CN1149380C - Heat-exchanger - Google Patents

Abstract

This invention provides a heat exchanger to integrate with a core of different type while preventing an increase in the size of a heat exchanger and the decrease in the heat exchanging efficiency. In the heat exchanger, both cooling fins are spaced at a predetermined interval, and a plurality of coupling parts for partly coupling the fins are provided. When the first and second cooling fins are unfolded, the length E of each the connecting portion in parallel with the longitudinal direction of the first and second cooling fins is equal to 5% or less of the length F between the adjacent connecting portions. Further, the first cooling fin is projected from the condenser tube toward the radiator tube side with a projection length Lc being in a range of 1.7 to 7.0 mm.

Description

Heat exchanger

The present invention relates to a kind of heat exchanger that the core (heat exchange department) with xenogenesis is combined into one, especially a kind of heat exchanger that combines with the condenser of air conditioner for vehicles about the radiator of the engine of the drive source of vehicle.

Past, after vehicle is made, for example peddle in the shop at vehicle, air conditioner for vehicles is assembled on the vehicle.Yet, in recent years, owing to the air conditioner for vehicles study plot is equipped on the vehicle, so in the vehicle assembling procedure, air conditioner for vehicles has been assembled on the vehicle with vehicle part.

In the past, the multiple heat exchanger that xenogenesis cores such as radiator and condenser are combined into one has been proposed.In this heat exchanger,, thereby seek the miniaturization of combination and the attenuating of assembling procedure with the condenser combination of the radiator and the air conditioner for vehicles of vehicle part.

Yet, because the core of xenogenesis is combined, so the heat conduction takes place by the part that is combined into one, thus the problem that the heat exchanger effectiveness of the core that existence heat is transmitted to reduces.That is, when radiator and condenser were combined into one, the heat of radiator was conducted on the condenser, so cause the problem that the heat exchanger effectiveness of condenser reduces.

For example, in the flat 3-177795 communique of Japanese Patent Application Laid-Open, means as the control amount of thermal conduction, the cold sink of the 1st core and the 2nd core is combined into one, and be provided with slot-shaped gap on the short transverse of this cold sink that is combined into one, form heat conducting road agley, thereby enlarged heat conducting road.

Yet, in above-mentioned heat exchanger, controlled from the heat of radiator, yet its method can not fully be interdicted the heat conduction to the condenser conduction thereby hot conducting pathway is enlarged.Therefore, in this heat exchanger,, must consider the reduction of rate of heat exchange earlier in order in the condenser core, to guarantee desired heat exchange amount, thus the volume of decision condenser core.

That is, when design uses the core of xenogenesis to form the heat exchanger of one, at first consider the reduction of the heat exchanger effectiveness in the hot core (condenser core) that is transmitted to, thereby enlarge the volume of the hot core (condenser core) that is transmitted to.

Yet, only merely enlarge the volume of core, integrally combine and form the initial purpose of small-sized heat exchanger thereby can not reach core with xenogenesis.

In view of above-mentioned existing issue, the purpose of this invention is to provide the heat exchanger that a kind of core with xenogenesis forms one, it can prevent the increase of volume of heat exchanger and the reduction of rate of heat exchange.

To achieve the above object, the present invention adopts following technical scheme.

In the present invention, be provided with a plurality of joint portions of certain compartment of terrain in conjunction with the end of facing the 1st cold sink side in the end of the end of facing the 2nd cold sink side in the end of the 1st cold sink and the 2nd cold sink.A plurality of bending parts in the bending part of cold sink are formed between another joint portion of joint portion in a plurality of joint portions and adjacency.Therefore, can reduce the summation that is equivalent to the basal area of a plurality of joint portions of the basal area of hot conducting pathway between two cold sinks.Its result can reduce the amount of thermal conduction between two cold sinks, thereby can interdict the heat conduction between two cold sinks effectively.

In addition, in the present embodiment, dwindle the basal area of hot conducting pathway, thereby interdicted heat conduction between two cold sinks.Therefore, it enlarges the heat conducting heat exchanger that hot conducting pathway interdicts between two cold sinks with passing through in the past compares, and can control the expansion of the size between two cold sinks.Its result can control the increase of the volume of heat exchanger in the present embodiment, and can interdict the heat exchange between two cold sinks effectively.

In the present invention, slot-shaped many interspaces are formed in the cold sink, and a gap intersects a plurality of bending parts.In addition, the joint portion is formed on the planar portions of the 1st and the 2nd liang of cold sink.Therefore, the heat of more effectively interdicting between two cold sinks is conducted.Under the two cold sink states of expansion, the parallel position of the length direction with two cold sinks in described joint portion is of a size of E, when being of a size of F between two of every adjacency joint portions in a plurality of joint portions, size E is below 5% of size F, thereby the deterioration amount of the 1st cold sink can be controlled to below 2%.Yet the 1st cold sink has been given prominence to from the 1st pipeline to the 2nd pipeline, and the outstanding size of the 1st cold sink is in 1.7～7mm scope, so the increment rate of the thermal discharge in the condenser core is roughly 2%.Thereby, use the outstanding of cold sink, offset the deterioration amount of the 1st cold sink.Therefore, the outstanding size Lc by suitably selecting the 1st cold sink and in conjunction with than E/F, outstanding with cold sink offset the deterioration amount of condenser.

In the present invention, the 2nd cold sink has been given prominence to from the 2nd pipeline to the 1st pipeline, and outstanding size Lr is not more than 5mm.Therefore, can prevent the increase of volume of heat exchanger and the reduction of heat exchanger effectiveness.In addition, owing to formed two cold sinks with the joint portion, thus can reduce the manufacturing cost of two cold sinks, thus the manufacturing cost of heat exchanger can be reduced.

In the present invention, distance member is arranged on the end of two cold sinks.Use this distance member, the air of circuitous described the 1st core can not pass through the gap between the 1st cold sink and the 2nd cold sink, thereby can access the pipeline effect.

In the present invention, the distance between two cold sinks (Ls) is not more than 5mm.Therefore, the air opposing increases, and can access the pipeline effect.

The simple declaration of accompanying drawing:

Fig. 1 is the oblique view of the heat exchanger core (the B-B section of Fig. 2) of expression the present invention the 1st embodiment;

Fig. 2 is the oblique view that the A arrow from Fig. 1 obtains;

Fig. 3 is the oblique view that the C arrow from Fig. 2 obtains;

Fig. 4 is the coordinate diagram of relation of the outstanding size of the increment rate of thermal discharge of the cold sink in the expression condenser core and cold sink;

Fig. 5 is expression by the coordinate diagram of the relation of the outstanding size of the increment rate of the ventilation opposing of the air of the cold sink in the condenser core and cold sink;

Fig. 6 represent to consider to ventilate coordinate diagram of relation of outstanding size of the increment rate of thermal discharge of cold sink of opposing and cold sink;

Fig. 7 is the oblique view of the shape of expression cold sink;

Fig. 8 is the plane of the deployed condition of expression cold sink;

Fig. 9 be the expression condenser deterioration amount and in conjunction with than the coordinate diagram of relation;

Figure 10 is the coordinate diagram of relation of the outstanding size of the increment rate of thermal discharge of the cold sink in the expression radiator core and cold sink;

Figure 11 represents to consider the coordinate diagram of relation of the outstanding size of the increment rate of thermal discharge of cold sink of the ventilation opposing in the radiator core and cold sink;

Figure 12 is the oblique view of the heat exchanger core (the B-B section that is equivalent to Fig. 2) of expression the present invention the 2nd embodiment;

Figure 13 is the oblique view that expression heat exchanger for vehicle of the present invention is installed in the state on the vehicle;

Figure 14 is the top figure that expression heat exchanger for vehicle of the present invention is installed in the state on the vehicle;

Figure 15 is the sketch of the flow direction of the air of expression when heat exchanger for vehicle is installed on the vehicle;

Figure 16 is the coordinate diagram of the relation between the increment rate of the distance L of expression two pipeline enclosures and the air quantity by the condenser core;

Figure 17 is the coordinate diagram of the relation between the increment rate of heat exchange of expression distance L of two pipeline enclosures and condenser core;

Figure 18 is the plane of deployed condition of the cold sink of other embodiment of expression;

Figure 19 is the plane of deployed condition of the cold sink of other embodiment of expression.

Embodiments of the invention are described below with reference to the accompanying drawings.

(the 1st embodiment)

In the heat exchanger for vehicle of present embodiment, the 1st core is the condenser core that Vehicular air-conditioning apparatus is used, and the 2nd core is the radiator core that engine cool is used.Under general situation, the temperature of the refrigerant that flows in the condenser core is lower than the temperature of the engine cooling water that flows in the radiator core.So the condenser core is arranged on the air upstream side of radiator core, and refrigerant device core and radiator core are set in upright arrangemently on the air-flow direction, and integrally formed heat exchanger is installed on the forefront of engine.Below, the heat exchanger of present embodiment is described with Fig. 1-Fig. 8.

Fig. 1 is 1 a part expanded view (the B-B section of Fig. 2) of the heat exchanger of present embodiment.In Fig. 1,2 expression condenser cores, the core of 3 expression radiators.In order to interdict the heat conduction between two cores 2,3, predetermined gap ground is arranged and on air-flow direction, be provided with two cores 2,3 in upright arrangemently at two pipeline enclosures described later.

Condenser core 2 by the pipeline 21 of the condenser of the path that forms refrigerant of flat and on the pipeline 21 of this condenser the formed undulatory cold sink 22 of a plurality of bending part 22a of soldering constitute.

In addition, radiator core 3 has the structure identical with condenser core 2.This radiator core 3 is made of the pipeline 31 and the cold sink 32 of the radiator that the pipeline 21 to condenser disposes abreast.With these pipelines 21,31 with cold sink 22,23 is alternately stacked and carry out soldering respectively.In order to promote heat exchange, louver 22b, 32b are respectively formed on two cold sinks 22,32, have formed two cold sink 22,32 and this louver 22b, 32b with forming processes such as rolling forming methods.

In conjunction with aspectant end 22d on the direction in the end of two cold sinks 22,32 and length direction right angles two pipelines 21,31, a plurality of joint portions 45 of 32d are formed between two cold sinks 22,32 respectively.As shown in Figure 7, be formed with two cold sinks 22 between joint portion 45 in these a plurality of joint portions 45 and another joint portion of adjacency, 32 a lot of bending part 22a, a plurality of bending part 22a among the 32a, 32a (forming 5-10 bending part in the present embodiment).

As shown in Figure 8, two cold sinks in expanded view 7 22,32 o'clock, joint portion 45 and clearance portion 47 alternately are arranged on the length direction of cooling radiator.In the present embodiment, the parallel position of the length direction with two cold sinks 22,32 in joint portion 45 is of a size of E, and when being of a size of F between two joint portions 45 of every adjacency in most joint portions 45, size E is below 5% of size F.Explain the ratio (following slightly be called in conjunction with than E/F) of size E and size F in the back.

Because the bending part 22a of two cold sinks 22,32,32a contact on two pipelines 21,31, so pine for this bending part 22a, the hot maximum of the last conduction of 32a in 22,32 conduction of two cold sinks.Thereby as Fig. 1, shown in 7, joint portion 45 is preferably formed in the planar portions 22c of two cold sinks 22,32, on the 23c.

In addition, bigger to the amplitude of two cold sinks 22,32 at the length direction right angle of two pipelines 21,31 than the flat amplitude of two pipelines 21,31, so two cold sinks 22,32 all protrude in gap 46 sides (with reference to Fig. 1).Wherein, from condenser tubes 21 to the side-prominent outstanding Lc that is of a size of in gap 46, from the pipeline 31 of radiator to the side-prominent outstanding Lr that is of a size of in gap 46.

23 and 33 expressions form the side plate of the strengthening part of two cores 2,3, and as shown in Figure 2, this side plate 23,33 is configured on the two ends of two cores 2,3.As shown in Figure 1, the section of these side plates 23,33 roughly is the U word shape, has formed this side plate 23,33 with an aluminium sheet.On the two ends of the length direction of biside plate 23,33, be formed with the connecting portion 4 that connects side plate 23 and side plate 33 respectively.On end, thereby the Z bend 42 of the Z bend 41 of connected side plate 23 and side plate 33 has formed this connecting portion 4.Compare with the size of the length direction of side plate 23 or side plate 33, the amplitude of the connecting portion 4 of She Dinging is very little here.In addition, thus on the top ends 43 of this connecting portion 4, be provided with the connecting portion 4 that recess forms thin plate.

As shown in Figure 2, on an end of the radiator core 3 that side plate 33 is not set, disposed the 1st header box 34 of cooling water being distributed to each radiator pipeline 31.The front shape of the 1st header box 34 roughly is a triangle, and the section configuration of the 1st header box 34 is oval, as shown in Figure 3.Be roughly hypotenuse along this, oval major diameter progressively diminishes, and oval major diameter equals oval minor axis (that is circle) on the side of summit.The inflow entrance 35 of the cooling water of inflow in radiator is arranged on the base side roughly triangular in shape.On this inflow entrance 35 soldering do not have the pipe arrangement 35a of pipe arrangement of the cooling water of expression on the connection layout.

In addition, it is identical with the 1st header box 34 to have disposed the shape of the 2nd header box 36, the 2 header boxs 36 that reclaim the cooling water of heat exchange after carrying out on the relative avris of the 1st header box 34.As shown in Figure 2, to the central point of the core 3 of radiator disposed the 1st header box 34 and the 2nd header box.In addition, the outlet 37 of discharge cooling water is arranged on the base side of the 2nd header box 36.With pipeline and cold sink etc., soldering has the pipe arrangement 37a of the pipe arrangement of the cooling water that does not have expression on the hookup on this outlet 37.As shown in Figure 2, the inflow entrance 35 of radiator and outlet 37 are towards the paper side of Fig. 2.

In addition, 24 among Fig. 3 is the 1st header boxs 24 of the refrigerant of condenser being distributed to the pipeline 21 of each condenser, formed the main body of the 1st header box 24 cylindricly.The space that regulation is arranged between the 2nd header box 36 of the 1st header box 24 of condenser and radiator.26a among Fig. 2 is the joint of pipe arrangement that does not have the refrigerant of expression on the hookup, and this joint 26a soldering is on the main body of the 1st header box 24.And the outlet 26 of refrigerant is arranged on this joint 26a.

As shown in Figure 3, the relative avris of the 1st header box 24 of condenser is provided with and reclaims the 2nd header box 25 that the condenser of refrigerant is afterwards carried out in heat exchange, formed the main body of the 2nd header box 25 cylindricly, and the space of regulation has been arranged between the 1st header box 34 of the 2nd header box 25 of condenser and radiator.As shown in Figure 2, there is not the joint 27a soldering of pipe arrangement of refrigerant of expression on the hookup on the main body of the 2nd header box 25.The inflow entrance 27 of refrigerant is arranged on this joint 27a.As shown in Figure 2, the inflow entrance 27 of condenser and outlet 26 are towards the paper side of Fig. 2.

The following describes the outstanding size Lc of two cold sinks 22,32, Lr.

As outstanding size Lc, when Lr increased, the heat release area of two cold sinks 22,32 increased, thereby the thermal discharge of two cold sinks 22,32 also increases.Yet, along with top, the temperature difference between two cold sinks 22,32 and the air is reduced from two pipelines 21,31 near two cold sinks 22,32, so thermal discharge can be according to outstanding size Lc, the ratio of the increase of Lr increases.That is, as shown in Figure 4, in condenser core 2, when the outstanding size Lc of cold sink 22 surpassed 4mm, the increment rate of thermal discharge entered saturation state.As shown in figure 10, in radiator core 3, when the outstanding size Lr of cold sink 32 surpassed 7mm, the increment rate of thermal discharge entered saturation state.

On the other hand, as outstanding size Lc, when Lr increases, as shown in Figure 5, and for outstanding size Lc, Lr, the ventilation of the air by two cores 2,3 is resisted and is increased roughly linearly.

Above-mentioned research is the numeric value analysis result that calculates according to Finite Element under following condition.In being provided with the corrugated cold sink of louver, this condition is as follows, that is: the spacing of louver is 1mm, and the angle of louver is 23 °; The height of cold sink is 8mm, and the gap size of 21,31 formation of two pipelines is 10mm, from condenser core 2 sides with certain wind speed (2m/sec) moving air.

In addition, the invention personnel have studied numeric value analysis under a lot of design conditions beyond the aforementioned calculation condition.Its result, under the gap size L of 4～10mm scope, the size of the thickness of cold sink and height does not influence the increment rate of thermal discharge and the opposing of ventilating, as Fig. 4, shown in 5,10, the increment rate of thermal discharge roughly becomes to give prominence to size Lc with the opposing of ventilating, Lr, function.

When thereby the opposing of ventilating increases air quantity by cold sink and reduces, reduce by the heat of the time per unit of two cores, 2,3 heat releases, so heat exchanger effectiveness reduces.When outstanding size Lc is calculated in the opposing of consider ventilating, during concerning between the increment rate of Lr and thermal discharge, obtain Fig. 6, the result shown in 11.That is, in condenser core 2, when outstanding size Lc is roughly 4mm, the increment rate maximum of thermal discharge.In radiator core 3, when outstanding when being of a size of 5～6mm scope, the increment rate maximum of thermal discharge.

Below, the combination that two cold sinks 22,32 are described is than E/F.

When combination increased than E/F, the connecting portion 4 of two cold sinks 22,32 increased, thus increase from the heat of radiator core 3 to 2 conduction of condenser core, thus make the heat exchanger effectiveness of condenser core 2 worsen (reduction).

The invention personnel have investigated the deterioration amount of the heat exchanger effectiveness in the condenser core 2 and quantitatively in conjunction with than the relation between the E/F.Its result, as shown in Figure 9, along with the increase of combination than E/F, the deterioration amount of the heat exchanger effectiveness in the condenser core 2 increases roughly linearly.When combination was not more than 0.05 than E/F, the deterioration amount of condenser can be controlled to below 2%.In addition, when combination was not more than 0.1 than E/F, the deterioration amount of condenser can be controlled to below 5%.

(two cores 2,3 are state fully independently) heat exchange amount when joint portion 45 not being set, poor between the heat exchange amount when removing the heat exchange amount when joint portion 45 not being set and joint portion 45 being set obtains the deterioration amount of the condenser represented on the ordinate of Fig. 9.

The following describes feature of the present invention.

By joint portion 45, heat is conducted to condenser core 2 from radiator core 3.So as shown in Figure 9, along with in conjunction with than the reducing of E/F, this amount of thermal conduction can reduce.In addition, as shown in Figure 6, the outstanding size Lc with the cold sink 22 of condenser core 2 in prescribed limit increases, thereby can improve the increment rate of the thermal discharge in the condenser core 2.

Therefore, the outstanding size by suitably selecting cold sink 22 and in conjunction with than E/F with the increment rate of the outstanding thermal discharge that causes of cold sink, can be offset the deterioration amount of the condenser that joint portion 45 is set and causes.In the present embodiment, give prominence on 46 sides of the gap of 2,3 of two cores, owing to cold sink 22 so can prevent the increase of the appearance and size of heat exchanger 1.

In the present embodiment, the outstanding size of condenser core 2 is roughly 1.7mm, in conjunction with being roughly 0.05 than E/F.That is, because in conjunction with being roughly 0.05, so the deterioration amount of condenser is roughly 2% than E/F.Yet outstanding size Lc is roughly 0.05, so the increment rate of the thermal discharge in the condenser core 2 is roughly 2%.Thereby, use the outstanding of cold sink 22, offset the deterioration amount of condenser.

According to the thickness of cold sink 22,32, shape and material are formed and louver 22b, factors such as 32b, should suitably select above-mentioned combination than with outstanding size Lc.When in conjunction with than E/F less than 0.05 the time, outstanding size Lc is preferably in 1.7～7mm scope.

Suitably select the size Ls in the gap 47 of two cold sinks 22,32, thereby can interdict the heat conduction between two cold sinks effectively.The size Ls in this gap 47 can be chosen in 0.5mm～2mm scope.In the present embodiment, the size in the gap 47 that two cold sinks are 22,32 is roughly 0.5mm, and the gap size L that two pipelines are 21,31 is roughly 4mm.

In addition, as shown in figure 11, the cold sink 32 of radiator core 3 is also given prominence on condenser core 2 sides, so the thermal discharge in the radiator core 3 also increases.Thereby, can control the increase of the appearance and size of heat exchanger 1, and can increase the thermal discharge in the radiator core 3.In the present embodiment, the outstanding size Lr of cold sink 32 is roughly 1.8mm, thereby can access the increase of 5% thermal discharge.

Suitably select outstanding size Lc respectively, Lr, thus can adjust the heat release ability of condenser core 2 and the heat release ability of radiator core 3 easily.Therefore, can not access desirable heat exchanger by the design alteration of heat exchanger significantly yet.

In addition, joint portion 45 in a plurality of joint portions 45 and 45 of joint portions of beautiful jade of adjacency are formed with a lot of bending part 22a of two cold sinks 22,32, a plurality of bending part 22a among the 32a, 32a (5～10 in the present embodiment).Therefore, can reduce the summation of basal area of a plurality of joint portions 45 of the basal area that is equivalent to 22,32 heat conducting hot conducting pathways of two cold sinks.Its result can reduce the amount of thermal conduction between two cold sinks, thereby can interdict the heat conduction of 22,32 of two cold sinks effectively.

In addition, in the present embodiment, dwindle the basal area of hot conducting pathway, thereby seek 22,32 heat conducting blockings of two cold sinks.Therefore, it and former passing through enlarge hot conducting pathway to be sought the heat exchanger of the heat conducting blocking of 22,32 of two cold sinks and compares, and can control the expansion of the size of 22,32 of two cold sinks.Its result can control the increase of the volume of heat exchanger 1 in the present embodiment, and can interdict the heat exchange of 22,32 of two cold sinks effectively.

In addition, owing to formed two cold sinks 22,32 in the present embodiment, thus can reduce the manufacturing cost of 22,32 of two cold sinks, thus the manufacturing cost of heat exchanger 1 can be reduced.

(the 2nd embodiment)

Consider in the present embodiment to enlarge the vehicle design philosophy in the modern age of car chamber, improved the heat exchanger effectiveness of heat exchanger for vehicle by dwindling engine room.

In the 2nd embodiment, as shown in figure 12,, seal the gap 46 of 2,3 of two cores, thereby increase air quantity by condenser core 2 with the side plate 23,33 (this integrally formed side plate abbreviates side plate (distance member) 50 as) that forms.

Pass through the reason of the air quantity increase of condenser core 2 when the following describes with side plate 50 closing gaps 46.

As noted above, in recent years,, very closely be provided with in-engine each machine in order to seek the miniaturization of engine room, each machine is close to the degree that the maintenance personal can keep in repair.Similarly, radiator core 3 is configured on the position near other machines.

Yet, when radiator core 3 during, cause the delay that the air in the engine room flows, thereby reduce by the air quantity in the radiator core 3 and reduce the heat release ability of radiator core 3 merely near other machine.

In order to ensure the sufficient air quantity in the radiator core 3, as Figure 13, shown in 14, radiator core 3 generally is installed on the front side of vehicle (engine room), simultaneously, be not limited to present embodiment, can be integrated into radiator core 3 ground effectively from the air of vehicle front inflow in engine room and dispose this radiator core 3.

That is, the gap (distance) between vehicle strengthening part such as near go up configuration the radiator core 3 machines except radiator core 3 and the gap (distance) between the radiator core 3 and top strengthening part (top cross member) 100 and bottom strengthening part (bottom cross member) 101 and the radiator core 3 is reduced.Thereby, after the circuitous radiator core 3 of the air in the engine room that vehicle front flows into, can directly not be flowing in the downstream side of air.

Therefore, as shown in figure 15, when flowing into air in engine room the closer to radiator core 3 from vehicle front, air stream concentrates on radiator core 3 more.When condenser core 2 is arranged on the air upstream side of radiator core 3, the air that flows in engine room from vehicle front is split into two air streams, promptly, the air stream of gap 46 inflow radiator cores 3 and the air stream by two cores 2,3 point-blank by 3 of condenser core 2 and radiator cores after the circuitous condenser core 2.

In this case, when the gap 46 between sealing two cores, interdicted circuitous condenser core 2, flowed so air can only pass through condenser core 2 afterwards by the air stream in gap 46.

Therefore, be arranged on the air upstream side of radiator core 3 when condenser core 2 and on the end of two cores 2,3 during closing gap 46, the air quantity of the air quantity by this condenser core 2 when not having closing gap 46 compared, and the air quantity of increase is arranged.The air quantity of this increase is equivalent to the air quantity (effect that this air quantity increases abbreviates the pipeline effect as) of circuitous condenser core 2.

The invention personnel are in order to investigate above-mentioned pipeline effect quantitatively, two cold sinks 22,32 outstanding size Lc, Lr is respectively 0mm and two cores 2,3 distinguish independently in (in conjunction with than E/F=0) heat exchanger for vehicle, tested the relation between the increment rate of the distance L of 21,31 in two pipelines and the air quantity by condenser core 2.This result of the test is illustrated on the coordinate diagram of Figure 16.Air quantity when the average distance L of 21,31 in two pipelines equals 20mm has been represented to pass through the increment rate of the air quantity of condenser core 2 as benchmark with percentage.

In above-mentioned test, imagination the heat exchanger for vehicle of the 2nd embodiment is installed in virtual condition on the vehicle, as shown in figure 15, radiator core 3 is arranged on the air downstream side of condenser core 2, and fin 51 is arranged on the air downstream side of radiator core 3.

In Figure 16, when this distance L of research equals 0 state, can access following conclusion.That is, when distance L equaled 0, two cores 2,3 contacted with each other, thereby the air stream of circuitous condenser core 2 can not take place.That is, when from flow direction two cores of air 2,3 o'clock, it is similar with the state in the gap 46 of 2,3 of sealing two cores that the distance L in the above-mentioned test equals 0 state.Therefore, as shown in figure 16, when distance L is more little, that is, distance L is more near 0 o'clock, and is big more by the air quantity of condenser core 2.Thereby, when sealing the gap 46 of 2,3 of two cores, can access the pipeline effect.

In the heat exchanger for vehicle in the gap 46 of 2,3 of two cores of sealing, the pressure loss during gap 46 by 2,3 of two cores is than very little by 2,3 o'clock the pressure loss of two cores, thereby, can omit the pressure loss when passing through gap 46.That is, on quantitative angle, it is similar with the state in the gap 46 of 2,3 of sealing two cores that the distance L in the above-mentioned test equals 0 state.

Therefore, the outstanding size Lc of two cold sinks 22,32, Lr is respectively 0mm, and, two cores 2,3 are respectively independently in the heat exchanger for vehicle, for example, when distance L equals 20mm, the increment rate of the air quantity that is increased by pipeline efficient is poor between the increment rate of the increment rate of the air quantity of distance L when equaling 0mm and the distance L air quantity when equaling 20mm, that is, and and 20%.

Figure 17 represents the relation between the heat exchange increment rate of distance L in the above-mentioned test and condenser core 2.Similar to Figure 16, in Figure 17, it is similar to the state of closing gap 46 that distance L equals 0 state.Therefore, when distance L is more little, that is, distance L is more near 0 o'clock, and the heat exchanger effectiveness of condenser core 2 is big more.

Here consider that by integrally formed side plate 50, heat is from the conduction of radiator core 3 side direction condenser cores 2 sides, thus the heat exchanger effectiveness of reduction condenser core 2.Yet, the basal area that can conduct heat in the side plate 50 is two header boxs 34 at radiator core 3, near 36 part seldom, and, the part of the conduction heat of this side plate 50 is compared very little with the area of the core of condenser core 2, so can omit the reduction of being conducted the heat exchanger effectiveness that causes by the heat of side plate 50.

Yet, as noted above, with methods such as rolling forming methods, formed two cold sinks 22,32 and louver 22b, 32b.So when combination reduced than E/F, difficulty or ease formed joint portion 45, thereby this can cause increasing of manufacturing cost.Just on the angle of making cold sink, in conjunction with being the bigger the better than E/F.

Yet, as noted above when combination increases than E/F on the other hand, the heat exchange of condenser core 2 is descended.Thereby, in conjunction with preferably more not excessive than E/F.

For example, distance L equals in the heat exchanger for vehicle of 20mm, only use the pipeline effect, make the heat exchange increment rate of condenser core 2 improve 10%, thereby in conjunction with (in conjunction with than E/F=0.24) till the value that can expand the deterioration amount that is equivalent to 10% condenser than E/F to.

In addition, when in conjunction with than E/F less than 0.1 the time, the deterioration amount of condenser is 5% (with reference to Fig. 9).If the increment rate of the heat exchange of rising with the pipeline effect may be thought of as at 10% o'clock, even outstanding size (departure) Lc be-and 1.5mm (outstanding size Lc is-during 1.5mm, the deterioration amount of the thermal discharge of condenser core 2 is 5%, with reference to Fig. 6) also can offset the deterioration amount of the thermal discharge of condenser core 2.

Here said outstanding size (departure) Lc defines in order to the below method.Promptly, when the end of radiator pipeline 31 sides in the condenser tubes 21 be reference position (0) and from condenser tubes 21 when the direction of radiator pipeline 31 sides is positive direction, the position of the end of radiator core 3 sides in the cold sink 22 that this outstanding size Lc is a condenser core 2.That is, outstanding size (departure) Lc=-1.5mm represents that the end of cold sink 22 is located at the state on the air upstream side of end of condenser tubes 21.

Invention personnel comparative studies the manufacturing original cost of the cold sink in the heat exchanger for vehicle of various designs and the heat-exchange capacity of condenser core 2, be to be not more than 0.1 conclusion thereby obtain appropriate combination than E/F.In addition, as described above, consider the raising of the increment rate of the heat exchange that causes by the pipeline effect again, outstanding size (departure) Lc can adopt the scope at-1.5～7mm.

Because the gap between two header boxs 24,25 of condenser core 2 and two header boxs 34,36 of radiator core 3 is very little, so exist hardly by the air quantity of inflow of the gap between header box in the gap 46 of 2,3 of two cores.Thereby, in the 2nd embodiment, do not carried out the special operation of closing gap 46.

Yet, when the gap that two header boxs 24,25 of and condenser core 2 enough big when distance L and two header boxs of radiator core 3 are 34,36 increases, preferably with parts closing gaps 46 such as dividing plates.

(the 3rd embodiment)

In the 3rd embodiment, the size Ls in the gap 47 of 22,32 of two cold sinks is narrowed down to till the suitable value.Therefore, the gap 46 of promptly using side plate 50 or dividing plate described later not to seal 2,3 of two cores also can access the pipeline effect.The following describes the size Ls in gap 47.

That is, along with dwindling of the size Ls in the gap 47 of 22,32 of two cold sinks, the ventilation of flow air opposing increases in the gap 46 that two cores are 2,3.Thereby size Ls is more little, and it is more near the state of closing gap 46.

The invention personnel have comparatively tested when two cold sinks 22, the size Ls in 32 gap 47 is the air quantity of 0 o'clock condenser core 2 by heat exchanger for vehicle and when two cores 2 of this heat exchanger for vehicle of sealing, the air quantity of the condenser core by heat exchanger for vehicle during 3 gap 46, the air quantity that obtains two kinds of situations almost is identical conclusion.Thereby, the size Ls in the gap 47 of 22,32 of two cold sinks is dwindled, can access the pipeline effect.

Obtain to draw a conclusion according to above-mentioned comparative test.That is, be not subjected to the influence of the distance L of 21,31 in two pipelines by the air quantity of condenser core 2, and be subjected to the influence of size Ls in the gap 47 of 22,32 of two cold sinks by the pipeline effect.Thereby at Figure 16, the result of the test shown in 17 can be regarded the relation between the heat exchange increment rate of the size Ls in relation between the increment rate of the size Ls that represents gap 47 and the air quantity by condenser core 2 and gap 47 and condenser core 2 as.

The invention personnel have tested the strong point of the pipeline effect that is caused by the dwindling of size Ls in gap 47 and the weakness that is caused by the increase of the opposing of ventilating, thereby the size Ls that obtains appropriate gap 47 is the conclusion that is not more than 5mm (0＜Ls≤5).If consider the raising of the increment rate of the heat exchange that caused by the pipeline effect, outstanding size (departure) Lc can adopt the scope at-1～7mm.

Yet in the coordinate diagram shown in Figure 11, the heat release ability of radiator core 3 is that the figure and the outstanding size Lr of the chevron shape that changes along with outstanding size Lr has maximum heat release ability when the scope of 5～6mm.Heat release ability when heat release ability when therefore, outstanding size Lr equals 8mm and outstanding size equal 3mm is roughly the same.Thereby in the present embodiment, maximum outstanding size Lr can adopt 8mm.

In addition, as shown in figure 18, make the width of cold sink differently can form the gap 47 of 22,32 of two cold sinks mutually.

In addition, as shown in figure 19, the length direction in gap 47 can favour the length direction of cold sink.

In addition, in the above-described embodiment, 22,32 of cold sinks are given prominence on 46 sides of gap.Yet cold sink 22,32 can be given prominence in the gap 46 opposition side.

In addition, in the 2nd embodiment, sealed gap 46 with integrally formed side plate 50.Yet, separately form after the biside plate 23,33 earlier, can with the dividing plate of closing gap 46 uniformly-spaced member make up biside plate 23,33.In this case, this dividing plate preferably forms with the little parts of pyroconductivities such as resin.

In addition, in side plate 50, the thickness of slab that is equivalent to 46 positions, gap can be thinner than other positions.

In above-mentioned the present invention, describe the present invention in conjunction with wherein specific embodiment.But, only otherwise depart from of the present invention main opinion and the scope that claims propose, to the various corrections of specific embodiment of the present invention with change and obviously can carry out.

Claims (13)

1, a kind of heat exchanger comprises:

For many articles the 1st mobile pipelines of the 1st refrigerant;

Be provided with at described the 1st pipeline enclosure of every adjacency, be formed with undulatory the 1st cold sink of bending part continuously;

Many articles the 2nd pipelines that flow for the 2nd refrigerant are set abreast with described the 1st pipeline;

Be provided with at described the 2nd pipeline enclosure of every adjacency, be formed with undulatory the 2nd cold sink of bending part continuously;

The a plurality of joint portions of the compartment of terrain of regulation in conjunction with the end of facing described the 1st cold sink side in the end of the end of facing described the 2nd cold sink side in the end of described the 1st cold sink and described the 2nd cold sink are arranged;

Wherein, a plurality of bending parts of the described the 1st and the 2nd cold sink are formed between another joint portion of joint portion in described a plurality of joint portion and adjacency;

It is characterized in that,

Launching under the described two cold sink states, the size at the position that the length direction with the described the 1st and the 2nd liang of cold sink in the described joint portion is parallel is not more than 10% of size between two joint portions of every adjacency in the described a plurality of joint portion.

2, according to the heat exchanger of claim 1, it is characterized in that,

Every the described the 1st and the 2nd cold sink has the planar portions that is formed between the adjacent bending part; And

Described joint portion is formed between the described planar portions of the described the 1st and the 2nd liang of cold sink.

3, according to the heat exchanger of claim 1, it is characterized in that,

Launching under the described two cold sink states, the size at the position that the length direction with described two cold sinks in the described joint portion is parallel is not more than 5% of size between two joint portions of every adjacency in the described a plurality of joint portion.

4, according to the heat exchanger of claim 1, it is characterized in that,

Is from described the 1st pipeline 1.7～7.0mm scope to the outstanding size of outstanding described the 1st cold sink of described the 2nd pipe side.

5, according to the heat exchanger of claim 3, it is characterized in that,

Be not more than 5mm from described the 2nd pipeline to the outstanding size of outstanding described the 2nd cold sink of described the 1st pipe side.

6, according to each heat exchanger in the claim 1 to 5, it is characterized in that,

The condenser tubes of the condenser core of the refrigerant that described the 1st pipeline is the condensation air conditioner for vehicles;

Described the 2nd pipeline is the radiator pipeline of radiator core of the cooling water of cooling mobile engine;

Described condenser core is arranged on the air upstream side of described radiator core.

7, a kind of heat exchanger for vehicle, it is arranged on the front side of vehicle, the refrigerant that circulates in the cooling water of cooled engine and the Vehicular air-conditioning apparatus, described heat exchanger for vehicle comprises:

For many articles the 1st mobile pipelines of described refrigerant;

Be provided with at described the 1st pipeline enclosure of every adjacency, contain the 1st core of undulatory the 1st cold sink;

On the air downstream side of described the 1st core, there is predetermined gap ground to be provided with abreast with described the 1st pipeline, for many articles the 2nd pipelines of described flow of cooling water;

Be provided with at described the 2nd pipeline enclosure of every adjacency, contain the 2nd core of undulatory the 2nd cold sink;

There is predetermined gap ground to separate described the 1st cold sink and described the 2nd cold sink, and partly in conjunction with a plurality of joint portions of described the 1st cold sink and described the 2nd cold sink; With

Be arranged on the distance member on the end of described the 1st cold sink and described the 2nd cold sink, wherein,

Use described distance member, the air of circuitous described the 1st core can not be by the gap between described the 1st core and described the 2nd core;

It is characterized in that,

Launching under the described the 1st and the 2nd cold sink state, the size at the position parallel with the described the 1st and the length direction of the 2nd cold sink in the described joint portion is not more than 10% of size between two joint portions of every adjacency in the described a plurality of joint portion.

8, according to the heat exchanger for vehicle of claim 7, it is characterized in that,

Described distance member is made of the side plate of the strengthening part of described the 1st core and described the 2nd core.

9, according to the heat exchanger for vehicle of claim 7, it is characterized in that,

When the end of the described the 1st ducted described the 2nd pipe side is reference position (0) and is positive direction when outstanding from described the 1st pipeline to the direction of described the 2nd pipe side that the end of described the 2nd pipe side in described the 1st cooling radiator is outstanding-1.5～7mm from described reference position.

10, according to each the heat exchanger for vehicle in the claim 7 to 9, it is characterized in that,

Be not more than 8mm from described the 2nd pipeline to the outstanding size of outstanding described the 2nd cold sink of described the 1st pipe side.

11, according to each the heat exchanger for vehicle in the claim 7 to 9, it is characterized in that, wherein,

Launching under the described the 1st and the 2nd cold sink state, the size at the position parallel with the described the 1st and the length direction of the 2nd cold sink in the described joint portion is not more than 5% of size between two joint portions of every adjacency in the described a plurality of joint portion.

12, a kind of heat exchanger for vehicle, it is arranged on the front side of vehicle, the refrigerant that circulates in the cooling water of cooled engine and the Vehicular air-conditioning apparatus, described heat exchanger for vehicle comprises:

Many articles the 1st pipelines that described refrigerant is mobile;

Be provided with at described the 1st pipeline enclosure of every adjacency, contain the 1st core of undulatory the 1st cold sink;

On the air downstream side of described the 1st core, there is predetermined gap ground to be provided with abreast with described the 1st pipeline, with many articles the 2nd pipelines of described flow of cooling water;

Be provided with at described many articles the 2nd pipeline enclosures, contain the 2nd core of undulatory the 2nd cold sink; With

There is predetermined gap ground to separate described the 1st cold sink and described the 2nd cold sink, and partly in conjunction with a plurality of joint portions of described the 1st cold sink and described the 2nd cold sink,

Wherein, the distance between described the 1st cold sink and described the 2nd fin is not more than 5mm.

13, according to the heat exchanger for vehicle of claim 12, it is characterized in that, wherein,

When the end of the described the 1st ducted described the 2nd pipe side is reference position (0) and is positive direction when outstanding from described the 1st pipeline to the direction of described the 2nd pipe side that the end of described the 2nd pipe side in described the 1st cooling radiator is outstanding-1～7mm from described reference position.

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