CN101010555A

CN101010555A - Heat exchanger device

Info

Publication number: CN101010555A
Application number: CNA2005800294930A
Authority: CN
Inventors: 尾崎龙雄
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2004-09-08
Filing date: 2005-09-07
Publication date: 2007-08-01
Also published as: WO2006028253A1; GB2431464A; US20070193730A1; JP2006078035A; DE112005002177T5; GB0703282D0

Abstract

Heat transmission performance of a heat exchanger positioned in the downstream of an airflow is improved by using turbulent flow of a heat exchanger positioned in the upstream of the airflow. A plurality of heat exchangers (10, 20) are arranged in series in an air flowing direction. At least a fin (12) of the heat exchanger (10) in the upstream of the airflow is provided with a colliding wall (12c) which is cut to vertically stand as a turbulent flow forming means to disturb the airflow.

Description

Heat exchanger device

Technical field

The present invention relates to heat exchanger device, wherein, a plurality of heat exchangers are along the airflow direction arranged in series, and it is suitable as a kind of heat exchanger device, wherein, are used for the cold-producing medium heat dissipation device and the radiator tandem layout that is used to cool off vehicle motor of vehicle air conditioning.

Background technology

Attempt to constitute the incision sheet (slit piece) of the section that is staggered arranged in form and by bend improves the fin of conventional heat exchanger with the growth of stirring air-flow and limit temperature boundary layer the coefficient of overall heat transmission is set by being provided with about air-flow, wherein, the upstream side bending of the air-flow of described bend by will cutting sheet is provided with (for example, the referenced patent file 1) by about 90 degree.

[patent document 1] Japanese unexamined patent open (spy opens) No.63-83591.

Incidentally, in the invention described in the patent document 1, the incision sheet forms by the part of cutting and raising plate-shaped fin, and bend is crossed about 90 degree by front end (leading edge) the lateral bending triton of the incision sheet that will be cut and be enhanced and is formed, therefore, there is problem as described below in the mill.

In other words, in the invention described in the patent document 1, the front that all bends cut sheet by bending forms, therefore, bending force in the same direction acts on the plate-shaped fin material in succession, and when bend was formed, fin material was out of shape along a direction in unbalanced mode.

In addition, need the incision sheet be set regularly, yet as mentioned above, in the invention described in the patent document 1, fin material is tending towards concentrating in one direction, therefore, is difficult to reduce the variation of cutting the spacing dimension between the sheet with fixing spacing dimension.So, become big if cut the variation of the spacing dimension between the sheet, then the coefficient of overall heat transmission reduces probably, can not realize required heat exchange performance.

In order to address the above problem, the present inventor has proposed a kind of heat exchanger in Japanese patent application 2004-62236 number patent application, and this heat exchanger has improved heat exchange performance and simple radiating plate shape.

In this application early, increase with the fin that carries out the heat exchange area of heat exchange around the pipe flow air and be set on the outer surface of pipe, wherein, there is fluid to flow through described pipe, and, the impact walls that this fin is provided with pancake flat part and forms by the part at vertical position cutting and raising flat part, and impact walls is provided with a plurality of along airflow direction symmetrically.

Therefore, when impact walls is formed, bending force along the directive effect of cancelling out each other in the power of air-flow upstream side with in the power of airflow downstream side in the plate-shaped fin material.So, when impact walls is formed, can prevent in advance that fin material is out of shape along a direction in unbalanced mode, therefore the change in size of impact walls can be kept little.

Therefore, can improve the productivity ratio (raising speed of production) of the fin of simple shape, the coefficient of overall heat transmission that improves between fin and the air by the turbulence effects of utilizing impact walls to cause is improved heat exchanger effectiveness simultaneously.

Incidentally, above-mentioned application early relates to the improvement of heat transfer property in the single heat exchanger.

Summary of the invention

Therefore, the objective of the invention is to, along in the heat exchanger device of airflow direction arranged in series, the turbulent flow that is positioned at the heat exchanger of air-flow upstream side by utilization forms the heat transfer property that structure is improved the heat exchanger that is positioned at the airflow downstream side at a plurality of heat exchangers.

To achieve these goals, a first aspect of the present invention is a kind of heat exchanger device, in described heat exchanger device, a plurality of heat exchangers (10,20) along the airflow direction arranged in series, it is characterized in that described a plurality of heat exchangers (10,20) comprising: the pipe that fluid flows through respectively (11,12); Be arranged on described pipe (11,21) fin (12 on the outer surface, 22), described fin is used to increase and the heat exchange area that carries out heat exchange around described pipe flow air, and, at described a plurality of heat exchangers (10,20) in, being provided with turbulent flow at the fin (12) of the heat exchanger (10) of air-flow upstream side forms device (12c 12g), is used to stir air-flow.

In view of the above, locate at the fin (12) of the heat exchanger (10) of air-flow upstream side, forms turbulent flow by stirring air-flow, therefore, the coefficient of overall heat transmission of heat exchanger (10) that can be by improvement air-flow upstream side is improved its heat exchange performance.In addition, the influence that forms by the turbulent flow that makes the air-flow upstream side also puts on the heat exchanger (20) of airflow downstream side, can be by also have turbulent flow to form to realize the improvement to the heat exchange performance of the heat exchanger (20) of airflow downstream side in the airflow downstream side.

In a second aspect of the present invention, according to the heat exchanger device of first aspect, at described a plurality of heat exchangers (10,20) in, also being provided with turbulent flow at the fin (22) of the heat exchanger (20) of airflow downstream side forms device (22c, 22g), described turbulent flow forms device and is used to stir air-flow.

In view of the above, except the effect of first aspect, in the fin (22) of the heat exchanger (20) of airflow downstream side, the turbulent flow that has added the heat exchanger (20) of airflow downstream side itself forms action, and thereby can further improve the heat exchange performance of the heat exchanger (20) of airflow downstream side.

According to first or the heat exchanger device of second aspect, in a third aspect of the present invention, the distance (L) between described a plurality of heat exchangers (10,20) is equal to or less than 20mm.

According to the experiment that the present inventor did, find, by according among the Fig. 7 that can describe after a while illustrated like that, should be set at 20mm or littler apart from (L), the influence that can form by the turbulent flow that makes the air-flow upstream side puts on the heat exchanger (20) of airflow downstream side effectively, thereby effectively improves the heat exchange performance of the heat exchanger (20) of airflow downstream side.

According to first to the heat exchanger device of the third aspect any one, in the fourth embodiment of the present invention, described fin (12,22) has right angle impact walls (12c, 22c), described right angle impact walls is by in vertical position cutting and improve pancake flat part (12a, part 22a) and be formed described right angle impact walls (12c, 22c) be provided with a plurality of symmetrically along airflow direction, and (12c 22c) constitutes described turbulent flow and forms device described right angle impact walls.

Rely on this mode, turbulent flow forms device and is specifically constructed by impact walls, and impact walls is by being formed in vertical position cutting and raising fin flat part.

Herein, when the right angle impact walls is formed, by be provided with symmetrically along airflow direction a plurality of right angles impact walls (12c, 22c), bending force along the directive effect of cancelling out each other in the power of air-flow upstream side with in the power of airflow downstream side in the plate-shaped fin material.Therefore, when impact walls is formed, can prevent in advance that fin material is out of shape along a direction in unbalanced mode, and thereby the variation of impact walls size can be kept little.

According to first to the heat exchanger device of the third aspect any one, in a fifth aspect of the present invention, described fin (12,22) has V-arrangement impact walls (12g, 22g), described V-arrangement impact walls is passed through pancake flat part (12a, the cutting of 22a) a part also improves the forming V-shape cross section and is formed, described V-arrangement impact walls (12g, 22g) be configured to make the formation direction in V-arrangement cross section alternately to reverse along airflow direction, and (12g 22g) constitutes described turbulent flow and forms device described V-arrangement impact walls.

Rely on this mode, can also specifically construct turbulent flow by described V-arrangement impact walls and form device, wherein, described V-arrangement impact walls is by being formed cutting of fin plat part and raising forming V-shape cross section.

Then, by described V-arrangement impact walls being arranged to make the formation direction in V-arrangement cross section alternately reverse along airflow direction, the bending stress of fin material when cutting and raising formation is cancelled, and can avoid residual stress to take place along a specific direction in fin.

Therefore, (12g when 22g) being formed, can prevent in advance that fin material is out of shape along a direction in unbalanced mode, and thereby can (12g, 22g) variation of size keeps for a short time with the V-arrangement impact walls when described V-arrangement impact walls.

According in the heat exchanger device of first to the 5th aspect any one, in a sixth aspect of the present invention, at described a plurality of heat exchangers (10,20) in, heat exchanger at the air-flow upstream side is the cold-producing medium heat dissipation device (10) that is used for vehicle air conditioning, and is the radiator (20) that is used to cool off vehicle motor at the heat exchanger of airflow downstream side.

In view of the above, the turbulent flow formation by air-flow in the cold-producing medium heat dissipation device (10) of air-flow upstream side can improve the heat exchange performance (heat dissipation performance) at the radiator (20) of airflow downstream side effectively.

Incidentally, be attached to specifically install among symbolic representation and the embodiment that will describe after a while in the bracket of above-mentioned each device corresponding.

By the description of the preferred embodiment of the present invention in conjunction with the accompanying drawings that proposes below, can understand the present invention more fully.

Description of drawings

Figure 1A is a schematic cross sectional views, shows that heat exchanger device according to the first embodiment of the present invention is installed in the state on the vehicle.

Figure 1B is the part section of the core of heat exchanger device among Figure 1A.

Fig. 2 is the front view according to the heat exchanger of first embodiment.

Fig. 3 A is the fragmentary, perspective view according to the core of the heat exchanger of the first embodiment of the present invention.

Fig. 3 B is the cutaway view of obtaining along the line A-A among Fig. 3 A.

Fig. 4 is a cutaway view, and demonstration is according to another embodiment of the impact walls of the fin of first embodiment.

Fig. 5 is the amplification view of fin portions, the definition that it is used to that cutting is described and improves the spacing dimension P of height H and L shaped cross-section.

Fig. 6 is the key diagram of air-flow in the different heat exchanger devices arranged of cold-producing medium heat dissipation device and radiator tandem wherein.

Fig. 7 is the figure of the heat dissipation PR of radiator.

Fig. 8 is the figure of the total air flow Resistance Ratio of cold-producing medium heat dissipation device and radiator.

Fig. 9 A is the fragmentary, perspective view of core of the heat exchanger of a third embodiment in accordance with the invention.

Fig. 9 B is the cutaway view of obtaining along the line B-B among Fig. 9 A.

The specific embodiment

(first embodiment)

Figure 1A to Fig. 5 and Fig. 6 (a) show the first embodiment of the present invention, and present embodiment relates to the heat exchanger for vehicle device, wherein, are used for the cold-producing medium heat dissipation device of vehicle air conditioning and are used to cool off the radiator of vehicle motor by arranged in series.

Figure 1A is for showing that this heat exchanger for vehicle device is installed on the vehicle according to the figure of the heat exchanger for vehicle device of present embodiment, and Figure 1B is the partial sectional view of the core of heat exchanger for vehicle device.Be used for the cold-producing medium heat dissipation device 10 of vehicle air conditioning and be used to cool off direction " a " arranged in series of the radiator 20 of vehicle motor about air-flow (cooling air).

Specify the mounting structure of heat exchanger.Be formed with enging cabin 31 30 times at hood of vehicle (vehicle hood) (hood (bonnet)), grill openings 32a and the 32b forefront in enging cabin 31 opens wide.Cold-producing medium heat dissipation device 10 and radiator 20 immediately following position behind grill openings 32a and 32b by arranged in series.Herein, cold-producing medium heat dissipation device 10 is disposed in the upstream side of air-flow, and radiator 20 is disposed in the downstream (at the rear side of vehicle) of cold-producing medium heat dissipation device 10.

In the downstream of radiator 20, the cooling fan of being made up of tube-axial fan 22 is arranged by guard shield (shroud) 21.This cooling fan 22 is an electric fan, and it rotates and drive tube-axial fan by motor 22a.

In the downstream of cooling fan 22 (at the rear side of vehicle), the travel engine (internal combustion engine) 33 of usefulness of vehicle is installed.This vehicle motor 33 is a water-cooling type, and the cooling water of vehicle motor 33 is cooled by being cycled through radiator 20 by unshowned water pump.

In addition, cold-producing medium heat dissipation device 10 is connected to the compressor discharge side of unshowned vehicle air conditioning kind of refrigeration cycle, and is dissipated to air-flow by the heat with compressor discharge cold-producing medium (high-pressure side cold-producing medium) and comes the cooling refrigeration agent.In the kind of refrigeration cycle of using common CFC (freon) (registration mark) cold-producing medium, the cold-producing medium blowdown presssure of compressor is less than the critical pressure of cold-producing medium, therefore, when cold-producing medium in cold-producing medium heat dissipation device 10 condensation the time, the cold-producing medium heat dissipation.Contrast therewith, in the kind of refrigeration cycle of using as the cold-producing medium of carbon dioxide (CO2) etc. and so on, the cold-producing medium blowdown presssure of compressor becomes and is equal to or greater than the critical pressure of cold-producing medium, therefore, cold-producing medium is not having heat dissipation under the situation of condensation in cold-producing medium heat dissipation device 10, under supercriticality.

The reason that radiator 20 is disposed in the downstream of cold-producing medium heat dissipation device 10 is in order to remain in the cold-producing medium heat dissipation device 10 and the temperature contrast of the air in radiator 20.In other words, in the ongoing operation state of vehicle motor 33, the temperature of engine cooling water becomes than the temperature height of cold-producing medium in the cold-producing medium heat dissipation device 10 in the radiator 20, therefore, in order to remain in the cold-producing medium heat dissipation device 10 and the temperature contrast of the air in radiator 20, the downstream that radiator 20 is arranged in cold-producing medium heat dissipation device 10 is favourable.

Fig. 2 illustrates the concrete structure of cold-producing medium heat dissipation device 10, and wherein, a plurality of pipes 11 that cold-producing medium flows through wherein are arranged in parallel with predetermined space, and are provided with fin 12 between a plurality of pipes 11.Fin 12 is engaged to pipe 11 outer surface, with by increasing and the heat transfer area of air promotes heat exchange between cold-producing medium and the air.

Pipe 11 two ends longitudinally are provided with upper water box (header tank) 13 and 14.Upper water box 13 and 14 along perpendicular to pipe 11 longitudinally direction extend, and be communicated with refrigerant path in each pipe 11.Then, along being furnished with the side plate 15 and 16 that constitutes reinforcement on the two ends of pipe and fin stacked direction (along the vertical direction among Fig. 2), wherein, core is made up of pipe 11, fin 12 etc. at core.

Incidentally, in the present embodiment, all pipes 11, fin 12, upper water box 13 and 14 and side plate 15 and 16 form by the good aluminium alloy of thermal conductivity, and these hardwares 11 to 16 are joined together by soldering becomes a unit.

Shown in Figure 1B and Fig. 3 A or Fig. 3 B, the pipe 11 of cold-producing medium heat dissipation device 10 is pancake antipriming pipe, and it forms by squeeze job or stretching operation, and wherein, a plurality of refrigerant path hole 11a is formed by parallel connection.The flat pattern of pipe 11 is parallel to airflow direction " a ".

In addition, shown in Fig. 3 A or Fig. 3 B, fin 12 is the ripple type fin, it is formed by being bent to waveform, thereby fin 12 has bend 12b and adjacent flat board 12a thereof, wherein, bend 12b is bent to connect pancake flat part 12a.In the present embodiment, by being used roll forming method (roller forming method), the thin-sheet metal material forms corrugated ripple type fin 12.Shown in Fig. 3 A or Fig. 3 B, the bend 12b of fin 12 contacts and is brazed to this pancake portion with the pancake portion (planar portions) of pipe 11.

Then, on the flat part 12a of fin 12, be provided with a plurality of impact walls 12c, the part that described a plurality of impact walls 12c have a flat part 12a is cut and improves the shape that forms at vertical position.Here, specifically be meant the part of cutting and improving flat part 12a in vertical position cutting and raising, so that its surface about flat part 12a meets at right angles, yet, impact walls 12c is cut and the angle that improves can promptly increase or reduce a low-angle by 90 degree near 90 degree.

Along fin 12, be that the surperficial flow air of flat part 12a is caused and impact walls 12 collisions, thereby stir along the air-flow on the surface of flat part 12a, increased the coefficient of overall heat transmission between fin 12 and the air.

Here, in the flat part 12a of fin 12, the flat part that is connected to impact walls 12c root is known as and cuts sheet 12d.Cut sheet 12d and impact walls 12c and form L shaped cross section.Then, this L shaped cross section is arranged to become symmetric relation about the imaginary plane M perpendicular to flat part 12a between air-flow upstream side and the airflow downstream side.

Specifically, when flat part 12a when airflow direction is divided into upstream side and downstream by imaginary plane M two, the quantity of the impact walls 12c that equals in the downstream in the quantity of the impact walls 12c of upstream side, and, at the upstream side of air-flow, the airflow downstream side of cutting part 12s is cut and improves at vertical position, simultaneously, in the downstream of air-flow, the air-flow upstream side that cuts part 12d is cut and improves at vertical position.

Incidentally, the essential structure that is used for the cold-producing medium heat dissipation device 10 of vehicle air conditioning can be identical with the radiator 20 that is used to cool off vehicle motor, therefore, in Fig. 2, Fig. 3 A and Fig. 3 B, the symbol of composition member that is used to cool off the radiator 20 of vehicle motor is written in the bracket of the symbol that is attached to cold-producing medium heat dissipation device 10 counterpart member, and, the specifying of radiator 20 that is used to cool off vehicle motor is omitted.

Yet, it is much lower that the pressure ratio that cycles through the engine cooling water of the radiator 20 that is used for cooling off vehicle motor is used for the refrigerant pressure of cold-producing medium heat dissipation device 10 of vehicle air conditioning, therefore, needn't as the pipe 11 that requires cold-producing medium heat dissipation device 10, increase the compression strength of the pipe 21 of radiator 20.For this reason, the pipe 21 of radiator 20 has the only simple pancake portion in a cooling water path of formation, shown in Figure 1B.

In the present embodiment, impact walls 22c and incision part 22d also are formed on the fin 22 of the radiator 20 that is positioned at the airflow downstream side, and the fin 12 that impact walls 22c and incision part 22d are similar to the cold-producing medium heat dissipation device 10 shown in Fig. 3 A or Fig. 3 B constitutes L shaped cross section.

Incidentally, the L shaped cross section that is formed by incision part 12d and impact walls 12c is not limited in the shape shown in Fig. 3 A and Fig. 3 B, contrast therewith, as shown in Figure 4, also can form

impact walls

12c and 22c at the air-flow upstream side that cuts

part

12d and 22d in the air-flow upstream side zone of

fin

12 and 22, and, on the other hand,

form impact walls

12c and 22c in the airflow downstream side of cutting

part

12d and 22d in territory, airflow downstream lateral areas.

Desired be arranged in

symmetrically fin

12 and 22 air-flow upstream side

zone impact walls

12c, 22d and at impact walls 12c, the 22c in territory, airflow downstream lateral areas.

The concrete example of the size of

fin

12,12 then is described.As mentioned above,

fin

12,22 is corrugated fin, it is formed by connecting adjacent

flat board

12a, 22a with

bend

12b, 22b and being bent to waveform, and, shown in Fig. 3 B, the inter fin space Pf of

corrugated fin

12,22 is twices of distance between adjacent flat board 12a, the 22a, and inter fin space Pf is for example 2.5mm.

The thickness of slab t (with reference to Fig. 5) of

corrugated fin

12,22 is for example 0.05mm, and the height H of

impact walls

12c, 22c (with reference to Fig. 5) is for example 0.3mm, and the spacing P of L shaped cross-section is for example 0.5mm.

In addition, preferably be set equal to or less than the short distance of 20mm, and more specifically, preferably this distance L=about 5mm along the distance L (with reference to Figure 1B and Fig. 6) between tandem two

heat exchangers

10,20 of airflow direction.

The function and the effect of present embodiment then are described.Fig. 6 (a) shows the air-flow of the cold-producing medium heat dissipation device 10 that is arranged in the air-flow upstream side in the present embodiment and is arranged in the air-flow of the radiator 20 of airflow downstream side.Incidentally, in Fig. 6 (a), identical among the layout of impact walls 12c, the 22c on the

fin

12,22 and

incision part

12d, 22d structure and Fig. 4.

In cold-producing medium heat dissipation device 10, upstream side zone at air-flow, because impact walls 12c has small size, so the air that has entered passes through when keeping being close to laminar condition, yet, along with air-flow near the downstream, impact walls 12c increases on amplitude gradually to the stirring effect of air-flow.For this reason, in the territory, airflow downstream lateral areas of cold-producing medium heat dissipation device 10, shown in Fig. 6 (a), air-flow enters turbulence state, and the coefficient of overall heat transmission of air side can be improved.

Here, owing to be set equal to or less than the short distance of 20mm along the distance L between tandem two

heat exchangers

10,20 of airflow direction, so, also can form the turbulence state of air-flow in the upstream side zone of radiator 20 by putting on the air-flow upstream side zone of radiator 20 in the influence of the turbulence state in the territory, airflow downstream lateral areas of cold-producing medium heat dissipation device 10.α portion among Fig. 6 (a) shows the coverage of the turbulence state in the cold-producing medium heat dissipation device 10.

By more than, can therefore, can effectively improve the heat dissipation performance of radiator 20 sides at the air-flow upstream side in the radiator 20 side fin 22 zone and zone, downstream formation turbulence state.

In the present embodiment,

impact walls

12c, 22c and

impact walls

12c, 22c in the downstream at upstream side are configured to along airflow direction symmetrical, therefore, when carrying out fin formation technology, direction is set to the bending force of cancelling out each other and acts on the plate-shaped fin material.

Therefore, can when forming

impact walls

12c, 22c, prevent that in advance fin material is out of shape along a direction in unbalanced mode, and the variation that will cut

part

12d, 22d and

impact walls

12c, 22c size keeps for a short time.

As a result, can improve the productivity ratio of the

fin

12,22 with simple shape, the turbulence effects that causes by

use impact walls

12c, 22c increases the coefficient of overall heat transmission between air and the

fin

12,22 simultaneously, thereby improves heat exchanger effectiveness.

(second embodiment)

Fig. 6 (b) shows second embodiment, wherein, the structure of fin 12 of cold-producing medium heat dissipation device 10 that is positioned at the air-flow upstream side is with first embodiment, and, relative therewith, the structure of fin 22 of radiator 20 that is positioned at the airflow downstream side is with prior art shown in Fig. 6 (c).

In other words, on the fin 22 of radiator 20 in a second embodiment, impact walls 22c not forming in first embodiment, but formed inclination shutter board 22f, be formed by cutting and improve by predetermined angular like that in the prior art shown in inclination shutter board 22f image pattern 6 (c) in obliquity.The cutting of the inclination shutter board 22f of air-flow upstream side and raising direction are opposite with the raising direction with the cutting of the inclination shutter board 22f of airflow downstream side.

According to second embodiment, the fin 22 of radiator 20 itself does not comprise the formation device, yet, the influence of the turbulence state in the territory, airflow downstream lateral areas of cold-producing medium heat dissipation device 10 also can be put on the air-flow upstream side zone of radiator 20.Therefore, as shown in the α portion of Fig. 6 (b), also can form the turbulence state of air-flow in the upstream side zone of radiator 20.

Therefore,, the coefficient of overall heat transmission can be improved, therefore, the heat dissipation performance of radiator 20 sides can be improved by also forming turbulent air flow in radiator 20 sides.

Incidentally, prior art shown in Fig. 6 (c) is a typical technology, this technology is by commercialization, wherein, by in obliquity by predetermined angular cutting with improve on the inclination shutter board 12f that is formed, the fin 12 that 22f is formed on cold-producing medium heat dissipation device 10 and on the fin 22 of radiator 20.In the prior art, air, therefore, can not form turbulent flow by

impact walls

12c, 22c and improve the heat dissipation performance as in first, second embodiment by between the shutter board 12f (22f) with laminar condition.

In addition, Fig. 6 (d) shows comparative example of the present invention, wherein, only on the fin 22 of the radiator 20 of downwind side (along the downstream of airflow direction) in the vertical position cutting and improve impact walls 22c.In this comparative example, in the fin 12 of the cold-producing medium heat dissipation device 10 of the side of being in the wind (along the upstream side of airflow direction), can not form the turbulence state of air-flow, therefore, can not improve heat dissipation performance by the be in the wind turbulence state of air-flows in the cold-producing medium heat dissipation device 10 of side of utilization at the radiator 20 of downwind side.

Then, specify the effect of first embodiment according to the experimental result shown in Fig. 7 and Fig. 8.As the experimental conditions shown in Fig. 7 and Fig. 8, the example of size of

fin

12 and 22 each several part is with above-mentioned measure-alike among first embodiment.In other words, fin thickness of slab t=0.05mm, inter fin space Pf=2.5mm, height H=0.3mm of

impact walls

12c, 22c, and, the spacing P=0.5mm of L shaped cross-section.

Then, the temperature of supposing the porch is 25 ℃ (room temperatures), the temperature of the cooling water of radiator 20 porch is 80 ℃, the flow velocity of cooling air is 4m/s, and, the flow rate that is used to be circulated to the cooling water of radiator 20 is 40L/min, and, set such state: the heat dissipation that the side of wherein being in the wind does not have cold-producing medium heat dissipation device 10 to cause, then, according to the heat dissipation performance (KW) of the radiator 20 of first embodiment and measured according to the heat dissipation performance (KW) of the radiator 20 of the prior art shown in Fig. 6 (c), and, shown in Figure 7 according to the heat dissipation performance of the radiator 20 of first embodiment with respect to ratio (%) according to the heat dissipation performance of the radiator 20 of prior art, wherein, be assumed to be 100% according to the heat dissipation performance of the radiator 20 of prior art.

Incidentally, much less, be configured to identical size with main body according to the core of the radiator 20 of prior art according to the main body of the core of the radiator 20 of first embodiment.

Rely on radiator 20 according to first embodiment, if distance L is reduced to about 20mm, then can be with the heat dissipation improvement in performance to compared with prior art being approximately 102%.

Then, confirm,, then the heat dissipation improvement in performance of radiator 20 extremely compared with prior art can be approximately 104% if distance L is reduced to about 5mm.

Then, Fig. 8 shows the influence according to the gas-flow resistance of first embodiment.According to the total air flow resistance (Pa) of the cold-producing medium heat dissipation device 10 of first embodiment and radiator 20 with measured according to the total air flow resistance (Pa) of the cold-producing medium heat dissipation device 10 of prior art and radiator 20, and, shown in Figure 8 according to the total air flow resistance of first embodiment with respect to ratio (%) according to the total air flow resistance of prior art, wherein, the total air flow resistance according to prior art is assumed that 100%.

According to first embodiment, if distance L is reduced to 20mm or littler, owing to form turbulent flow in the air-flow by forming turbulent flow in the air-flow in the cold-producing medium heat dissipation device 10 of the side of being in the wind in the radiator 20 of downwind side, so gas-flow resistance increases, yet, increase degree compared with prior art is very little, therefore has practical problem hardly.

Incidentally, although be not shown schematically in the heat dissipation PR under the situation of second embodiment among Fig. 7, the fin 22 of radiator 20 does not comprise that turbulent flow forms device in a second embodiment, therefore, the improvement ratio of the heat dissipation performance of radiator 20 becomes littler than first embodiment, yet, according to the experiment that the present inventor did, confirm, if distance L is reduced to about 5mm, then also the heat dissipation improvement in performance of radiator 20 extremely compared with prior art can be approximately 102% in a second embodiment.

Incidentally, according to the experiment that the present inventor did, as fin 12 with right

angle impact walls

12c, 22c and 22 size range, improvement, the formability of fin, fin intensity equal angles from heat exchanger performance, be preferably fin thickness of slab t=0.01 to 0.1mm, the height H of

impact walls

12c, 22c=0.1 is to 0.5mm, and the spacing P of L shaped cross-section is in the scope between about 1.5 times to 5 times of height H.

(the 3rd embodiment)

In first embodiment, form device as the turbulent flow in cold-producing medium heat dissipation device 10 and the radiator 20,

impact walls

12c, 22c are formed on apart from the flat part 12a of

fin

12,22, the vertical position of 22a, and, in a second embodiment, form device as the turbulent flow in the cold-producing medium heat dissipation device 10, impact walls (impact portions) 12c is formed on apart from the vertical position of the flat part 12a of fin 12, yet, in the 3rd embodiment, the impact walls with V-arrangement cross section forms device as turbulent flow and is formed on the

fin

12,22.

In other words, Fig. 9 A and Fig. 9 B show the structure according to the

fin

12,22 of the 3rd embodiment, wherein, V-arrangement impact walls 12g (22g) is formed on flat part 12a, the 22a of

fin

12 and 22, and the V-arrangement cross-section of V-arrangement impact walls 12g (22g) is extended along the direction perpendicular to airflow direction a.V-arrangement impact walls 12g (22g) can form by cutting and improve with roll former (roller forming machine) etc., and it is by collision and stir air-flow and form turbulent flow.

Specify the geometry of V-arrangement impact walls 12g (22g) below.V-arrangement impact walls 12g (22g) is formed the formation direction that makes the V-arrangement cross section and reverses along airflow direction " a " is alternately vertical.

Herein, the tip position in V-arrangement cross section is near

flat part

12a, 22a, and the forked end portion in V-arrangement cross section is positioned at the side away from

flat part

12a, 22a.

Such V-arrangement impact walls 12g (22g) is staggered mode about

flat part

12a, 22a (in other words, the fin material surface S in cutting and before improving shaping) and arranges, so that

flat part

12a, 22a are clipped in the middle.

According to the 3rd embodiment, air-flow and V-arrangement impact walls 12g (22g) collision are also stirred, then formed air stream turbulence, thereby can improve the coefficient of overall heat transmission of

fin

12,22 by forming turbulent flow.

Then, by forming V-arrangement impact walls 12g on the fin 12 of the side cold-producing medium heat dissipation device 10 of being in the wind and by in the downstream area of fin 12, forming air stream turbulence, can in the upstream region of the fin 22 of downwind side radiator 20, form air stream turbulence.For this reason, so in the 3rd embodiment, also can as in first, second embodiment, improve heat dissipation performance effectively at the radiator 20 of downwind side.

In addition, in the 3rd embodiment, as shown in Fig. 9 B, V-

arrangement impact walls

12g, 22g on the upstream portion and V-arrangement impact walls 12g, the 22g on the downstream portion form about imaginary plane M symmetrically along airflow direction " a " equally.Then, the formation direction in V-arrangement cross section reverses along airflow direction " a " is alternately vertical, therefore, in the cutting of fin material with improve the bending force that produces when being shaped and be cancelled, and can prevent to stay in the fin along the residual stress of a concrete direction.

Therefore,, can prevent in advance that fin material is out of shape towards a side, therefore can keep the change in size of V-

arrangement impact walls

12g, 22g little as V-arrangement impact walls 12g, when 22g is formed.

In addition, in V-arrangement, the various piece itself of V-

arrangement impact walls

12g, 22g is symmetrical, and therefore, the quantity of V-

arrangement impact walls

12g, 22g can be odd number or even number.

(other embodiment)

In the above-described embodiments, the heat exchanger for vehicle device of cold-producing medium heat dissipation device 10 and radiator 10 arranged in series has been described, yet, the present invention can be widely used in various uses, and be not limited in vehicular applications, as long as a plurality of heat exchangers are arranged in heat exchanger device along the airflow direction arranged in series.

Although reference has been described the present invention for the selected specific embodiment of explanation, yet those skilled in the art obviously can make many modifications to the present invention under the situation that does not break away from basic conception of the present invention and scope.

Claims

1. heat exchanger device, in described heat exchanger device, a plurality of heat exchangers (10,20) are along the airflow direction arranged in series, wherein:

Described a plurality of heat exchanger (10,20) comprising: fluid flows through pipe (11,12) wherein respectively; With the fin (12,22) on the outer surface that is arranged on described pipe (11,21), described fin is used for increasing and the heat exchange area that carries out heat exchange around described pipe (11,21) flow air; And

In described a plurality of heat exchangers (10,20), be provided with turbulent flow at the fin (12) of the heat exchanger (10) of air-flow upstream side and form device (12c 12g), is used to stir air-flow.

2. heat exchanger device as claimed in claim 1 wherein, in described a plurality of heat exchangers (10,20), also is provided with turbulent flow at the fin (22) of the heat exchanger (20) of airflow downstream side and forms device (22c 22g), is used to stir air-flow.

3. heat exchanger device as claimed in claim 1 or 2, wherein, the distance (L) between described a plurality of heat exchangers (10,20) is equal to or less than 20mm.

4. as any described heat exchanger device in the claim 1 to 3, wherein:

Described fin (12,22) have the right angle impact walls (12c, 22c), described right angle impact walls is by in vertical position cutting and improve pancake flat part (12a, part 22a) and being formed;

(12c 22c) is provided with a plurality of along airflow direction described right angle impact walls symmetrically; And

(12c 22c) constitutes described turbulent flow and forms device described right angle impact walls.

5. as any described heat exchanger device in the claim 1 to 3, wherein:

Described fin (12,22) have the V-arrangement impact walls (12g, 22g), described V-arrangement impact walls by with pancake flat part (12a, the cutting of 22a) a part also improves the forming V-shape cross section and is formed;

(12g 22g) is configured to make the formation direction in V-arrangement cross section alternately to reverse along airflow direction to described V-arrangement impact walls; And

(12g 22g) constitutes described turbulent flow and forms device described V-arrangement impact walls.

6. as any described heat exchanger device in the claim 1 to 5, wherein, at described a plurality of heat exchangers (10,20) in, heat exchanger at the air-flow upstream side is the cold-producing medium heat dissipation device (10) that is used for vehicle air conditioning, and is the radiator (20) that is used to cool off vehicle motor at the heat exchanger of airflow downstream side.