KR100768763B1 - Fluid flow contouring apparatus for enhanced heat transfer and method for enhancing heat transfer - Google Patents

Abstract

Baffles (20, 22) arranged alongside a plurality of conduits (12).

Description

Fluid flow forming device and improved heat transfer method for improved heat transfer {FLUID FLOW CONTOURING APPARATUS FOR ENHANCED HEAT TRANSFER AND METHOD FOR ENHANCING HEAT TRANSFER}

The present invention provides a method for improving heat transfer or heat transfer from orthogonally flowing fluids in contact with a thermally conductive outer cell of a plurality of axially arranged heat exchange conduits that can act as a heat source or heatsink. Relates to a device. The fluid is flowed in an orthogonal direction, at right angles to the axis of the heat exchange conduit, and upstream, downstream, or around the heat exchange conduit using slotted, perforated platelets, baffles or sleeved elements. By flowing side by side, a surprisingly efficient heat transfer is achieved between the flowing fluid and the heat conduction plane.

Process fluids, such as liquids or gases, are brought into contact with and flow through a heat transfer surface maintained at a temperature that is different from the temperature of the upstream process fluid, thereby transferring heat to the process fluid or heat transfer from such process fluids. It is well known to heat or cool the process fluid in such a way as to be maintained at a temperature). In one example of this technique, the heat transfer surface acting as a heat source or heat sink is, for example, a thermally conductive outer cell of a heat transfer tube or pipe that is heated or cooled by liquid flowing axially through the interior of the tube or pipe. In one variation of this technique, heat can be supplied directly into the heat exchanger tube by flameless combustion of fuel gas (hydrogen or hydrocarbon) as described, for example, in US Pat. Nos. 5,255,742 and 5,404,952. have.

It is also conventional to flow the process fluid in the axial direction in the same direction as the flow direction of the liquid flowing through the inside of the heat transfer tube along the heat transfer surface or in the reverse direction, or to flow the process fluid orthogonal to the axis of the heat transfer tube. Known and combinations of these two methods are also known. Typical examples of applications of heat transfer between cross flow fluids and heat exchange tubes are found in air coolers, combustors or economizers used in combustion furnaces, and cell-tube heat exchangers. In contrast to the well-known axial flow (end-end) reactors, various types of so-called radial or axial / semi-flow flow reactors have at least some of the fluidic process steam radially orthogonal (inner-outer, or outer- Inside) to move through the reactor. Examples of reactors that use partial radial crossflow of process fluids for a plurality of axially arranged continuous delivery tubes are described in U.S. Patents 4,230,669, 4,321,234, 4,594,227, 4,714,592, 4,909,808, 5,250,270 and 5,585,074.

Although cross-flow contact of the process fluid to the heat transfer surface may be an attractive option in many cases, the use of cross-flow contact on an industrial scale has been practically limited because of some inefficiency in heat transfer. . Typically in a cross flow mode, part of the process fluid contacts the heat transfer surface for only a short time compared to the axial flow method. In addition, the contact between the crossflow process fluid and the heat transfer surface is not constant due to the separation and recycling of the process fluid. Short surface contact time, uneven contact and limited fluid mixing make thermal energy transfer inefficient, insufficient and nonuniform.

Technical Document Int. In the article "Impingement heat transfer at a circular cylinder due to an offset of non-offset slot jet," published in J. Heat Mass Transfer., Vol. 27, no. 12, pp. 2297-2306 (1984), author Sparrow And Alhomoud show that the heat transfer efficiency related to the cross-flow of process gas can be changed with respect to the heat transfer tube by arranging the slotted surface at some distance upstream of the heat transfer tube to generate gas jet. Is reporting. Sparrow and Alhomoud vary the width of the jet-induced slot, the distance between the slot and the tube, the Reynolds number (fluid turbulence), and also align the slot jet to the tube or offset it out of alignment. I also saw. The authors conclude that the thermal conductivity increases with increasing slot width and Reynolds number, but decreases with increasing distance between the slot and tube and the degree of offset.

Since Sparrow's and Alhomoud's work concludes that the thermal conductivity increases with the width of the slot, the use of upstream slots to increase heat transfer is generally very vague based on these results. However, in the empirical structure by Sparrow and Alhomoud, it can be concluded that a relatively wide slot has no high value at all when the thermal conductivity is high and there is no upstream slot compared to a relatively narrow slot. The test was not carried out using a plurality of heat transfer tubes or using an upstream or downstream pair of perimeters or parallel to flow restricting means for forming a cross flow fluid passage in contact with the outer surface of each of the plurality of heat transfer tubes. However, no special estimate can be made for these very different structures or configurations based on the extremely limited data provided.

These drawbacks or limitations of conventional crossflow heat exchanger structures are addressed, in whole or in part, by the improved crossflow heat transfer methods and structures of the present invention.

Accordingly, it is a primary object of the present invention to provide a method and structure for improved cross flow heat transfer between process fluid and heat transfer surface.

It is a general object of the present invention to provide a method and structure for forming a fluid crossflow passage in contact with one or more heat transfer surfaces to enhance cross flow heat transfer between the process fluid and the heat transfer surface.

It is a particular object of the present invention to upstream, downstream or around or around a heat transfer surface such that a flow through which the process fluid passes in a direction orthogonal to the heat transfer surface is achieved in order to improve enhanced cross flow heat transfer between the process fluid and the heat transfer surface. Side by side to provide fluid flow restriction means.

Another particular object of the present invention is a curved or planar perforated plate disposed in each conduit in an array of heat exchange conduits to form a flow path through which fluid flows in an orthogonal direction outside of each conduit to allow for improved heat transfer or To provide perforated sleeves.                 

It is a further object of the present invention that each conduit has its own upstream side, downstream side or around or side by side to form a flow path through which fluid flows orthogonally to the outside of each conduit so that improved heat transfer can be achieved. It is to provide a heat transfer conduit array of various sizes and structures with fluid flow restriction means.

Other objects and advantages of the invention will be apparent from the following. Accordingly, the present invention consists of, but is not limited to, a method and an apparatus comprising a number of steps and components, and one or more of these steps and components correlated as illustrated in the following detailed description with reference to the accompanying drawings. . Many modifications and variations of the method and apparatus of the present invention will become apparent to those skilled in the art and such modifications and variations will be considered to be within the scope of the present invention.

In the present invention, a baffle structure composed of at least two pairs of fluid flow restrictors is formed to form a flow path of the process fluid flowing in the orthogonal direction in contact with the heat transfer surface in order to improve the improved cross-flow heat transfer between the process fluid and the heat transfer surface. do. The device is configured to restrict the bypass flow of the fluid so that a significant portion of the process fluid can be forced through the heat transfer surface. Typically the heat transfer surface will be one or more arrays of heat exchange conduits having heat transfer cells arranged axially with parallel axes perpendicular to the direction of fluid flow. The outer surface of the cells of each of these conduits is maintained at a temperature different from the temperature of the upstream process fluid so that when the fluid flows and contacts the outer surface of the heat exchange conduit, the conduction, convection, radiation, and combinations thereof, or Allow heat energy to be transferred from the process fluid.                 

The heat exchange conduits of the present invention can be tubes, pipes or other structures having heat sources or heat sinks. The outer surface of the heat exchange conduit may have the outer surface as it is described in detail below, or may have a finned surface, or a combination of the two. The cross section of the conduit may be in the shape of a circular, elliptical or other closed curve. If a large number of such heat exchange conduits are used, they will typically be arranged in a predetermined structure, such as an array of triangle arrays, square arrays, circular arrays, annular arrays or any other pattern, depending on the choice or condition of the particular structure. With respect to the flow direction of the fluid, adjacent conduits may also be arranged, ordered, or otherwise arranged in an orderly manner depending on the choice or conditions of the particular structure.

The size of the heat exchange conduit will be determined at least in part by the process conditions for thermal conductivity. In general, a conduit with a large cross section (in any given conduit structure) will provide greater surface area to exhibit greater heat transfer properties. Fin elements, baffles, or other structures that enhance heat transfer may be provided on the outer surface of some or all of the heat exchange conduits to further increase surface area and improve heat transfer characteristics. A first embodiment utilizes pins that are arranged in spiral proximity along the outer length of the conduit. This configuration increases the heat exchange surface area exposed to cross flow without disturbing flow. It will be appreciated that the nature and flow rate of the process fluid and the required fluid temperature change between the upstream side of the heat exchange conduit and the downstream side of the conduit will influence the choice of these structures.

The fluid flow restricting means for allowing cross flow of the process fluid is comprised of inlets, outlets and openings of various shapes and sizes of baffle structures arranged upstream, downstream or around or side by side of the heat exchange conduits. In another preferred embodiment, each heat exchange conduit has its own upstream and downstream fluid flow limiters or flow restrictors around or side by side, as described in detail below. A perforated baffle structure that acts as a fluid flow restriction means may be comprised of a plate, sleeve or other type of baffle consisting of a plane or curved surface or a combination of plane and curved surfaces. Perforated structures of this type, arranged in pairs upstream and downstream of the array of heat exchange conduits, have been found to improve heat transfer efficiency by 1.5 to 2 times. In some particularly advantageous embodiments, the fluid flow restriction structure is a large concentric sleeve structure that partially surrounds each conduit in an array of tubular heat exchange conduits, each such sleeve structure being an upstream side of the centrally arranged heat exchange tube. And through-holes on the downstream side. This type of perforated sleeve, which partially encloses each heat exchange conduit in the array of conduits, has been found to improve heat transfer efficiency by about five times or more.

In a fluid flow restriction structure, the through hole is preferably composed of a combination of perforated through holes or axial slots (long holes whose long axes are parallel to the axial direction of the heat exchange conduits). The through holes or slots formed in other parts of the device may be the same or different in curvature, size and shape. The edges around the inlet and outlet can be straight, curved, serrated or some combination thereof.

Fluid flow restricting structures have a distance between the centerline of the upstream or downstream aperture and the center of the heat exchange conduit of approximately 0 to 2.0 times the outer diameter of the conduit (or, in the case of non-circular conduits, the maximum cross section), preferably approximately It should be arranged against the heat exchange conduit so that it is 0.50 to 1.00 times. In some cases, the spacing between the aperture and the conduit should be close enough to allow for improved heat transfer. The width (shortest distance) of the elongated flow restriction hole or the diameter of the circular restriction hole should be about 0.02 to 1.5 times, preferably about 0.05 to 0.25 times the outer diameter of the conduit (in the case of non-circular conduits). . The fluid flow restricting structure is arranged relative to the heat exchange conduit such that the distance between the center of the through hole and the center of the heat exchange conduit is 0 to 0.5 times, preferably 0 times, the outer diameter of the conduit (or, in the case of non-circular conduits, the maximum cross section). It is good to be.

The improved cross flow heat exchanger of the present invention improves the heat transfer efficiency between the cross flow fluid and the plurality of heat exchange conduits by at least one of the following: (a) increasing the fluid velocity around the heat exchange conduit; (b) allow fluid to flow close to the outer surface of the heat exchange conduit; (c) restricts fluid flowing to the outer surface of the heat exchange conduit or through an area spaced from the outer surface of the heat exchange conduit; (d) reduce the “square” area and flow restriction around the heat exchange conduit; (e) increase the disturbance of the fluid; (f) Increase the mixing of the cold and hot parts of the fluid.

1 shows a first embodiment of a cross flow heat exchanger having increased heat transfer efficiency in accordance with the present invention, wherein a circular array of axially arranged heat exchange conduits is disposed within the fluid flow restricting ring;

FIG. 2A shows a second embodiment of a cross flow heat exchanger having increased heat transfer efficiency in accordance with the present invention, showing a circular array of heat exchange conduits arranged axially, each surrounded by concentric, fluid-limiting tubular sleeves. Schematic top view showing various fluid flow restricted sleeves coupled within a first ring-shaped structure.

2B is a side view of one conduit-sleeve combination showing an alternatingly arranged slot structure.

3 is a schematic top view of a variant embodiment of the FIG. 2 structure showing heat exchange conduits of a dual concentric array of radially contiguous conduits such that the fluid flow restriction holes of each flow restricting sleeve are radially aligned;

4 shows another embodiment of a cross flow heat exchanger having increased heat transfer efficiency in accordance with the present invention, wherein the heat exchange conduits arranged in a double row in an axial direction are arranged in a square array and include a first upstream fluid flow restriction baffle; A second intermediate fluid flow restricting baffle separating the conduits in the first and second rows, and a third downstream fluid flow restricting baffle following the conduits in the second row, the openings of the first, second and third baffles being Schematic top view showing alignment with each conduit and counterpart.

5 is an explanatory view showing another embodiment of an improved cross-flow heat transfer apparatus according to the present invention showing a multi-row (more than three rows) heat exchange conduit array arranged in a triangular form and showing two different fluid flow paths through the array; .

FIG. 6 is an explanatory view showing another embodiment of an improved cross-flow heat transfer apparatus according to the present invention showing a multi-row (more than three rows) heat exchange conduit array arranged in a rectangular shape and showing two different fluid flow paths through the array; .                 

Figure 7 is another embodiment of the improved cross-flow heat transfer apparatus according to the present invention showing that one plate or a plurality of plates can be arranged side by side on each side of each heat exchange conduit such that cross flow fluid flow is made to improve heat transfer characteristics. Illustrated diagram showing.

FIG. 8 is another structure configured by placing a curved plate having a contour corresponding to both sides of a conduit around each side of each heat exchange conduit such that one plate or multiple plates undergo a cross flow fluid flow to enhance heat transfer characteristics. Explanatory drawing showing another embodiment of the improved cross-flow heat transfer apparatus which concerns on the shape of the sleeve structure.

1 shows an axially arranged heat exchange conduit 12 arranged circularly inside an annular region 28 defined by a cylindrical inner wall 20 and a cylindrical outer wall 22, each having a common center point 14. A crossflow heat exchanger 10 according to the present invention having a circular array of is shown. As shown in FIG. 1, the conduits 12 have the same diameter less than the radial width of the annular region and are spaced apart from each other.

The upstream through-hole 24 is formed in the inner wall 20 in the radial direction corresponding to each heat exchange conduit 12, and the downstream through-hole 26 is formed in the outer wall 22. As shown in FIG. As shown in FIG. 1, each pair of upstream throughholes 24 and downstream throughholes 26 are radially aligned with respect to the corresponding conduit 12 and the counterpart. As such, in FIG. 1, the process fluid 30 flows axially toward the cylindrical inner region 16 of the heat exchanger 10 and is directed radially outward through the upstream through-hole 24 and then in fluid flow in FIG. 1. By contacting the heat exchange conduit 12 and flowing in an orthogonal direction as shown by the arrows, the process fluid flow is heated or cooled to form a heat regulated fluid flow 32 which is a downstream through-hole. Out of the annular region 28 through 26.

Although FIG. 1 shows a radially outflowing fluid flow path, the apparatus thermally processes the process fluid flow flowing radially inward toward the central region 16 and then axially flowing out of this region 16. It will be appreciated that it may be used. In such a case, the through hole 26 of the outer wall 22 will be an upstream hole and the through hole of the inner wall 20 will be a downstream hole.

만큼 방사상 라인에서 약간 벗어나 있다. 도 2b는 교열형의 슬로트구조를 보이는 원통형 슬리이브(120)를 갖는 열교환 도관(112)을 도 2a의 2B-2B선 방향에서 본 것이다. 도 2a에서 보인 바와 같은 이러한 교열형 슬로트 도관/슬리이브 조합의 평면도는 도 2b의 2A-2A선 방향에서 본 것이다. 교대로 어긋나게 배열된 슬로트 쌍으로부터 슬로트의 단부는 약간 중첩되거나 동일한 선상에 놓여 열교환장치의 축방향을 따라 유동하는 것을 방해하지 않게 되어 있다. 또한 이러한 오프셋트 슬로트의 분리 및 중첩 구조는 유체유동을 차단함이 없이 보다 양호한 주연방향의 기계적인 완벽성을 슬리이브(120)에 제공할 수 있도록 도 2b에서 부호 190으로 보인 인접한 오프셋트 슬로트의 축방향 중첩부분사이의 연결영역을 남긴다. 설명을 간단히 하기 위하여 도 2a는 두쌍의 오프셋트 통공구조를 갖는 하나의 천공형 슬리이브(120)를 보이고 있는 반면에 다른 슬리이브들은 한쌍의 정렬된 통공구조를 갖는다. 그러나, 실제로 본 발명의 장치(110)를 위한 모든 천공형 슬리이브는 전형적으로 동일한 통공구조를 갖는다.2A and 2B show perforated sleeves having an upstream aperture 124 and a downstream aperture 126 or offset aperture pairs 174, 176, 184, 186 arranged alternately with each other as described in detail below. A cross flow heat exchanger 110 according to the present invention is shown, each enclosed by 120 and having a circular array of axially arranged heat exchange conduits 112 arranged in a circle. Each sleeve 120 is coupled by a connecting wall 122 in a large ring or cylindrical structure. The through holes 124 and 126 consist of columns of axial through holes, e.g., elongated slots, aligned radially with respect to the conduit 112. Alternatively, in the preferred embodiment, which is partially shown in FIG. 2A, the aperture pairs 174, 176, 184, 186 are offset slightly offset in a radially aligned state with alternating slotted structures. The alternating slot structure of the pair of through holes 174, 176 (184, 186) is shown in FIG. 2A and is shown in detail in FIG. 2B, with misaligned offset pairs of through holes 174, 176 (184, 186). (Instead of through holes 124 and 126) are aligned from the front and angled from the center point 114

As long as it is slightly off the radial line. FIG. 2B shows a heat exchange conduit 112 having a cylindrical sleeve 120 showing an alternating slotted structure in the direction of 2B-2B in FIG. 2A. A plan view of such an articulated slotted conduit / sleeve combination as shown in FIG. 2A is seen from line 2A-2A in FIG. 2B. Ends of the slots from alternating pairs of slots are arranged slightly above or on the same line so as not to prevent flow along the axial direction of the heat exchanger. The separation and overlapping structure of these offset slots also allows adjacent offset slots, shown at 190 in FIG. 2B to provide the sleeve 120 with better peripheral mechanical integrity without blocking fluid flow. It leaves a connection between the axial overlap of the tracks. 2A shows one perforated sleeve 120 with two pairs of offset through structures, while the other sleeves have a pair of aligned through structures. In practice, however, all perforated sleeves for the device 110 of the present invention typically have the same aperture structure.

As such, in FIG. 2A, the process fluid 130 flows axially toward the cylindrical inner region 116 having the center point 114 of the heat exchanger 110 and radially outwards through the upstream aperture 124. Heat regulated fluid flow that flows and then flows orthogonally in contact with the heat exchange conduit 112 as shown by the arrows in FIG. 2A, leaving the interior region defined by the sleeve 120 through the downstream aperture 126. 132 is formed to heat or cool the process fluid flow. In embodiments with an orthogonal slot, the radially outflowing fluid flows through the upstream through hole 174 to contact the conduit 112 and flows out through the downstream through hole 176 or at an axial height. Thus it will flow through the pair of through holes 184, 186.

While FIG. 2A shows a radially outflowing fluid flow path, the device thermally processes the process fluid flow flowing radially inward toward the central zone 116 and then axially exiting the zone 116. It will be appreciated that it may be used. In this variant, the aperture 126 (or 176 and 186) will be an upstream aperture and the aperture 124 (or 174 and 184) will be a downstream aperture.

3 shows a cross flow heat exchanger 160 which is a variation of the cross flow heat exchanger 110 shown in FIG. 2. The device 160 differs from the device 110 in that it uses heat exchange conduits of dual concentric circular arrays instead of the single circular array of FIG. 2. As shown in FIG. 3, the heat exchange conduits 142 of the second circular array are radially aligned with respect to the conduits 112 of the first circular array. Each conduit 142 is surrounded by a perforated sleeve 150 having an upstream through hole 164 and a downstream through hole 166. The through holes 164 and 166 of the sleeve 150 coupled to the conduit 142 are radially aligned with the through holes 124 and 126 formed in the sleeve 120 of the radially adjacent conduit 112. Is shown. Each sleeve 150 is joined by a wall 152 into a large ring or cylindrical structure. Although FIG. 3 shows only one conduit 142 of the heat exchange conduit of the second circular array, it will be appreciated that the conduit 142 of the second circular array is coupled to all conduits 112 of the first circular array.

As such, in FIG. 3, the partially heat regulated process fluid flow 132 flowing out of the first downstream aperture 126 of the sleeve 120 is radially outwardly through the second upstream aperture 164. And flows orthogonally in contact with the heat exchange conduit 142 to form a sufficiently heat-regulated fluid flow 162 through the downstream through hole 166 that is beyond the interior region defined by the sleeve 150. The stream is heated or cooled. While FIG. 3 shows a radially flowing fluid flow path, the device thermally processes the process fluid flow flowing radially inward toward the central region 116 and then axially exiting the region 116. It will be appreciated that it may be used. In this variant, the apertures 166 and 126 will be the first and second upstream apertures and the apertures 164 and 124 will be the first and second downstream apertures.

4 shows a part of another cross-flow heat exchanger 210 according to the present invention. In FIG. 4, an upstream first perforated plate 220 having an aperture 226 is an axially arranged double row heat exchange conduit consisting of conduits 212 in an upstream first row and conduits 216 in a downstream second row. In a rectangular array with an intermediate second perforated plate 222 having a through hole 228 and separating the first and second rows of conduits and a downstream third perforated plate with a through hole 230. Is placed. Each set of through holes 226, 228, 230 corresponding to the upstream-downstream adjacent pair of conduits 212, 216 are linearly aligned with each other and the upstream and downstream conduits 212, 216. Are arranged according to).

As such, in FIG. 4, the process fluid 232 flows orthogonally in contact with the first upstream heat exchange conduit 212 through the aperture 226 as shown by the arrows, where the process fluid flow is partially. Heated or cooled to form a partially heat regulated fluid flow 234. The fluid flow 234 flows in an orthogonal direction through the through hole 228 in contact with the second downstream heat exchange conduit 216, where the process fluid flow is further heated or cooled to heat the entire fluid. It forms a flow 234 that flows out of the device 210 through the aperture 230.

5 shows a cross-flow heat exchanger 310 of another embodiment in accordance with the present invention, showing two types of flow paths through a multi-row set of heat exchange conduits 312 arranged in an offset or triangular array. In this FIG. 5, the heat exchange conduits of alternating rows are offset from adjacent rows rather than in a straight line, as shown in FIGS. 4 and 6. In this configuration, the center points of three adjacent conduits in two adjacent rows form an equilateral triangle 340. Although not shown in FIG. 5, the apparatus of FIG. 5 includes upstream and downstream perforated plates disposed respectively in front of the first row conduit and behind the last row of conduits, and an intermediate perforated plate separating the conduits in adjacent rows. Include. In addition, each conduit 312 may be surrounded by a perforated sleeve as already mentioned in the other figures.

Arrow 332 in FIG. 5 indicates the direction of the first flow path that can be used in the triangular conduit array of device 310. Arrow 334 in FIG. 5 indicates the direction of the second flow path that may be used in the triangular conduit array of device 310. Although FIG. 5 shows four rows of heat exchange conduits in a triangular array, fewer or more rows of conduits may be suitably used in this configuration.

6 shows two types of flow paths through a multi-row set of heat exchange conduits 412 arranged in a square array in accordance with another embodiment of a cross flow heat exchanger 410 according to the present invention. In this FIG. 6, heat exchange conduits 412 in adjacent rows are aligned in a straight line. In this configuration, the center points of four adjacent conduits in two adjacent rows form a square 440. Although not shown in FIG. 6, the apparatus of FIG. 6 includes upstream and downstream perforated plates disposed respectively in front of the first row conduit and behind the last row of conduits, and an intermediate perforated plate separating the conduits in adjacent rows. Include. In addition, each conduit 412 may be surrounded by a perforated sleeve as already mentioned.

Arrow 432 in FIG. 6 indicates the direction of the first flow path that can be used in the rectangular conduit array of device 410. Arrow 434 in FIG. 6 indicates the direction of the second flow path that may be used in the rectangular conduit array of device 410. Although FIG. 6 shows five rows of heat exchange conduits in a rectangular array, fewer or more rows of conduits may be suitably used in this configuration.

7 shows an improved cross flow heat exchanger 510 in another variant embodiment in accordance with the present invention. In FIG. 7, each heat exchange conduit 512 has one or more lateral flow restriction plates 520 disposed side by side in such conduits 512 and directed perpendicular to the fluid flow direction as shown by arrows 530, 532. 522, 524, 526, and 528 are combined. Sides of the lateral flow restriction plates 520, 522, 524, 526, and 528 closest to the conduit 512 are conduit walls disposed one at each side of these flow restriction plates and on each side of each conduit 512. There is a constant distance from the outer wall of the conduit 512 to form two fluid openings or channels therebetween. The gap between the edge of the flow restrictor and the conduit wall can be adjusted through a path test to optimize the fluid flow path to maximize heat transfer. If more than one lateral flow restriction plate is used for each conduit 512, the spacing between the edge of the flow restriction plate and the conduit wall may be the same or different to optimally form the fluid flow path.

As shown in FIG. 7, the lateral flow restriction plate is disposed side by side in conduit 512 (such as flow restriction plate 524) or the flow restriction plate so that the plane of the flow restriction plate passes through the center of conduit 512. To cross the conduit 512 either upstream of the plane center 518 (such as flow restriction 520 and 526) or downstream of center 518 (such as flow restriction 522 and 528) or in a combination thereof. Can be arranged. The distance 542 between the aperture and the conduit center 518 is less than one-half of the diameter 544 as shown and, for example, in the flow restriction plate 524 this distance is nearly zero. This is different from the baffle structure shown in FIGS. 1 and 4 where the distance between the through hole and the conduit center is at least 1/2 of the conduit diameter. As used herein, the phrase "lateral flow restriction plate disposed side by side in a heat exchange conduit" refers to the flow restriction plates 520, 522, 524, 526, 528 of FIG. 7 perpendicular to the direction of fluid flow. The planes of these plates intersect at any part of the heat exchange conduit.

Figure 8 shows another variant of the improved cross-flow heat exchanger 610 according to the present invention showing a variant of the perforated sleeve structure of Figure 2. In FIG. 8, each heat exchange conduit 612 is partially surrounded by a pair of opposed curved plates 620 with the curvature of the outer wall of the conduit 612 in a shell structure. Each curved plate 620 is coupled to a wall or side plate 622 disposed at right angles to the fluid flow direction as shown by arrows 630 and 632.

The pair of curved plates 620 around both sides of the conduit 612 are not in contact with each other nor extend upstream or downstream of the outer wall of the conduit 612. Thus, as shown for illustration in FIG. 8, a line or plane connecting the upstream or downstream sides of the pair of curved plates 620 will intersect the conduit 612. The upstream and downstream openings between the pair of curved plates 620 form a through hole through which the process fluid flow flows. The distance 642 between the aperture and the conduit center 618 is less than one half of the diameter 644 as shown and this distance is, for example, the length of the curved plate 620 as shown in FIG. ) To zero. This is different from the baffle structure shown in FIGS. 1 and 4 where the distance between the through hole and the conduit center is at least 1/2 of the conduit diameter.

The clamshell structure of FIG. 8 having each pair of curved plates 620 around each side of each conduit 612 has a slaw shown in FIG. 2A with a line or plane connecting the edges of the upstream and downstream fluid openings in FIG. 8. Unlike the slotted sleeve, the crossover of conduit 612 differs from the slotted sleeve structure of FIG. 2. In this regard, the embodiment of FIG. 8 may be considered an extreme variant of the embodiment of FIG. 7, as shown in FIG. 7, where each side plate disposed side by side in the heat exchange conduit is not spaced apart, instead of the conduit. The side edge portions are disposed to face each other to form the curved plate 620 of FIG. 8.

It will be appreciated by those skilled in the art that other changes and modifications can be made in the apparatus and method for improving cross-flow heat transfer mentioned above without departing from the scope of the invention, all of which are to be understood by the present invention. This is intended to be a measure of the nature and not of any limitation.

Claims (82)

delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete A fluid flow forming apparatus for forming a flow path of a process fluid flowing in an orthogonal direction in contact with a plurality of spaced heat transfer surfaces, the apparatus comprising a plurality of sleeve-type baffle structures continuous in a longitudinal direction, and And at least one set of pairs of fluid flow through holes for allowing fluid to pass from the upstream side to the downstream side through the fluid flow forming apparatus. 40. A fluid flow forming apparatus according to claim 39, wherein said heat transfer surface consists of an array of cylindrical heat exchange conduits arranged to have parallel axes. 41. The apparatus of claim 40, wherein each baffle structure is comprised of a sleeve-like element concentric in a heat exchange conduit. 42. A fluid flow forming apparatus according to claim 41, wherein said set pair of fluid flow holes consist of upstream and downstream holes of said sleeve-like element. 40. The fluid flow forming apparatus of claim 39, wherein two or more of the baffle structures are connected in series to allow fluid flow from the upstream through the plurality of heat transfer surfaces to the downstream through. 41. The device of claim 40, wherein the heat exchange conduits are arranged in a circular array. 45. The fluid of claim 44, wherein each baffle structure corresponding to the heat exchange conduit is connected in series to allow fluid flow from the upstream through the plurality of heat transfer surfaces to the downstream through. Flow forming device. 46. A fluid flow forming apparatus according to claim 45, wherein the pair of through holes for fluid flow is composed of upstream and downstream through holes arranged radially of each baffle structure. 46. A fluid flow forming apparatus according to claim 45, wherein the pair of through holes for allowing fluid flow is comprised of upstream and downstream through holes of each baffle structure offset from the radial line. 40. The concentric perforated sleeved structure of claim 39, wherein the heat transfer surface consists of a circular array of one or more heat exchange conduits, a portion of which has columns upstream and downstream through-hole pairs in a column parallel to the axis of the conduit. And fluidly formed by a plate-shaped baffle structure adjacent to the sleeve-type structure to form a large cylindrical structure. 49. An apparatus according to claim 48, wherein the pair of through holes consists of elongated slots, the major axis of each slot being parallel to the axis of the heat exchange conduit. 50. The apparatus of claim 49, wherein the pair of elongated slots are radially aligned. 50. The fluid flow formation of claim 49, wherein one heat exchange conduit is aligned with respect to two pairs of elongated slots, each pair of slots being offset from an axial and radial alignment of the large cylindrical structural plate. Device. 52. The fluid flow of claim 51, wherein two upstream and two downstream elongated slots corresponding to the heat exchange conduits are axially offset from each other and each upstream and downstream slot pair is axially aligned. Forming device. 49. A fluid flow forming apparatus according to claim 48, wherein the heat transfer surface is composed of a circular array of two or more heat exchange conduits arranged to have parallel axes, and the one side array is concentric with the other array. 55. A fluid flow forming apparatus according to claim 53, wherein the pair of apertures consists of elongated slots radially aligned, wherein the major axis of each slot is parallel to the axis of the heat exchange conduit. 54. The method of claim 53, wherein the baffle structures of the radially aligned adjacent pair of heat exchange conduits are connected such that the apertures between the baffle structures act as downstream fluid flow holes for one conduit and upstream fluid flow holes for the other conduit. Fluid flow forming apparatus. 56. The fluid flow forming apparatus of claim 55, wherein the pair of apertures consists of elongated slots radially aligned, the major axis of each slot being parallel to the axis of the heat exchange conduit. 40. The system of claim 39, wherein the heat transfer surface consists of a rectangular array of cylindrical heat exchange conduits of three or more axially aligned rows arranged to have parallel axes, the baffle structure having upstream and downstream aperture pairs. A fluid flow forming apparatus comprising concentric sleeve-like elements. 40. The axis of claim 39, wherein the heat transfer surface is comprised of a rectangular array of three or more rows of cylindrical heat exchange conduits, the alternating rows being axially offset from adjacent upstream and downstream rows, wherein the heat exchange conduits are parallel. And a baffle structure composed of concentric circular sleeve-like elements having upstream and downstream through-hole pairs. 40. The plate baffle structure of claim 39, wherein the baffle structure corresponding to the heat transfer surface comprises a set of plate-shaped baffle structures in which side edges are arranged in pairs on two sides of the heat transfer surface in close proximity without contact with the heat transfer surface. And a plane of which is disposed at right angles to the flow path of the process fluid to define an annular fluid flow region having upstream and downstream through-hole pairs around the heat transfer surface. 40. The plate-shaped baffle structure of claim 39, wherein the baffle structure corresponding to the heat transfer surface comprises a curved plate-shaped baffle structure in which side edges are arranged in pairs on two sides of the heat transfer surface in close proximity without contact with the heat transfer surface. The plate-shaped baffle structure has a contour corresponding to both sides of the heat transfer surface to define an annular fluid flow region having upstream and downstream through-hole pairs around the heat transfer surface, and the plate-shaped baffle structure corresponds to an adjacent heat transfer surface. Fluid flow forming apparatus, characterized in that coupled to the baffle structure. A method for improving heat transfer to fluids flowing in an orthogonal direction in contact with outer surfaces of a plurality of heat exchange conduits, the method comprising: a fluid around adjacent heat transfer surfaces surrounding each heat transfer surface and disposed transverse to the fluid flow direction Allowing fluid flow across the heat transfer surface by flowing fluid through one or more pairs of baffle structures that isolate the fluid flow around the heat transfer surface from the flow, wherein the baffle structure is directed to the other side and to the thermoelectric. Symmetrically disposed on each of the upstream and downstream sides of the heat transfer surface so as to be partially aligned upstream and downstream with respect to the lunar surface, wherein the baffle structure has a uniform fluid flow pattern around the contour of the heat transfer surface. A method for improving heat transfer, characterized by forming a flow path. 62. The method of claim 61, wherein the heat transfer surface consists of an array of cylindrical heat exchange conduits arranged to have parallel axes. 63. The method of claim 62 wherein each baffle structure is comprised of a sleeve-like element concentric in a heat exchange conduit. 64. The method of claim 63, wherein said set pair of fluid flow through holes is comprised of upstream and downstream through holes of said sleeved element. 62. The method of claim 61, wherein two or more of the baffle structures are connected in series to allow fluid flow from the upstream through the plurality of heat transfer surfaces to the downstream through. 64. The method of claim 63 wherein the heat exchange conduits are arranged in a circular array. 67. The method of claim 66, wherein each baffle structure corresponding to the heat exchange conduit is connected in series to allow fluid flow to flow from the upstream through the plurality of heat transfer surfaces around the downstream through hole. How to improve. 67. The method of claim 67, wherein the pair of through holes for fluid flow is comprised of radially aligned upstream and downstream through holes of each baffle structure. 68. The method of claim 67, wherein the pair of through holes for fluid flow is comprised of upstream and downstream through holes of each baffle structure offset from the radial line. 62. The concentric cylindrical sleeved structure of claim 61, wherein the heat transfer surface consists of a circular array of one or more heat exchange conduits, the portion of which has a column upstream and downstream through-hole pairs parallel to the axis of the conduit. And partially enclosed by the plate-type baffle structure to the adjacent sleeve-type structure to form a large cylindrical structure. 71. The method of claim 70, wherein the pair of apertures consists of elongated slots, the major axis of each slot being parallel to the axis of the heat exchange conduit. 72. The method of claim 71 wherein the pair of elongated slots are radially aligned. 72. The method of claim 71 wherein one heat exchange conduit is aligned with respect to two pairs of elongated slots, each slot pair being offset from being aligned radially with the axis of the large cylindrical structural plate. . 74. The heat transfer enhancement of claim 73 wherein two upstream and two downstream slots corresponding to the heat exchange conduit are axially offset from each other and each upstream and downstream slot pair is axially aligned. Way. 71. The method of claim 70 wherein said heat transfer surfaces comprise circular arrays of two or more heat exchange conduits arranged so as to have parallel axes, and wherein one array is concentric with respect to the other array. 76. The method of claim 75, wherein the pair of apertures consists of elongated slots radially aligned, wherein the major axis of each slot is parallel to the axis of the heat exchange conduit. 76. The method of claim 75, wherein the baffle structures of the radially aligned adjacent pair of heat exchange conduits are connected such that the apertures between the baffle structures act as downstream fluid flow holes for one conduit and upstream fluid flow holes for the other conduit. Heat transfer improvement method. 78. The method of claim 77 wherein the pair of apertures consists of elongated slots radially aligned, wherein the major axis of each slot is parallel to the axis of the heat exchange conduit. 62. The system of claim 61, wherein the heat transfer surface consists of a rectangular array of cylindrical heat exchange conduits of three or more axially aligned rows arranged to have parallel axes, the baffle structure having upstream and downstream aperture pairs. A method of improving heat transfer, characterized by consisting of concentric sleeve-like elements. 64. The axis of claim 62, wherein the heat transfer surface is comprised of a rectangular array of three or more rows of cylindrical heat exchange conduits, the alternating rows being axially offset from adjacent upstream and downstream rows, the heat exchange conduits being parallel. And a baffle structure composed of concentric circular sleeve-like elements having upstream and downstream through-hole pairs. 62. The plate-shaped baffle structure of Claim 61, wherein the baffle structure corresponding to the heat transfer surface comprises a set of plate-shaped baffle structures in which side edges are arranged in pairs on two sides of the heat transfer surface in close proximity without contact with the heat transfer surface. And a plane of the at least one annular fluid flow region having upstream and downstream through-hole pairs around the heat transfer surface at right angles to the flow path of the process fluid. 62. The plate-shaped baffle structure of claim 61, wherein the baffle structure corresponding to the heat transfer surface comprises a curved plate-shaped baffle structure in which side edges are arranged in pairs on two sides of the heat transfer surface in close proximity without contact with the heat transfer surface. The plate-shaped baffle structure has a contour corresponding to both sides of the heat transfer surface to define an annular fluid flow region having upstream and downstream through-hole pairs around the heat transfer surface, and the plate-shaped baffle structure corresponds to an adjacent heat transfer surface. The heat transfer improvement method characterized in that coupled to the baffle structure.

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