JP2945649B2 - Heat transfer tube and manufacturing method thereof - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

FIELD OF THE INVENTION The present invention relates generally to heat transfer tubes. In particular, the present invention relates to a heat exchange tube having a refrigerant surface shape suitable for a heat exchanger of an air conditioning and cooling system for both evaporation and condensation applications, as well as to a method of making the same.

[0002]

2. Description of the Related Art A multi-tube heat exchanger has a plurality of tubes in a single shell. Usually, these tubes are arranged such that one of the two fluids required for heat exchange forms a number of parallel flows in the heat exchanger. In a flooded evaporator, these tubes are immersed in a second fluid flowing through a heat exchange shell. Heat is transferred from one fluid to the other via the tube walls. Many air conditioning systems have multi-tube heat exchangers. In air conditioning applications,
Fluid, usually water, flows through the tubes and refrigerant flows through the heat exchange shell. In evaporator applications, the refrigerant cools the fluid by heat transfer from the fluid through the tube wall. The transferred heat evaporates the refrigerant in contact with the outer surface of the tube. In condenser applications, the refrigerant is cooled and condensed by the heat transfer of the fluid through the tube walls. The heat transfer efficiency of such a heat exchanger depends greatly on the heat transfer characteristics of the individual tubes. In establishing overall heat exchange properties, the shape of the outer surface of the individual tubes is important.

[0003] There are many known methods for improving the heat transfer coefficient in a heat transfer tube. One way is to increase the heat exchange area of the tube. The most commonly used method for increasing the heat exchange area of the heat exchange tube is to provide fins on the outer surface of the tube. The fin may be formed separately from the tube and attached to the outer surface of the tube, or the fin may be formed on the outer surface of the tube by processing the tube wall of the tube by any method.

In the refrigerant condensing application, the formation of such fins improves the efficiency of condensation heat exchange as compared with the case where the outer surface is flat, but only because the heat exchange area is increased. It is not. If the heat exchange tube surface is flat, the condensing refrigerant will form a layer of fluid refrigerant on its outer surface. If such a layer exists, the heat exchange efficiency due to the tube wall will be reduced. As the refrigerant layer becomes thicker, the heat exchange that occurs across the layer is hindered. The thickness of the refrigerant layer on the fin is smaller than the thickness of the refrigerant layer formed on the main body of the tube due to the effect of the surface tension. by this,
The degree of inhibition of heat exchange by the fins can be reduced.

[0005] In refrigerant evaporation applications, increasing the heat exchange area on the tube surface improves the heat transfer efficiency of the heat exchange tube. In addition, the heat transfer efficiency is also enhanced by a surface profile that promotes nucleate boiling on the surface of the tube in contact with the boiling fluid. In the process of nucleate boiling, the heat transferred from the heated surface evaporates the liquid in contact with the surface, and the vapor forms bubbles. Heat from the surface superheats the steam into bubbles, which grow to a certain size.
When the size of the foam becomes sufficient, the surface tension is lost and the foam detaches from the surface. When the foam leaves the surface, the liquid enters the space vacated by the foam, and the vapor remaining there becomes a source of evaporation of another liquid, forming another foam. The heat exchange of the heat transfer surface by thus continuously forming bubbles on the surface, separating the bubbles from the surface and re-wetting the surface with the convective effect of vapor bubbles rising through the liquid and mixing the liquid Rate rises.

The nucleate boiling process is enhanced by configuring the heat transfer surface to have nucleation sites that provide a place to store the vapor and promote the formation of vapor bubbles. For example, simply roughening the heat transfer surface provides a nuclear site that can improve the heat transfer characteristics of the surface as compared to a similar flat surface. Reentrant nuclear sites create persistent foam columns and have good surface heat transfer characteristics. Reentrant nuclear sites are surface depressions. The opening of the recess is smaller than the volume below the surface of the recess.
Excessive influx of surrounding liquid fills reentrant nuclear sites and renders them immobile. By shaping the heat transfer surface to have a relatively large communicating subsurface channel with a relatively small opening to the surface, steam accumulation or nuclear site overflow is reduced or prevented;
The heat transfer efficiency of the surface was improved.

In a falling film evaporator, the spread of the liquid film on the heat transfer surface and the promotion of the thin film are important for improving the ability to transfer heat.

[0008]

SUMMARY OF THE INVENTION It is a logistics to provide a heat transfer tube having an external heat transfer surface with excellent heat transfer efficiency in both the condensation and evaporation of refrigerant in a full and falling film evaporator. And from the point of manufacture. Therefore, a single tube shape can be used for both the condenser and the liquid-filled evaporator.

[0009]

SUMMARY OF THE INVENTION The present invention provides a method for condensing refrigerant,
The present invention relates to a heat transfer tube having an outer surface formed so as to exhibit excellent heat transfer performance for both the liquid-filled evaporation and the falling film evaporation, and a method for manufacturing the heat transfer tube.

[0010] The tube has one or more fin convolutions formed on its outer surface. The notches extend obliquely across the fin convolution at regular intervals around the circumference of the tube. Spikes are formed in the portion of the fin convolution between adjacent notches. The tip of the spike is split into two tips. Each tip extends outwardly from the root base of the fin toward the split fin tip of an adjacent fin convolution.

The notches and split spike tips further increase the outside surface area as compared to conventional finned tubes. The groove between adjacent fin convolutions with the split fin tips extending upwards forms a reentry cavity that promotes boiling of the refrigerant in a flooded evaporator.

In condensing and falling film evaporation applications, a relatively sharp spike tip facilitates drainage and distribution of refrigerant from the fins. In most equipment, tubes for multi-tube air conditioning heat exchangers are installed horizontally or nearly horizontally. For horizontal tubes, the shape of the notched and split fins facilitates the removal of condensing refrigerant from the fins into the grooves formed between the fins at the top of the tube surface, The lower side facilitates the removal of condensed refrigerant from the tubes. In the liquid film evaporation mode, the sharp tips, notches, and low surface tension of the refrigerant help spread the liquid over the tube surface along the tube axis. This promotes excellent wettability in a horizontal multi-tube falling film evaporator.

[0013] The notched detached tip finned tube is a tool gang for a fin forming apparatus of the type that forms fins on the outer surface of the tube by rolling the tube wall between an inner mandrel and an outer fin forming disk. It can be manufactured easily and inexpensively by adding a notching disk and a split disk. The notching tool is shaped to twist the normal spikes and facilitate splitting of the spike tips.

The above and other objects, features and advantages of the present invention will become apparent from the following description, read in conjunction with the accompanying drawings. Like reference numerals in the drawings denote like components.

[0015]

FIG. 1 is a perspective view of a heat exchange tube 10. FIG. The tube 10 comprises a tube wall 11, an inner surface 1
2. It is composed of the outer surface 13. An outer fin spike 22 extends from the outer surface of the tube wall 11. The outer diameter of tube 10 is _Do , which is the value from outer surface 13 excluding the height ( _Hf ) of outer fin spike 22.

The tube of the present invention can be easily manufactured by a rolling process. FIG. 2 illustrates such a process. In FIG. 2, a fin forming device 60 operates on a tube 10 made of a malleable metal such as copper, and forms both internal ribs and external fins on the tube. The fin forming device 60 includes the tool mandrel 61
Each of these tool axles has a tool gang 62, which comprises a plurality of fin forming disks 63, a notching wheel 66, and a split disk 67. In this tube, a mandrel shaft 65 provided with a mandrel 64 extends.

As the tube 10 rotates, the tube wall 1
1 is pressed between the mandrel 64 and the fin forming disk 63. Under pressure, metal enters the grooves between the fin forming disks 63 and forms ridges or fins on the outer surface of the tube. As it rotates, the tube 10 is sandwiched between the mandrel 64 and the tool gang 62 (from left to right in FIG. 2) and a number of spiral fin convolutions are formed on the tube. The number of fin convolutions formed depends on the number of fin forming disks of the tool gang 62,
It is a function of the number of tool spindles 61 installed in the fin forming device 60. In this step, the tool gang 62
Immediately after forming the fins in the tube 10, the notching wheel 66 imprints the diagonal notch in the metal of the fin convolution. Subsequent to the formation of the diagonal notch, split disk 67 splits the tip of each fin convolution into two.

The mandrel 64 is, as shown in FIG. 2, the inner surface 1 of the tube wall passing over the mandrel.
2 may be configured to imprint a certain pattern. Typical patterns include one or more spiral rib convolutions. With such a pattern, the efficiency of heat exchange between the fluid flowing in the tube and the tube tube wall is improved.

FIG. 3 shows a plan view of a portion of the outer surface of the tube. From the outer surface 13 of the tube 10, a number of fin convolutions 20 extend. The notch pattern 30 is formed so as to obliquely cross each fin convolution at a predetermined interval. A fin spike 22 having two tips 23 is formed between a pair of adjacent notches in any fin convolution.

FIG. 4 is a plan view of one of the fin convolutions of the tube of the present invention. The angle of inclination of the notch base 31 with respect to the longitudinal axis A _{T of the} tube is indicated by the angle α. The angle of inclination of the tip 23 of the fin spike 22 with respect to the longitudinal axis _{AT of the} tube is indicated by the angle β. During manufacture of the tube (see FIG. 2), the axis of the fin spike 22 shown in FIG. 4 is slightly offset from the angle between the teeth of the notching wheel and the fin convolution due to the interaction between the rotating and advancing tube 10 and the notching wheel 66. Twisted. At this time, the angle β of the tip is inclined with respect to the angle α, that is, β ≠ α. However, in certain cases β = α. Due to this twist of the spikes, the notched spikes provide more surface for splitting than the unnotched fin convolutions,
The split disk 67 can reliably split the spike.

It has been found that when the angle of the notching wheel is greater than 40 ° and the spacing between adjacent teeth on the notching wheel is each less than 0.0125, the spikes twist. This twisting of the spikes makes the spike splitting more effective. In particular, without torsion, the thickness of the tip of the fin would be too thin to reliably split the spike. In the case of twist, the shape of the spike after notching and immediately before division is basically a parallelogram. After division, the parallelogram is divided along its diagonal to form two triangles.

FIG. 5 is a sectional view schematically showing two adjacent fin convolutions of the tube of the present invention. It is described as pseudo because no section of any of the fin convolutions can look exactly the same as the section as shown in FIG. However, this figure serves to illustrate a number of features of the tube. The fin convolutions 20A and 20B protrude outward from the tube wall 11. The fin convolutions 20A and 20B have a root portion 21 and a spike portion 22. A notch having a notch base 32 extends to the fin convolution 20A. Overall height of the fin convolution 20A and 20B are H _f. The width of the foundation portion 21 is W _r, the width of the widest portion of the spike 22 is W _t. The outer limb of spike 22 has two tips 23. Notch penetrates the fin convolution to height H _n from the outer wall surface 13.

The notching wheel 66 (FIG. 2)
Does not cut through the notch in the fin convolution during the manufacturing process, but rather acts to push away the material in the notched portion and to force the notch into the fin convolution. The excess material pushed away from the notched portion of the fin convolution not only goes to the tube wall 11 on the fin convolution side, but also the area between the adjacent notches,
Move outward from the side of the fin convolution.
As a result, W _t is larger than W _r. The distance between similar points on adjacent fin convolutions, ie the fin pitch, is P _f . The angle between the two tips 23 of the spike portion 22, that is, the division angle is an angle δ. The tip extending from one side of the fin convolution extends toward the adjacent fin convolution, leaving a gap g between the tips.

The relatively large number of sharp tips promotes condensation on the surface of the tube when the tube is used for condensation applications. The tip lays up with a volume between adjacent fin convolutions, so that a reentrant cavity is formed, thus forming a tube surface that promotes evaporation.

Prototype tube 2 in accordance with the teachings of the present invention
One was manufactured and tested using refrigerant R-134a. The relevant parameters for these two prototypes were as follows:

[0026]

[Table 1] Prototype A Nominal outer diameter (D _o ): 1.9 cm (3/4 inch) Fin pitch (P _f ): 0.6 mm (0.024 inch) or 16.5 fins /
cm (42 fins / inch) fin height (H _f): 0.79mm (0.031 inch) notch base height (H _n): 0.58mm (0.02
Notch angle (α): 50 degrees, 30 degrees, 45 degrees Division angle (δ): 70 degrees, 90 degrees, 110 degrees Notch density, that is, the number of notches in the fin convolution per one round of the tube: 80, 140 Prototype B Nominal outer diameter (D _o ): 1.9 cm (3/4 inch) Fin pitch (P _f ): 0.45 mm (0.018 inch) or 22 fins
/ cm (56 fins / inch) Fin height (H _f ): 0.58 mm (0.024 inch) Notch base height (H _n ): 0.35 mm (0.01
4 inches) Notch angle (α): 50 degrees Split angle (δ): 90 degrees Notch density, that is, the number of notches in the fin convolution per tube circumference: 140 The performance and the heat flux state were compared. In evaporative applications, the performance of prototype A is about 2.10 times that of an average flat tube.
The performance of prototype B was about three times that of a flat tube. In condensing applications, the performance of prototype A is:
On average, the performance of the flat tube was about 19 times, and the performance of prototype B was about 23 times the performance of the flat tube.

From the above test data, the nominal outer diameter is 12.
From 5 millimeters (１ ／ inch) to 25 millimeters (1 inch) tubes, it can be assumed that they have the following comparative performance.

A) Fin pitch is 0.038 to 0.76
mm (0.015-0.030 inch, ie 0.03
8mm ≦ P _f ≦ 0.76mm (0.015 inch ≦ P
_f 0.030 inch) b) The ratio of the fin height to the outer diameter of the tube is 0.0
26 to 0.067, that is, 0.026 ≦ H _f / D _o ≦ 0.
067, c) Notch density is 60-190, d) Angle between notch axis and tube longitudinal axis is 20-6.
5 degrees, that is, 20 ° ≦ α ≦ 65 °, e) The height of the notch base is 0.50-0.
8, ie 0.050 ≦ H _n / H _f ≦ 0.8, f) The angle between the two tips on the spike is 70-130
Degrees, that is, 70 ° ≦ δ ≦ 130 °.

The prototype tested had three fin convolutions or "starts".
The optimal number of fin convolutions or starts depends on the ease of manufacture rather than the effect of the number of fin convolutions on heat exchange efficiency. As the number of starts increases, the rate of fin convolution on the tube surface increases.

As described above, the present invention relates to a heat transfer tube having an outer surface formed so as to exhibit excellent heat transfer performance for use in both evaporating and condensing refrigerant, and a heat transfer tube. It is intended to provide a method of manufacturing.

To summarize the invention, the heat transfer tube (1
0) is suitable for use in, for example, a multi-tube type air conditioning condenser, a full liquid evaporator, a falling liquid film evaporator, or an evaporator combining a full liquid and a falling liquid film. The tube (10) has at least one fin convolution (20) extending helically around the outer surface (13). The pattern of notches (30) extends at regular intervals around the circumference of the tube across the fin convolution at an oblique angle (α). There is a split spike (22) having two tips (23) between a pair of adjacent notches. Between the mandrel and the gang of the fin forming disk (63) first, and secondly the notching wheel (66),
And thirdly, fin convolutions, notches and split spikes are formed in the tube by rolling the wall of the tube between the split wheels (67). The interaction of the tube and the notching wheel rotates forward, during the manufacture of the tube, the maximum width of the spike (W _t) is greater than the fin convolution of the foundation portion in a width (W _r).

[Brief description of the drawings]

FIG. 1 is a perspective view of a tube of the present invention.

FIG. 2 is an explanatory view of a process for producing a tube of the present invention.

FIG. 3 is a plan view of a portion of the outer surface of the tube of the present invention.

FIG. 4 is a plan view of a portion of a single fin convolution of the tube of the present invention.

FIG. 5 is a schematic cross-sectional view of two adjacent fin convolutions of a tube of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 ... Heat exchange tube 11 ... Tube wall 12 ... Inner surface 13 ... Outer surface 20 ... Fin convolution 22 ... Outer fin spike 30 ... Notch pattern 60 ... Fin forming apparatus 61 ... Tool mandrel 62 ... Tool gang 63 ... Fin forming disk 64 ... Mandrel 65 ... Mandrel shaft 66 ... Notching wheel 67 ... Split disk

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Stephen Jay. Spencer United States, New York, Liverpool, Riverdale Road 205 (72) Inventor Daniel P. Gaffany United States of America, New York, Chitte Nango, West Genesee Street 351 (72) Inventor Zin Liu United States of America, New York, Baldwinsville, Hidden Lake Drive 3135 (56) References JP-A-5-231790 (JP, A) JP-A-5-215442 (JP, A) JP-A-60-149894 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F21D 53/06 F28F 1/16 F28F 1/36 B21H 3/00

Claims (7)

(57) [Claims] 1. A method for forming a heat exchange surface on an outer wall of a tube, the method comprising: rolling the wall between an inner mandrel and a gang of a fin forming disc to form a fin convolution; Notching the fin convolution using a notching wheel at regular intervals around the fin convolution to form a spike in the fin convolution; and dividing the spike into two tip portions for each spike.
And a step of forming a notch formed by the notching step, notch
The tip portion has a tip axis angle, and the notch forming step is such that the tip axis angle is the notch base angle.
The tip so that it is oblique to the base axis angle.
Including a twisting step, for which the notching wheel
Is greater than 40 ° with respect to the longitudinal axis of the tube
And the adjacent teeth of the notching wheel
The distance between the teeth is such that the tip axis is the axial angle of the notch base.
It is narrow enough to be oblique to the degree,
The tip of the spike is twisted more,
A method characterized by being easy to split. Wherein said notched step, except press material forming the tip, the exception was the material pressed, before
The width of the spike and W _t at the tip of the serial spike,
The width W _t is larger than the width W _r of foundation portion of the spike
The method of claim 1, wherein 3. A heat exchange surface formed by the method of claim 1. 4. An improved heat transfer tube (10) having an outer surface, at least one fin convolution (20) helically provided around said outer surface, and an outer periphery of said tube. Notches (3) extending radially into the fin convolution at regular intervals around
0) and the notch is the longitudinal axis (A _T ) of the tube.
A base axis having an angle (α) with respect to the notch, the notch splitting the fin convolution into a root (21) and a split spike (22) having two tips (23) ; The split spike is located between a pair of adjacent notches of the notch and has a maximum width (W _t ) that is larger than a maximum width (W _r ) of the root portion . The surface is wide for
So that the spikes
The heat transfer tube (10) , which is easily split . 5. The fin pitch (P _f ) is from 0.38 to
0.76 mm (0.015-0.030 inch); the tube has an outer diameter (D _o ); the fin convolution has a fin height (H _f ); fin height ratio of (H _f / D _o) 0.026
0.067; the number of notches in the fin convolution per tube circumference is 60-190; the angle between the notch axis and the longitudinal axis of the tube is 3
0 to 65 degrees, and the notch has a notch base height (H
_n ) has a base (32) having a fin height of 0.50 to 0.8, the tips extending outwardly from each other at a split angle (δ), The heat transfer tube according to claim 4 , wherein the axis angle (β) is 20 to 65 degrees. 6. The heat transfer tube according to claim 5 , wherein the division angle (δ) is 70 to 130 degrees. 7. The fin pitch is 0.42 to 0.60.
mm, the notch angle is 50 degrees, the number of notches in the fin convolution per tube circumference is 110 to 140, and the height of the notch base is 0.5 of the height of the fins.
The heat transfer tube according to claim 5, wherein the heat transfer tube has a value of 0 to 0.80.