CN100458345C - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN100458345C CN100458345C CNB2005100025245A CN200510002524A CN100458345C CN 100458345 C CN100458345 C CN 100458345C CN B2005100025245 A CNB2005100025245 A CN B2005100025245A CN 200510002524 A CN200510002524 A CN 200510002524A CN 100458345 C CN100458345 C CN 100458345C
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- heat
- transfer pipe
- plate
- radiating plate
- heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D29/00—Independent underground or underwater structures; Retaining walls
- E02D29/10—Tunnels or galleries specially adapted to house conduits, e.g. oil pipe-lines, sewer pipes ; Making conduits in situ, e.g. of concrete ; Casings, i.e. manhole shafts, access or inspection chambers or coverings of boreholes or narrow wells
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D29/00—Independent underground or underwater structures; Retaining walls
- E02D29/045—Underground structures, e.g. tunnels or galleries, built in the open air or by methods involving disturbance of the ground surface all along the location line; Methods of making them
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D2600/00—Miscellaneous
- E02D2600/20—Miscellaneous comprising details of connection between elements
Abstract
The present invention provided a heat exchanger capable of reducing pressure loss and inhibiting the deterioration with lapse of time, of heat transferring performance caused by accumulation of dust and frost formation. In this heat exchanger comprising a plurality of flat fins 10 arranged in parallel with each other at specific intervals and a heat transfer pipe 20 penetrated through the flat fins 10 in a state that a refrigerant passes inside, and exchanging the heat with the air passed between the fins from a front edge side of the flat fins 10, wing parts 11 having a width gradually narrowed from a base part to a tip part and allowing the passed air to generate longitudinal vortex S are formed by being cut and raised from the flat fins 10 at a front part in the air blowing direction, of the heat transfer pipe 20, and winglets 12 cut and raised from the flat fins 10, are formed at a rear part in the air blowing direction of the heat transfer pipe 20.
Description
Technical field
The present invention relates to heat exchanger, such as relating to the tubulation plate-fin heat exchanger that is applicable in automatic vending machine, the gondola etc.
Background technology
As shown in Figure 15, existing so-called tubulation plate-fin heat exchanger is known, this heat exchanger comprises the multi-disc that is arranged in parallel with predetermined distance dull and stereotyped 100 and has connected dull and stereotyped 100 and the heat-transfer pipe 110 of refrigerant in inner loop, this heat exchanger makes and carries out heat exchange between air and the refrigerant to dull and stereotyped 100 air-supplies.
In such tubulation plate-fin heat exchanger, in order to improve the performance of heat exchange, ratio as shown in Figure 16, various flat radiators 100 have been proposed, it forms the small incision that is known as shutter and digs 103 (with reference to patent documentation 1 and patent documentations 2) between heat-transfer pipe 110 and heat-transfer pipe 110.
Patent documentation 1: the spy opens flat 11-281279 communique
Patent documentation 2: the spy opens the 2001-141383 communique
Summary of the invention
But to dig 103 so-called shutter efficient good though formed such incision, digs 103 lip-deep air movement disorder owing to cut, and frictional resistance strengthened, thereby the pressure loss is strengthened.Because the accumulation of dust or the generation of frosting are along with the process of time can make the heat transfer property variation.And be difficult to maintain the shape that the small incision that forms on the surface of thin plate radiating plate is dug.
In view of above situation, the purpose of this invention is to provide a kind of heat exchanger, can reduce the pressure loss, suppress heat transfer property that accumulation or frosting owing to dust the cause problem of variation in time.
To achieve these goals, the heat exchanger of first aspect present invention comprise the multi-disc plate radiating plate that is arranged in parallel with predetermined distance and connect this plate radiating plate and in inside by the heat-transfer pipe of refrigerant, and carry out heat exchange from the leading edge of described plate radiating plate between the air mutual by described plate radiating plate, it is characterized in that, air supply direction the place ahead at heat-transfer pipe, dig the formation alar part from the plate radiating plate incision, this alar part narrows down gradually from the root forward end, and make the air that passes through produce longitudinal turbulence, at the rear of the air supply direction of heat-transfer pipe, form from plate radiating plate and cut the fin of digging.
Relate to the heat exchanger of the present invention the 2nd aspect, it is characterized in that,, set the inclination angle of described fin in the mode of the synchronous rotation composition of the contracted flow composition that flows behind generation and the heat-transfer pipe.
Relate to the heat exchanger of the present invention the 3rd aspect, it is characterized in that, with the deflection composition of the air that passes through be rotated into and be divided into synchronous mode, be set in the inclination angle of the fin that the air supply direction rear of the heat-transfer pipe of the rank rear of air supply direction forms.
Relate to the heat exchanger of the present invention the 4th aspect, it is characterized in that, described plate radiating plate is separately to make from the thin plate cutting that forms described alar part and described fin with predetermined distance continuously.
The heat exchanger of the 1st aspect according to the present invention, formed the alar part that narrows down gradually from the base portion forward end, can make the air generation longitudinal turbulence of passing through owing to upwards cutting to dig from plate radiating plate in the place ahead of heat-transfer pipe air supply direction, so lip-deep air supply direction at plate radiating plate, formed to the alar part inboard and be the longitudinal turbulence that the whirlpool shape flows, this longitudinal turbulence with the horse-hof shape eddy current of heat-transfer pipe root formation mutually mutual interference strengthened longitudinal turbulence and it be directed to around the heat-transfer pipe.In addition, owing to, upwards cut the formation fin, air is directed in the dead band at heat-transfer pipe air supply direction rear from plate radiating plate at the rear of heat-transfer pipe air supply direction.Therefore, can make the temperature boundary layer attenuation around heat-transfer pipe, be suppressed at heat-transfer pipe air supply direction rear and form the dead band, promote the heat transfer at heat-transfer pipe air supply direction rear.
The heat exchanger of the 2nd aspect according to the present invention owing to the mode with the synchronous rotation composition of the contracted flow composition that flows behind generation and the heat-transfer pipe, is set the inclination angle of described fin.Produce the stronger rotation composition of being partial to the fin front end in can flowing at the air that fin is crossed in crosscut, air is directed in the dead band at heat-transfer pipe air supply direction rear.Therefore, on plate radiating plate, produce in the longitudinal turbulence, can also make the temperature boundary layer attenuation that in the dead band at heat-transfer pipe air supply direction rear, develops, promote the heat transfer in dead band, heat-transfer pipe air supply direction rear.
The heat exchanger of the 3rd aspect according to the present invention, because with the deflection composition of the air that passes through be rotated into the synchronous mode that is divided into, be set in the inclination angle of the fin that the air supply direction rear of the heat-transfer pipe of the rank rear of air supply direction forms, so suppressed to generate the dead band at heat-transfer pipe air supply direction rear.Therefore promoted heat transfer at the last biographies heat pipe of air supply direction air supply direction rear.
The heat exchanger of the 4th aspect according to the present invention, described plate radiating plate are separately to make from the thin plate cutting that forms described alar part and described fin with predetermined distance continuously.So can make plate radiating plate with good efficiency.
Description of drawings
Fig. 1 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 1;
Fig. 2 is the side view of heat exchanger that plate radiating plate shown in Figure 1 is stacked;
Fig. 3 is explanation produces longitudinal turbulence on plate radiating plate a stereogram;
Fig. 4 is the stereogram that longitudinal turbulence that produces on plate radiating plate and the horse-hof shape eddy current that produces around heat-transfer pipe are described;
Fig. 5 is the stereogram of the effect of explanation first fin;
Fig. 6 is the stereogram that the effect of the longitudinal turbulence that produces on plate radiating plate, the horse-hof shape eddy current that produces around heat-transfer pipe and first fin is described;
Fig. 7 is the stereogram of the effect of explanation second fin;
Fig. 8 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 2;
Fig. 9 is the side view of heat exchanger that plate radiating plate shown in Figure 6 is stacked;
Figure 10 is the plane of the manufacture method of explanation plate radiating plate shown in Figure 6;
Figure 11 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 3;
Figure 12 is the side view of heat exchanger that plate radiating plate shown in Figure 11 is stacked;
Figure 13 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 4;
Figure 14 is the side view of heat exchanger that plate radiating plate shown in Figure 12 is stacked;
Figure 15 is the stereogram of the heat exchanger of prior art;
Figure 16 is the plane of plate radiating plate of the heat exchanger of prior art.
Symbol description: 10 plate radiating plates; 11 alar parts; 12 first fins; 13 second fins; 20 heat-transfer pipes; 30 plate radiating plates; 31 alar parts; 32 fins; 40 heat-transfer pipes; 50 plate radiating plates; 51 alar parts; 52 fins; 60 heat-transfer pipes; 70 plate radiating plates; 71 alar parts; 72 fins; 80 heat-transfer pipes; H horse-hof shape eddy current; The S longitudinal turbulence; The α angle of attack; The β inclination angle; The γ inclination angle.
The specific embodiment
Describe the preferred embodiment of heat exchanger of the present invention with reference to the accompanying drawings in detail.Yet the present invention is not limited to these embodiment.
Embodiment 1
The heat exchanger of the embodiment of the invention 1 is described based on Fig. 1～Fig. 6.Fig. 1 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 1; Fig. 2 is the side view of heat exchanger that plate radiating plate shown in Figure 1 is stacked; Fig. 3 is explanation produces longitudinal turbulence on plate radiating plate a stereogram; Fig. 4 is the stereogram that longitudinal turbulence that produces on plate radiating plate and the horse-hof shape eddy current that produces around heat-transfer pipe are described; Fig. 5 is the stereogram of the effect of explanation first fin; Fig. 6 is the stereogram that the effect of the longitudinal turbulence that produces on plate radiating plate, the horse-hof shape eddy current that produces around heat-transfer pipe and fin is described; Fig. 7 is the stereogram of the effect of explanation second fin.
The heat exchanger of embodiment 1 be same shown in Fig. 9, have with the parallel stacked multi-disc plate radiating plate 10 of predetermined distance, and perforation plate radiating plate 10 shown in Figure 1 and at the heat-transfer pipe 20 of inner loop refrigerant, to plate radiating plate 10 air-supply, between air and refrigerant, carry out heat exchange in the inner loop of heat-transfer pipe 20.
The thickness of plate radiating plate 10 below 0.5mm, is to be made by the sheet stamping of aluminium alloy usually, but the plate radiating plate 10 of present embodiment is that the sheet stamping of 0.3mm is made.
On the air supply direction of this plate radiating plate 10, be the latticed two biographies heat pipes 20 that are provided with of intersection.In the place ahead of heat-transfer pipe 20 air supply directions, dig formation alar part 11 from plate radiating plate 10 incisions.Alar part 11 is the shape of equilateral triangle, narrow down gradually from the root forward end, its front end (summit) projects on the extended line of the air supply direction that begins from the center of heat-transfer pipe 20, and (not in the stalling range) has angle of attack α with respect to air supply direction in the scope that the longitudinal turbulence S that produces on alar part 11 not have to collapse.
With respect to the air supply direction of the heat-transfer pipe 20 in air supply direction prostatitis,, cut to dig from plate radiating plate 10 and form first fin 12 at oblique rear.Set the angle of inclination beta (, being the shape of falling the Eight characters) of this first fin 12 with respect to heat-transfer pipe 20 from air supply direction in the mode of the synchronous rotation composition of the contracted flow composition that flows behind generation and the heat-transfer pipe.
With respect to the air supply direction of the heat-transfer pipe 20 of air supply direction rank rear (rank rear), cut to dig from plate radiating plate 10 at oblique rear and form second fin 13.The tilt angle gamma (from air supply direction, being positive Eight characters shape with respect to heat-transfer pipe 20) of this second fin 13 is set with deflection composition by air and the synchronous mode of rotation composition.
Then, boehmite being carried out on the surface of the plate radiating plate 10 that so forms handles (ベ one マ one ト processings) or carries out the hydrophily processing by coating immersion property coating.
When to this heat exchanger air-supply, shown on Fig. 3, alar part 11 both sides at the plate radiating plate 10 that has angle of attack α with respect to flow air (air supply direction), be created in a pair of longitudinal turbulence S of the interior sideway swivel of alar part 11, and as shown in FIG. 4, at the root of heat-transfer pipe 20, generate the horse-hof shape eddy current H in same direction rotation with longitudinal turbulence S.Longitudinal turbulence S is subjected to the influence of horse-hof shape eddy current H, when promoting longitudinal turbulence S powerful, longitudinal turbulence S is directed to the root of heat-transfer pipe 20.
Because longitudinal turbulence S blows to air downwards on the surface of plate radiating plate 10, can make the temperature boundary layer attenuation.And because horse-hof shape eddy current H guides to the root of heat-transfer pipe 20 with longitudinal turbulence, the rear that can be suppressed at air supply direction forms the dead band, recovers the heat transfer of heat-transfer pipe 20 at the air supply direction rear.
And as shown in FIG. 5, crosscut be disposed at air supply direction the place ahead heat-transfer pipe 20 oblique rear first fin 12 and in the flow air, generate the strong rotation composition of deflection at the front end of first fin 12, air is directed to the dead band of heat-transfer pipe 20 at the air supply direction rear.Therefore, as shown in FIG. 6, the longitudinal turbulence S with producing on the alar part 11 of plate radiating plate 10 can make the temperature boundary layer attenuation that grows up in the dead band at heat-transfer pipe 20 air supply direction rears.Thereby can recover heat transfer in dead band, heat-transfer pipe 20 air supply direction rear.
Especially as shown in FIG. 7, in second fin 13 of oblique rear configuration air supply direction rank rear (rank rear), heat-transfer pipe 20, air deflection composition that passes through and rotation composition are synchronous, have suppressed to form the dead band at the air supply direction rear of heat-transfer pipe 20.Therefore, on the alar part 11 of plate radiating plate 10, produce in the longitudinal turbulence, can make the temperature boundary layer attenuation that in the dead band at heat-transfer pipe 20 air supply direction rears, develops.Thereby can recover the heat transfer in dead band, heat-transfer pipe 20 air supply direction rear.
Because the longitudinal turbulence S that produces on alar part 11 makes near the air flowing acceleration set point of heat-transfer pipe 20 air supply direction the place aheads generation, this just can suppress the accumulation of dust and frosting takes place.Particularly, owing to carried out the hydrophily processing,, just can not make the increase pressure loss owing to longitudinal turbulence S causes that the heat transfer facilitation effect worsens even conflict mutually also not can frosting for the air that contains moisture and alar part 11 on the surface of plate radiating plate 10.
Thereby, heat exchanger according to embodiment 1, by alar part 11, first fin 12 and second fin 13, the heat-transfer pipe 20 that can recover the air supply direction prostatitis is in the dead band at air supply direction rear and the heat transfer of heat-transfer pipe 20 in dead band, air supply direction rear of air supply direction rank rear, and heat exchanger has just been brought into play high heat transfer property.
Such heat exchanger is different with the heat exchanger of prior art, because the turbulent flow that does not cause by shutter, air stream can not blocked by one section one section ground, has reduced because the pressure loss that friction causes.
The heat exchanger of embodiment 1 disposes heat-transfer pipe 20 by two row, but also can be applicable to the above most configuration of three row, under the situation of the multiple row configuration more than configuration three row, the preferred oblique rear of a biographies heat pipe 20 in the end disposes second fin 13, disposes first fin 12 at other the oblique rear of heat-transfer pipe 20 in prostatitis.
Embodiment 2
The heat exchanger of the embodiment of the invention 2 is described based on Fig. 8～Figure 10.Fig. 8 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 2; Fig. 9 is the side view of heat exchanger that plate radiating plate shown in Figure 8 is stacked; Fig. 9 is the plane of the manufacture method of explanation plate radiating plate shown in Figure 8.
The heat exchanger of embodiment 2 is the same with the heat exchanger of embodiment 1, comprise the multi-disc plate radiating plate 30 that is arranged in parallel with predetermined distance, connect plate radiating plate 30 and, make air and between the refrigerant of heat-transfer pipe 40 inner loop, carry out heat exchange to plate radiating plate 30 air-supplies at the heat-transfer pipe 40 of inner loop refrigerant.
At the air supply direction of this plate radiating plate 30, be the latticed configuration two biographies heat pipes 40 of intersection.In the front of the air supply direction of heat-transfer pipe 40, cut to dig from plate radiating plate 30 and form alar part 31.Alar part 31 is the equilateral triangle that narrows down gradually from the root forward end, on the extended line of the air supply direction that its front end (summit) begins at the center from heat-transfer pipe 40, (not in the stalling range) has angle of attack α with respect to air supply direction in the scope that the longitudinal turbulence S that produces on alar part 31 not have to collapse.
With respect to the air supply direction of heat-transfer pipe 40, dig formation fin 32 from plate radiating plate 30 incisions at oblique rear.The angle of inclination beta of this fin 32 with can produce with heat-transfer pipe after the mode of the synchronous rotation composition of the contracted flow composition that flows (from air supply direction, being the shape of falling the Eight characters with respect to heat-transfer pipe 40) is set.
Then, the surface of the plate radiating plate 30 that so forms is carried out boehmite is handled or carry out hydrophily by coating immersion property coating and handle.
When such heat exchanger is blown, the same with the heat exchanger of embodiment 1, have the both sides of the alar part 31 of the plate radiating plate 30 of angle of attack α at relative air supply direction, generation is towards a pair of longitudinal turbulence S of the interior sideway swivel of alar part 31, in addition, at the root of heat-transfer pipe 40, form the horse-hof shape eddy current H in same direction rotation with longitudinal turbulence S.Longitudinal turbulence S is subjected to the influence of horse-hof shape eddy current H, in intensity that promotes longitudinal turbulence and size, longitudinal turbulence S is directed to the root of heat-transfer pipe 40.
Because longitudinal turbulence S blows to air downwards on the surface of plate radiating plate 30, can make the temperature boundary layer attenuation.And because horse-hof shape eddy current H guides to the root of heat-transfer pipe 40 with longitudinal turbulence S, the rear that can be suppressed at air supply direction forms the dead band, recovers the heat transfer of heat-transfer pipe 40 at the air supply direction rear.
And, on the fin 32 at the oblique rear of air supply direction that is disposed at heat-transfer pipe 40, in the flow air, produce the stronger rotation composition of the front deflection of airfoil 32, and air guided to the dead angle area at the air supply direction rear of heat-transfer pipe 40.Therefore the longitudinal turbulence S that takes place with the alar part 31 at plate radiating plate 30 can make the temperature boundary layer attenuation that develops in the dead angle area at air supply direction rear of heat-transfer pipe 40.Thereby can recover the heat transfer of dead angle area at the air supply direction rear of heat-transfer pipe 40.
Because the longitudinal turbulence S that produces on alar part 31 makes near the air flowing acceleration set point of heat-transfer pipe 40 air supply direction the place aheads generation, this just can suppress the accumulation of dust and frosting takes place.Particularly, owing to carried out the hydrophily processing,, worsen and intensified pressure loses with regard to the heat transfer facilitation effect that longitudinal turbulence S is caused even collides mutually also not can frosting for the air that contains moisture and alar part 31 on the surface of plate radiating plate 30.
Thereby, according to the heat exchanger of embodiment 2, can recover the heat transfer in the dead band at air supply direction rear of heat-transfer pipe 40 by alar part 31 and fin 32, heat exchanger has just been brought into play high heat transfer property.
Such heat exchanger is different with the heat exchanger of prior art, because the turbulent flow that does not have shutter to cause, air stream can not blocked by one section one section ground, has reduced because the pressure loss that friction causes.
The heat exchanger of embodiment 2 disposes heat-transfer pipe 40 by two row, but also can be applicable to the above most configuration of three row.
As shown in Figure 10, plate radiating plate 30 preferably forms alar part 31 and fin 32 with the interval of regulation continuously on the thin plate of aluminium alloy, and cutting is made then.If like this, after forming alar part 31 and fin 32 continuously, plate radiating plate 30 is made in cutting, when having improved manufacturing efficient, can also suppress to produce leftover pieces.Plate radiating plate and the plate radiating plate that disposes the multiple row heat-transfer pipe 40 more than three row owing to the mode ground manufacturing configuration two biographies heat pipes 40 that just pass through the change cutting just there is no need individually to prepare instruments such as mould.
Embodiment 3
The heat exchanger of the embodiment of the invention 3 is described based on Figure 11 and Figure 12.Figure 11 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 3; Figure 12 is the side view of heat exchanger that plate radiating plate shown in Figure 11 is stacked.
The heat exchanger of embodiment 3 is the same with the heat exchanger of embodiment 1, comprise the multi-disc plate radiating plate 50 that is arranged in parallel with predetermined distance, with connect plate radiating plate 50 and, make air and between the refrigerant of heat-transfer pipe 60 inner loop, carry out heat exchange to plate radiating plate 50 air-supplies at the heat-transfer pipe 60 of inner loop refrigerant.
At the air supply direction of this plate radiating plate 50, be the latticed configuration two biographies heat pipes 60 of intersection.Between adjacent heat-transfer pipe 60, dig formation alar part 51 from plate radiating plate 50 incisions.Alar part 51 is the equilateral triangle that narrows down gradually from the root forward end, on the extended line of the air supply direction that its front end (summit) begins at the center from heat-transfer pipe 60, (not in the stalling range) has angle of attack α with respect to air supply direction in the scope that the longitudinal turbulence S that produces on alar part 51 not have to collapse.
With respect to the air supply direction of heat-transfer pipe 60, dig formation fin 52 from plate radiating plate 50 incisions at oblique rear.The angle of inclination beta of this fin 32 with can produce with heat-transfer pipe after the mode of the synchronous rotation composition of the contracted flow composition that flows (from air supply direction, being the shape of falling the Eight characters with respect to heat-transfer pipe 60) is set.
Then, the surface of the plate radiating plate 50 that so forms is carried out boehmite is handled or carry out hydrophily by coating immersion property coating and handle.
When to this heat exchanger air-supply, both sides at the alar part 51 of the plate radiating plate 50 that has angle of attack α with respect to air supply direction, formation is towards a pair of longitudinal turbulence S of the interior sideway swivel of alar part 51, in addition, at the root of rank rear heat-transfer pipe 60, form the horse-hof shape eddy current H in same direction rotation with longitudinal turbulence S.Longitudinal turbulence S is subjected to the influence of horse-hof shape eddy current H, in intensity that promotes longitudinal turbulence and size, longitudinal turbulence S is directed to the root of heat-transfer pipe 60.
Because longitudinal turbulence S blows to air downwards on the surface of plate radiating plate 50, can make the temperature boundary layer attenuation.And because horse-hof shape eddy current H guides to the root of heat-transfer pipe 60 with longitudinal turbulence S, the rear that can be suppressed at air supply direction forms the dead band, recovers the heat transfer of heat-transfer pipe 60 at the air supply direction rear.
In the air of the fin 52 at the oblique rear of air supply direction that is disposed at heat-transfer pipe 60 of flowing through, produce very strong rotation composition towards fin 52 front end deflections, air is directed in the dead band at air supply direction rear of heat-transfer pipe 60.Therefore, can be with make the temperature boundary layer attenuation that in the dead band at the air supply direction rear of heat-transfer pipe 60, develops at the longitudinal turbulence S that produces on the alar part 51 of plate radiating plate 50.Thereby can recover the heat transfer in the dead band, air supply direction rear of heat-transfer pipe 60.
Because the longitudinal turbulence S that produces on alar part 51 makes near the air flowing acceleration set point of rank rear heat-transfer pipe 60 air supply direction the place aheads generation, this just can suppress the accumulation of dust and frosting takes place.Particularly, owing to carried out the hydrophily processing,, thereby just do not have the problem of the heat transfer facilitation effect deterioration increase pressure loss that longitudinal turbulence S causes even conflict mutually also not can frosting for the air that contains moisture and alar part 51 on the surface of plate radiating plate 50.
Thereby according to the heat exchanger of embodiment 3, because alar part 51 and fin 52 can recover the heat transfer of heat-transfer pipe 60 in the dead band at air supply direction rear, heat exchanger has just been brought into play high heat transfer property.
Such heat exchanger is different with the heat exchanger of prior art, because the turbulent flow that does not have shutter to cause, air stream can not blocked by one section one section ground, has reduced because the pressure loss that friction causes.
The heat exchanger of embodiment 3 disposes heat-transfer pipe 60 by two row, but also can be applicable to the majorities configuration of the above heat-transfer pipe 60 of configuration three row.
Embodiment 4
The heat exchanger of the embodiment of the invention 4 is described based on Figure 13 and Figure 14.Figure 13 is the plane of plate radiating plate of the heat exchanger of the explanation embodiment of the invention 4; Figure 14 is the side view of heat exchanger that plate radiating plate shown in Figure 13 is stacked.
The heat exchanger of embodiment 4 is the same with the heat exchanger of embodiment 1, comprise the multi-disc plate radiating plate 70 that is arranged in parallel with predetermined distance, with connect plate radiating plate 70 and, make air and between the refrigerant of heat-transfer pipe 80 inner loop, carry out heat exchange to plate radiating plate 70 air-supplies at the heat-transfer pipe 80 of inner loop refrigerant.
At the air supply direction of this plate radiating plate 70, be the latticed configuration two biographies heat pipes 80 of intersection.In air supply direction the place ahead of heat-transfer pipe 80, dig formation alar part 71 from plate radiating plate 70 incisions.Alar part 71 is the shape of the equilateral triangle that narrows down gradually from the root forward end, on the extended line of the air supply direction that its front end (summit) begins at the center from heat-transfer pipe 80, (not in the stalling range) has angle of attack α with respect to air supply direction in the scope that the longitudinal turbulence S that produces on alar part 71 not have to collapse.
With respect to the air supply direction of heat-transfer pipe 80, dig formation fin 72 from the flat board incision at oblique rear.The angle of inclination beta of this fin 72 with produce with heat-transfer pipe after the mode of the synchronous rotation composition of the contracted flow composition that flows (from air supply direction, being the shape of falling the Eight characters with respect to heat-transfer pipe 80) is set.
Then, the surface of the plate radiating plate 70 that so forms is carried out boehmite is handled or carry out hydrophily by coating immersion property coating and handle.
When such heat exchanger is blown, the same with the heat exchanger of embodiment 1, have the both sides of the alar part 71 of the plate radiating plate 70 of angle of attack α at relative air supply direction, formation is towards a pair of longitudinal turbulence S of the interior sideway swivel of alar part 71, in addition, the root at heat-transfer pipe 80 forms the horse-hof shape eddy current H in same direction rotation with longitudinal turbulence S.Longitudinal turbulence S is subjected to the influence of horse-hof shape eddy current H, in intensity that promotes longitudinal turbulence and size, longitudinal turbulence S is directed to the root of heat-transfer pipe 80.
Because longitudinal turbulence S blows to air downwards on the surface of plate radiating plate 70, can make the temperature boundary layer attenuation.And because horse-hof shape eddy current H is directed to the root of heat-transfer pipe 80 with longitudinal turbulence, the rear that can be suppressed at air supply direction forms the dead band, recovers the heat transfer of heat-transfer pipe 80 at the air supply direction rear.
In the air of the fin 72 at the oblique rear of air supply direction that is disposed at heat-transfer pipe 80 of flowing through, produce very strong rotation composition towards fin 72 front end deflections, air is directed in the dead band at air supply direction rear of heat-transfer pipe 80.Therefore, can be with make the temperature boundary layer attenuation that in the dead band at the air supply direction rear of heat-transfer pipe 80, develops at the longitudinal turbulence S that produces on the alar part 71 of plate radiating plate 70.Thereby can recover the heat transfer in the dead band, air supply direction rear of heat-transfer pipe 80.
Because the longitudinal turbulence S that produces on alar part 71 makes near the air flowing acceleration set point of heat-transfer pipe 80 air supply direction the place aheads generation, this just can suppress the accumulation of dust and frosting takes place.Particularly, owing to carried out the hydrophily processing on the surface of plate radiating plate 70, even conflict mutually also not can frosting for the air that contains moisture and alar part 71, thereby the problem that longitudinal turbulence S causes the heat transfer facilitation effect deterioration increase pressure loss just can not take place.
Thereby according to the heat exchanger of embodiment 4, because alar part 71 and fin 72 can recover the heat transfer of heat-transfer pipe 80 in the dead band at air supply direction rear, heat exchanger has just been brought into play high heat transfer property.
Such heat exchanger is different with the heat exchanger of prior art, because the turbulent flow that does not have shutter to cause, air stream can not blocked by one section one section ground, has reduced because the pressure loss that friction causes.
The heat exchanger of embodiment 4 disposes heat-transfer pipe 80 by two row, but also can be applicable to the majorities configuration of the above heat-transfer pipe 80 of configuration three row.
The same with the heat exchanger of embodiment 2, plate radiating plate 70 preferably forms alar part 71 and fin 72 with the interval of regulation continuously on the thin plate of aluminium alloy, and cutting is made then.If like this, after forming alar part 71 and fin 72 continuously, plate radiating plate 70 is made in cutting, when having improved manufacturing efficient, can also suppress to produce leftover pieces.Owing to can only make the plate radiating plate of configuration two biographies heat pipes 80 and the plate radiating plate of the multiple row heat-transfer pipe 80 more than configuration three row, just there is no need individually to prepare instruments such as mould by the mode that changes incision.
Aforesaid heat exchanger of the present invention, can be used for air supply velocity is the heat exchanger of low speed, is specially adapted to tubulation plate-fin heat exchangers such as automatic vending machine, commodity display show window.
Claims (1)
1. heat exchanger, this heat exchanger comprise the multi-disc plate radiating plate that is arranged in parallel with predetermined distance and connect this plate radiating plate and in inside by the heat-transfer pipe of refrigerant, refrigerant with carry out heat exchange from the leading edge of the described plate radiating plate air by the mutual space of described plate radiating plate, it is characterized in that
In air supply direction the place ahead of heat-transfer pipe, dig the formation alar part from the plate radiating plate incision, this alar part narrows down gradually from the root forward end, and makes the air that passes through produce longitudinal turbulence,
At the rear of the air supply direction of heat-transfer pipe, form from plate radiating plate and cut the fin of digging,
In the mode of the synchronous rotation composition of the contracted flow composition that flows behind generation and the heat-transfer pipe, set the inclination angle of described fin.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004016271 | 2004-01-23 | ||
| JP2004016271A JP4254556B2 (en) | 2004-01-23 | 2004-01-23 | Heat exchanger |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008101343944A Division CN101334252A (en) | 2004-01-23 | 2005-01-20 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1645028A CN1645028A (en) | 2005-07-27 |
| CN100458345C true CN100458345C (en) | 2009-02-04 |
Family
ID=34879027
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100025245A Active CN100458345C (en) | 2004-01-23 | 2005-01-20 | Heat exchanger |
| CNA2008101343944A Pending CN101334252A (en) | 2004-01-23 | 2005-01-20 | Heat exchanger |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008101343944A Pending CN101334252A (en) | 2004-01-23 | 2005-01-20 | Heat exchanger |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4254556B2 (en) |
| KR (1) | KR100670717B1 (en) |
| CN (2) | CN100458345C (en) |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4775429B2 (en) * | 2008-05-26 | 2011-09-21 | パナソニック株式会社 | Finned tube heat exchanger |
| JP2012007778A (en) * | 2010-06-23 | 2012-01-12 | Komatsu Ltd | Heat exchanger |
| JP5111571B2 (en) * | 2010-08-09 | 2013-01-09 | 三菱電機株式会社 | Fin tube type heat exchanger and refrigeration cycle apparatus using the fin tube type heat exchanger |
| CN102141353B (en) * | 2011-03-25 | 2012-08-15 | 兰州交通大学 | Combined type circular pipe pipe-fin heat exchanger |
| CN102109282A (en) * | 2011-03-25 | 2011-06-29 | 兰州交通大学 | Finned flat tube heat exchanger with four plane vortex generators on each flat tube |
| CN102200405B (en) * | 2011-03-25 | 2012-12-05 | 兰州交通大学 | Combined triangular curved vortex generator type circular tube fin heat exchanger |
| CN102109289B (en) * | 2011-03-25 | 2012-08-15 | 兰州交通大学 | Fin-and-oval tube heat exchanger |
| JP5345189B2 (en) * | 2011-08-26 | 2013-11-20 | 三菱電機株式会社 | Heat exchanger and air conditioner equipped with this heat exchanger |
| CN102878664B (en) * | 2012-10-26 | 2015-02-04 | 湖北靛蓝科技有限公司 | Precise air conditioner for computer room and integral heat exchanger of precise air conditioner |
| CN104265384A (en) * | 2014-08-12 | 2015-01-07 | 东南大学 | Organic Rankine cycle device by adopting longitudinal vortex to overcome non-azeotropic working medium heat transfer deterioration |
| CN105600211B (en) * | 2016-01-15 | 2018-02-06 | 南京北大工道创新有限公司 | A kind of fin-plate type anti-shaking device suitable for motive liquid tank |
| US10378835B2 (en) | 2016-03-25 | 2019-08-13 | Unison Industries, Llc | Heat exchanger with non-orthogonal perforations |
| CN106595368A (en) * | 2016-11-29 | 2017-04-26 | 国电南京自动化股份有限公司 | Finned tube heat exchanger |
| CN107702583A (en) * | 2017-08-14 | 2018-02-16 | 茂名重力石化装备股份公司 | A kind of finned tube with uniform flow lid and there is its heating furnace |
| CN107702579A (en) * | 2017-08-14 | 2018-02-16 | 茂名重力石化装备股份公司 | A kind of studded tube with uniform flow lid and there is its heating furnace |
| KR101912561B1 (en) * | 2018-03-29 | 2018-10-26 | 안희성 | Energy saving drying apparatus having excellent drying efficiency |
| CN110230942A (en) * | 2019-05-29 | 2019-09-13 | 浙江大学衢州研究院 | A kind of Novel triangle fenestration heat exchanger fin |
| CN110230941A (en) * | 2019-05-29 | 2019-09-13 | 浙江大学衢州研究院 | Symmetrical arc fenestration heat exchanger fin |
| TWI801732B (en) * | 2020-04-13 | 2023-05-11 | 國立成功大學 | Heat exchange module and method of heat exchange |
| KR102232484B1 (en) * | 2020-06-26 | 2021-03-26 | 신용준 | heat supply system of laundry dryer and waste heat recovery method using the same |
| CN112066776A (en) * | 2020-08-04 | 2020-12-11 | 西安交通大学 | Bionic slotted corrugated fin for air-conditioning heat exchanger |
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| KR0136066Y1 (en) * | 1995-12-19 | 1999-03-20 | 김광호 | Heat transfer fin for heat exchanger |
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| JP4400244B2 (en) * | 2004-02-19 | 2010-01-20 | 富士電機リテイルシステムズ株式会社 | Heat exchanger |
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- 2004-01-23 JP JP2004016271A patent/JP4254556B2/en not_active Expired - Fee Related
-
2005
- 2005-01-19 KR KR1020050004951A patent/KR100670717B1/en active IP Right Grant
- 2005-01-20 CN CNB2005100025245A patent/CN100458345C/en active Active
- 2005-01-20 CN CNA2008101343944A patent/CN101334252A/en active Pending
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|---|---|---|---|---|
| JPS5575190A (en) * | 1978-12-04 | 1980-06-06 | Matsushita Refrig Co | Heat-exchanger |
| US4787442A (en) * | 1987-12-04 | 1988-11-29 | Carrier Corporation | Delta wing and ramp wing enhanced plate fin |
| JPH11166796A (en) * | 1997-10-03 | 1999-06-22 | Hitachi Ltd | Heat exchanger |
| CN2474980Y (en) * | 2001-02-28 | 2002-01-30 | 天津大学 | Fortified heat transfer or cooling airfoil longitudinal vortex generating element |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4254556B2 (en) | 2009-04-15 |
| JP2005207688A (en) | 2005-08-04 |
| KR100670717B1 (en) | 2007-01-19 |
| KR20050076815A (en) | 2005-07-28 |
| CN101334252A (en) | 2008-12-31 |
| CN1645028A (en) | 2005-07-27 |
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Owner name: FUJI ELECTRIC CO., LTD. Free format text: FORMER OWNER: FUJI ELECTRIC MOTOR RETAILING EQUIPMENT AND SYSTEM CO., LTD. Effective date: 20121218 |
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Effective date of registration: 20121218 Address after: Japan's Kawasaki City Patentee after: Fuji Electric Co., Ltd. Address before: Tokyo, Japan, Japan Patentee before: Fuji Electric Motor Retailing Equipment and System Co., Ltd. |