CN100533046C - Plate used for heat converter - Google Patents
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- CN100533046C CN100533046C CNB2006101599773A CN200610159977A CN100533046C CN 100533046 C CN100533046 C CN 100533046C CN B2006101599773 A CNB2006101599773 A CN B2006101599773A CN 200610159977 A CN200610159977 A CN 200610159977A CN 100533046 C CN100533046 C CN 100533046C
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Abstract
The invention relates to a plate for heat exchanger, comprising asymmetrically formed protrusions of refrigerant distribution part and streamline protrusions which are arranged on a flowing channel as a Z-shape with same quantity, therefore, refrigerant flowed in a box can be uniformly distributed and introduced in to a pipe, so that a formation of uniform flow distribution and a reduction of refrigerant pressure drop to increase thermal radiation magnitude and improve heat exchange efficiency, thereby the heat exchanger is miniaturized into compact size.
Description
Technical field
The present invention relates to a kind of plate that is used for heat exchanger, relate more specifically to a kind of like this plate that is used for heat exchanger, this plate has the projection (bead) of the cold-producing medium distribution portion that is formed asymmetrically, and equal number with the streamlined projection of zigzag arranged in form on flow channel, thereby the cold-producing medium that flows is distributed equably and inlet tube in, increase thermal exposure and strengthen heat exchanger effectiveness by forming even flow distribution thus, and the reduction refrigerant pressure drop, thereby make the small-sized compact size that changes into of heat exchanger.
Background technology
Usually, heat exchanger is meant such equipment, wherein, has the flow channel that is used for heat exchange medium, thereby heat exchange medium is at this flow channel circulation time of process and extraneous air heat-shift.Heat exchanger is used in the various air-conditioning equipments, and adopts various forms according to the various conditions of using heat exchanger, such as fin tube type, snakelike formula, pull and stretch is cup type and parallel flow type.
Heat exchanger has and uses the evaporimeter of cold-producing medium as heat exchange medium, this evaporimeter to be divided into a case, two casees and four box:
In a box type heat-exchanger, by connecting pipe that two one boxboards form by alternately laminated together with thermal radiation plate, described each plate all has a pair of cupule that is formed on the one end thereof place and the U-shaped passage that is limited by the separation projection that is arranged in this cupule.
In the two-box type heat exchanger, by connecting pipe that two two boxboards form by alternately laminated together with thermal radiation plate, described each plate all has the cupule that is respectively formed at its top and place, bottom.
In four box type heat-exchangers, by connecting pipe that two four boxboards form by alternately laminated together with thermal radiation plate, described each plate all has and is formed on its top and the paired cupule at place, bottom and two passages being opened by channels separated.
Hereinafter, for simplicity, will be described as example with a box type heat-exchanger.
As shown in Figures 1 to 3, heat exchanger 1 comprises: a plurality of by connecting two laminated tubes 10 that plate 11 forms, each Guan Jun has an a pair of cupule 14 and a U-shaped passage 12, this is formed on top or the top and the place, bottom of pipe 10 abreast to cupule 14, and having groove 14a respectively, this U-shaped passage 12 is used for fluid and is communicated with by vertically being formed on separation projection 13 casees that limit 40 between the case 40, predetermined length; Be laminated on the thermal radiation plate 50 between the pipe 10; And two end plates 30, this two end plates 30 is installed in the outermost of pipe 10 and fin 50 so that they are strengthened.
In addition, two plates 11 respect to one another are handled by relief (embossed), and a plurality of first projectioies 15 of inwardly stretching out of plate 11 are engaged, thereby form the turbulent flow of cold-producing medium in the flow channel 12 of pipe 10.
In addition, in each pipe 10, flow channel 12 has the cold-producing medium distribution portion 16 that is formed on its entrance side and outlet side, and wherein each cold-producing medium distribution portion 16 all has separated a plurality of passage 16b by a plurality of second protruding 16a, so that cold-producing medium is assigned in the flow channel 12 equably.
In addition, because double end plate and single head plate 11 are roughly the same except the bottom at the double end plate is provided with two cupules, therefore hereinafter for convenience's sake, only description has the single head plate 11 that is formed on two cupules 14 on the top.
Pipe 10 also comprises manifold 20 that stretches to case 40 sides and the manifold 20a that stretches to case 40 other sides, wherein a manifold in the manifold 20 has the inlet manifold 21 that links to each other with the inlet tube 2 that is used to introduce cold-producing medium, and a manifold among the manifold 20a has the outlet manifold 21a that links to each other with the outlet 3 that is used for refrigerant emission.
Manifold 21 is configured to by making two manifold plates that have semicircle manifold 21 and 21a respectively contact the round tube type that forms with 21a.Manifold 21 and 21a combine with inlet tube 2 and outlet 3 by ring-like brazing material, by moving weldering manifold 21 and 21a, inlet tube 2 and outlet 3 are combined each other then.
In addition, except manifold 21 and 21a, manifold 20 is identical with pipe 10 with 20a.
As mentioned above, with reference to Fig. 1 cold-producing medium flowing in heat exchanger 1 described below.
Therefore, case 40 is separated into the outlet side 5 that is used to introduce the entrance side 4 of cold-producing medium and is used for refrigerant emission based on dividing plate 60, in the drawings, the case 40 of entrance side 4 is represented as " A " and " B " part, and the case 40 that is used for the outlet side 5 of refrigerant emission is represented as " C " and " D " part.
When introducing by entrance side manifold 21, cold-producing medium is assigned in the A part of case 40 equably, and flows along the U-shaped flow channel 12 of pipe 10 and 20.Subsequently, cold-producing medium is introduced in the B part of adjacent case 40, and flows in the C part of same case 40.Cold-producing medium still flows along the U-shaped flow channel 12 of pipe 10 and 20a, and is introduced into subsequently in the D part of the case 40 with outlet manifold 21a, so that finally be discharged to the outside.
During the process that the cold-producing medium that circulates along refrigerant line in refrigeration system is introduced into and discharges, heat exchanger 1 and the air generation heat exchange of blowing between pipe 10,20 and 20a also make the cold-producing medium evaporation, thus, the air that is blown out to automotive interior is cooled by the heat absorption effect by means of the evaporation latent heat of cold-producing medium.
In recent years, along with the compactness of heat exchanger 1 and the development trend of miniaturization, heat exchanger 1 must be provided with structure and the performance that satisfies efficient and low refrigerant pressure drop.Especially, if refrigerant pressure descends,,, may cause that then work increase of compressor (not shown) and system effectiveness reduce because of high refrigerant pressure drop if therefore heat exchanger 1 is by the plate manufacturing of existing form because heat exchanger 1 narrows down gradually.
That is to say that the heat exchanger of prior art comprises: with first projection 15 that predetermined space forms along flow channel 12, these projectioies 15 are bonded to each other, so that increase the thermal efficiency of heat exchanger 1 and guarantee the durability of heat exchanger 1; And cold-producing medium distribution portion 16, this cold-producing medium distribution portion 16 has the second protruding 16a that forms with predetermined space, so that the cold-producing medium that will be stored in the case 40 is assigned in the flow channel 12 equably, and guarantees durability.
Yet, be similar to the plate 11 of prior art, if first projection 15 and the second protruding 16a that is formed on the cold-producing medium distribution portion 16 form at interval symmetrically with rule, as shown in Figure 4, then cold-producing medium can form uniform flow distribution, thermal exposure and heat exchanger effectiveness are reduced, and be difficult to make the small-sized compact size that changes into of heat exchanger.
That is to say that in Fig. 4, aterrimus is represented the part that big flow cold-producing medium flows fast, light/dark balance is represented the part that the low discharge cold-producing medium slowly flows.
Therefore, when the overall flow of our access panel, another problem that plate 11 has is, refrigerant flow is less in the center of width (laterally) direction, and bigger at both sides places, and when we only observe cold-producing medium distribution portion mobile, then there is such problem, promptly owing to the speed of cold-producing medium stream is slowed down gradually towards the both sides of cold-producing medium distribution portion 16, therefore big flow cold-producing medium flows in the center of cold-producing medium distribution portion 16, and the low discharge cold-producing medium is evenly mobile.
In addition, another problem that plate 11 is had is, when cold-producing medium along vertical (vertically) direction of this plate 11 big flow flow of refrigerant and assembling during further from cold-producing medium distribution portion 16.
As mentioned above, the plate 11 of prior art shows usually along the uneven flow of refrigerant of all directions and distributes.
Summary of the invention
Therefore, made the present invention for solving the problems referred to above that occur in the prior art, and the object of the present invention is to provide a kind of plate that is used for heat exchanger, this plate has center line with respect to a cupule and is formed asymmetrically second projection on the cold-producing medium distribution portion of this plate, and streamlined first projection that forms along flow channel, the arrangement of described first projection of equal number is with the zigzag arranged in form, so that the cold-producing medium of case is distributed and is incorporated into the flow channel of pipe, increase thermal exposure and improve heat exchanger effectiveness by forming even flow distribution thus, and the reduction refrigerant pressure drop, thereby make the small-sized compact size that changes into of described heat exchanger.
To achieve these goals, according to the present invention, provide a kind of plate that is used for heat exchanger, this plate comprises: thus the cupule that the flow channel fluid in being formed on described plate end place and being formed on this plate is communicated with; A plurality of first projectioies, described a plurality of first projectioies are stretched to described flow channel, so that the cold-producing medium that flows in described flow channel forms turbulent flow; And the cold-producing medium distribution portion that is formed on the entrance side and the outlet side of described flow channel, this cold-producing medium distribution portion have one or more second the projection and by described second the projection separated a plurality of paths, it is characterized in that: each is arranged described first projection and all repeats to arrange with the zigzag form with equal number, and described second projection is arranged with respect to the described center line of described cupule asymmetricly, the described inlet of wherein said flow channel and described outlet are formed parallel to each other by the separation projection that is formed on described plate center, and the area of section of path that is formed on described separation convex side with respect to the described center line of described cupule is less than the area of section of the path that is formed on opposition side, and it is big to be formed on described other second projectioies of described second convexity than MP major path one side.
Description of drawings
By can obviously finding out above-mentioned and other purposes, feature and advantage of the present invention to the detailed description of the preferred embodiment of the present invention, in the accompanying drawings below in conjunction with accompanying drawing:
Fig. 1 is the stereogram of prior art heat exchanger (evaporimeter);
The stereogram of Fig. 2 state that to be expression pipe be separated with the heat exchanger of prior art;
Fig. 3 is the view on top of the plate of Fig. 2;
Fig. 4 is the view that the flow of refrigerant of the plate of presentation graphs 3 is distributed;
Fig. 5 is the stereogram that the state that is separated with heat exchanger according to the present invention is managed in expression;
Fig. 6 is the view on top of the plate of presentation graphs 5;
Fig. 7 is expression heat-radiating properties and refrigerant pressure drop about the curve map according to the breadth length ratio of first projection of the present invention;
Fig. 8 is the view that the flow of refrigerant of the plate of presentation graphs 6 is distributed;
Fig. 9 is illustrated in according in the heat exchanger of the present invention, at the entrance side of the flow channel of plate and the view that outlet side forms the state of second projection with tilting; And
Figure 10 is that expression is formed on the view according to another form of first and second projectioies on the plate in the heat exchanger of the present invention.
The specific embodiment
The preferred embodiment of the present invention will be described in detail below with reference to accompanying drawings.
Use the same reference numerals to represent with prior art in same or analogous parts, and no longer repeat its description.
Fig. 5 is the stereogram that the state that is separated with heat exchanger according to the present invention is managed in expression, Fig. 6 is the view on top of the plate of presentation graphs 5, Fig. 7 is expression heat-radiating properties and refrigerant pressure drop about the curve map according to the breadth length ratio of first projection of the present invention, Fig. 8 is the view that the flow of refrigerant of the plate of presentation graphs 6 is distributed, and Fig. 9 is illustrated in according to the entrance side of the flow channel of the plate in the heat exchanger of the present invention and the view that outlet side forms the state of second projection with tilting; And Figure 10 is the view that is illustrated in according to another form of first and second projectioies that form on the plate in the heat exchanger of the present invention.
Although what obviously easily see is that the present invention can similarly be applied to a case, two casees and four box type heat-exchangers, for convenience's sake, below will only be described in conjunction with the single box heat exchanger.
As shown in the figure, heat exchanger 1 according to the present invention comprises: a plurality of pipes 100, each Guan Jun forms by engaging two plates 101, this plate 101 has the cupule 104 of the pair of parallel that is formed on its place, top, each Guan Jun has a pair of case 140 that forms by cupule 104 is engaged with each other, and it is inner around separating the U-shaped flow channel 102 that projection 103 medially forms at pipe, so that make case 140 fluid communication with each other, described separation projection 103 is vertically formed between case 140 with predetermined length;
Be plugged in the thermal radiation plate 50 of managing between 100 with curve form, be used for improving heat exchange performance by enlarging the electric heating area; And
Two end plates 30, these two end plates are installed in the outermost of pipe 100 and thermal radiation plate 50 so that this pipe 100 and thermal radiation plate 50 are strengthened.
In addition, pipe 10 also comprises manifold 20 that stretches to case 40 sides and the manifold 20a that stretches to case 40 other sides, wherein a manifold in the manifold 20 has the inlet manifold 21 that links to each other with the inlet tube 2 that is used to introduce cold-producing medium, and a manifold among the manifold 20a has the outlet manifold 21a that links to each other with the outlet 3 that is used for refrigerant emission.
Here, except the inlet manifold 20 and outlet manifold 21a that stretch to the side, manifold 20 is identical with pipe 10 with 20a.
In addition, the case 40 with inlet manifold 21 and outlet manifold 21a has the dividing plate 60 that is formed on wherein, and it is separated from one another that this dividing plate 60 is used for the cold-producing medium of the cold-producing medium that will introduce and discharging.
Laminated tube 100 is divided into the outlet side 5 that is used to introduce the entrance side 4 of cold-producing medium and is used for refrigerant emission by dividing plate 60.
Therefore, the cold-producing medium that is introduced in the inlet tube 2 flows along the pipe 20 of the entrance side 4 that is separated out by dividing plate 60 and 100 U-shaped flow channel 102, and flows to outlet side 5.Subsequently, cold-producing medium flows along the U-shaped flow channel 102 of the pipe 20a of outlet side 5 and 100, and with after outlet 3 discharge.Certainly, flow through in order in the process of pipe 100 of entrance side 4 and outlet side 5 at cold-producing medium, this cold-producing medium makes this extraneous air cooling by the heat exchange with extraneous air.
This heat exchanger 1 has the entrance side of the flow channel 102 that is formed on pipe 100 and the cold-producing medium distribution portion 106 of outlet side, and this cold-producing medium distribution portion 106 has separated a plurality of path 106b by a plurality of second protruding 106a.
At this, because the separation projection 103 of the center of flow channel 102 by being formed on plate 101 and forming with the U-shaped shape, so the entrance and exit of flow channel 102 forms abreast.Certainly, in this case, above-mentioned heat exchanger is a box type heat-exchanger, and still, in two-box type or four box type heat-exchangers, the entrance and exit of flow channel 102 forms in the opposite direction.
In addition, the second protruding 106a is formed asymmetrically and arranges with respect to the center line (CL) of cupule 104, distributes equably and is incorporated in the flow channel 102 so that will be stored in cold-producing medium in the case.
That is to say that the second protruding 106a is in quantity, interval and be formed asymmetrically with respect to the center line (CL) of cupule 104 in shape.
Fig. 6 represents to have the example of the plate of second projection that is formed asymmetrically.In Fig. 6, be formed with two second protruding 106a with respect to the center line (CL) of cupule 104 separating protruding 103 sides, and be formed with one second protruding 106a in the outside.In addition, in Fig. 6, the second protruding 106a between them the interval and all be asymmetric in shape.
Certainly, in the drawings, the second protruding 106a is at quantity, interval and be formed asymmetrically in shape, but the present invention is not limited to said structure, but can be in quantity, interval and shape at least a on be formed asymmetrically.
In addition, each second protruding 106a ranked first projection and 105 is formed asymmetrically with first on the interval.Here, preferred at least one second protruding 106a is formed asymmetrically, and ranked first interval (L1) between protruding 105 greater than the outermost second protruding 106a and first but preferred adjacent sub ranked first interval (L3) between the projection 105 every the second protruding 106a and first of projection 103.
In addition, path 106b is formed on the area of section of separating protruding 103 sides is formed on opposite side less than path 106b area of section with respect to the center line (CL) of cupule 104, thus, when the cold-producing medium in the case 140 was introduced in the flow channel 102, the cold-producing medium that concentrates on the middle part was directed into the outside of flow channel 102.In this case, form greatlyyer, gather the outside so that prevent too much cold-producing medium than other protruding 106a towards the second protruding 106a that forms than major path 106b.
In addition, in order when making heat exchanger, to make plate 101 have versatility, preferably the cold-producing medium distribution portion 106 and first projection 105 are formed symmetrically from separating projection 103.
That is to say, making pipe at 100 o'clock, make two plates 101 toward each other and engage, and in this case, make to be formed on the projection of first on two plates 101 105 and second protruding 106a and to be engaged with each other, so that strengthen the resistance to pressure of heat exchanger.As mentioned above, if the cold-producing medium distribution portion 106 and first projection 105 form symmetrically from separating projection 103, in order to make pipe 100, only one type plate 101 can be made being used for a general pressing mold, does not need to make individually two plates 101 so.
Simultaneously, the shape and size of the second protruding 106a of cold-producing medium distribution portion 106 increase laterally gradually, and at least one second protruding 106a is arranged on the same line with at least one first projection 105.
In addition, be formed with a plurality of first projectioies 105, these first projectioies 105 arrange by the side that engages a pair of plate that faces with each other 101, thereby form the turbulent flow of cold-producing medium in the flow channel 12 of pipe 100.
That is to say, by the relief method of moulding first projection 105 is inwardly stretched out along the flow channel 102 of plate 101, and arrange obliquely, so that improve the mobile of cold-producing medium and cause the turbulent flow of cold-producing medium with grid.First projection 105 that is formed on two plates 101 is engaged with each other by soldering under the state that contacts with each other.
In addition, the arrangement of first projection 105 has first projection 105 of equal number, and arranges at regular intervals, so that make that the flow distribution of cold-producing medium is even, still preferred arrangement with first projection 105 repeats to arrange with zigzag.
In this case, preferably, first projection 105 that is formed on the top place of flow channel 102 is formed asymmetrically with respect to the center line (CL) of cupule 104.
Therefore, the combination of the dissymmetrical structure by cold-producing medium distribution portion 106 and the dissymmetrical structure of first projection 105 topmost, assignment system cryogen equably.That is to say that the cold-producing medium that flows can flow in the flow channel 102 more equably in case 140.
In addition, first projection 105 is with streamlined formation, so that reduce refrigerant pressure drop.
That is to say, fairshaped first projection 105 makes refrigerant pressure drop reduce, thereby cold-producing medium can flow reposefully along the fairing ace of first projection 105, and can not produce big pressure on the stagnation point of the cold-producing medium inflow direction of first projection 105.
Therefore, first projection 105 according to the present invention is with streamlined formation, so that reduce the pressure of the front end of this first projection 105 along the cold-producing medium inflow direction, eliminate the inhomogeneities that flow of refrigerant is distributed, and strengthened electric heating property, this first projection 105 is subjected to the restriction of wide (W) long (L) than (W/L).
Shown in the curve of Fig. 7, when the breadth length ratio (W/L) of first projection 105 hour, the pressure drop of cold-producing medium reduces, but heat-radiating properties descends (approximately 2-3%).
But when the breadth length ratio (W/L) of first projection 105 was big, heat-radiating properties improved, but the pressure drop of cold-producing medium also increases, and therefore, flow of refrigerant is distributed and become inhomogeneous.
Therefore, the breadth length ratio of preferred first projection 105 (W/L) satisfies following formula: 0.3＜W/L＜0.9, and this is a suitable scope.
Fig. 8 represents to distribute according to the flow of refrigerant of the layout of first projection, the 105 and second protruding 106a, and as shown in the figure, compare with respect to the flow of refrigerant distribution of center line (CL) symmetric arrangement of cupule 104 with the rule interval with the second protruding 16a with first projection 15 of prior art, flow of refrigerant of the present invention is distributed more even usually.That is to say that because less with the velocity deviation of length (vertical) direction along width (laterally) direction of flow channel 102, therefore plate 101 according to the present invention shows usually uniformly and flows.
Fig. 9 is the view of the state that is formed obliquely of expression second projection.As shown in the figure, be formed on two second protruding 106a that separate protruding 103 sides with respect to the center line (CL) of cupule 104 and be formed obliquely, and one the second protruding 106a that is formed on opposite side is formed obliquely along outward direction towards separating projection 103.
Therefore, accumulate in the both sides that cold-producing medium around the middle part of cold-producing medium distribution portion 106 can be drawn towards flow channel 102.
Simultaneously, Fig. 9 represents that a pair of cupule 104 forms with circle, but should be appreciated that, this cupule 104 can form with other any one shape.
Figure 10 represents to form other forms of first and second projectioies onboard.As shown in the figure, be increased more than the quantity of before first and second projectioies in the quantity of first shown in Figure 10 projection, the 105 and second protruding 106a, promptly first projection 105 is with three formation of every row, and the second protruding 106a is with four formation of every row.
Equally in this case, the second protruding 106a of cold-producing medium distribution portion 106 is formed asymmetrically with respect to the center line (CL) of cupule 104, and first projection 105 forms with streamline form, and the arrangement that has in this case, first projection 105 of equal number repeats to arrange with zigzag.
As mentioned above, do not consider the quantity of first projection, the 105 and second protruding 106a, then second of the cold-producing medium distribution portion 106 protruding 106a is formed asymmetrically with respect to the center line (CL) of cupule 104, first projection 105 forms with streamline form, and the arrangement with first projection 105 of equal number repeats with zigzag, thus, the flow of refrigerant distribution becomes even, refrigerant pressure drop reduces, thereby increased thermal exposure and improved heat exchanger effectiveness, so that help to make the small-sized compact size that changes into of heat exchanger.
As mentioned above, the arrangement form of first projection, the 105 and second protruding 106a is applied to a box type heat-exchanger 1, but the present invention does not limit to above-mentioned layout, can revise first projection, the 105 and second protruding 106a in the scope of claim of the present invention in every way.In addition, also can be with identical structure applications in two-box type or four box type heat-exchangers, so that obtain the effect identical with the present invention.
The plate that is used for heat exchanger comprises that the center line with respect to cupule is formed asymmetrically second projection on the cold-producing medium distribution portion of plate, and streamlined first projection that forms along flow channel, whenever ranked first projection arranges by zigzag with equal number, so that in the flow channel with distribution of the cold-producing medium in the case and inlet tube, thus, increase thermal exposure and improve heat exchanger effectiveness by forming even flow distribution and reducing refrigerant pressure drop, thereby with the small-sized compact size that changes into of heat exchanger.
Although described the present invention with reference to concrete exemplary embodiment, the present invention is not limited by the examples, and only is limited by the appended claims.Should be understood that those skilled in the art can change or revise described embodiment under situation about not departing from the scope of the present invention with spirit.
Claims (10)
1. plate that is used for heat exchanger, this plate comprises: the end that cupule (104), this cupule (104) are formed on this plate sentence just be formed on described plate in flow channel (102) fluid be communicated with; A plurality of first projectioies (105), these a plurality of first projectioies (105) are stretched to described flow channel (102) so that make the cold-producing medium that flows form turbulent flow in this flow channel (102); And the cold-producing medium distribution portion (106) that is formed on the entrance side and the outlet side of described flow channel (102), this cold-producing medium distribution portion (106) has one or more second projectioies (106a) and by the separated a plurality of paths of described second projection (106a) (106b)
It is characterized in that: described first projection of every row (105) repeats to arrange by the zigzag form with equal number, and described second projection (106a) is arranged with respect to the center line (CL) of described cupule (104) asymmetricly;
The entrance and exit of wherein said flow channel (102) is formed parallel to each other by the separation projection (103) that is formed on described plate (101) center, and be formed on the area of section of the area of section of the described path (106b) of separating projection (103) side with respect to the described center line (CL) of described cupule (104), and it is bigger than other second projectioies (106a) to be formed on described second projection (106a) of the bigger path of cross-sectional area (106b) side less than the path that is formed on opposition side (106b).
2. the plate that is used for heat exchanger according to claim 1, the quantity of wherein said second projection (106a) is asymmetric.
3. the plate that is used for heat exchanger according to claim 1, wherein said second projection (106a) is asymmetric on the interval between this second projection.
4. the plate that is used for heat exchanger according to claim 1, wherein said second projection (106a) is being asymmetric in shape.
5. the plate that is used for heat exchanger according to claim 1, what wherein each described second projection (106a) and first was arranged described first projection (105) is irregular at interval.
6. the plate that is used for heat exchanger according to claim 1, wherein said first projection (105) is streamlined, and wide (W) long (L) satisfies following formula than (W/L):
0.3<W/L<0.9。
7. the plate that is used for heat exchanger according to claim 1, wherein, be formed on described described second projection (106a) of separating projection (103) side towards described separations projection (103) inclination with respect to the described center line (CL) of described cupule (104), and described second projection (106a) that is formed on opposite side tilts laterally.
8. the plate that is used for heat exchanger according to claim 1, wherein, described cold-producing medium distribution portion (106) and described first projection (105) form symmetrically with respect to described separation projection (103).
9. the plate that is used for heat exchanger according to claim 1, described first projection (105) that wherein is formed on the top place of described flow channel (102) is formed asymmetrically with respect to the described center line (CL) of described cupule (104).
10. the plate that is used for heat exchanger according to claim 5, wherein, contiguous described described second projection (106a) and first of separating projection (103) is arranged the interval (L3) of described first projection greater than the interval (L1) of outermost second projection (106a) with described first projection of first row.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006101599773A CN100533046C (en) | 2006-09-29 | 2006-09-29 | Plate used for heat converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006101599773A CN100533046C (en) | 2006-09-29 | 2006-09-29 | Plate used for heat converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101153771A CN101153771A (en) | 2008-04-02 |
| CN100533046C true CN100533046C (en) | 2009-08-26 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006101599773A Active CN100533046C (en) | 2006-09-29 | 2006-09-29 | Plate used for heat converter |
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| CN (1) | CN100533046C (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103759474B (en) * | 2014-01-28 | 2018-01-02 | 丹佛斯微通道换热器（嘉兴）有限公司 | Plate type heat exchanger |
| CN106322743B (en) * | 2015-06-30 | 2022-05-17 | 深圳市泰金田科技有限公司 | Electromagnetic heating device |
| CN108827676B (en) * | 2018-04-25 | 2020-12-11 | 合肥美的电冰箱有限公司 | Heat dissipation measurement system and method and control device thereof |
| JP7126048B2 (en) * | 2018-08-08 | 2022-08-26 | パナソニックＩｐマネジメント株式会社 | ultrasonic flow meter |
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2006
- 2006-09-29 CN CNB2006101599773A patent/CN100533046C/en active Active
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| CN101153771A (en) | 2008-04-02 |
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