CN105143806A - Condenser assembly for refrigerant - Google Patents
Condenser assembly for refrigerant Download PDFInfo
- Publication number
- CN105143806A CN105143806A CN201480015182.8A CN201480015182A CN105143806A CN 105143806 A CN105143806 A CN 105143806A CN 201480015182 A CN201480015182 A CN 201480015182A CN 105143806 A CN105143806 A CN 105143806A
- Authority
- CN
- China
- Prior art keywords
- share
- percentages
- region
- area
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 title 1
- 239000002826 coolant Substances 0.000 claims description 46
- 230000004308 accommodation Effects 0.000 claims description 2
- 230000000712 assembly Effects 0.000 claims 1
- 238000000429 assembly Methods 0.000 claims 1
- 238000003780 insertion Methods 0.000 claims 1
- 230000037431 insertion Effects 0.000 claims 1
- 238000001816 cooling Methods 0.000 description 13
- 238000005325 percolation Methods 0.000 description 8
- 230000002349 favourable effect Effects 0.000 description 5
- 238000005457 optimization Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- PZZOEXPDTYIBPI-UHFFFAOYSA-N 2-[[2-(4-hydroxyphenyl)ethylamino]methyl]-3,4-dihydro-2H-naphthalen-1-one Chemical group C1=CC(O)=CC=C1CCNCC1C(=O)C2=CC=CC=C2CC1 PZZOEXPDTYIBPI-UHFFFAOYSA-N 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/044—Condensers with an integrated receiver
- F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0084—Condensers
Abstract
The invention relates to a condenser assembly (1), comprising a plurality of heat-exchanger pipes (4), which are arranged equidistant from each other having corrugated fins (5) arranged therebetween and lead into deflection regions at both ends and have a free length (Lh) used for heat exchange and, in connection with the corrugated fins (5), form an end area (S) having a width corresponding to the free length (Lh) of the heat-exchanger pipes (4) and a height (Lv), such that the end area (S) results from the product of width and height, wherein the heat-exchanger pipes (4) are connected in parallel in groups and the individual groups are connected in series, wherein the heat-exchanger pipes (4) of the individual groups are arranged adjacent and each group comprises at least two heat-exchanger pipes (4). The percentage share (P) of the heat-exchanger pipes (4) of the first group results from 26.162 In (S/dm<2>) - 40.746 <=P <= 25.49 In (S/dm<2>) - 27.842 for an end area (S) having a ratio of width to height in the range of 0.5 to 1.0, an end area (S) in the range of 10 to 30 dm<2>, and a specification of the area of the end area (S) in dm<2>.
Description
Technical field
The present invention relates to a kind of condenser assembly of preamble according to claim 1.
Background technology
By application cooling agent R1234yf replacement cooling agent R134a up to now, in air conditioner of motor vehicle facility, in the scope of cooling agent circulation, obtain the power reduction that can not ignore.In order to improve the power of cooling agent circulation, the excessively cold greatly of the cooling agent liquefied is such as possible, is crossing by cooling agent the temperature being cooled to the condensation temperature lower than cooling agent in cool region.
Air conditioner of motor vehicle facility for cooling agent to have this condenser assembly for carrying high-power annex such as known from DE102010039511A1.Described known condenser assembly propose collection container on the first long limit of cooling agent condenser assembly, two collecting pipes, heat exchanger tube in superheat region with the cooling agent of cooling steam shape, for condensing cooling agent condenser zone and cross cool region, wherein cross cool region and be configured to that there are three cooling end sections, wherein at least two heat exchanger tubes are crossed cold portion in parallel section as first and are loaded with cooling agent in parallel in the mode of transfer fluid, lead to first cross cold intermediate flow channels from the first cooling agent crossing the section outflow of cold portion in parallel.The cold intermediate flow channels of described first mistake leads to be crossed at least two heat exchanger tubes of cold portion in parallel section as second.Described second mistake cold portion in parallel section is led in the cold intermediate flow channels of the second mistake.The cold intermediate flow channels of second mistake leads to be crossed at least two heat exchanger tubes of cold portion in parallel section as the 3rd, and its middle outlet is arranged on the second long limit of cooling agent condenser assembly.
By increase, the cold section of mistake---when total size of condenser assembly is similar---that formed by three regions be connected in series obtains the condenser zone that reduces, the high pressure increase thus in cooling agent circulation.Therefore, this condenser assembly also unrealized expectation in cooling power and efficiency.
Summary of the invention
Therefore, the object of this invention is to provide a kind of condenser assembly, described condenser assembly has the efficiency of better cooling power and Geng Gao.
Described object is realized by the condenser assembly with the feature of claim 1.Favourable design is the theme of dependent claims.
By the following design of condenser assembly, wherein the share of percentages of heat exchanger tube of first group is from 26.162ln (S/dm
2)-40.746≤P≤25.49ln (S/dm
2)-27.842 to draw, wherein end face (S) has the ratio in the scope of 0.5 to 1.0 of width and height, and end face is at 10dm
2to 30dm
2scope in and the area of end face with dm
2for unit (independent variable with natural logrithm) illustrates, draw the cooling power of the optimization relative to following condenser assembly, described condenser assembly has the share of the percentages greater or lesser about above-mentioned relation of the heat exchanger tube of the first assembly.
Especially preferably, the share of percentages of heat exchanger tube of first group is from 26.162ln (S/dm
2)-35.746≤P≤25.49ln (S/dm
2)-32.842 to draw.
This design especially can be applied to the condenser with cool region, and described cool region of crossing has respectively with three cooling end sections of at least two pipes in each cooling end section.
Can R134, R1234yf be used as cooling agent, but also can use other the approximate cooling agent with the characteristic similar with R134 or R1234yf.
When the ratio of Lh and Lv is 0.5, the share of percentages is preferably by 26.162ln (S/dm
2)-40.746≤P≤26.162ln (S/dm
2)-30 to draw, and when the ratio of Lh and Lv is 1.0, the share of percentages is preferably by 25.49ln (S/dm
2)-35≤P≤25.49ln (S/dm
2)-27.842 to draw.
Preferably, condenser assembly has at least four regions be connected in series, and the first area in the region be wherein connected in series occupies the share of the described percentages of total end face.At this, the share of the percentages in the region be connected in series can reduce along the normal flow direction from first area to second area of cooling agent.In addition, the share of the percentages in the region be connected in series can reduce along the normal flow direction from second area to the 3rd region of cooling agent.
Preferably, the share of the percentages in the region be connected in series to reduce when connecting and starting and constant at the end of series connection along the normal flow direction of cooling agent.
In a preferred condenser assembly, the share of the percentages of the first area in six regions that the normal flow direction of cooling agent is connected in series is greater than the share of the percentages of second area, and the share of the percentages in the 3rd region preferably respectively with four-range, the 5th region same large with the share of the percentages in the 6th region.
In the foursquare design of end face, the twice that the share of the percentages of the first area in six regions that the normal flow direction of cooling agent is connected in series is preferably the share of the percentages of second area is large, and the share of the percentages in the 3rd region preferably respectively with four-range, 5th region large equally with the share of the percentages in the 6th region, wherein the 3rd, 4th, the summation of share of the percentages in the 5th and the 6th region is same with the share of the percentages of second area large, and the share of the percentages of first area is same with the summation of the share of the percentages in all the other regions large.
Turn-around zone is preferably arranged within collecting pipe, wherein the volume of the accommodation cooling agent of collecting pipe is along in the second turn-around zone be preferably greater than in the first turn-around zone between first area and second area of the normal flow direction of cooling agent between second area and the 3rd region, wherein after the 3rd region, is preferably provided with collection container.
The present invention is particularly suitable for having respectively with the condenser assembly crossing cool region of three runners of at least two heat exchanger tubes, but also can be used in other condenser assembly, such as there is the condenser assembly crossing the condenser zone of cool region and three runners of single channel.
Other favourable designs are described by following accompanying drawing and are described by dependent claims.
Accompanying drawing explanation
Hereinafter, the present invention is elaborated with reference to the accompanying drawings based at least one embodiment.Accompanying drawing illustrates:
Fig. 1 illustrates the schematic diagram with the condenser assembly of three cooling end sections according to the first embodiment;
Fig. 2 illustrates the partial schematic diagram of the heat-transfer surface of the condenser assembly of Fig. 1;
Fig. 3 illustrates the schematic diagram with the condenser assembly of three cooling end sections according to the second embodiment; And
Fig. 4 illustrates the chart of the share of the percentages of the heat exchanger tube of first area about the end area of heat exchange.
Detailed description of the invention
Condenser assembly 1 is a part for the automobile air conditioners (not shown in detail) with evaporimeter and the compressor reducer arranged in cooling agent circulation, and described condenser assembly has the first long limit and the second long limit L1 or L2 in laterally disposed mode.Condenser assembly 1 loads in automobile usually, makes two long limit L1, L2 substantially vertically (y direction) extension and is spaced setting of turning up the soil in the z-direction.The degree of depth of condenser assembly 1 extends in the x-direction, and wherein x direction corresponds to the air-flow direction through condenser assembly 1, namely stretches on the contrary with the normal travel direction of vehicle.Hereinafter, corresponding direction illustrates for describing condenser assembly 1.
First long limit L1 is provided with entrance 2 above condenser assembly 1, and through described entrance, in cooling agent circulation, cooling agent, the in this case R1234yf of circulation arrive in condenser assembly 1.Each long limit L1, L2 of condenser assembly 1 are provided with current continuous print collecting pipe 3.The heat exchanger tube 4 that collecting pipe 3 is formed through flat tube is connected to each other in a way known.In collecting pipe 3, be provided with guide plate, pass the flow path (schematically being represented by arrow in the accompanying drawings) of heat exchanger tube 4 to preset cooling agent and each turn-around zone is separated from each other.Between heat exchanger tube 4, be provided with waveform fin 5 in known manner, described waveform fin and heat exchanger tube 4 thermally coupled and be mechanically connected, and heat exchanger tube 4 so that the heat-transfer surface of condenser assembly 1 increase.
The heat exchange area of condenser assembly 1 current in obviously larger upper area by z shape ground percolation, wherein cooling agent described upper area lower end updip tiltedly opposite with entrance 2 flow to be parallel to and be arranged in collection container 6 that the collecting pipe 3 on the second long limit L2 forms in a usual manner before, be arranged in parallel, significantly reduced downwards along a direction by the height of the heat exchanger tube 4 of cooling agent percolation and then quantity, wherein in described collection container, be provided with drier and filter (not shown).At this, described upper area is referred to as the first flow path (first area A) along a direction by the group on the top of the heat exchanger tube 4 of percolation abreast, by described upper area abreast and the group being in reverse to top be referred to as the second flow path (second area B) by the group of the centre of the heat exchanger tube A of percolation and by described upper area abreast and be in reverse to middle group and be referred to as the 3rd flow path (the 3rd region C) by the group of the bottom of the heat exchanger tube 4 of percolation.Described regional A-C is connected in series via described turn-around zone respectively.Due to following function: in the corresponding upper area of condenser assembly 1 by coolant cools that is overheated, gaseous state to saturation temperature, so first area A is also referred to as superheat region.Second and the 3rd region B and C be called condenser zone on the whole because in this region, be cooled to the cooling agent condensation of saturation temperature and arrive in collection container 6 as liquid subsequently.
After collection container 6, be provided with cool region 7 using the another part as condenser assembly 1 as less lower area, the coolant feed liquefied in condenser zone crosses cool region to described.From the end regions of the bottom of collection container 6, described cross cool region 7 this equally by z shape ground percolation.Cross cool region 7 to be formed by three cooling end sections being made up of the heat exchanger tube of two stretching, extensions parallel to each other respectively and the turn-around zone be arranged on in-between in collecting pipe 3 according to DE102010039511A1, wherein at the end of, cooling agent arrives outlet 8 via the collecting pipe 3 be arranged on the first long limit L1.Corresponding to the title in the region of larger upper area A-C, described heat exchanger tube is referred to as region D, E and F by the order of the normal percolation of cooling agent.Cooling agent cross in cool region 7 between each cooling end section turn to this in collecting pipe 3 by guide plate, carry out corresponding to turning in larger upper area, describedly turn to but also can carry out in any other modes, namely collecting pipe 3 such as also can be stopped and turn to can being undertaken by the turn-around zone formed dividually crossing on cool region 7.
Collecting pipe 3, heat exchanger tube 2, waveform fin 5 and possible turn-around zone are usually by metal, be made up of aluminium at this.Each component is connected to each other as being welded to connect in the mode of material fit at this, but also can consider that other have the manufacture of relative configurations.
Hereinafter, the design of the flow path of the cooling power of the optimization for condenser assembly 1 is elaborated.At this, to be limited by heat exchanger tube 4 (freely) length Lh between collecting pipe 3 in yz plane and in the z-direction hereinafter and in the y-direction by corresponding topmost or face that the upper seamed edge of waveform fin of foot and the spacing Lv of lower seamed edge limit be referred to as end face S, namely end face S is drawn by Lh × Lv.Hereinafter, also Lh is referred to as width, also Lv is referred to as height.Each heat exchanger tube 4 (freely) length Lh in the region of end face S is equal respectively in described embodiment.But in the embodiment of alternative, described length also can be different.In addition, all heat exchanger tubes 4 be configured to have correspond to each other and constantly on the length of heat exchanger tube 4 flow freely cross section, and all heat exchanger tubes 4 are equidistantly arranged on the height of condenser assembly 1.
Cooling agent draws as 3 × Lh owing to turning to be similar to respectively within the A-C of heat exchange area and according to the whole flow path crossing cool region D-E, wherein within regional A-F, be respectively equipped with the heat exchanger tube 4 of multiple extends parallel, and the quantity of the heat exchanger tube 4 be connected in parallel in region A, B, C reduces respectively along the direction of flow path.At this, the quantity of the heat exchanger tube 4 be connected in parallel in the D-E of region is constant.Described quantity also can correspond to the quantity of the heat exchanger tube be connected in parallel in the C of region.At this, the quantity of the heat exchanger tube be connected in parallel in the C-F of region is respectively two.
Thus, description content above corresponds to two embodiments of Fig. 1 and 3.
Importantly the heat exchanger tube quantity area fraction of end face S (and then about) being called nA hereinafter of first area A and the ratio of the heat exchanger tube quantity nB of second area B for the optimization of the cooling power of condenser assembly 1.The impact with the 3rd region C of nC heat exchanger tube is so unimportant for the power of condenser assembly 1.Heat exchanger tube quantity nD in the 4th to the 6th region, nE, nF are so unimportant equally.
Hereinafter, with total heat-transfer surface, namely with the ratio of total end face S in, the share of the percentages of the heat-transfer surface of first area A represents with P.
At this, the ratio of Lh and Lv be arranged in 0.5 to 1.0 scope and area with dm
2for unit illustrate when, be 26.162ln (S/dm at ratio
2)-35.746≤P≤25.49ln (S/dm
2)-32.842 time, draw the heat exchanger tube 4 of attaching troops to a unit in first area about heat exchanger tube 4 sum with the share of percentages, described share causes the power of the optimization of the air conditioner facility with the condenser assembly 1 formed according to the present invention.At this, what the limiting value of bottom was applicable to Lh and Lv is 0.5 ratio, what the limiting value on top was applicable to Lh and Lv is 1.0 ratio.
In other words, for 25dm
2heat exchange end face S, such as draw the favourable share of about 54% of heat exchanger tube 4 in the first region.Thus, in " foursquare " design of end face, also automatically draw the corresponding ratio P (in units of %) of the quantity of the heat exchanger tube 4 of first area A and the sum of heat exchanger tube 4:
P＝nA/[100×(nA+nB+nC+nD+nE+nF)]。
Correspondingly, the condenser assembly 1 of the Lh/Lv ratio with 1.0 is shown as the first embodiment in FIG.
When the ratio of Lh and Lv is 0.5, namely the width of end face be height twice large time, draw the favourable share of (heat exchanger tube 4 in the A of first area) about 43%, as schematically illustrated as the second embodiment in figure 3.Consider ground in advance, it should be noted that the theory building of heat-transfer surface is as broad as long when heat exchanger tube 4 and waveform fin 5.Unique difference is the setting of guide plate in collecting pipe 3 be not shown specifically, described guide plate causes the different percolation direction in the subregion of heat-transfer surface, compared with total height time, first direction turns to according to more top in the condenser assembly 1 of the second embodiment.
Thus, be 25dm in the foursquare design of end face S and the size of end face
2when, as proposed according to the first embodiment, the only about half of of all heat exchanger tubes 4 is attached troops to a unit in first area A.If but end face S increases, the share of so advantageously attaching troops to a unit in the heat exchanger tube 4 of first area A raises, if the size of end face S reduces, so share reduces, at such as 10dm
2end face S when be reduced to about 30%.
Have 0.5 Lh and Lv ratio end face S rectangle design in, as proposed according to the second embodiment, the share of the percentages of first area A is low by about 10% respectively.
Under the condition of safe range considering up and down 5%, be derived as 26.162ln (S/dm
2)-40.746≤P≤25.49ln (S/dm
2)-27.842 relation, the heat exchanger tube 4 of namely attaching troops to a unit in first area is about the share of the percentages of the sum of heat exchanger tube 4, and described share causes the good power of air conditioner facility with the condenser assembly 1 formed according to the present invention.
Above-mentioned relation is especially at 10dm
2to 30dm
2scope in, especially at 15dm
2to 25dm
2scope in end face S be general, wherein multiple condenser used in vehicular field has corresponding large end face S.
According to the first and second embodiments, second area B is approximate same with the 3rd to the 6th region C-F summation to be formed greatly.
Served as cool region unlike as described above three runners ground but the genuine or multithread of double fluid genuine formation time, also can consider for the corresponding relation of first area A about the design of the percentages of whole heat exchange end face S, wherein be at least 6 to 16 at the amount total crossing the flat tube in cool region.Thus, for the null situation of nE and/or nF, also can consider above-mentioned equation, as long as crossing the sum of the heat exchanger tube in cool region in the scope of 6 to 16.
Although according to the present embodiment and the continuous print pipe be described in the drawings as having guide plate, collecting pipe 3 also can be formed by turn-around zone that is independent, that separately form, its flow cross section and/or volume especially can reduce along the flow direction of cooling agent, as disclosed in DE102011007216A1.It is especially favourable that corresponding flow cross section reduces between the first turn-around zone (region between region A and region B) and the second turn-around zone (region between region B and region C), but advantageously can additionally propose between region subsequently.
Claims (11)
1. a condenser assembly (1), described condenser assembly has multiple heat exchanger tube (4) equidistantly arranged under the condition of insertion waveform fin (5), and described heat exchanger tube leads in turn-around zone in both sides,
Described heat exchanger tube (4) has freely, for the length (Lh) of heat exchange, and
Described heat exchanger tube (4) has the end face (S) of width corresponding to the described freely length (Lh) of described heat exchanger tube (4) and height (Lv) in conjunction with described waveform fin (5) formed, described end face (S) is drawn by the product of width and height
Described heat exchanger tube (4) is connected in parallel in groups and each group is connected in series, wherein each group described heat exchanger tube (4) be adjacent to arrange and each group be made up of at least two heat exchanger tubes (4),
It is characterized in that, the share (P) of the percentages of the described heat exchanger tube (4) of first group is from 26.162ln (S/dm
2)-40.746≤P≤25.49ln (S/dm
2)-27.842 to draw,
Wherein end face (S) has width with ratio highly in the scope of 0.5 to 1.0, and end face (S) is at 10dm
2to 30dm
2scope in and the area of described end face (S) with dm
2for unit illustrates.
2. condenser assembly according to claim 1, is characterized in that, at least two groups were set to the flow path in cool region.
3. condenser assembly according to claim 1 and 2, is characterized in that, the share (P) of the percentages of the described heat exchanger tube (4) of described first group is from 26.162ln (S/dm
2)-35.746≤P≤25.49ln (S/dm
2)-32.842 to draw.
4. according to the condenser assembly described in claim 1,2 or 3, it is characterized in that, when the ratio of Lh and Lv is 0.5, the share (P) of percentages is by 26.162ln (S/dm
2)-40.746≤P≤26.162ln (S/dm
2)-30 to draw,
And
When the ratio of Lh and Lv is 1.0, the share (P) of percentages is by 25.49ln (S/dm
2)-35≤P≤25.49ln (S/dm
2)-27.842 to draw.
5. the condenser assembly according to any one of the claims, it is characterized in that, described condenser assembly (1) has at least four regions be connected in series (A-F), and the first area (A) in the wherein said region (A-F) be connected in series occupies the share (P) of the described percentages of whole described end face (S).
6. condenser assembly according to claim 5, is characterized in that, described in the normal flow direction of share along cooling agent from described first area (A) to second area (B) of the percentages in region that be connected in series reduce.
7. condenser assembly according to claim 6, is characterized in that, described in the normal flow direction of share along cooling agent from described second area (B) to the 3rd region (C) of the percentages in region that be connected in series reduce.
8. the condenser assembly according to any one of the claims, it is characterized in that, described in the share of the percentages in region (A-F) that is connected in series reduce when connecting and starting along the normal flow direction of cooling agent and be constant at the end of series connection.
9. the condenser assembly according to any one of the claims, it is characterized in that, the share (P) of the percentages of the described first area (A) in six regions (A-F) that the normal flow direction of cooling agent is connected in series is greater than the share of the percentages of described second area (B), and same large with the share of the percentages in described 6th region (F) respectively with described 4th region (D), described 5th region (E) of the share of the percentages in described 3rd region (C).
10. the condenser assembly according to any one of the claims, it is characterized in that, in the foursquare design of described end face (S), the share of the percentages of the described first area (A) in six regions (A-F) that the normal flow direction of cooling agent is connected in series is that the twice of the share of the percentages of described second area (B) is large, and the share of the percentages in described 3rd region (C) is respectively with described 4th region (D), described 5th region (E) large equally with the share of the percentages in described 6th region (F), wherein said 3rd, 4th, the summation of the share of the percentages in the 5th and the 6th region (C-F) is same large with the share of the percentages of described second area (B), and the share of the percentages of described first area (A) is same large with the summation of the share of the percentages of all the other regions (B-F).
11. condenser assemblies according to any one of the claims, it is characterized in that, described turn-around zone is arranged within collecting pipe (3), the volume of the accommodation cooling agent of wherein said collecting pipe (3), along larger compared with the second turn-around zone between described second area (B) and described 3rd region (C) in the first turn-around zone between described first area (A) and described second area (B) of the normal flow direction of cooling agent, is wherein provided with collection container (6) in described 3rd region (C) downstream.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013204294.9A DE102013204294A1 (en) | 2013-03-12 | 2013-03-12 | Condenser assembly for refrigerant |
| DE102013204294.9 | 2013-03-12 | ||
| PCT/EP2014/054891 WO2014140133A1 (en) | 2013-03-12 | 2014-03-12 | Condenser assembly for refrigerant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105143806A true CN105143806A (en) | 2015-12-09 |
| CN105143806B CN105143806B (en) | 2018-04-03 |
Family
ID=50277227
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480015182.8A Active CN105143806B (en) | 2013-03-12 | 2014-03-12 | Condenser assembly for cooling agent |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20160069597A1 (en) |
| EP (1) | EP2972040B1 (en) |
| CN (1) | CN105143806B (en) |
| BR (1) | BR112015020809B1 (en) |
| DE (1) | DE102013204294A1 (en) |
| WO (1) | WO2014140133A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA1334627C (en) * | 1988-09-14 | 1995-03-07 | Hironaka Sasaki | Condenser |
| JPH09222267A (en) * | 1996-02-16 | 1997-08-26 | Mitsubishi Heavy Ind Ltd | Receiver type heat exchanger |
| JPH10300271A (en) * | 1997-04-30 | 1998-11-13 | Nippon Light Metal Co Ltd | Outdoor heat exchanger of heat pump type heating-cooling combination apparatus |
| EP1167910A2 (en) * | 2000-06-20 | 2002-01-02 | Showa Denko Kabushiki Kaisha | Condenser |
| EP1365200A1 (en) * | 2002-05-24 | 2003-11-26 | Halla Climate Control Corporation | Multistage gas and liquid phase separation condenser |
| FR2915793A1 (en) * | 2007-05-03 | 2008-11-07 | Valeo Systemes Thermiques | Heat exchanger e.g. subcooling-type condenser, for air-conditioning circuit of motor vehicle, has collector boxes including walls defining heat exchange paths, where path reduction between successive paths is defined by specific formula |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5682944A (en) * | 1992-11-25 | 1997-11-04 | Nippondenso Co., Ltd. | Refrigerant condenser |
| FR2709344B1 (en) * | 1993-08-27 | 1995-10-13 | Valeo Thermique Moteur Sa | Condenser for motor vehicle air conditioning system. |
| GB2346680A (en) * | 1999-02-11 | 2000-08-16 | Llanelli Radiators Ltd | Condenser |
| JP2001133077A (en) * | 1999-11-09 | 2001-05-18 | Showa Alum Corp | Heat exchanger with receiver tank |
| DE10065205A1 (en) * | 2000-12-23 | 2002-07-04 | Behr Gmbh & Co | Refrigerant condenser |
| DE10155001A1 (en) * | 2001-11-08 | 2003-05-22 | Behr Gmbh & Co | Refrigerant condenser |
| DE102007009923A1 (en) * | 2007-02-27 | 2008-08-28 | Behr Gmbh & Co. Kg | Condenser for air conditioning system, has accumulator in refrigerant-connection with undercooling section via overflow hole, and downpipe communicating with another overflow hole, at inlet side via inflow chamber arranged in accumulator |
| JP5501242B2 (en) * | 2008-10-20 | 2014-05-21 | 株式会社ケーヒン・サーマル・テクノロジー | Capacitor |
| JP5717474B2 (en) * | 2010-04-16 | 2015-05-13 | 株式会社ケーヒン・サーマル・テクノロジー | Capacitor |
| DE102010039518A1 (en) * | 2010-08-19 | 2012-02-23 | Behr Gmbh & Co. Kg | Refrigerant condenser assembly |
| DE102010039511A1 (en) * | 2010-08-19 | 2012-02-23 | Behr Gmbh & Co. Kg | Refrigerant condenser assembly |
| JP5651431B2 (en) * | 2010-11-08 | 2015-01-14 | 株式会社ケーヒン・サーマル・テクノロジー | Capacitor |
| DE102011007216A1 (en) * | 2011-04-12 | 2012-10-18 | Behr Gmbh & Co. Kg | Refrigerant condenser assembly |
-
2013
- 2013-03-12 DE DE102013204294.9A patent/DE102013204294A1/en not_active Withdrawn
-
2014
- 2014-03-12 CN CN201480015182.8A patent/CN105143806B/en active Active
- 2014-03-12 WO PCT/EP2014/054891 patent/WO2014140133A1/en active Application Filing
- 2014-03-12 EP EP14709946.9A patent/EP2972040B1/en active Active
- 2014-03-12 BR BR112015020809-6A patent/BR112015020809B1/en not_active IP Right Cessation
-
2015
- 2015-09-11 US US14/851,299 patent/US20160069597A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA1334627C (en) * | 1988-09-14 | 1995-03-07 | Hironaka Sasaki | Condenser |
| JPH09222267A (en) * | 1996-02-16 | 1997-08-26 | Mitsubishi Heavy Ind Ltd | Receiver type heat exchanger |
| JPH10300271A (en) * | 1997-04-30 | 1998-11-13 | Nippon Light Metal Co Ltd | Outdoor heat exchanger of heat pump type heating-cooling combination apparatus |
| EP1167910A2 (en) * | 2000-06-20 | 2002-01-02 | Showa Denko Kabushiki Kaisha | Condenser |
| EP1365200A1 (en) * | 2002-05-24 | 2003-11-26 | Halla Climate Control Corporation | Multistage gas and liquid phase separation condenser |
| FR2915793A1 (en) * | 2007-05-03 | 2008-11-07 | Valeo Systemes Thermiques | Heat exchanger e.g. subcooling-type condenser, for air-conditioning circuit of motor vehicle, has collector boxes including walls defining heat exchange paths, where path reduction between successive paths is defined by specific formula |
Also Published As
| Publication number | Publication date |
|---|---|
| BR112015020809A2 (en) | 2017-07-18 |
| DE102013204294A1 (en) | 2014-10-02 |
| US20160069597A1 (en) | 2016-03-10 |
| WO2014140133A1 (en) | 2014-09-18 |
| EP2972040A1 (en) | 2016-01-20 |
| BR112015020809B1 (en) | 2020-12-22 |
| CN105143806B (en) | 2018-04-03 |
| EP2972040B1 (en) | 2018-10-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP6333401B2 (en) | Heat exchanger and air conditioner | |
| JP4814907B2 (en) | Refrigeration cycle equipment | |
| JP6351494B2 (en) | Air conditioner | |
| JP6336100B2 (en) | Heat exchanger and air conditioner | |
| KR20130114249A (en) | Heat exchanger and air conditioner | |
| EP3156752B1 (en) | Heat exchanger | |
| CN104235965B (en) | Outdoor condenser and air-conditioner | |
| CN201368619Y (en) | Heat-pump type parallel flow heat exchanger | |
| EP2971982B1 (en) | Modular coil for air cooled chillers | |
| CN201621986U (en) | Microchannel heat exchanger | |
| WO2015046275A1 (en) | Heat exchanger and air conditioner using same | |
| CN203053095U (en) | Novel process parallel flow condenser of automobile air conditioner | |
| CN201876019U (en) | Parallel-flow evaporator for window air conditioner | |
| CN205014688U (en) | Heat exchanger and indirect heating equipment | |
| CN103047800A (en) | Novel process parallel flow condenser for automobile air conditioner | |
| CN108351188A (en) | Heat exchanger and air-conditioning | |
| CN106885395A (en) | A kind of Thermal Performance of Micro Channels device assembly and air-conditioning refrigeration system | |
| CN105841406A (en) | Heat exchange device, air conditioner and heat pump | |
| US11384970B2 (en) | Heat exchanger and refrigeration cycle apparatus | |
| CN203053094U (en) | Automobile air conditioning concurrent flow evaporator | |
| CN105143806A (en) | Condenser assembly for refrigerant | |
| KR20130057712A (en) | Heat pump having a heat exchanger of dual construction | |
| CN107560241A (en) | A kind of automobile-used supercooling extension condenser | |
| CN112629077B (en) | Heat exchanger and air conditioning system | |
| CN205747598U (en) | Heat-exchanger rig and air-conditioner, heat pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |