CN203798027U - Heat exchanger and refrigeration cycle air conditioning device with same - Google Patents
Heat exchanger and refrigeration cycle air conditioning device with same Download PDFInfo
- Publication number
- CN203798027U CN203798027U CN201420141694.6U CN201420141694U CN203798027U CN 203798027 U CN203798027 U CN 203798027U CN 201420141694 U CN201420141694 U CN 201420141694U CN 203798027 U CN203798027 U CN 203798027U
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- Prior art keywords
- heat exchanger
- heat exchange
- type heat
- exchange portion
- parallel flow
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- Expired - Lifetime
Links
- 238000004378 air conditioning Methods 0.000 title abstract 2
- 238000005057 refrigeration Methods 0.000 title abstract 2
- 201000007094 prostatitis Diseases 0.000 claims description 36
- 239000003507 refrigerant Substances 0.000 claims description 10
- 238000005520 cutting process Methods 0.000 claims description 3
- 238000005192 partition Methods 0.000 claims description 3
- 230000000694 effects Effects 0.000 description 7
- 239000003921 oil Substances 0.000 description 5
- 238000001704 evaporation Methods 0.000 description 4
- 239000012141 concentrate Substances 0.000 description 3
- RTZKZFJDLAIYFH-UHFFFAOYSA-N Diethyl ether Chemical compound CCOCC RTZKZFJDLAIYFH-UHFFFAOYSA-N 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000005273 aeration Methods 0.000 description 1
- 150000004996 alkyl benzenes Chemical class 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010696 ester oil Substances 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Classifications
-
- 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
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- 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
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
- F28D1/0435—Combination of units extending one behind the other
-
- 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
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0461—Combination of different types of heat exchanger, e.g. radiator combined with tube-and-shell heat exchanger; Arrangement of conduits for heat exchange between at least two media and for heat exchange between at least one medium and the large body of fluid
-
- 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
- F28D1/047—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 bent, e.g. in a serpentine or zig-zag
- F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
-
- 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
- F28F1/126—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 consisting of zig-zag shaped fins
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The utility model provides a heat exchanger and a refrigeration cycle air conditioning device with the same. The heat exchanger (1) is provided with a parallel flow type heat exchanging part (3). The parallel flow type heat exchanging part (3) is provided with a plurality of heat exchanging tubes (11 and 13) which extend vertically. The parallel flow type heat exchanging part at least comprises a front row part (7) and a rear row part (9). Each of the front row part and the rear row part is provided with the heat exchanging tubes which extend vertically. The plate-fin tube type heat exchanging part (5) of a plurality of plate fins (25) which respectively extend vertically is disposed in front of the lower portion of the front surface of the parallel flow type heat exchanging part. The outlet end of the plate-fin tube type heat exchanging part is connected with the inlet end of the parallel flow type heat exchanging part through a tubing. The lower headers of the front row part and the rear row part are disposed in a segmented manner according to rows. The upper headers of the front row part and the rear row part are integrated in a row span manner.
Description
Technical field
The utility model relates to heat exchanger and uses the freeze cycle aircondition of this heat exchanger.
Background technology
In heat exchanger, the reduction of the exchange capability of heat that frosting causes becomes problem repeatedly.As the utility model being associated with such problem, for example, there is the disclosed heat exchanger of patent documentation 1.In this heat exchanger, by heat exchange portion separate front and back and configure overlappingly along fore-and-aft direction, between an above-mentioned heat exchanging portion and lay respectively at and guarantee separately gap between the upper and lower a pair of collector portion of heat exchange portion.
According to such heat exchanger, even if any heat exchange portion of front and back because frosting loses aeration, also can seek to obtain minimal heat exchange function via another heat exchange portion that is flowing in of the air by gap.
Formerly technical literature
Patent documentation
Patent documentation 1: Japanese kokai publication hei 8-226727 communique (the first figure)
Utility model content
The problem that utility model will solve
But in above-mentioned existing heat exchanger, there are the following problems: in the situation that using as evaporimeter, do not consider to suppress the growth of frosting self, and, in heat exchanger bottom, the local frosting producing defrosts comparatively difficult.
The utility model is in view of above-mentioned and make, and its object is to provide a kind of heat exchanger that can be suppressed at the white growth of piling up heat exchanger bottom.
For solving the technical scheme of problem
Be for the utility model of realizing above-mentioned purpose, a kind of heat exchanger is provided, it possesses parallel flow type heat exchange portion, this parallel flow type heat exchange portion has the multiple heat exchanger tubes that extend along the vertical direction, wherein, described parallel flow type heat exchange portion at least comprises prostatitis part and rank rear part, described prostatitis part and described rank rear part have respectively the multiple heat exchanger tubes that extend along described above-below direction, the front configuration of the bottom of the front surface in described parallel flow type heat exchange portion has the plate finned tube type heat exchange portion of the multiple nest plates that extend along the vertical direction separately, the port of export of described plate finned tube type heat exchange portion is connected by pipe arrangement with the arrival end of described parallel flow type heat exchange portion, the lower header of described prostatitis part and described rank rear part is arranged by column split, the upper header of described prostatitis part and described rank rear part is to be set to one across the mode of row.
Heat exchanger of the present utility model also can be configured to, and the foot of described plate finned tube type heat exchange portion is between the foot of fin and the lower header of described prostatitis part of described parallel flow type heat exchange portion.
Heat exchanger of the present utility model also can be configured to, and the heat pipe of described plate finned tube type heat exchange portion uses pipe.
Heat exchanger of the present utility model also can be configured to, and the number of passages of described plate finned tube type heat exchange portion is less than the number of passages of described parallel flow type heat exchange portion.
Heat exchanger of the present utility model also can be configured to, as the bottom that becomes arrival end refrigerant inlet, described heat pipe and be configured in described fin in the situation of evaporimeter performance function.
Heat exchanger of the present utility model also can be configured to, described heat exchanger has refrigerant flow path, this refrigerant flow path as evaporimeter performance function in the situation that, make cold-producing medium and air on fore-and-aft direction towards identical towards advance and as condenser performance function in the situation that, make cold-producing medium and air on fore-and-aft direction towards on the contrary towards advancing.
Heat exchanger of the present utility model also can be configured to, and the fin of described parallel flow type heat exchange portion is outstanding towards upwind side compared with the described heat exchange conduit of described prostatitis part.
Heat exchanger of the present utility model also can be configured to, the inner utilization partition wall of the described lower header of described prostatitis part is divided into multiple spaces, each in described multiple spaces of this lower header has arrival end, between described plate finned tube type heat exchange portion and the described lower header of described prostatitis part, distributor is set, the port of export of described plate finned tube type heat exchange portion links pipe arrangement with described distributor by set and is connected, the multiple described arrival end of described lower header is cut apart link pipe arrangement with described distributor by multiple each self-corresponding these of cutting apart in link pipe arrangement separately and is connected.
Be for other the utility model of realizing same object, a kind of freeze cycle aircondition is provided, it possesses freeze cycle loop, this freeze cycle loop comprises compressor, outdoor heat exchanger, expansion valve, indoor heat exchanger, wherein, described heat exchanger of the present utility model is used in a side or the both sides in described outdoor heat exchanger and described indoor heat exchanger.
In addition, freeze cycle aircondition of the present utility model also can be configured to, the fin of described parallel flow type heat exchange portion is wave-shaped fins, and described parallel flow type heat exchange portion is configured in the framework face entirety of the weather side of the fan in corresponding described outdoor heat exchanger and described indoor heat exchanger.
Utility model effect
According to the utility model, can be suppressed at the white growth that pile up heat exchanger bottom.
Brief description of the drawings
Fig. 1 is the front view of the heat exchanger of embodiment 1 of the present utility model.
Fig. 2 is the side view of the heat exchanger of present embodiment 1.
Fig. 3 about embodiment 2 of the present utility model, with Fig. 1 with the figure of situation.
Fig. 4 about present embodiment 2, with Fig. 2 with the figure of situation.
Fig. 5 is the figure that represents the summary of the freeze cycle aircondition of embodiment 3 of the present utility model.
Fig. 6 is the top view that schematically shows the off-premises station of the freeze cycle aircondition of present embodiment 3.
Detailed description of the invention
Below, based on accompanying drawing, embodiment of the present utility model is described.It should be noted that, in the drawings, same reference numerals represents identical or corresponding part.In addition, direction in explanation is as described below: the upstream side of the ventilation of plan be made as effect that " front ", downstream be made as " afterwards ", gravity towards be made as D score, its on the contrary towards being made as " on ", will be made as " left and right " with above-mentioned fore-and-aft direction and the orthogonal direction of these both sides of above-below direction (gravity direction) in addition.Taking Fig. 2, when example represents, the paper of Fig. 2 is the above-below direction in explanation up and down, and paper left side and the right side of Fig. 2 are respectively front side and rear side, and in the table of the paper of Fig. 2, direction is left and right directions.It should be noted that, in Fig. 2 with reference to Reference numeral WD represent ventilation wind direction.
Embodiment 1.
Fig. 1 and Fig. 2 are respectively front view and the side views of the heat exchanger of embodiment 1 of the present utility model.Heat exchanger 1 is the aluminium heat-exchange device using in the off-premises station of freeze cycle aircondition.
Heat exchanger 1 possesses parallel flow type heat exchange portion 3.The front of the parallel flow type heat exchange portion 3 in heat exchanger 1 is provided with plate finned tube type heat exchange portion 5.
First, parallel flow type heat exchange portion 3 is included in that fore-and-aft direction is separated from each other and in fore-and-aft direction prostatitis part 7 and rank rear part 9 side by side.Prostatitis part 7 and rank rear part 9 have the multiple heat exchange conduits 11,13 that extend along the vertical direction separately.Heat exchange conduit the 11, the 13rd, the flat tube being crushed from left and right directions.Along left and right directions side by side, and multiple heat exchange conduits 13 of rank rear part 9 also along left and right directions side by side for multiple heat exchange conduits 11 of prostatitis part 7.Between multiple heat exchange conduits 11 of above-mentioned prostatitis part 7 and multiple heat exchange conduits 13 of rank rear part 9, guarantee gap 15 along fore-and-aft direction, heat exchange conduit 11 and heat exchange conduit 13 are along separate front and back.In addition, as an example, the radical of heat exchange conduit 11 is identical with the radical of heat exchange conduit 13.
Between multiple heat exchange conduits 11,13, be provided with fin 17.Specifically, fin 17 is wave-shaped fins, between adjacent a pair of fin, extends along the vertical direction separately in the warpage of left and right.In other words, fin 17 is formed as waveform in the mode alternately contacting with the heat exchange conduit in its left side and the heat exchange conduit on its right side.
In addition, two row before and after heat exchange conduit 11,13 is arranged in, fin 17 is at fore-and-aft direction previous column.In other words, between the corresponding heat exchanging conduit 13 between the corresponding heat exchanging conduit 11 of continual wave-shaped fins in prostatitis part 7 and in rank rear part 9.Compared with the heat exchange conduit 11 of fin 17 and prostatitis part 7, aweather is outstanding, that is, the exterior region of fin 17 is positioned at than the front end of the heat exchange conduit 11 of prostatitis part 7 position on the front.
Be provided with the lower header of prostatitis part 7 sides, i.e. inlet header 19 in the bottom of prostatitis part 7, be provided with the lower header of rank rear part 9 sides, i.e. outlet header 21 in the bottom of rank rear part 9.Top in prostatitis part 7 and rank rear part 9 is provided with across row collector 23.In prostatitis part 7 and rank rear part 9, share identical across row collector 23 as upper header separately.It should be noted that inlet header 19, outlet header 21 and form across the each freedom of row collector 23 one Room.Like this, the lower header of prostatitis part 7 and rank rear part 9 is arranged by column split, and the upper header of prostatitis part 7 and rank rear part 9 is to be wholely set across the mode of row.
In addition, from function, be configured in the mechanism that row that the inlet header 19 of bottom of parallel flow type heat exchange portion 3 and outlet header 21 possess the side of being in the wind make the distribution of wind direction heat exchange conduit become uniform mechanism and at the row of downwind side, gas be assembled, during with parallel flow type heat exchange portion 3 whole observation, lower header is cut apart by row.On the other hand, be configured in the having and can make cold-producing medium mobile mechanism between row across row collector 23 of top of parallel flow type heat exchange portion 3, during with parallel flow type heat exchange portion 3 whole observation, upper header two row are set to one.
The lower end of the heat exchange conduit 11 of prostatitis part 7 is connected with inlet header 19, the upper end of the heat exchange conduit 11 of prostatitis part 7 be connected across row collector 23.In addition, the lower end of the heat exchange conduit 13 of rank rear part 9 is connected with outlet header 21, the upper end of the heat exchange conduit 13 of rank rear part 9 be connected across row collector 23.
Plate finned tube type heat exchange portion 5 is configured in the front of the bottom of the front surface in parallel flow type heat exchange portion 3, in more detail, is configured in the front of the bottom of the front surface of prostatitis part 7, the i.e. top of inlet header 19.The foot (foot of nest plate 25) of plate finned tube type heat exchange portion 5 is configured between the foot and inlet header 19 of fin 17 of parallel flow type heat exchange portion 3.
Plate finned tube type heat exchange portion 5 has multiple nest plates 25 and for forming the heat pipe 27 of at least one path.
Multiple nest plates 25 extend respectively along the vertical direction, arrange substantially in parallel along left and right directions.In addition, the front end butt of the bottom of the fin 17 of the rear portion of multiple nest plates 25 and parallel flow type heat exchange portion 3 or close.
Heat pipe 27 for forming a pipe of a path, also extends along the vertical direction to run through multiple nest plates 25 along the mode of left and right directions warpage in illustrated example.Become the bottom that is configured in nest plate 25 as the arrival end 27a refrigerant inlet in the situation of evaporimeter performance function, heat pipe 27, become the top that is configured in nest plate 25 as the port of export 27b refrigerant outlet in the situation of evaporimeter performance function, heat pipe 27.It should be noted that, as heat pipe 27, as long as be less than the number of passages of parallel flow type heat exchange portion 3, also can use many pipes in order to form multiple paths.In addition, as heat pipe 27, also can substitute above-mentioned one or more pipes (plate wing tubular type), use one or more flat tubes (the partially flat cast of plate wing).
Plate finned tube type heat exchange portion 5 is connected by linking pipe arrangement 29 with parallel flow type heat exchange portion 3.That is, connect at the port of export 27b of the heat pipe 27 of plate finned tube type heat exchange portion 5 one end that links pipe arrangement 29, the arrival end 19a of the inlet header 19 in parallel flow type heat exchange portion 3 connects the other end that links pipe arrangement 29.
Next, the mobile of cold-producing medium described.It should be noted that, the arrow shown in Fig. 1 and Fig. 2 schematically shows heat exchanger 1 flowing as the cold-producing medium in the situation of evaporimeter performance function.Thereby, at heat exchanger 1 as condenser performance function in the situation that, cold-producing medium along contrary with this arrow towards flowing.For example, in the situation (be located at off-premises station and heat the situation of running) using as evaporimeter at heat exchanger 1, cold-producing medium in plate finned tube type heat exchange portion 5 via a path under upward flow, slave plate finned tube type heat exchange portion 5 flows out, by after linking pipe arrangement 29, flow into the inlet header 19 of parallel flow type heat exchange portion 3.Cold-producing medium in inlet header 19 in multiple heat exchange conduits 11 of the prostatitis part 7 as weather side under upward flow.That is, be separated into the quantity identical with the radical of heat exchange conduit 11, number of passages and in prostatitis part 7 rise after, flow into across row collector 23.In addition, cold-producing medium flow into across after row collector 23, multiple heat exchange conduits 13 of the rank rear part 9 as downwind side from towards current downflow.,, using as the quantity identical with the radical of heat exchange conduit 13, i.e. number of passages and after flowing down, flow into outlet header 21 in rank rear part 9, finally flow out from heat exchanger 1.
In the present embodiment 1 forming in the above described manner, obtain following such advantage.In heat exchanger 1, be provided with plate finned tube type heat exchange portion 5, therefore, in the time may producing the running of frosting, from inlet header 19 and fin 17, condensed water is guided to fin 25.That is to say, condensed water mainly concentrates on the plate finned tube type heat exchange portion 5 that drainage is good, therefore can prevent at the stacked ice in the bottom of heat exchanger 1.
In addition, the number of passages of plate finned tube type heat exchange portion 5 is less than the number of passages of parallel flow type heat exchange portion 3, and about the pressure loss in the conduit passing through for cold-producing medium, plate finned tube type heat exchange portion 5 is greater than parallel flow type heat exchange portion 3.Therefore, compared with the evaporating temperature of parallel flow type heat exchange portion 3, the evaporating temperature of plate finned tube type heat exchange portion 5 raises, and frosting degree when running reduces, and can suppress frost and concentrate in the bottom of heat exchanger 1.In addition, in the situation that using heat exchanger 1 as condenser, can increase the flow velocity of supercooling portion, improve heet transfer rate in pipe, improve heat exchanger efficiency.
In addition, in the situation that using heat exchanger 1 as evaporimeter, the entrance of plate finned tube type heat exchange portion 5 is arranged at the foot of plate finned tube type heat exchange portion 5, therefore can make the temperature rise of the foot of heat exchanger 1, also can suppress thus frosting degree.
In addition, fin that parallel flow type heat exchange portion 3 is used 17 forms as one with the heat exchange conduit 11,13 that front and back two are listed as, therefore in the layout of heat exchange conduit 11,13 so that each row become parallel situation arrange before and after when two row, can improve its assembleability.
In addition, the position between the row before and after becoming in fin 17, is provided with the otch of heat insulation use, and thus, the heat that can suppress to be caused by the temperature difference of 11,13, heat exchange conduit moves, and can improve heat exchanger efficiency.
In addition, fin 17 is fixing highlightedly with respect to heat exchange conduit 11 aweathers, and therefore the temperature of the exterior region of fin 17 approaches air themperature, can avoid making frost concentrate on the exterior region of fin 17 in the time that frosting is turned round.
In addition, as present embodiment 1, can enumerate the example of the heat-exchange method that has used heat exchanger 1, in this heat-exchange method, in the situation that heat exchanger 1 is brought into play function as evaporimeter, cold-producing medium and air (along identical towards flowing) (under macroscopic observation, cold-producing medium and air are all in the past mobile backwards) that substantially flow abreast, under the effect of the pressure loss, cold-producing medium evaporating temperature on flow direction reduces, also temperature reduction on flow direction of air, therefore the temperature difference of cold-producing medium and air diminishes.On the other hand, as condenser performance function in the situation that, cold-producing medium flows substantially opposite to each other with air, and (edge is contrary to flowing) (air flows in the past backwards, cold-producing medium under macroscopic observation from after forward flow), cold-producing medium is temperature reduction on flow direction in overheated, two-phase, supercooling region, air is temperature rise on flow direction, and therefore the temperature difference of cold-producing medium and air diminishes.Also improve thus heat exchanger efficiency.In other words, heat exchanger 1 is as the refrigerant flow path that relates to parallel flow type heat exchange portion 3 and plate finned tube type heat exchange portion 5, have as evaporimeter performance function in the situation that using cold-producing medium and air on fore-and-aft direction along identical towards carry out and as condenser performance function in the situation that by cold-producing medium and air on fore-and-aft direction edge on the contrary towards the refrigerant flow path carrying out.
Embodiment 2.
Next, the heat exchanger of embodiment 2 of the present utility model is described based on Fig. 3 and Fig. 4.Fig. 3 and Fig. 4 respectively about present embodiment 2, with Fig. 1 and Fig. 2 figure with situation.It should be noted that, present embodiment 2 is except the part of following explanation, identical with above-mentioned embodiment 1.In addition, set described later links pipe arrangement and cuts apart and links the connection in the region after pipe arrangement priority declaration is cut apart and illustrate, different from actual appearance, omit the correctness of the length of diagram, the pipe of caliber, and any one in Fig. 3 and Fig. 4 all links the mode that pipe arrangement do not overlap each other and illustrates to cut apart.
The heat exchanger 101 of present embodiment 2 have as the lower header of the row of weather side, utilize partition wall inside to be divided into the inlet header 119 in multiple (being three as a concrete example) space, also there is distributor 131.
When distributor 131 is brought into play function at heat exchanger 101 as evaporimeter, be configured in the downstream of plate finned tube type heat exchange portion 5 and the upstream side of parallel flow type heat exchange portion 3.In more detail, each in multiple spaces of inlet header 119 has arrival end 119a, the port of export 27b of the heat pipe 27 of plate finned tube type heat exchange portion 5 and distributor 131 link pipe arrangement 129a by a set and are connected, and multiple (three) arrival end 119a of inlet header 119 connects with the corresponding link pipe arrangement 129b of cutting apart respectively that distributor 131 is cut apart in link pipe arrangement 129b by multiple (three) separately.Cut apart link pipe arrangement 129b and bring into play function as capillary.It should be noted that, be also divided into accordingly multiple (three) with inlet header 119 across at least prostatitis side of row collector 123.
In present embodiment 2 as described above, in the situation that heat exchanger 101 is brought into play function as evaporimeter, cold-producing medium is after flowing out plate finned tube type heat exchange portion 5, utilize distributor 131 to be branched off into three tunnels, flow into three spaces of the inlet header 119 of the bottom of the row of the weather side that is positioned at parallel flow type heat exchange portion 3.Afterwards, in the interior rising of heat exchange conduit 11, utilize across row collector 123 and move between row, after flowing down in heat exchange conduit 13, flow out from the outlet header 21 of the row of downwind side.
In above-mentioned present embodiment 2, outside the above-mentioned advantage of embodiment 1, obtain advantage as described below.The inside that is attached to the collector of the bottom of the row of the weather side of parallel flow type heat exchange portion 3 is divided into three places, and therefore the size in the each space in collector diminishes, and can make the cold-producing medium in collector distribute adjustment to become easy.In addition, link multiple capillaries between distributor and collector (cut apart and link pipe arrangement) length separately by adjustment, also can make cold-producing medium distributed uniform, in addition, because the loss of overpressure in distributor and capillary is larger, therefore as evaporimeter performance function in the situation that, can make the evaporating temperature of plate finned tube type heat exchange portion increase, can suppress the white growth of heat exchanger bottom.
Embodiment 3.
Then,, based on Fig. 5 and Fig. 6, the refrigerating circulation system aircondition related to embodiment 3 of the present utility model describes.Fig. 5 is the figure that represents the summary of the refrigerating circulation system aircondition of present embodiment 3, and Fig. 6 is the top view that schematically shows the off-premises station of the refrigerating circulation system aircondition of present embodiment 3.
As described in Figure 5, freeze cycle aircondition 251 possesses the freeze cycle loop that at least comprises compressor 253, outdoor heat exchanger 255, throttling arrangement (expansion valve) 257, indoor heat exchanger 259.It should be noted that, the arrow of Fig. 5 represents to carry out the flow direction of the cold-producing medium in the situation of cooling operation.In addition, in freeze cycle aircondition 251, be provided with the fan of blowing separately 261 to outdoor heat exchanger 255 and indoor heat exchanger 259 and the CD-ROM drive motor 263 that said fans 261 is rotated.
Off-premises station 351 in freeze cycle aircondition 251, the inside of its framework is separated plate 365 and is divided into Machine Room 367 and plenum chamber 369.In Machine Room 367, contain compressor 253, in plenum chamber 369, contain outdoor heat exchanger 255, fan 261.
In present embodiment 3, the side in above-mentioned outdoor heat exchanger 255 and indoor heat exchanger 259 or both sides use the heat exchanger 1 of above-mentioned embodiment 1 or the heat exchanger 101 of embodiment 2.Thus, can realize the freeze cycle aircondition that energy efficiency is higher.It should be noted that, energy efficiency is made up of following formula.
Heat energy efficiency=indoor heat exchanger (condenser) ability/input entirely
Cooling power efficiency=indoor heat exchanger (evaporimeter) ability/input entirely
In addition, in the case of using the parallel flow type heat exchange portion of wave-shaped fins, at the two ends of left and right directions, pipe arrangement is less, the roughly entirety of the frame of the weather side of the fan in off-premises station can configure heat exchanger (parallel flow type heat exchange portion), therefore do not make heat exchanger bending and can guarantee enough erection spaces, thus, also have advantages of and can increase heat exchange efficiency.It should be noted that, in the situation that heat exchanger 1,101 is applied to indoor set, the framework face of the weather side of fan that also can be in indoor set roughly configure on the whole heat exchanger (parallel flow type heat exchange portion), obtain identical advantage.
Above, illustrate content of the present utility model with reference to preferred embodiment, but based on basic fundamental thought of the present utility model and enlightenment, it is self-explantory that those skilled in the art can adopt various deformations.
First, for the heat exchanger 1,101 described in above-mentioned embodiment 1 and 2 and use the freeze cycle aircondition 251 of this heat exchanger, in the cold-producing mediums such as R410A, R32, HFO1234yf, can realize its effect.
In addition, as working fluid, show the example of air and cold-producing medium, but use other gases, liquid, gas-liquid mixture fluid also to realize identical effect.
In addition, in the situation that the heat exchanger 1,101 described in above-mentioned embodiment 1 and 2 uses in indoor set, also can realize identical effect.
In addition, for the heat exchanger 1,101 described in above-mentioned embodiment 1 and 2 and use and have the freeze cycle aircondition 251 of this heat exchanger, utilize mineral oil, alkylbenzene oil system, ester oil system, ether oil system, fluorocarbon oil system etc., no matter whether oil can be dissolved in cold-producing medium, and refrigerator oil can both be realized above-mentioned effect arbitrarily.
In addition, apply flexibly example as of the present utility model other, can enumerate to be applied to and need to make easy to manufacture and improve heat exchange property, improve the example of heat pump assembly of energy-efficient performance.
Description of reference numerals:
1,101 heat exchangers, 3 parallel flow type heat exchange portions, 5 plate finned tube type heat exchange portions, 7 prostatitis parts, 9 rank rear parts, 11,13 heat exchange conduits, 17 fins, 19,119 inlet headers (lower header), 21 outlet headers (lower header), 23 across row collector (upper header), 25 nest plates, 27 heat pipes, 129a set links pipe arrangement, and 129b is cut apart link pipe arrangement, 131 distributors, 251 freeze cycle airconditions, 253 compressors, 255 outdoor heat exchangers, 257 throttling arrangements, 259 indoor heat exchangers, 261 fans.
Claims (10)
1. a heat exchanger, it possesses parallel flow type heat exchange portion, and this parallel flow type heat exchange portion has the multiple heat exchanger tubes that extend along the vertical direction, it is characterized in that,
Described parallel flow type heat exchange portion at least comprises prostatitis part and rank rear part,
Described prostatitis part and described rank rear part have respectively the multiple heat exchanger tubes that extend along described above-below direction,
The front configuration of the bottom of the front surface in described parallel flow type heat exchange portion has the plate finned tube type heat exchange portion of the multiple nest plates that extend along the vertical direction separately,
The port of export of described plate finned tube type heat exchange portion is connected by pipe arrangement with the arrival end of described parallel flow type heat exchange portion,
The lower header of described prostatitis part and described rank rear part is arranged by column split, and the upper header of described prostatitis part and described rank rear part is to be set to one across the mode of row.
2. heat exchanger according to claim 1, is characterized in that,
The foot of described plate finned tube type heat exchange portion is between the foot of fin and the lower header of described prostatitis part of described parallel flow type heat exchange portion.
3. heat exchanger according to claim 1, is characterized in that,
The heat pipe of described plate finned tube type heat exchange portion uses pipe.
4. heat exchanger according to claim 1, is characterized in that,
The number of passages of described plate finned tube type heat exchange portion is less than the number of passages of described parallel flow type heat exchange portion.
5. heat exchanger according to claim 1, is characterized in that,
As the bottom that becomes arrival end refrigerant inlet, described heat pipe and be configured in described nest plate in the situation of evaporimeter performance function.
6. heat exchanger according to claim 1, is characterized in that,
Described heat exchanger has refrigerant flow path, this refrigerant flow path as evaporimeter performance function in the situation that, make cold-producing medium and air on fore-and-aft direction towards identical towards advance and as condenser performance function in the situation that, make cold-producing medium and air on fore-and-aft direction towards on the contrary towards advancing.
7. heat exchanger according to claim 1, is characterized in that,
The fin of described parallel flow type heat exchange portion is outstanding towards upwind side compared with the described heat exchanger tube of described prostatitis part.
8. heat exchanger according to claim 7, is characterized in that,
The inner utilization partition wall of the described lower header of described prostatitis part is split into multiple spaces, and each in described multiple spaces of this lower header has arrival end,
Between described plate finned tube type heat exchange portion and the described lower header of described prostatitis part, distributor is set,
The port of export of described plate finned tube type heat exchange portion links pipe arrangement with described distributor by set and is connected, and the multiple described arrival end of described lower header is cut apart and linked pipe arrangement and be connected by multiple each self-corresponding these that link in pipe arrangement of cutting apart with described distributor separately.
9. a freeze cycle aircondition, it possesses freeze cycle loop, and this freeze cycle loop comprises compressor, outdoor heat exchanger, expansion valve, indoor heat exchanger, it is characterized in that,
In claim 1～8, the heat exchanger of any one is used in a side or the both sides in described outdoor heat exchanger and described indoor heat exchanger.
10. freeze cycle aircondition according to claim 9, is characterized in that,
The fin of described parallel flow type heat exchange portion is wave-shaped fins,
Described parallel flow type heat exchange portion is configured in the framework face entirety of the weather side of the fan in corresponding described outdoor heat exchanger and described indoor heat exchanger.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2013/058995 | 2013-03-27 | ||
| PCT/JP2013/058995 WO2014155560A1 (en) | 2013-03-27 | 2013-03-27 | Heat exchanger and refrigeration cycle air conditioner using same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203798027U true CN203798027U (en) | 2014-08-27 |
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ID=51380232
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420141694.6U Expired - Lifetime CN203798027U (en) | 2013-03-27 | 2014-03-27 | Heat exchanger and refrigeration cycle air conditioning device with same |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2980516B1 (en) |
| JP (1) | JP6157593B2 (en) |
| CN (1) | CN203798027U (en) |
| WO (1) | WO2014155560A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104236057A (en) * | 2014-09-17 | 2014-12-24 | 珠海格力电器股份有限公司 | Combined heat exchanger, window air conditioner using combined heat exchanger, dehumidifier and mobile air conditioner |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102168630B1 (en) * | 2013-11-05 | 2020-10-21 | 엘지전자 주식회사 | Refrigeration cycle of refrigerator |
| JP6765528B2 (en) * | 2017-06-22 | 2020-10-07 | 三菱電機株式会社 | Heat exchanger, refrigeration cycle device and air conditioner |
| CN110470074A (en) * | 2018-05-11 | 2019-11-19 | 开利公司 | Heat exchanger, heat pump system and heat-exchange method |
| EP3822570B1 (en) | 2018-07-11 | 2024-01-03 | Mitsubishi Electric Corporation | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
| JP6765144B1 (en) * | 2019-07-18 | 2020-10-07 | 株式会社 エコファクトリー | Ventilation air conditioning structure |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5296046U (en) * | 1976-01-14 | 1977-07-18 | ||
| JPH0642885Y2 (en) * | 1987-07-30 | 1994-11-09 | 富士重工業株式会社 | Refrigerator Evaporator |
| JP3214278B2 (en) | 1995-02-22 | 2001-10-02 | 株式会社デンソー | Air conditioner |
| JPH11201685A (en) * | 1998-01-08 | 1999-07-30 | Mitsubishi Electric Corp | Heat-exchanger device |
| JP3367467B2 (en) * | 1999-05-17 | 2003-01-14 | 松下電器産業株式会社 | Finned heat exchanger |
| JP4300502B2 (en) * | 2000-06-30 | 2009-07-22 | 株式会社ティラド | Parallel flow type heat exchanger for air conditioning |
| JP3668784B2 (en) * | 2001-07-30 | 2005-07-06 | ダイキン工業株式会社 | Outdoor heat exchanger, air conditioner, and outdoor air conditioning unit manufacturing method |
| JP4889011B2 (en) * | 2006-07-20 | 2012-02-29 | 株式会社Ｂ．Ｔ．Ｐ． | Air conditioning system |
| JP5191817B2 (en) * | 2008-06-19 | 2013-05-08 | シャープ株式会社 | Heat exchanger unit and air conditioner equipped with the same |
| JP5385589B2 (en) * | 2008-10-30 | 2014-01-08 | シャープ株式会社 | Air conditioner outdoor unit |
| JP2010127510A (en) * | 2008-11-26 | 2010-06-10 | Sharp Corp | Heat exchanger |
| SG187000A1 (en) * | 2010-07-13 | 2013-02-28 | Inertech Ip Llc | Systems and methods for cooling electronic equipment |
| JP5079857B2 (en) * | 2010-09-16 | 2012-11-21 | シャープ株式会社 | Air conditioner indoor unit |
-
2013
- 2013-03-27 EP EP13880586.6A patent/EP2980516B1/en active Active
- 2013-03-27 JP JP2015507767A patent/JP6157593B2/en active Active
- 2013-03-27 WO PCT/JP2013/058995 patent/WO2014155560A1/en active Application Filing
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2014
- 2014-03-27 CN CN201420141694.6U patent/CN203798027U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104236057A (en) * | 2014-09-17 | 2014-12-24 | 珠海格力电器股份有限公司 | Combined heat exchanger, window air conditioner using combined heat exchanger, dehumidifier and mobile air conditioner |
| CN104236057B (en) * | 2014-09-17 | 2022-03-11 | 珠海格力电器股份有限公司 | Window machine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014155560A1 (en) | 2014-10-02 |
| EP2980516A4 (en) | 2016-12-07 |
| EP2980516B1 (en) | 2018-01-31 |
| EP2980516A1 (en) | 2016-02-03 |
| JP6157593B2 (en) | 2017-07-05 |
| JPWO2014155560A1 (en) | 2017-02-16 |
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