Patent Publication Number: US-11644245-B2

Title: Indirect heat exchanger having circuit tubes with varying dimensions

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application is a continuation of U.S. patent application Ser. No. 15/291,773, filed Oct. 12, 2016, which issued as U.S. Pat. No. 10,655,918 on May 19, 2020, which is hereby incorporated herein by reference in its entirety. 
    
    
     BACKGROUND AND SUMMARY OF THE INVENTION 
     The present invention relates to heat exchangers, and more particularly, to an indirect heat exchanger comprised of a plurality of tube run circuits. Each circuit is comprised of a tube having a plurality of tube runs and a plurality of return bends. Each tube may have the same surface area from near its connection to an inlet header to near its connection to an outlet header. However, the geometry of the tube run is changed as the tube runs extend from the inlet to near the outlet header. In one case, the horizontal cross sectional dimension of the tube runs decrease as the tube runs extend to near the outlet header. Such decrease in horizontal cross sectional dimension may be progressive from the near the inlet header to near the outlet header or each coil tube run may have a uniform horizontal cross sectional dimension, with at least one horizontal cross section dimension of tube runs decreasing nearer to the outlet header. 
     In particular, an indirect heat exchanger is provided comprising a plurality of circuits, with an inlet header connected to an inlet end of each circuit and an outlet header connected to an outlet end of each circuit. Each circuit is comprised of a tube run that extends in a series of runs and return bends from the inlet end of each circuit to the outlet end of each circuit. In the embodiments, the tube runs may have return bends or may be one long straight tube with no return bends such as with a steam condenser coil. Each circuit tube run has a pre-selected horizontal cross sectional dimension near the inlet end of each coil circuit, and each circuit tube run has a decreasing horizontal cross sectional dimension as the circuit tube extends from near the inlet end of each circuit to near the outlet end of each coil circuit. 
     The embodiments presented start out with a larger tube geometry either in horizontal cross sectional dimension or cross sectional area in the first runs near the inlet header and then have a reduction or flattening (at least once) in the horizontal cross-sectional dimension of tube runs proceeding from the inlet to the outlet and usually in the direction of airflow. A key advantage towards progressive flattening in a condenser is that the internal cross sectional area needs to be the largest where the least dense vapor enters the tube run. This invites gas into the tube run by reducing the internal side pressure drop allowing more vapor to enter the tube runs. The reduction of horizontal tube run cross sectional dimension, or flattening of the tube in the direction of air flow accomplishes several advantages over prior art heat exchangers. First, the reduced projected area reduces the drag coefficient which imposes a lower resistance to air flow thereby allowing more air to flow. In addition to airflow gains, for condensers, as refrigerant is condensed there is less need for interior cross sectional area as one progresses from the beginning (vapor-low density) to the end (liquid-high density) so it is beneficial to reduce the internal cross sectional area as the fluid flows from the inlet to the outlet allowing higher internal fluid velocities and hence higher internal heat transfer coefficients. This is true for condensers and for fluid coolers, especially fluid coolers with lower internal fluid velocities. In one embodiment shown, the tube may start round and the geometric shape is progressively streamlined for each group of two tube runs. The decision of how many tube runs have a more streamlined shape and a reduction in the horizontal cross sectional dimension and how much of a reduction is required is a balance between the amount of airflow improvement desired, the amount of internal heat transfer coefficient desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop. 
     Typical tube run diameters covering indirect heat exchangers range from ¼″ to 2.0″ however this is not a limitation of the invention. When tube runs start with a large internal cross sectional area and then are progressively flattened, the circumference of the tube and hence surface area remain essentially unchanged at any of the flattening ratios for a given tube diameter while the internal cross sectional area is progressively reduced and the projected area in the air flow external to the indirect heat exchanger is also reduced. The general shape of the flattened tube may be elliptical, ovaled with one or two axis of symmetry, a flat sided oval or any streamlined shape. A key metric in determining the performance and pressure drop benefits of each pass is the ratio of the long (vertical) side of the oval to the shortest (horizontal) side. A round tube would have a 1:1 ratio. The level of flattening is indicated by increasing ratios of the sides. This invention relates to ratios ranging from 1:1 up to 6:1 to offer optimum performance tradeoffs. The optimum maximum oval ratio for each indirect heat exchanger tube run is dependent on the working fluid inside the coil, the amount of airside performance gain desired, the desired increase in internal fluid velocity and increase of internal heat transfer coefficients, the operating conditions of the coil, the allowable internal tube side pressure drop as well as the manufacturability of the desired geometry of the coil. In an ideal situation, all these parameters will be balanced to satisfy the exact need of the customer to optimize system performance, thereby minimizing energy and water consumption. 
     The granularity of the flattening progression is an important aspect of this invention. At one extreme is a design where by the amount of flattening is progressively increased through the length of multiple passes or tube runs of each circuit. This could be accomplished through an automated roller system built into the tube manufacturing process. A similar design with less granularity would involve at least one step reduction such that one or more passes or tube runs of each circuit would have the same level of flattening. For example, one design might have the first tube run with no degree of flattening, as would be the case with a round tube, and the next three circuit tube runs would have one level of compression factor (degree of flattening) and the final four tube run passes would have another level (higher degree) of compression factor. The least granular design would have one or more passes or tube runs of round tube followed by one or more passes or tube runs of a single level of flattened tube. This could be accomplished with a set of rollers or by supplying a top coil with round tubes and the bottom coil with elliptical or flattened tubes. Yet another means to manufacture the different tube geometric shapes would be to stamp out the varying tube shapes and weld the plates together as found in U.S. Pat. No. 4,434,112. It is likely that heat exchangers will soon be designed and produced via 3D printer machines to the exact geometries to optimize heat transfer as proposed in this invention. 
     The tube run flattening could be accomplished in-line with the tube manufacturing process via the addition of automated rollers between the tube mill and bending process. Alternately, the flattening process could be accomplished as a separate step with a pressing operation after the bending has occurred. The embodiments presented are applicable to any common heat exchanger tube material with the most common being galvanized carbon steel, copper, aluminum, and stainless steel but the material is not a limitation of the invention. 
     Now that the tube circuits can be progressively flattened thereby reducing the horizontal cross sectional dimension, it is possible now to extremely densify the tube run circuits without choking external air flow. The proposed embodiments thusly allow for “extreme densifying” of indirect heat exchanger tube circuits. A method described in U.S. Pat. No. 6,820,685 can be employed to provide depression areas in the area of overlap of the U-bends to locally reduce the diameter at the return bend if desired. In addition, users skilled in the art will be able to manufacture return bends in tube runs at the desired flattening ratios and this is not a limitation of the invention. 
     Another way to manufacture a change in geometrics shape is to employ the use of a top and bottom indirect heat exchanger. The top heat exchanger may be made of all round tubes while the bottom heat exchanger can be made with a more streamlined shape. This conserves the heat transfer surface area while increasing overall air flow and decreasing the internal cross sectional area. Another way to manufacture a change in geometric shape is to employ the use of a top and bottom indirect heat exchanger. The top heat exchanger may be made of all round tubes while the bottom heat exchanger can be made with a reduction in circuits compared to the top coil. This reduces the heat transfer surface area while increasing overall air flow and decreasing the internal cross sectional area. As long as the top and bottom coils have at least one change in geometric shape or number of circuits, the indirect heat exchange system would be in accordance with this embodiment. 
     It is an object of the invention to start out with large internal cross sectional area tube runs then progressively reduce the horizontal cross sectional dimension of tube runs as they progress from the inlet to the outlet to reduce the drag coefficient and allow more external airflow. 
     It is an object of the invention to start out with large internal cross sectional area tube runs then progressively reduce the horizontal cross sectional dimension of the tube runs as they progress from the inlet to the outlet to allow the lowest density fluid (vapor) to enter the tube run with very little pressure drop to maximize internal fluid flow rate. 
     It is an object of the invention to start out with large internal cross sectional area tube runs then progressively reduce the horizontal cross sectional dimension of tube runs as they progress from the inlet to the outlet to allow for extreme tube circuit densification without choking external airflow. 
     It is an object of the invention to start out with large internal cross sectional area tube runs then progressively reduce the horizontal cross sectional dimension of tube runs as they progress from the inlet to the outlet to increase the internal fluid velocity and increase internal heat transfer coefficients in the direction of internal fluid flow path. 
     It is an object of the invention to start out with large internal cross sectional area tube runs then progressively reduce the horizontal cross sectional dimension of tube runs as they progress from the inlet to the outlet on condensers to take advantage of the fact that as the vapor condenses, there is less cross sectional area needed resulting in higher internal heat transfer coefficients with more airflow hence more capacity. 
     It is an object of the invention to start out with large internal cross sectional area tube runs then progressively reduce the horizontal cross sectional dimension of tube runs as they progress from the inlet to the outlet by balancing the customer demand on capacity desired and allowable internal fluid pressure drop to customize the indirect heat exchanger design to meet and exceed customer expectations. 
     It is an object of the invention to change a circuits tube run geometric shape at least once along the circuit path to allow simultaneously balancing of the external airflow, internal heat transfer coefficients, cross sectional area and heat transfer surface area to optimize heat transfer. 
     It is an object of the invention to change a plate coil&#39;s geometric shape at least once along the circuit path to allow simultaneously balancing of the external airflow, internal heat transfer coefficients, cross sectional area and heat transfer surface area to optimize heat transfer. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       In the drawings: 
         FIG.  1    is a side view of a prior art indirect heat exchanger including a series of serpentine tube runs; 
         FIG.  2 A  is an end view of an indirect heat exchanger in accordance with the first embodiment of the present invention; 
         FIG.  2 B  is an end view of an indirect heat exchanger in accordance with a second embodiment of the present invention; 
         FIG.  3    is a side view of one circuit from the indirect heat exchanger in accordance with the first embodiment of the present invention; 
         FIG.  4 A  is an end view of an indirect heat exchanger in accordance with a third embodiment of the present invention; 
         FIG.  4 B  is an end view of an indirect heat exchanger in accordance with a fourth embodiment of the present invention; 
         FIG.  5    is an end view of an indirect heat exchanger in accordance with a fifth embodiment of the present invention; 
         FIG.  6    is an end view of two indirect heat exchangers in accordance with a sixth embodiment of the present invention; 
         FIG.  7 A  is an end view of two indirect heat exchangers in accordance with a seventh embodiment of the present invention; 
         FIG.  7 B  is an end view of two indirect heat exchangers in accordance with an eighth embodiment of the present invention; 
         FIG.  7 C  is an end view of two indirect heat exchangers in accordance with a ninth embodiment of the present invention; 
         FIG.  8    is an end view of two indirect heat exchangers in accordance with a tenth embodiment of the present invention; 
         FIG.  9    is a 3-D view of an indirect heat exchanger in accordance with an eleventh embodiment of the present invention. 
         FIG.  10 A ,  FIG.  10 B  and  FIG.  10 C  are partial perspective views of the eleventh embodiment of the present invention; 
         FIG.  11 A  is an end view of an indirect heat exchanger in accordance with a twelfth embodiment of the present invention; 
         FIG.  11 B  is a 3-D view of the twelfth embodiment of the present invention. 
     
    
    
     DETAILED DESCRIPTION 
     Referring now to  FIG.  1   , a prior art evaporative cooled coil product  10  which could be a closed circuit cooling tower or an evaporative condenser. Both of these products are well known and can operate wet in the evaporative mode, partially wet in a hybrid mode or can operate dry, with the spray pump  12  turned off when ambient conditions or lower loads permit. Pump  12  receives the coldest cooled evaporatively sprayed fluid, usually water, from cold water sump  11  and pumps it to primary spray water header  19  where the water comes out of nozzles or orifices  17  to distribute water over indirect heat exchanger  14 . Spray water header  19  and nozzles  17  serve to evenly distribute the water over the top of the indirect heat exchanger  14 . As the coldest water is distributed over the top of indirect heat exchanger  14 , motor  21  spins fan  22  which induces or pulls ambient air in through inlet louvers  13 , up through indirect heat exchanger  14 , then through drift eliminators  20  which serve to prevent drift from leaving the unit, and then the warmed air is blown to the environment. The air generally flows in a counterflow direction to the falling spray water. Although  FIG.  1    is shown with axial fan  22  inducing or pulling air through the unit, the actual fan system may be any style fan system that moves air through the unit including but not limited to induced and forced draft in a generally counterflow, crossflow or parallel flow with respect to the spray. Additionally, motor  21  may be belt drive as shown, gear drive or directly connected to the fan. Indirect heat exchanger  14  is shown with an inlet connection pipe  15  connected to inlet header  24  and outlet connection pipe  16  connected to outlet header  25 . Inlet header  24  connects to the inlet of the multiple serpentine tube circuits while outlet header  25  connects to the outlet of the multiple serpentine tube circuits. Serpentine tube runs are connected with return bend sections  18 . Return bend sections  18  may be continuously formed into the circuit called serpentine tube runs or may be welded between straight lengths of tubes. It should be understood that the process fluid direction may be reversed to optimize heat transfer and is not a limitation to embodiments presented. It also should be understood that the number of circuits and the number of passes or rows of tube runs within a serpentine indirect heat exchanger is not a limitation to embodiments presented. 
     Referring now to  FIG.  2 A , indirect coil  100  is in accordance with a first embodiment of the present invention.  FIG.  2 A  shows eight circuits and eight passes or tube rows of embodiment  100 . Indirect heat exchanger  100  has inlet and outlet headers  102  and  104  and is comprised of tube runs  106 ,  107 ,  108 ,  109 ,  110 ,  111 ,  112 , and  113 . Tube runs  106  and  107  are a pair of identical geometry round tubes and have equivalent tube diameters  101 . Tube runs  108  and  109  are another pair of tube runs having a different geometry compared to tubes run pairs  106  and  107  with equivalent shapes having reduced horizontal dimensions D 3  and increased vertical dimension D 4  with respect to round tubes  106  and  107 . The ratio of D 4  to D 3  is usually greater than 1.0 and less than 6.0. Further, indirect heat exchanger tube run  108  and  109  may have a uniform ratio of D 4  to D 3  along its length as shown, or a uniformly increasing ratio of D 4  to D 3  along its length. The pair of tube runs  110  and  111  have yet a different geometry and have equivalent shapes with reduced horizontal dimensions D 5  and increased vertical dimension D 6  with respect to tube runs  108  and  109 . The ratio of D 6  to D 5  is usually greater than 1.0, less than 6.0 and is also greater than ratio D 4  to D 3 . Further, tube run  110  and  111  may have a uniform ratio of D 6  to D 5  along its length as shown, or a uniformly increasing ratio of D 6  to D 5  along its length. The pair of tube runs  112  and  113  have yet a different geometry and have equivalent shapes with reduced horizontal dimensions D 7  and increased vertical dimension D 8  with respect to tube runs  110  and  111 . The ratio of D 8  to D 7  is usually greater than 1.0, less than 6.0 and also greater than ratio D 6  to D 5 . Further, tube runs  112  and  113  may have a uniform ratio of D 8  to D 7  along its length as shown, or a uniformly increasing ratio of D 8  to D 7  along its length. Tube run  106  is connected to inlet header  102  of indirect heat exchanger  100  and tube run  113  is connected to outlet header  104 . In a preferred embodiment arrangement, the tubes are round at the inlet having a 1.0 vertical to horizontal tube run dimension ratio and are progressively flattened up to a vertical to horizontal tube run dimension ratio near 3.0 near the outlet. The practical limits of horizontal to vertical dimension ratios are between 1.0 for round tubes and may be as high as 6. It should be understood in this first embodiment, that as the vertical to horizontal tube run dimension ratio increases, the tube runs become flatter and more streamlined which allows more airflow while keeping the internal and external surface area constant. It should be noted that in the first embodiment, the horizontal dimension is progressively reduced from the inlet to the outlet of the tube runs while the vertical dimension is progressively increased from the inlet to the outlet. It should be further understood that the tube shapes can start as round and be progressively flattened as shown, can start as flattened and be progressively more flattened or start out streamlined and become more streamlined. When dealing with elliptical shapes, the B/A ratio is usually greater than 1 and refers to the major and minor axis respectively. It should be further understood that the first tube run could be elliptical with a B/A ratio close to 1.0 and progressively increase the B/A elliptical ratio from the inlet to the outlet. It should be understood that the first embodiment shows progressively reduced horizontal dimensions and progressively increased vertical dimensions from the first to the last tube run and that the initial shape, whether round, elliptical or streamlined is not a limitation of the embodiment. It should further be understood that every two passes may have the same tube shape as shown or the entire tube may be progressively flattened or streamlined. The decision on how to make the indirect heat exchanger circuits is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop. 
     Referring now to  FIG.  2 B , indirect coil  150  is in accordance with a second embodiment of the present invention.  FIG.  2 B  shows eight circuits and eight passes or tube rows of embodiment  150 . Indirect heat exchanger  150  has inlet and outlet headers  102  and  104  and is comprised of tube runs  106 ,  107 ,  108 ,  109 ,  110 ,  111 ,  112 , and  113 . Tube runs  106  and  107  in  FIG.  2 B  are not round as they were in  FIG.  2 A , instead they are a pair of tube runs having initial horizontal dimension D 1  and initial vertical dimension D 2 . Tube runs  108  and  109  are another pair of tube runs having a different geometry compared to tubes run pairs  106  and  107  with equivalent shapes having reduced horizontal dimensions D 3  and increased vertical dimension D 4  with respect to round tubes  106  and  107 . The ratio of D 4  to D 3  is usually greater than 1.0 and less than 6.0 and the ratio of D 4  to D 3  is usually larger than the ratio of D 2  to D 1 . Further, indirect heat exchanger tube run  108  and  109  may have a uniform ratio of D 4  to D 3  along its length as shown, or a uniformly increasing ratio of D 4  to D 3  along its length. The pair of tube runs  110  and  111  have yet a different geometry and have equivalent shapes with reduced horizontal dimensions D 5  and increased vertical dimension D 6  with respect to tube runs  108  and  109 . The ratio of D 6  to D 5  is usually greater than 1.0, less than 6.0 and is also greater than ratio D 4  to D 3 . Further, tube run  110  and  111  may have a uniform ratio of D 6  to D 5  along its length as shown, or a uniformly increasing ratio of D 6  to D 5  along its length. The pair of tube runs  112  and  113  have yet a different geometry and have equivalent shapes with reduced horizontal dimensions D 7  and increased vertical dimension D 8  with respect to tube runs  110  and  111 . The ratio of D 8  to D 7  is usually greater than 1.0, less than 6.0 and also greater than ratio D 6  to D 5 . Further, tube runs  112  and  113  may have a uniform ratio of D 8  to D 7  along its length as shown, or a uniformly increasing ratio of D 8  to D 7  along its length. Tube run  106  is connected to inlet header  102  of indirect heat exchanger  100  and tube run  113  is connected to outlet header  104 . In one arrangement, the tubes begin nearly round at the inlet having a vertical to horizontal tube run dimension ratio near 1.0 and are progressively flattened up to a vertical to horizontal tube run dimension ratio near 3.0 near the outlet. The practical limits of horizontal to vertical dimension ratios are between 1.0 for round tubes and may be as high as 6. It should be understood in this second embodiment, that as the vertical to horizontal tube run dimension ratio increases, the tube runs become flatter and more streamlined which allows more airflow while keeping the internal and external surface area constant. It should be noted that in this second embodiment, the horizontal dimension is progressively reduced from the inlet to the outlet of the tube runs while the vertical dimension is progressively increased from the inlet to the outlet. It should be further understood that the tube shapes can start slightly flattened, as compared to the first embodiment shown in  FIG.  2 A  which started with round tubes, and then be progressively flattened as shown or start out streamlined and become more streamlined. When dealing with elliptical shapes, the B/A ratio is usually greater than 1 and refers to the major and minor axis respectively. It should be further understood that the first tube run could be elliptical with a B/A ratio close to 1.0 and progressively increase the B/A elliptical ratio from the inlet to the outlet. It should be understood that the second embodiment shows progressively reduced horizontal dimensions and progressively increased vertical dimensions from the first to the last tube run and that the initial shape, whether round, elliptical or streamlined is not a limitation of the embodiment. It should further be understood that every two passes may have the same tube shape as shown or the entire tube may be progressively flattened or streamlined. The decision on how to make the indirect heat exchanger circuits is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop. 
     Referring now to  FIG.  3   , circuit  103  from the first embodiment of  FIG.  2    is shown from a side view for understanding how each circuit may be constructed. Tube runs  106 ,  107 ,  108 ,  109 ,  110 ,  111 ,  112  and  113  are also shown from sectional view AA. Tube runs  106  and  107  are generally round tubes and have equivalent tube diameters  101 . Tube run  106  has round U-bend  120  connecting it to tube run  107 . Tube run  107  is connected to tube run  108  with transition  115 . Transition  115  starts as round on one end and transitions to the shape of D 4  to D 3  ratio at the other end. Transition  115  can be simply pressed or casted from a die, extruded, or can be a fitting which is typically welded or brazed into the tube runs. Transition  115  can also be pressed into the tube when the tube is going through the serpentine bending operation. The method of forming transition  115  is not a limitation of the invention. Round U-bends  120  can be formed to nest to the next return bend such that the number of circuits in the indirect heat exchanger may be densified as taught in U.S. Pat. No. 6,820,685. U-bends  120  may also be mechanically flattened while the tube runs are being bent and assume the general shape at each tube run pass which would be a changing return bends shape throughout the coil circuit. The previous discussion is the same for transitions  115 , 116  and  117 . Tube runs  108  and  109  have equivalent and reduced horizontal dimensions D 3  and increased vertical dimension D 4 . The ratio of D 4  to D 3  is usually greater than 1.0 and less than 6.0. Further, coil tube run  108  and  109  may have a uniform ratio of D 4  to D 3  along its length as shown, or a uniformly increasing ratio of D 4  to D 3  along its length. Tube runs  110  and  111  have equivalent and reduced horizontal dimensions D 5  and increased vertical dimension D 6 . The ratio of D 6  to D 5  is usually greater than 1.0, less than 6.0 and also greater than ratio D 4  to D 3 . Further, tube runs  110  and  111  may have a uniform ratio of D 6  to D 5  along its length as shown, or a uniformly increasing ratio of D 6  to D 5  along its length. Tube runs  112  and  113  have equivalent and reduced horizontal dimensions D 7  and increased vertical dimension D 8 . The ratio of D 8  to D 9  is usually greater than 1.0, less than 6.0 and also greater than ratio D 6  to D 5 . Further, tube run  112  and  113  may have a uniform ratio of D 8  to D 7  along its length as shown, or a uniformly increasing ratio of D 8  to D 7  along its length. 
     Referring now to  FIG.  4 A , indirect heat exchanger  200  is in accordance with a third embodiment of the present invention. Embodiment  200  has eight circuits and eight passes or tube runs. Embodiment  200  has at least one reduction in horizontal dimension and one increase in vertical dimension within the circuit tube runs. Indirect heat exchanger  200  has inlet and outlet headers  202  and  204  respectively and is comprised of coil tubes having run lengths  206 ,  207 , 208 , 209 , 210 , 211 , 212  and  213 . It should be noted that tube runs  206 , 207 , 208  and  209  have equivalent tube diameters  201 . Embodiment  200  also has tube runs  210 , 211 , 212 , and  213  each having equivalent horizontal cross section dimensions D 3  and equivalent vertical cross section dimensions D 4 . The ratio of D 4  to D 3  is usually greater than 1.0, less than 6.0 and the vertical dimension D 4  is larger than tube diameter  201  while the horizontal dimension D 3  is less than tube diameter  201 . In one arrangement of the third embodiment, the first ratio is greater than or equal to 1.0 and less than 2.0 (it&#39;s equal to 1.0 with round tubes) and the second ratio is greater than the first ratio but less than 6.0. Of note is that in the third embodiment of  FIG.  4 A , each circuit tube run length has at least one change in geometric shape as the circuit tube run extends from the inlet to the outlet. The decision of how many tube runs have reduced horizontal cross section dimensions as shown with  FIGS.  6  and  7    is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop and is not a limitation of the invention. 
     Referring now to  FIG.  4 B , indirect heat exchanger  250  is in accordance with a fourth embodiment of the present invention. Embodiment  250  has eight circuits and eight passes or tube runs. Embodiment  250  has at least one reduction in horizontal dimension and increase in vertical dimension within the circuit tube runs. Indirect heat exchanger  250  has inlet and outlet headers  202  and  204  respectively and is comprised of coil tubes having run lengths  206 ,  207 ,  208 , 209 , 210 , 211 , 212  and  213 . It should be noted that unlike the embodiment shown in  FIG.  4 A , which started with round tubes in the first passes or rows, embodiment  250  has tube runs  206 , 207 , 208  and  209  each having equivalent horizontal cross section dimensions D 1  and equivalent vertical cross section dimensions D 2 . The ratio of D 2  to D 1  is usually greater than 1.0 and less than 6.0. Embodiment  250  also has tube runs  210 ,  211 ,  212 , and  213  each having equivalent horizontal cross section dimensions D 3  and equivalent vertical cross section dimensions D 4 . The ratio of D 4  to D 3  is usually greater than 1.0, less than 6.0 and usually larger than the ratio of D 2  to D 1 . In one arrangement of the fourth embodiment, the first ratio (D 2 /D 1 ) is greater than or equal to 1.0 and less than 2.0 (D 2 /D 1  is greater than 1.0 as shown) and the second ratio (D 4 /D 3 ) is greater than the first ratio but less than 6.0. Of note is that in the fourth embodiment of  FIG.  4 B , each circuit tube run length has at least one change in geometric shape as the circuit tube run extends from the inlet to the outlet. The decision of how many tube runs have reduced horizontal cross section dimensions is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop and is not a limitation of the invention. 
     Referring now to  FIG.  5   , indirect heat exchanger  300  is in accordance with a fifth embodiment of the present invention. Embodiment  300  has eight circuits and eight passes or tube runs where each pair of tube runs have a different diameter and has progressively smaller diameters from the inlet tube run  306  to the outlet tube run  313 . Embodiment  300  has inlet and outlet headers  302  and  304  respectively and is comprised of coil tubes having tube runs  306 , 307 ,  308 , 309 , 310 , 311 , 312  and  313 . It should be noted that the pair of tube runs  306  and  307  have diameter D 1 , tube runs  308  and  309  have tube diameter D 2 , tube runs  310  and  311  have tube diameter D 3 , and tube runs  312  and  313  have tube diameter D 4 . It should be noted that there are progressively smaller tube run diameters proceeding from the inlet tube run  306  to the outlet tube run  313  and that D 1 &gt;D 2 &gt;D 3 &gt;D 4 . It is possible to have every tube run be a different diameter or there can only be one change in tube run diameter within the tube circuit runs and these both would still be in accordance with the fifth embodiment. The tubes are shown in the fifth embodiment as round but each tube could be flattened or streamlined as well to provide even more airflow and the actual geometry is not a limitation of the invention. The decision on how many tube runs have a different diameter is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop. Tubes runs of differing diameters may be joined together by being welded or brazed, joined by a reducing coupling, joined by sliding the smaller diameter tube inside the larger diameter tube and then brazing or could be mechanically fastened. The means of connecting tubes runs of differing diameters is not a limitation of the invention. The fifth embodiment has a reduction in cross sectional area, a reduction in tube surface area with an increase in external airflow. 
     Referring now to  FIG.  6   , sixth embodiment  450  is shown with at least two indirect heat exchangers  400  and  500 . Embodiment  450  has top indirect heat exchanger  400  with eight circuits and four passes or tube runs and bottom indirect heat exchanger  500  also has eight circuits and four passes or tube runs. Top indirect heat exchanger  400  is positioned on top of bottom indirect heat exchanger  500  such that there are a total of eight circuits and eight passes or tube runs for the entire indirect heat exchanger of embodiment  450 . Top indirect coil  400  has inlet and outlet headers  402  and  404  and is comprised of a tube runs  406 , 407 , 408  and  409  having generally round tube runs of the same diameter  465 . It should be understood that tube runs  406 , 407 , 408  and  409  are four passes and comprise one of the eight circuits of indirect coil  400  and that the coil tubes are connected by Ubends that are not shown. Bottom indirect heat exchanger  500  has inlet and outlet headers  502  and  504  and is comprised of tube runs  510 , 511 , 512  and  513 . Tube runs in the bottom indirect heat exchanger  500  all have the same D 2  to D 1  ratio which is usually larger than 1.0, less than 6.0 and vertical dimension D 2  is greater than top indirect tube run diameter  465 . It should be understood that tube runs  510 ,  511 ,  512  and  513  are four passes and comprise one of the eight circuits of indirect heat exchanger  500  and that the tube runs are connected by Ubends that are not shown. It should be further understood that all tubes shown in bottom indirect heat exchanger  500  have generally the same flattened tube shape and same D 2  to D 1  ratio. Top indirect heat exchanger outlet header  404  is connected to bottom indirect heat exchanger  500  inlet header  502  via connection piping  520  as shown. Alternatively, inlet headers  402  and  502  may be connected in together in parallel and outlet headers  404  and  504  may be connected in parallel (not shown). Note that bottom indirect heat exchanger  500  may instead employ smaller diameter tubes or simply a more streamlined tube shape than the top indirect heat exchanger  400  tube runs and still be in accordance with the sixth embodiment. Top indirect heat exchanger  400  is shown with round tubes but as shown in  FIG.  4 B , the tubes in top indirect section  400  may start with a less flattened shape than the bottom indirect heat exchange section  500  and still be in accordance with the sixth embodiment. Top and bottom indirect heat exchanger tube runs may all also be elliptical with the top indirect heat exchanger tube runs B/A ratio being smaller than the bottom indirect heat exchanger tube run B/A ratio and still is in accordance with the sixth embodiment. The decision on the geometry difference between the top and bottom indirect heat exchangers is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop. 
     Now referring to  FIGS.  7 A,  7 B and  7 C  the seventh, eighth and ninth embodiments are shown respectively. To further increase heat exchange efficiency of the sixth embodiment  450  shown in  FIG.  6   , seventh embodiment  550  is shown in  FIG.  7    A with gap  552  separating top indirect heat exchanger  400  and bottom indirect heat exchanger  500 . Gap  552 , which is greater than one inch in height, allows more rain zone cooling of the spray water by allowing direct contact between the air flowing and the spray water generally flowing downward. Another way to further increase the heat exchange efficiency of the sixth embodiment  450  of  FIG.  6    is to add direct heat exchange section  554  between top indirect heat exchange section  400  and bottom indirect heat exchange section  500  as shown in eighth embodiment  560  in  FIG.  7 B . Adding direct section  554 , which is at least one inch in height, allows spray water cooling between indirect heat exchange sections  400  and  500  by allowing direct heat exchange between the air flowing and the spray water which is flowing generally downward. To achieve a hybrid mode of operation of sixth embodiment  450  shown in  FIG.  6   , secondary spray section  556  is added between top indirect heat exchange section  400  and bottom indirect heat exchange section  500  as shown in ninth embodiment  570  in  FIG.  7 C . Adding secondary spray section  556  allows bottom indirect heat exchanger  500  to operate wet when top heat exchange section  400  may run dry which saves water and adds a hybrid mode of operation. 
     Referring now to  FIG.  8   , tenth embodiment  650  is shown with at least two indirect heat exchangers  600  and  700 . Embodiment  650  has top indirect heat exchanger  600  with eight circuits and four passes or tube runs. Note however, that bottom indirect heat exchanger  700  has a reduction in the number of circuits compared to top indirect heat exchange section  600 . In this case, bottom indirect section  700  has six circuits while top indirect section  600  has eight circuits. Top indirect heat exchanger  600  is positioned on top of bottom indirect heat exchanger  700  such that there are a total of eight tube runs but note that the reduction of horizontal tube projection is accomplished by changing the number of circuits hence changing the geometry of projected tubes in the airflow direction. This change in geometry between the top and bottom indirect sections  600  and  700  respectively decreases total tube cross section area, reduces total tube heat transfer surface area while increases external airflow. Top indirect heat exchange section  600  has inlet and outlet headers  602  and  604  and is comprised of a tube runs  606 , 607 , 608  and  609  having generally round tube runs of the same diameter  665 . It should be understood that tube runs  606 , 607 , 608  and  609  are four passes and comprise one of the eight circuits of indirect heat exchange section  600  and that the tube runs are connected by return bends that are not shown. Bottom indirect heat exchange section  700  has inlet and outlet headers  702  and  704  and is comprised of tube runs  710 ,  711 ,  712  and  713  all having generally round tube runs of the same diameter  765  which is generally the same diameter as tube run diameters  665 . It should be understood that tube runs  710 ,  711 ,  712  and  713  are four passes and comprise one of the six circuits of indirect heat exchanger  700  and that the tube runs are connected by return bends that are not shown. Top indirect heat exchanger outlet header  604  is connected to bottom indirect heat exchanger  700  inlet  702  via connection piping  620  as shown. Alternatively, inlet headers  602  and  702  may be connected in together in parallel and outlet headers  604  and  704  may be connected in parallel (not shown). Note that top and bottom indirect heat exchange sections  600  and  700  respectively may employ the same tube shape, whether round, elliptical, flattened, or streamlined. It is the reduction of circuits in bottom heat exchange section  700  which is the methodology to reduce the horizontal projected tube geometry to increase air flow, increase internal fluid velocity and internal heat transfer coefficients in the tenth embodiment  650 . The decision on the geometries used, and the difference in the number of circuits between the top and bottom indirect heat exchanger sections is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal tube side pressure drop. As was shown in  FIGS.  7 A,  7 B and  7 C  in how to further increase heat exchange efficiency of the sixth embodiment which included two indirect heat exchanger sections, the same can be done with the tenth embodiment where top indirect heat exchanger  600  and bottom indirect heat exchanger  700  can be separated by adding a gap greater than one inch as shown in  FIG.  7 A  or by adding a direct heat exchange section as shown in  FIG.  7 B . To add a hybrid mode of operation to the tenth embodiment, a secondary spray section may be added between the two indirect heat exchangers  600  and  700  as shown in  FIG.  7 C . 
     Now referring to  FIG.  9   , eleventh embodiment  770  is shown as an air cooled steam condenser. Steam header  772  feeds steam to tube runs  774 . Tube runs  774  are fastened to steam header  772  and condensate collection headers  779  by various techniques including welding and oven brazing and is not a limitation of the invention. Wavy fins  804  are fastened to tube runs  774  by various techniques such as welding and oven brazing and is not a limitation of the invention. The purpose of wavy fins  804  is to allow heat to transfer from the tube to the fin to the flowing air stream. As the steam condenses in tube runs  774 , water condensate is collected in condensate collection headers  779 . Fan motor  776  spins fan  777  to force air through steam condenser wavy fins  804 . Fan deck  775  seals off the pressurized air leaving fan  777  so it must exit through wavy fins  804 . There are multiple parallel tube run circuits  774  and to show the details of the change in geometry of the tube runs  774  and wavy fins  804 , two circuits shown within dotted lines  800  are shown in  FIGS.  10 A,  10 B, and  10 C  for clarity. 
     Now referring to  FIGS.  10 A,  10 B &amp;  10 C , eleventh embodiment  770  from  FIG.  9    is redrawn to show two tube runs in  FIG.  10 A  which is a detailed view of tube runs  774  from  FIG.  9   . It should be noted that tube runs  774  have no return bends but instead are one long tube run. The length of the tube runs are typically a few feet up to a hundred feet and is not a limitation of the invention. The tube run circuits  774  are shown with just two of many (hundreds) of repeated parallel tube runs now with tube runs  774  and wavy fins  804 . Wavy fins  804  are typically installed to each side of tube run  802  and function to increase the heat transfer from the air being forced through the wavy fins  804  to indirectly to condense the steam inside tube runs  774 . Tube runs  774  have a round internal cross section at the top (having maximum internal cross sectional area at the steam connection) with diameter  865  shown in  FIG.  10 C . Tube run  774  is then progressively flattened from the top to the bottom such that the horizontal cross section dimension D 5  is less then diameter  865  and the ratio of D 6  to D 5  is usually greater than 1 and less than 6. In the case of starting with a non-round shape, such as with micro channels for example, the ratio may be increase upwards to 20.0. The key to this embodiment is a change in geometric shape from the top to the bottom and can be any shape that is more streamlined near the bottom than the top and is not limited to a flattened shape. The distance between tube runs  774  can be seen at  838  at the top and wider dimension  840  at the bottom. The width of wavy fins  804  is  850  at the top and a wider dimension  852  at the bottom. This progressively widening of wavy fin  804  allows more contact area between the tube as one progresses from the top to bottom and more finned surface area as one travels from top to bottom which increases overall heat transfer to tube run  774 . Referring to  FIG.  10 C  where wavy fin  804  has been removed for clarity, it can be seen that tube run  774  is round with diameter  865  at the top and is flattened with width D 5  and length D 6 . As was discussed with all the other embodiments, the progressive flattening can be done in steps having a uniform flattening dimension every few feet or the tube runs may have a uniformly increasing ratio of length to width (shown as D 6  to D 5  at the bottom) along its entire length as shown in  FIG.  10 C . There are multiple improvements of the eleventh embodiment of  FIG.  10    over prior art. First, the internal cross sectional area is at a maximum at the top where the vapor to be condensed enters the tube. This allows the entering low density gas to flow at a higher flow rate with a lower pressure drop. Later as the vapor condenses, the need for internal cross sectional area is reduced because there is a much denser fluid having both vapor and condensate in the flow path and the geometry change allows optimum use of heat transfer surface area. In addition, the external and internal surface area is the same at the top and bottom of each tube run yet as the horizontal cross sectional dimension is progressively reduced, more air is invited to flow as the tube run is progressively flattened. In addition, the reduced horizontal cross sectional dimension with respect to the air flow path increases internal fluid velocities and internal heat transfer coefficients while allowing more external air to flow which increases the ability to condense more vapor. Another advantage is that as the tube run is flattened the wavy fin may be increased in size in both width and length if desired, and the fin to tube contact area increases as one proceeds from the tip to the bottom of the tube run which increases heat transfer to the tube. 
     Now referring to  FIG.  11   , an end view and 3D view of a twelfth embodiment of the present invention is shown as  950 . Indirect heat exchange section  950  consists of indirect heat exchange plates  952  where, in a closed circuit cooling tower or evaporative condenser, evaporative water is sprayed on the external side of the plates and air is also passed on the external side of the plates to indirectly cool or condense the internal fluid. Inlet plate header  951  allows the fluid to enter the inside of the plates and exit heat  953  allows fluid inside the plates to exit back to the process. Of particular note is that centerline top spacing  954  and centerline bottom spacing  954  between the plates are uniform and generally equal while exterior plate air spacing gap  956  is purposely smaller than air spacing  957 . Thus, the plates have a tapered shape in decreasing thickness from adjacent the inlet end to adjacent the outlet end. This change in plate geometry accomplishes many of the same benefits shown in all the other embodiments. In twelfth embodiment  950  there is essentially the same heat transfer surface area, a progressive reduction of internal cross sectional area from the inlet (top) to the outlet (bottom) and a progressively larger air gap  956  at the top compared to  957  at the bottom which allows more airflow, increases internal fluid velocity and increases internal heat transfer coefficients as one travels from the top to the bottom. The decision on the geometries used and the progressive air gaps between the top and bottom indirect plate heat exchanger sections is a balance between the amount of airflow improvement desired, difficulty in degree of manufacturing and allowable internal plate side pressure drop.