CN101310153B - Air flow management system comprising two fan with different diameter in heating ventilator unit and air conditioner unit - Google Patents
Air flow management system comprising two fan with different diameter in heating ventilator unit and air conditioner unit Download PDFInfo
- Publication number
- CN101310153B CN101310153B CN2005800520679A CN200580052067A CN101310153B CN 101310153 B CN101310153 B CN 101310153B CN 2005800520679 A CN2005800520679 A CN 2005800520679A CN 200580052067 A CN200580052067 A CN 200580052067A CN 101310153 B CN101310153 B CN 101310153B
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- China
- Prior art keywords
- fan
- air
- heat exchanger
- air flows
- flows
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
Abstract
Air is heated by a gas or electric heat exchanger or cooled in an evaporator coil. The air is discharged through a discharge opening to heat or cool an area. Two fans draw an exterior air stream over the gas or electric heat exchanger or the evaporator coil. A first fan has a diameter greater than a diameter of a second fan. When in a side discharge configuration, the second fan is located between the first fan and the side discharge opening. The first fan has a larger diameter to produce a stronger airflow to overcome the airflow produced by the second fan, better distributing the airflow from the first fan. The airflow generated by the second fan is directed to the discharge opening relatively unimpeded.
Description
Technical field
Relate generally to of the present invention comprises two air flow management systems of fan that air aspirated pervaporation device coil pipe and air was blowed the different-diameter of gas or electric heat exchanger.
Background technology
The large commercial air flow management system usually uses two less fans of equal diameter that air is aspirated pervaporation device coil pipe and air was blowed gas or electric heat exchanger in the zone.Two less fans provide the advantage that is better than single bigger fan.An advantage is, air is flowing on the evaporator plate tube section of broad and distributes more equably.Air flows and also distributes on gas or electric heat exchanger more equably, and this depends on that the air that distributes well flows to prevent overheated and to optimize efficient.In addition, the diameter of two fans is less than the diameter of single fan, thereby reduced the height that keeps the cabinet of fan.
Even the problem relevant with using two fans of equal diameter is two fans and also always do not carry the air of equivalent to flow when moving with identical speed.This problem is in vogue the air flow management system that can be converted into side discharge configuration from down discharge configuration especially.In down discharge configuration, directly flow to the exhaust openings of below by the air of first fan and the suction of second fan.Mobile from the air of two fans is to equate approx.In side discharge configuration, flow relatively not interrupted by air near second fan of side discharge opening.Yet, have bigger travel distance and blast area that must be by second fan to leave the side discharge opening by flowing away from the air of first fan of side discharge opening.Second fan has applied back pressure on the air that is generated by first fan flows, thereby has reduced the flow of the air that leaves first fan.Therefore second fan has been carried major part that air flows and first fan poor efficiency relatively.Fan also can with produce to impact and usually the mode of irregular operation interact, thereby make volume air flow and the static pressure setpoint that is difficult to be maintained fixed.
In the air flow management system of prior art, it is unsettled that air is flowing in the big fan speed scope.Fan power consumption increases, because second fan has been done main merit.The major part of evaporator coil has received very little air and has flowed, so gas or electric heat exchanger have the thermal efficiency of high surface temperature and difference.The safety margins switch that activates with temperature also moves erratically owing to unsettled air themperature.
Therefore, exist in the art for comprising different air being aspirated pervaporation device coil pipe and air was blowed the needs of air flow management system of the fan of gas or electric heat exchanger of two diameters, this has overcome the shortcoming and the weakness of prior art.
Summary of the invention
Air flow management system comprises vapor compression system.In refrigerating mode, cold-producing medium is compressed and enters then condenser coil and to the external fluid medium heat extraction in compressor.Cold-producing medium expands by bloating plant then.After expansion, cold-producing medium flows through evaporator coil and receives heat from the extraneous air stream that discharges by exhaust openings with cooled region.Thereby cold-producing medium and then enter compressor and finished circulation.In heating mode, evaporimeter does not cool off extraneous air stream, and mobile gas or the electric heat exchanger that is heated part of air heats with heating region.
First fan and second fan blowed gas or electric heat exchanger with extraneous air stream suction pervaporation device coil pipe and with extraneous air stream.First fan has first diameter, and first diameter is greater than second diameter of second fan.Exhaust openings can be exchanged into side discharge configuration from down discharge configuration.When being in side discharge configuration, second fan is between first fan and side discharge opening.In an example, fan is arranged coaxially.Air by the suction of second fan is not relatively guided the side discharge opening into not interruptedly.From the mobile blast area that must pass through second fan of the air of first fan.First fan has bigger diameter and flows and overcome the air that is produced by second fan and flow to produce stronger air, thereby distributes the air from first fan to flow better.
The speed of fan also can be regulated to optimize air and be flowed.Therefore first fan has higher speed and has produced the air bigger than second fan mobile.In addition, fan speed and fan diameter the two can regulate to optimize air and flow.
These and other features of the present invention will be understood from following specification and accompanying drawing best.
Description of drawings
Various features of the present invention and advantage will be from following to becoming obvious for persons skilled in the art the current detailed description of preferred embodiment.Follow the accompanying drawing of detailed description to be described below simply:
Fig. 1 schematically illustrates the air flow management system that comprises vapor compression system and heating system;
Fig. 2 A schematically illustrates the front view of the air flow management system with down discharge configuration;
Fig. 2 B schematically illustrates the side view of the air flow management system with down discharge configuration;
Fig. 3 A schematically illustrates the front view of the air flow management system with side discharge configuration; With
Fig. 3 B schematically illustrates the side view of the air flow management system with side discharge configuration.
The specific embodiment
Fig. 1 illustrates air flow management system 10.Control device 56 has determined that air flow management system 10 is with refrigerating mode or heating mode operation.This determines and can carry out by temperature-adjusting device or by the instruction that is provided by the operator.
Air flow management system 10 comprises vapor compression system 20, has compressor 22, condenser coil 24, bloating plant 26 and evaporator coil 28.Cold-producing medium is by vapor compression system 20 circulations of loop.During refrigerating mode, cold-producing medium leaves compressor 22 by floss hole 30 with high pressure and Gao Han.
Cold-producing medium flows through condenser coil 24 then.For example the external fluid medium 32 of water or air flow through condenser coil 24 and with the cold-producing medium heat exchange of flowing through condenser coil 24.Cold-producing medium leaves condenser coil 24 to external fluid medium 32 heat extractions and with relatively low enthalpy and high pressure.
Thereby cold-producing medium expands by bloating plant 26 then and reduces the pressure of cold-producing medium.Bloating plant 26 can be the known expansion device of mechanical swelling equipment (TXV), electric expansion valve (EXV) or other types.
After expansion, cold-producing medium flows through evaporator coil 28 and absorbs heat from extraneous air stream 34.Cold-producing medium leaves evaporator coil 28 with relatively high enthalpy and low pressure.Thereby cold-producing medium enters the pump orifice 38 of compressor 22 then and finishes circulation.
When air flow management system 10 moved with refrigerating mode, control device 56 sent signal and flows 34 by vapor compression system 20 with the extraneous air in the cool 28 to activate compressor 22 and pump refrigerant.Control device 56 sends signal to remove the gas in heating part 52 or the activation of electric heat exchanger 40.Gas or electric heat exchanger 40 comprise several heat exchanger coils of U-shaped (shown in Fig. 2 B and Fig. 3 B) substantially.Fan 36 and 37 (shown in Fig. 2 A, Fig. 2 B, Fig. 3 A and Fig. 3 B) is with extraneous air stream 34 suction pervaporation device coil pipes 28 and by air movable part 50, and extraneous air stream 34 blowed by heating part 52 (un-activation) and by down discharge opening 42 or side discharge opening 43 enters into zone to be cooled to cool off this zone.
Rotate back into Fig. 1, when air flow management system 10 moved with heating mode, control device 56 sent signal to remove the activation to compressor 22, passes through flowing of vapor compression system 20 and evaporator coil 28 thereby stop cold-producing medium.Control device 56 sends signal to activate gas or electric heat exchanger 40.During heating mode, gas or electric heat exchanger 40 that extraneous air stream 34 is heated in the part 52 heat with heating extraneous air stream 34 and heating region.Compressor 22 does not move during heating mode, and therefore cold-producing medium does not flow through vapor compression system 20, and does not flow 34 heat exchange with extraneous air.Extraneous air stream 34 was blowed gas with fan 36 and 37 or electric heat exchanger 40 flows 34 with the heating extraneous air.Heated extraneous air stream 34 by down discharge opening 42 or side discharge opening 43 leaves heating part 52 with heating region.
Cold-producing medium flowing in vapor compression system 20 can be reversed by using heat pump 54.When mobile being reversed of cold-producing medium, entering evaporator coil 28 (as condenser) from the cold-producing medium of compressor 22 and come heating region with heating extraneous air stream 34.
As shown in Fig. 2 A, Fig. 2 B, Fig. 3 A and Fig. 3 B, fan 36 and 37 with extraneous air stream 34 suction pervaporation device coil pipes 28, and blowed gas or electric heat exchanger 40 with extraneous air stream 34 in air movable part 50. Fan 36 and 37 moves concurrently.In an example, first fan 36 and second fan 37 are arranged coaxially around common axle 44.Yet each of passable is fan 36 and fan 37 is installed on the parallel substantially different axle.Extraneous air stream 34 is convertible between down discharge configuration and side discharge configuration.
Fig. 2 A and Fig. 2 B show the extraneous air stream 34 that flows through the down discharge opening 42 in the heating part 52 when air flow management system 10 moves with down discharge configuration.Extraneous air stream 34 is aspirated pervaporation device coil pipes 28 and was blowed gas or electric heat exchanger 40 by fan 36 and 37.Extraneous air stream 34 is directed to down discharge opening 42 along straight substantially path, with heating region in heating mode or in refrigerating mode cooled region.Flow from each air of fan 36 and 37 and not interfere mutually.In down discharge configuration, side discharge opening 43 is covered to prevent that extraneous air stream 34 from flowing through side discharge opening 43 by panel 60.Panel 60 can be connected to heating part 52 by any way.
Fig. 3 A and Fig. 3 B show the extraneous air stream 34 that flows through the side discharge opening 43 in the heating part 52 when air flow management system 10 moves with side discharge configuration.Extraneous air stream 34 is aspirated pervaporation device coil pipes 28 and blowed gas or electric heat exchanger 40 by fan 36 and 37.Extraneous air stream 34 is conducted through heating part 52 and passes through side discharge opening 43.In the view of Fig. 3 A, blowed on the direction of extraneous air stream 34 in pointing to paper.Yet, be understood that the air that is blowed by fan 36 and 37 can be with any horizontal direction towards 43 suctions of side discharge opening.In side discharge configuration, down discharge opening 42 is covered to prevent that extraneous air stream 34 from flowing through down discharge opening 42 by panel 62.Panel 62 can be connected to heating part 52 by any way.
This hinders in order to be in harmonious proportion, and is relatively stronger near second fan 37 of side discharge opening 43 away from first fan 36 of side discharge opening 43.Diameter A by making the fan 36 of winning and width C are greater than the diameter B and the width D of second fan 37, first fan 36 can produce stronger air and flow and to flow with the air that overcomes by second fan 37, thereby better will be from the air flow distribution of first fan 36 to side discharge opening 43.Because stronger air flows, flowing from the air of second fan 37 does not apply back pressure on the air from first fan 36 flows, and when air flows through the blast area of second fan 37 air mass flow of not restricted passage first fan 36.First fan 36 is stronger will trend towards because it is positioned at having on the position that not enough air flows, and second fan 37 a little less than will trend towards having the position that too much air flows because it is positioned at.The operation of air flow management system 10 can be stabilized, and can have the airflow balance of more wishing between two fans 36 and 37.
Air is flowing in the position of separately depending on fan 36 and 37, size and the speed between two fans 36 and 37.The geometry that separately also depends on air intake that air flows, the size and the position of the design of heating chamber and down discharge opening 42 and side discharge opening 43.
Aforementioned description only is the example of principle of the present invention.Can carry out many according to above teaching to modifications and variations of the present invention.The preferred embodiments of the present invention disclose, yet persons skilled in the art will be recognized within the scope of the invention can have some modification.Therefore, be understood that in the scope of subsidiary claim, the present invention can with the differently practice of describing especially.Owing to this reason, should study following claim carefully to determine real scope of the present invention and content.
Claims (20)
1. heat exchanger comprises:
Heat exchanger coils;
First fan that first air of the medium heat exchange in generation and the heat exchanger coils flows; With
Second fan that second air of the medium heat exchange in generation and the heat exchanger coils flows, wherein the mobile ratio of first air second air is mobile stronger, and first air flows and the common excessively floss hole of second air flow stream.
2. heat exchanger according to claim 1, wherein first fan has first diameter and second fan has second diameter, and first diameter is greater than second diameter.
3. heat exchanger according to claim 1, wherein first fan moves with first fan speed, and second fan moves with second fan speed, and first fan speed is greater than second fan speed.
4. heat exchanger according to claim 1, wherein first air flows and second air flows through common floss hole and leaves, and first air flows and second air flows is directed to common floss hole along straight substantially path respectively from first fan and second fan.
5. heat exchanger according to claim 1, wherein first air flows and second air flows through common floss hole and leaves, and when common floss hole was the side discharge opening, second fan was than more close this side discharge opening of first fan.
6. heat exchanger according to claim 1, wherein first fan and the second fan parallel running.
7. heat exchanger according to claim 1, wherein heat exchanger coils is an evaporator coil, and first fan and second fan flow first air and second air flows aspirates pervaporation device coil pipe respectively.
8. heat exchanger according to claim 1, wherein heat exchanger is gas or electric heat exchanger, and first fan and second fan flow first air and second air flows blowed gas or electric heat exchanger respectively.
9. air flow management system comprises:
Comprise the vapor compression system of evaporator coil, wherein cold-producing medium flows through evaporator coil;
Produce the heating heat exchanger of heated medium; With
The air movable part comprises:
Produce first fan that first air flows, when air flow management system moves with refrigerating mode, first air flows and the interior cold-producing medium heat exchange of evaporator coil, and when air flow management system moves with heating mode, first air flow with heating heat exchanger in heated medium heat exchange and
Produce second fan that second air flows, when air flow management system moves with refrigerating mode, second air flows and the interior cold-producing medium heat exchange of evaporator coil, and when air flow management system moves with heating mode, second air flows and the interior heated medium heat exchange of heating heat exchanger, wherein first air flows and flows by force than second air, and first air flows and the common excessively floss hole of second air flow stream.
10. system according to claim 9, wherein vapor compression system comprises two
Cold-producing medium is compressed to the compressor of high pressure;
The condenser that is used for heat exchange between cold-producing medium and fluid; With
Make cold-producing medium expand into the bloating plant of low pressure.
11. system according to claim 9, wherein first fan has first diameter and second fan has second diameter, and first diameter is greater than second diameter.
12. system according to claim 9, wherein first fan moves with first fan speed, and second fan moves with second fan speed, and first fan speed is greater than second fan speed.
13. system according to claim 9, wherein first air flows and second air flows through common floss hole and leaves air flow management system, and first air flows and second air flows is directed to common floss hole from first fan and second fan respectively along straight substantially path.
14. system according to claim 9, wherein first air flows and second air flows through common floss hole and leaves air flow management system, and when common floss hole was the side discharge opening, second fan was than more close this side discharge opening of first fan.
15. system according to claim 9, wherein first fan and the second fan parallel running.
16. system according to claim 9, wherein first fan and second fan flow first air respectively and the mobile suction of second air pervaporation device coil pipe.
17. system according to claim 9, wherein first fan and second fan flow first air respectively and the mobile heating heat exchanger that blowed of second air.
18. one kind is used to manage the method that air flows, comprises the steps:
An operation air flow management system with refrigerating mode and heating mode;
Generating first air flows, when air flow management system moved with refrigerating mode, first air flowed and the interior cold-producing medium heat exchange of evaporator coil, and when air flow management system moves with heating mode, first air flow with heating heat exchanger in heated medium heat exchange and
Generating second air flows, when air flow management system moves with refrigerating mode, second air flows and the interior cold-producing medium heat exchange of evaporator coil, and when air flow management system moves with heating mode, second air flows and the interior heated medium heat exchange of heating heat exchanger, and wherein the mobile ratio of first air second air flows strong.
19. method according to claim 18, wherein first air flows and is generated by first fan with first diameter, and second air is mobile by second fan generation with second diameter, and wherein first diameter is greater than second diameter.
20. method according to claim 18, wherein first air flows and to have first speed and second air and flow and have second speed, and first speed is greater than second speed.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2005/041279 WO2007061403A1 (en) | 2005-11-16 | 2005-11-16 | Airflow management system in a hvac unit including two fans of different diameters |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101310153A CN101310153A (en) | 2008-11-19 |
| CN101310153B true CN101310153B (en) | 2010-12-15 |
Family
ID=38067506
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2005800520679A Expired - Fee Related CN101310153B (en) | 2005-11-16 | 2005-11-16 | Air flow management system comprising two fan with different diameter in heating ventilator unit and air conditioner unit |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20090133856A1 (en) |
| CN (1) | CN101310153B (en) |
| CA (1) | CA2626064C (en) |
| HK (1) | HK1126269A1 (en) |
| WO (1) | WO2007061403A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114777219B (en) * | 2022-05-12 | 2023-10-27 | 江苏晋成空调工程有限公司 | Air treatment unit with adjustable cooling coil |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1157903A (en) * | 1996-04-12 | 1997-08-27 | 王曰信 | Warm meal refrigerater |
| US5857905A (en) * | 1996-10-22 | 1999-01-12 | Denso Corporation | Air conditioning apparatus for vehicle |
| CN1260868A (en) * | 1997-06-05 | 2000-07-19 | 尹明赫 | Air-flow switching type air conditioner for both cooling and heating |
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| US2280512A (en) * | 1940-05-02 | 1942-04-21 | B F Sturtevant Co | Refrigeration apparatus |
| US3410105A (en) * | 1967-02-15 | 1968-11-12 | Philco Ford Corp | Air conditioner |
| JPS61173031A (en) * | 1985-01-24 | 1986-08-04 | Nishida Tekko Kk | Floor-on fan type air conditioner |
| US4779672A (en) * | 1985-11-19 | 1988-10-25 | Toyota Jidosha Kabushiki Kaisha | Air conditioner for vehicle having blower with auxiliary intake port |
| JPS63263332A (en) * | 1987-04-20 | 1988-10-31 | Sanyo Electric Co Ltd | Heat exchanging unit |
| JPH01181032A (en) * | 1988-01-13 | 1989-07-19 | Toshiba Corp | Air conditioner |
| US5245836A (en) * | 1989-01-09 | 1993-09-21 | Sinvent As | Method and device for high side pressure regulation in transcritical vapor compression cycle |
| US5271238A (en) * | 1990-09-14 | 1993-12-21 | Nartron Corporation | Environmental control system |
| JPH04190023A (en) * | 1990-11-22 | 1992-07-08 | Fujitsu General Ltd | Air conditioner |
| US5309731A (en) * | 1991-12-27 | 1994-05-10 | Nippondenso Co., Ltd. | Air conditioning apparatus |
| US5488835A (en) * | 1993-07-28 | 1996-02-06 | Howenstine; Mervin W. | Methods and devices for energy conservation in refrigerated chambers |
| JP3476899B2 (en) * | 1994-04-12 | 2003-12-10 | 東芝キヤリア株式会社 | Air conditioner |
| US5490394A (en) * | 1994-09-23 | 1996-02-13 | Multibras S/A Eletrodomesticos | Fan control system for the evaporator of refrigerating appliances |
| JP3404150B2 (en) * | 1994-09-28 | 2003-05-06 | 東芝キヤリア株式会社 | Air conditioner and control method thereof |
| US5694783A (en) * | 1994-10-26 | 1997-12-09 | Bartlett; Matthew T. | Vapor compression refrigeration system |
| JPH08189658A (en) * | 1995-01-09 | 1996-07-23 | Daikin Ind Ltd | Air-conditioner |
| JPH0968316A (en) * | 1995-08-30 | 1997-03-11 | Toshiba Corp | Thermally cooking apparatus |
| US5657638A (en) * | 1995-10-02 | 1997-08-19 | General Electric Company | Two speed control circuit for a refrigerator fan |
| US5782101A (en) * | 1997-02-27 | 1998-07-21 | Carrier Corporation | Heat pump operating in the heating mode refrigerant pressure control |
| DE19713197B4 (en) * | 1997-03-28 | 2008-04-24 | Behr Gmbh & Co. Kg | Method for operating an air conditioning system in a motor vehicle and air conditioning with a refrigerant circuit |
| US6560980B2 (en) * | 2000-04-10 | 2003-05-13 | Thermo King Corporation | Method and apparatus for controlling evaporator and condenser fans in a refrigeration system |
| US6415617B1 (en) * | 2001-01-10 | 2002-07-09 | Johnson Controls Technology Company | Model based economizer control of an air handling unit |
| US6397610B1 (en) * | 2001-05-01 | 2002-06-04 | Cohand Technology Co., Ltd. | Method for controlling air conditioner/heater by coil temperature |
| US6694763B2 (en) * | 2002-05-30 | 2004-02-24 | Praxair Technology, Inc. | Method for operating a transcritical refrigeration system |
| US6968708B2 (en) * | 2003-06-23 | 2005-11-29 | Carrier Corporation | Refrigeration system having variable speed fan |
| JP2005059797A (en) * | 2003-08-19 | 2005-03-10 | Denso Corp | Air-conditioner for vehicle |
-
2005
- 2005-11-16 CA CA2626064A patent/CA2626064C/en not_active Expired - Fee Related
- 2005-11-16 CN CN2005800520679A patent/CN101310153B/en not_active Expired - Fee Related
- 2005-11-16 WO PCT/US2005/041279 patent/WO2007061403A1/en active Application Filing
- 2005-11-16 US US12/090,405 patent/US20090133856A1/en not_active Abandoned
-
2009
- 2009-05-14 HK HK09104419.6A patent/HK1126269A1/en not_active IP Right Cessation
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1157903A (en) * | 1996-04-12 | 1997-08-27 | 王曰信 | Warm meal refrigerater |
| US5857905A (en) * | 1996-10-22 | 1999-01-12 | Denso Corporation | Air conditioning apparatus for vehicle |
| CN1260868A (en) * | 1997-06-05 | 2000-07-19 | 尹明赫 | Air-flow switching type air conditioner for both cooling and heating |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2007061403B1 (en) | 2007-08-09 |
| CA2626064C (en) | 2011-06-28 |
| WO2007061403A1 (en) | 2007-05-31 |
| WO2007061403A8 (en) | 2008-09-25 |
| US20090133856A1 (en) | 2009-05-28 |
| HK1126269A1 (en) | 2009-08-28 |
| CN101310153A (en) | 2008-11-19 |
| CA2626064A1 (en) | 2007-05-31 |
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