CN111465812A - Heat exchanger for refrigerator - Google Patents
Heat exchanger for refrigerator Download PDFInfo
- Publication number
- CN111465812A CN111465812A CN201980006418.4A CN201980006418A CN111465812A CN 111465812 A CN111465812 A CN 111465812A CN 201980006418 A CN201980006418 A CN 201980006418A CN 111465812 A CN111465812 A CN 111465812A
- Authority
- CN
- China
- Prior art keywords
- fin
- heat exchanger
- refrigerator
- freezer
- equal
- 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.)
- Pending
Links
- 229910052751 metal Inorganic materials 0.000 claims abstract description 27
- 239000002184 metal Substances 0.000 claims abstract description 27
- 239000012530 fluid Substances 0.000 claims abstract description 17
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 15
- 229910000838 Al alloy Inorganic materials 0.000 claims abstract description 8
- 229910052782 aluminium Inorganic materials 0.000 claims abstract description 7
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims abstract description 7
- 239000011295 pitch Substances 0.000 claims description 45
- 239000003507 refrigerant Substances 0.000 claims description 14
- 229910052745 lead Inorganic materials 0.000 claims description 5
- 229910052697 platinum Inorganic materials 0.000 claims description 5
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 3
- 229910000881 Cu alloy Inorganic materials 0.000 claims description 3
- 229910052802 copper Inorganic materials 0.000 claims description 3
- 239000010949 copper Substances 0.000 claims description 3
- 238000001816 cooling Methods 0.000 abstract description 13
- 238000004804 winding Methods 0.000 abstract 1
- 230000000052 comparative effect Effects 0.000 description 9
- 238000009423 ventilation Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 5
- 238000011156 evaluation Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 4
- 230000005855 radiation Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 230000000149 penetrating effect Effects 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000010257 thawing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
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
- F25B39/02—Evaporators
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/04—Preventing the formation of frost or condensate
-
- 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
-
- 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
-
- 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
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a heat exchanger for a refrigerator-freezer, which can achieve both heat exchange performance and frosting time by more efficiently arranging fins in the heat exchanger. The heat exchanger for a freezer-refrigerator is provided with a plurality of fin groups (2), wherein the plurality of fin groups (2) are arranged at a predetermined interval (C) in the flowing direction (arrow X direction) of a cooling target fluid, and the heat exchanger for a freezer-refrigerator is provided with metal pipes (3), wherein the metal pipes (3) are arranged to sequentially penetrate through the fins (20) in the fin groups (2) and are in a winding form. The fin (20) is formed of a plate made of aluminum or an aluminum alloy. The fin pitch (Pb) in the fin group (2(a)) located most upstream in the flow direction of the fluid to be cooled, the fin pitch (Pt) in the fin group (2(g)) located most downstream, and the fin pitch (Pm) in the fin group (2(m)) located therebetween have the following relationship: pb is more than or equal to 10mm and less than or equal to 20mm, Pt is more than or equal to 1.8mm and less than or equal to 5.0mm, Pm is more than or equal to 2.2mm and less than or equal to 15mm, Pb/Pt is more than or equal to 2 and less than or equal to 11.2, and Pm/Pt is more than or equal to 1 and less than or equal to 8..
Description
Technical Field
The present invention relates to a heat exchanger for a refrigerator-freezer.
Background
A serpentine heat exchanger is generally used as a heat exchanger mounted in a refrigerator-freezer. The serpentine heat exchanger is composed of a plurality of fins arranged in parallel at a predetermined interval from each other in a row and one or more metal pipes penetrating the fins and allowing a refrigerant to flow therethrough. In addition, a plurality of fin groups each including a plurality of fins arranged in a row are arranged in a row and in multiple stages, and the air in the refrigerator as the cooling target fluid flows in the arrangement direction of the fin groups and sequentially passes through the plurality of stages of fin groups.
In a refrigerator-freezer, a heat exchanger is required to be downsized in order to increase the internal volume of food and the like as much as possible while maintaining sufficient refrigerating and freezing performance. On the other hand, in the freezer-refrigerator, since the temperature of the heat exchanger is sometimes lower than 0 ℃, water vapor contained in the air adheres to the fins of the heat exchanger to turn into frost. It has not been clarified what structure can improve the refrigerating and freezing performance, i.e., the heat exchange performance, and can be miniaturized in such a special use environment.
For example, in patent document 1, it is intended to suppress frost clogging, extend the interval of defrosting operation, and suppress temperature increase in a space by removing a part of heat exchange fins on the surface on the air inlet side or/and the upper side of the refrigerant inlet to widen the interval of the heat exchange fins on the surface. However, in the heat exchanger for a freezer-refrigerator in which the adhesion of frost cannot be avoided as described above, the structure of patent document 1 cannot sufficiently obtain the effect.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 2010-210140
Disclosure of Invention
Problems to be solved by the invention
The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger for a refrigerator-freezer that can achieve both heat exchange performance and frost formation time by more efficiently arranging fins in the heat exchanger.
Means for solving the problems
One aspect of the present invention is a heat exchanger for a refrigerator-freezer, characterized in that,
the heat exchanger for a refrigerator-freezer comprises a plurality of stages of fin groups each comprising a plurality of fins arranged in parallel at a predetermined interval from each other in a row, the plurality of stages of fin groups being arranged at a predetermined interval in a flow direction of a fluid to be cooled flowing through the refrigerator-freezer, and the heat exchanger for a refrigerator-freezer comprises one or more metal pipes arranged so as to penetrate the fins in the fin groups in order and to form a serpentine shape,
the fins are formed of a plate made of aluminum or an aluminum alloy,
the fin pitch Pb in the fin group located most upstream in the circulation direction of the cooled fluid, the fin pitch Pt in the fin group located most downstream, and the fin pitch Pm in the fin group located therebetween have the following relationship:
10mm≤Pb≤20mm、
1.8mm≤Pt≤5.0mm、
2.2mm≤Pm≤15mm、
2≤Pb/Pt≤11.2、
1≤Pm/Pt≤8.4。
effects of the invention
As described above, in the heat exchanger for a refrigerator-freezer, the fin pitch is changed so as to be narrowed from the inflow side toward the outflow side of the fluid to be cooled flowing in the refrigerator-freezer, and the specific dimension thereof is limited to the specific range. This makes it possible to make the frosting time relatively long while maintaining the heat exchange performance, thereby making it possible to achieve both the heat exchange performance and the frosting time.
Drawings
Fig. 1 is an explanatory diagram showing a structure of a heat exchanger for a freezer-refrigerator according to embodiment 1.
Detailed Description
As described above, the fin is made of aluminum or an aluminum alloy. More specifically, plates made of materials such as JIS a1050, JIS a1100, JIS a1200, and JIS a7072 can be used.
Preferably, the fin has a thickness of 0.08 to 0.25 mm. When the thickness of the fin is less than 0.08mm, the heat radiation efficiency, that is, "fin efficiency" indicating the ratio of the amount of heat radiation to the actual amount of heat radiation when the entire heat radiation surface is at the same temperature as the heat source may be reduced, while when the thickness of the fin exceeds 0.25mm, the effect of improving the fin efficiency may be saturated, and the entire weight may be increased.
In addition, the arrangement pitch of the fins in the fin group is wider on the inflow side of the fluid (air) to be cooled and becomes narrower toward the outflow side. That is, the fin pitch Pb in the fin group located most upstream in the flow direction of the fluid to be cooled, the fin pitch Pt in the fin group located most downstream, and the fin pitch Pm in the fin group located therebetween are set to be in the ranges of 10mm Pb ≦ 20mm, 1.8mm ≦ Pt ≦ 11.2mm, and 2.2mm ≦ Pm ≦ 15 mm.
When the fin pitch Pb on the side where the fluid to be cooled flows in (the most upstream side) is less than 10mm, clogging due to frost is fast, and ventilation resistance becomes high in advance. In addition, when the fin pitch Pb is wider than 20mm, the number of fins decreases, and therefore, the heat exchange performance is affected.
Since the fin pitch Pm in the second and subsequent stages from the cooling target fluid inflow side (most upstream side) is slightly low in temperature and humidity, it is necessary to increase the number of fins by narrowing the fin pitch as compared with the inflow side (most upstream side) to improve the heat exchange performance. Therefore, the fin pitch Pm is set to 15mm or less. On the other hand, when the flow of air between the fins is taken into consideration, when the fin pitch Pm is less than 2.2mm, improvement in heat exchange performance cannot be expected and ventilation resistance increases, so 2.2mm or more is set.
Since the air having the lowest temperature and humidity flows on the cooling target fluid outflow side (the most downstream side), the number of fins needs to be increased as much as possible. Therefore, the fin pitch Pt on the cooling target fluid outflow side (most downstream side) is set to 5mm or less. On the other hand, if the width is too small, frost adheres to the fins at an early stage, and it is difficult to secure the air duct, and therefore the fin pitch Pt is preferably 1.8mm or more, more preferably 2.2mm or more.
Moreover, the fin pitch Pb, the fin pitch Pt and the fin pitch Pm satisfy the relationship that Pb/Pt is more than or equal to 2 and less than or equal to 11.2, and Pm/Pt is more than or equal to 1 and less than or equal to 8.4. When Pb/Pt is less than 2, Pm is in the middle thereof, and therefore the effect of changing the fin pitch ratio may not be sufficiently exhibited, and when Pb/Pt exceeds 11.2, the following problem may occur: the cooling of the air at the inflow side becomes insufficient, and frost adheres to the surface earlier at an intermediate stage and later. Therefore, it is more preferable that Pb/Pt is 5 or less. On the other hand, when Pm/Pt is less than 1, the following problems may occur: in the middle portion, frost adheres to the middle portion at an early stage, and the ventilation resistance increases, the heat exchange area on the air outflow side becomes insufficient, the heat exchange performance also deteriorates, and when Pm/Pt exceeds 8.4, the following problem may occur: the cooling of the air in the middle portion becomes insufficient, and the fins on the air outflow side frost in advance. Therefore, it is more preferable that Pm/Pt is 6.8 or less.
The relationship between the fin pitch Pb and the fin pitch Pm is not particularly limited, but is 0.3. ltoreq. Pb/Pm. ltoreq.20, preferably 0.7. ltoreq. Pb/Pm. ltoreq.9.1, and more preferably 1 < Pb/Pm. ltoreq.9.1. By adjusting these relationships, the effects of heat exchange performance and frost formation time can be more reliably achieved. When the temperature is outside these ranges, the adjacent fins come into contact with each other to block the passage of the refrigerant, and therefore frost formation is likely to occur or the heat exchange performance is likely to deteriorate.
The metal pipe is preferably made of copper or a copper alloy, or aluminum or an aluminum alloy. Examples of aluminum or aluminum alloys for metal pipes include JIS a1050, JIS a1100, JIS a1200, and JISA 3003. Examples of copper or copper alloy for metal piping include JIS H3300C 1220 and JIS H3300C 5010.
The refrigerant circulating through the metal pipe may be selected from R134a, R600a, and CO2Any one of the above. Among these refrigerants, R600a is most common and has a low environmental load, and therefore is suitable for use in a heat exchanger for a refrigerator-freezer. However, from the viewpoint of cost, R134a, which is cheaper, may be used, and CO, which has a low environmental load, may be used2And the like.
Examples
< embodiment 1>
A heat exchanger 1 for a freezer-refrigerator according to an embodiment of the present invention will be described with reference to fig. 1. As shown in the drawing, the heat exchanger 1 for a refrigerator/freezer includes a plurality of stages of fin groups 2 each including a plurality of fins 20 arranged in parallel at a predetermined interval from each other in a row, the plurality of stages of fin groups 2 are arranged at a predetermined interval C in a flow direction (arrow X direction) of a fluid to be cooled flowing in the refrigerator/freezer, and the heat exchanger 1 for a refrigerator/freezer includes one or more metal pipes 3 arranged so as to sequentially penetrate the fins 20 in the fin groups 2 and to form a serpentine shape.
The fins 20 are formed of rectangular aluminum or aluminum alloy plates. And the fin pitch Pb in the most upstream fin group 2(a) in the circulating direction (the arrow X direction) of the fluid (air) to be cooled, the fin pitch Pt in the most downstream fin group 2(g), and the fin pitch Pm in the fin group 2(m) therebetween have a relationship of 10 mm. ltoreq. Pb. ltoreq.20 mm, 1.8 mm. ltoreq. Pt. ltoreq.5.0 mm, 2.2 mm. ltoreq. Pm. ltoreq.15 mm, 2. ltoreq. Pb/Pt. ltoreq.11.2, 1. ltoreq. Pm/Pt. ltoreq.8.4. The following describes the details further.
(example 1)
The heat exchanger 1 for a refrigerator/freezer according to example 1 has plate fins as fins 20, which are made of a plate material having a material quality of JIS a1050 and a thickness of 0.20 mm. The fins 20 each have a rectangular shape with a short side 21 having a length H of 20mm and a long side 21 having a length W of 60 mm. Then, each fin 20 has two through holes 25, and the metal pipes 3 are inserted into the through holes 25.
The inner diameter d of the through-hole 25 in the fin 20 is
This is a dimension corresponding to the outer diameter of the metal pipe 3. The metal pipe 3 is made of JIS A3003 material and has an outer diameter in the present example
An inner surface grooved tube having a groove in an inner peripheral surface and having a diameter of 8 mm. The wall thickness of the bottom portion of the metal pipe 3 was 0.65mm, the groove depth was 0.65mm, and the number of grooves was 30.
In this example, the fins 20 and the metal pipes 3 are joined by expanding the metal pipes 3 in a state where the metal pipes 3 having a slightly smaller outer diameter are inserted into the through holes 25 of the fins 20. The expansion of the metal pipe 3 can be performed by either a mechanical expansion method in which a mandrel (mandrel) (not shown) is pushed into the metal pipe 3 and moved, or a hydraulic expansion method in which oil is filled into the metal pipe 3 and pressurized.
As shown in fig. 1, the metal pipe 3 is arranged such that: after extending from the tip end 31 (fig. 1) and penetrating the fin group 2(g) on the lowermost stream side (uppermost side in fig. 1), the fin group 2(a) on the uppermost stream side (lowermost side in fig. 1) is passed through the fin group 2 on the upstream side while meandering so as to sequentially pass through the multistage fin group 2 on the upstream side via the plurality of U-shaped connecting portions 35, and after penetrating the fin group 2(a) again via the U-shaped connecting portions 35, the fin group 2(g) on the lowermost stream side (uppermost side in fig. 1) is passed through the fin group 2 on the downstream side while meandering so as to sequentially pass through the multistage fin group 2 on the downstream side via the plurality of U-shaped connecting portions 35 and reaches the tip end 32. When the heat exchanger 1 for a refrigerator/freezer is used, devices necessary for a refrigerator such as a compressor, not shown, are connected to the ends 31 and 32.
The fin group 2 of this example has 7-level specifications of the fin groups 2(a) to 2 (g). The intervals C between the adjacent fin groups 2 were set to 3.0 mm. Regarding the fin pitch, which is the arrangement pitch of the fins 20 in the 7-stage fin group 2, the fin pitch Pb of the most upstream fin group 2(a) is the widest and 10.0mm, the fin pitch Pt of the most downstream fin group 2(g) is the narrowest and 2.2mm, and the fin pitch Pm of all the fin groups 2(m) therebetween is 4.0 mm.
Comparative examples 1 and 2
Comparative example 1 is an example having the same basic structure as example 1 and aligning the fin pitches Pb, Pt, Pm of all the fin groups 2 from the most upstream to the most downstream to 2.2 mm. Comparative example 2 is an example having the same basic structure as example 1 and aligning the fin pitches Pb, Pt, Pm of all the fin groups 2 from the most upstream to the most downstream to 10.0 mm.
(evaluation test)
The heat exchangers of example 1, comparative example 1, and comparative example 2 were assembled in an actual refrigerating and freezing system, and an experiment was conducted to evaluate the performance thereof. Specifically, a known refrigeration system is configured by connecting necessary components such as an expansion valve and a compressor to each heat exchanger, and the refrigeration performance is evaluated under predetermined conditions.
First, the lower surface of the lower fin group 2(a) in fig. 1 is an inlet of air as a cooling medium in the heat exchanger, and the upper side in the figure is an outlet. Then, regarding the conditions of the air introduced into the inlet (air side conditions), the dry bulb temperature was set to 5.0 ℃, the wet bulb temperature was set to 3.8 ℃, and the wind speed was set to 0.5 m/s.
Regarding the conditions of the refrigerant introduced into the inlet of the metal pipe 3 (refrigerant side conditions), the pressure on the inlet side of the expansion valve (not shown) was set to 1.826MPa, the temperature on the inlet side of the expansion valve was set to 25 ℃, the pressure at the outlet of the heat exchanger was set to 0.485MPa, and the temperature at the outlet of the heat exchanger was set to-8 ℃.
Then, air as a cooling target fluid and the refrigerant were circulated, and the air temperature at the inlet and outlet of the heat exchanger and the refrigerant temperature at the inlet and outlet of the heat exchanger were measured for about 150 minutes. Then, the heat exchange capacity (air-side capacity [ W ]) based on the air is calculated from the temperature difference between the air at the inlet and the air at the outlet of the heat exchanger. Further, the heat exchange capacity (refrigerant side capacity [ W ]) based on the refrigerant is calculated from the temperature difference between the refrigerant at the inlet and the refrigerant at the outlet of the heat exchanger. Further, as the calculated values, both an average value and an instantaneous maximum value (instantaneous value) in the experimental period are obtained.
Further, a differential pressure between an inlet and an outlet of the air in the heat exchanger (fin group) was measured by a differential pressure gauge, and the value was used as ventilation resistance (pressure loss). Then, the frosting time was evaluated by the time from the start of the evaluation until the ventilation resistance (pressure loss) reached 150 Pa.
The obtained maximum heat exchange capacity, average heat exchange capacity, and frosting time were evaluated in the ratios of example 1 to comparative example 2, with the result of example 1 being 1. The evaluation results are shown in table 1.
[ Table 1]
As shown in table 1, example 1 has the following results compared with comparative example 1: although the maximum heat exchange capacity and the average heat exchange capacity are poor, it can be extended to more than 3 times for the frosting time. In addition, example 1 has the following results compared with comparative example 2: although the frosting time is poor, the maximum heat exchange capacity and the average heat exchange capacity are greatly improved. From these results, it can be said that example 1 can achieve both heat exchange performance and frosting time as compared with comparative examples 1 and 2.
< embodiment 2>
In a heat exchanger having a plurality of different structures in which the fin pitches Pb, Pt, Pm are changed as shown in table 2 based on the structure shown in fig. 1 in embodiment 1 (the structure of embodiment 1), the allowable range of combinations of the fin pitches is evaluated under the same conditions as in the case of the evaluation test in embodiment 1.
The outlet temperature of air as a cooling target medium was evaluated as appropriate when it reached-5.2 ℃ or lower, and as insufficient cooling performance when it exceeded-5.2 ℃.
The pressure loss (Pa) was measured by a differential pressure gauge at the inlet and outlet of the air in the heat exchanger (fin group) in the flow path of the ventilation, and the pressure loss 1 hour after the start of ventilation was examined. The pressure loss was evaluated as appropriate when the pressure loss was 10Pa or less, and the pressure loss was evaluated as high pressure loss when the pressure loss exceeded 10 Pa.
Regarding the frosting performance, the pressure loss 48 hours after the start of ventilation was measured in the same manner as described above, and the case where the pressure loss at this time was 10Pa or less was evaluated as a pass of the frosting performance, and the case where the pressure loss exceeded 10Pa due to the frosting of the fins was evaluated as a fail of the frosting performance. The evaluation results are shown in table 2.
[ Table 2]
As can be seen from Table 2, the structures E1, E4, E9 to E11, E13 and E14, which have all the relationships of Pb 10mm or more and 20mm or less, Pt 1.8mm or more and 5.0mm or less, Pm 2.2mm or more and 15mm or less, Pb/Pt 2 or more and 11.2 and Pm/Pt 1 or more and 8.4 or less, for the fin pitches Pb, Pt and Pm, were all evaluated as appropriate or acceptable. Among them, it is found that the structures E1 and E4, which further have the relationships of Pt ≥ 2.2mm, Pb/Pt ≤ 5, and Pm/Pt ≤ 6.8, exhibit particularly excellent characteristics of small pressure loss and good balance.
On the other hand, in the structures C2 and C3, the most upstream fin pitch Pb was too narrow, and the Pb/Pt range also deviated from the appropriate range, failing to produce frost.
With the structure C5, the fin pitch Pb at the most upstream is too wide, and the cooling performance is insufficient.
Structure C6 gives the following result: the fin pitch Pm at the intermediate position is too narrow, the range of Pm/Pt also deviates from the appropriate range, and the pressure loss becomes too high.
In the structure C7, the fin pitch Pm at the intermediate position is too wide, and the cooling performance is insufficient.
Structure C8 gives the following result: the most downstream fin pitch Pt is too narrow, the range of Pb/Pt and the range of Pm/Pt deviate from the proper ranges, and the pressure loss becomes too high.
With structure C12, the most downstream fin pitch Pt is too wide and the cooling performance is insufficient.
Claims (7)
1. A heat exchanger for a refrigerator-freezer is characterized in that,
the heat exchanger for a refrigerator-freezer comprises a plurality of stages of fin groups each comprising a plurality of fins arranged in parallel at a predetermined interval from each other in a row, the plurality of stages of fin groups being arranged at a predetermined interval in a flow direction of a fluid to be cooled flowing through the refrigerator-freezer, and the heat exchanger for a refrigerator-freezer comprises one or more metal pipes arranged so as to penetrate the fins in the fin groups in order and to form a serpentine shape,
the fins are formed of a plate made of aluminum or an aluminum alloy,
the fin pitch Pb in the fin group located most upstream in the circulation direction of the cooled fluid, the fin pitch Pt in the fin group located most downstream, and the fin pitch Pm in the fin group located therebetween have the following relationship:
10mm≤Pb≤20mm、
1.8mm≤Pt≤5.0mm、
2.2mm≤Pm≤15mm、
2≤Pb/Pt≤11.2、
1≤Pm/Pt≤8.4。
2. the heat exchanger for a refrigerator-freezer according to claim 1, wherein,
the fin pitches Pb, Pt, and Pm have the following relationship:
2.2mm≤Pt≤5.0mm、
2≤Pb/Pt≤5、
1≤Pm/Pt≤6.8。
3. the heat exchanger for a freezer-refrigerator according to claim 1 or 2, wherein,
the metal tubing has an outer diameter
The inner surface of the tube is provided with a groove of 5-10 mm.
4. The heat exchanger for a refrigerator-freezer according to any one of claims 1 to 3, wherein,
the metal piping is made of copper or copper alloy, or aluminum alloy.
5. The heat exchanger for a freezer-refrigerator according to any one of claims 1 to 4, wherein,
a plurality of metal pipes are inserted through one fin.
6. The heat exchanger for a freezer-refrigerator according to any one of claims 1 to 5, wherein,
the refrigerant circulating in the metal pipe is R134a, R600a, CO2Any one of the above.
7. The heat exchanger for a freezer-refrigerator according to any one of claims 1 to 6, wherein,
the metal pipe and the fin are assembled together by mechanical or hydraulic expansion.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018044306 | 2018-03-12 | ||
| JP2018-044306 | 2018-03-12 | ||
| PCT/JP2019/009473 WO2019176803A1 (en) | 2018-03-12 | 2019-03-08 | Heat exchanger for freezer refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111465812A true CN111465812A (en) | 2020-07-28 |
Family
ID=67906714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980006418.4A Pending CN111465812A (en) | 2018-03-12 | 2019-03-08 | Heat exchanger for refrigerator |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPWO2019176803A1 (en) |
| CN (1) | CN111465812A (en) |
| WO (1) | WO2019176803A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112113379A (en) * | 2020-10-12 | 2020-12-22 | 珠海格力电器股份有限公司 | Evaporating device, control method thereof and refrigeration display cabinet |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0602909D0 (en) * | 2005-12-21 | 2006-03-22 | Hook Martin | A heating module and system controller that increases the efficiency of heat pumps for domestic hot water and heating |
| JP2009079807A (en) * | 2007-09-26 | 2009-04-16 | Mitsubishi Electric Corp | Refrigerator |
| CN201311135Y (en) * | 2008-08-11 | 2009-09-16 | 宁波惠康实业有限公司 | Fin heat exchanger |
| CN203629159U (en) * | 2013-11-29 | 2014-06-04 | 珠海格力电器股份有限公司 | Refrigerant distributing device, flat tube heat exchanger, and air conditioner and heat-pump water heater employing flat tube heat exchanger |
| CN204187896U (en) * | 2014-10-16 | 2015-03-04 | 珠海格力电器股份有限公司 | Evaporimeter and air-cooler |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59217465A (en) * | 1983-05-25 | 1984-12-07 | 株式会社日本アルミ | Fin tube evaporator and manufacture thereof |
| JPS6179778U (en) * | 1984-10-30 | 1986-05-28 | ||
| CN1737470A (en) * | 2005-07-21 | 2006-02-22 | 上海交通大学 | Ribbed pipe type evaporator |
| JP5129464B2 (en) * | 2006-07-06 | 2013-01-30 | 住友軽金属工業株式会社 | Heat exchanger for refrigerator and method for manufacturing the same |
| JP2008064457A (en) * | 2007-11-28 | 2008-03-21 | Sharp Corp | Heat exchanger |
| JP5138408B2 (en) * | 2008-02-14 | 2013-02-06 | 住友軽金属工業株式会社 | Fin and tube heat exchanger |
| JP5405158B2 (en) * | 2009-03-10 | 2014-02-05 | 三洋電機株式会社 | Evaporator |
| JP5958075B2 (en) * | 2012-05-22 | 2016-07-27 | 三菱電機株式会社 | Showcase |
| JP6490221B2 (en) * | 2015-07-21 | 2019-03-27 | 三菱電機株式会社 | refrigerator |
-
2019
- 2019-03-08 CN CN201980006418.4A patent/CN111465812A/en active Pending
- 2019-03-08 JP JP2020506481A patent/JPWO2019176803A1/en active Pending
- 2019-03-08 WO PCT/JP2019/009473 patent/WO2019176803A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0602909D0 (en) * | 2005-12-21 | 2006-03-22 | Hook Martin | A heating module and system controller that increases the efficiency of heat pumps for domestic hot water and heating |
| JP2009079807A (en) * | 2007-09-26 | 2009-04-16 | Mitsubishi Electric Corp | Refrigerator |
| CN201311135Y (en) * | 2008-08-11 | 2009-09-16 | 宁波惠康实业有限公司 | Fin heat exchanger |
| CN203629159U (en) * | 2013-11-29 | 2014-06-04 | 珠海格力电器股份有限公司 | Refrigerant distributing device, flat tube heat exchanger, and air conditioner and heat-pump water heater employing flat tube heat exchanger |
| CN204187896U (en) * | 2014-10-16 | 2015-03-04 | 珠海格力电器股份有限公司 | Evaporimeter and air-cooler |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112113379A (en) * | 2020-10-12 | 2020-12-22 | 珠海格力电器股份有限公司 | Evaporating device, control method thereof and refrigeration display cabinet |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2019176803A1 (en) | 2021-03-11 |
| WO2019176803A1 (en) | 2019-09-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10627175B2 (en) | Heat exchanger and refrigeration cycle apparatus | |
| JP6109303B2 (en) | Heat exchanger and refrigeration cycle apparatus | |
| EP3021064B1 (en) | Heat pump device | |
| JP2008215733A (en) | Fin and tube type heat exchanger | |
| EP2455687A2 (en) | Outdoor heat exchanger and heat pump having the same | |
| US10101091B2 (en) | Heat exchanger and refrigeration cycle apparatus using the same heat exchanger | |
| CN105823271B (en) | Heat exchanger | |
| EP3191784B1 (en) | Turbulators in enhanced tubes | |
| CN111465812A (en) | Heat exchanger for refrigerator | |
| JP6415976B2 (en) | Heat transfer tube for fin-and-tube heat exchanger and fin-and-tube heat exchanger using the same | |
| JP6053693B2 (en) | Air conditioner | |
| JP5627635B2 (en) | Air conditioner | |
| JP2005201492A (en) | Heat exchanger | |
| JPWO2017208419A1 (en) | Fin tube type heat exchanger and heat pump device provided with the fin tube type heat exchanger | |
| JP5591285B2 (en) | Heat exchanger and air conditioner | |
| JPWO2020178977A1 (en) | Heat exchanger, heat exchanger unit, and refrigeration cycle equipment | |
| CN111556950A (en) | Heat exchanger for refrigerator | |
| CN113646597B (en) | Refrigeration cycle device | |
| JP5864030B1 (en) | Heat exchanger and refrigeration cycle apparatus equipped with the heat exchanger | |
| US11965701B2 (en) | Heat exchanger and refrigeration cycle apparatus | |
| JP2003279281A (en) | Heat exchanger | |
| US20160076828A1 (en) | Turbulators in enhanced tubes |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |