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    • 专利摘要:
    an improved indirect heat exchanger is provided in which it comprises a plurality of coil circuits, with each coil circuit comprising an indirect heat exchange sectional tube or exhaust. each plate or pipe exhaust has at least one change in geometric shape or may have a progressive change in geometric shape from input to output of the circuit. The change in geometric shape along the circuit length allows for simultaneous balancing of external air flow, internal heat transfer coefficients, internal fluid side pressure drop, transverse sectional area and heat transfer surface area to optimize heat transfer. heat.
    公开号:BR102017021821A2
    申请号:R102017021821-0
    申请日:2017-10-10
    公开日:2018-05-29
    发明作者:Beaver Andrew；Andrew Aaron David；Lilian Rousselet Yohann
    申请人:Baltimore Aircoil Company, Inc.；
    IPC主号:
    专利说明:

    (54) Title: INDIRECT HEAT EXCHANGER (51) Int. Cl .: F28F 1/02; F28F 13/08; F28F 3/12; F28D 1/047; F28D 7/00; (...) (30) Unionist Priority: 10/12/2016 US 15 / 291,773 (73) Holder (s): BALTIMORE AIRCOIL COMPANY, INC.
    (72) Inventor (s): ANDREW BEAVER; DAVID ANDREWAARON; YOHANN LILIAN ROUSSELET (74) Attorney (s): KASZNAR LEONARDOS INTELLECTUAL PROPERTY (57) Summary: An improved indirect heat exchanger is provided in which it comprises a plurality of coil circuits, with each coil circuit comprising a plate or exhaust from sectional indirect heat exchange tube. Each plate or pipe exhaust has at least one change in its geometric shape or it can have a progressive change in its geometric shape that takes place from the entrance to the exit of the circuit. The change in geometric shape along the length of the circuit allows simultaneously to balance the external air flow, internal heat transfer coefficients, lateral pressure drop of the internal fluid, cross sectional area and heat transfer surface area to optimize heat transfer. heat.
    / 28 "INDIRECT HEAT EXCHANGER" BACKGROUND AND SUMMARY OF THE INVENTION [001] The present invention relates to heat exchangers, and more particularly, to an indirect heat exchanger comprising a plurality of pipe exhaust circuits. Each circuit comprises a tube that has a plurality of pipe exhausts and a plurality of return folds. Each tube can have the same surface area from close to its connection to an inlet head up to close to its connection to an outlet head. However, the pipe exhaust geometry is changed as the pipe exhausts extend from the inlet close to the outlet head. In one case, the horizontal cross-sectional dimension of the pipe exhausts decreases as the pipe exhausts extend closer to the outlet head. Such a decrease in the horizontal cross-sectional dimension may be progressive from the proximity of the inlet head to the proximity of the outlet head or each coil tube exhaust may have a uniform horizontal cross-sectional dimension, with at least one horizontal cross-sectional dimension of pipe escapes that decrease closer to the outlet head.
    [002] In particular, an indirect heat exchanger is provided which comprises a plurality of circuits, with an input head connected to an input end of each circuit of an output head connected to an output end of each circuit. Each circuit comprises a pipe exhaust that extends in a series of exhausts and return bends from the input end of each circuit to the output end of each circuit. In the embodiments, the pipe exhausts may have return bends or may be a long straight pipe with no return bends, such as with a steam condenser coil. Each circuit pipe exhaust has a sectional dimension
    Petition 870170090013, of 11/22/2017, p. 7/53 / 28 pre-selected horizontal cross section near the inlet end of each coil circuit and each circuit pipe leak has a horizontal cross sectional dimension that decreases as the circuit pipe extends from the proximity of the end input of each circuit close to the output end of each coil circuit.
    [003] The modalities presented begin with a larger pipe geometry in the horizontal cross-sectional dimension or in the cross-sectional area in the first exhausts near the inlet head and then have a reduction or flattening (at least once) in the horizontal cross-sectional dimension of pipe escapes that proceed from the entrance to the exit and, generally, in the direction of air flow. A key advantage over progressively flattening a condenser is that the internal cross-sectional area needs to be the largest at the point where the least dense vapor enters the exhaust pipe. This attracts the gas to the pipe exhaust, reducing the lateral internal pressure drop, allowing more steam to enter the pipe exhaust. The reduction in cross-sectional dimension of horizontal pipe exhaust or flattening of the pipe in the air flow direction achieves several advantages over prior art heat exchangers. First, the reduced projected area reduces the drag coefficient, which imposes less resistance to the air flow, thus allowing greater air flow. In addition to gains in airflow for condensers, as the refrigerant is condensed, there is less need for an interior cross-sectional area as one progresses from the beginning (low vapor density) to the end (high density of vapor). liquid), so that it is beneficial for reducing the internal cross-sectional area as the fluid flows from the inlet to the outlet, allowing for higher internal fluid speeds and therefore greater internal heat transfer coefficients. This is true for condensers and fluid coolers, especially
    Petition 870170090013, of 11/22/2017, p. 8/53 / 28 fluid with low internal fluid speeds. In one (1) embodiment shown, the tube can start round and the geometric shape is gradually progressed for each group of two tube exhausts. The decision on how many pipe leaks are more loosely shaped and a reduction in horizontal cross-sectional dimension and how much of a reduction is needed is a balance between the amount of airflow improvement desired, the amount of internal heat transfer coefficient desired, difficulty in manufacturing degree and pressure drop of admissible inner side tube.
    [004] The typical pipe exhaust diameters covering indirect heat exchangers are in the range of 6.35 mm (1/4 inch) to 50.8 mm (2 inches), however, this is not a limitation of the invention. When pipe exhausts start with a large internal cross-sectional area and are then progressively flattened, the circumference of the tube and therefore the surface area, remains essentially unchanged in any of the flattening ratios for a given tube diameter, while that the internal cross-sectional area is progressively reduced and the area projected in the air flow outside the indirect heat exchanger is also reduced. The general shape of the flattened tube can be elliptical, oval with one or two geometric axes of symmetry, oval with a flat side or any flat shape. A key metric for determining the performance and pressure drop benefits of each stretch is the ratio of the long (vertical) side of the oval to the shortest (horizontal) side. A round tube can have a 1: 1 ratio. The level of flatness is indicated by increasing the side ratios. This invention refers to ratios that are in the range of 1: 1 to 6: 1 to provide optimized performance ratios. The optimized maximum oval ratio for each heat exchanger pipe leak is dependent on the working fluid inside the coil, the amount of performance gains on the desired air side, the desired increase in speed
    Petition 870170090013, of 11/22/2017, p. 9/53 / 28 of internal fluid and increase of internal heat transfer coefficients, of the coil operating conditions, of the permissible internal side tube pressure drop, as well as of the capacity to manufacture the desired coil geometry. In an ideal situation, all of these parameters will be balanced to satisfy the customer's exact need in order to optimize system performance, thereby minimizing energy and water consumption. [005] The granularity of the flattening progression is an important aspect of this invention. At one end, there is a design in which the amount of flattening is progressively increased through the length of multiple stretches or pipe exhausts from each circuit. This can be accomplished through an automated roll system built in the tube manufacturing process. A similar design with less granularity may involve at least one step reduction so that one or more sections or pipe leaks from each circuit can have the same level of flatness. For example, a project may have the first pipe exhaust without a degree of flatness, as may be the case with a round pipe, and the following three circuit pipe escapements may have a level of compression factor (degree of flatness) and the final four pipe exhaust sections may have another level (higher level) of compression factor. The less granular design may have one or more sections or exhausts of round pipe followed by one or more sections or exhausts of a single level of flattened pipe. This can be done with a set of rollers or by providing a top coil with round tubes and the bottom coil with elliptical or flat tubes. Yet another way to manufacture the different geometric tube shapes can be the stamping of the variant tube shapes and the welding of the plates together as found in document 4.434.112. It is likely that heat exchangers will soon be designed and produced using 3D printing machines for the exact geometries in order to optimize the
    Petition 870170090013, of 11/22/2017, p. 10/53 / 28 heat transfer, as proposed in that invention.
    [006] The exhaust pipe flattening can be carried out in line with the pipe manufacturing process, through the addition of automated rollers between the pipe laminator and the bending process. Alternatively, the flattening process can be carried out as a separate step with a pressing operation after flexing occurs. The presented modalities are applicable for any common heat exchanger tube material in which the most common is galvanized carbon steel, copper, aluminum and stainless steel, however, the material is not a limitation of the invention.
    [007] Now that the tube circuits can be progressively flattened, thereby reducing the horizontal cross-sectional dimension, it is possible to extremely densify the tube exhaust circuits without choking the external air flow. The proposed modalities thus allow an “extreme densification” of indirect heat exchanger tube circuits. A method described in U.S. Patent Number 6,820,685 can be employed to provide areas of depression in the U-fold overlap area, to locally reduce the diameter in the return bend, if desired. In addition, users skilled in the art will have the ability to fabricate return bends in pipe exhausts at the desired flattening ratios, and this is not a limitation of the invention.
    [008] Another way to fabricate a change in geometric shapes is to employ the use of an indirect top and bottom heat exchanger. The top heat exchanger can be produced from all round tubes while the bottom heat exchanger can be produced with a more used shape. This conserves the heat transfer surface area while increasing the overall air flow and decreasing the internal cross-sectional area. Another way of fabricating a shape change
    Petition 870170090013, of 11/22/2017, p. 11/53 / 28 geometric is to employ the use of an indirect top and bottom heat exchanger. The top heat exchanger can be produced from all round tubes while the bottom heat exchanger can be produced with a reduction in circuits, compared to the top coil. This reduces the heat transfer surface area while increasing the 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 in the number of circuits, the indirect heat exchanger system can comply with this modality.
    [009] An objective of the invention is to start with pipe exhausts of large internal cross-sectional area and then progressively reduce the horizontal cross-sectional dimension of pipe exhausts as they progress from inlet to outlet in order to reduce the drag coefficient and allow more external air flow.
    [0010] An objective of the invention is to start with pipe exhausts of large internal cross-sectional area and then progressively reduce the horizontal cross-sectional dimension of the pipe exhausts as they progress from inlet to outlet, to allow fluid of lesser density (steam) enter the exhaust pipe with very little pressure drop in order to maximize the internal fluid flow rate.
    [0011] An objective of the invention is to start with pipe exhausts of large internal cross-sectional area and then progressively reduce the horizontal cross-sectional dimension of pipe exhausts as they progress from inlet to outlet, in order to allow circuit densification tube end without choking external air flow.
    [0012] An objective of the invention is to start with pipe exhausts of large internal cross-sectional area and then reduce
    Petition 870170090013, of 11/22/2017, p. 12/53 / 28 progressively the horizontal cross-sectional dimension of pipe exhausts as they progress from the inlet to the outlet, in order to increase the internal fluid velocity and increase the internal heat transfer coefficients in the direction of the flow path. internal fluid.
    [0013] An objective of the invention is to start with pipe exhausts of large internal cross-sectional area and then progressively reduce the horizontal cross-sectional dimension of pipe exhausts as they progress from inlet to outlet in condensers, in order to take advantage of the fact that as the steam is condensed there is a need for a smaller cross-sectional area, which results in larger internal heat transfer coefficients with greater air flow, consequently, greater capacity.
    [0014] An objective of the invention is to start with pipe exhausts of large internal cross-sectional area and then progressively reduce the horizontal cross-sectional dimension of pipe exhausts as they progress from inlet to outlet, balancing customer demand on the desired capacity and permissible internal fluid pressure drop in order to customize the indirect heat exchanger design to meet and exceed customer expectations.
    [0015] An objective of the invention is to change a geometric shape of the pipe exhaust circuit at least once along the circuit path in order to allow to simultaneously balance the external air flow, the internal heat transfer coefficients, the cross sectional area and the heat transfer surface area to optimize the heat transfer.
    [0016] An objective of the invention is to change a geometric shape of the plate coil at least once along the circuit path, in order to allow to simultaneously balance the external air flow, the
    Petition 870170090013, of 11/22/2017, p. 13/53 / 28 internal heat transfer coefficients, cross sectional area and heat transfer surface area to optimize heat transfer.
    BRIEF DESCRIPTION OF THE DRAWINGS [0017] In the drawings:
    Figure 1 is a side view of a prior art indirect heat exchanger that includes a series of serpentine tube exhausts;
    Figure 2A is a rear view of an indirect heat exchanger, in accordance with the first embodiment of the present invention;
    Figure 2B is a rear view of an indirect heat exchanger, in accordance with a second embodiment of the present invention;
    Figure 3 is a side view of an indirect heat exchanger circuit, in accordance with the first embodiment of the present invention;
    Figure 4A is a rear view of an indirect heat exchanger, in accordance with a third embodiment of the present invention;
    Figure 4B is a rear view of an indirect heat exchanger, in accordance with a fourth embodiment of the present invention;
    Figure 5 is a rear view of an indirect heat exchanger, in accordance with a fifth embodiment of the present invention;
    Figure 6 is a rear view of two indirect heat exchangers, in accordance with a sixth embodiment of the present invention;
    Figure 7A is a rear view of two indirect heat exchangers, in accordance with a seventh embodiment of the present invention;
    Figure 7B is a rear view of two heat exchangers
    Petition 870170090013, of 11/22/2017, p. 14/53 / 28 indirect, in accordance with an eighth embodiment of the present invention;
    Figure 7C is a rear view of two indirect heat exchangers, in accordance with a ninth embodiment of the present invention;
    Figure 8 is a rear view of two indirect heat exchangers, in accordance with a tenth embodiment of the present invention;
    Figure 9 is a 3D view of an indirect heat exchanger, in accordance with an eleventh embodiment of the present invention.
    Figure 10A, Figure 10B and Figure 10C are partial perspective views of the eleventh embodiment of the present invention;
    Figure 11A is a rear view of an indirect heat exchanger, in accordance with a twelfth embodiment of the present invention;
    Figure 11B is a 3D view of the twelfth embodiment of the present invention.
    DETAILED DESCRIPTION [0018] Referring now to Figure 1, an evaporative-cooled coil product 10 of the prior art may be a closed circuit cooling tower or an evaporative condenser. Both of these products are well known and can operate wet in the evaporation 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. The pump 12 receives the evaporatively cooled sprayed fluid, usually water, from the cold water tank 11 and pumps it to the primary spray water head 19 where the water comes out of nozzles or holes 17 to distribute water over the exchanger of indirect heat 14. The water head of
    Petition 870170090013, of 11/22/2017, p. 15/53 / 28 spray 19 and the nozzles 17 serve to distribute the water evenly over the top of the indirect heat exchanger 14. As the cooler water is distributed over the top of the indirect heat exchanger 14, the motor 21 turns the fan 22, which induces or draws ambient air inwards through inlet skylights 13, upwards through the indirect heat exchanger 14, then by means of bypass eliminators 20, which serves to prevent deviations from leaving the unit and then the air heated air is blown into the environment. Air generally flows in a counterflow direction to the downward spray water. Although Figure 1 is shown with the axial fan 22 that induces or draws air through the unit, the actual fan system can be of any style of fan system that moves air through the unit, which includes, without limitation, inducing and forcing a deviation in a flow that is generally counter-flow, cross-flow or parallel to the jet. Additionally, motor 21 can be belt driven, as shown, gear driven or connected directly to the fan. The indirect heat exchanger 14 is shown with an input connection pipe 15 connected to the input head 24 and the output connection pipe 16 connected to the output head 25. The input head 24 is connected to the input of the multiple circuit serpentine tube, while the output head 25 is connected to the output of the multiple serpentine tube circuits. Serpentine tube exhausts are connected with return bend sections 18. The return bend sections 18 can be formed continuously in the circuit called serpentine tube exhausts or can be welded between straight lengths of tubes. It must be understood that the process fluid direction can be reversed to optimize the heat transfer and is not a limitation for the presented modalities. It should also be understood that the number of circuits and the number of sections or rows of pipe exhausts within an indirect serpentine heat exchanger is not a
    Petition 870170090013, of 11/22/2017, p. 16/53 / 28 limitation for the modalities presented.
    [0019] With reference now to Figure 2A, the indirect coil 100 conforms to a first embodiment of the present invention. Figure 2A shows eight circuits and eight stretches or rows of tube of modality 100. Indirect heat exchanger 100 has inlet and outlet heads 102 and 104 and comprises pipe exhausts 106, 107, 108, 109, 110, 111, 112 and 113. Tube exhausts 106 and 107 are a pair of round tubes of identical geometry and have equivalent tube diameters 101. Tube exhausts 108 and 109 are another pair of tube exhausts that have a different geometry compared to exhaust pipe pairs 106 and 107 with equivalent shapes that have reduced horizontal D3 dimensions and increased vertical D4 dimension in relation to round pipes 106 and 107. The ratio between D4 and D3 is usually greater than 1.0 and less than 6, 0. In addition, the heat exchanger pipe leak 108 and 109 can have a uniform ratio between D4 and D3 along its length, as shown, or a ratio that increases uniformly between D4 and D3 along its length. The pair of pipe exhausts 110 and 111 also have a different geometry and have equivalent shapes with reduced horizontal D5 dimensions and an increased vertical D6 dimension, in relation to pipe exhausts 108 and 109. The ratio between D6 and D5 is usually greater than 1.0, less than 6.0 and is also greater than the ratio between D4 and D3. In addition, the pipe leak 110 and 111 can have a uniform ratio between D6 and D5 along its length, as shown, or a ratio that increases uniformly between D6 and D5 along its length. The pair of pipe exhausts 112 and 113 also have a different geometry and have equivalent shapes with reduced horizontal D7 dimensions and an increased vertical D8 dimension in relation to pipe exhausts 110 and 111. The ratio between D8 and D7 is usually greater than 1 , 0, less than 6.0 and also greater than the ratio between D6 and D5.
    Petition 870170090013, of 11/22/2017, p. 17/53 / 28
    In addition, pipe exhausts 112 and 113 can have a uniform ratio between D8 and D7 along their length, as shown, or a ratio that increases uniformly between D8 and D7 along their length. The pipe exhaust 106 is connected to the inlet head 102 of the indirect heat exchanger 100 and the pipe exhaust 113 is connected to the outlet head 104. In a preferred arrangement, the pipes are round at the inlet which has a ratio of vertical pipe leakage dimension between vertical and horizontal of 1.0 and are progressively flattened to a pipe leakage dimension ratio between vertical and horizontal of approximately 3.0 near the outlet. The practical limits of dimension ratios between horizontal and vertical are between 1.0 for round pipes and can be as high as 6. It should be understood, in this first modality, that as the pipe leak dimension ratio between the vertical and the horizontal it increases, the exhausts of pipe become more flattened and more used, which allows greater air flow while keeping the external and internal surface areas constant. It should be noted that in the first mode, the horizontal dimension is progressively reduced from the inlet to the outlet of the pipe exhausts, while the vertical dimension is progressively increased from the inlet to the outlet. It should be further understood that the tube shapes can start out as round and be flattened progressively, as shown, they can start out as flattened and be more flattened progressively, or start flattened and become more flattened. When dealing with elliptical shapes, the B / A ratio is usually greater than 1 and refers to the major and minor geometric axes, respectively. It should also be understood that the first pipe leak can be elliptical with a B / A ratio close to 1.0 and progressively increase the elliptical B / A ratio between the inlet and the outlet. It must be understood that the first modality shows horizontal dimensions
    Petition 870170090013, of 11/22/2017, p. 18/53 / 28 progressively reduced and vertical dimensions progressively increased from the first to the last pipe leak and that the initial shape, whether round, elliptical or tapered is not a limitation of the modality. It should also be understood that each two sections can have the same tube shape, as shown, or the whole tube can be flattened or progressively flattened. The decision on how to make the indirect heat exchanger circuits is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and allowable internal side pipe pressure drop.
    [0020] With reference now to Figure 2B, the indirect coil 150 is in accordance with a second embodiment of the present invention. Figure 2B shows eight circuits and eight stretches or rows of tube of modality 150. Indirect heat exchanger 150 has inlet and outlet heads 102 and 104 and comprises pipe exhausts 106, 107, 108, 109, 110, 111, 112 and 113. The pipe exhausts 106 and 107 in Figure 2B are not as round as they were in Figure 2A, instead they are a pair of pipe exhausts that have an initial horizontal D1 dimension and an initial vertical D2 dimension. The pipe exhausts 108 and 109 are another pair of pipe exhausts that have a different geometry compared to the pipe exhaust pairs 106 and 107 with equivalent shapes that have reduced horizontal D3 dimensions and the increased vertical D4 dimension in relation to the pipes round 106 and 107. The ratio between D4 and D3 is usually greater than 1.0 and less than 6.0 and the ratio between D4 and D3 is usually greater than the ratio between D2 and D1. In addition, the heat exchanger pipe leak 108 and 109 can have a uniform ratio between D4 and D3 along its length, as shown, or a ratio that increases uniformly between D4 and D3 along its length. The pair of pipe exhausts 110 and 111 also have a different geometry and have equivalent shapes with reduced horizontal D5 dimensions and the dimension
    Petition 870170090013, of 11/22/2017, p. 19/53 / 28
    Increased vertical D6, in relation to pipe exhausts 108 and 109. The ratio between D6 and D5 is usually greater than 1.0, less than 6.0 and is also greater than the ratio between D4 and D3. In addition, the pipe leak 110 and 111 can have a uniform ratio between D6 and D5 along its length, as shown, or a ratio that increases uniformly between D6 and D5 along its length. The pair of pipe exhausts 112 and 113 also have a different geometry and have equivalent shapes with reduced horizontal D7 dimensions and an increased vertical D8 dimension in relation to pipe exhausts 110 and 111. The ratio between D8 and D7 is usually greater than 1 , 0, less than 6.0 and also greater than the ratio between D6 and D5. In addition, pipe exhausts 112 and 113 can have a uniform ratio between D8 and D7 along their length, as shown, or a ratio that increases uniformly between D8 and D7 along their length. The pipe exhaust 106 is connected to the inlet head 102 of the indirect heat exchanger 100 and the pipe exhaust 113 is connected to the outlet head 104. In one arrangement, the pipes start almost round at the inlet which has a dimension ratio of pipe leakage between vertical and horizontal close to 1.0 and are progressively flattened to a pipe leakage dimension ratio between vertical and horizontal close to 3.0 near the outlet. The practical limits of dimension ratios between horizontal and vertical are between 1.0 for round tubes and can be as high as 6. It should be understood in this second modality, that as the ratio of dimension of pipe leakage between the vertical and the horizontal increases, the pipe exhausts become flatter and more streamlined, which allows greater air flow while keeping the external and internal surface areas constant. It should be noted that in this second mode, the horizontal dimension is progressively reduced from the entrance to the outlet of the pipe exhausts while the vertical dimension is increased
    Petition 870170090013, of 11/22/2017, p. 20/53 / 28 progressively from entry to exit. It should be further understood that the tube shapes can start out slightly flattened, compared to the first embodiment shown in Figure 2A that starts with round tubes and then can be progressively flattened out, as shown, or start tapering and becoming more tapered. When dealing with elliptical shapes, the B / A ratio is usually greater than 1 and refers to the major and minor geometric axes, respectively. It should also be understood that the first pipe leak can be elliptical with a B / A ratio close to 1.0 and progressively increase the elliptical B / A ratio between the inlet and the outlet. It should be understood that the second modality shows horizontal dimensions progressively reduced and vertical dimensions progressively increased from the first to the last pipe leak and that the initial shape, whether round, elliptical or stretched is not a limitation of the modality. It should also be understood that each two sections can have the same tube shape, as shown, or the whole tube can be flattened or progressively flattened. The decision on how to make the indirect heat exchanger circuits is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and allowable internal side pipe pressure drop.
    [0021] Referring now to Figure 3, circuit 103 of the first embodiment of Figure 2 is shown from a side view to understand how each circuit can be constructed. Exhaust pipes 106, 107, 108, 109, 110, 111, 112 and 113 are also shown from a sectional view AA. Exhaust pipes 106 and 107 are generally round pipes and have equivalent pipe diameters 101. Exhaust pipe 106 has a round U-curve 120 that connects it to exhaust pipe 107. Exhaust pipe 107 is connected to the exhaust pipe 108 with transition 115. Transition 115 begins as round at one end and changes to the ratio format between D4 and D3 at the other end. THE
    Petition 870170090013, of 11/22/2017, p. 21/53 / 28 transition 115 can simply be pressed or cast from a die, extruded or it can be a joint that is typically welded or by braze-brazing the pipe exhausts. The transition 115 can also be pressed into the tube when the tube is undergoing serpentine bending operation. The method for shaping transition 115 is not a limitation of the invention. The round U-folds 120 can be formed to fit the following return fold so that the number of circuits in the indirect heat exchanger can be increased as taught in document 6.820.685. U-folds 120 can also be flattened mechanically while pipe exhausts are flexed and assume the general shape of each section of pipe exhaust which can be a return fold shape that changes along the coil circuit. The previous discussion is the same for transitions 115, 116 and 117. The pipe exhausts 108 and 109 have reduced and equivalent horizontal D3 dimensions and an increased vertical D4 dimension. The ratio between D4 and D3 is usually greater than 1.0 and less than 6.0. In addition, coil tube exhausts 108 and 109 can have a uniform ratio between D4 and D3 along their length, as shown, or a ratio that increases uniformly between D4 and D3 along their length. The pipe exhausts 110 and 11 have reduced and equivalent horizontal D5 dimensions and an increased vertical D6 dimension. The ratio between D6 and D5 is usually greater than 1.0, less than 6.0 and also greater than the ratio between D4 and D3. In addition, pipe exhausts 110 and 111 can have a uniform ratio between D6 and D5 along their length, as shown, or a ratio that increases uniformly between D6 and D5 along their length. The pipe exhausts 112 and 113 have reduced and equivalent horizontal D7 dimensions and an increased vertical D8 dimension. The ratio between D8 and D9 is usually greater than 1.0, less than 6.0 and also greater than the ratio between D6 and D5.
    Petition 870170090013, of 11/22/2017, p. 22/53 / 28
    In addition, the pipe exhaust 112 and 113 can have a uniform ratio between D8 and D7 along its length, as shown, or a ratio that increases uniformly between D8 and D7 along its length.
    [0022] Referring now to Figure 4A, the indirect heat exchanger
    200 complies with a third embodiment of the present invention. Mode 200 has eight circuits and eight sections or pipe exhausts. Mode 200 has at least a reduction in horizontal dimension and an increase in vertical dimension within circuit pipe exhausts. The indirect heat exchanger 200 has inlet and outlet heads 202 and 204 respectively and comprises coil tubes that have exhaust lengths 206, 207, 208, 209, 210, 211, 212 and 213. It should be noted that the exhaust pipe 206, 207, 208 and 209 have equivalent pipe diameters 201. Mode 200 also has pipe exhausts 210, 211, 212 and 213, each of which have equivalent horizontal cross-sectional D3 dimensions and vertical cross-sectional D4 dimensions equivalent. The ratio between D4 and D3 is usually greater than 1.0, less than 6.0 and the vertical D4 dimension is greater than the pipe diameter 201 while the horizontal D3 dimension is less than the pipe diameter 201. In one arrangement of the third modality, the first ratio is greater than or equal to 1.0 and less than 2.0 (it is equal to 1.0 with round tubes) and the second ratio is greater than the first ratio, however, less than 6.0 . It is observed that, in the third embodiment of Figure 4A, each circuit pipe exhaust length has at least one change in geometric shape as the circuit pipe exhaust extends from the inlet to the outlet. The decision on how many pipe leaks have reduced horizontal cross-sectional dimensions, as shown in Figures 6 and 7, is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and drop in pipe pressure
    Petition 870170090013, of 11/22/2017, p. 23/53 / 28 admissible internal side and is not a limitation of the invention.
    [0023] Referring now to Figure 4B, the indirect heat exchanger
    250 complies with a fourth embodiment of the present invention. The 250 modality has eight circuits and eight sections or pipe exhausts. Mode 250 has at least a reduction in the horizontal dimension and increases in the vertical dimension within the circuit pipe exhausts. The indirect heat exchanger 250 has inlet and outlet heads 202 and 204 respectively and comprises coil tubes that have exhaust lengths 206, 207, 208, 209, 210, 211, 212 and 213. It should be noted that, unlike of the modality shown in Figure 4A that started with round tubes in the first sections or rows, modality 250 has pipe exhausts 206, 207, 208 and 209, each of which have equivalent horizontal D1 dimensions and vertical D2 dimensions equivalent. The ratio between D2 and D1 is usually greater than 1.0 and less than 6.0. The 250 modality also has pipe exhausts 210, 211, 212 and 213, each of which has equivalent horizontal cross-sectional dimensions D3 and vertical cross-sectional dimensions D4. The ratio between D4 and D3 is usually greater than 1.0, less than 6.0, and generally greater than the ratio between D2 and D1. In a fourth embodiment, the first ratio (D2 / D1) is greater than or equal to 1.0 and less than 2.0 (D2 / D1 is greater than 1.0 as shown) and the second ratio (D4 / D3) ) is greater than the first ratio, but less than 6.0. It is observed that, in the fourth embodiment of Figure 4B, each circuit pipe exhaust length has at least one change in geometric shape as the circuit pipe exhaust extends from the entrance to the exit. The decision on how many pipe exhausts have reduced horizontal cross-sectional dimensions is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and allowable internal side pipe pressure drop and is not a limitation of the invention.
    Petition 870170090013, of 11/22/2017, p. 24/53 / 28 [0024] Referring now to Figure 5, the indirect heat exchanger
    300 complies with a fifth embodiment of the present invention. Modality 300 has eight circuits and eight sections or pipe exhausts, where each pair of pipe exhausts has a different diameter and has progressively smaller diameters from inlet pipe exhaust 306 to outlet pipe exhaust 313. A modality 300 has inlet and outlet heads 302 and 304, respectively, and comprises coil tubes that have pipe exhausts 306, 307, 308, 309, 310, 311, 312 and 313. It should be noted that the pair of exhaust pipes pipe 306 and 307 have a diameter D1, pipe exhausts 308 and 309 have a diameter D2 of pipe, pipe exhausts 310 and 311 have a diameter of pipe D3 and pipe exhausts 312 and 313 have a diameter of pipe D4. It should be noted that there are progressively smaller pipe exhaust diameters that proceed from the inlet pipe outlet 306 to the outlet pipe outlet 313 and that D1> D2> D3> D4. It is possible that each pipe leak is of a different diameter, or there may be only one change in the pipe leakage diameter within the pipe circuit passages, and these two still comply with the fifth embodiment. The tubes are shown in the fifth embodiment as round, but each tube can be flattened or flattened as well as providing even more airflow, and the actual geometry is not a limitation of the invention. The decision of how many pipe exhausts have a different diameter is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and allowable internal side pipe pressure drop. The tube passages with different diameters can be joined together by welding or braze-brazing, joined by a reducing coupling, joined by sliding the smaller diameter tube into the larger diameter tube and then by brazing brazing, or can be fixed mechanically. The means for connecting exhaust pipes of diameters
    Petition 870170090013, of 11/22/2017, p. 25/53 / 28 is not a limitation of the invention. The fifth modality has a reduction in cross-sectional area, a reduction in tube surface area with an increase in external air flow.
    [0025] With reference now to Figure 6, the sixth modality 450 is shown with at least two indirect heat exchangers 400 and 500. The modality 450 has an indirect top heat exchanger 400 with eight circuits and four sections or pipe exhausts and the indirect bottom heat exchanger 500 also has eight circuits and four sections or pipe exhausts. The indirect top heat exchanger 400 is placed on top of the indirect bottom heat exchanger 500, so that there are a total of eight circuits and eight sections or pipe exhausts for the entire 450 mode indirect heat exchanger. The coil indirect top 400 has inlet and outlet heads 402 and 404, and comprises pipe exhausts 406,407,408 and 409 which generally have round pipe exhausts of the same diameter 465. It should be understood that pipe exhausts 406,407,408 and 409 are four passages and they comprise one of eight indirect coil circuits 400 and that the coil tubes are connected by U-bends which are not shown. The indirect bottom heat exchanger 500 has inlet and outlet heads 502 and 504 and comprises pipe exhausts 510, 511, 512 and 513. All pipe exhausts in the indirect bottom heat exchanger 500 have the same ratio between D2 and D1, which is normally greater than 1.0, less than 6.0 and the vertical dimension D2 is greater than the top indirect pipe exhaust diameter 465. It should be understood that the pipe exhausts 510, 511, 512 and 513 are four passages and comprise one of the eight indirect heat exchanger circuits 500 and that the pipe exhausts are connected by U-folds that are not shown. It should be further understood that all tubes shown in the indirect bottom heat exchanger 500 generally have the same flattened tube shape and the same ratio between D2 and D1. The output head of
    Petition 870170090013, of 11/22/2017, p. 26/53 / 28 indirect top heat exchanger 404 is connected to the inlet head 502 of indirect bottom heat exchanger 500 via connection piping 520, as shown. Alternatively, the input heads 402 and 502 can be connected together in parallel and the output heads 404 and 504 can be connected in parallel (not shown). Note that the indirect bottom heat exchanger 500 may instead employ tubes of smaller diameter or simply a looser tube shape than the exhaust pipes of the indirect top heat exchanger 400 and still comply with the sixth modality. The indirect top heat exchanger 400 is shown with round tubes, however, as shown in Figure 4B, the tubes in indirect top section 400 can start with a less flattened shape than the bottom indirect heat exchange section 500 and still may comply with the sixth modality. Exhaust pipes from the top indirect heat exchanger and from the bottom of the pipe can also be elliptical, with the B / A ratio between exhausts from the indirect indirect heat exchanger tube being less than the B / A ratio between the exhausts. of indirect bottom heat exchanger tube, and still complies with the sixth modality. The decision of the difference in geometry between top and bottom indirect heat exchangers is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and allowable internal side pipe pressure drop.
    [0026] Now with reference to Figure 7A, 7B and 7C the seventh, eighth and ninth modalities are shown, respectively. To further increase the heat exchange efficiency of the sixth mode 450 shown in Figure 6, the seventh mode 550 is shown in Figure 7A with a gap 552 that separates the indirect top heat exchanger 400 and the indirect bottom heat exchanger 500 Clearance 552, which is greater than 25.4 mm (1 inch) in height, allows more cooling of the spray water rain zone, allowing direct contact between the flowing air and the water from
    Petition 870170090013, of 11/22/2017, p. 27/53 / 28 spray that usually flow down. Another way to further increase the heat exchange efficiency of the sixth modality 450 of Figure 6 is to add a direct heat exchange section 554 between the top indirect heat exchange section 400 and the bottom indirect heat exchange section 500 , as shown in the eighth modality 560 in Figure 7B. Adding the direct section 554, which is at least 25.4 mm (1 inch) high, allows spray water to be cooled between the indirect heat exchange sections 400 and 500, allowing direct heat exchange between the flowing air and the spray water that is generally flowing down. To perform a hybrid mode of operation of the sixth modality 450 shown in Figure 6, the secondary spray section 556 is added between the top indirect heat exchange section 400 and the bottom indirect heat exchange section 500, as shown in ninth modality 570 in Figure 7C. Adding the secondary spray section 556 allows the indirect bottom heat exchanger 500 to operate wet when the top heat exchange section 400 can run dry, which saves water and adds a hybrid mode of operation.
    [0027] With reference now to Figure 8, the tenth modality 650 is shown with at least two indirect heat exchangers 600 and 700. Modality 650 has an indirect top heat exchanger 600 with eight circuits and four sections or pipe exhausts . Note, however, that the indirect bottom heat exchanger 700 has a reduction in the number of circuits compared to the top indirect heat exchange section 600. In this case, the bottom indirect section 700 has six circuits, while that the top indirect section 600 has eight circuits. The indirect top heat exchanger 600 is placed on top of the indirect bottom heat exchanger 700, so that there are a total of eight pipe escapes, but it should be noted that the reduction of the horizontal pipe projection is accomplished by changing the number of circuits, thereby changing the geometry of projected tubes
    Petition 870170090013, of 11/22/2017, p. 28/53 / 28 in the air flow direction. This change in geometry between the top and bottom indirect sections 600 and 700, respectively, decreases the total pipe cross-sectional area, reduces the total pipe heat transfer surface area while increasing the external air flow. The top indirect heat exchange section 600 has inlet and outlet heads 602 and 604 and comprises pipe exhausts 606, 607, 608 and 609 which generally have round pipe exhausts of the same diameter 665. Exhausts should be understood tube tubes 606, 607, 608 and 609 are four passages and comprise one of the eight indirect heat exchange section circuits 600 and that the tube exhausts are connected by return bends which are not shown. The bottom indirect heat exchange section 700 has inlet and outlet heads 702 and 704 and comprises pipe exhausts 710, 711, 712 and 713, where all generally have round pipe exhausts of the same diameter 765, which is generally the same diameter as pipe exhaust diameters 665. It should be understood that pipe exhausts 710, 711, 712 and 713 are four sections and comprise one of the six indirect heat exchanger circuits 700 and that the pipe exhausts are connected for return folds that are not shown. The top indirect heat exchanger output head 604 is connected to the indirect bottom heat exchanger inlet 702 via connection piping 620, as shown. Alternatively, input heads 602 and 702 can be connected to each other in parallel and output heads 604 and 704 can be connected in parallel (not shown). It is observed that the top and bottom indirect heat exchange sections 600 and 700, respectively, can employ the same tube shape, whether round, elliptical, flat or flat. It is the reduction of circuits in the bottom heat exchange section 700 that is the methodology for reducing the horizontal pipe geometry designed to increase the air flow, increase the internal fluid velocity and the internal heat transfer coefficients in the tenth modality 650. A
    Petition 870170090013, of 11/22/2017, p. 29/53 / 28 decision of 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 desired airflow improvement, difficulty in manufacturing degree and fall permissible internal side tube pressure. As shown in Figure 7A, 7B and 7C of how to further increase the heat exchange efficiency of the sixth modality which included two sections of indirect heat exchanger, the same can be done with the tenth modality, in which top heat exchanger indirect 600 and the indirect bottom heat exchanger 700 can be separated by adding a gap greater than 25.4 mm (1 inch), as shown in Figure 7A or, by adding a direct heat exchange section, as shown in Figure 7B. To add a hybrid mode of operation to the tenth mode, the secondary spray section can be added between the two indirect heat exchangers 600 and 700, as shown in Figure 7C.
    [0028] Still with reference to Figure 9, the eleventh modality 770 is shown as an air-cooled vapor condenser. The steam head 772 supplies steam to the pipe exhausts 774. The pipe exhausts 774 are attached to the steam head 772 and the condensate collection heads 779 by various techniques including welding and oven welding and is not a limitation of invention. The corrugated fins 804 are fixed to the pipe exhausts 774 by various techniques such as welding and oven welding, and it is not a limitation of the invention. The purpose of 804 corrugated fins is to allow heat transfer from the tube to the fin for the flowing air stream. As steam is condensed in exhaust pipes 774, water condensate is collected in condensate collection heads 779. Fan motor 776 rotates fan 777 to force air through the wavy fins of steam condenser 804. The fan platform 775 seals the pressurized air that leaves the fan 777, so it must come out through
    Petition 870170090013, of 11/22/2017, p. 30/53 / 28 corrugated fins 804. There are multiple parallel pipe exhaust circuits 774 and, to show the details of the change in geometry of pipe exhaust 774 and corrugated fins 804, two circuits shown within dotted lines 800 are shown in Figures 10A, 10B and 10C to clarify.
    [0029] Now with reference to Figure 10A, 10B and 10C, the eleventh modality 770 of Figure 9 is redefined to show two pipe exhausts in Figure 10A, which is a detailed view of pipe exhausts 774 of Figure 9. if it is observed that the 774 pipe exhausts do not have return bends, however, they are instead a long pipe exhaust. The length of pipe exhausts is typically from a few feet up to 30.48 mm (100 feet) and is not a limitation of the invention. Pipe exhaust circuits 774 are shown with only two of many (hundreds) of parallel pipe exhausts now repeated with pipe exhausts 774 and corrugated fins 804. Corrugated fins 804 are typically installed on each side of pipe exhaust 802 and work to increase the heat transfer of the air that is forced through corrugated fins 804 to indirectly condense the steam inside the 774 pipe exhausts. The 774 pipe exhausts have a round internal cross section at the top (which has an internal cross sectional area steam connection) with a diameter of 865 shown in Figures 10C. The exhaust pipe 774 is then flattened progressively from the top to the bottom, so that the horizontal cross-sectional dimension D5 is smaller, so the diameter 865 and the ratio between D6 and D5 are usually greater than 1 and less than 6. If you start with a non-round shape, such as with microchannels, for example, the ratio can increase upwards by 20.0. The key to this modality is a change in geometric shape from the top to the bottom and it can be any shape that is more tapered towards the bottom than
    Petition 870170090013, of 11/22/2017, p. 31/53 / 28 from the top and is not limited to a flattened shape. The distance between pipe exhausts 774 can be seen at 838 at the top and at the widest dimension 840 at the bottom. The width of corrugated fins 804 is 850 at the top and a wider dimension 852 at the bottom. This progressive enlargement of the corrugated fin 804 allows greater contact area between the tube as one progresses from the top to the bottom and more finned surface area as one travels from the top to the bottom, which increases the overall heat transfer to the exhaust pipe 774. Referring to Figure 10C, where the corrugated fin 804 has been removed for clarity, it can be seen that the exhaust pipe 774 is round with a diameter 865 at the top and it is flattened with a width D5 and a length D6. As discussed with all other modalities, progressive flattening can be done in steps that have a uniform flattening dimension every few feet or the pipe escapes can have a ratio that increases uniformly between length and width (shown as D6 to D5 at the bottom) along the entire length, as shown in Figure 10C. There are multiple improvements to the eleventh modality in Figure 10 over the prior art. First, the internal cross-sectional area is at most at the top, where the steam to be condensed enters the pipe. This allows incoming low density gas to flow at a higher flow rate with a lower pressure drop. Then, as the steam is condensed, the need for internal cross-sectional area is reduced due to the fact that there is a much denser fluid that has both steam and condensate in the flow path and the change in geometry allows for use optimal heat transfer surface area. In addition, the external and internal surface area is the same at the top and bottom of each pipe exhaust, although as the horizontal cross-sectional dimension is progressively reduced, more air is invited to flow as the pipe exhaust is
    Petition 870170090013, of 11/22/2017, p. 32/53 / 28 progressively flattened. In addition, the reduced horizontal cross-sectional dimension in relation 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 steam. Another advantage is that as the pipe exhaust is flattened, the corrugated fin can be increased in size in both width and length if desired, and the fin for the pipe contact area increases as one proceeds from the tip to the bottom of the pipe exhaust, which increases the heat transfer to the pipe.
    [0030] Now with reference to Figure 11, a rear view and 3D view of a twelfth embodiment of the present invention is shown as 950. The 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 outside of the plates and air is also passed to the outside of the plates to indirectly cool or condense the internal fluid. The inlet plate head 951 allows fluid to enter the interior of the plates and the outlet heat 953 allows the fluid inside the plates to exit back into the process. Note in particular that the centerline top spacing 954 and centerline bottom spacing 954 between the plates are uniform and generally the same while the air gap clearance of the outer plate 956 is purposely less than the spacing of air 957. Thus, the plates have a conical shape in thickness that decreases from the one adjacent to the input end to the one adjacent to the output end. This change in plate geometry achieves many of the same benefits shown in all other modalities. In the twelfth modality 950, there is essentially the same heat transfer surface area, a progressive reduction in cross sectional area
    Petition 870170090013, of 11/22/2017, p. 33/53 / 28 internal from the inlet (top) to the outlet (bottom) and a 956 air gap progressively higher at the top compared to 957 at the bottom, which allows greater air flow, increases the internal fluid speed and increases the internal heat transfer coefficients as one travels from the top to the bottom. The decision of the geometries used and the progressive air gaps between top and bottom indirect plate heat exchanger sections is a balance between the amount of desired airflow improvement, difficulty in manufacturing degree and pressure drop on the side permissible internal plate.
    Petition 870170090013, of 11/22/2017, p. 34/53 / 6
    权利要求:
    Claims (20)
    [1]
    1. Indirect heat exchanger, characterized by the fact that it comprises:
    a plurality of coil circuits, an input head connected to an input end of each coil circuit and an output head connected to an output end of each coil circuit, each coil circuit comprising a circuit tube which extends in a series of exhaust lengths and return folds from the inlet end of each coil circuit to the outlet end of each coil circuit, each exhaust pipe length having a horizontal cross-sectional dimension that decreases and a vertical cross-sectional dimension that increases as the exhaust pipe length of the circuit extends from the proximity of the inlet end of each coil circuit to the proximity of the outlet end of each coil circuit.
    [2]
    2. Indirect heat exchanger according to claim 1, characterized in that each circuit tube has a cross sectional area that decreases from the input end of each coil circuit to the output end of each coil circuit .
    [3]
    Indirect heat exchanger according to claim 1, characterized in that a first ratio of the vertical cross-sectional dimension of each circuit pipe exhaust length to the horizontal cross-sectional dimension of each circuit pipe exhaust length exits close to the inlet end of each coil circuit, and a second ratio of the vertical cross-sectional dimension of each exhaust pipe length to the horizontal cross-sectional dimension of each length of
    Petition 870180027452, of April 5, 2018, p. 4/9
    2/6 circuit pipe exhaust exits close to the outlet end of each coil circuit, and the second ratio is greater than the first ratio.
    [4]
    4. Indirect heat exchanger according to claim 3, characterized by the fact that the first ratio is between 1.0 and 2.0, and the second ratio is greater than the first ratio, but less than 6.0 .
    [5]
    5. Indirect heat exchanger according to claim 1, characterized in that each circuit tube comprises galvanized steel, stainless steel, aluminum or copper.
    [6]
    6. Indirect heat exchanger according to claim 1, characterized in that each length of the exhaust pipe of the circuit has a horizontal cross-sectional dimension that decreases progressively and a vertical cross-sectional dimension that increases progressively as each circuit pipe becomes extends from the proximity of the input end of each coil circuit to the proximity of the output end of each coil circuit.
    [7]
    7. Indirect heat exchanger according to claim 1, characterized in that: each circuit tube comprises a series of exhaust lengths and return bends from the inlet end of each coil circuit to the outlet end each coil circuit; and, each individual circuit pipe exhaust length is of a uniform horizontal cross-sectional dimension and a uniform vertical cross-sectional dimension between return folds, and in which the horizontal cross-sectional dimension of exhaust pipe-circuit lengths decreases closer to outlet end of each circuit tube and the vertical cross-sectional dimension of each circuit tube exhaust lengths increases closer to the outlet end of each coil circuit.
    [8]
    8. Indirect heat exchanger according to claim 1,
    Petition 870180027452, of April 5, 2018, p. 5/9 characterized by the fact that each return bend of the circuit tube is circular in cross section.
    [9]
    9. Indirect heat exchanger according to claim 1, characterized by the fact that each length of circuit pipe exhaust at the inlet end of each coil circuit as connected to the inlet head is circular in cross section.
    [10]
    10. Indirect heat exchanger, characterized by the fact that it comprises:
    a plurality of coil circuits, an input head connected to an input end of each coil circuit and an output head connected to an output end of each coil circuit, each coil circuit comprises a circuit tube which extends in a series of exhaust lengths and return folds from the inlet end of each coil circuit to the outlet end of each coil circuit, each exhaust pipe length of circuit having a horizontal cross sectional dimension pre- selected for its total length, with the horizontal cross-sectional dimension of total circuit pipe exhaust lengths decreasing as the circuit pipes extend from the proximity of the input end of each coil circuit to near the output end of each coil circuit.
    [11]
    11. Indirect heat exchanger according to claim 10, characterized in that each length of the exhaust pipe has a cross sectional area that decreases from the inlet end of each coil circuit to the outlet end of each coil circuit.
    Petition 870180027452, of April 5, 2018, p. 6/9
    [12]
    Indirect heat exchanger according to claim 10, characterized in that a first ratio of the vertical cross-sectional dimension of each exhaust pipe length to the horizontal cross-sectional dimension of each exhaust pipe length it exits close to the inlet end of each coil circuit, and a second ratio of the vertical cross sectional dimension of each circuit pipe exhaust length to the horizontal cross sectional dimension of each circuit pipe exhaust length exits near the pipe end. output of each coil circuit, and where the second reason is greater than the first reason.
    [13]
    13. Indirect heat exchanger according to claim 12, characterized by the fact that the first ratio is between 1.0 and 2.0, and the second ratio is greater than the first ratio, but less than 6.0 .
    [14]
    14. Indirect heat exchanger according to claim 10, characterized in that each circuit tube comprises galvanized steel, stainless steel, aluminum or copper.
    [15]
    15. Indirect heat exchanger according to claim 10, characterized in that each circuit pipe exhaust length has a horizontal cross-sectional dimension that decreases progressively and a vertical cross-sectional dimension that increases progressively according to the exhaust length of circuit tube extends from near the input end of each coil circuit to near the output end of each coil circuit.
    [16]
    16. Indirect heat exchanger according to claim 10, characterized in that: each circuit tube comprises a series of exhaust lengths and return bends from the inlet end of each coil circuit to the end of
    Petition 870180027452, of April 5, 2018, p. 7/9 output of each coil circuit; and, each individual circuit pipe exhaust length is of a uniform horizontal cross-sectional dimension and a uniform vertical cross-sectional dimension between return folds, and in which the horizontal cross-sectional dimension of each exhaust length decreases closer to the end of outlet of each circuit tube and the vertical cross-sectional dimension of each exhaust length increases closer to the outlet end of each coil circuit.
    [17]
    17. Indirect heat exchanger according to claim 10, characterized in that each circuit tube comprises a series of exhaust lengths and return bends from the inlet end of each coil circuit to the outlet end of each coil circuit, and each return bend of the circuit tube is circular in cross section.
    [18]
    18. Indirect heat exchanger, characterized by the fact that it comprises:
    a plurality of coil circuits, an input head connected to an input end of each coil circuit and an output head connected to an output end of each coil circuit, each coil circuit comprises a circuit tube which extends in a series of exhaust lengths and return bends from the inlet end of each coil circuit to the outlet end of each coil circuit, each length of exhaust pipe circuit having a horizontal cross section at the end of inlet of each coil circuit and a vertical cross section at the inlet end of each coil circuit, each length of exhaust pipe circuit having
    Petition 870180027452, of April 5, 2018, p. 8/9 a horizontal cross-sectional dimension that decreases and a vertical cross-sectional dimension that increases as the exhaust pipe length of the circuit extends from the next to the input end of each coil circuit to the next to the output end of each coil circuit.
    [19]
    19. Indirect heat exchanger according to claim 18, characterized in that each circuit tube has a cross sectional area that decreases from the input end of each coil circuit to the output end of each coil circuit .
    [20]
    20. Indirect heat exchanger according to claim 18, characterized in that a first ratio of the vertical cross-sectional dimension of each circuit pipe exhaust length to the horizontal cross-sectional dimension of each circuit pipe exhaust length exits close to the inlet end of each coil circuit, and a second ratio of the vertical cross sectional dimension of each circuit pipe exhaust length to the horizontal cross sectional dimension of each circuit pipe exhaust length exits near the pipe end. output of each coil circuit, and where the second reason is greater than the first reason.
    Petition 870180027452, of April 5, 2018, p. 9/9
    1/11
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    法律状态:
    2018-05-29| B03A| Publication of a patent application or of a certificate of addition of invention [chapter 3.1 patent gazette]|
    2021-08-10| B06W| Patent application suspended after preliminary examination (for patents with searches from other patent authorities) [chapter 6.23 patent gazette]|
    优先权:
    申请号 | 申请日 | 专利标题
    US15/291,773|2016-10-12|
    US15/291,773|US10655918B2|2016-10-12|2016-10-12|Indirect heat exchanger having circuit tubes with varying dimensions|
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