Patent Description:
Fluid heat exchangers or coolers operate on a general principal of maintaining two fluids separate from each other with a thermally conductive material, such as metal, connecting the two fluids. The fluids may be in a liquid or gaseous form, depending on the application. Heat is then transferred from the higher temperature fluid to the lower temperature fluid across the thermally conductive material, cooling the higher temperature fluid and warming the lower temperature fluid.

An example of a heat exchanger is demonstrated in, <CIT>, which describes a liquid to liquid heat exchanger wherein a tube formed in a coil, with a working fluid flowing through the tube, is immersed in a cooling fluid. The tube is formed from a thermally conductive material and provides for the transfer of heat from the working fluid to the cooling fluid. Another example of a heat exchanger is demonstrated in <CIT>, which describes a pipe formed in a helical coil within a casing. The pipe has external fins that extend perpendicular to the axis of the pipe. The cooling fluid is passed by 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.

Heat exchangers may be used for removing heat from numerous processes. Some processes that utilize heat exchangers are, for example, air conditioning systems, industrial processes, internal combustion engines, industrial pumps, refrigeration systems, etc. Generally these systems utilize 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 through the heat exchanger. In many instances the second fluid is ambient air. In some processes, the second fluid may be allowed to passively move across the heat exchanger through naturally occurring wind or natural convection where a flow is induced by adding heat to the secondary fluid. In other processes, the secondary fluid may be mechanically forced across the heat exchanger using, for example, a fan, or a pump. A heat exchanger according to the preamble of claim <NUM> is known from document <CIT>.

The invention is defined by a fluid heat exchanger according to claim <NUM> and a method of cooling a fluid according to claim <NUM>. Further embodiments are described by the dependent claims.

The illustrations presented herein are not meant to be actual views of any particular fluid cooler, heat exchanger, or component thereof, but are merely idealized representations employed to describe illustrative embodiments. Elements common between figures may retain the same numerical designation.

As used herein, relational terms, such as "first," "second," "top," "bottom," etc., are generally used for clarity and convenience in understanding the disclosure and accompanying drawings and do not connote or depend on any specific preference, orientation, or order, except where the context clearly indicates otherwise.

As used herein, the term "and/or" means and includes any and all combinations of one or more of the associated listed items.

As used herein, the terms "vertical," "lateral," "top," "bottom," "upper," and "lower" may refer to the orientations as depicted in the figures.

As used herein, the term "substantially" or "about" in reference to a given parameter means and includes to a degree that one skilled in the art would understand that the given parameter, property, or condition is met with a small degree of variance, such as within acceptable manufacturing tolerances. For example, a parameter that is substantially met may be at least about <NUM>% met, at least about <NUM>% met, at least about <NUM>% met, or even <NUM>% met.

As used herein, the term "fluid" may mean and include fluids of any type and composition. Fluids may take a liquid form, a gaseous form, or combinations thereof, and, in some instances, may include some solid material. In some embodiments, fluids may convert between a liquid form and a gaseous form during a cooling or heating process as described herein.

Embodiments of the present disclosure may relate to heat exchangers for use in cooling or heating one fluid with another fluid, for example, without mixing the two fluids. In some embodiments, such heat exchangers or fluid coolers may be implemented with fluid management assemblies and systems, such as, for example, sealing assemblies, valve assemblies, pumps, etc. to assist in dissipating heat energy from such assemblies and systems.

Embodiments of the present 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 fluid through a thermally conductive material. The transfer of heat in such exchangers may be enhanced by increasing the surface area of the thermally conductive material in contact with each fluid. The increase in surface area may be achieved in several different ways. Such heat exchangers may accomplish the increase in 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 tube heat exchanger multiple tubes may be used within one shell providing substantially more surface area in contact with each fluid. Such heat exchangers also accomplish the increased surface area through the use of fins attached to the tubes or passages through which one of the fluids passes. The fins transfer heat to or from the tube, which, in turn, transfers the heat to or from the fluid within the tube. The fins increase the surface area in contact with a fluid residing on the exterior of the tube.

<FIG> demonstrates an embodiment of a tube <NUM> (e.g., pipe, hose, conduit, passage, etc.) of a heat exchanger. In some embodiments, the tube <NUM> may have fins <NUM> (e.g., plates) protruding from the tube <NUM>. The fins <NUM> may be spaced substantially evenly (e.g., at substantially common intervals) along the length of the tube <NUM>. In some embodiments, the fins <NUM> may be spaced at intervals between about <NUM> and about <NUM>, where the interval is measured from the center of each fin <NUM>. For example, the fins <NUM> may be spaced between about <NUM> and about <NUM>, or between about <NUM> and about <NUM>. In some embodiments, the fins <NUM> may be spaced at small intervals to generate more surface area. In other embodiments, the fins <NUM> may be spaced at larger intervals to enable fluids with higher viscosities to travel between the fins <NUM>. In some embodiments, the presence of natural airflow (e.g., wind, stack effect, etc.) may allow for smaller intervals between the fins.

In some embodiments, the fins <NUM> may have a spiral configuration extending around the tube <NUM>, where a middle section between two adjacent fins <NUM> may directly contact an outer surface of the tube <NUM> (e.g., to assist with heat transfer). As depicted, the fins <NUM> may have a substantially annular (e.g., circular) shape. In some embodiments, the fins <NUM> may be formed from an elongate strip of material wound around the tube <NUM> to form the substantially annular shape in a spiral configuration. In other embodiments, the fins <NUM> may have other shapes and configurations (e.g., a quadrilateral shape, a polygonal shape, a non-winding shape, the shapes and configurations discussed below, combinations thereof, etc.).

A first fluid <NUM> (e.g., working fluid, treated fluid, closed loop fluid, cooling fluid, etc.) may flow within the tube and a second fluid <NUM> (e.g., secondary cooling fluid, ambient fluid, renewable fluid, air, open loop fluid, etc.) may flow or reside along the exterior of the tube <NUM> and/or the fins <NUM>. The second fluid <NUM> may be provided in a passive and/or active manner.

In some embodiments, the first fluid <NUM> flowing in the tube <NUM> may carry residual heat from a process, such as, for example, a refrigerant process, a combustion process, a seal lubrication system, industrial processes, etc. The first fluid <NUM> may transfer heat (e.g., heat energy) to the tube <NUM> as the first fluid <NUM> travels through the tube <NUM>. The tube <NUM> may, in turn, transfer the heat from the first fluid <NUM> to the second fluid <NUM> through an exterior surface of the tube <NUM> and the fins <NUM>. As the length of the tube <NUM> increases, the amount of heat energy capable of being transferred from the first fluid <NUM> to the second fluid <NUM> will also increase depending on process conditions.

In some embodiments, the length required to expel the required amount of heat can become prohibitive. Some systems require a length of between <NUM> meter and <NUM> meters. These lengths in a straight pipe can be prohibitive given space and maintenance requirements in many applications. For example, in industrial applications space for equipment is often limited because of the amount of equipment and the limited space in the area where the equipment is located. In some examples, the pipe may be positioned vertically to reduce the floor space; however, this may result in instrumentation and controls that cannot be reached without the aid of a ladder, scaffold, or other accessibility tool.

The tube <NUM> may be formed into a non-linear shape to reduce the amount of space consumed by the heat exchanger while maintaining the additional length. For example, the tube <NUM> may weave back and forth, such as the tubes in a fin plate heat exchanger (e.g., automotive radiator, hot water heating coil, cold water cooling coil, etc.). When the tube <NUM> weaves back and forth additional factors begin to affect the efficiency of the heat exchanger. For example, when the tube <NUM> weaves back and forth the sharp bends create additional back pressure in the system. In some applications, the additional back pressure may be desirable for reducing the flow and extending the amount of time the fluid spends within the heat exchanger. In other applications, such as low pressure systems, the additional back pressure may create additional problems. Additionally, the fins <NUM> are often in direct contact with each other or may be a single fin <NUM> contacting the tube <NUM> in multiple places and therefore transfer heat between different portions of the tube <NUM>. In view of the above, fin plate exchangers often require forced flow of the second fluid <NUM> through the fin plate exchanger to efficiently transfer heat from the first fluid <NUM> to the second fluid <NUM>.

In some embodiments, the tube <NUM> may be formed into stacked rings, such as, for example, a curve, spiral, looped, concentric, or helical coil. The helical coil eliminates the sharp bends present in the fin plate. However, additional factors may still affect the efficiency of the heat exchangers in both a fin plate heat exchanger and a helical coil. For example, as heat dissipates into the second fluid <NUM> from one portion of the tube <NUM>, it may affect the heat transfer from the adjacent portions of the tube <NUM>. For example, in the helical coil, the rings may be stacked one above the next. In some embodiments, as the heat dissipates into the second fluid <NUM> from the tube <NUM> in a lower ring it may dissipate upwards through the second fluid <NUM> toward the next or adjacent ring in the stack thereby heating the adjacent ring and reducing the amount of heat that can be dissipated from the portion of the tube <NUM> that defines that ring. As the heat transfers up through the second fluid, eventually a point is reached where the temperature difference between the second fluid and the first fluid is not sufficient to maintain efficient heat transfer between the two fluids.

<FIG> illustrates an embodiment of a fluid heat exchanger <NUM>. In some embodiments, the fluid heat exchanger may include a pipe <NUM> with fins <NUM> extending radially outward from the surface of the pipe <NUM>, which may include similar features, such as the fin configurations, of one or more of the pipes or tubes discussed herein. In some embodiments, the pipe <NUM> may include pipe connections <NUM> (e.g., coupling, union, dielectric union, nipple, bushing, double-tapped bushing, flanged connection, compression fittings, etc.) on the ends of the pipe for connection into a fluid cooling system (see <FIG> and <FIG>). As depicted, the pipe connections <NUM> may be positioned at opposing ends of the fluid heat exchanger <NUM>. In other embodiments, the pipe connections <NUM> may be positioned on one end, side, or even middle portion of the fluid heat exchanger <NUM> where at least a portion of the pipe <NUM> may extend from a first pipe connection <NUM> and double back (e.g., return by traversing substantially the same route, for example, in a substantially parallel manner) to a second pipe connection <NUM> positioned proximate (e.g., adjacent) the first pipe connection <NUM>.

In some embodiments, the pipe <NUM> may define a plurality of stacked rings <NUM> (e.g., loops, hoops, etc.). The plurality of stacked rings <NUM> may include one or more rings that exhibit differing dimensions from the adjacent stacked rings <NUM> (e.g., at least some of the stacked rings <NUM> are offset from an adjacent stacked ring <NUM>). For example, at least some of the stacked rings <NUM> may be offset from an adjacent stacked ring <NUM> (e.g., in a lateral direction transverse to a longitudinal axis or centerline of the fluid heat exchanger <NUM>, where the stacked rings <NUM> extend around the longitudinal axis). As depicted, the plurality of stacked rings <NUM> may be formed in a curved or annular (e.g., circular) shape with a gradually increasing or decreasing diameter, such that the plurality of stacked rings <NUM> defines a conical shape (e.g., conical coil, conical helix, conical spiral, etc.). Decreasing the diameters of the plurality of stacked rings <NUM> may increase the efficiency of the heat exchanger by decreasing the likelihood that heat energy will transfer in an unintended or undesirable manner between adjacent stacked rings <NUM> rather than transferring to the surrounding environment.

In some embodiments, the stacked rings <NUM> may have a different shape (e.g., annular, oval, rectangular, polygonal, quadrilateral, square, triangular, hexagonal, etc.). In some embodiments, the differing dimension may be, for example, the length of a side, altitude, diagonal, apothem, radius, etc..

In some embodiments, the stacked rings <NUM> may exhibit other shapes where the adjacent rings are still at least partially offset from one another. For example, the diameters of the rings (e.g., rings <NUM>, <NUM>, <NUM>) may increase and decrease between each adjacent stacked ring <NUM> to define an undulating shape, rather than a normal conical shape.

In some embodiments, the stacked rings <NUM> may allow significantly longer pipes to be used in a confined space. For example, the pipe <NUM> may be between about <NUM> meters and <NUM> meters in length, such as, for example, between about <NUM> meters and <NUM> meters. When the pipe <NUM> is formed into stacked rings <NUM> the dimensions of the fluid heat exchanger <NUM> may be, for example, less than <NUM> meter in height and less than <NUM> meters in diameter.

In some embodiments, the stacked rings <NUM> may be formed in a conical shape with an apex angle (e.g., the angle between two lines tangential to the stacked rings <NUM> converging on a central axis of the conical stack) between about <NUM>° and about <NUM>°, such as between about <NUM>° and about <NUM>°, or about <NUM>° and about <NUM>°. For example, in some embodiments, a ratio of the spacing between the individual rings within the stacked rings <NUM> and the change in diameter of the rings <NUM> may be between about <NUM>:<NUM> and about <NUM>:<NUM>, such as between about <NUM>:<NUM> and about <NUM>:<NUM>, or about <NUM>:<NUM>, where the first number is the spacing and the second number is the change in diameter.

In some embodiments, the pipe <NUM> may have a diameter between about <NUM> and about <NUM>, such as between about <NUM> and about <NUM>, or about <NUM>. In some embodiments, a thickness of the pipe <NUM> may be between about <NUM> and about <NUM>, such as between about <NUM> and about <NUM>. In some embodiments, the fins <NUM> may extend a height from the pipe <NUM> that is less than the diameter of the pipe <NUM>. For example, the fins may extend a height of between about <NUM> and about <NUM>, such as between about <NUM> and about <NUM>, or about <NUM>.

In some embodiments, the pipe <NUM> may be formed from a thermally conductive material. For example, the pipe <NUM> may be formed from copper, aluminum, stainless steel, carbon steel, bronze, brass, titanium, or other metal alloys. In some embodiments, the pipe <NUM> may be formed from corrosion resistant materials that are also thermally conductive, such as, for example, stainless steel, chrome, nickel, iron, copper, tungsten, and titanium.

In some embodiments, the fins <NUM> may be formed from a thermally conductive material. For example, the fins <NUM> may be formed from copper, aluminum, stainless steel, carbon steel, bronze, brass, titanium, or other metal alloys. In some embodiments, the fins <NUM> may be formed from the same material as the pipe <NUM>. In other embodiments, the fins <NUM> may be formed from a different material from the pipe <NUM>. In some embodiments, the fins <NUM> may be formed as part of the pipe <NUM>, such as by extrusion, molding, rolling, etc. In some embodiments, the fins <NUM> may be formed separately from the pipe <NUM> and attached thereto. The fins <NUM> may be attached through a process of, for example, soldering, welding (e.g., arc welding, laser welding, electric resistance welding, oxy-fuel welding, etc.), brazing, adhesives, etc..

<FIG> illustrate pipe and fin configuration in accordance with some embodiments of the disclosure. For example, the fins <NUM> may include an interface surface <NUM> (e.g., flange) that may define the spacing between the fins <NUM>, as shown in <FIG>. The interface surface <NUM> may extend substantially perpendicular from the fin <NUM> forming a substantially flat surface to interface with a surface of the pipe <NUM>.

In some embodiments, the interface surface <NUM> may include an interlocking shelf <NUM>, as shown in <FIG>. The interlocking shelf <NUM> may secure the fin <NUM> to an adjacent fin <NUM>. As depicted, the interlocking shelf <NUM> may allow the fins <NUM> to support and/or secure the other adjacent fins <NUM>.

In some embodiments, the pipe may include a discontinuous feature (e.g., a knurled surface <NUM>), as shown in <FIG>. The knurled surface <NUM> may interface with the interface surface <NUM> of the fins <NUM>. In some embodiments, the knurled surface <NUM> may secure the interface surface <NUM> substantially limiting or preventing lateral motion along the surface of the pipe.

In some embodiments, the interface between the fins <NUM> and the pipe <NUM> may a tongue and groove interface (e.g., half lap joint, dovetail joint,) as shown in <FIG>. As depicted, the pipe <NUM> may include a groove <NUM>. The fins <NUM> may include a complementary base <NUM> (e.g., tongue, tenon) that may fit within the groove <NUM>. In some embodiments, the complementary base <NUM> may be secured within the groove <NUM> by an interference fit (e.g., compression fit, press fit, friction fit). In some embodiments, the complementary base <NUM> and the groove <NUM> may be a loose fit, wherein the groove <NUM> may substantially prevent lateral motion along the surface of the pipe <NUM>, while allowing motion within (e.g., along) the groove <NUM> to facilitate heat expansion and accommodate different rates of expansion, etc..

In some embodiments, the fins <NUM> may be extruded or rolled from the pipe <NUM>.

In some embodiments, the fins <NUM> may be extruded or rolled from a separate sleeve material <NUM> (e.g., a continuous material) within which the pipe may be inserted, as shown in <FIG>. The interface between the pipe <NUM> and the sleeve material <NUM> may be an interference fit. In some embodiments, the interface between the pipe <NUM> and the sleeve material <NUM> may include knurled surfaces on at least one of a surface of the pipe <NUM> or a surface of the sleeve material <NUM>.

<FIG> illustrates a temperature profile of the fluid heat exchanger <NUM>. As depicted, a first fluid <NUM> may flow within the pipe <NUM>. A second fluid <NUM> may be provided on the exterior of the pipe <NUM>. In some embodiments, the second fluid <NUM> may be ambient air. In other embodiments, the second fluid <NUM> may be another fluid, such as, for example, water, oil, or other coolants. In some embodiments, the plurality of stacked rings <NUM> may be arranged such that the conical shape is substantially vertical. In some embodiments, the largest ring <NUM> may be located on the bottom and the smallest ring <NUM> may be located on the top of the conical shape (e.g., in the vertical orientation as shown in <FIG>). In another embodiment, the conical shape may be inverted with the largest ring <NUM> on the top of the conical shape and the smallest ring <NUM> on the bottom of the conical shape. In other embodiments, the conical shape may include repeating the above configuration in a stacked manner.

In some embodiments, the first fluid <NUM> may carry heat energy from another process. The heat energy of the first fluid <NUM> may induce a flow on the second fluid <NUM> through natural or passive convection. The second fluid <NUM> may enter at the bottom of the conical shape as a cool fluid 208a. As heat is transferred to the cool fluid 208a, the cool fluid 208a may transition to a warm fluid 208b (e.g., a warmer fluid 208b having a temperature greater than the cool fluid 208a), which has a lower density than the cool fluid 208a and will generally move in an upward direction relative to the cool fluid 208a. The upward movement of the warm fluid 208b may create a natural flow through the conical shape. The warm fluid 208b will naturally move from the inside of the conical shape to the outside of the conical shape and continue upwards. This movement may create a low pressure volume inside the conical shape that will, in turn, draw the cool fluid 208a through the bottom of the conical shape to replace the fluid that transitioned to warm fluid 208b.

In some embodiments, the conical or otherwise offset shape may reduce the effect of the lower rings of the plurality of stacked rings <NUM> on the upper rings of the plurality of stacked rings <NUM> (e.g., to reduce the heating effects of the lower rings on upper rings that are adjacent to one or more of the lower rings). For example, the natural convection may induce a flow (e.g., an at least partially lateral flow) in the second fluid <NUM> from the inside of the conical shape to the outside of the conical shape through the spaces between the plurality of rings <NUM> rather than from a top surface of a lower ring to a bottom surface of an upper ring. The induced flow may remove heat from both the upper ring and the lower ring at a substantially similar rate because the cool fluid 208a may be a substantially uniform temperature throughout the inside portion of the conical shape and the cool fluid 208a may be drawn through the spaces between the plurality of rings <NUM> at a substantially uniform rate.

<FIG> illustrates an embodiment of a heat exchanger <NUM>. As depicted, the heat exchanger <NUM> may include a plurality of tubes <NUM> (e.g., two, three, four, five, or more tubes <NUM>, which may include similar features, such as the fin configurations, of one or more of the pipes or tubes discussed herein). For example, the heat exchanger <NUM> may include a first tube 302a and a second tube 302b. The tubes <NUM> may include fins <NUM> along the length of each of the tubes <NUM>. The tubes <NUM> may define a plurality of rings <NUM>. In some embodiments, the rings <NUM> may alternate with one ring defined with the first tube 302a and the next ring defined with the second tube 302b. The first and second tubes 302a, 302b may define a conical structure by extending side by side in a substantially parallel manner along a coiled path.

In some embodiments, a first ring <NUM> defined with the first tube 302a may have the largest diameter of the plurality of rings <NUM>. In some embodiments, the second ring <NUM> defined with the second tube 302b may be the same diameter as the first ring <NUM>. In other embodiments, the second ring <NUM> may have a smaller diameter than the first ring <NUM>. In some embodiments, a third ring <NUM> defined with the first tube 302a may have a diameter smaller than both the first ring <NUM> and the second ring <NUM>. Such a pattern of offset rings <NUM> may continue along a length or longitudinal axis of the heat exchanger <NUM>.

As depicted, the plurality of tubes <NUM> may be connected at a first manifold <NUM> and a second manifold <NUM>. The first manifold <NUM> and the second manifold <NUM> may create a common passageway between the tubes <NUM> enabling the plurality of tubes <NUM> to operate in parallel. In some embodiments, parallel operation may reduce backpressure caused by the heat exchanger <NUM> by reducing the actual length of the curved tubes <NUM>. A reduction in back pressure may enable the use of tubes <NUM> having a smaller diameter for increased heat transfer. In some embodiments, parallel operation may result in a long effective length of the plurality of tubes <NUM> with a shorter actual length of the tubes 302a, 302b. For example, if the individual tubes 302a, 302b are each <NUM> meters in length, the effective length of the heat exchanger may be about <NUM> meters.

While the tubes 302a, 302b exhibit a substantially parallel configuration with common pipe connections <NUM>, in other embodiments, the tubes 302a, 302b may be otherwise entwined together (e.g., with separate pipe connections, twisted in an overlapping configuration, with mirrored spiral configurations, etc.).

In some embodiments, the individual tubes 302a, 302b may be isolated from each other. For example, the first tube 302a may be connected to a first fluid source and the second tube 302b may be connected to a second fluid source. In some embodiments, the first fluid source and the second fluid source may be connected to the same fluid reservoir or heat source. In another embodiment, the first fluid source and the second fluid source may be connected to separate fluid reservoirs or heat sources of the same system. In another embodiment, the first fluid source and the second fluid source may be connected to different systems that are routed to a common location of the heat exchanger <NUM> (e.g., while entering or exiting the heat exchanger <NUM>) for other reasons, such as environmental conditions or space considerations.

<FIG> illustrates an embodiment of a heat exchanger <NUM> as part of a fluid cooling system <NUM>. The tube <NUM> of the heat exchanger <NUM> includes fins <NUM> along substantially the entire length of a tube <NUM>, which may include similar features, such as the fin configurations, of one or more of the pipes or tubes discussed herein. The tube <NUM> may define a series of loops <NUM> of decreasing/increasing diameter. In some embodiments, the fluid cooling system <NUM> may include a frame <NUM>. The fluid cooling system <NUM> may include a top connection point <NUM> (e.g., flange, bracket, support, etc.) that may connect to the top loop <NUM> of the heat exchanger <NUM>. The fluid cooling system <NUM> may include a bottom connection point <NUM> that may connect to the bottom loop <NUM> of the heat exchanger. In some embodiments, the series of loops <NUM> may be configured (e.g., mounted on the frame <NUM>) to move and absorb some vibration and shock from equipment movement and operation. For example, additional connection points may connect the frame to the heat exchanger at additional loops within the series of loops <NUM> to limit the movement of the series of loops to prevent fatigue failure of the heat exchanger.

In some embodiments, a vent <NUM> may be located at a high point (e.g., uppermost point, top, etc.) on the heat exchanger <NUM>. The vent <NUM> may include a vent valve <NUM> and a vent pipe <NUM>. The vent valve <NUM> may be opened to bleed air from the fluid cooling system <NUM> through the vent pipe <NUM>.

In some embodiments, a drain <NUM> may be located at a low point (e.g., lowermost point, bottom, etc.) on the heat exchanger <NUM>. The drain <NUM> may include a drain valve <NUM> and a drain pipe <NUM>. The drain valve <NUM> may be opened to remove fluid from the fluid cooling system <NUM> for maintenance, repairs, or removal.

As depicted, the fluid cooling system <NUM> may include an expansion tank <NUM> (e.g., bladder, diaphragm, etc.) to accommodate volume changes of the cooling fluid as the temperature of the cooling fluid changes.

Referring back to <FIG>, some embodiments may include a plurality of tubes <NUM> and manifolds <NUM>, <NUM> connecting the plurality of tubes <NUM>. A vent <NUM> may be included in the top manifold <NUM> and/or a drain <NUM> may be included in the bottom manifold <NUM>. For example, the vent <NUM> may be a spring valve, a bleed screw, a bleed port, a plug, or a vent pipe and valve combination. In some embodiments, a drain <NUM> may be included in the bottom manifold <NUM>. The drain <NUM> may be a spring valve, a bleed screw, a bleed port, a plug, or a drain pipe and valve combination.

<FIG> illustrates a schematic of a fluid cooling system <NUM>. In some embodiments, a fluid cooling system may be connected to a mechanical or pump seal <NUM> (e.g., shaft seal, dual seals, dual pressurized seals, etc.). Pump seals <NUM> generate significant amounts of heat when a pump is in operation. In some embodiments, a pump seal <NUM> may include a pump ring <NUM> (e.g., radial flow pumping ring or axial flow pumping ring) for moving a cooling fluid through the pump seals <NUM> for a fluid flush of the pump seal <NUM>. A fluid flush of the pump seal <NUM> may remove heat from the pump seal <NUM> and may also lubricate the pump seal <NUM>.

In some embodiments, the fluid cooling system <NUM> may be a closed loop system. A closed loop system may be necessary, for example, when the cooling fluid is hazardous or toxic, has high vapor pressure, has special additives (e.g., glycol, scale preventers, etc.), and/or the pumped fluid is not conducive to cooling and/or lubricating seals (e.g., dirty, abrasive, or polymerizing fluids). The cooling fluid may be completely isolated from the pumped fluid. The closed loop system may include an expansion tank <NUM> (e.g., bladder, diaphragm, etc.) to accommodate volume changes of the cooling fluid as the temperature of the cooling fluid changes. The fluid cooling system <NUM> may include a conical coil <NUM> (e.g., similar to those discussed herein) for removing heat from the system (e.g., from the cooling fluid as it passes through the conical coil <NUM>). The fluid cooling system <NUM> may also include a vent <NUM> and a drain <NUM> for removing and adding fluid to the system for maintenance, repair, or replacement processes.

The embodiments of the present disclosure may provide more efficient passive heat exchanger systems, where implemented. The embodiments may induce natural convective flow in a secondary cooling medium to remove heat more efficiently. Passive heat exchangers may provide additional cost saving benefits because of the reduced amount of hardware required and the reduced amount of moving parts that require maintenance.

Some embodiments may increase the effective length of the heat exchanger while maintaining easy access to any instrumentation and controls that may be present on the top and bottom of the heat exchanger. The increased effective length may increase the efficiency of the heat exchanger, while the compact design may provide space saving benefits in industries where floor space is a premium commodity.

Claim 1:
A fluid heat exchanger (<NUM>, <NUM>, <NUM>, <NUM>) comprising:
a first tube (<NUM>, <NUM>, <NUM>, <NUM>) defining a substantially conical coil, the first tube (<NUM>, <NUM>, <NUM>, <NUM>) extending around a longitudinal axis of the fluid heat exchanger (<NUM>, <NUM>, <NUM>, <NUM>), the first tube (<NUM>, <NUM>, <NUM>, <NUM>) having at least one arcuate section that is laterally offset from another arcuate section of the first tube (<NUM>, <NUM>, <NUM>, <NUM>) in a direction transverse to the longitudinal axis;
a plurality of fins (<NUM>, <NUM>, <NUM>, <NUM>) attached to an exterior surface of the first tube (<NUM>, <NUM>, <NUM>, <NUM>);
at least one fitting (<NUM>, <NUM>) coupled to the first tube (<NUM>, <NUM>, <NUM>, <NUM>) to enable fluid flow into and out of the first tube (<NUM>, <NUM>, <NUM>, <NUM>) in order to transfer heat energy between a first fluid within the first tube (<NUM>, <NUM>, <NUM>, <NUM>) and a second fluid on an exterior of the first tube (<NUM>, <NUM>, <NUM>, <NUM>) proximate the first tube (<NUM>, <NUM>, <NUM>, <NUM>) and the plurality of fins (<NUM>, <NUM>, <NUM>, <NUM>); and
characterized by the substantially conical coil being defined by a plurality of rings (<NUM>, <NUM>, <NUM>) including spaces between the plurality of rings (<NUM>, <NUM>, <NUM>) of the substantially conical coil; and
a second tube (<NUM>, <NUM>, <NUM>, <NUM>) defining the substantially conical coil, the first tube (<NUM>, <NUM>, <NUM>, <NUM>) and the second tube (<NUM>, <NUM>, <NUM>, <NUM>) extending along a similar path adjacent to each other; the first tube (<NUM>, <NUM>, <NUM>, <NUM>) and the second tube (<NUM>, <NUM>, <NUM>, <NUM>) connected to a first common fitting (<NUM>, <NUM>) at a first longitudinal end of the conical coil and a second common fitting (<NUM>, <NUM>) at a second, opposing longitudinal end of the conical coil.