CN1690636A - Heat exchanger - Google Patents
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- CN1690636A CN1690636A CNA2005100626016A CN200510062601A CN1690636A CN 1690636 A CN1690636 A CN 1690636A CN A2005100626016 A CNA2005100626016 A CN A2005100626016A CN 200510062601 A CN200510062601 A CN 200510062601A CN 1690636 A CN1690636 A CN 1690636A
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Abstract
An airflow heat exchanger includes a set of parallel spaced heat conduction area, a set of countersinks is set between the areas, each countersink includes a parallel baffle plate (24), and these baffle plates form the press plate of the passage (26) of the countersinks between the entries and exports (22, 23) which the airflow route is guided to through, these openings are arranged in the four parallel lines of the lateral surface of the countersinks, the two of the four parallel lines comprise respectively the entries and exports (22, 23) relating to the airflow route of the alternate countersinks of the subassemblies. The other two parallel lines comprise respectively the entries and exports relating to the spare countersinks of the heat exchanger's subassemblies. Each countersink includes a detachable frame (21) set on the end part's open of the airflow route which through the countersink and a parallel baffle plate of the press plate which supports in the frame and divides the airflow route into passage. All the passages provide the basically same length of stay for the air passing by.
Description
The application is that application number is 01809473.2, the applying date is March 14 calendar year 2001, denomination of invention is divided an application for the application for a patent for invention of " heat exchanger ".
Technical field
The present invention relates to a kind of heat exchanger that is used between two air flow paths, transmitting heat, heat exchanger more specifically to a kind of isolation of adverse current basically, this heat exchanger has major-minor gas flow loop separately, has the good heat transfer characteristic between these two loops.The present invention is particularly suitable to be used in air conditioning and the ventilating system.
Background technology
Air-flow is isolated heat exchanger and become more and more important for the cost that reduction is sent to the heating in the outdoor air source of enclosure space in for example building or cooling.These heat exchangers need be handled the air-flow of the outdoor air from 50l/s to 10000l/s for small-sized and large space, thereby transmit sensible heat and latent heat from the stale waste gas in room in theory.
The heat exchanger of the common form that supplied gas is used is the parallel-plate heat exchanger.This heat exchanger comprises a folded spaced apart parallel heat-conducting plate, and these plates are formed with the depression that air-flow therefrom passes between them.Depression alternately links to each other one that carries out in hot two air-flows that transmit to deliver therebetween, and remaining depression delivers another air-flow.The The Thermal Capacity of Gaseous amount is lower than liquid.This has caused using fluid passage thin material, wherein to have the development of the heat exchanger of bigger area of section, it is preferred using thin material, and this is because it takes place slowlyer along the heat transmission on the surface of advancing than the situation at wetting liquid that should the surface from gas to one.
In order to prolong " time of staying " of gas in heat exchanger, proposed thin substantially parallel baffle plate is set in depression, these depression extend throughs run through the length of their gas channel, and carry out good thermo-contact with these plates.In U.S. Patent No. 5829513 (Urch), disclosed a kind of like this device.This Patent publish a kind of feature of heat conducting film of sinuous winding is provided, this heat conducting film has many parallel depressions, each in these depressions comprises molded plastics skeleton insert.This insert is included in the flat frame that has wherein supported one group of parallel baffle, and these baffle plates define the pressing plate of the passage that extends between the entrance and exit in being located at framework.
Though have many advantages at the heat exchanger disclosed in the U.S. Patent No. 5829513, it also has many shortcomings.At first, pass in this heat exchanger that gas that special modality advances has spent and different " time of staying " of gas by adjacency channel in same pockets.Though every its width of passage is substantially the same, as shown in Fig. 3 of U.S. Patent No. 5829513, they nest together with U-shaped, thereby external channel is longer than the inner passage.This means and pass this passage by the gas that enters the inner passage to pass external channel than gas faster.The time that should in this passage, be spent " time of staying " for gas.The time of staying of passing the outside more gas of long-channel is longer than the time of staying of passing the inner more gas of jitty.On the time of staying these differentia influences the whole efficiency of this heat exchanger.Another shortcoming at the heat exchanger disclosed in the U.S. Patent No. 5829513 is that it has high pressure drop, therefore needs sizable fan energy to promote gas and therefrom passes.
The invention provides a kind of improved heat exchanger that is used between two air flow paths, transmitting heat.
Summary of the invention
According to first aspect, the present invention relates to a kind of airflow heat-exchanger, it comprises one group of parallel spaced thermal conductivity region, between these zones, be provided with one group of depression, each depression comprises parallel baffle plate, these baffle plates form the pressing plate that the steering current path is passed in the passage of the depression between the entrance and exit, these openings are arranged in four parallel lines at the place, side of this group depression, wherein two straight lines comprise the alternately relevant entrance and exit of air flow path of depression of organizing depression with this respectively, two other comprise respectively with this heat exchanger this group depression the relevant entrance and exit of remaining depression, each depression comprises the detachable framework of the opening that is formed with the place, end that is located at the air flow path that passes it and is bearing in the interior parallel baffle that air flow path is divided into the pressing plate of passage of this framework, it is characterized in that all provide the time of staying that equates basically for the gas that therefrom passes described passage.
In one embodiment, the described passage of each bar has equal lengths basically.Preferably, described baffle plate forms S or Z-shaped passage pressing plate basically.Preferably, the pressing plate of one passage is that mirror image symmetry with the pressing plate of the passage of adjacent depression is to provide the convection current that intersects in the described depression.Preferably, the inlet of every passage is positioned on the side relative with the outlet of this group depression.
In another embodiment, each pressing plate of passage is passage nested that is essentially U-shaped.Wherein the length of a described U-shaped passage is greater than the length of inside nested adjacent U-shaped passage thereon.Preferably, the size of one entrance and exit in the described U-shaped passage is greater than the size of the entrance and exit of inside nested adjacent U-shaped passage thereon.Preferably, every continuous U-shaped passage has bigger entrance and exit than inside nested passage thereon.
Preferably, it is identical and be orientated different frameworks and baffle plate that each depression includes structure, thereby be positioned on two straight lines with opening that alternately depression is relevant, and the opening of being correlated with remaining depression is positioned on two different straight lines.Preferably, the isolated rectangle or the square region of the Heat Conduction Material that parallel conductive thermal region that these depressions are separated from each other twines by wriggling are formed.
Preferably, described Heat Conduction Material is selected from metallic film and thin plastic.Preferably, described Heat Conduction Material is a kind of moisture permeable (Moisture permeable) material that sensible heat also can transmit latent heat that both can transmit.
Preferably in one embodiment, described moisture permeable material is a paper.Preferably, described paper has high water intensity texture.Preferably, described paper is a brown paper.About 45 grams of the every weight per square meter of preferably described brown paper.
Preferably, in another embodiment, described moisture permeable material is a kind of plastic material of fine and closely woven braiding.
Preferably, form the combination of framework and baffle plate by a kind of skeleton structure.Preferably, described skeleton structure is plastics.
A kind of air handling system of utilizing according to the described airflow heat-exchanger of first aspect of foregoing invention, wherein supply fan communicates with a pipeline fluid that comprises inlet at place, the side of depression group, be used for to its supply air, and exhaust fan communicates with another pipeline fluid that comprises inlet at place, the side of depression group, is used for transporting the waste gas from carrying out the space of air conditioning.
In a layout, described supply fan and described exhaust fan are adjacent one another are on the same side of depression group.
In another was arranged, described supply fan and described exhaust fan were positioned on the opposite flank of this depression group.
A kind of air handling system of utilizing according to the described airflow heat-exchanger of first aspect of foregoing invention, the air that has wherein entered airflow heat-exchanger leaves airflow heat-exchanger and is entering conveyance conduit so that pass evaporator coil before being transported to the space of carrying out air conditioning by the effect of supply fan.Preferably, described evaporator coil is selected from cooling water coil, vapor compression evaporator and hot-water coil pipe.Preferably, the waste gas that has entered airflow heat-exchanger leaves airflow heat-exchanger by the effect of exhaust fan and passes the evaporimeter liner, and it is cooled to almost wet-bulb temperature by water there.
A kind of air handling system of utilizing according to the described airflow heat-exchanger of first aspect of foregoing invention, wherein the thermoelectricity dish is arranged to communicate with the pipeline fluid that comprises outlet at place, depression group side, and the first of described thermoelectric dish and one of the pipeline of locating to comprise outlet in the side of this depression group relevant fluid communication with the air flow path of the alternately depression of this depression group, and the second portion of described thermoelectric dish and place, side in this depression group relevant with the air flow path of the residue depression of this assembly have one of the pipeline of outlet fluid communication, and control module is arranged between described first and second parts that thermoelectricity coils.Preferably, described thermoelectric dish comprises heat and cold finned type heat exchanger.
Preferably, the dc voltage that is applied on the described control module produces heating mode or refrigerating mode for described air handling system according to the polarity of described voltage.
A kind of air handling system of utilizing according to the described airflow heat-exchanger of first aspect of foregoing invention, wherein water jacket assembly is arranged to communicate with the pipeline fluid that comprises outlet at place, the side of depression group, and the first of described water jacket assembly comprises first water coil that is connected with first pump with first water jacket, described first water coil is adjacent with the root pipe that comprises outlet at the place, side with this relevant depression group of the air flow path that replaces depression of this depression group, and described water jacket assembly second portion comprise second water coil that is connected with the second pump fluid with second water jacket, and one of pipeline that described water coil and place, side in the depression group relevant with the air flow path of the residue depression of this assembly comprise outlet is adjacent, and control module is arranged between described first and second water jackets.
In optionally arranging, one in described first and second parts of described water jacket assembly by one group of air cooling fins replacement adjacent with described control module.
A kind of storeroom air handling system of utilizing according to the described airflow heat-exchanger of first aspect of foregoing invention, the fresh air that wherein enters described refrigerating chamber passes first fan, this fan communicates with pipeline fluid wherein, described these pipelines comprise the alternately relevant inlet of air flow path of depression with this depression group at the place, side of this depression group, and the waste gas that leaves described refrigerating chamber passes second fan, this fan communicates with pipeline fluid wherein, and described these pipelines comprise the relevant outlet of air flow path with the residue depression of this depression group at the place, side of this depression group.
Preferably, the air capacity of passing it that described first fan produces equals or less times greater than described second fan, thereby the air pressure in described refrigerating chamber is remained on substantially the same with extraneous gas or the bigger a little level.Preferably, described first and second fans are paddle wheel fans.
According to second aspect, the present invention relates to a kind of airflow heat-exchanger, it comprises one group of parallel spaced thermal conductivity region, between these zones, be provided with one group of depression, each depression comprises parallel baffle plate, these baffle plates form the pressing plate that the steering current path is passed in the passage of the depression between the entrance and exit, these openings are arranged in four parallel lines at the place, side of this depression group, wherein two straight lines comprise the alternately relevant entrance and exit of air flow path of depression with the depression group respectively, two other comprises the relevant entrance and exit of remaining depression with the depression group of this heat exchanger respectively, each depression comprises the detachable framework of the opening that is formed with the place, end that is located at the air flow path that passes it and is bearing in the interior parallel baffle that air flow path is divided into the passage pressing plate of this framework, the isolated rectangle or the square region of the Heat Conduction Material that the parallel conductive thermal region that these depressions are separated from each other twines by wriggling form, it is characterized in that, described Heat Conduction Material is a kind of moisture permeable material, and this material both can transmit sensible heat and also can transmit latent heat.
Preferably, described in one embodiment moisture permeable material is a paper.Preferably, described paper has a kind of high water intensity texture.Preferably, described paper is a brown paper.About 45 grams of the every weight per square meter of preferably described brown paper.
Preferably, the described in another embodiment moisture permeable material plastic material that is a kind of fine and closely woven establishment.
Description of drawings
Now will the present invention will be described with reference to accompanying drawing in the mode of embodiment, in these accompanying drawings:
Fig. 1 is the plane of first embodiment of detachable framework, and it has the baffle plate that defines according to the passage flat board of heat exchanger of the present invention;
Fig. 2 is the end-view at the detachable framework of the heat exchanger shown in Fig. 1;
Fig. 3 is at the I-I of the detachable framework shown in Fig. 1 section;
Fig. 4 is for using the decomposition diagram at the portion of hot interchanger of the detachable framework shown in Fig. 1;
Fig. 5 demonstrates the heat exchanger that assembles in type shown in Fig. 4, and demonstrates shell and airflow direction;
Fig. 6 is the plane of second embodiment of detachable framework, and it has the baffle plate that defines according to the passage pressing plate of heat exchanger of the present invention;
Fig. 7 is the end-view at the detachable framework of the heat exchanger shown in Fig. 6;
Fig. 8 is at the VI-VI of the detachable framework shown in Fig. 6 section;
Fig. 9 is for using the decomposition diagram at the portion of hot interchanger of the detachable framework shown in Fig. 6;
Figure 10 is the partial side view of amplification of the framework of Fig. 6, and it demonstrates the structure of inlet;
Figure 11 is the end details of two frameworks and the schematic diagram of their folded films in junction;
Figure 12 is the schematic diagram of the end details of a framework;
Figure 13 is the plane of the 3rd embodiment of detachable framework, and it has the baffle plate that defines according to the passage pressing plate of heat exchanger of the present invention;
Figure 14 is the decomposition diagram that has used at the portion of hot interchanger of the detachable framework shown in Figure 11;
Figure 15 constitutes first schematic side elevation of arranging of unit for gas;
Figure 16 constitutes second schematic side elevation of arranging of unit for gas;
Figure 17 demonstrates the 3rd schematic elevation view of arranging that constitutes the unit with the air of the fresh air fan coil pipe unit form with evaporation coil;
Figure 18 is at the XVII-XVII of the detachable framework shown in Figure 17 section;
Figure 19 demonstrates the 4th schematic elevation view of arranging that constitutes the unit with the air of the fresh air encapsulation unit form with evaporation coil, cooling fin and condenser coil;
Figure 20 demonstrates the 5th schematic elevation view of arranging that constitutes the unit with the air of the fresh air fan coil pipe unit form with thermoelectric dish;
Figure 21 demonstrates the 6th schematic elevation view of arranging that constitutes the unit with the air of the fresh air fan coil pipe unit form with thermoelectric dish;
Figure 22 demonstrates the 7th schematic elevation view of arranging that constitutes the unit with the air of the fresh air encapsulation unit form with thermoelectric dish and cooling fin;
Figure 23 demonstrates the 8th schematic elevation view of arranging that constitutes the unit with the air of the fresh air fan coil pipe unit form with thermoelectric dish;
Figure 24 demonstrates the 9th schematic elevation view of arranging that constitutes the unit with the air of the fresh air fan coil pipe unit form with thermoelectric dish;
Figure 25 demonstrates the decomposition diagram that constitutes the amplification of employed water jacket/control module assembly in the unit at the air of Figure 24;
Figure 26 demonstrates the perspective view that constitutes the amplification of employed water jacket-finned fin/control module assembly in the unit at the air of Figure 24;
Figure 27 is used to keep in cold storage first schematic side elevation of arranging of unit ventilators of chamber;
Figure 28 is used to keep in cold storage second schematic side elevation of arranging of unit ventilators of chamber.
Specific embodiments
In the first embodiment, as in the present invention as shown in Fig. 1-15 being a kind of airflow heat-exchanger assembly that is contained in the sealing shell 17.Similar to disclosed in the U.S. Patent No. 5829513, this airflow heat-exchanger comprises one group of parallel and isolated thermal conductivity region, between them, be provided with one group of depression 16, each depression includes baffle plate 4, and these baffle plates define the pressing plate that the passage 6 of the depression between the entrance and exit 2,3 is passed in the steering current path.
Each depression comprises detachable framework 1 as shown in fig. 1, and this framework has inlet 2 and outlet 3 at each place, end of air flow path.Framework 1 has a plurality of thin guidance tapes (baffle plate) 4, and these baffle plates form the passage that is essentially U-shaped 6 of a plurality of embeddings together, and these passages extend at the inlet on the upside at framework 2 with between the outlet on the downside of framework 13.Web 5 has the thin rectangular shape cross section and extends along the limit in framework 1 and across to trigger part as turbulent flow, be used for improving performance and support guide band 4.Thin web plate 7 extends along the limit and strides across inlet 2 and outlet 3 with at these edge of opening place support guide bands 4.The centre is with 8 to be arranged on inlet 2 and export between 3.Three-dimensional limit lead-in 9 provides support at three side upper support frameworks and for web 5.
Each enter the mouth 2 sizes relevant with respective channel 6 change.The inlet 2a of minimum dimension is positioned at and is nested on the innermost U-shaped passage 6a.Maximum sized inlet 2b is positioned at and is nested on the outmost U-shaped passage 6b.The size of inlet 2 increases for every the passage 6 that outwards moves to passage 6b from passage 6a gradually.Equally, the outlet 3a of minimum dimension is positioned at and is nested on the innermost U-shaped passage 6a, and maximum sized outlet 3b is positioned at and is nested on the outmost U-shaped passage 6b.The size of this outlet 3 increases for every the passage 6 that outwards moves to passage 6b from passage 6a gradually.As shown in fig. 1, by changing the size of entrance and exit 2,3, thereby the pressure of the gas by every passage can be become about equally with flow-control and has identical " time of staying ".
Though dispensable, can preferably make gas slow down slow and use more bight area in the extension projection 11 of the turning location of every passage.Use half groove (or hole) to discharge any water of condensation in framework 1.Tapering part 13 and 14 is used for increasing the zone of opening, and makes that entering gas can freely enter at inlet 2 places.
Fig. 4 demonstrates the film 15 that wriggles and twine, and it forms series of parallel depression 16.This film can be made by thin aluminum film or thin heat-conducting plastic.But, more preferably adopt a kind of permeable material for film 15, for example meticulous woven plastics material or have the paper of high water intensity texture, it can transmit sensible heat and latent heat.
A kind of paper of adequate types is the brown paper of about 45 grams of every weight per square meter.This paper has the good heat transfer characteristic, and has enough intensity for operation.Can use about 65 grams of for example every weight per square meter of heavier brown paper, so good but its heat transfer property does not have the paper of low weight.Though the weight that can adopt every square metre is less than 45 brown paper that restrain and have better heat-transfer character, this paper is frangible and be difficult to work during making this heat exchanger.
Perhaps, film 15 can be the material that a kind of thin polyester material of meticulous braiding is for example sold with trade mark TYDEK on market by Dupont.
As shown in Figure 4, this heat exchanger is made of a plurality of frameworks 1, and each framework is contained in the corresponding depression 16.The entrance and exit 2 of framework 1 and 3 turns over 180 degree so that gas can flow to the both sides of this depression group for optional depression 16, main there gas is arranged on the side with inlet 2c and outlet 3c and secondary gas access 2d and the opposite flank of outlet 3d in this depression group.Framework 1 is preferably made by elasticity and inactive plastic molded material by tough and tensile, firm.Suitable material is a kind of polyacrylate compound.
Figure 5 shows that the heat exchanger assemblies that assembles, demonstrate shell 17 and air path on every side.
Fig. 6-8 demonstrates second embodiment of the heat exchanger that is adverse current at work basically.In the first embodiment, entrance and exit 2,3 is positioned on the same side of framework 1.And in this embodiment, inlet 22 and outlet 23 are positioned on two opposite sides that tiltedly face toward of framework 21.Framework 21 has one group of parallel baffle (thin guidance tape) 24 therein, and these baffle plates are formed on the pressing plate of the passage 26 that extends between the entrance and exit 22,23 that is located in the framework 21.Web 25 is arranged in the mid-plane of framework 21 and is supporting these baffle plates 24.In this embodiment, the length of every passage 26 and width equate basically.Wherein these passages are essentially S or Z-shaped this structure and have guaranteed and the pressure through the gas of every passage can have been become about equally with flow-control and have identical " time of staying ".
Fig. 9 demonstrates the perspective and the decomposing schematic representation of the portion of hot interchanger of second embodiment.The sinuous film 35 that twines is similar with the film 15 of first embodiment on structure and material.This heat exchanger is made of a plurality of frameworks 21, and each framework is contained in the corresponding depression 36.This framework 21 is inserted in each depression, each adjacent framework 21 falls turnback there, thereby make in inlet 22 depressions that are located on the top and on the bottom of this assembly, have the outlet 23 of the reversing framework 21a of adjacent depression, but have and side identical shown in Fig. 9.
Be that according to advantage adjusting to a line of the straight line of outlet 23 that can be by making a heat exchanger and the inlet 22 of adjacent heat interchanger or the like fits together many this heat exchanger in series (side by side) to form bigger heat exchanger assemblies at the heat exchanger of second embodiment shown in Fig. 6-9.This makes that the heat exchanger effectiveness between the major-minor gas flow loop is higher.
Figure 10 has shown 22 the structure of entering the mouth, wherein two flat parallel and isolated side bands 31 form frameworks 1 the side continuously, thereby opening 22 is formed between them.The end of diversion belt 30 and side band 31 are together Unitarily molded.Every side band 31 is provided with along its length and extends and fit into rib 32 in the groove 33 of (referring to Figure 11 and 12) in the opposite flank that is formed on adjacent frame 21.Film 35 is clipped between rib 32 and the groove 33 in its edge, clamps these edges motionless firmly during their heat exchanger assemblies in installation diagram 9.
Figure 13 demonstrates the 3rd embodiment of framework 41, and this embodiment is adverse current at work basically.First embodiment among Fig. 8 and Fig. 1 is closely similar.Difference is to have the separation band 56 that makes entrance and exit 42 and opened in 43 minutes.This band 57 can for framework 41 length half or longer.Framework 41 has inlet 42 and the outlet 43 that is made of many groups of thin guidance tapes 44, and these bands are formed on the passage in the inlet 42 of upside and extension between the outlet 43 on framework 41 downsides together.These web 45 its cross sections are elongated rectangular and extend along the limit and cross framework 41 and trigger part with the turbulent flow as air-flow, are used for improving performance and supporting guidance tape 45.Thin web plate 47 extends through opening 42 and 43 and supporting band 44 along the limit.Three-dimensional limit lead-in 49 framework at three side upper supports.Opening 42 sizes are variable so that same amount of air can be drawn in every passage 46.By changing the size of inlet 42,43, can control every the passage 46 of flowing through gas pressure and flow about equally and have identical " time of staying ".Though the extension projection 51 in the turning location of every passage 46 is dispensable, can preferably makes gas slow down and use more turning area.Jack (or hole) 52 is used for discharging any water of condensation in framework 41.
Figure 14 demonstrates the perspective of portion gas heat exchanger of the 3rd embodiment and the schematic diagram of decomposition.Plastic frame 41 injects in each depression 56, and each replaces adjacent framework 41 and turns over 180 degree so that gas can flow to the both sides of this assembly there.
The sinuous film 55 that twines is similar to the film of first embodiment on structure and material.
Described in the above-described embodiment heat exchanger is suitable for use in the many air conditionings or ventilating system of the sensible heat of switch room's outer air and latent heat.This heat exchanger can be used in to be provided outdoor air in the air handling system of the return air that into has heating and/or cooling device now, perhaps just installs individually to send outdoor air to room.The total amount of heat brethaid can be incorporated into the fan coil assembly, being used for outdoor gas for 10%-100% provides energy transmission from off-air.This latent heat heat exchange amount institute energy delivered approximately is more than three times of sensible heat heat transfer heat exchanger of prior art.
Utilize second embodiment of above-mentioned heat exchanger that many purposes are described now.
Figure 15 demonstrates a kind of air component units with shell 117, is used for by enthalpy heat exchanger 100 outdoor air 102 being transported to opening 105 via supply fan 104, and this opening leads to the conveying loop that is used for to the space conveying that will carry out air conditioning.Heat exchanger 100 is in the sort of type described in above-mentioned second embodiment of the described heat exchanger of reference Fig. 6-9.Be discharged in the atmosphere by exhaust fan 107 and by exporting 108 from the waste gas 106 that will carry out air conditioning (stale gas).
In the optional layout shown in Figure 16, these air-flows are opposite each other.Performance is closely similar, but some equipment can require the layout of Figure 16 rather than in the layout shown in Figure 15.
Figure 17 and 18 demonstrates " fresh air fan coil pack " (air-conditioning package) of the shell 125 with equipment, be used for by major loop 109 via evaporator coil 129 to supply fan 104 with outdoor air 102 provide lead to the outlet 105.Flow to opening 108 from the stream of the waste gas in the room 106 subloops 109 via exhaust fan 107 by heat exchanger 100.This layout is planned to handle up to 100% outdoor gas and near 100% off-gas flows of balance and is passed through heat exchanger.This mainly uses when the whole fresh air of commercial needs, for example smoking bar, cinema or the air of many people or pollution is arranged in the space of sealing.Coil pipe 129 can be a kind of cooling water coil, vapor compression evaporator or hot-water coil pipe, and can be above-mentioned mixture.Common air-flow can be from 300l/s air feed and capacity to 10, in the scope of 000l/s.Owing to must have positive air pressure in the room, the supply air flows than waste gas usually and manys the air of 5%-10%.The filtration of air stream is carried out (not shown at these) at the place, entry position of air-flow usually.The energy of enthalpy heat exchanger 100 exchanges is about three times of sensible heat exchanger, therefore makes the temperature and humidity of discharging air-flow descend 75%.
Figure 19 demonstrates and at the similar apparatus of air conditioning described in Figure 17 and 18, still also is combined with a kind of evaporative cooling plate 145.This heat exchanger 100 is contained in and is used in the housing 125 by air cleaner 151 outdoor air 102 supplies being advanced in the major loop 109 of heat exchanger 100.This air flows in the evaporator coil 129 and leads to outlet 105 to be fed to the room via supply fan 104 then.Enter the compressor 149 and the subloop 110 of heat exchanger 100 by opening 106 from the waste gas in room, and flow to evaporative cooling plate 145, it is cooled to wet-bulb temperature from the condensed water of evaporimeter 129 there, and passes the top that pipeline 153 flows to coldplate 145 by being pumped at the pump 150 of dish in 152.This waste gas stream enters condenser coil 146 and passes outlet 108 via exhaust fan 107 and lead to atmosphere with replenishing air 154 then.
The whole efficiency of this steam compression system can improve by using evaporative cooling plate 145, and if cost be a factor then can come work without it.This system is ideally suited and is used for the recycled back heating or can heats (not shown) by using gases.With COP is that 2.3: 1 average unit compares, under the atmosphere of 35 ℃ of dry bulbs and 28 ℃ of wet bulbs and to use heat exchanger 100 and evaporative cooling dish 145 to become the reheater condenser coil pipe and have the backflow room temperature be that the performance of this system will have greater than the coefficient of performance of 5: 1 units (COP) under 25 ℃/18 ℃ conditions.
In this case, enthalpy heat exchanger 100 need cool off atmosphere greater than 50% gross energy and the needed supply temperature in this room of cooling that dehumidifies.
Figure 20 demonstrate at the similar replenish air assembly shown in Figure 15, but it also is combined with a kind of thermoelectricity (semiconductor) heating and cooling plate 120.The replenish air assembly has shell 117, and this shell is used for passing supply fan 104 by enthalpy heat exchanger 100 via the first finned type heat exchanger part 113 of thermoelectricity dish 120 outdoor air 102 is offered opening 105.The second finned type heat exchanger part 112 that waste gas 106 is sent to the thermoelectric dish 120 of heat exchanger 100 processes is discharged in the atmosphere to exhaust fan 107 and by exporting 108.Control module 114 is with the first and second finned type heat exchanger parts 112 and opened in 113 minutes.Drainage groove 115 is removed the water that condenses arbitrarily from atmosphere, and drains by floss hole 116.Such unit is fit to be used for be delivered into one or more rooms for example house, office or accommodation by pipeline, because it can make to become the low profile assembly.Enthalpy heat exchanger 100 provides the gas return path 109 and 110 of two adverse currents basically of isolating mutually, has good heat exchange performance between these two loops.Gas along basically each other the path flow of adverse current through heat exchanger 100, thereby make sensible heat and latent heat conversion between the arrowed subloop 110 that arrowed major loop 109 that the air that will cool off or heat is flowed through and waste gas 1 (or stale air) are flowed through maximum.The polar inductive that apply according to voltage of direct current (DC) voltage on module 114 goes out heating mode or refrigerating mode.
Figure 21 is similar to Figure 20, except heat exchanger 100 be in vertical position in and can for the length of any appropriate to allow higher heat load and air-flow.The shell 117 of equipment is used for loop 109 that conveying chamber outer air 102 passes enthalpy heat exchanger 100 and passes supply fan 104 through thermoelectric dish 120 and lead to opening 105.Exhaust fan 7 is led to via the exhaust side of the second portion 113 of thermoelectricity dish 120 in the loop 100 that waste gas 106 passes heat exchanger 100, is discharged in the atmosphere by exporting 8 then.As among Figure 20, this control module 114 is with the first and second finned type heat exchanger parts 112 and opened in 113 minutes.Drainage groove 115a and 115b remove any water that condensation goes out from atmosphere.
Figure 22 is identical with Figure 21, the evaporative cooling plate of installing before being discharged into atmosphere except the second portion 113 that enters thermoelectric dish 120 at waste gas 106 so that by fan 107 via opening 108 145.Condensed water from the first 112 of thermoelectricity dish 120 pumps out drainage groove 115 by pump 118, and is discharged into coldplate 145 by supply pipe 119, therefore improved should thermoelectricity dish 120 cooling performance.This has reduced supply temperature and has reduced input current.Control module 114 is with the first and second fin heater parts 112 and opened in 113 minutes.
Figure 23 is similar to Figure 20, except supply fan 104 and exhaust fan 107 have rotated 90 degree.Gas 102 passes the first finned type heat exchanger part 112 that air cleaner 160 enters the thermoelectric dish 120 of enthalpy heat exchanger 100 flow directions in loop 109 outside the supply room in shell 117, and enters the room via supply fan 104 by opening 105.Waste gas 6 passes air cleaner 161 and enters heat exchanger 100, and enters atmosphere by opening 108 via loop 110 then by exhaust fan 107.If do not need whole fresh air, then bypass opening 165 can provide extra air for the first and second finned type heat exchanger parts 112 and 113.
Demarcation strip 122 makes indoor and outdoors air-flow 102 and opened in 106 minutes.This assembly can be installed into wall opening 119 or the window opened in.
The advantage of the thermoelectricity dish 120 of utilization in the replenish air assembly as shown in Figure 20-23 is, compare with common driven compressor system, they have moving-member seldom, do not have the refrigerant gas that pollutes, and the low and outdoor air exchange of starting current is up to 100%.Because the DC starting current is low, so it also can use with the PV electronic component.
Because these replenish air assemblies are without any compressor, noise and vibration are very low.From the variation that is cooled to heating mode is to be undertaken by the polarity inversion that makes circuit simply.The heat exchanger of isolating cooled off and the outdoor air that dehumidifies by the enthalpy that exchange cold type on cool cycles goes out air in summer.Heating mode makes outdoor air warm and the moisture of discharging sent back enter air.Thermoelectric dish 120 heats as required or cool off and can change the temperature of electric current with the maintenance comfortable.
In refrigerating mode can by use from the evaporation water of air cooling fins and pumping on the evaporating plate it or it is ejected on the hot fin of discharge air of semiconductor board and raises the efficiency.
This system can be installed in the window opening or in the ceiling space or at underfloor.This system's ideal is used for accommodation, be used for the skyscraper in large pipeline zone or be single room.For accommodation, the thermoelectric dish of highly low fresh air assembly can be installed in top, ceiling space, bathroom, and has and pasting ceiling the small-sized fresh air pipe that leads to the outside is installed.
The heat exchanger that separates sends the energy of outside air to waste gas.First 112 by the thermoelectricity dish makes fresh supply gas cooling or heating as required.Bathroom waste gas 106 discharges the bathroom gas extraction system then and leads to atmosphere by the second portion 113 of heat exchanger 100 by thermoelectric dish 120.This assembly is can size less, be easy to install, quiet and have low starting current, this electric current has reduced the surge of building.Each room is separate then, and adjusting is used for air-flow and comfortable separately.The fresh air of sending into is the fresh air demand of accommodation head and shoulders above, and also surpasses the bathroom exhaust volume, and on the operating cost of accommodation without any influence.
Figure 24 demonstrates the modification of replenish air assembly.Figure 20 has the first and second water coil 120a and 120b replaces plate 120, and has water jacket 112a and the 113a that is installed on the control module 114a.First water loop 175 with pump 176 makes water be recycled to the first water coil 120a.Outside supply air 102 enters heat exchanger 100 and flow through water coil 120a and water jacket 112a, leads to supply fan 104 and opening 105 then.Second water loop 177 with pump 178 makes and is recycled to the second water coil 120b.Waste gas 106 transmits and leads to ventilating fan 107 through over-heat-exchanger 100 then by the second water coil 120b and water jacket 113, and is discharged in the atmosphere by exporting 108.Control module 114a divides the first and second water jacket 12a and 13a and opens so that water flows through in counter-flow arrangement.Like this, module 114a can away from air-flow or shell 117 even, and be connected with 178 with by heat exchanger 100 coolings or heat two air-flows that separate with pump 176 respectively with 177 by water loop 175.Figure 25 has described assembly water jacket 112a, 113a/ control module 114a assembly.
Air component units shown in Figure 20-24 also can be used for cooling automobile for example car, bus, train and military vehicle.
Figure 26 demonstrates the optional embodiment at the module 114a shown in Figure 21, this control module 114a can have be installed in one on the side water jacket 112a and be installed in a plurality of air cooling fins 113b on the opposite side.Like this, module 114b can be provided with away from air-flow or shell 117.
In another is arranged, heat exchanger of the present invention also be suitable for be equipped with food product for example the untainted air of needs of fruit, vegetables, meat, dough/pasta and other type keep their freshness and can deposit the fresh air environment of long food.Utilized this layout of the present invention to describe with reference to Figure 27 and 28, and related in particular to remove undesired gas from the room, stored those products can discharge undesired gas in described room.This embodiment is particularly useful for but is not unique commercial fruit locker room that is applicable to.
Figure 27 demonstrates the partial schematic diagram of fruit locker room 301, and comprises one group of fruit case 340 and be provided with the access door (not shown), can transmit these chests individually by this door and enter or withdraw from a room.Roughly be installed in locker room's ceiling centre be the opening 325 that is divided into air intake pipeline 302 and air outlet slit pipeline 305 by baffle plate 326.Opening 325 is covered by shell 330 at the within and without of locker room.Air filtration screen 331 has filtered the fresh air of input.
This fresh air is passed passage 310 and is left waste gas (stale gas) cooling of locker room, thereby is cooled under its dew point, and near room temperature.
The locker room can be provided with the air control equipment 323 of himself, is used for the concrete fruit stored to meet in the humidity of wherein air and the optimum value scope that temperature remains on them.This refrigeration plant can be incorporated into shell 330 where necessary.
This device can also be arranged to turn round continuously or enter main refrigeration system with running at the same time.
When this equipment of use, blast fan 304 and 307 promotes air continuously and passes entrance and exit passage 309,310.Because the operating characteristic of blast fan is higher than the main outside a little so the air pressure in the locker room remains, thereby when the access door (not shown) is temporarily opened, does not have extraneous air to flow to the locker room.This heat loss of just having guaranteed locker room under the situation of the door of opening is very little.
Comprise undesired gas for example the stale air of ethene be removed from the locker room by passage 310 continuously and replace and be cooled to main temperature in the locker room by the stale air that outwards flows by the fresh filtered air in passage 309.Therefore, so in the locker room, do not have any undesired gas build and have only considerably less heat loss owing to from the locker room, having removed stale gas.
When the air in the locker room is changed speed and is 250 liters/second by the employed energy of fan motor less than 200 watts, thereby the work calories that produces by the fan motor that is designed to be positioned at the outside, locker room in fact in the temperature of locker room without any influence.
Figure 28 demonstrates the optional embodiment in the system shown in Figure 27, and it is designed to be assemblied on the wall of locker room 301.Outside atmosphere enters air cleaner 331 and flows to input channel 302, flows to heat exchanger 300 then under the effect of fan 304.It is followed this loop 309 and flows to fresh air opening 305.Waste gas stream enters heat exchanger 300 at opening 306 places by loop 310, flows to atmosphere via fan 307 by exporting 308 then.
Figure 28 can also be assemblied in the roof area, but its shortcoming is that compare with the embodiment of Figure 27 and put in the ceiling manyly, this produces speech for fork lifter load and unloading is an individual problem.By the enthalpy heat exchanger of use transmission sensible heat and latent heat, thereby the advantage of this equipment do not need to be drainpipe.
This assembly can also be routed to continuous running or wiring enters main refrigeration system with running at the same time.
When the air in the locker room is changed speed and is 250 liters/second by the employed energy of fan motor less than 200 watts, thereby the work calories that produces by the fan motor that is designed to be positioned at the outside, cold house in fact in the temperature of locker room without any influence.
Because this layout can not relate to the recirculation of air in the room, so can avoid using cleaning equipment and additional cost.Therefore a spot of heat loss only can take place in the operation of this equipment, and it is with improved performance and the whole efficiency operation higher than the previous cleaning equipment that uses.
Though in conjunction with the fruit locker room the present invention's use is in this embodiment specified, the present invention can be used in equally and want to keep in the space of sealing air conditions to be implemented in simultaneously in the situation of saving on investment and the operating cost arbitrarily.The space of these sealings for example can comprise the locker room or be used for fish or the compartment of meat that they all need to keep specified moisture and stable low temperature so that the possibility that reduces the dry of the agricultural product of storing or rot.Owing to do not need drainpipe, so this equipment also can be ideally suited for carrying the transport box of agricultural product or food product to ventilate to being used for.This assembly can also be used in and be used for carrying in cold storage compartment in the automobile of food.
In another embodiment, present invention resides in the heat exchanger described in the US5829513, but utilized the moisture permeable material that is used for the Heat Conduction Material film.The same with foregoing embodiment, moisture permeable material can be fine and closely woven woven plastics material or the paper with high water intensity texture, and it both can transmit sensible heat also can transmit latent heat.A kind of suitable paper is the brown paper of about 45 grams of every weight per square meter, and this is illustrated in front.
Though with reference to specific embodiment describe the present invention, what those one of ordinary skill in the art will appreciate that is that the present invention can implement with many other forms.
Claims (9)
1. airflow heat-exchanger, it comprise one group parallel, isolated thermal conductivity region, between these zones, be provided with one group of depression, each depression comprises parallel baffle plate, these baffle plates form the pressing plate that the steering current path is passed in the passage of the depression between the entrance and exit, these openings are arranged in four parallel lines at the place, side of this depression group, wherein two straight lines comprise the alternately relevant entrance and exit of air flow path of depression with the depression group respectively, two other comprises the relevant entrance and exit of remaining depression with the depression group of this heat exchanger respectively, each depression comprises the detachable framework of the opening that is formed with the place, end that is located at the air flow path that passes it and is bearing in the interior parallel baffle that air flow path is divided into the passage pressing plate of this framework, the isolated rectangle or the square region of the Heat Conduction Material that the parallel conductive thermal region that these depressions are separated from each other twines by wriggling form, it is characterized in that, described Heat Conduction Material is a kind of moisture permeable material, and this material both can transmit sensible heat and also can transmit latent heat.
2. an airflow heat-exchanger as claimed in claim 1 is characterized in that, described moisture permeable material is a paper.
3. an airflow heat-exchanger as claimed in claim 2 is characterized in that, described paper has a kind of high water intensity texture.
4. an airflow heat-exchanger as claimed in claim 3 is characterized in that, described paper is a brown paper.
5. an airflow heat-exchanger as claimed in claim 4 is characterized in that, about 45 grams of the every weight per square meter of described brown paper.
6. an airflow heat-exchanger as claimed in claim 1 is characterized in that, described moisture permeable material is a kind of plastic material of fine and closely woven establishment.
7. one kind as the described airflow heat-exchanger of one of claim 1-6, it is characterized in that described airflow heat-exchanger is in the described the sort of type of claim 1.
8. an airflow heat-exchanger as claimed in claim 7 is characterized in that, forms the combination of framework and baffle plate by a kind of skeleton structure.
9. an airflow heat-exchanger as claimed in claim 8 is characterized in that, described skeleton structure is plastics.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AUPQ6199A AUPQ619900A0 (en) | 2000-03-14 | 2000-03-14 | Total-heat moulded frame heat exchanger |
| AUPQ6199 | 2000-03-14 | ||
| AUPQ9019 | 2000-07-27 | ||
| AUPQ9181 | 2000-08-03 | ||
| AUPR1925 | 2000-12-12 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB018094732A Division CN1209596C (en) | 2000-03-14 | 2001-03-14 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1690636A true CN1690636A (en) | 2005-11-02 |
| CN100455971C CN100455971C (en) | 2009-01-28 |
Family
ID=3820298
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100626016A Expired - Fee Related CN100455971C (en) | 2000-03-14 | 2001-03-14 | Heat exchanger |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN100455971C (en) |
| AU (1) | AUPQ619900A0 (en) |
| ES (1) | ES2371745T3 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103175292A (en) * | 2013-03-26 | 2013-06-26 | 中南大学 | Guide plate film type total-heat heat exchange core body for fresh air ventilator |
| CN103201580A (en) * | 2010-11-09 | 2013-07-10 | 株式会社电装 | Heat exchanger |
| CN106168389A (en) * | 2016-08-15 | 2016-11-30 | 浙江普林艾尔电器工业有限公司 | A kind of band Intermediate Heat Exchanger quasiconductor degree of depth dehumidifier |
| CN107144158A (en) * | 2017-06-14 | 2017-09-08 | 西安热工研究院有限公司 | A kind of compact heat exchanger of supercritical carbon dioxide and water heat exchange |
| CN111336855A (en) * | 2020-03-10 | 2020-06-26 | 杭州龙碧科技有限公司 | Novel exchange core framework, total heat exchange core and preparation method thereof |
| CN113218060A (en) * | 2021-03-26 | 2021-08-06 | 深圳通利机电工程有限公司 | Multi-stage heat recovery fresh air processing device of energy-saving central air conditioning system |
| CN113587701A (en) * | 2021-07-16 | 2021-11-02 | 北京科荣达航空科技股份有限公司 | Heat exchanger with ozone conversion and high-temperature precooling functions |
| CN114110743A (en) * | 2021-11-15 | 2022-03-01 | 金国达科技（湖南）有限公司 | Central air conditioning end device that heat exchange efficiency is high |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1498621A (en) * | 1975-06-16 | 1978-01-25 | Page R | Heat exchanger |
| NL8901559A (en) * | 1989-06-21 | 1991-01-16 | Nefit Nv | HEATING DEVICE. |
| US5829513A (en) * | 1992-03-12 | 1998-11-03 | Urch; John Francis | Moulded baffle heat exchanger |
| JP3362611B2 (en) * | 1996-09-12 | 2003-01-07 | 三菱電機株式会社 | Heat exchanger and method for manufacturing heat exchange member of the heat exchanger |
-
2000
- 2000-03-14 AU AUPQ6199A patent/AUPQ619900A0/en not_active Abandoned
-
2001
- 2001-03-14 CN CNB2005100626016A patent/CN100455971C/en not_active Expired - Fee Related
- 2001-03-14 ES ES01911272T patent/ES2371745T3/en not_active Expired - Lifetime
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103201580A (en) * | 2010-11-09 | 2013-07-10 | 株式会社电装 | Heat exchanger |
| CN103201580B (en) * | 2010-11-09 | 2015-06-24 | 株式会社电装 | Heat exchanger |
| CN103175292B (en) * | 2013-03-26 | 2015-05-20 | 中南大学 | Guide plate film type total-heat heat exchange core body for fresh air ventilator |
| CN103175292A (en) * | 2013-03-26 | 2013-06-26 | 中南大学 | Guide plate film type total-heat heat exchange core body for fresh air ventilator |
| CN106168389B (en) * | 2016-08-15 | 2022-06-24 | 浙江普林艾尔电器工业有限公司 | Semiconductor deep dehumidifier with intermediate heat exchanger |
| CN106168389A (en) * | 2016-08-15 | 2016-11-30 | 浙江普林艾尔电器工业有限公司 | A kind of band Intermediate Heat Exchanger quasiconductor degree of depth dehumidifier |
| CN107144158A (en) * | 2017-06-14 | 2017-09-08 | 西安热工研究院有限公司 | A kind of compact heat exchanger of supercritical carbon dioxide and water heat exchange |
| CN107144158B (en) * | 2017-06-14 | 2024-02-27 | 西安热工研究院有限公司 | Compact heat exchanger for heat exchange between supercritical carbon dioxide and water |
| CN111336855A (en) * | 2020-03-10 | 2020-06-26 | 杭州龙碧科技有限公司 | Novel exchange core framework, total heat exchange core and preparation method thereof |
| CN113218060B (en) * | 2021-03-26 | 2022-04-15 | 深圳通利机电工程有限公司 | Multi-stage heat recovery fresh air processing device of energy-saving central air conditioning system |
| CN113218060A (en) * | 2021-03-26 | 2021-08-06 | 深圳通利机电工程有限公司 | Multi-stage heat recovery fresh air processing device of energy-saving central air conditioning system |
| CN113587701A (en) * | 2021-07-16 | 2021-11-02 | 北京科荣达航空科技股份有限公司 | Heat exchanger with ozone conversion and high-temperature precooling functions |
| CN114110743A (en) * | 2021-11-15 | 2022-03-01 | 金国达科技（湖南）有限公司 | Central air conditioning end device that heat exchange efficiency is high |
| CN114110743B (en) * | 2021-11-15 | 2023-09-22 | 金国达科技（湖南）有限公司 | Central air conditioner terminal device with high heat exchange efficiency |
Also Published As
| Publication number | Publication date |
|---|---|
| ES2371745T3 (en) | 2012-01-09 |
| AUPQ619900A0 (en) | 2000-04-06 |
| CN100455971C (en) | 2009-01-28 |
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Granted publication date: 20090128 Termination date: 20140314 |