CN101639310A - Hot-gas bypass and surface cooler supercooling defrosting device - Google Patents
Hot-gas bypass and surface cooler supercooling defrosting device Download PDFInfo
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- CN101639310A CN101639310A CN200910042060A CN200910042060A CN101639310A CN 101639310 A CN101639310 A CN 101639310A CN 200910042060 A CN200910042060 A CN 200910042060A CN 200910042060 A CN200910042060 A CN 200910042060A CN 101639310 A CN101639310 A CN 101639310A
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- heat exchanger
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- supercooling
- surface cooler
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Abstract
The invention discloses a hot-gas bypass and surface cooler supercooling defrosting device, comprising a compression engine, a first heat interchanger, a first solenoid valve and a second heat interchanger which are sequentially connected by a pipeline and form a loop; wherein the heat exchange tube in the second heat interchanger is composed of a supercooling section heat exchange tube at the bottom and an upper part section heat exchange tube, and the supercooling section heat exchange tube is connected with the upper part section heat exchange tube by an expansion valve. Another solenoid valve is also connected between the compression engine and the upper part section heat exchange tube. Compared with the prior art, the invention greatly reduces frosting speed, thus the hot-gas bypass defrosting effect is more rapid and effective; besides, through the supercooling of an evaporator, system energy efficiency ratio is improved, energy consumption is saved, and economic cost is reduced.
Description
Technical field
The present invention relates to a kind of refrigeration cycle apparatus, in particular, relate to a kind of device that utilizes the contained heat of cold-producing medium to carry out defrosting.
Background technology
At present, when the air-source heat pump hot water group of using in dwelling house or commercial building is produced health hot water, when lower and relative humidity is big when environment temperature, finned evaporator is understood a large amount of frostings and is influenced the heat exchange effect, cause unit normally not move when serious, industry adopts such as multiple defrosting modes such as hot-gas bypass, cross valve commutation, electrical heating, though almost not fluctuation of water temperature in the existing hot-gas bypass mode defrost process, low, the weak effect of efficient.
During heat pump to melt frost, system utilizes four-way change-over valve that the function of original evaporimeter and condenser is changed mutually, realizes heat pump cycle.Evaporimeter during heat pump cycle (condenser during kind of refrigeration cycle) inner refrigerant absorbs heat from surrounding medium (air), promote refrigerant pressure by compressor and arrive in the condenser (evaporimeter when being kind of refrigeration cycle), the frost that utilizes cold-producing medium condensation heat release under high pressure to melt on the evaporimeter to be tied.During heat pump to melt frost, the evaporating temperature of heat pump directly has influence on the efficient of defrosting, and evaporating temperature is high more, and the heating efficiency of heat pump is high more, and the defrosting time is short more.So the temperature of surrounding medium directly has influence on the efficient of heat pump cycle, in the time of especially in the winter time, the caloric requirement of heat pump to melt frost is extracted from lower surrounding medium, because this moment, air themperature was lower, the also corresponding reduction of thermo-compression evaporation temperature, systematic energy efficiency ratio is less relatively, and defrosting is longer running time.
Summary of the invention
In order to overcome existing defrosting recycle unit energy consumption height, little, defrosting long deficiency running time of system energy efficiency, the invention provides and a kind ofly can effectively reduce frosting speed, improve systematic energy efficiency ratio, energy efficient, the hot-gas bypass and the surface cooler supercooling defrosting device of reduction financial cost.
The technical solution adopted for the present invention to solve the technical problems is: this hot-gas bypass and surface cooler supercooling defrosting device, comprise the compressor, first heat exchanger, first magnetic valve, second heat exchanger that connect successively by pipeline, and formation loop, heat exchanger tube in second heat exchanger divides the super cooled sect heat exchanger tube and the heat exchanger upper segment heat exchanger tube of heat exchanger bottom, the super cooled sect heat exchanger tube is connected by expansion valve with the upper segment heat exchanger tube, also is connected with another magnetic valve between compressor refrigerant outlet and the upper segment heat exchanger tube.
First heat exchanger of the present invention be in board-like, shell-tube type or the double pipe heat exchanger any; Second heat exchanger is a fin-tube heat exchanger; Expansion valve be in heating power expansion valve, electric expansion valve or the capillary any; Compressor 1 can be displacement type or velocity profile; Magnetic valve is this area magnetic valve commonly used.
Compared with prior art, the present invention has the following advantages:
1. increase super cooled sect in the finned evaporator bottom, reduce frosting speed greatly, make the hot-gas bypass defrosting effect more effective and rapid;
2. pass through the cold excessively of evaporimeter, improved systematic energy efficiency ratio;
3. save energy consumption, reduced financial cost.
Description of drawings
Fig. 1 is hot-gas bypass of the present invention and surface cooler supercooling defrosting device principle schematic.
The specific embodiment
Describe the present invention for the ease of it will be appreciated by those skilled in the art that below in conjunction with accompanying drawing:
Fig. 1 is hot-gas bypass of the present invention and surface cooler supercooling defrosting device schematic diagram, comprise compressor 1, first heat exchanger 2, second heat exchanger 4, magnetic valve 3, expansion valve 5, the refrigerant inlet of compressor 1 refrigerant outlet and first heat exchanger 2 is connected, the refrigerant outlet of first heat exchanger 2 is connected with magnetic valve 3 imports, and magnetic valve 3 outlets are connected with second heat exchanger, 4 refrigerant inlet.
Heat exchanger tube in second heat exchanger 4 divides the super cooled sect heat exchanger tube 41 and the heat exchanger upper segment heat exchanger tube 42 of heat exchanger bottom, and super cooled sect heat exchanger tube 41 is connected by expansion valve 5 with upper segment heat exchanger tube 42.
Also be connected with another magnetic valve 6 between compressor 1 refrigerant outlet and second heat exchanger, the 4 upper segment heat exchanger tubes 42.
The first above-mentioned heat exchanger 2 of the present invention be in board-like, shell-tube type or the double pipe heat exchanger any; Second heat exchanger 4 is a fin-tube heat exchanger; Expansion valve 5 be in heating power expansion valve, electric expansion valve or the capillary any; Compressor 1 can be displacement type or velocity profile; Magnetic valve is this area magnetic valve commonly used.
Embodiment 1
During use, in cooling cycle system, fill refrigerant vapour.Enter in first heat exchanger 2 by pipeline behind compressed machine 1 adherence pressure of refrigerant vapour, the refrigerant vapour condensation is become highly pressurised liquid, and after magnetic valve 3 enters the super cooled sect heat exchanger tube 41 of the heat exchanger tube bottom in second heat exchanger 4, because the cold-producing medium in the super cooled sect heat exchanger tube 41 is middle temperature highly pressurised liquid, therefore the temperature of supercooling tube is higher relatively, when lower and relative humidity is big when environment temperature, just effectively prevented the condensed water that heat exchanger tube produced in second heat exchanger 4, particularly winter, a large amount of globule frostings on the heat exchanger tube of second heat exchanger, 4 bottoms was assembled in the evaporimeter bottom, in the cold-producing medium of warm highly pressurised liquid after expansion valve 5 throttling step-downs are the refrigerant liquid of low-temp low-pressure, enter the refrigerant gas that heat that evaporimeter 4 middle and upper part section heat exchanger tubes 42 absorb refrigerating mediums becomes low-temp low-pressure and get back to compressor 1, forms a kind of refrigeration cycle also so repeatedly.In the case, magnetic valve 6 can dead electricity.
When environment needs heat-obtaining, can allow magnetic valve 3 dead electricity, magnetic valve 6, heat exchanger tube upper segment heat exchanger tube 42 in compressor 1, magnetic valve 6 and second heat exchanger 4 is connected by pipeline and forms the loop, the compressed machine 1 adherence pressure rear electromagnetic valve 6 of refrigerant vapour directly enters in second heat exchanger, the 4 middle and upper part section heat exchanger tubes 42 along pipeline, carry out exchange heat with extraneous cryogenic media, at this moment, geothermal liquid or middle temperature steam and mixtures of liquids during refrigerant condenses in the heat exchanger tube becomes, reflux then in the compressor 1, circulate.
Although relate to a kind of hot-gas bypass and surface cooler supercooling defrosting device has carried out special description to disclosed with reference to embodiment, embodiment described above is illustrative and not restrictive, under the situation that does not break away from the spirit and scope of the present invention, all variations and modification are all within the scope of the present invention.
Claims (5)
1. hot-gas bypass and surface cooler supercooling defrosting device, comprise the compressor (1), first heat exchanger (2), first magnetic valve (3), second heat exchanger (4) that connect successively by pipeline, and formation loop, it is characterized in that: the heat exchanger tube in described second heat exchanger (4) is made up of the super cooled sect heat exchanger tube (41) and the upper segment heat exchanger tube (42) of bottom, and super cooled sect heat exchanger tube (41) is connected by expansion valve (5) with upper segment heat exchanger tube (42).
2. hot-gas bypass according to claim 1 and surface cooler supercooling defrosting device is characterized in that: described expansion valve (5) in heating power expansion valve, electric expansion valve or the capillary any.
3. hot-gas bypass according to claim 2 and surface cooler supercooling defrosting device is characterized in that: also be connected with another magnetic valve (6) between described upper segment heat exchanger tube (42) and compressor (1) refrigerant outlet.
4. according to claim 1 or 2 or 3 described hot-gas bypass and surface cooler supercooling defrosting devices, it is characterized in that: described second heat exchanger (4) is a fin-tube heat exchanger.
5. according to claim 1 or 2 or 3 described hot-gas bypass and surface cooler supercooling defrosting devices, it is characterized in that: described first heat exchanger (2) be in board-like, shell-tube type or the double pipe heat exchanger any.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910042060A CN101639310A (en) | 2009-08-21 | 2009-08-21 | Hot-gas bypass and surface cooler supercooling defrosting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910042060A CN101639310A (en) | 2009-08-21 | 2009-08-21 | Hot-gas bypass and surface cooler supercooling defrosting device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101639310A true CN101639310A (en) | 2010-02-03 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910042060A Pending CN101639310A (en) | 2009-08-21 | 2009-08-21 | Hot-gas bypass and surface cooler supercooling defrosting device |
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| CN (1) | CN101639310A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102226608A (en) * | 2011-04-27 | 2011-10-26 | 海尔集团公司 | Air conditioner defrosting system, air conditioner and air conditioner defrosting method |
| CN103673138A (en) * | 2013-12-27 | 2014-03-26 | Tcl空调器(中山)有限公司 | Air conditioner and control method thereof |
| CN111351143A (en) * | 2020-04-02 | 2020-06-30 | 北京工业大学 | Integral room air conditioner |
-
2009
- 2009-08-21 CN CN200910042060A patent/CN101639310A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102226608A (en) * | 2011-04-27 | 2011-10-26 | 海尔集团公司 | Air conditioner defrosting system, air conditioner and air conditioner defrosting method |
| CN102226608B (en) * | 2011-04-27 | 2013-03-27 | 海尔集团公司 | Air conditioner defrosting system, air conditioner and air conditioner defrosting method |
| CN103673138A (en) * | 2013-12-27 | 2014-03-26 | Tcl空调器(中山)有限公司 | Air conditioner and control method thereof |
| CN103673138B (en) * | 2013-12-27 | 2016-09-21 | Tcl空调器(中山)有限公司 | Air-conditioner and control method thereof |
| CN111351143A (en) * | 2020-04-02 | 2020-06-30 | 北京工业大学 | Integral room air conditioner |
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Application publication date: 20100203 |