CN204787452U - Fountain refrigerating plant - Google Patents
Fountain refrigerating plant Download PDFInfo
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- CN204787452U CN204787452U CN201520263828.6U CN201520263828U CN204787452U CN 204787452 U CN204787452 U CN 204787452U CN 201520263828 U CN201520263828 U CN 201520263828U CN 204787452 U CN204787452 U CN 204787452U
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Abstract
The utility model provides a fountain refrigerating plant. Fountain refrigerating plant includes: cooling cycle system, liquid circulation system, control system and box, cooling cycle system is including the compressor, condenser, capillary and the evaporimeter that link together, liquid circulation system includes liquor pump, nozzle and liquid storage pot, the liquor pump warp the evaporimeter with the nozzle is connected, the nozzle stretches into the inner chamber of box, the liquor pump with the liquid storage pot is connected, the inner chamber bottom of box is formed with ji yekou, the liquid storage pot is connected ji yekou. Cool off through the spray liquid of cooling cycle system in to liquid circulation system, improved refrigeration plant's coefficient of performance, improved energy utilization efficiency, realized the function of fast cold, simultaneously, because cooling speed is very fast, also makes opening of compressor stop the number of times and obviously reduce, prolonged fountain refrigerating plant's life.
Description
Technical field
The utility model relates to refrigerating plant, particularly relates to a kind of fountain refrigerating plant.
Background technology
The cold transmittance process (heat transfer process in contrast) of current refrigeration plant: the cold-producing medium evaporation endothermic in evaporimeter, produce cold by the mode of " heat conduction " make to be close to evaporimeter liner of refrigeration equipment temperature reduce, the liner of refrigeration equipment of low temperature passes through free convection, radiation (if inside has the heat exchange mode of forced convection device to be forced convertion) makes refrigeration plant enclose inside gas lower the temperature, cryogenic gas carries out heat exchange by free convection (if inside has the heat exchange mode of forced convection device to be forced convertion) and storing, the heat of storing is taken away.The heat of storing is also taken away by the mode of radiation heat transfer by refrigeration plant inwall and storing.
There are two subject matters in above-mentioned cold transmittance process: one is refrigeration plant inside is be main heat transferring medium with air, due to the density (1.164kg/m3 of air, 20 DEG C) and thermal conductivity factor (2.524 × 10-2W/ (m DEG C)) lower, cause heat transfer coefficient low; Two is that free convection and radiation heat transfer (refrigeration plant internal face and storing temperature range in) two kinds of coefficients of heat transfer of heat exchange mode own are lower, in 10 ~ 100W/ (m2 DEG C) scope.On the one hand, according to the thermal conduction study fundamental formular of the heat exchange amount=coefficient of heat transfer × heat transfer temperature difference × heat exchange area, when refrigeration plant storing is more, need higher heat exchange heat, refrigeration plant generally realizes by reducing evaporating temperature (namely increasing heat transfer temperature difference), and according to thermodynamics Carnot's theorem, refrigeration plant evaporating temperature is lower, coefficient of performance of refrigerating (COP) is lower, and cooling rate is slower; On the other hand; the temperature-sensitive bag of current refrigeration plant temperature controller is placed on the pipeline of refrigeration system and (is generally positioned over evaporator pipeline exit); judge whether refrigeration indoor air temperature is reduced to setting value by the temperature at evaporator outlet place; under the air themperature of refrigeration plant inside is reduced to design temperature, namely compressor shuts down in limited time, until compressor is just started shooting work again when the air themperature of refrigeration plant inside rises to the temperature upper limit of temperature controller setting.Because air themperature and storing temperature exist the larger temperature difference; so when the compressor is shut down, storing temperature is not reduced to design temperature, and therefore storing heat heats refrigeration plant inner air very soon; temperature is elevated to compressor and again starts shooting work, directly causes the frequent start-stop of compressor.Cooling rate makes the energy saving of refrigerator-freezer in urgent need to be improved slowly, and the start and stop of compressor frequently make the functional reliability of refrigerator-freezer decline, and greatly shortens the service life of compressor.
At present, water is utilized to replace air as the water refrigeration plant of heat exchange refrigerant, by the forced-convection heat transfer of water and storing, heat transfer coefficient scope is at 1000 ~ 10000W/ (m2 DEG C), this adds the heat transfer coefficient of refrigeration plant to a certain extent, but the inside of water refrigeration plant must have large water gaging to exist, the liquid level of water determines the producing level of refrigeration plant volume, and the existence of large water gaging simultaneously too increases the requirement of refrigeration plant intensity.In addition the evaporimeter of refrigeration system is positioned over refrigeration plant inside, occupies the dischargeable capacity of refrigeration plant.
Summary of the invention
In view of this, the utility model provides a kind of fountain refrigerating plant, is intended to the start-stop time of the compressor reducing fountain refrigerating plant, realizes the function that speed is cold.
The technical scheme that the utility model provides is, a kind of fountain refrigerating plant, comprising: cooling cycle system, fluid circulation system, control system and casing; Described cooling cycle system comprises the compressor, condenser, capillary and the evaporimeter that link together; Described fluid circulation system comprises liquor pump, nozzle and fluid reservoir, described liquor pump is connected with described nozzle through described evaporimeter, described nozzle stretches into the inner chamber of described casing, described liquor pump is connected with described fluid reservoir, the intracavity bottom of described casing is formed with liquid collection opening, and described fluid reservoir connects described liquid collection opening.
Further, described evaporimeter is plate type heat exchanger or double pipe heat exchanger, and described liquor pump is connected with described nozzle by described evaporimeter.
Further, described liquor pump is connected by pipeline with between nozzle, and described pipeline is connected with described evaporimeter heat conduction.
Further, control valve and filter is also disposed with between described fluid reservoir and described liquor pump.
Further, also comprise control system, described control system comprises temperature controller, temperature sensor, differential pressure pickup and position switch, described temperature sensor is located between the liquid collection opening of described fluid reservoir and described bottom half, described temperature controller is connected respectively with described temperature sensor, described liquor pump, described compressor, described differential pressure pickup is located between the import and export of described liquor pump, described differential pressure pickup is connected to described compressor, and described position switch is located at the door body place of described casing.
Further, the median particle diameter of the spray droplet of described nozzle is 0.5-5.5mm.
The fountain refrigerating plant that the utility model provides, by cooling cycle system, the ejecting liquid in fluid circulation system is cooled, ejecting liquid will be directly injected on storing that cabinets cavity holds by shower nozzle, direct and storing are carried out heat exchange by the ejecting liquid of low temperature, and change due to the heat transfer coefficient of liquid, the ejecting liquid on storing can fast and storing carry out heat exchange, improve the coefficient of performance of refrigeration plant, improve energy utilization efficiency, achieve the function that speed is cold; Meanwhile, because cooling rate is very fast, also makes the start-stop time of compressor obviously reduce, extend the service life of fountain refrigerating plant.
Accompanying drawing explanation
In order to be illustrated more clearly in the utility model embodiment or technical scheme of the prior art, be briefly described to the accompanying drawing used required in embodiment or description of the prior art below, apparently, accompanying drawing in the following describes is embodiments more of the present utility model, for those of ordinary skill in the art, under the prerequisite not paying creative work, other accompanying drawing can also be obtained according to these accompanying drawings.
Fig. 1 is the schematic diagram of the utility model fountain refrigerating plant embodiment.
Detailed description of the invention
For making the object of the utility model embodiment, technical scheme and advantage clearly, below in conjunction with the accompanying drawing in the utility model embodiment, technical scheme in the utility model embodiment is clearly and completely described, obviously, described embodiment is the utility model part embodiment, instead of whole embodiments.Based on the embodiment in the utility model, those of ordinary skill in the art are not making the every other embodiment obtained under creative work prerequisite, all belong to the scope of the utility model protection.
As shown in Figure 1, the present embodiment fountain refrigerating plant, mainly comprises compressor 1, condenser 3, capillary 4, evaporimeter 5, liquor pump 6, nozzle 7, fluid reservoir 8, control valve 9, filter 10, temperature controller 11, temperature sensor 12, differential pressure pickup 13, position switch 14 and casing 15.Wherein, compressor 1, condenser 3, capillary 4 and evaporimeter 5 form cooling cycle system; Liquor pump 6, filter 10, nozzle 7, fluid reservoir 8 and control valve 9 form fluid circulation system; Temperature controller 11, temperature sensor 12, differential pressure pickup 13 and position switch 14 forming control system.
The structure of cooling cycle system is specially: compressor 1, condenser 3, capillary 4 and evaporimeter 5 circulate successively and be joined together to form the refrigerating circuit of confession refrigerant flowing.
The structure of fluid circulation system is specially: the ejecting liquid that liquor pump 6 exports is transported to nozzle 7 after evaporimeter 5 freezes, nozzle 7 stretches into the inner chamber of casing 15, liquor pump 6 is connected with fluid reservoir 8 through filter 10, control valve 9 successively, and fluid reservoir 8 is connected to the inner chamber of casing 15.Wherein, the intracavity bottom of casing 15 can be formed with liquid collection opening (not shown), and fluid reservoir 8 is connected the ejecting liquid in collection tank 15 with this osculum; In addition, evaporimeter 15 can adopt the structure such as plate type heat exchanger or double pipe heat exchanger, there are in evaporimeter 15 two streams, wherein a stream is for refrigerant flowing, another stream is for spray liquid flowing, and liquor pump 6 is connected with nozzle 7 by evaporimeter 5, or, directly be connected by pipeline between liquor pump 6 with nozzle 7, this pipeline be attached on evaporimeter 5 with by evaporimeter 5 refrigeration stream through this ducted spray liquid.
The structure of control system is specially: temperature sensor 12 is located between the liquid collection opening bottom fluid reservoir 8 and casing 15, temperature controller 11 is connected respectively with temperature sensor 12, liquor pump 6, compressor 1, differential pressure pickup 13 is located between the import and export of liquor pump 6, differential pressure pickup 13 is also connected to compressor 1, position switch 14 is located at the door body place of casing 15, for judging whether the door body (not shown) on casing 15 is opened.
Below in conjunction with accompanying drawing, the course of work of the present embodiment fountain refrigerating plant and control method are described, for the storing of refrigeration in casing 15 for beverage.
The duty of the present embodiment fountain refrigerating plant is mainly divided into startup, operation, shutdown and door body to open four kinds of operating modes; beverage is deposited in the inner chamber of casing 15 in the mode of vertical angles as far as possible; the spray droplet size of setting nozzle 7 is to median size; the particle size values of the spray droplet of median is 1-3mm; close door body; temperature controller 11 set temperature value is 10 DEG C, switches on power, and the present embodiment fountain refrigerating plant enters the start operating performance stage.
Cooling cycle system is by evaporimeter 5 and the ejecting liquid heat exchange in fluid circulation system, and the ejecting liquid after refrigeration to be ejected on storing by nozzle 7 and to carry out heat exchange by fluid circulation system; Control system controls cooling cycle system and fluid circulation system simultaneously; Fluid circulation system controls cooling cycle system simultaneously, and the step of cooling cycle system is specially:
First judge whether door body is opened (now closing) according to the position switch 14 of unexpected winner body; Then temperature sensor 12 passes to the temperature signal of temperature controller 11 is normal temperature (because beverage is just put into), deviation is had with set temperature value, temperature controller 11 controls liquor pump 6 power supply immediately and connects, and fluid circulation system is started working, and connects compressor 1 power supply simultaneously;
After but compressor 1 power supply is connected, whether compressor 1 starts the control of also pressure difference sensor 13, judge whether the import and export of liquor pump 6 successfully set up pressure reduction by differential pressure pickup 13, if successfully set up pressure reduction, then fluid circulation system normally works, compressor 1 starts, and cooling cycle system is started working.
The transmittance process of cold is: the cold-producing medium evaporation endothermic in the evaporimeter 5 of cooling cycle system produces cold, fluid circulation system is (for water, ejecting liquid is pure water, ethylene glycol, one or more or the ethanol water of phenol in glycerine or the soluble-salt of alkali and alkaline earth metal ions are (as sodium chloride, calcium chloride) the aqueous solution, according to the refrigeration of storing, cryogenic temperature selects the ejecting liquid be suitable for) water be pumped to evaporimeter 5 by liquor pump 6 and freeze, the cold of absorption refrigeration agent becomes cold water, cold water is atomized as high speed droplet by nozzle 7, droplet is directly injected to beverage packaging surface, with beverage heat exchange, simultaneously because droplet has very high flow velocity, getting on beverage to make beverage shake, cold is made to be delivered to beverage inside from beverage packaging fast, reduce the peripheral and inner temperature difference of beverage simultaneously, beverage is fully cooled, through with beverage heat exchange after drop temperature raise, and come together in bottom casing 15, enter the fluid reservoir 8 of fluid circulation system by gravity from liquid collection opening, be then pumped into evaporimeter 5 place through control valve 9, filter 10 by liquor pump 6 successively, enter next round circulation.
Water can flow through temperature sensor 12 when the liquid collection opening of casing 15 enters fluid reservoir 8, and the temperature signal of water is passed to temperature controller 11.Due to the continuous transmission of cold, the temperature of beverage reduces gradually, and the temperature of backwater also reduces gradually.When temperature reaches 10 DEG C of setting, temperature controller 11 disconnects the power supply of liquor pump 6 and compressor 1 simultaneously, and fluid circulation system and cooling cycle system quit work simultaneously, enter shutdown operating mode.Due to constantly importing into of external heat, make internal beverage temperature increase gradually, when reaching the higher limit of temperature controller 11 startup, fountain refrigerating plant restarts.
Fountain refrigerating plant is when normally running, if opening door body is beaten in midway, for the liquid preventing nozzle 7 from spraying flies out casing 15, the power-off while that position switch 14 controlling liquor pump 6 and compressor 1, fluid circulation system and cooling cycle system are cut off simultaneously, and fountain refrigerating plant quits work.After a body closes, restart liquor pump 6 and compressor 1.
Analyze and find, cold and storing heat exchange just inner at fountain refrigerating plant at weakest link, thus the spray heat transfer technology that the coefficient of heat transfer can be reached 100000W/ (m2) by the utility model is incorporated into fountain refrigerating plant refrigerating field, simultaneously, propose the adjustable and spray droplet size of spray mode according to the philosophy of hydrodynamics, thermal conduction study to be determined by casing 15 interior reservoir species, with regard to refrigerating function, the utility model fountain refrigerating plant, except selling the soft bottle beverage of refrigeration, can also realize the quick-frozen to fruit or packaged food.
Such as:
For bottled drink, select, close to the spray droplet size of column, liquid is sprayed storing surface, secondly less spray droplet size (scope of the median diameter value of drop is 0.5-2mm) then selected by (scope of the median diameter value of drop is 1-3mm), fruit to select larger spray droplet size (the median particle diameter of drop is 2-5.5mm), plastic bottle liquid beverage for glass, metal bottle dixie cup.This is because larger size droplet diameter has relatively high kinetic energy, beverage bottle and internal liquid vibrations can be made, also internal heat be strengthened while strengthening storing external heat-exchanging, realize cold/fast hot merit energy of speed of refrigeration plant further.
And for the storing of such as fruits, because of its surperficial rapid wear and inner heat conduction is the bottleneck of whole heat transfer, undue strengthening external heat-exchanging is little to overall contribution, therefore only need provide uniform low temperature environment, so select the spray droplet size close to being atomized.
The raising of casing 15 internal heat coefficient makes the coefficient of heat transfer from cold-producing medium to storing improve, the temperature difference transmitted required for identical heat will reduce, the technical solution of the utility model is adopted to freeze, the temperature difference≤5 DEG C between the evaporating temperature of cooling cycle system and the temperature-sensitive bag temperature of temperature controller 11, and the temperature difference≤10 DEG C between the target temperature of storing, optimize the performance of cooling cycle system greatly.
The basic reason of conventional refrigeration equipment high frequent start and stop under heavy load has two: one to be the position of temperature controller temperature-sensitive bag; Two is have the larger temperature difference between evaporating temperature and storing.Wherein, as previously mentioned, the introducing of spraying technique decreases the temperature difference between evaporating temperature and storing, and on the other hand, temperature sensor 12 is installed between liquid collection opening bottom refrigeration plant casing 15 and fluid reservoir 8 by the utility model.Under 128L refrigeration plant inside loads the prerequisite of 80 bottles of 500ml bottled waters, contrast by experiment, in 24h, conventional refrigeration equipment start-stop 100 times, and the only start and stop 2 times of the cold energy-saving cabinet of speed of the present utility model.
Last it is noted that above embodiment is only in order to illustrate the technical solution of the utility model, be not intended to limit; Although be described in detail the utility model with reference to previous embodiment, those of ordinary skill in the art is to be understood that: it still can be modified to the technical scheme described in foregoing embodiments, or carries out equivalent replacement to wherein portion of techniques feature; And these amendments or replacement, do not make the essence of appropriate technical solution depart from the spirit and scope of each embodiment technical scheme of the utility model.
Claims (6)
1. a fountain refrigerating plant, is characterized in that, comprising: cooling cycle system, fluid circulation system, control system and casing; Described cooling cycle system comprises the compressor, condenser, capillary and the evaporimeter that link together; Described fluid circulation system comprises liquor pump, nozzle and fluid reservoir, described liquor pump is connected with described nozzle through described evaporimeter, described nozzle stretches into the inner chamber of described casing, described liquor pump is connected with described fluid reservoir, the intracavity bottom of described casing is formed with liquid collection opening, and described fluid reservoir connects described liquid collection opening.
2. fountain refrigerating plant according to claim 1, is characterized in that, described evaporimeter is plate type heat exchanger or double pipe heat exchanger, and described liquor pump is connected with described nozzle by described evaporimeter.
3. fountain refrigerating plant according to claim 1, is characterized in that, described liquor pump is connected by pipeline with between nozzle, and described pipeline is connected with described evaporimeter heat conduction.
4. fountain refrigerating plant according to claim 1, is characterized in that, is also disposed with control valve and filter between described fluid reservoir and described liquor pump.
5. fountain refrigerating plant according to claim 4, it is characterized in that, also comprise control system, described control system comprises temperature controller, temperature sensor, differential pressure pickup and position switch, described temperature sensor is located between the liquid collection opening of described fluid reservoir and described bottom half, described temperature controller and described temperature sensor, described liquor pump, described compressor is connected respectively, entering of described liquor pump be located at by described differential pressure pickup, between outlet, described differential pressure pickup is connected to described compressor, described position switch is located at the door body place of described casing.
6. fountain refrigerating plant according to claim 4, is characterized in that, the median particle diameter of the spray droplet of described nozzle is 0.5-5.5mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520263828.6U CN204787452U (en) | 2014-09-09 | 2015-04-28 | Fountain refrigerating plant |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410455996.5A CN104180553A (en) | 2014-09-09 | 2014-09-09 | Spraying type energy-saving fast refrigerator and control method thereof |
| CN201420515218 | 2014-09-09 | ||
| CN201520263828.6U CN204787452U (en) | 2014-09-09 | 2015-04-28 | Fountain refrigerating plant |
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| CN204787452U true CN204787452U (en) | 2015-11-18 |
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| CN201520263825.2U Active CN204787390U (en) | 2014-09-09 | 2015-04-28 | Fountain equipment of heating |
| CN201510207304.XA Active CN106152630B (en) | 2014-09-09 | 2015-04-28 | Fountain refrigerating plant and control method |
| CN201510207066.2A Active CN106152589B (en) | 2014-09-09 | 2015-04-28 | Fountain heating-cooling equipment and control method |
| CN201510207273.8A Active CN106152591B (en) | 2014-09-09 | 2015-04-28 | Fountain storage equipment and control method |
| CN201520263937.8U Active CN204787391U (en) | 2014-09-09 | 2015-04-28 | Fountain refrigeration plant |
| CN201520263828.6U Active CN204787452U (en) | 2014-09-09 | 2015-04-28 | Fountain refrigerating plant |
| CN201520263717.5U Active CN204787389U (en) | 2014-09-09 | 2015-04-28 | Fountain storing equipment |
| CN201510219890.XA Active CN106196830B (en) | 2014-09-09 | 2015-05-04 | Water cooled refrigeration equipment and control method |
| CN201510219907.1A Active CN106196687B (en) | 2014-09-09 | 2015-05-04 | Spray refrigeration equipment and control method |
| CN201520279360.XU Active CN204787513U (en) | 2014-09-09 | 2015-05-04 | Water -cooled refrigeration plant |
| CN201520279178.4U Active CN204787392U (en) | 2014-09-09 | 2015-05-04 | Refrigerating plant sprays |
| CN201510220152.7A Active CN106196688B (en) | 2014-09-09 | 2015-05-04 | Spray refrigerating plant and control method |
| CN201520279359.7U Active CN204787393U (en) | 2014-09-09 | 2015-05-04 | Refrigeration plant sprays |
| CN201510285611.XA Active CN106196690B (en) | 2014-09-09 | 2015-05-29 | Fountain refrigeration equipment and control method |
| CN201520360057.2U Active CN204787395U (en) | 2014-09-09 | 2015-05-29 | Fountain refrigeration plant |
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| CN201510285448.7A Active CN106196708B (en) | 2014-09-09 | 2015-05-29 | Adjustable spraying refrigeration equipment and control method |
| CN201520360018.2U Active CN204787403U (en) | 2014-09-09 | 2015-05-29 | Refrigeration plant sprays with adjustable |
| CN201510285568.7A Active CN106196689B (en) | 2014-09-09 | 2015-05-29 | Fountain refrigerating plant and control method |
| CN201510370431.1A Active CN105444460B (en) | 2014-09-09 | 2015-06-30 | Fountain refrigeration equipment and control method |
| CN201510370432.6A Active CN106196691B (en) | 2014-09-09 | 2015-06-30 | Fountain refrigerating plant and control method |
| CN201510370460.8A Active CN106196692B (en) | 2014-09-09 | 2015-06-30 | Spray refrigeration equipment and control method |
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| CN201510207235.2A Active CN106152701B (en) | 2014-09-09 | 2015-04-28 | Fountain refrigeration equipment and control method |
| CN201520263825.2U Active CN204787390U (en) | 2014-09-09 | 2015-04-28 | Fountain equipment of heating |
| CN201510207304.XA Active CN106152630B (en) | 2014-09-09 | 2015-04-28 | Fountain refrigerating plant and control method |
| CN201510207066.2A Active CN106152589B (en) | 2014-09-09 | 2015-04-28 | Fountain heating-cooling equipment and control method |
| CN201510207273.8A Active CN106152591B (en) | 2014-09-09 | 2015-04-28 | Fountain storage equipment and control method |
| CN201520263937.8U Active CN204787391U (en) | 2014-09-09 | 2015-04-28 | Fountain refrigeration plant |
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| CN201520263717.5U Active CN204787389U (en) | 2014-09-09 | 2015-04-28 | Fountain storing equipment |
| CN201510219890.XA Active CN106196830B (en) | 2014-09-09 | 2015-05-04 | Water cooled refrigeration equipment and control method |
| CN201510219907.1A Active CN106196687B (en) | 2014-09-09 | 2015-05-04 | Spray refrigeration equipment and control method |
| CN201520279360.XU Active CN204787513U (en) | 2014-09-09 | 2015-05-04 | Water -cooled refrigeration plant |
| CN201520279178.4U Active CN204787392U (en) | 2014-09-09 | 2015-05-04 | Refrigerating plant sprays |
| CN201510220152.7A Active CN106196688B (en) | 2014-09-09 | 2015-05-04 | Spray refrigerating plant and control method |
| CN201520279359.7U Active CN204787393U (en) | 2014-09-09 | 2015-05-04 | Refrigeration plant sprays |
| CN201510285611.XA Active CN106196690B (en) | 2014-09-09 | 2015-05-29 | Fountain refrigeration equipment and control method |
| CN201520360057.2U Active CN204787395U (en) | 2014-09-09 | 2015-05-29 | Fountain refrigeration plant |
| CN201520359889.2U Active CN204787394U (en) | 2014-09-09 | 2015-05-29 | Fountain refrigerating plant |
| CN201510285448.7A Active CN106196708B (en) | 2014-09-09 | 2015-05-29 | Adjustable spraying refrigeration equipment and control method |
| CN201520360018.2U Active CN204787403U (en) | 2014-09-09 | 2015-05-29 | Refrigeration plant sprays with adjustable |
| CN201510285568.7A Active CN106196689B (en) | 2014-09-09 | 2015-05-29 | Fountain refrigerating plant and control method |
| CN201510370431.1A Active CN105444460B (en) | 2014-09-09 | 2015-06-30 | Fountain refrigeration equipment and control method |
| CN201510370432.6A Active CN106196691B (en) | 2014-09-09 | 2015-06-30 | Fountain refrigerating plant and control method |
| CN201510370460.8A Active CN106196692B (en) | 2014-09-09 | 2015-06-30 | Spray refrigeration equipment and control method |
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| CN106152630A (en) * | 2014-09-09 | 2016-11-23 | 青岛海尔特种电冰柜有限公司 | Fountain refrigerating plant and control method |
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| CN109632636A (en) * | 2019-01-09 | 2019-04-16 | 南京航空航天大学 | The refrigerating plant and method of high throughput test fiber and resin micro interface performance |
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2015
- 2015-04-28 CN CN201510207235.2A patent/CN106152701B/en active Active
- 2015-04-28 CN CN201520263825.2U patent/CN204787390U/en active Active
- 2015-04-28 CN CN201510207304.XA patent/CN106152630B/en active Active
- 2015-04-28 CN CN201510207066.2A patent/CN106152589B/en active Active
- 2015-04-28 CN CN201510207273.8A patent/CN106152591B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106152630A (en) * | 2014-09-09 | 2016-11-23 | 青岛海尔特种电冰柜有限公司 | Fountain refrigerating plant and control method |
| CN106152630B (en) * | 2014-09-09 | 2018-12-18 | 青岛海尔特种电冰柜有限公司 | Fountain refrigerating plant and control method |
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