CN108844258B - Evaporator and air conditioning unit - Google Patents
Evaporator and air conditioning unit Download PDFInfo
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- CN108844258B CN108844258B CN201810829283.9A CN201810829283A CN108844258B CN 108844258 B CN108844258 B CN 108844258B CN 201810829283 A CN201810829283 A CN 201810829283A CN 108844258 B CN108844258 B CN 108844258B
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- heat exchange
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 11
- 239000007788 liquid Substances 0.000 claims abstract description 111
- 239000003507 refrigerant Substances 0.000 claims abstract description 58
- 238000013021 overheating Methods 0.000 claims description 24
- 238000001035 drying Methods 0.000 claims description 19
- 230000002195 synergetic effect Effects 0.000 claims description 14
- 239000011552 falling film Substances 0.000 claims description 7
- 238000001704 evaporation Methods 0.000 description 11
- 230000008020 evaporation Effects 0.000 description 11
- 238000000034 method Methods 0.000 description 6
- 238000011161 development Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000012935 Averaging Methods 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000009412 basement excavation Methods 0.000 description 1
- 230000002860 competitive effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000010408 film Substances 0.000 description 1
- 238000007654 immersion Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000012546 transfer Methods 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
- 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
- F28D5/00—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, using the cooling effect of natural or forced evaporation
- F28D5/02—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, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The application provides an evaporator and an air conditioning unit. In the evaporator, a first heat exchange tube group and a second heat exchange tube group are arranged in a shell, and the second heat exchange tube group is positioned below a liquid distributor. The first liquid equalizing pipe group is arranged in the shell and located between the first heat exchange pipe group and the second heat exchange pipe group, the pipe diameter of a heat exchange pipe of the first liquid equalizing pipe group is smaller than that of the heat exchange pipe of the first heat exchange pipe group, and the distribution density of the heat exchange pipes of the first liquid equalizing pipe group is larger than that of the heat exchange pipes of the first heat exchange pipe group. By applying the technical scheme of the invention, after the refrigerant flows through the first heat exchange tube group, the refrigerant falls on the first liquid homogenizing tube group. When the refrigerant flows through the first liquid-homogenizing pipe group, the refrigerant is more uniformly distributed by the heat exchange pipes of the first liquid-homogenizing pipe group at random, so that the refrigerant can be homogenized again, and the refrigerant can uniformly fall on the second heat exchange pipe group for heat exchange. Therefore, the heat exchange uniformity of the evaporator is improved, and the overall heat exchange efficiency is improved.
Description
Technical Field
The invention relates to the technical field of refrigeration equipment, in particular to an evaporator and an air conditioning unit.
Background
In air conditioning refrigeration systems, the pressure vessel is the primary element, such as the evaporator, condenser, oil separator, flash tank, etc. With the continuous development of the technical level, products with higher heat exchange capacity are more dominant and competitive under the condition of small price cost difference. Research on heat exchange capacity shows that the evaporator is greatly changed in technology, a dry evaporator, a flooded evaporator and a falling film evaporator exist in the prior shell-and-tube heat exchanger, and the falling film evaporator has considerable development from the perspective and rapid development in the industry.
However, the falling film evaporator still has a plurality of technical bottlenecks and also has great excavation potential in the heat exchange capacity. The existing liquid distributor has various structures, and the structure is basically mature. However, only by the design of the structure of the liquid distributor, the heat exchange uniformity of the upper area of the heat exchanger can be ensured, and the whole heat exchange area cannot be covered. Therefore, the heat exchange structure design of the falling film evaporator is still to be improved.
Disclosure of Invention
The embodiment of the invention provides an evaporator and an air conditioning unit, and aims to solve the technical problem that the evaporator in the prior art is low in heat exchange uniformity.
An embodiment of the present application provides an evaporator, including: a housing; the liquid inlet and the air outlet are arranged on the shell; the liquid distributor is arranged at the upper part in the shell and corresponds to the liquid inlet and is used for dispersing the refrigerant introduced into the liquid inlet; the first heat exchange tube group is arranged in the shell and is positioned below the liquid distributor; the second heat exchange tube group is arranged in the shell and is positioned below the first heat exchange tube group; the first liquid equalizing pipe group is arranged in the shell and located between the first heat exchange pipe group and the second heat exchange pipe group, the pipe diameter of a heat exchange pipe of the first liquid equalizing pipe group is smaller than that of the heat exchange pipe of the first heat exchange pipe group, and the distribution density of the heat exchange pipes of the first liquid equalizing pipe group is larger than that of the heat exchange pipes of the first heat exchange pipe group.
In one embodiment, the evaporator further comprises a second liquid homogenizing pipe group, the second liquid homogenizing pipe group is arranged in the shell and is located between the liquid distributor and the first heat exchange pipe group, the diameter of a heat exchange pipe of the second liquid homogenizing pipe group is smaller than that of a heat exchange pipe of the first heat exchange pipe group, and the distribution density of the heat exchange pipes of the second liquid homogenizing pipe group is larger than that of the heat exchange pipes of the first heat exchange pipe group.
In one embodiment, the evaporator further comprises an overheating heat exchange tube set disposed at a lower portion within the case and below the second heat exchange tube set.
In one embodiment, the evaporator further comprises a third liquid equalizing pipe group, the third liquid equalizing pipe group is arranged in the shell and is positioned between the second heat exchange pipe group and the overheating heat exchange pipe group, the pipe diameter of the heat exchange pipe of the third liquid equalizing pipe group is smaller than that of the heat exchange pipe of the overheating heat exchange pipe group, and the distribution density of the heat exchange pipes of the third liquid equalizing pipe group is greater than that of the heat exchange pipes of the overheating heat exchange pipe group.
In one embodiment, the evaporator further comprises an efficiency-increasing pipe group, the efficiency-increasing pipe group is arranged in the shell and is located below the overheating heat exchange pipe group, the diameter of the heat exchange pipe of the efficiency-increasing pipe group is smaller than that of the heat exchange pipe of the overheating heat exchange pipe group, and the distribution density of the heat exchange pipes of the efficiency-increasing pipe group is greater than that of the heat exchange pipes of the overheating heat exchange pipe group.
In one embodiment, the evaporator further comprises a first drying tube bank and a second drying tube bank, the first drying tube bank and the second drying tube bank being respectively distributed on both sides within the housing.
In one embodiment, the first heat exchange tube group, the second heat exchange tube group, and the superheating heat exchange tube group are distributed in the middle of the housing in the width direction.
In one embodiment, the first header-averaging tube assembly is in two parts, a first part being adjacent to the first heat exchange tube bank and a second part being adjacent to the second heat exchange tube bank.
In one embodiment, the evaporator is a falling film evaporator.
The application also provides an air conditioning unit, which comprises an evaporator, wherein the evaporator is the evaporator.
In the above embodiment, after the refrigerant flows through the first heat exchange tube set, the refrigerant falls on the first liquid equalizing tube set. Because the heat exchange tube pipe diameter of first liquid pipe group is little, and distribution density is big, when the refrigerant flows through first liquid pipe group, will be more even by the heat exchange tube random distribution of first liquid pipe group for the refrigerant can be by liquid once more, and the refrigerant just can be dropped on second heat exchange tube group and carry out the heat transfer uniformly. Therefore, the heat exchange uniformity of the evaporator is improved, and the overall heat exchange efficiency is improved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic sectional view of an evaporator according to a first embodiment of the present invention;
fig. 2 is a schematic sectional view of an evaporator according to a second embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the following embodiments and accompanying drawings. The exemplary embodiments and descriptions of the present invention are provided to explain the present invention, but not to limit the present invention.
It is found that the liquid refrigerant is uniformly distributed to the heat exchange tube set by the liquid distributor 30 after entering the housing 10 through the liquid inlet 21. The liquid refrigerant is continuously evaporated on the heat exchange tube group. The distribution uniformity of the liquid refrigerant can be poor under the influence of the gaseous refrigerant, and the heat exchange uniformity is poor.
Fig. 1 shows a first embodiment of the evaporator of the present invention, which comprises a housing 10, a liquid inlet 21 and a gas outlet 22, wherein the liquid inlet 21 and the gas outlet 22 are arranged on the housing 10. The evaporator further comprises a liquid distributor 30, a first heat exchange pipe group 41, a second heat exchange pipe group 42 and a first liquid equalizing pipe group 51, the liquid distributor 30 is arranged at the upper part in the shell 10 and corresponds to the liquid inlet 21, and the liquid distributor 30 is used for dispersing a refrigerant introduced into the liquid inlet 21. A first heat exchange tube group 41 and a second heat exchange tube group 42 are provided in the case 10, and the second heat exchange tube group 42 is located below the liquid distributor 30. The first liquid equalizing pipe group 51 is arranged in the shell 10 and located between the first heat exchange pipe group 41 and the second heat exchange pipe group 42, the pipe diameter of a heat exchange pipe of the first liquid equalizing pipe group 51 is smaller than that of the heat exchange pipe of the first heat exchange pipe group 41, and the distribution density of the heat exchange pipes of the first liquid equalizing pipe group 51 is greater than that of the heat exchange pipes of the first heat exchange pipe group 41.
By applying the technical scheme of the present invention, after the refrigerant flows through the first heat exchange tube set 41, the refrigerant falls on the first liquid equalizing tube set 51. Because the heat exchange tubes of the first liquid equalizing tube group 51 have small tube diameters and large distribution density, when the refrigerant flows through the first liquid equalizing tube group 51, the refrigerant is randomly distributed more uniformly by the heat exchange tubes of the first liquid equalizing tube group 51, so that the refrigerant can be equalized again, and the refrigerant can uniformly fall on the second heat exchange tube group 42 for heat exchange. Therefore, the heat exchange uniformity of the evaporator is improved, and the overall heat exchange efficiency is improved.
Optionally, in the technical solution of the present embodiment, the liquid inlet 21 and the air outlet 22 are disposed at the top of the housing 10, and as another optional embodiment, the liquid inlet 21 and the air outlet 22 may also be disposed at the side of the housing 10.
It should be noted that the liquid equalizing tube group and the heat exchange tube group are also composed of heat exchange tubes capable of performing evaporation heat exchange.
As shown in fig. 1, preferably, in the solution of the first embodiment, the evaporator further includes an overheating heat exchange tube set 60, and the overheating heat exchange tube set 60 is disposed at the lower part in the casing 10 and below the second heat exchange tube set 42. In the process of using the evaporator, the refrigerant that is not gasified by the heat exchange tube set is accumulated at the lower part of the shell 10, and the overheating heat exchange tube set 60 at the lower part of the shell 10 exchanges heat with the part of the refrigerant, so that the part of the refrigerant is also evaporated into the gaseous refrigerant.
In the process of using the evaporator, the phenomenon of air absorption and liquid carrying can occur when the liquid refrigerant is evaporated, which is not beneficial to full heat exchange. As a preferred implementation, as shown in fig. 1, in the technical solution of the first embodiment, the evaporator further includes a synergistic tube set 70, and the synergistic tube set 70 is disposed in the casing 10 and below the superheated heat exchange tube set 60. The heat exchange pipe diameter of the synergistic pipe group 70 is smaller than that of the overheating heat exchange pipe group 60, and the heat exchange pipe distribution density of the synergistic pipe group 70 is greater than that of the overheating heat exchange pipe group 60. The synergistic tube group 70 arranged below the overheating heat exchange tube group 60 can not only increase one evaporation process to be beneficial to immersion type heat exchange, but also can enable the thickness of a liquid film on the synergistic tube group 70 to be thinner than that of the overheating heat exchange tube group 60 due to the characteristics of small heat exchange tube diameter and large heat exchange tube distribution density of the synergistic tube group 70, so that the space in the shell 10 can be more fully utilized for arranging the heat exchange tubes, the heat exchange tubes are arranged to the maximum extent, the occupied space of the heat exchanger is saved, the heat exchange area is enlarged, and the heat exchange is fully performed.
It should be noted that the synergistic tube group and the heat exchange tube group are also composed of heat exchange tubes capable of performing evaporation heat exchange.
More preferably, the evaporator further comprises a first drying tube bank 81 and a second drying tube bank 82, and the first drying tube bank 81 and the second drying tube bank 82 are respectively distributed on both sides in the casing 10. By respectively disposing the first drying tube set 81 and the second drying tube set 82 at two sides of the housing 10, a drying process can be added to the air flow channel to make the refrigerant more sufficiently gasified.
Alternatively, in the technical solution of the first embodiment, as shown in fig. 1, the first heat exchange tube group 41, the second heat exchange tube group 42, and the superheated heat exchange tube group 60 are distributed in the middle of the housing 10 in the width direction. More preferably, the first heat exchange tube group 41 is located at an upper middle portion in the case 10, and the second heat exchange tube group 42 is located at a lower middle portion in the case 10. Thus, the arrangement of the heat exchange pipes can be reasonably realized by utilizing the space in the shell 10.
When the technical scheme of the first embodiment is used, after the liquid refrigerant enters the shell 10 through the liquid inlet 21, the liquid refrigerant is uniformly distributed on the first heat exchange tube group 41 by the liquid distributor 30 for evaporation. The remaining liquid refrigerant drips from the first heat exchange tube set 41 to the first liquid equalizing tube set 51, and is evaporated and more uniformly distributed through the first liquid equalizing tube set 51, the refrigerant after being equalized drips to the second heat exchange tube set 42 for evaporation, and the remaining refrigerant drips to the lower portion of the casing 10 and is evaporated by the superheating heat exchange tube set 60 and the efficiency increasing tube set 70, and meanwhile, the efficiency increasing tube set 70 also prevents the refrigerant at the lower portion of the casing 10 from being subjected to air suction and liquid entrainment. The first and second drying tube groups 81 and 82 located at both sides in the housing 10 dry the refrigerant in the airflow channel, so that the refrigerant is more fully gasified. The gaseous refrigerant generated during the evaporation process is discharged through the outlet 22 at the top of the housing 10.
Fig. 2 shows a second embodiment of the evaporator according to the present invention, and the difference between the second embodiment and the first embodiment is that the evaporator further includes a second liquid equalizing tube group 52. The second flow equalization tube set 52 is disposed within the housing 10 and between the liquid distributor 30 and the first heat exchange tube set 41. The pipe diameter of the heat exchange pipe of the second liquid equalizing pipe group 52 is smaller than that of the heat exchange pipe of the first heat exchange pipe group 41, and the distribution density of the heat exchange pipes of the second liquid equalizing pipe group 52 is greater than that of the heat exchange pipes of the first heat exchange pipe group 41. After the refrigerant is distributed from the liquid distributor 30, the refrigerant falls on the second liquid equalizing pipe group 52, is evaporated and better equalized by the second liquid equalizing pipe group 52, so that the refrigerant can be more uniformly distributed on the first heat exchange pipe group 41, and the heat exchange uniformity of the evaporator is improved.
In a more preferred embodiment, the evaporator further comprises a third equalization tube bank 53, the third equalization tube bank 53 being disposed within the shell 10 between the second heat exchange tube bank 42 and the superheating heat exchange tube bank 60. The pipe diameter of the heat exchange pipe of the third liquid equalizing pipe group 53 is smaller than that of the heat exchange pipe of the overheating heat exchange pipe group 60, and the distribution density of the heat exchange pipes of the third liquid equalizing pipe group 53 is greater than that of the heat exchange pipes of the overheating heat exchange pipe group 60. The liquid refrigerant evaporated by the second heat exchange tube set 42 falls on the third liquid equalizing tube set 53, and is evaporated and better equalized, so that the refrigerant can be more uniformly distributed on the superheating heat exchange tube set 60, and the heat exchange uniformity of the evaporator is improved.
As shown in fig. 2, the first heat exchange tube group 41 is located at an upper middle portion in the case 10, and the second heat exchange tube group 42 is located at a lower middle portion in the case 10. Preferably, the first liquid equalizing tube set 51 is divided into two portions, a first portion being adjacent to the first heat exchange tube set 41 and a second portion being adjacent to the second heat exchange tube set 42.
In the second technical solution of the embodiment, after the liquid refrigerant enters the casing 10 through the liquid inlet 21, the liquid refrigerant is uniformly distributed on the second liquid equalizing tube group 52 by the liquid distributor 30, evaporated and equalized by the second liquid equalizing tube group 52, and then falls onto the first heat exchange tube group 41 for evaporation. The remaining liquid refrigerant drops from the first heat exchange tube set 41 to the first liquid equalizing tube set 51, and the refrigerant is evaporated and more uniformly distributed through the first liquid equalizing tube set 51, and the liquid-equalized refrigerant drops to the second heat exchange tube set 42 for evaporation. The unevaporated liquid refrigerant will continue to fall down onto the third liquid-equalizing tube group 53, and be evaporated and equalized by the third liquid-equalizing tube group 53, so that the refrigerant can be more uniformly distributed on the superheating heat exchange tube group 60. The rest of the refrigerant drips and collects at the lower part of the shell 10 and is evaporated by the superheating heat exchange tube group 60 and the synergistic tube group 70, and meanwhile, the synergistic tube group 70 also prevents the refrigerant at the lower part of the shell 10 from generating the phenomenon of air suction and liquid entrainment. The first and second drying tube groups 81 and 82 located at both sides in the housing 10 dry the refrigerant in the airflow channel, so that the refrigerant is more fully gasified. The gaseous refrigerant generated during the evaporation process is discharged through the outlet 22 at the top of the housing 10.
It should be noted that the evaporator solution described above is particularly suitable for use in a falling film evaporator. The first heat exchange tube group 41, the second heat exchange tube group 42, and the superheating heat exchange tube group 60 may be large heat exchange tubes with the same diameter, or large heat exchange tubes with different diameters. The first liquid equalizing tube group 51, the second liquid equalizing tube group 52, the third liquid equalizing tube group 53, the effect enhancing tube group 70, the first drying tube group 81, and the second drying tube group 82 may be small heat exchange tubes having the same diameter or small heat exchange tubes having different diameters.
The invention also provides an air conditioning unit which comprises the evaporator. The air conditioning unit adopting the evaporator can ensure that the liquid refrigerant is more uniformly distributed in the evaporation process, effectively prevents the phenomenon of air suction and liquid entrainment, is favorable for protecting the service life of the compressor, improves the evaporation efficiency of the liquid refrigerant and further improves the operating efficiency of the air conditioning unit.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes may be made to the embodiment of the present invention by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (7)
1. An evaporator, comprising:
a housing (10);
a liquid inlet (21) and a gas outlet (22) which are arranged on the shell (10);
the liquid distributor (30) is arranged at the upper part in the shell (10) and corresponds to the liquid inlet (21), and the liquid distributor (30) is used for dispersing a refrigerant introduced into the liquid inlet (21);
the first heat exchange tube group (41) is arranged in the shell (10) and is positioned below the liquid distributor (30);
a second heat exchange tube group (42) disposed within the housing (10) and located below the first heat exchange tube group (41);
the first liquid equalizing pipe group (51) is arranged in the shell (10) and is positioned between the first heat exchange pipe group (41) and the second heat exchange pipe group (42), the pipe diameter of a heat exchange pipe of the first liquid equalizing pipe group (51) is smaller than that of the heat exchange pipe of the first heat exchange pipe group (41), and the distribution density of the heat exchange pipes of the first liquid equalizing pipe group (51) is greater than that of the heat exchange pipes of the first heat exchange pipe group (41);
the overheating heat exchange tube set (60), the overheating heat exchange tube set (60) is arranged at the lower part in the shell (10) and is positioned below the second heat exchange tube set (42);
a first drying pipe group (81) and a second drying pipe group (82), wherein the first drying pipe group (81) and the second drying pipe group (82) are respectively distributed on two sides in the shell (10);
the second liquid equalizing pipe group (52) is arranged in the shell (10) and located between the liquid distributor (30) and the first heat exchange pipe group (41), the pipe diameter of a heat exchange pipe of the second liquid equalizing pipe group (52) is smaller than that of the heat exchange pipe of the first heat exchange pipe group (41), and the distribution density of the heat exchange pipes of the second liquid equalizing pipe group (52) is larger than that of the heat exchange pipes of the first heat exchange pipe group (41).
2. An evaporator according to claim 1 further comprising a third liquid equalizing tube group (53), wherein the third liquid equalizing tube group (53) is arranged in the shell (10) and is positioned between the second heat exchange tube group (42) and the overheating heat exchange tube group (60), the heat exchange tube diameter of the third liquid equalizing tube group (53) is smaller than that of the overheating heat exchange tube group (60), and the heat exchange tube distribution density of the third liquid equalizing tube group (53) is greater than that of the overheating heat exchange tube group (60).
3. The evaporator according to claim 1, further comprising a synergistic tube group (70), wherein the synergistic tube group (70) is arranged in the shell (10) and is positioned below the overheating heat exchange tube group (60), the heat exchange tube diameter of the synergistic tube group (70) is smaller than that of the overheating heat exchange tube group (60), and the heat exchange tube distribution density of the synergistic tube group (70) is greater than that of the overheating heat exchange tube group (60).
4. An evaporator according to claim 1 wherein the first heat exchange tube group (41), the second heat exchange tube group (42), and the superheated heat exchange tube group (60) are distributed in the middle in the width direction of the case (10).
5. An evaporator according to claim 1 wherein the first liquid equalizing tube group (51) is divided into two portions, a first portion being adjacent to the first heat exchange tube group (41) and a second portion being adjacent to the second heat exchange tube group (42).
6. The evaporator according to any one of claims 1 to 5, wherein the evaporator is a falling film evaporator.
7. An air conditioning assembly comprising an evaporator, wherein the evaporator is as claimed in any one of claims 1 to 6.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810829283.9A CN108844258B (en) | 2018-07-25 | 2018-07-25 | Evaporator and air conditioning unit |
| PCT/CN2018/121166 WO2020019636A1 (en) | 2018-07-25 | 2018-12-14 | Evaporator and air conditioning unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810829283.9A CN108844258B (en) | 2018-07-25 | 2018-07-25 | Evaporator and air conditioning unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108844258A CN108844258A (en) | 2018-11-20 |
| CN108844258B true CN108844258B (en) | 2021-05-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810829283.9A Active CN108844258B (en) | 2018-07-25 | 2018-07-25 | Evaporator and air conditioning unit |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN108844258B (en) |
| WO (1) | WO2020019636A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108844258B (en) * | 2018-07-25 | 2021-05-04 | 珠海格力电器股份有限公司 | Evaporator and air conditioning unit |
| CN109780896B (en) * | 2019-02-18 | 2019-10-11 | 中国空气动力研究与发展中心超高速空气动力研究所 | A kind of high-temperature cooler Pipe bundle structure and high-temperature cooler |
| CN111854232A (en) * | 2019-04-26 | 2020-10-30 | 荏原冷热系统（中国）有限公司 | Evaporator for compression refrigerator and compression refrigerator provided with same |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN208720577U (en) * | 2018-07-25 | 2019-04-09 | 珠海格力电器股份有限公司 | Evaporator and air conditioning unit |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
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| US6293112B1 (en) * | 1999-12-17 | 2001-09-25 | American Standard International Inc. | Falling film evaporator for a vapor compression refrigeration chiller |
| JP4192413B2 (en) * | 2000-09-06 | 2008-12-10 | 株式会社Ｉｈｉ | Ice cooler supercooler |
| US6830099B2 (en) * | 2002-12-13 | 2004-12-14 | American Standard International Inc. | Falling film evaporator having an improved two-phase distribution system |
| JP2007198701A (en) * | 2006-01-30 | 2007-08-09 | Hitachi Zosen Corp | Evaporator for multiple effect type fresh water generator |
| US9541314B2 (en) * | 2012-04-23 | 2017-01-10 | Daikin Applied Americas Inc. | Heat exchanger |
| CN102759227B (en) * | 2012-07-16 | 2015-05-13 | 佛山市顺德区高美空调设备有限公司 | Falling film evaporator for refrigeration circuit |
| CN106673098A (en) * | 2016-11-02 | 2017-05-17 | 天津大学 | Mounting method for uniform liquid distribution structure of transverse tube falling film evaporator |
| CN106766407B (en) * | 2016-11-21 | 2018-08-07 | 重庆美的通用制冷设备有限公司 | Distributor, evaporator and handpiece Water Chilling Units |
| CN207006640U (en) * | 2017-06-30 | 2018-02-13 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioning device |
| CN107255375A (en) * | 2017-06-30 | 2017-10-17 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioning device |
| CN108592458B (en) * | 2018-07-10 | 2019-10-18 | 珠海格力电器股份有限公司 | Flow equalizing structure, falling film evaporator and water chilling unit |
| CN108844258B (en) * | 2018-07-25 | 2021-05-04 | 珠海格力电器股份有限公司 | Evaporator and air conditioning unit |
-
2018
- 2018-07-25 CN CN201810829283.9A patent/CN108844258B/en active Active
- 2018-12-14 WO PCT/CN2018/121166 patent/WO2020019636A1/en active Application Filing
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN208720577U (en) * | 2018-07-25 | 2019-04-09 | 珠海格力电器股份有限公司 | Evaporator and air conditioning unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108844258A (en) | 2018-11-20 |
| WO2020019636A1 (en) | 2020-01-30 |
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