Sealing system and method of cooling a fluid in a sealing assembly

Abstract

A sealing system and a method of cooling a fluid in a sealing assembly are provided. The sealing system includes: a fluid cooler including a tapered coil including a duct defining vertically stacked and spaced apart loop portions of reduced diameter and fins protruding from an outer surface of the duct; and a sealing assembly connected to the fluid cooler, a fluid cooler configured to receive a fluid from a portion of the seal assembly to transfer thermal energy between the fluid within the conical disk and another fluid proximate to the conical disk and the fins located outside the conical disk and also configured to cause the another fluid to laterally flow from the interior of the conical shape of the conical disk by natural convection and a fluid cooler that moves through the space between the rings of the conical coil to the exterior of the conical shape rather than flowing from the top surface of the lower ring to the bottom surface of the upper ring, the fluid cooler including a closed loop system that separates the fluid within the conical coil from another fluid to be cooled by the fluid within the conical coil.

Description

[0001] This application is a divisional application of the invention patent application filed on April 12, 2019, with application number 2019800254808 and entitled "Fluid cooler, heat exchanger, sealing assembly and system and related methods including fluid cooler or heat exchanger".

[0002] Priority requirements This application claims the benefit of the filing date of U.S. Provisional Patent Application No. 62 / 657,343, filed April 13, 2018, entitled “Fluid coolers, heat exchangers, sealing assemblies, and systems and related methods including fluid coolers or heat exchangers,” the disclosure of which is incorporated herein by reference in its entirety. Technical Field

[0003] Embodiments of this disclosure generally relate to fluid coolers and / or heat exchangers, and related systems and methods. Specifically, some embodiments of this disclosure relate to air-cooled fluid coolers and heat exchangers, as well as systems and related methods for sealing assemblies. Background Technology

[0004] Fluid heat exchangers or coolers operate on the general principle of keeping two fluids separate by connecting them using a heat-conducting material, such as a metal. Depending on the application, the fluids can be in liquid or gaseous form. Heat is transferred from the high-temperature fluid to the low-temperature fluid through the heat-conducting material, thereby cooling the high-temperature fluid and heating the low-temperature fluid.

[0005] An example of a heat exchanger is shown in U.S. Patent 6,076,597, which describes a liquid-liquid heat exchanger in which a tube formed as a coil is immersed in a cooling fluid, through which a working fluid flows. The tube is formed of a thermally conductive material and configured to transfer heat from the working fluid to the cooling fluid. Another example of a heat exchanger is shown in U.S. Patent 3,802,499, which describes a pipe formed as a helical coil within a housing. The pipe has external fins extending perpendicular to its axis. The cooling fluid flows around the pipe in a direction parallel to the fins. The fins provide additional surface area of ​​the thermally conductive material to provide additional heat transfer between the two fluids.

[0006] Heat exchangers can be used to remove heat from many processes. Some processes that utilize heat exchangers include air conditioning systems, industrial processes, internal combustion engines, industrial pumps, and refrigeration systems. Generally, these systems use a cooling fluid to transfer heat generated by the process to the heat exchanger. The heat exchanger then transfers the heat from the cooling fluid to a second fluid. In many cases, the second fluid is ambient air. In some processes, where flow is induced by adding heat to the second fluid, the second fluid can be allowed to move passively across the heat exchanger by naturally generated wind or natural convection. In other processes, the second fluid can be mechanically propelled across the heat exchanger using, for example, a fan or pump. Summary of the Invention

[0007] In some embodiments, the fluid heat exchanger may include a tube and a plurality of fins. The plurality of fins may be attached to the outer surface of the tube. The tube may be formed as a generally conical disc.

[0008] In some embodiments, the fluid heat exchanger may include a coiled tube extending around the longitudinal axis of the heat exchanger, the coiled tube having at least a portion that is laterally offset relative to another portion of the coiled tube in a direction transverse to the longitudinal axis.

[0009] In some embodiments, the sealing system (e.g., a pump or mechanical seal) may include an air-cooled fluid cooler and a sealing assembly. The air-cooled fluid cooler may include a conical disc and multiple fins. The conical disc may be formed from at least one conduit. The at least one conduit may define multiple stacked ring-shaped portions with decreasing diameters. The at least one conduit may also include multiple fins projecting from the outer surface of the conduit. The sealing assembly may be connected to the air-cooled fluid cooler.

[0010] In some embodiments, the fluid cooling system may include a single tube, a vent, a drain, and at least two mounting flanges. The single tube may define a ring with a decreasing diameter. The ring may define a vertically oriented tapered helix. The vent may extend from the uppermost portion of the tube, while the drain may extend from the lowermost portion of the tube. The vent may include a vent valve and a vent pipe. The drain may include a drain valve and a drain pipe. The at least two mounting flanges may include a first mounting flange and a second mounting flange. The first mounting flange may connect between the top ring of the tapered helix and a frame. The second mounting flange may connect between the bottom ring of the tapered helix and the frame.

[0011] Some embodiments may include a fluid heat exchanger comprising a tube defining a generally conical disc. The tube extends about a longitudinal axis of the heat exchanger and has at least one arcuate portion that is laterally offset relative to another arcuate portion of the tube in a direction transverse to the longitudinal axis. The exchanger also includes a plurality of fins and at least one fitting attached to the outer surface of the tube, the fins being positioned on the tube to allow fluid to flow in and out of the tube, thereby transferring heat between the fluid inside the tube and another fluid located on the outside of the tube near the tube and the fins.

[0012] Some embodiments may include a sealing system comprising a fluid cooler including a conical disc with at least one conduit defining a tapered, stacked ring portion of decreasing diameter and fins projecting from the outer surface of the at least one conduit. In some embodiments, the fluid cooler may include the heat exchanger discussed above. The sealing system also includes a sealing assembly connected to the fluid cooler. The fluid cooler is configured to receive fluid from a portion of the sealing assembly to transfer heat between fluid within the conical disc and another fluid located on the outside of the conical disc, adjacent to the conical disc and fins.

[0013] Some implementations may include a method for cooling a fluid, the method comprising: transferring fluid from a fluid assembly including one or more fluid seals to a heat exchanger; passing the fluid through at least one finned tube defining a conical helical structure of the heat exchanger, the conical helical structure being located between a first end and a second end of the conical helical structure, the diameter of the first portion of the conical helical structure being larger than the diameter of an adjacent second portion of the conical helical structure; and cooling the fluid while passing the fluid through the conical helical structure to transfer thermal energy from the fluid within the at least one finned tube to another fluid located on the outside of the at least one finned tube. Attached Figure Description

[0014] Although the specification concludes with claims that specifically point out and expressly claim protection for embodiments considered to be of this disclosure, the various features and advantages of embodiments of this disclosure can be more readily identified from the following description of exemplary embodiments of this disclosure, when read in conjunction with the accompanying drawings: Figure 1 This is a side view of a pipe according to an embodiment of the present disclosure; Figure 2 This is a perspective view of a fluid cooler according to an embodiment of the present disclosure; Figure 3 This is a view of the temperature profile for a fluid cooler according to an embodiment of the present disclosure; Figure 4 This is a perspective view of a fluid cooler according to an embodiment of the present disclosure; Figure 5 This is a perspective view of a fluid cooler system according to an embodiment of the present disclosure; Figure 6 This is a schematic diagram of a fluid cooler system according to an embodiment of the present disclosure; Figure 7a This is an enlarged view of a pipe fin configuration according to an embodiment of the present disclosure; Figure 7b This is an enlarged view of a pipe fin configuration according to an embodiment of the present disclosure; Figure 7c This is an enlarged view of a pipe fin configuration according to an embodiment of the present disclosure; Figure 7d This is an enlarged view of a pipe fin configuration according to an embodiment of the present disclosure; Figure 7e This is an enlarged view of a pipe fin configuration according to an embodiment of the present disclosure. Detailed Implementation

[0015] The illustrations presented herein are not intended to be actual views of any particular fluid cooler, heat exchanger, or component of a heat exchanger, but are merely idealized representations used to describe exemplary embodiments. The figures are not necessarily to scale. Identical elements throughout the figures may retain the same numerical designations.

[0016] As used herein, related terms such as “first,” “second,” “top,” and “bottom” are generally used for clarity and convenience of understanding this disclosure and the accompanying drawings, and do not imply or depend on any particular preference, orientation, or order unless the context clearly indicates otherwise.

[0017] As used herein, the term “and / or” means and includes any and all combinations of one or more of the associated listed items.

[0018] As used herein, the terms “vertical,” “horizontal,” “top,” “bottom,” “upper,” and “lower” may refer to the orientation depicted in the accompanying figures.

[0019] As used herein, the terms “approximately” or “about” with respect to a given parameter mean and include, as would be understood by those skilled in the art, the degree to which a given parameter, characteristic, or condition is satisfied with a small degree of variation, such as within acceptable manufacturing tolerances. For example, a parameter that is approximately satisfied may be satisfied with at least about 90%, at least about 95%, at least about 99%, or even 100%.

[0020] As used herein, the term "fluid" can refer to and include fluids of any type and composition. Fluids can take the form of a liquid, a gas, or a combination of both, and in some cases, fluids may include solid materials. In some embodiments, the fluid can transition between liquid and gaseous forms during cooling or heating processes as described herein.

[0021] Embodiments of this disclosure may relate to heat exchangers for cooling or heating one fluid with another fluid without mixing the two fluids. In some embodiments, such heat exchangers or fluid coolers may be implemented in conjunction with fluid management components and systems—such as sealing components, valve components, pumps, etc.—to aid in dissipating heat energy from such components and systems.

[0022] Embodiments of this disclosure may include fluid-to-fluid heat exchangers (e.g., fluid coolers, waste heat recovery units, radiators, evaporators, etc.) that operate by transferring heat from one fluid to another through a heat-conducting material. Heat transfer in such exchangers can be enhanced by increasing the surface area of ​​the heat-conducting material in contact with each fluid. This increase in surface area can be achieved in several different ways. Such heat exchangers can increase the surface area by increasing the length or number of tubes (e.g., pipes, passages, channels, etc.) through which the fluids pass. For example, in a shell-and-tube heat exchanger, multiple tubes can be used within a shell, thereby providing a substantially larger surface area in contact with each fluid. Such heat exchangers also achieve an increased surface area by using fins attached to the tubes or passages through which one of the fluids passes. The fins transfer heat to or from the tubes, which in turn transfer heat to or from the fluid within the tubes. The fins increase the surface area in contact with the fluid remaining on the outside of the tubes.

[0023] Figure 1An embodiment of a heat exchanger tube 102 (e.g., pipe, hose, conduit, channel, etc.) is shown. In some embodiments, the tube 102 may have fins 104 (e.g., plates) projecting from the tube 102. The fins 104 may be spaced approximately uniformly along the length of the tube 102 (e.g., spaced at approximately the same interval). In some embodiments, the fins 104 may be spaced at intervals between about 1 mm and about 8 mm, wherein the interval is measured from the center of each fin 104. For example, the fins 104 may be spaced between about 3 mm and about 6 mm, or between about 4 mm and about 5 mm. In some embodiments, the fins 104 may be spaced at smaller intervals to create a larger surface area. In other embodiments, the fins 104 may be spaced at larger intervals to allow fluids with higher viscosity to travel between the fins 104. In some embodiments, the presence of natural airflow (e.g., wind, chimney effect, etc.) may allow for even smaller intervals between the fins.

[0024] In some embodiments, fins 104 may have a spiral configuration extending around tube 102, wherein the intermediate portion between two adjacent fins 104 may directly contact the outer surface of tube 102 (e.g., to aid heat transfer). As shown, fins 104 may have a generally annular (e.g., circular) shape. In some embodiments, fins 104 may be formed from an elongated strip of material wound around tube 102 to form a generally annular shape with a spiral configuration. In other embodiments, fins 104 may have other shapes and configurations (e.g., quadrilateral shapes, polygonal shapes, non-wound shapes, shapes and configurations discussed below, and combinations thereof).

[0025] A first fluid 106 (e.g., working fluid, treated fluid, closed-loop fluid, cooling fluid, etc.) may flow inside the pipe, while a second fluid 108 (e.g., auxiliary cooling fluid, ambient fluid, regenerable fluid, air, open-loop fluid, etc.) may flow or reside along the exterior of the pipe 102 and / or the fins 104. The second fluid 108 may be provided in a passive and / or active manner.

[0026] In some embodiments, the first fluid 106 flowing in the pipe 102 can carry residual heat from processes such as refrigeration, combustion, sealing and lubrication systems, and industrial processes. The first fluid 106 can transfer heat (e.g., thermal energy) to the pipe 102 as it travels through it. The pipe 102 can then transfer heat from the first fluid 106 to the second fluid 108 through its outer surface and fins 104. As the length of the pipe 102 increases, the amount of heat energy that can be transferred from the first fluid 106 to the second fluid 108 also increases depending on the processing conditions.

[0027] In some implementations, the required length for dissipating the heat may become excessive. Some systems require lengths between 1 meter and 10 meters. In many applications, these lengths of straight piping may be too long, considering space and maintenance requirements. For example, in industrial applications, space for equipment is often limited due to the sheer volume of equipment and the limited space in the area where it is located. In some examples, piping may be positioned vertically to reduce its footprint; however, this can result in instruments and controls being inaccessible without the aid of ladders, scaffolding, or other access tools.

[0028] The tube 102 can be formed in a non-linear shape to reduce the amount of space consumed by the heat exchanger while maintaining additional length. For example, the tube 102 can travel back and forth, such as in a finned plate heat exchanger (e.g., an automotive radiator, a hot water heating plate, a cold water cooling plate, etc.). When the tube 102 travels back and forth, additional factors begin to affect the efficiency of the heat exchanger. For example, when the tube 102 travels back and forth, the sharp bends generate additional back pressure in the system. In some applications, the additional back pressure may be desirable for reducing flow and increasing the amount of time the fluid spends within the heat exchanger. In other applications, such as in low-pressure systems, the additional back pressure may cause other problems. Additionally, the fins 104 are typically in direct contact with each other, or the fins 104 may be a single fin 104 contacting the tube 102 at multiple locations, thus transferring heat between different sections of the tube 102. In view of the above, finned plate heat exchangers typically require the second fluid 108 to be forced to flow through the finned plate heat exchanger in order to effectively transfer heat from the first fluid 106 to the second fluid 108.

[0029] In some embodiments, tube 102 can be formed as a stacked ring, such as a curved, spiral, coiled, coaxial, or helical coil. Helical coils eliminate the sharp bends present in finned plates. However, additional factors can still affect the efficiency of both finned plate heat exchangers and helical coil heat exchangers. For example, when heat dissipates from a portion of tube 102 into the second fluid 108, this heat can affect heat transfer from adjacent portions of tube 102. For example, in a helical coil, rings can be stacked one on top of the next. In some embodiments, when heat dissipates from the lower ring of tube 102 into the second fluid 108, this heat can dissipate upwards through the second fluid 108 towards the next or adjacent ring in the stack, thereby heating the adjacent ring and reducing the amount of heat that can dissipate from the portion of tube 102 defining that ring. As heat is transferred upwards through the second fluid, a point eventually reaches where the temperature difference between the second and first fluids is insufficient to maintain effective heat transfer between the two fluids.

[0030] Figure 2 An embodiment of a fluid heat exchanger 200 is illustrated. In some embodiments, the fluid heat exchanger may include a conduit 202 having fins 204 extending radially outward from the surface of the conduit 202. The conduit may include similar features to one or more of the conduits or pipes discussed herein, such as including a finned configuration. In some embodiments, the conduit 202 may include a feature located at the end of the conduit for connecting the conduit to a fluid cooling system (see [link to documentation]). Figure 5 and Figure 6 The pipe connection 216 (e.g., coupling, joint, dielectric joint, nipple, bushing, double-threaded bushing, flange connection, compression fitting, etc.) can be positioned at opposite ends of the fluid heat exchanger 200, as shown. In other embodiments, the pipe connection 216 can be positioned at one end, one side, or even the middle portion of the fluid heat exchanger 200, wherein at least a portion of the pipe 202 can extend from the first pipe connection 216 and return along the same route (e.g., by returning through substantially the same route, for example, in a substantially parallel manner) to a second pipe connection 216 positioned near the first pipe connection 216 (e.g., adjacent to the first pipe connection 216).

[0031] In some embodiments, conduit 202 may define a plurality of stacked rings 210 (e.g., loops, hoops, etc.). The plurality of stacked rings 210 may include one or more rings exhibiting a different size from adjacent stacked rings 210 (e.g., at least some of the stacked rings 210 are offset from adjacent stacked rings 210). For example, at least some of the stacked rings 210 may be offset from adjacent stacked rings 210 (e.g., in a transverse direction transverse to the longitudinal axis or centerline of the fluid heat exchanger 200, wherein the stacked rings 210 extend about the longitudinal axis). As shown, the plurality of stacked rings 210 may be formed as curved or annular (e.g., circular) shapes with gradually increasing or decreasing diameters, such that the plurality of stacked rings 210 are defined as conical (e.g., conical discs, conical spirals, conical coils, etc.). Reducing the diameter of multiple stacked rings 210 can increase the efficiency of the heat exchanger by reducing the likelihood that heat energy is transferred between adjacent stacked rings 210 in an undesirable or unwanted manner rather than to the surrounding environment.

[0032] In some embodiments, the stacked ring 210 may have different shapes (e.g., ring, ellipse, rectangle, polygon, quadrilateral, square, triangle, hexagon, etc.). In some embodiments, different dimensions may be, for example, the length of the side, height, diagonal, center distance, radius, etc.

[0033] In some implementations, the stacked rings 210 may take on other shapes while the adjacent rings are still at least partially offset from each other. For example, the diameter of the rings (e.g., rings 212, 213, 214) may be increased and decreased between each adjacent stacked ring 210 to define an undulating shape, rather than a normal conical shape.

[0034] In some implementations, the stacked ring 210 can allow for the use of significantly longer pipes within a limited space. For example, the length of the pipe 202 can be between approximately 4 meters and 15 meters, such as between approximately 6 meters and 12 meters. When the pipe 202 is formed as a stacked ring 210, the dimensions of the fluid heat exchanger 200 can be, for example, less than 1 meter in height and less than 0.5 meters in diameter.

[0035] In some embodiments, the stacking ring 210 may be formed in a conical shape, wherein the apex angle (e.g., the angle between two lines converging on the central axis of the conical stack and tangent to the stacking ring 210) is between about 10º and about 90º, such as between about 15º and about 50º, or between about 20º and about 30º. For example, in some embodiments, the ratio of the spacing between the individual rings within the stacking ring 210 to the variation in the diameter of the ring 210 may be between about 1:1 and about 12:1, such as between about 5:1 and about 10:1 or about 7:1, where the first number is the spacing and the second number is the variation in diameter.

[0036] In some embodiments, the diameter of the conduit 202 may be between about 8 mm and about 84 mm, for example, between about 15 mm and about 25 mm or about 19 mm. In some embodiments, the thickness of the conduit 202 may be between about 1 mm and about 5 mm, for example, between about 2.5 mm and about 4 mm. In some embodiments, the fins 204 may extend from the conduit 202 to a height that may be smaller than the diameter of the conduit 202. For example, the fins may extend to a height between about 2 mm and about 20 mm, for example, between about 7 mm and about 12 mm or about 10 mm.

[0037] In some embodiments, the conduit 202 may be formed of a heat-conducting material. For example, the conduit 202 may be formed of copper, aluminum, stainless steel, carbon steel, bronze, brass, titanium, or other metal alloys. In some embodiments, the conduit 202 may be formed of a corrosion-resistant material that is also heat-conducting, such as stainless steel, chromium, nickel, iron, copper, tungsten, and titanium.

[0038] In some embodiments, fins 204 may be formed of a heat-conducting material. For example, fins 204 may be formed of copper, aluminum, stainless steel, carbon steel, bronze, brass, titanium, or other metal alloys. In some embodiments, fins 204 may be formed of the same material as pipe 202. In other embodiments, fins 204 may be formed of a different material than pipe 202. In some embodiments, fins 204 may be formed as part of pipe 202, for example, by extrusion, molding, rolling, etc. In some embodiments, fins 204 may be formed separately from pipe 202 and attached to it. Fins 204 may be attached by processes such as brazing, welding (e.g., arc welding, laser welding, resistance welding, oxy-fuel welding, etc.), copper welding, adhesives, etc.

[0039] Figures 7a to 7e The diagram illustrates the configuration of the pipe and fins according to some embodiments of the present disclosure. For example, as... Figure 7a As shown, fins 204 may include mating surfaces 704 (e.g., flanges) that define the spacing between fins 204. The mating surfaces 704 may extend generally perpendicularly from the fins 204 to form generally flat surfaces for mating with the surfaces of the conduit 202.

[0040] In some implementations, such as Figure 7b As shown, the mating surface 704 may include an interlocking bracket 706. The interlocking bracket 706 can secure the fin 204 to an adjacent fin 204. As shown, the interlocking bracket 706 can allow the fin 204 to support and / or secure other adjacent fins 204.

[0041] In some implementations, such as Figure 7c As shown, the conduit may include discontinuous features (e.g., a raised surface 708). The raised surface 708 may engage with the mating surface 704 of the fin 204. In some embodiments, the raised surface 708 may fix the mating surface 704, thereby substantially limiting or preventing lateral movement along the surface of the conduit.

[0042] In some implementations, such as Figure 7dAs shown, the connection between fin 204 and pipe 202 can be a tongue-and-groove joint (e.g., a semi-lap joint, a wedge tenon joint). As shown, pipe 202 may include a groove 710. Fin 204 may include a complementary base 712 (e.g., a tongue, a tenon) that can be fitted within the groove 710. In some embodiments, the complementary base 712 may be secured within the groove 710 by an interference fit (e.g., a compression fit, a press fit, a friction fit). In some embodiments, the complementary base 712 and groove 710 may be a loose fit, wherein the groove 710 can substantially prevent lateral movement along the surface of pipe 202 while allowing movement within the groove 710 (e.g., along the groove 710) to facilitate thermal expansion and accommodate different expansion rates, etc.

[0043] In some embodiments, the fins 204 can be extruded or rolled from the pipe 202.

[0044] In some implementations, such as Figure 7e As shown, fins 204 can be extruded or rolled from a separate sleeve material 714 (e.g., a continuous material) into which a conduit can be inserted. The joint between the conduit 202 and the sleeve material 714 can be an interference fit. In some embodiments, the joint between the conduit 202 and the sleeve material 714 may include a raised surface on at least one of the surfaces of the conduit 202 or the sleeve material 714.

[0045] Figure 3 The temperature distribution of the fluid heat exchanger 200 is shown. As shown, a first fluid 206 can flow within a conduit 202. A second fluid 208 can be provided outside the conduit 202. In some embodiments, the second fluid 208 can be ambient air. In other embodiments, the second fluid 208 can be another fluid, such as water, oil, or other coolant. In some embodiments, a plurality of stacked rings 210 can be arranged such that the conical shape is generally vertical. In some embodiments, the largest ring 212 can be located at the bottom of the conical shape, while the smallest ring 214 can be located at the top of the conical shape (e.g., along the conical shape). Figure 3 (The vertical orientation shown). In another embodiment, the cone shape can be inverted such that the largest ring 212 is located on top of the cone shape and the smallest ring 214 is located on the bottom of the cone shape. In other embodiments, the cone shape may include the above configuration repeated in a stacked manner.

[0046] In some embodiments, the first fluid 206 may carry thermal energy from another process. The thermal energy of the first fluid 206 may cause the flow of the second fluid 208 through natural or passive convection. The second fluid 208 may enter at the bottom of the conical shape as a cooling fluid 208a. As heat is transferred to the cooling fluid 208a, the cooling fluid 208a may transform into a warmer fluid 208b (e.g., a warmer fluid 208b having a higher temperature than the cooling fluid 208a), which has a lower density than the cooling fluid 208a, and will move generally upward relative to the cooling fluid 208a. The upward movement of the warmer fluid 208b can generate a natural flow through the conical shape. The warmer fluid 208b will naturally move from the inside of the conical shape to the outside of the conical shape and continue to move upward. This movement can create a low-pressure volume inside the conical shape, which in turn draws cooling fluid 208a through the bottom of the conical shape to replace the fluid that has been transformed into warmer fluid 208b.

[0047] In some embodiments, a conical or other offset shape can reduce the influence of the lower rings of the plurality of stacked rings 210 on the upper rings of the plurality of stacked rings 210 (e.g., to reduce the heating effect of the lower rings on the upper rings adjacent to one or more of the lower rings). For example, natural convection can cause the second fluid 208 to flow from the interior of the conical shape through the space between the plurality of rings 210 to the exterior of the conical shape, rather than from the top surface of the lower ring to the bottom surface of the upper ring (e.g., at least partially laterally). Since the cooling fluid 208a can have a substantially uniform temperature throughout the interior portion of the conical shape, and the cooling fluid 208a can be drawn through the space between the plurality of rings 210 at a substantially uniform rate, the resulting flow can remove heat from both the upper and lower rings at substantially similar rates.

[0048] Figure 4 An embodiment of heat exchanger 300 is illustrated. As shown, heat exchanger 300 may include a plurality of tubes 302 (e.g., two, three, four, five or more tubes 302, which may include pipes or similar features of one or more of the tubes discussed herein, such as including a finned configuration). For example, heat exchanger 300 may include a first tube 302a and a second tube 302b. Tubes 302 may include fins 304 along the length of each tube 302. Tubes 302 may define a plurality of rings 310. In some embodiments, rings 310 may alternate with one ring defined by the first tube 302a and a next ring defined by the second tube 302b. The first tube 302a and the second tube 302b may define a tapered structure by extending side by side along a coiling path in a generally parallel manner.

[0049] In some embodiments, the first ring 312 defined by the first tube 302a may have the largest diameter among the plurality of rings 310. In some embodiments, the second ring 313 defined by the second tube 302b may have the same diameter as the first ring 312. In other embodiments, the diameter of the second ring 313 may be smaller than the diameter of the first ring 312. In some embodiments, the third ring 314 defined by the first tube 302a may have a diameter smaller than both the diameters of the first ring 312 and the second ring 313. This configuration of the bias rings 310 may extend along the length or longitudinal axis of the heat exchanger 300.

[0050] As shown, multiple pipes 302 can be connected to a first manifold 320 and a second manifold 322. The first manifold 320 and the second manifold 322 can create a common passage between the pipes 302, allowing the multiple pipes 302 to operate in parallel. In some embodiments, parallel operation can reduce the back pressure caused by the heat exchanger 300 by reducing the actual length of the bent pipes 302. The reduction in back pressure allows for the use of pipes 302 with smaller diameters to increase heat transfer. In some embodiments, parallel operation can result in a long effective length of the multiple pipes 302 when the actual lengths of pipes 302a and 302b are short. For example, if the length of each pipe 302a and 302b is 6 meters, the effective length of the heat exchanger can be approximately 12 meters.

[0051] Although pipes 302a and 302b are generally parallel to the common pipe fitting 316, in other embodiments, pipes 302a and 302b may be wound together in other ways (e.g., by separate pipe fittings, by twisting in an overlapping configuration, by a mirror-coiled configuration, etc.).

[0052] In some embodiments, the individual pipes 302a and 302b may be separate from each other. For example, the first pipe 302a may be connected to a first fluid source, while the second pipe 302b may be connected to a second fluid source. In some embodiments, the first and second fluid sources may be connected to the same fluid reservoir or heat source. In another embodiment, the first and second fluid sources may be connected to separate fluid reservoirs or heat sources within the same system. In yet another embodiment, the first and second fluid sources may be connected to different systems that are located at the same position in the heat exchanger 300 for reasons such as environmental conditions or space considerations (e.g., when entering or leaving the heat exchanger 300).

[0053] Figure 5An embodiment of a heat exchanger 400 as part of a fluid cooling system 450 is shown. The tube 402 of the heat exchanger 400 includes fins 404 along its substantially entire length. The tube may include similar features to one or more of the pipes discussed herein, such as including a finned configuration. The tube 402 may define a series of concentric rings 410 with decreasing / increasing diameters. In some embodiments, the fluid cooling system 450 may include a frame 452. The fluid cooling system 450 may include a top connection point 454 (e.g., flange, bracket, support, etc.) that can be connected to the top concentric ring 414 of the heat exchanger 400. The fluid cooling system 450 may include a bottom connection point 456 that can be connected to the bottom concentric ring 412 of the heat exchanger. In some embodiments, the series of concentric rings 410 may be configured (e.g., mounted on the frame 452) to move and absorb some vibrations and shocks from equipment movement and operation. For example, additional connection points can be used to connect the frame to the heat exchanger at additional coil sections within a series of coil sections 410 to restrict the movement of the series of coil sections and prevent fatigue failure of the heat exchanger.

[0054] In some embodiments, the vent 458 may be located at a high point on the heat exchanger 400 (e.g., the highest point, the top, etc.). The vent 458 may include a vent valve 460 and a vent duct 462. The vent valve 460 may be opened to allow air to escape from the fluid cooling system 450 through the vent duct 462.

[0055] In some embodiments, the drain element 464 may be located at a low point on the heat exchanger 400 (e.g., lowest point, bottom, etc.). The drain element 464 may include a drain valve 466 and a drain line 468. The drain valve 466 may be opened to remove fluid from the fluid cooling system 450 for maintenance, repair, or removal.

[0056] As shown, the fluid cooling system 450 may include an expansion tank 406 (e.g., a bladder, membrane, etc.) to accommodate volume changes in the cooling fluid due to temperature variations.

[0057] Reference Figure 4 Some embodiments may include multiple pipes 302 and manifolds 320, 322 connecting the multiple pipes 302. A vent 360 may be included in the top manifold 322 and / or an exhaust 364 may be included in the bottom manifold 320. For example, the vent 360 may be a spring valve, a drain screw, a drain port, a plug, or a combination of exhaust pipe and valve. In some embodiments, the exhaust 364 may be included in the bottom manifold 320. The exhaust 364 may be a spring valve, a drain screw, a drain port, a plug, or a combination of exhaust pipe and valve.

[0058] Figure 6 A schematic diagram of a fluid cooling system 600 is shown. In some embodiments, the fluid cooling system may be connected to a mechanical seal or pump seal 602 (e.g., a shaft seal, a dual seal, a dual-boost seal, etc.). When the pump is running, the pump seal 602 generates a significant amount of heat. In some embodiments, the pump seal 602 may include a pump ring 604 (e.g., a radial flow pumping ring or an axial flow pumping ring) for moving cooling fluid through the pump seal 602 to fluid flush the pump seal 602. Fluid flushing of the pump seal 602 can remove heat from the pump seal 602 and can also lubricate the pump seal 602.

[0059] In some embodiments, the fluid cooling system 600 may be a closed-loop system. A closed-loop system may be needed, for example, when the cooling fluid is harmful or toxic, has high vapor pressure, contains special additives (e.g., ethylene glycol, antiscalants, etc.), and / or the pumped fluid is unfavorable for cooling and / or lubricating seals (e.g., dirty, rough, or polymeric fluid). The cooling fluid may be completely isolated from the pumped fluid. The closed-loop system may include an expansion tank 606 (e.g., a bladder, membrane, etc.) to accommodate volume changes in the cooling fluid due to temperature variations. The fluid cooling system 600 may include a conical disc 608 (e.g., similar to those discussed herein) for removing heat from the system (e.g., heat removal via the cooling fluid as it passes through the conical disc 608). The fluid cooling system 600 may also include a vent 610 and an outlet 612 for removing fluid from the system and adding fluid to the system for maintenance, repair, or replacement processes.

[0060] The embodiments of this disclosure, when implemented, can provide a more efficient passive heat exchanger system. The embodiments can induce natural convection flow in the auxiliary cooling medium to remove heat more effectively. Passive heat exchangers can provide additional cost savings due to the reduced number of required hardware components and moving parts requiring maintenance.

[0061] Some implementations can increase the effective length of a heat exchanger while maintaining easy access to any instruments and controls that may be present on the top and bottom of the heat exchanger. The increased effective length can improve the efficiency of the heat exchanger, while the compact design can offer space-saving benefits in industries where floor space is of paramount value.

[0062] While this disclosure has been described herein with respect to certain illustrated embodiments, it will be recognized and understood by those skilled in the art that this disclosure is not so limited. Rather, many additions, deletions, and modifications may be made to the illustrated embodiments without departing from the scope of this disclosure as claimed above—including its legal equivalents. Furthermore, features from one embodiment may be combined with features from another embodiment while still being included within the scope of this disclosure as contemplated by the inventors.

Claims

1. A sealing system, the sealing system comprising: A fluid cooler, the fluid cooler comprising: A conical disc, the conical disc comprising at least one conduit defining vertically stacked and spaced-apart ring portions of decreasing diameter, the ring portions being vertically positioned such that the largest, lowest ring portion is located at the bottom portion of the ring portion, and the smallest, uppermost ring portion is located at the upper portion of the ring portion; and Fins, the fins protruding from the outer surface of the at least one pipe; and A sealing assembly connected to the fluid cooler is configured to receive a portion of fluid from the sealing assembly to transfer heat between the fluid within the conical disc and another fluid located on the outside of the conical disc near the conical disc and the fins. The fluid cooler is also configured to allow the other fluid to flow laterally from the interior of the conical shape of the conical disc through the space between the vertically stacked and spaced ring portions of the conical disc to the exterior of the conical shape via natural convection, rather than flowing from the top surface of the lower ring to the bottom surface of the upper ring. The fluid cooler includes a closed-loop system in which the fluid within the conical disc is separated from the other fluid to be cooled by the fluid within the conical disc.

2. The sealing system according to claim 1, wherein, The sealing assembly includes a pump.

3. The sealing system according to claim 1, wherein, The at least one conduit includes at least two conduits defining the vertically stacked and spaced-apart ring portions.

4. The sealing system of claim 3, further comprising at least one manifold connected to at least one end of the at least two pipes.

5. The sealing system according to claim 1, wherein, The fluid cooler also includes: A venting element, located at the uppermost part of the conical disc, the venting element including a venting valve and a venting pipe; A discharge device, located at the lowest portion of the conical disc, comprising a discharge valve and a discharge pipe; and At least two mounting flanges, wherein a first mounting flange connects the top ring of the conical disc to the frame, and a second mounting flange connects the bottom ring of the conical disc to the frame.

6. The sealing system according to claim 5, wherein, The distance between the vent valve and the discharge valve is less than 1 meter.

7. The sealing system according to claim 6, wherein, The conical disc includes a single tube with a length between approximately 6 meters and approximately 15 meters.

8. The sealing system according to claim 1, wherein, The joint between the at least one pipe and the fin includes at least one of the following: a flange extending between adjacent fins; an interlocking joint between the fins; a joint with a protrusion between adjacent fins; a joint between a tongue and a groove; or a continuous joint between adjacent fins.

9. The sealing system according to claim 1, wherein, The fluid cooler includes a frame, and the at least one conduit includes at least two tubes connected to the first fitting and the second fitting and extending between the first fitting and the second fitting. The at least two tubes define a generally tapered disc. The at least two tubes extend about the longitudinal axis of the fluid cooler, and the centerline of the tapered disc defined by the at least two tubes coincides with the vertical axis, which extends perpendicular to the transverse surface of the frame.

10. The sealing system according to claim 9, wherein, The at least two tubes are connected to the first fitting at an upper position on the surface of the conical disc along the vertical axis and relatively away from the frame, and are connected to the second fitting at a lower position on the surface of the conical disc along the vertical axis and relatively close to the frame.

11. A sealing system, the sealing system comprising: A fluid cooler, the fluid cooler comprising: A tube defining a generally conical disc extending about the longitudinal axis of the fluid heat exchanger, the tube having at least one arcuate portion that is laterally offset relative to another arcuate portion of the tube in a direction transverse to the longitudinal axis; Fins, the fins being attached to the outer surface of the tube; Fittings, which are connected to the tube to allow fluid to flow into and out of the tube; and A frame, the tube being connected to a first and a second fitting in the fitting and extending between the first and second fittings, the tube defining a generally tapered disc extending about the longitudinal axis of the fluid cooler, the centerline of the tapered disc defined by the tube coinciding with a vertical axis extending perpendicular to the transverse surface of the frame; and A sealing assembly is connected to the fluid cooler, which is configured to receive a portion of the fluid from the sealing assembly to transfer heat between the fluid within the conical disc and another fluid located on the outside of the conical disc near the conical disc and the fins.

12. A method for cooling fluid in a sealing assembly, the method comprising: To transfer fluid from a fluid assembly including one or more fluid seals to a heat exchanger; The fluid is allowed to pass through at least one finned tube, which defines a vertically arranged conical spiral structure of the heat exchanger, the conical spiral structure being located between a first lower end and a second upper end of the conical spiral structure, the diameter of the first lower portion of the conical spiral structure being larger than the diameter of the adjacent second upper portion of the conical spiral structure; By laterally separating each ring of the conical spiral structure from its adjacent rings, the influence of the lower ring of the conical spiral structure on the upper ring is reduced. Natural convection causes the flow of the second fluid to flow at least partially laterally from the interior of the conical spiral structure through the space between the multiple rings of the conical spiral structure to the exterior of the conical spiral structure, rather than from the top surface of the lower ring to the bottom surface of the upper ring; The flow is guided by the shape of the conical spiral structure to remove heat from both the upper and lower rings as the second fluid is drawn through the space between the plurality of rings; By supplying a relatively warm fluid at the bottom portion of the heat exchanger to guide the relatively warm fluid to flow upward through the heat exchanger to the relatively cold fluid in the upper portion of the heat exchanger, the fluid is passively convected through the heat exchanger. as well as The fluid is cooled during the process of transferring the heat energy of the fluid from inside the at least one finned tube to another fluid located outside the at least one finned tube by passing the fluid through the conical spiral structure.

13. The method according to claim 12, further comprising: The conical spiral structure is defined by a second tube, and the at least one finned tube and the second tube extend along similar paths adjacent to each other; as well as The at least one finned tube and the second tube are connected to a first common fitting at the first longitudinal end of the tapered structure and to a second common fitting at the opposite second longitudinal end of the tapered structure.

14. A method for cooling fluid in a sealing assembly, the method comprising: To transfer fluid from a fluid assembly including one or more fluid seals to a heat exchanger; The fluid passes through two finned tubes that together define a conical helical structure of the heat exchanger. The conical helical structure is vertically oriented, and the fluid passes between a first end and a second end of the conical helical structure. The diameter of a first lower portion of the conical helical structure is larger than the diameter of an adjacent second upper portion of the conical helical structure. Each of the two finned tubes is axially and radially spaced from its adjacent counterpart. During the process of transferring the thermal energy of the fluid from inside the two finned tubes to another fluid located outside the two finned tubes by passing the fluid through the conical spiral structure, the fluid is cooled to provide cooled fluid. as well as The fluid cooler includes a closed-loop system in which the fluid within the conical spiral structure flows laterally through the space between the two finned tubes of the conical spiral structure to the outside of the conical spiral structure via natural convection, rather than flowing from the top surface of the two finned tubes to the adjacent bottom surface of the two finned tubes.

15. The method according to claim 14, further comprising: By supplying the other fluid, which is relatively warmer, at the bottom portion of the heat exchanger to guide the relatively warmer fluid to flow upward through the heat exchanger to the relatively cooler fluid in the upper portion of the heat exchanger, the other fluid is passively convected via the heat exchanger.

16. The method of claim 14, further comprising: The cooled fluid is returned to the fluid assembly comprising the one or more fluid seals.

17. The method of claim 14, further comprising: During operation of the fluid assembly, thermal energy is applied to the cooled fluid, thereby forming a heated fluid.

18. The method according to claim 14, wherein, The fluid assembly includes one or more pump seals, and the method further includes: moving the cooled fluid through the one or more pump seals to flush the one or more pump seals.

19. The method of claim 14, further comprising: Passive convection allows at least a portion of another fluid surrounding the tube to flow from the interior of the conical spiral structure through the space between the rings of the tube to the exterior of the conical spiral structure.

20. A method for cooling a fluid in a sealing assembly, the method comprising: A fluid cooler is connected to a sealing assembly. The fluid cooler includes a conical disc and fins. The conical disc includes at least one conduit defining vertically stacked and spaced annular portions of decreasing diameter. The vertically stacked and spaced annular portions are positioned in a vertical orientation, wherein the largest lowermost annular portion is located at the bottom portion of the annular portion, and the smallest uppermost annular portion is located at the upper portion of the annular portion. The fins protrude from the outer surface of the at least one conduit. Receiving fluid from a portion of the sealing assembly to transfer heat between the fluid within the conical disc and another fluid located on the outside of the conical disc, near the conical disc and the fins; and The fluid cooler includes a closed-loop system in which the fluid within the conical disc flows laterally through the space between the vertically stacked and spaced rings of the conical disc to the outside of the conical shape via natural convection, rather than flowing from the top surface of the lower ring to the bottom surface of the upper ring.

21. The method according to claim 20, further comprising: By supplying the other fluid, which is relatively warmer, at the bottom portion of the fluid cooler to guide the relatively warmer fluid to flow upward through the fluid cooler to the relatively cooler fluid in the upper portion of the fluid cooler, the other fluid is passively convected via the fluid cooler.

22. The method according to claim 20, further comprising: The cooled fluid is returned to the sealing assembly; as well as During operation of the sealing assembly, heat energy is applied to the cooled fluid, thereby forming a heated fluid.

23. The method of claim 20, wherein, The sealing assembly includes one or more pump seals, and the method further includes: moving the cooled fluid through the one or more pump seals to flush the one or more pump seals.

24. The method according to claim 20, further comprising: Passive convection causes at least a portion of the other fluid to flow around the conical disc from the interior to the exterior of the conical disc.

25. The method according to claim 20, further comprising: The fluid is allowed to pass through two finned tubes that together define the conical disc.

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