CN102889713B - Parallel flow heat exchanger special for bus air conditioner - Google Patents
Parallel flow heat exchanger special for bus air conditioner Download PDFInfo
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- CN102889713B CN102889713B CN201210350445.3A CN201210350445A CN102889713B CN 102889713 B CN102889713 B CN 102889713B CN 201210350445 A CN201210350445 A CN 201210350445A CN 102889713 B CN102889713 B CN 102889713B
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Abstract
The invention provides a parallel flow heat exchanger special for a bus air conditioner. The parallel flow heat exchanger comprises a first collecting pipe, a second collecting pipe, a plurality of flat pipes and fins, wherein the first collecting pipe and the second collecting pipe are separated in a preset distance and are parallel to each other; a first end and a second end of each flat pipe are respectively connected with the first collecting pipe and the second collecting pipe; the fins are arranged between adjacent flat pipes; the first collecting pipe comprises a first pipe cavity, a second pipe cavity, a first porous plate and a first slot; the first slot is formed in an inner wall of the first pipe cavity along the axial direction of the first collecting pipe; the first porous plate is inserted into the first pipe cavity through the first slot along the axial direction of the first collecting pipe; a plurality of pores are distributed in the first porous plate along the length direction of the first porous plate; and a refrigerant is allowed to flow from one side of the first pipe cavity to the other side of the first pipe cavity through the pores. The parallel flow heat exchanger has the advantages that each flat pipe can exert the highest efficiency, so that the heat exchange efficiency is improved; and moreover, a die is reasonable in structure, easy and convenient, the refrigeration capacity is not limited, and the refrigeration capacity is universal.
Description
Technical field
The present invention relates to the manufacture field of air conditioning for automobiles, specifically, relate to the special parallel-flow heat exchanger of a kind of coach air conditioner.
Background technology
Heat exchanger comprises condenser, evaporimeter, and it is the chief component in automotive air-conditioning system, is responsible for the task of emission and absorption heat in air dielectric, and its heat exchange property has important impact to the operation characteristic of air conditioning for automobiles and economy.Pursuing that heat exchanger is efficient, in the process of miniaturization, the structure of heat exchanger of automobile air-conditioner experienced by the development course of pipe type, corrugated tube type and parallel flow type.
Parallel-flow heat exchanger is by tube-strip heat exchanger development evolvement, heat exchange main body is made up of header, flat tube and corrugated fins, fin has louver seam to strengthen heat convection, there is header at the flat tube two ends that every root blocks, and according to header segmentation whether, be divided into unit parallel-flow heat exchanger and multiunit parallel flow heat exchanger.Parallel-flow heat exchanger adopts aluminum alloy materials manufacture, has that quality is light, easy-formation and a low advantage of cost.
At present, parallel-flow heat exchanger uses in a large number on car, if by car by multiunit parallel flow heat exchanger applications on passenger vehicle, then there is following shortcoming:
One, there is very big difference in the environment for use of parallel-flow heat exchanger on car and passenger vehicle.Due to passenger vehicle and the difference of car on appearance and size, weight and volume larger, in the process of moving, bus body is compared with chassis with coachbuilt body with chassis, vibration, distortion, dust, environment temperature etc. are more severe, and the density of the filtering dust net of passenger vehicle parallel-flow heat exchanger is much less than the density of the filtering dust net of car parallel-flow heat exchanger.Make the environment for use of parallel-flow heat exchanger on car and passenger vehicle there is very big difference, compared with the parallel-flow heat exchanger on car, the parallel-flow heat exchanger torsional deformation on passenger vehicle is large, and the power that is hit is large, and decay is fast.
Two, parallel-flow heat exchanger differs larger at car with the mounting condition on passenger vehicle.For parallel flow condenser, the parallel flow condenser of car is arranged on the foremost of water tank, remains the dust on parallel flow condenser surface and foul at ordinary times, cleaner by high wind-force and rain drop erosion under steam.The parallel flow condenser of passenger vehicle is arranged on roof or the tailstock, and be generally horizontal positioned, remain high wind-force not as car of dust on parallel flow condenser surface and foul and rainwash, and, the fin of parallel flow condenser is the shape of isosceles triangle and a pitch of fins is little, makes dust can be more long-pending thicker like this.Because dust can with number acid, alkali and corrosion-prone residue, this residue meeting accelerated corrosion fin, makes parallel flow condenser efficiency decay rapidly.
In addition, to be applied on passenger vehicle and parallel-flow heat exchanger on car exists common shortcoming: service life cannot repair after short, internal leakage; For parallel-flow evaporator, not easily get rid of condensate water, the much more long-pending windage that can cause of water is large, and the heat exchange efficiency of air side is declined.
Existing parallel-flow heat exchanger refrigerant glide path figure can with reference to shown in accompanying drawing 1, and in accompanying drawing 1, flat tube vertical design, parallel-flow heat exchanger uses as evaporimeter.Refrigerant perpendicular flow in this parallel-flow evaporator, refrigerant enters in a chamber of the first header 10, and the flat tube corresponding from this chamber flows through; Refrigerant, by entering in a chamber of the second header 11 after flat tube, enters another chamber by the through hole between two chambeies of the second header 11 from a chamber; The flat tube that this chamber is corresponding is flowed to after entering another chamber; Refrigerant, by entering another chamber of the first header 10 after flat tube, is discharged from this chamber.Refrigerant flows in flat tube, achieves heat exchange.The shortcoming of refrigerant perpendicular flow is that upper down-pipe is more, and be difficult to shunting up and down evenly, the whole heat exchange efficiency of parallel-flow evaporator declines greatly.
Summary of the invention
The object of the invention is, solve above-mentioned technical problem, provide the coach air conditioner that a kind of heat exchange efficiency is high special parallel-flow heat exchanger.
The technical scheme that the present invention takes is, the special parallel-flow heat exchanger of a kind of coach air conditioner, comprises the first header, the second header, multiple flat tube and fin; And the parallel placement spaced a predetermined distance from the second header of described first header, the first end of described each flat tube is connected with the second header with the first header respectively with the second end, described flat tube allows refrigerant to flow between the first header and the second header, and described fin is arranged between adjacent flat tube; Described first header comprises the first tube chamber and the second tube chamber, described first tube chamber and the second tube chamber are axially parallel to each other along the length direction of the first header, described first header also comprises the first porous plate and the first slot, described first slot is axially set in the first lumen wall along the first header, described first porous plate inserts in the first tube chamber by described first slot along the axis of the first header, described first porous plate is distributed with multiple hole along its length, and described hole allows refrigerant to flow to opposite side from the side of the first tube chamber.
Further, described second header comprises the second slot and the second porous plate, described second slot is axially set in the second header inwall along the second header, described second porous plate inserts in the second header by described second slot along the axis of the second header, described second header is divided into the 3rd tube chamber and the 4th tube chamber, described second porous plate is distributed with multiple hole along its length, and described hole allows refrigerant to flow between the 3rd tube chamber and the 4th tube chamber.
Further, the length direction of described flat tube is parallel with passenger-carrying chassis, makes refrigerant bottom horizontal flow sheet in flat tube.
Further, described flat tube comprises first group of flat tube and second group of flat tube, described first tube chamber is communicated with by first group of flat tube with the 3rd tube chamber, refrigerant is flowed between the first tube chamber and the 3rd tube chamber, described second tube chamber is communicated with by second group of flat tube with the 4th tube chamber, and refrigerant is flowed between the 4th tube chamber and the second tube chamber.
Further, in the second tube chamber of described first header and in the tube chamber corresponding with described second tube chamber of the second header, be provided with commutation dividing plate, described commutation dividing plate is for intercepting the path of refrigerant.
Further, the special parallel-flow heat exchanger of described coach air conditioner also comprises reservoir, the import of described reservoir is positioned at one end of the second tube chamber, and the outlet of described reservoir is positioned at the other end of the second tube chamber, and one end and the other end of described second tube chamber are separated by the dividing plate that commutates.
Further, described flat tube inside is provided with multiple dividing plate, and flat tube is divided into multiple through hole parallel to each other by described dividing plate, and the length direction of described through hole is parallel with the axis of flat tube.
Further, described fin is rectangular corrugated shape fin, and crest and trough are connected with contiguous flat tube respectively.
Further, described flat tube comprises first group of flat tube and second group of flat tube, described first tube chamber is communicated with by first group of flat tube with the 3rd tube chamber, refrigerant is flowed between the first tube chamber and the 3rd tube chamber, described second tube chamber is communicated with by second group of flat tube with the 4th tube chamber, refrigerant is flowed between the 4th tube chamber and the second tube chamber, and the crest of described fin and the centre position of trough are provided with osculum, and described osculum is just to the space between first group of flat tube and second group of flat tube.
Further, doped with tin, copper, manganese corrosion-resistant material in the manufactured materials of described fin and flat tube.
Good effect of the present invention is, first porous plate is set in the first header, the shunting uniformity that reasonable Arrangement enters the refrigerant of header is carried out by the number in the hole on the first porous plate, the distribution of size and location, make every root flat tube can give play to maximum usefulness, thus improve heat exchange efficiency.Parallel-flow heat exchanger mould structure of the present invention is reasonable, easy, does not limit cold, and cold range size is general.
The special parallel-flow heat exchanger of coach air conditioner of the present invention, compared with pipe type heat exchanger, has following characteristics: (1) lightweight 40%; (2) compact conformation, volume-diminished 40%; (3) heat exchange efficiency is high, and heat exchange efficiency improves 30%; (4) cost is low by 40%, system coolant injection amount few 45%.The special parallel-flow heat exchanger of coach air conditioner of the present invention is compared with car parallel-flow heat exchanger, and the life-span of product, structure, intensity all have a more substantial increase, module combined type, and flexibility is flexible coupling, and shock resistance is good.
Accompanying drawing explanation
Figure 1 shows that existing parallel-flow heat exchanger refrigerant glide path figure;
Figure 2 shows that the structural representation of parallel-flow heat exchanger first embodiment of the present invention;
Fig. 3 A is depicted as the internal structure schematic diagram of the first header;
Fig. 3 B is depicted as the cross-sectional structure schematic diagram of the first header;
Fig. 4 A is depicted as the cross-sectional structure schematic diagram of the second header;
Fig. 4 B is depicted as the cross-sectional structure schematic diagram of the second header being placed with the second porous plate;
Figure 5 shows that the front schematic cross-section of parallel-flow heat exchanger shown in Fig. 2;
Figure 6 shows that the structural representation of flat tube;
Figure 7 shows that the structural representation of fin;
Fig. 8 A is depicted as the crest of fin and the annexation schematic diagram of trough and contiguous flat tube;
Fig. 8 B is depicted as F position enlarged diagram in Fig. 5;
Fig. 9 A is depicted as along A-A in Fig. 5 to sectional view;
Fig. 9 B is depicted as along B-B in Fig. 5 to sectional view;
Figure 10 shows that the structural representation of parallel-flow heat exchanger second embodiment of the present invention;
Figure 11 A is depicted as the elevation cross section view of parallel-flow heat exchanger shown in Figure 10;
Figure 11 B is depicted as along D-D in Figure 11 A to sectional view;
Figure 11 C is depicted as along E-E in Figure 11 A to sectional view.
Reference numeral
10,20: the first headers; 11,21: the second headers; 22: flat tube; 23: fin; 201: the first tube chambers; 202: the second tube chambers; 203: the first porous plates; 204: the first slots; 205: hole; 210: the second slots; 211: the second porous plates; 212: the three tube chambers; 213: the four tube chambers; 230: crest; 231: trough; 232: louver is stitched; 233: osculum; 220: dividing plate; 229: through hole; 221: the first groups of flat tubes; 222: the second groups of flat tubes; 223: the first commutation dividing plates; The Part I of 224: the second tube chambers; The Part II of 225: the second tube chambers; 226: the second commutation dividing plates; The Part I of 227: the four tube chambers; The Part II of 228: the four tube chambers; 24: reservoir; 241: reservoir import; 242: reservoir outlet.
Detailed description of the invention
Elaborate below in conjunction with the detailed description of the invention of accompanying drawing to parallel-flow heat exchanger provided by the invention.Accompanying drawing only schematically shows structure and the annexation of the special parallel-flow heat exchanger of a kind of coach air conditioner of the present invention, does not represent its practical structures.
First embodiment
In the first embodiment for the special parallel-flow heat exchanger of a kind of coach air conditioner of the present invention as evaporimeter, be described.See Fig. 2, parallel-flow heat exchanger of the present invention comprises the first header 20, second header 21, multiple flat tube 22 and fin 23.And the parallel placement spaced a predetermined distance from the second header 21 of described first header 20.The first end of described each flat tube 22 is connected with the first header 20, and the second end is connected with the second header 21, and described flat tube 22 allows refrigerant to flow between the first header 20 and the second header 21.Described fin 23 is arranged between two adjacent flat tubes 22, in the present embodiment, in order to make simplified form clear, only schematically shows part fin, and described fin 23 is for realizing parallel-flow heat exchanger and extraneous heat exchange.Also be provided with fixed support and upper and lower backplate (not indicating in accompanying drawing) in the present embodiment, for fixing and protection parallel-flow heat exchanger, can installation be stablized.
The internal structure schematic diagram of the first header 20 is see Fig. 3 A, and the first header 20 comprises the first tube chamber 201, second tube chamber 202, and described first tube chamber 201 and the second tube chamber 202 are axially arranged in parallel along the length direction of the first header 20.Described first header also comprises the first porous plate 203 and the first slot 204(is shown in Fig. 3 B), described porous plate 103 is inserted in the first tube chamber 201 by the axis of described first slot 204 along the first header 20.
The cross-sectional structure schematic diagram of the first header 20, see Fig. 3 B, in order to structure and the position of clear expression first slot 204, does not arrange porous plate in figure 3b.Described first slot 204 is axially set in the first tube chamber 201 inwall along the first header 20, and described first slot 204 not only allows the first porous plate 203 to insert, and can also play the effect fixing the first porous plate 203.Certainly, in the second tube chamber 202, also can slot be set, allows porous plate to insert.In the specific embodiment of the present invention, the width according to parameter first slots 204 such as the thickness of the first porous plate 203 is 1.2 ~ 1.6mm, and in the present embodiment, the width of described first slot is 1.6mm.Described first porous plate 203 is distributed with multiple hole 205 along its length, and described hole 205 allows refrigerant to flow to opposite side from the side of the first tube chamber 201.The quantity in described hole 205, the design of size and location distribution can make the refrigerant entering the first header 20 be evenly distributed when the first header 20 flows to flat tube 22, thus make every root flat tube 22 to play maximum efficiency, improve the heat exchange efficiency of parallel-flow heat exchanger.Quantity, the size and location distribution in described hole 205 can be selected, as long as without prejudice to the object of the invention according to design needs.
Further, in the present embodiment, described second header 21 comprises the second slot 210 and the second porous plate 211, the cross-sectional structure schematic diagram of the second header 21 is see shown in Fig. 4 A, in order to structure and the position of clear expression second slot 210, do not arrange the second porous plate in Figure 4 A, Fig. 4 B is depicted as the cross-sectional structure schematic diagram of the second header 21 being inserted with the second porous plate 211.See Fig. 4 A and Fig. 4 B, described second slot 210 is axially set in the second header 21 inwall along the second header 21, described second porous plate 211 to be inserted in the second header 21 along the axis of the second header 21 by described second slot 210 and described second header 21 is divided into the 3rd tube chamber 212 and the 4th tube chamber 213, described second porous plate 211 is distributed with multiple hole along its length, and described hole allows refrigerant to flow between the 3rd tube chamber 212 and the 4th tube chamber 213.The quantity in described hole, the design of size and location distribution can make the refrigerant entering the second header 21 be evenly distributed when the second header 21 flows to flat tube 22, thus make every root flat tube 22 to play maximum efficiency further, improve the heat exchange efficiency of parallel-flow heat exchanger.
In prior art, second porous plate 211 is not set between the 3rd tube chamber 212 and the 4th tube chamber 213, but when manufacture the second header 21, directly produce the 3rd tube chamber 212 and the 4th tube chamber 213, adopt other techniques to do on the sidewall that the 3rd tube chamber 212 is adjacent with the 4th tube chamber 213 again to portal, refrigerant can be flowed between two tube chambers.The method of prior art is at the inner manufacturing hole of the second header 21, and complex process, manufacture difficulty is large, and Expenses Cost, once after having manufactured hole, can't change the distribution in hole, thus make the cold scope of parallel-flow heat exchanger be subject to a definite limitation.The second porose porous plate 211 of band inserts in the second header 21 by the second slot 210 by parallel-flow heat exchanger of the present invention, realize refrigerant between the 3rd tube chamber 212 and the 4th tube chamber 213 to be uniformly distributed, and, when the pore size distribution of the second porous plate 211 is unreasonable, second porous plate 211 that more can also renew while not changing parallel-flow heat exchanger.Parallel-flow heat exchanger technique of the present invention is simple, and manufacture difficulty is low, and can change the second porous plate at any time, and refrigerant is more evenly distributed, and heat exchange efficiency improves.
With the side contacted with flat tube 22 of the second header 21, all there is multiple flat type perforate at the first header 20 see Fig. 3 A, described flat type perforate allows flat tube 22 insert or be connected with flat tube 22, allow refrigerant flow into from the first header 20 and the second header 21 or flow out flat tube 22, thus realize the flowing of refrigerant between the first header 20, flat tube 22 and the second header 21.
Further, in the present embodiment, flat tube 22 comprises first group of flat tube 221 and second group of flat tube 222, the elevation cross section view of parallel-flow heat exchanger of the present invention is see Fig. 5, first tube chamber 201 of described first header 20 is communicated with by first group of flat tube 221 with the 3rd tube chamber 212 of the second header 21, refrigerant is made to flow to the 3rd tube chamber 212 from the first tube chamber 201, second tube chamber 202 of described first header 20 is communicated with by second group of flat tube 222 with the 4th tube chamber 213 of the second header 21, makes refrigerant flow to the second tube chamber 202 from the 4th tube chamber 213.
Further, in the present embodiment, the inside of described each flat tube 22 is provided with multiple dividing plate 220, and the structural representation of flat tube 22 is see Fig. 6, flat tube is divided into multiple through hole 229 parallel to each other by described multiple dividing plate 220, and the length direction of described through hole 229 is parallel with the axis of flat tube 22.Such structural design makes flat tube intensity good, and front face area is little, and air flow resistance is low, and after pipe, tail region diminishes, and parallel-flow heat exchanger of the present invention has higher heat exchange area per unit volume, and heat exchange efficiency is significantly improved.The surface spray zinc of described flat tube 22, the thickness that described flat tube 22 sprays zinc is 10 ~ 12g/m
2, the zinc layers on flat tube 22 surface makes flat tube 22 have the surface of high-strength corrosion-resistant.The quantity of flat tube 22 can be selected according to the length of header or the density of flat tube or the purposes of parallel-flow heat exchanger, and such as in present embodiment, one group of flat tube quantity is set to 14, and in second embodiment of the invention, one group of flat tube quantity is 42.
Further, in the present embodiment, described fin 23 is square wave corrugated fin, and the structural representation of fin 23 is see Fig. 7, and the crest 230 of fin 23 and trough 231 are connected with contiguous flat tube respectively.Shown in Fig. 8 A, in Fig. 8 A, clearly show the crest 230 of fin 23 and the annexation of trough 231 and contiguous flat tube.Fin 23 is designed to rectangular corrugated shape, can increase the contact area of fin 23 and flat tube 22, thus heat exchange efficiency is improved.The surface that described fin 23 is not connected with flat tube is provided with multiple louver and stitches 232, and described louver seam 232 can strengthen heat convection.Described fin is also provided with osculum 233 in the centre position of crest 230 and trough 231, described osculum 233 is just to the space between first group of flat tube 221 and second group of flat tube 222, as Fig. 8 B, Fig. 8 B is F position enlarged diagram in Fig. 5, described osculum 233 can make the water accumulating in flat tube 22 and fin 23 inside discharge, and solves the problem of the eliminating of parallel-flow heat exchanger condensate water, frosting.The square wave corrugated fin of the present invention's application, compared with the fin used in traditional parallel-flow heat exchanger, not easily accumulate dust, and drainage performance is good, heat exchange efficiency of fins is improved.In the present embodiment, fin 23 peak width scope is 1.5 ~ 3mm, and thickness is 0.15 ~ 0.2mm, and manufacturing the material of fin is clad aluminum foil, described material high strength and corrosion-resistant, can improve the service life of fin, thus extend the service life of parallel-flow heat exchanger.
In order to improve fin 23 and the antiseptic property of flat tube 22 further, in the material manufacturing flat tube 22 and fin 23, adding the anti-corrosion materials such as tin, copper, manganese, also can be coated with anti-corrosion material at flat tube 22 and the surface of fin 23 simultaneously.Described anti-corrosion material can be anti-corrosion material well known to those skilled in the art, does not limit at this.
Further, in the present embodiment, the length direction of described flat tube 22 is parallel with passenger-carrying chassis, makes refrigerant bottom horizontal flow sheet in flat tube.Used as evaporimeter by parallel-flow heat exchanger, as by car, design the flat tube form of refrigerant perpendicular flow, then pad increases more than ten times, and the many leak sources that certainly will cause of solder joint are many, and qualification rate declines; And on evaporator refrigerant down-pipe quantity too many after, be difficult to shunting up and down evenly, the whole efficiency of parallel-flow evaporator declines greatly, thus cannot design the evaporimeter of High cooling power.So parallel-flow evaporator cold-producing medium be designed to horizontal flow to, the aperture of the second porous plate of the first porous plate in the first header 20 and the second header 21 and the appropriate design of number are arranged, uniform refrigerant being flowed, will receiving than vertically arranging dirty efficiency on the better cold-producing medium of flat tube.
In the present embodiment, when parallel-flow heat exchanger uses as evaporimeter, the flow schematic diagram of refrigerant as shown in fig. 9 a and fig. 9b, Fig. 9 A be in Fig. 5 A-A to sectional view, Fig. 9 B be in Fig. 5 B-B to sectional view.The flow path following (as shown in arrow in accompanying drawing) of refrigerant:
(1) refrigerant enters into the side of the first tube chamber 201 of the first header 20 from evaporator;
(2) refrigerant entered in the first tube chamber 201 flows to opposite side by the first porous plate 203 arranged in the first tube chamber 201 equably from the side of the first tube chamber 201;
(3) refrigerant entering the first tube chamber 201 opposite side flows into first group of flat tube 221 by the flat type perforate of the first tube chamber 201 opposite side;
(4) refrigerant entering first group of flat tube 221 in first group of flat tube 221 the 3rd tube chamber 212 from bottom horizontal flow sheet to the second header 21 and to enter the 3rd tube chamber 212 by the flat type perforate being arranged on the 3rd tube chamber 212 inner;
(5) refrigerant entering the 3rd tube chamber 212 inside evenly flows to the 4th tube chamber 213 by the second porous plate 11 be arranged between the 3rd tube chamber 212 and the 4th tube chamber 213 from the 3rd tube chamber 212;
(6) refrigerant entering the 4th tube chamber 213 enters second group of flat tube 222 by the flat type perforate of the 4th tube chamber 213;
(7) refrigerant entering second group of flat tube 222 in second group of flat tube 222 the second tube chamber 202 from bottom horizontal flow sheet to the first header 20 and to enter the second tube chamber 202 by the flat type perforate being arranged on the second tube chamber 202 inner;
(8) refrigerant entering the second tube chamber 202 inside flows out evaporimeter by evaporator outlet, completes the flowing of refrigerant in evaporimeter.
In the present embodiment, first porous plate 203 is set in the first header 20, second porous plate 211 is set in the second header 21, the shunting uniformity that reasonable Arrangement enters the refrigerant of header is carried out by the number in hole on the first porous plate 203 and the second porous plate 211, the distribution of size and location, make every root flat tube can give play to maximum usefulness, thus improve heat exchange efficiency; Refrigerant bottom horizontal flow sheet can also be realized simultaneously, increase the heat exchange area of parallel-flow heat exchanger.Parallel-flow heat exchanger mould structure of the present invention is reasonable, easy, does not limit cold, and cold range size is general.
Second embodiment
In this second embodiment for the special parallel-flow heat exchanger of a kind of coach air conditioner of the present invention as condenser, be described.See Figure 10, parallel-flow heat exchanger of the present invention comprises the first header 20, second header 21, multiple flat tube 22 and fin 23.And the parallel placement spaced a predetermined distance from the second header 21 of described first header 20.The first end of described each flat tube 22 is connected with the first header 20, and the second end is connected with the second header 21, and described flat tube 22 allows refrigerant to flow between the first header 20 and the second header 21.Described fin 23 is arranged between two adjacent flat tubes 22, in the present embodiment, in order to make simplified form clear, only schematically shows part fin, and described fin 23 is for realizing parallel-flow heat exchanger and extraneous heat exchange.Also be provided with fixed support and upper and lower backplate (not indicating in accompanying drawing) in the present embodiment, for fixing and protection parallel-flow heat exchanger, can installation be stablized.
Parallel-flow heat exchanger elevation cross section view see Figure 11 A, wherein in Figure 11 A along D-D to sectional view see Figure 11 B, along E-E to sectional view see Figure 11 C.First header 20 comprises the first tube chamber 201, second tube chamber 202, and described first tube chamber 201 and the second tube chamber 202 are axially arranged in parallel along the length direction of the first header 20.Described first header 20 also comprises the first porous plate 203 and the first slot 204, and described first porous plate 203 is inserted in the first tube chamber 201 by the axis of described first slot 204 along the first header 20.Structure and the mutual alignment relation of the first porous plate 203 and the first slot 204 are identical with the first embodiment, do not repeat them here.Described second tube chamber 202 is provided with the first commutation dividing plate 223, and described first commutation dividing plate 223, for intercepting the path of refrigerant, makes refrigerant change and flows to.Described first commutation dividing plate 223 is arranged in the second tube chamber 202, and in the present embodiment, the second tube chamber 202 is divided into the long Part I of length 224 and the short Part II 225 of length by described first commutation dividing plate 223.
Further, in the present embodiment, described second header 21 comprises the second slot and the second porous plate 211, and the second header 21 is divided into the 3rd tube chamber 212 and the 4th tube chamber 213 by described second porous plate 211.Structure in the second header 21 in the relative position relation of described second slot, the second porous plate 211 and the second header 21 and first embodiment of the invention is identical, does not repeat them here.In the present embodiment, described second header 21 also comprises the second commutation dividing plate 226, and described second commutation dividing plate 226, for intercepting the path of refrigerant, makes refrigerant change and flows to.
Described second commutation dividing plate 226 is arranged in the tube chamber corresponding with the second tube chamber 202 of the first header 20, in the present embodiment, second commutation dividing plate 226 is arranged in the 4th tube chamber 213, and the first commutation dividing plate 223 is identical with the position in the 4th tube chamber 213 at the second tube chamber 202 with the second commutation dividing plate 226, in the present embodiment, first commutation dividing plate 223 and the second commutation dividing plate 226 are positioned at 2/3rds places of the length of the second tube chamber 202 and the 4th tube chamber 213 respectively, shown in Figure 11 C.In the present embodiment, 4th tube chamber 213 is divided into the long Part I 227 of length and the short Part II 228 of length by the second commutation dividing plate 226, the hole of the second porous plate 211 is only arranged on Part I 227, and at Part II 228 place, between 3rd tube chamber 212 and the 4th tube chamber 213, because the second porous plate 211 does not have providing holes, so refrigerant does not circulate.
With the side contacted with flat tube 22 of the second header 21, all there is multiple flat type perforate at the first header 20, described flat type perforate allows flat tube 22 insert or be connected with flat tube 22, allow refrigerant flow into from the first header 20 and the second header 21 or flow out flat tube 22, thus realize the flowing of refrigerant between the first header 20, flat tube 22 and the second header 21.
Further, in the present embodiment, flat tube 22 comprises first group of flat tube 221 and second group of flat tube 222, see Figure 11 A, first tube chamber 201 of described first header 20 is communicated with by first group of flat tube 221 with the 3rd tube chamber 212 of the second header 21, refrigerant is made to flow to the 3rd tube chamber 212 from the first tube chamber 201, second tube chamber 202 of described first header 20 is communicated with by second group of flat tube 222 with the 4th tube chamber 213 of the second header 21, makes refrigerant flow to the second tube chamber 202 from the 4th tube chamber 213.
Further, in the present embodiment, the inside of described each flat tube 22 is provided with multiple dividing plate, and the structure of flat tube 22 is identical with the structure of the flat tube 22 in the first embodiment.The quantity of flat tube 22 can be selected according to the length of header or the density of flat tube or the purposes of parallel-flow heat exchanger, and such as in present embodiment, parallel-flow heat exchanger is used as condenser, and one group of flat tube quantity is set to 42.In the present embodiment, the structure of described fin is identical with the structure of fin in the first embodiment.
Further, in the present embodiment, see Figure 10 ~ Figure 11 C, the special parallel-flow heat exchanger of described coach air conditioner also comprises reservoir 24, the import 241 of described reservoir 24 is positioned at one end of the second tube chamber 202, this end is the Part I 224 of the second tube chamber, and the import 241 of reservoir is near the first commutation dividing plate 223.The outlet 242 of described reservoir 24 is positioned at the other end of the second tube chamber 202, and this end is the Part II 225 of the second tube chamber.When parallel-flow heat exchanger load is little, described reservoir may be used for storing a part of refrigerant, or considers the problems such as device leakage when filling refrigerant, the refrigerant of meeting how filling about 20%, in order to not affect the performance of heat exchanger, the unnecessary refrigerant of this part is stored in reservoir 24.
In the present embodiment, commutation dividing plate is provided with in header, header is separated into multistage by described commutation dividing plate, because the length of every section is different, so different from the quantity of the flat tube that every section is communicated with, along with the change of cold-producing medium specific volume, flow area (i.e. flat tube number) also respective change, the variable flow structure of multiunit parallel flow heat exchanger, makes the dischargeable capacity of heat exchanger reasonably be utilized, and the flow and heat transfer process of cold-producing medium is more rational.
In the present embodiment, first group of flat tube 221 and second group of flat tube 222 stacked and include 42 flat tubes, second tube chamber 202 and the 4th tube chamber 213 inside are provided with commutation dividing plate, second tube chamber 202 and the 4th tube chamber 213 are divided into two parts, thus the flow process of refrigerant is divided into three flow processs, wherein first pass is from the first tube chamber 201 to the three tube chamber 212, through whole first group of flat tube 221; Second flow process is 28 flat tubes that the Part I 227 of Part I the 224, four tube chamber 213 of Part I 227 to the second tube chamber 202 from the 4th tube chamber 213 and the Part I 224 of the second tube chamber 202 all comprise second group of flat tube 222; 3rd flow process is remaining 14 flat tubes all comprising second group of flat tube 222 from the Part II 225 of Part II 228, second tube chamber 202 of Part II 225 to the four tube chamber 213 of the second tube chamber 202 and the Part II 228 of the 4th tube chamber 213.In the present invention, the quantity often organizing the flat tube that the flat tube quantity that comprises of flat tube and each flow process comprise is not limited to this, under the prerequisite meeting user's needs, can select as the case may be, such as, first pass is through 49 flat tubes, and the second flow process is through 33 flat tubes, and the 3rd flow process is through 16 flat tubes.
See Figure 11 B and Figure 11 C, when in present embodiment, parallel-flow heat exchanger uses as condenser, the flow path following (as shown by arrows in FIG.) of refrigerant:
(1) refrigerant enters into the side of the first tube chamber 201 of the first header 20 from the import of condenser;
(2) refrigerant entered in the first tube chamber 201 flows to opposite side by the first porous plate 203 arranged in the first tube chamber 201 equably from the side of the first tube chamber 201;
(3) refrigerant entering the first tube chamber 201 opposite side flows into first group of flat tube 221 by the flat type perforate of the first tube chamber 201 opposite side;
(4) refrigerant entering first group of flat tube 221 in first group of flat tube 221 the 3rd tube chamber 212 from bottom horizontal flow sheet to the second header 21 and to enter the 3rd tube chamber 212 by the flat type perforate being arranged on the 3rd tube chamber 212 inner;
(5) refrigerant entering the 3rd tube chamber 212 inside evenly to flow to the Part I 227 of the 4th tube chamber 213 from the 3rd tube chamber 212 by being arranged on the second porous plate 211 between the 3rd tube chamber 212 and the 4th tube chamber 213;
(6) refrigerant entering the Part I 227 of the 4th tube chamber 213 enters second group of flat tube 222 by the flat type perforate of the Part I 227 of the 4th tube chamber 213;
(7) refrigerant entering second group of flat tube 222 in second group of flat tube 222 Part I 224 from bottom horizontal flow sheet to the second tube chamber 202 of the first header 20 and to enter the Part I 224 of the second tube chamber 202 by the flat type perforate being arranged on the second tube chamber 202 inner;
(8) refrigerant entering Part I 224 inside of the second tube chamber 202 enters reservoir by reservoir import 241 and flow to reservoir outlet 242 in reservoir 24;
(9) Part II 225 that the refrigerant flowed out from the outlet 242 of reservoir 24 enters the second tube chamber 202 of the first header 20 is inner;
(10) refrigerant entering the Part II 225 of the second tube chamber 202 enters second group of flat tube 222 by the flat type perforate of the Part II 225 of the second tube chamber 202;
(11) refrigerant entering second group of flat tube 222 in second group of flat tube 222 Part II 228 from bottom horizontal flow sheet to the 4th tube chamber 213 and to enter the Part II 228 of the 4th tube chamber 213 by the flat type perforate being arranged on the 4th tube chamber 213 inner;
(12) refrigerant entering Part II 228 inside of the 4th tube chamber flows out condenser from condensator outlet, completes the flowing of refrigerant in condenser.
In the present embodiment, the flowing of refrigerant in parallel-flow heat exchanger is divided into several flow process, the dischargeable capacity of heat exchanger is reasonably utilized, the flow and heat transfer process of cold-producing medium is more rational.
The above is only the preferred embodiment of the present invention; it should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (9)
1. the special parallel-flow heat exchanger of coach air conditioner, comprises the first header, the second header, multiple flat tube and fin, and the parallel placement spaced a predetermined distance from the second header of described first header, the first end of described each flat tube is connected with the second header with the first header respectively with the second end, described flat tube allows refrigerant to flow between the first header and the second header, and described fin is arranged between adjacent flat tube, it is characterized in that, described first header comprises the first tube chamber and the second tube chamber, described first tube chamber and the second tube chamber are axially parallel to each other along the length direction of the first header, described first header also comprises the first porous plate and the first slot, described first slot is axially set in the first lumen wall along the first header, described first porous plate inserts in the first tube chamber by described first slot along the axis of the first header, described first porous plate is distributed with multiple hole along its length, described hole allows refrigerant to flow to opposite side from the side of the first tube chamber, the length direction of described flat tube is parallel with passenger-carrying chassis, make refrigerant bottom horizontal flow sheet in flat tube.
2. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 1, it is characterized in that, described second header comprises the second slot and the second porous plate, described second slot is axially set in the second header inwall along the second header, described second porous plate inserts in the second header by described second slot along the axis of the second header, and described second header is divided into the 3rd tube chamber and the 4th tube chamber, described second porous plate is distributed with multiple hole along its length, described hole allows refrigerant to flow between the 3rd tube chamber and the 4th tube chamber.
3. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 2, it is characterized in that, described flat tube comprises first group of flat tube and second group of flat tube, described first tube chamber is communicated with by first group of flat tube with the 3rd tube chamber, refrigerant is flowed between the first tube chamber and the 3rd tube chamber, described second tube chamber is communicated with by second group of flat tube with the 4th tube chamber, and refrigerant is flowed between the second tube chamber and the 4th tube chamber.
4. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 2, it is characterized in that, in the second tube chamber of described first header and in the tube chamber corresponding with described second tube chamber of the second header, be provided with commutation dividing plate, described commutation dividing plate is for intercepting the path of refrigerant.
5. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 4, it is characterized in that, the special parallel-flow heat exchanger of described coach air conditioner also comprises reservoir, the import of described reservoir is positioned at one end of the second tube chamber, the outlet of described reservoir is positioned at the other end of the second tube chamber, and one end and the other end of described second tube chamber are separated by the dividing plate that commutates.
6. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 1, it is characterized in that, described flat tube inside is provided with multiple dividing plate, and flat tube is divided into multiple through hole parallel to each other by described dividing plate, and the length direction of described through hole is parallel with the axis of flat tube.
7. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 1, is characterized in that, described fin is rectangular corrugated shape fin, and crest and trough are connected with contiguous flat tube respectively.
8. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 2, it is characterized in that, described fin is rectangular corrugated shape fin, crest and trough are connected with contiguous flat tube respectively, described flat tube comprises first group of flat tube and second group of flat tube, described first tube chamber is communicated with by first group of flat tube with the 3rd tube chamber, refrigerant is flowed between the first tube chamber and the 3rd tube chamber, described second tube chamber is communicated with by second group of flat tube with the 4th tube chamber, refrigerant is flowed between the second tube chamber and the 4th tube chamber, the crest of described fin and the centre position of trough are provided with osculum, described osculum is just to the space between first group of flat tube and second group of flat tube.
9. the special parallel-flow heat exchanger of a kind of coach air conditioner according to claim 1, is characterized in that, doped with tin, copper, manganese corrosion-resistant material in the manufactured materials of described fin and flat tube.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210350445.3A CN102889713B (en) | 2012-09-20 | 2012-09-20 | Parallel flow heat exchanger special for bus air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210350445.3A CN102889713B (en) | 2012-09-20 | 2012-09-20 | Parallel flow heat exchanger special for bus air conditioner |
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| CN102889713B true CN102889713B (en) | 2015-04-08 |
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| CN201210350445.3A Expired - Fee Related CN102889713B (en) | 2012-09-20 | 2012-09-20 | Parallel flow heat exchanger special for bus air conditioner |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103822407B (en) * | 2014-03-03 | 2017-05-31 | 浙江金宸三普换热器有限公司 | The parallel-flow heat exchanger and its manufacture method of a kind of double flat tube |
| CN107907000A (en) * | 2017-11-22 | 2018-04-13 | 上海加冷松芝汽车空调股份有限公司 | The heat exchanger of air-conditioning heat exchanger flat tube and the application flat tube |
| CN112629077B (en) * | 2020-12-24 | 2022-11-15 | 超酷（上海）制冷设备有限公司 | Heat exchanger and air conditioning system |
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| DE112006000179T5 (en) * | 2005-01-18 | 2007-12-06 | Showa Denko K.K. | heat exchangers |
| CN101936670B (en) * | 2009-06-30 | 2013-05-15 | 王磊 | Heat exchanger with micro-channel, parallel-flow and all-aluminum flat pipe welding structure and application |
| US9267737B2 (en) * | 2010-06-29 | 2016-02-23 | Johnson Controls Technology Company | Multichannel heat exchangers employing flow distribution manifolds |
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| JP2003214794A (en) * | 2002-01-23 | 2003-07-30 | Denso Corp | Heat exchanger |
| CN201100787Y (en) * | 2007-09-06 | 2008-08-13 | 天津市亚星散热器有限公司 | Novel parallel flow evaporator |
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