CN203928478U - A kind of low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier - Google Patents
A kind of low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier Download PDFInfo
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- CN203928478U CN203928478U CN201420251782.1U CN201420251782U CN203928478U CN 203928478 U CN203928478 U CN 203928478U CN 201420251782 U CN201420251782 U CN 201420251782U CN 203928478 U CN203928478 U CN 203928478U
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Abstract
The utility model provides a kind of low condensing pressure degree of depth to cross cold high-efficiency dehumidifier, comprises air channel, the first blower fan and refrigerant dehumidification system, and refrigerant dehumidification system comprises evaporimeter, the first condenser, the second condenser, compressor, throttling arrangement.The utility model, by adding bypass flow passage on the air channel between the first condenser and the second condenser, has increased the ventilation of the first condenser, has reduced the condensing pressure of refrigerant gas in condenser; In the utility model, the first condenser is for heat release cooling and the refrigerant gas heat release condensation liquefaction of superheated refrigerant gas sensible heat part, the second condenser was lowered the temperature cold for refrigerant liquid, disconnected the fin heat bridge between the first condenser and the second condenser, improved the degree of supercooling of the second condenser ends refrigerant liquid, be conducive to reduce the vaporization ratio of refrigerant liquid in throttling arrangement, improve the evaporation endothermic ability of cold-producing medium in evaporimeter, significantly improved dehumidifier Energy Efficiency Ratio.
Description
Technical field
The utility model relates to dehumidifier design field, relates in particular to a kind of low condensing pressure degree of depth and crosses cold high-efficiency dehumidifier.
Background technology
Dehumidifier is to utilize refrigeration means to reduce airborne water vapour component, reaches the electric equipment that reduces air absolute moisture content object.The moistureproof and mildewproof of the article such as crop seeds, electronic product, precision instrument, audio-visual product, paper, clothes, leatherware, medicine, the dehumidifying of coastal area and fog-zone, the patient who suffers from rheumatism, respiratory disease, and old man, puerpera and infant's daily life, nurse, all need to create especially a suitable humidity environment.Therefore, dehumidifier is widely used in the manufacturing shop of electronic product, precision instrument, food and medicine, and audio-video chamber, library, archive office, inspection and quarantine chamber, computer floor, laboratory, equipment chamber, telecommunication closet, bank, operating room, tobacco warehouse, civil air defense constructions and installations, military depot, and the Code in Hazardous Special Locations such as food, medicine, seed storehouse.
In recent years, along with improving constantly of people's living standard, Domestic dehumidifying machine has showed thriving business opportunity, and enters rapidly vast average family room and conventional office, for people create more comfortable live and work environment.The dehumidifier of main flow, is all to adopt vapor compression type refrigerating system at present.During refrigeration system operation, what blower fan sucked cools to by evaporimeter under the dew-point temperature of humid air containing humid air, and airborne water vapour is heat release condensation on the aluminium fin of evaporimeter, completes dehumidifying.
This dehumidifier is simple in structure, cheap, reliable, is easy to safeguard.But the dehumidification rate of this dehumidifier is low, and easily cause energy dissipation, now subject matter enumerated as follows:
One, condenser ventilation is less than normal, and condensing pressure is raised, and causes power consumption increase, pressure reduction increase, compression ratio increase, the Energy Efficiency Ratio of compressor to reduce
Refrigerant dehumidification system of the prior art is when operation, the condensation thermal discharge of high-temperature high-pressure refrigerant gas in condenser, be refrigerant gas from evaporimeter, bring cool-down dehumidification time the humid air sensible heat Q1 that emits, humid air water vapour condensation heat Q2 and the summation of compressor to the work done during compression A three of low pressure refrigerant gas, be generally 3 times of left and right of the sensible heat Q1 that emits of the humid air cooling of vaporizer side.And the condenser of refrigerant dehumidification system, evaporimeter are in same air channel, share a blower fan, adopt series system to ventilate; For evaporimeter can dehumidify by effective temperature-reducing to air amount under the dew-point temperature of air, the ventilation of blower fan just can not be too large; And met the ventilation of evaporimeter cool-down dehumidification, less than normal again for condenser; Cause the air themperature of the condenser of flowing through to rise excessive, drive condenser condenses temperature to raise, namely condensing pressure is raised, and causes the pressure reduction of refrigerant dehumidification system condensing pressure and evaporating pressure to increase, the power consumption of compressor increases, compression ratio increases, and Energy Efficiency Ratio reduces.
Two, monoblock type condenser has weakened condenser ends refrigerant liquid " excessively cold " degree, causes the evaporation endothermic ability of evaporimeter to comprise the decline of dehumidifying effect
Existing dehumidifier adopts monoblock type condenser, attempt in a monoblock type condenser, heat release cooling, the condensation heat release liquefaction of refrigerant gas and the further cooling of refrigerant liquid of sensible heat part that completes continuously the superheated refrigerant gas that compressor discharges is excessively cold.In fact, because the selected material of monoblock type condenser is all copper, the good conductor of the heat such as aluminium, thereby in " the heat release cooling of superheated refrigerant gas sensible heat part ", " refrigerant gas condensation heat release liquefaction " and " refrigerant liquid further lower the temperature cold " these three has between the region of obvious temperature fall along fin direction formation " heat bridge ", cause heat from " the heat release cooling of superheated refrigerant gas sensible heat part ", transmit to " refrigerant liquid was lowered the temperature cold " region along fin in " refrigerant gas condensation heat release liquefaction " region, seriously undermined " excessively cold " degree of condenser ends refrigerant liquid.Due in condenser ends refrigerant liquid " excessively cold " deficiency, refrigerant liquid temperature exceeds much than the cold-producing medium evaporating temperature in evaporimeter, and refrigerant liquid carries out before evaporation endothermic will be first self temperature being reduced to evaporating temperature in evaporimeter, for this reason, in capillary before entering evaporimeter, there is again a small amount of liquid refrigerant and do not enter just in advance carburation by evaporation of evaporimeter, absorb the sensible heat of most liquid refrigerants to promote its " excessively cold " to evaporating temperature.And a small amount of liquid refrigerant does not enter evaporimeter just shift to an earlier date carburation by evaporation in capillary, this further causes again the evaporation endothermic ability of evaporimeter to comprise the decline of dehumidifying effect.
Utility model content
For dehumidifier of the prior art, " condenser ventilation is less than normal, condensing pressure is raised, cause the power consumption of compressor to increase, pressure reduction increases, compression ratio increases, Energy Efficiency Ratio reduces " and " the heat bridge effect of monoblock type condenser fin has weakened condenser ends refrigerant liquid ' excessively cold ' degree, cause the evaporation endothermic ability of evaporimeter to comprise the decline of dehumidifying effect " two large problems, the utility model is that a kind of low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier, this dehumidifier comprises air channel and is arranged on the first blower fan and the refrigerant dehumidification system in described air channel, wherein,
On described air channel, be provided with air inlet and air outlet, and described refrigerant dehumidification system is positioned at described air inlet, described the first blower fan is positioned at described air outlet;
Described refrigerant dehumidification system comprises compressor and evaporimeter and the first condenser, and described steamer is connected and forms a circulation canal of flowing through for cold-producing medium with described compressor with the pipeline in described the first condenser; The pipeline of described cold-producing medium in described compressor starts is flowed through described the first condenser and described evaporimeter successively;
Described evaporimeter is near described air inlet, and described the first condenser, between described the first blower fan and described evaporimeter, and offers two or more bypass flow passages on the air channel between described evaporimeter and described the first condenser;
Under the effect of described the first blower fan, from air inlet, start containing humid air successively after described evaporimeter, described the first condenser and described blower fan, from described air outlet discharge dry air; Meanwhile, under the effect of described the first blower fan, the air that two or more bypass flow passages of offering on the air channel between described evaporimeter and described the first condenser enter, has significantly increased the ventilation of the first condenser.
Preferably, described refrigerant dehumidification system also comprises second condenser of connecting with described the first condenser, described the second condenser is between described evaporimeter and described bypass flow passage, and the heat release area of described the first condenser is greater than the heating area of described the second condenser; Pipe ends in described the second condenser connects respectively the pipeline in described the first condenser and described evaporimeter.
Preferably, the bottom of described evaporimeter is provided with a water-collecting tray, and described water-collecting tray is connected with a return water tank or sewer by a water pipe.
Preferably, described throttling arrangement adopts capillary or electric expansion valve.
Preferably, described the first blower fan adopts centrifugal blower.
Preferably, between described the second condenser and described bypass flow passage, be also provided with the second blower fan.
The utility model, owing to adopting above technical scheme, makes it compared with prior art, and the advantage having and good effect are:
1) a kind of low condensing pressure degree of depth that the utility model provides is crossed cold high-efficiency dehumidifier, by adding bypass flow passage on the air channel between evaporimeter and the first condenser, thereby the ventilation that makes the first condenser reaches the more than 3 times of evaporimeter ventilation, reduced the condensing pressure of refrigerant gas in condenser, thereby refrigerant dehumidification system condensing pressure and the pressure reduction of evaporating pressure have been reduced, the power consumption of compressor, compressor pressure ratios have significantly improved dehumidifying Energy Efficiency Ratio;
2) a kind of low condensing pressure degree of depth that the utility model provides is crossed cold high-efficiency dehumidifier, a condenser of the prior art is split into the first condenser and the second condenser being cascaded, the first condenser is mainly used in heat release cooling and the refrigerant gas heat release condensation liquefaction of superheated refrigerant gas sensible heat part, and the second condenser is mainly used in refrigerant liquid and lowered the temperature cold; Thereby disconnected the fin heat bridge between the first condenser and the second condenser, improved the degree of supercooling of the second condenser ends refrigerant liquid, be conducive to reduce the vaporization ratio of refrigerant liquid in throttling arrangement, guarantee the completeness and efficiency of the evaporation endothermic ability of cold-producing medium in evaporimeter, thereby improved evaporation endothermic ability and the dehumidifying effect of evaporimeter.
Accompanying drawing explanation
By reference to the accompanying drawings, by the detailed description of stating below, can more clearly understand above-mentioned and other feature and advantage of the present utility model, wherein:
Fig. 1 is the structural representation of existing dehumidifier Facad structure schematic diagram of the present utility model;
Fig. 2 is the structural representation of the utility model embodiment mono-;
Fig. 3 is the structural representation of the utility model embodiment bis-;
Fig. 4 is the refrigerated dehumidification pressure-enthalpy chart of refrigerated dehumidification pressure-enthalpy chart in prior art, the utility model embodiment bis-;
Fig. 5 is the structural representation of the utility model embodiment tri-.
Symbol description:
1-air channel
101-air inlet
102-air outlet
103-bypass flow passage
2-evaporimeter
3-condenser
301-the first condenser
302-the second condenser
4-the first blower fan
5-compressor
6-throttling arrangement
7-water pipe
8-reclaims tank
9-gas-liquid separation device
10-the second blower fan.
The specific embodiment
Referring to the accompanying drawing that the utility model embodiment is shown, below the utility model will be described in more detail.Yet the utility model can be with many multi-form realizations, and should not be construed as the restriction of the embodiment being subject in this proposition.On the contrary, it is abundant and complete open in order to reach proposing these embodiment, and makes those skilled in the art understand scope of the present utility model completely.In these accompanying drawings, for clarity sake, may amplify size and the relative size in layer and region.
Be available technology adopting vapor compression type refrigerating system dehumidifier as shown in fig. 1, containing humid air from the air inlet in air channel 1 start successively to heat up through evaporimeter cool-down dehumidification and condenser dry after, via centrifugal blower 4, dry air is discharged, but dehumidifier of the prior art exists, " condenser ventilation is less than normal, condensing pressure is raised, cause the power consumption of compressor to increase, pressure reduction increases, compression ratio increases, Energy Efficiency Ratio reduces " and " the heat bridge effect of monoblock type condenser fin has weakened condenser ends refrigerant liquid ' excessively cold ' degree, cause the evaporation endothermic ability of evaporimeter to comprise the decline of dehumidifying effect " two large problems, in order to address the above problem, the utility model provides a kind of low condensing pressure degree of depth to cross cold high-efficiency dehumidifier.
Embodiment mono-
With reference to Fig. 2, this low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier and is comprised that this dehumidifier comprises air channel 1, the first blower fan 4 and refrigerant dehumidification system, and the first blower fan 4 and refrigerant dehumidification system are arranged side by side in air channel 1.Wherein, air channel 1 has air outlet 102 places that an air inlet 101 and air outlet 102, the first blower fans 4 are positioned at air channel 1; The preferred centrifugal blower of the first blower fan 4, also selects other types blower fan certainly, is not restricted herein.
In the present embodiment, refrigerant dehumidification system comprises evaporimeter 2, condenser 3, compressor 5, and wherein evaporimeter 2 and condenser 3 include bending pipeline and be arranged on the fin that bends pipeline outside, and wherein fin can be aluminium fin, and bending pipeline can be copper pipe.Evaporimeter 2 and condenser 3 are arranged side by side, and evaporimeter 2 is near air inlet 101, and condenser 3, near the first blower fan 4, once passes through evaporimeter 2, condenser 3 and the first blower fan 4 containing humid air from air inlet 101 enters; The pipeline of evaporimeter 2 is connected with the pipeline of condenser 3, and the pipeline in the pipeline in condenser 3, evaporimeter 2 is connected successively with compressor 5, forms a circulation canal.On this circulation canal, be still provided with throttling arrangement 6 and gas-liquid separation device 9, from compressor 5, start cold-producing medium and flow to successively condenser 3 → throttling arrangement 6 → evaporimeter 2 → gas-liquid separation device 9, finally get back to again in compressor 5; Wherein, throttling arrangement 6 is for reducing the pressure that flows to the cold-producing medium in evaporimeter 2, and throttling arrangement 6 can adopt capillary, electric expansion valve etc., is not restricted herein; Gas-liquid separation device 9 is for separating of the liquid part in the refrigerant gas going out in flash-pot out.
In the present embodiment, the below of evaporimeter 2 is provided with water-collecting tray, and during containing humid air process evaporimeter 2, heat release cools under the dew-point temperature containing humid air, and airborne water vapour heat release is condensed into water, and flows in water-collecting tray along the fin of evaporimeter 2; Water-collecting tray is also input to the water of collecting in one return water tank 8 by a water pipe.
In the present embodiment, on the air channel 1 between evaporimeter 2 and condenser 3, also offer bypass flow path 10 3, can in air channel 1 upper side wall and lower wall, symmetry offer two bypass flow path 10s 3, certainly the size of bypass flow path 10 3 and number is set all can regulates as the case may be is not restricted herein.The utility model is by offering bypass flow path 10 3, thereby increased the air quantity of the condenser 3 of flowing through, and its air quantity reached flow through the more than 3 times of evaporimeter 2 air quantity.
The operation principle that this low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier is specific as follows:
One, the periodic duty principle of cold-producing medium
High temperature refrigerant gas after out pressurized of compressor 5, starts to enter from a side of condenser 3, realizes the heat release cooling of refrigerant gas sensible heat part; Along the copper pipe pipeline in condenser 3, the direction against air draught in air channel travels forward in refrigerant gas continuation, and further cooling realizes refrigerant gas condensation heat release liquefaction; When refrigerant liquid passes through the tail end of condenser 3, then carried out cold treatment, obtained the refrigerant liquid of lower temperature, and realized refrigerant liquid and lowered the temperature cold.The refrigerant liquid of low temperature, after throttling arrangement 6 decompression, is transfused in evaporimeter 2, absorbs after the heat of air of the evaporimeter 2 of flowing through, and evaporation becomes low pressure refrigerant gas; Compressor 5 flows to condenser 3 after the low pressure refrigerant gas of being come by evaporimeter 2 being pressurizeed again, thereby forms a complete refrigerant circulation.
Two, the dehumidification principle that contains humid air
Under the effect of the first blower fan 4, containing humid air, from air inlet 101, enter in air channel 1; The air evaporimeter 2 of first flowing through, the fin by evaporimeter 2 transfers heat to the refrigerant liquid in evaporimeter 2 pipelines, makes refrigerant liquid evaporation become low pressure refrigerant gas and discharges; Simultaneously, flow through being cooled to below dew point containing humid air of evaporimeter 2, thereby make to be converted into water containing the water vapour condensation heat release in humid air, and along evaporimeter 2, flow in the water leg of evaporimeter below setting, water leg is input to water in return water tank 8 and reclaims by a water pipe again.
Remove the Cryogenic air after water vapour, from evaporimeter 2, flow to condenser 3; Owing to also offering bypass flow path 10 3 on the air channel 1 between evaporimeter 2 and condenser 3, thereby the air quantity that flows to condenser 3 is increased; The right of the self cooling condenser 3 of Cryogenic air starts, when first Cryogenic air passes through the afterbody of condenser 3 rightmost sides, now the temperature of air is relatively low, refrigerant liquid in condenser 3 ends is carried out to heat exchange, thereby realized refrigerant liquid in the condenser 3 ends cold effect of lowering the temperature, realized again the intensification effect of air.Air continues to flow to the right along condenser 3, when condenser 3 most of centre position, absorbs a large amount of heats and heats up, and makes the liquefaction of the refrigerant gas condensation heat release in condenser 3 on this position simultaneously; Finally, air stream is through the high order end of condenser 3, and further the sensible heat of absorptive condenser 2 inner refrigerant gases, becomes dry air, discharges, thereby completed whole air initial procedure after the first blower fan 4.
In the present embodiment, by set up bypass flow path 10 3 between condenser 3 and evaporimeter, significantly increase the ventilation of condenser 3, make the ventilation of condenser 3 reach the more than 3 times of evaporimeter 2 ventilations; And improve condenser 3 outside air mass flows and improve convective heat-transfer coefficient, just reduced the condensing pressure of refrigerant gas in condenser 3, thereby refrigerant dehumidification system condensing pressure and the pressure reduction of evaporating pressure have been reduced, the power consumption of compressor, compressor pressure ratios have significantly improved dehumidifying Energy Efficiency Ratio.
Embodiment bis-
With reference to figure 3, the present embodiment is the improvement of doing on the basis of embodiment mono-.Concrete, in the present embodiment, refrigerant dehumidification system comprises two condensers, concrete the first condenser 301 that comprises series connection and the second condenser 302, the first condenser 301 and the second condenser 302 are arranged side by side, the first condenser 301 is near a side of the first blower fan 4, and the second condenser 302 is near evaporimeter 2 one sides, and bypass flow path 10 3 is between the first condenser 301 and the second condenser 302; Pipe ends in the second condenser 302 connects respectively the pipeline in the first condenser 301 and evaporimeter 2, and throttling arrangement 6 is arranged on the pipeline between the second condenser 302 and evaporimeter 2.
In the present embodiment, the heat release area of the first condenser 301 is greater than the heat release area of the second condenser 302, is equivalent to spatially the condenser in embodiment mono-3 be split into the first condenser 301 and the second condenser 302; Wherein, the first condenser 301 is equivalent to the part that condenser 3 in embodiment mono-is realized " the heat release cooling of superheated refrigerant gas sensible heat part " and " refrigerant gas condensation heat release liquefaction ", and the second condenser 302 is equivalent to the part that condenser 3 in embodiment mono-is realized " refrigerant liquid was further lowered the temperature cold ".Other structures that this low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier in the present embodiment, with reference to the explanation in embodiment mono-, repeat no more herein.
The utility model is by arranging two condensers, and the Cryogenic air that evaporimeter 2 cool-down dehumidifications that make to flow through obtain, by the second condenser 302, improves " excessively cold " degree of the second condenser 2 end refrigerant liquids; Improve " excessively cold " degree of the second condenser 302 end refrigerant liquids, be conducive to reduce the vaporization ratio of refrigerant liquid in throttling arrangement, guarantee refrigerant liquid processed enter into evaporimeter 2 interior after, at the completeness and efficiency of the evaporation endothermic ability of 2 li, evaporimeter.
Refrigerant R134a take below as example, be elaborated:
In evaporimeter, under 4.1 kilograms of pressure, 10 ℃ of conditions of saturation temperature, every kg liquid refrigerant evaporation endothermic amount is 190.74kJ; And this refrigerant liquid specific heat capacity under 16.8 kilograms of pressure, 60 ℃ of conditions of saturation temperature in condenser is 1.66kJ/kg, if increase by 10 ℃ excessively cold at the refrigerant liquid of condenser ends, just in condenser, increased by the thermal discharge of 16.6 kJ/kg, this is also just equivalent to increase by the caloric receptivity of 16.6 kJ/kg in evaporimeter, this caloric receptivity be this cold-producing medium in evaporimeter evaporation endothermic amount 190.74kJ/kg 8.7%; If increase by 20 ℃ excessively cold at the refrigerant liquid of condenser ends, just in condenser, increased by the thermal discharge of 33.2 kJ/kg, this is also just equivalent to increase by the caloric receptivity of 33.2 kJ/kg in evaporimeter, and this caloric receptivity is the 17.4%! of this cold-producing medium evaporation endothermic amount 190.74kJ/kg in evaporimeter
Result of calculation shows, 1 ℃ of the every increase of the degree of supercooling of refrigerant R134a in condenser, the average increment rate of the refrigerating capacity of caused unit mass cold-producing medium approximately 0.8 % (calculating 1-50 ℃ of degree of supercooling scopes); And 1 ℃ of the every increase of the degree of supercooling of cold-producing medium R22 in condenser, the average increment rate of the refrigerating capacity of caused unit mass cold-producing medium is about 1%.
Therefore, a kind of low condensing pressure degree of depth that the utility model provides is crossed cold high-efficiency dehumidifier, cut off in prior art in a complete condenser " the heat release cooling of superheated refrigerant gas sensible heat part ", " refrigerant gas condensation heat release liquefaction " and " refrigerant liquid was further lowered the temperature cold " these three has " heat bridge " forming along fin direction between the region of obvious temperature fall, cut off heat from " the heat release cooling of superheated refrigerant gas sensible heat part ", " refrigerant gas condensation heat release liquefaction " region transmission along fin to " refrigerant liquid was lowered the temperature cold " region, the second condenser 302 after splitting is connected with the first condenser 301, spatially be set up in parallel with evaporimeter 2, make the Cryogenic air of flowing through after evaporimeter cool-down dehumidification flow through the second condenser 302, improve " excessively cold " degree of the second condenser 302 end refrigerant liquids, realize refrigerant liquid excessively cold in the degree of depth of condenser ends, thereby effectively improve the heat absorption capacity of dehumidifier evaporimeter, improve dehumidifying Energy Efficiency Ratio.
With reference to figure 4, Fig. 4 is the comparison diagram of the refrigerated dehumidification pressure-enthalpy chart of refrigerated dehumidification pressure-enthalpy chart and the utility model embodiment bis-in prior art, in Fig. 4,1-2-3-4-5-6-1 is refrigerated dehumidification circulation in prior art, 1-2 '-3 '-4 '-5 '-6 '-1 is refrigerated dehumidification circulation in the present embodiment, can find out thus, condensing pressure decline, degree of supercooling that the low condensing pressure degree of depth that the utility model provides is crossed in cold high-efficiency dehumidifier improve.
Embodiment tri-
With reference to figure 5, the present embodiment is the improvement of doing on the basis of embodiment bis-.Concrete, between the second condenser 302 and bypass flow passage 9, being also provided with the second blower fan 10, other structures that this low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier, with reference to the explanation in embodiment bis-, repeat no more herein.
In the present embodiment, the utility model by adding the second blower fan 10 between the second condenser 302 and bypass flow passage 9, solved with bypass flow path 10 3 and compared, the problem that the second condenser 302 is bigger than normal with the windage of evaporimeter 2 place passage area, contribute to stablize the ventilation of the second condenser 302 and evaporimeter 2, the air distribution that contributes to bypass flow path 10 3, thereby the stable air quantity that increases the condenser 301 of flowing through, reach its air quantity to flow through the more than 3 times of evaporimeter 2 ventilations.
Those skilled in the art should be understood that the utility model can not depart from spirit or scope of the present utility model with many other concrete forms realizations.Although also described embodiment of the present utility model, the utility model should be understood and these embodiment should be restricted to, within the utility model spirit and scope that those skilled in the art can define as appended claims, make and change and revise.
Claims (7)
1. the low condensing pressure degree of depth is crossed a cold high-efficiency dehumidifier, it is characterized in that, this dehumidifier comprises air channel and be arranged on the first blower fan and the refrigerant dehumidification system in described air channel, wherein,
On described air channel, be provided with air inlet and air outlet, and described refrigerant dehumidification system is positioned at described air inlet, described the first blower fan is positioned at described air outlet;
Described refrigerant dehumidification system comprises compressor and evaporimeter and the first condenser, and described evaporimeter is connected and forms a circulation canal of flowing through for cold-producing medium with described compressor with the pipeline in described the first condenser; The pipeline of described cold-producing medium in described compressor starts is flowed through described the first condenser and described evaporimeter successively;
Described evaporimeter is near described air inlet, and described the first condenser, between described the first blower fan and described evaporimeter, and offers two or more bypass flow passages on the air channel between described evaporimeter and described the first condenser;
Under the effect of described the first blower fan, from air inlet, start containing humid air successively after described evaporimeter, described the first condenser and described blower fan, from described air outlet discharge dry air; Meanwhile, under the effect of described the first blower fan, the air that two or more bypass flow passages of offering on the air channel between described evaporimeter and described the first condenser enter, has significantly increased the ventilation of described the first condenser.
2. the low condensing pressure degree of depth according to claim 1 is crossed cold high-efficiency dehumidifier, it is characterized in that, described refrigerant dehumidification system also comprises second condenser of connecting with described the first condenser, described the second condenser is between described evaporimeter and described bypass flow passage, and the heat release area of described the first condenser is greater than the heat release area of described the second condenser; Pipe ends in described the second condenser connects respectively the pipeline in described the first condenser and described evaporimeter.
3. the low condensing pressure degree of depth according to claim 1 and 2 is crossed cold high-efficiency dehumidifier, it is characterized in that, the bottom of described evaporimeter is provided with a water-collecting tray, and described water-collecting tray is connected with a return water tank or sewer by a water pipe.
4. the low condensing pressure degree of depth according to claim 1 and 2 is crossed cold high-efficiency dehumidifier, it is characterized in that, on the entrance of described evaporimeter interior conduit, is provided with throttling arrangement.
5. the low condensing pressure degree of depth according to claim 4 is crossed cold high-efficiency dehumidifier, it is characterized in that, described throttling arrangement adopts capillary or electric expansion valve.
6. the low condensing pressure degree of depth according to claim 1 and 2 is crossed cold high-efficiency dehumidifier, it is characterized in that, described the first blower fan adopts centrifugal blower.
7. the low condensing pressure degree of depth according to claim 2 is crossed cold high-efficiency dehumidifier, it is characterized in that, between described the second condenser and described bypass flow passage, is also provided with the second blower fan.
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104019574A (en) * | 2014-05-16 | 2014-09-03 | 上海伯涵热能科技有限公司 | Low-condensing-pressure deep supercooling efficient dehumidifier |
| TWI671494B (en) * | 2017-01-12 | 2019-09-11 | 日商三菱電機股份有限公司 | Dehumidifier |
| CN110290851A (en) * | 2017-02-23 | 2019-09-27 | 三菱电机株式会社 | Dehumidifier |
| CN111676049A (en) * | 2020-05-19 | 2020-09-18 | 青岛科技大学 | Accurate high-efficient multistage condensation splitter |
| CN114562770A (en) * | 2021-07-16 | 2022-05-31 | 浙江普林艾尔电器工业有限公司 | Take big amount of wind dehumidifier of bypass |
-
2014
- 2014-05-16 CN CN201420251782.1U patent/CN203928478U/en active Active
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104019574A (en) * | 2014-05-16 | 2014-09-03 | 上海伯涵热能科技有限公司 | Low-condensing-pressure deep supercooling efficient dehumidifier |
| CN104019574B (en) * | 2014-05-16 | 2017-10-31 | 浙江普林艾尔电器工业有限公司 | A kind of low condensing pressure deeply undercooling high-efficiency dehumidifier |
| TWI671494B (en) * | 2017-01-12 | 2019-09-11 | 日商三菱電機股份有限公司 | Dehumidifier |
| CN110290851A (en) * | 2017-02-23 | 2019-09-27 | 三菱电机株式会社 | Dehumidifier |
| CN111676049A (en) * | 2020-05-19 | 2020-09-18 | 青岛科技大学 | Accurate high-efficient multistage condensation splitter |
| CN114562770A (en) * | 2021-07-16 | 2022-05-31 | 浙江普林艾尔电器工业有限公司 | Take big amount of wind dehumidifier of bypass |
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Effective date of registration: 20160324 Address after: Hangzhou City, Zhejiang province 311612 large hangtou town in the city of Jiande Industrial Zone Patentee after: Zhejiang Preair Electrical Appliance Industry Co., Ltd. Address before: 200237 Shanghai, Hongmei South Road, No. 777, the bottom floor, room 53, 2101 Patentee before: Shanghai Bohan Thermal Energy Technology Co., Ltd. |