspects of the present disclosure. And a refrigeration cycle is performed by circulating the refrigerant in the refrigerant circuit (20).
- the number of heat exchange portions in each heat exchange region (35, 37) (37, 135, 235) (335, 337, 365, 367) is the most upstream when the heat exchanger functions as an evaporator.
- the heat exchange regions (37) and (337) are increased in steps toward the most downstream heat exchange regions (35), (135), and (335). Therefore, when the heat exchanger functions as an evaporator, in the plurality of heat exchange regions (35, 37) (37, 135, 235) (335, 337, 365, 367) connected in series, the downstream heat exchange region is more likely to drift. Since the number of communication spaces increases in the downstream heat exchange region, it is possible to effectively suppress refrigerant drift in the communication space. Therefore, the performance of the heat exchanger can be fully exhibited.
- Compressor (21) is a scroll type or rotary type hermetic compressor.
- the four-way switching valve (22) includes a first state (state indicated by a solid line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port; The port is switched to a second state (state indicated by a broken line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port.
- the expansion valve (24) is a so-called electronic expansion valve.
- the heat exchanger unit (30) is divided into two heat exchange regions (35, 37) on the top and bottom.
- the upper heat exchange region is the main heat exchange region (35)
- the lower heat exchange region is the auxiliary heat exchange region (37).
- the flat tube (31) provided in the heat exchanger unit (30) the one located in the main heat exchange region (35) constitutes the main row portion (51) and is located in the auxiliary heat exchange region (37).
- the number of flat tubes (31) constituting the auxiliary row portion (54) is smaller than the number of flat tubes (31) constituting the main row portion (51).
- the main heat exchange area (35) is divided into six main heat exchange sections (36a to 36f) on the top and bottom.
- the auxiliary heat exchanging region (37) is divided into three auxiliary heat exchanging portions (38a to 38c) in the vertical direction. Note that the numbers of the main heat exchange units (36a to 36f) and the auxiliary heat exchange units (38a to 38c) shown here are merely examples.
- the upper space (72) is divided into six main communication spaces (75a to 75f) by five partition plates (74). That is, on the upper side of the partition plate (71) in the second header collecting pipe (70), in order from bottom to top, the first main communication space (75a), the second main communication space (75b), and the first A three main communication space (75c), a fourth main communication space (75d), a fifth main communication space (75e), and a sixth main communication space (75f) are formed.
- the first connecting branch pipe (110) connects the first auxiliary row block (55a) and the first main row block group (53a). Specifically, in the first connecting branch pipe (110), the open end of the main pipe portion (111) communicates with the first auxiliary communication space (77a), and the open end of one branch pipe portion (112a) is the first.
- the main communication space (75a) communicates, and the open end of the other branch pipe (112b) communicates with the second main communication space (75b). Therefore, the first auxiliary communication space (77a) includes the first main communication space (75a) corresponding to the first main row block (52a) and the second main communication space (75a) corresponding to the second main row block (52b). 75b) both connected.
- the first to third connecting branch pipes (110, 120, 130) do not have a restriction in the main pipe portions (111, 121, 131) and branch the refrigerant without depressurization, and are different from so-called flow dividers.
- the refrigerant that has passed through the plurality of flat tubes (31) of the first main row block (52a) enters the first main communication space (75a) and merges.
- the refrigerant that has passed through the plurality of flat tubes (31) of the second main row block (52b) enters the second main communication space (75b) and merges.
- the refrigerant that has passed through the plurality of flat tubes (31) of the third main row block (52c) enters the third main communication space (75c) and merges.
- the refrigerant that has passed through the plurality of flat tubes (31) of the fourth main row block (52d) enters the fourth main communication space (75d) and joins.
- Part of the refrigerant that has flowed from the first auxiliary communication space (77a) into the main pipe portion (111) of the first connection branch pipe (110) passes through the one branch pipe portion (112a). (75a), and the remainder flows into the second main communication space (75b) through the other branch pipe (112b).
- a part of the refrigerant flowing from the second auxiliary communication space (77b) into the main pipe part (121) of the second connecting branch pipe (120) passes through the one branch pipe part (122a) to form the third main communication space. (75c), the remainder flows into the fourth main communication space (75d) through the other branch pipe (122b).
- the refrigerant in the third main communication space (75c) flows into the flat tube (31) of the third main heat exchange part (36c) constituting the third main row block (52c).
- the refrigerant in the fourth main communication space (75d) flows into the flat tube (31) of the fourth main heat exchange part (36d) constituting the fourth main row block (52d).
- the refrigerant in the fifth main communication space (75e) flows into the flat tube (31) of the fifth main heat exchange part (36e) constituting the fifth main row block (52e).
- the refrigerant in the sixth main communication space (75f) flows into the flat tube (31) of the sixth main heat exchange part (36f) constituting the sixth main row block (52f).
- the refrigerant flowing through the flat tube (31) of each main row block (52a to 52f) exchanges heat with the outdoor air supplied to the outdoor heat exchanger (23).
- the refrigerant that has passed through the plurality of flat tubes (31) of each main row block (52a to 52f) enters the upper space (42) of the first header collecting tube (40) and joins, and then the gas side connecting tube ( 102) and flows out of the outdoor heat exchanger (23).
- the outdoor heat exchanger (23) of the first embodiment when the number of the flat tubes (31) is different in the plurality of heat exchange portions (36a to 36f) of the heat exchange region (35), the flat tubes When the outdoor heat exchanger (23) functions as an evaporator, the number of (31) is large and the heat exchanger (36a) is prone to drift when the outdoor heat exchanger (23) functions as an evaporator.
- the liquid refrigerant is arranged on the lower side where a large amount of liquid refrigerant easily flows.
- connection branch pipes 110, 120, 130
- Each connecting branch pipe (110, 120, 130) has one main pipe part (111, 121, 131) and two branch pipe parts (112a, 112b, 122a, 122b, 132a, 132b) connected to the ends of the main pipe parts (111, 121, 131). I have.
- the second connecting branch pipe (120) connects the second lower main heat exchange section (236b), the third upper main heat exchange section (136c), and the fourth upper main heat exchange section (136d).
- the second connection branch pipe (120) has an open end of the main pipe portion (121) communicating with the second lower main communication space (143b), and an open end of one branch pipe portion (122a).
- the third upper main communication space (142c) communicates, and the open end of the other branch pipe portion (122b) communicates with the fourth upper main communication space (142d).
- the second lower main communication space (143b) includes the third upper main communication space (142c) of the third upper main heat exchange portion (136c) and the fourth upper side of the fourth upper main heat exchange portion (136d). It is connected to both main communication spaces (142d).
- the third connection branch pipe (130) connects the third lower main heat exchange section (236c), the fifth upper main heat exchange section (136e), and the sixth upper main heat exchange section (136f).
- the third connection branch pipe (130) has an open end of the main pipe portion (131) communicating with the third lower main communication space (143c), and an open end of one branch pipe portion (132a).
- the fifth upper main communication space (142e) communicates, and the open end of the other branch pipe portion (132b) communicates with the sixth upper main communication space (142f).
- the third lower main communication space (143c) includes the fifth upper main communication space (142e) of the fifth upper main heat exchange part (136e) and the sixth upper side of the sixth upper main heat exchange part (136f). Connected to both main communication spaces (142f).
- the refrigerant drift can be suppressed, so that the performance of the outdoor heat exchanger (23) can be sufficiently exerted.
- the outdoor heat exchanger (23) of the second embodiment includes the number of auxiliary heat exchange sections (78a to 78c) in the auxiliary heat exchange area (37) and the lower main heat exchange area (235).
- the number of heat exchange parts (236a to 236c) is the same.
- the number of the lower main heat exchange sections (236a to 236c) of the lower main heat exchange region (235) is set to the auxiliary heat exchange region (37).
- the number of heat exchanging parts (78a to 78c) is increased to function as an evaporator, the number of heat exchanging parts gradually increases from the most upstream heat exchanging area to the most downstream heat exchanging area. You may comprise as follows.
- the auxiliary heat exchange area (37) is divided into two auxiliary heat exchange sections, the lower main heat exchange area (235) is divided into four lower main heat exchange sections, and the upper main heat exchange area (135). May be divided into eight upper main heat exchange sections.
- the outdoor heat exchanger (23) functions as an evaporator
- the downstream heat exchange region (135) is more likely to drift, but the number of communication spaces is the most upstream. Since it gradually increases from the heat exchange region (37) toward the most downstream heat exchange region (135), it is possible to effectively suppress the drift of the refrigerant flowing from each communication space into the flat tube (31). Therefore, the performance of the outdoor heat exchanger (23) can be sufficiently exerted.
- the total number of flat tubes (31) arranged vertically in the heat exchanger unit (30) is significantly larger than that of the outdoor heat exchanger (23) of the first embodiment. Too many. Therefore, in the outdoor heat exchanger (23) of the second embodiment, the number of heat exchange regions (37, 135, 235) arranged in the vertical direction in the heat exchanger unit (30) is larger than that of the outdoor heat exchanger (23) of the first embodiment. By doing so, the total number of flat tubes (31) distributed to one heat exchange region (37,135,235) is reduced. As a result, the number of flat tubes (31) distributed to the heat exchange units (38a to 38c, 135a to 135f, 235a to 235c) is reduced.
- the three flat tubes (31) of the first upwind auxiliary heat exchange section (338a) communicate with the first auxiliary communication space (347a).
- Three flat tubes (31) of the second upwind auxiliary heat exchange section (338b) communicate with the second auxiliary communication space (347b).
- Three flat tubes (31) of the third upwind auxiliary heat exchange section (338c) communicate with the third auxiliary communication space (347c).
- the number of flat tubes (31) in each leeward main heat exchange section (366a to 366c) shown here is merely an example.
- the number of flat tubes (31) of the first leeward main heat exchange section (366a) is equal to the number of flat tubes (31) of the first leeward main heat exchange section (336a) and the second upwind main heat exchange section.
- the number of flat tubes (31) constituting the second leeward main heat exchanging portion (366b) is the same as the sum of the number of flat tubes (31) of (336b).
- the first leeward auxiliary heat exchange unit (368a), the second leeward auxiliary heat exchange unit (368b), and the third leeward auxiliary heat exchange unit. (368c) is formed.
- each of the lee auxiliary heat exchangers (368a to 368c) is provided with three flat tubes (31).
- the upper space (382) is divided into three main communication spaces (382a to 382c) by two partition plates. That is, on the upper side of the partition plate (381) in the second leeward header collecting pipe (380), in order from bottom to top, the first main communication space (382a), the second main communication space (382b), A third main communication space (382c) is formed.
- the refrigerant in the gas single-phase state that has flowed into the upper space (342) of the first upwind header collecting pipe (340) from the gas side connection pipe (102) flows into each upwind main heat exchange section (336a to 336f) into the flat pipe (31) and flows.
- the refrigerant flowing through the flat tube (31) of each upwind main heat exchanger (336a to 336f) exchanges heat with the outdoor air supplied to the outdoor heat exchanger (23).
- the refrigerant in the first auxiliary communication space (373a) flows into the first main communication space (372a) through the first connection pipe (311).
- the refrigerant in the second auxiliary communication space (373b) flows into the second main communication space (372b) through the second connection pipe (321).
- the refrigerant in the third auxiliary communication space (373c) flows into the third main communication space (372c) through the third connection pipe (331).
- the outdoor heat exchanger (23) of Embodiment 3 since two heat exchanger units (30) were provided, the total number of flat tubes (31) is the outdoor heat exchanger (23) of Embodiment 1. Compared to Therefore, compared with the outdoor heat exchanger (23) of Embodiment 1, a heat exchange capacity can be increased.
- the outdoor heat exchanger (23) functions as an evaporator
- the configuration in which the number of heat exchange parts in the downstream heat exchange region is larger than the number of heat exchange parts in the upstream heat exchange region is
- the number of heat exchange sections in the downstream heat exchange areas (35) (135) (335) is three times the number of heat exchange sections in the upstream heat exchange areas (37) (235) (365)
- it may be configured to be a multiple of the above. In that case, for example, a connecting branch pipe (110, 120, 130) having three or more branch pipe portions may be used.
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Abstract
Description
本発明の実施形態1について説明する。本実施形態の熱交換器は、空気調和機(10)に設けられた室外熱交換器(23)である。以下では、先ず空気調和機(10)について説明し、その後に室外熱交換器(23)について詳細に説明する。
空気調和機(10)について、図1を参照しながら説明する。
空気調和機(10)は、室外ユニット(11)及び室内ユニット(12)を備えている。室外ユニット(11)と室内ユニット(12)は、液側連絡配管(13)及びガス側連絡配管(14)を介して互いに接続されている。空気調和機(10)では、室外ユニット(11)、室内ユニット(12)、液側連絡配管(13)及びガス側連絡配管(14)によって、冷媒回路(20)が形成されている。
空気調和機(10)は、冷房運転と暖房運転を選択的に行う。
室外熱交換器(23)について、図2~7を適宜参照しながら説明する。なお、以下の説明に示す扁平管(31)の本数は、単なる一例である。
上述したように、第1ヘッダ集合管(40)のうち下側空間(43)を形成する部分は、分流器(150)を構成する。この分流器(150)は、室外熱交換器(23)が蒸発器として機能する場合に、室外熱交換器(23)へ供給された気液二相状態の冷媒を三つの補助熱交換部(38a~38c)へ分配する。ここでは、分流器(150)について、図7を参照しながら説明する。
空気調和機(10)の冷房運転中には、室外熱交換器(23)が凝縮器として機能する。冷房運転中における室外熱交換器(23)での冷媒の流れを説明する。
空気調和機(10)の暖房運転中には、室外熱交換器(23)が蒸発器として機能する。暖房運転中における室外熱交換器(23)での冷媒の流れを説明する。
本実施形態1の室外熱交換器(23)によれば、蒸発器として機能する際に、最下流の主熱交換領域(35)の熱交換部(36a~36f)の数が、最上流の補助熱交換領域(37)の熱交換部(38a~38c)の数よりも多くなるように構成することとした。これに伴い、主熱交換領域(35)の熱交換部の数が補助熱交換領域(37)の熱交換部の数と同数である場合に比べて、主熱交換領域(35)における連通空間(75a~75f)の数が多くなるため、該連通空間(75a~75f)に連通する扁平管(31)の数が少なくなり、該連通空間(75a~75f)の高さが低くなる。室外熱交換器(23)が蒸発器として機能する際に、最下流の主熱交換領域(35)の各連通空間(75a~75f)では最も偏流が生じ易いが、上述のように、主熱交換領域(35)の各連通空間(75a~75f)の高さを低減することで、ガス冷媒と液冷媒とが分離され難くなり、主熱交換領域(35)の各連通空間(75a~75f)において冷媒の偏流が生じ難くなる。従って、本実施形態1の室外熱交換器(23)によれば、蒸発器として機能する際に冷媒の偏流が最も生じ易い最下流の主熱交換領域(35)の各連通空間(75a~75f)において冷媒の偏流を抑制することができるため、室外熱交換器(23)の性能を十分に発揮させることができる。
本発明の実施形態2について説明する。実施形態1の室外熱交換器(23)の熱交換器ユニット(30)は、上下に二つの領域に区分され、上側の領域が主熱交換領域(35)となり、下側の領域が補助熱交換領域(37)となっていた。実施形態2では、図8及び図9に示すように、熱交換器ユニット(30)が、上下に三つの領域に区分されている。
空気調和機(10)の冷房運転中には、室外熱交換器(23)が凝縮器として機能する。冷房運転中における室外熱交換器(23)での冷媒の流れを説明する。
空気調和機(10)の暖房運転中には、室外熱交換器(23)が蒸発器として機能する。暖房運転中における室外熱交換器(23)での冷媒の流れを説明する。
本実施形態2の室外熱交換器(23)によれば、蒸発器として機能する際に、最下流の上側主熱交換領域(135)の熱交換部(136a~136f)の数が、最上流の補助熱交換領域(37)の熱交換部(38a~38c)の数よりも多くなるように構成することとした。これに伴い、上側主熱交換領域(135)の熱交換部の数が補助熱交換領域(37)の熱交換部の数と同数である場合に比べて、上側主熱交換領域(135)の連通空間(142a~142f)の数が多くなるため、該連通空間(142a~142f)に連通する扁平管(31)の数が少なくなり、該連通空間(142a~142f)の高さが低くなる。室外熱交換器(23)が蒸発器として機能する際に、最下流の上側主熱交換領域(135)の各連通空間(142a~142f)では最も偏流が生じ易いが、上述のように、上側主熱交換領域(135)の各連通空間(142a~142f)の高さを低減することで、ガス冷媒と液冷媒とが分離され難くなり、上側主熱交換領域(135)の各連通空間(142a~142f)において冷媒の偏流が生じ難くなる。従って、本実施形態2の室外熱交換器(23)によれば、蒸発器として機能する際に冷媒の偏流が最も生じ易い最下流の上側主熱交換領域(135)の各連通空間(142a~142f)において冷媒の偏流を抑制することができるため、室外熱交換器(23)の性能を十分に発揮させることができる。
本発明の実施形態3について説明する。実施形態1の室外熱交換器(23)は、一つの熱交換器ユニット(30)を備えていた。実施形態3では、図10に示すように、室外熱交換器(23)が、二つの熱交換器ユニット(30)を備えている。
風上熱交換器ユニット(330)は、一つの第1風上ヘッダ集合管(340)と、一つの第2風上ヘッダ集合管(345)とを備えると共に、図示を省略するが、実施形態1と同様に構成された多数の扁平管(31)とフィン(32)とを備えている。第1風上ヘッダ集合管(340)、第2風上ヘッダ集合管(345)、扁平管(31)及びフィン(32)は、何れもアルミニウム合金製の部材であって、互いにロウ付けによって接合されている。
風下熱交換器ユニット(360)は、一つの第1風下ヘッダ集合管(370)と、一つの第2風下ヘッダ集合管(380)とを備えると共に、図示を省略するが、実施形態1と同様に構成された多数の扁平管(31)とフィン(32)とを備えている。第1風下ヘッダ集合管(370)、第2風下ヘッダ集合管(380)、扁平管(31)及びフィン(32)は、何れもアルミニウム合金製の部材であって、互いにロウ付けによって接合されている。
第2風上ヘッダ集合管(345)と第2風下ヘッダ集合管(380)とには、三本の接続用分岐配管(分岐管)(110,120,130)と、三本の接続用配管(106,107,108)とが取り付けられている。各接続用分岐配管(110,120,130)は、一つの主管部(111,121,131)と、主管部(111,121,131)の端部に接続する二つの分岐管部(112a,112b,122a,122b,132a,132b)とを備えている。
空気調和機(10)の冷房運転中には、室外熱交換器(23)が凝縮器として機能する。冷房運転中における室外熱交換器(23)での冷媒の流れを説明する。
空気調和機(10)の暖房運転中には、室外熱交換器(23)が蒸発器として機能する。暖房運転中における室外熱交換器(23)での冷媒の流れを説明する。
本実施形態3の室外熱交換器(23)によれば、蒸発器として機能する際に、最下流の風上主熱交換領域(335)の熱交換部(336a~336f)の数が、最上流の風上補助熱交換領域(337)の熱交換部(338a~338c)の数よりも多くなるように構成することとした。これに伴い、風上主熱交換領域(335)の熱交換部の数が風上補助熱交換領域(337)の熱交換部の数と同数である場合に比べて、風上主熱交換領域(335)の連通空間(346a~346f)の数が多くなるため、各連通空間(346a~346f)に連通する扁平管(31)の数が少なくなり、該連通空間(346a~346f)の高さが低くなる。室外熱交換器(23)が蒸発器として機能する際に、最下流の風上主熱交換領域(335)の各連通空間(346a~346f)では最も偏流が生じ易いが、上述のように、風上主熱交換領域(335)の各連通空間(346a~346f)の高さを低減することで、ガス冷媒と液冷媒とが分離され難くなり、偏流が生じ難くなる。従って、本実施形態3の室外熱交換器(23)によれば、蒸発器として機能する際に冷媒の偏流が最も生じ易い最下流の風上主熱交換領域(335)の各連通空間(346a~346f)において冷媒の偏流を抑制することができるため、室外熱交換器(23)の性能を十分に発揮させることができる。
上記各実施形態の室外熱交換器(23)では、蒸発器として機能する際に互いに接続される二つの熱交換領域であって、上流側よりも下流側の方が熱交換部の数が多い二つの熱交換領域(35,37)(135,235)(335,365)において、下流側の熱交換領域(35)(135)(335)の熱交換部の数が、上流側の熱交換領域(37)(235)(365)の熱交換部の数の二倍となるように構成していた。しかしながら、室外熱交換器(23)が蒸発器として機能する際に、下流側の熱交換領域の熱交換部の数を上流側の熱交換領域の熱交換部の数より多くする構成はこれに限られず、下流側の熱交換領域(35)(135)(335)の熱交換部の数が、上流側の熱交換領域(37)(235)(365)の熱交換部の数の三倍以上の倍数となるように構成することとしてももちろんよい。その場合、例えば、分岐管部を三つ以上有する接続用分岐配管(110,120,130)を用いればよい。
20 冷媒回路
23 室外熱交換器(熱交換器)
30 熱交換器ユニット
31 扁平管
32 フィン
35 主熱交換領域(熱交換領域)
36a~36f 第1~第6主熱交換部(熱交換部)
37 補助熱交換領域(熱交換領域)
38a~38c 第1~第3補助熱交換部(熱交換部)
40 第1ヘッダ集合管
70 第2ヘッダ集合管
75a~75f 第1~第6主連通空間(連通空間)
77a~77c 第1~第3補助連通空間(連通空間)
110、120、130 第1、第2、第3接続用分岐配管(分岐管)
135 上側主熱交換領域(熱交換領域)
136a~136f 第1~第6上側主熱交換部(熱交換部)
142a~142f 第1~第6上側主連通空間(連通空間)
143a~143c 第1~第3下側主連通空間(連通空間)
173a~173c 第1~第3下側主連通空間(連通空間)
235 下側主熱交換領域(熱交換領域)
236a~236c 第1~第3下側主熱交換部(熱交換部)
335 風上主熱交換領域(熱交換領域)
336a~336f 第1~第6風上主熱交換部(熱交換部)
337 風上補助熱交換領域(熱交換領域)
338a~338c 第1~第3風上補助熱交換部(熱交換部)
340 第1風上ヘッダ集合管(第1ヘッダ集合管)
345 第2風上ヘッダ集合管(第2ヘッダ集合管)
346a~346f 第1~第6主連通空間(連通空間)
347a~347c 第1~第3補助連通空間(連通空間)
365 風下主熱交換領域(熱交換領域)
366a~366c 第1~第3風下主熱交換部(熱交換部)
367 風下補助熱交換領域(熱交換領域)
368a~368c 第1~第3風下補助熱交換部(熱交換部)
370 第1風下ヘッダ集合管(第1ヘッダ集合管)
372a~372c 第1~第3主連通空間(連通空間)
373a~373c 第1~第3補助連通空間(連通空間)
380 第2風下ヘッダ集合管(第2ヘッダ集合管)
382a~382c 第1~第3主連通空間(連通空間)
383a~383c 第1~第3補助連通空間(連通空間)
Claims (7)
- 上下に並ぶ複数の扁平管(31)と、上記扁平管(31)に接合されたフィン(32)と、複数の上記扁平管(31)の一端が接続された第1ヘッダ集合管(40)(340,370)と、複数の上記扁平管(31)の他端が接続された第2ヘッダ集合管(70)(345,380)とを有し、上下に並ぶ複数の熱交換領域(35,37)(37,135,235)(335,337,365,367)に区分された熱交換器ユニット(30)を少なくとも一つ備え、蒸発器として機能する際に、複数の上記熱交換領域(35,37)(37,135,235)(335,337,365,367)が直列に接続され、上記扁平管(31)を流れる冷媒を空気と熱交換させる熱交換器であって、
上記各熱交換領域(35,37)(37,135,235)(335,337,365,367)は、上下に並ぶ複数の熱交換部にさらに区分され、
上記第1及び第2ヘッダ集合管(40,70)(340,345,370,380)のそれぞれの内部には、複数の上記扁平管(31)と連通する連通空間が上記熱交換部毎に形成され、
上記熱交換器が蒸発器として機能する際に、互いに接続される二つの上記熱交換領域において、下流側の上記熱交換領域(35)(135,235)(335,365,367)の上記熱交換部の数が、上流側の上記熱交換領域(37)(37,235)(337,365,367)の上記熱交換部の数以上となり、且つ、最下流の上記熱交換領域(35)(135)(335)の上記熱交換部の数が、最上流の上記熱交換領域(37)(337)の上記熱交換部の数よりも多くなるように構成されている
ことを特徴とする熱交換器。 - 請求項1において、
上記各熱交換領域(35,37)(37,135,235)(335,337,365,367)の上記熱交換部の数が、上記熱交換器が蒸発器として機能する際に、最上流の上記熱交換領域(37)(337)から最下流の上記熱交換領域(35)(135)(335)に向かって段階的に増加するように構成されている
ことを特徴とする熱交換器。 - 請求項1又は2において、
上記熱交換器が蒸発器として機能する際に互いに接続される二つの上記熱交換領域であって、上流側よりも下流側の方が上記熱交換部の数が多い二つの上記熱交換領域(35,37)(135,235)(335,365)において、下流側の上記熱交換領域(35)(135)(335)の上記熱交換部の数が、上流側の上記熱交換領域(37)(235)(365)の上記熱交換部の数の倍数となるように構成されている
ことを特徴とする熱交換器。 - 請求項3において、
上記熱交換器が蒸発器として機能する際に互いに接続される二つの上記熱交換領域であって、上流側よりも下流側の方が上記熱交換部の数が多い二つの上記熱交換領域(35,37)(135,235)(335,365)の間には、上流側の上記熱交換領域(37)(235)(365)の上記各熱交換部と下流側の上記熱交換領域(35)(135)(335)の互いに異なる複数の上記熱交換部とを接続する分岐管(110,120,130)が設けられている
ことを特徴とする熱交換器。 - 請求項1乃至4のいずれか一つにおいて、
上記各熱交換領域(35,37)(37,135,235)(335,337,365,367)において、上記扁平管(31)の数が最も多い上記熱交換部が、最も下側に配置されている
ことを特徴とする熱交換器。 - 請求項1乃至5のいずれか一つにおいて、
上記熱交換器ユニット(30)は複数設けられ、
上記熱交換器が蒸発器として機能する際に、複数の上記熱交換器ユニット(30)の全ての上記熱交換領域(35,37)(37,135,235)(335,337,365,367)が直列に接続される
ことを特徴とする熱交換器。 - 請求項1乃至6のいずれか一つに記載の熱交換器(23)が設けられた冷媒回路(20)を備え、
上記冷媒回路(20)において冷媒を循環させて冷凍サイクルを行うことを特徴とする空気調和機。
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Also Published As
Publication number | Publication date |
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JP5741657B2 (ja) | 2015-07-01 |
EP3045856B1 (en) | 2018-01-31 |
EP3045856A4 (en) | 2017-05-31 |
CN105473977B (zh) | 2017-08-01 |
US10309701B2 (en) | 2019-06-04 |
CN105473977A (zh) | 2016-04-06 |
ES2661019T3 (es) | 2018-03-27 |
JP2015055404A (ja) | 2015-03-23 |
EP3045856A1 (en) | 2016-07-20 |
US20160216014A1 (en) | 2016-07-28 |
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