HEAT EXCHANGER UTILIZING TUBULAR STRUCTURES HAVING INTERNAL FLOW ALTERING MEMBERS AND EXTERNAL CHAMBER ASSEMBLIES

Abstract

A heat exchanger includes at least one cylindrical tubular member formed from a tubular structure and chamber assemblies. A plurality of flow altering members are coupled at predetermined intervals within the tubular structure. The flow altering members have an angled surface on their respective sides facing the flow of a heat exchange medium. Pairs of inlet orifices and outlet orifices are formed on the wall of the tubular structure at the same intervals as the flow altering members. Chamber assemblies are coupled as a full or partial collar on the exterior of the tubular structure. Each chamber assembly is hollow, permitting fluid flow within, and is in fluid communication with a corresponding inlet orifice, outlet orifice pair so that the heat exchange medium repeatedly flows out of the tubular structure into a chamber assembly and back into the tubular structure. Multiple cylindrical tubular members may be coupled between manifolds.

Description

RELATED APPLICATION DATA

This is a divisional application of U.S. patent application Ser. No. 13/677,953, filed Nov. 15, 2012, which is incorporated herein by reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates generally to heat exchanger tubes and heat exchangers and, more specifically, to heat exchanger tubes and heat exchangers with a cylindrical tubular member having a plurality of flow altering members within each tubular member. The flow altering members are each paired with a chamber assembly attached to the external surface of the cylindrical tubular member.

2. Discussion of Related Art

Heat exchangers are commonly utilized in systems where it is desired for heat to be removed. Typical basic heat exchangers are made of generally straight pipes, which channel heat exchanging medium within. Headers or manifolds are typically attached to each end of the pipes. These headers and manifolds act as receptacles for the heat exchanging medium. The efficiency of pipe heat exchangers is limited by the amount of surface area available for the transfer of heat. In a tube and chamber heat exchanger, a plurality of tube and chamber assemblies extend in spaced relation between a pair of headers or manifolds, forming the core of a heat exchanger. Heat exchanging performance of the heat exchanger is dictated by the overall surface area provided by the plurality of tube and chamber assemblies.

To increase surface area to enhance heat exchange performance, typical heat exchangers such as condensers, incorporate a flat-tube design, usually of extruded tubular material with extended surfaces provided by corrugated fin material, the corrugated fin material being generally interposed between a pair of extruded tubular materials. This type of heat exchanger typically includes flattened tubes having a fluid passing therethrough and a plurality of corrugated fins extending between the tubes. The fins are attached to the tubes to effectively increase the surface area of the tubes, thereby enhancing the heat transfer capability of the tubes. A number of tubes and fins may be stacked on top of each other, with a small opening to allow passage of air therethrough. To further improve heat transfer efficiency, the tube's wall thickness may be made thinner. As a result, the parts are lighter in weight, which in turn makes the overall heat exchanger lighter in weight. However, the pressure resistance is reduced, and the thinner tubes are more prone to damage. Also, the assembly process is complicated due to the fragile nature of the parts. In addition, extruded tubes are prone to plugging during the manufacturing process, particularly if a brazing process is utilized. The complexity of the extruding process results in higher costs and higher defect rates. Furthermore, as flat tubes are generally extruded into shape utilizing metal extrusion processes, only material that can be easily extruded into shape is typically made into flat tubes, restricting the available materials for flat tubes generally to aluminum and various aluminum alloys known in the art.

The overall cost for the flat tube heat exchanging system is higher because a powerful compressor is necessary to move the heat exchanging medium through the smaller openings of the tubes. Conversely, if a higher powered compressor is not utilized, then additional tubes are necessary to obtain the desired heat exchanging performance because the smaller tubes reduce the flow of the heat exchange medium significantly. The addition of tubes increase the overall cost for the heat exchanging system. Currently, this type of heat exchanger is used in applications requiring high heat exchanging capabilities, such as automotive air conditioner condensers.

In another tube-and-fin design, the tube can be of a serpentine design, therefore eliminating the need for headers or manifolds, as the tube is bent back and forth in an “S” shape to create a similar effect. Typical applications of this type of heat exchanger, besides condensers, are evaporators, oil coolers, and heater cores. This tube-and-fin design is also utilized in radiators for automobiles. Outside of the automotive field, the tube and fin design is implemented by industrial oil coolers, compressor oil coolers, and in other similar applications requiring a higher efficiency heat exchanger. The serpentine design is essentially a single, long tube material with a single chamber to transfer a heat exchange medium from the inlet of the serpentine design heat exchanger to the outlet, thereby increasing the pressure resistance of heat exchange medium travelling through the heat exchanger. This is detrimental to the performance of a heat exchanger, especially in an application such as an evaporator, wherein pressure drop significantly diminishes the performance of the compressor, for example.

A variation on the tube-based heat exchanger involves stacking flat ribbed plates. When stacked upon each other, these ribbed plates create chambers for transferring heat exchanging medium. In essence, this type of heat exchanger performs substantially the same as tube-and-fin type heat exchangers, but is fabricated differently. This type of heat exchanger is commonly implemented by contemporary evaporators.

In another variation of a tube heat exchanger, a bundle of tubes are arranged to form a heat exchanger generally known in the art as shell-and-tube heat exchanger. In a shell-and-tube heat exchanger, a plurality of generally straight tubes are bundled together, leaving sufficient space between the tubes to allow a first heat exchanging medium to flow around the exterior of the individual tubes, and a second heat exchanging medium to flow within the individual tubes. The heat exchanging medium that flows on the exterior of the individual tubes and the heat exchanging medium that flows within the individual tubes may be of the same type of heat exchanging medium, or may be of different types. This type of a heat exchanger typically involves having a first end of bundled tubes to be coupled to a first manifold, and a second end of the bundled tubes to be coupled to a second manifold. The entire tube bundle is typically enclosed in a water-tight vessel. Shell-and-tube heat exchangers are generally used in application requiring extremely high pressure, and typically employ two heat exchange mediums, with one heat exchange medium flowing inside the tube bundle, and a second heat exchange medium flowing around the tube bundle within the water-tight vessel. Shell-and-tube heat exchangers are also commonly utilized in large scale heat exchanging devices for commercial and industrial applications requiring large heat exchanging capacity. Shell-and-tube heat exchangers typically bundle together generally straight tubes with no surface enhancements either to the inside or the outside of the tubes, resulting in limited heat exchanging performance characteristics. This causes shell-and-tube heat exchanger to be larger in size to meet a desired heat exchanging performance, thus requiring a large footprint for installation purposes.

Another variation of a heat exchanger is a chamber and tube design with a medium directing member inserted within the chamber assembly. The chamber and tube design heat exchanger functions by preventing the heat exchange medium from flowing in a straight line, and causing turbulent flow within the heat exchanger by forcing the heat exchange medium to constantly change directions within the heat exchanger, first by a medium directing member and then by a chamber assembly. As a heat exchange medium enters the chamber and tube design heat exchanger, the heat exchange medium flows in a straight line through a straight tube section. At the end of the straight tube section is the medium directing member. The function of the medium directing member is to alter the direction of the heat exchange medium flow from the generally straight line flow to almost a perpendicular flow, while leading the heat exchange medium into the chamber section of the heat exchanger. The chamber section is connected to the tube section, and is generally of a larger diameter than the tube section. As the heat exchange medium is introduced into the chamber assembly, the flow of heat exchange medium follows in two semi-circular paths. At the end of the semi-circular paths, the heat exchange medium again encounters the medium directing member. As the heat exchange medium again encounters the medium directing member, the flow is restored into a generally straight flow, as the heat exchange medium is led to yet another tube section of the heat exchanger. This process repeats itself within the length of a chamber and tube design heat exchanger.

SUMMARY

The present invention is an enhanced tubular heat exchanger comprising a cylindrical tubular member with a plurality of chamber assemblies coupled to the external surface of the cylindrical tubular member. The cylindrical tubular member is hollow, allowing fluid flow within, with a plurality of flow altering members coupled at predetermined intervals within the fluid flow path of the cylindrical tubular member along the longitudinal length of the cylindrical tubular member. The flow altering members positioned inside the cylindrical tubular member substantially alter the flow path of the heat exchange medium flowing inside the cylindrical tubular member, preventing the heat exchange medium from continually flowing in a generally straight line from the inlet of the cylindrical tubular member to the outlet of the cylindrical tubular member.

The flow altering members placed inside the cylindrical tubular member may be each paired with an inlet orifice and an outlet orifice formed on the wall of the cylindrical tubular member. The flow altering member has an angled plane on the side facing the flow of heat exchange medium within the cylindrical tubular member. The inlet orifice and the outlet orifice are formed on the wall of the cylindrical tubular member, each inlet orifice and outlet orifice going through the entire thickness of the material forming the cylindrical tubular member, creating a flow path for heat exchange medium from the interior of the cylindrical tubular member to the exterior of the cylindrical tubular member. A plurality of chamber assemblies are coupled on the exterior of the cylindrical tubular member. The chamber assemblies are generally of larger diameter than the diameter of the cylindrical tubular member, and have an axial span generally drastically shorter than the axial span of the cylindrical tubular member. The chamber assemblies are hollow, allowing for fluid flow within. Chamber assemblies may be circular, but can be a cylinder, rectangular, or of other geometric shapes. Chamber assemblies are positioned along the length of the cylindrical tubular member, each chamber assembly overlapping a pairing of an inlet orifice and an outlet orifice formed in the wall of the cylindrical tubular member. One end of the cylindrical tubular member may connect to a header or a manifold. A second end of the cylindrical tubular manifold may connect to another header or a manifold.

Heat exchange medium flows from the header or the manifold into the cylindrical tubular member. The heat exchange medium within the cylindrical tubular member flows in a first line of flow generally parallel to the cylindrical tubular member. The heat exchange medium, flowing in the first line of flow inside the cylindrical tubular member, travels towards a flow altering member. The flow altering member has an angled surface facing the flow of heat exchange medium and directs the flow of heat exchange medium towards the first inlet orifice formed in the wall of the cylindrical tubular member, said inlet orifice going through the entire thickness of the wall forming the cylindrical tubular member. Flow altering members generally feature an angled surface on the side facing the flow of the heat exchange medium, allowing a smooth, yet substantial change in directional flow of the heat exchange medium.

The heat exchange medium flowing in the cylindrical tubular member initially flows in a first line of flow. A plurality of flow altering members are coupled within the inner surface of the cylindrical tubular member. The heat exchange medium, as it encounters the flow altering member, is directed to flow in a second line of flow. The second line of flow is generally at an acute angle, approaching an angle, in some embodiment of the present invention, that is generally perpendicular to the first line of flow, guiding the flow of heat exchange medium towards the inlet orifice. A chamber assembly, being hollow, is coupled to the external surface of the cylindrical tubular member. The chamber assembly generally is of larger diameter than the cylindrical tubular member, with an axial length generally substantially shorter than that of the cylindrical tubular member. The chamber assembly is in fluid communication with the inlet orifice of the cylindrical tubular member. The heat exchange medium exits the cylindrical tubular member through the inlet orifice and enters the chamber assembly. Once inside the chamber assembly, the heat exchange medium is dispersed within the chamber assembly, led towards the outlet orifice formed in the wall of the cylindrical tubular member.

Although not to be limiting, the outlet orifice is positioned on a side of the wall of the cylindrical tubular member that is generally opposite the side on which the inlet orifice is positioned. In other embodiments, the position of the inlet orifice and the outlet orifice may be offset. The chamber assembly is in fluid communication with both the inlet orifice and the outlet orifice formed on the wall of the cylindrical tubular member. This arrangement allows the heat exchange medium that exits the cylindrical tubular member through the inlet orifice to enter the chamber assembly and to re-enter the cylindrical tubular member through the outlet orifice. The heat exchange medium flowing back into the cylindrical tubular member through the outlet orifice encounters a flow altering member. The flow altering member has an angled surface on a side facing the outlet of the cylindrical tubular member and generally restores the heat exchange medium's directional flow to that of the first line of flow. This process is repeated throughout the length of the cylindrical tubular member. At the end of the tubular member, heat exchange medium may exit to a second header or a manifold.

As the heat exchange medium flows through the cylindrical tubular member and a plurality of chamber assemblies, heat contained within the heat exchange medium is absorbed by the material comprising the cylindrical tubular member and the chamber assemblies. Heat absorbed by the tubular member and the chamber assemblies is then released to the environment external to the assemblies.

In an embodiment of the present invention, the heat exchange medium flows into the cylindrical tubular member from the first manifold, attached on a first end of the cylindrical tubular member. The heat exchange medium flows in a first line of flow in the cylindrical tubular member, generally along the long axis of the cylindrical tubular member. As the heat exchange medium approaches a first flow altering member, the heat exchange medium is directed to flow in a second line of flow, generally perpendicular to the first line of flow. The flow altering members are generally coupled to the inner surface of the cylindrical tubular member. As the heat exchange medium is directed in the second line of flow by the flow altering member, the heat exchange medium exits the cylindrical tubular member through the inlet orifice formed on the wall of the cylindrical tubular member and enters the chamber assembly. Once inside the chamber assembly, the heat exchange medium is directed to flow in a third line of flow, the flow dictated by the inner contour of the chamber assembly. Although not meant to be limiting, the third line of flow of heat exchange medium may be at least one semi-circular flow pattern. The heat exchange medium then exits the chamber assembly and re-enters the cylindrical tubular member through the outlet orifice, the outlet orifice being formed on the wall of the cylindrical tubular member. Once the heat exchange medium re-enters the cylindrical tubular member, the heat exchange medium is directed to flow generally in the first line of flow by the flow altering member, the flow altering member featuring an angled surface on the side facing the heat exchange medium flow. The process repeats itself within the cylindrical tubular member, until the heat exchange medium reaches the end of the cylindrical tubular member, which medium then exits the cylindrical tubular member and enters the second header or a manifold.

In embodiments of the present invention, the cylindrical tubular member may comprise a seamless tubular structure, or a seamed tubular structure. Seamless tubular structures may be formed by extrusion, by casting, or by other forming methods. Seamed tubular structures may be formed by high frequency welding, other welding methods, or mechanical means.

In an embodiment of the present invention, heat exchanging characteristics may be enhanced by adding additional plate materials on the surface of the cylindrical tubular member or on one or more surfaces of the chamber assemblies. Adding additional plate materials on the surface, increases the overall surface area of the heat exchanger, and the performance of the heat exchanger is enhanced by having more surface area to dissipate heat away from the heat exchanger. The additional plate material may comprise a substantially thinner material in comparison to the material comprising the cylindrical tubular member, thereby further enhancing the heat transfer performance of a heat exchanger for particular applications.

In an embodiment of the present invention, the cylindrical tubular member and the chamber assemblies for a heat exchanger are provided, for example, for a condenser, evaporator, radiator, etc. The heat exchanger may also be a heater core, intercooler, or an oil cooler for an automotive application (e.g., steering, transmission, engine, etc.) as well as for non-automotive applications. An advantage of the present invention is that the heat exchanger has a larger surface area for radiating heat over a shorter distance than that of a conventional heat exchanger, with the surface area provided by both the cylindrical tubular member and the chamber assemblies. With the provision of a large surface area for exchanging heat, the efficiency of the heat exchanger is greatly increased. Additionally, the structural rigidity provided by having the cylindrical tubular member comprised of a single seamless or seamed tube lends itself for use in high internal or external pressure applications.

Another advantage of the present invention is that the overall length of the enhanced tube for heat exchanging applications may be shortened compared to a conventional heat exchanger, which in turn provides for a lower overall cost, as less raw material and less packaging are necessary. Additionally, the cylindrical tubular member may be made from a thicker gage material, allowing the heat exchanger to be used for high pressure applications. Furthermore, the smaller footprint of the present invention lends itself to be used in applications where space is limited. Yet another advantage of the present invention over a conventional heat exchanger is that the manufacturing process may be simpler because the present invention requires less fragile components and less manufacturing steps. The present invention provides an easy to assemble heat exchanger, providing enhanced heat exchanging performance while being cost effective. The present invention also excels in high pressure applications typical of commercial and industrial applications, by providing a rigid cylindrical tubular member, which can be manufactured of thick gage tubular material. The entire unit may be brazed together, or any portion of the unit can be brazed first, and then additional components may be brazed, soldered together, or attached by mechanical means, with or without utilization of gaskets.

The present invention also lends itself for ease of assembly by having a single piece cylindrical tubular member. The cylindrical tubular member may be a single piece tubular structure with a plurality of inlet orifices and outlet orifices formed at predetermined intervals in the wall of the cylindrical tubular member. The orifices can be machine drilled, punched out by pressing, or formed by other mechanical means, as long as the method used creates orifices that go through the entire thickness of the wall of the cylindrical tubular member. A plurality of flow altering members may be inserted inside the cylindrical tubular member to align with an inlet orifice and an outlet orifice pairing. In an embodiment of the present invention, a plurality of flow altering members may be formed from a single piece of material, or a plurality of flow altering members may be coupled together to form a single piece of material with a plurality of flow altering features. In another embodiment of the present invention, a plurality of flow altering members may be inserted inside the cylindrical tubular member, with the length of each flow altering member predetermined, so that once the individual flow altering members are inserted into the cylindrical tubular member end-to-end, each flow altering member aligns to a pairing of an inlet orifice and an outlet orifice. On the outer surface of the cylindrical tubular member, a plurality of chamber assemblies are coupled, each chamber assembly being positioned over a pair comprising of an inlet orifice and an outlet orifice.

Chamber assemblies may be mechanically coupled to the outer surface of the cylindrical tubular member, or may be attached by other means, such as brazing, soldering, or welding, for example. A plurality of chamber assemblies may be first combined together to form a unitary unit of a plurality of chamber assemblies, prior to coupling the chamber assemblies to the cylindrical tubular members. By combining a plurality of chamber assemblies prior to coupling to the cylindrical tubular members, the assembly process is simplified. Additionally, a plurality of chamber assemblies may be formed from a single piece of material, by stamping, casting, hydroforming, or other machining processes.

In another embodiment of the present invention, fins or plate members may be attached to the outside surface of the cylindrical tubular member, to the outer surface of chamber assemblies or to surfaces of both the cylindrical tubular member and the chamber assemblies. Fins or plate members attached to the outer surface further increase the surface area of a heat exchanger, thereby enhancing the performance characteristics of the heat exchanger. Fins and plate members provide an economical means to increase the heat exchanging capability of a heat exchanger by enhancing the surface area available for heat transfer, without greatly increasing the size of a heat exchanger or costing more to produce a heat exchanger.

In yet another embodiment of the present invention, the chamber assembly size may vary from one chamber assembly to the next.

In another embodiment of the present invention, a plurality of cylindrical tubular members may be bundled together to form a heat exchanger with a plurality of cylindrical tubular members. One end of the bundled cylindrical tubular member may connect to a first manifold or a header, and a second end of the bundled cylindrical tubular member may connect to a second manifold or a header. In an embodiment of the present invention, the size of the cylindrical tubular member may vary from one cylindrical tubular member to the next.

In yet another embodiment of the present invention, a plurality of cylindrical tubular members may be bundled together, leaving enough space between each of the bundled tubes to allow flow of heat exchange medium around the exterior of the individual cylindrical tubular member. The first end of the bundled cylindrical tubular member may connect to a first manifold or a header. The second end of the bundled cylindrical tubular member may connect to a second manifold or a header. The entire area comprising the bundled cylindrical tubular member may be sealed in a water tight vessel, allowing a heat exchange medium to flow on the outer surface of the bundled cylindrical tubular member. The vessel may have an inlet to allow a first heat exchange medium to flow inside the vessel. The vessel may also have an outlet to allow the first heat exchange medium to exit the vessel. Furthermore, the vessel may feature baffles to direct flow of heat exchange medium within the vessel. In an embodiment of the present invention, a second heat exchange medium may flow within the bundled cylindrical tubular member. The first heat exchange medium flowing outside the bundled cylindrical tubular member and the second heat exchange medium flowing inside the bundled cylindrical tubular member may be a gas, a liquid, or a combination of both.

In a further embodiment of the present invention, each chamber assembly may disperse heat exchanging medium throughout the chamber, which further enhances the heat exchanging capabilities of the present invention. Also, the cylindrical tubular member may also mix heat exchanging medium.

In another embodiment of the present invention, the inner surface of the cylindrical tubular member may feature indentations to increase the surface area. Also, in yet another embodiment of the present invention, the inner surface of the chamber assembly may also feature indentations to increase the surface area. In a further embodiment of the present invention, the flow altering member may also feature indentations. In an embodiment of the present invention, the chamber assembly may have other surface features such as, but not limited to, indentations, louvers, dimples, as well as other extended surface features to alter the fluid flow characteristics within the chamber assembly.

The cylindrical tubular member and the chamber assemblies may be made of aluminum, either with cladding or without cladding. The flow altering member may be made of aluminum, either with cladding or without cladding. The cylindrical tubular member, the chamber assemblies, and the flow altering members may also be made of stainless steel, copper or other ferrous or non-ferrous materials. The cylindrical tubular member, the chamber assemblies, and the flow altering members may also be a plastic material or other composite materials.

The cylindrical tubular member, the chamber assemblies, and the flow altering members may be manufactured by stamping, cold forging, casting, hydroforming, or machining

Other features and advantages of the present invention will be readily appreciated, as the same becomes better understood after reading the subsequent description taken in conjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a perspective view of a heat exchanger comprising cylindrical tubular member with plurality of chamber assembly attachments according to embodiments of the present invention;

FIG. 1B is a side view of a prior art tubular structure typically used in a pipe heat exchanger;

FIG. 1C is a perspective view of a tubular structure according to embodiments of the present invention;

FIG. 1D illustrates a cross-sectional view of a cylindrical tubular member with a plurality of chamber assemblies coupled to the outer surface of a tubular structure, and with a plurality of flow altering members positioned in predetermined locations within the cylindrical tubular member according to embodiments of the present invention;

FIG. 2A illustrates another cross-sectional view of the heat exchanger, according to an embodiment of the present invention;

FIG. 2B is a side view of the tubular structure according to embodiments of the present invention;

FIG. 2C illustrates a side view of the flow altering member, according to an embodiment of the present invention;

FIG. 2D illustrate a side view of the chamber assemblies, according to an embodiment of the present invention;

FIG. 2E is a perspective view of a chamber assembly, according to embodiments of the present invention;

FIG. 3A illustrates flow patterns of a heat exchange medium inside the cylindrical tubular member according to embodiments of the present invention;

FIG. 3B is a cross-sectional view of a heat exchanger according to embodiments of the present invention;

FIG. 3C is a cross-sectional view of the tubular structure according to embodiments of the present invention;

FIG. 3D is a cross-sectional view of a plurality of flow-altering members according to an embodiment of the present invention;

FIG. 3E is a cross-sectional view of another chamber assembly, according to embodiments of the present invention;

FIG. 4A is a perspective view of a heat exchanger, according to embodiments of the present invention;

FIG. 4B is a side view of a heat exchanger, according to embodiments of the present invention;

FIG. 4C is a top view of a heat exchanger, according to embodiments of the present invention;

FIG. 4D is a perspective view of another heat exchanger, according to embodiments of the present invention;

FIG. 4E is a side view of a heat exchanger, according to another embodiment of the present invention;

FIG. 4F is a top view of a heat exchanger, according to another embodiment of the present invention;

FIG. 5A is a perspective view of a flow altering member, according to embodiments of the present invention;

FIG. 5B is a top view of a flow altering member, according to embodiments of the present invention;

FIG. 5C is a forward view of a flow altering member, according to embodiments of the present invention;

FIG. 5D is a side view of a flow altering member, according to embodiments of the present invention;

FIG. 5E is a perspective view of another embodiment of a flow altering member, according to embodiments of the present invention;

FIG. 5F is a side view of a plurality of flow altering member, according to embodiments of the present invention;

FIG. 6A is a side view of a heat exchanger, according to another embodiment of the present invention;

FIG. 6B is a perspective view of a heat exchanger, according to another embodiment of the present invention;

FIG. 6C is a top view of a heat exchanger, according to another embodiment of the present invention;

FIG. 6D is a side view of a cylindrical tubular member, according to another embodiment of the present invention;

FIG. 6E is a perspective view of a cylindrical tubular member, according to another embodiment of the present invention;

FIG. 6F is a top view of a cylindrical tubular member, according to another embodiment of the present invention;

FIG. 7A is a perspective view of a flow altering member, according to another embodiment of the present invention;

FIG. 7B is a frontal view of a flow altering member, according to another embodiment of the present invention;

FIG. 7C is a back view of a flow altering member, according to another embodiment of the present invention;

FIG. 7D is a perspective view of a flow altering member, according to another embodiment of the present invention; and

FIG. 8A is a frontal view of a heat exchanger, and illustrates flow patterns of a heat exchange medium inside the cylindrical tubular member and the chamber assemblies, according to embodiments of the present invention.

DETAILED DESCRIPTION

Referring to the drawings and in particular FIG. 1A, an embodiment of a cylindrical tubular member 100 is shown. The cylindrical tubular member 100 has an inlet 5 to introduce a heat exchange medium into the cylindrical tubular member 100, and an outlet 10 to allow the heat exchange medium to flow out of the cylindrical tubular member 100. The cylindrical tubular member 100 has a tubular structure 15. Referring also to FIG. 1D, the exterior surface of the tubular structure 15 has a plurality of chamber assemblies 20 attached to the exterior surface of the tubular structure 15. Referring to FIG. 1C, the tubular structure 15 features a plurality of inlet orifices 30 and outlet orifices 35, to allow heat exchange medium to flow out of the tubular structure 15, and enter a chamber assembly 20, then allow the heat exchange medium to re-enter the tubular structure 15 from the chamber assembly 20 through the outlet orifice 35. Referring to FIG. 1C and FIG. 1D, the inlet orifice 30 and the outlet orifice 35 are formed on the wall of the tubular structure 15, the orifices 30 and 35 going through the entire thickness of the material forming the tubular structure 15. Each inlet orifice 30 is paired with an outlet orifice 35, the outlet orifice 35 is positioned on the side of the tubular structure 15 which is opposite the side on which the paired inlet orifice member 30 is disposed. Referring to FIG. 1D, each pairing of an inlet orifice 30 and an outlet orifice 35 is paired with a flow altering member 25. Flow altering member 25 is coupled to the inner wall of the tubular structure 15. Flow altering regimes, each comprising an inlet orifice member 30, a chamber assembly 20, an outlet orifice 35, and a flow altering member 25, are repeated throughout the length of the tubular structure 15. A plurality of flow altering regimes are disposed throughout the cylindrical tubular member 100. In comparison, referring now to FIG. 1B, a typical prior art tube type heat exchanger has a tubular structure 15a, which is hollow and extends axially in a generally straight line, permitting flow of a heat exchange medium within the tubular structure. The interior and exterior of the tubular structure are generally smooth and contain no through holes. The tubular structure has an inlet 5a to introduce heat exchange medium into the tubular structure 15a and an outlet 10a to allow heat exchange medium to exit the tubular structure 15a. The prior art tubular structure 15a may have surface enhancement features such as fins on the inside as well as on the outside of the tubular structure to enhance heat transfer characteristics.

Referring to FIG. 2A, another embodiment of the present invention is shown. The cylindrical tubular member 100 has an inlet 5 to introduce heat exchange medium into the cylindrical tubular member 100, and an outlet 10 to allow the heat exchange medium to flow out of the cylindrical tubular member 100. The cylindrical tubular member 100 has a tubular structure 15. Referring now to FIG. 2B, the tubular structure 15 has plurality of inlet orifices 30 and outlet orifices 35 formed on the tubular structure 15, the orifices going through the entire thickness of the material forming the tubular structure 15. Each inlet orifice 30 is paired to an outlet orifice 35. Referring to FIG. 2A and FIG. 2C, inserted inside the tubular structure 15 is a plurality of flow altering members 25 attached together by an attachment member 45, creating a single unit of an insert 40 with a plurality of flow altering members 25. The insert 40 is placed within the tubular structure 15, so that each flow altering member is aligned to a pairing of an inlet orifice 30 and an outlet orifice 35. The attachment member 45 of the insert 40 is positioned so that the material forming the attachment member 45 does not obstruct the inlet orifice 30 or the outlet orifice 35 formed on the tubular structure 15.

Referring to FIG. 2A, on the exterior surface of the tubular structure 15, a plurality of chamber assemblies 20 are coupled, each chamber assembly forming a watertight fit with the exterior surface of the tubular structure 15. Referring to FIGS. 2D and 2E, the chamber assembly 20 comprises of a first planar wall 90 and a second planar wall 95, the second planar wall 95 is set apart at a distance from the first planar wall 90, leaving a space between the first planar wall 90 and the second planar wall 95. Interconnecting the first planar wall 90 and the second planar wall 95 is a lateral wall 85. The first planar wall 90, the second planar wall 95, and the lateral wall 85 form a watertight connection, leaving a chamber 50 within the chamber assembly 20. Through the first planar wall 90 and the second planar wall 95, an orifice 55 is formed. The orifice 55 has a size, e.g., a diameter, slightly larger than the size, e.g., the diameter of the exterior dimension of the tubular structure 15, allowing the chamber assembly 20 and a tubular structure to form a tight fit when the tubular structure 15 is inserted inside the orifice 55. A plurality of said chamber assemblies 20 are coupled to the exterior surface of the tubular structure 15, as illustrated in FIG. 2A. Each chamber assembly 20 is positioned so that each chamber assembly 20 is aligned to a pairing of an inlet orifice 30 and an outlet orifice 35 formed in the tubular structure 15. Flow altering regimes, each comprising an inlet orifice member 30, a chamber assembly 20, an outlet orifice member 35, and the flow altering member 25, are repeated throughout the length of the tubular structure 15. Thus, a plurality of flow altering regimes are provided by the cylindrical tubular member 100.

Referring now to FIG. 3A and FIG. 3B, another embodiment of the present invention is shown. In this embodiment, tubular structure 15 is fabricated with a plurality of inlet orifices 30 and outlet orifices 35. Chamber assembly 60 is a unitary unit, having a plurality of chamber units 20 positioned with a predetermined spacing therebetween. The chamber units 20 are connected with each other by a tubular section 70 (See FIG. 3B ad FIG. 3E). A tubular structure 15, with inlet orifices 30 and outlet orifices 35, is shown by itself in FIG. 3C. Inlet orifices 30 and outlet orifices 35 are positioned on the tubular structure 15 so that each inlet orifice 30 is paired with an outlet orifice 35. The positioning of the inlet orifice 30 and outlet orifice 35 on the tubular structure 15 is made so that an outlet orifice 35 is on a side generally opposite to an inlet orifice 30, although the positioning of the outlet orifice 35 may also be offset in some embodiments of the present invention. For each pairing of an inlet orifice 30 and an outlet orifice 35, a flow altering member is positioned, so that the flow of heat exchange medium entering the inlet 5 of the tubular structure 15, encounters the flow altering member 25, a first side 75 of the flow altering member 25 having an angled surface, causing the flow of the heat exchange medium to be led towards the inlet orifice 30. For each flow altering member 25 positioned within the tubular structure 15, the first face 75 of the flow altering member 25 faces the inlet orifice 30 and a second face 80 of the flow altering member 25 faces the outlet orifice 35 (see FIG. 3D in relation to FIG. 3C).

Referring to FIG. 4A, FIG. 4B, and FIG. 4C, an embodiment of a heat exchanger 200 is shown. The heat exchanger 200 includes a pair of manifolds 210 and 230. A plurality of cylindrical tubular members 100 extend in a spaced relation relative to each other between the manifolds 210 and 230. One free end of a cylindrical tubular member 100 is coupled to the first manifold 210. The other free end of the cylindrical tubular member 100 is coupled to the second manifold 230. The first manifold 210 has an inlet 220 to introduce a heat exchange medium in to the heat exchanger 200. The second manifold 230 has an outlet 240 to allow the heat exchange medium to exit the heat exchanger 200. The heat exchange medium introduced into the first manifold 210 may be dispersed to a plurality of cylindrical tubular members 100. The second manifold 230 may receive the heat exchange medium from a plurality of cylindrical tubular members 100. The manifolds 210 and 230 may feature baffles so that the flow pattern may be a simple single directional flow from a first manifold to a second manifold, or a more complex multiple flow pattern, wherein multiple flow patterns exist between the first manifold and the second manifold.

In another embodiment of the present invention, referring to FIG. 4D and FIG. 4E, the heat exchanger 300 includes a pair of manifolds 210 and 230. A plurality of cylindrical tubular members 100 extend between the pair of manifolds 210 and 230. One free end of a cylindrical tubular member 100 is coupled to a first manifold 210. The other free end of the cylindrical tubular member 100 is coupled to a second manifold 230. The space between the pair of manifolds 210 and 230 is fully enclosed in a vessel 350. The vessel provides a water-tight enclosure, having a vessel inlet 310 and a vessel outlet 320, to allow flow of a heat exchange medium in and out of the vessel 350 surrounding the cylindrical tubular members 100. The first manifold 210 has an inlet 220 to introduce a first heat exchange medium into the plurality of cylindrical tubular members 100. The second manifold 230 has an outlet 240 to allow the first heat exchange medium to exit the plurality of cylindrical tubular members 100. The manifolds 210 and 230 may feature baffles within so that the flow pattern may be a simple single direction flow from a first manifold to a second manifold, or more complex multiple flow pattern, wherein multiple flow patterns exist between the first manifold and the second manifold. The second heat exchange medium enters the vessel 350 through the vessel inlet 310. The second heat exchange medium flows around the plurality of cylindrical tubular members 100 positioned within the vessel 350. The second heat exchange medium flows out of the vessel 350 through the vessel outlet 320.

Thus, in embodiments of the present invention, the heat exchanger (e.g. 300), features two heat exchange mediums, one heat exchange medium flowing inside the plurality of cylindrical tubular members 100, and a second heat exchange medium flowing outside the plurality of cylindrical tubular members 100. The first heat exchange medium flowing inside the plurality of cylindrical tubular members 100 may contain heat, transferring heat to the second heat exchange medium flowing outside of the plurality of cylindrical tubular members 100. In another embodiment of the present invention, the heat exchange medium flowing inside the plurality of cylindrical tubular members 100 may absorb heat from the second heat exchange medium flowing outside the plurality of cylindrical tubular members 100.

In another embodiment of the present invention, both an inlet and an outlet can be positioned on a first manifold, with a second manifold facilitating the return of heat exchange medium towards the first manifold. Referring to FIG. 4F, the heat exchanger 355 includes a pair of manifolds 215 and 235. A plurality of cylindrical tubular members 100 (as in FIG. 4C) extend in a spaced relation between the pair of manifolds 215 and 235. One free end of a cylindrical tubular member 100 is coupled to the first manifold 215. The other free end of the cylindrical tubular member 100 is coupled to the second manifold 235. The first manifold 215 has an inlet 220 to introduce heat exchange medium in to the heat exchanger 355 and an outlet 245 to allow the heat exchange medium to exit the heat exchanger 355. The first manifold 215 has a partition within to segregate a portion of the plurality of cylindrical tubular members 100 into at least two groups. One portion of the plurality of cylindrical tubular members 100 functions to allow flow of the heat exchange medium from the first manifold 215 to the second manifold 235, and the rest of the plurality of cylindrical tubular members 100 functions to allow flow of the heat exchange medium from the second manifold 235 to the first manifold 215. The second manifold 235 receives the heat exchange medium from the first manifold 215, through the plurality of cylindrical tubular members 100 in the first partition of the first manifold 215. Once the second manifold receives the heat exchange medium, the heat exchange medium is returned to the first manifold 215 through the plurality of cylindrical tubular members in the second partition of the first manifold 215. The inlet 220 is connected to the first partition of the first manifold 215, and the outlet 245 is connected to the second partition of the first manifold 215.

Referring to FIG. 3A, a flow pattern for the heat exchange medium within the cylindrical tubular member 100 is shown. One free end of the cylindrical tubular member 100 is an inlet 5. The other free end of the cylindrical tubular member 100 is an outlet 10. A heat exchange medium enters the cylindrical tubular member through the inlet 5 flows in a first line of flow, generally flowing parallel to the tubular structure 15. The heat exchange medium flowing in the first line of flow encounters a flow altering member 25. A plurality of flow altering members 25 are preferably positioned at a predetermined spacing within the tubular structure 15. Referring to FIG. 3A, FIG. 3D, FIG. 5A, and FIG. 5D, the flow altering member 25 features an angled surface 75 on the surface that faces toward the inlet of the cylindrical tubular member 100, allowing the heat exchange medium flowing in the first line of flow to be directed to a second line of flow within the tubular structure 15. Referring to FIGS. 5A and 5C, the external circumference of the flow altering member 25 is generally contoured to match the inner circumference of the tubular structure 15. The heat exchange medium directed in the second line of flow by the flow altering member 25, flows towards the inlet orifice 30 on the tubular structure 15. Once the heat exchange medium reaches the inlet orifice 30, the heat exchange medium exits the tubular structure 15 and enters the chamber assembly 20. Within the chamber assembly 20, the heat exchange medium flows within the chamber assembly, following the inner contour of the chamber assembly, which is hollow to facilitate flow of the heat exchange medium within. Although not meant to be limiting, the chamber assembly 20 has a cylindrical shape, the diameter of the chamber assembly being larger than the diameter of the tubular structure 15. The axial span of the chamber assembly 20 is substantially shorter than the axial span of the tubular structure 15, allowing a plurality of chamber assemblies 20 to be coupled to the tubular structure 15. The heat exchange medium flowing within a chamber assembly 20 flows in at least one semi-circular flow pattern. The heat exchange medium flowing within the chamber assembly re-enters the tubular structure 15 through the outlet orifice 35 formed on the wall forming the tubular structure 15. Once the heat exchange medium re-enters the tubular structure 15, the heat exchange medium encounters the flow altering member 25. Referring to FIG. 5D, the flow altering member has an angled surface 80 on the side of the flow altering member facing the outlet 10, which generally restores the first directional flow of the heat exchange medium within the tubular structure 15. The process repeats itself until the heat exchange medium introduced into the cylindrical tubular member 100 from the inlet 5 exits through the outlet 10 of said cylindrical tubular member 100.

Now referring to FIGS. 5E and 5F, another embodiment of a flow altering member is shown. In an embodiment of a flow altering member presented in FIG. 5E and FIG. 5F, a plurality of flow altering features may be formed from a single piece of material, or a plurality of flow altering members may be coupled together to form a singular unit with a plurality of flow altering features, shown as a flow altering member 40 in FIG. 5E. Along the lateral span of the flow altering member 40, a plurality of flow altering surfaces 75 are featured. The flow altering surfaces 75 facing the inlet 5 of the tube assembly 15 feature an angled surface, and direct the heat exchange medium flowing in the first line of flow within the tube assembly 15 to change course and flow in a second line of flow, directing the heat exchange medium into the chamber assembly 20 through the inlet orifice 30. The flow altering member 40 also features a plurality of flow altering surfaces 80, the flow altering surfaces 80 facing the outlet 10 of the tube assembly 15. The surface of the flow altering surfaces 80 is set at an angle in relation to the outlet 10 of the tube assembly 15. The flow altering surfaces 80 direct the flow of the heat exchange medium exiting the chamber assembly 20 and entering the tube assembly 15 through the outlet orifice 35, to flow in the first line of flow. The flow altering member 40 features connecting members 45 forming the lateral wall of the flow altering member 40. The general exterior contour of the connecting members 45 conforms to the inner contour of the tube assembly 15, coupling the exterior surface of the flow altering member 40 to the inner surface of the tubular member 15.

Now referring to FIG. 6A, FIG. 6B, and FIG. 6E, another embodiment of the present invention is shown, wherein such embodiment employs a cylindrical tubular member 105 which includes a tubular structure 110 and pairs of chamber assemblies 125, 126. Referring to FIG. 6E in particular, a tubular structure 110 forms a structural foundation of a heat exchanger, with a plurality of inlet orifices and outlet orifices formed on the tubular structure 110. Referring to FIG. 7A, positioned at predetermined intervals within the tubular structure 110 are a plurality of flow altering members 150. On the exterior of the tubular structure, a plurality of chamber assemblies 125 and 126 are coupled to the exterior surface of the tubular structure 110. Referring to FIG. 6C and FIG. 7A, a flow altering member 150 has a channel on a plane of the flow altering member surface facing the inlet 115 of the tubular structure 110, with an angled planar surface 170 facing the inlet 115 of the tubular structure 110. The channel on the flow altering member 150 comprises a first lateral wall 155 defining a first wall of a channel, a second lateral wall 160 defining a second wall of a channel, and a base wall 165 defining a base of the channel. Each flow altering member 150 is paired with a plurality of inlet orifices 130 and 135. Referring to FIG. 6B, FIG. 6C, and FIG. 8A, each inlet orifice 130 is paired with a chamber assembly 125. A chamber assembly 125 is coupled to the exterior surface of the tubular structure 110, the chamber assembly being hollow, permitting fluid flow within.

The heat exchange medium flowing in the tubular structure 110 initially flows in a first line of flow. As the heat exchange medium travels within the tubular structure 110, the heat exchange medium comes into contact with a flow altering member 150. As the heat exchange medium contacts the flow altering member 150, the flow of the heat exchange medium is directed towards a second line of flow, the directional change being dictated by the angled planar surface 170 of the flow altering member 150, and by the channel formed by the first lateral wall 155, the second lateral wall 160, and the base wall 165 of the flow altering member 150. The heat exchange medium directed in the second line of flow is then led out of the tubular structure 110 into a chamber assembly 125. Referring to FIG. 8A, a portion of the heat exchange medium is directed into the inlet orifice 130 and flows into a first chamber assembly 125, more specifically into a semi-cylindrical chamber 180. Another portion of the heat exchange medium is directed into the inlet orifice 135 and flows into a second chamber assembly 126, more specifically into a semi-cylindrical chamber 182. The flow of heat exchange medium within the respective chamber assemblies 125, 126 is dictated by the inner contour of the chamber assemblies, generally following a semi-circular flow pattern dictated by the respective semi-cylindrical chambers 180, 182. The heat exchange medium flowing in the first chamber assembly 125 is directed towards the outlet orifice 140. Upon reaching the outlet orifice 140, the heat exchange medium travelling within the first chamber assembly 125 exits the chamber assembly 125, and re-enters the tubular structure 110. The heat exchange medium flowing in the second chamber assembly 126 is directed towards the outlet orifice 145. Upon reaching the outlet orifice 145, the heat exchange medium travelling within the second chamber assembly 126 exits the chamber assembly 126, and re-enters the tubular structure 110. The heat exchange medium that has travelled within the first chamber assembly 125 and the second chamber assembly 126 converge within the tubular structure 110. Referring to FIG. 7C, the heat exchange medium that has re-entered the tubular structure 110 comes in contact with the flow altering member 150, affecting the directional flow of the heat exchange medium. The flow altering member 150 has an angled planar surface 185 facing the outlet 120 of the tubular structure 110. The plane of the surface facing the outlet 120 of the tubular structure has a channel defined by a first lateral wall 190, a second lateral wall 195, and a base wall 205 as shown in FIG. 7C. As the heat exchange medium exits the first chamber assembly 125 and the second chamber assembly 126 through the outlet orifices 140 and 145, respectively, the heat exchange medium comes into contact with the angled planar surface 185 of the flow altering member 150. As the heat exchange medium comes into contact with the angled surface 185 of the flow altering member 150, the directional flow is restored generally to that of the first line of flow. This process repeats itself within the tubular structure 110, until the heat exchange medium exits the tubular structure 110 through the outlet 120.

Referring to FIG. 7A, a plurality of flow altering members 150 may be arranged within the tubular structure 110, preferably at predetermined intervals. Now referring to FIG. 7D, in another embodiment of the present invention, plural flow altering members 150 may be coupled together forming a unitary unit. In this embodiment, a first lateral wall 155 and a second lateral wall 160 of a second flow altering member 150 engage a first lateral wall 190 and second lateral wall 195 of a first flow altering member. In this embodiment, individual flow altering members 150 may be coupled together, or a unitary unit with multiple flow altering features may be formed from a single piece of material, or any combination in between.

Throughout the transport of the heat exchange medium through the cylindrical tubular member 100, 105, the heat contained within the heat exchange medium is transferred to the material comprising the cylindrical tubular member 100, 105. The heat absorbed by the cylindrical tubular member 100, 105 is then transferred to the environment outside of the cylindrical tubular member 100, 105. Although not meant to be limiting, common heat exchange medium known in the art includes various refrigerants (i.e.; R-134A, R-410A), ammonium, gases, water, oils, and various mixtures of chemicals.

As previously explained, a first heat exchange medium may flow within the cylindrical tubular member 100, 105 and a second heat exchange medium may flow on the outside of the cylindrical tubular member 100, 105. The first heat exchange medium may be a heat exchange medium known in the art, such as various refrigerants (i.e.; R-134A, R-410A), ammonium, gases, water, oils, and various mixtures of chemicals. The second heat exchange medium may also be various refrigerants (i.e.; R-134A, R-410A), ammonium, gases, water, oils, and various mixtures of chemicals. When more than one heat exchange medium is utilized, heat from the first heat exchange medium may be absorbed by the second heat exchange medium, or vice versa.

Referring to FIG. 1C and FIG. 6E, the tubular structure 15, 110 in the illustrated embodiments is hollow and circular. In other embodiments, the tubular structure may be hollow but non-circular, such as an oval, rectangular shape, or other geometric shapes.

Referring to FIG. 2E, in the illustrated embodiment, the chamber assembly 20 is hollow and cylindrical in shape. In other embodiments, the chamber assembly 20 may be hollow, but non-cylindrical in shape, such as an oval cylinders or a box shape, for example.

The tubular structure 15, 110 and chamber assembly 20, 125, 126 may be made of aluminum, either with cladding or without cladding. The tubular structure and chamber assembly may also be made of stainless steel, copper, or other ferrous or non-ferrous material. The tubular structure and chamber assembly may also be a plastic material or other composite materials. Likewise, the flow altering member may also be made of aluminum, either with cladding or without cladding. The flow altering member may also be made of stainless steel, copper or other ferrous or non-ferrous materials. The flow altering member may also be a plastic material or other composite materials. Also, an embodiment of the present invention allows for the tubular structure and chamber assembly to be made of different material from each other. Additionally, a gasket material may be used to seal between the tubular structure and the chamber assembly.

The tubular structure may be made of seamless tube, utilizing an extrusion process. The tubular structure may also be made of a seamed tube, utilizing ultrasonic welding, roll-forming process, or other mechanical means or casting methods.

Many modifications and variations of the present invention are possible in light of the above teachings. For example, the various embodiments of the flow altering members may be used in conjunction with tubular structures other than in the combinations described above and illustrated in the drawings Therefore, within the scope of the appended claims, the present invention may be practiced other than as specifically described.

Claims

1. A heat exchanger having at least one cylindrical tubular member, the cylindrical tubular member including:

a tubular structure with an inlet at one end and an outlet at the other end and having a plurality of inlet orifices and outlet orifices, the plurality of inlet and outlet orifices being spaced along respective sides of the tubular structure such that for each inlet orifice there is a paired outlet orifice disposed on the generally opposite side of the tubular structure;

a plurality of generally semi-cylindrical chamber assemblies attached to the exterior surface of the tubular structure, each chamber assembly having first and second generally planar walls, the first and second generally planar walls surrounding a portion of the tubular structure to at least partially define a generally semi-cylindrical chamber external to and partially surrounding the tubular structure, a first set of chamber assemblies being positioned on the tubular structure such that each of its respective chambers is in fluid communication with a corresponding inlet and outlet orifice pair and a second set of chamber assemblies being positioned on the tubular structure such that each of its respective chambers is in fluid communication with a corresponding inlet and outlet orifice pair, the chamber assemblies in the first and second sets being spaced along the tubular structure such that for each chamber assembly in the first set, there is an associated chamber assembly in the second set which is disposed on the generally opposite side of the tubular structure; and

a plurality of flow altering members disposed within the tubular structure, each flow altering member having a first side which has an angled surface facing two corresponding inlet orifices and a second side which has an angled surface facing the two outlet orifices respectively paired with the two corresponding inlet orifices.

2. The heat exchanger according to claim 1, wherein each chamber assembly further includes a lateral wall joining the first planar wall to the second planar wall to further define the respective generally semi-cylindrical chamber.

3. The heat exchanger according to claim 1, further including tubular sections which surround the tubular structure between consecutive chamber assemblies to interconnect the consecutive chamber assemblies.

4. The heat exchanger according to claim 1, further including attachment members which interconnect adjacent flow altering members.

5. The heat exchanger according to claim 1, wherein each flow altering member has a first lateral wall and a second lateral wall which together with the first side of the flow altering member define a first channel disposed in fluid communication with the corresponding inlet orifices.

6. The heat exchanger according to claim 5, wherein each flow altering member has a third lateral wall and a fourth lateral wall which together with the second side of the flow altering member define a second channel disposed in fluid communication with the corresponding outlet orifices.

7. The heat exchanger according to claim 6, wherein the first lateral wall of a first flow altering member engages the third lateral wall of an adjacent flow altering member, and the second lateral wall of the first flow altering member engages the fourth lateral wall of the adjacent flow altering member to maintain a spaced relation between the adjacent flow altering members.

8. The heat exchanger according to claim 7, wherein each flow altering member includes a first base wall and a second base wall, the first base wall being disposed between the first lateral wall and the second lateral wall to further define the first channel, and the second base wall being disposed between the third lateral wall and the fourth lateral wall to further define the second channel.

9. The heat exchanger according to claim 1, including a plurality of the cylindrical tubular members disposed between a first manifold and a second manifold, with the inlet of each tubular structure being in fluid communication with either the first manifold or the second manifold, and the outlet of each tubular structure being in fluid communication with either the first manifold or the second manifold.

10. The heat exchanger according to claim 9, wherein the first manifold and the second manifold are joined by a vessel in which the plurality of cylindrical tubular members are disposed.

11. A heat exchanger having at least one cylindrical tubular member, the cylindrical tubular member including:

a tubular structure with an inlet at one end and an outlet at the other end and having a plurality of inlet orifices and outlet orifices, the plurality of inlet and outlet orifices being spaced along respective sides of the tubular structure such that for each inlet orifice there is a paired outlet orifice disposed on the generally opposite side of the tubular structure;

a plurality of generally semi-cylindrical chamber assemblies attached to the exterior surface of the tubular structure, each chamber assembly having first and second generally planar walls, the first and second generally planar walls surrounding a portion of the tubular structure to at least partially define a generally semi-cylindrical chamber external to and partially surrounding the tubular structure, each chamber assembly being positioned on the tubular structure such that its chamber is in fluid communication with a corresponding inlet and outlet orifice pair; and

a plurality of flow altering members disposed within the tubular structure, each flow altering member having a first side which has an angled surface facing a corresponding inlet orifice and a second side which has an angled surface facing the outlet orifice respectively paired with the corresponding inlet orifice.

12. The heat exchanger according to claim 11, wherein each chamber assembly further includes a lateral wall joining the first planar wall to the second planar wall to further define the respective generally semi-cylindrical chamber.

13. The heat exchanger according to claim 11, further including tubular sections which surround the tubular structure between adjacent chamber assemblies to interconnect the adjacent chamber assemblies.

14. The heat exchanger according to claim 11, further including attachment members which interconnect adjacent flow altering members.

15. The heat exchanger according to claim 11, wherein each flow altering member has a first lateral wall and a second lateral wall which together with the first side of the flow altering member define a first channel disposed in fluid communication with the corresponding inlet orifice.

16. The heat exchanger according to claim 15, wherein each flow altering member has a third lateral wall and a fourth lateral wall which together with the second side of the flow altering member define a second channel disposed in fluid communication with the corresponding outlet orifice.

17. The heat exchanger according to claim 16, wherein the first lateral wall of a first flow altering member engages the third lateral wall of an adjacent flow altering member, and the second lateral wall of the first flow altering member engages the fourth lateral wall of the adjacent flow altering member to maintain a spaced relation between the adjacent flow altering members.

18. The heat exchanger according to claim 17, wherein each flow altering member includes a first base wall and a second base wall, the first base wall being disposed between the first lateral wall and the second lateral wall to further define the first channel, and the second base wall being disposed between the third lateral wall and the fourth lateral wall to further define the second channel.

19. The heat exchanger according to claim 11, including a plurality of the cylindrical tubular members disposed between a first manifold and a second manifold, with the inlet of each tubular structure being in fluid communication with either the first manifold or the second manifold, and the outlet of each tubular structure being in fluid communication with either the first manifold or the second manifold.

20. The heat exchanger according to claim 19, wherein the first manifold and the second manifold are joined by a vessel in which the plurality of cylindrical tubular members are disposed.