CN1981168A - Evaporator - Google Patents
Evaporator Download PDFInfo
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- CN1981168A CN1981168A CN 200580022765 CN200580022765A CN1981168A CN 1981168 A CN1981168 A CN 1981168A CN 200580022765 CN200580022765 CN 200580022765 CN 200580022765 A CN200580022765 A CN 200580022765A CN 1981168 A CN1981168 A CN 1981168A
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- exchanger tube
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Abstract
An evaporator 1 comprises a plurality of flat heat exchange tubes 12 arranged in a left-right direction at a spacing with the widthwise direction thereof pointing forward or rearward, and fins 14 arranged between respective adjacent pairs of heat exchange tubes 12. The fins 14 have at least front edges thereof projected forwardly outward beyond the heat exchange tubes 12. Assuming that the amount of projection of the fins 14 beyond the heat exchange tubes 12 is X mm and that the heat exchange tubes 12 are Y mm in thickness in the left-right direction, i.e., in height, X and Y have the relationship of 0.11Y=X=1.0Y. The surfaces of the fins 14 can be drained of condensation water efficiently.
Description
The cross reference of related application
The application proposes according to 35 U.S.C. § 111 (a), and require the provisional application No.60/585 on July 8th, 2004 and submission on June 8th, 2005 according to 35 U.S.C. § 111 (b) according to 35 U.S.C. § 119 (e) (1), 839 and No.60/688,352 applying date interests.
Technical field
The present invention relates to the evaporimeter in automotive air conditioning device to be installed, this automotive air conditioning device has the kind of refrigeration cycle that is used for automobile.
The downstream (this direction is by the indication of the arrow X among Fig. 1,3 and 6) for the treatment of respectively to exchange the air stream in the air duct gap between the heat pipe by evaporimeter adjacent in the text be called as " front portion " in the claims, and opposite side is called as " rear portion ".In addition, evaporimeter from after top, bottom, left side and the right side (upper and lower of Fig. 2 and left-hand side and right-hand side) that look to the front be called as respectively " on ", D score, " left side " and " right side ".
Background technology
The evaporimeter that uses so-called accumulation board type up to now widely is as the motor vehicle air conditioning system evaporimeter, it comprises the parallel a plurality of flat hollow bodies that are provided with, each hollow body comprises respect to one another and along the mutual soldering of its circumferential edge a pair of discoid plate together, and is arranged between every pair of adjacent flat hollow bodies and the corrugated fin of soldering blind shaped thereon.But, in recent years, need provide size and weight further to reduce and have a more high performance evaporimeter.
In order to satisfy this requirement, the applicant has proposed a kind of evaporimeter, and this evaporimeter comprises: be the heat exchange core of forming along the two pipe groups of arranging that fore-and-aft direction be arranged in parallel (each pipe group comprises a plurality of heat exchanger tubes that are provided with at a distance of certain intervals ground) by form; Be arranged on the refrigerant inlet-EXPORT CARTON of the upper end of this heat exchange core; And the refrigerant turn tank that is arranged on the bottom of this heat exchange core, the inside of this refrigerant inlet-EXPORT CARTON is separated the refrigerant outlet collector that part is divided into the refrigerant inlet header that is positioned at the front side and is positioned at rear side, this inlet header has refrigerant inlet at the one end, this outlet header has refrigerant outlet at itself and this inlet end side by side, the inside of this refrigerant turn tank is separated wall and is divided into the cold-producing medium outflow collector that the cold-producing medium that is positioned at the front side flows into collector and is positioned at rear side, be formed with a plurality of cold-producing mediums in the partition wall of this refrigerant turn tank and pass through the hole, this cold-producing medium is by hole vertically being provided with at a distance of certain intervals ground along this wall, the upper end of the heat exchanger tube of described anterior pipe group joins inlet header to, the upper end of the heat exchanger tube of described rear portion pipe group joins outlet header to, the lower end of the heat exchanger tube of described anterior pipe group joins the inflow collector to, and the lower end of the heat exchanger tube of described rear portion pipe group joins the outflow collector to.The cold-producing medium that flows into the inlet header of refrigerant inlet-EXPORT CARTON flows into the inflow collector of steering box by the heat exchanger tube of anterior pipe group, go into to flow out collector by the cold-producing medium in the partition wall by orifice flow then, and further flow into the outlet header (seeing open file JP-A No.2003-75024) of refrigerant inlet-EXPORT CARTON by the heat exchanger tube of rear portion pipe group.
The weight of disclosed evaporimeter reduces and the performance raising in the above-mentioned open file, thereby compares with traditional accumulation plate-type evaporator, produces more substantial condensed water on the surface of corrugated fin.Therefore the amount of the condensed water of evaporimeter unit volume is bigger.Therefore, condensed water easily is dispersed in around the surface of corrugated fin or is frozen on this surface, makes the heat exchange efficiency variation.For evaporimeter, fall by the gap between the louver board usually at the condensed water that produces on the fin surface.Therefore can realize higher drainage efficiency by increasing louvered length.But,, need reduce the interval between the adjacent heat exchange tubes in order as the situation of the evaporimeter of above-mentioned open file, to guarantee compactness and to reduce weight.Therefore the louver board that extends is restricted.
Target of the present invention is to overcome the problems referred to above, and a kind of evaporimeter that can discharge the condensed water of fin surface effectively is provided.
Summary of the invention
In order to realize above-mentioned target, the present invention includes following pattern:
1) a kind of evaporimeter, this evaporimeter comprise along left and right directions at a distance of a plurality of flat heat exchange tube of certain intervals ground setting be arranged on the adjacent fin of respectively exchanging between the heat pipe, the width of described heat exchanger tube forward or backward,
The leading edge of described at least fin is outwards outstanding forward above described heat exchanger tube.
2) according to paragraph 1) evaporimeter, wherein have only the leading edge of described fin to be projected into the front of described heat exchanger tube.
3) according to paragraph 1) evaporimeter, suppose that wherein the outstanding overhang that surpasses described heat exchanger tube of described fin is Xmm, and described heat exchanger tube highly is Ymm promptly along the thickness of left and right directions, the pass of X and Y is 0.11Y≤X≤1.0Y.
4) according to paragraph 1) evaporimeter, suppose that wherein the outstanding overhang that surpasses described heat exchanger tube of described fin is Xmm, and described heat exchanger tube highly is Ymm promptly along the thickness of left and right directions, the pass of X and Y is 0.3Y≤X≤0.8Y.
5) according to paragraph 1) evaporimeter, wherein in the outstanding side of the fin of described evaporimeter, each described heat exchanger tube has such end face, and promptly to show as cross section be with respect to the outside form of outstanding face of cylinder section in middle part of the short transverse of heat exchanger tube at it to this end face.
6) according to paragraph 1) evaporimeter, wherein in the outstanding side of the fin of described evaporimeter, each described heat exchanger tube has and the left side of heat exchanger tube and each the rectangular planar end surface in the opposite flank, right side.
7) according to paragraph 6) evaporimeter, wherein in the outstanding side of the fin of described evaporimeter, the end face of described heat exchanger tube and the left side of heat exchanger tube become fillet ground joint with in the opposite flank, right side each.
8) according to paragraph 1) evaporimeter, wherein the form of each described fin is a corrugated fin, it comprises crest part, trough part and the coupling part that crest part and this trough are partly interconnected, this coupling part has a plurality of louver boards that be arranged in parallel along the air flue direction, and the louver board that forms in the end adjacent with the outstanding edge of fin of fin is positioned to from the heat exchanger tube end of the outstanding side of the fin that is positioned at described evaporimeter inside with respect to fore-and-aft direction.
9) according to paragraph 8) evaporimeter, wherein in the louver board of the fin end adjacent and the distance between the heat exchanger tube end of the outstanding side of fin with outstanding edge up to 1mm.
10) according to paragraph 8) evaporimeter, the vertical range of wherein said fin between crest part and trough part be promptly highly for 7.0mm arrives 10.0mm, the spacing of coupling part is that spacing of fin is 1.3 to arrive 1.8mm.
11) according to paragraph 8) evaporimeter, the crest part and the trough of wherein said corrugated fin partly include flat and fillet part, this fillet part branch is arranged on each place in the opposite side of this flat and is integral with described coupling part, and the radius of curvature of this fillet part is up to 0.7mm.
12) according to paragraph 1) evaporimeter, the height of wherein said heat exchanger tube is that thickness is that 0.75mm is to 1.5mm.
13) according to paragraph 1) evaporimeter, wherein the heat exchanger tube that is provided with at a distance of certain intervals ground along left and right directions is arranged on the adjacent fin of respectively exchanging between the heat pipe and all prolongs together with described set of heat exchange tubes to be arranged to set of heat exchange tubes along the forms that are arranged to many rows of direction forward or backward.
14) according to paragraph 13) evaporimeter, described evaporimeter comprises: be arranged on each heat exchanger tube an end the front side and be the refrigerant inlet header that at least one row's set of heat exchange tubes engages with form; Be arranged on the rear portion of this inlet header and the refrigerant outlet collector that is provided with towards an end of each heat exchanger tube, this outlet header engages with remaining heat exchanger tube; Towards the other end setting of each heat exchanger tube and first intermediate header that engages with the heat exchanger tube that joins refrigerant inlet header to; And be arranged on the rear portion of first intermediate header and second intermediate header that is provided with towards the other end of each heat exchanger tube, and this second intermediate header engages with the heat exchanger tube that joins described outlet header to, and these two intermediate header maintenances are interconnected.
15) a kind of kind of refrigeration cycle that comprises compressor, condenser and evaporimeter, this evaporimeter comprises according to paragraph 1) to 14) in any one described heat exchanger.
16) kind of refrigeration cycle a kind of wherein being equipped with according to paragraph 15) is as the vehicle of motor vehicle air conditioning system.
For according to paragraph 1), 2) and 5) to 7) in any one evaporimeter, the outwards outstanding forward or backward heat exchanger tube that surpasses of the leading edge of each fin and at least one in the trailing edge, thus between the left border of the ledge of fin and the pipe adjacent or margo dexter, form recessed portion with this fin.The condensed water that produces on fin surface flows to recessed portion because of surface tension with being attracted, and after this flows downward with drippage along the end face of recessed portion and heat exchanger tube.Therefore, can discharge the condensed water of fin surface more efficiently.Therefore, prevent that condensed water is scattered or freezes, thereby prevent the heat exchange property variation.Especially, flowing through the downstream that the air of air by the gap between adjacent every exchange heat pipe make the condensed water that produces on the fin surface successfully flow to air-flow direction promptly flows towards the front portion.According to paragraph 2) the situation of evaporimeter under draining effectively.
For according to paragraph 3) or 4) evaporimeter, improve the efficient of the condensed water of discharging fin surface reliably.Efficient that can be higher is discharged according to paragraph 4) the condensed water of evaporimeter.
According to paragraph 8) evaporimeter in, the louver board that forms in the end adjacent with the outstanding edge of this fin of fin is positioned to from the end of the heat exchanger tube of giving prominence to side at fin inside with respect to fore-and-aft direction, the condensed water that the result produces on fin surface successfully is attracted to recessed portion by surface tension, to obtain higher drainage efficiency.More properly, the condensed water that produces on the upper surface of each coupling part of corrugated fin flows through the gap between every pair of adjacent louver board, arrive the surface of heat exchanger tube by the lower surface of this coupling part, and when flowing in the junction surface of heat exchanger tube surface and fin, successfully be attracted to recessed portion.Outwards be positioned to from the heat exchanger tube end if be positioned at the louver board of the end adjacent of fin, then can retain condensed water on the louver board with respect to fore-and-aft direction with the outstanding edge of this fin.
According to paragraph 9) evaporimeter have more significantly according to paragraph 8) the effect of evaporimeter.
For according to paragraph 10) evaporimeter, can suppress the increase of air flue resistance, and can improve heat exchange efficiency simultaneously, and between them, keep good balance.
For according to paragraph 11) evaporimeter, can suppress the increase of air flue resistance, and can improve heat exchange efficiency simultaneously, and between them, keep good balance.
Description of drawings
Fig. 1 is a part abridged perspective view, and it illustrates and will adopt the overall structure of the evaporimeter of heat exchanger of the present invention;
Fig. 2 is a vertical sectional view, and the evaporimeter that it illustrates the Fig. 1 when the rear portion is seen has omitted mid portion simultaneously;
Fig. 3 is the partial enlarged view along the section of the line A-A gained of Fig. 2;
Fig. 4 is the decomposition diagram of refrigerant inlet-EXPORT CARTON;
Fig. 5 is the decomposition diagram of refrigerant turn tank;
Fig. 6 is the zoomed-in view along the cross section of the line B-B gained of Fig. 3;
Fig. 7 is the enlarged perspective that the part of heat exchange core is shown;
Fig. 8 is the partial enlarged view of Fig. 6;
Fig. 9 is the curve map that is depicted as the result of the test of determining the outstanding overhang Xmm that surpasses heat exchanger tube of corrugated fin and the relation between the pipe height Ymm and carrying out, and this highly is the thickness along the left and right directions of heat exchanger tube;
Figure 10 is the view corresponding to Fig. 6, and it illustrates another embodiment according to evaporimeter of the present invention;
Figure 11 comprises the view corresponding to Fig. 8, and it illustrates the heat exchanger tube after the improvement.
The specific embodiment
Embodiments of the invention are described below with reference to accompanying drawings.
Fig. 1 and 2 illustrates the overall structure according to motor vehicle air conditioning system evaporimeter of the present invention, and Fig. 3 to 8 illustrates the structure of critical piece.
Fig. 1 and 2 illustrates the evaporimeter 1 of the motor vehicle air conditioning system that is used for wherein using the CFC cold-producing medium.This evaporimeter 1 comprises the refrigerant inlet-EXPORT CARTON 2 of an aluminum that is provided with at a distance of certain intervals ground and the refrigerant turn tank 3 of aluminum on another, and is arranged on the heat exchange core 4 between these two casees 2,3.
Refrigerant inlet-EXPORT CARTON 2 comprises (with respect to the downstream of the flow direction of the air by evaporimeter) refrigerant inlet header 5 that is arranged on the front side and the refrigerant outlet collector 6 that is positioned at rear side (with respect to the upstream side of air-flow).The refrigerant inlet pipe 7 of aluminum is connected to the inlet header 5 of refrigerant inlet-EXPORT CARTON 2, and the refrigerant outlet pipe 8 of aluminum is connected to the outlet header 6 of refrigerant inlet-EXPORT CARTON.The cold-producing medium outflow collector 11 (second intermediate header) that refrigerant turn tank 3 comprises the cold-producing medium inflow collector 9 (first intermediate header) that is positioned at the front side and is positioned at rear side.
With reference to Fig. 3 and 4, refrigerant inlet-EXPORT CARTON 2 comprises: tabular first parts 16, and these first parts are made by the aluminium soldering sheet material that has the brazing material layer on its apparent surface, and heat exchanger tube 12 joins on these parts; That make by the exposed aluminium extrusion profile and cover second parts 17 of the upside of first parts 16; And the aluminium lid of making by the aluminium soldering sheet material that on its apparent surface, has the brazing material layer 18,19, this aluminium lid joins the opposite end of two parts 16,17 to, and each is relative open-ended so that seal.Aluminum joint plate 21 solderings of extending along fore-and-aft direction on the outer surface of lid 19 right-hand members, with toilet cover on inlet header 5 and outlet header 6.Refrigerant inlet pipe and outlet 7,8 join fish plate 21 to.
The cross section of second parts 17 is roughly m shape and under shed, these parts comprise two walls 26 of front and rear of horizontal expansion, be arranged on the partition wall 27 at two middle parts between the wall 26, this partition wall horizontal expansion is divided into the separating device in two spaces of front and rear and two connecting walls 28 that are roughly circular arc protruding upward and that partition wall 27 and front and rear wall 26 are connected in their upper end with being integral as the inside with refrigerant inlet-EXPORT CARTON 2.Rear wall 26 and partition wall 27 interconnect on the whole length of second parts 17 by resistance plate 29 in their lower end with being integral.Resistance plate 29 is formed with the cold-producing medium of extending transversely by hole 31A, 31B except the left part of plate and right part in its rear portion, this cold-producing medium by the hole along this resistance plate laterally at a distance of the setting of certain intervals ground.The outstanding lower end that surpasses front and rear wall 26 of the lower ends downward of partition wall 27, and have a plurality of protruding 27a with being integral, this projection is outstanding downwards from the lower edge of partition wall 27, along laterally being provided with at a distance of certain intervals ground and being assemblied in the through hole 25 of first parts 16.Projection 27a forms by the specified portions of excising partition wall 27.
Soldering is together in the following manner for 16,17, two of first and second parts of refrigerant inlet-EXPORT CARTON 2 lid 18,19 and fish plate 21.The mutual soldering of brazing material layer that first and second parts 16,17 utilize first parts 16 together, simultaneously the protruding 27a of second parts 17 inserts the respective through hole 25 of first parts 16 and engages (crimping engagement) with its crimping, thereby the upper end of the front and rear vertical wall 22a of first parts 16 engages with the lower end of the front and rear wall 26 of second parts 17.Two lids 18,19 utilizations cover 18,19 brazing material layer soldering is at first and second parts 16, on 17, anterior simultaneously protuberance 32 partly, 37 are assemblied in two parts 16, in 17 in the front space of partition wall 27 fronts, the top protuberance 33 of rear portion, 38 are assemblied in two parts 16, in 17 in partition wall 27 back and the upper space above resistance plate 29, the bottom protuberance 34 of rear portion, 39 are assemblied in from partition wall 27 backward and be lower than in the lower space of resistance plate 29, top engaging lug 35,41 engage with the connecting wall 28 of second parts 17, and bottom engaging lug 36,42 engage with the sweep 22 of first parts 16.Fish plate 21 utilizes the brazing material layer soldering of right cap 19 on right cap 19.Like this, make refrigerant inlet-EXPORT CARTON 2.The part in partition wall 27 fronts of second parts 17 is used as inlet header 2, and the part in partition wall 27 back of parts 17 is used as outlet header 6.Outlet header 6 is divided into space, upper and lower 6a, 6b by resistance plate 29, and they keep being communicated with by hole 31A, 31B by cold-producing medium.The refrigerant outlet 44 of right cap 19 is communicated with the upper space 6a of outlet header 6.The refrigerant inlet part 45 of fish plate 21 is communicated with refrigerant inlet 43, and its refrigerant outlet part 46 is communicated with refrigerant outlet 44.
With reference to Fig. 3 and Fig. 5, refrigerant turn tank 3 comprises: tabular first parts of being made by the aluminium soldering sheet material that has the brazing material layer on its apparent surface and engage with heat exchanger tube 12 48; That make by the exposed aluminium extrusion profile and cover second parts 49 of the downside of first parts 48; And the aluminium lid 51 that seals left side and opposite end, right side opening by the aluminium soldering sheet material that on its apparent surface, has the brazing material layer being used to of making.
The cross section of the end face 3a of refrigerant turn tank 3 is circular arc on the whole, thereby its middle part with respect to fore-and-aft direction is the highest part 52, and this highest part reduces gradually towards front side and rear side.Refrigerant turn tank 3 has groove 53 in its front and rear opposite side portion, and this groove extends to front and rear opposite flank 3b respectively from the front and rear opposite side of the highest part 52 of end face 3a, and laterally is provided with at a distance of certain intervals ground.
The cross section of first parts 48 is a circular arc, it is protruding upward at the middle part with respect to fore-and-aft direction, and these first parts each place in its front and rear lateral margin has been integrally formed into dependent wall 48a with it, and this dependent wall is extended on the whole length of first parts 48.The upper surface of first parts 48 is as the end face 3a of refrigerant turn tank 3, and the outer surface of dependent wall 48a is as the front portion or the rear portion side surface 3b of refrigerant turn tank 3.Groove 53 is formed in the front and rear sidepiece of first parts 48 each, and this groove extends to the lower end of dependent wall 48a from the highest part 52 with respect to the middle part of fore-and-aft direction of first parts 48.Each place in the front and rear sidepiece except the highest part 52 at its middle part of first parts 48, adjacent each be formed with the pipe interpolation slit 54 that prolongs along fore-and-aft direction between to groove 53.Every pair of corresponding front and rear pipe interpolation slit 54 is with respect to laterally being in same position.First parts 48 have a plurality of through holes 55 that form and laterally be provided with at a distance of certain intervals ground in the highest part 52.When aluminium soldering sheet material being made first parts 48, form dependent wall 48a, groove 53, pipe interpolation slit 54 and the through hole 55 of first parts 48 by working pressure processing.
The cross section of second parts 49 is generally w shape and upward opening, and second parts comprise: two walls 56 of front and rear of make progress forward and backward respectively outwardly-bent and horizontal expansion; Be arranged on two between the wall 56 middle part, horizontal expansion and as the vertical partition wall 57 that the inside of refrigerant turn tank 3 is divided into the escapement in two spaces of front and rear; And two connecting walls 58 that partition wall 57 and each front and rear wall 56 are connected in their lower end with being integral.The upper end of partition wall 57 projects upwards the upper end above front and rear wall 56, and partition wall have that edge from it projects upwards with a plurality of protruding 57a of its all-in-one-piece, this projection laterally is provided with at a distance of certain intervals ground, and is assemblied in the respective through hole 55 of first parts 48.Partition wall 57 its adjacent each form cold-producing medium by otch 57b in to the upper limb between the protruding 57a.Projection 57a and otch 57b form by the specified portions of excising partition wall 57.
Each lid front portion of 51 is integrally formed into protuberance 59 laterally inwardly with it on its horizontal inboard, this protuberance can be assemblied in and flow in the collector 9.The rear portion of lid 51 has been integrally formed therewith laterally inwardly protuberance 61 on its horizontal inboard, this protuberance can be assemblied in and flow out in the collector 11.Circular arc portion between each lid 51 each in its lower edge and its front side and rear side is provided with laterally inwardly outstanding engaging lug 62 integratedly, and is integrally formed therewith a plurality of engaging lugs 63 that be provided with at a distance of certain intervals along fore-and-aft direction, laterally inwardly outstanding on the edge thereon.
Soldering is together in the following manner for first and second parts 48,49 of steering box 3 and this steering box two lids 51.The mutual soldering of brazing material layer that first and second parts 48,49 utilize first parts 48 together, the protruding 57a of second parts 49 inserts respective through hole 55 and engages with its crimping simultaneously, and the lower end of the front and rear dependent wall 48a of first parts 48 engages with the upper end of the front and rear wall 56 of second parts 49.Two lids 51 utilize and to cover 51 brazing material layer soldering on first and second parts 48,49, simultaneously anterior protuberance 59 is assemblied in that limit and be positioned at the space of partition wall 57 fronts by two parts 48,49, rear portion protuberance 61 is assemblied in that limit and be positioned at the space of partition wall 57 back by two parts 48,49, top engaging lug 63 engages with first parts 48, and bottom engaging lug 62 engages with the front and rear wall 56 of second parts 49.Like this, form refrigerant turn tank 3.The part in partition wall 57 fronts of second parts 49 is used as and flows into collector 9, and its part in partition wall 57 back is used as outflow collector 11.The upper end open of otch 57b in the partition wall 57 of second parts 49 is passed through hole 64 by 48 sealings of first parts thereby form cold-producing medium.
With reference to Fig. 6 and 7, the heat exchanger tube 12 of front and rear pipe group 13 is smooth, is made and horizontally set by aluminum extruded section bar, and their width is towards the front portion or the rear portion.Each heat exchanger tube 12 portion within it has and be arranged in parallel and along a plurality of coolant channel 12a of the longitudinal extension of pipe.Heat exchanger tube 12 has the front and rear opposing end surface, and each end face shows as the form of the section on the face of cylinder when seeing cross section, is that the middle part of short transverse of heat exchanger tube is outwards outstanding with respect to the transverse width direction at it.The slit 23 of first parts 16 of refrigerant inlet-EXPORT CARTON 2 is inserted in the upper end of heat exchanger tube 12, and the brazing material layer soldering that utilizes first parts 16 is on first parts 16.The slit 54 of first parts 48 of refrigerant turn tank 3 is inserted in the bottom of heat exchanger tube 12, and the brazing material layer soldering that utilizes first parts 48 is on first parts 48.
Preferably, the height h of heat exchanger tube 12 is 0.75 to 1.5mm along the thickness (see figure 7) of horizontal direction promptly, width along fore-and-aft direction is 12 to 18mm, the wall thickness of its circumferential wall is 0.175 to 0.275mm, with the thickness of coolant channel 12a partition wall separated from one another is 0.175 to 0.275mm, the spacing of partition wall is 0.5 to 3.0mm, and the radius of curvature of front and rear end face is 0.35 to 0.75mm.
The heat exchanger tube 12 that can use the resistance weld pipe of aluminum to replace aluminum extruded section bar to make, this resistance weld pipe is formed with a plurality of coolant channels within it, and this coolant channel forms by inner fin is inserted in the pipe.Also can use the pipe of being made by such plate, promptly this plate is to be used in the aluminium soldering sheet material that has the aluminium soldering material layer on the one surface to prepare by rolling processing, and this plate comprises: two flat wall that engage by the coupling part form part; Each flat wall form be integrally formed therewith on the part and from the outstanding sidewall formation part of its lateral margin relative with this coupling part; And from each flat wall form part with it outstanding integratedly and a plurality of partition walls formation parts that be provided with at a distance of certain intervals ground along its width, this pipe is made like this: by described plate being bent to hair clip shape in the coupling part, and to ground connection with sidewall form part mutually soldering form partition wall to form part with partition wall together.
Corrugated fin 14 is to be used in the aluminium soldering sheet material that has the brazing material layer on its opposite flank to make by making this sheet material form waveform.Fin comprises crest part, trough part and is roughly the coupling part 14a of level that this coupling part partly interconnects crest part and trough.This coupling part 14a has a plurality of louver boards 65 that are provided with at a distance of parallel at certain interval along fore-and-aft direction.Corrugated fin 14 is shared for front and rear pipe group 13.The leading edge of corrugated fin 14 is (outside forward) outstanding front end face that surpasses the heat exchanger tube 12 of anterior pipe group 13 forward, and trailing edge (outside backward) outstanding rear end face that surpasses the heat exchanger tube 12 of rear portion pipe group 13 backward.These ledges are indicated with 14b.In the case, forwardly divide between the 14b of ledge forward of the front end face of the heat exchanger tube 12 of pipe group 13 and corrugated fin 14 and at the back step of the rear end face of the heat exchanger tube 12 of rear portion pipe group 13 and fin 14 and form recessed portion 66 between the 14b.The condensed water that produces on the surface of corrugated fin 14 is owing to surface tension flows to recessed portion 66 with being attracted, and after this along the surface of recessed portion 66 and heat exchanger tube 12 to dirty.The efficient of the condensed water on these feasible discharging fin 14 surfaces improves, and anti-sealing splashes or be freezing to avoid heat exchange efficiency to worsen.The adjacent air of air by the gap of respectively exchanging between the heat pipe 12 flow through in utilization, promptly flow forward in the downstream that the condensed water that produces on the surface of fin 14 can successfully flow to air-flow direction, therefore the outstanding forward front end face that surpasses the heat exchanger tube 12 of anterior pipe group 13 of leading edge that has only fin 14, and the not outstanding backward rear end face that surpasses the heat exchanger tube 12 of rear portion pipe group 13 of the trailing edge of fin 14.For example, the fin trailing edge can be positioned in the same vertical plane with respect to left and right directions with the rear end face middle part of heat exchanger tube 12.If the trailing edge of corrugated fin 14 is positioned at the rear end face front of the heat exchanger tube 12 of rear portion group 13, then condensed water may be frozen on the surface of the tube portion that fin 14 is not set.
With reference to Fig. 8, suppose that the corrugated fin 14 outstanding overhangs that surpass heat exchanger tube 12 are Xmm, the thickness along left and right directions of heat exchanger tube 12 highly is Ymm promptly.The pass of wishing overhang X and pipe height Y so is 0.11Y≤X≤1.0Y, more preferably is 0.3Y≤X≤0.8Y.During as X＜0.11Y and as X＞1.0Y, the surface of corrugated fin 14 may not be discharged condensed water effectively.The louver board 65 that is positioned at the end with ledge 14b of fin 14 is positioned to from the end face of heat exchanger tube 12 inside with respect to fore-and-aft direction, and preferably mostly is most 1mm apart from Z between the end face of louver board 65 and heat exchanger tube 12.
The fin height H that wishes corrugated fin 14 be 7.0mm to 10.0mm, this highly is the vertical range of the part from crest part to trough, and spacing of fin P is 1.3 to 1.7mm, this spacing of fin is the spacing of coupling part 14a.When each in partly of the crest of corrugated fin part and trough comprise soldering on heat exchanger tube 12 and with its flat that closely contacts, with each place of the opposite side that is arranged in this flat and with coupling part 14a all-in-one-piece fillet part timesharing, the radius of curvature R of this fillet part is preferably up to the 0.7mm (see figure 7).Can between adjacent every exchange heat pipe 12 of each pipe group 13, a corrugated fin be set, rather than be common to a corrugated fin of front and rear pipe group 13.In the case, the leading edge that is arranged on the corrugated fin 14 between adjacent every exchange heat pipe 12 of each pipe group 13 at least is arranged to from this exchange heat pipe 12 outwards outstanding forward.
Preference relation 0.11Y≤X≤1.0Y between overhang Xmm and the pipe height Ymm confirms to obtain by the following test that we carry out.It is that 1.4mm, width are the heat exchanger tube 12 of 17mm that employed evaporimeter has height h, and height H is 8mm and spacing P is the corrugated fin 14 of 1.5mm.Use is measured hot property simultaneously according to the resistance of the air that therefrom passes through of the method test evaporator of JIS D1618, to determine the corrugated fin 14 outstanding overhang of heat exchanger tube 12 and the relations between the air flue resistance of surpassing.The air flue resistance that increases means and does not discharge the condensed water that produces on the surface of fin 14 effectively.Fig. 9 illustrates this result.It is that 0 o'clock Resistance Value is 100% benchmark, the air flue Resistance Value represented with percentage that the curve map of Fig. 9 illustrates with respect to overhang.The curve map of Fig. 9 shows, when overhang be at least 0.154mm and during up to 1.4mm the air passage resistance be not higher than 98%, this can cause draining effectively.In the case, discharge the condensed water of fin, cause the air flue resistance to reduce.Because pipe highly be 1.4mm, so can find to give prominence to above the height of the overhang Xmm of heat exchanger tube 12 and heat exchanger tube 12 promptly when the thickness Ymm of left and right directions has the 0.11Y of relation≤X≤1.0Y when corrugated fin 14, the air flue resistance is not higher than 98%.The curve map of Fig. 9 shows that also overhang Xmm and pipe height Ymm more preferably have the 0.3Y of relation≤X≤0.8Y.Therefore, overhang X is preferably about 0.5Y.
For described evaporimeter 1, the gas-liquid mixed double-deck cold-producing medium mutually that flows through compressor, condenser and expansion valve dividedly flows into the coolant channel 12a of whole heat exchanger tubes 12 of anterior pipe group 13 via the refrigerant inlet header 5 that the refrigerant inlet 43 of the refrigerant inlet part 45 of refrigerant inlet pipe 7, fish plate 21 and right cap 19 enters inlet-EXPORT CARTON 2.
The cold-producing medium that flows into the passage 12a of all heat exchanger tubes 12 is downward through passage 12a, and the cold-producing medium that enters refrigerant turn tank 3 flows into collector 9.Cold-producing mediums in the cold-producing medium inflow collector 9 flow into cold-producing mediums outflow collector 11 by the cold-producing medium of partition wall 59 by hole 66.
The cold-producing medium of inflow and outflow collector 11 dividedly flows into the coolant channel 12a of all heat exchanger tubes 12 of rear portion pipe group 13, changes its route and upwards enters the lower space 6b that flows out collector 6 by passage 12a.The resistance that 29 pairs of cold-producing medium streams of resistance plate apply makes cold-producing medium can flow into all heat exchanger tubes 12 of rear portion pipe group 13 from outflow collector 11 equably, and this also makes cold-producing medium flow into all heat exchanger tubes 12 of anterior pipe group 13 more equably from inlet header 5.As a result, cold-producing medium flows through all heat exchanger tubes 12 of two pipe groups 13 with uniform amount.
Subsequently, the cold-producing medium of cold-producing medium by resistance plate 29 flows into the upper space 6a of outlet header 6 by hole 31A, 31B, and via the cold-producing medium of right cap 19 go out 44, the exit portion 46 and the outlet 8 of fish plate 21 flow out evaporimeters.When the coolant channel 12a of the heat exchanger tube 12 of the coolant channel 12a of the heat exchanger tube 12 that flows through anterior pipe group 13 and rear portion pipe group 13, the direction of cold-producing medium and arrow X shown in Fig. 1 flows through the air of air by the gap and carries out heat exchange, and flows out evaporimeter with gas phase.
At this moment, on the surface of corrugated fin 14, produce water owing to condensation.Condensed water flows between the 14b of ledge forward of the front end face of heat exchanger tube 12 of anterior pipe group 13 and fin 14 with being attracted, and the back step of the rear end face of the heat exchanger tube 12 of rear portion pipe group 13 and fin 14 divides the recessed portion 66 between the 14b, after this flow downward along recessed portion 66, and flow on the end face 3a of steering box 3 along the end face of heat exchanger tube 12.Water on the case end face 3a is owing to capillary effect enters groove 53, flows through groove 53 and falls steering box 3 belows from the front-end and back-end of groove 53.Like this, can prevent between the lower end of turn tank top surface 3a and corrugated fin 14 to assemble a large amount of condensed waters, thereby and prevent condensate freezes, thereby prevent that heat exchange property from worsening.
Figure 10 illustrates another embodiment of evaporimeter.
In the embodiment shown in fig. 10, the outstanding backward rear end face that surpasses the heat exchanger tube 12 of rear portion pipe group 13 of the trailing edge of corrugated fin 14, but be positioned at same vertical plane with respect to left and right directions with the middle part of the rear end face of heat exchanger tube 12.In others, present embodiment is identical with the structure of previous embodiment, and same parts is indicated with same tag.Because the form of the rear end face of each heat exchanger tube 12 is the section on the face of cylinder, so the middle part of the rear end face of the trailing edge of fin 14 and heat exchanger tube 12 is positioned at same vertical plane with respect to the trailing edge that left and right directions is positioned at part that rear end face that same vertical plane means heat exchanger tube 12 is projected into last portion position and fin 14.
Under the situation of this embodiment, flowing through the downstream that the air of air by the gap between adjacent every exchange heat pipe 12 allows in the gap and the condensed water that produces on the surface of fin 14 successfully flows to air-flow direction promptly flows forward, therefore, the not outstanding backward rear end face that surpasses the heat exchanger tube 12 adjacent of rear portion pipe group 13 of fin 14 trailing edges with this fin, and drainage efficiency is not influenced by this can substantially.But if the trailing edge of fin is positioned at the rear end face front of the heat exchanger tube 12 of rear portion pipe group 13, then condensed water can be frozen on the part that fin 14 is not set of heat exchanger tube 12.
Figure 11 illustrates the improvement of heat exchanger tube.
Under the situation of the heat exchanger tube 12 shown in Figure 11 (a), corrugated fin 14 has the outstanding part that surpasses each front and rear end face of heat exchanger tube 12, and this front and rear end pattern is and the left side of heat exchanger tube and each the rectangular planar end surface among the apparent surface of right side.
Under the situation of the heat exchanger tube 12 shown in Figure 11 (b), corrugated fin 14 has the outstanding part that surpasses each front and rear end face of heat exchanger tube 12, the form of this front and rear end face is planar end surface, and the junction surface of the left surface of this planar end surface and heat exchanger tube and right lateral surface is a fillet.
According to aforementioned two embodiment, at the inlet header 5 of two casees 2,3 with flow between the collector 9, with and outlet header 6 and flow out between the collector 11 and be provided with a set of heat exchange tubes 13, but this setting is not restrictive; Can the inlet header 5 of two casees 2,3 and flow out between the collector 9 with and outlet header 6 and flow out between the collector 11 one or at least two set of heat exchange tubes 13 are set.Steering box selectively is arranged on inlet-EXPORT CARTON below.
In addition, for the evaporimeter of described two embodiment, steering box 3 has to be arranged on adjacently respectively exchanges the groove 53 between the heat pipe 12 so that improve drainage efficiency, but this setting is not restrictive; Groove can form with each heat exchanger tube 12 and be provided with accordingly so that improve drainage efficiency.In the case, steering box 3 has groove at its end face 3a to front and rear side 3b, and each groove all is made for from the outer end forward or backward of each pipe interpolation slit 54 and extends, so that discharge the water of steering box 3 efficiently.
Evaporimeter of the present invention also can be used for supercritical refrigeration cycle, this circulation comprises compressor, gas cooler, evaporimeter, as the expansion valve of pressure reducer, as the reservoir of gas-liquid separator, and be used to make the Intermediate Heat Exchanger that carries out heat exchange from gas cooler cold-producing medium that flows out and the cold-producing medium that flows out from evaporimeter, and this recycles CO
2Or similar supercritical refrigerant.This supercritical refrigeration cycle is installed in vehicle, and for example motor vehicle is interior as aircondition.
Industrial applicability
Evaporimeter of the present invention is applicable to for example motor vehicle air conditioning system, and this aircondition adopts to be installed Kind of refrigeration cycle in motor vehicle.
Claims (16)
1. evaporimeter, this evaporimeter comprise along left and right directions at a distance of a plurality of flat heat exchange tube of certain intervals ground setting be arranged on the adjacent fin of respectively exchanging between the heat pipe, the width of described heat exchanger tube forward or backward,
The leading edge of described at least fin is outwards outstanding forward above described heat exchanger tube.
2. evaporimeter according to claim 1 is characterized in that, has only the leading edge of described fin to be projected into the front of described heat exchanger tube.
3. evaporimeter according to claim 1 is characterized in that, suppose that the outstanding overhang that surpasses described heat exchanger tube of described fin is Xmm, and the thickness along left and right directions of described heat exchanger tube highly is Ymm promptly, and the pass of X and Y is 0.11Y≤X≤1.0Y.
4. evaporimeter according to claim 1 is characterized in that, suppose that the outstanding overhang that surpasses described heat exchanger tube of described fin is Xmm, and the thickness along left and right directions of described heat exchanger tube highly is Ymm promptly, and the pass of X and Y is 0.3Y≤X≤0.8Y.
5. evaporimeter according to claim 1, it is characterized in that, in the outstanding side of the fin of described evaporimeter, each heat exchanger tube has such end face, and promptly to show as cross section be with respect to the outside form of outstanding face of cylinder section in middle part of the short transverse of heat exchanger tube at it to this end face.
6. evaporimeter according to claim 1 is characterized in that, in the outstanding side of the fin of described evaporimeter, each heat exchanger tube has and the left side of heat exchanger tube and each the rectangular planar end surface in the opposite flank, right side.
7. evaporimeter according to claim 6 is characterized in that, in the outstanding side of the fin of described evaporimeter, the end face of described heat exchanger tube and the left side of heat exchanger tube become fillet ground joint with in the opposite flank, right side each.
8. evaporimeter according to claim 1, it is characterized in that, the form of each described fin is a corrugated fin, it comprises crest part, trough part and the coupling part that crest part and trough are partly interconnected, this coupling part has a plurality of louver boards that be arranged in parallel along the air flue direction, and the louver board that forms in the end adjacent with the outstanding edge of fin of fin is positioned to from the heat exchanger tube end of the outstanding side of the fin that is positioned at described evaporimeter inside with respect to fore-and-aft direction.
9. evaporimeter according to claim 8 is characterized in that, in the louver board of the fin end adjacent and the distance between the heat exchanger tube end of the outstanding side of fin with outstanding edge up to 1mm.
10. evaporimeter according to claim 8 is characterized in that, the vertical range of described fin between crest part and trough part is promptly highly for 7.0mm arrives 10.0mm, and the spacing of coupling part is that spacing of fin is 1.3 to 1.8mm.
11. evaporimeter according to claim 8, it is characterized in that, the crest part and the trough of described corrugated fin partly include flat and fillet part, this fillet part branch is arranged on each place in the opposite side of this flat and is integral with described coupling part, and the radius of curvature of this fillet part is up to 0.7mm.
12. evaporimeter according to claim 1 is characterized in that, the height of described heat exchanger tube is that thickness is that 0.75mm is to 1.5mm.
13. evaporimeter according to claim 1, it is characterized in that, the heat exchanger tube that is provided with at a distance of certain intervals ground along left and right directions is arranged to set of heat exchange tubes with the forms that are arranged to many rows along direction forward or backward, is arranged on the adjacent fin of respectively exchanging between the heat pipe and all prolongs together with described set of heat exchange tubes.
14. evaporimeter according to claim 13 is characterized in that, described evaporimeter comprises: be arranged on each heat exchanger tube an end the front side and be the refrigerant inlet header that at least one row's set of heat exchange tubes engages with form; Be arranged on the rear portion of this inlet header and the refrigerant outlet collector that is provided with towards an end of each heat exchanger tube, this outlet header engages with remaining heat exchanger tube; Towards the other end setting of each heat exchanger tube and first intermediate header that engages with the heat exchanger tube that joins inlet header to; And second intermediate header that is arranged on the first intermediate header rear portion and is provided with towards the other end of each heat exchanger tube, this second intermediate header engages with the heat exchanger tube that joins described outlet header to, and these two intermediate header maintenances are interconnected.
15. a kind of refrigeration cycle that comprises compressor, condenser and evaporimeter, this evaporimeter comprise according to any one the described evaporimeter in the claim 1 to 14.
16. vehicle that kind of refrigeration cycle according to claim 15 wherein is installed as motor vehicle air conditioning system.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004197959 | 2004-07-05 | ||
| JP197959/2004 | 2004-07-05 | ||
| US60/585,839 | 2004-07-08 | ||
| JP332644/2004 | 2004-11-17 | ||
| US60/688,352 | 2005-06-08 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1981168A true CN1981168A (en) | 2007-06-13 |
| CN100432579C CN100432579C (en) | 2008-11-12 |
Family
ID=38131579
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800227654A Expired - Fee Related CN100432579C (en) | 2004-07-05 | 2005-06-29 | Evaporator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100432579C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103245248A (en) * | 2012-02-10 | 2013-08-14 | 上海协合散热器制造有限公司 | Novel rectangular radiating belt |
| CN103307924A (en) * | 2013-07-05 | 2013-09-18 | 上海交通大学 | Micro-channel heat exchanger with optimized drainage |
| CN102395854B (en) * | 2009-04-22 | 2013-10-16 | 夏普株式会社 | Heat exchanger and air conditioner having the heat exchanger mounted therein |
| CN103353250A (en) * | 2013-06-14 | 2013-10-16 | 阳江市宝马利汽车空调设备有限公司 | Fin preventing frosting to be easy to drain water |
| WO2016074399A1 (en) * | 2014-11-11 | 2016-05-19 | 广东美的制冷设备有限公司 | Parallel-flow heat exchanger and air conditioner having same |
| WO2018059443A1 (en) * | 2016-09-28 | 2018-04-05 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchange assembly for heat exchanger, heat exchanger, and mold |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107514841B (en) * | 2016-06-17 | 2020-06-16 | 杭州三花微通道换热器有限公司 | Heat exchanger assembly |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19719263C2 (en) * | 1997-05-07 | 2002-04-25 | Valeo Klimatech Gmbh & Co Kg | Flat tube evaporator with vertical longitudinal direction of the flat tubes in motor vehicles |
| JP4122608B2 (en) * | 1998-12-10 | 2008-07-23 | 株式会社デンソー | Refrigerant evaporator |
| CN2444193Y (en) * | 2000-08-18 | 2001-08-22 | 江西新电汽车空调机有限公司 | Parallel-flow evaporator for air conditioner |
| JP4554144B2 (en) * | 2001-06-18 | 2010-09-29 | 昭和電工株式会社 | Evaporator |
-
2005
- 2005-06-29 CN CNB2005800227654A patent/CN100432579C/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102395854B (en) * | 2009-04-22 | 2013-10-16 | 夏普株式会社 | Heat exchanger and air conditioner having the heat exchanger mounted therein |
| CN103245248A (en) * | 2012-02-10 | 2013-08-14 | 上海协合散热器制造有限公司 | Novel rectangular radiating belt |
| CN103353250A (en) * | 2013-06-14 | 2013-10-16 | 阳江市宝马利汽车空调设备有限公司 | Fin preventing frosting to be easy to drain water |
| CN103307924A (en) * | 2013-07-05 | 2013-09-18 | 上海交通大学 | Micro-channel heat exchanger with optimized drainage |
| WO2016074399A1 (en) * | 2014-11-11 | 2016-05-19 | 广东美的制冷设备有限公司 | Parallel-flow heat exchanger and air conditioner having same |
| WO2018059443A1 (en) * | 2016-09-28 | 2018-04-05 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchange assembly for heat exchanger, heat exchanger, and mold |
| US11118839B2 (en) | 2016-09-28 | 2021-09-14 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat exchange assembly for heat exchanger, heat exchanger, and mold |
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|---|---|
| CN100432579C (en) | 2008-11-12 |
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