CN102338428A - Total heat recovery fresh air dehumidifying unit - Google Patents
Total heat recovery fresh air dehumidifying unit Download PDFInfo
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- CN102338428A CN102338428A CN2010102379635A CN201010237963A CN102338428A CN 102338428 A CN102338428 A CN 102338428A CN 2010102379635 A CN2010102379635 A CN 2010102379635A CN 201010237963 A CN201010237963 A CN 201010237963A CN 102338428 A CN102338428 A CN 102338428A
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- fresh air
- heat recovery
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- full heat
- dehumidifying unit
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- 238000011084 recovery Methods 0.000 title claims abstract description 43
- 238000007791 dehumidification Methods 0.000 claims abstract description 24
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 23
- 238000001816 cooling Methods 0.000 claims description 14
- 239000007788 liquid Substances 0.000 claims description 12
- 239000003507 refrigerant Substances 0.000 abstract description 11
- 238000004378 air conditioning Methods 0.000 abstract description 6
- 230000000694 effects Effects 0.000 abstract description 4
- 238000005057 refrigeration Methods 0.000 abstract description 3
- 238000009434 installation Methods 0.000 abstract description 2
- 238000010438 heat treatment Methods 0.000 abstract 1
- 238000005507 spraying Methods 0.000 abstract 1
- 238000009833 condensation Methods 0.000 description 12
- 230000005494 condensation Effects 0.000 description 12
- 239000007789 gas Substances 0.000 description 5
- 239000007921 spray Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000004108 freeze drying Methods 0.000 description 2
- 238000001035 drying Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000796 flavoring agent Substances 0.000 description 1
- 235000019634 flavors Nutrition 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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Abstract
The utility model provides a total heat recovery fresh air dehumidification unit, its includes fresh air dehumidification system, the total heat recovery system of return air, refrigerant refrigeration cycle system, bilayer structure about this total heat recovery fresh air dehumidification unit adopts, and this fresh air dehumidification system is located the upper strata, and this total heat recovery system of return air is located the lower floor. The floor area of the unit is reduced, the transportation and the installation are convenient, the water spraying device is effectively arranged, and the heat exchange efficiency of the unit is improved. The total heat recovery fresh air dehumidifying unit is applied to a temperature and humidity independent control air conditioning system to bear latent heat load of all air conditioners, fully utilizes exhaust air to recover energy, improves energy utilization rate, improves sensible heat treatment efficiency and achieves an energy-saving effect.
Description
[technical field]
The present invention relates to field of air conditioning, refer in particular to a kind of full heat recovery fresh air dehumidifying unit.
[background technology]
The purpose of building air conditioning is outdoor indoor waste heat, surplus wet discharge, and the new wind that satisfies hygienic requirements is provided.The load of air-conditioning system is made up of four major parts: indoor sensible heat, indoor latent heat, new wind sensible heat, new wind latent heat.Warm and humid independent control in the fresh air processor group, the fresh air processor group provides the new wind of drying to bear whole latent heat, new wind sensible heat and the indoor sensible heat of part, the requirement that satisfy row CO2 simultaneously, rejects and distinguish the flavor of and fresh air is provided; High temperature cold water unit (12～20 ℃ of freezing water outlets) is born remaining most of indoor sensible heat.
Warm and humid independent control fresh air processor group dehumidification mode mainly contains three kinds: freeze drying, solution dehumidification and rotary wheel dehumidifying.The new blower fan group system of solution dehumidification is complicated, volume is big, there are shortcomings such as corrosivity, cost height in solution, and there are shortcomings such as volume is big in the new blower fan group of rotary wheel dehumidifying and can't extensively promote.And can't satisfying humiture because of its Energy Efficiency Ratio is low, the new blower fan group of existing freeze drying independently controls the high requirement of energy saving.
Therefore, provide the high brand-new full heat recovery fresh air dehumidifying unit of a kind of Energy Efficiency Ratio real for necessary.
[summary of the invention]
The object of the present invention is to provide the high brand-new full heat recovery fresh air dehumidifying unit of a kind of unit eer (COP); This unit is applied to humiture independence control air conditioner system and bears whole air-conditioning latent heat loads; Make full use of air draft and carry out the energy recovery, improve energy utilization rate.
For realizing the object of the invention, following technical scheme is provided:
A kind of full heat recovery fresh air dehumidifying unit; It comprises fresh air dehumidification system, the full heat recovery system of return air, cold-producing medium cooling cycle system; And this full heat recovery fresh air dehumidifying unit adopts double-decker up and down, and this fresh air dehumidification system is positioned at the upper strata, and the full heat recovery system of this return air is positioned at lower floor.Reduced the floor space of unit like this, convenient transportation and installation, and help effectively to be provided with liquid distribution, improve set heat exchange efficient.
This fresh air dehumidification system comprises precooling surface cooler, evaporimeter, second condenser and the pressure fan that sets gradually; The new wind of outdoor high temperature high humidity gets into from unit one side; At first pass through the precooling surface cooler by cool-down dehumidification to precooling point; New wind after the precooling through evaporator by further cool-down dehumidification to state point, by the new wind of the dry low temperature of degree of depth dehumidifying again through second condenser by etc. wetly be heated to new wind air-supply point, last new wind is sent into indoor whole latent heat and the indoor sensible heat of part born.Wherein, be connected with 16～18 ℃ of cold water in the heat exchanger tube of this precooling surface cooler, be connected with 5～7 ℃ cold-producing medium in the cold-producing medium cooling cycle system in the heat exchanger tube of this evaporimeter.
The full heat recovery system of this return air comprises first condenser and exhaust blower, and indoor return air is through first condenser, absorb the first condenser heat after, temperature raises and discharges outdoor by the exhaust blower that is positioned at the outside.
This cold-producing medium cooling cycle system comprises compressor, throttling arrangement and described evaporimeter, first condenser, second condenser that is connected.Enter condenser after coming the low-pressure low-temperature refrigerant vapour machine of being compressed of flash-pot to be compressed into the gas of high pressure-temperature; Cooled off by second condenser outer return air and condensed water deep again after the new air cooling outside first condenser; The high-temperature high-pressure refrigerant liquid that condenser comes gets into evaporimeter after the throttling arrangement throttling becomes low pressure, low temperature liquid; In the evaporimeter heat exchanger tube, behind new wind picked-up heat, be evaporated to gas; Thereby the machine that is compressed again of the refrigerant vapour in the realization kind of refrigeration cycle, evaporimeter sucks and compresses repeated compression, condensation, throttling, evaporation process.
Further; This fresh air dehumidification system also comprises the drip tray that is arranged under precooling surface cooler and the evaporimeter; The full heat recovery system of this return air also comprises the liquid distribution of the connection drip tray that is arranged on first condenser top; Liquid distribution sprays the condensed water in the drip tray to first condenser, thereby reduces condenser heat exchanger tube inner refrigerant condensation temperature, improves new blower fan group heat exchange efficiency.
More preferably, this compressor places the lower floor of this full heat recovery fresh air dehumidifying unit, makes the center of gravity of unit lower like this, avoids the upper strata to bear the weight of compressor, makes unit integral body more firm.
More preferably, the oblique placement of this first condenser can make condensed water longer through the time of condenser, and more the good utilisation condensed water cools off first condenser.
More preferably, the full heat recovery system of this return air comprises the water-cooled case tube heat exchanger, and said case tube heat exchanger has water inlet and delivery port.Adopt the water-cooled case tube heat exchanger as condenser, condensation effect is better, and the efficiency of unit is higher.
The contrast prior art, the present invention has the following advantages:
1) adopt double-decker up and down, reduced the floor space of new blower fan group, be convenient to transportation and install, the condensed water that the while upper strata produces relies on self gravitation to spray to the condenser of lower floor, improves efficiency; 2) adopt dual surface cooler (precooling surface cooler and evaporimeter) that new wind is carried out cool-down dehumidification and handle, make full use of the new wind of high temperature cold water precooling, reduce to carry compressor horsepower, improve the unit efficiency; 3) the double-condenser structure has not only been avoided new wind air-supply generation condensed water but also has been reduced condensation temperature, improves heat exchange efficiency; 3) full recuperation of heat air draft energy adopts the low return air cooler condenser of temperature, improves heat exchange efficiency; 4) condensed water spray cooling, the condensed water spray that precooling surface cooler and evaporimeter are produced reduces condensation temperature, raising unit efficiency significantly to first condenser.
Full heat recovery fresh air dehumidifying unit of the present invention is applied to humiture independence control air conditioner system and bears whole air-conditioning latent heat loads; Make full use of air draft and carry out the energy recovery; Improve energy utilization rate, the efficient that sensible heat is handled improves more than 30%, and whole air conditioner system energy saving is more than 20%.
[description of drawings]
Fig. 1 is the full heat recovery fresh air dehumidifier group system sketch map of the embodiment of the invention one;
Fig. 2 is the full heat recovery fresh air dehumidifier group system sketch map of the embodiment of the invention two.
[specific embodiment]
Embodiment one sees also Fig. 1, and the present invention is a kind of full heat recovery fresh air dehumidifying unit that carries low temperature cold source, and unit adopts double-layer structure up and down, comprises three parts: fresh air dehumidification system, the full heat recovery system of return air, cold-producing medium cooling cycle system.
The fresh air dehumidification system all is positioned at the unit upper strata, comprises precooling surface cooler 5, evaporimeter 4, is positioned at drip tray 7, second condenser 2 and the pressure fan 1 of precooling surface cooler 5 and evaporimeter 4 belows.The new wind of outdoor high temperature high humidity gets into from a side; At first pass through precooling surface cooler 5; Be connected with 16～18 ℃ of cold water in the heat exchanger tube of precooling surface cooler 5, new wind is outer by cool-down dehumidification to precooling point (19～21 ℃ of & relative humidity 90% of dry-bulb temperature) through the heat exchanger tube of precooling surface cooler 5; New wind after the precooling is through evaporator 4, is connected with in the cold-producing medium cooling cycle system 5～7 ℃ cold-producing medium in the heat exchanger tube of evaporimeter 4, and new wind is outer by further cool-down dehumidification to state point (14 ℃ of relative humidity 90% of dry-bulb temperature) through the heat exchanger tube of evaporimeter 4; By the new wind of the dry low temperature of degree of depth dehumidifying again through second condenser 2 by etc. wetly be heated to new wind air-supply point (18 ℃ of & relative humidity 66% of dry-bulb temperature); Be positioned at the new wind of dry low temperature that the pressure fan 1 of indoor will meet the demands at last and send into indoor whole latent heat and the indoor sensible heat of part born.
The full heat recovery system of return air all is positioned at unit lower floor, comprises first condenser 9, is positioned at liquid distribution 8, the exhaust blower 6 of first condenser, 9 tops.Indoor return air (26 ℃ of & relative humidity 60% of dry-bulb temperature) is through first condenser 9, absorb the heat of first condenser after, temperature raises and discharges outdoor by the exhaust blower that is positioned at the outside 6.Liquid distribution 8 is connected with drip tray 7, and the spray of the condensed water in the drip tray 7 to first condenser 9, is reduced the interior condensation of refrigerant temperature of heat exchanger tube of first condenser 9, improves new blower fan group heat exchange efficiency.
The cold-producing medium cooling cycle system comprises compressor 10, throttling arrangement 3, and described evaporimeter 4, first condenser 9 and second condenser 2, and throttling arrangement 3 is connected between the evaporimeter 4 and second condenser 2.This cold-producing medium cooling cycle system operation principle is divided into compression, condensation, throttling, four processes of evaporation.Compression: come the low-pressure low-temperature refrigerant vapour of flash-pot 4 to be compressed and enter first condenser 9 and second condenser 2 after machine 10 is compressed into the gas of high pressure-temperature.Condensation: the refrigerant gas of high pressure-temperature is cooled off by second condenser, the 2 outer new wind degree of depth after indoor return air outside first condenser 9 and the condensed water cooling in the condenser heat exchanger tube again, reduces condensation temperature, the raising heat exchange efficiency.Throttling: the high-temperature high-pressure refrigerant liquid through first condenser 9 and second condenser 2 gets into evaporimeter 4 after throttling arrangement 3 throttlings become low pressure, low temperature liquid.Evaporation: the low-pressure low-temperature refrigerant liquid is evaporated to gas behind new wind picked-up heat in evaporimeter 4 heat exchanger tubes; Make new wind be reduced to 18 ℃ of & relative humidity 90% of dry-bulb temperature simultaneously; Thereby realization kind of refrigeration cycle; Refrigerant vapour in the evaporimeter 4 is compressed machine 10 suctions again and compresses repeated compression, condensation, throttling, evaporation process.
These first condenser, 9 all right oblique placements can make condensed water longer through the time of condenser, and more the good utilisation condensed water cools off first condenser.
Embodiment two sees also Fig. 2, is positioned at the lower floor of full heat recovery fresh air dehumidifying unit of the present invention, is provided with compressor 10 and water-cooled case tube heat exchanger 11, and water-cooled case tube heat exchanger 11 has water inlet 111 and air outlet 112; The upper strata that is positioned at full heat recovery fresh air of the present invention dehumidifying unit has the fresh air dehumidification system, comprises precooling surface cooler 5, evaporimeter 4, is positioned at drip tray 7, second condenser 2 and the pressure fan 1 of precooling surface cooler 5 and evaporimeter 4 belows.With respect to embodiment one; Embodiment two is replaced by water-cooled package condenser 11 with first condenser 9; Shower water structure and exhaust blower 6 have been saved simultaneously; This cold-producing medium cooling cycle system comprises compressor, throttling arrangement and described evaporimeter, water-cooled case tube heat exchanger, second condenser, and the flow process of cold-producing medium is identical, repeats no more at this.Though so the return air of lower floor is not carried out full recuperation of heat, the condensation effect of water-cooled package condenser 11 is good than the condensation effect of first condenser 9, so the whole efficiency of unit can be improved.
The above is merely preferred embodiment of the present invention, and protection scope of the present invention is not limited thereto, and anyly all belongs within the protection domain of the present invention based on the equivalent transformation on the technical scheme of the present invention.
Claims (8)
1. full heat recovery fresh air dehumidifying unit; Comprise fresh air dehumidification system, the full heat recovery system of return air, cold-producing medium cooling cycle system; It is characterized in that; Said full heat recovery fresh air dehumidifying unit adopts double-decker up and down, and this fresh air dehumidification system is positioned at the upper strata, and the full heat recovery system of this return air is positioned at lower floor.
2. full heat recovery fresh air dehumidifying unit as claimed in claim 1; It is characterized in that; This fresh air dehumidification system comprises precooling surface cooler, evaporimeter, second condenser and the pressure fan that sets gradually; The full heat recovery system of this return air comprises first condenser and exhaust blower, and this cold-producing medium cooling cycle system comprises compressor, throttling arrangement and described evaporimeter, first condenser, second condenser that is connected.
3. full heat recovery fresh air dehumidifying unit as claimed in claim 2; It is characterized in that; This fresh air dehumidification system also comprises the drip tray that is arranged under precooling surface cooler and the evaporimeter; The full heat recovery system of this return air also comprises the liquid distribution of the connection drip tray that is arranged on first condenser top, and liquid distribution is connected with drip tray.
4. full heat recovery fresh air dehumidifying unit as claimed in claim 3 is characterized in that said compressor is arranged at the lower floor of said full heat recovery fresh air dehumidifying unit.
5. like each described full heat recovery fresh air dehumidifying unit of claim 2～4, it is characterized in that the oblique placement of this first condenser.
6. full heat recovery fresh air dehumidifying unit as claimed in claim 1; It is characterized in that; This fresh air dehumidification system comprises precooling surface cooler, evaporimeter, second condenser and the pressure fan that sets gradually; The full heat recovery system of this return air comprises the water-cooled case tube heat exchanger, and said water-cooled case tube heat exchanger has water inlet and delivery port, and this cold-producing medium cooling cycle system comprises compressor, throttling arrangement and described evaporimeter, water-cooled case tube heat exchanger, second condenser.
7. like each described full heat recovery fresh air dehumidifying unit of claim 2～4, it is characterized in that, be connected with 16～18 ℃ of cold water in the heat exchanger tube of this precooling surface cooler.
8. like each described full heat recovery fresh air dehumidifying unit of claim 2～4, it is characterized in that, be connected with 5～7 ℃ cold-producing medium in the heat exchanger tube of this evaporimeter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN2010102379635A CN102338428A (en) | 2010-07-26 | 2010-07-26 | Total heat recovery fresh air dehumidifying unit |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102379635A CN102338428A (en) | 2010-07-26 | 2010-07-26 | Total heat recovery fresh air dehumidifying unit |
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| CN102338428A true CN102338428A (en) | 2012-02-01 |
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| CN2010102379635A Pending CN102338428A (en) | 2010-07-26 | 2010-07-26 | Total heat recovery fresh air dehumidifying unit |
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Cited By (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102563763A (en) * | 2010-12-09 | 2012-07-11 | 珠海格力电器股份有限公司 | Dehumidifier |
| CN102721129A (en) * | 2012-06-29 | 2012-10-10 | 湖南工业大学 | Fresh air ventilator capable of recycling waste heat |
| CN102748820A (en) * | 2012-07-03 | 2012-10-24 | 稳力（天津）环保科技有限公司 | Fixed water-cooling fresh air system |
| CN103017262A (en) * | 2012-11-28 | 2013-04-03 | 江苏高科应用科学研究所有限公司 | Heat recovery fresh air dehumidifier |
| CN103363598A (en) * | 2012-03-28 | 2013-10-23 | 杭州迈驰除湿净化设备有限公司 | Intelligent temperature and humidity control integrated machine and control method for same |
| CN103398457A (en) * | 2013-08-21 | 2013-11-20 | 广州同方瑞风空调有限公司 | Refrigeration system, and condensation heat and electrodeless heat recovery device thereof |
| CN103727615A (en) * | 2013-12-06 | 2014-04-16 | 靖江市宝钢空调设备厂 | Evaporative condensation heat pump type total heat recovery fresh air unit |
| CN103822303A (en) * | 2014-02-26 | 2014-05-28 | 广东申菱空调设备有限公司 | Energy-saving variable working condition air-conditioning system with precisely adjustable whole range and control method thereof |
| CN103912935A (en) * | 2014-03-27 | 2014-07-09 | 成信绿集成股份有限公司 | System and method for precise hierarchical control of temperature and humidity |
| CN105202654A (en) * | 2015-09-02 | 2015-12-30 | 广东申菱环境系统股份有限公司 | Integrated air conditioning unit applied to subway station and control method thereof |
| CN105276736A (en) * | 2015-11-25 | 2016-01-27 | 南通华信中央空调有限公司 | Heat pump type total heat recovery new-air air conditioning unit with condensation reheating function |
| CN105805876A (en) * | 2016-04-27 | 2016-07-27 | 四川省建筑科学研究院 | Heat-recovery fresh air ventilator |
| CN106123159A (en) * | 2016-08-26 | 2016-11-16 | 苏州海派特热能设备有限公司 | A kind of degree of depth dehumidifying unit |
| CN107036194A (en) * | 2017-05-27 | 2017-08-11 | 山东美诺邦马节能科技有限公司 | The double low-temperature receiver dehumidifying fresh-air ventilation units of high-temperature water cooling |
| CN107781923A (en) * | 2016-08-29 | 2018-03-09 | 南京腾亚睿尼环境科技有限公司 | A kind of normal temperature fresh air dehumidification device |
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| US11254183B2 (en) | 2017-08-25 | 2022-02-22 | Dometic Sweden Ab | Recreational vehicle, cooling device, controlling system and method for controlling the cooling device |
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Cited By (30)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102563763A (en) * | 2010-12-09 | 2012-07-11 | 珠海格力电器股份有限公司 | Dehumidifier |
| CN103363598A (en) * | 2012-03-28 | 2013-10-23 | 杭州迈驰除湿净化设备有限公司 | Intelligent temperature and humidity control integrated machine and control method for same |
| CN102721129A (en) * | 2012-06-29 | 2012-10-10 | 湖南工业大学 | Fresh air ventilator capable of recycling waste heat |
| CN102748820A (en) * | 2012-07-03 | 2012-10-24 | 稳力（天津）环保科技有限公司 | Fixed water-cooling fresh air system |
| CN103017262B (en) * | 2012-11-28 | 2015-06-10 | 江苏高科应用科学研究所有限公司 | Heat recovery fresh air dehumidifier |
| CN103017262A (en) * | 2012-11-28 | 2013-04-03 | 江苏高科应用科学研究所有限公司 | Heat recovery fresh air dehumidifier |
| CN103398457A (en) * | 2013-08-21 | 2013-11-20 | 广州同方瑞风空调有限公司 | Refrigeration system, and condensation heat and electrodeless heat recovery device thereof |
| CN103727615A (en) * | 2013-12-06 | 2014-04-16 | 靖江市宝钢空调设备厂 | Evaporative condensation heat pump type total heat recovery fresh air unit |
| CN103822303A (en) * | 2014-02-26 | 2014-05-28 | 广东申菱空调设备有限公司 | Energy-saving variable working condition air-conditioning system with precisely adjustable whole range and control method thereof |
| CN103912935A (en) * | 2014-03-27 | 2014-07-09 | 成信绿集成股份有限公司 | System and method for precise hierarchical control of temperature and humidity |
| CN105202654A (en) * | 2015-09-02 | 2015-12-30 | 广东申菱环境系统股份有限公司 | Integrated air conditioning unit applied to subway station and control method thereof |
| CN105202654B (en) * | 2015-09-02 | 2019-02-22 | 广东申菱环境系统股份有限公司 | A kind of integral air conditioner unit and its control method applied to subway station |
| CN105276736A (en) * | 2015-11-25 | 2016-01-27 | 南通华信中央空调有限公司 | Heat pump type total heat recovery new-air air conditioning unit with condensation reheating function |
| CN105276736B (en) * | 2015-11-25 | 2018-05-22 | 南通华信中央空调有限公司 | A kind of heat pump type total heat recovering fresh air air-conditioner set of band condensation reheating |
| CN105805876A (en) * | 2016-04-27 | 2016-07-27 | 四川省建筑科学研究院 | Heat-recovery fresh air ventilator |
| CN106123159A (en) * | 2016-08-26 | 2016-11-16 | 苏州海派特热能设备有限公司 | A kind of degree of depth dehumidifying unit |
| CN107781923A (en) * | 2016-08-29 | 2018-03-09 | 南京腾亚睿尼环境科技有限公司 | A kind of normal temperature fresh air dehumidification device |
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