CN1550727A - Finned tube heat exchanger for air conditioner - Google Patents
Finned tube heat exchanger for air conditioner Download PDFInfo
- Publication number
- CN1550727A CN1550727A CNA200410045138XA CN200410045138A CN1550727A CN 1550727 A CN1550727 A CN 1550727A CN A200410045138X A CNA200410045138X A CN A200410045138XA CN 200410045138 A CN200410045138 A CN 200410045138A CN 1550727 A CN1550727 A CN 1550727A
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- fin
- heat
- heat transfer
- air conditioner
- 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.)
- Granted
Links
Images
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Abstract
本发明的目的是提供一种空调机的翅片管型热交换器，其目的是提高室内机中所具备的热交换器的热交换性能，同时通过进一步减小热交换器的外形，构成部件和组装工序，来提高生产效率。其解决手段是一种空调机的翅片管型热交换器5，其配置在由室内机和室外机构成的空调机的室内机中，通过使传热管D在以一定间隔并列设置的多个翅片F上贯通形成，在该空调机的翅片管型热交换器中：除了使设置在翅片的传热管贯通部分的翅片套环的外径Dc为：5.5mm≤Dc≤8.7mm以外，还沿气流方向上设置3列传热管，并将沿垂直于传热管气流方向的行间距L1与翅片套环外径Dc的差值与气流方向上列间距L2之间的关系设定为：1.2≤(L1－Dc)/L2≤1.5。
The object of the present invention is to provide a finned tube heat exchanger for an air conditioner. and assembly process to improve production efficiency. The solution is a finned tube heat exchanger 5 for an air conditioner, which is arranged in an indoor unit of an air conditioner composed of an indoor unit and an outdoor unit. In the finned tube heat exchanger of the air conditioner: except that the outer diameter Dc of the fin collar provided on the through part of the heat transfer tube of the fin is: 5.5mm≤Dc≤ In addition to 8.7mm, three rows of heat transfer tubes are arranged along the airflow direction, and the relationship between the difference between the row spacing L1 perpendicular to the airflow direction of the heat transfer tubes and the outer diameter Dc of the fin collar and the column spacing L2 in the airflow direction The setting is: 1.2≤(L1－Dc)/L2≤1.5.
Description
Technical field that the present invention belongs to
The present invention relates to a kind of air-conditioner machine that constitutes by indoor set and off-premises station, relate in particular to fin-and-tube type (fin-tube type) heat exchanger in the indoor set.
Background technology
As domestic air conditioner, adopt usually to constitute, and be connected the air conditioner that indoor set and off-premises station form with electric wiring by the refrigerant pipe by indoor set and off-premises station.Be configured in the heat exchanger in the above-mentioned indoor set, the fin-and-tube type that connects heat-transfer pipe in a plurality of fins of spacing parallel arranging setting becomes main flow.
For this heat exchanger, various schemes have been proposed in order to improve heat exchanger effectiveness.For example, form projection between the heat-transfer pipe breakthrough part of fin divides, the contact area of increase and air perhaps by at heat-transfer pipe breakthrough part branch the collar (collar) being set, increases the contact area with heat-transfer pipe.
In addition, the spy opens to disclose by secondary unit is set in the flat 8-313049 communique increases the structure of heat-transfer pipe columns and line number.
Invent technical task to be solved
But, only on fin, form projection and the collar be set and be difficult to significantly improve heat exchanger effectiveness at heat-transfer pipe breakthrough part branch.In addition, increased flowing resistance and reduced air quantity, therefore heat exchanger effectiveness has significantly been increased owing to only increase the columns of heat-transfer pipe separately.In addition, the latter also can increase formation number of components and parts and assembling procedure quantity, reduces production efficiency.
In addition,, cause indoor set to maximize, just must occupy bigger space (space) because the line number of the heat-transfer pipe that increase airflow direction and vertical direction are arranged in juxtaposition makes the volume of heat exchanger itself become big.
Therefore, the purpose of this invention is to provide a kind of fin tube heat exchanger of air conditioner, this heat exchanger can improve heat exchange performance, and profile is little, and component parts and assembling procedure quantity are few, and production efficiency improves thus.
Solve the means of above-mentioned problem
In order to solve above-mentioned problem, realize goal of the invention, first kind of form of the present invention is:
A kind of fin tube heat exchanger of air conditioner makes heat-transfer pipe connect a plurality of fins that are set up in parallel at certain intervals, in the fin tube heat exchanger of this air conditioner:
List and state heat-transfer pipe along being arranged side by side 3 on the air-flow direction at least,
Above-mentioned fin heat transfer pipe is connected the outer diameter D c that partly goes up the fin collar that is provided with to be set at:
5.5mm≤Dc≤8.7mm，
For the line space L1 along the above-mentioned heat-transfer pipe that is set up in parallel perpendicular to fin draft direction, the column pitch L2 of the heat-transfer pipe that is set up in parallel along airflow direction and the relation between the above-mentioned fin collar outer diameter D c are set at:
1.2≤(L1-Dc)/L2≤1.5
In addition, realize goal of the invention in order to solve above-mentioned problem, second kind of form of the present invention is:
In above-mentioned fin tube heat exchanger, at least being arranged side by side 3 on the airflow direction that is ventilated by fin lists and states heat-transfer pipe, when heating was turned round, refrigerant was set at the relation between the caliber Db of the mobile heat-transfer pipe of gas-liquid two-phase state with the caliber Ds and the refrigerant of the heat-transfer pipe that the supercooling state flows:
0.8≤Ds/Db≤0.9。
Embodiments of the present invention
Embodiments of the invention are described below with reference to accompanying drawings.
Fig. 1 is the profile that the indoor machine of air-conditioner of the present invention that is made of indoor set and off-premises station of expression roughly constitutes.The casing of this indoor set 1 is made of front panel 2A and rear board 2B.Front panel 2A is to front curve and outstanding.Back plate 2B is installed on the wall of air-conditioned room, other part that is used to support above-mentioned front panel 2A and constitutes heat exchanger indoor unit.
The front of plate 2A offers the anterior suction inlet 3 that embeds grid 3a in front, in front plate 2A above offer the top suction inlet 4 that embeds grid 4a.The inboard of front panel 2A forwardly with top suction inlet 3,4 places, is equipped with the filter of not representing among the figure that can mount and dismount, and is used for catching and removing the contained dust of air that sucks indoor set.
In indoor set 1, be equipped with by what front side heat exchanger part 5A and rear side heat exchanger part 5B were combined into and see the fin tube heat exchanger 5 that becomes the V font substantially from the side.In addition, the detailed formation of this fin tube heat exchanger 5 will be described in the back.
Because above-mentioned front side heat exchanger part 5A bending makes the part of anterior suction inlet 3 and top suction inlet 4 opposed mutually.On the front face side of this front side heat exchanger part 5A air cleaning unit 6 is installed, inhaled air further is purified in the indoor set 1.Rear side heat exchanger part 5B makes straight shape, is provided with the position that tilts with respect to top suction inlet 4.
In the V figure space that constitutes by above-mentioned front side heat exchanger part 5A and rear side heat exchanger part 5B, circular cross flow fan 7 is set abreast with this 5A, 5B.Length on the width of the axial length of this cross flow fan 7 and front and back side heat exchanger part 5A, 5B is identical.The gyroaxis of cross flow fan 7 is connected by the fan electromotor of not expressing among the figure and drives.
Above-mentioned fin tube heat exchanger 5 and cross flow fan 7 support by the bracing or strutting arrangement of not expressing among the figure together, and are installed on the above-mentioned back plate 2B.In addition, drain pan 8A before insert the lower end of front side heat exchanger part 5A is in the back drain pan 8B that insert the lower end of rear side heat exchanger part 5B and back plate 2B is integrally formed.
Preceding drain pan 8A and back drain pan 8B are communicated with by the path of not expressing in the accompanying drawing.Back drain pan 8B is than the position height of preceding drain pan 8A, and the draining that receives by back drain pan 8B flows to preceding drain pan 8A by above-mentioned path.
Be provided with blow-off outlet 9 below the above-mentioned casing.Be provided with the blading 10 that constitutes by cross blade and longitudinal blade by these blow-off outlet 9 places, can change the direction of air that blow-off outlet 9 blows out in the horizontal direction with on the vertical direction.
The upper end of above-mentioned back plate 2B is connected with the last rearward end of front panel 2A.In addition, the middle part of above-mentioned back plate 2B and above-mentioned back drain pan 8B are one-body molded.Especially, above-mentioned back plate 2B end portion is outstanding forward, and marks off above-mentioned blow-off outlet 9 between the lower end of above-mentioned preceding drain pan 2A.In addition, from the pars intermedia of above-mentioned back plate 2B to the bottom, the internal air passageways 11 that blows out towards blow-off outlet 9 with the following formation of preceding drain pan 8A.
To describe above-mentioned fin-type heat exchanger 5 below in detail.
Begin now with reference to the Fig. 2 and the 3 explanation first embodiment of the present invention.
Fig. 2 is the part side view of detailed construction of the fin-type heat exchanger 5 of expression first embodiment of the invention.
This fin tube heat exchanger 5 is made of a plurality of fin F that are set up in parallel according to certain intervals and the heat-transfer pipe D that passes these fins F.
Above-mentioned heat-transfer pipe and is installed on the above-mentioned fin along airflow direction at least and be provided with 3 row.
Because be formed with fin F and fin collar K on the perforation of the heat-transfer pipe D of the above-mentioned fin F part, the heat conductivility between heat-transfer pipe D and the fin F improves.In addition, in order to improve convection heat transfer and the heat absorption capacity of fin F, also can on fin F, projection be set to air.
The external diameter of above-mentioned fin collar K is set at:
5.5mm≤Dc≤8.7mm。
Further, the line space L1 of the outer diameter D c of above-mentioned fin collar K and heat-transfer pipe D and the caliber between the column pitch L2 are set at:
1.2≤(L1-Dc)/L2≤1.5 (1)
The setting reason of (1) formula is described with reference to Fig. 3 below.
The concrete numerical value that (L1-Dc)/L2 is got in Fig. 3 (A), (B) expression is as abscissa, the characteristic pattern when getting fin efficiency and flowing resistance as ordinate.In addition, Fig. 3 (A) is when airflow direction (width of fin F) the be provided with three biographies heat pipes of the present invention characteristic pattern of expression as a feature of the present invention, and Fig. 3 (B) be represent as a comparative example, when equidirectional is provided with two biographies heat pipes characteristic pattern of the present invention.
Can know from Fig. 3 (A), (B), be under which kind of situation of 3 row and 2 row at heat-transfer pipe, and fin efficiency and flowing resistance become with (L1-Dc)/L2 value together and reduce greatly.
But, be under the situations of 3 row at the heat-transfer pipe shown in Fig. 3 (A), (L1-Dc)/when the value of L2 was approximately 1.5 left and right sides, the reduction of fin efficiency was slow, be approximately 1.2 when above, flowing resistance reduces slowly.
Therefore, constitute when of the present invention when 3 biographies heat pipes are set along airflow direction, (1) formula represent on a large scale in obtain the optimum value of (L1-Dc)/L2.
On the contrary, under the situation that two biographies heat pipes are arranged of Fig. 3 (B) expression, when (L1-Dc)/L2 value surpasses approximately 1.15 the time, fin efficiency sharply reduces, and about 0.95 when following, flowing resistance is sharply reduction also greatly.
Therefore, when 2 biographies heat pipe D being set along airflow direction constituting comparative example, can not obtain the optimum value of (L1-Dc)/L2 in the narrow range that following formula is represented, this formula is
0.95≤(L1-Dc)/L2≤1.15.
And the scope of optimum value is different under 3 situations about being listed as with heat-transfer pipe.Therefore, only increase by 1 row and form 3 row on the basis of original 2 row, can not improve fin efficiency, flowing resistance increases, and heat transfer property can not get improving.
Then the second embodiment of the present invention is described with reference to Fig. 4 to Fig. 6.
Fig. 4 is the part side view of the detailed construction of finned tube type heat exchanger 5 in the expression second embodiment of the present invention.
Above-mentioned finned tube type heat exchanger 5 is made of the heat-transfer pipe D of a plurality of fin F that are set up in parallel at regular intervals and these fins of perforation F.
At least be set side by side with three biographies heat pipes along airflow direction, and be installed on the fin F.
Be formed with fin F and fin collar K on the breakthrough part of the heat-transfer pipe D of above-mentioned fin F, thereby improve the fluid-tight engagement performance of heat-transfer pipe D and fin F.Said structure is identical with the situation of aforementioned first embodiment.
The 2nd embodiment of the present invention is characterised in that, the caliber Ds of the first biographies heat pipe D of weather side designs forr a short time than the caliber Db of two biographies heat pipe D of downwind side among the heat-transfer pipe D.
In recent years, fin tube heat exchanger is designed to, and refrigerant is flowed with vapour-liquid two-phase state, and refrigerant is flowed in a part of heat-transfer pipe with the supercooling state.By doing like this, enthalpy has increased, and heat-exchange capacity has also improved.
Because the heat-transfer pipe D that refrigerant is crossed with the supercooling state flow is littler than the refrigerant pipe friction resistance of the heat-transfer pipe D that refrigerant is crossed with the two-phase state flow, therefore can reduce its caliber.
Therefore, in the second embodiment of the present invention, among the weather side first biographies heat pipe D, the caliber Ds of the heat-transfer pipe D of the supercooling state refrigerant that flows is less than the caliber Db of the heat-transfer pipe D of the two-phase state refrigerant that flows.
Like this, though the little side's heat-exchange capacity height of caliber of the heat-transfer pipe D of the supercooling state refrigerant that flows, flowing resistance also reduces, and when caliber diminished, cold medium flux diminished, and the shortcoming of the heat exchange amount that reduces heat exchanger is arranged.
Therefore, the relation with the diameter Db of the heat-transfer pipe D of the refrigerant of the caliber Ds of the heat-transfer pipe D of the supercooling state refrigerant that flows and mobile two-phase state is set at:
0.8≤Ds/Db≤0.9 (2)
The setting reason of (2) formula is then described with reference to Fig. 5.
Fig. 5 is that the ratio (Ds/Db) of getting above-mentioned caliber Ds and caliber Db is an abscissa, gets the characteristic pattern that the heat output measured according to the various variations of this value and flowing resistance are represented as ordinate.
As shown in Figure 5, heat output is approximately at 0.8 to 0.9 o'clock in the Ds/Db value and reaches maximum, all sharply reduces below the scope and when above at this.On the one hand, the Ds/Db value is big more, and flowing resistance increases more, and particularly surpassing at about 0.9 o'clock in this value sharply increases.
According to The above results, second embodiment has provided the optimum range of the Ds/Db value that obtains good fin efficiency and flowing resistance by (2) formula.
Fig. 6 is the figure that refrigerant flows in the explanation second embodiment of the invention.Fin F is equipped with carrier pipe (jumping pipe) Pa, Pb outward, and dehumidifying throttling arrangement 20 is housed on the carrier pipe Pb.
The flowing of refrigerant when solid arrow is represented heating operation among the figure, refrigerant flows when dotted arrow is represented refrigerating operaton and during the dehumidifying operation.Dehumidifying is controlled so as to when the heating operation with throttling arrangement 20 and standard-sized sheet during refrigerating operaton, brings into play throttling action when the dehumidifying operation.Among the figure, the heat-transfer pipe part that the refrigerant of supercooling state flowed when the position of representing on the spot with blacking was heating operation.
As one of feature of the present invention, the fin F that constitutes front side heat exchanger part 5A and rear side heat exchanger part 5B respectively all constitutes indivisible integral fins with every biographies heat pipe D.
Like this, by being set up in parallel three biographies heat pipes, 1 biographies heat pipe formation secondary unit is simple in structure than adding on the main heat exchanger that two biographies heat pipes are set, and has also simplified production technology.And, can prevent that also flowing resistance from increasing because the phenomenon of generation deviation in position between the main and auxiliary heat-exchanger fin can not take place.
Fig. 7 represents the side view of the fin tube heat exchanger 5 of the 3rd embodiment according to the present invention.
Above-mentioned fin tube heat exchanger 5 is made of a plurality of fin F of spacing parallel arranging setting and the heat-transfer pipe D of these fins of perforation F.
On above-mentioned fin F, 3 biographies heat pipes are installed at least side by side along airflow direction.
In addition, though not expression among the figure, the pipe arrangement of representing among Fig. 6 is directly applied for this fin tube heat exchanger 5 too.
In addition, the fin tube heat exchanger 5 of a fourth embodiment in accordance with the invention, be roughly horizontal cutting Ca and be roughly cutting Cb longitudinally in order when dehumidifying is turned round, to block the heat transmission between refrigerant evaporation regional evapotranspiration part Z and the refrigerant condenser zone condensation portion G, on fin F, to have formed.
Like this, causing between when running dehumidifying blocking-up refrigerant evaporation regional evapotranspiration part Z and the refrigerant condenser zone condensation portion G for the temperature difference increases, generation direct heat transmission between these zones, can prevent and heat exchange air between heat transfer impaired.
Equally, during heating operation, in order when dehumidifying is turned round, to block the supercooling part W of refrigerant with supercooling state flow region, and the heat transmission between the flow region that the refrigerant of this supercooling part W downwind side flows with the two-phase state, be roughly horizontal cutting Ca and be roughly cutting Cb longitudinally by on fin F, forming, so that not only improve wet-out property, also improve heating performance simultaneously.
Fig. 8 illustrates the setting reason of the foregoing description, the temperature distributing characteristic figure of indoor heat converter when being heating operation (condenser).Getting condenser locations is abscissa, and getting refrigerant temperature is that ordinate comes structure more of the present invention and existing structure.
Though in the flow region that refrigerant flows with gas-liquid two-phase, there is not difference substantially in the refrigerant temperature of structure of the present invention and existing structure, but at refrigerant with the single-phase mobile zone of liquid state, compare with the heat exchanger of existing structure, the refrigerant temperature with heat exchanger of the present invention's structure can reduce.
In other words, in having the indoor heat converter of structure of the present invention, under the situation identical, not only can reduce refrigerant with the single-phase mobile zone of liquid state, and can reduce the quantity of the heat-transfer pipe that connects fin with the refrigerant charging quantity of indoor heat converter with existing structure.
In addition, shown in Fig. 1 and 6 and 8, the anterior suction inlet 3 of the casing of indoor set 1 is relative with top suction inlet 4, sees that from the side forming circular-arc front side heat exchanger part 5A surrounds blowing fan 7 a part of side faces.Like this, just obtain constituting the fin F of front side heat exchanger part 5A, surround cross flow fan 7 a part of side faces like this, can reduce manufacturing process than the situation of warpage.
The invention effect
According to above-mentioned the present invention, also have the heat exchange performance that can improve fin tube heat exchanger, make The heat exchanger miniaturization reduces installation procedure and amount of parts, the effect of boosting productivity etc.
Brief Description Of Drawings
Fig. 1 represents to constitute the summary section of the indoor set of air conditioner of the present invention.
Fig. 2 represents the part side view according to the indoor heat converter of the first embodiment of the present invention.
Fig. 3 represents characteristic (B) comparison diagram of the comparative example of the characteristic (A) of the first embodiment of the present invention and prior art.
Fig. 4 represents the side view of the part of indoor heat converter according to a second embodiment of the present invention.
Fig. 5 represents the figure of the characteristic (A) of second embodiment of the invention.
Fig. 6 represents the figure that refrigerant flows in the second embodiment of the invention.
Fig. 7 represents according to third embodiment of the invention, and fin tube heat exchanger refrigerant state region when heating operation is described.
Fig. 8 is illustrated in the comparison diagram of refrigerant state region in the example compared with the prior art of refrigerant state in the third embodiment of the invention.
Symbol description
The F fin D heat-transfer pipe K fin collar 5 fin tube heat exchangers
Claims (3)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003129100A JP2004333013A (en) | 2003-05-07 | 2003-05-07 | Heat exchanger for air conditioner |
| JP2003129100 | 2003-05-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1550727A true CN1550727A (en) | 2004-12-01 |
| CN1263989C CN1263989C (en) | 2006-07-12 |
Family
ID=33505051
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200410045138 Expired - Fee Related CN1263989C (en) | 2003-05-07 | 2004-04-30 | Fin tube type heat exchanger for air conditioner |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2004333013A (en) |
| CN (1) | CN1263989C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103874901A (en) * | 2011-10-14 | 2014-06-18 | 松下电器产业株式会社 | Finned tube heat exchanger |
| CN105485885A (en) * | 2010-09-28 | 2016-04-13 | 日立空调·家用电器株式会社 | Air conditioner |
| CN105934645A (en) * | 2014-01-15 | 2016-09-07 | 三星电子株式会社 | Heat exchanger and air conditioner equipped with it |
| CN108931078A (en) * | 2018-06-26 | 2018-12-04 | 广东美的制冷设备有限公司 | New type heat exchanger, air conditioner indoor unit and air conditioner |
| CN110008579A (en) * | 2019-03-29 | 2019-07-12 | 中国原子能科学研究院 | Design method of vertical fin-and-tube heat exchanger |
| CN110892211A (en) * | 2017-08-07 | 2020-03-17 | 三菱电机株式会社 | Heat exchanger, indoor unit of air conditioner, and air conditioner |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006329534A (en) * | 2005-05-26 | 2006-12-07 | Toshiba Kyaria Kk | Heat exchanger, air conditioner |
| DE112019007149T5 (en) | 2019-04-03 | 2021-12-23 | Mitsubishi Electric Corporation | Heat exchanger and air conditioning |
-
2003
- 2003-05-07 JP JP2003129100A patent/JP2004333013A/en active Pending
-
2004
- 2004-04-30 CN CN 200410045138 patent/CN1263989C/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485885A (en) * | 2010-09-28 | 2016-04-13 | 日立空调·家用电器株式会社 | Air conditioner |
| CN105485885B (en) * | 2010-09-28 | 2019-08-02 | 日立江森自控空调有限公司 | air conditioner |
| CN103874901A (en) * | 2011-10-14 | 2014-06-18 | 松下电器产业株式会社 | Finned tube heat exchanger |
| CN103874901B (en) * | 2011-10-14 | 2015-12-23 | 松下电器产业株式会社 | Finned tube heat exchanger |
| CN105934645A (en) * | 2014-01-15 | 2016-09-07 | 三星电子株式会社 | Heat exchanger and air conditioner equipped with it |
| CN110892211A (en) * | 2017-08-07 | 2020-03-17 | 三菱电机株式会社 | Heat exchanger, indoor unit of air conditioner, and air conditioner |
| CN110892211B (en) * | 2017-08-07 | 2021-12-28 | 三菱电机株式会社 | Heat exchanger, indoor unit of air conditioner, and air conditioner |
| CN108931078A (en) * | 2018-06-26 | 2018-12-04 | 广东美的制冷设备有限公司 | New type heat exchanger, air conditioner indoor unit and air conditioner |
| CN110008579A (en) * | 2019-03-29 | 2019-07-12 | 中国原子能科学研究院 | Design method of vertical fin-and-tube heat exchanger |
| CN110008579B (en) * | 2019-03-29 | 2021-06-25 | 中国原子能科学研究院 | Design method of vertical fin-and-tube heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2004333013A (en) | 2004-11-25 |
| CN1263989C (en) | 2006-07-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1174213C (en) | Plate heat exchanger | |
| CN1100238C (en) | Outdoor unit of air conditioner | |
| CN100350194C (en) | Ventilator | |
| CN1209591C (en) | Air conditioner | |
| CN1873335A (en) | Total heat exchanger and ventilation system using the same | |
| CN1735783A (en) | Heat exchangers for ventilation systems | |
| CN1690639A (en) | Densified Heat Exchanger Tube Bundle | |
| CN1590925A (en) | Heat exchanger with flat tubes | |
| WO2019009158A1 (en) | Heat exchanger | |
| CN1833142A (en) | Finned heat exchanger and method of manufacturing the same | |
| CN1550727A (en) | Finned tube heat exchanger for air conditioner | |
| CN100347491C (en) | Indoor unit of air conditioner | |
| CN1098445C (en) | Structure of machine room of refrigeration | |
| CN1436984A (en) | Heat exchanger | |
| CN1109861C (en) | Air conditioner | |
| CN1912504A (en) | Evaporator | |
| CN1967062A (en) | Air conditioner | |
| CN1782601A (en) | Indoor unit of air conditioner | |
| CN1521477A (en) | Finned tube heat exchanger and air conditioner using same | |
| CN1228833A (en) | Heat exchangers for air conditioners | |
| JP2006097953A (en) | Finned heat exchanger | |
| CN210475935U (en) | Workstation is used in LED lamp production welding | |
| CN217383114U (en) | Indoor machine of air conditioner | |
| JP2006105416A (en) | Wall-mounted indoor unit of air conditioner | |
| CN203177329U (en) | Air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20060712 Termination date: 20130430 |