WO2009100007A2

WO2009100007A2 - Energy transfer tube apparatus, systems, and methods

Info

Publication number: WO2009100007A2
Application number: PCT/US2009/032842
Authority: WO
Inventors: Shaun E. Sullivan
Original assignee: Greencentaire, Llc
Priority date: 2008-02-09
Filing date: 2009-02-02
Publication date: 2009-08-13
Also published as: WO2009100007A3; US20090200005A1

Abstract

The invention provides an energy transfer tube apparatus in which rotating inner and outer fluid flows are established. The invention also provides systems and methods involving at least one energy transfer tube apparatus of this nature.

Description

ENERGY TRANSFER TUBE APPARATUS, SYSTEMS, AND

METHODS FIELD OF THE INVENTION

The present invention relates to an energy transfer tube apparatus. More specifically, the invention relates to an energy transfer tube apparatus in which rotating inner and outer fluid flows are established. The invention also relates to systems and methods involving at least one energy transfer tube apparatus of this nature.

BACKGROUND OF THE INVENTION

Vapor-compression systems are useful in a wide variety of applications. In a typical system, a working fluid (such as Freon) enters a compressor as a vapor. The vapor is compressed at constant entropy and exits the compressor superheated. The superheated vapor then travels through a condenser. The condenser cools and removes the superheat, and condenses the vapor into a liquid by removing more heat at constant pressure and temperature. The liquid then goes through an expansion valve or orifice. Here, the pressure of the working fluid decreases rapidly. This causes a flash evaporation, e.g., of perhaps less than half the liquid. The result is a mixture of liquid and vapor at a lower temperature and pressure. Next, this cold liquid-vapor mixture travels through the evaporator and is vaporized by warm air (e.g., from a space being refrigerated) that is blown by a fan across the evaporator coil or tubes. The resulting vapor then returns to the compressor inlet to finish the cycle.

It would be desirable to provide an energy transfer tube apparatus that can be used for, among other things, improving and/or expanding the capabilities and practical applications of vapor-compression systems. It would also be desirable to provide a vapor-compression system having as a component at least one such energy transfer tube apparatus.

SUMMARY OF THE INVENTION

In certain embodiments, the invention provides an energy transfer tube apparatus comprising an energy transfer tube having opposed first and second end regions. In the present embodiments, the apparatus is provided with first and second inlets (optionally tangential inlets) adjacent to the tube's first end region. Preferably, the first inlet is closer to the tube's second end region than is the second inlet. In the present embodiments, a flow separator is provided adjacent to the tube's second end region. The flow separator bounds separate inner and outer flow pathways. The inner pathway is adapted to receive a rotating inner flow of cold fluid, and the outer pathway is adapted to receive a rotating outer flow of hot fluid. Preferably, the inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow is then adapted to be delivered out of the energy transfer tube apparatus. Some embodiments of the invention provide a method of using an energy transfer tube apparatus. In the present method, the apparatus involved comprises an energy transfer tube with opposed first and second end regions. Preferably, the apparatus is provided with first and second inlets (optionally tangential inlets) adjacent to the tube's first end region. The first inlet is closer to the tube's second end region than is the second inlet. Preferably, a flow separator is provided adjacent to the tube's second end region. The flow separator bounds separate inner and outer flow pathways. The inner pathway is adapted to receive a rotating inner flow of fluid, and the outer pathway is adapted to receive a rotating outer flow of fluid. Preferably, the inner and outer pathways ultimately merge. The present method comprises delivering a flow comprising vapor (optionally a predominantly vapor flow) of working fluid through the first inlet of the apparatus so as to create the rotating outer flow, and delivering a flow comprising liquid (optionally a predominantly liquid flow) of working fluid through the second inlet of the apparatus so as to create the rotating inner flow. The inner and outer flows both move through the energy transfer tube before being separated by the flow separator such that the outer flow travels along the outer pathway while the inner flow travels along the inner pathway until reaching a location where the inner and outer pathways ultimately merge so as to combine the inner and outer flows.

In some embodiments, the invention provides a system in which a working fluid is adapted to be circulated so as to flow from a compressor or pump to an energy transfer tube apparatus, then from the energy transfer tube apparatus to an evaporator, then from the evaporator to the compressor or pump. Preferably, the energy transfer tube apparatus comprises an energy transfer tube having opposed first and second end regions. The apparatus is provided with first and second inlets (optionally tangential inlets) adjacent to the tube's first end region. The first inlet is closer to the tube's second end region than is the second inlet. Preferably, a flow separator is provided adjacent to the tube's second end region. The flow separator bounds separate inner and outer flow pathways. The inner pathway is adapted to receive a rotating inner flow of cold fluid, and the outer pathway is adapted to receive a rotating outer flow of hot fluid. Preferably, the inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow is then adapted to be delivered out of the energy transfer tube apparatus. Certain embodiments of the invention provide a system in which a working fluid is adapted to be circulated so as to flow from a compressor or pump to an energy transfer tube apparatus, then from the energy transfer tube apparatus to a heat sink structure in thermal communication with a central processing unit, then from the heat sink structure to said compressor or pump. In the present embodiments, the energy transfer tube apparatus comprises an energy transfer tube having opposed first and second end regions. Preferably, the apparatus is provided with first and second inlets adjacent to the tube's first end region. The first inlet is closer to the tube's second end region than is the second inlet. Preferably, a flow separator is provided adjacent to the tube's second end region. The flow separator bounds separate inner and outer flow pathways. The inner pathway is adapted to receive a rotating inner flow of cold fluid, and the outer pathway is adapted to receive a rotating outer flow of hot fluid. In some of the present embodiments, the inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow is then adapted to be delivered out of the energy transfer tube apparatus.

BRIEF DESCRIPTION OF THE DRAWINGS

Figure IA is a schematic longitudinal sectional view of an energy transfer tube apparatus in accordance with certain embodiments of the invention.

Figure IB is a schematic cross sectional view of the energy transfer tube shown in Figure IA along the line A-A.

Figure 2 is a perspective view of another energy transfer tube apparatus in accordance with certain embodiments of the invention. Figure 3 is a longitudinal sectional view of the energy transfer tube apparatus shown in Figure 2.

Figure 4A is a view of an intake manifold shown in accordance with certain embodiments of the invention.

Figure 4B is a perspective view of an intake manifold shown in accordance with certain embodiments of the invention.

Figure 5 is a sectional perspective view of an intake manifold and flow generator in accordance with certain embodiments of the invention. Figure 6 A is a perspective view of a flow generator in accordance with certain embodiments of the invention.

Figure 6B is a sectional view of the flow generator shown in Figure 6 A.

Figure 7 A is a cross sectional view of an intake manifold and flow generator in accordance with certain embodiments of the invention.

Figure 7B is another cross sectional view of the intake manifold and flow generator shown in Figure 7A.

Figure 8 A is a perspective view of another flow generator in accordance with certain embodiments of the invention. Figure 8 B is a sectional view of the flow generator shown in Figure 8 A.

Figure 9 A is a cross sectional view of an intake manifold and flow generator in accordance with certain embodiments of the invention.

Figure 9B is another cross sectional view of the intake manifold and flow generator shown in Figure 9A. Figure 10 is a perspective, sectional view a flow separator and cooling jacket in accordance with certain embodiments of the invention.

Figure 1 IA is a perspective view of a flow separator in accordance with certain embodiments of the invention.

Figure 1 IB is a side elevation view of the flow separator shown in Figure 1 IA. Figure 11C is a sectional view of the flow separator shown in Figure 1 IA.

Figure 12 shows a system in accordance with certain embodiments of the invention.

Figure 13 shows another system in accordance with certain embodiments of the invention. Figure 14 shows still another system in accordance with certain embodiments of the invention.

Figure 15 shows yet another system in accordance with certain embodiments of the invention.

Figure 16 is an exploded view of a vapor/liquid separator in accordance with certain embodiments of the invention.

Figure 17A is an end view of the vapor/liquid separator of Figure 16.

Figure 17B is a cross-sectional view of the vapor/liquid separator of Figure 17A, taken along lines A-A.

Figure 17C is a front side view of the vapor/liquid separator of Figure 17A. Figure 17D is a rear side perspective view of the vapor/liquid separator of Figure 17 A.

Figure 18 shows a system in accordance with certain embodiments of the invention. Figure 19 shows another system in accordance with certain embodiments of the invention.

Figure 20 is an exploded side view of an energy transfer tube apparatus in accordance with certain embodiments of the invention.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS The following detailed description is to be read with reference to the drawings, in which like elements in different drawings have like reference numbers. The drawings, which are not necessarily to scale, depict selected embodiments and are not intended to limit the scope of the invention. Skilled artisans will recognize that the given examples have many alternatives that fall within the scope of the invention. Figure IA schematically illustrates a longitudinal section of an energy transfer tube apparatus 100 in accordance with certain embodiments of the invention. Briefly, the apparatus 100 comprises an energy transfer tube 102 with a first end region 104 and a second end region 106. Adjacent to the first end region 104, there is provided an intake manifold 105 having a first inlet 107 and a second inlet 108. (In some embodiments, the intake manifold may be integral to the energy transfer tube.) A flow generator 110 is provided adjacent to the tube's first end region 104. (In some cases, the flow generator may be integral to the energy transfer tube and/or the intake manifold.) A flow separator 112 is provided adjacent to the tube's second end region 106. In embodiments like that shown in Figure IA, the flow separator 112 is surrounded by a cooling jacket 114, although this is not strictly required. (The flow separator in some embodiments may be integral to the cooling jacket. Further, in some cases the flow separator and the cooling jacket may be integral to the energy transfer tube. Many variants of this nature are possible.)

With continued reference to the embodiment of Figure IA, the energy transfer tube apparatus 100 receives a first pressurized fluid flow through the first inlet 107. This flow is directed into a first inlet chamber 132, then through one or more passages 144 in the flow generator 110, and into a first flow chamber 116, which in the illustrated embodiment is defined by the generator 110. In this way, the generator 110 creates a rotating outer flow 118, which travels through the energy transfer tube 102 (e.g., from left to right as seen in Figure IA). The second inlet 108 delivers a second pressurized fluid flow into a second inlet chamber 133, then through one or more passages 146 in the flow generator 110, and into a second flow chamber 120, which in the illustrated embodiments is also defined by the generator 110. In this manner, the generator 110 also creates a rotating inner flow 122, which travels through the energy transfer tube 102.

Preferably, the rotating inner flow 122 is located radially within (e.g., is surrounded by) the rotating outer flow 118. For example, the rotating inner flow 122 may travel substantially along the axis AX of the tube 102. As shown in Figure IB (which is a cross-section of the tube 102 looking towards the second end region 106 along the line A-A shown in Figure IA), the outer and inner flows 118, 122 may both rotate in the same direction (e.g., clockwise in the embodiment of Figure IB) as they move towards the tube's second end region 106. However, this orientation is merely exemplary — the inner and outer flows can alternatively both rotate counter-clockwise. For some applications, it may even be possible to have the inner flow rotate counterclockwise while the outer flow rotates clockwise, or vice versa.

With continued reference to Figure IA, as the inner and outer flows move through the energy transfer tube 102, energy is transferred from the inner flow 122 to the outer flow 118, thus making the inner flow 122 relatively cold while the outer flow becomes relatively hot. Preferably, the inner flow 122 becomes increasingly cold as it moves towards the second end region 106 of the tube 102, and the outer flow 118 becomes increasingly hot as it moves towards the tube's second end region. Near the second end region 106 of the illustrated tube 102, a flow separator 112 separates the outer and inner flows. Here, the cold inner flow 122 is channeled along an inner pathway 124, and the hot outer flow 118 is diverted along an outer pathway 126. In embodiments like that shown in Figure IA, a cooling jacket 114 (or another heat exchanger) is adapted to transfer heat from the outer flow 118 to a surrounding medium (optionally via heat transfer fins 128 or another high surface area mechanism). After being cooled in this manner, the rotating outer flow 118 is combined with the inner flow 122, and the resulting combined flow is then delivered out of the energy transfer tube apparatus 100.

In the illustrated embodiments, the energy transfer tube apparatus 100 has a single outlet. If desired, it would be possible to divide the output from the energy transfer tube apparatus so as to provide multiple outflows. In general, the fluid delivered into the apparatus 100 through the first and second inlets 107, 108 can be vapor, liquid, or a liquid- vapor mixture. As described below, a liquid- vapor separator can be used to supply a predominantly vapor flow to the first inlet 107, while supplying a predominantly liquid flow to the second inlet 108. Thus, in some cases, the rotating outer flow 118 originating in the first flow chamber 116 is predominantly vapor, while the rotating inner flow originating in the second flow chamber 120 is predominantly liquid. During operation, the inner flow 122 preferably travels along the axis AX of the energy transfer tube (e.g., while being located radially inwardly of the outer flow). The inner flow, for example, may be a cold, dense rotating liquid flow that travels generally on the axis of the energy transfer tube. Due to the tight rotation of such a flow, it may be considered to wobble as it flows axially through the tube. In some embodiments, a vacuum zone may exist in a location radially between the inner flow 122 and the outer flow 118. In some embodiments where an aqueous solution working fluid is used, at least some of the water leaves the energy transfer tube 102 in the form OfH₃O.

Referring to Figures 2, 3, and 20, respective perspective, sectional, and exploded views are shown of an exemplary energy transfer tube apparatus 100. Here again, the illustrated apparatus 100 comprises an energy transfer tube 102 with an intake manifold 105 having a first inlet 107 and a second inlet 108. The illustrated inlets are tangential inlets, although this is not strictly required. The first inlet 107 is closer to the tube's second end region 106 than is the second inlet 108. Although the figures show a single first inlet and a single second inlet, the apparatus 100 can alternatively have multiple first inlets, multiple second inlets, or both.

In the embodiment of Figure 3, the flow separator 112 is adjacent to the tube's second end region 106. Preferably, the flow separator 112 bounds (e.g., surrounds or otherwise defines) the inner flow pathway 124. In the illustrated embodiment, the flow separator 112 also bounds the outer flow pathway 126. In more detail, the illustrated flow separator 112 defines the outer flow pathway 126 in cooperation with the cooling jacket 114. Once the rotating outer flow 118 has been mechanically separated from the rotating inner flow 122, the outer flow travels along the outer pathway and in the process transfers heat to the cooling jacket 114. The rotation of the hot outer flow 118 is believed to be advantageous in providing a high rate of heat transfer (e.g., via the cooling jacket to a surrounding medium) from the outer flow as it travels along the outer pathway. Preferably, the flow generator 110 comprises first and second walls 130, 131, respectively bounding the first and second fluid flow chambers 116, 120. In the illustrated embodiments, the first and second walls 130, 131 also bound, respectively, a first inlet chamber 132 (which is in fluid communication with the first inlet 107) and a second inlet chamber 133 (which is in fluid communication with the second inlet 108). The first 130 and second 131 walls of the flow generator 110 here each have a generally cylindrical configuration, although this is not strictly required.

In the embodiment of Figures 2 and 3, the energy transfer tube 102 is a cylindrical tube that bounds an energy transfer chamber 134 comprising a generally cylindrical interior space. In one practical embodiment, the energy transfer tube has an inner diameter of about 7/16 inch. The length of the tube may be, for example, about 4 ³A inches. These dimensions, however, are not limiting — they are merely examples. For example, smaller diameters are anticipated. Moreover, larger diameters may be preferred for some applications. In addition, the tube 102 can be provided in many different forms. For example, it is not strictly required to be circular in cross section. In certain alternate embodiments, it may be possible to use an elongated block formed with appropriate interior bores (including an elongated cylindrical bore).

The energy transfer tube 102 can be formed of many different materials. In one exemplary embodiment, the tube comprises stainless steel (such as AISI 304), although brass, copper, aluminum, and other metals may be used. Various non-metals may also be used. The invention is not limited to any particular material.

Figures 4A and 4B provide additional views of the exemplary intake manifold 105 shown in Figure 2. Here, the intake manifold 105 comprises a generally cylindrical housing 138 bounding an interior space (or "chamber") 140, which preferably is at least generally or substantially cylindrical. The chamber 140 is open at one end, and closed at another end by an end wall 141 of the manifold 105. The first and second inlets 107, 108 can be formed integrally with (or coupled to) the manifold housing 138. As is perhaps best shown in Figure 4A, the illustrated inlets 107, 108 meet the manifold housing (and open into chamber 140) at an angle A (e.g., an oblique angle) relative to a plane perpendicular to a central axis CA of the interior chamber 140 (and/or relative to tube axis AX). One or both of the first and second inlets, for example, may angle away from the open end of the manifold, preferably at an angle A of at least about one degree, such as about 7 degrees. This incline is adapted to impart a forward (towards the second end region 106 of the tube 102) component of velocity to the fluid flowing out of the inlets. Of course, different angles A are possible depending upon the application.

Figure 5 is a sectional view of the intake manifold 105, flow generator 110, and energy transfer tube 102 of Figure 3. When the illustrated apparatus 100 is operatively assembled, the flow generator 110 is located within (or "housed by") the intake manifold 105 (e.g., the flow generator 110 can be disposed in the manifold's interior chamber 140). In Figures 3 and 5, the interior of the manifold 105 and the first wall 130 of the flow generator 110 together bound a first annular inlet chamber 132. This inlet chamber 132 is in fluid communication with the first inlet 107. A second annular inlet chamber 133 is bounded by the second wall 131 of the generator together with the interior of the manifold 105. This inlet chamber 133 is in fluid communication with the second inlet 108. In the illustrated embodiment, the first annular inlet chamber 132 is partially defined by an annular recess (or "channel") 143 extending about the interior of the manifold 105. In the embodiment of Figure 5, the flow generator 110 includes a flange 142 that separates the first and second inlet chambers 132, 133. The inlet chambers can alternatively be separated and/or defined by other structural means. For example, the illustrated flange could extend inwardly from the intake manifold 105, rather than being part of the flow generator. Many other configurations can be used as well.

The illustrated manifold 105 is adapted to deliver pressurized fluid into the first and second inlet chambers 132, 133 (e.g., via the first and second inlets 107, 108). As fluid in the first inlet chamber 132 flows around the generator's first wall 130, the fluid enters one or more passages 144 in the generator's first wall 130. The passage(s) 144 lead to the first flow chamber 116. The configuration of the passage(s) 144 is such that fluid delivered into the first flow chamber 116 rotates around the interior periphery of this chamber 116, creating the rotating outer flow 118, which then moves through the energy transfer tube 102. As fluid in the second inlet chamber 133 flows around the generator's second wall 131, the fluid enters one or more passages 146 in the second wall 131. The passage(s) 146 lead to the second flow chamber 120. The configuration of the passage(s) 146 is such that fluid delivered into the second flow chamber 120 rotates around the interior periphery of that chamber 120, creating the rotating inner flow, which then moves through the second flow chamber 120 and into the energy transfer tube 102.

In some embodiments, the passages 144, 146 are adapted to impart a forward (towards the second end region 106 of the tube 102) component of velocity to fluid flowing into the chambers 116, 120. Thus, one or more (optionally all) of the passages 144, 146 may be configured so as to be (e.g., may extend along an axis that is) oblique to a plane perpendicular to an axis of the generator (and/or to tube axis AX). The angular offset from such a plane preferably is a positive angle, such as about 1 degree or more. In certain embodiments, the intake manifold 105 and the energy transfer tube 102 are coupled via matching male and female threading. In such cases, the flow generator 110 can be placed inside the manifold 105 and then secured in place by threading the tube 102 onto the manifold 105. However, the invention is not limited to any particular type of coupling or attachment means. Moreover, the flow generator, intake manifold, and/or energy transfer tube may be formed as integral parts in some cases.

The intake manifold 105 and the flow generator 110 can both be formed of various materials. Examples include brass, stainless steel, and other metals. Various non-metals may also be used. The invention is not limited to using any particular materials for the intake manifold or the flow generator. Turning now to Figures 6 A and 6B, an embodiment of the flow generator 110 is depicted. Preferably, the generator 110 is adapted to create both the rotating outer flow and the rotating inner flow. In the illustrated embodiments, the generator 110 defines part of a first inflow path along which pressurized fluid from the first inlet 107 travels to the first flow chamber 116, and the generator also defines part of a second inflow path along which pressurized fluid from the second inlet 108 travels to the second flow chamber 120.

As noted above, the illustrated generator 110 has one or more passages 144 leading through its first wall 130 to the first flow chamber 116. The passage(s) 144 is/are configured to deliver pressurized fluid into the first flow chamber 116. Similarly, the illustrated generator has one or more passages 146 leading through its second wall 131 to the second flow chamber 120. The passage(s) 146 is/are configured to deliver pressurized fluid into the second flow chamber 120.

In some embodiments, the generator's first 130 and second 131 walls each have a plurality of passages 144, 146 spaced circumferentially about the generator. For example, the first wall 130, the second wall 131, or both can optionally have multiple clusters of passages, where the clusters are spaced circumferentially about the generator 110. In some embodiments, each cluster includes at least one row of passages, such row being substantially parallel to the axis of the energy transfer tube (when the apparatus is operatively assembled). Reference is made to Figures 6A and 8A, which depict two exemplary embodiments of this nature. Here, each row is aligned with (e.g., is generally or substantially parallel to) the axis AX of the energy transfer tube. These features, however, are by no means required.

Thus, the first 130 and second 131 walls of the illustrated generator 110 each have multiple groups of passages, where the groups are spaced circumferentially about the generator. As noted above, the groups can be rows. If desired, each group can include multiple rows of passages. However, other arrangements can be used. For example, staggered arrangements can be provided.

The embodiments shown in Figures 6A-7B include rows of four passages leading into the first flow chamber 116 and rows of two passages leading into the second flow chamber 120, different numbers of passages can be used. As just one other example, Figures 8A-9B show a flow generator 110 with rows of six passages 144 leading into the first flow chamber and rows of three passages 146 leading into the second flow chamber. Figure 7A is a cross-section of an intake manifold 105 and a flow generator 110, with the generator's first wall 130 and the first flow chamber 116 being shown in detail. As pressurized fluid is delivered from the first inlet 107, the fluid rotates through the first inlet chamber 132 around the generator's first wall 130 and passes through the passage(s) 144 into the first flow chamber 116. In the embodiment of Figures 6 A and 7 A, the exterior of the generator's first wall 130 comprises a plurality of ridges adjacent to respective clusters of the passages 144. Here, the passages 144 of each cluster are provided with an adjacent ridge adapted to facilitate flow into the passages 144. Each such ridge 151 may, for example, be located behind (relative to the fluid's direction of rotation) each cluster of passages, e.g., so as to partially block fluid from rotating and divert it into the passages 144. Each ridge 151 may be tapered so its exterior surface becomes gradually closer to the axis of the generator with increasing distance (in the direction of fluid rotation) around the perimeter of the generator. This too can help guide the rotating fluid into the passages 144.

Figure 7B is a cross-sectional view detailing the second wall 131 of the generator when positioned inside the manifold 105. As pressurized fluid is delivered from the second inlet 108, the fluid rotates through the second inlet chamber 133 around the generator's second wall 131 and passes through the passage(s) 146 into the second flow chamber 120. As with the first wall, the second wall 131 can have tapered ridges 151 that facilitate fluid flow into the passages 146. In certain embodiments, the flow generator 110 has a plurality of circumferentially-spaced clusters of passages, and the clusters are located in respective recesses on the exterior of the generator. Reference is made to Figures 9 A and 9B. Here, the recesses 150 are spaced circumferentially about the generator. These features, however, are not required.

When provided, the recesses 150 on the exterior of the flow generator 110 can have various configurations. In Figures 8A-9B, the illustrated recesses 150 are configured such that the passages 144, 146 open through surfaces that face the rotating fluid. Thus, the passages 144, 146 here are oriented so as to open toward oncoming fluid rotating through the inlet chambers.

The first and second walls 130, 131 of the illustrated flow generator 110 are generally cylindrical, and there is a generally annular flow path around each wall 130, 131 of the generator. Due to the orientation of the first and second inlets 107, 108, the pressurized fluid delivered into the inlet chambers rotates within the inlet chambers. Also, due to the orientation of the passages leading through the generator, the pressurized fluid delivered into the flow chambers rotates within the flow chambers.

It is not strictly necessary to provide the annular inlet chambers. For example, the inlets 107, 108 could deliver fluid directly to the respective flow chambers 116, 120. In such cases, the inlets preferably have oblique orientations adapted to start flow in the chambers rotating toward the second end region 106 of the tube 102.

In the illustrated embodiments, the inner diameter of the first flow chamber 116 is larger than the inner diameter of the second flow chamber 118. For example, the first flow chamber 116 may be about twice the diameter of the second flow chamber 120. In one practical embodiment, the inner diameter of the first flow chamber 116 is about 0.4 inches, while the second flow chamber 120 has an inner diameter of about 0.187 inches. Of course, these dimensions are merely exemplary, and are not limiting. Many different dimensions may be used depending upon the application.

As noted above, the illustrated flow generator 110 comprises a plurality of passages 144, 146 extending from the inlet chambers 132, 133, through the generator walls 130, 131, and opening into the flow chambers 116, 120. Referring to Figures 7A, 7B, 9A and 9B, in certain embodiments, the passages 144, 146 have a spiral configuration. When provided, this can facilitate the rotational motion of pressurized fluid entering the flow chambers. In connection with the intake manifold 105, the first inlet 107 and/or the second inlet 108 can optionally be formed so as to be tangential to the first and second inlet chambers 132, 133, respectively. Thus, each inlet can (rather than extending along an axis that is radial to the manifold/tube) be generally or substantially tangential to its inlet chamber, the manifold, and/or the tube 102. A tangential interface between the inlets and the inlet chambers can provide a smooth transition for the pressurized fluid flowing into the inlet chambers.

As shown in Figure 4A, the first and second inlets 107, 108 preferably meet the housing 138 of the manifold 105 at an angle that imparts a forward component of velocity to the fluid flows. The term "forward" direction here means toward the second end region 106 of the tube 102. Preferably, the flow generator 110 also imparts a forward component of velocity to the rotating fluid. In Figures 6B and 8B, the passages 144, 146 leading into the flow chambers 116, 120 are slanted forward. In embodiments of this nature, when pressurized fluid exits the passages 144, 146 and enters the first 116 and second 120 flow chambers, the fluid is directed somewhat forward, i.e., towards the second end region of the energy transfer tube 102.

Preferably, the apparatus 100 includes a flow separator 112 adjacent to the second end region 106 of the energy transfer tube 102. The flow separator bounds separate inner and outer flow pathways. As shown in the illustrated embodiment, the flow separator 112 preferably provides mechanical separation between the inner pathway 124 and the outer pathway 126.

Turning to Figure 10, the flow separator 112 and the cooling jacket 114 are shown in a perspective, sectional view according to certain embodiments of the invention. As noted above, the flow separator 112 bounds separate inner and outer flow pathways 124, 126. The inner pathway 124 is adapted to receive the rotating inner flow of cold fluid, while the outer pathway 126 is adapted to receive the rotating outer flow of hot fluid. In some embodiments, heat is removed from the rotating outer flow (as it travels along the outer pathway) by a plurality of heat transfer fins 128 (or another high surface area structure) on the cooling jacket 114. The inner and outer pathways 124, 126 ultimately merge so as to combine the inner and outer flows. The resulting combined flow is then delivered out of the energy transfer tube apparatus.

Figures 1 IA-11C are additional views of the flow separator 112 shown in Figure 10. The illustrated flow separator 112 comprises a cylindrical wall 160 that mechanically separates the inner pathway 124 from the outer pathway 126. This cylindrical wall 160 bounds the outer flow pathway inwardly. In the illustrated embodiment, the same cylindrical wall 160 bounds the inner flow pathway outwardly. However, this is not required. In the embodiment of Figures 1 IA-11C, to initially separate the rotating outer flow from the rotating inner flow, the flow separator has a projecting axial inlet tube 166 adapted to receive the cold inner flow. Preferably, the axial inlet tube 166 receives a majority (e.g., substantially all, or all) of the cold inner flow, while a majority (e.g., substantially all, or all) of the hot outer flow travels past the axial inlet tube 166 and flows through a plurality of openings 168 in the separator 112 to reach the outer pathway. In the illustrated embodiments, the separator 112 has a first set of openings 168 adjacent to the second end region 106 of the energy transfer tube 102, and a second set of openings 170 located further from the second end region of the energy transfer tube than is the first set of openings. The first set of openings 168 provides passage of the rotating outer flow to the outer pathway, and the second set of openings subsequently provides passage of the outer flow to the inner pathway. In the illustrated embodiment, each set of openings comprises a plurality of circumferentially spaced openings. Preferably, these openings are oblique openings aligned with the outer flow's direction of rotation. These features, however, are not strictly required.

Thus, the cylindrical wall 160 of the illustrated flow separator 112 includes a plurality of openings 168 proximate its first end 162. In some embodiments, the outer surface of the axial inlet tube 166 tapers outwardly towards the openings 168 to direct the rotating outer flow into these openings. The openings 168 mark the beginning of the outer pathway 126. As is perhaps best seen in Figures 1 IB and 11C, the openings 168 can have an angled orientation so as to facilitate smooth delivery of the rotating outer flow into the outer pathway 126. The cylindrical wall of the illustrated flow separator also has openings 170 proximate its second end 164. These are the openings through which the outer flow passes when it is ultimately combined with the inner flow. Thus, the openings 170 can have an angled orientation that facilitates smooth delivery of the outer flow into the inner pathway. In Figures 10-11C, the illustrated flow separator 112 includes a mounting flange

172 adjacent to the first end 162 of the cylindrical wall 160. Here, the mounting flange 172 facilitates mounting the flow separator 112 inside the cooling jacket 114, e.g., such that the exterior of the cylindrical wall 160 bounds the outer pathway 126 inwardly while the interior of the cooling jacket bounds the outer pathway 126 outwardly. In certain embodiments, the cooling jacket 114 and the mounting flange 172 of the flow separator 112 have mating threads so the two pieces can be screwed together. Also, the interior of the mounting flange 172 may have threads so the energy transfer tube 102 can be screwed into the flange 172. In other cases, one or both of these connections are made by a press fit. Of course, these are merely examples: any suitable attachment means can be used to removedly or fixedly join the tube 102, the flow separator 112, and/or the cooling jacket 114.

The cooling jacket 114 and the flow separator 112 can be formed of various materials. Examples include brass, copper, and aluminum. In some embodiments, the heat transfer fins 128 are formed of brass. Various non-metals may also be used. The invention is not limited to using any particular materials for the cooling jacket or the flow separator.

Some embodiments of the invention provide a system 500 that includes at least one energy transfer tube apparatus 100 of the nature described above. Preferably, the system 500 is adapted for creating a heat cycle, e.g., wherein a working fluid undergoes a phase change from a gas to a liquid and back. The system 500, for example, can comprise a closed loop, such as a closed-loop vapor-compression circuit through which working fluid circulates continuously.

In general, the working fluid can be any condensable fluid, such as CO₂ (R-744), highly purified liquefied propane gas (R-290), R41 Oa, Rl 34, Freon, etc. If desired, R- 11 may be used, and it may have particular advantages for low-pressure systems due to its relatively high boiling point, which can allow low-pressure systems to be constructed with lesser mechanical strength required for the components. Other refrigerants can also be used. In a preferred group of embodiments, the working fluid is a mixture comprising water and glycol, a mixture comprising water and sorbitol, a mixture comprising water, glycol, and sorbitol, or a mixture comprising water and one or more other natural water antifreezes. When used, the glycol preferably is a food glycol (e.g., propylene glycol), which is non-toxic, e.g., insofar as being generally recognized as safe for use as a direct food additive. In one practical example, the working fluid is a 50-50 mix of water and glycol. This, however, is merely one example. This is by no means limiting to the invention.

The present system 500 includes at least one energy transfer tube apparatus 100. Preferred energy transfer tube apparatuses 100 are described above in detail. Briefly, the apparatus 100 comprises an energy transfer tube 102 with opposed first 104 and second

106 end regions. The apparatus 100 is provided with first 107 and second 108 inlets (optionally tangential inlets) adjacent to the tube's first end region 104. The first inlet

107 is closer to the tube's second end region 106 than is the second inlet 108. A flow separator 112 is provided adjacent to the tube's second end region 106. The flow separator 112 bounds separate inner 124 and outer 126 flow pathways. The inner pathway 124 is adapted to receive a rotating inner flow of cold fluid, and the outer pathway is adapted to receive a rotating outer flow of hot fluid. The inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow can then be delivered out of the energy transfer tube apparatus 100. The present invention covers any system (e.g., any refrigeration system and/or heat-cycle system, or any other assembly or device) that includes at least one energy transfer apparatus 100 of the type described herein.

One group of embodiments provides a system that can be used advantageously as a low-pressure vapor-compression system. Reference is made to Figure 12. Here, the system includes a compressor (or a pump) C, a vapor/liquid separator VL, an energy transfer tube apparatus 100, an accumulator A, and an evaporator EV. In some embodiments, the accumulator may be omitted. For example, if the flow is sufficiently smooth, then the accumulator may be omitted. Also, the vapor/liquid separator VL may be omitted in some cases, e.g., a single line leading away from the pump C may diverge into two separate lines — one leading to the first inlet 107 of the energy transfer tube apparatus, the other leading to the second inlet 108 of the energy transfer tube apparatus. Thus, the vapor/liquid separator VL is optional.

It may be possible to add other components to a system like that shown in Figure 12, including without limitation, another energy transfer tube apparatus, a condenser, an expansion device, and/or a diffuser. Examples are discussed further below in referring to Figures 13-15.

In Figure 12, the system includes a compressor (or a pump) C, a vapor/liquid separator VL, an energy transfer tube apparatus 100, an accumulator A, and an evaporator EV. The components can be connected by any suitable conduit, such as flexible tubing of plastic or rubber. In general, any other fluid connector can be used (e.g., air conditioning hose may be used). Commonly, the working fluid will enter the pump C as a vapor (some of the fluid here may be vapor, while some is liquid). In some cases, the vapor is compressed at constant entropy and exits the compressor C superheated. In other cases, a relatively small pump (such as 15 gallons/minute, as just one example) is used, and the working fluid leaves the pump at close to ambient temperature.

The specific type of compressor or pump is not limiting to the invention. In one group of embodiments, the compressor is a scroll compressor. Useful compressors are available commercially from a variety of suppliers, such as Air Squared (Bloomfield, Colorado, U.S.A.) or Visteon Corporation (Van Buren Township, Michigan, U.S.A.). However, reciprocating compressors (e.g., piston compressors) can also be used. Thus, the compressor can be virtually any compressor or pump suitable for use in a refrigeration system and/or heat-cycle system.

With continued reference to Figure 12, after the working fluid leaves the compressor, it flows to a vapor/liquid separator VL. Here, the working fluid is separated into two flows — one that is largely (e.g., predominantly) vapor and another that is largely (e.g., predominantly) liquid. Commonly, the two flows will not be entirely fluid and entirely vapor. Rather, this separation will commonly be a coarse separation.

Preferably, the liquid outflow from the vapor/liquid separator VL has a greater mass volume than the vapor outflow from the vapor/liquid separator. In some non-limiting examples, the liquid outflow is designed to be 60% or more, 70% or more, 75% or more, or even 80% or more of the total mass outflow from the vapor/liquid separator VL. In one embodiment, the liquid outflow is designed to be about 60-90%, such as about 70- 80%, of the total mass outflow from the vapor/liquid separator VL. Preferably, the system (e.g,. compressor or pump and evaporator) is chosen to facilitate such relative mass flows.

The specific type of vapor/liquid separator VL is not limiting to the invention. In fact, the vapor/liquid separator VL is optional, as already explained. On the other hand, two or more vapor/liquid separators VL may be arranged in series, e.g., so as to obtain finer separation of liquid and vapor.

Figures 16 and 17A-D show one exemplary vapor/liquid separator VL. Here, a separator block BL is provided. The illustrated separator block BL has an inlet IF in fluid communication with multiple outlets, including a liquid outlet LQ and a vapor outlet VP. The liquid outlet LQ is provided with an orifice adapted to provide a path of relatively low resistance for the working fluid, e.g., so as to be adapted to selectively pass a stream composed largely (e.g., predominately) of liquid. The illustrated vapor outlet VP is provided with a plurality of small orifices adapted to provide a path of relatively high resistance for the working fluid, e.g., so as to be adapted to selectively pass a stream composed largely (e.g., predominately) of vapor. Thus, the vapor outlet VP (and/or the flow path leading up to it) may be configured/equipped so as to have higher flow resistance than the liquid outlet LQ. In one practical embodiment, inlet IF comprises a ¹A" NPT bore to which a fluid connector is attached so as to deliver working fluid into a primary bore extending into the separator block, two bores 887 pass crosswise (relative to the primary bore) through the block BL so as to intersect the main primary and open respectively toward two outlet bores in the neck portions of which two removable orifice inserts LI, VI are respectively fitted (e.g., by a press fit), the outflow sections of the outlet bores are provided as 1/8" NPT bores, such that two fluid connectors with corresponding fittings can be threadingly attached to these outlets, the liquid flow orifice insert LI defines a 0.22" orifice, the vapor flow orifice insert VI has eighteen 0.052" orifices, and the plugs PL are ¹A" NPT plugs. These details, however, are strictly exemplary, i.e., they are optional. Thus, separate vapor and liquid lines can deliver the working fluid (e.g., from a vapor/liquid separator VL) to the energy transfer tube apparatus 100. As noted above, the energy transfer tube apparatus 100 preferably has separate inlets. For example, the apparatus 100 can include a first inlet 107 for delivering vapor into the apparatus 100 and a second inlet 108 for delivering liquid into the apparatus 100. If desired, the apparatus 100 can actually have a plurality of first inlets (e.g., vapor inlets) 107 and a plurality of second inlets (e.g., liquid inlets) 108. By way of non-limiting example, the liquid flow into the apparatus 100 may account for 60% or more, 70% or more, 75% or more, or even 80% or more of the total mass flow into the apparatus 100. In one embodiment, the liquid inflow accounts for about 60-90%, such as about 70-80%, of the total mass flow into the energy transfer tube apparatus 100.

Flow through the first inlet(s) 107 is directed into a first flow chamber 116, as already explained. This creates a rotating outer flow 118 that travels through the energy transfer tube 102, e.g., toward the second end region of the tube. Flow through the second inlet(s) 108 is directed into a second flow chamber 120, creating a rotating inner (or "central" or "axial") flow 122 that travels through the tube 102, e.g., toward the second end region of the tube (preferably while being surrounded axially by the outer flow 118). As the inner and outer flows move through the tube 102, energy is transferred from the inner flow 122 to the outer flow 118, making the inner flow increasingly cold while the outer flow becomes increasingly hot. Adjacent the second end region 106 of the tube 102, a flow separator 112 separates the inner and outer flows, directing the cold inner flow 122 along an inner pathway 124, while the hot outer flow 118 is diverted along an outer pathway 126. At this point, a cooling jacket 114 or another heat exchanger preferably transfers heat from the outer flow 118, e.g., to a surrounding medium (in some cases, via optional fins 128 or another high surface area structure). Depending on the particular application, a fan or the like may move air or other fluid over the cooling jacket on the tube 102. In this way, a great deal of heat is removed from the outer flow 118. After being cooled in this manner, the outer flow 118 is combined with the inner flow 122, and the resulting combined flow is then delivered out of the energy transfer tube apparatus 100.

With continued reference to Figure 12, the working fluid then flows to an accumulator A. The accumulator A smooths or dampens the flow, preferably attenuating any back pressure or pulsation. The specific type of accumulator is not limiting to the invention. Rather, the accumulator A can be virtually any accumulator suitable for use in a refrigeration system and/or heat-cycle system. Accumulators useful for flattening fluid flow are available from a variety of commercial suppliers, such as Parker Hannifin Corp. (Cleveland, Ohio, U.S.A.) or Delphi (Troy, Michigan U.S.A).

Next, the cold working fluid flows to the evaporator EV. Upon entering the evaporator, the working fluid will typically be a liquid- vapor mixture, preferably comprising as much liquid as possible. When the cold working fluid travels through the evaporator (e.g., through a coil or tubes of the evaporator), at least some of the working fluid is vaporized. In some embodiments, this is due to relatively warm air (e.g., from a space being refrigerated) blown by a fan across the evaporator. After passing through the evaporator, the working fluid (which comprises vapor, perhaps together with some liquid) returns to the compressor inlet to finish the cycle.

In one practical example of a system 500 like that shown in Figure 12, the working fluid is a 50-50 mixture of water and food glycol, the pump is a Parker aerospace pump about 2 inches long with a diameter of about 1 Vi inches, the evaporator is of about 4" x 8" size, and the connecting hose is 3/8" flexible plastic hose. This is merely one example. It is by no means limiting to the invention. To the contrary, skilled artisans will appreciate that many different components and combinations can be used.

The system shown in Figure 13 includes an additional energy transfer tube apparatus 100 (e.g., of the nature described above). Here, the second energy transfer tube apparatus 100 is located between the evaporator EV and the compressor C. This particular arrangement may be preferred when it is desirable to provide additional heat extraction from the working fluid flowing between the evaporator EV and the compressor C.

In other embodiments, the system has a second energy transfer tube apparatus at a location different from that shown in Figure 13. Further, it may be desirable to use two or more energy transfer tube apparatuses in series. For example, a series of two or more energy transfer tube apparatuses can be provided: (i) after a compressor/before an evaporator, or (ii) after an evaporator/before a compressor. If desired, each of the locations (i) and (ii) can have two or more energy transfer tube apparatuses in series. In Figures 12 and 13, the system 500 does not have any expansion valve, orifice, or other means for rapidly decreasing the pressure of the working fluid, e.g., as is commonly provided in some systems to cause a flash evaporation. Thus, some of the present embodiments provide a system 500 that is devoid of any expansion device, e.g., is devoid of any flash-evaporation means. This, however, is not the case for all embodiments.

One group of embodiments provides a system that can be used advantageously as a high-pressure vapor-compression system. Reference is made to Figure 14. This system includes a compressor C, a vapor/liquid separator VL, an energy transfer tube apparatus 100, a condenser CN, an accumulator A, an expansion device ED, and an evaporator EV. In some cases, the accumulator may be omitted. Ifthe flow is sufficiently smooth, for example, then the accumulator may be omitted. The vapor/liquid separator VL is also optional, and may be omitted in some cases. Also, it may be possible to add other components to a system like that shown in Figure 14, including without limitation, one or more additional energy transfer tube apparatuses, and/or a diffuser. Examples are discussed further below in referring to Figure 15.

In Figure 14, the system includes a compressor C, a vapor/liquid separator VL, an energy transfer tube apparatus 100, a condenser CN, an accumulator A, an expansion device ED, and an evaporator EV. The components can be connected by any suitable fluid connector, such as a rubber type hose, e.g., air conditioning hose. The working fluid will typically enter the compressor C as a vapor (some of the fluid here may be vapor, while some is liquid). In many cases, the vapor is compressed at constant entropy and exits the compressor C superheated.

The specific type of compressor here is not limiting to the invention. In one group of embodiments, the compressor is a scroll compressor. However, reciprocating compressors can also be used. In general, the compressor can be any type suitable for use in a refrigeration system and/or heat-cycle system.

With continued reference to Figure 14, after the working fluid leaves the compressor, it flows to a vapor/liquid separator V, which separates the working fluid into two flows: one that is largely (e.g., predominantly) vapor and another that is largely (e.g., predominantly) liquid. The liquid outflow from the vapor/liquid separator VL preferably has a greater mass volume than the vapor outflow from the vapor/liquid separator. In some embodiments, the liquid outflow is 60% or more, 70% or more, 75% or more, or even 80% or more of the total mass outflow from the vapor/liquid separator VL. In one embodiment, the liquid outflow is about 60-90%, such as about 70-80%, of the total mass outflow from the vapor/liquid separator VL. The system (e.g., compressor and evaporator) preferably is chosen to accomplish the desired relative mass flows.

The specific vapor/liquid separator VL is not limiting to the invention. A separator block BL like that described above in connection with Figures 16 and 17A-D is advantageous.

Thus, separate vapor and liquid lines may deliver the working fluid from the vapor/liquid separator VL to the energy transfer tube apparatus 100. As already explained, the energy transfer tube apparatus 100 has separate inlets. Preferably, the apparatus 100 has a first inlet 107 for delivering vapor into the apparatus 100 and a second inlet 108 for delivering liquid into the apparatus 100. If desired, the apparatus 100 can have a plurality of first inlets (e.g., vapor inlets) 107 and a plurality of second inlets (e.g., liquid inlets) 108. In some embodiments, the liquid flow into the apparatus 100 accounts for 60% or more, 70% or more, 75% or more, or even 80% or more of the total mass flow into the apparatus 100. In one embodiment, the liquid inflow accounts for about 60-90%, such as about 70-80%, of the total mass flow into the energy transfer tube apparatus 100.

Flow through the first inlet(s) 107 is directed into a first flow chamber 116, as previously explained. This creates a rotating outer flow 118 that travels through the energy transfer tube 102, e.g., toward the second end region of the tube. Flow through the second inlet(s) 108 is directed into a second flow chamber 120, creating a rotating inner (or "central") flow 122 that travels through the tube 102, e.g., toward the second end region of the tube (preferably while being surrounded axially by the outer flow 118). As the inner and outer flows move through the tube 102, energy is transferred from the inner flow 122 to the outer flow 118, making the inner flow increasingly cold while the outer fluid flow becomes increasingly hot.

Adjacent the second end region 106 of the tube 102, a flow separator 112 separates the inner and outer flows, directing the cold inner flow 122 along an inner pathway 124, while the hot outer flow 118 is diverted along an outer pathway 126. At this point, a cooling jacket 114 (or other heat exchanger) preferably transfers heat from the outer flow 118, e.g., to a surrounding medium (in some cases, via optional fins 128 or another high surface area structure). Depending on the particular application, a fan or the like may move air or other fluid over the cooling jacket. In this way, a great deal of heat can be removed from the outer flow 118. After being cooled in this manner, the outer flow 118 is combined with the inner flow 122, and the resulting combined flow can then be delivered out of the energy transfer tube apparatus.

The working fluid then flows to a condenser CN. The condenser cools and removes more heat from the working fluid, so as to condense some of vapor into a liquid by removing heat at constant pressure and temperature.

The specific type of condenser is not limiting to the invention. Useful condensers are available commercially from a variety of suppliers, such as Parker Hannifin Corp. (Cleveland, Ohio, U.S.A.). In general, the condenser can be any model suitable for use in a refrigeration system and/or heat-cycle system. The working fluid then flows to an accumulator A. The accumulator A smooths or dampens the flow, preferably attenuating any back pressure or pulsation. The specific accumulator is by no means limiting to the invention. Rather, the accumulator A can be virtually any type suitable for use in a refrigeration system and/or heat-cycle system. Useful accumulators are available commercially from a variety of suppliers, such as Parker Hannifin Corp. (Cleveland, Ohio, U.S.A.) or Delphi (Troy, Michigan U.S.A).

The working fluid then goes through an expansion device. The expansion device ED can be an expansion valve, orifice, capillary tube, etc. Here, the pressure of the working fluid decreases rapidly. Preferably, this causes a flash evaporation. The result is a mixture of liquid and vapor at a lower temperature and pressure. Next, this cold liquid- vapor mixture travels through the evaporator. While passing through the evaporator, at least some of the working fluid is vaporized. In some applications, this is due to warm air (e.g., from a space being refrigerated) blown by a fan across the evaporator coil or tubes. After passing through the evaporator, the working fluid returns to the compressor inlet to finish the cycle. In one practical example of a system 500 like that shown in Figure 14, the working fluid is a 50-50 mixture of water and food glycol, the compressor is a Visteon AC scroll compressor (SHl 5, OE#4596550AB) modified by enlarging the discharge and entry points, the connecting hose is 1/2" tubing, the condenser has a size of about 12" x 20", and the evaporator has a size of about 12" x 12". This, however, is merely one example — it is not limiting. Rather, skilled artisans will appreciate that many different components and combinations can be used.

It may be desirable to service the system with the working fluid above its boiling point, e.g., installing the working fluid in a gaseous state may be preferred. For example, when the working fluid is an aqueous (e.g., water-based) solution, it may be preferred to put the water into the system as steam. This, however, is optional: it is by no means required.

The system shown in Figure 15 includes an additional energy transfer tube apparatus 100 (e.g., of the nature described above). Here, the second energy transfer tube apparatus 100 is located between the evaporator EV and the compressor C. This arrangement may be preferred when it is desirable to provide additional heat extraction from the working fluid flowing between the evaporator EV and the compressor C.

In other embodiments, the system has a second energy transfer tube apparatus at a location different from that shown in Figure 15. Further, it may be desirable to use two or more energy transfer tube apparatuses in series. For example, a series of two or more energy transfer tube apparatuses can be provided: (i) after a compressor/before a condenser, or (ii) after an evaporator/before a compressor. If desired, each of the locations (i) and (ii) can have two or more energy transfer tube apparatuses in series.

The system 500 can be used for virtually any application that involves a vapor- compression cycle. Examples include air conditioning systems, heat pumps, coolers, and/or refrigerators.

In one group of embodiments, an evaporator EV in any system 500 described above is replaced with a heat sink structure comprising a fluid grid FG. Reference is made to Figure 18, which schematically depicts an exemplary system of this nature. Here, the evaporator EV from the system 500 of Figure 12 is replaced with such a heat sink structure. The heat sink structure may, for example, be in thermal communication with a CPU, although many different heat sink applications can be used. The heat sink structure, as just one example, may include a fluid grid FG comprising block or another body (optionally formed of a high heat transfer rate material, such as a copper alloy) having formed therein at least one passage (optionally an S -shaped passage) for the cold working fluid. Optionally, the heat sink structure can further include a plate PLT or another body (preferably formed of metal, such as iron) in thermal communication with (optionally located between, e.g., sandwiched between) the CPU and the fluid grid FG. The other components and features of the embodiment of Figure 18 can be in accordance with any of the various teachings above relating to the system of Figure 12.

Figure 19 schematically depicts another exemplary embodiment. Here, the evaporator EV from the system 500 of Figure 14 is replaced with a heat sink structure comprising a fluid grid FG. The other components and features of the embodiment of Figure 19 can be in accordance with any of the various teachings above relating to the system of Figure 14.

In some embodiments, it may be desirable to provide the energy transfer tube 102 with a transducer (e.g., by placing a transducer in, or on, an energy transfer tube of the apparatus). This may be provided to generate an acoustic tone. For example, the tube 102 can optionally be provided with a band or strap type frequency generator, e.g., secured around the energy transfer tube. This type of frequency generator may create frequency all along the band, rather than just at one point on the strap. Alternatively, a point-type frequency generator may be used.

For embodiments where the energy transfer tube 102 exhibits acoustic toning, this acoustic event may be characterized by an acoustic frequency and amplitude propagating throughout a plurality of fluid flows (preferably propagating throughout both fluid flows in the tube 102). This is contrary to acoustic streaming, in which an acoustic stream is isolated (or "localized") between two adjacent fluid flows. Thus, in acoustic toning, the acoustic tone propagates over a plurality (preferably over all) of the flow layers, rather than being trapped between two adjacent flow layers, as is the case with acoustic streaming. In some embodiments, the acoustic tone may exist over substantially the entire length of the energy transfer tube, although this is not required.

While a preferred embodiment of the present invention has been described, it should be understood that various changes, adaptations and modifications may be made therein without departing from the spirit of the invention and the scope of the appended claims.

Claims

WHAT IS CLAIMED IS:

1. An energy transfer tube apparatus comprising an energy transfer tube having opposed first and second end regions, the apparatus being provided with first and second inlets adjacent to the tube's first end region, the first inlet being closer to the tube's second end region than is the second inlet, wherein a flow separator is provided adjacent to the tube's second end region, the flow separator bounding separate inner and outer flow pathways, the inner pathway being adapted to receive a rotating inner flow of cold fluid, the outer pathway being adapted to receive a rotating outer flow of hot fluid, wherein the inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow is then adapted to be delivered out of the energy transfer tube apparatus.

2. The energy transfer tube apparatus of claim 1 wherein the flow separator provides mechanical separation of the inner and outer flow pathways.

3. The energy transfer tube apparatus of claim 2 wherein the flow separator includes a cylindrical wall that mechanically separates the inner flow pathway from the outer flow pathway, and wherein an exterior of the cylindrical wall bounds the outer flow pathway inwardly.

4. The energy transfer tube apparatus of claim 3 wherein the flow separator has a first set of openings adjacent to the second end region of the energy transfer tube, this first set of openings comprising a plurality of circumferentially-spaced openings through which the rotating outer flow of hot fluid passes to reach the outer pathway, and wherein the flow separator has a second set of openings that are further from the second end region of the energy transfer tube than are the first set of openings, this second set of openings comprising a plurality of circumferentially-spaced openings through which the outer flow ultimately passes so as to be combined with the inner flow.

5. The energy transfer tube apparatus of claim 4 wherein the flow separator's first and second sets of openings both comprise oblique openings aligned with a rotation direction of the outer flow.

6. The energy transfer tube apparatus of claim 1 wherein a cooling jacket is provided such that an interior of the cooling jacket bounds the outer flow pathway outwardly, the cooling jacket having a plurality of heat transfer fins on an exterior of the cooling jacket, the heat transfer fins comprising a metal selected from the group consisting of brass, copper, and aluminum.

7. The energy transfer tube apparatus of claim 1 wherein a fluid flow generator is provided adjacent to the tube's first end region, the generator being adapted to create both the rotating outer flow and the rotating inner flow.

8. The energy transfer tube apparatus of claim 7 wherein the first and second inlets are both tangential inlets, and wherein the generator defines part of a first inflow path along which pressurized fluid from the first inlet travels into a first fluid flow chamber so as to create the rotating outer flow, and wherein the generator also defines part of a second inflow path along which pressurized fluid from the second inlet travels into a second fluid flow chamber so as to create the rotating inner flow.

9. The energy transfer tube apparatus of claim 8 wherein the first fluid flow chamber is closer to the tube's second end region than is the second fluid flow chamber, the first fluid flow chamber has a larger diameter than the second fluid flow chamber, and wherein the first and second fluid flow chambers are coaxial to each other.

10. The energy transfer tube apparatus of claim 8 wherein the generator includes a first wall surrounding the first fluid flow chamber and having a plurality of passages configured to deliver pressurized fluid into the first fluid flow chamber, and wherein the generator also includes a second wall surrounding the second fluid flow chamber and having a plurality of passages configured to deliver pressurized fluid into the second fluid flow chamber.

11. The energy transfer tube apparatus of claim 10 wherein the first and second walls of the generator each have multiple clusters of passages, the clusters being spaced circumferentially about the generator.

12. The energy transfer tube apparatus of claim 11 wherein each cluster comprises at least one row of passages, such row being substantially parallel to an axis of the energy transfer tube.

13. The energy transfer tube apparatus of claim 11 wherein the passages of each cluster are provided with an adjacent ridge adapted to facilitate flow into the passages.

14. The energy transfer tube apparatus of claim 11 wherein the clusters are located in respective recesses on an exterior of the generator, the recesses being spaced circumferentially about the generator.

15. A method of using an energy transfer tube apparatus, the apparatus comprising an energy transfer tube having opposed first and second end regions, the apparatus being provided with first and second inlets adjacent to the tube's first end region, the first inlet being closer to the tube's second end region than is the second inlet, wherein a flow separator is provided adjacent to the tube's second end region, the flow separator bounding separate inner and outer flow pathways, the inner pathway being adapted to receive a rotating inner flow of fluid, the outer pathway being adapted to receive a rotating outer flow of fluid, wherein the inner and outer pathways ultimately merge, the method comprising delivering a predominantly vapor flow of working fluid through the first inlet of the apparatus so as to create the rotating outer flow, and delivering a predominantly liquid flow of working fluid through the second inlet of the apparatus so as to create the rotating inner flow, the inner and outer flows both moving through the energy transfer tube before being separated by the flow separator such that the outer flow travels along the outer pathway while the inner flow travels along the inner pathway until reaching a location where the inner and outer pathways ultimately merge so as to combine the inner and outer flows.

16. The method of claim 15 wherein the predominantly liquid flow delivered through the second inlet has a greater mass volume than the predominantly vapor flow delivered through the first inlet.

17. The method of claim 16 wherein said predominantly liquid flow and said predominantly vapor flow together provide a total mass flow of working fluid delivered into the apparatus, the mass flow of said predominantly liquid flow being about 60-90% of the total mass flow.

18. The method of claim 15 wherein the method comprises using a vapor/liquid separator to receive an intake flow that is part vapor, part liquid and to separate that intake flow into first and second outflows, the first outflow being predominantly vapor and supplying the first inlet of the energy transfer tube apparatus, the second outflow being predominantly liquid and supplying the second inlet of the energy transfer tube apparatus.

19. A system in which a working fluid is adapted to be circulated so as to flow from a compressor or pump to an energy transfer tube apparatus, then from the energy transfer tube apparatus to an evaporator, then from the evaporator to said compressor or pump, the energy transfer tube apparatus comprising an energy transfer tube having opposed first and second end regions, the apparatus being provided with first and second inlets adjacent to the tube's first end region, the first inlet being closer to the tube's second end region than is the second inlet, wherein a flow separator is provided adjacent to the tube's second end region, the flow separator bounding separate inner and outer flow pathways, the inner pathway being adapted to receive a rotating inner flow of cold fluid, the outer pathway being adapted to receive a rotating outer flow of hot fluid, wherein the inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow is then adapted to be delivered out of the energy transfer tube apparatus.

20. The system of claim 19 wherein the first and second inlets are tangential inlets.

21. The system of claim 19 wherein a vapor/liquid separator is provided between said compressor or pump and the energy transfer tube apparatus, the vapor/liquid separator being adapted to receive an intake flow that is part vapor, part liquid and to separate that intake flow into first and second outflows, the first outflow being predominantly vapor and supplying the first inlet of the energy transfer tube apparatus, the second outflow being predominantly liquid and supplying the second inlet of the energy transfer tube apparatus.

22. The system of claim 19 wherein an accumulator is provided between the energy transfer tube apparatus and the evaporator.

23. The system of claim 19 wherein the system does not have an expansion valve, orifice, or any other flash-evaporation means.

24. The system of claim 19 wherein a condenser is provided between the energy transfer tube apparatus and the evaporator.

25. The system of claim 24 wherein an expansion valve is provided between the condenser and the evaporator.

26. The system of claim 25 an accumulator is provided between the condenser and the expansion valve.

27. A system in which a working fluid is adapted to be circulated so as to flow from a compressor or pump to an energy transfer tube apparatus, then from the energy transfer tube apparatus to a heat sink structure in thermal communication with a central processing unit, then from the heat sink structure to said compressor or pump, the energy transfer tube apparatus comprising an energy transfer tube having opposed first and second end regions, the apparatus being provided with first and second inlets adjacent to the tube's first end region, the first inlet being closer to the tube's second end region than is the second inlet, wherein a flow separator is provided adjacent to the tube's second end region, the flow separator bounding separate inner and outer flow pathways, the inner pathway being adapted to receive a rotating inner flow of cold fluid, the outer pathway being adapted to receive a rotating outer flow of hot fluid, wherein the inner and outer pathways ultimately merge so as to combine the inner and outer flows, such that a combined flow is then adapted to be delivered out of the energy transfer tube apparatus.

28. The system of claim 27 wherein the first and second inlets are tangential inlets.

29. The system of claim 27 wherein the heat sink structure comprises a fluid grid through which the working fluid passes, the fluid grid comprising a body having formed therein at least one passage through which the working fluid is adapted to flow.

30. The system of claim 29 wherein the passage has an S-shaped configuration or is otherwise serpentine.

31. The system of claim 29 wherein said body of the fluid grid comprises copper.

32. The system of claim 29 wherein the heat sink structure further includes a plate in thermal communication with both the CPU and the fluid grid.

33. The system of claim 32 wherein the plate comprises iron and is positioned between the CPU and the fluid grid.