CN2821505Y - Evaporator heat exchanging tube - Google Patents
Evaporator heat exchanging tube Download PDFInfo
- Publication number
- CN2821505Y CN2821505Y CN 200520074448 CN200520074448U CN2821505Y CN 2821505 Y CN2821505 Y CN 2821505Y CN 200520074448 CN200520074448 CN 200520074448 CN 200520074448 U CN200520074448 U CN 200520074448U CN 2821505 Y CN2821505 Y CN 2821505Y
- Authority
- CN
- China
- Prior art keywords
- fin
- wing
- exchange tube
- outer fin
- heat exchange
- 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.)
- Expired - Lifetime
Links
Images
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A heat exchanging tube for an evaporator in a refrigerating system and an air conditioning system belongs to the technical field of heat exchange. The heat exchanging tube for an evaporator comprises a tube body, outer fins and grooves, wherein the outer fins which are provided with fin-top dummy clubs are arranged at the top part of the surface of the outer wall of the tube body, each of the grooves is positioned between every two contiguous outer fins, and fin-top edges are extended from both sides of each of the fin-top dummy clubs in opposite directions. The fin-top edges correspond to the fin-top edges which are formed by that both sides of each of the fin-top dummy clubs of two contiguous outer fins are similarly extended in opposite directions. The corresponding degree is that cavity openings of groove cavities of the grooves are closed in the state that the cavity openings have gaps, and the whole groove cavities are in the structures of hollow cavities. Horizontal fins which are used for forming the hollow cavities into the structures of duplex hollow cavities are arranged at intervals on the fin walls which are along the extending directions of the outer fins and near the middle parts of the outer fins. The utility model has the advantages of excellent boiling heat exchanging coefficient can be brought, the effect of boiling heat exchange can be strengthened and the utility model has the effect of saving materials and reducing the weight of the tube body of the tube.
Description
Technical field
The utility model relates to the heat-exchange tube that the evaporimeter in a kind of refrigeration and the air-conditioning system is used, and more specifically says it is the heat exchange tube of evaporator that a kind of outer wall of pipe is formed with compound void structure surface, belongs to technical field of heat exchange.
Background technology
In many fields such as refrigeration, air-conditioning, process engineering, petrochemical industry and the energy and power engineerings, relate to boiling and the evaporation of liquid at the tube bank outer surface.Especially the refrigeration and air-conditioning system in used evaporimeter, the forced-convection heat transfer thermal resistance is suitable even greater than forced-convection heat transfer thermal resistance in managing in the boiling heat transfer thermal resistance of its cold-producing medium when the outer boiling of pipe and the pipe, therefore, the outer boiling heat transfer of enhanced tube can play remarkable result for the heat transfer property that improves evaporimeter.
About studies show that of nucleate boiling mechanism, the boiling of liquid needs the existence of the nucleus of boiling.Under the condition of the degree of superheat of the given area of heating surface, have only radius when the nucleus of boiling greater than the needed least radius of air bubble growth, bubble just can be grown up, and nucleate boiling just can be carried out.And the formed hole in groove on the area of heating surface and crack most probable becomes the nucleus of boiling.In boiling process, after bubble is grown up the disengaging hole, because the effect of surface tension of liquid, the liquid that the part steam that hold back in these holes is difficult to be flowed into is thoroughly evicted from, just become the new nucleus of boiling, grow new bubble, make boiling process constantly continue.Hence one can see that, need to strengthen the nucleate boiling heat exchange, and key is to form numerous nucleus of boiling at the area of heating surface.Therefore, the many developments that start from the enhanced boiling heat transfer surface of the seventies in 20th century all launch round forming loose structure at the area of heating surface, and in numerous documents, can be seen in, for example Chinese patent 95246323.7 (Granted publication 2257376Y) and the disclosed evaporimeter heat-exchange tube of Chinese patent 03207498.0 (Granted publication 2662187Y), its outer surface is the helical fin that the top is pressed into T shape, to constitute groove structure; Chinese patent 95118177.7 (Granted publication 1090750C) and the disclosed heat-exchange tube of Chinese patent 02263461.4 (Granted publication 2557913Y), its outer surface is provided with has along the circumferential direction uniform the helical fin of helical teeth, the fin tooth top is extended to both sides constitute void structure; The disclosed heat-exchange tube of Chinese patent application prospectus CN1366170A (application number 02101870.7), its outer surface adopt machining process to form fin, and the bottom land of the preliminary trench between fin forms secondary slot; The disclosed heat-exchange tube of Chinese patent CN1100517A (application number 94116309.1) is toppled over Yi Bian the fin of its outer surface is pressed towards, and constitutes void structure by pressing groove again at the fin shoulder; The disclosed evaporimeter heat-exchange tube of Chinese patent 02264793.7 (Granted publication 2572324Y), its outer surface adopt machining process to form the helical fin with broached-tooth design, and extrude skewed slot at the sawtooth top, so as to constituting void structure.The common feature that above-mentioned document promptly is accustomed to the structure of alleged outer fin to the outer wall surface of heat-exchange tube is to have smaller groove structure of opening or a void structure, constructing the place that forms the nucleus of boiling, thereby reaches the effect of strengthening boiling heat transfer.
Along with to the going deep into of nucleate boiling mechanism research, it is found that after bubble formed, in the growth course of bubble, the evaporation of bubble end liquid microbedding played important or even overriding effect.The experiment of low liquid level boiling heat transfer shows, after liquid level is lower than certain critical value (this critical value is less than 2 times of bubble diameter), behind previous bubble disengagement area of heating surface buoyance lift, because of the inhibition that is subjected to liquid level can not be at once away from the area of heating surface, back one bubble just has been subjected to constraining of last bubble and has been hemispherical growth when growth, thereby can make bubble end liquid microbedding have bigger disengagement area, boiling heat transfer coefficient be had the effect of obvious rising.Experiment shows that also because the thickness of bubble end liquid microbedding is approximately 1 micron the order of magnitude, its thermal resistance is very little, if the duration of managing to increase the area of bubble end microbedding liquid film or prolonging bubble end microbedding liquid film just can make boiling heat transfer be strengthened.Yet, the structure that finds expression in the outer outer fin of heat exchange tube of evaporator pipe in the disclosed document all is not enough to embody by indicated the having of above-mentioned experimental result and makes boiling heat transfer coefficient effect that significantly improves and the effect that boiling heat transfer is significantly strengthened, and the weight of pipe is bigger, causes waste of raw materials.
Summary of the invention
But the purpose of this utility model is will provide a kind of can make that heat-exchange tube outer surface and the boiling heat transfer coefficient of pipe between the outer liquid are significantly improved, boiling heat transfer is significantly strengthened and the heat exchange tube of evaporator of weight reduction also.
The purpose of this utility model reaches like this, a kind of heat exchange tube of evaporator, comprise body 1 and extend the outer fin 2 of tool wing top, the top boss 3 on the outside wall surface of body 1 and groove between the fin 26 outside adjacent, extend in opposite directions and constitute wing top edge 3a in the both sides of described wing top boss 3, the wing top edge 3a that wing top edge 3a constitutes with similarly being extended in opposite directions by the both sides of the wing top boss 3 of adjacent outer fin 2 scoops out mutually, the degree that scoops out that this scoops out be so that the vallecular cavity accent of described groove 6 is closed into the state in tool gap and make vallecular cavity be void structure on the whole; Outside described the nearly middle part of fin 2 and along outside on the wing wall of fin 2 bearing of trends the compartment of terrain extend and be useful on the horizontal fin 4 that described hole is constituted compound void structure.
The wing top boss 3 at the top of outer fin 2 described in the utility model is any one in T shape, the spike.
The utility model is provided with skewed slot 8 between going back on the fin 2 outside described, the bottom position of skewed slot 8 is higher than the root position of described horizontal fin 4, the 0.1-0.5mm that the degree of depth of skewed slot 8 is, and the groove number of skewed slot 8 on every centimetre length on the bearing of trend of fin outside described 2 is the 10-25 bar, and the angle α between the bearing of trend of outer fin 2 is 40-50 °, by skewed slot 8 shape of described wing top boss 3 is constituted spike tooth platform, spike tooth platform and contrate 4 constitute staggered, at the top surface of spike tooth platform and then have additional tooth top skewed slot 11, the degree of depth of tooth top skewed slot 11 is 0.05-0.25mm, and the angle β between the bearing of trend of outer fin 2 is 130-140 °.
Being provided with on the outer fin 2 that quantity is the every centimetre length of fin 2 bearing of trends in addition of horizontal fin 4 described in the utility model established 10-25, the distance of center to the bottom of groove 6, wing top of each horizontal fin 4 is 0.2-0.75 with the wing height ratio of outer fin 2, the width of horizontal fin 4 is 〉=0.2mm, and with its ratio≤0.8 along the wing distance of the bearing of trend of outer fin 2.
The inwall of body 1 described in the utility model is provided with inner fin 7, and this inner fin 7 is that shape is provided with in the shape of a spiral, highly is 0.3-0.5mm, and with the angle γ of the center line formation of body 1 be 40-50 °.
One of the utility model advantage compared with the prior art, by being extended in opposite directions in the both sides of wing top boss 3 groove 6 is constituted void structure, set horizontal fin 4 on the direction that the waist that is aided with outer fin 2 again extends along outer fin 2, thereby with previous hole and then form compound void structure.In boiling heat transfer process, the bubble that generates in the bottom of groove 6 is subjected to the constraining of bubble above horizontal fin 4 and the horizontal fin 4 and expands to both sides along the bearing of trend of outer fin 2 in growth course, thereby makes the area of the bottom bubble end liquid microbedding of groove 6 obtain expansion.Along with bubble continue grow up, bubble will be broken through constraining of horizontal fin 4, with the bubbling polymerization on horizontal fin 4 tops, and overflow the gap between wing top boss 3, break away from heat-exchange tube.After bubble is overflowed, subcooled liquid will pour groove 6, and at this moment, horizontal fin 4 plays a part the impact of barrier liquid to residual gas again, makes void structure maintain the abundant nucleus of boiling, make the reinforcement boiling heat transfer be continued to carry out.The obvious effect that can bring excellent boiling heat transfer coefficient and strengthen boiling heat transfer; Two, because of contrate 4 is to extend and form in the nearly middle part of fin 2 outside,, have the effect of economical with materials, reduction body 1 weight so need not obtain heat exchange area by the height that improves outer fin 2.
Description of drawings
Fig. 1 is an example structure schematic diagram of the present utility model.
Fig. 2 is another example structure schematic diagram of the present utility model.
Fig. 3 is also example structure schematic diagram of the present utility model.
Fig. 4 is an example structure schematic diagram of horizontal fin 4 of the present utility model.
Fig. 5 is another example structure schematic diagram of horizontal fin 4 of the present utility model.
Fig. 6 is an also example structure schematic diagram of horizontal fin 4 of the present utility model.
Fig. 7 is the overall structure figure of the resulting heat exchange tube of evaporator of embodiment of the present utility model.
Fig. 8 is the variation relation figure of the overall heat-transfer coefficient of the heat exchange tube of evaporator of pressing the utility model making of measuring and the heat exchange tube of evaporator of pressing the prior art making with heat flow density.
Fig. 9 is the variation relation figure of the outer boiling heat transfer coefficient of pipe of the heat exchange tube of evaporator of pressing the utility model making of measuring and the heat exchange tube of evaporator of pressing the prior art making with heat flow density.
The specific embodiment
Below in conjunction with the drawings and specific embodiments the utility model is further described below.To help understanding the utility model, but do not constitute restriction of the present utility model.
Please refer to Fig. 1 to Fig. 4, process described outside after the fin 2, can adopt the different cutters nearly middle part of fin 2 outside, more properly say it is that the waist of fin 2 outside processes difform horizontal fin 4.Horizontal fin 4 that side surface of wing top boss 3 outward is the plane, and surperficial parallel with body 1.Horizontal fin 4 shown in Fig. 4 forms for adopting sharp-pointed Tool in Cutting, and makes horizontal fin 4 that side surface and outer fin 2 intersections formation acute angle of wing top boss 3 outward, and the direction of horizontal fin 4 fin 2 outside deviating from is slightly crooked.This horizontal fin 4 forms the additional nucleus of boiling at the easier residual gas of holding back in the acute angle place of root.
Please in conjunction with Fig. 5 and Fig. 6, the arrangement mode of horizontal fin 4 is decided on the width of groove 6.Relative arrangement mode shown in first-selected Fig. 1 to Fig. 4, the bearing of trend of horizontal fin 4 fin 2 outside described is equally spaced, and stretch out relative position from the side surface of the outer fin 2 of described groove 6 both sides, form pairing each other, its wing tip 5 or overlap or leave the horizontal fin 4 in gap each other makes in the vallecular cavity of described groove 6 and forms compound void structure.Here the notion in said compound hole can obtain understanding in the arbitrary accompanying drawing by Fig. 1 to Fig. 6, promptly becoming the vallecular cavity accent that makes groove 6 that extends in opposite directions the original both sides by wing top boss 3 only is closed into surplus one close clearance and the vallecular cavity of whole groove 6 is formed after the structure that is tending towards or claims the hole of approaching to seal again by horizontal fin 4 separations, make previous single hole become upper and lower two groups of holes, thereby be called compound hole.When the spacing of outer fin 2 too little, when groove 6 is too narrow, can adopt arrangement mode as shown in Figure 5, the bearing of trend of horizontal fin 4 fin 2 outside described is equally spaced, and outside described groove 6 both sides described, alternately stretch out on the position of sustained height on the fin 2 respectively, constitute each other staggered, its wing tip 5 or coincide with relative outer fin side surface, perhaps with between the relative outer fin side surface leave gap 10, both can both make at described groove 6 and constitute compound void structure; If the arrangement mode that horizontal fin 4 adopts as shown in Figure 6, horizontal fin 4 is located at a side of described outer fin 2 so, the bearing of trend of fin 2 is equally spaced outside described, its wing tip 5 or coincide with relative outer fin side surface, perhaps with between the relative outer fin side surface leave narrow crack 9, make described groove 6 form compound void structure.
Density on the bearing of trend of horizontal fin 4 fin 2 outside the edge is that the number of horizontal fin 4 on every centimetre length on the bearing of trend of fin outside described 2 is 10～25.Concrete numerical value is not only relevant with the width of groove 6, also depends on the shape of the wing top boss 3 of outer fin 2.For the T-shaped outer fin 2 of cross sectional shape as shown in Figure 1, the wing of horizontal fin 4 is 1.5～2 apart from the preference value with the ratio of the width of groove 6, and the actual horizontal fin wing of the heat-exchange tube of making according to the utility model is 1.6 apart from the ratio with recess width.For the structure of the spike tooth platform on the outer fin 2 shown in Fig. 2 and Fig. 3, the density on the bearing of trend of first-selected horizontal fin 4 fin 2 outside the edge is that horizontal fin 4 equates with the number of described spike tooth platform on every centimetre length on the bearing of trend of fin outside described 2 in the number on every centimetre length on the bearing of trend of fin outside described 2; Look from the direction perpendicular to the outer surface of described body 1 in its position, described horizontal fin 4 forms alternately with described spike tooth platform and arranges.
The existence of horizontal fin 4 has been divided into upper and lower two parts with groove 6, and the first half of groove 6 is near wing top boss 3, and the latter half is near the root of outer fin 2.Consider in the degree of superheat of the outer fin surface of the first half of groove 6 the latter half a little less than groove 6, therefore should be more bigger at the radius in the hole of the first half of groove 6, in addition, for ease of leaving heat-exchange tube simultaneously after the bubbling polymerization in groove 6 upper and lower two parts, the height of the first half of groove 6 is 1～2 with the first-selected span of the ratio of the height of the latter half, thereby get so that the first half of groove 6 can be held a complete bubble, and the latter half can be held a hemisphere bubble.The ratio of distance and the wing height of described outer fin 2 that the determining of the height and position of horizontal fin 4 preferably got center, wing top to the bottom of described groove 6 of horizontal fin 4 is 0.2～0.75.Because the effect of horizontal fin 4 is growth forms of constraining bubble, rather than hinders the growth of bubble or isolate bubble, therefore, horizontal fin 4 should form smooth curved surface towards that side surface of outer fin 2 roots, and avoids the wing tip 5 of horizontal fin 4 to form tip shape.If form tip shape owing to technologic restriction makes the wing tip 5, can allow the relative wing tip 5 coincide, perhaps allow the wing tip 5 and the side surface of outer fin 2 coincide.For same Consideration, the value of the width of horizontal fin 4 is, the width of horizontal fin 4 is more than or equal to 0.2mm, and is less than or equal to 0.8 with the ratio of the wing distance of the bearing of trend of described horizontal fin 4 fin 2 outside described.Excessive width will hinder the growth and the rising of bubble, and narrow width will isolate bubble, rather than flatten bubble.
After processing horizontal fin 4, can adopt prior art to continue the wing top boss 3 of the outer fin 2 of processing.One of scheme is that the wing top boss 3 of external fin 2 is vertically exerted pressure, and wing top boss 3 is extended to both sides, and what make described outer fin 2 is shaped as T shape (see figure 1).
Two of scheme is to leave one group of skewed slot 8 on the fin 2 outside, and externally the wing top boss 3 of fin 2 is vertically exerted pressure then, and the position of skewed slot 8 bottoms on the formed outer fin 2 is higher than the position of horizontal fin 4 roots; By two adjacent skewed slots 8 shape of wing top boss 3 is become spike tooth platform (seeing Fig. 2, Fig. 3).Offering of skewed slot 8 is not only in order to constitute spike tooth platform, but also in order to constitute netted groove structure together with groove 6, help the effusion of bubble and the inflow of liquid, therefore skewed slot 8 is of a size of, the degree of depth of skewed slot 8 is 0.1～0.5mm, and the position of described skewed slot 8 bottoms is not less than the position of described horizontal fin 4 roots, to avoid undermining or to claim to cut horizontal fin 4, and the number of skewed slot 8 on every centimetre length on the bearing of trend of fin outside described 2 be 10～25, and and the bearing of trend of described outer fin 2 between angle α be 40～50 °.
Three of scheme is to leave one group of skewed slot 8 on the fin 2 outside, outer fin 2 is constituted zigzag, and leave tooth top skewed slot 11 again one on the surface of each tooth platform, makes wing top boss 3 form spike tooth platform.Be understood that out that spike tooth platform is vertically to be exerted pressure in the top to spike tooth platform that the tooth top material forms to the passing of tooth top skewed slot 11 both sides, the opening size of groove 6 is controlled at according to the scope that needs, the heating surface of Xing Chenging therefrom, the position of its skewed slot 8 bottoms is higher than the position of horizontal fin 4 roots; The degree of depth of tooth top skewed slot 11 is 0.05～0.25mm, and the angle β between the bearing of trend of tooth top skewed slot and outer fin 2 is 130～140 °.
Can also adopt other schemes that the material of the wing top boss 3 of outer fin 2 is partly extended or is offset to side surface direction, so that the vallecular cavity of groove 6 forms other forms of void structure.In view of this, can't think that these void structures have the scope of taking off technical scheme disclosed in the utility model because of the appearance of the void structure of other form.
Outside enhanced tube, in the boiling heat transfer, be necessary the forced-convection heat transfer in the enhanced tube.This is because owing to be phase-change heat-exchange outside the pipe, when being the monophasic fluid forced-convection heat transfer in the pipe, the thermal resistance of pipe inboard is usually greater than pipe outside thermal resistance or suitable with the pipe external thermal resistance, have only when the inboard measure that also should take augmentation of heat transfer of pipe, improve the forced-convection heat transfer coefficient in the pipe, could effectively increase heat-transfer effect.If therefore inner fin 7 is set in body 1, can make the utility model boiling heat transfer system of mentioning in front and the effect of strengthening boiling heat transfer obtain more ultimate attainment raising so, because inner fin helped to improve the convection transfer rate in the body 1 in 70 minutes.Inner fin 7 discloses in Fig. 1 to Fig. 3, and it is the triangle inner fin; And be trapezoidal inner fin shown in Fig. 7, the inner fin of other cross sectional shapes can also be arranged, so the concrete shape of inner fin 7 is not limited by concrete shape disclosed in the utility model.But the common trait of inner fin 7 shows as helical form, and the angle γ of the helical angle that forms with the center line of described body 1 is preferably 40～50 °, and the height of inner fin 7 is preferably 0.3～0.5mm.
Please in conjunction with Fig. 8 and Fig. 9, the boiling heat transfer performance of the heat-exchange tube made according to the utility model is tested.The outer fin 2 of this body 1 is a helical fin, and the external diameter of body 1 (to the external diameter of wing top boss 3) is 18.89mm, and the wing height of outer fin 2 is 0.62mm, and the wing distance is 0.522mm; The degree of depth of skewed slot 8 is 0.18mm, and the angle α between the bearing of trend of outer fin 2 is 45 °, and the number on along the circumferential direction every centimetre length is 17; The degree of depth of tooth top skewed slot 11 is 0.08mm, and the angle β between the bearing of trend of outer fin 2 is 135 °; The width of horizontal fin 4 is 0.4mm, and the degree of depth is 0.32mm, and the number on along the circumferential direction every centimetre length is 19; Inner fin 7 is trapezoidal fin, and the wing height is 0.36mm, and wing is apart from be 1.14mm, with the angle γ of the helical angle of the center line formation of body 1 be 45 °.Heat-exchange tube does not as a comparison have horizontal fin 4.Experimental result shown in Figure 8 provided the heat-exchange tube made by the utility model and the overall heat-transfer coefficient of the heat-exchange tube made by prior art between comparison, experiment condition is: water flow velocity 1.6m/s in cold-producing medium R22,14.4 ℃ of saturation temperatures, the body 1, abscissa is heat flow density (kW/m among the figure
2), ordinate is overall heat-transfer coefficient (kW/m
2K), the filled circles among the figure is represented according to the resulting heat-exchange tube of the utility model, and filled box is represented heat-exchange tube of the prior art.Experimental result shown in Figure 9 provided the heat-exchange tube made by the utility model and the outer boiling heat transfer coefficient of pipe of the heat-exchange tube made by prior art between comparison, the implication of the filled circles among experiment condition and the figure, filled box representative is with the explanation to Fig. 8, and abscissa is heat flow density (kW/m among the figure
2), ordinate is the outer boiling heat transfer coefficient (kW/m of pipe
2K).Can see that therefrom the heat-exchange tube of making by the utility model is owing to set up horizontal fin 4, its heat transfer property has compared with prior art had ultimate attainment raising.
Claims (10)
1, a kind of heat exchange tube of evaporator, comprise body (1) and extend the outer fin (2) of tool wing top, the top boss (3) on the outside wall surface of body (1) and be positioned at groove (6) between the adjacent outer fin (2), extend in opposite directions and constitute wing top edge (3a) in the both sides that it is characterized in that described wing top boss (3), the wing top edge (3a) that wing top edge (3a) constitutes with similarly being extended in opposite directions by the both sides of the wing top boss (3) of adjacent outer fin (2) scoops out mutually, the degree that scoops out that this scoops out be so that the vallecular cavity accent of described groove (6) is closed into the state in tool gap and make vallecular cavity be void structure on the whole; The nearly middle part of fin outside described (2) and along outside on the wing wall of fin (2) bearing of trend the compartment of terrain extend and be useful on the horizontal fin (4) that described hole is constituted compound void structure.
2, heat exchange tube of evaporator according to claim 1, it is characterized in that described outer fin (2) be with helical form, annular shape, with body (1) be axial shape in extending any one extension mode and extend on the outside wall surface of body (1), the wing height of outer fin (2) is 0.4-1.6mm, and the wing distance is 0.4-1.5mm.
3, heat exchange tube of evaporator according to claim 1 and 2, the wing top boss (3) that it is characterized in that the top of described outer fin (2) are any one in T shape, the spike.
4, heat exchange tube of evaporator according to claim 1 and 2, it is characterized in that fin outside described (2) is provided with skewed slot (8) between going up also, the bottom position of skewed slot (8) is higher than the root position of described horizontal fin 4, the 0.1-0.5mm that the degree of depth of skewed slot (8) is, and the groove number of skewed slot (8) on every centimetre length on the bearing of trend of fin outside described (2) is the 10-25 bar, and the angle α between the bearing of trend of outer fin (2) is 40-50 °, by skewed slot (8) shape of described wing top boss (3) is constituted spike tooth platform, spike tooth platform and contrate (4) constitute staggered, at the top surface of spike tooth platform and then have additional tooth top skewed slot (11), the degree of depth of tooth top skewed slot (11) is 0.05-0.25mm, and the angle β between the bearing of trend of outer fin (2) is 130-140 °.
5, heat exchange tube of evaporator according to claim 1 is characterized in that described horizontal fin (4) is that plane and the mode parallel with the surface formation of body (1) extend in the middle part of outer fin (2) with its that side surface towards wing top boss (3).
6, heat exchange tube of evaporator according to claim 1 is characterized in that described horizontal fin (4) intersects towards that side surface of wing top boss (3) and outer fin (2) with it and constitutes acute angle and the mode of the bearing of trend formation bending of fin (2) towards deviating from outside and extending in the middle part of outer fin (2).
7, according to claim 1 or 5 or 6 described heat exchange tube of evaporator, it is individual to it is characterized in that being provided with of described horizontal fin (4) established 10-25 on the outer fin (2) that quantity is the every centimetre length of fin (2) bearing of trend in addition, the distance of center to the bottom of groove (6), wing top of each horizontal fin (4) is 0.2-0.75 with the wing height ratio of outer fin (2), the width of horizontal fin (4) is 〉=0.2mm, and with its ratio≤0.8 along the wing distance of the bearing of trend of outer fin (2).
8, heat exchange tube of evaporator according to claim 1, the inwall that it is characterized in that described body (1) is provided with inner fin (7), this inner fin (7) is that shape is provided with in the shape of a spiral, highly is 0.3-0.5mm, and with the angle γ of the center line formation of body (1) be 40-50 °.
9, heat exchange tube of evaporator according to claim 7, it is characterized in that described horizontal fin (4) is arranged on a side of outer fin (2), the bearing of trend of fin outside described (2) is equally spaced, the extension degree of its tooth tip (5) be stretched over contact with the wing wall of the outer fin (2) of a corresponding side and and the wing wall of the outer fin (2) of a corresponding side between constitute any one extension degree in narrow crack (9).
10, heat exchange tube of evaporator according to claim 7, it is characterized in that described horizontal fin (4) is made into the both sides that are arranged on outer fin (2) over the ground, the bearing of trend of fin outside described (2) is equally spaced, and any one degree of contacting, between the two constituting gap (10) interlocked, between the two constituted to the degree of correspondence of the tooth tip (5) each other for corresponding to constitute between the two.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520074448 CN2821505Y (en) | 2005-08-09 | 2005-08-09 | Evaporator heat exchanging tube |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520074448 CN2821505Y (en) | 2005-08-09 | 2005-08-09 | Evaporator heat exchanging tube |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2821505Y true CN2821505Y (en) | 2006-09-27 |
Family
ID=37018059
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200520074448 Expired - Lifetime CN2821505Y (en) | 2005-08-09 | 2005-08-09 | Evaporator heat exchanging tube |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2821505Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100365369C (en) * | 2005-08-09 | 2008-01-30 | 江苏萃隆铜业有限公司 | Heat exchange tube of evaporator |
| CN103903658A (en) * | 2014-03-19 | 2014-07-02 | 清华大学 | Sealing head with enhanced boiling heat exchange array hole surface with communicated net-shaped groove |
| CN105066761A (en) * | 2015-09-22 | 2015-11-18 | 烟台恒辉铜业有限公司 | Evaporating pipe with narrow-gap steam exhaust opening |
| CN109099741A (en) * | 2018-06-05 | 2018-12-28 | 东南大学 | A kind of heat exchange structure for strengthening boiling |
-
2005
- 2005-08-09 CN CN 200520074448 patent/CN2821505Y/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100365369C (en) * | 2005-08-09 | 2008-01-30 | 江苏萃隆铜业有限公司 | Heat exchange tube of evaporator |
| CN103903658A (en) * | 2014-03-19 | 2014-07-02 | 清华大学 | Sealing head with enhanced boiling heat exchange array hole surface with communicated net-shaped groove |
| CN105066761A (en) * | 2015-09-22 | 2015-11-18 | 烟台恒辉铜业有限公司 | Evaporating pipe with narrow-gap steam exhaust opening |
| CN109099741A (en) * | 2018-06-05 | 2018-12-28 | 东南大学 | A kind of heat exchange structure for strengthening boiling |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100365369C (en) | Heat exchange tube of evaporator | |
| US7841391B2 (en) | Flooded type evaporating heat-exchange copper tube for an electrical refrigeration unit | |
| US8091616B2 (en) | Enhanced heat transfer tube and manufacture method thereof | |
| EP0206640B1 (en) | Improved heat transfer tube having internal ridges | |
| CN1287117C (en) | Heat exchanger | |
| US6073686A (en) | High efficiency modular OLF heat exchanger with heat transfer enhancement | |
| US6786072B2 (en) | Method of fabricating a heat exchanger tube | |
| CN101793475B (en) | Heat transfer tube and method for its production | |
| CN1158409A (en) | Heat exchanger | |
| CN2821505Y (en) | Evaporator heat exchanging tube | |
| US11598518B2 (en) | Devices with an enhanced boiling surface with features directing bubble and liquid flow and methods thereof | |
| CN101532795B (en) | Metallic heat exchanger tube | |
| CN102305569A (en) | Heat exchanger tube used for evaporator | |
| JP2002115987A (en) | Internally finned heat exchanging tube arranged with fins of different height while being shifted | |
| CN104006579B (en) | A kind of high-efficient heat-exchanger of evaporimeter | |
| CN102349152B (en) | Ebullient cooling device | |
| CN103791754A (en) | Efficient heat exchange tube used for condenser | |
| CN202221261U (en) | Heat exchange pipe for evaporator | |
| CN109269337A (en) | A kind of flooded evaporator heat exchanger tube | |
| DE102016006914B4 (en) | heat exchanger tube | |
| CN110425773B (en) | Heat exchange tube for flooded evaporator | |
| CN2539948Y (en) | Intermittent tooth internal thread seamless high-efficiency heat transfer pipe | |
| CN1745288A (en) | Air/water heat exchanger with partial water ways | |
| CN1303380C (en) | Heat exchanger | |
| CN100554856C (en) | A kind of intensify heat transfer pipe |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Effective date of abandoning: 20080130 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |