CN203771807U - Heat exchange device and refrigeration circulation device with heat exchange device - Google Patents
Heat exchange device and refrigeration circulation device with heat exchange device Download PDFInfo
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- CN203771807U CN203771807U CN201420065077.2U CN201420065077U CN203771807U CN 203771807 U CN203771807 U CN 203771807U CN 201420065077 U CN201420065077 U CN 201420065077U CN 203771807 U CN203771807 U CN 203771807U
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- heat
- transfer pipe
- slot part
- area
- pipe
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Abstract
The utility model relates to a heat exchange device and a refrigeration circulation device with the heat exchange device. The heat exchange device at least comprises a first heat conduction pipe (20A) and a second heat conduction pipe (20B), wherein the first heat conduction pipe is arranged on the upstream side relative to gas flowing, the second heat conduction pipe is arranged close to the downstream side compared with the first heat conduction pipe, the second heat conduction pipe and the first heat conduction pipe are arranged in parallel, a groove is formed in the inner face of the first heat conduction pipe, a groove is formed in the inner face of the second heat conduction pipe, the ratio (Aa/Do) of the area (Aa) of the portion, in the plane orthogonal to the pipe axis, of the groove portion of the first heat conduction pipe to the outer diameter (Do) of the first heat conduction pipe is larger than the ratio (Ab/Do) of the area (Ab) of the portion, in the plane orthogonal to the pipe axis, of the groove portion of the second heat conduction pipe to the outer diameter (Do) of the second heat conduction pipe, and inner-pipe heat conduction performance such as condensation and evaporation can be improved without increasing pressure loss.
Description
Technical field
The utility model relates to the heat-exchanger rig that possesses heat-transfer pipe and the refrigerating circulatory device with this heat-exchanger rig, and the pipe internal surface of this heat-transfer pipe has groove.
Background technology
In the past, in the heat exchanger using at refrigerating plant, aircondition or heat pump, in general, on a plurality of fins of spacing parallel arranging with regulation, through hole was set, heat-transfer pipe through through hole configure.Heat-transfer pipe configures multiple row along airflow direction, is formed with groove on inner surface.Heat-transfer pipe becomes a part for the refrigerant loop in refrigerating circulatory device, and cold-producing medium (fluid) is in pipe internal flow.
The angled mode of direction that the groove of pipe internal surface extends with tube axial direction and groove is processed to helical form.By forming groove, can make pipe internal surface produce concavo-convex,, the space of recess is called to slot part here, the convex portion that the sidewall of the groove by adjacent is formed is called tooth portion.
And cold-producing medium mobile in such heat-transfer pipe for example, by the undergoing phase transition of heat exchange (condensation or evaporation) of the fluid with in heat-transfer pipe flows outside (air).And, in order to carry out efficiently this phase change, liquid refrigerant maintenance effect between the slot part that utilizes fluid agitation effect that surface area in pipe increases, produced by slot part, accompanies with the capillarity of slot part, the improving of heat transfer property (for example, patent documentation 1) of realizing heat-transfer pipe.
[prior art document]
[patent documentation]
[patent documentation] Japanese kokai publication hei 5-322471 communique (Fig. 1)
Yet, in above-mentioned heat exchanger, by making inner surface separation and the groove lead angle of heat-transfer pipe of air-flow upstream side less than the inner surface separation of the heat-transfer pipe of airflow downstream side and groove lead angle, improve thus the heat transfer facilitation effect of groove.But, make like this separation of heat-transfer pipe of air-flow upstream side and groove lead angle than the inner surface separation of the heat-transfer pipe of airflow downstream side and the little heat exchanger of groove lead angle in, the maintenance dose of liquid refrigerant diminishes, and exists the interior pyroconductivity reduction of pipe, the efficiency factor (COP) of the heat-transfer pipe of air-flow upstream side to reduce such difficult point.
Utility model content
The utility model is researched and developed for solving described problem, its objective is a kind of heat-exchanger rig is provided, and can improve the interior pyroconductivity of pipe of heat exchanger, does not increase overpressure loss and obtains predefined heat transfer property.
Heat-exchanger rig of the present utility model at least has the first heat-transfer pipe and the second heat-transfer pipe, described the first heat-transfer pipe with respect to the flow arrangement of gas at upstream side, described the second heat-transfer pipe is being compared downstream with described the first heat-transfer pipe and described the first heat-transfer pipe configures side by side, described the first heat-transfer pipe and described the second heat-transfer pipe have groove at pipe inner face, the area (Aa) of slot part in described the first heat-transfer pipe and plane tubular axis quadrature and the ratio (Aa/Do) of external diameter (Do) form the area (Ab) of slot part and the ratio (Ab/Do) of external diameter (Do) being greater than in described the second heat-transfer pipe and plane tubular axis quadrature.
Preferably, described heat-exchanger rig has a plurality of described heat exchangers, between described a plurality of heat exchanger, via dehumidifying valve, connect, interval under cooling operation before from refrigerant inlet to described dehumidifying valve, or under heating running after described dehumidifying valve to the interval of refrigerant outlet, the area (Aa) of slot part and the ratio (Aa/Do) of external diameter (Do) in described the first heat-transfer pipe and plane tubular axis quadrature form the area (Ab) of slot part and the ratio (Ab/Do) of external diameter (Do) in described heat-transfer pipe and plane tubular axis quadrature that is greater than described the second heat-transfer pipe.
Preferably, the area (Aa) of slot part in described the first heat-transfer pipe and plane tubular axis quadrature and the ratio (Aa/Do) of external diameter (Do) are at 0.0075(mm
2/ mm) to 0.0125(mm
2/ mm) in scope, form, the area (Ab) of slot part in described the second heat-transfer pipe and plane tubular axis quadrature and the ratio (Ab/Do) of external diameter (Do) are at 0.0028(mm
2/ mm) to 0.0074(mm
2/ mm) in scope, form.
Preferably, do not change described the first heat-transfer pipe and described the second heat-transfer pipe described slot part groove to heavens, make the separation of described slot part of described the first heat-transfer pipe larger than the separation of the described slot part of described the second heat-transfer pipe, make thus the described of described the first heat-transfer pipe form and be greater than the described than (Ab/Do) of described the second heat-transfer pipe than (Aa/Do).
The utility model also provides a kind of refrigerating circulatory device, it at least has compressor, condenser, pressure reducer and evaporimeter, they are connected to loop-like by refrigerant piping, the heat-exchanger rig described in operation technique scheme 1 or 2 is as described condenser or described evaporimeter.
The effect of utility model
According to heat-exchanger rig of the present utility model, owing at least thering is the first heat-transfer pipe and the second heat-transfer pipe, described the first heat-transfer pipe with respect to the flow arrangement of gas at upstream side, described the second heat-transfer pipe is compared in downstream and described the first heat-transfer pipe and is configured side by side with described the first heat-transfer pipe, described the first heat-transfer pipe and described the second heat-transfer pipe have groove at pipe inner face, the area (Aa) of slot part in described the first heat-transfer pipe and plane tubular axis quadrature and the ratio (Aa/Do) of external diameter (Do) form the area (Ab) of slot part and the ratio (Ab/Do) of external diameter (Do) being greater than in described the second heat-transfer pipe and plane tubular axis quadrature, so the liquid refrigerant being maintained in slot part becomes many.Thus, compare with heat-transfer pipe in the past, can not increase the pressure loss and improve the intraductal heat transfer performance of condensation, evaporation, heat exchanger effectiveness improves.
Accompanying drawing explanation
Fig. 1 means the mobile figure of cold-producing medium of the heat-exchanger rig of embodiment 1 of the present utility model.
Fig. 2 is that side is observed the partial enlarged drawing of the vertical direction section that the heat-exchanger rig of embodiment 1 of the present utility model sees from the side.
Fig. 3 is the key diagram that the liquid refrigerant between the slot part that accompanies of capillarity in the heat-transfer pipe of first row of heat-exchanger rig of embodiment 1 of the present utility model and slot part keeps effect.
Fig. 4 is the refrigerant loop figure of the air conditioner of embodiment 2 of the present utility model.
The explanation of Reference numeral
1 heat-exchanger rig, 1A main heat exchanger, 1B auxiliary heat exchanger, 10 fins, 20 heat-transfer pipes, the heat-transfer pipe of 20A first row (the first heat-transfer pipe), the heat-transfer pipe (the second heat-transfer pipe) that 20B secondary series is later, 21a, 21b slot part, 22a, 22b tooth portion, 30 dehumidifying valves, 40 liquid refrigerants, 50 indoor sets, 60 off-premises stations, 61 compressors, 62 cross valves, 63 outdoor heat exchangers, 64 pressure reducers, 65 indoor heat exchangers, 66 outdoor fans, 67 indoor fans, 68 air valves, 69 liquid valves, 70 refrigerant pipings, the area of the slot part in the heat-transfer pipe of Aa first row and plane tubular axis quadrature, the area of the slot part in the heat-transfer pipe that Ab secondary series is later and plane tubular axis quadrature, Do external diameter, the separation of the slot part of the heat-transfer pipe of Pa first row, the separation of the slot part of the heat-transfer pipe of Pb secondary series.
The specific embodiment
Embodiment 1
Fig. 1 means the mobile figure of cold-producing medium of the heat-exchanger rig of embodiment 1 of the present utility model.In Fig. 1, heat-exchanger rig 1 is the heat exchanger of the fin tube type that is widely used as the evaporimeter of refrigerating plant or aircondition, condenser.
The heat-exchanger rig 1 of present embodiment 1 has the group of at least 2 (main heat exchanger 1A and auxiliary heat exchanger 1B) heat exchangers, the group of this heat exchanger is formed by following mode, make that a plurality of heat-transfer pipes 20 at pipe internal surface with groove are interted to the heat exchanger that forms in a plurality of fins 10, along the flow direction of gas mobile between a plurality of fins 10, multiple row is set, then the heat exchanger being formed by this multiple row.And, between these main heat exchangers 1A and auxiliary heat exchanger 1B, via dehumidifying valve 30, connect.In addition, dehumidifying valve 30 is in when dehumidifying (with the dehumidifying of carrying out in heating clamber simultaneously), a part for heat exchanger is used as condenser, uses and arrange other parts as evaporimeter.
Heat-transfer pipe 20 becomes a part for the refrigerant loop in refrigerating circulatory device, cold-producing medium is in pipe internal flow, heat-transfer pipe 20 is delivered to externally mobile air by the heat of the cold-producing medium in internal flow via fin 10, thus, the heat transfer area that is configured to the contact-making surface between expansion and air, can carry out the heat exchange between cold-producing medium and air efficiently.
Fig. 2 is that side is observed the partial enlarged drawing of the vertical direction section that the heat-exchanger rig of embodiment 1 of the present utility model sees from the side, represents enlargedly shape and the separation of the pipe internal surface of heat-transfer pipe 20.Fig. 3 is the key diagram that the liquid refrigerant between the slot part that accompanies of capillarity in the heat-transfer pipe of first row of heat-exchanger rig of embodiment 1 of the present utility model and slot part keeps effect.Under cooling operation from refrigerant inlet to dehumidifying the interval before valve 30, or under heating running from dehumidifying valve 30 after to the interval of refrigerant outlet, from the first heat-transfer pipe shown in Fig. 2, be windward side play first row heat-transfer pipe 20A and plane tubular axis quadrature in the area A a(of slot part 21a hereinafter referred to as " the area A a of the slot part 21a of heat-transfer pipe 20A ") be greater than the second heat-transfer pipe with the ratio (Aa/Do) of outer diameter D o, from windward side the area A b(of the slot part 21b later heat-transfer pipe 20B and plane tubular axis quadrature of secondary series hereinafter referred to as " the area A b of the slot part 21b of heat-transfer pipe 20B ") form with the ratio of outer diameter D o (Ab/Do).; by making the separation Pa of slot part 21a of the heat-transfer pipe 20A of first row from windward side be greater than the separation Pb of the slot part 21b of the later heat-transfer pipe 20B of from windward side secondary series; thus; do not change these heat-transfer pipes 20A, 20B slot part 21a, 21b groove to heavens, make the described of heat-transfer pipe 20A of first row from windward side be greater than the described than (Ab/Do) of the later heat-transfer pipe 20B of from windward side secondary series than (Aa/Do).
Among the heat-transfer pipe 20A of first row from windward side, the temperature difference of air and cold-producing medium is large.That is to say, from windward side, the heat-transfer pipe 20A of first row is that liquid refrigerant exists to obtain many regions.Thus, if increase the area A a of slot part 21b and the ratio (Aa/Do) of outer diameter D o of the heat-transfer pipe 20A of first row, as illustrated in fig. 3 and the liquid refrigerant being kept by the 22a of tooth portion between slot part 40 that accompanies of the capillarity of slot part 21a become many, the 22a of tooth portion that sidewall by the slot part 21a by adjacent forms, heat exchanger effectiveness improves.
On the other hand, the heat-transfer pipe 20B after secondary series from windward side, the temperature difference of air and cold-producing medium is little, is the region that liquid refrigerant exists less, is maintained at liquid refrigerant 40(in slot part 21b with reference to Fig. 3) tail off.Thus, by reducing the area A b of slot part 21b and the ratio (Ab/Do) of outer diameter D o of the later heat-transfer pipe 20B of secondary series, can make and the liquid refrigerant 40 being kept by the 22b of tooth portion between slot part that the capillarity of slot part 21b accompanies relatively increases, the 22b of tooth portion that the sidewall by the slot part 21b by adjacent forms improves heat exchanger effectiveness.
In the heat-exchanger rig 1 of present embodiment 1, under cooling operation from refrigerant inlet to dehumidifying the interval before valve 30 or heating under running after dehumidifying valve 30 to the interval of refrigerant outlet, from windward side, the heat-transfer pipe 20A of first row becomes 0.0075(mm with the area A a of the slot part 21a of heat-transfer pipe 20A and the ratio (Aa/Do) of outer diameter D o
2/ mm) to 0.0125(mm
2the mode of scope/mm) forms.In addition, from windward side, the later heat-transfer pipe 20B of secondary series becomes 0.0028(mm with the area A b of the slot part 21b of heat-transfer pipe 20B and the ratio (Ab/Do) of outer diameter D o
2/ mm) to 0.0074(mm
2the mode of scope/mm) forms.
Like this, in heat-exchanger rig 1, set the area A a of the slot part 21a of the heat-transfer pipe 20A of first row from windward side for 0.0075(mm with the ratio (Aa/Do) of outer diameter D o
2/ mm) to 0.0125(mm
2the reason of scope/mm) is, if make the area A a of slot part 21a and the ratio (Aa/Do) of outer diameter D o of the heat-transfer pipe 20A of first row compare 0.0075(mm
2/ mm) little, the liquid refrigerant being maintained in slot part 21a tails off, and to the thickness of liquid film thickening of the 22a of tooth portion, intraductal heat transfer performance reduces as a whole.In addition, if make the area A a of slot part 21a and the ratio (Aa/Do) of outer diameter D o of the heat-transfer pipe 20A of first row compare 0.0125(mm
2/ mm) large, liquid refrigerant keeps effect to reduce, and intraductal heat transfer performance reduces as a whole.By making the area A a of slot part 21a and the ratio (Aa/Do) of outer diameter D o of the heat-transfer pipe 20A of first row from windward side become aforesaid scope, utilize as illustrated in fig. 3 the liquid refrigerant that the capillarity with slot part 21a in the heat-transfer pipe 20A of first row accompanies to keep effect, can improve intraductal heat transfer performance.
In addition, in heat-exchanger rig 1, set the area A b of the slot part 21b of the heat-transfer pipe 20B of secondary series from windward side for 0.0028(mm with the ratio (Ab/Do) of outer diameter D o
2/ mm) to 0.0074(mm
2the reason of scope/mm) is, if make the area A b of slot part 21b and the ratio (Ab/Do) of outer diameter D o of the heat-transfer pipe 20B of secondary series from windward side compare 0.0028(mm
2/ mm) little, the liquid refrigerant being maintained in slot part 21b tails off, and to the thickness of liquid film thickening of the 22b of tooth portion, intraductal heat transfer performance reduces as a whole.In addition, if make the area A b of slot part 21b and the ratio (Ab/Do) of outer diameter D o of the heat-transfer pipe 20B of secondary series from windward side compare 0.0074(mm
2/ mm) large, liquid refrigerant keeps effect to reduce, and intraductal heat transfer performance reduces as a whole.By making the area A b of slot part 21b and the ratio (Ab/Do) of outer diameter D o of the heat-transfer pipe 20B of secondary series from windward side become aforesaid scope, can similarly utilize with the heat-transfer pipe 20A of first row the maintenance effect of the liquid refrigerant 40 that the adjacent capillarity with slot part 21b accompanies, improve intraductal heat transfer performance.
Above, according to the heat-exchanger rig 1 of present embodiment 1, in the indoor heat exchanger a plurality of heat-transfer pipes 20 being interted more than 2 row that form in a plurality of fins 10, under cooling operation from refrigerant inlet to dehumidifying the interval before valve 30, or under heating running from dehumidifying valve 30 after to the interval of refrigerant outlet, the area A b of slot part 21b and the ratio of outer diameter D o that from windward side, the ratio (Aa/Do) of the area A a of the slot part 21a of the heat-transfer pipe 20A of first row and outer diameter D o is greater than the later heat-transfer pipe 20B of from windward side secondary series form (Ab/Do), can improve intraductal heat transfer performance thus, and can improve rate of heat exchange (heat-transfer pipe is by the ratio of the heat of front and back).Thus, can realize energy-conservation.In addition, when can also maintain decrement, the efficiency of the cold-producing medium in refrigerant loop, realize miniaturization.
[embodiment]
Below, about embodiment, compare to illustrate with the comparative example beyond scope of the present utility model.As shown in table 1, the area A a/ outer diameter D o of slot part 21a that has made the heat-transfer pipe 20A of first row is 0.0075,0.0095,0.0115,0.0125(mm
2/ mm) and the area A b/ outer diameter D o of the slot part 21b of the heat-transfer pipe 20B of secondary series be 0.0035(mm
2/ mm) the heat-exchanger rig 1(embodiment 1～4 of embodiment 1～4).In addition, as a comparative example, the area A a/ outer diameter D o of slot part 21a that has made the heat-transfer pipe 20A of first row is 0.005,0.035(mm
2/ mm) and the area A b/ outer diameter D o of the slot part 21b of the heat-transfer pipe 20B of secondary series be 0.0035(mm
2/ mm) heat-exchanger rig (comparative example 1,2).
[table 1]
As known from Table 1, the rate of heat exchange of the heat-exchanger rig 1 of embodiment 1～4 all, higher than the rate of heat exchange of the heat exchanger of comparative example 1,2, has improved intraductal heat transfer performance.
As shown in table 2, the area A a/ outer diameter D o of slot part 21a that has made the heat-transfer pipe 20A of first row is 0.0095(mm
2/ mm) and the area A b/ outer diameter D o of the slot part 21b of the heat-transfer pipe 20B of secondary series is 0.0028,0.0035,0.005,0.0074(mm
2/ mm) heat-exchanger rig 1 of embodiment 5～8.In addition, as a comparative example, the area A a/ outer diameter D o of slot part 21a that has made the heat-transfer pipe 20A of first row is 0.0095(mm
2/ mm) and the area A b/ outer diameter D o of the slot part 21b of the heat-transfer pipe 20B of secondary series is 0.0025,0.008(mm
2/ mm) heat-exchanger rig (comparative example 3,4).
[table 2]
As known from Table 2, the rate of heat exchange of the heat-exchanger rig 1 of embodiment 5～8 all, higher than the rate of heat exchange of the heat exchanger of comparative example 3,4, has improved intraductal heat transfer performance.
In addition, with main heat exchanger 1A and auxiliary heat exchanger 1B, all the group of the heat exchanger forming with multiple row, consist of, that is to say, the structure that fin 10 is divided into multiple row along the flow direction of gas is that example is illustrated, but is not limited to this.For example, can fin 10 not cut apart along the flow direction of gas yet, and adopt the structure that heat-transfer pipe is interted in fin 10 with multiple row along the flow direction of gas.
Embodiment 2
Fig. 4 represents the refrigerant loop figure of the air conditioner of embodiment 2 of the present utility model, and the heat-exchanger rig of explanation in aforesaid embodiment 1 is used as indoor heat exchanger.
It is loop-like that the air conditioner of present embodiment 2 makes compressor 61, cross valve 62, outdoor heat exchanger 63, pressure reducer 64 and indoor heat exchanger 65 connect into by refrigerant piping 70, disposes air valve 68 and liquid valve 69 between indoor set 50 and off-premises station 60.In addition, on outdoor heat exchanger 63, set up outdoor fan 66, on indoor heat exchanger 65, set up indoor fan 67.
In the air conditioner of present embodiment 2, when cooling operation, the gas refrigerant of low-pressure low-temperature is compressed into the gas refrigerant of HTHP by the compressor 61 of off-premises station 60, and carries to cross valve 62.And, by refrigerant piping 70, from cross valve 62, being imported outdoor heat exchanger 63, gas refrigerant liquefaction, using condensation heat to outdoor emitting (outdoor heat exchanger 63 plays a role as condenser).The liquid refrigerant of the high pressure of emitting from outdoor heat exchanger 63 becomes the gas-liquid two-phase cold-producing medium of low-pressure low-temperature by pressure reducer 64, be imported into the indoor heat exchanger 65 of indoor set 50 via liquid valve 69.Here, the airborne heat in absorption chamber, cold-producing medium evaporates, and becomes the gas refrigerant of low-pressure low-temperature, carries out cooling operation (indoor heat exchanger 65 plays a role as evaporimeter).And the gas refrigerant of low-pressure low-temperature is imported into compressor 61 via air valve 68, cross valve 62, carries out refrigerant circulation running.
In the situation that heating running, switch cross valve 62 and make flowing for the contrary direction of the situation with cooling operation of cold-producing medium, thus, indoor heat exchanger 65 plays a role as freezing machine, and outdoor heat exchanger 63 plays a role as evaporimeter.In addition, identical with the situation of cooling operation.
According to present embodiment 2, as indoor heat exchanger 65, use the heat-exchanger rig 1 of aforesaid embodiment 1, therefore can improve the intraductal heat transfer performance of indoor heat exchanger 65, can improve rate of heat exchange (heat-transfer pipe is by the ratio of the heat of front and back).Therefore, can realize energy-conservation.In addition, in the decrement of cold-producing medium that can also be in the refrigerant loop that maintains indoor heat exchanger 65, efficiency, realize miniaturization.
In addition, in aforesaid embodiment 1,2, about heat-exchanger rig of the present utility model, for the situation that is applicable to refrigerating plant or aircondition, be illustrated, but the utility model is not limited to these devices.For example, the utility model can also form refrigerant loop as heat pump assembly, is applicable to have other the refrigerating circulatory device that becomes the heat exchanger of evaporimeter, condenser.
Claims (5)
1. a heat-exchanger rig, it is characterized in that at least thering is the first heat-transfer pipe and the second heat-transfer pipe, described the first heat-transfer pipe with respect to the flow arrangement of gas at upstream side, described the second heat-transfer pipe is being compared downstream with described the first heat-transfer pipe and described the first heat-transfer pipe configures side by side
Described the first heat-transfer pipe and described the second heat-transfer pipe have groove at pipe inner face,
The area (Aa) of slot part in described the first heat-transfer pipe and plane tubular axis quadrature and the ratio (Aa/Do) of external diameter (Do) form the area (Ab) of slot part and the ratio (Ab/Do) of external diameter (Do) being greater than in described the second heat-transfer pipe and plane tubular axis quadrature.
2. heat-exchanger rig as claimed in claim 1, is characterized in that, described heat-exchanger rig has a plurality of described heat exchangers, between described a plurality of heat exchangers, via dehumidifying valve, connect,
Interval under cooling operation before from refrigerant inlet to described dehumidifying valve or heating under running after described dehumidifying valve to the interval of refrigerant outlet, the area (Aa) of slot part and the ratio (Aa/Do) of external diameter (Do) in described the first heat-transfer pipe and plane tubular axis quadrature form the area (Ab) of slot part and the ratio (Ab/Do) of external diameter (Do) in described heat-transfer pipe and plane tubular axis quadrature that is greater than described the second heat-transfer pipe.
3. heat-exchanger rig as claimed in claim 1 or 2, is characterized in that, the area (Aa) of slot part in described the first heat-transfer pipe and plane tubular axis quadrature and the ratio (Aa/Do) of external diameter (Do) are at 0.0075(mm
2/ mm) to 0.0125(mm
2/ mm) in scope, form, the area (Ab) of slot part in described the second heat-transfer pipe and plane tubular axis quadrature and the ratio (Ab/Do) of external diameter (Do) are at 0.0028(mm
2/ mm) to 0.0074(mm
2/ mm) in scope, form.
4. heat-exchanger rig as claimed in claim 1 or 2, it is characterized in that, do not change described the first heat-transfer pipe and described the second heat-transfer pipe described slot part groove to heavens, make the separation of described slot part of described the first heat-transfer pipe larger than the separation of the described slot part of described the second heat-transfer pipe, make thus the described of described the first heat-transfer pipe form and be greater than the described than (Ab/Do) of described the second heat-transfer pipe than (Aa/Do).
5. a refrigerating circulatory device, it at least has compressor, condenser, pressure reducer and evaporimeter, and they connect into loop-like by refrigerant piping, it is characterized in that,
Heat-exchanger rig described in right to use requirement 1 or 2 is as described condenser or described evaporimeter.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2013/053577 | 2013-02-14 | ||
| PCT/JP2013/053577 WO2014125603A1 (en) | 2013-02-14 | 2013-02-14 | Heat exchange device and refrigeration cycle device equipped with same |
| JPPCT/JP2014/052790 | 2014-02-06 | ||
| PCT/JP2014/052790 WO2014125997A1 (en) | 2013-02-14 | 2014-02-06 | Heat exchange device and refrigeration cycle device equipped with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203771807U true CN203771807U (en) | 2014-08-13 |
Family
ID=51288992
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420065077.2U Expired - Fee Related CN203771807U (en) | 2013-02-14 | 2014-02-14 | Heat exchange device and refrigeration circulation device with heat exchange device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203771807U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109964094A (en) * | 2016-11-28 | 2019-07-02 | 三菱电机株式会社 | The manufacturing method of heat exchanger, refrigerating circulatory device and heat exchanger |
-
2014
- 2014-02-14 CN CN201420065077.2U patent/CN203771807U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109964094A (en) * | 2016-11-28 | 2019-07-02 | 三菱电机株式会社 | The manufacturing method of heat exchanger, refrigerating circulatory device and heat exchanger |
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|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140813 Termination date: 20200214 |