CN204006862U - The independent refrigerated dehumidification device of controlling - Google Patents
The independent refrigerated dehumidification device of controlling Download PDFInfo
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- CN204006862U CN204006862U CN201420427003.9U CN201420427003U CN204006862U CN 204006862 U CN204006862 U CN 204006862U CN 201420427003 U CN201420427003 U CN 201420427003U CN 204006862 U CN204006862 U CN 204006862U
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- liquid refrigerant
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Abstract
The utility model provides a kind of independent desiccant cooling device of controlling, and the humidity based on this regional air when regional air is freezed dehumidifies, and it is characterized in that, comprising: refrigeration module, comprises: compressor, condenser, evaporimeter, cold pipe; And flow-control module, for controlling the flow of high pressure sub-cooled liquid refrigerant, comprise: temperature and humidity sensing portion; Set storage part; Comparing section; Judgement control part; Flow restriction portion, when judgement control part output low discharge control signal control flow restriction portion carries out low discharge current limliting by high pressure sub-cooled liquid refrigerant, obtain low evaporating pressure cold-producing medium, evaporimeter evaporates absorption region air heat by low evaporating pressure cold-producing medium and regional air is dehumidified simultaneously; Judgement control part output high flow capacity flow control signal control flow restriction portion carries out high flow capacity current limliting by high pressure sub-cooled liquid refrigerant and obtains high evaporation pressure cold-producing medium, and evaporimeter evaporates absorption region air heat by high evaporation pressure cold-producing medium.
Description
Technical field
The utility model relates to environment and regulates guarantee field, is specifically related to a kind of independent desiccant cooling device of controlling.
Background technology
The design evaporating temperature of refrigeration (dehumidifying) circulations such as tradition aircondition, constant temperature and humidity device is lower, no matter make the actual humiture situation of actual air control band, even if the interior humidity of air conditioning area is outside comfort zone (partially dry), thereby also can not improving evaporating temperature, refrigeration machine do not reduce moisture removal.In addition, the low wind pushing temperature that causes of evaporating temperature is too low, the blowing feeling that causes user more strongly, more uncomfortable.
In prior art, for consideration energy-conservation and that improve comfortableness, some central air conditioner systems adopt the means such as solution dehumidification or rotary wheel dehumidifying to realize the independent process of thermic load and humidity load.But said system is generally bulky, all need thermal source for the regeneration of solution or runner, system architecture is complicated, and initial cost is very high, needs professional and technical personnel to safeguard and moves, and for most of occasions such as family and business, all can not be suitable for.The patent No. is 200820171750.5 the warm and humid independent air-conditioning system > > regulating of utility model patent < <, this patent provides a kind of technical scheme of the warm and humid independent air-conditioning system regulating, comprise coolant circulating system, water circulation system and air-cooled ducted air conditioner supply air system, use the independent chilled water of 12～22 ℃, by sensible heat in radiation or convection end decontamination chamber; Detect indoor humidity simultaneously, when needs dehumidify, adopt freeze drying, realize the energy-conservation double effects improving with indoor air quality, but this system too complex, cost is expensive, and it is large that the structure of system and adjusting etc. realize difficulty.
Utility model content
The utility model carries out in order to solve above-mentioned problem, and object is to provide a kind of independence simple in structure and the saving energy to control desiccant cooling device.
The utility model provides a kind of independent desiccant cooling device of controlling, there is such feature, comprise: refrigeration module, for regional air is freezed, comprise: for gaseous refrigerant being compressed to the compressor of rear discharge high temperature and high pressure gaseous refrigerant, for high temperature and high pressure gaseous refrigerant is carried out to the cooling condenser that obtains high pressure sub-cooled liquid refrigerant, heat for absorption region air freezes and exports gaseous refrigerant to the evaporimeter of the entrance of compressor, and be arranged between condenser and evaporimeter the cold pipe for delivery of high pressure sub-cooled liquid refrigerant, and flow-control module, for regulating high pressure sub-cooled liquid refrigerant at the flow of cold pipe, comprise: be arranged on place, evaporimeter inlet scoop for arriving corresponding temperature value according to the temperature acquisition of regional air and the temperature and humidity sensing portion to corresponding humidity value according to the humidity collection of regional air, setting storage part for capping humidity value and ceiling temperature value storing temperature value and humidity value, for by temperature value and ceiling temperature value compares and humidity value and upper limit humidity value compare comparing section, according to comparing section to temperature value and humidity value, relatively judge whether that temperature value is greater than ceiling temperature value and humidity value and is greater than upper limit humidity value and when being judged as YES, exports low discharge conditioning signal when being judged as the judgement control part that sends high flow capacity conditioning signal while not being, be arranged in cold pipe for receiving low discharge conditioning signal or high flow capacity conditioning signal and limitting the flow restriction portion of the flow of refrigerator pipes mesohigh sub-cooled liquid refrigerant according to low discharge conditioning signal or high flow capacity conditioning signal, wherein, high pressure sub-cooled liquid refrigerant after flow restriction portion, enter that evaporimeter is evaporated and the heat of absorption region air after become gaseous refrigerant, when regulating flow restriction portion that high pressure sub-cooled liquid refrigerant is carried out to low discharge current limliting, judgement control part output low discharge conditioning signal obtains low evaporating pressure cold-producing medium, judgement control part output high flow capacity flow regulating signal regulates flow restriction portion that high pressure sub-cooled liquid refrigerant is carried out to high flow capacity current limliting and obtains high evaporation pressure cold-producing medium.
The independent control in desiccant cooling device providing at the utility model, can also there is such feature, comprise: wherein, flow restriction portion comprises: for high pressure sub-cooled liquid refrigerant is converted into high evaporation pressure cold-producing medium high evaporation pressure capillary, be arranged on high evaporation pressure capillary for according to receiving the magnetic valve of low discharge conditioning signal or the folding of high flow capacity conditioning signal control valve and the low evaporating pressure capillary being in parallel with electromagnetic valve entrance and high evaporation pressure capillary outlet.
The independent control in desiccant cooling device providing at the utility model, there is such feature, comprise: wherein, flow restriction portion is electric expansion valve, and electric expansion valve is arranged in cold pipe for receiving judgement control part and sends correspondingly control valve openings of sizes of low discharge conditioning signal or high flow capacity conditioning signal.
The effect of utility model and effect
According to the involved independent desiccant cooling device of controlling of the utility model, by flow-control module according to the temperature value of regional air and humidity value and ceiling temperature value and upper limit humidity value relatively after, when the humidity of regional air is not more than upper limit humidity, judgement control part regulates flow restriction portion to carry out high flow capacity current limliting, and making high pressure sub-cooled liquid refrigerant is that high evaporation pressure cold-producing medium enters evaporation endothermic in evaporimeter by throttling; When regional air temperature is greater than ceiling temperature value and when region humidity is greater than upper limit humidity value, judgement control part regulates flow restriction portion to carry out low discharge current limliting, and to make high pressure sub-cooled liquid refrigerant be low evaporating pressure cold-producing medium by throttling and enter in evaporimeter.Low evaporating pressure cold-producing medium is low at the evaporating pressure of evaporimeter, and corresponding evaporating temperature is lower, thereby the steam of regional air is discharged after the surface of evaporimeter is condensed into condensate water.This device is realized simultaneously the independence of temperature and humidity is regulated, and when regional air humidity is excessive, regional air is dehumidified, otherwise only freezes, the advantage of improve service efficiency, saving the energy.
Accompanying drawing explanation
Fig. 1 is the independent structural representation of controlling desiccant cooling device in the utility model embodiment;
Fig. 2 is the independent thermodynamic analysis LgP-h schematic diagram of controlling in desiccant cooling device in the utility model embodiment; And
Fig. 3 is the independent example calculation thermodynamic analysis LgP-h figure controlling in desiccant cooling device in the utility model embodiment.
The specific embodiment
For technological means, creation characteristic that the utility model is realized, reach object with effect is easy to understand, following examples are specifically addressed independent control desiccant cooling device of the present utility model by reference to the accompanying drawings.
Fig. 1 is the independent structural representation of controlling desiccant cooling device in the utility model embodiment.
As shown in Figure 1, the independent desiccant cooling device 100 of controlling freezes for the air to air conditioning area in the present embodiment, and when regional air humidity exceeds human body comfort zone humidity range, regional air is dehumidified.
The independent desiccant cooling device 100 of controlling specifically comprises refrigeration module 10 and flow-control module 20.
Refrigeration module 10, for regional air is freezed, comprises compressor 11, condenser 12, evaporimeter 13, cold pipe 14, device for drying and filtering 15 and liquid-sighting glass 16.Cold pipe 14 is arranged between the gas outlet of condenser 12 and the import of evaporimeter 13, for delivery of high pressure sub-cooled liquid refrigerant.
Compressor 11 is for compressing gaseous refrigerant rear discharge high temperature and high pressure gaseous refrigerant.The air inlet of condenser 12 is connected with the gas outlet of compressor 11, condenser 12 for receiving high temperature and high pressure gaseous refrigerant and it being cooled to high pressure sub-cooled liquid refrigerant.The outlet of evaporimeter 13 is connected with the entrance of compressor 11, and the logical supercooling tube 14 of high pressure sub-cooled liquid refrigerant enters in evaporimeter 13 and is evaporated to gaseous refrigerant after processing, and gaseous refrigerant outputs to compressor 11 from the outlet of evaporimeter 13.Device for drying and filtering 15 and liquid-sighting glass 16 are arranged in cold pipe 14 successively, and device for drying and filtering 15 is for high pressure sub-cooled liquid refrigerant is dried, and liquid-sighting glass 16 is for observing the liquid level of high pressure sub-cooled liquid refrigerant.
Flow-control module 20 carries out Flow-rate adjustment for the high pressure sub-cooled liquid refrigerant to cold pipe 14, comprises temperature and humidity sensing portion 21, signal processor 22 and flow restriction portion 23.
Temperature and humidity sensing portion 21 is arranged on the place, inlet scoop of evaporimeter 13, for gathering the temperature and humidity of air section, and by the temperature value obtaining and humidity value input signal processor 22.
Signal processor 22, for regulating flow restriction portion 23, comprises and sets storage part 22a, comparing section 22b judgement control part 22c.Set storage part 22a for capping temperature value and upper limit humidity value, and temperature value and the humidity value of the regional air that collects of storage temperature and humidity sensing portion 21.Comparing section 22b compares with ceiling temperature value and the upper limit humidity value set respectively for temperature value and the humidity value that setting storage part 22a is stored, judgement control part 22c judges according to the comparative result of comparing section 22b, when temperature value is greater than ceiling temperature value and humidity value and is greater than upper limit humidity value, be judged as YES, judgement control part 22c output low discharge conditioning signal carries out low discharge current limliting in flow restriction portion 23; When temperature value is greater than ceiling temperature value and humidity value and is not more than upper limit humidity value, be judged as NO, judgement control part 22c output high flow capacity conditioning signal carries out high flow capacity current limliting in flow restriction portion 23.
Flow restriction portion 23, on the cold pipe 14 between liquid-sighting glass 16 and evaporimeter 13, carries out throttling action for high pressure sub-cooled liquid refrigerant is carried out to current limliting realization to high pressure sub-cooled liquid refrigerant.Flow restriction portion 23 adopts high evaporation pressure capillary 23a and low evaporating pressure capillary 23b in parallel, and the magnetic valve 23c that is arranged in high evaporation pressure capillary 23a.
Magnetic valve 23c is for receiving low discharge conditioning signal and the high flow capacity conditioning signal of judgement control part 22c output.When magnetic valve 23c receives low discharge conditioning signal, the valve closing of magnetic valve 23c, high pressure sub-cooled liquid refrigerant obtains low evaporating pressure cold-producing medium after low evaporating pressure capillary 23b throttling; When magnetic valve 23c receives high flow capacity conditioning signal, the valve opening of magnetic valve 23c, high pressure sub-cooled liquid refrigerant obtains high evaporation pressure cold-producing medium after high evaporation pressure capillary 23b throttling.
The independent of the present embodiment controlled in desiccant cooling device 100, according to flow-control module 20, the humidity of regional air is adjusted in comfort zone humidity range.Use the independent desiccant cooling device 100 of controlling to dehumidify, concrete steps are as follows:
Normal refrigeration step, when the temperature value collecting when temperature and humidity sensing portion 21 is greater than ceiling temperature value and humidity value and is not more than upper limit humidity value, judgement control part 22c output high flow capacity conditioning signal is in magnetic valve 23c, make the valve opening of magnetic valve 23c, switch to high evaporation pressures cycle: it is cooling to carrying out in condenser 12 that gaseous refrigerant is discharged high temperature and high pressure gaseous refrigerant after by compressor 11 compression, and high temperature and high pressure gaseous refrigerant is cooled to high pressure sub-cooled liquid refrigerant.High pressure sub-cooled liquid refrigerant is become after high evaporation pressure cold-producing medium by throttling by the less high evaporation pressure capillary 23a of throttling action, in high evaporation pressure cold-producing medium input evaporimeter 13, evaporate, high evaporation pressure cold-producing medium is evaporated into as gaseous refrigerant, continues to enter in compressor 11.So move in circles, realize circularly cooling, because the evaporating pressure of high evaporation pressure cold-producing medium is high, corresponding evaporating temperature is higher, stable higher than dew point, steam in regional air is not condensed, and realizes when regional air humidity is being freezed when the comfort humidity scope and not dehumidifying.
Refrigerated dehumidification step, when the temperature value collecting when temperature and humidity sensing portion 21 is greater than ceiling temperature value and humidity value and is greater than upper limit humidity value, judgement control part 22c output low discharge conditioning signal is in magnetic valve 23c, make the valve closing of magnetic valve 23c, switch to the circulation of low evaporating pressure: it is cooling to carrying out in condenser 12 that gaseous refrigerant is discharged high temperature and high pressure gaseous refrigerant after by compressor 11 compressions, high temperature and high pressure gaseous refrigerant is cooled to high pressure sub-cooled liquid refrigerant, because the valve closing of magnetic valve 23c, high pressure sub-cooled liquid refrigerant is become after low evaporating pressure cold-producing medium by throttling by the larger low evaporating pressure capillary 23b of throttling action, in low evaporating pressure cold-producing medium input evaporimeter 13, evaporate, the low height of evaporating pressure due to low evaporating pressure cold-producing medium, corresponding evaporating temperature is lower, stable lower than dew point, steam in regional air is discharged at evaporimeter 13 surface sweatings and after flowing into water accumulating disc (not shown in FIG.), low evaporating pressure cold-producing medium is evaporated into as gaseous refrigerant, continue to enter in compressor 11.So move in circles, realize according to regional air humidity situation is dehumidified when freezing.
Fig. 2 is the independent thermodynamic analysis LgP-h schematic diagram of controlling desiccant cooling device in the utility model embodiment.
As shown in Figure 2, in Fig. 2 with numeral " 1 ", " 2 ", " 4 " respectively corresponding enthalpy be followed successively by h
1, h
2, h
4, numeral " 1' ", " 2' ", the ratio enthalpy that " 4' " is corresponding are followed successively by h
1', h
2', h
4'.The design evaporating pressure of conventional air-conditioning refrigeration machine is p '
e, corresponding evaporating temperature is T '
e, because evaporating pressure is lower, refrigerating capacity q
e' less, q '
e=h '
1-h '
4, w' is larger for compressor wasted work, w '=h '
2-h '
1, coefficient of performance of refrigerating ε ' is less,
the object of traditional low evaporating pressure, the design of low evaporating temperature is by making evaporator coil surface temperature bear indoor humidity load lower than the method for dew-point temperature.When not needing to dehumidify, more than evaporator surface temperature is increased to dew-point temperature, can avoids unnecessary dehumidifying, and can improve the coefficient of performance of kind of refrigeration cycle, as shown in Figure 2, when not needing to dehumidify, evaporating pressure is increased to p
e, corresponding evaporating temperature is T
e, because evaporating pressure is higher, refrigerating capacity q
elarger, q
e=h
1-h
4, when condensing pressure is constant, w is less for compressor wasted work, w=h
2-h
1, coefficient of performance of refrigerating ε is larger,
Fig. 3 is the independent example calculation thermodynamic analysis LgP-h figure that controls desiccant cooling device in the utility model embodiment.
Concrete data instance calculates:
Suppose and take R410A as cold-producing medium, condensation temperature is T
k=50 ℃, corresponding condensing pressure P
k=3071.10kPa, during high evaporation pressures cycle, high evaporation pressure P
e=1248.89kPa, corresponding high evaporation temperature T
e=15 ℃, and during low evaporating pressure, low evaporating pressure P
e=933.50kPa, should low evaporating temperature T
e=5 ℃.
In Fig. 3 with numeral " 1 " to " 6 " 1 to the 6 state enthalpy of corresponding high evaporation pressures cycle heating power below in calculating respectively, 1' to the 6' state enthalpy below numeral " 1' " to " 6' " is corresponding respectively in the calculating of high evaporation pressures cycle heating power.
High evaporation pressures cycle heating power calculates: 1 state enthalpy h
1=206.07kJ/kg, 2 state enthalpy h
2=431.04kJ/kg, 2 state entropy s
2=1815.32kJ/ (kgK), compression process is isentropic Compression, therefore, 3 state entropy s
3=1815.32kJ/ (kgK), 3 state delivery temperature T
3=72.28 ℃, 3 state enthalpy h
3=459.51kJ/kg, 4 state enthalpy h
4=292.56kJ/kg, 5 state enthalpy h
5=279.04kJ/kg, throttling process is constant-enthalpy process, therefore, 6 state enthalpy h
6=279.04kJ/kg, unit mass refrigerating capacity q
e=h
2-h
5=155.60kJ/kg, compressor wasted work w=h
3-h
2=24.87kJ/kg, coefficient of performance of refrigerating
High evaporation pressures cycle heating power calculates: 1 ' state enthalpy h
1 '=219.06kJ/kg, 2 ' state enthalpy h
2 '=431.04kJ/kg, 2 ' state entropy s
2 '=1830.42kJ/ (kgK), compression process is isentropic Compression, therefore, 3 ' state entropy s
3 '=1830.42kJ/ (kgK), 3 ' state delivery temperature T
3 '=76.66 ℃, 3 ' state enthalpy h
3 '=464.79kJ/kg, 4 state enthalpy h
4=292.56kJ/kg, 5 state enthalpy h
5=279.04kJ/kg, throttling process is constant-enthalpy process, therefore, 6 ' state enthalpy h
6 '=279.04kJ/kg, unit mass refrigerating capacity q '
e=h
2 '-h
5=152kJ/kg, compressor wasted work w '=h
3 '-h
2 '=33.75kJ/kg, coefficient of performance of refrigerating
Visible, by concrete data, bring the computation structure obtaining in coefficient of performance of refrigerating calculating formula into known, adopt the independent desiccant cooling device of controlling of the present embodiment, during high evaporation pressures cycle, refrigeration performance improves 39.1%.
The effect of embodiment and effect
According to the present embodiment, according to the involved independence of the utility model, control desiccant cooling device, by flow-control module according to the temperature value of regional air and humidity value and ceiling temperature value and upper limit humidity value relatively after, when the humidity of regional air is not more than upper limit humidity, judgement control part regulates flow restriction portion to carry out high flow capacity current limliting, and making high pressure sub-cooled liquid refrigerant is that high evaporation pressure cold-producing medium enters evaporation endothermic in evaporimeter by throttling; When regional air temperature is greater than ceiling temperature value and when region humidity is greater than upper limit humidity value, judgement control part regulates flow restriction portion to carry out low discharge current limliting, and to make high pressure sub-cooled liquid refrigerant be low evaporating pressure cold-producing medium by throttling and enter in evaporimeter.Low evaporating pressure cold-producing medium is low at the evaporating pressure of evaporimeter, and corresponding evaporating temperature is lower, thereby the steam of regional air is discharged after the surface of evaporimeter is condensed into condensate water.This device is realized simultaneously the independence of temperature and humidity is regulated, and when regional air humidity is excessive, regional air is dehumidified, otherwise only freezes, the advantage of improve service efficiency, saving the energy.
In the present embodiment, due to low evaporating pressure capillary and high evaporation pressure capillary, therefore, realize and in evaporimeter, carry out two evaporating pressure evaporations, this device has advantages of energy-saving and emission-reduction simple in structure and saves operating cost.In addition, user's comfort level significantly improves.Therefore, adopt the present embodiment not only to realize indoor temperature and humidity and regulate more accurately, improved indoor air quality and comfortableness, can also increase refrigerating capacity, improve comprehensive coefficient of performance of refrigerating, save the energy and cost of use.Experiment test show the initial cost increasing only need 8 months recyclable, have advantages of that system forms and regulates simple, energy-saving and emission-reduction and saving operating cost.
Above-mentioned embodiment is preferred case of the present utility model, is not used for limiting protection domain of the present utility model.
Flow restriction portion is also not only limited to low evaporating pressure capillary and the high evaporation pressure capillary in preferred case; Also can adopt electric expansion valve, by regulating the openings of sizes of electric expansion valve can realize high evaporation pressures cycle and low evaporating pressure circulates.When judgement control part sends low discharge conditioning signal, electric expansion valve receives this low discharge conditioning signal, controlling opening of valve turns down, because throttling action is large, make high pressure sub-cooled liquid refrigerant be become low evaporating pressure cold-producing medium and enter evaporimeter by throttling and carry out evaporation endothermic, realize refrigeration and dehumidifying; When judgement control part sends high flow capacity conditioning signal, electric expansion valve receives this high flow capacity conditioning signal, and controlling opening of valve is opened greatly, because throttling action is little, make high pressure sub-cooled liquid refrigerant be become high evaporation pressure cold-producing medium and enter evaporimeter by throttling and carry out evaporation endothermic, realize refrigeration.
Claims (3)
1. the independent desiccant cooling device of controlling, is characterized in that, comprising:
Refrigeration module, for regional air is freezed, comprise: for gaseous refrigerant is compressed rear discharge high temperature and high pressure gaseous refrigerant compressor, for described high temperature and high pressure gaseous refrigerant is carried out the cooling condenser that obtains high pressure sub-cooled liquid refrigerant, for absorb the heat of described regional air carry out described refrigeration and export described gaseous refrigerant to the evaporimeter of the entrance of described compressor and be arranged on described condenser and described evaporimeter between for delivery of the cold pipe of described high pressure sub-cooled liquid refrigerant; And
Flow-control module, for regulating described high pressure sub-cooled liquid refrigerant at the flow of cold pipe, comprise: be arranged on place, described evaporimeter inlet scoop for arriving corresponding temperature value according to the temperature acquisition of described regional air and the temperature and humidity sensing portion to corresponding humidity value according to the humidity collection of described regional air; For capping humidity value and ceiling temperature value and store the setting storage part of described temperature value and described humidity value; For by described temperature value and described ceiling temperature value compares and described humidity value and described upper limit humidity value compare comparing section; According to described comparing section to described temperature value and described humidity value, relatively judge whether that described temperature value is greater than described ceiling temperature value and described humidity value and is greater than described upper limit humidity value and when being judged as YES, exports low discharge conditioning signal when being judged as the judgement control part that sends high flow capacity conditioning signal while not being; Be arranged on described cold pipe for receiving described low discharge conditioning signal or high flow capacity conditioning signal and limiting the flow restriction portion of the flow of high pressure sub-cooled liquid refrigerant described in described cold pipe according to described low discharge conditioning signal or high flow capacity conditioning signal,
Wherein, described high pressure sub-cooled liquid refrigerant after described flow restriction portion, enter described evaporimeter be evaporated and absorb the heat of described regional air after become described gaseous refrigerant,
When regulating described flow restriction portion that described high pressure sub-cooled liquid refrigerant is carried out to low discharge current limliting, the low discharge conditioning signal of described judgement control part output obtains low evaporating pressure cold-producing medium,
The high flow capacity flow regulating signal of described judgement control part output regulates described flow restriction portion that described high pressure sub-cooled liquid refrigerant is carried out to high flow capacity current limliting and obtains high evaporation pressure cold-producing medium.
2. independence according to claim 1 is controlled desiccant cooling device, it is characterized in that:
Wherein, described flow restriction portion comprises: for described high pressure sub-cooled liquid refrigerant is converted into described high evaporation pressure cold-producing medium high evaporation pressure capillary, be arranged on described high evaporation pressure capillary for according to receiving the magnetic valve of described low discharge conditioning signal or the folding of high flow capacity conditioning signal control valve and the low evaporating pressure capillary being in parallel with described electromagnetic valve entrance and described high evaporation pressure capillary outlet.
3. independence according to claim 1 is controlled desiccant cooling device, it is characterized in that:
Wherein, described flow restriction portion is electric expansion valve,
Described electric expansion valve is arranged in described cold pipe for receiving described judgement control part and sends correspondingly control valve openings of sizes of described low discharge conditioning signal or high flow capacity conditioning signal.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420427003.9U CN204006862U (en) | 2014-07-31 | 2014-07-31 | The independent refrigerated dehumidification device of controlling |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420427003.9U CN204006862U (en) | 2014-07-31 | 2014-07-31 | The independent refrigerated dehumidification device of controlling |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104165487A (en) * | 2014-07-31 | 2014-11-26 | 上海理工大学 | Independent-control refrigeration and dehumidification device and method |
| CN115218310A (en) * | 2022-08-01 | 2022-10-21 | 上海理工大学 | Temperature and humidity separate control multi-working-condition air conditioning system based on single-machine double-evaporation heat pump unit |
-
2014
- 2014-07-31 CN CN201420427003.9U patent/CN204006862U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104165487A (en) * | 2014-07-31 | 2014-11-26 | 上海理工大学 | Independent-control refrigeration and dehumidification device and method |
| CN115218310A (en) * | 2022-08-01 | 2022-10-21 | 上海理工大学 | Temperature and humidity separate control multi-working-condition air conditioning system based on single-machine double-evaporation heat pump unit |
| CN115218310B (en) * | 2022-08-01 | 2023-11-07 | 上海理工大学 | Temperature-humidity-division control multi-station air conditioning system based on single-machine double-evaporation heat pump unit |
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