CN201281431Y - Thermal recovery fresh air unit with distributed cold and thermal sources - Google Patents
Thermal recovery fresh air unit with distributed cold and thermal sources Download PDFInfo
- Publication number
- CN201281431Y CN201281431Y CNU2008201101851U CN200820110185U CN201281431Y CN 201281431 Y CN201281431 Y CN 201281431Y CN U2008201101851 U CNU2008201101851 U CN U2008201101851U CN 200820110185 U CN200820110185 U CN 200820110185U CN 201281431 Y CN201281431 Y CN 201281431Y
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
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Abstract
Disclosed is a heat recovery fresh air unit with distributed cold and heat sources, pertaining to the fresh air unit in the technical field of air conditioners. The unit is composed of a heat pump system and a ventilation system; wherein, the heat pump system is composed of a compressor, a four-way valve, a check valve, an expansion valve, a reservoir, a gas-liquid separator condenser and an evaporator to form an air conditioner refrigeration and heating system; the ventilation system is composed of a filter, a fresh air bypass ventilation valve, a bypass ventilation valve controller, a heat recovery heat exchanger, a water coil, a humidifier, an air blower and an exhaust fan. The unit is characterized in that the condenser and the evaporator of the heat pump system are separately arranged in the ventilation system; the condenser is arranged at the air intake outlet of the heat recovery heat exchanger and the evaporator is arranged at the air exhaust outlet of the heat recovery heat exchanger. When the centralized cold and heat sources are not put into use, the cooling and dehumidification or heating and humidification and indoor air exchange of the fresh air is carried out so as to improve the indoor comfortableness, and the unit has higher energy efficiency ratio and obtains higher heat recovery efficiency simultaneously.
Description
Technical field
The utility model belongs to the new blower fan group in the air-conditioning technical field, particularly with the heat recovery fresh air unit of distributed cold and heat source.
Background technology
New blower fan group provides a kind of apparatus of air conditioning of fresh air.Operation principle be outdoor extraction ozone through dedusting, dehumidifying (or humidification), that cooling (or intensification) waits processing then to deliver to by blower fan is indoor, replaces indoor original air when entering the interior space.
Existing new blower fan group, great majority comprise fillter section, surface cooling section, bringing-up section, fan section, send into indoor after outdoor new wind is handled through humiture.Wherein cool-down dehumidification and heating function are that centralized Cooling and Heat Source by air-conditioning system provides.Excessively season, under the situation that centralized Cooling and Heat Source does not come into operation, new blower fan group can't be carried out humiture to air-supply and be regulated.
Along with the appearance to the understanding and the standard of building energy conservation, high-grade at present new blower fan group has increased heat recovery function, and main pattern is board-like, plate-fin, rotary heat exchanger.Because this heat reclamation device is to drive by the temperature difference or enthalpy difference, general organic efficiency is less than 70%.In addition, new wind can't be handled claimed condition by the recovery effect merely, also need the centralized Cooling and Heat Source of air-conditioning system to carry out subsequent treatment, therefore, the new blower fan group of band heat recovery function also can't work independently.Excessive season, when centralized Cooling and Heat Source does not come into operation, can't satisfy the comfortableness requirement in transition season by the fixing new blower fan group of resh air requirement (generally only satisfying personnel's basic demand) merely.
Summary of the invention
In order to solve above-mentioned problems of the prior art, the purpose of this utility model provides a kind of heat recovery fresh air unit with distributed cold and heat source.It can carry out cool-down dehumidification or warming and humidifying processing, replace room air new wind under the situation that centralized Cooling and Heat Source does not come into operation, and improves indoor comfort level, and when realizing the higher thermal organic efficiency, has higher Energy Efficiency Ratio.
In order to reach the foregoing invention purpose, the technical solution of the utility model realizes as follows:
The heat recovery fresh air unit of band distributed cold and heat source, it is made up of heat pump and ventilating system.Heat pump is formed the air conditioner refrigerating heating by compressor, cross valve, check valve, expansion valve, reservoir, gas-liquid separator condenser and evaporimeter.Ventilating system is made up of filter, new wind bypass air-valve, bypass wind valve controller, heat recovering heat exchanger, water coil, humidifier, pressure fan and exhaust blower.Its design feature is that condenser in the described heat pump and evaporimeter partition place ventilating system.Condenser places the air intake outlet of heat recovering heat exchanger, and evaporimeter places the wind exhausting outlet of heat recovering heat exchanger.
The utility model transfers the time period can carry out new wind running separately owing to adopted said structure at non-NULL, improves indoor air quality.Cold (heat) amount of carrying in the air-conditioning time period can be with indoor exhaust wind reclaims, and passes to new wind.The utlity model has following beneficial effect:
1, the utility model can greatly improve the performance of system because the operating mode of evaporimeter and condenser is different with the operating mode of normal air source heat pump.Under the environment-8 degree situation, the heating performance coefficient can reach 8.2 to the utility model unit in the winter time; Under summer environment temperature 33.2 degree situations, coefficient of performance of refrigerating can reach 5.1.And the heating performance coefficient of traditional air source heat pump when environment temperature-8 is spent be less than 2.5, and coefficient of performance of refrigerating was less than 3.0 when spent summer 33.2.
2, the utility model reclaims by two levels of thermal, can fully finish energy exchange and recovery between the new air draft.
3, the utlity model has the function of efficient distributed energy.Especially in transition season, before centralized Cooling and Heat Source does not put into operation, can provide certain cold and hot amount to indoor by the utility model unit, satisfy the demand in building transition season, improve the comfort level of architectural environment.
4, the utility model unit makes full use of the stability of indoor exhaust wind, guarantees that unit keeps the higher coefficient of performance in whole season, and is higher than the Energy Efficiency Ratio of centralized cold and heat source system
Below in conjunction with the drawings and specific embodiments the utility model is described further.
Description of drawings
Accompanying drawing is a structure principle chart of the present utility model.
The specific embodiment
Referring to accompanying drawing, the new blower fan group of the utility model is made up of heat pump and ventilating system.Heat pump is formed the air conditioner refrigerating heating by compressor 1, cross valve 2, check valve 4, expansion valve 5, reservoir 6, gas-liquid separator 9 condensers 3 and evaporimeter 8.Ventilating system is made up of filter 11, new wind bypass air-valve 12, bypass wind valve controller 10, heat recovering heat exchanger 13, water coil 14, humidifier 15, pressure fan 16 and exhaust blower 17.Condenser 3 in the heat pump and evaporimeter 8 partitions place ventilating system.Condenser 3 places the air intake outlet of heat recovering heat exchanger 13, and evaporimeter 8 places the wind exhausting outlet of heat recovering heat exchanger 13.
During the utility model work, following several mode of operation is arranged:
The air vent mode of pattern one, refrigeration transition season (when outdoor temperature is lower than indoor temperature):
New wind by-passing valve 12 is opened the new wind side closure of heat recovering heat exchanger 13.Behind new wind process filter 11, new wind by-passing valve 12, condenser 3 and the water coil 14, introduce indoor by pressure fan 16.Air draft is discharged outdoor through filter 11, exhaust blower 17, heat recovering heat exchanger 13 and evaporimeter 8 backs successively.At this moment, source pump is not worked, and heat recovering heat exchanger 13 is not worked (there is not heat exchange in single stream), and centralized Cooling and Heat Source does not come into operation.Therefore, new wind is had only filtration treatment, do not have the processing of temperature and humidity.
Pattern two, heat transition season the air vent mode of (when outdoor temperature is lower than indoor temperature but do not need heat supply):
New wind by-passing valve 12 cuts out, and heat recovering heat exchanger 13 comes into operation.The absorption air draft heat of new wind process filter 11, heat recovering heat exchanger 13 is after behind the humidification of condenser 3, water coil 14,15 pairs of new wind of humidifier, introduce indoor by pressure fan 16.The cooling of air draft process filter 11, exhaust blower 17, heat recovering heat exchanger 13 is after evaporimeter 8 backs are discharged outdoor.At this moment, source pump is not worked, and heat recovering heat exchanger 13 comes into operation, and centralized Cooling and Heat Source does not come into operation.New wind has only passed through filtration and heat exchange just is admitted to indoor under this pattern.
Pattern three, distributed refrigeration pattern (centralized low-temperature receiver does not come into operation, but the indoor cooling that needs):
When outdoor environment temperature was lower than indoor temperature, new wind by-passing valve 12 was opened heat recovering heat exchanger 13 bypass.Enter condenser 3 (refrigeration mode is an evaporimeter) cool-down dehumidification behind new wind process filter 11, the new wind by-passing valve 12, behind water coil 14, humidifier 15 (not working), introduce indoor then by pressure fan 16.Discharge outdoor after air draft process filter 11, exhaust blower 17, heat recovering heat exchanger 13, evaporimeter 8 (refrigeration mode is a condenser) the absorption condensation heat.Under this pattern, new wind has passed through the cool-down dehumidification processing and has delivered to indoor.At this moment, heat recovering heat exchanger 13 bypass are avoided heat exchange between new, the air draft.
When outdoor environment temperature was higher than indoor temperature, new wind by-passing valve 12 cut out, and heat recovering heat exchanger 13 comes into operation.New wind enters condenser 3 (refrigeration mode is an evaporimeter) cool-down dehumidification through filter 11, heat recovering heat exchanger 13 after absorbing the interior cold of air draft, behind water coil 14, humidifier 15 (not working), introduces indoor by pressure fan 16 then.Air draft through filter 11, exhaust blower 17, heat recovering heat exchanger 13 slightly heats up, after evaporimeter 8 (refrigeration mode is a condenser) the absorption condensation heat discharge outdoor.Under this pattern, the recuperation of heat of new wind process has slightly been carried out significantly cool-down dehumidification processing through distributed low-temperature receiver after the cooling, delivers to indoor.
Pattern four, distributed heating mode (indoor temperature needs heat supply, but centralized low-temperature receiver does not come into operation):
New wind by-passing valve 12 cuts out, and heat recovering heat exchanger 13 comes into operation.New wind absorbs through filter 11, heat recovering heat exchanger 13 that air draft part heats are laggard goes into condenser 3 and heats up once more, and is behind water coil 14,15 pairs of new wind humidifications of humidifier, indoor by pressure fan 16 introducings then.Air draft enter after through 13 coolings of filter 11, exhaust blower 17, heat recovering heat exchanger evaporimeter 8 once more heat is passed to discharge after the source pump outdoor.Under this pattern, new wind has passed through recuperation of heat and intensification and has added wet process and deliver to indoorly, solves the indoor heating problem.
Pattern five: the refrigeration mode of distributed cold and heat source and centralized low-temperature receiver cooperation (centralized low-temperature receiver comes into operation, outdoor environment temperature height indoor temperature):
New wind by-passing valve 12 cuts out, and heat recovering heat exchanger 13 comes into operation.New wind enters condenser 3 (refrigeration mode is an evaporimeter) cool-down dehumidification through filter 11, heat recovering heat exchanger 13 after absorbing the interior cold of air draft, then through behind the water coil 14 further cool-down dehumidifications through humidifier 15 (not working) after, introduce indoor by pressure fan 16.Air draft through filter 11, exhaust blower 17, heat recovering heat exchanger 13 slightly heats up, after evaporimeter 8 (refrigeration mode is a condenser) the absorption condensation heat discharge outdoor.Under this pattern, the recuperation of heat of new wind process is slightly carried out significantly cool-down dehumidification processing through distributed low-temperature receiver and chilled water coil 14 after the cooling, delivers to indoor.
Pattern six: the heating mode of distributed cold and heat source and centralized thermal source cooperation (centralized thermal source comes into operation, and outdoor environment temperature is lower than indoor temperature):
New wind by-passing valve 12 cuts out, and heat recovering heat exchanger 13 comes into operation.New wind absorbs through filter 11, heat recovering heat exchanger 13 that air draft part heats are laggard goes into condenser 3 and heat up, then through water coil 14 heats up once more, behind 15 pairs of new wind humidifications of humidifier, indoor by pressure fan 16 introducings.Air draft is through filter 11, exhaust blower 17, enter after heat recovering heat exchanger 13 coolings evaporimeter 8 once more heat is passed to discharge after the source pump outdoor.Under this pattern, new wind has passed through recuperation of heat and intensification adds wet process, delivers to indoorly, solves the indoor heating problem.
Claims (1)
1, the heat recovery fresh air unit of band distributed cold and heat source, it is made up of heat pump and ventilating system, and heat pump is formed the air conditioner refrigerating heating by compressor (1), cross valve (2), check valve (4), expansion valve (5), reservoir (6), gas-liquid separator (9) condenser (3) and evaporimeter (8); Ventilating system is made up of filter (11), new wind bypass air-valve (12), bypass wind valve controller (10), heat recovering heat exchanger (13), water coil (14), humidifier (15), pressure fan (16) and exhaust blower (17), it is characterized in that, condenser in the described heat pump (3) and evaporimeter (8) partition place ventilating system, condenser (3) places the air intake outlet of heat recovering heat exchanger (13), and evaporimeter (8) places the wind exhausting outlet of heat recovering heat exchanger (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201101851U CN201281431Y (en) | 2008-09-11 | 2008-09-11 | Thermal recovery fresh air unit with distributed cold and thermal sources |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201101851U CN201281431Y (en) | 2008-09-11 | 2008-09-11 | Thermal recovery fresh air unit with distributed cold and thermal sources |
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| CN201281431Y true CN201281431Y (en) | 2009-07-29 |
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| CNU2008201101851U Expired - Lifetime CN201281431Y (en) | 2008-09-11 | 2008-09-11 | Thermal recovery fresh air unit with distributed cold and thermal sources |
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| CN (1) | CN201281431Y (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101858625A (en) * | 2010-04-27 | 2010-10-13 | 江苏国莱特空调设备有限公司 | Compound low-carbon type brand-new air/water source heat pump |
| CN102425822A (en) * | 2011-09-02 | 2012-04-25 | 张洪 | Fresh air conditioner |
| CN102705920A (en) * | 2012-05-24 | 2012-10-03 | 吕智 | Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof |
| CN103267328A (en) * | 2013-05-31 | 2013-08-28 | 南京埃科净化技术有限公司 | Intelligent air quality guaranteeing system and controlling method thereof |
| CN103398427A (en) * | 2013-08-19 | 2013-11-20 | 苏州惠林节能材料有限公司 | Self-temperature-recovery dehumidification cooling fresh air unit |
| CN104976704A (en) * | 2014-04-08 | 2015-10-14 | 上海诺佛尔建筑科技发展有限公司 | Working method of secondary heat recovery fresh air processing device |
| CN105371412A (en) * | 2014-11-28 | 2016-03-02 | 吴忠禄 | Heat exchanging ventilator capable of mixing indoor air into outdoor air |
| JP2020159595A (en) * | 2019-03-26 | 2020-10-01 | パナソニックＩｐマネジメント株式会社 | Heat exchange type ventilation device with humidity control function |
| CN112954955A (en) * | 2021-01-25 | 2021-06-11 | 华为技术有限公司 | Cooling system and data center |
-
2008
- 2008-09-11 CN CNU2008201101851U patent/CN201281431Y/en not_active Expired - Lifetime
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101858625B (en) * | 2010-04-27 | 2012-07-25 | 江苏国莱特空调设备有限公司 | Compound low-carbon type brand-new air/water source heat pump |
| CN101858625A (en) * | 2010-04-27 | 2010-10-13 | 江苏国莱特空调设备有限公司 | Compound low-carbon type brand-new air/water source heat pump |
| CN102425822B (en) * | 2011-09-02 | 2013-12-18 | 张洪 | Fresh air conditioner |
| CN102425822A (en) * | 2011-09-02 | 2012-04-25 | 张洪 | Fresh air conditioner |
| CN102705920A (en) * | 2012-05-24 | 2012-10-03 | 吕智 | Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof |
| CN102705920B (en) * | 2012-05-24 | 2015-02-04 | 吕智 | Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof |
| CN103267328B (en) * | 2013-05-31 | 2015-09-02 | 美埃（中国）环境净化有限公司 | A kind of intelligent air quality safeguards system and control method thereof |
| CN103267328A (en) * | 2013-05-31 | 2013-08-28 | 南京埃科净化技术有限公司 | Intelligent air quality guaranteeing system and controlling method thereof |
| CN103398427A (en) * | 2013-08-19 | 2013-11-20 | 苏州惠林节能材料有限公司 | Self-temperature-recovery dehumidification cooling fresh air unit |
| CN104976704A (en) * | 2014-04-08 | 2015-10-14 | 上海诺佛尔建筑科技发展有限公司 | Working method of secondary heat recovery fresh air processing device |
| CN104976704B (en) * | 2014-04-08 | 2017-07-18 | 上海诺佛尔生态科技股份有限公司 | The method of work of secondary recuperation of heat Fresh air handing device |
| CN105371412A (en) * | 2014-11-28 | 2016-03-02 | 吴忠禄 | Heat exchanging ventilator capable of mixing indoor air into outdoor air |
| CN105371412B (en) * | 2014-11-28 | 2018-03-13 | 吴忠禄 | The heat exchange ventilating device of indoor and outdoor air can be mixed |
| JP2020159595A (en) * | 2019-03-26 | 2020-10-01 | パナソニックＩｐマネジメント株式会社 | Heat exchange type ventilation device with humidity control function |
| JP7429835B2 (en) | 2019-03-26 | 2024-02-09 | パナソニックＩｐマネジメント株式会社 | Heat exchange type ventilation device with humidity control function |
| CN112954955A (en) * | 2021-01-25 | 2021-06-11 | 华为技术有限公司 | Cooling system and data center |
| EP4033869A1 (en) * | 2021-01-25 | 2022-07-27 | Huawei Digital Power Technologies Co., Ltd. | Cooling system and data center |
| CN112954955B (en) * | 2021-01-25 | 2024-07-05 | 华为数字能源技术有限公司 | Cooling system and data center |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: JIANGSU JIXIANG AIR-CONDITIONING EQUIPMENT CO., LT Free format text: FORMER OWNER: TONGFANG ARTIFICIAL ENVIRONMENT CO., LTD. Effective date: 20140403 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| COR | Change of bibliographic data |
Free format text: CORRECT: ADDRESS; FROM: 100083 CHAOYANG, BEIJING TO: 214500 TAIZHOU, JIANGSU PROVINCE |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20140403 Address after: 214500 No. 111 middle Gushan Road, Jiangsu, Jingjiang Patentee after: JIANGSU JIXIANG AIR CONDITIONING EQUIPMENT CO., LTD. Address before: 100083 A, block 2901, Tongfang science and Technology Square, Beijing Patentee before: Tongfang Artificial Environment Co., Ltd. |
|
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20090729 |